EP4130493B1 - Hydraulic control assembly - Google Patents

Hydraulic control assembly Download PDF

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Publication number
EP4130493B1
EP4130493B1 EP22186950.6A EP22186950A EP4130493B1 EP 4130493 B1 EP4130493 B1 EP 4130493B1 EP 22186950 A EP22186950 A EP 22186950A EP 4130493 B1 EP4130493 B1 EP 4130493B1
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EP
European Patent Office
Prior art keywords
valve
pressure
control
proportional valve
control assembly
Prior art date
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Active
Application number
EP22186950.6A
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German (de)
French (fr)
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EP4130493A1 (en
Inventor
Andreas Guender
Henning Freigang
Marc Weigand
Jan Lukas Bierod
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP4130493A1 publication Critical patent/EP4130493A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/30505—Non-return valves, i.e. check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/3051—Cross-check 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/3058—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve having additional valves for interconnecting the fluid chambers of a double-acting actuator, e.g. for regeneration mode or for floating mode
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • 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
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3127—Floating position connecting the working ports and the return line
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/351—Flow control by regulating means in feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/35—Directional control combined with flow control
    • F15B2211/353—Flow control by regulating means in return line, i.e. meter-out control
    • 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
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6658—Control using different modes, e.g. four-quadrant-operation, working mode and transportation mode
    • 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
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • 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
    • F15B2211/765—Control of position or angle of the output member

