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EP2541072B1 - Agencement de commande et procédé de commande de plusieurs consommateurs hydrauliques - Google Patents

Agencement de commande et procédé de commande de plusieurs consommateurs hydrauliques Download PDF

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Publication number
EP2541072B1
EP2541072B1 EP12170158.5A EP12170158A EP2541072B1 EP 2541072 B1 EP2541072 B1 EP 2541072B1 EP 12170158 A EP12170158 A EP 12170158A EP 2541072 B1 EP2541072 B1 EP 2541072B1
Authority
EP
European Patent Office
Prior art keywords
pressure
control
individual
consumers
compensators
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
EP12170158.5A
Other languages
German (de)
English (en)
Other versions
EP2541072A3 (fr
EP2541072A2 (fr
Inventor
Jan Amrhein
Thomas Weickert
Uwe Neumann
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 EP2541072A2 publication Critical patent/EP2541072A2/fr
Publication of EP2541072A3 publication Critical patent/EP2541072A3/fr
Application granted granted Critical
Publication of EP2541072B1 publication Critical patent/EP2541072B1/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
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04B—POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS
    • F04B13/00—Pumps specially modified to deliver fixed or variable measured quantities
    • 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
    • E02F9/2225—Control of flow rate; Load sensing arrangements using pressure-compensating valves
    • E02F9/2228—Control of flow rate; Load sensing arrangements using pressure-compensating valves including an electronic controller
    • 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
    • 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
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • 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
    • 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/3054—In combination with a pressure compensating valve the pressure compensating valve is arranged between directional control valve and 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a 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
    • F15B2211/60—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
    • 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
    • F15B2211/65—Methods of control of the load sensing 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
    • F15B2211/70—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
    • F15B2211/7052—Single-acting output members

