EP1625011B1 - Entrainement hydraulique - Google Patents

Entrainement hydraulique Download PDF

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Publication number
EP1625011B1
EP1625011B1 EP04732933A EP04732933A EP1625011B1 EP 1625011 B1 EP1625011 B1 EP 1625011B1 EP 04732933 A EP04732933 A EP 04732933A EP 04732933 A EP04732933 A EP 04732933A EP 1625011 B1 EP1625011 B1 EP 1625011B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
hydraulic drive
switching
drive mechanism
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.)
Expired - Lifetime
Application number
EP04732933A
Other languages
German (de)
English (en)
Other versions
EP1625011A1 (fr
Inventor
Stefan Schmidt
Rolf Heidenfelder
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.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
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 Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1625011A1 publication Critical patent/EP1625011A1/fr
Application granted granted Critical
Publication of EP1625011B1 publication Critical patent/EP1625011B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • B30B15/161—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03C—POSITIVE-DISPLACEMENT ENGINES DRIVEN BY LIQUIDS
    • F03C1/00—Reciprocating-piston liquid engines
    • F03C1/007—Reciprocating-piston liquid engines with single cylinder, double-acting piston
    • 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
    • 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
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • 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
    • F15B11/028—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force
    • F15B11/036—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the actuating force by means of servomotors having a plurality of working chambers
    • 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
    • F15B2211/20592—Combinations of pumps for supplying high and low pressure
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure control

