EP3002461B1 - Circuit hydraulique destine a alimenter un moyen de pression d'un verin differentiel - Google Patents

Circuit hydraulique destine a alimenter un moyen de pression d'un verin differentiel Download PDF

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Publication number
EP3002461B1
EP3002461B1 EP15182643.5A EP15182643A EP3002461B1 EP 3002461 B1 EP3002461 B1 EP 3002461B1 EP 15182643 A EP15182643 A EP 15182643A EP 3002461 B1 EP3002461 B1 EP 3002461B1
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EP
European Patent Office
Prior art keywords
tank
working line
pressure medium
hydraulic circuit
flow path
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
EP15182643.5A
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German (de)
English (en)
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EP3002461A1 (fr
Inventor
Gottfried Hendrix
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.)
Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3002461A1 publication Critical patent/EP3002461A1/fr
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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
    • F15B7/00—Systems in which the movement produced is definitely related to the output of a volumetric pump; Telemotors
    • F15B7/005—With rotary or crank input
    • F15B7/006—Rotary pump input
    • 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
    • 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
    • F15B2211/20561—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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/27—Directional control by means of the pressure source
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members

Definitions

  • the invention relates to a hydraulic circuit for supplying pressure medium to a differential cylinder according to the preamble of claim 1.
  • a differential volume flow In the case of a hydraulic circuit for supplying pressure medium to a differential cylinder, a differential volume flow must be taken into account, which results from a difference in area between a piston area delimiting a piston head space and an annular area of a piston delimiting an annular space.
  • a load hanging on the differential cylinder such as, for example, a press
  • the weight of the load acting on the differential cylinder in or against an actuation direction must be taken into account.
  • the DE 10 2009 058 408 A1 discloses an electro-hydraulic control for a safe electro-hydraulic axis, in which a reliable and as simple / inexpensive as possible implementation of occupational safety requirements is to be achieved in that two monitored switching valves are arranged one behind the other in a path that allows pressure medium to be discharged from a first working connection, and that there are at least two independently effective safety means which, in a predetermined state, limit a supply of pressure medium into a second working connection.
  • the JP 2001 259 900 A discloses a ram movement method in a hydraulic device, by means of which a ram should be able to be driven in the shortest possible time without a shock, that when a movement command of the ram from a Is given to a speed distribution processing unit, such an instruction is given that the ram command speed is suppressed to a predetermined warming-up speed, the warming-up speed being not greater than a target speed, before a release speed judging unit makes a judgment that the moving speed of the ram reaches the predetermined warming-up speed.
  • circuits of this type contain electrically operated switching valves in connection with variable displacement pumps or multiple pumps, which means an increased use of components, space requirements and control effort.
  • Pressure surges can also occur when switching the direction of actuation of the differential cylinder with electrically actuated switching valves.
  • the invention is based on the object of creating a simplified hydraulic circuit for supplying pressure medium to a differential cylinder with a suspended load.
  • a hydraulic circuit according to the invention for supplying pressure medium to a differential cylinder, via which a suspended load can be moved contains a bidirectional pressure medium source via which an annular space of the differential cylinder can be supplied with a first volume flow via a first working line of the hydraulic circuit, and via which a piston floor space of the differential cylinder can be supplied a second working line of the hydraulic circuit can be supplied with a second volume flow, the first volume flow being smaller than the second volume flow.
  • the hydraulic circuit according to the present invention contains a first check valve, via which a reduced amount of pressure medium caused by a difference in the volume flows can be sucked in from a pressure medium sink into the piston head space in order to enable at least one downward movement of the load caused by a weight of the load.
