EP1644643A1 - Dispositif et procede de commande d'au moins deux recepteurs hydrauliques - Google Patents

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

Info

Publication number
EP1644643A1
EP1644643A1 EP04762391A EP04762391A EP1644643A1 EP 1644643 A1 EP1644643 A1 EP 1644643A1 EP 04762391 A EP04762391 A EP 04762391A EP 04762391 A EP04762391 A EP 04762391A EP 1644643 A1 EP1644643 A1 EP 1644643A1
Authority
EP
European Patent Office
Prior art keywords
pump
pressure
metering
control
consumers
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
EP04762391A
Other languages
German (de)
English (en)
Other versions
EP1644643B1 (fr
Inventor
Horst Hesse
Gerhard Keuper
Heinrich Lödige
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Bosch Rexroth AG
Original Assignee
Bosch Rexroth AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Bosch Rexroth AG filed Critical Bosch Rexroth AG
Publication of EP1644643A1 publication Critical patent/EP1644643A1/fr
Application granted granted Critical
Publication of EP1644643B1 publication Critical patent/EP1644643B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
  • Hydraulic systems are frequently used to control several consumers, in which the consumers are supplied with pressure medium via a variable pump.
  • a metering orifice and a pressure compensator are provided between the variable pump and each consumer, the latter being able to be connected upstream (metering principle) or downstream (metering principle).
  • EP 0 566 449 AI discloses a hydraulic control arrangement which operates on the current divider principle and works on the load-sensing (LS) principle.
  • LS load-sensing
  • a variable displacement pump is adjusted depending on the highest load pressure of the hydraulic consumers actuated so that the inlet pressure is above the highest load pressure by a certain pressure difference.
  • the pressure medium flows to the two hydraulic consumers via two adjustable metering orifices, the first of which is arranged between a pump line coming from the variable displacement pump and a first hydraulic consumer and the second between the pump line and the second hydraulic consumer.
  • the pressure compensators downstream of the metering orifices are acted upon in the opening direction by the pressure after the respective metering orifice and in the closing direction by a control pressure present in a rear control chamber, which usually corresponds to the highest load pressure of all hydraulic consumers supplied by the same hydraulic pump. If, when several hydraulic consumers are operated at the same time, the metering orifices are opened to such an extent that the quantity of pressure medium supplied by the hydraulic pump adjusted to the stop is smaller than the total quantity of pressure medium required, the pressure medium quantities flowing to the individual hydraulic consumers become independent of the respective load pressure the hydraulic consumer is reduced proportionally. In this case, one speaks of a control with load-independent flow distribution (LUDV control) (current divider principle).
  • LUDV control load-independent flow distribution
  • an LUDV control system is practically a special case of a load-sensing control system.
  • a load-sensing control system For several hydraulic consumers, to which pressure medium flows via a metering orifice with an upstream pressure compensator (current regulator principle), which is acted upon in the closing direction by the pressure in front of the metering orifice and in the opening direction by the load pressure of the respective hydraulic consumer and by a compression spring, no load-independent flow distribution is obtained. If several hydraulic consumers are actuated simultaneously and the quantity of pressure medium supplied by the variable displacement pump is insufficient, only the quantity of pressure medium flowing to the hydraulic consumer with the highest load pressure is reduced.
  • variable displacement pump is controlled as a function of the highest load pressure in such a way that a pressure is established in the pump line which is a pressure difference equivalent to the force of a control spring of a pump control valve above the highest load pressure (so-called ⁇ p control of the Variable pump).
  • variable displacement pump pump with a variable delivery rate
  • adjustable metering orifices connected upstream of each consumer can be actuated proportionally, preferably electrically, the actuating pump being actuated as a function of target values specified for the metering orifices.
  • the variable pump is not adjusted as a function of a pressure signal corresponding to the highest load pressure, but as a function of setpoints that are specified by an operator, for example in order to move the consumer at a certain speed.
  • the adjustment pump is then set depending on these setpoints so that it can supply all consumers with the preset So11 volume flows. This means that the variable displacement pump must be adjusted to a swivel angle at which you requested it
  • such a system represents a volume flow control, in which volume flow errors due to volumetric losses of the pump play no role, since the operator, when the volume flow and thus the speed of the consumer is too low, readjusted manually and thus compensates for the volume flow error. Since the control of the variable pump takes place independently of the highest load pressure as volume 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 the method according to the invention is that when a consumer is operated individually, the metering orifices can be opened completely outside the fine control range, the volume flow to the consumer being determined by the control of the variable displacement pump - the throttling losses at the metering orifice are then minimal.
  • the throttle losses can be reduced according to an advantageous development of the invention in that the metering orifice of the consumer to which the highest pressure medium volume flow flows, i.e. the highest
  • Setpoint set consumers is fully controlled and the cross sections of the other metering orifices are adjusted according to the ratio of the pressure medium volume flows, so that the system losses compared to conventional solutions are minimized. However, this case does not occur as often, as a consumer is usually driven at maximum speed.
  • variable displacement pump and the metering foils are controlled via a central control device, which preferably has a data memory in which the characteristic curves of the variable displacement pump and the metering orifices are stored.
