EP2028376A2 - Hydraulic control device - Google Patents
Hydraulic control device Download PDFInfo
- Publication number
- EP2028376A2 EP2028376A2 EP08012275A EP08012275A EP2028376A2 EP 2028376 A2 EP2028376 A2 EP 2028376A2 EP 08012275 A EP08012275 A EP 08012275A EP 08012275 A EP08012275 A EP 08012275A EP 2028376 A2 EP2028376 A2 EP 2028376A2
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- EP
- European Patent Office
- Prior art keywords
- pressure
- pump
- hydraulic control
- control arrangement
- arrangement according
- 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.)
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Images
Classifications
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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
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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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- 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
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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
- E02F9/2278—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
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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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- 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
- 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
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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
- F15B2211/20—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
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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
- F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
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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
- F15B2211/50—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
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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
- F15B2211/605—Load sensing circuits
- F15B2211/6058—Load sensing circuits with isolator 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
- F15B2211/65—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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Abstract
Description
Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung mehrerer Verbraucher gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of
Derartige hydraulische Steueranordnungen werden insbesondere bei mobilen Arbeitsgeräten, beispielsweise bei Radladern oder Schleppern verwendet, um deren Verbraucher, beispielsweise die Arbeitshydraulik, die Lenkung, Fahrantriebe oder/und Zusatzgeräte mit Druckmittel zu versorgen. Aus der
Zum Anschluss von Anbaugeräten oder Zusatzgeräten ohne eigene Druckmittelversorgung ist ein sogenannter Power-Beyond-Anschluss vorgesehen, der eine Druckleitung, eine Rücklaufleitung und eine LS-Leitung aufweist. Dieser Power-Beyond-Anschluss macht das Load-Sensing-System des Arbeitsgerätes auch für das Anbaugerät nutzbar. Der Power-Beyond-Anschluss, zum Anschließen eines Power-Beyond-Verbrauchers, zweigt von dem Druckmittelströmungspfad zwischen der Pumpe und der Eingangsdruckwaage ab. Die federseitige Druckbeaufschlagung der Eingangsdruckwaage erfolgt dann durch einen der Lastdrücke der Verbraucher der Arbeitshydraulik oder eines Power-Beyond-Verbrauchers. Diese hydraulische Steueranordnung gestattet eine priorisierte Versorgung der Power-Beyond-Verbraucher sowie eine Anhebung der Regeldruckdifferenz zwischen Pumpendruck und höchstem Lastdruck bei Versorgung von Power-Beyond-Verbrauchern.To connect attachments or attachments without their own pressure medium supply a so-called power beyond connection is provided, 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.
Entsprechend der Lösung aus der
Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine geeignete hydraulische Steueranordnung zu schaffen, bei der das Übertragungsverhalten verbessert ist.In contrast, the invention has for its object to provide a suitable hydraulic control arrangement in which the transmission behavior is improved.
