EP3272511A1 - Dispositif d'entraînement hydraulique - Google Patents

Dispositif d'entraînement hydraulique Download PDF

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Publication number
EP3272511A1
EP3272511A1 EP17181834.7A EP17181834A EP3272511A1 EP 3272511 A1 EP3272511 A1 EP 3272511A1 EP 17181834 A EP17181834 A EP 17181834A EP 3272511 A1 EP3272511 A1 EP 3272511A1
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EP
European Patent Office
Prior art keywords
hydraulic
press
piston chamber
drive device
hydraulic drive
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP17181834.7A
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German (de)
English (en)
Other versions
EP3272511B1 (fr
Inventor
Roland Menzel
Martin Rossi
Max Hälterlein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
DORST Technologies GmbH and Co KG
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DORST Technologies GmbH and Co KG
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Publication of EP3272511A1 publication Critical patent/EP3272511A1/fr
Application granted granted Critical
Publication of EP3272511B1 publication Critical patent/EP3272511B1/fr
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/161—Control arrangements for fluid-driven presses controlling the ram speed and ram pressure, e.g. fast approach speed at low pressure, low pressing speed at high pressure

Definitions

  • the invention relates to a hydraulic drive device with a press cylinder for a hydraulic press, preferably a powder press, according to claim 1 and a hydraulic press, preferably a powder press and a method for pressing a pressed part, in particular for powder pressing a powder press 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 more than 500 kN, in particular more than 1000 kN, preferably more than 1500 kN.
  • the central component of hydraulic presses are press cylinders that perform various functions.
  • such press cylinders are used for opening and closing a pressing tool of the hydraulic press at a high speed (rapid traverse).
  • a high force in the closing direction is built on such press cylinder.
  • the high closing forces required for pressing require a correspondingly large piston surface for generating a maximum pressing force at a predetermined maximum pressure.
  • a large piston area correspondingly high volume flows result, so that in the prior art comparatively large or dimensioned pumps and valves are required.
  • the rapid traverse and press functions are separated in the prior art.
  • a hydraulic drive device with a press cylinder for a hydraulic press, preferably a powder press
  • the hydraulic drive device is configured to feed a cylinder piston in a forward rapid traverse at increased speed to a pressing part and in a low-speed pressing to press the pressing member
  • the pressing cylinder has a cylinder piston defining a piston chamber and a rod space
  • a pump means for providing a volume flow of a hydraulic fluid into the piston chamber, so that the pressing space is passed
  • a hydraulic storage device for providing at least 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, is provided.
  • a central idea of the invention is to provide a hydraulic storage device and overall to configure the hydraulic drive device so that at least a considerable (in particular predominant) part of the comparatively large volume flow which is required in the forward rapid traverse is provided via this hydraulic storage device.
  • a "predominant part” is to be understood as a proportion of at least 50%. However, the proportion may 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, 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 may in particular be a hydraulic storage device with gas tensioning device.
  • the hydraulic storage device may comprise a (pressure) container.
  • the hydraulic storage device may include a movable member (for example, a movable piston) for separating hydraulic fluid and a (pressurized) gas. The hydraulic fluid can then be pressed against the pressure of the gas in the hydraulic storage device (in particular the container).
  • the hydraulic storage device can be dispensed with an additional press cylinder for the realization of a rapid traverse, as usually provided in the prior art.
  • the drive device is structurally considerably simplified, whereby costs can be reduced.
  • the control, in particular control, of such a drive device is simplified, since a second press cylinder (with correspondingly assigned elements, in particular a feed pump) can be dispensed with.
  • the hydraulic drive device according to the invention comes with only one pump device. Overall, the costs (in terms of both manufacturing and operation or maintenance) are significantly reduced.
  • hydraulic fluid is in particular (hydraulic) oil in question.
  • the hydraulic drive device is preferably configured to lead the cylinder piston away from the pressed part at a high speed in a reverse rapid traverse, wherein a volume flow of the hydraulic fluid exiting the piston chamber in reverse rapid traverse is at least partially, in particular predominantly, transferred into the hydraulic accumulator device.
  • the hydraulic storage device is therefore used in this development at the same time as a receptacle for the (large) amount of hydraulic fluid, which is ejected from the piston chamber during reverse rapid traverse. At the same time, the hydraulic storage device is loaded again so that it can discharge again in a next cycle (in a subsequent forward rapid traverse). This further simplifies the structure and the control effort.
  • the speed in the forward rapid traverse and / or reverse 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 press gear.
  • the hydraulic drive device is configured such that, in the forward rapid traverse, a volume flow of the hydraulic fluid into the piston chamber is provided in part from the rod space, in particular via the pump device.
  • the hydraulic drive device can be configured such that in the reverse rapid traverse the volume flow emerging from the piston chamber can be partially transferred into the rod chamber, in particular via the pump device.
  • the entire volume flow flowing into the piston chamber in forward rapid traverse can be provided (exclusively) via the hydraulic accumulator device and the pump device.
  • the entire volume flow flowing out of the piston chamber in the reverse rapid traverse can be (exclusively) pushed in the direction of the hydraulic storage device and pump device.
