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EP3523120B1 - Groupe d'entraînement électo-hydraulique - Google Patents

Groupe d'entraînement électo-hydraulique Download PDF

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Publication number
EP3523120B1
EP3523120B1 EP17772687.4A EP17772687A EP3523120B1 EP 3523120 B1 EP3523120 B1 EP 3523120B1 EP 17772687 A EP17772687 A EP 17772687A EP 3523120 B1 EP3523120 B1 EP 3523120B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
piston
working chamber
valve
arrangement
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP17772687.4A
Other languages
German (de)
English (en)
Other versions
EP3523120A1 (fr
Inventor
Stefan GUTH
Martin Rauwolf
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.)
HAWE Altenstadt Holding GmbH
Original Assignee
HAWE Altenstadt Holding GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by HAWE Altenstadt Holding GmbH filed Critical HAWE Altenstadt Holding GmbH
Publication of EP3523120A1 publication Critical patent/EP3523120A1/fr
Application granted granted Critical
Publication of EP3523120B1 publication Critical patent/EP3523120B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/163—Control arrangements for fluid-driven presses for accumulator-driven presses
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B30—PRESSES
    • B30B—PRESSES IN GENERAL
    • B30B15/00—Details of, or accessories for, presses; Auxiliary measures in connection with pressing
    • B30B15/16—Control arrangements for fluid-driven presses
    • B30B15/18—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram
    • B30B15/20—Control arrangements for fluid-driven presses controlling the reciprocating motion of the ram controlling the speed of the ram, e.g. the speed of the approach, pressing or return strokes