Definitions

  • the invention relates to a hydraulic control arrangement according to the preamble of patent claim 1 and a method for controlling a plurality of hydraulic consumers.
  • hydraulic systems are used in which these consumers are supplied via a pump with adjustable delivery volume with pressure medium.
  • a metering orifice and a pressure compensator is provided, the latter may be upstream or downstream of the metering orifice.
  • the pressure compensator is connected downstream of the metering orifice.
  • LUDV systems represent a subset of the LS systems in which the highest load pressure of the hydraulic load is reported to a variable displacement and this is controlled so that in the pump line to a predetermined pressure difference above the highest load pressure lying pump pressure is applied.
  • LUDV control arrangement as for example in the DE 10 2005 033 222 A1 is described, the adjustment of the pressure medium volume flow to the respective consumer via adjustable inlet orifices, which in each case an individual pressure compensator is assigned, via which the pressure drop across the respective inlet orifice can be kept constant.
  • the individual pressure compensators are arranged downstream of the metering orifices and throttle the pressure medium volume flow between the metering orifice and the load to such an extent that the pressure after all inlet metering orifices is equal, preferably equal to or slightly above the highest load pressure.
  • the pump pressure is applied in the same way, so that the pressure difference changes in the same way at all orifices if at a deficiency of the pump pressure is lower.
  • the pressure medium volume flow distribution (flow divider principle) is maintained between the inlet orifices of the driven consumers.
  • variable displacement pump is actuated as a function of the highest load pressure tapped via an LS line such that a pressure is established in the pump line which is above the highest pressure difference equivalent to the force of a control spring of a pump control valve Load pressure is.
  • EFM architecture Electronic Flow Matching
  • valves present for controlling the pressure medium volume flows are generally grouped together in a control block which is accommodated, for example, in the case of an excavator in the area of the superstructure.
  • the DE 199 09 480 A1 shows a hydraulic control arrangement from Japanese Patent Application 1-247805, in which also according to the load-sensing principle, the consumer load pressures on associated individual pressure compensators together with a respective spring in the opening direction act. Via a control, the pressure compensators are acted upon in the closing direction with a common control pressure.
  • the invention has for its object to reduce the device complexity for the realization of a hydraulic control system and to provide a simplified method for driving multiple consumers.
  • the hydraulic control arrangement is designed to supply pressure to a plurality of consumers with a variable displacement pump, via which pressure medium can be conveyed to each consumer via an adjustable inlet orifice plate and an individual pressure compensator associated therewith.
  • the individual pressure compensators are acted upon in the opening direction by the pressure downstream of the respective inlet orifice plate.
  • According to the invention acts in the closing direction of each individual pressure compensator, a control pressure which is adjustable via a central control unit.
  • a conventional LUDV architecture to the effect that the respective individual pressure compensators are no longer acted upon in the closing direction with the highest load pressure of the consumer, but with a set via a control unit control pressure. It therefore eliminates the need to tap the LS pressure to the respective consumers and lead over a common LS channel in the control block to the individual pressure compensators.
  • a division of the control block into individual valve discs is possible, which can then be arranged decentralized to or near the consumers.
  • the decentralized arrangement has the advantage that the consumers can be supplied via a common high and low pressure line. Compared to a conventional LUDV architecture with a central control block, in which each consumer is at least supplied with its own high-pressure line, this represents a considerable saving Hydraulic lines dar. With the elimination of the need to tap the LS pressure of the consumer, can also be dispensed with conventional LS lines. Furthermore, there is no need to determine the highest of the LS pressures via a shuttle valve cascade.
  • the individual pressure compensators acting in the closing direction control pressures are the same, so that the device engineering and control engineering effort is further reduced. Due to the function of the individual pressure compensators, the same pressure results downstream of the inlet metering orifices due to the same control pressures. This is at least equal to the control pressure or larger. Since the pump pressure is present in front of each inlet orifice plate, the pressure drop at each of the inlet orifices is thus the same, resulting in the load pressure-independent flow distribution (LUDV).
  • LUDV load pressure-independent flow distribution
  • the individual pressure compensators are designed with a position transducer, which is inexpensive compared to the conventional means for load pressure determination discussed above.
  • Opening cross-sections or these corresponding strokes are set to the individual pressure compensators in a known manner depending on the pressure drop across the respective pressure compensator.
  • a change in the load pressures or a change in the pressure downstream of the Zulaufmessblenden thus leads to a movement of the affected individual pressure compensators and thus to changed opening cross-sections.
