EP3272511B1 - Hydraulic drive device - Google Patents

Hydraulic drive device 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
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EP17181834.7A
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German (de)
French (fr)
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EP3272511A1 (en
Inventor
Roland Menzel
Martin Rossi
Max Hälterlein
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DORST Technologies GmbH and Co KG
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DORST Technologies GmbH and Co KG
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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.

Description

Die Erfindung betrifft eine hydraulische Antriebseinrichtung mit einem Presszylinder für eine hydraulische Presse, vorzugsweise Pulverpresse, nach Anspruch 1 sowie eine hydraulische Presse, vorzugsweise Pulverpresse und ein Verfahren zum Pressen eines Pressteils, insbesondere zum Pulverpressen eines Pulverpressteils. Insbesondere betrifft die vorliegende Erfindung eine hydraulische Presse bzw. ein entsprechendes Verfahren und eine entsprechende Antriebseinrichtung, die für eine (maximale) Presskraft von über 500 kN, insbesondere über 1000 kN, vorzugsweise über 1500 kN ausgelegt sind.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. In particular, 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.

Zentrales Bauteil von hydraulischen Pressen sind Presszylinder, die verschiedene Funktionen erfüllen. Einerseits werden solche Presszylinder zum Öffnen und Schließen eines Presswerkzeugs der hydraulischen Presse mit einer hohen Geschwindigkeit (Eilgang) genutzt. Andererseits wird über solche Presszylinder eine hohe Kraft in Schließrichtung (bei geringer Geschwindigkeit) aufgebaut. Die hohen zum Pressen benötigten Schließkräfte erfordern eine entsprechend große Kolbenfläche zur Erzeugung einer maximalen Presskraft bei einem vorbestimmten Maximaldruck. Bei einer großen Kolbenfläche ergeben sich entsprechend hohe Volumenströme, so dass im Stand der Technik vergleichsweise groß bauende bzw. dimensionierte Pumpen und Ventile benötigt werden. Zur Vermeidung von übergroßen hydraulischen Antriebs- und Steuerelementen werden im Stand der Technik die Eilgang- und Pressenfunktion getrennt. Das heißt, es werden Zylindereinheiten mit einer großen Fläche für die Schließkraft sowie mit einer kleinen Fläche für die vergleichsweise schnellen und "kraftlosen" Öffnungs- und Schließbewegungen verwendet. Derartige Presszylinder können mit integriertem oder mit getrenntem Eilgangzylinder ausgestattet sein. Bei bestimmten Lösungen werden Schließzylinderkolben während der Eilgangbewegung mitgezogen. Die Zufuhr der Hydraulikflüssigkeit (Ölzufuhr) kann separat aus einem Behälter gespeist werden ("Nachsaugbetrieb"). Alternativ können Kolben- und Ringraum mittels eines hydraulischen Schaltventils zyklisch verbunden werden ("Umspülung").The central component of hydraulic presses are press cylinders that fulfill various functions. On the one hand, such press cylinders are used to open and close a press tool of the hydraulic press at high speed (rapid traverse). On the other hand, a high force in the closing direction (at low speed) 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. To avoid oversized hydraulic drive and control elements, the rapid traverse and press functions are separated in the prior art. That is, there will be cylinder units with a large area for the clamping force as well as with a small area used for the comparatively quick and "powerless" opening and closing movements. Such press cylinders can be equipped with an integrated or with a separate rapid traverse cylinder. With certain solutions, lock cylinder pistons are pulled along during the rapid traverse movement. The supply of hydraulic fluid (oil supply) can be fed separately from a container ("suction operation"). Alternatively, the piston and annulus can be cyclically connected by means of a hydraulic switching valve ("flushing").

Derartige Lösungen sind sowohl hinsichtlich des Aufwandes für die Herstellung (insbesondere die Zylinderbauweise) als auch hinsichtlich des steuerungstechnischen Aufwandes (insbesondere betreffend die Hydraulikansteuerung) vergleichsweise komplex und daher mit hohen Kosten verbunden.Such solutions are comparatively complex both in terms of the effort involved in production (in particular the cylinder design) and in terms of the outlay in terms of control technology (in particular with regard to the hydraulic control) and are therefore associated with high costs.

Es ist daher Aufgabe der Erfindung, eine hydraulische Antriebseinrichtung, eine hydraulische Presse sowie ein Verfahren zum Pressen eines Pressteils vorzuschlagen, wobei der konstruktive Aufwand und insbesondere auch der verfahrenstechnische Aufwand reduziert sein sollen.It is therefore the object of the invention to propose a hydraulic drive device, a hydraulic press and a method for pressing a pressed part, the design effort and, in particular, also the procedural effort being reduced.

Diese Aufgabe wird durch die Merkmale des Anspruchs 1 gelöst.This object is achieved by the features of claim 1.

Insbesondere wird die Aufgabe durch eine hydraulische Antriebseinrichtung mit einem Presszylinder für eine hydraulische Presse, vorzugsweise Pulverpresse, gelöst, wobei die hydraulische Antriebseinrichtung konfiguriert ist, um einen Zylinderkolben in einem Vorwärts-Eilgang mit erhöhter Geschwindigkeit zu einem Pressteil hinzuführen und in einem Pressgang mit niedriger Geschwindigkeit das Pressteil zu pressen, wobei der Presszylinder einen Zylinderkolben aufweist, der einen Kolbenraum und einen Stangenraum definiert, wobei eine Pumpeneinrichtung zur Bereitstellung eines Volumenstroms einer Hydraulikflüssigkeit in den Kolbenraum, so dass der Pressraum durchlaufen wird, vorgesehen ist, wobei eine hydraulische Speichereinrichtung zur Bereitstellung zumindest eines Teiles, insbesondere eines überwiegenden Teiles, eines Volumenstroms der Hydraulikflüssigkeit in den Kolbenraum, so dass der Vorwärts-Eilgang durchlaufen wird, und zwar unter Verzicht auf einen zusätzlichen Eilgang-Zylinder zur Realisierung des Eilgangs, vorgesehen ist, wobei Kolbenraum und Stangenraum über eine Fluidverbindung verbunden oder verbindbar sind, wobei innerhalb dieser Fluidverbindung die Pumpeneinrichtung und die hydraulische Speichereinrichtung, zueinander fluidtechnisch parallel geschalt, angeordnet sind, wobei ein mit dem Kolbenraum verbundener erster Fluidverbindungsabschnitt mit einer ersten Verzweigungsstelle verbunden ist, von der eine zweiter Fluidverbindungsabschnitt in Richtung Pumpeneinrichtung abzweigt und ein dritter Fluidverbindungsabschnitt in Richtung hydraulischer Speichereinrichtung abzweigt, wobei ein mit dem Stangenraum verbundener vierter Fluidverbindungsabschnitt mit einer zweiten Verzweigungsstelle verbunden ist, von der ein fünfter Fluidverbindungsabschnitt in Richtung Pumpeneinrichtung abzweigt und ein sechster Fluidverbindungsabschnitt in Richtung hydraulischer Speichereinrichtung abzweigt.In particular, the object is achieved by 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, wherein the press cylinder has a cylinder piston which defines a piston chamber and a rod chamber, wherein 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, with 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 having a first branch point is connected, 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, wherein a fourth fluid connection section connected to the rod space is connected to a second branch point, from which a fifth fluid connection section in the direction Pump device branches off and a sixth fluid connection section branches off in the direction of the hydraulic storage device.