  • the respective pressures in the piston chamber and the rod space are preferably adjusted so that the forces acting on the piston are neutralized (at least substantially; there may be an at least small difference to overcome frictional forces or the like).
  • the pressing cylinder is a differential cylinder.
  • a ratio of the larger area to the smaller area may preferably be at least 2, more preferably at least 5.
  • an upper limit for said ratio may be at most 20, more preferably at most 10.
  • Particularly preferred is a ratio of (about) 7. With such a dimensioning, the hydraulic drive device can be operated particularly effectively.
  • the hydraulic drive device is configured so that in a first power-reduction phase, the piston chamber with the hydraulic storage device, preferably via the pump device, is connectable, such 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 may be configured so that in a second power reduction phase, a pressure in the rod space (preferably by the pump device) can be increased.
  • the storage and pump device are thus used synergistically to allow a controllable and reliable power reduction. Damage to the part to be pressed (pressed part) can thus be prevented (or at least less likely).
  • Piston space and rod space can be connected or connectable via a fluid connection.
  • this fluid connection pump device and hydraulic storage device (in particular fluidly connected to each other in parallel) may be arranged.
  • a first fluid connection section connected to the piston chamber may be connected to a first branching point (branching 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 may be connected to a second branching point (branching structure) from which a fifth fluid connection section branches off toward the pump device sixth fluid connection section branches off in the direction of hydraulic storage device.
  • a first valve device is provided in the fifth fluid connection section.
  • a second valve device may be provided in the sixth fluid connection section. Parallel to the second valve device is preferably a (non-return) valve fluidly connected.
  • a desired volume flow can be achieved with little effort. The effort in terms of design and control technology is further simplified.
  • the pump device may comprise a bidirectional pump, in particular a 4-quadrant pump, and / or a servomotor.
  • the pump device allows bidirectional delivery of the hydraulic fluid.
  • this can also be realized by providing a unidirectional pump (eg 1- or 2-quadrant pump) and providing corresponding valves (servo-valves or the like).
  • a unidirectional pump eg 1- or 2-quadrant pump
  • corresponding valves servo-valves or the like
  • An effective area (ie an area defined by the cylinder piston and in contact with the hydraulic fluid) of the piston space may 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 may correspond to the upper values divided by 7.
  • a ratio of an effective area of the piston chamber to an effective area of the rod space may be at least 3, preferably at least 6 and / or at most 15, preferably at most 9. More preferably, this ratio is (about) 7. With such a ratio, effective driving and control of the pressing cylinder can be enabled.
  • the hydraulic storage device may have a volume of at least 10 l, preferably at least 30 l and / or at most 100 l, preferably at most 70 l. Particularly preferred is a volume of (about) 50 l.
  • the volume occupied by the hydraulic fluid in the hydraulic accumulator may be at least 3 liters, preferably at least 10 liters and / or at most 30 liters, preferably at most 20 liters. More preferably, this volume is (about) 12 liters.
  • the hydraulic storage device may 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 may be at least 12 bar, preferably at least 30 bar and / or at most 100 bar, preferably at most 60 bar. More preferably, the pressure in this case is (about) 40 bar.
  • the rod space preferably forms an annular space defined by an inner wall of the pressing cylinder and a rod passing through the rod space.
  • a ratio between the inside diameter of the pressing cylinder and the outside diameter of the rod may be, for example, 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 control device for controlling, in particular control, of the individual components of the hydraulic drive device.
  • This control device can be associated with corresponding sensors (such as pressure sensors and / or volumetric flow measuring devices), for example, a measured variable (pressure and / or volume flow) at a connection (output or input) of the piston chamber and / or a connection (Input or output) of the rod space. From the measured variables (in particular pressure and / or volume flow) then required switching operations, in particular concerning the above-described first and second valve devices can be performed and / or the pump device can be controlled accordingly (regulated).
  • sensors such as pressure sensors and / or volumetric flow measuring devices
  • 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 for pressing a press part, in particular for powder pressing a powder press 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 type described above, dissolved, wherein a cylinder piston of a pressing cylinder in a forward rapid traverse at increased speed is led to a pressing part and the pressing member is pressed in a press gear at low speed of the cylinder piston, wherein in the press passage via a pump means a volume flow is pumped into a piston chamber of the pressing cylinder, wherein at least a part, in particular a predominant part, of a volume flow into the piston space is provided at rapid traverse via a hydraulic storage device.
  • a volumetric flow is provided either by the pumping device or the hydraulic accumulator device, this means in particular that the corresponding volumetric flow is instantaneously, i. at best, via appropriate valve means in the piston chamber or rod space out or is derived from there (ie in particular not on the respective other device).
  • provision of a volume flow via (or through) the hydraulic storage device should mean that the respective volume flow is not conducted via the pump.
  • providing a volume flow through the pump means to mean that the respective volume flow is not additionally guided via the hydraulic storage device.