Definitions

  • the present invention relates to an electrohydraulic drive unit of the generic type specified in the preamble of claim 1.
  • Electrohydraulic drive units which - designed as linear drives - each comprise at least one cylinder-piston arrangement which can be acted upon by a hydraulic pump and are particularly suitable as machine drives, are known in various configurations.
  • the DE 10 2011 116 964 A1 discloses an electrohydraulic drive unit which comprises a cylinder-piston arrangement and a hydraulic pump which serves to act upon it and is driven by an electric motor at variable speeds.
  • the delivery direction of the hydraulic pump can be reversed so that it can be switched between an application of the first hydraulic working chamber on the piston side and the second hydraulic working chamber on the piston rod side, so that it does not have a defined tank connection and a defined working connection.
  • the line arrangement is designed in such a way that in both directions of movement of the piston of the cylinder-piston arrangement, hydraulic fluid can be pumped out of one of the working spaces into the other working space.
  • An electrohydraulic drive unit of the generic type is in particular the one mentioned above DE 202015106161 U1 removable.
  • One of the characteristics is that the hydraulic pump with its working connection can be switched to either of the two hydraulic working spaces of the - double-acting - cylinder-piston arrangement.
  • the piston of the cylinder-piston arrangement can be actively moved in either of the two directions of movement (lowered and raised with a vertical axis of movement) by appropriately loading one of the two hydraulic working spaces from the hydraulic pump.
  • the piston of the cylinder-piston arrangement is under considerable tension at its bottom dead center.
  • the first hydraulic working space of the cylinder-piston arrangement at the bottom dead center of the piston is under considerable pressure.
  • a so-called decompression phase is provided, which follows the holding phase.
  • the latest end of the decompression phase results from the process itself, namely at the latest at the point of equilibrium of the forces acting on the piston (in particular hydraulic forces, weight forces, reaction or springback forces of the workpiece, restoring forces of the machine parts deformed elastically during pressing), whereby the tool is typically still on the workpiece gets up.
  • the hydraulic system is then reversed in the sense that the second hydraulic working chamber is acted upon, causing the piston to be actively raised, by the hydraulic pump, which in turn is switched back to pumping mode.
  • the present invention has set itself the task of providing an electrohydraulic drive unit of the generic type, which is characterized by a further improved operating behavior, in particular in the area of movement reversal of the piston of the hydraulic cylinder-piston arrangement.
  • the electrohydraulic drive unit is characterized in that a decompression module comprising a hydraulic accumulator is integrated in the hydraulic system the cylinder-piston arrangement can be coupled or separated therefrom. In this way, the hydraulic decompression module can be switched on and off within the respective working cycle.
  • the drive unit according to the invention is particularly suitable as a press drive, the piston being used for forming a workpiece and drives from movable tool, the present invention is mainly explained below with reference to this use. However, a limitation of the invention to this use cannot be derived from this.
  • the effective interaction of the hydraulic accumulator of the hydraulic decompression module with the second hydraulic working space can be restricted to a (preferably small) part of the working cycle (more or less adjacent to the bottom dead center of the piston), so that during the predominant one Share of the respective work cycle of the hydraulic accumulator is separated from the second hydraulic work space.
  • the hydraulic fluid displaced from the second hydraulic working chamber after the decompression module is switched on (by opening the loading / unloading valve) when the piston approaches the bottom dead center is displaced into the hydraulic accumulator of the decompression module via the line arrangement.
  • the point at which the hydraulic decompression module is activated effectively when the piston moves downward is preferably selected so that the hydraulic energy stored in the hydraulic accumulator of the decompression module and the volume of hydraulic fluid stored are sufficient to support the piston during the (an active "return stroke creep speed" including) decompression phase so that there is no longer any contact between the tool and the workpiece.
  • a hydraulic accumulator in the rest of the hydraulic system which is characteristic of the present invention, in particular allows the pressure conditions in the two hydraulic work spaces decouple the cylinder-piston arrangement and the movement of the piston in the particularly critical phase of the pressure reduction in the first hydraulic working space and the onset of the return movement of the piston from the interaction with a formed workpiece or the like, by said pressure reduction in the first hydraulic Working space and the beginning return movement of the piston is not a force induced in the piston by the workpiece or the like to be formed, but rather the hydraulic pressure induced in the second hydraulic working space by the decompression module. In this way it is possible, among other things, to achieve good reproducibility of the work cycle and to carry out the process particularly gently for the workpiece.
  • the return stroke of the piston in the decompression phase is, moreover, not determined and limited by the elastic springback of the workpiece and the machine parts deformed elastically during pressing; rather, the decompression module specifies the degree of return stroke of the piston in the decompression phase. So in the Decompression phase, which, depending on the individual execution of the cycle, can also represent a "return stroke creep speed", by means of the decompression module the pistons are continuously, steadily and jerk-free (actively) raised so that there is no longer any contact between the tool and the workpiece.
  • Discontinuities such as those that occur due to various switching processes, when switching to the active lifting of the piston in rapid traverse (by applying the second hydraulic working chamber from the hydraulic pump in pump mode) cannot have a detrimental effect on the workpiece in this way.