Definitions

  • the invention relates to a hydraulic control arrangement for actuating a hydraulic actuator/consumer, in particular a differential hydraulic cylinder, according to the preamble of patent claim 1.
  • Regeneration is understood to mean a return of fluid from a (piston) rod side of the hydraulic cylinder to a piston side of the hydraulic cylinder by fluidly connecting the two sides to one another.
  • a load holding function is understood to mean blocking the movement of a piston of the hydraulic cylinder.
  • An internally known control arrangement has a directional control valve that connects two working lines, which are connected to pressure chambers of the actuator (hydraulic cylinder) acting in opposite directions, to a pressure medium source or a pressure medium sink, depending on the switching position.
  • a check valve is arranged in each of the two working lines (power pressure lines), which can be unlocked by pressurizing the other working line.
  • a load-dependent valve is arranged in a short-circuit line connecting the two working lines, which switches between the functions of load holding and the normal and regeneration circuit. This means that the function switching takes place without electrical control signals.
  • the disadvantage of the known control arrangement is that it does not work with switching loads can be used, so that four-quadrant operation is not possible.
  • the mutually unlockable check valves cannot have clearly defined circuit states, which severely impairs the control functionality.
  • the function switchover of the normal and regeneration circuit must be set mechanically during project planning or during commissioning.
  • Another internally known control arrangement also has a directional control valve, which pressurizes or relieves pressure on the two working lines depending on the switching position, as well as a check valve arranged in each of the two working lines.
  • a first solenoid valve is used to unlock the check valves and a second solenoid valve is used to short-circuit the two working lines so that the functions of load holding and the normal and regeneration circuit can be switched valve-controlled. This means that the function switching takes place using two electrical control signals.
  • the disadvantage of this solution is that two solenoid valves are required, so that this control arrangement is cost-intensive due to the number of solenoid valves and the power electronics required for an output stage for switching.
  • the invention is based on the object of providing a hydraulic control arrangement with which the hydraulic functions described can be implemented, but which is at the same time simple, compact and inexpensive.
  • the control arrangement according to the invention is used to operate a hydraulic actuator, in particular a differential hydraulic cylinder.
  • the control arrangement has two working lines, one of which can be connected to pressure chambers of the actuator acting in opposite directions for actuating the actuator and in each of which an unlockable check valve is arranged, the blocked flow direction of which can be released from the direction of the pressure chambers by hydraulic control becomes.
  • the Control arrangement has a proportional valve, through which the two working lines can be connected to a pressure medium source to pressurize the associated pressure chamber with a pressure medium source or to relieve the pressure of the associated pressure chamber with a pressure medium sink, depending on the (switching) position of the proportional valve.
  • control arrangement has a short-circuit line which connects the two working lines with the interposition of two check valves with opposite flow directions.
  • one of the check valves arranged in the short-circuit line is designed to be lockable and the other of the check valves arranged in the short-circuit line is designed to be unlockable.
  • control arrangement has a, preferably magnetically controlled, switching valve, through which the unlockable check valves arranged in the working lines and the lockable check valve arranged in the short-circuit line can be hydraulically controlled in a switching position of the switching valve.
  • the control arrangement according to the present invention has a first working line which is connectable (or connected) to a first pressure chamber of an actuator, so that the actuator can be moved by pressurizing the first working line in a first direction, in particular in an extension direction of a hydraulic cylinder, for example of such an actuator, is adjustable, as well as a second working line which can be connected (or is connected) to a second pressure chamber of the actuator, so that the actuator can be moved by pressurizing the second working line in a second direction, in particular a retraction direction of the hydraulic cylinder as an example of such an actuator , is adjustable.
  • a first check valve is arranged in the first working line and a second check valve is arranged in the second working line, each of which allows a flow of pressure medium only in the direction of the actuator or the respective pressure chamber and blocks it in a blocking direction/opposite direction/opposite direction.
  • the first and second check valves are designed to be unlockable in the sense that the blocking direction is released/unlocked (controlled) when a control port of the respective check valve is pressurized.
  • the control arrangement has the proportional valve, which is used to continuously regulate a hydraulic resistance and, depending on the (switching) position, the first working line or second working line for pressurizing with a pump/the Pressure medium source or a tank/the pressure medium sink connects.
  • control arrangement has a short-circuit line through which the two working lines are or can be fluidly connected to one another.
  • a third check valve arranged in the short-circuit line enables a pressure medium flow in only one flow direction from one working line into the other working line, in particular from the second working line into the first working line, and blocks, in particular, a pressure medium flow in a blocking direction/opposite direction/opposite direction the first work management to the second work management.
  • a fourth check valve arranged in the short-circuit line enables a pressure medium flow in only one flow direction from the other working line into one working line, in particular from the first working line into the second working line, and blocks a pressure medium flow in a blocking direction/opposite direction/opposite direction, in particular from the second line into the first line.
  • the third check valve is designed to be lockable, i.e. the flow direction is closed/blocked (controlled) when a control port of the third check valve is pressurized.
  • the fourth check valve is designed to be unlockable in the sense that the blocking direction is released/unlocked (controlled) when a control port of the fourth check valve is pressurized.
  • the control arrangement has a switching valve which controls/switches the first, second and third check valves. This means that in a first switching position the switching valve relieves pressure on the control connections of the first, second and third check valves, i.e. does not control these three check valves (in the above sense), and in a second switching position pressurizes the control connections of the first, second and third check valves, i.e. controls these three check valves (in the above sense).
  • control arrangement according to the invention has (only) one switching valve through which three of the four check valves can be controlled hydraulically at the same time.
  • the structure of the control arrangement according to the invention has the advantage that the three hydraulic functions of a normal switching/force position control, one Regeneration circuit and load holding can be implemented and at the same time can only be switched between the hydraulic functions in a defined manner using a proportional valve (with integrated controller), a magnetically controlled switching valve and logic elements in the form of lockable/unlockable check valves.
  • a proportional valve with integrated controller
  • a magnetically controlled switching valve and logic elements in the form of lockable/unlockable check valves.
  • the unlockable check valve arranged in the short-circuit line can be hydraulically controlled when a first working line of the two working lines is pressurized. This has the advantage that the pressure caused by frictional force in the first working line can be used to open the unlockable check valve between the two working lines, so that the two working lines can be connected to one another.
  • the short-circuit line can be connected to the working lines downstream of the unlockable check valves arranged in the working lines.
  • the proportional valve can have a zero position in which the two working lines are pressure-relieved and control positions in which a hydraulic resistance between the working lines on the one hand and the pressure medium source and the pressure medium sink on the other hand can be adjusted. This means that all required hydraulic functions can be implemented with the simply constructed control arrangement.
  • a force-position control can be implemented in an actuated switching position of the switching valve and the control positions of the proportional valve
  • a regeneration circuit can be implemented in the actuated switching position of the switching valve and the control positions of the proportional valve, and in an unactuated switching position of the switching valve and the Zero position of the proportional valve can be implemented as a load holding function.
  • control electronics and power electronics for controlling the proportional valve can be mounted directly on the proportional valve. This allows a particularly compact structure to be implemented.
  • the proportional valve can be designed as an integrated axle control valve (IAC valve), so that an already existing component can be used.
  • IAC valve integrated axle control valve
  • one of the two working lines or both working lines can be connected to the pressure medium sink via a pressure control valve/pressure relief valve.
  • the first working line can be connected to the pressure medium sink via a first pressure control valve and/or the second working line can be connected to the pressure medium sink via a second pressure control valve.
  • a pressure sensor can be arranged in one of the two working lines or in both working lines. This means that a first pressure sensor is arranged in the first working line and/or a second pressure sensor is arranged in the second working line. By detecting the pressure in the working lines, force-position control can be implemented with the hydraulic control arrangement.
  • control arrangement can have a position measuring sensor for detecting the position of the actuator and the proportional valve can have an input for a signal from the position measuring sensor.
  • the proportional valve can have a position measuring sensor for detecting the position of a control piston of the proportional valve.
  • a position measuring system in which Proportional valve is integrated so that the position data of the control piston can be used for control.
  • FIG. 1 a simplified hydraulic circuit diagram of a hydraulic control arrangement.
  • Fig. 1 shows a preferred embodiment of a hydraulic control arrangement 1.
  • the control arrangement 1 is used to operate a hydraulic actuator 2.
  • the actuator 2 which is designed in particular as a differential hydraulic cylinder, can be supplied with pressure medium via a pressure medium source (not shown) and via a pressure medium source (not shown). shown) pressure medium sink can be relieved of pressure.
  • a piston-side first pressure chamber 3 of the actuator 2 is connected to a first working line 4 of the control arrangement 1 and a piston rod-side second pressure chamber 5 of the actuator 2 is connected to a second working line 6 of the control arrangement 1.
  • the actuator 2 has a displacement sensor 7 for detecting the position of the actuator 2, ie the differential hydraulic cylinder.
  • the first working line 4 and the second working line 6 can be connected to the pressure medium source via a pressure connection 8 / P connection of the control arrangement 1 or to the pressure medium sink via a tank connection 9 / T connection of the control arrangement 1.
  • the control arrangement 1 has a proportional valve/proportional directional control valve 10, which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 with the first working line 4 (A connection) or with the second working line 6 (B connection).
  • a first switching end position 11 of the proportional valve 10 the pressure connection 8 is connected to the first working line 4 and the tank connection 9 is connected to the second working line 6.
  • a second switching end position 12 of the proportional valve 10 the tank connection 9 is connected to the first working line 4 and the pressure connection 8 is connected to the second working line 6.
  • a switching center position 13 of the proportional valve 10 there is a pressureless circulation between the pressure connection 8 and the tank connection 9, and the first working line 4 and the second working line 6 are relieved towards the tank connection 9.
  • the switching center position 13 is a floating position.
  • a zero position 14 of the proportional valve 10 the first working line 4 and the second working line 6 are connected to the tank connection 9, and the pressure connection 8 is blocked.
  • the zero position 14 is a floating position.
  • the proportional valve 10 can be actuated by an electromagnet 15. When unactuated, the proportional valve 10 is in the zero position 14.
  • the proportional valve 10 has a position measuring sensor 16 for detecting the position of a control piston of the proportional valve 10.
  • the proportional valve 10 has control electronics 17.
  • the proportional valve 10 can have an input for a signal from the position measuring sensor 7.
  • the control arrangement 1 has a switching valve 18 which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 to a control line 19.
  • a switching valve 18 which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 to a control line 19.
  • the control line 19 In a first switching position 20 of the switching valve 18, the control line 19 is connected to the tank connection 9.
  • a second switching position 21 of the switching valve 18, the control line 19 is connected to the pressure connection 8.
  • the switching valve 18 can be actuated by an electromagnet 22. When not actuated, the switching valve 18 is in the first switching position 20.
  • a first check valve 23 is arranged in the first working line 4 and is arranged between the proportional valve 10 and the actuator 2.
  • the first check valve 23 enables a flow of pressure medium towards the actuator 2/from the proportional valve 10 and blocks a flow of pressure medium from the actuator 2/back to the proportional valve 10.
  • the first check valve 23 is designed to be switchable/controllable.
  • the first check valve 23 can be controlled hydraulically through the control line 19, i.e. through the switching valve 18.
  • the first check valve 23 can be unlocked, so that closing is prevented when hydraulically controlled.
  • a second check valve 24 is arranged in the second working line 6 and is arranged between the proportional valve 10 and the actuator 2.
  • the second check valve 24 enables a flow of pressure medium in the direction of the actuator 2/from the proportional valve 10 and blocks a flow of pressure medium in the direction out of the actuator 2/back to the proportional valve 10.
  • the second check valve 24 is designed to be switchable/controllable.
  • the second check valve 24 can be controlled hydraulically through the control line 19, ie through the switching valve 18.
  • the Second check valve 24 can be unlocked, so that closing is prevented when hydraulic control is used.
  • the control arrangement 1 has a short-circuit line 25, which connects the first working line 4 to the second working line 6.
  • the short-circuit line 25 is connected downstream of the first check valve 23 to the first working line 4 and connected downstream of the second check valve 24 to the second working line 6.
  • a third check valve 26 is arranged in the short-circuit line 25, which enables a pressure medium flow in the direction of the second working line 6 and blocks it in the direction back into the second working line 6.
  • the third check valve 26 is designed to be switchable/controllable.
  • the third check valve 26 can be controlled hydraulically through the control line 19, i.e. through the switching valve 18.
  • the third check valve 26 can be locked so that opening is prevented when hydraulic control is used.
  • a fourth check valve 27 is arranged in the short-circuit line 25, which enables a flow of pressure medium in the direction of the first working line 4 and blocks it in the direction back into the first working line 4.
  • the fourth check valve 27 is designed to be switchable/controllable.
  • the fourth check valve 27 can be controlled hydraulically by the first working line 4.
  • the fourth check valve 27 can be unlocked, so that closing is prevented when hydraulically controlled.
  • control arrangement 1 has a first pressure sensor 28 connected to the first working line 4 and a second pressure sensor 29 connected to the second working line 6. Furthermore, the control arrangement 1 has a first pressure relief valve 30 connecting the first working line 4 to the tank connection 9 and a second pressure relief valve 31 connecting the second working line 6 to the tank connection 9.
  • the hydraulic control arrangement 1 works according to the following mode of operation: In a first operating state, a hydraulic function of a regeneration circuit is realized, in which the hydraulic cylinder extends and the two pressure chambers 3, 5 of the hydraulic cylinder are hydraulically connected via the short-circuit line 25.
  • the proportional valve 1 is in control, that is, the proportional valve 10 connects the pressure connection 8 with the first working line 4, and the switching valve 18 is closed, ie in its first switching position 20.
  • the hydraulic cylinder moves out and can be regulated by means of force-position control through the proportional valve 10, while by the pressure caused by friction in the first working line 4 or the first pressure chamber 3 the unlockable fourth check valve 27 is opened between in the short-circuit line 25, so that the first working line 4 and the second working line 6 are connected to one another and the hydraulic cylinder can extend at a higher speed.
  • a hydraulic force-position control function is implemented.
  • the proportional valve 1 is in control, i.e. that the proportional valve 10 is not in the zero position 14, and the switching valve 18 is open, i.e. in its second switching position 21.
  • the force-position control is carried out by the proportional valve 10, in particular also by the Distance measuring sensor 16 and the input for the signal of the distance measuring sensor 7.
  • the lockable third check valve 26 is hydraulically controlled by the switching valve 18, so that the first working line 4 and the second working line 6 are separated from one another.
  • the unlockable first check valve 23 and the unlockable second check valve 24 are hydraulically controlled by the switching valve 18, so that they are open in a defined manner and four-quadrant operation is possible.
  • a hydraulic function of a load holding circuit is implemented.
  • the proportional valve 1 is not in control, i.e. that the proportional valve 10 is in the zero position 14, and the switching valve 18 is closed, i.e. in a first switching position 20.
  • the check valves 23, 24, 26, 27 are not hydraulically controlled and are located in their basic position. The connection between the first working line 4 and the second working line 6 is closed in a defined manner and the unlockable first check valve 23 and the unlockable second check valves 24 are closed in a defined manner by the load.
  • the check valves 23, 24, 26, 27 are preferably designed in a seat valve design, so that no leakage and therefore no gradual hydraulic cylinder movement is possible.