  • the cylinder piston can be guided away from the pressed part in a reverse rapid traverse at an increased speed, wherein a volume flow exiting the piston chamber in the reverse rapid traverse can be transferred at least partially, in particular predominantly, into the hydraulic accumulator device.
  • a volume flow is provided in the piston chamber partly from the rod space, in particular via the pump device.
  • the volume flow emerging from the piston chamber is partially transferred into the rod chamber, in particular via the pump device.
  • the piston chamber is connected to the hydraulic storage device, preferably via the pump device, such that the pressure in the piston chamber is reduced to the pressure level of the hydraulic storage device.
  • a pressure in the rod space is preferably increased by the pump device.
  • the above-described drive means as well as the press described above may be configured accordingly to produce such a press force.
  • a maximum differential pressure between the piston chamber and rod space in the amount of at least 100 bar, preferably at least 250 bar generated.
  • the above described drive means as well as the above described press may be configured accordingly to generate such a pressure.
  • the above-mentioned object is further achieved in particular by the use of 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 press part.
  • a drive and a hydraulic control of a pressing cylinder of a hydraulic press are proposed in particular.
  • the press cylinder is preferably differential (with a large piston area and a small differential area). This can result in the movements at a connection to the piston chamber comparatively high volume flows, which can be supplied by a hydraulic storage device. At a connection to the rod space may be present comparatively low volume flows, which are used for positioning the Cylinder piston can be controlled.
  • the regulation of force or pressure, position and speed of the cylinder piston can be effected by means of a pump unit (in particular servo pump unit).
  • the design of the pump can enable 4-quadrant operation, so that regulation of pressures in both directions of flow is possible.
  • Fig. 1 shows a press cylinder 1, both for opening and closing a (not in Fig. 1 shown) pressing tool at a high speed (Rapid traverse) is used as well as to build a high force in the closing direction at low speed (press gear for pressing a pressed part).
  • the pressing cylinder is designed in differential construction 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 withdrawal of a cylinder piston 9. Due to this design of the pressing cylinder 1, a comparatively high volume flow of a hydraulic fluid must be brought to a terminal 10 of the piston chamber.
  • This high volume flow Q1 to the piston chamber is realized by a hydraulic storage 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 opened and a second valve device 5 (Y2) is closed.
  • first and second valve means 3, 5 are each closed.
  • a supply of hydraulic fluid (oil supply) to the piston chamber 13 then takes place (exclusively) via the pump device 2.
  • the regulation of pressure and (delivery) speed via speed and torque of a servomotor 7 of the pump device 2.
  • the pump device 2 in this case comprises a bidirectional pump 14th
  • the force reduction of the pressing cylinder takes place in two phases.
  • a first power reduction phase the second valve device 5 opens, so that a connection between the hydraulic storage device 4 and rod space 12 is realized.
  • the pressure in the piston chamber 13 is reduced (from its maximum value) to the pressure level of the hydraulic storage device 4.
  • a compression volume is thereby relieved from the piston chamber 13 via the pump device 2 into the hydraulic storage device 4.
  • the second power reduction phase begins.
  • the second valve device 5 is closed and the first valve device is opened.
  • pressure builds up in the rod space 12 (the pressure p 1 in the piston chamber remains at the value of the pressure in the hydraulic storage device 4).
  • a force on the cylinder piston is reduced proportionally to this pressure increase in the rod space 12 (down to zero).
  • Fig. 2 shows in addition to the illustration according to Fig. 1 Arrows that indicate the respective volume flow (or a discharge flow).
  • arrows 15 show a volume flow, which results in the forward rapid traverse.
  • Arrows 16 show a volume flow that results during the pressing phase.
  • Arrows 17 show a volumetric flow (discharge flow) during the first power-down phase.
  • Arrows 18 show a volumetric flow (discharge flow) that results during the second power-down phase.
  • Arrows 19 show a volume flow, which results in the reverse rapid traverse.
  • connection structures between the connection 10 of the piston chamber 13 and the connection 11 of the rod space 12 will be explained below.
  • first a first fluid connection section 21 closes (see FIG Fig. 1 ) connected to a first branching point 31.
  • a second fluid connection section 22 branches off 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 branches off, which is connected to the pump device 2.
  • a sixth fluid connection section 26 which is connected to the hydraulic storage device 4.
  • the second valve device 3 Parallel to the second valve device 5 extends a seventh fluid connection section 27, in which the check valve 6 is arranged. Basically, it depends in the present context on how the individual elements are connected either in series or in parallel. In general, however, both the pump device 2 and the hydraulic storage device 4 are arranged in a fluid connection between the piston chamber and rod space.
  • a control device (not shown) is preferably provided.
  • Sensors for example, a pressure and / or flow rate measuring device
  • the control device via which the control device, the valves 3, 5 so switches and the pump device 2 controls so that the necessary volume flows and pressures are realized.
  • a force during pressing may be 1600 kN.
  • a force at the end of the first power-down phase may be 320 kN.
  • a force at the end of the second power take-off phase may be 0 kN.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Press Drives And Press Lines (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
EP17181834.7A 2016-07-19 2017-07-18 Dispositif d'entraînement hydraulique Active EP3272511B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102016113294.2A DE102016113294A1 (de) 2016-07-19 2016-07-19 Hydraulische Antriebseinrichtung

