EP3816455A1 - Dispositif de commande hydraulique destiné à l'alimentation en fluide de pression d'au moins deux consommateurs hydrauliques - Google Patents

Dispositif de commande hydraulique destiné à l'alimentation en fluide de pression d'au moins deux consommateurs hydrauliques Download PDF

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Publication number
EP3816455A1
EP3816455A1 EP20203260.3A EP20203260A EP3816455A1 EP 3816455 A1 EP3816455 A1 EP 3816455A1 EP 20203260 A EP20203260 A EP 20203260A EP 3816455 A1 EP3816455 A1 EP 3816455A1
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EP
European Patent Office
Prior art keywords
hydraulic
pressure medium
consumer
pressure
consumers
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EP20203260.3A
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German (de)
English (en)
Inventor
Botond Szeles
Matthias Jerg
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Robert Bosch GmbH
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Robert Bosch GmbH
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    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0416—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor with means or adapted for load sensing
    • F15B13/0417—Load sensing elements; Internal fluid connections therefor; Anti-saturation or pressure-compensation 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
    • 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
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
    • 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
    • F15B21/02—Servomotor systems with programme control derived from a store or timing device; Control devices therefor
    • 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
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • 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
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid 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
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in 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
    • F15B2211/405—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
    • F15B2211/60—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
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6309—Electronic controllers using input signals representing a pressure the pressure being a pressure source supply pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/633—Electronic controllers using input signals representing a state of the prime mover, e.g. torque or rotational speed
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • 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
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a hydraulic control arrangement with which at least two hydraulic consumers can be supplied with predeterminable individual pressure medium quantities at the same time and which has a hydraulic pump whose stroke volume is adjustable, at least two valve arrangements, each of which comprises a metering orifice and a pressure compensator arranged downstream of the metering orifice, which from Pressure downstream of the respective metering orifice in the opening direction and can be acted upon by the highest load pressure or a pressure derived therefrom in the closing direction, and each of which is arranged between a pump line outgoing from the hydraulic pump and a hydraulic consumer, and with an electronic control device from which the hydraulic pump can be controlled in such a way that it conveys the sum of the individual pressure medium quantities, and from which the metering orifices can be controlled with control signals when the flow rate of the hydraulic pump is sufficient in such a way that their flow cross sections middle are in the same relationship to one another as the individual quantities of pressure medium.
  • a hydraulic control arrangement in which pressure compensators arranged in series with the metering orifices are acted upon in the opening direction by the pressure downstream of the respective metering orifice and by a spring and in the closing direction by the pressure upstream of the metering orifice.
  • the pressure compensator is usually arranged upstream of the metering orifice so that the pressure downstream of the metering orifice is the load pressure of the respective hydraulic consumer.
  • the highest load pressure is selected with the help of a shuttle valve chain and reported to a load-sensing controller of the hydraulic pump, which adjusts the stroke volume of the hydraulic pump so that the pump pressure in the pump line by a fixed pressure difference of, for example, 20 bar is above the highest load pressure.
  • the amount of pressure medium flowing to a hydraulic consumer is determined solely by the flow cross-section of the respective metering orifice, independent of the load pressure, as long as the sum of the individual pressure medium quantities specified by the sum of the flow cross-sections of the metering orifices does not exceed the maximum delivery rate of the hydraulic pump.