  • the hydraulic pump since in that braking mode in the "decompression phase" the hydraulic pump remains connected to the first hydraulic work area, the effective piston area of which is regularly many times larger than the effective piston area of the second hydraulic work area, a particularly sensitive movement control of the piston is also possible, decidedly more sensitive than in the return stroke with active loading of the second hydraulic work space from the hydraulic pump.
  • powder presses can also be designed using drive units according to the invention, in which the green compact is then treated particularly gently, so that a particularly low error and reject rate can be achieved. Because of their outstanding characteristic The present invention is also very well suited for use in press brakes for sensor-controlled bending.
  • the steady and jerk-free active decompression stroke possible in application of the invention is ideal until the tool is completely lifted off the workpiece or beyond. This is evidently also true when going through several post-bending cycles in "shuttle operation".
  • the present invention also proves to be extremely useful in forming processes which are carried out using bending aids as a result of the specific workpiece geometry; because the full path control during active decompression enables a controlled transfer of the workpiece to the bending aid.
  • the decompression module can be switched on via the loading / unloading valve in the switching phase that is present anyway at the end of the rapid traverse (operated in braking mode) (see above). This is favorable with regard to the possibility of a time-coordinated shut-off of the line connection of the second hydraulic work space to the tank.
  • the like is not mandatory;
  • a later activation of the decompression module may also offer advantages only when the piston is in motion. Limiting the effective connection of the decompression module to the part of the work cycle required to achieve the advantages described above has a positive effect, inter alia, in that the hydraulic accumulator of the decompression module can be designed accordingly small.
  • the capacity of the hydraulic accumulator of the decompression module can be significantly smaller than the maximum volume of the second hydraulic work space, for example only less than 30% of it.
  • the loading / unloading valve can in particular open in a pressure-controlled manner, the control pressure line communicating with the first hydraulic working space.
  • the decompression module is to a certain extent automatically switched on at the beginning or during the power train when a predefined pressure value is reached in the first hydraulic working space. If activation is desired right at the start of the power gear, the threshold value that switches the load / unload valve is matched to the pressure jump that occurs in the first hydraulic work space during the transition from rapid gear to power gear.
  • the threshold value switching the loading / unloading valve can be matched, for example, to the pressure jump that occurs when the tool is placed on the workpiece.
  • an even later switching point can possibly be set, namely more or less towards the end of the power gear at a correspondingly high pressure in the first hydraulic work space.
  • the decompression module When the hydraulic pump switches to braking operation in such a way that hydraulic fluid braked flows back from the first hydraulic working space (via the hydraulic pump working in braking operation) back into the tank, the decompression module is effective as long (in the sense of loading the second hydraulic working space out of the hydraulic accumulator via the line arrangement with the loading / unloading valve open) until the pressure in the first hydraulic working space falls below the switching pressure of the loading / unloading valve again. From then on, the further work cycle proceeds without the action of the decompression module.
  • the hydraulic accumulator is automatically charged during the work cycle only during the power train or even only a part of it, from the second hydraulic work space to the extent that it is for the application of the second hydraulic work area from the hydraulic accumulator is required during the phase of controlled active decompression (possibly including a return stroke creep speed).
  • the line arrangement comprises a first connecting line with a pressure limiting valve with a flow direction from the second hydraulic work space to the hydraulic accumulator and a second connecting line with a check valve opening in the flow direction from the hydraulic accumulator to the second hydraulic work space, the loading / unloading valve in one for the first connecting line and the second Connection line common wiring harness is arranged.
  • Yet another preferred development of the invention is characterized in that the means of the Machine control in a braking mode with a reversible direction of rotation and flow direction hydraulic pump is designed as a 2-quadrant pump.
  • This further development uses the possibility of using comparatively simple, inexpensive and reliable pump technology for the implementation of the concept on which the invention is based.
  • a filter unit is connected between the working connection of the hydraulic pump and the valve arrangement.
  • the filter unit comprises a filter through which the hydraulic fluid delivered by the hydraulic pump flows in pump operation. In braking mode, the hydraulic fluid is led past the filter unit via a bypass.
  • This arrangement and design of the filter unit is characterized by a particularly high efficiency.
  • the electro-hydraulic drive unit according to the in the Figures 1 and 2nd illustrated first embodiment corresponds to a significant extent to that drive unit, as in the DE 202015106161 U1 is described and explained in detail.
  • the scope of this agreement with the prior art is based on a separate, detailed explanation at this point waived and instead the DE 202015106161 U1 the entire disclosure content of which is made by reference to the content of the present patent application.
  • the illustrated electrohydraulic drive unit as it is particularly suitable for use on a machine press, such as a straightening, bending or folding press, or else a powder press, comprises a hydraulic cylinder-piston arrangement 1, a hydraulic pump 3 driven by an electric motor 2 with variable speed ( 2-quadrant pump) with a tank connection T and a working connection P, a hydraulic fluid storage tank 4, a plurality of electrically controllable switching valves S1, S2, S3, S4, connected between the working connection P of the hydraulic pump 3 and the hydraulic cylinder-piston arrangement 1, S5 and S6 comprehensive valve arrangement and - not shown - a machine control acting on the switching valves S1 - S6 and the electric motor 2.
