EP1989450B1 - Hydraulic control arrangement - Google Patents

Hydraulic control arrangement Download PDF

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Publication number
EP1989450B1
EP1989450B1 EP07702809A EP07702809A EP1989450B1 EP 1989450 B1 EP1989450 B1 EP 1989450B1 EP 07702809 A EP07702809 A EP 07702809A EP 07702809 A EP07702809 A EP 07702809A EP 1989450 B1 EP1989450 B1 EP 1989450B1
Authority
EP
European Patent Office
Prior art keywords
pump
spring
control system
recited
control
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP07702809A
Other languages
German (de)
French (fr)
Other versions
EP1989450A1 (en
Inventor
Gerhard Keuper
Milan Djurovic
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1989450A1 publication Critical patent/EP1989450A1/en
Application granted granted Critical
Publication of EP1989450B1 publication Critical patent/EP1989450B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F15B2211/20553—Type of pump variable capacity with pilot circuit, e.g. for controlling a swash plate
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7142—Multiple output members, e.g. multiple hydraulic motors or cylinders the output members being arranged in multiple groups
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/78—Control of multiple output members
    • F15B2211/781—Control of multiple output members one or more output members having priority

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a pressure compensator for such a hydraulic control arrangement.
  • Hydraulic control arrangements are used in particular in mobile working equipment, for example in wheel loaders or tractors, in order to supply their consumers, for example the working hydraulics, the steering, traction drives and / or additional equipment with pressure medium.
  • DE 41 27 342 C2 Hydraulic control arrangements are known, which are designed as LS system.
  • the delivery rate of the pump is controlled so that in the pump line is applied by a certain pressure difference Ap over 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 flow to the load can be kept constant independent of the load depending on the position of the metering orifice.
  • an inlet pressure compensator can be provided, via which a connection to the tank can be opened.
  • These inlet pressure compensators are acted upon in the closing direction by a control pressure corresponding to the highest load pressure.
  • the pressure difference at which the inlet pressure compensator opens is usually slightly larger than the pressure difference ⁇ p set by the pump.
  • a so-called power beyond connection provided, which may have 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 DE 10 2004 048 684 is an example of a hydraulic control assembly provided with a power beyond port.
  • the pump connection of a power beyond pressure compensator is provided in a flow path between the pressure connection of the pump and the pump connections of the pressure compensators of the other consumers.
  • the Power Beyond Weigh Scale is connected in series with the Power Beyond consumer.
  • a disadvantage of this known solution is that it can lead to uncontrolled behavior of one or more consumers in the operation of the power beyond consumer, especially in an undersupply. Since the volume demand of the power beyond consumer is usually not known, the valve or pump control can not be adapted to the requirements of the power beyond consumer.
  • the invention has for its object to provide a hydraulic control arrangement, a suitable pressure compensator and a control method, which ensure a need-based pressure medium supply of all consumers when connecting at least one power beyond consumer to a power beyond connection.
  • a hydraulic control arrangement for controlling at least two consumers, which can be supplied with pressure medium via a pump with adjustable flow rate and to which an adjustable metering orifice is assigned in each case.
  • This hydraulic control arrangement is preferably used in mobile work equipment and has a power beyond connection for connecting a power beyond consumer and an input pressure compensator, which is connected downstream of the pump.
  • a connection to the tank can be opened and this is adjustable in response to a load pressure of the consumer or the at least one power beyond consumer.
  • the pump is preferably controlled as a function of the setting of the inlet pressure compensator, so that a demand-based supply of consumers takes place.
  • a control of the pump in response to the position of a control piston of the inlet pressure compensator, whereby an accurate control is inexpensive possible.
  • Actuation of the pump as a function of the volume flow at a connection of the inlet pressure compensator enables the direct selection of hydraulic parameters for targeted influencing of the pump control with good dynamic properties.
  • the pump control is also a signal for controlling the metering orifice at least one Usable by the consumer.
  • the position and / or residual flow control of the inlet pressure compensator only has to compensate for relatively small control deviations.
  • the largest of the load pressures act on the inlet pressure compensator in the closing direction, so that the load sensing system of the consumer can also be used by the power beyond consumer.
  • the inlet pressure compensator closes the inlet pressure compensator in a spring-biased position the connection to at least one consumer and the tank and controls this when adjusting in the opening direction, the connection to at least one of the two consumers and further adjustment in the opening direction, the connection to the tank. A sufficient supply of all consumers is ensured when the residual volume flow flows through the controlled inlet pressure compensator to the tank.
  • the inlet pressure compensator is preferably acted upon in the closing direction by the force of at least one spring and by the largest of the load pressures and in the opening direction by the pressure at the inlet of the inlet pressure compensator.
  • the inlet pressure compensator is provided in the closing direction and for switching the control pressure difference with a spring assembly or a progressive spring, whereby a path-dependent change in the spring force on a control piston of the inlet pressure compensator can be realized.
  • control arrangement is provided for raising the control pressure difference with a device for increasing the bias of the spring, this Magnification mechanically, hydraulically or electrically effected.
  • This adaptation of the control of the inlet pressure compensator to special design conditions is possible and the control of the control piston of the inlet pressure compensator can be realized over longer distances by the operator of a working device.
  • the pump is preferably an electrically controllable variable displacement pump or a variable speed fixed displacement pump, whereby the pump control is inexpensive to implement.
  • each metering orifice is preceded by an individual pressure balance, which can be acted upon in the opening direction by the respectively associated load pressure of the associated consumer and a pressure compensating spring and in the closing direction by the pressure at the outlet of the individual pressure compensator.
  • the result is a responsive load-sensing system.
  • the metering orifices are preferably formed by electrically, hydraulically or mechanically adjustable directional control valves.
  • a pressure compensator is further provided for one of the above control arrangements, wherein the control piston of this pressure compensator in the closing direction of a pressure compensator spring arrangement and in the opening direction of a load pressure can be acted upon.
  • This pressure compensating spring arrangement preferably has two springs which can be brought into engagement one after the other, which allow small installation spaces for the inlet pressure compensator.
  • control pressure difference is raised at the inlet pressure compensator with switching on of the power beyond consumer, so that in addition to the prioritization of the power beyond consumer at the same time an increase in the control pressure difference is ensured in order to allow safe operation of body equipment, even with increased pressure drops in the line system to the attachment.
  • Fig. 1 shows a hydraulic control arrangement of a mobile implement, such as a tractor.
  • This control arrangement can be formed, for example, by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working equipment, in the present case two double-acting cylinders 2,4 can be supplied with pressure medium supplied by a pump 6 and from the consumers 2, 4 to a tank T is returned.
  • the pump 6 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.
  • a pump line 12 which branches into two supply lines 14, 18, wherein the supply line 14 to the cylinder 2 and the supply line 18 is assigned to the cylinder 4.
  • an individual pressure compensator 16 is provided, wherein the direction of pressure fluid flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 24.
  • an individual pressure compensator 20 is provided, wherein the pressure medium flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 38.
  • a flow line 28 which is connected to a bottom-side cylinder chamber 32 of the cylinder 2 is, and a return line 30 which is connected to a piston rod side annular space 34 of the cylinder 2, connected.
  • a flow line 42 which is connected to a bottom-side cylinder chamber 46 of the cylinder, and a return line 44, which is connected to a piston rod-side annular space 48 of the cylinder 4 connected.
  • the control piston 26 of the directional control valve 24 and the control piston 40 of the directional control valve 38 are controlled via a pilot control device 54 or by manual operation.
  • the pilot control device 54 or by manual operation By actuating the pilot control device 54 or by manual operation, the control pressure difference is adjusted, so that the respective control piston 26 or 40 from the in Fig. 1 shown blocking position (0) in the indicated positions (a) or (b) is adjusted, in which either the cylinder chamber 32, 46 or the annular space 34, 48 is supplied with pressure medium, while the pressure medium is displaced from the respective other pressure medium space.
  • an inlet orifice plate in the directional control valves 24, 38 is opened via an inlet control edge, wherein the opening cross section of the respective inlet orifice determines the pressure medium volume flow to the cylinder 2, 4.
  • the pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T at the respective directional control valve 24, 38 and a line 50 connected to it.
  • the individual pressure compensators 16, 20 are each acted upon in the opening direction by the force of a pressure compensator spring 56, 58 and the load applied to the respective load 2, 4. In the closing direction acts on the pressure compensator slide of the individual pressure compensators 16, 20 respectively, the pressure in the supply line 14 and 18 between the output of the respective individual pressure compensator 16, 20th
  • a current regulator is formed, via which the pressure drop across the metering orifice can be kept constant independent of the load ,
  • a hydraulic control arrangement as described above Fig. 1 corresponds essentially to the structure of the hydraulic control arrangement of the DE 10 2004 048 684 , According to the present invention, an inlet pressure compensator 60 is provided in the pump line 12 between the pressure connection of the pump 6 and the branch point of the supply lines 14, 18, which is designed as a 3/3-way pressure balance.
  • a power beyond port 72 From the portion of the pump line 12, which is located between the pressure port of the pump 6 and the input port P of the input pressure compensator 60, branches off a power beyond port 72 from. Via this power beyond connection 72, it is possible to connect one or more additional hydraulic consumers 74 to the mobile working device, for example a loader wagon or a potato harvesting machine.
  • the power beyond consumer 74 is also connected via a tank channel 76 to the tank T in fluid communication.
  • the load pressure of the power beyond consumer 74 is tapped via a shuttle valve 80 a shuttle valve cascade of shuttle valve 78 and shuttle valve 80 of the LS line.
  • the control piston 62 of the inlet pressure compensator 60 is acted upon in the closing direction by the force of a spring 64 and the highest of the load pressures of the two consumers 2, 4 and the power beyond consumer 74.
  • the highest the load pressures of the consumer 2, 4 is tapped via a shuttle valve 78 and then fed to the shuttle valve 80, to which also the load pressure of the power beyond consumer 74 is applied.
  • the pressure in the pump line 12 is applied to the control piston 62 of the inlet pressure compensator.
  • the input port P of the inlet pressure compensator 60 is connected to the pump line 12 in pressure medium connection, the working port A of the inlet pressure compensator 60 opens into the inlet lines 14, 18.