Die Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruchs 1 gelöst.The object is achieved by a hydraulic control arrangement having the features of
Es wird eine hydraulische Steueranordnung zur Ansteuerung von vorzugsweise zumindest zwei Verbrauchern vorgesehen, die über eine Pumpe mit einstellbarer Fördermenge mit Druckmittel versorgbar sind, insbesondere eines mobilen Arbeitsgerätes, und denen jeweils eine verstellbare Zumessblende zugeordnet ist, mit einem Power-Beyond-Anschluss, an den zumindest ein Power-Beyond-Verbraucher anschließbar ist, und mit einer der Pumpe nachgeschalteten Eingangsdruckwaage, die im Druckmittelströmungspfad zwischen der Pumpe und zumindest einem der zwei Verbraucher vorgesehen ist und dass der Power-Beyond-Anschluss im Druckmittelströmungspfad zwischen der Pumpe und der Eingangsdruckwaage abzweigt, und wobei die Eingangsdruckwaage in Schließrichtung von der Kraft einer Feder und in Öffnungsrichtung vom Druck an ihrem Eingang beaufschlagt ist, wobei die hydraulische Steueranordnung dadurch gekennzeichnet ist, dass die Eingangsdruckwaage in Schließrichtung zusätzlich wahlweise vom größten Lastdruck oder von einem Druck oberhalb des größten Lastdrucks beaufschlagbar ist. Auf diese Weise ist die Druckanhebung der Pumpe auf hydraulische Weise realisierbar, wodurch sich das Übertragungsverhalten des Systems verbessert.It is a hydraulic control arrangement for controlling preferably at least two consumers provided which can be supplied via a pump with adjustable flow rate with pressure medium, in particular a mobile implement, and each associated with an adjustable metering orifice, with a power beyond connection to the at least one power beyond consumer is connectable, and with a pump downstream input pressure compensator, which is provided in the pressure medium flow path between the pump and at least one of the two consumers and that the power beyond branch in the pressure fluid flow path between the pump and the inlet pressure compensator, and wherein the inlet pressure compensator in the closing direction is acted upon by the force of a spring and in the opening direction by the pressure at its input, wherein the hydraulic control arrangement is characterized in that the inlet pressure compensator in the closing direction additionally optionally from the largest La or pressure from a pressure above the maximum load pressure can be acted upon. In this way, the pressure increase of the pump can be realized in a hydraulic manner, whereby the transmission behavior of the system improves.
Es wird bevorzugt, wenn der Druck oberhalb des größten Lastdrucks an einem Druckmittelpfad zwischen dem Eingang der Eingangsdruckwaage und einer Lastmeldeleitung für den größten der Lastdrücke abgegriffen wird, so dass mit geringem schaltungstechnischem Aufwand der Druck oberhalb des größten Lastdrucks realisierbar ist.It is preferred if 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.
Vorzugsweise wird der Druck oberhalb des größten Lastdrucks zwischen zwei Blenden abgegriffen, so dass diese wie ein Druckteiler funktionieren. Die Druckdifferenz zum höchsten gemeldeten Lastdruck kann somit durch Variation der Geometrien der Blenden fein eingestellt werden.Preferably, 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.
In einer vorteilhaften Ausbildung ist der Druckmittelpfad zwischen dem Eingang der Eingangsdruckwaage und der Lastmeldeleitung für den größten der Lastdrücke über ein Schaltventil schaltbar. Es wird ferner bevorzugt, dass das Schaltventil zwischen einer der Blenden und dem Eingang der Eingangsdruckwaage vorgesehen ist. Insbesondere bei elektrischer Ansteuerung des Schaltventils ist eine kurze Ansprechzeit für das Schalten der Eingangsdruckwaage umsetzbar.In an advantageous embodiment of the pressure medium path between the input of the input pressure compensator and the load reporting line for the largest of the load pressures via 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.
In einer Weiterbildung ist zwischen den zwei Blenden und dem Vorsteueranschluss der Eingangsdruckwaage, über den die Eingangsdruckwaage in Schließrichtung beaufschlagbar ist, ein weiteres Schaltventil vorgesehen. Vorzugsweise ist durch das weitere Schaltventil eine Druckmittelverbindung zwischen dem Vorsteueranschluss der Eingangsdruckwaage und einem Ausgangsanschluss zu zumindest einem der zwei Verbraucher schaltbar. Dadurch kann eine Pumpendruckanhebung auf ein Maximaldruckniveau umgesetzt werden, so dass alle Verbraucher in einem Konstantdrucksystem arbeiten können und sich eine Komfortfunktion realisieren lässt.In a further development, 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. Preferably, 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. As a result, a pump pressure increase can be implemented to a maximum pressure level, so that all consumers can work in a constant pressure system and a comfort function can be realized.
