EP2028376B1 - Agencement de commande hydraulique - Google Patents

Agencement de commande hydraulique Download PDF

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Publication number
EP2028376B1
EP2028376B1 EP08012275.7A EP08012275A EP2028376B1 EP 2028376 B1 EP2028376 B1 EP 2028376B1 EP 08012275 A EP08012275 A EP 08012275A EP 2028376 B1 EP2028376 B1 EP 2028376B1
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EP
European Patent Office
Prior art keywords
pressure
inlet
pump
hydraulic control
control device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP08012275.7A
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German (de)
English (en)
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EP2028376A3 (fr
EP2028376A2 (fr
Inventor
Gerhard Dr. Keuper
Heinrich Lödige
Peter Dr. Stachnik
Milan Djurovic
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Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
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Priority claimed from DE102007045803A external-priority patent/DE102007045803A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2028376A2 publication Critical patent/EP2028376A2/fr
Publication of EP2028376A3 publication Critical patent/EP2028376A3/fr
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Publication of EP2028376B1 publication Critical patent/EP2028376B1/fr
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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
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • F15B11/055—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive by adjusting the pump output or bypass
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2221—Control of flow rate; Load sensing arrangements
    • E02F9/2232—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps
    • E02F9/2235—Control of flow rate; Load sensing arrangements using one or more variable displacement pumps including an electronic controller
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2285—Pilot-operated systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2292—Systems with two or more pumps
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—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
    • 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
    • F15B11/168—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load with an isolator valve (duplicating valve), i.e. at least one load sense [LS] pressure is derived from a work port load sense pressure but is not a work port pressure itself
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load 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
    • F15B2211/305—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
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50536—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using unloading valves controlling the supply pressure by diverting fluid to the return line
    • 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
    • F15B2211/605—Load sensing circuits
    • F15B2211/6058—Load sensing circuits with isolator 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
    • F15B2211/65—Methods of control of the load sensing pressure
    • F15B2211/653—Methods of control of the load sensing pressure the load sensing pressure being higher than the load pressure

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1.
  • Such hydraulic control arrangements are used in particular in mobile work equipment, such as wheel loaders or tractors to provide their consumers, such as the working hydraulics, the steering, traction drives and / or accessories with pressure medium.
  • a hydraulic control arrangements is known, which is designed as a LS system.
  • the delivery rate of the pump is controlled so that in the pump line is applied by a certain pressure difference Ap above the highest load pressure of the consumer lying pump pressure.
  • each consumer an adjustable metering orifice and an individual pressure compensator are assigned, via which the pressure medium volume flow to the load can be adjusted independently of the load depending on the opening cross section of the metering orifice.
  • an inlet pressure compensator can be provided, via which a connection to the tank can be opened.
  • the inlet pressure compensator is acted upon in the closing direction by a control pressure corresponding to the highest load pressure and a spring and in the opening direction by the pump pressure. Their position is a measure of the difference between the pump pressure and the highest load pressure.
  • a so-called power beyond connection which has a pressure line, a return line and an LS line.
  • This power-beyond connection makes the load-sensing system of the implement also usable for the attachment.
  • the power beyond port for connecting a power beyond consumer, branches off the fluid flow path between the pump and the input pressure compensator.
  • the spring-side pressurization of the input pressure compensator is then carried out by one of the load pressures of the load of the working hydraulics or a power beyond consumer.
  • This hydraulic control arrangement allows a prioritized supply of power beyond consumers and an increase in the control pressure difference between the pump pressure and the highest load pressure when supplying power beyond consumers.
  • the invention has for its object to provide a suitable hydraulic control arrangement in which the transmission behavior is improved.
  • the pressure above the highest load pressure is tapped at a pressure medium path between the input of the inlet pressure compensator and a load reporting line for the largest of the load pressures, so that the pressure above the maximum load pressure can be realized with little circuitry outlay.
  • the pressure is tapped above the largest load pressure between two diaphragms, so that they work like a pressure divider.