  • the tank port T of the inlet pressure compensator 60 is connected via a tank channel 66 with the tank line 50 in fluid communication.
  • Fig. 1 illustrated blocking position (0) of the inlet pressure compensator 60 is no pressure medium connection between the pump port P, the working port A and the tank port T.
  • the voltage of the spring 64 acts on the control piston 62 of the inlet pressure compensator 60 in the direction of its blocking position (0).
  • the pump connection P and the working connection A are in pressure medium connection, while the pressure medium connection to the tank connection T is blocked.
  • the working position (b) following the working position (a) the pump connection P, the working connection A and the tank connection T are in pressure medium connection.
  • the position of the control piston 62 of the inlet pressure compensator 60 is detected by a position transducer 68 whose output signal is fed to a control unit 10 which controls the pump regulator 8.
  • the control unit 10 is a setpoint y1 EDWsoll and y2 EDWsoll supplied. Between these two setpoints becomes in response to the actuation of a power beyond control 81 switched. If the power beyond consumer 74 is either not connected to the power beyond port 72, or the power beyond consumer 74 is not acknowledged, the setpoint y1 is EDWsoll , while with the connected and confirmed power beyond consumer 74 the setpoint value y2 EDWsetpoint is used.
  • the power beyond driver 81 is initialized by a signal from an operator U PB .
  • the respective desired value is compared with the output signal y EDW of the displacement transducer 68 and fed to a controller 70 in the control unit 10.
  • the setpoint Y 1 EDWyoll is selected in such a way that when not connected or not operated power beyond consumer 74 with the setpoint y1 EDwsoll the position (a) of the spool 62 of the input pressure compensator 60 is regarded as a setpoint, while connected and actuated power beyond consumer 74 with the setpoint y2 EDWsoll the position (b) of the spool 62 of the input pressure compensator 60 is set.
  • the inlet pressure compensator 60 In the position (a) of the inlet pressure compensator 60 ensures that the pressure medium from the pump 6 via the input pressure compensator 60 the consumers 2, 4 is supplied loss, while upon actuation of the power beyond consumer 74, the input pressure compensator 60 in the position (b ) is brought, in the appropriate adjustment of the pump 6, a small residual volume flow through the tank port T and the tank passage 66 flows. In this way, the power beyond consumer 74 is prioritized, whereby even with a high volume flow demand of the power beyond consumer 74, both the consumers 2, 4 and, the power beyond consumers 74 are adequately supplied with pressure medium, if the Pump 6 is designed accordingly.
  • the 3 and 4 which relate to a second embodiment of the invention, differ from the first embodiment only in that in the second embodiment in the tank channel 66, a residual current sensor 100 is provided, through which the residual volume flow from the tank port T of the inlet pressure compensator 60 to the tank line 50 can be measured.
  • the control unit 110 differs from the control unit 10 of the first embodiment in that at a state indicated by actuation of the power beyond control 81, in which the power beyond consumer 74 is connected and actuated, as setpoint instead of the setpoint Y EDWsoll of First embodiment, now a setpoint Q Eowsoll , which represents the residual flow is used. For the actual value is switched in the control unit 110 with connected and actuated power beyond consumer 74 from the path y EDW to the residual volume flow Q EDW .
  • the advantage of the second exemplary embodiment consists in the direct measurement of the residual volume flow and the associated control of the pump regulator 8, which is more sensitive and precise compared to the first exemplary embodiment.
  • a hydraulic control arrangement according to the third embodiment which in the FIGS. 5 and 6 is different from the hydraulic control arrangement according to the first embodiment in that now instead of the pilot control device 54, which causes a hydraulic actuation of the control piston 26, 40 of the directional control valves 24, 38, or a manual operation in the third embodiment, a joystick 254 is used by the output electrical signals, the actuation of the control piston 26, 40th the directional control valves 24, 38 takes place.
  • the output signals of the joystick 254 are also supplied to the controller 210, so that it as in Fig. 6
  • the controller 270 additionally performs driving of the pump controller 8 based on the operation of the joystick 254.
  • a proportional pilot control of the pump 6 is possible, so that the control algorithm of the controller 270 for the position control of the inlet pressure compensator 60 only has to compensate for small deviations.
  • the dynamic transmission characteristics of the hydraulic control assembly are improved.
  • FIGS. 7 and 8 A hydraulic control device according to the fourth embodiment is shown in FIGS FIGS. 7 and 8 shown.
  • This hydraulic control arrangement differs from the hydraulic control arrangement of the second embodiment only in the use of the joystick 254, similar to the third embodiment. More precisely, in contrast to the second exemplary embodiment, the control unit 310 is now additionally supplied with the electrical output signals of the joystick 254, so that the control algorithm for the residual current control of the inlet pressure compensator 60 only has to compensate for small control deviations. As a result, similar to the third embodiment, the dynamic transmission characteristics of the hydraulic control device are improved.
  • FIGS. 9, 10 and 11 show a fifth, sixth and seventh embodiments of the present invention.
  • the bias of the spring 64 of the input pressure compensator 60 is changed mechanically (fifth embodiment), hydraulically (sixth embodiment) or electrically (seventh embodiment).
  • the other hydraulic structure in the fifth, sixth and seventh embodiments corresponds to that of the first embodiment.
  • the in Fig. 9 is shown, the end portion of the spring 64, which is opposite to the support of the spring 64 on the control piston 62 of the inlet pressure compensator 60, supported on an adjusting screw 490, the relative position in the direction of movement of the control piston 62 is variable.
  • adjustment screw 490 When the power beyond consumer 74 is neither connected nor actuated, the adjustment screw 490 is in its right position in FIG Fig. 9 , wherein the target position of the inlet pressure compensator is the position a. When power beyond consumer 74 is connected and actuated, adjustment screw 490 is in its left position in FIG Fig. 9 , wherein the position b of the control piston is the target position with increased bias.
  • a control piston 590 of an actuating cylinder 592 acts on the end remote from the control piston 62 end portion of the spring 64, a control piston 590 of an actuating cylinder 592, wherein a cylinder space of the actuating cylinder 592 is acted upon via a switching valve 594 with pressure to a movement of the control piston 62 in Fig. 10 to move to the left.
  • a spring 596 pushes the control piston of the switching valve 594 in a position in which the cylinder space of the actuating cylinder 592 is relieved to the tank, wherein the spring 64 has the lowest clamping.
  • the cylinder chamber of the actuating cylinder 592 is supplied with pressure medium so that there builds up a pressure through which the actuating piston 590 in Fig. 10 is moved to the left to additionally tension the spring 64.
  • the actuating piston 590 In the rest position of the switching valve 594 and thus at unloaded cylinder space of the actuating cylinder 592 is the actuating piston 590 in its right position, wherein the position a of the input pressure compensator 60 is the target value.
  • the adjusting piston 590 When pressurizing the cylinder space of the adjusting cylinder 592 via the switching valve 594, the adjusting piston 590 is moved to its left position in FIG Fig. 10 brought, wherein the position b of the input pressure compensator 60 is the desired position.
  • an electric servomotor 690 is provided on which a threaded shaft 692 is provided.
  • the opposite to the control piston 62 of the input pressure compensator 60 end portion of the spring 64 is changeable in its position by actuation of the servomotor 690.
  • the position b of the inlet pressure compensator 60 is preset as the target position when the threaded shaft 692 is unscrewed to the servomotor 690.
  • the position a of the control piston 62 of the inlet pressure compensator 60 is predetermined.
  • the fifth, sixth and seventh embodiments have in common that with the use of only one spring an increase in the control pressure difference by increasing the spring preload can be realized.
  • Fig. 12, 13 and 14 show an eighth embodiment of the present invention, in which by using a spring package, a self-increasing the control pressure difference at the inlet pressure compensator 60 is carried out when adjusting the control position from the position a to the position b.
  • a self-increasing the control pressure difference at the inlet pressure compensator 60 is carried out when adjusting the control position from the position a to the position b.
  • an additional spring 764 is activated in addition to the spring 64 in the eighth embodiment, starting from a predetermined displacement path of the control piston 62.
  • Fig. 13 shows by way of example a structural design for the connection of the additional spring 764.
  • the end portion of the control piston 62 of the inlet pressure compensator 60 opens and is held in a cylinder bore by means of the retaining ring 702.
  • the spring 64 is likewise supported on this retaining ring 702, whose opposite end section is supported on the spring housing 700 via a spring mount 704.
  • a support rod 706 is provided which is fixed in the spring housing 700, for example via retaining rings.
  • a spring plate 708 is slidably received, on which an end portion of the auxiliary spring 764 is supported.
  • the opposite end portion of the auxiliary spring 764 is supported on the spring holder 704.
  • the control piston 62 After covering a predetermined path, the control piston 62 runs on the spring plate 708. Upon further movement of the control piston 62 to the right in Fig. 13 the spring plate 708 is entrained by the control piston 62, wherein a compression of the auxiliary spring 764 on the piston rod 106 is effected so that both springs 64, 764 are effective. When the control piston 62 runs onto the support rod 706, further movement of the control piston 62 is in Fig. 13 prevented to the right.
  • a progressive spring can also be used in one variant.
  • Fig. 14 represents an exemplary characteristic is input pressure compensator 60 with pressure increase.
  • the pressure difference of the inlet pressure compensator over the valve position or the control position is plotted. From this characteristic it can be seen that, starting from a certain valve position / control position, the pressure difference increases from the value ⁇ p EDW1 to the value ⁇ p EDW2 .
  • a power beyond consumer 74 can be prioritized to maintain the function.
  • an electronically, hydraulically or mechanically triggered increase in the pressure level takes place only when the power beyond consumer is activated.
  • needs-based and energy-saving supply of all active consumers 2, 4, 74 is possible.
  • the present invention is not limited to the fact that the consumers 2, 4 are connected in parallel, but the inlet pressure compensator can also be connected upstream of only one of the consumers 2, 4. In this case, the other consumer is directly connected to the pressure port of the pump and thus hydraulically prioritized.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

The hydraulic control arrangement has a input pressure balance (60), which is provided in a pressure medium flow path between a pump (6) and one of the two consumers (2,4). A power beyond connection (72) in the pressure medium flow path branches off between the pump and the input pressure balance. The pump is controllable against the adjustment of the input pressure balance. The pump is controllable against the position of a control piston (62) of the input pressure balance. Independent claims are also included for the following: (1) a pressure balance for control arrangement (2) a control method for control arrangement.

Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur Ansteuerung mehrerer Verbraucher gemäß dem Oberbegriff des Patentanspruchs 1 sowie eine Druckwaage für eine derartige hydraulische Steueranordnung.The invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a pressure compensator for such a hydraulic control arrangement.

Eine solche Steueranordnung ist in EP1245834 offenbart.Such a control arrangement is in EP1245834 disclosed.