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Description

Die Erfindung betrifft eine hydraulische Steueranordnung zur Betätigung eines hydraulischen Aktuators/Verbrauchers, insbesondere eines Differential-Hydraulikzylinders, gemäß dem Oberbegriff des Patentanspruchs 1.The invention relates to a hydraulic control arrangement for actuating a hydraulic actuator/consumer, in particular a differential hydraulic cylinder, according to the preamble of patent claim 1.

Hintergrund der ErfindungBackground of the invention

Um eine lineare Antriebsanforderung über einen Aktuator, z.B. Hydraulikzylinder zu realisieren, ist es erforderlich, dass die hydraulische Steueranordnung die Funktionen einer Kraft-Positions-Regelung, eines Umschaltens zwischen einer Normal- und einer Regenerationsschaltung, eines Lasthaltens sowie einer Druck- bzw. Kraftabsicherung umsetzen kann. Dabei wird unter einer Regeneration eine Rückspeisung von Fluid von einer (Kolben-)Stangenseite des Hydraulikzylinders zu einer Kolbenseite des Hydraulikzylinders verstanden, indem die beiden Seiten fluidisch miteinander verbunden werden. Unter einer Lasthaltefunktion wird eine Sperrung der Bewegung eines Kolbens des Hydraulikzylinders verstanden.In order to implement a linear drive request via an actuator, e.g. hydraulic cylinder, it is necessary that the hydraulic control arrangement implement the functions of force-position control, switching between a normal and a regeneration circuit, load holding and pressure or force protection can. Regeneration is understood to mean a return of fluid from a (piston) rod side of the hydraulic cylinder to a piston side of the hydraulic cylinder by fluidly connecting the two sides to one another. A load holding function is understood to mean blocking the movement of a piston of the hydraulic cylinder.

Stand der TechnikState of the art

Eine intern bekannte Steueranordnung weist dafür ein Wegeventil auf, das zwei Arbeitsleitungen, die mit in entgegengesetzte Richtungen wirkenden Druckkammern des Aktuators (Hydraulikzylinders) verbunden sind, je nach Schaltstellung mit einer Druckmittelquelle oder einer Druckmittelsenke verbindet. Dabei ist in den beiden Arbeitsleitungen (Leistungsdruckleitungen) jeweils ein Rückschlagventil angeordnet, welches durch Druckbeaufschlagung der jeweils anderen Arbeitsleitung entsperrbar ist. Zudem ist in einer die beiden Arbeitsleitungen verbindenden Kurzschlussleitung ein lastabhängiges Ventil angeordnet, das zwischen den Funktionen des Lasthaltens und der Normal- und Regenerationsschaltung umschaltet. Das heißt, dass die Funktionsumschaltung ohne elektrische Steuersignale erfolgt. Nachteilig an der bekannten Steueranordnung ist jedoch, dass sie nicht bei umschaltenden Lasten einsetzbar ist, so dass ein Vier-Quadranten-Betrieb nicht möglich ist. Zudem können die gegenseitig entsperrbaren Rückschlagventile nicht klar definierte Schaltungszustände aufweisen, was die Regelfunktionalität stark beeinträchtigt. Zudem muss die Funktionsumschaltung der Normal- und Regenerationsschaltung bereits zur Projektierung bzw. bei der Inbetriebnahme mechanisch eingestellt werden.An internally known control arrangement has a directional control valve that connects two working lines, which are connected to pressure chambers of the actuator (hydraulic cylinder) acting in opposite directions, to a pressure medium source or a pressure medium sink, depending on the switching position. A check valve is arranged in each of the two working lines (power pressure lines), which can be unlocked by pressurizing the other working line. In addition, a load-dependent valve is arranged in a short-circuit line connecting the two working lines, which switches between the functions of load holding and the normal and regeneration circuit. This means that the function switching takes place without electrical control signals. However, the disadvantage of the known control arrangement is that it does not work with switching loads can be used, so that four-quadrant operation is not possible. In addition, the mutually unlockable check valves cannot have clearly defined circuit states, which severely impairs the control functionality. In addition, the function switchover of the normal and regeneration circuit must be set mechanically during project planning or during commissioning.

Eine andere intern bekannte Steueranordnung weist ebenfalls ein Wegeventil, das die zwei Arbeitsleitungen je nach Schaltstellung druckbeaufschlagt oder druckentlastet, sowie jeweils ein in den beiden Arbeitsleitungen angeordnetes Rückschlagventil auf. Ein erstes Magnetventil dient zur Entsperrung der Rückschlagventile und ein zweites Magnetventil dient zum Kurzschließen der beiden Arbeitsleitungen, so dass die Funktionen des Lasthaltens und der Normal- und Regenerationsschaltung ventilgesteuert umgeschaltet werden können. Das heißt, dass die Funktionsumschaltung mittels zweier elektrischer Steuersignalen erfolgt. Nachteilig an dieser Lösung ist jedoch, dass zwei Magnetventile benötigt werden, so dass diese Steueranordnung aufgrund der Anzahl der Magnetventile und einer erforderlichen Leistungselektronik für eine Endstufe zum Schalten kostenintensiv ist.Another internally known control arrangement also has a directional control valve, which pressurizes or relieves pressure on the two working lines depending on the switching position, as well as a check valve arranged in each of the two working lines. A first solenoid valve is used to unlock the check valves and a second solenoid valve is used to short-circuit the two working lines so that the functions of load holding and the normal and regeneration circuit can be switched valve-controlled. This means that the function switching takes place using two electrical control signals. However, the disadvantage of this solution is that two solenoid valves are required, so that this control arrangement is cost-intensive due to the number of solenoid valves and the power electronics required for an output stage for switching.

Eine weitere Steueranordnung ist aus JP2020007160A bekannt.Another tax order is out JP2020007160A known.

Kurzbeschreibung der ErfindungBrief description of the invention

Demgegenüber liegt der Erfindung die Aufgabe zugrunde, eine hydraulische Steueranordnung bereitzustellen, mit welcher die beschriebenen hydraulischen Funktionen realisierbar sind, die aber gleichzeitig einfach, kompakt und kostengünstig aufgebaut ist.In contrast, the invention is based on the object of providing a hydraulic control arrangement with which the hydraulic functions described can be implemented, but which is at the same time simple, compact and inexpensive.

Diese Aufgabe wird durch eine hydraulische Steueranordnung mit den Merkmalen des Patentanspruchs 1 gelöst. Vorteilhafte Weiterbildungen der Erfindung sind Gegenstand der Unteransprüche.This task is achieved by a hydraulic control arrangement with the features of patent claim 1. Advantageous developments of the invention are the subject of the subclaims.