  • the stroke of the individual pressure compensator is thus a measure of the load pressure assigned to it. Since the individual pressure compensators are subjected to the same control pressure, the load pressures of a comparison of the strokes of the individual pressure compensators are comparable to one another in a particularly simple and advantageous manner.
  • the individual pressure balance of the load pressure highest consumer has the largest opening cross section and the corresponding stroke and is characterized by this identifiable.
  • control pressure is adjusted such that this individual pressure compensator is set to a desired opening position below its maximum opening cross-section, and the individual pressure compensators of the lower-load consumers are set to a smaller opening cross-section. In this way it is prevented that the load pressure highest consumer associated individual pressure balance is completely open and thus a control function is no longer possible. It may also be necessary to adjust the flow rate of the pump via the control unit accordingly.
  • the control arrangement according to the invention can be implemented particularly simply if the adjustment of the control pressure takes place via pressure reducing valves, by means of which the pressure regulated by the variable displacement pump upstream of the inlet metering orifice can be reduced to the predetermined control pressure.
  • the pressure drop across the inlet orifices can be directly preset via the control unit and the pressure reducing valves it controls.
  • the pressure drop across the inlet orifice plates is greater, the lower the control pressure is, or the more the pressure regulated by the variable displacement pump is throttled by the pressure reducing valves.
  • the pressure reducing valves are electrically or electro-hydraulically adjustable via the control unit.
  • the pressure drop across the pressure reducing valve or via the associated inlet orifice can be increased.
  • the control pressure is set as a function of the stroke of the load pressure highest consumer associated individual pressure compensator.
  • the control pressure is adjusted so that the stroke or, in other words, the opening cross section of the individual pressure compensator does not reach its maximum value, but is just below it.
  • the adjustment of the control pressure is preferably carried out as a function of the stroke of the load pressure highest consumer associated with individual pressure compensator.
  • control pressure is set in the individual pressure compensators associated with this priority consumers such that the pressure difference across the associated inlet orifice at Substantial remains substantially constant, so that a sufficient pressure medium supply of the priority consumer is guaranteed.
  • control arrangement is implemented as a decentralized solution, in which the individual pressure compensators, the pressure reducing valves and the inlet metering orifices are arranged decentrally in the region of the respective consumer. In this way, the device-technical effort for tubing - as explained above - significantly reduce.
  • variable displacement pump is preferably designed with an electro-proportional swivel angle control, so that it is adjustable in dependence on a signal of a control device, such as a joystick, and thus eliminates the need to tap the highest load pressure of the consumer and lead to the pump regulator.
  • control arrangement according to the invention can be realized particularly advantageously in mobile hydraulics, for example in working cylinders of a mobile implement, for example an excavator.
  • a method according to the invention serves to control a plurality of hydraulic consumers, each of which is in pressure fluid communication with a variable displacement pump via an individual pressure compensator and an inlet metering orifice.
  • the individual pressure compensators are in the opening direction of a pressure downstream of the associated inlet orifices and in the closing direction of a control pressure applied.
  • the control pressure is set via a control unit.
  • the inventive method thus solves the conventional use of a LS-pressure for a LUDV method.
  • the "substitution" of the LS pressure to be determined by the suitably adjustable control pressure according to the invention opens up the possibility, compared to the prior art, of creating considerably less expensive control arrangements in terms of the apparatus.
  • the substitution implies that the need for LS lines and a cascade of shuttle valves for determining a highest of the LS pressures is eliminated.
  • the elimination of the shuttle valve cascade is a division of a conventional central control block into individual decentralized valve discs, which can be arranged at or near the consumers, made possible with advantage. Via the decentralized arrangement, the consumers can be supplied in sequence via a common high and low pressure line.
  • each consumer when using a conventional LS-pressure-based LUDV method with a central control block, each consumer must be supplied with their own high-pressure line.
  • decentralized valve discs would also be possible using a conventional LS-pressure-based method, but the shuttle valve cascade would then be spatially distributed to the individual consumers, which would represent a significant piping expense.
  • the determination of the highest load pressure could alternatively be made in a known manner with the help of electronic pressure sensors with high accuracy.
  • Opening cross-sections or these corresponding strokes are set to the individual pressure compensators in a known manner depending on the pressure drop across the respective pressure compensator.
  • a change in the load pressure situation or a change in the pressure downstream of the Zulaufmessblenden thus leads to a movement of the individual pressure compensator affected by the change and thus to the changed opening cross-section.
