EP1644643B1 - Dispositif et procede de commande d'au moins deux recepteurs hydrauliques - Google Patents

Dispositif et procede de commande d'au moins deux recepteurs hydrauliques Download PDF

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Publication number
EP1644643B1
EP1644643B1 EP04762391A EP04762391A EP1644643B1 EP 1644643 B1 EP1644643 B1 EP 1644643B1 EP 04762391 A EP04762391 A EP 04762391A EP 04762391 A EP04762391 A EP 04762391A EP 1644643 B1 EP1644643 B1 EP 1644643B1
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EP
European Patent Office
Prior art keywords
pump
pressure
meter
control
orifices
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
EP04762391A
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German (de)
English (en)
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EP1644643A1 (fr
Inventor
Horst Hesse
Gerhard Keuper
Heinrich Lödige
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Bosch Rexroth AG
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Bosch Rexroth AG
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Classifications

    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • 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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • F15B21/087—Control strategy, e.g. with block diagram
    • 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
    • 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
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40553—Flow control characterised by the type of flow control means or valve with pressure compensating valves
    • F15B2211/40569—Flow control characterised by the type of flow control means or valve with pressure compensating valves the pressure compensating valve arranged downstream of the flow control means
    • 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
    • F15B2211/41—Flow control characterised by the positions of the valve element
    • F15B2211/413—Flow control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/415—Flow control characterised by the connections of the flow control means in the circuit
    • F15B2211/41572—Flow control characterised by the connections of the flow control means in the circuit being connected to a pressure source and an output member
    • 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in 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
    • F15B2211/40—Flow control
    • F15B2211/465—Flow control with pressure compensation
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6346—Electronic controllers using input signals representing a state of input means, e.g. joystick position