Erfindungsgemäße 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 DE 41 27 342 C2 sind hydraulische Steueranordnungen bekannt, die als LS-System ausgeführt sind. Bei derartigen LS-Systemen wird die Fördermenge der Pumpe so geregelt, dass in der Pumpenleitung ein um eine bestimmte Druckdifferenz Δp über dem höchsten Lastdruck der Verbraucher liegender Pumpendruck anliegt. Bei den bekannten Systemen sind jedem Verbraucher eine einstellbare Zumessblende und eine Individualdruckwaage zugeordnet, über die der Druckmittelvolumenstrom zum Verbraucher in Abhängigkeit von der Stellung der Zumessblende lastunabhängig konstant gehalten werden kann. Bei diesen LS-Systemen kann stromabwärts der Pumpe eine Eingangsdruckwaage vorgesehen werden, über die eine Verbindung zum Tank aufsteuerbar ist. Diese Eingangsdruckwaagen sind in Schließrichtung von einem dem höchsten Lastdruck entsprechenden Steuerdruck beaufschlagt. Die Druckdifferenz, bei der die Eingangsdruckwaage öffnet, ist in der Regel geringfügig größer als die über die Pumpe eingestellte Druckdifferenz Δp.Hydraulic control arrangements according to the invention are used in particular in mobile working equipment, for example in wheel loaders or tractors, in order to supply their consumers, for example the working hydraulics, the steering, traction drives and / or additional equipment with pressure medium. From the DE 41 27 342 C2 Hydraulic control arrangements are known, which are designed as LS system. In such LS systems, the delivery rate of the pump is controlled so that in the pump line is applied by a certain pressure difference Ap over the highest load pressure of the consumer lying pump pressure. In the known systems each consumer an adjustable metering orifice and an individual pressure compensator are assigned, via which the pressure medium flow to the load can be kept constant independent of the load depending on the position of the metering orifice. In these LS systems downstream of the pump, an inlet pressure compensator can be provided, via which a connection to the tank can be opened. These inlet pressure compensators are acted upon in the closing direction by a control pressure corresponding to the highest load pressure. The pressure difference at which the inlet pressure compensator opens is usually slightly larger than the pressure difference Δp set by the pump.

Zum Anschluss von Anbaugeräten oder Zusatzgeräten ohne eigene Druckmittelversorgung ist ein so genannter Power-Beyond-Anschluss vorgesehen, der eine Druckleitung, eine Rücklaufleitung und eine LS-Leitung aufweisen kann. Dieser Power-Beyond-Anschluss macht das Load-Sensing-System des Arbeitsgerätes auch für das Anbaugerät nutzbar.To connect attachments or attachments without their own pressure medium supply is a so-called power beyond connection provided, which may have 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.

Die DE 10 2004 048 684 ist ein Beispiel für eine mit einem Power-Beyond-Anschluss versehene hydraulische Steueranordnung. Bei dieser Steueranordnung ist der Pumpenanschluss einer Power-Beyond-Druckwaage in einem Strömungspfad zwischen dem Druckanschluss der Pumpe und den Pumpenanschlüssen der Druckwaagen der anderen Verbraucher vorgesehen. Die Power-Beyond-Druckwaage ist mit dem Power-Beyond-Verbraucher in Reihe geschaltet. Ein Nachteil dieser bekannten Lösung ist, dass es bei der Betätigung des Power-Beyond-Verbrauchers zu unkontrolliertem Verhalten von einem oder von mehreren Verbrauchern kommen kann, insbesondere bei einer Unterversorgung. Da der Volumenstrombedarf des Power-Beyond-Verbrauchers in der Regel nicht bekannt ist, kann die Ventil- bzw. Pumpensteuerung nicht an die Anforderungen des Power-Beyond-Verbrauchers angepasst werden.The DE 10 2004 048 684 is an example of a hydraulic control assembly provided with a power beyond port. In this control arrangement, the pump connection of a power beyond pressure compensator is provided in a flow path between the pressure connection of the pump and the pump connections of the pressure compensators of the other consumers. The Power Beyond Weigh Scale is connected in series with the Power Beyond consumer. A disadvantage of this known solution is that it can lead to uncontrolled behavior of one or more consumers in the operation of the power beyond consumer, especially in an undersupply. Since the volume demand of the power beyond consumer is usually not known, the valve or pump control can not be adapted to the requirements of the power beyond consumer.

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung, eine dafür geeignete Druckwaage sowie ein Steuerverfahren zu schaffen, die bei Anschluss zumindest eines Power-Beyond-Verbrauchers an einen Power-Beyond-Anschluss eine bedarfsgerechte Druckmittelversorgung aller Verbraucher gewährleisten.In contrast, the invention has for its object to provide a hydraulic control arrangement, a suitable pressure compensator and a control method, which ensure a need-based pressure medium supply of all consumers when connecting at least one power beyond consumer to a power beyond connection.

Die Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruchs 1 und eine Druckwaage mit den Merkmalen des Patentanspruchs 15 gelöst.The object is achieved by a hydraulic control arrangement having the features of patent claim 1 and a pressure compensator having the features of patent claim 15.

Erfindungsgemäß wird eine hydraulische Steueranordnung zur Ansteuerung von zumindest zwei Verbrauchern vorgesehen, die über eine Pumpe mit einstellbarer Fördermenge mit Druckmittel versorgbar sind und denen jeweils eine verstellbare Zumessblende zugeordnet ist. Diese hydraulische Steueranordnung wird bevorzugt bei mobilen Arbeitsgeräten eingesetzt und hat einen Power-Beyond-Anschluss zum Anschließen eines Power-Beyond-Verbrauchers sowie eine Eingangsdruckwaage, die der Pumpe nachgeschaltet ist. Über diese Eingangsdruckwaage ist eine Verbindung zum Tank aufsteuerbar und diese ist in Abhängigkeit von einem Lastdruck der Verbraucher oder des zumindest einen Power-Beyond-Verbrauchers einstellbar. Durch die Anordnung der Eingangsdruckwaage im Druckmittelströmungspfad zwischen der Pumpe und zumindest einem der Verbraucher und aufgrund des Abzweigens des Power-Beyond-Anschlusses von einem Druckmittelströmungspfad zwischen Pumpe und Eingangsdruckwaage ist eine priorisierte Versorgung des Power-Beyond-Verbrauchers gewährleistet.According to the invention, a hydraulic control arrangement is provided for controlling at least two consumers, which can be supplied with pressure medium via a pump with adjustable flow rate and to which an adjustable metering orifice is assigned in each case. This hydraulic control arrangement is preferably used in mobile work equipment and has a power beyond connection for connecting a power beyond consumer and an input pressure compensator, which is connected downstream of the pump. About this inlet pressure compensator, a connection to the tank can be opened and this is adjustable in response to a load pressure of the consumer or the at least one power beyond consumer. The arrangement of the inlet pressure compensator in the pressure medium flow path between the pump and at least one of the consumers and due to the branching of the power beyond connection of a pressure medium flow path between the pump and the inlet pressure compensator, a prioritized supply of the power beyond consumer is ensured.

Die Pumpe ist bevorzugt in Abhängigkeit von der Einstellung der Eingangsdruckwaage ansteuerbar, so dass eine bedarfsgerechte Versorgung der Verbraucher erfolgt. Insbesondere erfolgt eine Ansteuerung der Pumpe in Abhängigkeit von der Position eines Steuerkolbens der Eingangsdruckwaage, wodurch eine genaue Regelung kostengünstig möglich ist.The pump is preferably controlled as a function of the setting of the inlet pressure compensator, so that a demand-based supply of consumers takes place. In particular, a control of the pump in response to the position of a control piston of the inlet pressure compensator, whereby an accurate control is inexpensive possible.

Eine Ansteuerung der Pumpe in Abhängigkeit vom Volumenstrom an einem Anschluss der Eingangsdruckwaage ermöglicht das direkte Abgreifen von hydraulischen Parametern zur gezielten Beeinflussung der Pumpenregelung mit guten dynamischen Eigenschaften.Actuation of the pump as a function of the volume flow at a connection of the inlet pressure compensator enables the direct selection of hydraulic parameters for targeted influencing of the pump control with good dynamic properties.

Als Parameter für die Pumpen-Ansteuerung ist auch ein Signal zur Ansteuerung der Zumessblende zumindest eines Verbrauchers einsetzbar. Damit muss die Lage- und/oder Reststromregelung der Eingangsdruckwaage nur noch relativ geringe Regelabweichungen ausgleichen.As a parameter for the pump control is also a signal for controlling the metering orifice at least one Usable by the consumer. Thus, the position and / or residual flow control of the inlet pressure compensator only has to compensate for relatively small control deviations.

Es wird bevorzugt, dass der größte der Lastdrücke die Eingangsdruckwaage in Schließrichtung beaufschlagt, so dass das Load-Sensing-System der Verbraucher auch für den Power-Beyond-Verbraucher nutzbar ist.It is preferred that the largest of the load pressures act on the inlet pressure compensator in the closing direction, so that the load sensing system of the consumer can also be used by the power beyond consumer.

Entsprechend einer vorteilhaften Weiterbildung der Erfindung sperrt die Eingangsdruckwaage in einer federvorgespannten Grundstellung die Verbindung zu zumindest einem Verbraucher und dem Tank ab und steuert diese bei Verstellen in Öffnungsrichtung die Verbindung zu zumindest einem der zwei Verbraucher und bei weiterem Verstellen in Öffnungsrichtung die Verbindung zum Tank auf. Eine hinreichende Versorgung aller Verbraucher ist dann sichergestellt, wenn der Restvolumenstrom über die aufgesteuerte Eingangsdruckwaage zum Tank abströmt.According to an advantageous embodiment of the invention closes the inlet pressure compensator in a spring-biased position the connection to at least one consumer and the tank and controls this when adjusting in the opening direction, the connection to at least one of the two consumers and further adjustment in the opening direction, the connection to the tank. A sufficient supply of all consumers is ensured when the residual volume flow flows through the controlled inlet pressure compensator to the tank.

Die Eingangsdruckwaage ist vorzugsweise in Schließrichtung von der Kraft zumindest einer Feder und vom größten der Lastdrücke und in Öffnungsrichtung vom Druck am Eingang der Eingangsdruckwaage beaufschlagt.The inlet pressure compensator is preferably acted upon in the closing direction by the force of at least one spring and by the largest of the load pressures and in the opening direction by the pressure at the inlet of the inlet pressure compensator.

Bei einer bevorzugten Steueranordnung ist die Eingangsdruckwaage in Schließrichtung und zum Umschalten der Regeldruckdifferenz mit einem Federpaket oder einer Progressivfeder versehen, wodurch eine wegabhängige Änderung der Federkraft auf einen Steuerkolben der Eingangsdruckwaage realisierbar ist.In a preferred control arrangement, the inlet pressure compensator is provided in the closing direction and for switching the control pressure difference with a spring assembly or a progressive spring, whereby a path-dependent change in the spring force on a control piston of the inlet pressure compensator can be realized.

