EP3816455A1 - Hydraulic control arrangement for supplying compressed media of at least two hydraulic consumers - Google Patents
Hydraulic control arrangement for supplying compressed media of at least two hydraulic consumers Download PDFInfo
- 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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- European Patent Office
- Prior art keywords
- hydraulic
- pressure medium
- consumer
- pressure
- consumers
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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
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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
- 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
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- 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
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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
- F15B13/06—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with two or more servomotors
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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
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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
- 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.
Abstract
Die Erfindung betrifft eine hydraulische Steueranordnung, mit der wenigstens zwei hydraulische Verbraucher gleichzeitig mit vorgebbaren individuellen Druckmittelmengen versorgbar sind und die aufweist eine in ihrem Hubvolumen verstellbaren Hydropumpe, wenigstens zwei Ventilanordnungen, von denen jede eine Zumessblende und eine stromab der Zumessblende angeordnete Druckwaage umfasst, die vom Druck stromab der jeweiligen Zumessblende in Öffnungsrichtung und von dem höchsten Lastdruck oder einem davon abgeleiteten Druck in Schließrichtung beaufschlagbar ist, und von denen jede zwischen einer von der Hydropumpe abgehenden Pumpenleitung und einem Verbraucher angeordnet ist, und mit einem elektronischen Steuereinrichtung, von der die Hydropumpe derart ansteuerbar ist, dass diese die Summe der individuellen Druckmittelmengen fördert, und von der die Zumessblenden bei ausreichender Fördermenge der Hydropumpe derart mit Steuersignalen ansteuerbar sind, dass deren Durchflussquerschnitte zueinander in denselben Verhältnissen stehen wie die individuellen Druckmittelmengen.Bei einer derartigen hydraulischen Steueranordnung ist eine auch veränderbare Priorisierung von Verbrauchern dadurch möglich, dass bei gleichzeitiger Ansteuerung mehrerer Zumessblenden und nicht ausreichender Fördermenge der Hydropumpe, die gleichzeitig angesteuerten Zumessblenden zugunsten eines bevorzugt mit Druckmittel zu versorgenden Verbrauchers mit Steuersignalen ansteuerbar sind, deren Verhältnisse zueinander von den Verhältnissen der individuellen Druckmittelmengen abweichen.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 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 consumer, and with an electronic control device from which the hydraulic pump is operated it can be controlled that it conveys the sum of the individual pressure medium quantities, and by 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 relative to one another With such a hydraulic control arrangement, a variable prioritization of consumers is possible in that with simultaneous control of several metering orifices and insufficient flow rate of the hydraulic pump, the simultaneously controlled metering orifices in favor of a consumer who is preferably to be supplied with pressure medium can be controlled with control signals, the ratios of which differ from the ratios of the individual pressure medium quantities.
Description
Die Erfindung betrifft eine hydraulische Steueranordnung, mit der wenigstens zwei hydraulische Verbraucher gleichzeitig mit vorgebbaren individuellen Druckmittelmengen versorgbar sind und die aufweist eine in ihrem Hubvolumen verstellbare Hydropumpe, wenigstens zwei Ventilanordnungen, von denen jede eine Zumessblende und eine stromab der Zumessblende angeordnete Druckwaage umfasst, die vom Druck stromab der jeweiligen Zumessblende in Öffnungsrichtung und von dem höchsten Lastdruck oder einem davon abgeleiteten Druck in Schließrichtung beaufschlagbar ist, und von denen jede zwischen einer von der Hydropumpe abgehenden Pumpenleitung und einem hydraulischen Verbraucher angeordnet ist, und mit einen elektronischen Steuereinrichtung, von der die Hydropumpe derart ansteuerbar ist, dass diese die Summe der individuellen Druckmittelmengen fördert, und von der die Zumessblenden bei ausreichender Fördermenge der Hydropumpe derart mit Steuersignalen ansteuerbar sind, dass deren Durchflussquerschnitte zueinander in denselben Verhältnissen stehen wie die individuellen Druckmittelmengen.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.
Aus der
Bei einer anderen, zum Beispiel aus der
In der
Der Erfindung liegt die Aufgabe zugrunde, eine hydraulische Steueranordnung mit den eingangs angeführten Merkmalen, derart weiterzuentwickeln, dass ein hydraulischer Verbraucher oder mehrere hydraulische Verbraucher gegenüber anderen hydraulischen Verbrauchern im Falle einer Unterversorgung bevorzugt mit hydraulischem Druckmittel versorgt werden.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.