Zwischen Pumpe und Eingangsdruckwaage kann ein Prioritätsventil vorgesehen sein, über das eine Druckmittelversorgung eines Prioritätsverbrauchers mit geringem schaltungstechnischem Aufwand umsetzbar ist.Between the pump and the inlet pressure compensator, a priority valve can be provided, via which a pressure medium supply of a priority consumer can be implemented with little circuit complexity.
Alternativ dazu kann ein Prioritätsverbraucher über eine Hilfspumpe und über die Pumpe mit Druckmittel versorgbar sein oder kann ein Prioritätsverbraucher nur über eine Hilfspumpe mit Druckmittel versorgbar sein. Im Fall der Unterversorgung durch die Hauptpumpe oder einer hohen dynamischen Beanspruchung von dieser ist somit eine sichere Umsetzung der Prioritätsfunktion möglich. Die Hilfspumpe ist bevorzugt eine Konstantpumpe.Alternatively, 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. In the case of undersupply by the main pump or a high dynamic load of this, therefore, a secure implementation of the priority function is possible. The auxiliary pump is preferably a constant displacement pump.
Der Druck zwischen Pumpe und Eingangsdruckwaage ist bevorzugt über ein Druckbegrenzungsventil begrenzbar, so dass eine Druckerhöhung bei der Pumpe über ein Maximaldruckniveau hinaus vermieden werden kann.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.
Es kann ferner eine elektronische Sollwertermittlung der Mengenanforderungen aller zu versorgenden Verbraucher und eine hydraulische Druckanhebung bei defekter elektronischer Steuerung erfolgen, wodurch sich ein verbessertes Übertragungsverhalten ergibt.It can also be an electronic setpoint determination of the quantity requirements of all consumers to be supplied and a hydraulic pressure increase in case of defective electronic control, resulting in an improved transmission behavior.
Die Pumpe kann in Abhängigkeit von der Position eines Steuerkolbens der Eingangsdruckwaage oder in Abhängigkeit von einem Restvolumenstrom an einem Tankanschluss der Eingangsdruckwaage ansteuerbar sein, so dass eine schnelle Reaktion auf veränderte Druckverhältnisse an der Eingangsdruckwaage durch eine elektronische Steuerung möglich ist.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.
In einer vorteilhaften Weiterbildung sperrt die Eingangsdruckwaage in einer federvorgespannten Grundstellung die Verbindung zu dem zumindest einen der zwei Verbraucher und zum Tank ab und steuert diese bei Verstellen in Öffnungsrichtung zunächst die Verbindung zu dem zumindest einen der zwei Verbraucher und dann zum Tank auf. Wird die Pumpe über einen zum Tank fließenden Restvolumenstrom gesteuert, befindet sich die Eingangsdruckwaage knapp in der dritten Position. In dieser Position lässt die Druckwaage auch Überschussmengen zum Tank abfließen.In an advantageous refinement, 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.
Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.Advantageous developments of the invention are the subject of the dependent claims.
Im Folgenden werden bevorzugte Ausführungsbeispiele der Erfindung anhand schematischer Zeichnungen näher erläutert. Es zeigen:
- Die
Fig. 1 eine hydraulische Steueranordnung entsprechend einem ersten Ausführungsbeispiel, - die
Fig. 2 einen Ausschnitt aus der hydraulischen Steueranordnung entsprechend dem ersten Ausführungsbeispiel, - die
Fig. 3 ein Steuerungskonzept entsprechend dem ersten Ausführungsbeispiel, - die Fit. 4 eine hydraulische Steueranordnung entsprechend dem zweiten Ausführungsbeispiel,
- die
Fig. 5 eine hydraulische Steueranordnung entsprechend einer ersten Abwandlung des zweiten Ausführungsbeispiels, und - die
Fig. 6 eine hydraulische Steueranordnung entsprechend einer zweiten Abwandlung des zweiten Ausführungsbeispiels.