Entsprechend einer weiteren bevorzugten Weiterbildung der vorliegenden Erfindung ist die Steueranordnung zum Anheben der Regeldruckdifferenz mit einer Einrichtung zur Vergrößerung der Vorspannung der Feder versehen, die diese Vergrößerung mechanisch, hydraulisch oder elektrisch bewirkt. Damit ist eine Anpassung der Ansteuerung der Eingangsdruckwaage an spezielle konstruktive Gegebenheiten möglich und die Ansteuerung des Steuerkolbens der Eingangsdruckwaage lässt sich auch über größere Entfernungen durch die Bedienperson eines Arbeitsgerätes realisieren.According to a further preferred embodiment of the present invention, the control arrangement is provided for raising the control pressure difference with a device for increasing the bias of the spring, this Magnification mechanically, hydraulically or electrically effected. This adaptation of the control of the inlet pressure compensator to special design conditions is possible and the control of the control piston of the inlet pressure compensator can be realized over longer distances by the operator of a working device.

Die Pumpe ist bevorzugt eine elektrisch steuerbare Verstellpumpe oder eine drehzahlgeregelte Konstantpumpe, wodurch die Pumpenregelung kostengünstig umsetzbar ist.The pump is preferably an electrically controllable variable displacement pump or a variable speed fixed displacement pump, whereby the pump control is inexpensive to implement.

Es ist besonders vorteilhaft, wenn jeder Zumessblende eine Individualdruckwaage vorgeschaltet ist, die in Öffnungsrichtung vom jeweils zugehörigen Lastdruck des zugeordneten Verbrauchers und einer Druckwaagefeder und in Schließrichtung vom Druck am Ausgang der Individualdruckwaage beaufschlagbar ist. Das Ergebnis ist ein schnell ansprechendes Load-Sensing-System.It is particularly advantageous if each metering orifice is preceded by an individual pressure balance, which can be acted upon in the opening direction by the respectively associated load pressure of the associated consumer and a pressure compensating spring and in the closing direction by the pressure at the outlet of the individual pressure compensator. The result is a responsive load-sensing system.

Die Zumessblenden werden bevorzugt durch elektrisch, hydraulisch oder mechanisch verstellbare Wegeventile gebildet.The metering orifices are preferably formed by electrically, hydraulically or mechanically adjustable directional control valves.

Erfindungsgemäß ist ferner eine Druckwaage für eine der vorstehenden Steueranordnungen vorgesehen, wobei der Steuerkolben dieser Druckwaage in Schließrichtung von einer Druckwaagenfederanordnung und in Öffnungsrichtung von einem Lastdruck beaufschlagbar ist. Diese Druckwaagefederanordnung weist vorzugsweise zwei nacheinander in Eingriff bringbare Federn auf, die geringe Einbauräume für die Eingangsdruckwaage ermöglichen.According to the invention, a pressure compensator is further provided for one of the above control arrangements, wherein the control piston of this pressure compensator in the closing direction of a pressure compensator spring arrangement and in the opening direction of a load pressure can be acted upon. This pressure compensating spring arrangement preferably has two springs which can be brought into engagement one after the other, which allow small installation spaces for the inlet pressure compensator.

Entsprechend einem erfindungsgemäßen Steuerverfahren wird die Regeldruckdifferenz an der Eingangsdruckwaage mit Zuschalten des Power-Beyond-Verbrauchers angehoben, so dass neben der Priorisierung des Power-Beyond-Verbrauchers zugleich eine Anhebung der Regeldruckdifferenz gewährleistet ist, um damit einen sicheren Betrieb von Aufbaugeräten zu ermöglichen, auch bei erhöhten Druckabfällen im Leitungssystem zum Anbaugerät.According to a control method according to the invention, the control pressure difference is raised at the inlet pressure compensator with switching on of the power beyond consumer, so that in addition to the prioritization of the power beyond consumer at the same time an increase in the control pressure difference is ensured in order to allow safe operation of body equipment, even with increased pressure drops in the line system to the attachment.

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 und 2 eine hydraulische Steueranordnung entsprechend dem ersten Ausführungsbeispiel,
  • die Fig. 3 und 4 eine hydraulische Steueranordnung entsprechend einem zweiten Ausführungsbeispiel der Erfindung,
  • die Fig. 5 und 6 eine hydraulische Steuerungsanordnung entsprechend einem dritten Ausführungsbeispiel der vorliegenden Erfindung,
  • die Fig. 7 und 8 eine hydraulische Steuerungsanordnung entsprechend einem vierten Ausführungsbeispiel der Erfindung,
  • die Fig. 9, 10 und 11 ein fünftes, sechstes und siebtes Ausführungsbeispiel in Bezug auf eine Umschaltung der Regeldruckdifferenz der Eingangsdruckwaage und
  • die Fig. 12, 13 und 14 ein achtes Ausführungsbeispiel für die Umschaltung der Regeldruckdifferenz der Eingangsdruckwaage entsprechend der vorliegenden Erfindung, wobei Fig. 14 eine exemplarische Kennlinie der Eingangsdruckwaage zur Darstellung der Druckanhebung zeigt.
In the following preferred embodiments of the invention will be explained in more detail with reference to schematic drawings. Show it:
  • The Fig. 1 and 2 a hydraulic control arrangement according to the first embodiment,
  • the 3 and 4 a hydraulic control arrangement according to a second embodiment of the invention,
  • the FIGS. 5 and 6 a hydraulic control arrangement according to a third embodiment of the present invention,
  • the FIGS. 7 and 8 a hydraulic control arrangement according to a fourth embodiment of the invention,
  • the FIGS. 9, 10 and 11 a fifth, sixth and seventh embodiment with respect to a switching of the control pressure difference of the inlet pressure compensator and
  • the Fig. 12, 13 and 14 an eighth embodiment for switching the control pressure difference of the inlet pressure compensator according to the present invention, wherein Fig. 14 an exemplary characteristic of the inlet pressure compensator for showing the pressure increase shows.

Fig. 1 zeigt eine hydraulische Steueranordnung eines mobilen Arbeitsgerätes, beispielsweise eines Ackerschleppers. Diese Steueranordnung kann beispielsweise durch ein Mobilsteuerblock gebildet sein, über den die hydraulischen Verbraucher der Arbeitshydraulik des Arbeitsgerätes, im vorliegenden Fall zwei doppeltwirkende Zylinder 2,4 mit Druckmittel versorgbar sind, das von einer Pumpe 6 geliefert und von den Verbrauchern 2, 4 zu einem Tank T zurückgeführt wird. Die Pumpe 6 ist beim dargestellten Ausführungsbeispiel als elektrisch ansteuerbare Verstellpumpe ausgebildet, deren Schwenkwinkel über ein Pumpenzegler 8 verstellbar ist. An Stelle einer elektrisch ansteuerbaren Verstellpumpe kann auch eine drehzahlgeregelte Konstantpumpe oder eine andere über einen Pumpenregler ansteuerbare Pumpe eingesetzt werden. Fig. 1 shows a hydraulic control arrangement of a mobile implement, such as a tractor. This control arrangement can be formed, for example, by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working equipment, in the present case two double-acting cylinders 2,4 can be supplied with pressure medium supplied by a pump 6 and from the consumers 2, 4 to a tank T is returned. The pump 6 is formed in the illustrated embodiment as an electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8. Instead of an electrically controllable variable displacement pump, a variable speed fixed displacement pump or another pump controllable via a pump regulator can also be used.

Das von der Pumpe 6 aus dem Tank T angesaugte Druckmittel wird in eine Pumpenleitung 12 gefördert, die in zwei Zulaufleitungen 14, 18 verzweigt, wobei die Zulaufleitung 14 dem Zylinder 2 und die Zulaufleitung 18 dem Zylinder 4 zugeordnet ist. In der zu einem stetig verstellbaren Wegeventil 24 führenden Zulaufleitung 14 ist eine Individualdruckwaage 16 vorgesehen, wobei durch das Wegeventil 24 die Druckmittelströmungsrichtung zum Verbraucher bzw. vom Verbraucher und der Druckmittelvolumenstrom einstellbar sind. In der zu einem stetig verstellbaren Wegeventil 38 führenden Zulaufleitung 18 ist eine Individualdruckwaage 20 vorgesehen, wobei durch das Wegeventil 38 die Druckmittelströmungsrichtung zum Verbraucher bzw. vom Verbraucher und der Druckmittelvolumenstrom einstellbar sind. An die Arbeitsanschlüsse A, B des Wegeventils 24 sind eine Vorlaufleitung 28, die mit einem bodenseitigen Zylinderraum 32 des Zylinders 2 verbunden ist, und eine Rücklaufleitung 30, die mit einem kolbenstangenseitigen Ringraum 34 des Zylinders 2 verbunden ist, angeschlossen. An die Arbeitsanschlüsse A, B des Wegeventils 38 sind eine Vorlaufleitung 42, die mit einem bodenseitigen Zylinderraum 46 des Zylinders verbunden ist, und eine Rücklaufleitung 44, die mit einem kolbenstangenseitigen Ringraum 48 des Zylinders 4 verbunden ist, angeschlossen.The sucked by the pump 6 from the tank T pressure fluid is conveyed into a pump line 12, which branches into two supply lines 14, 18, wherein the supply line 14 to the cylinder 2 and the supply line 18 is assigned to the cylinder 4. In the leading to a continuously adjustable directional control valve 24 supply line 14, an individual pressure compensator 16 is provided, wherein the direction of pressure fluid flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 24. In the leading to a continuously adjustable directional control valve 38 supply line 18, an individual pressure compensator 20 is provided, wherein the pressure medium flow direction to the consumer or from the consumer and the pressure medium volume flow are adjustable by the directional control valve 38. To the working ports A, B of the directional control valve 24 are a flow line 28 which is connected to a bottom-side cylinder chamber 32 of the cylinder 2 is, and a return line 30 which is connected to a piston rod side annular space 34 of the cylinder 2, connected. To the working ports A, B of the directional control valve 38, a flow line 42 which is connected to a bottom-side cylinder chamber 46 of the cylinder, and a return line 44, which is connected to a piston rod-side annular space 48 of the cylinder 4 connected.

