EP3317088A1 - Unité d'entraînement hydroélectrique - Google Patents

Unité d'entraînement hydroélectrique

Info

Publication number
EP3317088A1
EP3317088A1 EP16795020.3A EP16795020A EP3317088A1 EP 3317088 A1 EP3317088 A1 EP 3317088A1 EP 16795020 A EP16795020 A EP 16795020A EP 3317088 A1 EP3317088 A1 EP 3317088A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
drive unit
cylinder
unit according
tank
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
EP16795020.3A
Other languages
German (de)
English (en)
Other versions
EP3317088B1 (fr
Inventor
Josef RITZL
Stefan GUTH
Roland Thurner
Ilker ÖZCANOGLU
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
Hoerbiger Automatisierungstechnik 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 Hoerbiger Automatisierungstechnik Holding GmbH filed Critical Hoerbiger Automatisierungstechnik Holding GmbH
Publication of EP3317088A1 publication Critical patent/EP3317088A1/fr
Application granted granted Critical
Publication of EP3317088B1 publication Critical patent/EP3317088B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/022—Systems essentially incorporating special features for controlling the speed or actuating force of an output member in which a rapid approach stroke is followed by a slower, high-force working stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B15/00—Fluid-actuated devices for displacing a member from one position to another; Gearing associated therewith
    • F15B15/18—Combined units comprising both motor and pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/26—Supply reservoir or sump assemblies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20538—Type of pump constant capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20561—Type of pump reversible
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3057—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having two valves, one for each port of a double-acting output member
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6651—Control of the prime mover, e.g. control of the output torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/775—Combined control, e.g. control of speed and force for providing a high speed approach stroke with low force followed by a low speed working stroke with high force, e.g. for a hydraulic press