  • the cylinder-piston arrangement 1 is double-acting; it has a first hydraulic working chamber 5 on the piston side and a second hydraulic working chamber 6 on the piston rod side.
  • the cylinder-piston arrangement 1 is oriented with a vertical movement axis X of the piston 7 in such a way that the first hydraulic working space 5 is arranged above the second hydraulic working space 6. Pressurizing the first hydraulic working space 5 by means of the hydraulic pump 3 results in a downward movement, but pressurizing the second hydraulic working space 6 results in an upward movement of the piston 7.
  • a Nachsaugventil 8 switched by through which the first hydraulic working space 5 is filled with hydraulic fluid during a downward movement of the piston 7 in rapid traverse.
  • the drive unit has a hydraulic decompression module 9.
  • This comprises a hydraulic accumulator 10, which can be connected to the second hydraulic working space 6 via a line arrangement L.
  • the line arrangement L in this case comprises two different connecting lines 11 and 12, which, however, in some areas have a matching common line line 13 with a charge / discharge valve 14 arranged therein.
  • the hydraulic accumulator 10 of the hydraulic decompression module 9 can be connected to the second hydraulic working chamber 6 via a first connecting line 11 with a pressure limiting valve 15 with the flow direction from the second hydraulic working chamber 6 to the hydraulic accumulator 10; the first connecting line 11 thus represents a “charging line” for the hydraulic accumulator 10.
  • the hydraulic accumulator 10 can be connected via a second connecting line 12 to a check valve 16 opening in the flow direction from the hydraulic accumulator 10 to the second hydraulic working chamber 6; the second connecting line 12 thus represents a “discharge line” for the hydraulic accumulator 10.
  • the loading / unloading valve 14 opens (and closes) under pressure control, that is, as a function of a control pressure.
  • the control pressure is the pressure prevailing in the first hydraulic working space 5.
  • the control pressure line 17 of the loading / unloading valve 14 communicates with the first hydraulic work space 5.
  • the switching pressure threshold of the loading / unloading valve 14 is set so that this is already the case (due to the pressure relief valve 15) at the beginning of the power gear in the first hydraulic working space 5 opens pressure.
  • the representation of the switching and operating states is partially schematic, namely in the sense that instead of the gradual change in the speed of the electric motor explained above, a sudden change is shown. Accordingly, the piston movement is also characterized by discontinuities.
  • the electric motor 2 driving the hydraulic pump 3 is first operated at a speed which is reduced in comparison with the phase upward rapid traverse (VII); and the suction valve 8 is initially not yet switched to continuous flow, since the switching valve S5 initially remains energized as during phases II-VI, so that the hydraulic fluid is displaced through the valve arrangement from the first hydraulic working chamber 5 into the tank 4.
  • a filter unit 18 is connected between the working port P of the hydraulic pump 3 and the valve arrangement, by means of which the entire hydraulic fluid delivered by the latter is cleaned by the filter 19 in the pumping operation of the hydraulic pump 3. Only when the filter 19 is clogged does the hydraulic fluid delivered by the hydraulic pump 3 flow via the "small" bypass 20, in which the check valve 21 acts as a pressure relief valve and opens when the filter 19 is loaded or clogged, in order to prevent a filter breakage. In the braking operation of the hydraulic pump 3, the hydraulic fluid flows past the filter unit 18 via the “large” bypass 22 with the check valve 23.
  • Fig. 3 The second embodiment to which Fig. 3 is largely identical to the first embodiment according to the Figures 1 and 2nd . For this reason it is limited Fig. 3 even on just a section of the hydraulic circuit diagram, namely that part which shows the only modification.
  • the line arrangement L assigned to the decompression module 9, into which the charge / discharge valve 14 is integrated connects the hydraulic accumulator 10 of the decompression module 9 directly, ie without additional valves, to the second hydraulic working space 6 of the cylinder-piston arrangement 1.
  • the control of the loading / unloading valve 14 after Fig. 3 is done in the same manner as in the first embodiment.
  • the pressure relief valve 15 only serves here - during the power train - to generate such a counterpressure in the second hydraulic working chamber 6 (with the switching valve S1 blocked) that a downward movement of the piston 7 due to gravity alone is prevented.
  • the hydraulic decompression module - due to the sudden increase in pressure then occurring in the first hydraulic working space - switches on at the beginning of the power train, ie in the changeover phase, at the same time - by controlled closing of the switching valve S2 -
  • the outflow of the liquid displaced from the second hydraulic working space to the tank is prevented.
  • a shift of the connection of the hydraulic decompression module to a later operating point for example that caused by putting on the "Clamping point" characterized on the workpiece by specifying a correspondingly higher switching pressure threshold for the loading / unloading valve would go hand in hand with a modification of the hydraulic system.
  • the switching valve S2 would remain correspondingly longer, ie at least still open during a first part of the power course; and expediently the simultaneous activation of the hydraulic decompression module (by hydraulic opening of the loading / unloading valve) by means of a likewise pressure-controlled valve connected in series with the switching valve S2 would prevent the outflow of the liquid displaced from the second hydraulic working space to the tank.
  • the loading / unloading valve of the hydraulic decompression module is not hydraulically operated, as in the exemplary embodiments, but rather is controlled electrically, it would be particularly easy to appropriately coordinate the hydraulic decompression module with simultaneous locking of the drain to the tank (e.g. location-controlled) realize any operating point of the gear train. In this case, the respective process management could be easily optimized in terms of need in terms of maximum efficiency.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (6)