Definitions

  • the invention relates to a control arrangement for pressure medium supply at least two hydraulic consumers according to the preamble of claim 1 and a method for controlling such consumer according to the preamble of claim.
  • hydraulic systems are often used in which the consumers are supplied via a variable displacement pump with pressure medium. Between the variable and each consumer a metering orifice and a pressure compensator are provided, the latter upstream of the metering orifice (current regulator principle) or downstream (current dividing principle) can be.
  • the pressure compensators downstream of the metering orifices are acted upon in the opening direction by the pressure downstream of the respective metering orifice and in the closing direction by a control pressure prevailing in a rearward control chamber, which usually corresponds to the highest load pressure of all the hydraulic consumers supplied by the same hydraulic pump. If, in a simultaneous operation of several hydraulic consumers, the metering orifices are opened so far that the pressure medium supplied by the stoppered hydraulic pump is less than the total required pressure medium, the individual hydraulic consumers inflowing pressure medium quantities regardless of the respective load pressure of the hydraulic consumer proportions reduced. In this case, therefore, we speak of a controller with load-independent flow distribution (LUDV control) (flow divider principle). Because in such a LUDV control and the highest load pressure is tapped and generated by the pressure medium source to a certain pressure difference above the highest load pressure lying inlet pressure, a LUDV control is practically a special case of a load-sensing control.
  • LUDV control load-independent flow distribution
  • variable displacement pump is controlled in response to the highest load pressure such that in the pump line adjusts a pressure equivalent to the force of a control spring of a pump control valve pressure difference above the highest load pressure (so-called Ap control of variable).
  • the invention has the object, a hydraulic control arrangement for controlling at least two consumers and a method for controlling these consumers in such a way that the energy losses and susceptibility to vibration are reduced.
  • variable displacement pump pump with variable delivery rate
  • each consumer upstream adjustable metering orifices - preferably electrically - proportional actuated the control of the variable displacement pump depending on predetermined for the orifices setpoints occurs. That is, in contrast to the LS systems described above, the variable displacement pump is not adjusted in response to a pressure signal corresponding to the highest load pressure, but in response to setpoints that are given by an operator to move the consumer, for example, at a certain speed. The setting of the variable displacement pump then takes place as a function of these setpoint values so that it can supply all consumers with the preset nominal volume flows. That is, the variable displacement pump must be adjusted to a pivoting angle at which it delivers just this requested consumer sum current.
  • Such a system is in principle a volume flow control in which volumetric flow losses due to volumetric losses of the pump play no role, since the operator, if the flow and thus the speed the consumer is too low, manually readjusted and thus compensates for the volume flow error. Since the control of the variable displacement pump is independent of the highest load pressure as a flow control, the system has a much lower susceptibility to vibration than the known LS control arrangements.
  • Another advantage of the control arrangement according to the invention and of the method according to the invention is that the individual metering of a consumer, the metering orifices outside the Fein Kunststoffes can be completely opened, the volume flow to the consumer of the control of the variable is determined - the throttle losses at the metering orifice are then minimal.
  • the throttle losses can be reduced according to an advantageous embodiment of the invention characterized in that the metering orifice of that consumer to which the highest pressure medium flow rate flows, i. the consumer set to the highest nominal value is fully controlled and the cross sections of the other metering orifices are tracked according to the ratio of the pressure medium volume flows, so that the system losses are minimized compared to conventional solutions.
  • this case does not occur as often as usually a consumer is driven at maximum speed.
  • variable displacement pump and the metering orifices via a central control device, which preferably has a data storage, are stored in the characteristics of the variable displacement pump and the metering orifices.
  • variable displacement pump is preferably provided with a speed sensor, via which the current pump speed can be detected, so that the target volume flow is easily adjustable via the stored characteristics.
  • the control arrangement according to the invention is preferably carried out with suction valves, via which pressure medium can be sucked into a low-pressure side of the consumer during a pulling load.
  • the pump is reset in the inventive solution, so that the system losses compared to conventional solutions are further reduced.
  • the determination of the desired values is preferably carried out by evaluating the setting of a joy stick or detecting the position of the control piston of the metering orifice.
  • the figure shows a circuit diagram of a hydraulic control device 1 according to the invention, which is practically a modified LUDV system.
  • the control arrangement according to the invention has a variable displacement pump 2, via which two or more consumers 4, 6 can be supplied with pressure medium.
  • the control of the consumers 4, 6 by means of a control device, such as a joystick 8, are discharged via the control signals to a control device 10. These signals are practically a command to move the consumers at a certain speed.
  • the output of the variable displacement pump 2 is connected to a pump line 12, which branches into two supply lines 14, 16.
  • a pump line 12 which branches into two supply lines 14, 16.