Die erfindungsgemäße Steueranordnung dient zur Betätigung eines hydraulischen Aktuators, insbesondere eines Differential-Hydraulikzylinders. Die Steueranordnung weist zwei Arbeitsleitungen auf, von denen jeweils eine zur Betätigung des Aktuators mit in entgegengesetzte Richtungen wirkenden Druckkammern des Aktuators verbindbar ist und in denen jeweils ein entsperrbares Rückschlagventil angeordnet ist, deren gesperrte Durchflussrichtung aus Richtung der Druckkammern durch hydraulische Ansteuerung freigebbar ist bzw. freigegeben wird. Ferner weist die Steueranordnung ein Proportionalventil auf, durch das die beiden Arbeitsleitungen je nach (Schalt-)Stellung des Proportionalventils zur Druckbeaufschlagung der zugehörigen Druckkammer mit einer Druckmittelquelle oder zur Druckentlastung der zugehörigen Druckkammer mit einer Druckmittelsenke verbindbar sind. Zudem weist die Steueranordnung eine Kurzschlussleitung auf, welche die beiden Arbeitsleitungen unter Zwischenschaltung von zwei, entgegengesetzte Durchflussrichtungen aufweisenden Rückschlagventilen miteinander verbindet. Erfindungsgemäß ist das eine der in der Kurzschlussleitung angeordneten Rückschlagventile sperrbar und das andere der in der Kurzschlussleitung angeordneten Rückschlagventile entsperrbar ausgebildet.The control arrangement according to the invention is used to operate a hydraulic actuator, in particular a differential hydraulic cylinder. The control arrangement has two working lines, one of which can be connected to pressure chambers of the actuator acting in opposite directions for actuating the actuator and in each of which an unlockable check valve is arranged, the blocked flow direction of which can be released from the direction of the pressure chambers by hydraulic control becomes. Furthermore, the Control arrangement has a proportional valve, through which the two working lines can be connected to a pressure medium source to pressurize the associated pressure chamber with a pressure medium source or to relieve the pressure of the associated pressure chamber with a pressure medium sink, depending on the (switching) position of the proportional valve. In addition, the control arrangement has a short-circuit line which connects the two working lines with the interposition of two check valves with opposite flow directions. According to the invention, one of the check valves arranged in the short-circuit line is designed to be lockable and the other of the check valves arranged in the short-circuit line is designed to be unlockable.

Gemäß der Erfindung weist die Steueranordnung ein, vorzugsweise magnetisch gesteuertes, Schaltventil auf, durch das die in den Arbeitsleitungen angeordneten, entsperrbaren Rückschlagventile sowie das in der Kurzschlussleitung angeordnete, sperrbare Rückschlagventil in einer Schaltstellung des Schaltventils hydraulisch ansteuerbar sind.According to the invention, the control arrangement has a, preferably magnetically controlled, switching valve, through which the unlockable check valves arranged in the working lines and the lockable check valve arranged in the short-circuit line can be hydraulically controlled in a switching position of the switching valve.

Mit anderen Worten hat die Steueranordnung gemäß der vorliegenden Erfindung eine erste Arbeitsleitung, die mit einer ersten Druckkammer eines Aktuators verbindbar (oder verbunden) ist, so dass der Aktuator durch Druckbeaufschlagung der ersten Arbeitsleitung in eine erste Richtung, insbesondere in eine Ausfahrrichtung eines Hydraulikzylinders als Beispiel eines solchen Aktuators, verstellbar ist, sowie eine zweite Arbeitsleitung, die mit einer zweiten Druckkammer des Aktuators verbindbar (oder verbunden) ist, so dass der Aktuator durch Druckbeaufschlagen der zweiten Arbeitsleitung in eine zweite Richtung, insbesondere eine Einfahrrichtung des Hydraulikzylinders als Beispiel eines solchen Aktuators, verstellbar ist. Dabei ist in der ersten Arbeitsleitung ein erstes Rückschlagventil angeordnet und in der zweiten Arbeitsleitung ein zweites Rückschlagventil angeordnet, welche jeweils einen Druckmittelstrom nur in Richtung zu dem Aktuator bzw. der jeweiligen Druckkammer ermöglicht und in eine Sperrrichtung/Gegenrichtung/entgegengesetzte Richtung sperrt. Das erste und zweite Rückschlagventil sind entsperrbar ausgebildet und zwar in dem Sinne, dass die Sperrrichtung bei Druckbeaufschlagung eines Steueranschlusses des jeweiligen Rückschlagventils (gesteuert) freigegeben/entsperrt ist. Zudem hat die Steueranordnung das Proportionalventil, das zur kontinuierlichen Regelung eines hydraulischen Widerstands dient und je nach (Schalt-)Stellung die erste Arbeitsleitung bzw. zweite Arbeitsleitung zur Druckbeaufschlagung mit einer Pumpe/der Druckmittelquelle oder einem Tank/der Druckmittelsenke verbindet. Zusätzlich hat die Steueranordnung eine Kurzschlussleitung, durch welche die beiden Arbeitsleitungen fluidisch miteinander verbunden sind bzw. werden können. Dabei ermöglicht ein drittes, in der Kurzschlussleitung angeordnetes Rückschlagventil einen Druckmittelstrom in nur einer Durchflussrichtung aus der einen Arbeitsleitung in die andere Arbeitsleitung, insbesondere aus der zweiten Arbeitsleitung in die erste Arbeitsleitung, und sperrt einen Druckmittelstrom in eine Sperrrichtung/Gegenrichtung/entgegengesetzte Richtung, insbesondere aus der ersten Arbeitsleitung in die zweite Arbeitsleitung.In other words, the control arrangement according to the present invention has a first working line which is connectable (or connected) to a first pressure chamber of an actuator, so that the actuator can be moved by pressurizing the first working line in a first direction, in particular in an extension direction of a hydraulic cylinder, for example of such an actuator, is adjustable, as well as a second working line which can be connected (or is connected) to a second pressure chamber of the actuator, so that the actuator can be moved by pressurizing the second working line in a second direction, in particular a retraction direction of the hydraulic cylinder as an example of such an actuator , is adjustable. A first check valve is arranged in the first working line and a second check valve is arranged in the second working line, each of which allows a flow of pressure medium only in the direction of the actuator or the respective pressure chamber and blocks it in a blocking direction/opposite direction/opposite direction. The first and second check valves are designed to be unlockable in the sense that the blocking direction is released/unlocked (controlled) when a control port of the respective check valve is pressurized. In addition, the control arrangement has the proportional valve, which is used to continuously regulate a hydraulic resistance and, depending on the (switching) position, the first working line or second working line for pressurizing with a pump/the Pressure medium source or a tank/the pressure medium sink connects. In addition, the control arrangement has a short-circuit line through which the two working lines are or can be fluidly connected to one another. A third check valve arranged in the short-circuit line enables a pressure medium flow in only one flow direction from one working line into the other working line, in particular from the second working line into the first working line, and blocks, in particular, a pressure medium flow in a blocking direction/opposite direction/opposite direction the first work management to the second work management.

Ein viertes, in der Kurzschlussleitung angeordnetes Rückschlagventil ermöglicht einen Druckmittelstrom in nur einer Durchflussrichtung aus der anderen Arbeitsleitung in die eine Arbeitsleitung, insbesondere aus der ersten Arbeitsleitung in die zweite Arbeitsleitung, und sperrt einen Druckmittelstrom in eine Sperrrichtung/Gegenrichtung/entgegengesetzte Richtung, insbesondere aus der zweiten Leitung in die erste Leitung. Das dritte Rückschlagventil ist sperrbar ausgebildet, d.h., dass die Durchflussrichtung bei Druckbeaufschlagung eines Steueranschlusses des dritten Rückschlagventils (gesteuert) verschlossen/gesperrt ist. Das vierte Rückschlagventil ist entsperrbar ausgebildet und zwar in dem Sinne, dass die Sperrichtung bei Druckbeaufschlagung eines Steueranschlusses des vierten Rückschlagventils (gesteuert) freigegeben/entsperrt ist.A fourth check valve arranged in the short-circuit line enables a pressure medium flow in only one flow direction from the other working line into one working line, in particular from the first working line into the second working line, and blocks a pressure medium flow in a blocking direction/opposite direction/opposite direction, in particular from the second line into the first line. The third check valve is designed to be lockable, i.e. the flow direction is closed/blocked (controlled) when a control port of the third check valve is pressurized. The fourth check valve is designed to be unlockable in the sense that the blocking direction is released/unlocked (controlled) when a control port of the fourth check valve is pressurized.