Publications (2)

Publication Number Publication Date
EP3272511A1 true EP3272511A1 (fr) 2018-01-24
EP3272511B1 EP3272511B1 (fr) 2021-11-03

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EP17181834.7A Active EP3272511B1 (fr) 2016-07-19 2017-07-18 Dispositif d'entraînement hydraulique

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EP (1) EP3272511B1 (fr)
DE (1) DE102016113294A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018120000A1 (de) * 2018-08-16 2020-02-20 Moog Gmbh Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter
US20210239136A1 (en) * 2020-01-31 2021-08-05 Robert Bosch Gmbh Hydraulic Axis With Energy Storage Feature

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021121461A1 (de) 2021-08-18 2023-02-23 Dorst Technologies Gmbh & Co. Kg Pulverpresse mit hydraulischem Pressenantrieb

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6477835B1 (en) * 2001-08-29 2002-11-12 Moog Inc. Single-motor injection-and-screw drive hybrid actuator
US20060070378A1 (en) * 2004-10-01 2006-04-06 David Geiger Closed-system electrohydraulic actuator
DE202007001504U1 (de) * 2007-02-01 2007-03-29 Klimas, Joachim Hydraulische Einpreßvorrichtung mit reduzierter Leistungsaufnahme
US20100212521A1 (en) * 2007-09-12 2010-08-26 Markus Resch Drive device for a bending press
DE102011116964A1 (de) * 2010-11-11 2012-05-16 Robert Bosch Gmbh Hydraulische Achse
DE102011078241B3 (de) * 2011-06-28 2012-09-27 Voith Patent Gmbh Hydraulikeinheit und Verfahren zum Betreiben einer Hydraulikeinheit

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102013020585A1 (de) * 2013-12-13 2015-06-18 Hydac Fluidtechnik Gmbh Ventilvorrichtung
DE102014226236A1 (de) * 2014-09-29 2016-03-31 Robert Bosch Gmbh Hydraulische Schaltung und Maschine mit einer hydraulischen Schaltung
DE102014219734A1 (de) * 2014-09-30 2016-03-31 Robert Bosch Gmbh Hydraulische Schaltung zur Druckmittelversorgung eines Differentialzylinders

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6477835B1 (en) * 2001-08-29 2002-11-12 Moog Inc. Single-motor injection-and-screw drive hybrid actuator
US20060070378A1 (en) * 2004-10-01 2006-04-06 David Geiger Closed-system electrohydraulic actuator
DE202007001504U1 (de) * 2007-02-01 2007-03-29 Klimas, Joachim Hydraulische Einpreßvorrichtung mit reduzierter Leistungsaufnahme
US20100212521A1 (en) * 2007-09-12 2010-08-26 Markus Resch Drive device for a bending press
DE102011116964A1 (de) * 2010-11-11 2012-05-16 Robert Bosch Gmbh Hydraulische Achse
DE102011078241B3 (de) * 2011-06-28 2012-09-27 Voith Patent Gmbh Hydraulikeinheit und Verfahren zum Betreiben einer Hydraulikeinheit

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102018120000A1 (de) * 2018-08-16 2020-02-20 Moog Gmbh Elektrohydrostatisches Aktuatorsystem mit Nachsaugbehälter
US11603867B2 (en) 2018-08-16 2023-03-14 Moog Gmbh Electrohydrostatic actuator system with an expansion reservoir
US20210239136A1 (en) * 2020-01-31 2021-08-05 Robert Bosch Gmbh Hydraulic Axis With Energy Storage Feature

Also Published As

Publication number Publication date
DE102016113294A1 (de) 2018-01-25
EP3272511B1 (fr) 2021-11-03

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