  • an electrically proportionally adjustable metering orifice 18 and 20 is arranged, each of which a pressure compensator 22 and 24 is connected downstream.
  • the output of the two pressure compensators 22, 24 is connected in each case via a flow line 26, 28 to the consumer.
  • the consumers are 4, 6 hydraulic cylinders whose cylinder chambers are connected to the flow line 26 and 28, respectively.
  • the metering orifices 18, 20 are carried out by electrically or hydraulically proportionally adjustable directional control valves.
  • the pressure compensators 22, 24 are acted upon in the opening direction by the pressure after the respective metering orifice 18, 20 and in the closing direction by a pressure which corresponds to the highest load pressure at the two consumers 4, 6.
  • This highest load pressure is tapped via an LS line 34 and a shuttle valve 36 of those flow line 26, 28, applied to the highest load pressure.
  • the control of the two metering orifices 18, 20 takes place via the control device 10 as a function of the control signal (set value) set on the joystick 8.
  • the pressures behind the two orifices 18, 20 are the same and the size of the volume flows to the consumers 4, 6 behave like the opening cross sections of the two metering orifices (18, 20).
  • About the downstream pressure compensator 22, 24 of the applied after the metering orifices 18, 20 pressure is throttled to the respective applied load pressure.
  • variable displacement pump 2 is designed in the illustrated embodiment with a pressure sensor for detecting the pump pressure, a speed sensor for detecting the pump speed and a swivel angle sensor for detecting the pump swivel angle. Furthermore, the characteristic curves of the variable displacement pump 2 and the two proportionally adjustable metering orifices 18, 20 are stored in the data memory of the control device, so that extremely precise volume flow control via the variable displacement pump 2 is possible with the aid of all or some of the aforementioned sensors and the characteristic curves.
  • the function of the control arrangement according to the invention is as follows:
  • variable displacement pump 2 To actuate the two consumers 4, 6 8 control signals are generated by the operator via one or more joysticks, which are delivered to the control device 10.
  • the variable displacement pump 2 For the corresponding control of the consumers 4, 6, the variable displacement pump 2 must provide a certain pressure medium volume flow which corresponds to the sum of the setpoint volume flows set via the joystick 8. That is, the variable displacement pump 2 must be adjusted depending on the setting of the joystick 8 to a swivel angle at which this total volume flow is delivered.
  • the corresponding adjustment of the variable displacement pump 2 can be carried out in a simple manner as a function of the setpoint value by detecting the current pump pressure, the current pump speed and the set pivoting angle via the pump characteristic curve. That is, according to the invention receives the pump controller no pressure signal, which usually corresponds to the highest load pressure, but the control of the variable only takes place in dependence on the set via the joystick setpoints.
  • volumetric flow errors due to volumetric losses of the variable displacement pump 2 can be compensated because the operator immediately readjusted via the joystick 8, if the consumers 4, 6 are not operated at the desired speed.
  • Another special feature of the invention is that in parallel operation of the consumer 4, 6 via the control device 10 that consumer 4, 6 is determined, which is to be supplied with the largest pressure medium volume flow. This can be done in a simple manner via the set values set on the joystick 8, so that no further sensors are required.
  • the metering orifice 18, 20 of this consumer 4, 6 to be supplied with the highest pressure medium volume flow is then completely opened by means of the control device 10 and the opening cross sections of the other metering orifices 20 and 18 are adjusted accordingly, so that the system losses are minimized compared to conventional solutions.
  • the associated metering orifice 18 or 20 outside the fine-control area can be opened fully in order to minimize system losses.
  • the pressure medium volume flow to the consumer is then controlled solely by means of the variable displacement pump.
  • the cylinder chambers 30, 32 of the consumer 4, 6 are each connected via an evacuation valve to the tank T, so that in the case of a pulling load on this Not shown Nachsaugventile pressure medium in the cylinder chambers 30, 32 (low pressure side) can be sucked.
  • This pressure in the low pressure side is detected and delivered via the control device 10, a control signal to the variable displacement pump 2, so that the pivot angle of the variable displacement pump 2 is moved back and no pressure medium is pumped through the pump.
  • the losses can be further minimized compared to conventional circuits.
  • the setpoint values are predetermined via a joystick 8.
  • the target volume flow can also be determined from the path of the valve spool of the metering orifice 18, 20, ie, in this case, not the set on the joystick 8 signal directly, but the himself due to this signal on the valve spool of the metering orifices 18, 20 adjusting Actual value used.
  • variable displacement pump can be designed as described above so that the geometric displacement volume is adjustable, but it can also be used constant-speed or variable displacement pumps with variable-speed drive.
  • a control arrangement for controlling at least two hydraulic consumers and a method for controlling these consumers. These are supplied via a pump with pressure medium, wherein between the consumers and the pump each have a metering orifice and a downstream pressure compensator are provided. According to the invention, the adjustment of the pump takes place in dependence on the desired values to which the metering orifices are set.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid Mechanics (AREA)
  • Physics & Mathematics (AREA)
  • Mechanical Engineering (AREA)
  • Structural Engineering (AREA)
  • Civil Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Control Of Positive-Displacement Pumps (AREA)
  • Operation Control Of Excavators (AREA)