Diese Aufgabe wird dadurch gelöst, dass in dem Fall, dass gleichzeitig mehrere Zumessblenden angesteuert werden und bei einer Unterversorgung die Summe der individuellen Druckmittelmengen die maximale Fördermenge der Hydropumpe überschreitet, die gleichzeitig angesteuerten Zumessblenden zugunsten eines bevorzugt mit Druckmittel zu versorgenden hydraulischen Verbrauchers mit Steuersignalen ansteuerbar sind, deren Verhältnisse zueinander von den Verhältnissen der vorgegebenen individuellen Druckmittelmengen abweichen. Bei einer erfindungsgemäßen hydraulischen Steueranordnung werden also im Falle einer Unterversorgung die Verhältnisse zwischen den Durchflussquerschnitten der gleichzeitig angesteuerten Zumessblenden im Vergleich zu den Durchflussquerschnitten, die den vorgegebenen individuellen Druckmittelmengen entsprechen, verändert.This object is achieved in that, in the event that several metering orifices are controlled simultaneously, and in the event of an undersupply, the sum of the individual Pressure medium quantities exceed the maximum delivery rate of the hydraulic pump, the simultaneously controlled metering orifices in favor of a hydraulic consumer preferably to be supplied with pressure medium can be controlled with control signals whose ratios differ from the ratios of the specified individual pressure medium quantities. In a hydraulic control arrangement according to the invention, in the event of an undersupply, the ratios between the flow cross-sections of the simultaneously actuated metering orifices are changed compared to the flow cross-sections which correspond to the specified individual pressure medium quantities.
Vorteilhafte Weiterbildungen einer erfindungsgemäßen hydraulischen Steueranordnung kann man den Unteransprüchen entnehmen.Advantageous further developments of a hydraulic control arrangement according to the invention can be found in the subclaims.
Die Verhältnisse zwischen den Durchflussquerschnitten können bei einer Unterversorgung dadurch verändert werden, dass der Durchflussquerschnitt einer einem bevorzugten hydraulischen Verbraucher zugeordneten Zumessblende bei gleicher vorgegebener Druckmittelmenge für diesen Verbraucher gegenüber dem Fall der ausreichenden Fördermenge vergrößert wird. Eine Vergrößerung des Durchflussquerschnitts ist allerdings nur bis zum maximalen Durchflussquerschnitt möglich. Außerdem kann das Verhalten eines hydraulischen Verbrauchers bei kleinen Durchflussquerschnitten stabiler als bei großen Durchflussquerschnitten sein.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. However, an increase in the flow cross-section is only possible up to the maximum flow cross-section. In addition, the behavior of a hydraulic consumer can be more stable with small flow cross-sections than with large flow cross-sections.
Deshalb wird es besonders bevorzugt, wenn bei einer Unterversorgung der Durchflussquerschnitt einer einem nachrangigen hydraulischen Verbraucher zugeordneten Zumessblende bei gleicher vorgegebener Druckmittelmenge für diesen Verbraucher gegenüber dem Fall der ausreichenden Fördermenge verkleinert wird. Es können jedoch im Fall einer Unterversorgung auch gleichzeitig der Durchflussquerschnitt der Zumessblende eines bevorzugten hydraulischen Verbrauchers vergrößert und der Durchflussquerschnitt der Zumessblende eines nachrangigen hydraulischen Verbrauchers verkleinert sein.It is therefore particularly preferred if, in the event of an undersupply, 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. In the event of an undersupply, however, 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.
Es ist auch möglich, im Fall einer Unterversorgung die einem bevorzugten hydraulischen Verbraucher zugeordnete Zumessblende und die einem nachrangigen hydraulischen Verbraucher zugeordnete Zumessblende derart anzusteuern, dass im Vergleich zum Fall einer ausreichenden Fördermenge das Verhältnis zwischen dem Steuersignal für die dem bevorzugten hydraulischen Verbraucher zugeordnete Zumessblende und dem Steuersignal für die dem nachrangigen hydraulischen Verbraucher zugeordnete Zumessblende vergrößert ist und die dem bevorzugten hydraulischen Verbraucher zufließende Druckmittelmenge verkleinert ist. Das heißt, dass im Fall der Unterversorgung dem bevorzugten hydraulischen Verbraucher zwar nicht die vorgegebene individuelle Druckmittelmenge zufließt, dass ihm jedoch im Verhältnis zum nachrangigen hydraulischen Verbraucher mehr Druckmittelmenge als bei ausreichender Fördermenge der Hydropumpe.It is also possible, in the event of an undersupply, to control the metering orifice assigned to a preferred hydraulic consumer and the metering orifice assigned to a subordinate hydraulic consumer in such a way that, compared to the case of a sufficient delivery rate, the ratio between the control signal for the metering orifice assigned to the preferred hydraulic consumer and the control signal for the metering orifice assigned to the subordinate hydraulic consumer is increased and the amount of pressure medium flowing to the preferred hydraulic consumer is reduced. This means that in the event of an undersupply, the preferred hydraulic consumer does not receive the specified individual amount of pressure medium, but that, in relation to the subordinate hydraulic consumer, it receives more pressure medium than with a sufficient flow rate of the hydraulic pump.