- The
Fig. 1 a hydraulic control arrangement according to a first embodiment, - the
Fig. 2 a detail of the hydraulic control arrangement according to the first embodiment, - the
Fig. 3 a control concept according to the first embodiment, - the fit. 4 shows a hydraulic control arrangement according to the second embodiment,
- the
Fig. 5 a hydraulic control arrangement according to a first modification of the second embodiment, and - the
Fig. 6 a hydraulic control arrangement according to a second modification of the second embodiment.
In
Der Steuerkolben 48 des Wegeventils 24 und der Steuerkolben 50 des Wegeventils 30 werden über ein in
Die Individualdruckwaagen 20, 26 werden jeweils in Öffnungsrichtung von der Kraft einer Druckwaagenfeder 56, 58 sowie von dem Lastdruck am jeweiligen Verbraucher 10, 12 beaufschlagt. In Schließrichtung wirkt auf die Druckwaagenschieber der Individualdruckwaagen 20, 26 jeweils der Druck in der Zulaufleitung 16 bzw. 18 zwischen dem Ausgang der jeweiligen Individualdruckwaage 20, 26 und dem Druckeingang P des nachgeschalteten Wegeventils 24, 30. Durch die jeweilige Individualdruckwaage 24, 30 und die zugeordnete Zumessblende, die durch das jeweilige Wegeventil 24, 30 ausgebildet ist, wird ein Stromregler gebildet. Der Druckabfall über dessen Messblende wird lastunabhängig konstant gehalten, so dass die über die Messblende fließende Druckmittelmenge allein vom Öffnungsquerschnitt der Messblende abhängt.The
Gemäß
Von einer Pumpenleitung 14 zwischen dem Druckanschluss der Pumpe 4 und dem Eingangsanschluss P der Eingangsdruckwaage 5 zweigt ein Power-Beyond-Anschluss 64 ab. Über diesen ist es möglich, einen oder mehrere zusätzliche hydraulische Power-Beyond-Verbraucher 66, beispielsweise eines Ladewagens oder einer Kartoffelvollerntemaschine, an das mobile Arbeitsgerät anzuschließen.From a
Die Power-Beyond-Verbraucher 66 können ferner über die Tankleitung 54 mit dem Tank 6 verbunden werden. Der höchste Lastdruck der Power-Beyond-Verbraucher 66 wird über eine Wechselventilkaskade ermittelt und über eine Steuerleitung 69 dem Wechselventil 68 zugeführt. Der höchste der Lastdrücke der Verbaucher 10, 12 wird über das Wechselventil 74 (s.
Der Schieber 70 der Eingangsdruckwaage 5 wird in Schließrichtung von der Kraft einer Feder 72 sowie dem Druck an einem Verzweigungspunkt 76 eines Druckmittelpfades zwischen dem Mittenanschluss des Wechselventils 68 und der Pumpenleitung 14 beaufschlagt. Im Druckmittelpfad zwischen dem Verzweigungspunkt 76 und der Pumpenleitung 14 sind eine Blende 78 und ein 2/2-Schaltventil 80 in Reihenschaltung angeordnet. Zwischen dem Verzweigungspunkt 76 und dem Wechselventil 68 befindet sich im Druckmittelpfad eine Blende 82. Das 2/2-Schaltventil 80 wird elektrisch betätigt und ist in
Beim Anlegen einer Steuerspannung an das Schaltventil 80 öffnet sich der Druckmittelpfad zwischen der Pumpenleitung 14 und der Blende 78. Infolge des unterschiedlichen Druckniveaus an der Pumpenleitung 14 und am Wechselventil 68 fließt ein Volumenstrom über die Blenden 80, 82, wobei diese als ein Druckteiler wirken. Der Druck am Verzweigungspunkt 76 liegt an der Federseite des Schiebers 70 an und ist höher als der am Wechselventil 68 gemeldete höchste Lastdruck. Durch diese Druckerhöhung wird die gewollte Druckanhebung im System umgesetzt.When a control voltage is applied to the switching
Zur Umsetzung der Druckanhebung im System entsprechend dem ersten Ausführungsbeispiel der Erfindung muss in der Lastmeldeleitung ein geringer Volumenstrom zum lasthöchsten Verbraucher, der sowohl der Zylinder 10, 12 als auch ein Power-Beyond-Verbraucher 66 sein kann, fließen. Daher müssen alle Wechselventile 74, 68 für diese Strömungsrichtung geeignet sein.In order to implement the pressure increase in the system according to the first exemplary embodiment of the invention, a low volume flow to the highest-load consumer, which may be both the
Die Druckdifferenz zwischen dem Druck am Verzweigungspunkt 76 und am Wechselventil 68 ist bei Vorgabe eines maximal zulässigen Volumenstroms in der Lastmeldeleitung durch Variation der Geometrie der Blenden 78, 82 fein einstellbar.The pressure difference between the pressure at the branching
Die in
Der Eingangsanschluss P der Eingangsdruckwaage steht mit der Pumpenleitung 14 in Druckmittelverbindung, der Arbeitsanschluss A der Eingangsdruckwaage 5 ist über den Pumpenkanal 15 mit der Zulaufleitung 16, 18 (s.