Definitions

  • the invention relates to a hydraulic drive for a punching or forming machine according to the preamble of claim 1.
  • a working cylinder 2 is divided by a piston 4 into a piston bottom end cylinder chamber 6 and a piston rod side annular space 8.
  • the cylinder chamber 6 is supplied via a continuously adjustable valve 10 with pressure medium.
  • An input port E of the continuously variable valve 10 is connected to a valve assembly 12.
  • the valve arrangement 12 has a pilot-operated check valve 14 and a counter-blocking check valve 16 connected in parallel thereto.
  • the unlockable check valve 14 can be unlocked via a predetermined load pressure in the cylinder chamber 6. It is connected via a supply line 28 to a high-pressure accumulator HD.
  • the check valve 16 is connected via a supply line 32 with a low-pressure accumulator ND.
  • the annular space 8 is constantly connected to the low-pressure accumulator ND.
  • the continuously adjustable valve 10 and the valve assembly 12 For quick extension of the piston 4 are the continuously adjustable valve 10 and the valve assembly 12 in the illustrated basic positions.
  • the cylinder chamber 6 is acted upon by low pressure, so that the piston 4 expands quickly due to its area difference.
  • the pressure in the cylinder chamber 6 increases.
  • This load pressure is reported to the pilot operated check valve 14. From a certain load pressure this acts as a switching pressure and the check valve 14 is unlocked. Consequently, the high-pressure accumulator HD is switched on.
  • the high pressure is conducted to the input port E and thus into the cylinder chamber 6, so that a maximum punching force can be applied.
  • the high pressure is also applied to the check valve 16 so that it closes and the pressure medium connection to the low-pressure accumulator ND is shut off. After punching the load pressure in the cylinder chamber 6 decreases, whereby the pilot-operated check valve 14 resumes its basic position and the low-pressure accumulator ND is switched on.
  • a disadvantage of this known solution is that the check valve in the low pressure line only by means of a time delay of 2ms to 5ms closes, so that the pressurized high pressure fluid flows through the check valve to the low-pressure accumulator. At stroke times of about 10ms to 20ms for the extension of the working cylinder thus creates a significant loss of time and energy.
  • the drive unit has a working cylinder with a piston which separates an annulus from a cylinder space.
  • the annular space acts in the retraction direction and the cylinder space acts in the extension direction on the piston.
  • a motor-adjustable valve assembly with two mutually in mechanical operative engagement control valves of two control valves of the cylinder chamber with high pressure, low pressure or a tank pressure can be acted upon.
  • the annulus is constantly subjected to low pressure.
  • the spools are in contact with each other at the front and are biased by a spring in their basic positions.
  • a cam disc acting on one of the spools is controlled via an electric motor such that, depending on the rotation of the cam disc, the spools are transferred from their basic positions to control positions.
  • the cylinder chamber is subjected to low pressure. Due to the difference in the area of the piston, the latter extends until it hits a workpiece to be machined.
  • To apply a high punching force of the cylinder chamber is subjected to high pressure.
  • the cylinder space is depressurized to the tank, so that due to the low pressure acting in the annular space, the piston is moved back to its original position.
  • valve arrangement with the two control spools in contact with one another and the motor control is designed to be technically complex.
  • the object of the present invention is to provide a hydraulic drive for a stamping or forming machine in which no significant time and energy losses occur during pressure switching.
  • the drive unit has a working cylinder whose piston acts directly or indirectly on a workpiece to be machined. At least one pressure chamber of the working cylinder is acted upon for retraction and extension of the piston via a continuously adjustable valve with a tank pressure or a supply pressure. Furthermore, a valve arrangement is provided, which is connected upstream of the continuously adjustable valve, and via which an input terminal of the continuously adjustable valve with a higher or lower supply pressure can be acted upon. According to the invention, the valve arrangement has a switching valve which can be switched between a basic position and a switching position as a function of the load pressure on the working cylinder in order to tap the supply pressure from a low-pressure source or a high-pressure source.
  • the working cylinder has a cylinder space and an annulus.
  • the pressure in the cylinder chamber acts in the extension direction, and the pressure in the annulus acts in the retraction direction on the piston.
  • the pressure in the cylinder chamber acts on a large control surface of the switching valve and forms from a certain load pressure, the switching pressure for switching the switching valve in its switching position, in the opposite direction, the pressure in the annular space acts on a small control surface of the switching valve.
  • a pilot valve is provided, via which in the direction of the basic position effective small control surface of the switching valve is relieved, so that at reduced load pressure in the cylinder chamber, the switching valve can be switched and high pressure can be performed to the cylinder chamber.
  • the pilot valve is electrically operated.
  • the annulus can constantly be subjected to high pressure.
  • the annular space is constantly connected to the low-pressure source, since the annular surface is then larger and higher load capacity as a stop.
  • the working cylinder can have two or three pressure chambers.
  • FIG. 2 shows a highly simplified circuit diagram of a drive 1 of a high-speed nibbling machine. In such Nibbelmaschinen the extension movement takes place within 10 ms to 20 ms.
  • the nibbling machine has a working cylinder 2, which has a piston 4 as in the known solution described above, which separates a cylinder chamber 6 from an annular space 8 and acts directly or indirectly on a punching tool.
  • the piston 4 has a rear piston rod 18 which extends away from the piston crown and the working cylinder 2 passes through the front side.
  • the cylinder chamber 6 is connected to a working port A of a continuously adjustable valve 10 which in one of its control positions (b) opens a connection between the cylinder chamber 6 and a tank line 20 connected to a tank.
  • a tank line damper 22 and a biasing valve 24 are arranged in the tank line 20 in the tank line 20, a tank line damper 22 and a biasing valve 24 are arranged in the tank line 20 in the tank line 20, a tank line damper 22 and a biasing valve 24 are arranged.
  • the tank line damper 22 pressure fluctuations in the tank line 20 are suppressed and the biasing valve 24, the tank line 20 on biased to the spring of the biasing valve 22 equivalent pressure.
  • An input port P of the continuously variable valve 12 is connected to a working port B of a switching valve 26, which is connected to a pressure port P or a pressure port P 'of the switching valve 26 depending on the switching position (1), (2) of the switching valve 26.
  • the pressure port P is connected via a feed line 28 to a high pressure accumulator HD, and the pressure port P 'is connected via a branch line 30 and a portion of a feed line 32 with a low pressure accumulator ND.
  • the supply line 32 connects the low-pressure accumulator ND with the annular space 8.
  • the pressure in the annular space 8 is tapped via a control line 34 and an electrically operated pilot valve 38.
  • the pressure is led to a small control surface of the switching valve 26 which is effective in the direction of the basic position (1) of the switching valve 26.
  • a control position (y) of the pilot valve 38 the connection to the small control surface is shut off and a connection of the small control surface to the tank T is opened.
  • the pressure in the cylinder chamber 6 is tapped off via a control line 36 and led to an effective in the direction of the switching position (2) large control surface of the switching valve 26.
  • the switching valve 26 is in its illustrated basic position (1).
  • the pilot valve 34 is in its home position (x) and the pressure acting in the annulus 8 becomes the small control surface the switching valve 26 out.
  • the continuously adjustable valve 10 is in its illustrated basic position (a).
  • the cylinder chamber 6 is subjected to low pressure.
  • the annular space 8 is also supplied via the supply line 32 with low pressure, so that the piston 4 extends due to its area difference, wherein pressure medium is displaced from the annular space 8 in the low-pressure accumulator ND.
  • the load pressure in the cylinder chamber 6 increases.
  • this acts as a switching pressure and the switching valve 26 is brought against the force of a return spring and a force corresponding to the pressure acting on the small control surface in its switching position (2) in which the working port B to the pressure port P is connected so that high pressure on the piston bottom surface is effective and thus the force applied by the working cylinder 2 punching force is increased.
  • the switching valve 26 switches back to its normal position (1), in which the pressure port P is shut off and the pressure port P 'is turned on, so that at the working port B is again low pressure.
  • the continuously adjustable valve 10 is transferred to its designated (b) control positions, in which the cylinder chamber 6 is connected to the tank T. Due to the low pressure acting in the annular space 8, the piston 4 is pushed back to its original position.
  • the pilot valve 38 can be brought into its control position (y), in which the control line 34 shut off and the small control surface of the switching valve 26 is relieved of pressure to the tank.
  • the switching valve 26 is transferred against the force of the return spring from its basic position (1) in its switching position (2), so that the pressure port P 'shut off and the pressure port P is turned on. Accordingly, the cylinder chamber 6 is subjected to high pressure, so that even before the construction of the maximum load pressure, the maximum workforce is available.
  • the inventive solution with a continuously adjustable valve 10 upstream switching valve 26 can also be used in other cylinder designs, eg. With three pressure chambers.
  • a hydraulic drive for a punching or forming machine with a plurality of pressure chambers having working cylinder whose piston acts directly or indirectly on a workpiece to be machined, wherein at least one pressure chamber of the working cylinder for retraction or extension of the piston via a continuously adjustable valve with a Tank pressure or a supply pressure can be acted upon, and with a valve assembly which is connected upstream of the continuously variable valve and via which an input port of the continuously variable valve with a higher or lower supply pressure can be acted upon, the valve assembly having a switching valve, which in dependence on the load pressure on Working cylinder between a basic position and a switching position is switchable to tap the supply pressure from a low pressure source or a high pressure source.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Combustion & Propulsion (AREA)
  • Chemical & Material Sciences (AREA)
  • Control Of Presses (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Press Drives And Press Lines (AREA)
  • Valve Device For Special Equipments (AREA)
  • Hydraulic Clutches, Magnetic Clutches, Fluid Clutches, And Fluid Joints (AREA)
  • Multiple-Way Valves (AREA)
  • Fluid-Driven Valves (AREA)