  • the first check valve can be unlocked via a first pressure in the first working line in such a way that when the load moves upwards, an excess amount of pressure medium caused by the difference in volume flows can be discharged from the piston head space into the pressure medium sink via the check valve.
  • a directional control valve is connected to the first working line in such a way that the annular space can only be connected to the pressure medium source, or the annular space and an annular space-side flow path of the pressure medium source can be connected to the pressure medium sink.
  • One advantage of the present invention is that the actuation direction of the differential cylinder is switched over, for example from extending to retracting the differential cylinder, solely by changing a conveying direction of the pressure medium source. This results in a reduced use of components, a reduced space requirement and a reduced control effort.
  • Another advantage is that the pressure medium in the piston head space or in the annular space can be compressed or decompressed simply by changing the conveying direction of the pressure medium source.
  • the resulting decompression energy can be used to pretension a respective piston counter space of the differential cylinder, whereby a stepless switchover of the operating direction of the differential cylinder is made possible.
  • a cylinder rod runs through the piston crown space, the cylinder rod in the piston crown space having a smaller diameter than the cylinder rod in the annular space.
  • the pressure medium source contains a bidirectionally operable hydraulic machine and a bidirectionally operable motor generator coupled therewith.
  • the bidirectionally operable hydraulic machine can be operated as a pump or as a motor.
  • the motor generator can be operated as a direction of rotation reversible and speed adjustable electric motor for driving the pump or as a direction of rotation reversible generator for converting hydrostatic energy into electrical energy.
  • the electric motor is designed in particular as a servomotor.
  • the above-mentioned change in the conveying direction of the pressure medium source is brought about by changing the direction of rotation and / or controlling the torque of the motor generator operated as an electric motor.
  • This enables the use of a fixed displacement pump instead of a variable displacement pump or a multiple pump, which simplifies the hydraulic circuit.
  • the direction of rotation of the motor generator operated as an electric motor dictates a conveying direction of the hydraulic machine operated as a pump, the conveying direction dictates an actuation direction of the differential cylinder.
  • the speed of the motor generator operated as an electric motor, by which the hydraulic machine operated as a pump can be driven, is adjustable in order to set a speed of the differential cylinder. A behavior during the above-mentioned decompression of the respective piston chamber can advantageously be influenced by a control of the motor generator.
  • a speed of the downward movement of the load which is caused in particular by the weight of the load, can be controlled via a discharge of the pressure medium from the annular space.
  • the discharge takes place in particular via the hydraulic machine operated as a pump.
  • the directional valve is designed as a 4/3-way valve or as an electromagnetically actuated first 2/2-way valve.
  • the 4/3-way valve is connected to the first working line between the hydraulic machine and the annular space.
  • the 4/3-way valve interrupts the first working line in a blocking position, opens the first working line in a first through position or connects the first working line in a second through position with a flow path from the hydraulic machine to the tank.
  • a flow path that branches off from the first working line between the hydraulic machine and the annular space and leads to the tank can be closed by the electromagnetically actuated first 2/2-way valve.
  • An electromagnetically actuable second 2/2-way valve, via which this flow path can be closed, is also advantageously arranged in a flow path between the 4/3 way valve and the annular space.
  • a third check valve is advantageously arranged between the 4/3-way valve and the tank and blocks in the direction of the tank.
  • a third 2/2-way valve is also advantageously arranged, via which the parallel connection to this flow path can be closed is.
  • a press brake is realized by means of the hydraulic circuit according to the invention, which has a variable-speed drive with a high rapid traverse speed and a high pressing speed at high pressure, and which has a fixed displacement pump and a variable-speed servomotor.
  • the hydraulic circuit according to the invention advantageously enables force, speed and position control.
  • FIG. 1 The circuit diagram shown shows a hydraulic circuit 1 according to the invention for supplying pressure medium to a differential cylinder 2 with a suspended load 4 according to a first exemplary embodiment in a hydraulic press.