  • Such a hydraulic control arrangement is therefore also referred to as a load-sensing (or LS) control arrangement for short.
  • the hydraulic pump tries to convey the amount of pressure medium that is required due to the flow cross-sections of the metering orifices.
  • undersupply i.e. when the sum of the individual pressure medium quantities exceeds the maximum delivery rate of the hydraulic pump, which results from the maximum stroke volume and the speed of the hydraulic pump, only the hydraulic consumer with the highest load pressure flows less pressure medium than desired.
  • the pressure compensators are arranged downstream of the metering orifices and are acted upon in the opening direction by the pressure after the respective metering orifice and in the closing direction by a control pressure in a 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 actuated at the same time, the metering orifices are opened to such an extent that the amount of pressure medium supplied by the hydraulic pump, which is adjusted to the stop, is less than the total amount of pressure medium required, i.e.
  • valve arrangement which, like an LUDV control arrangement, comprises a metering orifice and a pressure compensator arranged downstream of the metering orifice, which can be acted upon by the pressure downstream of the respective metering orifice in the opening direction and by the highest load pressure in the closing direction.
  • a weak spring can also act in the closing direction.
  • the metering orifices can be controlled by the electrical control device with control signals in such a way that the flow cross-sections are in the same relationship to one another as the individual pressure medium quantities.
  • the flow rate of the hydraulic pump and the flow cross-sections of the metering orifices are precisely matched to one another, since the flow distribution is determined by the flow cross-sections of the metering orifices and deviations in the flow rate of the hydraulic pump are not in a different movement sequence, but only in the speed of the movement is noticeable.
  • this can easily be corrected for the individual pressure medium quantities by entering other setpoint values, which is usually done via a joystick.
  • the DE 10332120 A1 known EFM control arrangement reduces the pressure medium quantities flowing to the individual hydraulic consumers regardless of the respective load pressure of the hydraulic consumers in the ratio of the actual flow rate to the desired flow rate.
  • the invention is based on the object of further developing a hydraulic control arrangement with the features listed above in such a way that a hydraulic consumer or several hydraulic consumers are preferably supplied with hydraulic pressure medium compared to other hydraulic consumers in the event of an undersupply.
  • the ratios between the flow cross-sections can be changed in the event of an undersupply by increasing the flow cross-section of a metering orifice assigned to a preferred hydraulic consumer with the same predetermined amount of pressure medium for this consumer compared to the case of a sufficient delivery rate.
  • an increase in the flow cross-section is only possible up to the maximum flow cross-section.
  • the behavior of a hydraulic consumer can be more stable with small flow cross-sections than with large flow cross-sections.
  • the flow cross-section of a metering orifice assigned to a subordinate hydraulic consumer is reduced with the same predetermined amount of pressure medium for this consumer compared to the case of a sufficient delivery rate.
  • the flow cross-section of the metering orifice of a preferred hydraulic consumer can simultaneously be increased and the flow cross-section of the metering orifice of a subordinate hydraulic consumer can be reduced.
  • the metering orifices can be controlled in such a way that a minimum amount of pressure medium still flows to the subordinate hydraulic consumer.
  • control signals to the metering orifices assigned to these equally preferred hydraulic consumers can be changed proportionally compared to the control signals when there is sufficient flow in the event of an undersupply.
  • control signals to the metering orifices assigned to these subordinate hydraulic consumers are changed proportionally compared to the control signals when the flow rate is sufficient.
  • a minimum amount preferably flows in total.
  • the electronic control device has an input for a signal indicating the speed of the hydraulic pump. With the aid of the known maximum stroke volume of the hydraulic pump and the speed of the hydraulic pump, the electronic control device can determine the instantaneous maximum delivery rate.
  • a hydraulic control arrangement can be designed in such a way that the highest load pressure is fed to a control valve of the hydraulic pump and the hydraulic pump is regulated, as in the known load-sensing control arrangements, so that it delivers a volume flow which is a certain pressure difference above the pump pressure lying at the highest load pressure.