In der in
Die Position des Schiebers 70 der Eingangsdruckwaage wird über einen Wegaufnehmer 88 erfasst, dessen Ausgangssignal einem Steuergerät 90 zugeleitet wird, das auch den Pumpenregler 8 steuert.The position of the
Unter Bezugnahme auf
Der Sollwert yEDWsoll wird mit einem Ausgangssignal yEDW des Wegaufnehmers 88 verglichen und einem Regler 94 im Steuergerät 90 zugeführt. Der Sollwert yEDWsoll entspricht der Position (b) des Schiebers 70 der Eingangsdruckwaage. Die Ausgangssignale des Vorsteuergeräts 52 können, wie es in den
Die Eingangsdruckwaage 5, s.
Wird bei Aktivierung eines Power-Beyond-Verbrauchers 66 das Schaltventil 80 in seine Schaltposition (a) gebracht, so fließt ein Druckmittelstrom von der Pumpenleitung 14 über das geöffnete Schaltventil 80 und die Blenden 78, 82 zum Wechselventil 68. Die Blenden 78, 82 funktionieren als Druckteiler, wobei ein höherer Druck als der am Wechselventil 68 gemeldete höchste Lastdruck am Verzweigungspunkt 76 und somit am Schieber 70 zu seiner Sperrposition hin vorliegt. Bei einer ausreichenden Druckanhebung in der Pumpenleitung 14 wird die Eingangsdruckwaage 5 in der Arbeitsposition (b) in ihrer Sollposition gehalten, in der wieder ein Restvolumenstrom über den Tankanschluss T und die Tankleitung 86 abströmt. Selbst bei einem hohen Volumenstrombedarf des Power-Beyond-Verbrauchers 66 werden sowohl die Verbraucher 10, 12 als auch der Power-Beyond-Verbraucher 66 hinreichend mit Druckmittel versorgt, sofern die Pumpe 6 entsprechend ausgelegt ist.If, when activating a power beyond
Mit der hydraulischen Steueranordnung entsprechend dem ersten Ausführungsbeispiel ist sichergestellt, dass bei Unterversorgung die Eingangsdruckwaage 5 in Schließrichtung verstellt und der Druckmittelstrom zu den anderen Verbrauchern 10, 12 durch die Eingangsdruckwaage 5 vermindert oder eingestellt wird, und somit eine Unterversorgung des Power-Beyond-Verbrauchers 66 vermieden wird und dieser priorisiert ist.With the hydraulic control arrangement according to the first embodiment, it is ensured that in case of insufficient supply the
In einer alternativen Ausführungsform des ersten Ausführungsbeispiels ist der Wegaufnehmer 88 durch einen Reststromsensor an der Tankleitung 86 ersetzt. Durch eine direkte Messung des Restvolumenstroms in der Arbeitposition (b) ist eine feinfühlige und genaue Pumpensteuerung möglich. Da bei der hydraulischen Steuerungsanordnung entsprechend dem ersten Ausführungsbeispiel der Lagesollwert der Eingangsdruckwaage 5 unabhängig vom Aktivierungsstatus der Druckanhebung sein kann, kann dieser durch einen Restvolumenstrom-Sollwert ersetzt werden.In an alternative embodiment of the first embodiment, the