  • the hydraulic circuit 1 has a pressure medium source 6 which contains a hydraulic machine 8 which is reversible in its direction of rotation and which can be operated bidirectionally and a motor generator 10 which is reversible in its direction of rotation and which is coupled to the hydraulic machine 8.
  • the bidirectional hydraulic machine 8 can be operated as a pump in both conveying directions or as a motor in both drive directions.
  • the bidirectional motor generator 10 can be operated as an electric motor in both drive directions or as a generator in both directions of rotation.
  • the direction of rotation of the motor generator 10 operated as an electric motor determines a conveying direction of the hydraulic machine 8 operated as a pump, the conveying direction requires an actuation direction of the differential cylinder 2.
  • the speed of the motor generator 10 operated as an electric motor, from which the hydraulic machine 8 operated as a pump can be driven, is adjustable by to set a speed of the differential cylinder 2.
  • the hydraulic machine 8 can be fluidically connected to the annular chamber 14 via an electromagnetically actuatable 4/3-way valve 16 which is connected to a first working line 12 between the hydraulic machine 8 and an annular space 14. Between the 4/3-way valve 16 and the annular space 14, a flow path branches off to a tank 18 in which a first pressure limiting valve 20 is arranged. In a parallel connection to this flow path, a fluid connection between this flow path and the 4/3-way valve 16 is established.
  • the hydraulic machine 8 is fluidically connected to a piston head space 24 via a second working line 22.
  • a flow path branches off from the second working line 22 to the tank 18, in which a first check valve 26 is arranged, which blocks a pressure medium connection from the piston head space 24 in the direction of the tank 18 and releases it in the opposite direction.
  • a difference in volume flow results from a difference between a piston area delimiting the piston crown space 24 and an annular area of a piston of the differential cylinder 2 delimiting the annular space 14, more precisely a difference between a first volume flow with which the annular space 14 can be supplied and a second volume flow with which the piston space 24 can be supplied.
  • the first check valve 26 is above a first pressure in the first working line 12 unlockable.
  • a flow path branches off between the piston base space 24 and the first check valve 26, which flow path leads to the tank 18 via a second pressure limiting valve 28.
  • a flow path branches off from the first working line 12 and leads via a second check valve 30 to the tank 18, this flow path from the second check valve 30 as a control line 32 to the first check valve 26 is continued.
  • the load 4 hangs on a cylinder rod 34 that extends at least partially through the annular space 14 and causes a load pressure on the pressure medium in the annular space 14.
  • This load pressure is in the illustrated case as a rule less than an opening pressure for the first pressure relief valve 20 and is therefore on the first pressure relief valve 20 and to the 4/3-way valve 16 switched to a blocking position, so that the load 4 is held in the position shown.
  • Figure 2 shows the hydraulic circuit Figure 1 in rapid downward traverse, which means that the load 4 is to be moved in the direction of gravity at a greater speed than in a pressing traverse.
  • the 4/3-way valve 16 is connected in the illustrated first through position via the first working line 12 to the annular space 14 and discharges pressure medium via the hydraulic machine 8 operated as a pump into the piston crown space 24, the hydraulic machine 8 from the motor generator 10 operated as an electric motor is driven accordingly. As a result, the downward movement is controlled and can therefore be carried out in a controlled manner.
  • Figure 3 shows a circuit diagram of the hydraulic circuit from Figure 1 in the pressing process, that is, the load 4 is to be driven at a lower speed than in the in Figure 2 are moved in the direction of gravity.
  • the 4/3-way valve 16 remains in the in Figure 2
  • the first passage position shown and the hydraulic machine 8 operated as a pump discharges pressure medium from the annular space 14, the hydraulic machine 8 being accordingly driven by the motor generator 10 operated as an electric motor.
  • the pressure medium is fed to the piston head space 24, the shortage of the pressure medium caused by the differently sized piston surfaces, which delimit the annular space 14 and the piston head space 24, as in FIG Figure 1 - is sucked out of the tank 18 via the second check valve 30 and fed to the hydraulic machine 8 via the flow path between the tank 18 and the first working line 12.