Ein zentraler Gedanke der Erfindung liegt darin, eine hydraulische Speichereinrichtung bereitzustellen und insgesamt die hydraulische Antriebseinrichtung so zu konfigurieren, dass über diese hydraulische Speichereinrichtung zumindest ein erheblicher (insbesondere überwiegender) Teil des vergleichsweise großen Volumenstroms, der im Vorwärts-Eilgang benötigt wird, bereitgestellt wird. Unter einem "überwiegenden Teil" ist ein Anteil von mindestens 50% zu verstehen. Der Anteil kann aber vorzugsweise auch mindestens 70% oder weiter vorzugsweise mindestens 90% betragen. Die hydraulische Speichereinrichtung ist eine Einrichtung zur Speicherung der Hydraulikflüssigkeit unter Druck (auf beispielsweise mindestens 10 bar oder mindestens 30 bar oder mindestens 35 bar). Weiterhin kann die hydraulische Speichereinrichtung entladen werden und dadurch einen Volumenstrom der Hydraulikflüssigkeit abgeben. Bei der hydraulischen Speichereinrichtung kann es sich insbesondere um eine hydraulische Speichereinrichtung mit Gasspannvorrichtung handeln.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.

Insofern kann die hydraulische Speichereinrichtung einen (Druck-) Behälter umfassen. Weiterhin kann die hydraulische Speichereinrichtung ein bewegliches Element (beispielsweise einen beweglichen Kolben) zur Trennung von Hydraulikflüssigkeit und einem (unter Druck stehenden) Gas aufweisen. Die Hydraulikflüssigkeit kann dann gegen den Druck des Gases in die hydraulische Speichereinrichtung (insbesondere den Behälter) gepresst werden.In this respect, the hydraulic storage device can comprise a (pressure) container. Furthermore, 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.

Durch die hydraulische Speichereinrichtung kann auf einen zusätzlichen Presszylinder zur Realisierung eines Eilgangs, wie im Stand der Technik, siehe zum Beispiel DE 10 2011 116964 A1 , üblicherweise vorgesehen, verzichtet werden. Dadurch wird die Antriebseinrichtung in struktureller Hinsicht erheblich vereinfacht, wodurch Kosten gesenkt werden können. Weiterhin vereinfacht sich auch die Steuerung, insbesondere Regelung, einer solchen Antriebseinrichtung, da ein zweiter Presszylinder (mit entsprechend zugeordneten Elementen, wie insbesondere einer Förderpumpe) verzichtet werden kann. Insbesondere kommt die hydraulische Antriebseinrichtung gemäß der Erfindung mit nur einer Pumpeneinrichtung aus. Insgesamt werden die Kosten (sowohl im Hinblick auf die Herstellung als auch den Betrieb bzw. die Wartung) erheblich reduziert.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. As a result, the drive device is considerably simplified in structural terms, as a result of which costs can be reduced. Furthermore, 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. In particular, 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.

Als Hydraulikflüssigkeit kommt insbesondere (Hydraulik-)ÖI in Frage.(Hydraulic) oil is particularly suitable as the hydraulic fluid.

Vorzugsweise ist die hydraulische Antriebseinrichtung konfiguriert, um den Zylinderkolben in einem Rückwärts-Eilgang mit erhöhter Geschwindigkeit von dem Pressteil wegzuführen, wobei ein im Rückwärts-Eilgang aus dem Kolbenraum austretender Volumenstrom der Hydraulikflüssigkeit zumindest teilweise, insbesondere überwiegend, in die hydraulische Speichereinrichtung transferiert wird. Die hydraulische Speichereinrichtung wird also bei dieser Weiterbildung gleichzeitig als Aufnahmebehälter für die (große) Menge an Hydraulikflüssigkeit verwendet, die beim Rückwärts-Eilgang aus dem Kolbenraum ausgeschoben wird. Gleichzeitig wird die hydraulische Speichereinrichtung dabei wieder beladen, so dass sie sich in einem nächsten Zyklus wieder (in einem darauffolgenden Vorwärts-Eilgang) entladen kann. Dadurch wird die Struktur und der Steuerungs- bzw. Regelungsaufwand weiter vereinfacht.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. In this development, 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. At the same time, 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.

Grundsätzlich kann die Geschwindigkeit im Vorwärts-Eilgang und/oder Rückwärts-Eilgang mindestens 1,5mal, weiter vorzugsweise mindestens 3mal, noch weiter vorzugsweise mindestens 4mal so hoch sein wie die Geschwindigkeit im Pressgang.In principle, 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.

In einer bevorzugten Ausführungsform kann der gesamte im Rückwärts-Eilgang aus dem Kolbenraum strömende Volumenstrom (ausschließlich) in Richtung hydraulische Speichereinrichtung und Pumpeneinrichtung geschoben werden.In a preferred embodiment, 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.

Im Rückwärts-Eilgang und/oder Vorwärts-Eilgang werden die jeweiligen Drücke im Kolbenraum sowie Stangenraum vorzugsweise so eingestellt, dass sich die auf den Kolben wirkenden Kräfte neutralisieren (zumindest im Wesentlichen; ggf. kann eine zumindest geringe Differenz zur Überwindung von Reibungskräften oder dergleichen vorliegen).In the reverse rapid traverse and / or forward rapid traverse, 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).

Vorzugsweise ist der Presszylinder ein Differentialzylinder. Ein Verhältnis der größeren Fläche zu der kleineren Fläche kann vorzugsweise mindestens 2, weiter vorzugsweise mindestens 5 betragen. Alternativ oder zusätzlich kann ein oberer Grenzwert für das genannte Verhältnis höchstens 20, weiter vorzugsweise höchstens 10 sein. Besonders bevorzugt ist ein Verhältnis von (etwa) 7. Bei einer derartigen Dimensionierung kann die hydraulische Antriebseinrichtung besonders effektiv betrieben werden.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. Alternatively or additionally, 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.

In einer konkreten Ausführungsform ist die hydraulische Antriebseinrichtung so konfiguriert, dass in einer ersten Kraftabbau-Phase der Kolbenraum mit der hydraulischen Speichereinrichtung, vorzugsweise über die Pumpeneinrichtung, verbindbar ist, derart, dass der Druck im Kolbenraum (von seinem Maximalwert) auf das Druckniveau der hydraulischen Speichereinrichtung abbaubar ist. Alternativ oder zusätzlich kann die hydraulische Antriebseinrichtung so konfiguriert sein, dass in einer zweiten Kraftabbau-Phase ein Druck im Stangenraum (vorzugsweise durch die Pumpeneinrichtung) erhöhbar ist. Die Speicher- und Pumpeneinrichtung werden hier also synergistisch genutzt, um einen kontrollierbaren und zuverlässigen Kraftabbau zu ermöglichen. Beschädigungen am zu pressenden Teil (Pressteil) können damit verhindert werden (oder sind zumindest weniger wahrscheinlich).In a specific embodiment, 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. Alternatively or additionally, 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).