  • the pressure difference to the highest reported load pressure can thus be finely adjusted by varying the geometries of the aperture.
  • a switching valve is switchable. It is further preferred that the switching valve is provided between one of the orifices and the inlet of the inlet pressure compensator. In particular, with electrical control of the switching valve, a short response time for the switching of the inlet pressure compensator can be implemented.
  • a further switching valve is provided between the two diaphragms and the pilot control port of the inlet pressure compensator, via which the inlet pressure compensator can be acted upon in the closing direction.
  • a pressure medium connection between the pilot control port of the inlet pressure compensator and an output port to at least one of the two consumers can be switched by the further switching valve.
  • a priority valve can be provided, via which a pressure medium supply of a priority consumer can be implemented with little circuit complexity.
  • a priority consumer can be supplied via an auxiliary pump and the pump with pressure medium or a priority consumer can only be supplied via an auxiliary pump with pressure medium.
  • the auxiliary pump is preferably a constant displacement pump.
  • the pressure between the pump and the inlet pressure compensator can preferably be limited by way of a pressure limiting valve, so that an increase in pressure in the pump above a maximum pressure level can be avoided.
  • the pump can be controlled depending on the position of a control piston of the inlet pressure compensator or in response to a residual volume flow to a tank connection of the inlet pressure compensator, so that a quick response to changing pressure conditions at the inlet pressure compensator by an electronic control is possible.
  • the inlet pressure compensator in a spring-biased basic position shuts off the connection to the at least one of the two consumers and to the tank and initially controls the connection to the at least one of the two consumers and then to the tank when adjusting in the opening direction. If the pump is controlled by a residual volume flow flowing to the tank, the inlet pressure balance is just in the third position. In this position, the pressure compensator also allows excess quantities to flow to the tank.
  • FIG. 1 shows a first embodiment of a hydraulic control arrangement of a mobile implement, such as a tractor.
  • This control arrangement may for example be formed by a mobile control block, via which a working hydraulic 2 is supplied with pressure medium, which is conveyed by a pump 4 and returned via an inlet pressure compensator 5 and the working hydraulics 2 to consumers and from these to a tank 6.
  • the pump 4 is formed in the illustrated embodiment as an electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8.
  • a variable speed fixed displacement pump or another pump controllable via a pump regulator can also be used.
  • FIG. 2 is the structure of the working hydraulics 2 off FIG. 1 which in this case has two double-acting cylinders 10, 12.
  • the sucked by the pump 4 from the tank 6 pressure fluid (s. Fig. 1 ) is conveyed via the inlet pressure compensator 5 in a pump channel 15, which branches into two supply lines 16, 18, wherein the supply line 16 to the cylinder 10 and the supply line 18 is assigned to the cylinder 12.
  • an individual pressure compensator 20 is provided, wherein the direction of pressure medium flow to the assigned consumer or the associated consumer and the pressure medium volume flow in relation to the associated consumer can be adjusted by the directional control valve 24.
  • an individual pressure compensator 26 is provided, wherein the direction of pressure medium flow direction to the associated consumer or the associated consumer and the pressure medium flow in relation to the associated consumer is adjustable by the directional control valve 30.
  • a flow line 32 which is connected to a bottom-side cylinder chamber 34 of the cylinder 10
  • a return line 36 which is connected to a piston rod-side annulus 38 of the cylinder 10 connected.
  • a flow line 40 which is connected to a bottom-side cylinder chamber 42 of the cylinder 12
  • a return line 44 which is connected to a piston rod side annular space 46 of the cylinder 12 connected.
  • pilot control device 52 By manual operation, or actuation of the pilot control device 52, whereby the control pressure difference is adjusted, the respective control piston 48 and 50 from the in Fig. 2 shown blocking position (0) in the direction of the indicated positions (a) or (b) adjusted, in which either the cylinder space 34, 42 or the annular space 38, 46 is supplied with pressure medium, while from the other pressure medium chamber, the pressure medium is displaced.
  • an inlet orifice plate in the directional control valves 24, 30 is controlled via an inlet control edge, the opening cross section of the respective inlet orifice plate determining the pressure medium volume flow to the cylinder 10, 12.