  1. Unité d'entraînement électro-hydraulique, en particulier pour utilisation sur une presse, comprenant
    un ensemble vérin-piston (1) comprenant un premier espace de travail hydraulique (5) côté piston et un deuxième espace de travail hydraulique (6) côté tige,
    un réservoir (4) stockant le fluide hydraulique,
    une pompe hydraulique (3) entraînée à vitesse variable par un moteur électrique (2) comprenant un raccord de réservoir (T) et un raccord de travail (P),
    un ensemble de valves qui est disposé entre ledit raccord de travail (P) de la pompe hydraulique (3) et ledit ensemble vérin-piston (1) et qui comprend des valves de commutation (S1 - S6) à commande électrique,
    un clapet anti-cavitation (8) disposé entre le réservoir (4) et ledit premier espace de travail hydraulique (5) dudit ensemble vérin-piston (1), et
    une commande de machine qui agit sur les valves de commutation (S1 - S6) et le moteur électrique (2) et moyennant laquelle les valves de commutation (S1 - S6) sont aptes à être commutées entre une pressurisation dudit premier espace de travail hydraulique (5) et dudit deuxième espace de travail hydraulique (6) de l'ensemble vérin-piston (1) en mode de pompage de la pompe hydraulique (3) par son raccord de travail (P),
    caractérisée en ce qu'elle comprend un module de décompression hydraulique (9) comprenant un accumulateur hydraulique (10) qui est apte à être connecté avec ledit deuxième espace de travail hydraulique (6) par voie d'un ensemble (L) de conduits comprenant une valve de charge/décharge (14).
  2. Unité d'entraînement électro-hydraulique selon la revendication 1, caractérisée en ce que l'ouverture de ladite valve de charge/décharge (14) est effectue pilotée par pression, le conduit de pilotage (17) étant en communication avec ledit premier espace de travail hydraulique (5).
  3. Unité d'entraînement électro-hydraulique selon la revendication 1 ou 2, caractérisée en ce que ledit ensemble (L) de conduits comprend un premier conduit de connexion (11) comprenant une valve (15) de limitation de pression, le sens d'écoulement à travers celle-ci étant depuis ledit deuxième espace de travail hydraulique (6) audit accumulateur hydraulique (10), et un deuxième conduit de connexion (12) comprenant un clapet anti-retour (16), celui-ci étant en état ouvert lors d'un sens d'écoulement depuis ledit accumulateur hydraulique (10) audit deuxième espace de travail hydraulique (6), ladite valve de charge/décharge (14) étant disposée dans une ligne de conduit qui est commune audit premier conduit de connexion (11) et audit deuxième conduit de connexion (12).
  4. Unité d'entraînement électro-hydraulique selon l'une quelconque des revendications 1 à 3, caractérisée en ce que l'orientation de l'axe de mouvement du piston de l'ensemble vérin-piston (1) est essentiellement vertical, ledit premier espace de travail hydraulique (5) étant disposé en dessus dudit deuxième espace de travail hydraulique (6).
  5. Unité d'entraînement électro-hydraulique selon l'une quelconque des revendications 1 à 4, caractérisée en ce qu'une unité de filtration (18) est disposée entre ledit raccord de travail (P) de la pompe hydraulique (3) et ledit ensemble de valves.
  6. Unité d'entraînement électro-hydraulique selon l'une quelconque des revendications 1 à 5, caractérisée en ce que ladite pompe hydraulique (3) est une pompe à opération dans 2 quadrants et elle est apte à être commutée, par la commande de machine, à un mode de freinage présentant un sens de rotation et d'écoulement inverse au mode de pompage.
EP17772687.4A 2016-10-05 2017-09-21 Groupe d'entraînement électo-hydraulique Active EP3523120B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102016118854.9A DE102016118854A1 (de) 2016-10-05 2016-10-05 Elektrohydraulische Antriebseinheit
PCT/EP2017/073886 WO2018065226A1 (fr) 2016-10-05 2017-09-21 Groupe d'entraînement électo-hydraulique