Es kann vorgesehen sein, dass im Fall einer Unterversorgung die Zumessblenden derart ansteuerbar sind, dass dem nachrangigen hydraulischen Verbraucher noch eine Mindestmenge an Druckmittel zufließt.It can be provided that, in the event of an undersupply, the metering orifices can be controlled in such a way that a minimum amount of pressure medium still flows to the subordinate hydraulic consumer.
Es kann eine Gruppe mit mindestens zwei in gleicher Weise bevorzugten hydraulischen Verbrauchern vorhanden sein, wobei im Fall einer Unterversorgung die Steuersignale an die diesen in gleicher Weise bevorzugten hydraulischen Verbrauchern zugeordneten Zumessblenden im Vergleich zu den Steuersignalen bei ausreichender Fördermenge verhältnisgleich verändert werden.There can be a group with at least two equally preferred hydraulic consumers, with the control signals to the metering orifices assigned to these equally preferred hydraulic consumers being changed proportionally compared to the control signals when there is sufficient flow in the event of an undersupply.
Es kann auch eine Gruppe mit mindestens zwei in gleicher Weise nachrangigen hydraulischen Verbrauchern vorhanden sein, wobei im Falle einer Unterversorgung die Steuersignale an die diesen nachrangigen hydraulischen Verbrauchern zugeordneten Zumessblenden im Vergleich zu den Steuersignalen bei ausreichender Fördermenge verhältnisgleich verändert werden.There can also be a group with at least two equally subordinate hydraulic consumers, in which case the 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.
Bevorzugt fließt im Fall einer Unterversorgung der Gruppe der nachrangigen hydraulischen Verbraucher in Summe noch eine Mindestmenge zu.In the event of an undersupply of the group of subordinate hydraulic consumers, a minimum amount preferably flows in total.
Wird die Hydropumpe nicht mit einer konstanten Drehzahl angetrieben, wie dieses bei Anwendungen auf mobilen Arbeitsmaschinen normalerweise der Fall ist, so hat die elektronische Steuereinrichtung einen Eingang für ein die Drehzahl der Hydropumpe angebendes Signal hat. Mit Hilfe des bekannten maximalen Hubvolumens der Hydropumpe und der Drehzahl der Hydropumpe kann elektronische Steuereinrichtung die augenblickliche maximale Fördermenge ermitteln.If the hydraulic pump is not driven at a constant speed, as is normally the case in applications on mobile work machines, 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.
Grundsätzlich kann eine erfindungsgemäße hydraulische Steueranordnung derart ausgebildet sein, dass einem Regelventil der Hydropumpe der höchste Lastdruck zugeführt wird und die Hydropumpe wie bei den bekannten Load-Sensing-Steueranordnungen so geregelt wird, dass sie einen Volumenstrom fördert, der einen um eine bestimmte Druckdifferenz über dem höchsten Lastdruck liegenden Pumpendruck erzeugt. Besonders bevorzugt ist jedoch eine Ausbildung einer erfindungsgemäßen hydraulischen Steueranordnung, bei der von der elektronischen Steuereinrichtung mit einem unter Berücksichtigung der Drehzahl der Hydropumpe der Summe der individuellen Druckmittelmengen entsprechendes Steuersignal die Hydropumpe derart volumenstromgeregelt steuerbar ist, dass diese die Summe der vorgegebenen individuellen Druckmittelmengen fördert. Das Hubvolumen, auf das die Hydropumpe bei einer bestimmten Summe der individuellen Druckmittelmengen zu stellen ist, ergibt sich aus der Drehzahl und der Summe der vorgegebenen individuellen Druckmittelmengen.In principle, a hydraulic control arrangement according to the invention 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. Particularly preferred, however, is an embodiment of a hydraulic control arrangement according to the invention in which 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.