Erfindungsgemäß hat die Steueranordnung ein Schaltventil, welches das erste, zweite und dritte Rückschlagventil steuert/schaltet. Das heißt, dass das Schaltventil in einer ersten Schaltstellung die Steueranschlüsse des ersten, zweiten und dritten Rückschlagventils druckentlastet, d.h. diese drei Rückschlagventile nicht (im vorstehenden Sinne) steuert, und in einer zweiten Schaltstellung die Steueranschlüsse des ersten, zweiten und dritten Rückschlagventils druckbeaufschlagt, d.h. diese drei Rückschlagventile (im vorstehenden Sinne) steuert.According to the invention, the control arrangement has a switching valve which controls/switches the first, second and third check valves. This means that in a first switching position the switching valve relieves pressure on the control connections of the first, second and third check valves, i.e. does not control these three check valves (in the above sense), and in a second switching position pressurizes the control connections of the first, second and third check valves, i.e. controls these three check valves (in the above sense).

Mit einfachen Worten gesagt, weist die erfindungsgemäße Steueranordnung (nur) ein Schaltventil auf, durch das drei der vier Rückschlagventile gleichzeitig hydraulisch angesteuert werden können.In simple words, the control arrangement according to the invention has (only) one switching valve through which three of the four check valves can be controlled hydraulically at the same time.

Der erfindungsgemäße Aufbau der Steueranordnung hat den Vorteil, dass die drei hydraulischen Funktionen einer Normalschaltung/Kraft-Positions-Regelung, einer Regenerationsschaltung und einem Lasthalten realisiert werden können und gleichzeitig nur durch ein Proportionalventil (mit integriertem Regler), ein magnetisch gesteuertes Schaltventil und Logikelementen in Form der sperrbaren/entsperrbaren Rückschlagventile definiert zwischen den hydraulischen Funktionen umgeschaltet werden kann. Somit ergibt sich ein besonders einfacher und kostengünstiger Aufbau, der sich jedoch nicht nachteilig auf die Funktionalität auswirkt. Somit kann ein hochintegrierter Aktor mit einer 3-in-2 Schaltfunktion bereitgestellt werden.The structure of the control arrangement according to the invention has the advantage that the three hydraulic functions of a normal switching/force position control, one Regeneration circuit and load holding can be implemented and at the same time can only be switched between the hydraulic functions in a defined manner using a proportional valve (with integrated controller), a magnetically controlled switching valve and logic elements in the form of lockable/unlockable check valves. This results in a particularly simple and cost-effective structure, which, however, does not have a detrimental effect on functionality. This means that a highly integrated actuator with a 3-in-2 switching function can be provided.

Gemäß einer vorteilhaften Weiterbildung der Erfindung kann das in der Kurzschlussleitung angeordnete, entsperrbare Rückschlagventil bei Druckbeaufschlagung einer ersten Arbeitsleitung der beiden Arbeitsleitungen hydraulisch angesteuert sein. Dies hat den Vorteil, dass der durch Reibkraft verursachte Druck in der ersten Arbeitsleitung genutzt werden kann, um das entsperrbare Rückschlagventil zwischen den beiden Arbeitsleitungen zu öffnen, so dass die beiden Arbeitsleitungen miteinander verbunden werden können.According to an advantageous development of the invention, the unlockable check valve arranged in the short-circuit line can be hydraulically controlled when a first working line of the two working lines is pressurized. This has the advantage that the pressure caused by frictional force in the first working line can be used to open the unlockable check valve between the two working lines, so that the two working lines can be connected to one another.

Gemäß einer vorteilhaften Weiterbildung kann die Kurzschlussleitung den in den Arbeitsleitungen angeordneten, entsperrbaren Rückschlagventilen nachgeschaltet mit den Arbeitsleitungen verbunden sein.According to an advantageous development, the short-circuit line can be connected to the working lines downstream of the unlockable check valves arranged in the working lines.

In einer bevorzugten Ausführungsform kann das Proportionalventil eine Nullstellung, in der die beiden Arbeitsleitungen druckentlastet sind, und Regelstellungen aufweisen, in denen ein hydraulischer Widerstand zwischen den Arbeitsleitungen einerseits und der Druckmittelquelle und der Druckmittelsenke andererseits einstellbar ist. Dadurch lassen sich mit der einfach aufgebauten Steueranordnung alle erforderlichen hydraulischen Funktionen realisieren.In a preferred embodiment, the proportional valve can have a zero position in which the two working lines are pressure-relieved and control positions in which a hydraulic resistance between the working lines on the one hand and the pressure medium source and the pressure medium sink on the other hand can be adjusted. This means that all required hydraulic functions can be implemented with the simply constructed control arrangement.

Gemäß einer vorteilhaften Weiterbildung kann in einer betätigten Schaltstellung des Schaltventils und den Regelstellungen des Proportionalventils eine Kraft-Positions-Regelung realisiert sein, in der betätigten Schaltstellung des Schaltventils und den Regelstellungen des Proportionalventils eine Regenerationsschaltung realisiert sein, und in einer unbetätigten Schaltstellung des Schaltventils und der Nullstellung des Proportionalventils eine Lasthaltefunktion realisiert sein.According to an advantageous development, a force-position control can be implemented in an actuated switching position of the switching valve and the control positions of the proportional valve, a regeneration circuit can be implemented in the actuated switching position of the switching valve and the control positions of the proportional valve, and in an unactuated switching position of the switching valve and the Zero position of the proportional valve can be implemented as a load holding function.

Gemäß einer vorteilhaften Weiterbildung kann eine Regelelektronik und eine Leistungselektronik zur Steuerung des Proportionalventils direkt auf das Proportionalventil montiert sein. So lässt sich ein besonders kompakter Aufbau umsetzen.According to an advantageous development, control electronics and power electronics for controlling the proportional valve can be mounted directly on the proportional valve. This allows a particularly compact structure to be implemented.

Insbesondere kann das Proportionalventil als ein integriertes Achsregelventil (IAC Ventil) ausgebildet sein, so dass eine bereits existierende Komponente genutzt werden kann.In particular, the proportional valve can be designed as an integrated axle control valve (IAC valve), so that an already existing component can be used.

In einer bevorzugten Ausführungsform kann/können eine der beiden Arbeitsleitungen oder beide Arbeitsleitungen über ein Druckregelventil/Druckbegrenzungsventil mit der Druckmittelsenke verbindbar sein. Das heißt, dass die erste Arbeitsleitung über ein erstes Druckregelventil mit der Druckmittelsenke verbindbar ist und/oder die zweite Arbeitsleitung über ein zweites Druckregelventil mit der Druckmittelsenke verbindbar ist. Durch das Vorsehen der Druckregelventile kann eine Druck- bzw. Kraftabsicherung der hydraulischen Steueranordnung erfolgen.In a preferred embodiment, one of the two working lines or both working lines can be connected to the pressure medium sink via a pressure control valve/pressure relief valve. This means that the first working line can be connected to the pressure medium sink via a first pressure control valve and/or the second working line can be connected to the pressure medium sink via a second pressure control valve. By providing the pressure control valves, the pressure or force of the hydraulic control arrangement can be secured.

In einer bevorzugten Ausführungsform kann in einer der beiden Arbeitsleitungen oder in beiden Arbeitsleitungen ein Drucksensor angeordnet sein. Das heißt, dass in der ersten Arbeitsleitung ein erster Drucksensor angeordnet ist und/oder in der zweiten Arbeitsleitung ein zweiter Drucksensor angeordnet ist. Durch die Erfassung des Drucks in den Arbeitsleitungen lässt sich eine Kraft-Positions-Regelung mit der hydraulischen Steueranordnung realisieren.In a preferred embodiment, a pressure sensor can be arranged in one of the two working lines or in both working lines. This means that a first pressure sensor is arranged in the first working line and/or a second pressure sensor is arranged in the second working line. By detecting the pressure in the working lines, force-position control can be implemented with the hydraulic control arrangement.