  • variable pump is preferably provided with a speed sensor, via which the current pump speed is detectable, so that the target volume flow can be easily adjusted via the stored characteristic curves.
  • 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 when there is a pulling load.
  • the pump is reset in the solution according to the invention, so that the system losses are further reduced compared to conventional solutions.
  • the setpoints are preferably acquired by evaluating the setting of a joy stick or by detecting the position of the control pistons of the metering orifice.
  • the figure shows a circuit diagram of a hydraulic control arrangement 1 according to the invention, which practically represents 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 consumers 4, 6 are controlled by means of a control device, for example a joystick 8, via which control signals are output to a control device 10. These signals are practically a command to move consumers at a certain speed.
  • the output of the variable displacement pump 2 is connected to a pump line 12 which branches into two feed lines 14, 16.
  • An electrically proportionally adjustable metering orifice 18 or 20 is arranged in each inlet line 14, 16, and a pressure compensator 22 or 24 is connected downstream of each.
  • the outlet of the two pressure compensators 22, 24 is connected to the consumer via a flow line 26, 28.
  • the consumers are 4, 6 hydraulic cylinders, the cylinder spaces of which are connected to the feed line 26 or 28.
  • the metering orifices 18, 20 are implemented by way of electrically or hydraulically proportionally adjustable directional valves.
  • the return and discharge lines connecting the cylinder spaces 30, 32 mentioned to the tank T are omitted, the flow cross-sections of which are preferably likewise opened or closed via the proportional valve forming the orifice plate 18, 20.
  • 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 from the flow line 26, 28 to which the highest load pressure is present.
  • the two metering orifices 18, 20 are controlled via the control device 10 as a function of the control signal (setpoint) set on the joystick 8.
  • the pressures behind the two metering orifices 18, 20 are the same and the size of the volume flows to the consumers rather 4, 6 behave like the opening cross-sections of the two metering orifices (18, 20).
  • the pressure applied after the metering orifices 18, 20 is throttled to the respective load pressure applied via the downstream pressure compensator 22, 24.
  • variable displacement pump 2 is designed 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.
  • the characteristics of the variable displacement pump 2 and the two proportionally adjustable metering orifices 18, 20 are also 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 help 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, control signals are generated by the operator via one or more joysticks 8, which are output to the control device 10.
  • the variable displacement pump 2 In order to control the consumers 4, 6 accordingly, the variable displacement pump 2 must provide a specific pressure medium volume flow which corresponds to the sum of the set volume flows set via the joystick 8. That is, the variable 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 desired value by detecting the current pump pressure, the current pump speed and the set swivel angle via the pump characteristic.
  • the pump controller receives no pressure signal, which usually corresponds to the highest load pressure, but the control of the variable pump takes place solely depending on the setpoints set with the joystick.
  • volume flow errors due to volumetric losses of the variable displacement pump 2 can be compensated for by this setpoint adjustment via the joystick 8, since the operator immediately adjusts via the joystick 8 if the consumers 4, 6 are not actuated at the desired speed.
  • Another special feature of the invention is that when consumers 4, 6 are operated in parallel, the consumer 4, 6 that is to be supplied with the greatest pressure medium volume flow is determined via control device 10. This can be done in a simple manner using the setpoints 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 opened completely 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 assigned metering orifice 18 or 20 can be opened fully outside the fine control range in order to minimize the system losses.
  • the pressure medium volume flow to the consumer is then controlled solely via the variable pump.
  • the cylinder spaces 30, 32 of the consumers 4, 6 are each connected to the tank T via a suction valve, so that in the event of a pulling load, the tank T Suction valves, not shown, pressure medium can be sucked into the cylinder chambers 30, 32 (low pressure side).
  • This pressure in the low-pressure side is recorded and a control signal is sent to the adjusting pump 2 via the control device 10, so that the swivel angle of the adjusting pump 2 is reduced and no pressure medium is conveyed via the pump.
  • the losses can be further minimized compared to conventional circuits.
  • the setpoints are specified via a joystick 8.
  • the desired volume flow can also be determined from the travel of the valve slide of the metering orifice 18, 20, ie in this case it is not the signal set on the joystick 8 that is direct, but rather the signal on the valve slide of the metering orifices 18, 20 setting actual value used. Since in the system according to the invention volume flow control takes place via the variable displacement pump 2, the susceptibility to vibrations is significantly lower than in the previously known solutions. By eliminating the LS signal lines to the control valve, the circuitry complexity compared to the ⁇ p systems described at the beginning can be minimized.
  • variable displacement pump can be designed as described above in such a way that the geometric displacement volume can be set, but constant or variable displacement pumps with a variable-speed drive can also be used.
  • a control arrangement for controlling at least two hydraulic consumers and one are disclosed
  • Procedure for controlling these consumers This are supplied with pressure medium via a pump, a metering orifice and a downstream pressure compensator being provided between the consumers and the pump.
  • the pump is set as a function of the setpoints to which the metering orifices are set.

