EP1930604B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique Download PDF

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Publication number
EP1930604B1
EP1930604B1 EP20070022458 EP07022458A EP1930604B1 EP 1930604 B1 EP1930604 B1 EP 1930604B1 EP 20070022458 EP20070022458 EP 20070022458 EP 07022458 A EP07022458 A EP 07022458A EP 1930604 B1 EP1930604 B1 EP 1930604B1
Authority
EP
European Patent Office
Prior art keywords
pressure
brake valve
control
hydraulic
control device
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.)
Not-in-force
Application number
EP20070022458
Other languages
German (de)
English (en)
Other versions
EP1930604A2 (fr
EP1930604A3 (fr
Inventor
Gerold Liebler
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 EP1930604A2 publication Critical patent/EP1930604A2/fr
Publication of EP1930604A3 publication Critical patent/EP1930604A3/fr
Application granted granted Critical
Publication of EP1930604B1 publication Critical patent/EP1930604B1/fr
Not-in-force 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
    • 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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • 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
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow 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
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • 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
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6333—Electronic controllers using input signals representing a state of the pressure source, e.g. swash plate angle
    • 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
    • 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 control arrangement according to the preamble of patent claim 1.
  • Hydraulic control arrangements in which the hydraulic consumer is driven directly by an adjustable pressure medium source, ie a variable displacement pump and is controlled by the control or regulation of the variable displacement pump in terms of its speed or force, are very efficient.
  • an adjustable pressure medium source ie a variable displacement pump and is controlled by the control or regulation of the variable displacement pump in terms of its speed or force.
  • a typical application is a plastic injection machine in which 5 to 6 hydraulic axes are moved one after the other and always individually within the injection cycle.
  • An adjustable, pressure-controlled or volume flow-controlled pressure medium source that can be used for such an application is described in the applicant's data sheet RD 30630 / 06.06.
  • the simplest construction of such a hydraulic control arrangement is that of an open hydraulic circuit.
  • the pressure medium is supplied by the consumer to the pressure medium tank.
  • a brake valve is usually arranged in the pressure medium line from the consumer to the pressure medium tank.
  • the brake valve throttles the outflow of pressure medium to the pressure medium tank to brake the consumer.
  • the brake valve is actuated by the pressure with which the load is supplied to the source side.
  • Such a brake valve is shown in RE 64 298 / 09.97.
  • the essential component of the brake valve is a hydraulically actuated 2/2-way proportional valve. When pressure is removed from the control input, a spring controls the 2/2-way proportional valve, which throttles the connection between the consumer and the tank and slows down the consumer due to the accumulated pressure medium.
  • the brake valve causes a hydrostatic feedback to its input signal, namely the pressure of the pressure medium supplied to the consumer.
  • the damping of the brake valve and its accumulation line must each be tailored to the hydraulic control arrangement. This has a high technical and personnel costs for the establishment of such control orders result.
  • the voting process requires a detailed knowledge of the respective control arrangement and is therefore to be accomplished only by appropriately trained persons.
  • EP 1 403 529 A2 deals with a method of distributing fluid between multiple hydraulic functions.
  • a pump is used to actuate hydraulic actuators.
  • Via a return line the fluid is returned to a tank.
  • a control valve is arranged in the return line.
  • a controller controls the control valve using pressure signals.
  • the drive system has a pressure medium tank, a pressure medium from the tank sucking and discharging into a supply line hydraulic pump with variable delivery, a double-acting hydraulic consumer, in particular a hydraulic cylinder from which the load is movable, and a directional control valve with a Inlet connection, with an outlet connection connected to the pressure medium tank, with two load connections and with a centered by at least one centering spring in a neutral position and displaceable from the neutral position control piston.
  • a pressure medium tank a pressure medium from the tank sucking and discharging into a supply line hydraulic pump with variable delivery
  • a double-acting hydraulic consumer in particular a hydraulic cylinder from which the load is movable
  • a directional control valve with a Inlet connection, with an outlet connection connected to the pressure medium tank, with two load connections and with a centered by at least one centering spring in a neutral position and displaceable from the neutral position control piston.
  • a directional control valve with a Inlet connection, with an outlet connection connected to the pressure
  • EP 1 338 802 A2 deals with a hydraulic control circuit for operating two hydraulic cylinders.
  • the present invention is therefore directed to provide a simpler and in particular with less coordination effort afflicted hydraulic control arrangement of the type described above.