  • the pressure medium flowing back from the cylinder 10, 12 is supplied via a tank connection T to the respective directional control valve 24, 30 and a tank line 54 connected to the tank 6 (see FIG. Fig. 1 ) returned.
  • the individual pressure compensators 20, 26 are each acted upon in the opening direction by the force of a pressure compensator spring 56, 58 and by the load pressure at the respective consumer 10, 12.
  • In the closing direction acts on the pressure compensator slide of the individual pressure compensators 20, 26 each of the pressure in the supply line 16 and 18 between the output of the respective individual pressure compensator 20, 26 and the pressure input P of the downstream directional control valve 24, 30 through the respective individual pressure compensator 24, 30 and associated metering orifice, which is formed by the respective directional control valve 24, 30, a current regulator is formed.
  • the pressure drop across the orifice plate is kept constant independent of the load, so that the amount of pressure medium flowing through the measuring orifice depends solely on the opening cross section of the orifice.
  • the inlet pressure compensator 5 is provided, which is designed in this embodiment as a continuously adjustable 3/3-way valve.
  • a power beyond port 64 From a pump line 14 between the pressure port of the pump 4 and the input port P of the inlet pressure compensator 5 branches off a power beyond port 64. Via this it is possible to connect one or more additional hydraulic power beyond consumers 66, for example a loading wagon or a potato harvesting machine, to the mobile implement.
  • the power beyond consumers 66 can also be connected via the tank line 54 to the tank 6.
  • the highest load pressure of the power beyond consumers 66 is determined via a shuttle valve cascade and fed via a control line 69 to the shuttle valve 68.
  • the highest of the load pressures of the consumer 10, 12 is via the shuttle valve 74 (s. Fig. 2 ) and also supplied to the shuttle valve 68.
  • the slider 70 of the inlet pressure compensator 5 is acted upon in the closing direction by the force of a spring 72 and the pressure at a branch point 76 of a pressure medium path between the center port of the shuttle valve 68 and the pump line 14.
  • a branch point 76 of a pressure medium path between the center port of the shuttle valve 68 and the pump line 14 In the pressure medium path between the branch point 76 and the pump line 14, an aperture 78 and a 2/2-way switching valve 80 are arranged in series.
  • a diaphragm 82 Between the branching point 76 and the shuttle valve 68 is located in the pressure medium path, a diaphragm 82.
  • the 2/2-way valve 80 is electrically operated and is in Fig. 1 in the spring-biased locking position dargterrorism.
  • a low volume flow to the highest-load consumer which may be both the cylinder 10, 12 and a power beyond consumer 66, must flow in the load reporting line. Therefore, all shuttle valves 74, 68 must be suitable for this flow direction.
  • the pressure difference between the pressure at the branching point 76 and at the shuttle valve 68 is finely adjustable upon specification of a maximum permissible volume flow in the load reporting line by varying the geometry of the aperture 78, 82.
  • Fig. 1 illustrated spring 72 and the present at the branch point 76 and acting on the slider 70 pressure act on the slider 70 in the closing direction with a force.
  • the opening direction is located on the slider 70 of the Input pressure 5, the pressure in a control line 84, which is tapped upstream of the inlet pressure compensator 5 of the pump line 14, between the power beyond port 64 and the inlet pressure compensator 5.
  • the switching valve 80 is switched, so that the desired position of the pressure compensator slide 70 is reached only at a higher pump pressure. This setpoint position can be the same as before the pressure increase.
  • the aim is a constant EDW position setpoint.
  • the input port P of the inlet pressure compensator communicates with the pump line 14 in pressure medium connection
  • the working port A of the inlet pressure compensator 5 is connected via the pump channel 15 with the supply line 16, 18 (s. Fig. 2 ) connected.
  • the tank connection T of the inlet pressure compensator is connected via a tank line 86 to the tank 6 in pressure medium connection.
  • blocking position (0) of the inlet pressure compensator 5 is no pressure medium connection between the pump port P, the working port A and the tank port T.