Abstract

L'invention concerne un dispositif et un procédé de commande d'au moins deux récepteurs hydrauliques. Lesdits récepteurs hydrauliques sont alimentés en fluide de pression par l'intermédiaire d'une pompe, respectivement un diaphragme de dosage et une balance de pression montée en aval étant disposés entre chaque récepteur et la pompe. Selon l'invention, le réglage de la pompe est effectué en fonction des valeurs de consignes auxquelles les diaphragmes de dosage sont réglés.

Claims (11)

  1. Ensemble de commande pour l'alimentation en fluide sous pression d'au moins deux récepteurs hydrauliques (4, 6), avec une pompe (2), dont le débit peut être modifié et avec deux obturateurs de dosage (18, 20) réglables, dont un premier est disposé entre une conduite d'amenée (14) sortant de la pompe (2) et un premier récepteur (4) hydraulique et le second est disposé entre une conduite d'amenée (16) et un second récepteur (6) hydraulique, et avec deux compensateurs de pression (22, 24), dont un premier est monté en aval du premier obturateur de dosage (18) et le second est monté en aval du second obturateur de dosage (20) et dont le piston de régulation peut être sollicité sur un côté avant par la pression après l'obturateur de dosage (18, 20) respectif dans le sens d'ouverture et dans le sens de fermeture par la pression de charge maximale ou une pression en dérivant, la pompe (2) et les obturateurs de dosage (18, 20) pouvant être réglés, de préférence proportionnellement, caractérisé par un dispositif de commande (10) pour la remise d'un signal de commande à la pompe (2) pour sa commande de débit volumique en fonction de la somme des valeurs de consigne prescrites pour les obturateurs de dosage (18, 20).
  2. Ensemble de commande selon la revendication 1, dans lequel le débit de la pompe (2) peut être réglé électriquement au moyen d'aimants proportionnels.
  3. Ensemble de commande selon la revendication 1 ou 2, dans lequel au moyen du dispositif de commande (10), l'obturateur de dosage (18, 20) peut être totalement commandé avec la valeur de consigne maximale et les autres obturateurs de dosage (18, 20) peuvent être réajustés en conséquence.
  4. Ensemble de commande selon l'une quelconque des revendications précédentes, caractérisé en ce que le dispositif de commande (10) présente une mémoire de données, dans laquelle les caractéristiques de la pompe à débit variable (2) et des obturateurs de dosage (18, 20) sont enregistrées.
  5. Ensemble de commande selon l'une quelconque des revendications précédentes, caractérisé en ce que la pompe (2) est une pompe à pistons axiaux.
  6. Ensemble de commande selon l'une quelconque des revendications précédentes, avec un capteur de vitesse de rotation pour la détection de la vitesse de rotation de la pompe.
  7. Ensemble de commande selon l'une quelconque des revendications précédentes, avec des soupapes d'aspiration ultérieure, par le biais desquelles des espaces de fluide sous pression des récepteurs (4, 6) peuvent être reliés à un réservoir de sorte qu'en cas de charge de traction, du fluide sous pression puisse être aspiré ultérieurement dans les espaces de fluide sous pression (30, 32).
  8. Ensemble de commande selon l'une quelconque des revendications précédentes, dans lequel les valeurs de consigne sont détectées en fonction du réglage d'un joystick (8) ou en fonction de la position de piston de régulation des obturateurs de dosage (18, 20).
  9. Procédé de commande d'au moins deux récepteurs hydrauliques qui peuvent être alimentés par le biais d'une pompe (2) à débit variable en fluide sous pression, dans lequel à chaque récepteur est associé un obturateur de dosage (18, 20) qui est prévu entre la pompe et le récepteur (4, 6) respectif et en aval duquel est monté à chaque fois un compensateur de pression (22, 24), dont le piston de régulation est sollicité dans le sens d'ouverture par la pression après l'obturateur de dosage (18, 20) monté en amont et dans le sens de fermeture par la pression de charge maximale ou une pression en dérivant, caractérisé en ce que la pompe (2) est commandée pour sa commande de débit volumique en fonction de la somme des valeurs de consigne prescrites pour les obturateurs de dosage (18, 20).
  10. Procédé selon la revendication 9, dans lequel les obturateurs de dosage (18, 20) à régler sur la valeur de consigne maximale sont complètement commandés et les autres obturateurs de dosage sont réajustés en conséquence.
  11. Procédé selon la revendication 9 ou 10, dans lequel en cas de charge de traction, le débit de la pompe est reculé et du fluide sous pression est aspiré ultérieurement par des soupapes d'aspiration ultérieure vers le côté basse pression des récepteurs (4, 6).
EP04762391A 2003-07-15 2004-07-15 Dispositif et procede de commande d'au moins deux recepteurs hydrauliques Not-in-force EP1644643B1 (fr)

Applications Claiming Priority (2)

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DE10332120A DE10332120A1 (de) 2003-07-15 2003-07-15 Steueranordnung und Verfahren zur Ansteuerung von wenigstens zwei hydraulischen Verbrauchern
PCT/DE2004/001536 WO2005008076A1 (fr) 2003-07-15 2004-07-15 Dispositif et procede de commande d'au moins deux recepteurs hydrauliques

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EP1644643A1 EP1644643A1 (fr) 2006-04-12
EP1644643B1 true EP1644643B1 (fr) 2009-07-15

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US (1) US7275370B2 (fr)
EP (1) EP1644643B1 (fr)
JP (1) JP4818915B2 (fr)
KR (1) KR101085984B1 (fr)
CN (1) CN100445575C (fr)
DE (2) DE10332120A1 (fr)
WO (1) WO2005008076A1 (fr)

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DE10332120A1 (de) 2005-02-03
JP4818915B2 (ja) 2011-11-16
DE502004009762D1 (de) 2009-08-27
US7275370B2 (en) 2007-10-02
WO2005008076A1 (fr) 2005-01-27
CN100445575C (zh) 2008-12-24
US20060230753A1 (en) 2006-10-19
KR101085984B1 (ko) 2011-11-22
KR20060026484A (ko) 2006-03-23
EP1644643A1 (fr) 2006-04-12
CN1823230A (zh) 2006-08-23
JP2007506921A (ja) 2007-03-22

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