  • the electronic control device can control the hydraulic pump in a volume flow-controlled manner by the electronic control device with a control signal corresponding to the sum of the individual pressure medium quantities, taking into account the speed of the hydraulic pump, that it delivers the sum of the specified individual pressure medium quantities.
  • the stroke volume to which the hydraulic pump is to be set for a certain sum of the individual pressure medium quantities results from the speed and the sum of the specified individual pressure medium quantities.
  • Each metering orifice is advantageously formed on a control slide, the control slide can be actuated electro-hydraulically.
  • At least one operating element for example a joystick, can be present for generating signals for the electronic control device that correspond to the individual quantities of pressure medium.
  • a hydraulic pump 10 adjustable in its stroke volume, which has a load-sensing controller 11 and from which four hydraulic cylinders 12, 13, 14 and 15 can be supplied with pressure medium as hydraulic consumers in the exemplary embodiment.
  • the hydraulic pump 10 is, for example, an axial piston pump and sucks pressure medium from a tank 16 and discharges it into a pump line 17.
  • the load sensing controller 11 is connected to the pump line 17.
  • the load-sensing controller 11 is reported the highest load pressure of all hydraulic consumers actuated at the same time.
  • the stroke volume of the hydraulic pump 10 is set so that the pressure in the pump line 17 is a certain pressure difference, the so-called pump ⁇ p, above the highest load pressure.
  • FIG. 2 includes a hydraulic pump 20, which is also adjustable in its stroke volume and sucks pressure medium from a tank 16 and discharges it into a pump line 17.
  • the hydraulic pump 20 also supplies four hydraulic cylinders 12, 13, 14 and 15 with pressure medium.
  • the hydraulic pump 20 is not load sensing regulated, but rather volume flow regulated and has an EP control device 21, for example.
  • the stroke volume of a hydraulic pump is set proportionally to an electrical signal, for example proportionally to the level of the electrical current flowing through an electro-proportional magnet.
  • the hydraulic consumer 12 can be fluidically connected to the pump line 17 via a valve arrangement 25, the hydraulic consumer 13 via a valve arrangement 26, the hydraulic consumer 14 via a valve arrangement 27 and the hydraulic consumer 15 via a valve arrangement 28.
  • Each valve arrangement 25, 26, 27 and 28 has an electro-hydraulically proportionally adjustable metering orifice 30, which is usually on a control slide is formed, which also serves to control the direction of the respective hydraulic consumer, and a pressure compensator 31, which is arranged downstream of the metering orifice 30 between this and the respective hydraulic consumer.
  • All pressure compensators 31 are acted upon in the closing direction by the highest load pressure of all simultaneously actuated hydraulic consumers and possibly by a weak spring and in the opening direction by the pressure that is present between a metering orifice and a pressure compensator. If one disregards a possibly existing weak spring, the pressure between a metering orifice and a pressure compensator is equal to the highest load pressure, since the control piston of a pressure compensator always tries to assume a position in which there is an equilibrium of forces, and therefore that of a hydraulic one The flow rate flowing in the consumer is throttled until the pressure acting in the opening direction is equal to the highest load pressure acting in the closing direction.
  • the same pressure is present downstream of all metering orifices, so that the same pressure difference exists across all metering orifices, namely the difference between the pump pressure in the pump line and the pressure downstream of the metering orifices. If the pump pressure changes, the pressure difference across all controlled metering orifices changes in the same way, regardless of the individual load pressure of the hydraulic consumers. This means that when the pump pressure changes, the volume flow distribution between the controlled metering orifices remains independent of the load pressure.
  • the highest load pressure is selected via a chain of shuttle valves 33 and applied to one side of the pressure compensators 31.
  • the highest load pressure is also reported to the load sensing controller. The latter is not the case in the exemplary embodiment according to FIG Figure 2 .
  • the hydraulic control arrangement according to Figure 1 has an electronic control unit 35, which is connected via electrical lines 37, 38, 39 and 40 to electrical actuators (not shown in detail), for example to electro-proportional magnets, each of which actuates a pilot valve designed as a pressure reducing valve.