Gemäß einer vorteilhaften Weiterbildung kann die Steueranordnung einen Wegmesssensor zur Erfassung der Position des Aktuators aufweisen und das Proportionalventil einen Eingang für ein Signal des Wegmesssensors aufweisen. Durch die Erfassung der Position des Aktuators, insbesondere des Hydraulikzylinders, welche an das Proportionalventil übertragen wird, kann eine effiziente Kraft-Positions-Regelung umgesetzt werden.According to an advantageous development, the control arrangement can have a position measuring sensor for detecting the position of the actuator and the proportional valve can have an input for a signal from the position measuring sensor. By detecting the position of the actuator, in particular the hydraulic cylinder, which is transmitted to the proportional valve, efficient force-position control can be implemented.

Gemäß einer vorteilhaften Weiterbildung kann das Proportionalventil einen Wegmesssensor zur Erfassung der Position eines Steuerkolbens des Proportionalventils aufweisen. Das heißt, dass ein Wegmesssystem in dem Proportionalventil integriert ist, so dass die Positionsdaten des Steuerkolbens zur Regelung verwendet werden können.According to an advantageous development, the proportional valve can have a position measuring sensor for detecting the position of a control piston of the proportional valve. This means that a position measuring system in which Proportional valve is integrated so that the position data of the control piston can be used for control.

Eine bevorzugte Ausführungsform der Erfindung wird im Folgenden anhand einer schematischen Zeichnung näher erläutert. Es zeigt:
Fig. 1 einen vereinfachten Hydraulikschaltplan einer hydraulischen Steueranordnung.A preferred embodiment of the invention is explained in more detail below using a schematic drawing. It shows:
Fig. 1 a simplified hydraulic circuit diagram of a hydraulic control arrangement.

Fig. 1 zeigt eine bevorzugte Ausführungsform einer hydraulischen Steueranordnung 1. Die Steueranordnung 1 dient zur Betätigung eines hydraulischen Aktuators 2. Der Aktuator 2, der insbesondere als ein Differential-Hydraulikzylinder ausgebildet ist, ist über eine (nicht dargestellte) Druckmittelquelle mit Druckmittel versorgbar und über eine (nicht dargestellte) Druckmittelsenke druckentlastbar. Dabei ist eine kolbenseitige erste Druckkammer 3 des Aktuators 2 mit einer ersten Arbeitsleitung 4 der Steueranordnung 1 verbunden und eine kolbenstangenseitige zweite Druckkammer 5 des Aktuators 2 mit einer zweiten Arbeitsleitung 6 der Steueranordnung 1 verbunden. Der Aktuator 2 weist einen Wegmesssensor 7 zum Erfassen der Position des Aktuators 2, d.h. des Differential-Hydraulikzylinders auf. Die erste Arbeitsleitung 4 und die zweite Arbeitsleitung 6 können je nach Schaltung der Steueranordnung 1 über einen Druckanschluss 8 / P-Anschluss der Steueranordnung 1 mit der Druckmittelquelle bzw. über einen Tankanschluss 9 / T-Anschluss der Steueranordnung 1 mit der Druckmittelsenke verbunden werden. Fig. 1 shows a preferred embodiment of a hydraulic control arrangement 1. The control arrangement 1 is used to operate a hydraulic actuator 2. The actuator 2, which is designed in particular as a differential hydraulic cylinder, can be supplied with pressure medium via a pressure medium source (not shown) and via a pressure medium source (not shown). shown) pressure medium sink can be relieved of pressure. A piston-side first pressure chamber 3 of the actuator 2 is connected to a first working line 4 of the control arrangement 1 and a piston rod-side second pressure chamber 5 of the actuator 2 is connected to a second working line 6 of the control arrangement 1. The actuator 2 has a displacement sensor 7 for detecting the position of the actuator 2, ie the differential hydraulic cylinder. Depending on the circuit of the control arrangement 1, the first working line 4 and the second working line 6 can be connected to the pressure medium source via a pressure connection 8 / P connection of the control arrangement 1 or to the pressure medium sink via a tank connection 9 / T connection of the control arrangement 1.

Die Steueranordnung 1 weist ein Proportionalventil / Proportional-Wegeventil 10 auf, das je nach Schaltstellung den Druckanschluss 8 oder den Tankanschluss 9 mit der ersten Arbeitsleitung 4 (A-Anschluss) bzw. mit der zweiten Arbeitsleitung 6 (B-Anschluss) verbindet. In einer ersten Schaltendstellung 11 des Proportionalventils 10 ist der Druckanschluss 8 mit der ersten Arbeitsleitung 4 verbunden und der Tankanschluss 9 mit der zweiten Arbeitsleitung 6 verbunden. In einer zweiten Schaltendstellung 12 des Proportionalventils 10 ist der Tankanschluss 9 mit der ersten Arbeitsleitung 4 verbunden und der Druckanschluss 8 mit der zweiten Arbeitsleitung 6 verbunden. In einer Schaltmittelstellung 13 des Proportionalventils 10 herrscht zwischen dem Druckanschluss 8 und dem Tankanschluss 9 ein druckloser Umlauf, und die erste Arbeitsleitung 4 und die zweite Arbeitsleitung 6 sind zum Tankanschluss 9 hin entlastet. Die Schaltmittelstellung 13 ist eine Schwimmstellung. In einer Nullstellung 14 des Proportionalventils 10 sind die erste Arbeitsleitung 4 und die zweite Arbeitsleitung 6 mit dem Tankanschluss 9 verbunden, und der Druckanschluss 8 ist gesperrt. Die Nullstellung 14 ist eine Schwimmstellung. Das Proportionalventil 10 ist durch einen Elektromagnete 15 betätigbar. Unbetätigt befindet sich das Proportionalventil 10 in der Nullstellung 14. Das Proportionalventil 10 weist einen Wegmesssensor 16 zum Erfassen der Position eines Steuerkolbens des Proportionalventils 10 auf. Zudem weist das Proportionalventil 10 eine Ansteuerungselektronik 17 auf. Das Proportionalventil 10 kann einen Eingang für ein Signal des Wegmesssensors 7 aufweisen.The control arrangement 1 has a proportional valve/proportional directional control valve 10, which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 with the first working line 4 (A connection) or with the second working line 6 (B connection). In a first switching end position 11 of the proportional valve 10, the pressure connection 8 is connected to the first working line 4 and the tank connection 9 is connected to the second working line 6. In a second switching end position 12 of the proportional valve 10, the tank connection 9 is connected to the first working line 4 and the pressure connection 8 is connected to the second working line 6. In a switching center position 13 of the proportional valve 10, there is a pressureless circulation between the pressure connection 8 and the tank connection 9, and the first working line 4 and the second working line 6 are relieved towards the tank connection 9. The switching center position 13 is a floating position. In a zero position 14 of the proportional valve 10, the first working line 4 and the second working line 6 are connected to the tank connection 9, and the pressure connection 8 is blocked. The zero position 14 is a floating position. The proportional valve 10 can be actuated by an electromagnet 15. When unactuated, the proportional valve 10 is in the zero position 14. The proportional valve 10 has a position measuring sensor 16 for detecting the position of a control piston of the proportional valve 10. In addition, the proportional valve 10 has control electronics 17. The proportional valve 10 can have an input for a signal from the position measuring sensor 7.

Die Steueranordnung 1 weist ein Schaltventil 18 auf, das je nach Schaltstellung den Druckanschluss 8 oder den Tankanschluss 9 mit einer Steuerleitung 19 verbindet. In einer ersten Schaltstellung 20 des Schaltventils 18 ist die Steuerleitung 19 mit dem Tankanschluss 9 verbunden. In einer zweiten Schaltstellung 21 des Schaltventils 18 ist die Steuerleitung 19 mit dem Druckanschluss 8 verbunden. Das Schaltventil 18 ist durch einen Elektromagneten 22 betätigbar. Unbetätigt befindet sich das Schaltventil 18 in der ersten Schaltstellung 20.The control arrangement 1 has a switching valve 18 which, depending on the switching position, connects the pressure connection 8 or the tank connection 9 to a control line 19. In a first switching position 20 of the switching valve 18, the control line 19 is connected to the tank connection 9. In a second switching position 21 of the switching valve 18, the control line 19 is connected to the pressure connection 8. The switching valve 18 can be actuated by an electromagnet 22. When not actuated, the switching valve 18 is in the first switching position 20.