  • the control pressures, which are applied to the individual pressure compensators the same, so that the opening cross-sections as a measure of the load pressures of the individual pressure compensators on particularly simple and advantageous manner are comparable to each other.
  • the suitable value of the control pressure is preferably set via the control unit as a function of the opening cross sections or strokes of the individual pressure compensators.
  • the method according to the invention preferably has a step "determining opening cross sections of the individual pressure compensators" before setting the control pressure.
  • the individual pressure balance of the load pressure highest consumer has the largest opening cross-section or the corresponding stroke and is thus identifiable over this.
  • the adjustment of the control pressure via the control unit then takes place particularly preferably as a function of that individual pressure balance which has the largest of the opening cross sections or the stroke corresponding thereto.
  • the method according to the invention preferably has a step "determining a largest of the opening cross-sections".
  • the method according to the invention preferably has a step "determining a deviation of the largest of the opening cross-sections from a desired value". The step "setting the control pressure via the control unit” then takes place as a function of the determined deviation from the setpoint.
  • the step "determination of opening cross sections of the individual pressure compensators" is carried out in a particularly simple and advantageous manner by determining strokes of the individual pressure compensators via position transducers.
  • the step "setting of the control pressure via the control unit” preferably takes place via pressure reducing valves controlled by the control unit. These throttle a pump pressure established by the pump to the control pressure.
  • the control is preferably the same for all pressure reducing valves and in such a way that the opening cross section of the most open individual pressure compensator is adjusted to the desired value.
  • the individual pressure compensator of the consumer is adjusted via the central control unit, wherein the control pressure is adjusted such that the individual pressure compensator associated with the load pressure highest consumer is set to an opening cross section which is below the maximum Opening cross section is.
  • priority consumers can be excluded from the control concept by the control pressure of this priority consumer is selected so that always a predetermined pressure difference at the associated inlet orifice plate and thus a sufficient pressure medium supply is ensured.
  • FIG. 1 shows a highly schematic schematic diagram of a mobile implement, in the present case an excavator 1, the superstructure 2 is rotatably mounted on a chassis 6 via a slewing gear 4.
  • the upper carriage 2 carries a boom 8, on which a handle 10 is articulated with a spoon 12.
  • the excavator 1 has a hydraulic drive, wherein the actuation of the slewing gear 4 is hydraulically.
  • the operation of the spoon 12, the handle 10 and the boom 8 via a respective hydraulic cylinder 14, 16 and 18.
  • the pressure medium supply of the hydraulic consumers via a variable displacement pump 20 and a control valve assembly, which is explained in more detail below.
  • variable displacement pump 20 The control of the variable displacement pump 20 and some of the control valves of the control valve assembly via a central control unit 22, which in the illustration according to FIG. 1 is highlighted for clarity, but is integrated in the superstructure or the like.
  • control valve assemblies 24, 26, 28 associated with each consumer are not arranged in a control block but close to the respective hydraulic consumers, for example the hydraulic cylinders 14, 16, 18.
  • FIG. 2 The basic concept of the control arrangement of the mobile working device according to FIG. 1 is based FIG. 2 explained.
  • some consumers of the mobile working device for example the hydraulic cylinder 14 of the spoon 12 and the hydraulic cylinder 16 for actuating the handle 10, are shown.
  • the cylinder for the boom and the hydraulic motors of the chassis and slewing are not shown for simplicity.
  • the pressure medium supply via the variable displacement pump 20, the delivery volume is set by a pump controller 30.
  • a pump controller 30 This allows for example via an electro-proportional swivel angle control a continuous and reproducible adjustment of the delivery volume of the pump.
  • the operation of such a pump controller is, for example, in the aforementioned DE 10 2007 029 358 A1 explained.
  • the control signal is given via pilot control devices 34, 36, which are adjusted in a conventional manner by means of joysticks 38, 40 from the driver, the adjustment of the joysticks 38, 40 in the illustrated embodiment, to actuate the spoon 12 and the stem 10 ,
  • the flow rate Q of the pump is set so that the set via the joysticks 38, 40 pressure medium requirement is met and thus the consumers are operated at the speed provided by the driver.
  • variable displacement pump 20 sucks pressure medium from a tank T and conveys this via its pressure port P into a feed line 42, which branches off to the consumers 14, 16. In this feed line 42, the pump pressure p P is applied .
  • a control valve arrangement 44 and 46 is arranged, which have a respectively identical structure.
  • the basic principle of the control valve arrangement 44 or 46 corresponds to an LUDV architecture, in which an inlet measuring orifice 48, 50, which is embodied by an adjustable directional control valve or the like, is assigned an individual pressure balance 52, 54.