  • working position (a) there is a pressure medium connection between the pump port P and the working port A.
  • working position (b) the pump port P, the working port A and the tank port T are in fluid communication.
  • the position of the slider 70 of the inlet pressure compensator is detected by a position transducer 88, whose output signal is fed to a control unit 90 which also controls the pump regulator 8.
  • the control unit 90 is an internal setpoint YEDW should be supplied.
  • a power beyond driver 92 triggers the pressure boost by switching the switching valve 80.
  • the power beyond driver 92 is initialized by a signal from an operator, or automatically.
  • the desired value y EDWsoll is compared with an output signal y EDW of the position transducer 88 and fed to a controller 94 in the control unit 90.
  • the setpoint y EDWsoll corresponds to the position (b) of the slider 70 of the inlet pressure compensator.
  • the outputs of the pilot 52 may, as shown in the Fig. 1 and 3 is also fed to the controller 84 and intervene in the control algorithm.
  • the inlet pressure compensator 5, s. FIG. 1 is moved with the power beyond consumer 66, from the locked position (0) to the working position (b) out swinging the pump 4 and concomitant increase in the amount of conveyed fluid.
  • the inlet pressure compensator reaches its setpoint position, the pump pressure is high enough. Next, the pump no longer swings.
  • the working position (b) of the inlet pressure compensator 5 ensures that the consumers 10, 12, the pressure medium from the pump 4 via the inlet pressure compensator 5 (s. Fig. 2 ) is supplied.
  • a residual volume flow flows via the tank connection T and the tank line 86.
  • the switching valve 80 is brought into its switching position (a)
  • a flow of pressure medium flows from the pump line 14 via the opened switching valve 80 and the orifices 78, 82 to the shuttle valve 68.
  • the orifices 78, 82 function as a pressure divider, wherein a higher pressure than the reported at the shuttle valve 68 highest load pressure at the branch point 76 and thus on the slider 70 is present to its blocking position.
  • the inlet pressure compensator 5 is kept in the working position (b) in its desired position, in which again flows a residual volume flow through the tank port T and the tank line 86.
  • the displacement sensor 88 is replaced by a residual current sensor on the tank line 86.
  • a direct measurement of the residual volume flow in the working position (b) is a sensitive and accurate pump control possible. Since in the hydraulic control arrangement according to the first embodiment, the position setpoint of the inlet pressure compensator 5 can be independent of the activation status of the pressure increase, this can be replaced by a residual volume flow setpoint.
  • the slider 70 of the inlet pressure compensator 5 then has the same position at high pump ⁇ p as at low pump ⁇ p.
  • the influence of the absolute height of the pump pressure on the residual volume flow, the position of the pressure compensator slide 70 and the pump ⁇ p is negligible.
  • a soft spring 72 may be used, whereby a small change in position of the slider 70 of the inlet pressure compensator 5 has only a slight effect on the pressure of the pump 4.
  • control can be adjusted by the control unit 90 in such a way that in the case in which the pump 4 in Unterbuch device and the input pressure compensator 5 closes to a certain extent, so that one of the consumers slows or stops, the Volume flow values of all active consumers of the working hydraulics are reduced in the same ratio until this state of undersupply is canceled again. Subsequently, the inlet pressure compensator 5 opens and can work in the switching position (b) with a predetermined residual chromium value.
  • FIG. 4 Referring to a second embodiment of the invention differs from the first embodiment in that priority functions of a priority consumer 96 and comfort functions of a comfort consumer 98 in the concept of hydraulic pressure increase of the first embodiment are included.
  • Fig. 1 For the implementation of the priority function, in Fig. 1 The following changes are made in the hydraulic control arrangement shown: In the spring-biased position (0) a pressure medium connection between the pressure port of the pump 4 and the inlet port of the priority consumer 96 (control valve plus actual consumer ), while the pressure medium connection to the pump port P of the pressure compensator 5 is blocked. In the position (a) of the priority valve 100, the pressure medium connection from the pump 4 to both the inlet port of the priority consumer 96 and the pump port P of the inlet pressure compensator 5 is opened.