Der Steuerkolben 26 des Wegeventils 24 und der Steuerkolben 40 des Wegeventils 38 werden über ein Vorsteuergerät 54 oder über Handbetätigung angesteuert. Durch Betätigung des Vorsteuergerätes 54 oder durch Handbetätigung wird die Steuerdruckdifferenz eingestellt, so dass der jeweilige Steuerkolben 26 bzw. 40 aus der in Fig. 1 dargestellten Sperrposition (0) in die angedeuteten Positionen (a) oder (b) verstellt wird, in denen entweder der Zylinderraum 32, 46 oder der Ringraum 34, 48 mit Druckmittel versorgt wird, während aus dem jeweils anderen Druckmittelraum das Druckmittel verdrängt wird. Dabei wird über eine Zulaufsteuerkante eine Zulaufmessblende in den Wegeventilen 24, 38 aufgesteuert, wobei der Öffnungsquerschnitt der jeweiligen Zulaufmessblende den Druckmittelvolumenstrom zum Zylinder 2, 4 bestimmt. Das vom Zylinder 2, 4 zurückströmende Druckmittel wird über einen Tankanschluss T am jeweiligen Wegeventil 24, 38 und eine an diese angeschlossene Leitung 50 zum Tank T zurückgeführt.The control piston 26 of the directional control valve 24 and the control piston 40 of the directional control valve 38 are controlled via a pilot control device 54 or by manual operation. By actuating the pilot control device 54 or by manual operation, the control pressure difference is adjusted, so that the respective control piston 26 or 40 from the in Fig. 1 shown blocking position (0) in the indicated positions (a) or (b) is adjusted, in which either the cylinder chamber 32, 46 or the annular space 34, 48 is supplied with pressure medium, while the pressure medium is displaced from the respective other pressure medium space. In this case, an inlet orifice plate in the directional control valves 24, 38 is opened via an inlet control edge, wherein the opening cross section of the respective inlet orifice determines the pressure medium volume flow to the cylinder 2, 4. The pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T at the respective directional control valve 24, 38 and a line 50 connected to it.

Die Individualdruckwaagen 16, 20 werden jeweils in Öffnungsrichtung von der Kraft einer Druckwaagenfeder 56, 58 sowie dem am jeweiligen Verbraucher 2, 4 anliegenden Lastdruck beaufschlagt. In Schließrichtung wirkt auf die Druckwaagenschieber der Individualdruckwaagen 16, 20 jeweils der Druck in der Zulaufleitung 14 bzw. 18 zwischen dem Ausgang der jeweiligen Individualdruckwaage 16, 20 und dem Eingang des nachgeschalteten Wegeventils 24, 38. Durch die jeweilige Individualdruckwaage 16, 20 und die zugeordnete Zumessblende, die durch das jeweilige Wegeventil 38, 24 ausgebildet ist, wird ein Stromregler gebildet, über den der Druckabfall über der Messblende lastunabhängig konstant gehalten werden kann.The individual pressure compensators 16, 20 are each acted upon in the opening direction by the force of a pressure compensator spring 56, 58 and the load applied to the respective load 2, 4. In the closing direction acts on the pressure compensator slide of the individual pressure compensators 16, 20 respectively, the pressure in the supply line 14 and 18 between the output of the respective individual pressure compensator 16, 20th By the respective individual pressure compensator 16, 20 and the associated metering orifice, which is formed by the respective directional valve 38, 24, a current regulator is formed, via which the pressure drop across the metering orifice can be kept constant independent of the load ,

Eine hydraulische Steueranordnung entsprechend der vorstehenden Beschreibung zu Fig. 1 entspricht im Wesentlichen dem Aufbau der hydraulischen Steueranordnung aus der DE 10 2004 048 684 . Entsprechend der vorliegenden Erfindung ist in der Pumpenleitung 12 zwischen dem Druckanschluss der Pumpe 6 und dem Verzweigungspunkt der Zulaufleitungen 14, 18 eine Eingangsdruckwaage 60 vorgesehen, die als 3/3-Wegedruckwaage ausgeführt ist.A hydraulic control arrangement as described above Fig. 1 corresponds essentially to the structure of the hydraulic control arrangement of the DE 10 2004 048 684 , According to the present invention, an inlet pressure compensator 60 is provided in the pump line 12 between the pressure connection of the pump 6 and the branch point of the supply lines 14, 18, which is designed as a 3/3-way pressure balance.

Von dem Abschnitt der Pumpenleitung 12, der sich zwischen dem Druckanschluss der Pumpe 6 und dem Eingangsanschluss P der Eingangsdruckwaage 60 befindet, zweigt ein Power-Beyond-Anschluss 72 ab. Über diesen Power-Beyond-Anschluss 72 ist es möglich, einen oder mehrere zusätzliche hydraulische Verbraucher 74 an das mobile Arbeitsgerät, beispielsweise einen Ladewagen oder eine Kartoffelvollerntemaschine, anzuschließen.From the portion of the pump line 12, which is located between the pressure port of the pump 6 and the input port P of the input pressure compensator 60, branches off a power beyond port 72 from. Via this power beyond connection 72, it is possible to connect one or more additional hydraulic consumers 74 to the mobile working device, for example a loader wagon or a potato harvesting machine.

Der Power-Beyond-Verbraucher 74 steht ferner über einen Tankkanal 76 mit dem Tank T in Druckmittelverbindung. Der Lastdruck des Power-Beyond-Verbrauchers 74 wird über ein Wechselventil 80 einer Wechselventilkaskade aus Wechselventil 78 und Wechselventil 80 der LS-Leitung abgegriffen.The power beyond consumer 74 is also connected via a tank channel 76 to the tank T in fluid communication. The load pressure of the power beyond consumer 74 is tapped via a shuttle valve 80 a shuttle valve cascade of shuttle valve 78 and shuttle valve 80 of the LS line.

Der Steuerkolben 62 der Eingangsdruckwaage 60 wird in Schließrichtung von der Kraft einer Feder 64 sowie den höchsten der Lastdrücke der beiden Verbraucher 2, 4 und des Power-Beyond-Verbrauchers 74 beaufschlagt. Der höchste der Lastdrücke der Verbraucher 2, 4 wird über ein Wechselventil 78 abgegriffen und anschließend dem Wechselventil 80 zugeführt , an dem ebenfalls der Lastdruck des Power-Beyond-Verbrauchers 74 anliegt.The control piston 62 of the inlet pressure compensator 60 is acted upon in the closing direction by the force of a spring 64 and the highest of the load pressures of the two consumers 2, 4 and the power beyond consumer 74. The highest the load pressures of the consumer 2, 4 is tapped via a shuttle valve 78 and then fed to the shuttle valve 80, to which also the load pressure of the power beyond consumer 74 is applied.

In Öffnungsrichtung liegt an dem Steuerkolben 62 der Eingangsdruckwaage der Druck in der Pumpenleitung 12 an. Der Eingangsanschluss P der Eingangsdruckwaage 60 steht mit der Pumpenleitung 12 in Druckmittelverbindung, der Arbeitsanschluss A der Eingangsdruckwaage 60 mündet in die Zulaufleitungen 14, 18. Der Tankanschluss T der Eingangsdruckwaage 60 steht über einen Tankkanal 66 mit der Tankleitung 50 in Druckmittelverbindung.In the opening direction, the pressure in the pump line 12 is applied to the control piston 62 of the inlet pressure compensator. The input port P of the inlet pressure compensator 60 is connected to the pump line 12 in pressure medium connection, the working port A of the inlet pressure compensator 60 opens into the inlet lines 14, 18. The tank port T of the inlet pressure compensator 60 is connected via a tank channel 66 with the tank line 50 in fluid communication.

In der Fig. 1 dargestellten Sperrposition (0) der Eingangsdruckwaage 60 besteht keine Druckmittelverbindung zwischen dem Pumpenanschluss P, dem Arbeitsanschluss A und dem Tankanschluss T. Die Spannung der Feder 64 beaufschlagt den Steuerkolben 62 der Eingangsdruckwaage 60 in Richtung seiner Sperrposition (0). In der Arbeitsposition (a) stehen der Pumpenanschluss P und der Arbeitsanschluss A in Druckmittelverbindung, während die Druckmittelverbindung zum Tankanschluss T gesperrt ist. In der sich an die Arbeitsposition (a) anschließende Arbeitsposition (b) stehen der Pumpenanschluss P, der Arbeitsanschluss A und der Tankanschluss T in Druckmittelverbindung.In the Fig. 1 illustrated blocking position (0) of the inlet pressure compensator 60 is no pressure medium connection between the pump port P, the working port A and the tank port T. The voltage of the spring 64 acts on the control piston 62 of the inlet pressure compensator 60 in the direction of its blocking position (0). In the working position (a), the pump connection P and the working connection A are in pressure medium connection, while the pressure medium connection to the tank connection T is blocked. In the working position (b) following the working position (a), the pump connection P, the working connection A and the tank connection T are in pressure medium connection.

Die Stellung des Steuerkolbens 62 der Eingangsdruckwaage 60 wird über einen Wegaufnehmer 68 erfasst, dessen Ausgangssignal einem Steuergerät 10 zugeleitet wird, der den Pumpenregler 8 steuert.The position of the control piston 62 of the inlet pressure compensator 60 is detected by a position transducer 68 whose output signal is fed to a control unit 10 which controls the pump regulator 8.

Unter Bezugnahme auf Fig. 2 wird die Betätigung des Pumpenreglers 8 über das Steuergerät 10 näher beschrieben. Dem Steuergerät 10 wird ein Sollwert y1EDWsoll und y2EDWsoll zugeführt. Zwischen diesen beiden Sollwerten wird in Abhängigkeit von der Betätigung einer Power-Beyond-Ansteuerung 81 geschaltet. Wenn der Power-Beyond-Verbraucher 74 an den Power-Beyond-Anschluss 72 entweder nicht angeschlossen ist, oder der Power-Beyond-Verbraucher 74 nicht bestätigt wird, wird als Sollwert y1EDWsoll verwendet, während bei angeschlossenem und bestätigtem Power-Beyond-Verbraucher 74 der Sollwert y2EDWsoll zum Einsatz gelangt. Die Power-Beyond-Ansteuerung 81 wird durch ein Signal von einem Bediener UPB initialisiert.With reference to Fig. 2 the operation of the pump controller 8 is described in more detail via the control unit 10. The control unit 10 is a setpoint y1 EDWsoll and y2 EDWsoll supplied. Between these two setpoints becomes in response to the actuation of a power beyond control 81 switched. If the power beyond consumer 74 is either not connected to the power beyond port 72, or the power beyond consumer 74 is not acknowledged, the setpoint y1 is EDWsoll , while with the connected and confirmed power beyond consumer 74 the setpoint value y2 EDWsetpoint is used. The power beyond driver 81 is initialized by a signal from an operator U PB .