Der Schieber 70 der Eingangsdruckwaage 5 hat dann beim hohen Pumpen-Δp dieselbe Position wie bei niedrigem Pumpen-Δp. Der Einfluss der absoluten Höhe des Pumpendrucks auf den Restvolumenstrom, die Position des Druckwaagenschiebers 70 und das Pumpen-Δp ist vernachlässigbar. Zudem kann eine weiche Feder 72 verwendet werden , wodurch sich eine geringe Positionsänderung des Schiebers 70 der Eingangsdruckwaage 5 nur in geringem Maße auf den Druck der Pumpe 4 auswirkt.The
Ferner kann die Steuerung durch das Steuergerät 90 in einer solchen Weise angepasst werden, dass in dem Fall, in dem die Pumpe 4 in Unterversorgung gerät und die Eingangsdruckwaage 5 in einem bestimmten Maße schließt, so dass einer der Verbraucher langsamer wird oder stehen bleibt, die Volumenstromwerte aller aktiven Verbraucher der Arbeitshydraulik in gleichem Verhältnis verringert werden, bis dieser Zustand der Unterversorgung wieder aufgehoben ist. Im Anschluss öffnet die Eingangsdruckwaage 5 und kann in der Schaltposition (b) mit vorgegebenem Restromwert arbeiten.Furthermore, the control can be adjusted by the
Für die Umsetzung der Prioritätsfunktion wurden in der in
Der Steuerkolben 102 des Prioritätsventils 100 ist in Schließrichtung durch den Druck einer Feder 104 und den Lastdruck des Prioritätsverbrauchers an einer Lastdruckleitung 106 und in Öffnungsrichtung durch den Druck am Einlassanschluss des Prioritätsverbrauchers 96 beaufschlagt. Der Lastdruck des Prioritätsverbrauchers an der Lastdruckleitung 106 wird über ein Wechselventil 108 mit dem Lastdruck des Power-Beyond-Verbrauchers 66 verglichen und der höhere von diesen zum Wechselventil 68 gemeldet.The
Für die normale Funktion liegt der Druck am Verzweigungspunkt 76 zwischen den Blenden 78 und 82 bei dem in
Um einen übermäßigen Druckanstieg am Druckanschluss der Pumpe 4 zu vermeiden, ist ein Druckbegrenzungsventil 114 mit dem Druckanschluss der Pumpe 4 verbunden.In order to avoid an excessive increase in pressure at the pressure connection of the
Nachfolgend erfolgt eine Beschreibung der Prioritätsfunktion, durch die beispielsweise die Lenkung, die Anhängerbremsfunktion oder die Getriebeschmierung, die mit erster Priorität zu versorgen sind, umsetzbar sind. Dabei stellt der Prioritätsverbraucher 96 genauso wie der Power-Beyond-Verbraucher 66 einen unbekannten Verbraucher dar. Bei einem hohen Lastdruck in der Lastdruckleitung 106 und bei Unterversorgung durch die Pumpe 4 befindet sich das Prioritätsventil 100 in der in
Der Power-Beyond-Anschluss 64 befindet sich stromabwärts von dem Prioritätsventil 100 in der Pumpenleitung 14.The power beyond
Komfortfunktionen, wie die Vorderachsfederung, sind in der Regel nicht in den hydraulischen Signalkreis des Versorgungssystems integriert. Um nun den in
Die sonstigen hydraulischen Elemente der Steuerungsanordnung gemäß dem zweiten Ausführungsbeispiel entsprechen denjenigen des ersten Ausführungsbeispiels und werden daher nicht näher beschrieben.The other hydraulic elements of the control arrangement according to the second embodiment correspond to those of the first embodiment and are therefore not described in detail.