Jede Zumessblende ist vorteilhafterweise an einem Steuerschieber ausgebildet, der Steuerschieber elektrohydraulisch betätigbar ist.Each metering orifice is advantageously formed on a control slide, the control slide can be actuated electro-hydraulically.
Es kann mindestens ein Bedienungselement, zum Beispiel ein Joystick, zur Erzeugung von den individuellen Druckmittelmengen entsprechenden Signalen für die elektronische Steuereinrichtung vorhanden sein.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.
Zwei Ausführungsbeispiele einer erfindungsgemäßen hydraulischen Steueranordnung, ein Diagramm mit einer beispielhaften Aufteilung einer maximalen Fördermenge einer Hydropumpe auf verschiedene hydraulische Verbraucher sowie ein ausführlicheres Schaltbild einer Hydropumpe, deren Hubvolumen elektronisch geregelt wird und die in einer hydraulischen Steueranordnung gemäß den
- Figur 1Figure 1
- das erste Ausführungsbeispiel, bei dem der höchste Lastdruck an die loadsensing geregelte Hydropumpe gemeldet wird und eine elektronische Steuereinheit die Zumessblenden ansteuert,the first embodiment, in which the highest load pressure is reported to the load sensing regulated hydraulic pump and an electronic control unit controls the metering orifices,
- Figur 2Figure 2
- das zweite Ausführungsbeispiel, bei dem eine elektronische Steuereinheit nicht nur die Zumessblenden ansteuert, sondern auch ein der Summe der für die hydraulischen Verbraucher vorgegebenen Druckmittelmengen entsprechendes elektrisches Signal an einen Pumpenregler gibt,the second embodiment, in which an electronic control unit not only controls the metering orifices, but also one of the sum of the for the hydraulic consumer gives the corresponding electrical signal to a pump controller, given the quantities of pressure medium,
- Figur 3Figure 3
- das Diagramm mit der beispielhaften Aufteilung einer maximalen Fördermenge einer Hydropumpe undthe diagram with the exemplary division of a maximum flow rate of a hydraulic pump and
- Figur 4Figure 4
- das Schaltbild einer Hydropumpe mit einem Schwenkwinkelsensor zusammen mit einem elektronischen Steuergerät.the circuit diagram of a hydraulic pump with a swivel angle sensor together with an electronic control unit.
Zu der hydraulischen Steueranordnung gemäß
Zu der hydraulischen Steueranordnung gemäß
Bei beiden hydraulischen Steueranordnungen ist der hydraulische Verbraucher 12 über eine Ventilanordnung 25, der hydraulische Verbraucher 13 über eine Ventilanordnung 26, der hydraulische Verbraucher 14 über eine Ventilanordnung 27 und der hydraulische Verbraucher 15 über eine Ventilanordnung 28 mit der Pumpenleitung 17 fluidisch verbindbar. Jede Ventilanordnung 25, 26, 27 und 28 weist eine elektrohydraulisch proportional verstellbare Zumessblende 30, die üblicherweise an einem Steuerschieber ausgebildet ist, der auch der Richtungssteuerung des jeweiligen hydraulischen Verbrauchers dient, und eine Druckwaage 31 auf, die stromab der Zumessblende 30 zwischen dieser und dem jeweiligen hydraulischen Verbraucher angeordnet ist. Alle Druckwaagen 31 sind in Schließrichtung vom höchsten Lastdruck aller gleichzeitig betätigten hydraulischen Verbraucher und eventuell von einer schwachen Feder und in Öffnungsrichtung von dem Druck beaufschlagt, der zwischen einer Zumessblende und einer Druckwaage ansteht. Sieht man von einer eventuell vorhanden schwachen Feder ab, so ist der Druck zwischen einer Zumessblende und einer Druckwaage gleich dem höchsten Lastdruck, da der Regelkolben einer Druckwaage jeweils eine Position einzunehmen sucht, in der an ihm ein Kräftegleichgewicht herrscht, und deshalb den zu einem hydraulischen Verbraucher fließenden Volumenstrom jeweils so stark androsselt, bis der in Öffnungsrichtung wirkende Druck gleich dem in Schließrichtung wirkenden höchsten Lastdruck ist. Weil alle Druckwaagen mit der gleichen Kraft in Schließrichtung beaufschlagt sind, steht stromab aller Zumessblenden derselbe Druck an, so dass über alle Zumessblenden dieselbe Druckdifferenz, nämlich die Differenz zwischen dem in der Pumpenleitung anstehenden Pumpendruck und dem Druck stromab der Zumessblenden besteht. Ändert sich der Pumpendruck, so ändert sich unabhängig vom individuellen Lastdruck der hydraulischen Verbraucher die Druckdifferenz über alle angesteuerten Zumessblenden in gleicher Weise. Das bedeutet, dass bei einer Änderung des Pumpendrucks die Volumenstromverteilung zwischen den angesteuerten Zumessblenden lastdruckunabhängig erhalten bleibt.In both hydraulic control arrangements, the