  • the flow cross-section of a metering orifice 30 is set proportionally to an electrical signal that is generated by the electronic control unit 35.
  • the electronic control unit 35 is supplied with control signals from a joystick 41, which represent the setpoint signals for the flow cross-section of the metering orifices, thus the setpoint volume flows to the hydraulic cylinders and thus the setpoint speed at which a hydraulic cylinder should move.
  • an input signal 42 representing the speed of the hydraulic pump 20 is fed to control unit 35.
  • the hydraulic control arrangement according to Figure 2 has an electronic control unit 36 which, like the control unit 35, has Figure 1 controls the metering orifices via electrical lines 36, 37, 38 and 39.
  • the control unit 36 of the exemplary embodiment is also used Figure 2 an input signal 42 representing the speed of the hydraulic pump 20 is supplied.
  • a sum signal is formed which corresponds to the sum of all specified individual pressure medium quantities.
  • a control signal for the EP control device 21 of the hydraulic pump 20 is generated in the control device 36, taking into account the speed of the hydraulic pump 20, which sets such a stroke volume of the hydraulic pump 20 that it delivers the sum of all specified individual pressure medium quantities at the given speed . If the speed or the sum signal change, the control signal for the EP control device 21 is also changed.
  • control units 35 and 36 control the metering orifices 30 of the valve assemblies 25, 26, 27 and 28 via the electrical lines 36, 37, 38 and 39 as a function of the individual pressure medium quantities specified via the joystick 41 in such a way that the Metering orifices result in flow cross-sections that are in the same relationship to one another as the specified individual pressure medium quantities.
  • the two hydraulic cylinders 12 and 13 are to flow the same first amount of pressure medium, the hydraulic cylinder 14 a second amount of pressure medium that is twice as large as the first amount of pressure medium, and the hydraulic cylinder 15 is to be supplied with a third amount of pressure medium that is three times as large as is the first pressure medium quantity, the metering orifices are controlled in such a way that their flow cross-sections behave like one to one to two to three.
  • the delivery rate of the hydraulic pump 20 is independent of how large the flow cross-sections of the metering orifices 30 are for predetermined individual pressure medium quantities. Depending on the size of the flow cross-section, the pump pressure is higher or lower. In practice, the flow cross-sections are selected so that a pressure drop in the range between 10 bar and 20 bar occurs across the metering orifices, as is also the case across the metering orifices in the exemplary embodiment Figure 1 consists.
  • the metering orifice that is assigned to the hydraulic consumer with the greatest volume flow requirement can be fully opened, with the metering orifices of the other simultaneously actuated hydraulic consumers being opened in the same ratio as in FIG DE 103 32 120 A1 is described.
  • the hydraulic cylinder 12 is a preferred hydraulic consumer to which the predetermined amount of pressure medium is to flow in each case.
  • the other hydraulic cylinders 13, 14 and 15 are considered equal.
  • the hydraulic pump 10 or 20 may be able to deliver a maximum of 180 liters at the present speed.
  • the hydraulic cylinder 12 should 80 liters, the hydraulic cylinder 13 should 60 liters, the hydraulic cylinder 14 should 40 liters and the hydraulic cylinder 15 should not have anything.
  • the liter data always relate to 1 minute. So at the moment a total of 180 liters are requested. There is no undersupply and the metering orifices of the valve assemblies 25, 26 and 27 are opened according to the specified individual pressure medium quantities.
  • control unit 35 or 36 it is determined that there is an undersupply.
  • control of the metering orifices is now changed in various ways.
  • the flow cross-section of the metering orifice assigned to the hydraulic cylinder 12 can remain unchanged, while the flow cross-sections of the metering orifices assigned to the hydraulic cylinders 13 and 14 are reduced to a flow cross-section corresponding to 50 liters.
  • the flow cross-section of the metering orifice assigned to the hydraulic cylinder 12 can also be increased to 96 liters, while the flow cross-sections of the metering orifices assigned to the hydraulic cylinders 13 and 14 remain unchanged. It is also conceivable to enlarge the flow cross-section of one metering orifice and to reduce the flow cross-sections of the other two metering orifices. For example, the flow cross-section of the metering orifice assigned to the hydraulic cylinder 12 can be adjusted to 88 liters. The flow cross-sections of the other two metering orifices then correspond to 55 liters.
