EP0103727A1 - Gleichlaufregelungseinrichtung für den elektrohydraulischen Antrieb einer Abkantpresse - Google Patents

Gleichlaufregelungseinrichtung für den elektrohydraulischen Antrieb einer Abkantpresse Download PDF

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Publication number
EP0103727A1
EP0103727A1 EP83107762A EP83107762A EP0103727A1 EP 0103727 A1 EP0103727 A1 EP 0103727A1 EP 83107762 A EP83107762 A EP 83107762A EP 83107762 A EP83107762 A EP 83107762A EP 0103727 A1 EP0103727 A1 EP 0103727A1
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EP
European Patent Office
Prior art keywords
pump
pumps
hydraulic cylinder
control device
driven
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.)
Withdrawn
Application number
EP83107762A
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German (de)
English (en)
French (fr)
Inventor
Theo Frei
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.)
Inventio AG
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Inventio AG
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Filing date
Publication date
Application filed by Inventio AG filed Critical Inventio AG
Publication of EP0103727A1 publication Critical patent/EP0103727A1/de
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/17—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors using two or more pumps
    • 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
    • B30B15/24—Control arrangements for fluid-driven presses controlling the movement of a plurality of actuating members to maintain parallel movement of the platen or press beam
    • 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
    • F15B2211/20576—Systems with pumps with multiple pumps
    • 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
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding valves
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • 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
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41563—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and a return line
    • 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
    • F15B2211/40—Flow control
    • F15B2211/45—Control of bleed-off flow, e.g. control of bypass flow to the return line
    • 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups

Definitions

  • the invention relates to a synchronization control device for the electrohydraulic drive of a press brake, the drive having devices for generating the forward, working and creep speed as well as the return speed of the hydraulic cylinders of the press brake, and wherein a displacement feedback device is provided in the synchronization control device for each hydraulic cylinder, and the synchronism of the hydraulic cylinders can be regulated as a function of the control deviation formed from the difference between the actual travel values.
  • a synchronization control device according to the preamble has become known.
  • the hydraulic cylinders are driven by a pump driven by an electric motor.
  • the actuator is a two-stage servo valve in the spool design provided, with each cylinder being assigned a servo valve.
  • the synchronism is achieved in that the position of the two cylinders is continuously recorded by means of the actual position encoder and the control deviation determined from the difference between the actual position values is fed to the servo valve of the faster cylinder.
  • the servo valves used as actuators are relatively expensive, can get dirty very easily and are therefore quite prone to failure. In addition, they act like throttle elements, so that additional energy losses occur.
  • each hydraulic cylinder has a separate drive, the drives being simultaneously designed as an actuator.
  • two further pumps are provided, driven by a common, non-controllable electric motor, which are connected in parallel to the pumps of the drives designed as actuators.
  • the actuator is assigned to only one hydraulic cylinder, the other hydraulic cylinder being operated by a pump driven at a constant speed.
  • the advantages achieved by the invention are, in particular, that in one embodiment an actuator with only one pump and one controllable electric motor is required.
  • the actuator has a pump and a controllable electric motor for each hydraulic cylinder
  • the advantages are that the pumps of the actuator serve simultaneously to drive the hydraulic cylinders and the plunger in synchronism in a horizontal position or in an inclined position downwards can be driven.
  • the proposed actuator has a robust design, is not prone to malfunction and causes practically no energy losses.
  • Z1 and Z2 denote the hydraulic cylinders of a press brake, which are actuated by pumps P1, P2, which can be driven by means of controllable direct current motors M1, M2.
  • the direct current motors M1, M2 can be, for example, direct current shunt motors, the speeds of which can be regulated by changing the armature voltage by means of thyristors.
  • S1 and S2 designate filling valves, by means of which the hydraulic cylinders ZI, Z2 are filled during the advance and emptied during the return, the hydraulic fluid being one container each ter Rl, R2 is removed or supplied.
  • the filling valves S1, S2 are controlled via a control system STS.
  • a first, the first hydraulic cylinder Z1 and a second, the second hydraulic cylinder Z2 associated pressure relief valve DB1, DB2 is set so that the pressure is slightly above that generated by the weight of the ram and punch of the press brake.
  • Another pressure relief valve DBG which is connected to the outputs of pumps P1, P2 via check valves RV1, RV2, is assigned to both hydraulic cylinders Z1, Z2 and set to the maximum pressing force of the press brake.
  • Each hydraulic cylinder Z1, Z2 is assigned a flow valve V1, V2 which is open during the advance and which is connected on the one hand to the input of the relevant pump P1, P2 and on the other hand to the lower end of the associated hydraulic cylinder Z1, Z2.
  • Each hydraulic cylinder Z1, Z2 is also assigned a return valve W1, W2, which is connected on the one hand to the outlet of the pump P1, P2 in question and on the other hand in a first position at the upper end and in a second position at the lower end of the associated hydraulic cylinder Z1, Z2.
  • the pumps P1, P2 are connected on the suction side to a further hydraulic fluid container R3 via further check valves RV3, RV4.
  • the actual travel value transmitters MS1, MS2 consist, for example, of code rulers and code reading devices, the actual travel values determined being fed to a digital subtractor in order to form a control deviation.
  • the control device can also be designed, for example, in such a way that the output of the digital subtractor is connected via a DA converter to a control amplifier, the output variable of which is fed to a subordinate speed control loop as a setpoint, the output of the speed controller being connected to an actuator which is made from an ignition angle control , the thyristors, the DC shunt motors M1, M2 and the pumps P1, P2 is formed.
  • the work step means the slow closing of the press brake.
  • Switching takes place by closing the flow valves V1, V2, the brake pressure occurring being limited by the pressure relief valves DB1, DB2.
  • the filling valves S1, S2 are now also closed with a slight delay, so that the pumps P1, P2 deliver from the hydraulic fluid container R3 into the closed cylinder spaces, the hydraulic fluid on the piston ring sides being discharged via the pressure-limiting valves DB1, DB2 and the working speed that is established depending of the pump speed.
  • the hydraulic cylinders Z1, Z2 cannot advance because of the ram weight, since the hydraulic fluid can only be displaced via the pressure relief valves DB1, DB2.
  • the return flow is initiated when the exact end position of the ram is reached.
  • the return valves W1, W2 are switched over, the flow valves V1, V2 are closed and the filling valves S1, S2 are opened, the return speed being given by the pump speed.
  • FIG. 2 Compared to FIG. 1, further pumps P3, P4 are provided in FIG. 2, which are connected in parallel to pumps P1, P2 and are driven together by an asynchronous motor M3.
  • the outputs of the other pumps P3, P4 are connected to the hydraulic fluid container R3 via a reversing valve UV1.
  • the control of the flow, the operation and the return as well as the generation of the corresponding speeds takes place in the same way as in the embodiment according to FIG. 1, but with the hydraulic cylinders Z1, Z2 being driven by both pumps P1, P3 and P2, P4, respectively and the pumps P1-P4 are dimensioned accordingly smaller.
  • the Synchronous control takes place in the same way as in FIG. 1, with the difference that controllable direct current motors M1, M2 of lower power are provided.
  • the normal working speed may be too high, so that you have to continue with a creep speed.
  • the changeover from the work cycle to the creep speed is carried out by opening the reversing valve UV1, the pumps P3, P4 delivering into the hydraulic fluid container R3 and the creep speed being set in accordance with the small delivery rates of the pumps P1, P2.
  • the switchover from work operation to creep speed takes place by opening the reversing valves UV1, UV2, pump P4 pumping into pressure fluid container R3 on the one hand and pump P3 branching off a part of the delivery quantity predetermined by appropriate setting of the two-flow regulator SR into pressure fluid container R3.
  • the required creep speed is set here by the remaining delivery rate of pump P3 and the delivery rate of controllable pump P2.
  • the pump P3 driven by the asynchronous motor M3 at a constant speed and the first hydraulic cylinder Z1 are matched to one another in such a way that a specific speed can be achieved.
  • the actual travel value determined on the first hydraulic cylinder Z1 is now fed to the digital subtractor as the setpoint and the actual travel value determined on the second hydraulic cylinder Z2 as the actual value.
  • the speed of the DC shunt motor M2 and the pump P2 is adjusted via the thyristors in such a way that the speed of the delivery flow and thus of the second hydraulic cylinder Z2 is either reduced or enlarged until the synchronization of both hydraulic cylinders Z1, Z2 is established and the ram moves downwards in the horizontal position.
  • the embodiment according to FIG. 4 corresponds to the embodiment according to FIG. 3, however the two-flow controller SR is omitted and the reversing valve UV2 is connected on the output side to the input of the pump P4.
  • the input of the controllable pump P2 is connected to the input of the pump_P4 via a check valve RV5 and to the pressure fluid container R3 via a further check valve RV6.
  • the pump P4 works as a hydraulic motor, so that part of the drive energy expended is recovered.
  • the creep speed required for the first hydraulic cylinder Z1 results from the difference in the delivery rates of the pumps P3, P4 and for the second hydraulic cylinder Z2 from the delivery rate of the controllable pump P2, the delivery rates for both hydraulic cylinders Z1, Z2 at an average speed of the pump P2 are the same.
  • an adjustable DC motor for the actuator can also be used with an adjustable asynchronous motor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Presses (AREA)
  • Control Of Fluid Pressure (AREA)
EP83107762A 1982-09-02 1983-08-06 Gleichlaufregelungseinrichtung für den elektrohydraulischen Antrieb einer Abkantpresse Withdrawn EP0103727A1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH5214/82 1982-09-02
CH521482 1982-09-02