Bei beiden Ausführungsbeispielen wird der höchste Lastdruck über eine Kette von Wechselventilen 33 ausgewählt und auf die eine Seite der Druckwaagen 31 gegeben. Bei dem Ausführungsbeispiel nach
In den
Die hydraulische Steueranordnung nach
Die hydraulische Steueranordnung nach
Bei beiden Ausführungsbeispielen steuern die Steuergeräte 35 und 36 über die elektrischen Leitungen 36, 37, 38 und 39 die Zumessblenden 30 der Ventilanordnungen 25, 26, 27 und 28 in Abhängigkeit von den über den Joystick 41 vorgegebenen individuellen Druckmittelmengen derart an, dass sich an den Zumessblenden Durchflussquerschnitte ergeben, die im selben Verhältnis zueinander wie die vorgegebenen individuellen Druckmittelmengen stehen. Nimmt man zum Beispiel an, dass gleichzeitig den beiden Hydrozylindern 12 und 13 dieselbe, erste Druckmittelmenge, dem Hydrozylinder 14 eine zweite Druckmittelmenge, die doppelt so groß wie die erste Druckmittelmenge ist, und dem Hydrozylinder 15 eine dritte Druckmittelmenge zufließen sollen, die dreimal so groß wie die erste Druckmittelmenge ist, so werden die Zumessblenden so angesteuert, dass sich ihre Durchflussquerschnitte wie eins zu eins zu zwei zu drei verhalten.In both exemplary embodiments, the
Bei dem Ausführungsbeispiel nach
Bei dem Ausführungsbeispiel nach
Bei einer Ansteuerung der Zumessblenden entsprechend den vorgegebenen individuellen Druckmittelmengen würden in dem Fall, dass die Hydropumpe die Summe der vorgegebenen individuellen Druckmittelmengen nicht fördern kann, also im Fall der Unterversorgung, die den hydraulischen Verbrauchern zufließenden Druckmittelmengen verhältnisgleich reduziert.When the metering orifices are controlled according to the specified individual pressure medium quantities, in the event that the hydraulic pump cannot deliver the sum of the specified individual pressure medium quantities, i.e. in the case of undersupply, the pressure medium quantities flowing to the hydraulic consumers would be reduced proportionally.
Erfindungsgemäß ist jedoch nun vorgesehen, dass im Fall der Unterversorgung bestimmte hydraulische Verbraucher im Verhältnis zu anderen hydraulischen Verbrauchern bevorzugt mit Druckmittel versorgt werden. Dazu sind bei den hydraulischen Steueranordnungen nach den
Beispielhaft sei angenommen, dass bei den hydraulischen Steueranordnungen gemäß den
Mit dem Joystick 41 werden nun für den Hydrozylinder 14 anstatt 40 Liter auch 60 Liter wie für den Hydrozylinder 13 angefordert, so dass die Summe der vorgegebenen individuellen Druckmittelmengen auf 200 Liter steigt. Im Steuergerät 35 beziehungsweise 36 wird festgestellt, dass Unterversorgung vorliegt. Je nachdem, welcher Ablauf im Steuergerät hinterlegt ist, wird nun die Ansteuerung der Zumessblenden in verschiedener Weise geändert. Es kann der Durchflussquerschnitt der dem Hydrozylinder 12 zugeordneten Zumessblende unverändert bleiben, während die Durchflussquerschnitte der den Hydrozylindern 13 und 14 zugeordneten Zumessblenden auf einen 50 Litern entsprechenden Durchflussquerschnitt reduziert werden. Es kann aber auch der Durchflussquerschnitt der dem Hydrozylinder 12 zugeordneten Zumessblende auf 96 Liter vergrößert werden, während die Durchflussquerschnitte der den Hydrozylindern 13 und 14 zugeordneten Zumessblenden unverändert bleiben. Denkbar ist es auch, den Durchflussquerschnitt der einen Zumessblende zu vergrößern und die Durchflussquerschnitte der beiden anderen Zumessblenden zu verkleinern. Zum Beispiel kann der Durchflussquerschnitt der dem Hydrozylinder 12 zugeordneten Zumessblende entsprechend 88 Liter eingestellt werden. Die Durchflussquerschnitte der beiden anderen Zumessblenden entsprechen dann 55 Liter.With the