  • the diagram according to Figure 3 illustrates a procedure in which, in the event of an undersupply, subordinate hydraulic consumers are also included a minimum amount can be supplied and the pressure medium quantities flowing to the preferred hydraulic consumers are less reduced in relation to the pressure medium quantities requested by the joystick than the volume flows to the subordinate hydraulic consumers.
  • the minimum amount for the subordinate hydraulic consumers can be a percentage of the maximum delivery rate currently possible at the present speed of the hydraulic pump or an absolute minimum amount.
  • the height of a rectangle symbolizing a hydraulic pump 44 indicates the maximum delivery rate of the hydraulic pump 44.
  • six hydraulic consumers 46 to 51 are symbolized by smaller rectangles lying one above the other, the height of a smaller rectangle being the specified individual pressure medium quantity for a hydraulic consumer and the height of rectangle 45 being the sum of those given for the six hydraulic consumers 46 to 51 symbolize individual pressure medium quantities.
  • the six hydraulic consumers are divided into two groups, namely a group with the hydraulic consumers 46, 47 and 48 and a group with the hydraulic consumers 49, 50 and 51, which are subordinate to the consumers 46, 47 and 48, but in the case the undersupply should still be supplied with a minimum amount overall.
  • the hydraulic consumers within a group have equal rights.
  • the maximum delivery rate of the hydraulic pump is again 180 liters.
  • the hydraulic consumers 49, 50 and 51 should also receive 60 liters in the event of an undersupply.
  • the same pressure medium quantities of 60 liters are now requested for all hydraulic consumers via one or more joysticks.
  • the sum of the required pressure medium quantities is therefore 360 liters and far exceeds the maximum flow rate of the hydraulic pump.
  • the metering orifices are therefore controlled in such a way that 20 liters of pressure medium flow to each of the hydraulic consumers 49, 50 and 51 and 40 liters to each of the hydraulic consumers 46, 47 and 48.
  • the metering orifices are thus controlled such that the flow cross section of the metering orifices assigned to the preferred hydraulic consumers 46, 47 and 48 is twice as large as the flow cross section of the metering orifices assigned to the lower-ranking hydraulic consumers 49, 50 and 51.
  • the circuit diagram according to Figure 4 symbolizes an axial piston machine 60 in swash plate design, the swivel angle of the swash plate and thus the stroke volume of the hydraulic pump 60 being regulated.
  • the swash plate can be adjusted above zero, so that the axial piston machine 60 can be operated both as a hydraulic pump and as a hydraulic motor without reversing the direction of rotation.
  • the axial piston machine 60 is referred to as the hydraulic pump 60 for short. This has a tank connection S and a pressure connection A.
  • the adjustment device for adjusting the swash plate comprises an actuating piston 62, which acts in one adjustment direction, and a counter-piston 63, which acts together with a spring 64 in the opposite direction and whose effective area is smaller than the effective area of the actuating piston 62.
  • a shuttle valve 65 is used to determine whether the pressure in pressure port A or an external pressure present at port P is the higher pressure. The higher pressure applied to the Opposing piston 64. Due to the spring 63, the swash plate assumes an end position when the hydraulic pump 60 is out of operation.
  • the swivel angle of the swash plate is detected by a swivel angle sensor 66, which sends a corresponding electrical signal to an electronic control unit 67.
  • the inflow and outflow of pressure medium to and from an actuating chamber into which the actuating piston 62 is immersed is controlled by a proportionally adjustable 3/2-way valve 70, which in a rest position, which it assumes under the action of a compression spring 71, with the actuating chamber connects its pressure connection, at which the higher pressure selected by the shuttle valve 65 is also present.
  • a proportional solenoid 72 By means of a proportional solenoid 72, the 3/2-way valve 70 can be brought into a position in which pressure medium can flow out of the actuating chamber into the interior of the housing of the hydraulic pump and from there via a tank connection T to a tank.
  • the proportional solenoid 72 is according to the specifications by an in Figure 4 Joystick (not shown), the speed of the hydraulic pump 60 and the signal emitted by the swivel angle sensor 66 are controlled by the electronic control unit 67 in such a way that the hydraulic pump 60 conveys the sum of the requested individual pressure medium quantities.
  • the control of metering orifices by the electronic control unit 67 takes place with a hydraulic pump according to FIG Figure 4 in the case of a sufficient amount of pressure medium conveyed and in the case of undersaturation as in the exemplary embodiments according to the Figures 1 and 2 by the control device 35 or by the control device 36.