Definitions

  • the present invention relates to a
  • electro-hydraulic drive unit in particular for use on a machine press.
  • Electrohydraulic drive units like them
  • the respective drive units are designed so that the piston (at least in one of the two directions of movement) with
  • Hydraulic unit is acted upon.
  • WO 2011/003506 AI US 2010/0212521 AI, AT 8633 Ul, DE 102012013098 AI, WO 2011/021986 AI, EP 103727 AI and DE 102013000725 AI.
  • the present invention is concerned with
  • Electro-hydraulic drive units as used for machine presses according to the second of the above-mentioned concepts (rapid downwards movement of the tool carrier / tool unit as a result of
  • Electro-hydraulic drive units include a
  • Switch valves comprehensive valve assembly and acting on the switching valves and the electric motor
  • Machine control by means of which the switching valves between a loading of the first hydraulic working space and the second hydraulic working space of the cylinder-piston assembly in the pumping operation of
  • Hydraulic pump from the pressure port are reversible.
  • Electro-hydraulic drive devices of the type in question here must in practice a number of Meet requirements that are partly in conflict with each other. Be required, depending on the
  • the present invention has set itself the task of providing an electro-hydraulic drive unit, which with regard to typical requirements, as in particular in applications of presses
  • the hydraulic pump is designed as a 2-quadrant hydraulic pump, which by means of a (in particular designed as a servo motor) electric motor in the pumping operation (for an active movement of the piston in both directions of movement, ie downwards for pressing in power and up to lift the tool carrier / tool Unit) in exactly one
  • predetermined direction of rotation is driven variable speed and a directly (ie., Typically, without further controls) opening in the tank
  • electro-hydraulic drive unit which also meets the other requirements set out above to a high degree.
  • electro-hydraulic drive unit the cylinder-piston assembly with at least substantially vertical
  • Moving direction of a downward movement and the second direction of movement corresponds to an upward movement of the piston.
  • the hydraulic pump is both in a first movement phase (rapid-down), while (via the valve assembly) is a flow connection of the second hydraulic working space of the cylinder-piston assembly with the pressure port of the hydraulic pump, as well as in a second movement phase (decompression-up ), in which there is a flow connection of the first hydraulic working space of the cylinder-piston arrangement with the pressure connection of the hydraulic pump, in the braking operation uncontrollable.
  • Throttle gets done in the decompression phase, d. H. in the second movement phase during the
  • a pressure-dependent control of the speed of the hydraulic pump driving - or in this mode of operation - braking electric motor a pressure-dependent control of the speed of the hydraulic pump driving - or in this mode of operation - braking electric motor.
  • a pressure sensor is provided in this case, which detects the pressure prevailing in the first hydraulic working space pressure and the signal is switched to the machine control.
  • the hydraulic pump is disposed inside lying in the tank. This allows a laid inside the tank flow to the pressure outlet of the
  • Hydraulic pump subsequent pressure line which represents a significant advantage from the standpoint of reliability and continues to be favorable to
  • Terminal block is provided with a first
  • Flange surface for connection to a valve block housing the switching valves and a second
  • Terminal block can in particular to a
  • Flange surface can each have a hydraulic
  • valve block is housed in a lateral recess of the tank.
  • valve block receiving recess may be arranged in one of the corner regions of the tank.
  • the invention is characterized in that a hydraulically releasable suction valve is arranged in the tank. Particularly advantageous is the arrangement of the
  • a connecting flange for direct connection with the cylinder of the cylinder-piston assembly exhibit.
  • the suction valve is completely in the - arranged outside the tank - flange and
  • connection block only the latter is connected via its second flange directly with the cylinder of the cylinder-piston assembly.
  • Suction valve can be provided via a control line with one on the flange and connection block
  • Control output be connected.
  • Flange and connection block stands on a channel with a control fluid interface on the first
  • Electro-hydraulic drive unit with distinct advantages (especially in the case of use as
  • Pre-assembled and tested units which are equipped with a mechanical interface to the respective cylinder-piston arrangement and thus easy to connect to the latter, resulting in minimal
  • the drive unit uses a small amount of hydraulic fluid. It has a low temperature dependence on a very high energy efficiency, so that usually neither a designated oil cooling time is provided, nor an oil cooler is needed. So can the drive unit have particularly small dimensions.
  • Valve control is a return stroke of the tool in
  • Tool clamping and crowning can be done without
  • Pressure sensors although such may certainly be provided with advantage in certain embodiments of the drive unit according to the invention (see above).
  • a variable displacement pump is not required.
  • Highly dynamic machine presses eg press brakes
  • Fig. 1 in perspective view a
  • Electro-hydraulic drive unit according to a first embodiment of the invention without the associated machine control
  • Electro-hydraulic drive unit according to a second embodiment of the invention without the associated machine control
  • the electro-hydraulic drive unit according to a first exemplary embodiment of the invention shown in FIGS. 1 and 2 comprises as main components a cylinder-piston arrangement 1 with a vertical movement axis Y, a tank 2 storing a hydraulic fluid
  • Hydraulic unit 3 with an electric motor 4 and a driven by this hydraulic pump 5 and a valve block 6 with a plurality of disposed thereon or housed therein hydraulically active elements
  • the cylinder-piston assembly 1 includes in a manner known per se linear in a cylinder 7 displaceable, connected to a piston rod 8 piston 9, through which the interior of the cylinder 7 is divided into two working spaces, namely a first hydraulic working space 10, which is so associated with a first direction of movement Yl of the piston, that during this increases its volume, and a second hydraulic working space 11 which is associated with a second movement direction Y2 of the piston, which is opposite to the first movement direction Y1, during which it increases its volume.
  • a first hydraulic working space 10 which is so associated with a first direction of movement Yl of the piston, that during this increases its volume
  • a second hydraulic working space 11 which is associated with a second movement direction Y2 of the piston, which is opposite to the first movement direction Y1, during which it increases its volume.