Kolbenraum und Stangenraum können über eine Fluidverbindung verbunden oder verbindbar sein. Innerhalb dieser Fluidverbindung können Pumpeneinrichtung und hydraulische Speichereinrichtung (insbesondere zueinander fluidtechnisch parallelgeschaltet) angeordnet sein. Ein mit dem Kolbenraum verbundener erster Fluidverbindungsabschnitt kann mit einer ersten Verzweigungsstelle (Verzweigungsstruktur) verbunden sein, von der ein zweiter Fluidverbindungsabschnitt in Richtung Pumpeneinrichtung abzweigt und ein dritter Fluidverbindungsabschnitt in Richtung hydraulischer Speichereinrichtung abzweigt. Ein mit dem Stangenraum verbundener vierter Fluidverbindungsabschnitt kann mit einer zweiten Verzweigungsstelle (Verzweigungsstruktur) verbunden sein, von der ein fünfter Fluidverbindungsabschnitt in Richtung Pumpeneinrichtung abzweigt und ein sechster Fluidverbindungsabschnitt in Richtung hydraulischer Speichereinrichtung abzweigt. Besonders bevorzugt ist in dem fünften Fluidverbindungsabschnitt eine erste Ventileinrichtung vorgesehen. Alternativ oder zusätzlich kann in dem sechsten Fluidverbindungsabschnitt eine zweite Ventileinrichtung vorgesehen. Parallel zu der zweiten Ventileinrichtung ist vorzugsweise ein (Rückschlag-) Ventil fluidtechnisch geschaltet. Durch die genannten Ventile bzw. Ventileinrichtungen kann mit geringem Aufwand ein jeweils gewünschter Volumenstrom erreicht werden. Der Aufwand in konstruktiver und steuerungstechnischer Hinsicht wird weiter vereinfacht.The piston chamber and the rod chamber can be connected or connectable via a fluid connection. Within this 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. Alternatively or additionally, 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. By means of the valves or valve devices mentioned, a desired volume flow can be achieved with little effort. The effort in terms of construction and control is further simplified.

In konkreten Ausführungsformen kann die Pumpeneinrichtung eine bidirektionale Pumpe, insbesondere eine 4-Quadrantenpumpe, und/oder einen Servomotor umfassen. Im Allgemeinen ist es bevorzugt, wenn die Pumpeneinrichtung ein bidirektionales Fördern der Hydraulikflüssigkeit ermöglicht. Beispielsweise kann dies auch dadurch realisiert werden, dass eine unidirektionale Pumpe (beispielsweise 1- oder 2-Quadrantenpumpe) bereitgestellt wird und entsprechende Ventile (Servoventile oder dergleichen) vorgesehen sind. In jedem Fall wird es dadurch ermöglicht, dass die Pumpeneinrichtung sowohl vom Kolbenraum zu dem Stangenraum hin fördern kann als auch umgekehrt. Dadurch wird auf einfache Art und Weise ein effizienter Betrieb der hydraulischen Antriebseinrichtung ermöglicht.In specific embodiments, the pump device can comprise a bidirectional pump, in particular a 4-quadrant pump, and / or a servomotor. In general, it is preferred if the pump device enables bidirectional delivery of the hydraulic fluid. For example, this can also be implemented in that a unidirectional pump (for example 1- or 2-quadrant pump) is provided and corresponding valves (servo valves or the like) are provided. In any case, this makes it possible for the pump device to be able to deliver both from the piston chamber to the rod chamber and vice versa. This enables efficient operation of the hydraulic drive device in a simple manner.

Eine Wirkfläche (also eine Fläche, die durch den Zylinderkolben definiert wird und in Kontakt mit der Hydraulikflüssigkeit steht) des Kolbenraums kann mindestens 200 cm2, vorzugsweise mindestens 450 cm2 und/oder höchstens 1100 cm2, vorzugsweise höchstens 700 cm2 betragen. Untere und obere Grenzwerte für die Wirkfläche des Stangenraums können den oberen Werten geteilt durch 7 entsprechen.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.

Ein Verhältnis einer Wirkfläche des Kolbenraums zu einer Wirkfläche des Stangenraums kann mindestens 3, vorzugsweise mindestens 6 betragen und/oder höchstens 15, vorzugsweise höchstens 9 betragen. Besonders bevorzugt beträgt dieses Verhältnis (etwa) 7. Bei einem derartigen Verhältnis kann ein effektives Antreiben und Steuern des Presszylinders ermöglicht werden.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.

Die hydraulische Speichereinrichtung kann ein Volumen von mindestens 10 l, vorzugsweise mindestens 30 l und/oder höchstens 100 l, vorzugsweise höchstens 70 l aufweisen. Besonders bevorzugt ist ein Volumen von (etwa) 50 l. In einem maximal beladenen Zustand kann das Volumen, das durch die Hydraulikflüssigkeit in der hydraulischen Speichereinrichtung eingenommen wird, mindestens 3 l, vorzugsweise mindestens 10 l und/oder höchstens 30 l, vorzugsweise höchstens 20 l betragen. Besonders bevorzugt beträgt dieses Volumen (etwa) 12 l.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. In a maximally loaded state, 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.

Die hydraulische Speichereinrichtung kann einen Basisdruck (also einen Druck ohne Beladung durch die Hydraulikflüssigkeit) von mindestens 10 bar, vorzugsweise mindestens 25 bar und/oder höchstens 80 bar, vorzugsweise höchstens 50 bar aufweisen. Besonders bevorzugt beträgt dieser Druck 30 bar. Im (maximal beladenen) Zustand kann der Druck innerhalb der hydraulischen Speichereinrichtung mindestens 12 bar, vorzugsweise mindestens 30 bar und/oder höchstens 100 bar, vorzugsweise höchstens 60 bar aufweisen. Besonders bevorzugt beträgt der Druck in diesem Fall (etwa) 40 bar.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. In the (maximally loaded) state, 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.

Der Stangenraum bildet vorzugsweise einen Ringraum aus, der durch eine Innenwandung des Presszylinders sowie eine durch den Stangenraum laufende Stange definiert wird. Ein Verhältnis zwischen Innendurchmesser des Presszylinders und Außendurchmesser der Stange kann beispielsweise mindestens 1,05; vorzugsweise mindestens 1,15 betragen und/oder höchstens 1,5; vorzugsweise höchstens 1,3.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.

