EP3002461A1 - 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
EP3002461A1
EP3002461A1 EP15182643.5A EP15182643A EP3002461A1 EP 3002461 A1 EP3002461 A1 EP 3002461A1 EP 15182643 A EP15182643 A EP 15182643A EP 3002461 A1 EP3002461 A1 EP 3002461A1
Authority
EP
European Patent Office
Prior art keywords
pressure medium
hydraulic circuit
working line
way valve
annular space
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
EP15182643.5A
Other languages
German (de)
English (en)
Other versions
EP3002461B1 (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
Original Assignee
Robert Bosch 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 Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP3002461A1 publication Critical patent/EP3002461A1/fr
Application granted granted Critical
Publication of EP3002461B1 publication Critical patent/EP3002461B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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 pressure medium supply of a differential cylinder according to the preamble of patent claim 1.
  • a differential volume flow In a hydraulic circuit for supplying pressure medium to a differential cylinder, a differential volume flow must be taken into account, which results from an area difference between a piston surface delimiting a piston head space and an annular space defining an annular space of a piston.
  • a load suspended on the differential cylinder such as, for example, in the case of a press, in particular the weight force of the load acting on the differential cylinder in or against an actuating direction must be taken into account.
  • circuits include electrically operated switching valves in conjunction with variable displacement pumps or multiple pumps, which means increased component use, space and control effort.
  • the invention is based on the object to provide a simplified hydraulic circuit for supplying pressure medium of 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 is movable, 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 head space of the differential cylinder 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 comprises a first check valve, via which a reduced by a difference of the volume flow of a pressure medium from a pressure medium sink is nachsaugbar in the piston head space to allow at least one caused by a weight of the load downward movement of the load.
  • the first check valve can be unlocked via a first pressure present in the first working line in such a way that an excess amount of the pressure medium from the piston head space into the pressure medium sink can be discharged via the check valve during an upward movement of the load.
  • a directional control valve is connected to the first working line such that the annular space can be connected exclusively 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.
  • An advantage of the present invention is that a switching over of the actuating direction of the differential cylinder, for example from an extension to a retraction of the differential cylinder, is effected solely by a change in a conveying direction of the pressure medium source. This results in a reduced component usage, a reduced space requirement and a reduced control effort.
  • Another advantage is that solely by the change of the conveying direction of the pressure medium source, the pressure medium in the piston head space or in the annular space is compressible or decompressible. A resulting decompression energy can be used to bias a respective piston counter space of the differential cylinder, whereby a stepless switching of the actuating direction of the differential cylinder is made possible.
  • a cylinder rod passes through the piston head space, wherein the cylinder rod in the piston head space has 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 thereto.
  • the bidirectionally operable hydraulic machine can be operated as a pump or as a motor.
  • the motor generator is operable as a reversible and speed adjustable electric motor for driving the pump or as a reversible generator for converting a hydrostatic energy into an electrical energy.
  • the electric motor is designed in particular as a servomotor.
  • the abovementioned change in the conveying direction of the pressure medium source is effected via a change in the direction of rotation and / or torque control of the motor generator operated as an electric motor.
  • This makes it possible to use a constant-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 requires a conveying direction of the hydraulic machine operated as a pump, the conveying direction requires an actuating direction of the differential cylinder.
  • the rotational speed of the motor generator operated as an electric motor, by which the hydraulic machine operated as a pump can be driven, is adjustable to set a speed of the differential cylinder.
  • a behavior in the above-mentioned decompression of the respective piston chamber can 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, controllable via a discharge of the pressure medium from the annular space.
  • the removal takes place in particular via the operated as a pump hydraulic machine.
  • the directional control valve is designed as a 4/3-way valve or as a first 2/2-way valve.
  • the 4/3-way valve between the hydromachine and the annulus is connected to the first working line.
  • the 4/3-way valve interrupts the first working line in a blocking position, opens the first working line in a first passage position or connects the first working line in a second passage position with a flow path from the hydraulic machine to the tank.
  • a flow path which 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 first 2/2-way valve.
  • an electromagnetically operable second 2/2-way valve is arranged in a flow path between the 4/3-way valve and the annular space, via which this flow path can be closed.
  • a third check valve which blocks in the direction of the tank.
  • a press brake which has a variable speed drive with a high rapid traverse speed and a high pressing speed at high pressure, and a fixed displacement pump and a variable speed servomotor.
  • FIG. 1 illustrated circuit diagram shows a hydraulic circuit 1 according to the invention for the pressure medium supply of a differential cylinder 2 with a suspended load 4 according to a first embodiment in a hydraulic press.
  • the hydraulic circuit 1 has a pressure medium source 6 which contains a bidirectionally operable hydromachine 8 which can be reversed in its direction of rotation and a bi-directionally operable motor generator 10 which is reversible in its direction of rotation and which is coupled to the hydraulic machine 8.
  • the bidirectionally operable hydraulic machine 8 can be operated as a pump in both conveying directions or as a motor in both drive directions.
  • the bidirectionally operable motor generator 10 can be operated in both drive directions as an electric motor or in both directions of rotation as a generator.
  • the direction of rotation of the motor generator 10 operated as an electric motor requires a conveying direction of the hydraulic machine 8 operated as a pump, the conveying direction requires an actuating direction of the differential cylinder 2.
  • the speed of the motor generator 10 operated as an electric motor, by which the hydraulic machine 8 operated as a pump can be driven, is adjustable to set a speed of the differential cylinder 2.
  • the hydraulic machine 8 can be fluidically connected to the annular space 14 via a electromagnetically actuated 4/3-way valve 16 connected to the 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 branches off a flow path to a tank 18, in which a first pressure relief valve 20 is arranged. In a parallel circuit to this flow path, a fluid connection of this flow path is made with the 4/3-way valve 16.