Der jeweilige Sollwert wird mit dem Ausgangssignal yEDW des Wegaufnehmers 68 verglichen und einem Regler 70 im Steuergerät 10 zugeführt. Der Sollwert Y1 EDWyoll ist in einer solchen Weise gewählt, dass bei nicht angeschlossenem oder nicht betätigtem Power-Beyond-Verbraucher 74 mit dem Sollwert y1EDwsoll die Stellung (a) des Steuerschiebers 62 der Eingangsdruckwaage 60 als Sollwert angesehen wird, während bei angeschlossenem und betätigtem Power-Beyond-Verbraucher 74 mit dem Sollwert y2EDWsoll die Stellung (b) des Steuerschiebers 62 der Eingangsdruckwaage 60 eingestellt ist.The respective desired value is compared with the output signal y EDW of the displacement transducer 68 and fed to a controller 70 in the control unit 10. The setpoint Y 1 EDWyoll is selected in such a way that when not connected or not operated power beyond consumer 74 with the setpoint y1 EDwsoll the position (a) of the spool 62 of the input pressure compensator 60 is regarded as a setpoint, while connected and actuated power beyond consumer 74 with the setpoint y2 EDWsoll the position (b) of the spool 62 of the input pressure compensator 60 is set.

In der Stellung (a) der Eingangsdruckwaage 60 ist sichergestellt, dass das Druckmittel von der Pumpe 6 über die Eingangsdruckwaage 60 den Verbrauchern 2, 4 verlustarm zugeführt wird, während bei Betätigung des Power-Beyond-Verbrauchers 74 die Eingangsdruckwaage 60 in die Stellung (b) gebracht wird, in der bei geeigneter Einstellung der Pumpe 6 ein geringer Restvolumenstrom über den Tankanschluss T und den Tankkanal 66 abströmt. Auf diese Weise wird der Power-Beyond-Verbraucher 74 priorisiert, wodurch selbst bei einem hohen Volumenstrombedarf des Power-Beyond-Verbrauchers 74 sowohl die Verbraucher 2, 4 als auch, der Power-Beyond-Verbraucher 74 hinreichend mit Druckmittel versorgt werden, sofern die Pumpe 6 entsprechend ausgelegt ist.In the position (a) of the inlet pressure compensator 60 ensures that the pressure medium from the pump 6 via the input pressure compensator 60 the consumers 2, 4 is supplied loss, while upon actuation of the power beyond consumer 74, the input pressure compensator 60 in the position (b ) is brought, in the appropriate adjustment of the pump 6, a small residual volume flow through the tank port T and the tank passage 66 flows. In this way, the power beyond consumer 74 is prioritized, whereby even with a high volume flow demand of the power beyond consumer 74, both the consumers 2, 4 and, the power beyond consumers 74 are adequately supplied with pressure medium, if the Pump 6 is designed accordingly.

Mit der hydraulischen Steueranordnung entsprechend dem ersten Ausführungsbeispiel ist ferner abgesichert, dass bei einer Unterversorgung der Verbraucher die Eingangsdruckwaage 60 schließt, wodurch eine Priorisierung des Power-Beyond-Verbrauchers 74 gegenüber den Verbrauchern 2, 4 abgesichert ist.With the hydraulic control arrangement according to the first embodiment is further ensured that at a deficiency of the consumer, the input pressure compensator 60 closes, whereby a prioritization of the power beyond consumer 74 against the consumers 2, 4 is secured.

Die Fig. 3 und 4, die sich auf ein zweites Ausführungsbeispiel der Erfindung beziehen, unterscheiden sich vom ersten Ausführungsbeispiel lediglich dadurch, dass beim zweiten Ausführungsbeispiel im Tankkanal 66 ein Reststromsensor 100 vorgesehen ist, durch den der Restvolumenstrom vom Tankanschluss T der Eingangdruckwaage 60 zur Tankleitung 50 messbar ist. Das Steuergerät 110 unterscheidet sich vom Steuergerät 10 des ersten Ausführungsbeispiels dadurch, dass bei einem durch Betätigung der Power-Beyond-Ansteuerung 81 angezeigten Zustand, in dem der Power-Beyond-Verbraucher 74 angeschlossen und betätigt ist, als Sollwert statt des Sollwertes YEDWsoll des ersten Ausführungsbeispiels nun ein Sollwert QEowsoll, der den Restvolumenstrom darstellt, verwendet wird. Für den Ist-Wert wird im Steuergerät 110 bei angeschlossenem und betätigtem Power-Beyond-Verbraucher 74 vom Weg yEDW auf den Restvolumenstrom QEDW umgeschaltet.The 3 and 4 , Which relate to a second embodiment of the invention, differ from the first embodiment only in that in the second embodiment in the tank channel 66, a residual current sensor 100 is provided, through which the residual volume flow from the tank port T of the inlet pressure compensator 60 to the tank line 50 can be measured. The control unit 110 differs from the control unit 10 of the first embodiment in that at a state indicated by actuation of the power beyond control 81, in which the power beyond consumer 74 is connected and actuated, as setpoint instead of the setpoint Y EDWsoll of First embodiment, now a setpoint Q Eowsoll , which represents the residual flow is used. For the actual value is switched in the control unit 110 with connected and actuated power beyond consumer 74 from the path y EDW to the residual volume flow Q EDW .

Der Vorteil des zweiten Ausführungsbeispiels besteht in der direkten Messung des Restvolumenstroms und der damit verbundenen, im Vergleich zum ersten Ausführungsbeispiel feinfühligeren und genaueren Regelung des Pumpenreglers 8.The advantage of the second exemplary embodiment consists in the direct measurement of the residual volume flow and the associated control of the pump regulator 8, which is more sensitive and precise compared to the first exemplary embodiment.

Eine hydraulische Steueranordnung entsprechend dem dritten Ausführungsbeispiel, das in den Fig. 5 und 6 dargestellt ist, unterscheidet sich von der hydraulischen Steueranordnung entsprechend dem ersten Ausführungsbeispiel dadurch, dass nun statt des Vorsteuergerätes 54, das eine hydraulische Betätigung der Steuerkolben 26, 40 der Wegeventile 24, 38 bewirkt, bzw. einer Handbetätigung im dritten Ausführungsbeispiel ein Joystick 254 verwendet wird, durch dessen ausgegebene elektrische Signale die Betätigung der Steuerkolben 26, 40 der Wegeventile 24, 38 erfolgt.A hydraulic control arrangement according to the third embodiment, which in the FIGS. 5 and 6 is different from the hydraulic control arrangement according to the first embodiment in that now instead of the pilot control device 54, which causes a hydraulic actuation of the control piston 26, 40 of the directional control valves 24, 38, or a manual operation in the third embodiment, a joystick 254 is used by the output electrical signals, the actuation of the control piston 26, 40th the directional control valves 24, 38 takes place.

Die Ausgangssignale des Joysticks 254 werden ebenfalls dem Steuergerät 210 zugeführt, so dass es wie in Fig. 6 gezeigt ist, im Steuergerät 210 der Regler 270 eine Ansteuerung des Pumpenreglers 8 zusätzlich auf der Grundlage der Betätigung des Joysticks 254 ausführt. Damit ist eine proportionale Voransteuerung der Pumpe 6 möglich, so dass der Regelalgorithmus des Reglers 270 für die Lageregelung der Eingangsdruckwaage 60 nur noch geringe Regelabweichungen ausgleichen muss. Im Ergebnis sind die dynamischen Übertragungseigenschaften der hydraulischen Steueranordnung verbessert.The output signals of the joystick 254 are also supplied to the controller 210, so that it as in Fig. 6 In the controller 210, the controller 270 additionally performs driving of the pump controller 8 based on the operation of the joystick 254. Thus, a proportional pilot control of the pump 6 is possible, so that the control algorithm of the controller 270 for the position control of the inlet pressure compensator 60 only has to compensate for small deviations. As a result, the dynamic transmission characteristics of the hydraulic control assembly are improved.

Eine hydraulische Steueranordnung entsprechend dem vierten Ausführungsbeispiel ist in den Fig. 7 und 8 gezeigt. Diese hydraulische Steueranordnung weicht von der hydraulischen Steueranordnung des zweiten Ausführungsbeispiels lediglich in der Verwendung des Joysticks 254 ähnlich dem dritten Ausführungsbeispiel ab. Genauer gesagt werden dem Steuergerät 310 im Unterschied zum zweiten Ausführungsbeispiel nun zusätzlich die elektrischen Ausgangssignale des Joysticks 254 zugeführt, so dass der Regelalgorithmus für die Reststromregelung der Eingangsdruckwaage 60 hier nur noch geringe Regelabweichungen ausgleichen muss. Im Ergebnis sind ähnlich dem dritten Ausführungsbeispiel die dynamischen Übertragungseigenschaften der hydraulischen Steueranordnung verbessert.A hydraulic control device according to the fourth embodiment is shown in FIGS FIGS. 7 and 8 shown. This hydraulic control arrangement differs from the hydraulic control arrangement of the second embodiment only in the use of the joystick 254, similar to the third embodiment. More precisely, in contrast to the second exemplary embodiment, the control unit 310 is now additionally supplied with the electrical output signals of the joystick 254, so that the control algorithm for the residual current control of the inlet pressure compensator 60 only has to compensate for small control deviations. As a result, similar to the third embodiment, the dynamic transmission characteristics of the hydraulic control device are improved.

Die Fig. 9, 10 und 11 zeigen ein fünftes, sechstes und siebtes Ausführungsbeispiel der vorliegenden Erfindung. Die Vorspannung der Feder 64 der Eingangsdruckwaage 60 wird mechanisch (fünftes Ausführungsbeispiel), hydraulisch (sechstes Ausführungsbeispiel) oder elektrisch (siebtes Ausführungsbeispiel) verändert. Der sonstige hydraulische Aufbau beim fünften, sechsten und siebten Ausführungsbeispiel entspricht dem des ersten Ausführungsbeispiels.The FIGS. 9, 10 and 11 show a fifth, sixth and seventh embodiments of the present invention. The bias of the spring 64 of the input pressure compensator 60 is changed mechanically (fifth embodiment), hydraulically (sixth embodiment) or electrically (seventh embodiment). The other hydraulic structure in the fifth, sixth and seventh embodiments corresponds to that of the first embodiment.