Publications (1)

Publication Number Publication Date
EP0103727A1 true EP0103727A1 (de) 1984-03-28

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP83107762A Withdrawn EP0103727A1 (de) 1982-09-02 1983-08-06 Gleichlaufregelungseinrichtung für den elektrohydraulischen Antrieb einer Abkantpresse

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EP (1) EP0103727A1 (ja)
JP (1) JPS5961600A (ja)

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2294977A (en) * 1994-11-09 1996-05-15 Nicholas John Funnell Hydraulic drive system
WO1997025532A1 (de) * 1996-01-10 1997-07-17 Aeroquip-Vickers Internatonal Gmbh Verlustarmer antrieb für mehrere hydraulische aktuatoren
EP1291467A1 (en) * 2000-05-23 2003-03-12 Kobelco Construction Machinery Co., Ltd. Construction machinery
DE102009052531A1 (de) 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
ITMI20111408A1 (it) * 2011-07-27 2013-01-28 Promau Srl Apparato e metodo per il controllo elettroidraulico del parallelismo in una calandra per la lavorazione di manufatti in metallo
CN104088835A (zh) * 2014-07-06 2014-10-08 上海宏信设备工程有限公司 组合式螺纹自锁的液压冗余钢支撑轴力补偿系统
CN104088858A (zh) * 2014-07-06 2014-10-08 上海宏信设备工程有限公司 电源及液压冗余的螺纹自锁型轴力补偿系统
CN104196807A (zh) * 2014-09-18 2014-12-10 芜湖高昌液压机电技术有限公司 二柱龙门举升机液压马达同步回路
CN104405705A (zh) * 2014-09-18 2015-03-11 芜湖高昌液压机电技术有限公司 二柱龙门举升机自校正液压马达同步回路
DE202015106161U1 (de) 2015-11-13 2015-11-27 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
DE102016118853B3 (de) * 2016-10-05 2017-10-26 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
DE102016118854A1 (de) 2016-10-05 2018-04-05 Hoerbiger Automatisierungstechnik Holding Gmbh Elektrohydraulische Antriebseinheit
CN111347713A (zh) * 2018-12-20 2020-06-30 罗伯特·博世有限公司 特别是用于压力机或注塑机的静液的驱动器
CN114263780A (zh) * 2021-12-20 2022-04-01 山东大学 一种压力逐级升降自平衡的高压或超高压阀门切换系统
DE102021006222B3 (de) 2021-12-16 2023-04-20 Hydac International Gmbh Pressenvorrichtung und 2/2-Wege-Proportional-Sitzventil