  • a hydraulic control arrangement is equipped with an adjustable pressure medium source for controlling a hydraulic consumer with a pressure medium.
  • an electronic control system for controlling an actuator of the pressure medium source and a brake valve, by which a hydraulic connection between the consumer and a pressure medium tank can be throttled provided.
  • the peculiarity is that the brake valve can be controlled arbitrarily by an electromechanical actuator.
  • This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms.
  • the electronic control mechanism may be designed to operate reliably, in a predetermined manner and in particular without oscillations in the braking phase, without adaptation for a plurality of the usual applications.
  • a simple parameter-based configuration can be provided.
  • the aforementioned advantages reduce the installation effort of the hydraulic control device, increase their maintenance and ease of use and also ensure increased acceptance by the customer.
  • the brake valve with electromechanical actuator can be represented by a simple, available in mass production proportional directional control valve. This may possibly be cheaper available than a brake valve of conventional design.
  • the control electronics is connected to the actuating device of the brake valve.
  • the variable, the associated control electronics and the brake valve forms a ready-to-use preconfigurable drive system that can be easily integrated by the user in their own application.
  • the control electronics forms a uniform interface for controlling the consumer by means of variable and brake valve. If the control electronics includes a microcontroller, this conventional way still has sufficient resources to control the brake valve can. Therefore, the hardware complexity in the control of the brake valve by the control electronics of the variable is very low.
  • the control electronics detects a pressure actual value and / or volume flow actual value of the pressure medium source and, based on this, forms an actuation signal for the brake valve.
  • the said signals are available for the regulation of the variable displacement of the pressure medium source anyway. They can be used without additional recording effort to control the brake valve. It is also advantageous to form the actuation signal on the basis of a time derivative of the actual pressure value or of the actual volume flow value. By using the derivative signal, among other things, an oscillation tendency of the drive during braking can be reduced.
  • control electronics form the actuation signal for the brake valve on the basis of a pressure set value supplied to it and / or volumetric flow setpoint of the pressure medium source, a feedback can be avoided even better. In addition, it enables precise, fast and, if necessary, even abrupt braking.
  • the control electronics automatically selects a pressure or a volume flow control of the pressure medium source and forms in dependence on the selected control mechanism, the actuation signal for the brake valve.
  • a complete closing of the brake valve e.g. have a disturbing effect, because then it is not sure whether the force generated by the pressure in the pressure medium on the consumer actually acts on a workpiece. This can be prevented by including the operating state, ie the selected control mechanism.
  • a predetermined in the case of pressure control minimum throttling by the brake valve can prevent a runaway or overshoot of the consumer when breaking away an opposing force.
  • a good match between the speed of the load and the volume flow actual value can be achieved by setting a minimum brake pressure.
  • control electronics comprises a pump control component for the control of a variable displacement pump and a Bremsventilan Kunststoffkomponenten for driving the brake valve, both of which are arranged in a common housing. This facilitates the assembly and setup of the hydraulic control assembly.
  • a particularly preferred embodiment provides that the housing is arranged on the variable displacement pump. This allows a compact design of the hydraulic control arrangement and the presentation as a user-friendly, easy to handle and controllable functional unit.
  • control electronics starting from a drive signal for a pilot valve of the pressure medium source forms an actuating signal for the brake valve. Since the control signal for the pilot valve corresponds approximately to a time derivative of the flow rate actual value, it can be used to improve the time response in braking phases.
  • FIG. 1 is the hydraulic control assembly 1 for controlling a hydraulic consumer 2 with a variable displacement pump 5, a 4/2-way switching valve 7 for adjusting the direction of movement of the consumer 2 and equipped with a brake valve 9.
  • the brake valve 9 is arranged in the pressure medium line between the consumer 2 and the pressure medium tank 3 and designed as a continuously adjustable 2/2-way valve. By a proportional solenoid 10, the brake valve 9 is actuated.
  • a swash plate axial piston machine is used as a variable displacement pump 5, a swash plate axial piston machine is used. About the actuating piston 12, the pivot angle of the swash plate and thus the scoop volume of the variable 5 is set. A spring element 13 ensures a deflection of the swash plate in the unpressurized state. The swivel angle detects a swivel angle sensor 14. The swivel angle is a measure of the pumping volume of the pump and also for the flow rate, if one assumes a constant drive speed.
  • the actuating piston 12 is controlled via a pilot valve 16.
  • the pilot valve 16 is designed as a continuous valve and equipped with a proportional solenoid 17 and a separate displacement sensor 18 for detecting the valve position. Downstream of the output terminal of the variable displacement pump 5, a pressure sensor 20 is arranged to detect the output pressure of the variable displacement pump 5.