  • Figure 4 shows a circuit diagram of the hydraulic circuit from Figure 1 in a decompression phase, in which the particular under pressure from the previous one too Figure 3 Press process described standing pressure medium is relaxed.
  • the 4/3-way valve 16 is switched into a second passage position, whereby a flow path from the annular space 14 to the tank 18 is formed.
  • the hydraulic machine 8 is operated as a motor via the relieving pressure medium, the pressure medium being discharged from the piston crown space 24 into the tank 18 via a flow path established through the second passage position.
  • the hydrostatic energy which drives the hydraulic machine 8 operated as a motor, is converted into mechanical kinetic energy and converted into electrical energy by the generator operated as a generator 10, which is driven by the hydraulic machine 8 operated as a motor, into electrical energy, for example in a Energy storage device, not shown, can be stored, or which can be fed into an energy network.
  • the directional valve is designed as an alternative to the 4/3-way valve 16 as an electromagnetically actuated first 2/2-way valve which is connected to the first working line in such a way that a flow path, in particular a bypass, which flows from the first working line 12 branches off between the hydraulic machine 8 and the annular space 14 and leads to the tank 18, can be closed.
  • Figure 5 shows a circuit diagram of the hydraulic circuit from Figure 1 in rapid upward traverse, which means that the load 4 is to be moved at a greater speed than in a pressing traverse against the direction of gravity.
  • the 4/3-way valve 16 is already in Figure 1
  • the first passage position shown is connected to the annular space 14 via the first working line 12.
  • pressure medium is pumped from the piston crown space 24 into the annular space 14 via the hydraulic machine 8 operated as a pump, the hydraulic machine 8 being operated by the motor generator 10 operated as an electric motor in the other direction of rotation as in FIG Figure 1 is driven.
  • the pressure medium of the piston crown space 24 or of the annular space 14 can be compressed or decompressed.
  • a decompression energy released during decompression can be used to pretension the respective counter space of the piston of the differential cylinder 2. This preload by decompression effects a stepless changeover of the direction of actuation of the differential cylinder 2.
  • Figure 6 shows a circuit diagram of the hydraulic circuit according to the invention according to a second exemplary embodiment in a hydraulic press at a standstill, the second exemplary embodiment containing the components of the first exemplary embodiment and only the components added in relation to the first exemplary embodiment being described below.
  • an electromagnetically actuatable second 2/2-way valve 36 is arranged, via which this flow path can be closed.
  • a third check valve 38 is arranged between the 4/3-way valve 16 and the tank 18, which in the direction of the tank 18 blocks.
  • a third 2/2-way valve 40 is arranged via which this parallel connection can be closed to this flow path.
  • the second 2/2-way valve 36, the third check valve 38 and the third 2/2-way valve 40 as well as the 4/3-way valve 16 and the motor generator 10 are equipped in such a way that they meet the safety requirements of the applicable machinery directive.
  • Figure 7 shows a circuit diagram of the hydraulic circuit according to the invention according to a third embodiment in a hydraulic press at a standstill, the third Embodiment contains the components of the first embodiment and only the components added with respect to the first embodiment are described below.
  • a fourth 2/2-way valve 42 is arranged in the control line 32, which closes or opens the control line 32 and thus represents an electrical control of the first check valve 26.
  • Figure 8 shows a circuit diagram of the hydraulic circuit according to the invention according to a fourth embodiment in a hydraulic press with a hydraulic counter-hold on an annulus side of a differential cylinder, the fourth embodiment containing the components of the first embodiment and only the components added with respect to the first embodiment are described below.
  • the third check valve 38 is arranged, which in the direction of the tank 18 locks.
  • a third pressure limiting valve 44 is arranged in a flow path connected in parallel with the third check valve 38.
  • a hydraulic circuit for supplying pressure medium to a differential cylinder with a suspended load, which has a variable-speed and bidirectionally operable drive for a pressure medium source.
  • a directional control valve is connected in a first working line between the drive and an annular space of the differential cylinder in such a way that the annular space can only be connected to the pressure medium source, or the annular space and an annular space-side flow path of the pressure medium source can be connected to a pressure medium sink.

