EP1989450B1 - Dispositif de commande hydraulique - Google Patents

Dispositif de commande hydraulique 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)
English (en)
Other versions
EP1989450A1 (fr
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
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Publication of EP1989450A1 publication Critical patent/EP1989450A1/fr
Application granted granted Critical
Publication of EP1989450B1 publication Critical patent/EP1989450B1/fr
Not-in-force legal-status Critical Current
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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)

Claims (16)

  1. Dispositif de commande hydraulique comprenant :
    - une pompe et au moins deux utilisateurs, dans lequel
    - le dispositif de commande commandant au moins les deux utilisateurs (2, 4) alimentés par la pompe (6) avec un débit réglable de liquide hydraulique, en particulier un outil mobile auquel est associé respectivement au moins un diaphragme de dosage réglable (24, 38),
    - un branchement hydraulique Power-Beyond (72), auquel peut être relié au moins un utilisateur Power-Beyond (74), et
    - une balance de pression d'entrée (60) branchée en aval de la pompe (6) qui commande une liaison avec un réservoir (T) et dont le réglage se fait en fonction d'une pression de charge des utilisateurs (2, 4) ou au moins de l'utilisateur Power-Beyond (74),
    caractérisé en ce que
    - la balance de pression d'entrée (60) est installée dans le chemin de liquide hydraulique entre la pompe (6) et au moins l'un des deux utilisateurs (2, 4), et
    - le branchement Power-Beyond (72) dans le chemin de liquide hydraulique bifurque entre la pompe (6) et la balance de pression d'entrée (60).
  2. Dispositif de commande selon la revendication 1,
    caractérisé en ce que
    la pompe (6) est commandée en fonction du réglage de la balance de pression d'entrée (60).
  3. Dispositif de commande selon la revendication 2,
    dans lequel
    la pompe (6) est commandée en fonction de la position d'un piston de commande (62) de la balance de pression d'entrée (60).
  4. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    la pompe (6) est commandée en fonction du débit volumique à un branchement (T) de la balance de pression d'entrée (60).
  5. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    la pompe (6) est commandée en fonction de la commande du diaphragme de dosage (24, 38) d'au moins un utilisateur (2, 4).
  6. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    la plus grande des pressions de charge alimente la balance de pression d'entrée (60) dans le sens de la fermeture.
  7. Dispositif de commande selon la revendication 6,
    dans lequel
    dans une position de base précontrainte par un ressort, la balance de pression d'entrée (60), coupe la liaison vers au moins l'un des deux utilisateurs (2, 4) et vers le réservoir (T), et lors du déplacement dans le sens de l'ouverture, elle ouvre d'abord la liaison vers au moins l'un des utilisateurs (2, 4) et ensuite vers le réservoir (T).
  8. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    la balance de pression d'entrée (60) est sollicitée dans le sens de sa fermeture par la force d'un ressort (64) et par la plus grande des pressions de charge et dans le sens de l'ouverture par la pression à son entrée (P).
  9. Dispositif de commande selon la revendication 8, comprenant un bloc de ressorts (64, 764) ou un ressort progressif pour solliciter la balance de pression d'entrée (60) dans le sens de la fermeture et commuter la régulation de différence de pression en fonction de la course de ressort.
  10. Dispositif de commande selon la revendication 8, comprenant une installation (490, 590, 690) pour augmenter la précontrainte des ressorts (64).
  11. Dispositif de commande selon la revendication 10,
    dans lequel
    l'installation pour augmenter la précontrainte des ressorts (64) est une vis de réglage (490) pour le réglage mécanique de l'appui des ressorts, un piston de réglage (590) pour le réglage hydraulique de l'appui des ressorts ou un moteur de réglage (690) pour le réglage électrique de l'appui des ressorts.
  12. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    la pompe (6) est une pompe électrique de réglage ou une pompe constante régulée en vitesse de rotation.
  13. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    chaque diaphragme de dosage (24, 38) est branché en amont d'une pompe de pression individuelle (16, 20) qui, dans le sens de l'ouverture, est sollicité par un ressort de balance de pression (56, 58) et la plus haute charge de pression des utilisateurs et, dans le sens de la fermeture, par la pression à la sortie de la balance de pression individuelle (16, 20) correspondante.
  14. Dispositif de commande selon l'une des revendications précédentes,
    dans lequel
    les diaphragmes de dosage sont constitués par des distributeurs à tiroirs (24, 38) à commande électrique, hydraulique ou mécanique.
  15. Dispositif de commande selon l'une des revendications précédentes, comprenant une balance de pression (60) dont le piston de commande (62) est sollicité dans le sens de la fermeture par un dispositif de balance de pression (64, 764) et dans le sens de l'ouverture par une pression de charge, le dispositif de ressort de balance de pression comportant deux ressorts (64, 764) agissant l'un après l'autre.
  16. Procédé de commande dans lequel on utilise un dispositif de commande selon l'une des revendications 1 à 15, avec l'étape consistant à relever la différence de pression de réglage à la balance de pression d'entrée (60) en branchant l'utilisateur Power-Beyond (74).
EP07702809A 2006-02-23 2007-01-17 Dispositif de commande hydraulique Not-in-force EP1989450B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006008940A DE102006008940A1 (de) 2006-02-23 2006-02-23 Hydraulische Steueranordnung
PCT/EP2007/000352 WO2007096030A1 (fr) 2006-02-23 2007-01-17 Dispositif de commande hydraulique

Publications (2)

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

Family

ID=37991057

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07702809A Not-in-force EP1989450B1 (fr) 2006-02-23 2007-01-17 Dispositif de commande hydraulique

Country Status (5)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012110978B4 (de) 2012-11-15 2024-02-15 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem

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WO2008101458A2 (fr) * 2007-02-21 2008-08-28 Luk Lamellen Und Kupplungsbau Beteiligungs Kg Système hydraulique
EP2025948A3 (fr) * 2007-08-16 2013-03-27 Robert Bosch GmbH Agencement de commande hydraulique
DE102007045802A1 (de) 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102007045803A1 (de) 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulische Steueranordnung
EP2028376B1 (fr) * 2007-08-22 2013-11-27 Robert Bosch GmbH Agencement de commande hydraulique
JP5388461B2 (ja) * 2008-03-21 2014-01-15 株式会社小松製作所 ステアリング操作装置
DE102012014250A1 (de) 2012-07-19 2014-01-23 Hydac System Gmbh Ventil, insbesondere Stetigventil
DE102014208019A1 (de) * 2014-04-29 2015-10-29 Robert Bosch Gmbh Hydraulische Steueranordnung für mehrere Aktuatoren

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US3587630A (en) * 1969-05-02 1971-06-28 Deere & Co Pressure-compensated flow control valve
US4070857A (en) * 1976-12-22 1978-01-31 Towmotor Corporation Hydraulic priority circuit
US4977928A (en) * 1990-05-07 1990-12-18 Caterpillar Inc. Load sensing hydraulic system
DE4127342C2 (de) 1991-08-19 1995-02-16 Danfoss As Hydraulisches System mit einer Pumpe
DE10115650A1 (de) 2001-03-29 2002-10-02 Bosch Gmbh Robert Hydraulische Steuereinrichtung
DE102004048684A1 (de) 2004-10-06 2006-04-13 Bosch Rexroth Ag Hydraulische Steueranordnung
DE102007045802A1 (de) * 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulische Steueranordnung

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Publication number Priority date Publication date Assignee Title
DE102012110978B4 (de) 2012-11-15 2024-02-15 Linde Hydraulics Gmbh & Co. Kg Hydrostatisches Antriebssystem

Also Published As

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

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