In einer kombinierten Ausführungsform ist mindestens eine Steuereinrichtung, insbesondere Regeleinrichtung zur Steuerung, insbesondere Regelung, der einzelnen Komponenten der hydraulischen Antriebseinrichtung, vorgesehen. Dieser Steuereinrichtung (Regeleinrichtung) können entsprechende Sensoren (wie Drucksensoren und/oder Volumenstrom-Messeinrichtungen) zugeordnet sein, die beispielsweise eine Messgröße (Druck- und/oder Volumenstrom) an einem Anschluss (Aus- bzw. Eingang) des Kolbenraums und/oder einem Anschluss (Aus- bzw. Eingang) des Stangenraumes messen. Aus den gemessenen Größen (insbesondere Druck- und/oder Volumenstrom) können dann erforderliche Schaltvorgänge, insbesondere betreffend die oben beschriebenen ersten und zweiten Ventileinrichtungen durchgeführt werden und/oder die Pumpeneinrichtung entsprechend angesteuert (geregelt) werden.In a combined embodiment, 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 (such as pressure sensors and / or volume flow measuring devices) 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.

Die oben genannte Aufgabe wird weiterhin insbesondere durch eine hydraulische Presse, vorzugsweise Pulverpresse, umfassend eine hydraulische Antriebseinrichtung der oben beschriebenen Art, gelöst.The above-mentioned object is also achieved in particular by a hydraulic press, preferably a powder press, comprising a hydraulic drive device of the type described above.

Weiterhin wird die oben genannte Aufgabe insbesondere durch ein Verfahren gemäß Anspruch 11 zum Pressen eines Pressteils, insbesondere zum Pulverpressen eines Pulverpressteils, vorzugsweise unter Verwendung einer hydraulischen Antriebseinrichtung der oben beschriebenen Art und/oder einer hydraulischen Presse der oben beschriebenen Art, insbesondere hydraulischen Pulverpresse der oben beschriebenen Art, gelöst, wobei ein Zylinderkolben eines Presszylinders in einem Vorwärts-Eilgang mit erhöhter Geschwindigkeit zu einem Pressteil hingeführt wird und das Pressteil in einem Pressgang mit niedriger Geschwindigkeit des Zylinderkolbens gepresst wird, wobei im Pressgang über eine Pumpeneinrichtung ein Volumenstrom in einen Kolbenraum des Presszylinders gepumpt wird, wobei im Eilgang über eine hydraulische Speichereinrichtung zumindest ein Teil, insbesondere ein überwiegender Teil, eines Volumenstroms in den Kolbenraum bereitgestellt wird. Wenn hier (genauso wie weiter oben und im Folgenden) angegeben wird, dass ein Volumenstrom entweder von der Pumpeneinrichtung oder der hydraulischen Speichereinrichtung bereitgestellt wird, bedeutet dies insbesondere, dass der entsprechende Volumenstrom unmittelbar, d.h. bestenfalls über entsprechende Ventileinrichtungen in den Kolbenraum bzw. Stangenraum geführt oder von dort abgeleitet wird (also insbesondere nicht über die jeweilige andere Einrichtung). Beispielsweise soll eine Bereitstellung eines Volumenstroms über (oder durch) die hydraulische Speichereinrichtung bedeuten, dass der jeweilige Volumenstrom nicht über die Pumpe geführt wird. Umgekehrt soll eine Bereitstellung eines Volumenstroms durch die Pumpeneinrichtung bedeuten, dass der jeweilige Volumenstrom nicht zusätzlich noch über die hydraulische Speichereinrichtung geführt wird.Furthermore, 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. If it is stated here (just as above and below) that 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). For example, 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. Conversely, 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.

Der Zylinderkolben kann in einem Rückwärts-Eilgang mit erhöhter Geschwindigkeit von dem Pressteil weggeführt werden, wobei ein im Rückwärts-Eilgang aus dem Kolbenraum austretender Volumenstrom zumindest teilweise, insbesondere überwiegend, in die hydraulische Speichereinrichtung transferiert werden kann.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.

Vorzugsweise wird im Vorwärts-Eilgang ein Volumenstrom in den Kolbenraum teilweise aus dem Stangenraum, insbesondere über die Pumpeneinrichtung, bereitgestellt. Alternativ oder zusätzlich wird im Rückwärts-Eilgang der aus dem Kolbenraum austretende Volumenstrom teilweise in den Stangenraum, insbesondere über die Pumpeneinrichtung, transferiert. Alternativ oder zusätzlich wird in einer ersten Kraftabbau-Phase der Kolbenraum mit der hydraulischen Speichereinrichtung, vorzugsweise über die Pumpeneinrichtung, verbunden derart, dass der Druck im Kolbenraum auf das Druckniveau der hydraulischen Speichereinrichtung abgebaut wird. Alternativ oder zusätzlich wird in einer zweiten Kraftabbau-Phase ein Druck im Stangenraum vorzugsweise durch die Pumpeneinrichtung erhöht.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. As an alternative or in addition, the volume flow exiting the piston chamber is partially transferred into the rod chamber, in particular via the pump device, in reverse rapid traverse. Alternatively or additionally, in a first force reduction phase, the piston chamber 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. Alternatively or additionally, a pressure in the rod space is increased, preferably by the pump device, in a second force reduction phase.

Vorzugsweise wird in dem Verfahren eine Presskraft von mindestens 100 kN, insbesondere mindestens 500 kN, vorzugsweise mindestens 1500 kN erzeugt. Die oben beschriebene Antriebseinrichtung sowie die oben beschriebene Presse können entsprechend konfiguriert sein, um eine derartig Pressekraft zu erzeugen.A pressing force of at least 100 kN, in particular at least 500 kN, preferably at least 1500 kN, is preferably generated in the method. The drive device described above and the press described above can be configured accordingly in order to generate such a pressing force.

Vorzugsweise wird ein maximaler Differenzdruck zwischen Kolbenraum und Stangenraum in Höhe von mindestens 100 bar, vorzugsweise mindestens 250 bar erzeugt. Die oben beschriebene Antriebseinrichtung sowie die oben beschriebene Presse können entsprechend konfiguriert sein, um einen derartigen Druck zu erzeugen.A maximum differential pressure between the piston chamber and the rod chamber of at least 100 bar, preferably at least 250 bar, is preferably generated. The drive device described above and the press described above can be configured accordingly in order to generate such a pressure.

Die obengenannte Aufgabe wird weiterhin insbesondere gelöst durch die Verwendung gemäß Anspruch 15
einer hydraulischen Antriebseinrichtung der oben beschriebenen Art oder einer Presse der oben beschriebenen Art zum Pressen eines Pressteils, insbesondere zum Pulverpressen eines Pulverpressteils.The above-mentioned object is also achieved in particular by the use according to claim 15
a hydraulic drive device of the type described above or a press of the type described above for pressing a pressed part, in particular for powder pressing a powder pressed part.