Publications (2)

Publication Number Publication Date
EP3523120A1 EP3523120A1 (fr) 2019-08-14
EP3523120B1 true EP3523120B1 (fr) 2020-04-22

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP17772687.4A Active EP3523120B1 (fr) 2016-10-05 2017-09-21 Groupe d'entraînement électo-hydraulique

Country Status (3)

Country Link
EP (1) EP3523120B1 (fr)
DE (1) DE102016118854A1 (fr)
WO (1) WO2018065226A1 (fr)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021006222B3 (de) 2021-12-16 2023-04-20 Hydac International Gmbh Pressenvorrichtung und 2/2-Wege-Proportional-Sitzventil

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EP0103727A1 (fr) 1982-09-02 1984-03-28 Inventio Ag Dispositif de réglage de synchronisation pour la commande électrohydraulique d'une presse à plier
DE4036564A1 (de) 1990-11-16 1992-05-21 Bosch Gmbh Robert Hydraulische einrichtung zur steuerung eines arbeitszylinders einer presse
DE4314801B4 (de) 1993-05-05 2004-09-09 Bosch Rexroth Ag Hydraulische Anlage, insbesondere für eine Abkantpresse
DE102005029822A1 (de) 2005-04-01 2006-10-05 Bosch Rexroth Aktiengesellschaft Hydraulische Umformanlage
AT505724B1 (de) * 2007-09-12 2010-06-15 Trumpf Maschinen Austria Gmbh Antriebsvorrichtung für eine biegepresse
DE102009058408A1 (de) 2009-07-09 2011-01-13 Robert Bosch Gmbh Elektrohydraulische Steuerung
DE102009052531A1 (de) 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
WO2012062416A1 (fr) * 2010-11-11 2012-05-18 Robert Bosch Gmbh Essieu hydraulique
TR201101488A2 (tr) 2011-02-16 2012-03-21 Ermaksan Maki̇na Sanayi̇ Ve Ti̇caret Anoni̇m Şi̇rketi̇ Düşük gürültü seviyesine sahip enerji tasarruflu abkant pres
DE102012013098B4 (de) 2012-06-30 2014-08-07 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102012020581A1 (de) * 2012-10-22 2014-04-24 Robert Bosch Gmbh Hydraulische Schaltung für eine hydraulische Achse und eine hydraulische Achse
DE102014005352B4 (de) 2014-04-11 2016-03-10 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE202015106161U1 (de) 2015-11-13 2015-11-27 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit

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Also Published As

Publication number Publication date
WO2018065226A1 (fr) 2018-04-12
EP3523120A1 (fr) 2019-08-14
DE102016118854A1 (de) 2018-04-05

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