  • the hydraulic machine 8 is fluidically connected to a piston bottom space 24 via a second working line 22. From the second working line 22 branches off a flow path to the tank 18, in which a first check valve 26 is arranged, which blocks a pressure fluid connection from the piston head space 24 in the direction of the tank 18 and releases in the reverse direction.
  • a differential volume flow 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 results in a difference between a piston surface bounding the piston head space 24 and an annular area of a piston of the differential cylinder 2 delimiting the annular space 14 24 is available.
  • a caused by the differential volume flow undersupply of a pressure medium from the tank 18 in the piston head space 24 is nachsaugbar, whereby in particular a caused by a weight force of the load 4 downward movement of the load 4 is made possible.
  • the first check valve 26 is over a first pressure in the first working line 12th unblocked.
  • a flow path branches off from the first working line 12 and leads via a second check valve 30 to the tank 18, said flow path from the second check valve 30 as a control line 32 to the first check valve 26th is continued.
  • the load 4 On a at least partially extending through the annular space 14 cylinder rod 34, the load 4 and causes a load pressure on the pressure medium in the annular space 14.
  • This load pressure is smaller than an opening pressure for the first pressure relief valve 20 in the illustrated case and is thus at the first pressure relief valve 20 and at the switched into a blocking position 4/3-way valve 16, so that the load 4 is held in the position shown.
  • FIG. 2 shows the hydraulic circuit FIG. 1 in rapid traverse downwards, that is, the load 4 is to be moved at a greater speed than in a press gear in the direction of gravity.
  • the 4/3-way valve 16 is connected in the illustrated first passage position via the first working line 12 with the annular space 14 and leads pressure medium via the operated as a pump hydraulic machine 8 in the piston head space 24, wherein the hydraulic machine 8 of the operated as an electric motor motor generator 10th is driven accordingly.
  • the downward movement is controlled and thus controlled feasible.
  • FIG. 3 shows a circuit diagram of the hydraulic circuit FIG. 1 in press, that is, the load 4 should be at a lower speed than in the FIG. 2 described rapid traverse be moved in the direction of gravity.
  • the 4/3-way valve 16 remains in the in FIG. 2 shown first passage position and operated as a pump hydraulic machine 8 performs pressure medium from the annular space 14, wherein the hydraulic machine 8 is driven accordingly by the operated as an electric motor motor generator 10.
  • the pressure medium is supplied to the piston head space 24, wherein the limited by the different sized piston surfaces, of which the annular space 14 and the piston head space 24, limited amount of the pressure medium - as in FIG. 1 described - sucked via the second check valve 30 from the tank 18 and the hydraulic machine 8 is supplied via the flow path between the tank 18 and the first working line 12.
  • FIG. 3 shows pressing the hydraulic machine operated as a pump 8 driven by the operated as an electric motor motor generator 10 with higher speed and / or higher torque, so that a downward movement of the load 4 is realized at a lower speed than during rapid down.
  • FIG. 4 shows a circuit diagram of the hydraulic circuit FIG. 1 in a decompression phase, in particular under pressure from the previous one FIG. 3 described pressure line pressure medium is relaxed.
  • the 4/3-way valve 16 is connected in a second passage position, whereby a flow path from the annular space 14 toward the tank 18 is formed.
  • the hydraulic machine 8 is operated via the relaxing pressure medium as a motor, wherein the pressure medium is discharged via a flow path produced by the second passage position from the piston head space 24 into the tank 18.
  • the hydrostatic energy whereby the motor-driven hydraulic machine 8 is driven, converted into mechanical kinetic energy and converted by the driven as a generator motor generator 10, which is driven by the motor-driven hydraulic machine 8, into electrical energy, for example, in a Energy storage, not shown, is storable, or which can be fed into a power grid.
  • no pressure build-up takes place in an annular space-side flow path of the hydraulic machine 8, which otherwise would lead to an unlocking of the first check valve 26 and thus to a not controlled via the hydraulic machine 8 and thus to a too rapid decompression.
  • the directional control valve is alternatively formed to the 4/3-way valve 16 as an electromagnetically operable first 2/2-way valve which is connected to the first working line such that thereby a flow path, in particular a bypass, of the first working line 12 branches off between the hydraulic machine 8 and the annular space 14 and leads to the tank 18, is closable.
  • FIG. 5 shows a circuit diagram of the hydraulic circuit FIG. 1 in rapid upwards, that is, the load 4 is to be moved at a greater speed than in a press gear against the direction of gravity.
  • the 4/3-way valve 16 is in the already in FIG. 1 shown first passage position via the first working line 12 connected to the annular space 14.
  • pressure medium is pumped via the operated as a pump hydraulic machine 8 from the piston crown chamber 24 in the annular space 14, wherein the hydraulic machine 8 of the operated as an electric motor motor generator 10 in the other direction of rotation as in FIG. 1 is driven.
  • the pressure medium of the piston head space 24 or the annular space 14 is compressible or decompressible.
  • a decompression energy released during decompression can be used to bias the respective piston counter space of the differential cylinder 2. This bias by decompression causes a stepless switching of the operating direction of the differential cylinder. 2
  • FIG. 6 shows a circuit diagram of the hydraulic circuit according to the invention according to a second embodiment in a hydraulic press at a standstill, wherein the second embodiment includes the components of the first embodiment and will be described below, only the added with respect to the first embodiment components.
  • an electromagnetically operable second 2/2-way valve 36 is arranged, via which this flow path can be closed.
  • a third check valve 38 is arranged, which in the direction of the tank 18 locks.
  • a third 2/2-way valve 40 is arranged, via which this parallel circuit 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 so that they meet the safety requirements of the respective machine directive.
  • FIG. 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, wherein the third Embodiment containing the components of the first embodiment and will be described below only the added with respect to the first embodiment components.
  • a fourth 2/2-way valve 42 is arranged, which shuts off or opens the control line 32 and thus represents an electrical control of the first check valve 26.
  • FIG. 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-holding on an annulus side of a differential cylinder, the fourth embodiment includes the components of the first embodiment and only the components added in relation to the first embodiment will be described below.
  • the third check valve 38 is arranged in the direction the tank 18 locks.
  • a third pressure relief valve 44 is arranged in a flow path parallel to 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 that the annulus is connectable exclusively to the pressure medium source, or the annulus and an annular space-side flow path of the pressure medium source with a pressure medium sink is connectable.