  • the control piston 102 of the priority valve 100 is acted upon in the closing direction by the pressure of a spring 104 and the load pressure of the priority consumer on a load pressure line 106 and in the opening direction by the pressure at the inlet port of the priority consumer 96.
  • the load pressure of the priority consumer on the load pressure line 106 is compared via a shuttle valve 108 with the load pressure of the power beyond consumer 66 and reported the higher of these to the shuttle valve 68.
  • the pressure at branch point 76 between orifices 78 and 82 is at the in Fig. 4 illustrated, the second embodiment via a in its rest position (a) located comfort valve 110 on the slider 70 of the inlet pressure compensator 5.
  • the comfort valve 110 will be explained below in connection with the comfort function.
  • a pressure limiting valve 114 is connected to the pressure connection of the pump 4.
  • the priority consumer 96 as well as the power beyond consumer 66 is an unknown consumer.
  • the priority valve 100 At a high load pressure in the load pressure line 106 and undersupply by the pump 4, the priority valve 100 is in the in Fig. 4 shown position (0), in which a pressure medium connection between the pressure port of the pump 4 and only the input port of the priority consumer 96 is present. The pressure at the input port of the priority consumer 96 is applied to the control piston 102 of the priority valve 100 in the opening direction, while in the closing direction, the pressure of the spring 104 and the load pressure of the priority consumer 96 act.
  • the priority valve 100 is placed in position (a) in which a fluid communication between the pressure port of the pump 4 and both the input port of the priority consumer 96 and the pump port P of the inlet pressure compensator 5 is made.
  • the in Fig. 2 shown cylinder 10, 12 are also supplied with pressure medium.
  • the priority valve 100 is switched to the position (0), in the pressure medium connection to the cylinders 10, 12 is interrupted and only the priority consumer 96 is supplied with pressure medium.
  • the power beyond port 64 is located downstream of the priority valve 100 in the pump line 14.
  • Comfort functions such as the front axle suspension, are usually not integrated in the hydraulic signal circuit of the supply system.
  • comfort consumers 98 which is also connected downstream of the priority valve 100 to the pump line 14 to activate, the pressure of the pump 64 is raised to a maximum pressure level, which is controlled by the pressure cut of the pump 4.
  • This lifting is carried out by electrical control of the comfort valve 110 in the position (b) in which a pressure medium connection is blocked from the branch point 76 to the slider 70 of the input pressure compensator, while a pressure medium connection between the working port A of the inlet pressure compensator 5 and a pilot control line 112 is opened.
  • the pressure compensator now works like a pressure difference valve.
  • FIGS. 5 and 6 show alternative embodiments of the second embodiment for implementing the priority function.
  • the in the FIGS. 5 and 6 not shown, upper part of the hydraulic circuit is the upper part of the hydraulic circuit of Fig. 4 refer to.
  • auxiliary pump 116 mechanically coupled to the pump 4 for use, which is preferably a fixed displacement pump and by the priority consumer 96 with pressure medium can be supplied.
  • the highest of the load pressures of the priority consumer 96 and the power beyond consumer 66 is reported to the shuttle valve 68 via the shuttle valve 108 as in the second embodiment.
  • both the pump 4 and the auxiliary pump 116 convey pressure medium to the priority consumer 96.
  • the second modification of the second embodiment according to Fig. 6 differs from the first modification in that no pressure medium connection between the pump line 14 and the input terminal of the priority consumer 96 is provided.
  • the priority consumer 96 is thus supplied exclusively by the auxiliary pump 116 with pressure medium.
  • an electronic setpoint determination of all consumers to be supplied and an immediate integration in the supply concept via the control unit 90 via an adjustment of the valve setpoints is provided.
  • the hydraulic realization of the pressure increase and / or the prioritization of selected functions is limited to the case of defective electronic control. In normal operation, the prioritization or complete volume flow distribution in the system would take place via modification of the valve setpoint values and could be defined as desired.