In der ersten Arbeitsleitung 4 ist ein erstes Rückschlagventil 23 angeordnet, das zwischen dem Proportionalventil 10 und dem Aktuator 2 angeordnet ist. Das erste Rückschlagventil 23 ermöglicht einen Druckmittelstrom in Richtung zu dem Aktuator 2/von dem Proportionalventil 10 und sperrt einen Druckmittelstrom aus dem Aktuator 2/zurück zu dem Proportionalventil 10. Das erste Rückschlagventil 23 ist schaltbar/steuerbar ausgebildet. Insbesondere ist das erste Rückschlagventil 23 durch die Steuerleitung 19, d.h. durch das Schaltventil 18, hydraulisch ansteuerbar. Das erste Rückschlagventil 23 ist entsperrbar, so dass ein Schließen bei hydraulischer Ansteuerung verhindert wird.A first check valve 23 is arranged in the first working line 4 and is arranged between the proportional valve 10 and the actuator 2. The first check valve 23 enables a flow of pressure medium towards the actuator 2/from the proportional valve 10 and blocks a flow of pressure medium from the actuator 2/back to the proportional valve 10. The first check valve 23 is designed to be switchable/controllable. In particular, the first check valve 23 can be controlled hydraulically through the control line 19, i.e. through the switching valve 18. The first check valve 23 can be unlocked, so that closing is prevented when hydraulically controlled.

In der zweiten Arbeitsleitung 6 ist ein zweites Rückschlagventil 24 angeordnet, das zwischen dem Proportionalventil 10 und dem Aktuator 2 angeordnet ist. Das zweite Rückschlagventil 24 ermöglicht einen Druckmittelstrom in Richtung zu dem Aktuator 2/von dem Proportionalventil 10 und sperrt einen Druckmittelstrom in Richtung aus dem Aktuator 2/zurück zu dem Proportionalventil 10. Das zweite Rückschlagventil 24 ist schaltbar/steuerbar ausgebildet. Insbesondere ist das zweite Rückschlagventil 24 durch die Steuerleitung 19, d.h. durch das Schaltventil 18, hydraulisch ansteuerbar. Das zweite Rückschlagventil 24 ist entsperrbar, so dass ein Schließen bei hydraulischer Ansteuerung verhindert wird.A second check valve 24 is arranged in the second working line 6 and is arranged between the proportional valve 10 and the actuator 2. The second check valve 24 enables a flow of pressure medium in the direction of the actuator 2/from the proportional valve 10 and blocks a flow of pressure medium in the direction out of the actuator 2/back to the proportional valve 10. The second check valve 24 is designed to be switchable/controllable. In particular, the second check valve 24 can be controlled hydraulically through the control line 19, ie through the switching valve 18. The Second check valve 24 can be unlocked, so that closing is prevented when hydraulic control is used.

Die Steueranordnung 1 weist eine Kurzschlussleitung 25 auf, welche die erste Arbeitsleitung 4 mit der zweiten Arbeitsleitung 6 verbindet. Die Kurzschlussleitung 25 ist dem ersten Rückschlagventil 23 nachgeschaltet mit der ersten Arbeitsleitung 4 verbunden und dem zweiten Rückschlagventil 24 nachgeschaltet mit der zweiten Arbeitsleitung 6 verbunden. In der Kurzschlussleitung 25 ist ein drittes Rückschlagventil 26 angeordnet, das einen Druckmittelstrom in Richtung von der zweiten Arbeitsleitung 6 ermöglicht und in Richtung zurück in die zweite Arbeitsleitung 6 sperrt. Das dritte Rückschlagventil 26 ist schaltbar/steuerbar ausgebildet. Insbesondere ist das dritte Rückschlagventil 26 durch die Steuerleitung 19, d.h. durch das Schaltventil 18, hydraulisch ansteuerbar. Das dritte Rückschlagventil 26 ist sperrbar, so dass ein Öffnen bei hydraulischer Ansteuerung verhindert wird. In der Kurzschlussleitung 25 ist ein viertes Rückschlagventil 27 angeordnet, das einen Druckmittelstrom in Richtung von der ersten Arbeitsleitung 4 ermöglicht und in Richtung zurück in die erste Arbeitsleitung 4 sperrt. Das vierte Rückschlagventil 27 ist schaltbar/steuerbar ausgebildet. Insbesondere ist das vierte Rückschlagventil 27 durch die erste Arbeitsleitung 4 hydraulisch ansteuerbar. Das vierte Rückschlagventil 27 ist entsperrbar, so dass ein Schließen bei hydraulischer Ansteuerung verhindert wird.The control arrangement 1 has a short-circuit line 25, which connects the first working line 4 to the second working line 6. The short-circuit line 25 is connected downstream of the first check valve 23 to the first working line 4 and connected downstream of the second check valve 24 to the second working line 6. A third check valve 26 is arranged in the short-circuit line 25, which enables a pressure medium flow in the direction of the second working line 6 and blocks it in the direction back into the second working line 6. The third check valve 26 is designed to be switchable/controllable. In particular, the third check valve 26 can be controlled hydraulically through the control line 19, i.e. through the switching valve 18. The third check valve 26 can be locked so that opening is prevented when hydraulic control is used. A fourth check valve 27 is arranged in the short-circuit line 25, which enables a flow of pressure medium in the direction of the first working line 4 and blocks it in the direction back into the first working line 4. The fourth check valve 27 is designed to be switchable/controllable. In particular, the fourth check valve 27 can be controlled hydraulically by the first working line 4. The fourth check valve 27 can be unlocked, so that closing is prevented when hydraulically controlled.

Zudem weist die Steueranordnung 1 einen mit der ersten Arbeitsleitung 4 verbundenen ersten Drucksensor 28 sowie einen mit der zweiten Arbeitsleitung 6 verbundenen zweiten Drucksensor 29 auf. Ferner weist die Steueranordnung 1 ein die erste Arbeitsleitung 4 mit dem Tankanschluss 9 verbindendes erstes Druckbegrenzungsventil 30 sowie ein die zweite Arbeitsleitung 6 mit dem Tankanschluss 9 verbindendes zweites Druckbegrenzungsventil 31 auf.In addition, the control arrangement 1 has a first pressure sensor 28 connected to the first working line 4 and a second pressure sensor 29 connected to the second working line 6. Furthermore, the control arrangement 1 has a first pressure relief valve 30 connecting the first working line 4 to the tank connection 9 and a second pressure relief valve 31 connecting the second working line 6 to the tank connection 9.

Die hydraulische Steueranordnung 1 arbeitet gemäß folgender Funktionsweise:
In einem ersten Betriebszustand wird eine hydraulische Funktion einer Regenerationsschaltung realisiert, bei welcher der Hydraulikzylinder ausfährt und die beiden Druckkammern 3, 5 des Hydraulikzylinders über die Kurzschlussleitung 25 hydraulisch verbunden sind. Das Proportionalventil 1 ist in Regelung, d.h., dass das Proportionalventil 10 den Druckanschluss 8 mit der ersten Arbeitsleitung 4 verbindet, und das Schaltventil 18 ist geschlossen, d.h. in seiner ersten Schaltstellung 20. Der Hydraulikzylinder fährt aus uns kann mittels Kraft-Positions-Regelung durch das Proportionalventil 10 geregelt werden, während durch den durch Reibung verursachten Druck in der ersten Arbeitsleitung 4 bzw. der ersten Druckkammer 3 das entsperrbare vierte Rückschlagventil 27 zwischen in der Kurzschlussleitung 25 geöffnet wird, so dass die erste Arbeitsleitung 4 und die zweite Arbeitsleitung 6 miteinander verbunden sind und der Hydraulikzylinder mit höherer Geschwindigkeit ausfahren kann.The hydraulic control arrangement 1 works according to the following mode of operation:
In a first operating state, a hydraulic function of a regeneration circuit is realized, in which the hydraulic cylinder extends and the two pressure chambers 3, 5 of the hydraulic cylinder are hydraulically connected via the short-circuit line 25. The proportional valve 1 is in control, that is, the proportional valve 10 connects the pressure connection 8 with the first working line 4, and the switching valve 18 is closed, ie in its first switching position 20. The hydraulic cylinder moves out and can be regulated by means of force-position control through the proportional valve 10, while by the pressure caused by friction in the first working line 4 or the first pressure chamber 3 the unlockable fourth check valve 27 is opened between in the short-circuit line 25, so that the first working line 4 and the second working line 6 are connected to one another and the hydraulic cylinder can extend at a higher speed.