Claims (7)

  1. Entraînement hydraulique pour une machine d'estampage ou de formage avec un cylindre de travail (2) comprenant plusieurs chambres de pression (6, 8) et dont le piston (4) agit directement ou indirectement sur une pièce à usiner, dans lequel au moins une chambre de pression (6) du cylindre de travail (2) peut être soumise à une pression de réservoir ou à une pression d'alimentation au moyen d'une soupape réglable en permanence (10) pour faire entrer ou sortir le piston (4), et avec un dispositif de soupape (26) qui est monté avant la soupape réglable en permanence (10) et par lequel un raccord d'entrée (E) de la soupape réglable en permanence (10) peut être soumis à une pression d'alimentation plus haute ou plus basse, dans lequel le dispositif de soupape (26) comporte une soupape de commande (26), qui peut être commutée entre une position de base (1) et une position de commande (2) en fonction de la pression de charge sur le cylindre de travail (2), caractérisé en ce que, dans la position de base (1), le raccord d'entrée (E) de la soupape réglable en permanence (10) est raccordé à la source à basse pression et dans la position de commande (2) le raccordement avec la source à basse pression (ND) est fermé et le raccord d'entrée (E) est raccordé à la source à haute pression (HD).
  2. Entraînement hydraulique selon la revendication 1, dans lequel le cylindre de travail (2) comprend une chambre annulaire (8) agissant dans la direction d'entrée et une chambre cylindrique (6) agissant dans la direction de sortie, et dans lequel la pression de charge agissant dans la chambre cylindrique (6) agit sur une grande face de commande de la soupape de commande (26).
  3. Entraînement hydraulique selon la revendication 2, dans lequel la grande face de commande est active en direction d'une position de commande (2) de la soupape de commande (26), et dans lequel une petite face de commande de la soupape de commande (26), agissant en direction de la position de base (1) de la soupape de commande (26), est raccordée à la source à basse pression (32) par une conduite de commande (34).
  4. Entraînement hydraulique selon la revendication 3, dans lequel une soupape pilote (38) est disposée dans la conduite de commande (34), par laquelle la petite face de commande peut être soumise à une pression de réservoir pour une commutation dépendant de la pression de charge.
  5. Entraînement hydraulique selon la revendication 4, dans lequel la soupape pilote (38) est actionnée électriquement.
  6. Entraînement hydraulique selon l'une quelconque des revendications précédentes, dans lequel la chambre annulaire (8) est en permanence raccordée à la source à basse pression (ND).
  7. Entraînement hydraulique selon l'une quelconque des revendications précédentes, dans lequel le cylindre de travail (2) est réalisé avec deux ou trois chambres de pression.
EP04732933A 2003-05-16 2004-05-14 Entrainement hydraulique Expired - Lifetime EP1625011B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10322169 2003-05-16
DE102004005020 2004-01-30
PCT/DE2004/001014 WO2004103692A1 (fr) 2003-05-16 2004-05-14 Entrainement hydraulique