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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)

Claims (7)

  1. Circuit hydraulique pour l'alimentation en fluide sous pression d'un vérin différentiel (2) qui permet de déplacer une charge suspendue (4), comprenant une source de fluide sous pression bidirectionnelle (6) qui comprend une machine hydraulique (8) à fonctionnement bidirectionnel et un groupe convertisseur (10) à fonctionnement bidirectionnel, couplé à celle-ci, et qui permet d'alimenter avec un premier débit volumique un espace annulaire (14) du vérin différentiel (2) par une première conduite de travail (12) du circuit hydraulique, et qui permet d'alimenter avec un deuxième débit volumique un espace de tête de piston (24) du vérin différentiel (2) par une deuxième conduite de travail (22) du circuit hydraulique, le premier débit volumique étant inférieur au deuxième débit volumique, et un premier clapet antiretour (26) qui permet d'aspirer ultérieurement, à partir d'un réservoir (18) dans l'espace de tête de piston (24), une quantité diminuée du fluide sous pression, due à une différence des débits volumiques, afin de permettre un mouvement descendant de la charge (4) provoqué par le poids de la charge (4), le premier clapet antiretour (26) pouvant être débloqué par une première pression régnant dans la première conduite de travail (12) de telle sorte que lors d'un mouvement ascendant de la charge (4), une quantité excessive du fluide sous pression, due à la différence des débits volumiques, peut être évacuée de l'espace de tête de piston (24) dans le réservoir (18) en passant par le premier clapet antiretour (26), caractérisé en ce qu'une vanne (16) est rattachée à la première conduite de travail (12) de telle sorte que l'espace annulaire (14) ne peut être relié qu'à la source de fluide sous pression (6), ou l'espace annulaire (14) et un trajet d'écoulement côté espace annulaire de la source de fluide sous pression (6) peuvent être reliés au réservoir (18), dans lequel la vanne est réalisée sous la forme d'une vanne 4/3 voies (16) et est rattachée à la première conduite de travail (12) entre la machine hydraulique (8) et l'espace annulaire (14), et coupe la première conduite de travail (12) dans une position de blocage, ouvre la première conduite de travail (12) dans une première position de passage, ou relie la première conduite de travail (12) dans une deuxième position de passage à un trajet d'écoulement de la machine hydraulique (8) au réservoir (18), ou
    dans lequel la vanne est réalisée sous la forme d'une première vanne 2/2 voies à actionnement électromagnétique, et un trajet d'écoulement, qui bifurque de la première conduite de travail (12) entre la machine hydraulique (8) et l'espace annulaire (14) et conduit jusqu'au réservoir (18), peut être fermé par la première vanne 2/2 voies.
  2. Circuit hydraulique selon la revendication 1, dans lequel la machine hydraulique (8) peut fonctionner comme une pompe ou comme un moteur.
  3. Circuit hydraulique selon la revendication 1 ou 2, dans lequel le groupe convertisseur (10) peut fonctionner comme un moteur électrique à sens de rotation réversible et à vitesse de rotation réglable pour entraîner la machine hydraulique (8) fonctionnant comme une pompe, ou comme un générateur à sens de rotation réversible pour convertir de l'énergie hydrostatique et/ou cinétique mécanique en énergie électrique.
  4. Circuit hydraulique selon l'une quelconque des revendications 1 à 3, dans lequel une vitesse du mouvement descendant de la charge (4) peut être commandée par une évacuation du fluide sous pression de l'espace annulaire (14).
  5. Circuit hydraulique selon l'une quelconque des revendications précédentes 1 à 4, dans lequel, sur un trajet d'écoulement entre la vanne 4/3 voies (16) et l'espace annulaire (14), une deuxième vanne 2/2 voies (36) à fonctionnement électromagnétique est disposée qui permet de fermer le trajet d'écoulement.
  6. Circuit hydraulique selon l'une quelconque des revendications précédentes 1 à 5, dans lequel, dans un circuit parallèle à un trajet d'écoulement qui bifurque entre la vanne 4/3 voies (16) et l'espace annulaire (14) vers le réservoir (18), un troisième clapet antiretour (38) qui bloque en direction du réservoir (18) est disposé entre la vanne 4/3 voies (16) et le réservoir (18).
  7. Circuit hydraulique selon l'une quelconque des revendications précédentes, dans lequel dans un circuit parallèle à un trajet d'écoulement qui bifurque de la deuxième conduite de travail (12) entre l'espace de tête de piston (24) et le premier clapet antiretour (26) et conduit jusqu'au réservoir (18) en passant par une deuxième soupape de limitation de pression (28), une troisième vanne 2/2 voies (40) est disposée qui permet de fermer le circuit parallèle au trajet d'écoulement.
EP15182643.5A 2014-09-30 2015-08-27 Circuit hydraulique destine a alimenter un moyen de pression d'un verin differentiel Active EP3002461B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102014219734.1A DE102014219734A1 (de) 2014-09-30 2014-09-30 Hydraulische Schaltung zur Druckmittelversorgung eines Differentialzylinders

Publications (2)

Publication Number Publication Date
EP3002461A1 EP3002461A1 (fr) 2016-04-06
EP3002461B1 true EP3002461B1 (fr) 2021-04-21

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EP (1) EP3002461B1 (fr)
DE (1) DE102014219734A1 (fr)
ES (1) ES2876255T3 (fr)

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Publication number Priority date Publication date Assignee Title
DE102016113294A1 (de) * 2016-07-19 2018-01-25 Dorst Technologies Gmbh & Co. Kg Hydraulische Antriebseinrichtung
DE102021212944B3 (de) 2021-11-18 2023-04-13 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulische Schaltung mit einem Hydrozylinder

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Publication number Priority date Publication date Assignee Title
JP4587518B2 (ja) * 2000-03-10 2010-11-24 株式会社アマダエンジニアリングセンター 液圧装置におけるラム移動制御装置
DE102009058408A1 (de) * 2009-07-09 2011-01-13 Robert Bosch Gmbh Elektrohydraulische Steuerung
DE102009043034A1 (de) * 2009-09-25 2011-03-31 Robert Bosch Gmbh Vorgespannter hydraulischer Antrieb mit drehzahlvariabler Pumpe
EP2917592B1 (fr) * 2012-11-07 2018-09-19 Parker Hannifin Corporation Système de commande de taux de décélération d'actionneur électro-hydrostatique

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EP3002461A1 (fr) 2016-04-06
DE102014219734A1 (de) 2016-03-31
ES2876255T3 (es) 2021-11-12

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