Das Diagramm gemäß
In
Man erkennt an der Höhe der kleinen Rechtecke, dass für alle sechs hydraulischen Verbraucher 46 bis 51 gleiche Druckmittelmengen angefordert werden. Und man erkannt an der Höhe des Rechtecks 45, dass die Summe der angeforderten Druckmittelmengen die maximale Fördermenge der Hydropumpe 45 weit übersteigt. Wie nun die maximale Fördermenge der Hydropumpe 44 verteilt wird, wird anhand des Rechtecks 52 deutlich, dessen Höhe der Höhe der Hydropumpe 44 entspricht und damit die maximale Fördermenge der Hydropumpe 44 symbolisiert. In das Rechteck 52 sind übereinander sechs kleinere Rechtecke eingezeichnet, die an sich die sechs Verbraucher 46 bis 51 darstellen und deren Höhe ein Maß für die einem hydraulischen Verbraucher tatsächlich zufließende Druckmittelmenge ist. Man erkennt, dass die für die untereinander gleichberechtigten hydraulischen Verbraucher 49, 50 und 51 in Summe vorgesehene Mindestmenge gleichmäßig auf diese hydraulischen Verbraucher verteilt ist. Man erkannt weiterhin, dass die noch für eine Verteilung zur Verfügung stehende Restmenge gleichmäßig auf die untereinander gleichberechtigten hydraulische Verbraucher 46, 47 und 48 verteilt ist, wobei jedem bevorzugten hydraulischen Verbrauchern 46, 47 und 48 eine größere Druckmittelmenge als jedem nachrangigen hydraulischen Verbraucher 49, 50 und 51 zufließt.It can be seen from the height of the small rectangles that the same pressure medium quantities are requested for all six
Auch hier sei ein zahlenmäßiges Beispiel betrachtet, wobei die maximale Fördermenge der Hydropumpe wiederum 180 Liter sei. Den hydraulischen Verbrauchern 49, 50 und 51 sollen auch im Fall einer Unterversorgung 60 Liter zufließen. Über einen oder mehrere Joysticks seien nun für alle hydraulischen Verbraucher gleiche Druckmittelmengen von 60 Litern angefordert. Die Summe der angeforderten Druckmittelmengen ist also 360 Liter und übersteigt weit die maximale Fördermenge der Hydropumpe. Deshalb werden die Zumessblenden so angesteuert, dass jedem der hydraulischen Verbraucher 49, 50 und 51 20 Liter und jedem der hydraulischen Verbraucher 46, 47 und 48 40 Liter an Druckmittel zufließen. Die Zumessblenden werden also so angesteuert, dass der Durchflussquerschnitt der den bevorzugten hydraulischen Verbrauchern 46, 47 und 48 zugeordneten Zumessblenden doppelt so groß wie der Durchflussquerschnitt der den nachrangigen hydraulischen Verbrauchern 49, 50 und 51 zugeordneten Zumessblenden ist. Man könnte also den Durchflussquerschnitt der den bevorzugten hydraulischen Verbrauchern 46, 47 und 48 zugeordneten Zumessblenden auf einen Wert stellen, wie er für 60 Liter bei ausreichender Versorgung vorgesehen ist, und den Durchflussquerschnitt der den nachrangigen hydraulischen Verbrauchern 49, 50 und 51 zugeordneten Zumessblenden auf einen Wert stellen, wie er für 30 Liter bei ausreichender Versorgung vorgesehen ist.Here, too, consider a numerical example, where the maximum delivery rate of the hydraulic pump is again 180 liters. The
Das Schaltbild gemäß
Der Zufluss und der Abfluss von Druckmittel zu und aus einer Stellkammer, in die der Stellkolben 62 eintaucht, wird durch ein proportional verstellbares 3/2 Wegeventil 70 gesteuert, das in einer Ruhestellung, die es unter der Wirkung einer Druckfeder 71 einnimmt, die Stellkammer mit seinem Druckanschluss verbindet, an dem ebenfalls der vom Wechselventil 65 ausgewählte höhere Druck ansteht. Durch einen Proportionalelektromagneten 72 kann des 3/2 Wegeventil 70 in eine Stellung gebracht werden, in der Druckmittel aus der Stellkammer in des Innere des Gehäuses der Hydropumpe und von dort über eine Tankanschluss T weiter zu einem Tank abfließen kann. Der Proportionalelektromagnet 72 wird entsprechend den Vorgaben durch einen in
Die Ansteuerung von Zumessblenden durch das elektronische Steuergerät 67 erfolgt mit einer Hydropumpe gemäß
- 1010
- HydropumpeHydraulic pump