Erfindungsgemäß wird insbesondere ein Antrieb und eine hydraulische Steuerung eines Presszylinders einer hydraulischen Presse vorgeschlagen. Der Presszylinder ist vorzugsweise in Differentialbauweise ausgeführt (mit einer großen Kolbenfläche und einer kleinen Differenzfläche). Daraus können sich bei den Verfahrbewegungen an einem Anschluss zum Kolbenraum vergleichsweise hohe Volumenströme ergeben, die durch eine hydraulische Speichereinrichtung versorgt werden können. An einem Anschluss zum Stangenraum können vergleichsweise niedrige Volumenströme anstehen, die zur Positionierung des Zylinderkolbens geregelt werden können. Die Regelung von Kraft bzw. Druck, Position und Geschwindigkeit des Zylinderkolbens kann mittels einer Pumpeneinheit (insbesondere Servopumpeneinheit) erfolgen. Insbesondere kann die Bauart der Pumpe einen 4-Quadranten-Betrieb ermöglichen, so dass eine Regelung von Drücken in beiden Durchflussrichtungen möglich ist.According to the invention, 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). In particular, the design of the pump can enable 4-quadrant operation, so that pressures can be regulated in both flow directions.

Insgesamt ergibt sich durch die erfindungsgemäße Ausbildung der Antriebsvorrichtung eine Reihe von Vorteilen. Zunächst kann ein zusätzlicher Zylinder (Eilgang-Zylinder), wie er üblicherweise im Stand der Technik vorgesehen ist, entfallen. Weiterhin kann eine aufwändige "Umspülung" (wie weiter oben im Zusammenhang mit dem Stand der Technik erläutert) entfallen. Insgesamt handelt es sich um ein eingespanntes System, so dass die Effizienz gesteigert wird. Durch die vorliegende Struktur kann ein äußerst genauer (aktiver) Kraftabbau ermöglicht werden. Es ist keine aufwändige Verrohrung notwendig. Die Größe der Pumpeneinrichtung kann vergleichsweise klein sein. Es kann ggf. auf weitere Pumpeneinrichtungen verzichtet werden. Insgesamt ergeben sich Kosteneinsparungen bei der Bereitstellung des (Zylinder-) Antriebs, von Ventilen, der Pumpe und der Steuerung.Overall, the design of the drive device according to the invention results in a number of advantages. First of all, an additional cylinder (rapid traverse cylinder), as is usually provided in the prior art, can be omitted. Furthermore, there is no need for a complex “flushing” (as explained above in connection with the prior art). Overall, 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.

Weitere Ausführungsformen ergeben sich aus den Unteransprüchen.Further embodiments emerge from the subclaims.

Nachfolgend wird die Erfindung anhand eines Ausführungsbeispiels beschrieben, das anhand der Abbildungen näher erläutert wird. Hierbei zeigen

Fig. 1
eine schematische Darstellung einer hydraulischen Antriebsvorrichtung gemäß einer Ausführungsform der Erfindung; und
Fig. 2
eine schematische Darstellung der Ausführungsform gemäß Fig. 1 mit einer Darstellung der jeweiligen Volumenströme.
The invention is described below using an exemplary embodiment which is explained in more detail using the figures. Show here
Fig. 1
a schematic representation of a hydraulic drive device according to an embodiment of the invention; and
Fig. 2
a schematic representation of the embodiment according to Fig. 1 with a representation of the respective volume flows.

In der nachfolgenden Beschreibung werden für gleiche und gleichwirkende Teile dieselben Bezugsziffern verwendet.In the following description, the same reference numbers are used for parts that are the same and have the same effect.

Fig. 1 zeigt einen Presszylinder 1, der sowohl zum Öffnen und Schließen eines (nicht in Fig. 1 gezeigt) Presswerkzeuges mit einer hohen Geschwindigkeit (Eilgang) verwendet wird als auch zum Aufbau einer hohen Kraft in Schließrichtung bei geringer Geschwindigkeit (Pressgang zum Pressen eines Pressteils). Der Presszylinder ist in Differentialbauweise ausgeführt und weist eine vergleichsweise große Kolbenfläche A1 zur Erzeugung einer (maximalen) Presskraft und eine vergleichsweise kleine Differenzfläche A2 für den Rückzug eines Zylinderkolbens 9 auf. Aufgrund dieser Bauweise des Presszylinders 1 muss ein vergleichsweise hoher Volumenstrom eines Hydraulikfluids an einen Anschluss 10 des Kolbenraums herangeführt werden. Dieser hohe Volumenstrom Q1 zum Kolbenraum wird durch eine hydraulische Speichereinrichtung 4 realisiert. Ein Anschluss 11 eines Stangenraums 12 wird durch eine Pumpeneinrichtung 2 geregelt. Bei diesem Vorwärts-Eilgang ist eine erste Ventileinrichtung 3 (Y1) geöffnet und eine zweite Ventileinrichtung 5 (Y2) geschlossen. 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.

Beim Rückwärts-Eilgang (also beim Öffnen des Presswerkzeuges oder einer Kolbenbewegung nach oben in Fig. 1) wird umgekehrt ein Hydraulikflüssigkeitsvolumen aus dem Kolbenraum 13 in die hydraulische Speichereinrichtung 4 geschoben. Auch bei diesem Rückwärts-Eilgang ist die erste Ventileinrichtung 3 geöffnet und die zweite Ventileinrichtung 5 geschlossen.With reverse rapid traverse (i.e. when opening the press tool or moving the piston upwards in Fig. 1 ) Conversely, a hydraulic fluid volume is pushed out of the piston chamber 13 into the hydraulic storage device 4. In this reverse rapid traverse, too, the first valve device 3 is open and the second valve device 5 is closed.

In der Pressphase (Pressgang) des Presszylinders sind erste und zweite Ventileinrichtung 3, 5 jeweils geschlossen. Eine Zufuhr der Hydraulikflüssigkeit (Ölzufuhr) zum Kolbenraum 13 erfolgt dann (ausschließlich) über die Pumpeneinrichtung 2. Die Regelung von Druck und (Förder-) Geschwindigkeit erfolgt über Drehzahl und Drehmoment eines Servomotors 7 der Pumpeneinrichtung 2. Die Pumpeneinrichtung 2 umfasst hierbei eine bidirektionale Pumpe 14.In the pressing phase (pressing cycle) of the press cylinder, 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

Aufgrund der vergleichsweise kleinen Fläche A2 (im Verhältnis zu A1) und des Kompressionsvolumens (aufgrund des Druckaufbaus in der Pressphase) entsteht in dieser Pressphase an der Pumpeneinrichtung 2 (Saugseite) ein Mangel an Hydraulikflüssigkeit (Ölmangel), der über eine Verbindung zu der hydraulischen Speichereinrichtung 4 und ein Rückschlagventil 6 ausgeglichen wird. Sobald (aufgrund des Mangels an Hydraulikflüssigkeit) an der Saugseite der Pumpeneinrichtung 2 der Druck unter das Druckniveau der hydraulischen Speichereinrichtung 4 sinkt, öffnet sich das Rückschlagventil 6 und die Hydraulikflüssigkeit aus der hydraulischen Speichereinrichtung 4 gleicht das Differenzvolumen aus.Due to the comparatively small area A 2 (in relation to A 1 ) and the compression volume (due to the pressure build-up in the pressing phase), a lack of hydraulic fluid (lack of oil) arises in this pressing phase on the pump device 2 (suction side), which is via a connection to the hydraulic storage device 4 and a check valve 6 is compensated. As soon as the pressure on the suction side of the pump device 2 falls below the pressure level of the hydraulic accumulator device 4 (due to the lack of hydraulic fluid), the non-return valve 6 and the valve open Hydraulic fluid from the hydraulic storage device 4 compensates for the difference in volume.