  • the invention relates to a hydraulic control arrangement for controlling at least two consumers, which can be supplied via a pump with adjustable flow rate with pressure medium, in particular a mobile working device, and each of which is associated with an adjustable metering orifice.
  • a power beyond connection is provided, to which at least one power beyond consumer can be connected.
  • the pump is followed by an inlet pressure compensator, which in the pressure medium flow path between the pump and at least one of the two consumers is provided.
  • the power beyond port branches off in the fluid flow path between the pump and the input pressure compensator.
  • the inlet pressure compensator is acted upon in the closing direction by the force of a spring and in the opening direction by the pressure at its input. Furthermore, the inlet pressure compensator in the closing direction can optionally additionally be acted upon by the greatest load pressure or by a pressure above the greatest load pressure.

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

Claims (18)

  1. Agencement de commande hydraulique pour commander de préférence au moins deux consommateurs (10, 12) qui peuvent être alimentés en fluide sous pression avec une quantité refoulée ajustable par le biais d'une pompe (4), en particulier d'un engin de travail mobile, et auxquels est à chaque fois associé un diaphragme de dosage réglable (20, 26), comprenant un raccord Power-Beyond (64) auquel peut être raccordé au moins un consommateur de type Power-Beyond (66), et
    comprenant une balance de pression d'entrée (5) montée en aval de la pompe (4),
    la balance de pression d'entrée (5) étant prévue dans le trajet d'écoulement de fluide sous pression entre la pompe (4) et au moins l'un des deux consommateurs (10, 12) et le raccord Power-Beyond (64) se ramifiant dans le trajet d'écoulement de fluide sous pression entre la pompe (4) et la balance de pression d'entrée (5), et
    la balance de pression d'entrée (5) étant sollicitée dans le sens de la fermeture par la force d'un ressort (72) et dans le sens de l'ouverture par la pression à son entrée (P),
    caractérisé en ce que la balance de pression d'entrée (5) peut être sollicitée dans le sens de la fermeture en outre de manière sélective par la pression de charge maximale ou par une pression au-dessus de la pression de charge maximale.
  2. Agencement de commande hydraulique selon la revendication 1, dans lequel la pression au-dessus de la pression de charge maximale est prélevée au niveau d'un trajet de fluide sous pression entre l'entrée (P) de la balance de pression d'entrée (5) une ligne de signalisation de charge pour la plus importante des pressions de charge.
  3. Agencement de commande hydraulique selon la revendication 2, dans lequel la pression au-dessus de la pression de charge maximale est prélevée entre deux diaphragmes (78, 82).
  4. Agencement de commande hydraulique selon la revendication 2 ou 3, dans lequel le trajet de fluide sous pression entre l'entrée (P) de la balance de pression d'entrée (5) et la ligne de signalisation de charge pour la plus importante des pressions de charge peut être commuté par le biais d'une soupape de commutation (80).
  5. Agencement de commande hydraulique selon la revendication 4, dans lequel la soupape de commutation (80) est prévue entre l'un (78) des diaphragmes et l'entrée (P) de la balance de pression d'entrée (5).
  6. Agencement de commande hydraulique selon la revendication 2, dans lequel une soupape de commutation supplémentaire (110) est prévue entre les deux diaphragmes (78, 82) et le raccord pilote de la balance de pression d'entrée (5), par le biais duquel la balance de pression d'entrée peut être sollicitée dans le sens de la fermeture.
  7. Agencement de commande hydraulique selon la revendication 6, dans lequel une liaison de fluide sous pression entre le raccord pilote de la balance de pression d'entrée (5), par le biais duquel la balance de pression d'entrée peut être sollicitée dans le sens de la fermeture, et un raccord de sortie (A) à au moins l'un des deux consommateurs (10, 12) peut être commutée par la soupape de commutation supplémentaire (110).
  8. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel une soupape de priorité (100) est prévue entre la pompe (4) et la balance de pression d'entrée (5), par le biais de laquelle soupape de priorité une alimentation en fluide sous pression d'un consommateur prioritaire (96) peut être assurée.