  • An input terminal of the pressure reducing valve 60, 62 is connected via a line 69, 70 with the supply line 42, so that the pressure applied to the inlet of the respective inlet orifice 48, 50 tapped pressure via the pressure reducing valve 60, 62 and to the predetermined via the control unit 22 control pressure 56, 58 is reduced.
  • the setting of the pressure reducing valve 60, 62 takes place in the illustrated embodiment electrically via a proportional solenoid 64, 66 which is connected via a control signal line 68 to the central control unit 22, wherein in the illustrated embodiment, both proportional solenoids 64, 66 are subjected to the same control signal to the Set output pressure.
  • the individual pressure compensators 52, 54 are each designed with a displacement transducer 72, 74, via which the stroke of the valve body of the individual pressure compensator 52, 54 can be detected.
  • the control signals corresponding to the respective stroke are reported to the control unit 22 via signal lines 76, 78.
  • the adjustment of the inlet orifices 48, 50 is also hydraulically or electro-hydraulically, via the control unit 22 and signal lines 49, 51, the opening cross-section of the inlet orifices 48, 50 and thus the pressure medium volume flow to the respective hydraulic cylinder 14, 16 is set.
  • the two hydraulic cylinders (working cylinder) 14, 16 executed in the simplistic representation as a single-acting cylinder, wherein an effective in the extension direction pressure chamber 80 with a connected to the output terminal of the respective individual pressure compensator 52, 54 feed line 84, 86 is connected.
  • the rear annular spaces 88, 90 of the hydraulic cylinders 14, 16 are relieved to the tank T out.
  • the cylinders would not be simple but double acting.
  • the two joysticks 38, 40 are actuated and adjusted via the control unit 22 in response to stored in this characteristic curves a control signal in the control signal line 32, which via the joysticks 38, 40 set volume flow demand of the consumer 14, 16 corresponds.
  • the pivoting angle of the variable displacement pump 20 is then adjusted via the pump regulator 30 in order to cover the required pressure medium volume flow Q pump .
  • the inventive concept corresponds to an EFM architecture.
  • the opening cross-section of the feed orifices 48, 50 is adjusted as a function of the control signal predetermined by the control unit 22.
  • the pressures p * downstream of the Zulaufmessblenden 48, 50 are identical, so that both inlet orifices 48, 50 flows through pressure-independent and the pressure medium volume flow depends only on the opening cross-section.
  • the control pressure in the control lines 56, 58 is adjusted via the respective pressure reducing valves 60, 62 such that the individual pressure balance of the load pressure highest consumer, for example, the individual pressure compensator 54 of the hydraulic cylinder 16 does not reach its stroke stop, and thus is fully opened. In such a case, the control function of this individual pressure compensator 54 would be ineffective.
  • the stroke of the individual pressure compensators 52, 54 is monitored via the displacement transducer 72, 74 and set by suitable control of the load pressure highest pressure reducing valve 62 of the associated individual pressure compensator 54 control pressure so that it is not adjusted to its maximum open position.
  • the stroke of the lower-pressure individual pressure compensators in the present case the individual pressure compensator 52 must be set to a lower stroke, since the pressure p * is throttled to the load pressure in the pressure chamber 80, below the higher load pressure in the pressure chamber 82 of load pressure higher hydraulic cylinder 16 is located. That is, the stroke of the individual pressure compensator 52 is less than that of the load pressure-highest pressure compensator 54.
  • the opening stroke of the load pressure-highest individual pressure compensator 54 is chosen to be as large as possible so that it opens as far as possible, but does not reach the stroke stop and, accordingly, the throttling losses of the pressure-highest pressure compensator are minimized.
  • FIG. 3 shows the adjusting loop according to the concept of the invention.
  • a setting signal is output to the proportional solenoids 64, 66 of the pressure reducing valves 60, 62.
  • This control signal corresponds to a predetermined magnetic force F Mag . Accordingly, the pump pressure p P is then reduced via the respective pressure reducing valve 60, 62 to a control pressure in the control line 56, 58 and the associated individual pressure compensator 52, 54 adjusted.
  • the stroke x of the individual pressure is then detected by the transducer 72, 74 and then out of a comparator of the maximum stroke value x max of the driven individual pressure compensators 52, determined 54th This maximum value is compared with a desired stroke x soll stored in the memory of the control unit 22 and a signal is output via the control unit 22 when the stroke x max of the most widely open individual pressure compensator 54 is greater than the desired value. In this case, the control function of the widest open individual pressure compensator is no longer guaranteed.
  • a signal is then output via the control unit 22 to the pressure reducing valves 60, 62 in order to increase the pressure in the control line 56, 58 and thus to adjust the load pressure highest individual pressure compensator 54 in the closing direction until the setpoint stroke x soll is reached.
  • variable displacement pump 20 and inlet orifices 48, 50 the response of the system is improved by the almost simultaneous activation of variable displacement pump 20 and inlet orifices 48, 50.
  • a control arrangement for controlling a plurality of hydraulic consumers and a method for controlling the consumers, wherein each consumer an inlet orifice plate and an individual pressure compensator are assigned. This is acted upon in the closing direction by a controllable via a control unit control pressure.