Die
Statt des Prioritätsventils 100 aus
In der ersten Abwandlung nach
Die zweite Abwandlung des zweiten Ausführungsbeispiels nach
Bei der ersten und zweiten Abwandlung des zweiten Ausführungsbeispiels werden Leistungsverluste des Hilfskreises bei inaktivem Prioritätsverbraucher 96 durch einen Neutralumlauf reduziert.In the first and second modification of the second embodiment, power losses of the auxiliary circuit with
Alternativ zur hydraulischen Steueranordnung entsprechend dem ersten und zweiten Ausführungsbeispiel und deren Abwandlungen kann eine elektronische Sollwertermittlung aller zu versorgenden Verbraucher und eine unmittelbare Einbindung in das Versorgungskonzept über das Steuergerät 90 über eine Anpassung der Ventilsollwerte erfolgen. Dadurch ist eine weitere Verbesserung des Ubertragungsverhaltens der hydraulischen Steueranordnung bei einem hohen Flexibilitätsgrad möglich. Die hydraulische Realisierung der Druckanhebung und/oder der Priorisierung ausgewählter Funktionen ist auf den Fall der defekten elektronischen Steuerung begrenzt. Im normalen Betrieb würde die Priorisierung bzw. die komplette Volumenstromverteilung im System über Modifikation der Ventilsollwerte erfolgen und könnte beliebig definiert werden.As an alternative to the hydraulic control arrangement according to the first and second embodiments and their modifications, an electronic setpoint determination of all consumers to be supplied and an immediate integration in the supply concept via the
Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung von zumindest zwei Verbrauchern, die über eine Pumpe mit einstellbarer Fördermenge mit Druckmittel versorgbar sind, insbesondere eines mobilen Arbeitsgerätes, und denen jeweils eine verstellbare Zumessblende zugeordnet ist. Es ist ein Power-Beyond-Anschluss vorgesehen, an den zumindest ein Power-Beyond-Verbraucher anschließbar ist. Der Pumpe ist eine Eingängsdruckwaage nachgeschaltet, die im Druckmittelströmungspfad zwischen der Pumpe und zumindest einem der zwei Verbraucher vorgesehen ist. Der Power-Beyond-Anschluss zweigt im Druckmittelströmungspfad zwischen der Pumpe und der Eingangsdruckwaage ab. Die Eingangsdruckwaage ist in Schließrichtung von der Kraft einer Feder und in Öffnungsrichtung vom Druck an ihrem Eingang beaufschlagt. Ferner ist die Eingangsdruckwaage in Schließrichtung wahlweise zusätzlich vom größten Lastdruck oder von einem Druck oberhalb des größten Lastdrucks beaufschlagbar.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.
Claims (18)
mit einem Power-Beyond-Anschluss (64), an den zumindest ein Power-Beyond-Verbraucher (66) anschließbar ist, und
mit einer der Pumpe (4) nachgeschalteten Eingangsdruckwaage (5),
wobei die Eingangsdruckwaage (5) im Druckmittelströmungspfad zwischen der Pumpe(4) und zumindest einem der zwei Verbraucher (10, 12) vorgesehen ist und dass der Power-Beyond-Anschluss (64) im Druckmittelströmungspfad zwischen der Pumpe (4) und der Eingangsdruckwaage (5) abzweigt, und
wobei die Eingangsdruckwaage (5) in Schließrichtung von der Kraft einer Feder (72) und in Öffnungsrichtung vom Druck an ihrem Eingang (P) beaufschlagt ist,
dadurch gekennzeichnet, dass die Eingangsdruckwaage (5) in Schließrichtung zusätzlich wahlweise vom größten Lastdruck oder von einem Druck oberhalb des größten Lastdrucks beaufschlagbar ist.Hydraulic control arrangement for controlling preferably at least two consumers (10, 12), which are supplied via a pump (4) with adjustable flow rate with pressure medium, in particular a mobile implement, and each associated with an adjustable metering orifice (20, 26),
with a power beyond port (64) to which at least one power beyond consumer (66) is connectable, and
with one of the pump (4) downstream inlet pressure compensator (5),
wherein the input pressure balance (5) is provided in the pressure medium flow path between the pump (4) and at least one of the two consumers (10, 12) and that the power beyond port (64) in the pressure medium flow path between the pump (4) and the inlet pressure balance ( 5) branches off, and
wherein the inlet pressure compensator (5) is acted upon in the closing direction by the force of a spring (72) and in the opening direction by the pressure at its inlet (P),
characterized in that the inlet pressure compensator (5) in the closing direction is additionally acted upon optionally either by the greatest load pressure or by a pressure above the maximum load pressure.