Publications (2)

Publication Number Publication Date
EP1625011A1 EP1625011A1 (fr) 2006-02-15
EP1625011B1 true EP1625011B1 (fr) 2008-03-19

Family

ID=33420017

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04732933A Expired - Lifetime EP1625011B1 (fr) 2003-05-16 2004-05-14 Entrainement hydraulique

Country Status (6)

Country Link
US (1) US7370569B2 (fr)
EP (1) EP1625011B1 (fr)
JP (1) JP2007502213A (fr)
AT (1) ATE389530T1 (fr)
DE (2) DE102004024126A1 (fr)
WO (1) WO2004103692A1 (fr)

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CZ303050B6 (cs) * 2006-07-19 2012-03-14 Pitrík@Václav Zarízení pro ovládání hydraulického lisu
DE102007027603A1 (de) 2007-06-12 2008-12-18 Voith Patent Gmbh Hydraulischer Antrieb, insbesondere für Werkzeugmaschinen, und Verfahren zum Steuern des hydraulischen Antriebs
DE102009005998B4 (de) 2009-01-23 2012-12-27 Voith Patent Gmbh Hydraulische Antriebsvorrichtung mit zwei Druckräumen und Verfahren zum Betreiben einer hydraulischen Antriebsvorrichtung mit zwei Druckräumen
US9453805B2 (en) * 2010-01-19 2016-09-27 Celgard, Llc X-ray sensitive battery separators and related methods
US9003951B2 (en) 2011-10-05 2015-04-14 Caterpillar Inc. Hydraulic system with bi-directional regeneration
DE102011116477A1 (de) * 2011-10-20 2013-04-25 Hesta Blasformtechnik Gmbh & Co. Kg Verfahren zum Betrieb einer Blasformmaschine
CN104870833B (zh) * 2012-12-20 2019-12-13 Smc株式会社 流体压力缸
WO2017030475A1 (fr) * 2015-08-18 2017-02-23 Saab Ab Agencement d'actionneur à fluide
CN106337852B (zh) * 2016-11-16 2019-01-11 中南大学 二通插装式激振阀
WO2019040826A1 (fr) * 2017-08-24 2019-02-28 The Penn State Research Foundation Obturateur de buse commutée
EP3633184B1 (fr) * 2018-10-02 2022-01-12 GE Renewable Technologies Dispositif et procédé d'optimisation de fermeture de vanne annulaire
ES2944440T3 (es) * 2019-04-18 2023-06-21 Lapmaster Wolters Gmbh Método para operar un sistema de troquelado fino
US20230373714A1 (en) * 2022-05-23 2023-11-23 Ab Närpes Trä & Metall - Oy Närpiön Puu Ja Metalli Refuse compression apparatus and a method for operating refuse compression apparatus

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3219730A1 (de) 1982-05-26 1983-12-01 Robert Bosch Gmbh, 7000 Stuttgart Einrichtung zur steuerung eines hydraulischen servomotors
DE3221758A1 (de) * 1982-06-09 1983-12-15 Hartmann & Lämmle GmbH & Co KG, 7255 Rutesheim Hydraulische antriebsvorrichtung
DE3720266A1 (de) 1987-06-19 1988-12-29 Bw Hydraulik Gmbh Elektrohydraulisches regelsystem
DE3814580A1 (de) * 1988-04-29 1989-11-09 Eckehart Schulze Hydraulische steuereinrichtung fuer die antriebssteuerung eines doppelt-wirkenden hydrozylinders

Also Published As

Publication number Publication date
JP2007502213A (ja) 2007-02-08
WO2004103692A1 (fr) 2004-12-02
EP1625011A1 (fr) 2006-02-15
DE502004006585D1 (de) 2008-04-30
US7370569B2 (en) 2008-05-13
US20070012171A1 (en) 2007-01-18
ATE389530T1 (de) 2008-04-15
DE102004024126A1 (de) 2004-12-02

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