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • Mining & Mineral Resources (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Fluid-Pressure Circuits (AREA)

Claims (14)

  1. Ensemble de commande hydraulique destiné à alimenter en fluide sous pression plusieurs consommateurs (14, 16, 18), une pompe (20) à cylindrée variable alimentant chacun des consommateurs (14, 16, 18) en fluide sous pression par un diaphragme d'amenée ajustable (48, 50) de mesure auquel est associée une balance individuelle de pression (52, 54),
    une pression pilote sensiblement identique pour toutes les balances individuelles (52, 54) de pression et ajustable par une unité de commande (22) étant appliquée sur les balances individuelles (52, 54) de pression dans la direction d'ouverture par la pression en aval de chacun des diaphragmes d'amenée ajustables (48, 50),
    caractérisé en ce que
    les balances individuelles (52, 54) de pression sont dotées d'un enregistreur de déplacement (72, 74) pour détecter une course.
  2. Ensemble de commande selon la revendication 1, dans lequel la pression pilote est réglée de telle sorte que la balance individuelle de pression (54) du consommateur (16) présentant la pression de charge la plus élevée est ajustée à une position d'ouverture de consigne (xsoll) et en ce que les balances individuelles de pression (52) des consommateurs (14, 18) à charge plus basse sont réglées à une section transversale d'ouverture plus petite.
  3. Ensemble de commande selon l'une des revendications 1 et 2, présentant une soupape (60, 62) de réduction de pression qui ajuste la pression pilote.
  4. Ensemble de commande selon la revendication 3, dans lequel la soupape (60, 62) de réduction de pression peut être ajustée électriquement ou électrohydrauliquement par l'intermédiaire de l'unité de commande (22).
  5. Ensemble de commande selon l'une des revendications précédentes, dans lequel l'établissement de la pression pilote s'effectue en fonction de la course (x) des balances individuelles (52, 54) de pression associés aux consommateurs (14, 16, 18).
  6. Ensemble de commande selon l'une des revendications précédentes, dans lequel en fonctionnement, l'établissement de la pression pilote s'effectue en fonction de la course (x) de la balance individuelle (54) de pression associée au consommateur (16) dont la pression de charge est la plus élevée.
  7. Ensemble de commande selon l'une des revendications précédentes, dans lequel au moins la balance individuelle de pression d'un consommateur prioritaire peut être réglée par ajustement de la pression pilote de telle sorte que la différence de pression à travers le diaphragme de mesure d'amenée associé reste essentiellement constante.
  8. Ensemble de commande selon l'une des revendications précédentes, dans lequel la pompe (20) à cylindrée variable est électro-proportionnelle.
  9. Ensemble de commande selon l'une des revendications précédentes, dans lequel la balance individuelle (52, 54) de pression et le diaphragme ajustable (48, 50) ainsi qu'éventuellement les soupapes (60, 62) de réduction de pression sont décentralisés et disposés au niveau de chaque consommateur hydraulique (14, 16, 18).
  10. Ensemble de commande selon l'une des revendications précédentes, dans lequel une section transversale d'ouverture de consigne aussi proche que possible de la section transversale maximale d'ouverture (butée de fin de course) est prévue.
  11. Ensemble de commande selon l'une des revendications précédentes, dans lequel les consommateurs sont des vérins hydrauliques (14, 16, 18) d'un engin mobile (1).
  12. Procédé de commande de plusieurs consommateurs hydrauliques (14, 16, 18) alimentés en fluide sous pression par une pompe (20) par l'intermédiaire d'une balance individuelle (52, 54) de pression et d'un diaphragme d'amenée ajustable (48, 50),
    une pression pilote sensiblement identique pour toutes les balances individuelles (52, 54) de pression et ajustable par une unité de commande (22) étant appliquée sur les balances individuelles (52, 54) de pression dans la direction d'ouverture par la pression en aval de chacun des diaphragmes d'amenée ajustables (48, 50),
    caractérisé par l'étape qui consiste à
    ajuster la pression pilote en fonction des sections transversales d'ouverture des balances individuelles (52, 54) de pression par l'intermédiaire d'une unité de commande (22).
  13. Procédé selon la revendication 12, dans lequel l'étape d'ajustement de la pression pilote par l'unité de commande (22) s'effectue en fonction de la balance individuelle (52, 54) de pression qui présente la plus grande des sections transversales d'ouverture.
  14. Procédé selon la revendication 13, dans lequel la valeur de consigne de la plus grande des sections transversales d'ouverture est inférieure à la section transversale d'ouverture maximale de la balance individuelle (52, 54) de pression.
EP12170158.5A 2011-07-01 2012-05-31 Agencement de commande et procédé de commande de plusieurs consommateurs hydrauliques Not-in-force EP2541072B1 (fr)

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DE102011106307A DE102011106307A1 (de) 2011-07-01 2011-07-01 Steueranordnung und Verfahren zum Ansteuern von mehreren hydraulischen Verbrauchern

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EP2541072A2 EP2541072A2 (fr) 2013-01-02
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EP2541072B1 true EP2541072B1 (fr) 2018-08-29

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Publication number Publication date
EP2541072A3 (fr) 2016-11-02
EP2541072A2 (fr) 2013-01-02
US20130167518A1 (en) 2013-07-04
CN102852872A (zh) 2013-01-02
CN102852872B (zh) 2016-09-14
DE102011106307A1 (de) 2013-01-03
US9200646B2 (en) 2015-12-01

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