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DE102007039732 | 2007-08-22 | ||
DE102007045803A DE102007045803A1 (en) | 2007-08-22 | 2007-09-25 | Hydraulic control arrangement |
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EP2028376A2 true EP2028376A2 (en) | 2009-02-25 |
EP2028376A3 EP2028376A3 (en) | 2012-08-08 |
EP2028376B1 EP2028376B1 (en) | 2013-11-27 |
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Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2875268B1 (en) | 2012-07-19 | 2019-02-20 | HYDAC Systems & Services GmbH | Hydraulic system with pressure compensator in form of a valve, in particular continuously adjustable valve |
IT202100014123A1 (en) * | 2021-05-28 | 2022-11-28 | Walvoil Spa | HYDRAULIC DISTRIBUTOR WITH COMPENSATING DEVICE FOR DIRECTIONAL VALVES |
WO2023035365A1 (en) * | 2021-09-13 | 2023-03-16 | 烟台杰瑞石油装备技术有限公司 | Hydraulic system of wire saw machine and wire saw machine |
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DE102004048684A1 (en) * | 2004-10-06 | 2006-04-13 | Bosch Rexroth Ag | Hydraulic control arrangement |
DE102006008940A1 (en) * | 2006-02-23 | 2007-08-30 | Robert Bosch Gmbh | Hydraulic control arrangement for actuating multiple consumers, has input pressure balance provided in pressure medium flow path between pump and one of two consumers |
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2008
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US4977928A (en) * | 1990-05-07 | 1990-12-18 | Caterpillar Inc. | Load sensing hydraulic system |
DE102004048684A1 (en) * | 2004-10-06 | 2006-04-13 | Bosch Rexroth Ag | Hydraulic control arrangement |
DE102006008940A1 (en) * | 2006-02-23 | 2007-08-30 | Robert Bosch Gmbh | Hydraulic control arrangement for actuating multiple consumers, has input pressure balance provided in pressure medium flow path between pump and one of two consumers |
Cited By (4)
Publication number | Priority date | Publication date | Assignee | Title |
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EP2875268B1 (en) | 2012-07-19 | 2019-02-20 | HYDAC Systems & Services GmbH | Hydraulic system with pressure compensator in form of a valve, in particular continuously adjustable valve |
IT202100014123A1 (en) * | 2021-05-28 | 2022-11-28 | Walvoil Spa | HYDRAULIC DISTRIBUTOR WITH COMPENSATING DEVICE FOR DIRECTIONAL VALVES |
EP4095393A1 (en) * | 2021-05-28 | 2022-11-30 | Walvoil S.p.A. | Hydraulic distributor with compensator device for directional valves and hydraulic circuit comprising the same |
WO2023035365A1 (en) * | 2021-09-13 | 2023-03-16 | 烟台杰瑞石油装备技术有限公司 | Hydraulic system of wire saw machine and wire saw machine |
Also Published As
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EP2028376B1 (en) | 2013-11-27 |
EP2028376A3 (en) | 2012-08-08 |
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