Nach der Pressphase (Pressgang) erfolgt der Kraftabbau des Presszylinders in zwei Phasen. In einer ersten Kraftabbau-Phase öffnet sich die zweite Ventileinrichtung 5, so dass eine Verbindung zwischen hydraulischer Speichereinrichtung 4 und Stangenraum 12 realisiert ist. Der Druck im Kolbenraum 13 wird (von seinem Maximalwert) abgebaut auf das Druckniveau der hydraulischen Speichereinrichtung 4. Ein Kompressionsvolumen wird dabei vom Kolbenraum 13 über die Pumpeneinrichtung 2 in die hydraulische Speichereinrichtung 4 entlastet.After the pressing phase (pressing cycle), the force of the press cylinder is reduced in two phases. In 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.

Sobald der Druck im Kolbenraum 13 den Druck in der hydraulischen Speichereinrichtung 4 erreicht hat, beginnt die zweite Kraftabbau-Phase. Dazu wird die zweite Ventileinrichtung 5 geschlossen und die erste Ventileinrichtung geöffnet. In der zweiten Kraftabbau-Phase erfolgt ein Druckaufbau im Stangenraum 12 (der Druck p1 im Kolbenraum bleibt auf dem Wert des Drucks in der hydraulischen Speichereinrichtung 4). Eine Kraft am Zylinderkolben wird proportional zu diesem Druckanstieg im Stangenraum 12 (bis auf Null) abgebaut.As soon as the pressure in the piston chamber 13 has reached the pressure in the hydraulic accumulator device 4, the second force reduction phase begins. For this purpose, the second valve device 5 is closed and the first valve device is opened. In 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).

Nach Erreichen eines notwendigen Drucks p2 im Stangenraum 12 startet der Zylinderkolben 9 (übergangslos) eine Öffnungsbewegung nach oben. Der Volumenstrom Q1 aus dem Kolbenraum 13 wird (zum größeren Teil) wieder in die hydraulische Speichereinrichtung 4 geschoben, wobei der Volumenstromanteil entsprechend Q2 über die Pumpeneinrichtung 2 gefördert wird.After a necessary pressure p 2 has been reached in the rod space 12, 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 zeigt in Ergänzung zu der Darstellung gemäß Fig. 1 Pfeile, die den jeweiligen Volumenstrom (oder einen Entlastungsstrom) kennzeichnen. Hierbei zeigen Pfeile 15 einen Volumenstrom, der sich im Vorwärts-Eilgang ergibt. Pfeile 16 zeigen einen Volumenstrom, der sich während der Pressphase ergibt. Pfeile 17 zeigen einen Volumenstrom (Entlastungsstrom) während der ersten Kraftabbau-Phase. Pfeile 18 zeigen einen Volumenstrom (Entlastungsstrom), der sich während der zweiten Kraftabbau-Phase ergibt. Pfeile 19 zeigen einen Volumenstrom, der sich im Rückwärts-Eilgang ergibt. Fig. 2 shows in addition to the representation according to Fig. 1 Arrows that indicate the respective volume flow (or a relief flow). Here, 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.

Die Verbindungsstrukturen zwischen Anschluss 10 des Kolbenraums 13 und Anschluss 11 des Stangenraums 12 werden nachfolgend erläutert. Ausgehend von dem Anschluss 10 des Kolbenraums 13 schließt sich zunächst ein erster Fluidverbindungsabschnitt 21 (siehe Fig. 1) an, der mit einer ersten Verzweigungsstelle 31 verbunden ist. Von der ersten Verzweigungsstelle 13 zweigt ein zweiter Fluidverbindungsabschnitt 22 in Richtung Pumpeneinrichtung 2 ab sowie ein dritter Fluidverbindungsabschnitt 23 in Richtung hydraulische Speichereinrichtung 4. In dem dritten Fluidverbindungsabschnitt ist die erste Ventileinrichtung 3 vorgesehen. Der Anschluss 11 des Stangenraums 12 ist über einen vierten Fluidverbindungsabschnitt 24 mit einer zweiten Verzweigungsstelle 32 verbunden. Von dort zweigt ein fünfter Fluidverbindungsabschnitt 25 ab, der mit der Pumpeneinrichtung 2 verbunden ist. Außerdem zweigt von dort ein sechster Fluidverbindungsabschnitt 26 ab, der mit der hydraulischen Speichereinrichtung 4 verbunden ist. In dem sechsten Fluidverbindungsabschnitt 26 befindet sich die zweite Ventileinrichtung 3. Parallel zu der zweiten Ventileinrichtung 5 verläuft ein siebter Fluidverbindungsabschnitt 27, in dem das Rückschlagventil 6 angeordnet ist. Grundsätzlich kommt es im vorliegenden Zusammenhang darauf an, wie die einzelnen Elemente entweder in Serie oder parallel zueinander geschaltet werden. Im Allgemeinen sind jedoch sowohl Pumpeneinrichtung 2 als auch hydraulische Speichereinrichtung 4 in einer Fluidverbindung zwischen Kolbenraum und Stangenraum angeordnet.The connection structures between connection 10 of piston chamber 13 and connection 11 of rod chamber 12 are explained below. Starting from the connection 10 of the piston chamber 13, 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. In addition, 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.

Insgesamt ergibt sich durch die erfindungsgemäße Ausbildung der Antriebsvorrichtung eine Reihe von Vorteilen. Zunächst kann ein zusätzlicher Zylinder (Eilgang-Zylinder), wie er üblicherweise im Stand der Technik vorgesehen ist, entfallen. Weiterhin kann eine aufwändige "Umspülung" (wie weiter oben im Zusammenhang mit dem Stand der Technik erläutert) entfallen. Insgesamt handelt es sich um ein eingespanntes System, so dass die Effizienz gesteigert wird. Durch die vorliegende Struktur kann ein äußerst genauer (aktiver) Kraftabbau ermöglicht werden. Es ist keine aufwändige Verrohrung notwendig. Die Größe der Pumpeneinrichtung kann vergleichsweise klein sein. Es kann ggf. auf weitere Pumpeneinrichtungen verzichtet werden. Insgesamt ergeben sich Kosteneinsparungen bei der Bereitstellung des (Zylinder-) Antriebs, von Ventilen, der Pumpe und der Steuerung.Overall, the design of the drive device according to the invention results in a number of advantages. First of all, an additional cylinder (rapid traverse cylinder), as is usually provided in the prior art, can be omitted. Furthermore, there is no need for a complex “flushing” (as explained above in connection with the prior art). Overall, 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.