  • the existing installation position corresponds to the first
  • Movement direction Yl of the downward movement of piston 9 and piston rod 8 and the second direction of movement Y2 their upward movement.
  • the tank 2 which is ventilated via a ventilation filter 12, so that in it ambient pressure prevails (so-called.
  • open system has an L-shape. He thus has a lateral recess 13 in which the valve block 6 is housed. On one of the side walls of the tank 2, a level sensor 34 is arranged.
  • the hydraulic pump 5 is disposed inside the tank 2 ("under oil"). However, the drive 4 serving electric motor 4 is located outside of the tank 2, flanged to the bottom 14. Also in the tank 2 are a suction valve 15 and (with a major part of its volume) a flange and terminal block 16. However, the latter protrudes through corresponding openings in the side wall 17 and the bottom 14 of the tank 2 out of this. At the protruding through the side wall 17 of the tank portion 18 of the flange and
  • Terminal block 16 is a first flange 19 for Connection provided with the valve block 6; and on the protruding through the bottom 14 of the tank 2 portion of the flange and terminal block 16 is a second flange 21 for connection to the cylinder 7 of the cylinder-piston assembly 1.
  • 21 is respectively a
  • hydraulic interface which comprises two communicating with the two working spaces 10, 11 of the cylinder-piston assembly 1 working ports A, B.
  • the flange and connection block 16 has an opening 22, in which the Nachsaugventil 15 is inserted. This in turn has a connection flange for direct connection to the cylinder 7 of the
  • the Nachsaugventil 15 is hydraulically unlocked, what it over a - within the tank 2 routed - control line 23 with a provided on the flange and terminal block 16
  • Control terminal is connected, which in turn via a - the flange and terminal block 16 passing through
  • Control output of the valve block 6 communicates.
  • a near-ground opening intake 24 is provided.
  • Terminal block 16 provided pressure connection connected which in turn has a flange and
  • Terminal block 16 passing through channel and provided on the first flange 19 Druckfluid- interface with a pressure fluid port of the
  • Valve block 6 communicates.
  • Fig. 3 Hydraulic circuit is illustrated in Fig. 3. (To avoid misunderstanding, it should be noted that in Fig. 3 the line symbolizing the valve block 6 comprises the physical valve block 6 of Figures 1 and 2 together with the bodily flange and terminal block 16, these two components structurally separate according to Figures 1 and 2 could well be grouped into a single component)
  • Hydraulic unit 3 The control of the switching valves Sl to S6 and the servomotor 27 in the individual
  • phase I the servomotor 27 is at a standstill
  • the piston 9 is held redundantly by the group of closed switching valve S2 and closed pressure limiting valve 30 as well as the likewise closed switching valve S3 in the sense that the weight of the connected to the piston rod 8 components (eg tool carrier and
  • Hydraulic fluid are kept. (The safety valve 28, which is set to the maximum permissible system pressure plus an additional charge, is always closed in normal operation anyway.)
  • the switching valves Sl, S2, S3, S5 and S6 activated (switch position "I").
  • the second working space 11 (lifting-working space) of the cylinder-piston unit 7 is connected to the pressure port 29 of the hydraulic pump 5 via the (opened) switching valves S2 and S3 and the switching valve S5 opened according to bP.
  • the servomotor 27 rotates in reverse (operating state L *), d. H. in its braking operation, by the weight of the driven by the drive unit, with the
  • This Phase II extends to a - stored in the machine control - switching point, the freely programmable and is suitably chosen near the touchdown of the tool on the workpiece.
  • the servomotor 27 is at a standstill.
  • the switching valves S2, S4 and S5 are reversed, ie the switching valves S2 and S5 are deactivated (switching position "0") / and the switching valve S4 is activated (switching position "I").
  • the first working chamber 10 of the cylinder-piston assembly 7 via the switching valve S4 with the pressure side 29 of
  • Hydraulic pump 5 brought into fluid communication.
  • the second working chamber 11 of the cylinder-piston assembly 7 is in contrast via the pressure relief valve 30, the switching valve S3, the flow path BT of the switching valve S5 and the oil filter 20 with the tank side in
  • Servomotor 27 is also on the subsequent
  • throttle 31 is conveyed into the tank 2.
  • the switching valves S4, S5 and S6 are reversed, ie the switching valves S4 and S6 are deactivated (switching state "0") and the
  • Switching valve S5 is activated (switching state "I").
  • the suction valve 15 is opened (unlocked).
  • the second working space 11 of the cylinder-piston arrangement 7 is connected to the pressure side 29 of the hydraulic pump 5 via the admission pressure valve 32 and the two switching valves S3 and S2 (in each case through the path protected by the check valve).
  • Hydraulic fluid via the switching valve S4 (path aT) and the oil filter 20 into the tank 2 drain.
  • TDC top dead center
  • the hydraulic pump 5 can, if necessary, be put into operation to
  • Hydraulic fluid via the (opened) switching valve Sl through the oil filter 20 to promote.
  • an oil cooler 33 can be connected to the oil filter 20, connected in series therewith.
  • Fig. 3 it is illustrated that the switching valves Sl, S2, S3, S4 and S6 are equipped with a switch position monitoring 34. This can - in the case of lesser
  • an optional oil cooler 33 is provided, then this is
  • the oil supply to the oil cooler 33 takes place via a - inside the tank 2 laid pipe, which is connected to a provided on the flange and terminal block 16 cooling power connection, which in turn via a - the flange and terminal block 16 passing through - channel and at the first
  • Flange surface 19 provided cooling flow interface with a cooling flow connection of the valve block. 6
  • the flange and port block 16 ' is not located in the tank, but rather (completely) outside the tank 2'. He is namely below the tank 2 ', d. H.
  • a self-functional suction valve in a recess or an opening of the flange and terminal block in which a self-functional suction valve in a recess or an opening of the flange and terminal block
  • Connection is the (in the second embodiment provided) pressure-dependent control of the decompression by appropriate control of the hydraulic pump 5 in braking operation by the controller, for which purpose the signal of a hydraulic pressure in the first hydraulic working chamber detecting pressure sensor 34 is connected to the controller.
  • the filtering of the hydraulic fluid is designed differently.
  • a filter unit 35 is provided such that in the pumping operation of the hydraulic pump 5, the entire of
  • Pressure relief valve acts and loaded or
  • Embodiment provided switching valve Sl omitted; because there is the second
  • Embodiment no pure circulation filter operation more.
  • the second embodiment could make do with a switching valve less than the first