  • a regulation and control electronics 25 includes a pump regulator component 26 and a brake valve control component 28.
  • the pump regulator component 26 and the brake valve control component 28 are housed in a common housing (not shown).
  • the pump control component 26 is supplied with the actual value signals of the pressure sensor 20, the swivel angle sensor 14, the displacement sensor 18 and a pressure setpoint value applied to an input connection 30 and / or a volumetric flow setpoint value.
  • the pump regulator component 26 regulates the swivel angle of the variable displacement pump 5 on the basis of the actual value signals and setpoint signals supplied to it.
  • the pump regulator component 26 has inter alia a regulator for the output pressure and a regulator for the flow rate.
  • the brake valve control component 28 receives at least one of the following input signals: the actual pressure value, the actual swivel angle value, the desired value for pressure or delivery flow. It is of course also possible to use a plurality of said actual values or desired values in combination as input signals of the brake valve control component 28.
  • the pump controller component 26 can provide a signal 32 which indicates which of the variables-pressure, flow or power-is currently being regulated.
  • the pressure detected at the sensor 20 can be used as a control variable for controlling the control valve 9.
  • the brake valve control component 28 applies e.g. below a certain pressure threshold a to the output pressure of the variable displacement pump 5 inversely proportional actuation current for the proportional magnet 10 is generated.
  • the control characteristic can be influenced electronically and adapted very easily. Thus, unwanted vibrations during braking can be avoided by a suitable damping or by a frequency-selective filter.
  • the actual pressure value can be subjected to a time derivation and the derived pressure actual value can be used as a control signal for the brake valve.
  • the brake valve is actuated only at a pressure drop. This allows a more stable control behavior and energy savings for the pump drive can be achieved.
  • the swivel angle - as a measure of the actual flow - or its time derivative for controlling the brake valve 9 can be used by the brake valve control component 28.
  • the speed of the load 2 is largely proportional to the swing angle during acceleration and constant speed travel.
  • By controlling the brake valve 9 with a control current proportional to the time derivative of the swivel angle signal can be a quick reaction of the consumer to a swivel angle return - ie in the braking phases - achieve. The speed of the consumer thus follows even with a flow reduction, the predetermined flow profile.
  • the control of the brake valve 9 is feedback-free.
  • the reaction rate of the control of the brake valve 9 can be significantly increased.
  • a control delay between the setpoint input 30 and the actual value signals measured at the sensors 14 and 20 does not affect the activation of the brake valve.
  • Very fast and powerful braking is possible. Due to the backpressure built up during the braking process, which acts back on the output of the variable displacement pump 5, a return operation of the variable displacement pump 5 is accelerated.
  • a feedback-free control of the brake valve 9 is ensured even when using the desired pressure signal or its derivative.
  • signal 32 e.g. in a pressure control phase by setting the brake valve 9 in a throttle position a passage of the consumer can be prevented when breaking away a counterforce.
  • the brake valve to minimize the energy consumption can be fully opened.
  • a certain detectable at the pressure sensor 20 minimum backpressure to reduce the influence of disturbances on the movement of the consumer and to ensure a high degree of proportionality between the swivel angle signal and the speed of the consumer 2.
  • variable displacement pump 5 may comprise, instead of a swash plate type axial piston pump, all known variable displacement hydraulic machines accessible to pressure or flow control, e.g. Axialkoibenpumpen in Schrägachsenbauweise, vane pumps or radial piston pumps.
  • the pump regulator component 26 and the brake valve control component 28 can be implemented in analog circuit technology or particularly advantageously as program modules of a control / control program of a microcontroller be educated. Due to the already existing input signals - the signals of the sensors 14 and 20 and the setpoint signals - the additional hardware effort is exhausted in an additional amplifier stage 10 required for driving the proportional magnet 10.
  • the amplifier stage can be mounted on the valve, for example. In the control electronics 25 and then no additional hardware is required compared to a conventional pump control electronics.
  • the brake valve as part of a scheme.
  • the pressure accumulated by the brake valve is detected via its own pressure sensor or via the pressure sensor 20 and used as a controlled variable.
  • this could also be operated without an electrical pressure feedback or swivel angle feedback, and e.g. only have a hydrostatic pressure feedback to the actuator piston 12 or a similar actuator.
  • the brake valve can be controlled arbitrarily by an electromechanical actuator. This makes it possible to control the brake valve by robust and easily configurable electronic control or regulating mechanisms. In addition, a control can be done with little effort by the control electronics of the adjustable pressure medium source.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Braking Systems And Boosters (AREA)
  • Regulating Braking Force (AREA)