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  • Engineering & Computer Science (AREA)
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  • Civil Engineering (AREA)
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EP20203260.3A 2019-10-30 2020-10-22 Dispositif de commande hydraulique destiné à l'alimentation en fluide de pression d'au moins deux consommateurs hydrauliques Pending EP3816455A1 (fr)

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DE102019216771.3A DE102019216771A1 (de) 2019-10-30 2019-10-30 Hydraulische Steueranordnung zur Druckmittelversorgung wenigstens zweier hydraulischer Verbraucher

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021212305A1 (de) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Elektronische Steuereinheit für einen hydraulischen Antrieb, hydraulischer Antrieb und Verfahren mit einem hydraulischen Antrieb

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11261582B1 (en) * 2021-01-29 2022-03-01 Cnh Industrial America Llc System and method for controlling hydraulic fluid flow within a work vehicle using flow control valves

Citations (6)

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Publication number Priority date Publication date Assignee Title
DE4341244A1 (de) * 1993-12-03 1995-06-08 Orenstein & Koppel Ag Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher
EP0566449B1 (fr) 1992-04-06 1995-12-20 Rexroth-Sigma Distributeur hydraulique combinant la compensation de pression et la sélection de pression maximale
DE19714141A1 (de) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung
DE10332120A1 (de) 2003-07-15 2005-02-03 Bosch Rexroth Ag Steueranordnung und Verfahren zur Ansteuerung von wenigstens zwei hydraulischen Verbrauchern
WO2005024245A1 (fr) * 2003-09-11 2005-03-17 Bosch Rexroth Ag Dispositif de commande et procede d'alimentation en milieu sous pression d'au moins deux charges hydrauliques
EP2541072A2 (fr) * 2011-07-01 2013-01-02 Robert Bosch Gmbh Agencement de commande et procédé de commande de plusieurs consommateurs hydrauliques

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0566449B1 (fr) 1992-04-06 1995-12-20 Rexroth-Sigma Distributeur hydraulique combinant la compensation de pression et la sélection de pression maximale
DE4341244A1 (de) * 1993-12-03 1995-06-08 Orenstein & Koppel Ag Steuerung zur Aufteilung des Förderstromes bei Hydrauliksystemen auf mehrere Verbraucher
DE19714141A1 (de) 1997-04-05 1998-10-08 Mannesmann Rexroth Ag Hydraulische Steueranordnung
DE10332120A1 (de) 2003-07-15 2005-02-03 Bosch Rexroth Ag Steueranordnung und Verfahren zur Ansteuerung von wenigstens zwei hydraulischen Verbrauchern
WO2005024245A1 (fr) * 2003-09-11 2005-03-17 Bosch Rexroth Ag Dispositif de commande et procede d'alimentation en milieu sous pression d'au moins deux charges hydrauliques
EP2541072A2 (fr) * 2011-07-01 2013-01-02 Robert Bosch Gmbh Agencement de commande et procédé de commande de plusieurs consommateurs hydrauliques

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021212305A1 (de) 2021-11-02 2023-05-04 Robert Bosch Gesellschaft mit beschränkter Haftung Elektronische Steuereinheit für einen hydraulischen Antrieb, hydraulischer Antrieb und Verfahren mit einem hydraulischen Antrieb

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CN112746997A (zh) 2021-05-04
DE102019216771A1 (de) 2021-05-06
US20210131455A1 (en) 2021-05-06

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