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.
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)

Application Number Priority Date Filing Date Title
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

Publications (2)

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

Family

ID=33560130

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04762391A Not-in-force EP1644643B1 (fr) 2003-07-15 2004-07-15 Dispositif et procede de commande d'au moins deux recepteurs hydrauliques

Country Status (7)

Country Link
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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US7905089B2 (en) * 2007-09-13 2011-03-15 Caterpillar Inc. Actuator control system implementing adaptive flow control
DE102008008102A1 (de) 2008-02-08 2009-08-13 Robert Bosch Gmbh Verfahren und Vorrichtung zur Druckmittelversorgung von zumindest drei hydraulischen Verbrauchern
WO2009114407A1 (fr) * 2008-03-10 2009-09-17 Parker-Hannifin Corporation Système hydraulique ayant de multiples actionneurs et procédé de commande associé
EP2218839B1 (fr) * 2009-02-17 2013-06-12 Kwc Ag Armature sanitaire dotée d'une articulation
ES2395599T3 (es) * 2009-02-17 2013-02-13 Kwc Ag Grifería sanitaria con control de mando
CN201574992U (zh) * 2009-11-10 2010-09-08 三一重工股份有限公司 多路阀、液压装置及混凝土泵车
US8215107B2 (en) 2010-10-08 2012-07-10 Husco International, Inc. Flow summation system for controlling a variable displacement hydraulic pump
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CN1823230A (zh) 2006-08-23
WO2005008076A1 (fr) 2005-01-27
DE10332120A1 (de) 2005-02-03
DE502004009762D1 (de) 2009-08-27
US7275370B2 (en) 2007-10-02
JP4818915B2 (ja) 2011-11-16
JP2007506921A (ja) 2007-03-22
EP1644643B1 (fr) 2009-07-15
KR101085984B1 (ko) 2011-11-22
CN100445575C (zh) 2008-12-24
US20060230753A1 (en) 2006-10-19
KR20060026484A (ko) 2006-03-23

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