Im fünften Ausführungsbeispiel, das in Fig. 9 gezeigt ist, ist der Endabschnitt der Feder 64, der entgegengesetzt zur Abstützung der Feder 64 am Steuerkolben 62 der Eingangsdruckwaage 60 liegt, an einer Einstellschraube 490 abgestützt, deren Relativposition in Bewegungsrichtung des Steuerkolben 62 veränderbar ist.In the fifth embodiment, the in Fig. 9 is shown, the end portion of the spring 64, which is opposite to the support of the spring 64 on the control piston 62 of the inlet pressure compensator 60, supported on an adjusting screw 490, the relative position in the direction of movement of the control piston 62 is variable.

Wenn der Power-Beyond-Verbraucher 74 weder angeschlossen noch betätigt ist, befindet sich die Einstellschraube 490 in ihrer rechten Position in Fig. 9, wobei die Sollposition der Eingangsdruckwaage die Position a ist. Wenn der Power-Beyond-Verbraucher 74 angeschlossen und betätigt ist, befindet sich die Einstellschraube 490 in ihrer linken Position in Fig. 9, wobei die Position b des Steuerkolbens die Sollposition mit erhöhter Vorspannung ist.When the power beyond consumer 74 is neither connected nor actuated, the adjustment screw 490 is in its right position in FIG Fig. 9 , wherein the target position of the inlet pressure compensator is the position a. When power beyond consumer 74 is connected and actuated, adjustment screw 490 is in its left position in FIG Fig. 9 , wherein the position b of the control piston is the target position with increased bias.

Beim sechsten Ausführungsbeispiel wirkt auf dem vom Steuerkolben 62 entfernten Endabschnitt der Feder 64 ein Stellkolben 590 eines Stellzylinders 592, wobei ein Zylinderraum des Stellzylinders 592 über ein Schaltventil 594 mit Druck beaufschlagbar ist, um eine Bewegung des Steuerkolbens 62 in Fig. 10 nach links zu bewirken. Im Ruhezustand drückt eine Feder 596 den Steuerkolben des Schaltventils 594 in eine Position, in der der Zylinderraum des Stellzylinders 592 zum Tank hin entlastet ist, wobei die Feder 64 die geringste Einspannung aufweist. Bei einer elektrischen Betätigung des Schaltventils 594 wird der Zylinderraum des Stellzylinders 592 mit Druckmittel gespeist so dass sich dort ein Druck aufbaut, durch den der Stellkolben 590 in Fig. 10 nach links bewegbar ist, um die Feder 64 zusätzlich zu spannen.In the sixth embodiment acts on the end remote from the control piston 62 end portion of the spring 64, a control piston 590 of an actuating cylinder 592, wherein a cylinder space of the actuating cylinder 592 is acted upon via a switching valve 594 with pressure to a movement of the control piston 62 in Fig. 10 to move to the left. At rest, a spring 596 pushes the control piston of the switching valve 594 in a position in which the cylinder space of the actuating cylinder 592 is relieved to the tank, wherein the spring 64 has the lowest clamping. In an electrical actuation of the switching valve 594, the cylinder chamber of the actuating cylinder 592 is supplied with pressure medium so that there builds up a pressure through which the actuating piston 590 in Fig. 10 is moved to the left to additionally tension the spring 64.

In der Ruheposition des Schaltventils 594 und damit bei entlastetem Zylinderraum des Stellzylinders 592 befindet sich der Stellkolben 590 in seiner rechten Position, wobei die Position a der Eingangsdruckwaage 60 der Sollwert ist. Bei einer Druckbeaufschlagung des Zylinderraums des Stellzylinders 592 über das Schaltventil 594 wird der Stellkolben 590 in seine linke Position in Fig. 10 gebracht, wobei die Position b der Eingangsdruckwaage 60 die Sollposition ist.In the rest position of the switching valve 594 and thus at unloaded cylinder space of the actuating cylinder 592 is the actuating piston 590 in its right position, wherein the position a of the input pressure compensator 60 is the target value. When pressurizing the cylinder space of the adjusting cylinder 592 via the switching valve 594, the adjusting piston 590 is moved to its left position in FIG Fig. 10 brought, wherein the position b of the input pressure compensator 60 is the desired position.

Beim siebenten Ausführungsbeispiel nach Fig. 11 ist ein elektrischer Stellmotor 690 vorgesehen, an dem ein Gewindeschaft 692 vorgesehen ist. Der zum Steuerkolben 62 der Eingangsdruckwaage 60 entgegengesetzt liegende Endabschnitt der Feder 64 ist in seiner Position durch eine Betätigung des Stellmotors 690 veränderbar. Dabei ist bei zum Stellmotor 690 hin herausgeschraubtem Gewindeschaft 692 die Position b der Eingangsdruckwaage 60 als Sollposition vorgegeben. In einer eingeschraubten Position des Gewindeschaftes 692 ist die Position a des Steuerkolbens 62 der Eingangsdruckwaage 60 vorgegeben.According to the seventh embodiment Fig. 11 an electric servomotor 690 is provided on which a threaded shaft 692 is provided. The opposite to the control piston 62 of the input pressure compensator 60 end portion of the spring 64 is changeable in its position by actuation of the servomotor 690. In this case, the position b of the inlet pressure compensator 60 is preset as the target position when the threaded shaft 692 is unscrewed to the servomotor 690. In a screwed-in position of the threaded shaft 692, the position a of the control piston 62 of the inlet pressure compensator 60 is predetermined.

Dem fünften, sechsten und siebten Ausführungsbeispiel ist gemeinsam, dass unter dem Einsatz von nur einer Feder eine Anhebung der Regeldruckdifferenz durch Vergrößerung der Federvorspannung realisierbar ist. Es sind daher herkömmliche elektronische Steuereinrichtungen für das Steuergerät 10 nutzbar, wobei lediglich eine geringe mechanische, elektrische, oder hydraulische Modifikationen notwendig ist, um die Anhebung der Regeldruckdifferenz der Eingangsdruckwaage zu realisieren.The fifth, sixth and seventh embodiments have in common that with the use of only one spring an increase in the control pressure difference by increasing the spring preload can be realized. There are therefore conventional electronic control devices for the controller 10 available, with only a small mechanical, electrical, or hydraulic modifications necessary is to realize the increase in the control pressure difference of the inlet pressure compensator.

Die Fig. 12, 13 und 14 zeigen ein achtes Ausführungsbeispiel der vorliegenden Erfindung, bei dem durch die Verwendung eines Federpakets eine selbständige Erhöhung der Regeldruckdifferenz an der Eingangsdruckwaage 60 bei Verstellung der Regelposition von der Position a auf die Position b erfolgt. Hierbei wird der Umstand ausgenutzt, dass mit der Zuschaltung eines Power-Beyond-Verbrauchers 74 des ersten Ausführungsbeispiels die Regelposition der Eingangsdruckwaage weiter nach rechts verschoben wird. Um diese Regelposition zu erreichen wird eine entsprechend höhere Regeldruckdifferenz benötigt.The Fig. 12, 13 and 14 show an eighth embodiment of the present invention, in which by using a spring package, a self-increasing the control pressure difference at the inlet pressure compensator 60 is carried out when adjusting the control position from the position a to the position b. Here, the fact is exploited that with the connection of a power beyond consumer 74 of the first embodiment, the control position of the inlet pressure compensator is further shifted to the right. To achieve this control position, a correspondingly higher control pressure difference is required.

Im Unterschied zum ersten bis vierten Ausführungsbeispiel wird dabei beim achten Ausführungsbeispiel ab einem vorbestimmten Verschiebungsweg des Steuerkolbens 62 zusätzlich zur Feder 64 eine Zusatzfeder 764 aktiv.In contrast to the first to fourth embodiments, an additional spring 764 is activated in addition to the spring 64 in the eighth embodiment, starting from a predetermined displacement path of the control piston 62.

Fig. 13 zeigt beispielhaft eine konstruktive Ausgestaltung für die Zuschaltung der Zusatzfeder 764. In einem zylinderförmigen Gehäuse 700 mündet der Endabschnitt des Steuerkolbens 62 der Eingangsdruckwaage 60 und wird in einer Zylinderbohrung mittels des Halterings 702 gehalten. An diesem Haltering 702 stützt sich ebenfalls die Feder 64 ab, deren entgegengesetzter Endabschnitt über eine Federhalterung 704 am Federgehäuse 700 abgestützt ist. Innerhalb der Feder 64 ist eine Stützstange 706 vorgesehen, die im Federgehäuse 700 beispielsweise über Halteringe befestigt ist. Auf diese Stützstange 706 ist gleitfähig ein Federteller 708 aufgenommen, an dem sich ein Endabschnitt der Zusatzfeder 764 abstützt. Der entgegengesetzte Endabschnitt der Zusatzfeder 764 stützt sich an der Federhalterung 704 ab. Fig. 13 shows by way of example a structural design for the connection of the additional spring 764. In a cylindrical housing 700, the end portion of the control piston 62 of the inlet pressure compensator 60 opens and is held in a cylinder bore by means of the retaining ring 702. The spring 64 is likewise supported on this retaining ring 702, whose opposite end section is supported on the spring housing 700 via a spring mount 704. Within the spring 64, a support rod 706 is provided which is fixed in the spring housing 700, for example via retaining rings. On this support rod 706, a spring plate 708 is slidably received, on which an end portion of the auxiliary spring 764 is supported. The opposite end portion of the auxiliary spring 764 is supported on the spring holder 704.

Wenn sich der Haltering 702 mit dem Haltegehäuse 700 in Anlage befindet, wirkt auf den Haltering 702 die Kraft der Feder 64. Beim Bewegen des Steuerkolbens 62 in Fig. 13 nach rechts bewegt sich der Haltering 702 mit dem Steuerkolben 62 ebenfalls nach rechts, wodurch ein Zusammendrücken der Feder 64 bewirkt wird. Dieses entspricht einer Bewegung des Steuerkolbens von der Position 0 zu Position a in Fig. 1.When the retainer ring 702 is in abutment with the retainer housing 700, the force of the spring 64 acts on the retainer ring 702. When moving the control piston 62 in FIG Fig. 13 to the right, the retaining ring 702 moves with the control piston 62 also to the right, whereby a compression of the spring 64 is effected. This corresponds to a movement of the control piston from the position 0 to position a in Fig. 1 ,

Nach der Zurücklegung eines vorbestimmten Weges läuft der Steuerkolben 62 auf den Federteller 708 auf. Bei einer weiteren Bewegung des Steuerkolbens 62 nach rechts in Fig. 13 wird der Federteller 708 von dem Steuerkolben 62 mitgenommen, wobei ein Zusammendrücken der Zusatzfeder 764 auf der kolbenstange 106 bewirkt wird, so dass beide Federn 64, 764 wirksam sind. Wenn der Steuerkolben 62 auf die Stützstange 706 aufläuft, ist eine weitere Bewegung des Steuerkolbens 62 in Fig. 13 nach rechts verhindert.After covering a predetermined path, the control piston 62 runs on the spring plate 708. Upon further movement of the control piston 62 to the right in Fig. 13 the spring plate 708 is entrained by the control piston 62, wherein a compression of the auxiliary spring 764 on the piston rod 106 is effected so that both springs 64, 764 are effective. When the control piston 62 runs onto the support rod 706, further movement of the control piston 62 is in Fig. 13 prevented to the right.