In der Ausführungsform gemäß Fig. 1 und 2 ist vorzugsweise noch eine (nicht dargestellte) Steuereinrichtung vorgesehen. Zur Steuerung, insbesondere Regelung sind weiterhin (siehe Fig. 1) Sensoren (beispielsweise eine Druck- und/oder Volumenstrom-Messeinrichtung) vorgesehen, über die die Steuereinrichtung die Ventile 3, 5 so schaltet und die Pumpeneinrichtung 2 so ansteuert, dass die notwendigen Volumenströme und Drücke realisiert werden.In the embodiment according to Figs. 1 and 2 a control device (not shown) is preferably also provided. For control, in particular regulation, are still (see Fig. 1 ) Sensors (for example a pressure and / or volume flow measuring device) are provided, via which 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.

Im Folgenden wird tabellarisch ein Beispiel für bestimmte Parameter während des Betriebs der Antriebseinrichtung angegeben. TABELLE 1 Y1 Y2 p1 P2 Vorwärts-Eilgang Auf Zu 40 bar 280 bar Pressen Zu Zu 290 bar 40 bar Erste Kraftabbau-Phase Zu Auf 40 bar 40 bar Zweite Kraftabbau-Phase Auf Zu 40 bar 280 bar Rückwärts-Eilgang Auf Zu 40 bar 280 bar An example of certain parameters during operation of the drive device is given in a table below. <b> TABLE 1 </b> Y1 Y2 p 1 P2 Forward rapid traverse on to 40 bar 280 bar Press to to 290 bar 40 bar First force reduction phase to on 40 bar 40 bar Second force reduction phase on to 40 bar 280 bar Reverse rapid traverse on to 40 bar 280 bar

Eine Kraft während des Pressens kann 1600 kN betragen. Eine Kraft zum Ende der ersten Kraftabbau-Phase kann 320 kN betragen. Eine Kraft zum Ende der zweiten Kraftabbau-Phase kann 0 kN betragen.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.

Im Nachfolgenden werden noch tabellarisch exemplarische Werte für Volumenstrom und Geschwindigkeit des Hydraulikfluids angegeben. TABELLE 2 Q1 Q2 v Vorwärts-Eilgang 620 l/min 88 l/min 180 mm/s Pressen 137 l/min 20 l/min 40 mm/s Rückwärts-Eilgang 620 l/min 88 l/min 180 mm/s In the following, exemplary values for volume flow and speed of the hydraulic fluid are given in tabular form. <b> TABLE 2 </b> Q 1 Q 2 v Forward rapid traverse 620 l / min 88 l / min 180 mm / s Press 137 l / min 20 l / min 40 mm / s Reverse rapid traverse 620 l / min 88 l / min 180 mm / s

Sämtliche obengenannten Werte (in Tabelle 1 und 2) sind exemplarisch angegeben. Abweichungen davon (beispielsweise jeweils in einem Bereich von +/- 10 %) sind möglich.All of the above values (in Tables 1 and 2) are given by way of example. Deviations from this (for example in a range of +/- 10% in each case) are possible.

An dieser Stelle sei darauf hingewiesen, dass alle oben beschriebenen Teile für sich alleine gesehen und in jeder Kombination, insbesondere die in den Zeichnungen dargestellten Details, als erfindungswesentlich beansprucht werden. Abänderungen hiervon sind dem Fachmann geläufig.At this point it should be pointed out that all of the parts described above, seen on their own and in any combination, in particular the details shown in the drawings, are claimed to be essential to the invention. Changes to this are familiar to the person skilled in the art.

BezugszeichenReference number

A1A1
(Wirk-) Fläche des Kolbenraums(Effective) area of the piston chamber
A2A2
(Wirk-) Fläche des Stangenraums(Effective) area of the rod space
p1p1
Druck im KolbenraumPressure in the piston chamber
p2p2
Druck im StangenraumPressure in the rod space
Q1Q1
Volumenstrom an einem Anschluss des KolbenraumsVolume flow at one connection of the piston chamber
Q2Q2
Volumenstrom an einem Anschluss des StangenraumsVolume flow at one connection of the rod compartment
11
PresszylinderPress cylinder
22
PumpeneinrichtungPump device
33
Erste VentileinrichtungFirst valve device
44th
Hydraulische SpeichereinrichtungHydraulic storage device
55
Zweite VentileinrichtungSecond valve device
66th
Rückschlagventilcheck valve
77th
ServomotorServo motor
8a8a
MesseinrichtungMeasuring device
8b8b
MesseinrichtungMeasuring device
99
ZylinderkolbenCylinder piston
1010
Anschlussconnection
1111
Anschlussconnection
1212th
StangenraumPole space
1313th
KolbenraumPiston chamber
1414th
Bidirektionale PumpeBidirectional pump
1515th
Pfeilarrow
1616
Pfeilarrow
1717th
Pfeilarrow
1818th
Pfeilarrow
1919th
Pfeilarrow
2121
Erster FluidverbindungsabschnittFirst fluid connection section
2222nd
Zweiter FluidverbindungsabschnittSecond fluid connection section
2323
Dritter FluidverbindungsabschnittThird fluid connection section
2424
Vierter FluidverbindungsabschnittFourth fluid connection section
2525th
Fünfter FluidverbindungsabschnittFifth fluid connection section
2626th
Sechster FluidverbindungsabschnittSixth fluid communication section
2727
Siebter FluidverbindungsabschnittSeventh fluid communication section
3131
Erste VerzweigungsstelleFirst branch point
3232
Zweite VerzweigungsstelleSecond branch point

Claims (15)