- 1111
- Load-Sensing-ReglerLoad sensing regulator
- 1212th
- HydrozylinderHydraulic cylinder
- 1313th
- HydrozylinderHydraulic cylinder
- 1414th
- HydrozylinderHydraulic cylinder
- 1515th
- HydrozylinderHydraulic cylinder
- 1616
- Tanktank
- 1717th
- PumpenleitungPump line
- 2020th
- HydropumpeHydraulic pump
- 2121
- EP-RegelgerätEP control device
- 2525th
- VentilanordnungValve arrangement
- 2626th
- VentilanordnungValve arrangement
- 2727
- VentilanordnungValve arrangement
- 2828
- VentilanordnungValve arrangement
- 3030th
- ZumessblendeMetering orifice
- 3131
- DruckwaagePressure compensator
- 3333
- WechselventilShuttle valve
- 3535
- elektronisches Steuergerätelectronic control unit
- 3636
- elektronisches Steuergerätelectronic control unit
- 3737
- elektrische Leitungelectrical line
- 3838
- elektrische Leitungelectrical line
- 3939
- elektrische Leitungelectrical line
- 4040
- elektrische Leitungelectrical line
- 4141
- Joystickjoystick
- 4242
- Eingangssignal DrehzahlInput signal speed
- 4444
- HydropumpeHydraulic pump
- 4545
- Rechteckrectangle
- 4646
- hydraulischer Verbraucherhydraulic consumer
- 4747
- hydraulischer Verbraucherhydraulic consumer
- 4848
- hydraulischer Verbraucherhydraulic consumer
- 4949
- hydraulischer Verbraucherhydraulic consumer
- 5050
- hydraulischer Verbraucherhydraulic consumer
- 5151
- hydraulischer Verbraucherhydraulic consumer
- 5252
- Rechteckrectangle
- 6060
- HydropumpeHydraulic pump
- 6262
- StellkolbenControl piston
- 6363
- GegenkolbenOpposed piston
- 6464
- Federfeather
- 6565
- WechselventilShuttle valve
- 6666
- SchwenkwinkelsensorSwivel angle sensor
- 6767
- elektronisches Steuergerätelectronic control unit
- 6868
- DrucksensorPressure sensor
- 7070
- 3/2 Wegeventil3/2 way valve
- 7171
- DruckfederCompression spring
- 7272
- ProportionalelektromagnetProportional solenoid
- SS.
- TankanschlussTank connection
- AA.
- DruckanschlussPressure connection
- PP
- FremddruckanschlussExternal pressure connection
- TT
- TankanschlussTank connection
Claims (12)
dadurch gekennzeichnet, dass in dem Fall, dass gleichzeitig mehrere Zumessblenden (30) angesteuert werden und bei einer Unterversorgung die Summe der individuellen Druckmittelmengen die maximale Fördermenge der Hydropumpe (10, 20, 44) überschreitet, die gleichzeitig angesteuerten Zumessblenden (30) zugunsten eines bevorzugt mit Druckmittel zu versorgenden hydraulischen Verbrauchers (12; 46, 47, 48) mit Steuersignalen ansteuerbar sind, deren Verhältnisse zueinander von den Verhältnissen der vorgegebenen individuellen Druckmittelmengen abweichen.Hydraulic control arrangement with which at least two hydraulic consumers (12, 13, 14, 15; 46, 47, 48, 49, 50, 51) can be supplied with predeterminable individual pressure medium quantities at the same time and which has a hydraulic pump (10, 20 with adjustable stroke volume) , 44), from which the sum of the individual pressure medium quantities can be conveyed, at least two valve arrangements (25, 26, 27, 28), each of which comprises a metering orifice (30) and a pressure compensator (31) arranged downstream of the metering orifice (30), which can be acted upon by the pressure downstream of the respective metering orifice (30) in the opening direction and by the highest load pressure or a pressure derived therefrom in the closing direction, and each of which is between a pump line (17) and a hydraulic consumer (12, 13, 14, 15; 46, 47, 48, 49, 50, 51) is arranged, and with an electronic control device (35, 36), from which the metering orifices (30) start with control signals it is controllable that their flow cross-sections are in the same relationship to one another as the individual pressure medium quantities,