Claims (8)

  1. Dispositif de commande hydraulique comprenant une source de fluide de pression réglable (5) pour la commande d'un consommateur hydraulique (2) avec un fluide de pression, comprenant une électronique de commande (25) pour la commande d'un actionneur (12, 16) de la source de fluide de pression (5) et une soupape de freinage (9) par laquelle une liaison hydraulique entre le consommateur (2) et un réservoir de fluide de pression (3) peut être étranglée, la soupape de freinage (9) pouvant être commandée arbitrairement par un dispositif d'actionnement électromécanique (10),
    caractérisé en ce que
    l'électronique de commande (25) sélectionne automatiquement une régulation de pression ou de débit volumique de la source de fluide de pression (5) et, en fonction du mécanisme de régulation sélectionné, forme le signal d'actionnement pour la soupape de freinage (9) ou en ce que l'électronique de commande (25), à partir d'un signal de commande pour une soupape pilote (16) de la source de fluide de pression (5), forme le signal d'actionnement pour la soupape de freinage (9).
  2. Dispositif de commande hydraulique selon la revendication 1, caractérisé en ce que le dispositif d'actionnement électromécanique (10) est un aimant proportionnel.
  3. Dispositif de commande hydraulique selon la revendication 1 ou 2, caractérisé en ce que l'électronique de commande (25) est connectée au dispositif d'actionnement (10) de la soupape de freinage (9).
  4. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que l'électronique de commande (25) détecte une valeur de pression instantanée et/ou une valeur de débit volumique instantanée de la source de fluide de pression (5) et à partir de cette détection, forme un signal d'actionnement pour la soupape de freinage (9).
  5. Dispositif de commande hydraulique selon la revendication 4, caractérisé en ce que l'électronique de commande (25), à partir d'une dérivée dans le temps de la valeur de pression instantanée ou de la valeur de débit volumique instantanée, forme le signal d'actionnement.
  6. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que l'électronique de commande (25), à partir d'une valeur de consigne de pression (30) et/ou de débit volumique (30) de la source de fluide de pression (5) qui lui est acheminée, forme le signal d'actionnement pour la soupape de freinage (9).
  7. Dispositif de commande hydraulique selon l'une quelconque des revendications 1 à 6, caractérisé en ce que l'électronique de commande comprend un composant de régulation de pompe (26) pour la régulation d'une pompe de réglage et un composant de commande de soupape de freinage (28) pour la commande de la soupape de freinage (9), et en ce que les deux composants (26, 28) sont disposés dans un boîtier commun.
  8. Dispositif de commande hydraulique selon la revendication 7, caractérisé en ce que le boîtier est disposé sur la pompe de réglage.
EP20070022458 2006-12-06 2007-11-20 Dispositif de commande hydraulique Not-in-force EP1930604B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE200610057475 DE102006057475A1 (de) 2006-12-06 2006-12-06 Hydraulische Steueranordnung

Publications (3)

Publication Number Publication Date
EP1930604A2 EP1930604A2 (fr) 2008-06-11
EP1930604A3 EP1930604A3 (fr) 2012-03-28
EP1930604B1 true EP1930604B1 (fr) 2013-05-15

Family

ID=39153990

Family Applications (1)

Application Number Title Priority Date Filing Date
EP20070022458 Not-in-force EP1930604B1 (fr) 2006-12-06 2007-11-20 Dispositif de commande hydraulique

Country Status (2)

Country Link
EP (1) EP1930604B1 (fr)
DE (1) DE102006057475A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020213262A1 (de) 2020-10-21 2022-04-21 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben eines hydraulischen Antriebs

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013165951A1 (fr) * 2012-04-30 2013-11-07 Parker-Hannifin Corporation Écoulement de pompe hydraulique régulé par opérateur
DE102014222326B4 (de) * 2014-10-31 2016-06-09 Tadano Faun Gmbh Hydraulikanordnung

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19950910B4 (de) * 1999-10-22 2010-11-04 Bosch Rexroth Aktiengesellschaft Hydraulisches Antriebssystem und darin verwendbares hydraulisches 4/3-Wegeventil
US6715402B2 (en) * 2002-02-26 2004-04-06 Husco International, Inc. Hydraulic control circuit for operating a split actuator mechanical mechanism
US6779340B2 (en) * 2002-09-25 2004-08-24 Husco International, Inc. Method of sharing flow of fluid among multiple hydraulic functions in a velocity based control system

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102020213262A1 (de) 2020-10-21 2022-04-21 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben eines hydraulischen Antriebs
EP3988801A1 (fr) 2020-10-21 2022-04-27 Robert Bosch GmbH Procédé de fonctionnement d'un entraînement hydraulique

Also Published As

Publication number Publication date
EP1930604A2 (fr) 2008-06-11
DE102006057475A1 (de) 2008-06-12
EP1930604A3 (fr) 2012-03-28

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