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1125280B (de) * 1955-07-20 1962-03-08 Us Industries Inc Gleichlaufsteuerung fuer hydraulische Pressen, insbesondere Blechpressen
DE1577168A1 (de) * 1965-09-01 1971-10-07 Houdaille Industries Inc Angetriebenes Werkzeug
FR2214053A1 (ja) * 1973-01-11 1974-08-09 Picot Sa
EP0029223A2 (de) * 1979-11-15 1981-05-27 Politechnika Krakowska Hydraulisches Versorgungssystem einer Pulsationspresse

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1125280B (de) * 1955-07-20 1962-03-08 Us Industries Inc Gleichlaufsteuerung fuer hydraulische Pressen, insbesondere Blechpressen
DE1577168A1 (de) * 1965-09-01 1971-10-07 Houdaille Industries Inc Angetriebenes Werkzeug
FR2214053A1 (ja) * 1973-01-11 1974-08-09 Picot Sa
EP0029223A2 (de) * 1979-11-15 1981-05-27 Politechnika Krakowska Hydraulisches Versorgungssystem einer Pulsationspresse

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
\LHYDRAULIK UND PHEUMATIK, Band 24, Nr. 6, 1980, Seiten 462,465,466, Mainz (DE); *

Cited By (30)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2294977A (en) * 1994-11-09 1996-05-15 Nicholas John Funnell Hydraulic drive system
GB2294977B (en) * 1994-11-09 1997-08-06 Nicholas John Funnell Hydraulic drive system
WO1997025532A1 (de) * 1996-01-10 1997-07-17 Aeroquip-Vickers Internatonal Gmbh Verlustarmer antrieb für mehrere hydraulische aktuatoren
US6205780B1 (en) 1996-01-10 2001-03-27 Aeroquip-Vickers International Gmbh Low-loss drive system for a plurality of hydraulic actuators
EP1291467A1 (en) * 2000-05-23 2003-03-12 Kobelco Construction Machinery Co., Ltd. Construction machinery
EP1291467A4 (en) * 2000-05-23 2008-01-23 Kobelco Constr Machinery Ltd CONSTRUCTION MACHINE
US9044913B2 (en) 2009-11-11 2015-06-02 Hoerbiger Automatierungstechnik Holding GmbH Machine press
WO2011057773A2 (de) 2009-11-11 2011-05-19 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
DE102009052531A1 (de) 2009-11-11 2011-05-12 Hoerbiger Automatisierungstechnik Holding Gmbh Maschinenpresse
ITMI20111408A1 (it) * 2011-07-27 2013-01-28 Promau Srl Apparato e metodo per il controllo elettroidraulico del parallelismo in una calandra per la lavorazione di manufatti in metallo
EP2551029A1 (en) * 2011-07-27 2013-01-30 Promau S.R.L. Apparatus and method for the electrohydraulic control of parallelism in a bending machine for working metal products
US9669443B2 (en) 2011-07-27 2017-06-06 Promau S.R.L. Apparatus and method for the electrohydraulic control of parallelism in a bending machine for working metal products
US9468961B2 (en) 2011-07-27 2016-10-18 Promau S.R.L. Apparatus and method for the electrohydraulic control of parallelism in a bending machine for working metal products
CN104088835B (zh) * 2014-07-06 2016-05-18 上海宏信设备工程有限公司 组合式螺纹自锁的液压冗余钢支撑轴力补偿系统
CN104088835A (zh) * 2014-07-06 2014-10-08 上海宏信设备工程有限公司 组合式螺纹自锁的液压冗余钢支撑轴力补偿系统
CN104088858A (zh) * 2014-07-06 2014-10-08 上海宏信设备工程有限公司 电源及液压冗余的螺纹自锁型轴力补偿系统
CN104088858B (zh) * 2014-07-06 2016-05-18 上海宏信设备工程有限公司 电源及液压冗余的螺纹自锁型轴力补偿系统
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