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Details Of Reciprocating Pumps (AREA)

Abstract

L'invention concerne une unité d'entraînement hydroélectrique, comprenant un ensemble de cylindre et piston (1) avec un premier espace de travail (10) hydraulique associé à une première direction de mouvement (Y1) du piston (9) et un second espace de travail (11) hydraulique associé à une seconde direction de mouvement (Y2) opposée du piston (9), un réservoir (2) stockant du fluide hydraulique, une pompe hydraulique (5) à 2 quadrants entraînée à régime variable dans précisément une direction de rotation prédéfinie lors du pompage au moyen d'un moteur électrique (4) avec un raccord de réservoir débouchant directement dans le réservoir (2) et un raccord de pression (29), un ensemble de soupapes branché entre le raccord de pression (29) de la pompe hydraulique (5) et l'ensemble de piston et cylindre (1), comprenant plusieurs soupapes de commutation (S1-S6) à actionnement électrique.
EP16795020.3A 2015-11-13 2016-11-10 Unité d'entraînement hydroélectrique Active EP3317088B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE202015106161.7U DE202015106161U1 (de) 2015-11-13 2015-11-13 Elektrohydraulische Antriebseinheit
DE102016119823.4A DE102016119823A1 (de) 2015-11-13 2016-10-18 Elektrohydraulische Antriebseinheit
PCT/EP2016/077348 WO2017081202A1 (fr) 2015-11-13 2016-11-10 Unité d'entraînement hydroélectrique

Publications (2)

Publication Number Publication Date
EP3317088A1 true EP3317088A1 (fr) 2018-05-09
EP3317088B1 EP3317088B1 (fr) 2019-08-14

Family

ID=54866550

Family Applications (1)

Application Number Title Priority Date Filing Date
EP16795020.3A Active EP3317088B1 (fr) 2015-11-13 2016-11-10 Unité d'entraînement hydroélectrique

Country Status (5)

Country Link
EP (1) EP3317088B1 (fr)
CN (1) CN108136707B (fr)
DE (2) DE202015106161U1 (fr)
ES (1) ES2755813T3 (fr)
WO (1) WO2017081202A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016114635B4 (de) 2016-08-08 2018-09-20 Hoerbiger Automatisierungstechnik Holding Gmbh Bearbeitungsmaschine
DE102016118854A1 (de) 2016-10-05 2018-04-05 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
DE102016118853B3 (de) 2016-10-05 2017-10-26 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
CN108435854A (zh) * 2018-03-27 2018-08-24 芜湖卓越空调零部件有限公司 一种空调储液器压缩机连接支架成型用曲面液压装置
DE102018126114A1 (de) * 2018-10-19 2020-04-23 Robert Bosch Gmbh Hydraulikaggregat
DE102018218113A1 (de) 2018-10-23 2020-04-23 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102021111207A1 (de) * 2021-04-30 2022-11-03 Voith Patent Gmbh Automatische Zugkupplung und Verfahren zum Entkuppeln einer automatischen Zugkupplung
CN113294408A (zh) * 2021-06-01 2021-08-24 天地上海采掘装备科技有限公司 紧凑式掘锚机泵站

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0103727A1 (fr) 1982-09-02 1984-03-28 Inventio Ag Dispositif de réglage de synchronisation pour la commande électrohydraulique d'une presse à plier
DE3734329A1 (de) * 1987-10-10 1989-04-20 Bosch Gmbh Robert Hydraulische steuereinrichtung fuer eine presse
JP3782710B2 (ja) * 2001-11-02 2006-06-07 日邦興産株式会社 油圧プレス装置
AT8633U1 (de) 2005-09-19 2006-10-15 Hoerbiger Automatisierungstech Hydraulikantriebseinheit
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
TR200906352A2 (tr) 2009-08-18 2010-12-21 Demi̇rer Teknoloji̇k Si̇stemler Sanayi̇ Ti̇caret Li̇mi̇ted Şi̇rketi̇ Hidrolik abkant preslerde enerji tasarrufu sağlayan bir yapılanma.
DE102012015118B3 (de) * 2012-04-17 2013-10-10 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102012013098B4 (de) 2012-06-30 2014-08-07 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102013000725B4 (de) 2013-01-17 2024-02-08 Robert Bosch Gmbh Elektrohydraulische Steuerung

Also Published As

Publication number Publication date
DE102016119823A1 (de) 2017-05-18
DE202015106161U1 (de) 2015-11-27
ES2755813T3 (es) 2020-04-23
CN108136707A (zh) 2018-06-08
CN108136707B (zh) 2020-05-29
EP3317088B1 (fr) 2019-08-14
WO2017081202A1 (fr) 2017-05-18

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