  9. Agencement de commande hydraulique selon l'une quelconque des revendications 1 à 7, dans lequel un consommateur prioritaire (96) peut être alimenté en fluide sous pression par le biais d'une pompe auxiliaire (116) et par le biais de la pompe (4).
  10. Agencement de commande hydraulique selon l'une quelconque des revendications 1 à 7, dans lequel un consommateur prioritaire (96) ne peut être alimenté en fluide sous pression que par le biais d'une pompe auxiliaire (116).
  11. Agencement de commande hydraulique selon la revendication 9 ou 10, dans lequel la pompe auxiliaire (116) est une pompe à débit constant.
  12. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la pression entre la pompe (4) et la balance de pression d'entrée (5) peut être limitée par une soupape de limitation de pression (114).
  13. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel on effectue une détermination de valeur de consigne électronique de tous les consommateurs à alimenter ainsi qu'une augmentation de la pression hydraulique dans le cas d'une commande électronique défectueuse.
  14. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la pompe (4) peut être commandée en fonction de la position d'un coulisseau (70) de la balance de pression d'entrée (5).
  15. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la pompe (4) peut être commandée en fonction d'un débit volumique résiduel au niveau d'un raccord de réservoir (T) de la balance de pression d'entrée (5).
  16. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la balance de pression d'entrée (5) peut être sollicitée par la pression de charge maximale ou par une pression au-dessus de la pression de charge maximale de telle sorte que le piston de la balance de pression d'entrée (5), lorsque le consommateur de type Power-Beyond est branché et lorsque le consommateur de type Power-Beyond n'est pas branché, soit à chaque fois dans une position dans la région de la position de travail du piston dans laquelle un débit volumique résiduel s'écoule au niveau d'un raccord de réservoir (T) de la balance de pression d'entrée (5).
  17. Agencement de commande hydraulique selon la revendication 16, dans lequel la position dans la région de la position de travail du piston, dans laquelle un débit volumique résiduel s'écoule au niveau d'un raccord de réservoir (T) de la balance de pression d'entrée (5), lorsque le consommateur de type Power-Beyond est branché et que le consommateur de type Power-Beyond n'est pas branché, est la même.
  18. Agencement de commande hydraulique selon l'une quelconque des revendications précédentes, dans lequel la balance de pression d'entrée (5) dans une position de base précontrainte par un ressort bloque la liaison à l'au moins un des deux consommateurs (10, 12) et au réservoir (6) et lors du réglage dans le sens de l'ouverture commande à l'ouverture d'abord la liaison à l'au moins un des deux consommateurs (10, 12) puis au réservoir (6).
EP08012275.7A 2007-08-22 2008-07-08 Agencement de commande hydraulique Active EP2028376B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007039732 2007-08-22
DE102007045803A DE102007045803A1 (de) 2007-08-22 2007-09-25 Hydraulische Steueranordnung

Publications (3)

Publication Number Publication Date
EP2028376A2 EP2028376A2 (fr) 2009-02-25
EP2028376A3 EP2028376A3 (fr) 2012-08-08
EP2028376B1 true EP2028376B1 (fr) 2013-11-27

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Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012014250A1 (de) 2012-07-19 2014-01-23 Hydac System Gmbh Ventil, insbesondere Stetigventil
IT202100014123A1 (it) * 2021-05-28 2022-11-28 Walvoil Spa Distributore idraulico con dispositivo di compensazione per valvole direzionali
CN113638924A (zh) * 2021-09-13 2021-11-12 烟台杰瑞石油装备技术有限公司 绳锯机的液压系统和绳锯机

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4977928A (en) * 1990-05-07 1990-12-18 Caterpillar Inc. Load sensing hydraulic system
DE102004048684A1 (de) * 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulische Steueranordnung
DE102006008940A1 (de) * 2006-02-23 2007-08-30 Robert Bosch Gmbh Hydraulische Steueranordnung

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EP2028376A2 (fr) 2009-02-25

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