characterized in that in the event that several metering orifices (30) are controlled simultaneously and in the event of an undersupply, the sum of the individual pressure medium quantities exceeds the maximum delivery rate of the hydraulic pump (10, 20, 44), the simultaneously controlled metering orifices (30) are preferred in favor of one Hydraulic consumers (12; 46, 47, 48) to be supplied with pressure medium can be controlled with control signals, the ratios of which differ from the ratios of the predetermined individual pressure medium quantities.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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DE102019216771.3A DE102019216771A1 (en) | 2019-10-30 | 2019-10-30 | Hydraulic control arrangement for supplying pressure medium to at least two hydraulic consumers |
Publications (1)
Publication Number | Publication Date |
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EP3816455A1 true EP3816455A1 (en) | 2021-05-05 |
Family
ID=73013195
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20203260.3A Pending EP3816455A1 (en) | 2019-10-30 | 2020-10-22 | Hydraulic control arrangement for supplying compressed media of at least two hydraulic consumers |
Country Status (4)
Country | Link |
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US (1) | US11268545B2 (en) |
EP (1) | EP3816455A1 (en) |
CN (1) | CN112746997A (en) |
DE (1) | DE102019216771A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021212305A1 (en) | 2021-11-02 | 2023-05-04 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electronic control unit for a hydraulic drive, hydraulic drive and method with a hydraulic drive |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
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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)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4341244A1 (en) * | 1993-12-03 | 1995-06-08 | Orenstein & Koppel Ag | Control for dividing the flow in hydraulic systems among several consumers |
EP0566449B1 (en) | 1992-04-06 | 1995-12-20 | Rexroth-Sigma | Hydraulic maximum load and pressure compensating valve |
DE19714141A1 (en) | 1997-04-05 | 1998-10-08 | Mannesmann Rexroth Ag | Hydraulic control arrangement |
DE10332120A1 (en) | 2003-07-15 | 2005-02-03 | Bosch Rexroth Ag | Control arrangement and method for controlling at least two hydraulic consumers |
WO2005024245A1 (en) * | 2003-09-11 | 2005-03-17 | Bosch Rexroth Ag | Control system and method for supplying pressure means to at least two hydraulic consumers |
EP2541072A2 (en) * | 2011-07-01 | 2013-01-02 | Robert Bosch Gmbh | Control assembly and method for controlling multiple hydraulic consumers |
-
2019
- 2019-10-30 DE DE102019216771.3A patent/DE102019216771A1/en active Pending
-
2020
- 2020-10-22 EP EP20203260.3A patent/EP3816455A1/en active Pending
- 2020-10-26 US US17/079,666 patent/US11268545B2/en active Active
- 2020-10-30 CN CN202011195707.4A patent/CN112746997A/en active Pending
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP0566449B1 (en) | 1992-04-06 | 1995-12-20 | Rexroth-Sigma | Hydraulic maximum load and pressure compensating valve |
DE4341244A1 (en) * | 1993-12-03 | 1995-06-08 | Orenstein & Koppel Ag | Control for dividing the flow in hydraulic systems among several consumers |
DE19714141A1 (en) | 1997-04-05 | 1998-10-08 | Mannesmann Rexroth Ag | Hydraulic control arrangement |
DE10332120A1 (en) | 2003-07-15 | 2005-02-03 | Bosch Rexroth Ag | Control arrangement and method for controlling at least two hydraulic consumers |
WO2005024245A1 (en) * | 2003-09-11 | 2005-03-17 | Bosch Rexroth Ag | Control system and method for supplying pressure means to at least two hydraulic consumers |
EP2541072A2 (en) * | 2011-07-01 | 2013-01-02 | Robert Bosch Gmbh | Control assembly and method for controlling multiple hydraulic consumers |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102021212305A1 (en) | 2021-11-02 | 2023-05-04 | Robert Bosch Gesellschaft mit beschränkter Haftung | Electronic control unit for a hydraulic drive, hydraulic drive and method with a hydraulic drive |
Also Published As
Publication number | Publication date |
---|---|
US20210131455A1 (en) | 2021-05-06 |
DE102019216771A1 (en) | 2021-05-06 |
CN112746997A (en) | 2021-05-04 |
US11268545B2 (en) | 2022-03-08 |
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