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

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EP15182643.5A Active EP3002461B1 (fr) 2014-09-30 2015-08-27 Circuit hydraulique destine a alimenter un moyen de pression d'un verin differentiel

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016113294A1 (de) * 2016-07-19 2018-01-25 Dorst Technologies Gmbh & Co. Kg Hydraulische Antriebseinrichtung

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021212944B3 (de) 2021-11-18 2023-04-13 Robert Bosch Gesellschaft mit beschränkter Haftung Hydraulische Schaltung mit einem Hydrozylinder

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001259900A (ja) * 2000-03-10 2001-09-25 Amada Eng Center Co Ltd 液圧装置におけるラム移動方法および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
WO2014074708A1 (fr) * 2012-11-07 2014-05-15 Parker-Hannifin Corporation Système de commande de taux de décélération d'actionneur électro-hydrostatique

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2001259900A (ja) * 2000-03-10 2001-09-25 Amada Eng Center Co Ltd 液圧装置におけるラム移動方法および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
WO2014074708A1 (fr) * 2012-11-07 2014-05-15 Parker-Hannifin Corporation Système de commande de taux de décélération d'actionneur électro-hydrostatique

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016113294A1 (de) * 2016-07-19 2018-01-25 Dorst Technologies Gmbh & Co. Kg Hydraulische Antriebseinrichtung

Also Published As

Publication number Publication date
EP3002461B1 (fr) 2021-04-21
DE102014219734A1 (de) 2016-03-31
ES2876255T3 (es) 2021-11-12

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