  1. Hydraulic drive device with a press cylinder (1) for a hydraulic press, preferably a powder press, wherein the hydraulic drive device is configured to guide a cylinder piston (9) in a forward rapid motion at increased speed towards a press part and to press the press part in a press motion at low speed,
    wherein the cylinder piston (9) defines a piston chamber (13) and a rod chamber (12),
    wherein a pump device (2) is provided for providing a volumetric flow of a hydraulic fluid into the piston chamber (13) in order to perform the press motion,
    wherein a hydraulic accumulator device (4) is provided for providing at least a part, in particular a predominant part, of a volumetric flow of the hydraulic fluid into the piston chamber (13) so that the forward rapid motion is performed, dispensing with an additional rapid motion cylinder for realizing the rapid motion,
    wherein the piston chamber (13) and the rod chamber (12) are or can be connected via a fluid connection, wherein the pump device (2) and the hydraulic accumulator device (4) are arranged within this fluid connection, fluid-technically connected in parallel with one another, wherein a first fluid connection section (21) connected to the piston chamber is connected to a first branching point (31), from which a second fluid connection section (22) branches off in the direction of the pump device (2) and a third fluid connection section (23) branches off in the direction of the hydraulic accumulator device (4),
    wherein a fourth fluid connection section (24) connected to the rod chamber (12) is connected to a second branching point (32) from which a fifth fluid connection section (25) branches off in the direction of the pump device (2) and a sixth fluid connection section (26) branches off in the direction of the hydraulic accumulator device (4).
  2. Hydraulic drive device according to claim 1,
    characterized in that
    the hydraulic drive device is configured to guide the cylinder piston (9) away from the pressing part in a reverse rapid motion at increased speed, wherein a volumetric flow of the hydraulic fluid emerging from the piston chamber in the reverse rapid motion is transferred at least partially, in particular predominantly, into the hydraulic accumulator device (4).
  3. Hydraulic drive device according to claim 1 or 2,
    characterized in that
    the hydraulic drive device is configured such that, in forward rapid motion, a volumetric flow into the piston chamber (13) can be provided partially from the rod chamber (12), in particular via the pump device (2), and/or wherein the hydraulic drive device is configured such that, in the reverse rapid motion, the volumetric flow exiting from the piston chamber (13) can be partially transferred into the rod chamber (12), in particular via the pump device (2).
  4. Hydraulic drive device according to claim 1, 2 or 3,
    characterized in that
    the press cylinder (1) is a differential cylinder,
    wherein a ratio of the larger area to the smaller area is preferably at least 2, further preferably at least 5, and/or
    wherein a ratio of the larger area to the smaller area is preferably at most 20, further preferably at most 10.
  5. Hydraulic drive device according to one of the preceding claims,
    characterized in that
    the hydraulic drive device is configured such that, in a first force reduction phase, the piston chamber (13) can be connected to the hydraulic accumulator device (4), preferably via the pump device (2), in such a way that the pressure in the piston chamber (13) can be reduced to the pressure level of the hydraulic accumulator device (4), and/or
    wherein the hydraulic drive device is configured such that in a second force reduction phase a pressure in the rod chamber (12) can be increased preferably by the pump device (9).
  6. Hydraulic drive device according to one of the preceding claims,
    characterized in that
    a first valve device (3) is provided in the third fluid connection section (23) and/or wherein a second valve device (5) is provided in the sixth fluid connection section (26), wherein a non-return valve (6) is further preferably fluid-technically connected in parallel with the second valve device (5).
  7. Hydraulic drive device according to one of the preceding claims,
    characterized in that
    the pump device (2) comprises a bidirectional pump (14), in particular a 4-quadrant pump, and/or a servomotor (7).
  8. Hydraulic drive device according to one of the preceding claims,
    characterized in that
    an effective area of the piston chamber (13) is at least 200 cm2, preferably at least 450 cm2 and/or at most 1100 cm2, preferably at most 700 cm2, and/or
    a ratio of an effective area of the piston chamber (13) to an effective area of the rod chamber (12) is at least 3, preferably at least 6, and/or is at most 15, preferably at most 9, and/or
    the hydraulic accumulator device (4) has a volume of at least 10 I, preferably at least 30 I and/or at most 100 I, preferably at most 70 I, and/or the hydraulic accumulator device (4) has a base pressure of at least 10 bar, preferably at least 25 bar and/or at most 80 bar, preferably at most 50 bar.
  9. Hydraulic drive device according to one of the preceding claims,
    characterized in that
    at least one control device, in particular regulating device, is provided for controlling, in particular regulating, the individual components of the hydraulic drive device.
  10. Hydraulic press, preferably a powder press, comprising a hydraulic drive device according to any one of the preceding claims.
  11. Method for pressing a pressed part, in particular for powder pressing a powder pressed part, using a hydraulic drive device according to any one of claims 1 to 9 and/or a press, in particular a powder press, according to claim 10,
    wherein a cylinder piston (4) of a press cylinder is guided in a forward rapid motion at an increased speed towards a press part and the press part is pressed in a press motion at a low speed of the cylinder piston (9), wherein a volumetric flow is pumped in the direction of a piston chamber (13) of the press cylinder (1) via a pump device (2) in the press motion, wherein in rapid motion via a hydraulic accumulator device (4) at least a part, in particular a predominant part, of a volumetric flow is provided in the piston chamber (13).
  12. Method according to claim 11,
    characterized in that
    the cylinder piston is guided away from the pressing part in a reverse rapid motion at increased speed, a volume flow emerging from the piston chamber in the reverse rapid motion being transferred at least partially, in particular predominantly, into the hydraulic accumulator device.
  13. Method according to claim 11 or 12,
    characterized in that
    in the forward rapid motion, a volume flow into the piston chamber (13) is partially provided from the rod chamber (12), in particular via the pump device (2), and/or
    in reverse rapid motion, the volumetric flow exiting the piston chamber is partially transferred to the rod chamber, in particular via the pump device and/or in a first force reduction phase the piston chamber (13) is connected to the hydraulic accumulator device (4), preferably via the pump device (1), in such a way that the pressure in the piston chamber (13) is reduced to the pressure level of the hydraulic accumulator device (4), and/or
    in a second force reduction phase, a pressure in the rod chamber (12) is preferably increased by the pump device (2).
  14. Method according to any one of claims 11 to 13,
    characterized in that
    a pressing force of at least 100 kN, preferably at least 500 kN, more preferably at least 1500 kN is generated and/or
    a maximum differential pressure between piston chamber (13) and rod chamber (12) of at least 100 bar, preferably at least 250 bar, is generated.
  15. Use of a hydraulic drive device according to any one of claims 1 to 9 or a press according to claim 10 for pressing a pressed part, in particular for powder pressing a powder pressed part.
EP17181834.7A 2016-07-19 2017-07-18 Hydraulic drive device Active EP3272511B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016113294.2A DE102016113294A1 (en) 2016-07-19 2016-07-19 Hydraulic drive device

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EP3272511B1 true EP3272511B1 (en) 2021-11-03

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EP17181834.7A Active EP3272511B1 (en) 2016-07-19 2017-07-18 Hydraulic drive device

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018120000A1 (en) * 2018-08-16 2020-02-20 Moog Gmbh Electrohydrostatic actuator system with suction tank
US11512716B2 (en) * 2020-01-31 2022-11-29 Bosch Rexroth Corporation Hydraulic axis with energy storage feature
DE102021121461A1 (en) 2021-08-18 2023-02-23 Dorst Technologies Gmbh & Co. Kg Powder press with hydraulic press drive

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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 (en) * 2007-02-01 2007-03-29 Klimas, Joachim Hydraulic injection device with reduced shaft power has injection cylinder in which piston is pushed from start via feed position into injection position and hydraulic feed device to move piston from start to feed position
AT505724B1 (en) * 2007-09-12 2010-06-15 Trumpf Maschinen Austria Gmbh DRIVE DEVICE FOR A BEND PRESS
EP2637852B1 (en) * 2010-11-11 2017-01-18 Robert Bosch GmbH Hydraulic axis
DE102011078241B3 (en) * 2011-06-28 2012-09-27 Voith Patent Gmbh Hydraulic unit, has valve connecting flow-reversible pump with connection line of another flow-reversible pump before switching another valve in load drive state, where hydraulic fluid is not conveyed to piston chamber in load drive state
DE102013020585A1 (en) * 2013-12-13 2015-06-18 Hydac Fluidtechnik Gmbh valve device
DE102014226236A1 (en) * 2014-09-29 2016-03-31 Robert Bosch Gmbh Hydraulic circuit and machine with a hydraulic circuit
DE102014219734A1 (en) * 2014-09-30 2016-03-31 Robert Bosch Gmbh Hydraulic circuit for supplying pressure to a differential cylinder

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DE102016113294A1 (en) 2018-01-25

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