Auf Grund der in Fig. 13 gezeigten Gestaltung ist das möglich, dass ab einem vorbestimmten Hub des Steuerkolbens 62 in Fig. 13 nach rechts, durch den die Feder 64 zusammengedrückt wird, der Steuerkolben 62 bei einer weiteren Bewegung in Fig. 13 nach rechts ebenfalls die Zusatzfeder 764 zusammendrücken muss, bevor der Steuerkolben 62 auf das Ende des Stützstange 706 trifft und eine weitere Bewegung des Steuerkolben 62 in Fig. 13 nach rechts verhindert ist. Auf Grund dieser parallelen Anordnung der Feder 64 und der Zusatzfeder 764 lassen sich sehr kurze Einbauräume im Gehäuse der Eingangsdruckwaage 60 erzielen.Due to the in Fig. 13 As shown, it is possible that from a predetermined stroke of the control piston 62 in Fig. 13 to the right, by which the spring 64 is compressed, the control piston 62 in a further movement in Fig. 13 to the right also the auxiliary spring 764 must squeeze before the control piston 62 meets the end of the support rod 706 and a further movement of the control piston 62 in Fig. 13 is prevented to the right. Due to this parallel arrangement of the spring 64 and the additional spring 764 can be very short installation spaces in the housing of the inlet pressure compensator 60 achieve.

Alternativ zum Federpaket des achten Ausführungsbeispiels lässt sich in einer Variante auch eine Progressivfeder verwenden.As an alternative to the spring assembly of the eighth embodiment, a progressive spring can also be used in one variant.

Fig. 14 stellt eine exemplarische Kennlinie dar Eingangsdruckwaage 60 mit Druckanhebung dar. Dabei ist die Druckdifferenz der Eingangsdruckwaage über der Ventilstellung bzw. der Regelstellung aufgetragen. Dieser Kennlinie kann entnommen werden, dass ab einer bestimmten Ventilstellung/Regelstellung die Druckdifferenz vom Wert ΔpEDW1 auf den Wert ΔpEDW2 ansteigt. Fig. 14 represents an exemplary characteristic is input pressure compensator 60 with pressure increase. In this case, the pressure difference of the inlet pressure compensator over the valve position or the control position is plotted. From this characteristic it can be seen that, starting from a certain valve position / control position, the pressure difference increases from the value Δp EDW1 to the value Δp EDW2 .

Mit einer hydraulischen Steueranordnung entsprechend einer der vorstehenden Ausführungsbeispiele lässt sich ein Power-Beyond-Verbraucher 74 zur Aufrechterhaltung der Funktion priorisiert versorgen. Dabei erfolgt eine elektronisch, hydraulisch oder mechanisch ausgelöste Anhebung des Druckniveaus nur bei einer Aktivierung des Power-Beyond-Verbrauchers. In Ergebnis ist eine bedarfsgerechte und energiesparende Versorgung aller aktiven Verbraucher 2, 4, 74 möglich.With a hydraulic control arrangement according to one of the preceding embodiments, a power beyond consumer 74 can be prioritized to maintain the function. In this case, an electronically, hydraulically or mechanically triggered increase in the pressure level takes place only when the power beyond consumer is activated. As a result, needs-based and energy-saving supply of all active consumers 2, 4, 74 is possible.

Die vorliegende Erfindung ist nicht darauf beschränkt, dass die Verbraucher 2, 4 parallel geschaltet sind, sondern die Eingangsdruckwaage kann auch nur einem der Verbraucher 2,4 vorgeschaltet sein. In diesem Fall ist der andere Verbraucher direkt mit dem Druckanschluss der Pumpe verbunden und damit hydraulisch priorisiert.The present invention is not limited to the fact that the consumers 2, 4 are connected in parallel, but the inlet pressure compensator can also be connected upstream of only one of the consumers 2, 4. In this case, the other consumer is directly connected to the pressure port of the pump and thus hydraulically prioritized.

Claims (16)

  1. A hydraulic control system for controlling preferably at least two consumers (2, 4), which a pump (6) with an adjustable delivery quantity is able to supply with pressure fluid and which in particular belong to a mobile machine, which consumers are each associated with an adjustable metering orifice (24, 38) having a power beyond connection (72) to which at least one power beyond consumer (74) is connectable, and
    having an inlet pressure governor unit (60) that is connected downstream of the pump (6) and that is able to open a connection to a tank (T) and whose setting occurs as a function of a load pressure of the consumers (2, 4) or of the at least one power beyond consumer (74),
    wherein the inlet pressure governor (60) is provided in the pressure fluid flow path between the pump (6) and at least one of the two consumers (2, 4), while the power beyond connection (72) branches off from the pressure fluid path between the pump (6) and the inlet pressure governor (60).
  2. The control system as recited in claim 1,
    wherein the pump (6) is controllable as a function of the setting of the inlet pressure governor (60).
  3. The control system as recited in claim 2,
    wherein the pump (6) is controllable as a function of the position of a control piston (62) of the inlet pressure governor (60).
  4. The control system as recited in one of the preceding claims,
    wherein the pump (6) is controllable as a function of the volumetric flow at a connection (T) of the inlet pressure governor (60).
  5. The control system as recited in one of the preceding claims,
    wherein the pump (6) is controllable as a function of the control of the metering orifice (24, 38) of at least one consumer (2, 4).
  6. The control system as recited in one of the preceding claims,
    wherein the maximum of the load pressures act on the inlet pressure governor (60) in the closing direction.
  7. The control system as recited in claim 6,
    wherein the inlet pressure governor (60) closes the connection to the at least one of the two consumers (2, 4) and to the tank (T) in a spring-prestressed starting position and as it is moved in the opening direction, opens the connection first to the at least one of the two consumers (2, 4) and the to the tank (T).
  8. The control system as recited in one of the preceding claims,
    wherein the inlet pressure governor (60) is acted on in the closing direction by the force of a spring (64) and by the maximum of the load pressures and is acted on in the opening direction by the pressure in its inlet (P).
  9. The control system as recited in claim 8, equipped with a spring packet (64, 764) or a progressive spring for acting on the inlet pressure governor (60) in the closing direction and for switching the regulating pressure difference as a function of the spring stroke.
  10. The control system as recited in claim 8, equipped with a device (490, 590, 690) for increasing the prestressing force of the spring (64).
  11. The control system as recited in claim 10,
    wherein the device for increasing the prestressing force of the spring (64) is an adjusting screw (490) for mechanically moving the spring support, an adjusting piston (590) for hydraulically moving the spring support, or an actuating motor (690) for electrically moving the spring support.
  12. The control system as recited in one of the preceding claims,
    wherein the pump (6) is an electrically controllable variable displacement pump or a speed-regulated fixed displacement pump.
  13. The control system as recited in one of the preceding claims,
    wherein each of the metering orifices (24, 38) has an individual pressure governor (16, 20) connected upstream of it, which is acted on in the opening direction by a pressure governor spring (56, 58) and by the maximum load pressure of the consumers and is acted on in the closing direction by the pressure at the outlet of the respective individual pressure governor (16, 20).
  14. The control system as recited in one of the preceding claims, wherein the metering orifices are comprised of electrically, hydraulically, or mechanically movable directional control valves (24, 38).
  15. A pressure governor (60) for a control system as recited in one of the preceding claims,
    whose control piston (62) is acted on in the closing direction by a pressure governor spring arrangement (64, 764) and is acted on in the opening direction by a load pressure, in which the pressure governor spring arrangement has two springs (64, 764) that have the capacity to be brought into engagement one after the other.
  16. A control method for a control system as recited in one of claims 1 through 14, including the step of increasing the regulating pressure difference at the inlet pressure governor (60) upon activation of the power beyond consumer (74).
EP07702809A 2006-02-23 2007-01-17 Hydraulic control arrangement Not-in-force EP1989450B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006008940A DE102006008940A1 (en) 2006-02-23 2006-02-23 Hydraulic control arrangement for actuating multiple consumers, has input pressure balance provided in pressure medium flow path between pump and one of two consumers
PCT/EP2007/000352 WO2007096030A1 (en) 2006-02-23 2007-01-17 Hydraulic control arrangement

Publications (2)

Publication Number Publication Date
EP1989450A1 EP1989450A1 (en) 2008-11-12
EP1989450B1 true EP1989450B1 (en) 2010-05-12

Family

ID=37991057

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07702809A Not-in-force EP1989450B1 (en) 2006-02-23 2007-01-17 Hydraulic control arrangement

Country Status (5)

Country Link
US (1) US8286544B2 (en)
EP (1) EP1989450B1 (en)
AT (1) ATE467769T1 (en)
DE (2) DE102006008940A1 (en)
WO (1) WO2007096030A1 (en)

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DE102012110978B4 (en) 2012-11-15 2024-02-15 Linde Hydraulics Gmbh & Co. Kg Hydrostatic drive system

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DE112008000285A5 (en) * 2007-02-21 2009-10-29 Luk Lamellen Und Kupplungsbau Beteiligungs Kg hydraulic system
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DE102007045802A1 (en) 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulic control arrangement
EP2028376B1 (en) * 2007-08-22 2013-11-27 Robert Bosch GmbH Hydraulic control device
DE102007045803A1 (en) 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulic control arrangement
JP5388461B2 (en) * 2008-03-21 2014-01-15 株式会社小松製作所 Steering device
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DE102014208019A1 (en) * 2014-04-29 2015-10-29 Robert Bosch Gmbh Hydraulic control arrangement for a plurality of actuators

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DE102004048684A1 (en) 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulic control arrangement
DE102007045802A1 (en) * 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulic control arrangement

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DE102012110978B4 (en) 2012-11-15 2024-02-15 Linde Hydraulics Gmbh & Co. Kg Hydrostatic drive system

Also Published As

Publication number Publication date
US8286544B2 (en) 2012-10-16
WO2007096030A1 (en) 2007-08-30
ATE467769T1 (en) 2010-05-15
DE502007003725D1 (en) 2010-06-24
US20090007556A1 (en) 2009-01-08
EP1989450A1 (en) 2008-11-12
DE102006008940A1 (en) 2007-08-30

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