In einem zweiten Betriebszustand wird eine hydraulische Funktion einer Kraft-Positions-Regelung realisiert. Das Proportionalventil 1 ist in Regelung, d.h., dass das Proportionalventil 10 nicht in der Nullstellung 14 ist, und das Schaltventil 18 ist geöffnet, d.h. in seiner zweiten Schaltstellung 21. Die Kraft-Positions-Regelung erfolgt durch das Proportionalventil 10, insbesondere auch durch den Wegmesssensor 16 und den Eingang für das Signal des Wegmesssensors 7. Das sperrbare dritte Rückschlagventil 26 ist durch das Schaltventil 18 hydraulisch angesteuert, so dass die erste Arbeitsleitung 4 und die zweite Arbeitsleitung 6 voneinander getrennt sind. Das entsperrbare erste Rückschlagventil 23 und das entsperrbare zweite Rückschlagventil 24 sind durch das Schaltventil 18 hydraulisch angesteuert, so dass sie definiert geöffnet sind und ein Vier-Quadranten-Betrieb möglich ist.In a second operating state, a hydraulic force-position control function is implemented. The proportional valve 1 is in control, i.e. that the proportional valve 10 is not in the zero position 14, and the switching valve 18 is open, i.e. in its second switching position 21. The force-position control is carried out by the proportional valve 10, in particular also by the Distance measuring sensor 16 and the input for the signal of the distance measuring sensor 7. The lockable third check valve 26 is hydraulically controlled by the switching valve 18, so that the first working line 4 and the second working line 6 are separated from one another. The unlockable first check valve 23 and the unlockable second check valve 24 are hydraulically controlled by the switching valve 18, so that they are open in a defined manner and four-quadrant operation is possible.

In einem dritten Betriebszustand wird eine hydraulische Funktion einer Lasthalteschaltung realisiert. Das Proportionalventil 1 ist nicht in Regelung, d.h., dass das Proportionalventil 10 in der Nullstellung 14 ist, und das Schaltventil 18 ist geschlossen, d.h. in einer ersten Schaltstellung 20. Die Rückschlagventile 23, 24, 26, 27 sind hydraulisch nicht angesteuert und befinden sich in ihrer Grundstellung. Die Verbindung zwischen der ersten Arbeitsleitung 4 und der zweiten Arbeitsleitung 6 ist definiert geschlossen und das entsperrbare erste Rückschlagventil 23 und das entsperrbare zweite Rückschlagventile 24 sind definiert durch die Last geschlossen. Die Rückschlagventile 23, 24, 26, 27 sind vorzugsweise in Sitzventilbauweise ausgeführt, so dass keine Leckage und somit keine schleichende Hydraulikzylinderbewegung möglich ist.In a third operating state, a hydraulic function of a load holding circuit is implemented. The proportional valve 1 is not in control, i.e. that the proportional valve 10 is in the zero position 14, and the switching valve 18 is closed, i.e. in a first switching position 20. The check valves 23, 24, 26, 27 are not hydraulically controlled and are located in their basic position. The connection between the first working line 4 and the second working line 6 is closed in a defined manner and the unlockable first check valve 23 and the unlockable second check valves 24 are closed in a defined manner by the load. The check valves 23, 24, 26, 27 are preferably designed in a seat valve design, so that no leakage and therefore no gradual hydraulic cylinder movement is possible.

Claims (10)

  1. Hydraulic control assembly (1) for actuating a hydraulic actuator (2), in particular a differential-hydraulic cylinder, with
    two working lines (4, 6), one of which can be respectively connected to pressure chambers (3, 5) of the actuator (2), acting in opposite directions, for actuating the actuator (2) and arranged in which there is respectively a pilot-operated unblockable check valve (23, 24), the blocked direction of flow of which, from the direction of the pressure chambers (3, 5), can be released by hydraulic activation;
    a proportional valve (10), by which the two working lines (4, 6) can be connected, depending on the position of the proportional valve (10), to a pressure medium source for applying pressure to the associated pressure chamber (3, 5) or to a pressure medium sink for relieving the pressure of the associated pressure chamber (3, 5); and
    a bypass line (25), which connects the two working lines (4, 6) to one another while interposing two check valves (26, 27) having opposite directions of flow, characterized in that
    one of the check valves (26) arranged in the bypass line (25) is designed to be blockable in a pilot-operated manner and the other of the check valves (27) arranged in the bypass line (25) is designed to be unblockable in a pilot-operated manner, and
    the control assembly has a switching valve (18), by which the pilot-operated unblockable check valves (23, 24) arranged in the working lines (4, 6) and the pilot-operated blockable check valve (26) arranged in the bypass line (25) are hydraulically activated in a single switching position (21) of the switching valve (18).
  2. Control assembly (1) according to Claim 1, characterized in that the pilot-operated unblockable check valve (27) arranged in the bypass line (25) is hydraulically activated when pressure is applied to a first working line (4) of the two working lines (4, 6).
  3. Control assembly (1) according to Claim 1 or 2, characterized in that the bypass line (25) is connected to the working lines (4, 6) downstream of the pilot-operated unblockable check valves (23, 24) arranged in the working lines (4, 6).
  4. Control assembly (1) according to one of Claims 1 to 3, characterized in that the proportional valve has a neutral position (14), in which the two working lines (4, 6) are relieved of pressure, and control positions (11, 12, 13), in which a hydraulic resistance between the working lines (4, 6) on the one hand and the pressure medium source and the pressure medium sink on the other hand can be set.
  5. Control assembly (1) according to Claim 4, characterized in that, in an actuated switching position (21) of the switching valve (18) and the control positions (11, 12, 13) of the proportional valve (10), a force-position control is realized, in the actuated switching position (21) of the switching valve (18) and the control positions (11, 12, 13) of the proportional valve (10) a regeneration circuit is realized, and in an unactuated switching position (20) of the switching valve (18) and the neutral position (14) of the proportional valve (10) a load-holding function is realized.
  6. Control assembly (1) according to one of Claims 1 to 5, characterized in that control electronics and power electronics for controlling the proportional valve (10) are mounted directly on the proportional valve (10).
  7. Control assembly (1) according to one of Claims 1 to 6, characterized in that one of the two working lines (4, 6) or both working lines (4, 6) can be connected to the pressure medium sink by way of a pressure control valve (30, 31).
  8. Control assembly (1) according to one of Claims 1 to 7, characterized in that a pressure sensor (28, 29) is arranged in one of the two working lines (4, 6) or in both working lines (4, 6).
  9. Control assembly (1) according to one of Claims 1 to 8, characterized in that the control assembly has a distance measuring sensor (7) for sensing the position of the actuator (2) and the proportional valve (10) has an input for a signal of the distance measuring sensor (7) .
  10. Control assembly (1) according to one of Claims 1 to 9, characterized in that the proportional valve (10) has a distance measuring sensor (16) for sensing the position of a control piston of the proportional valve (10) .
EP22186950.6A 2021-08-02 2022-07-26 Hydraulic control assembly Active EP4130493B1 (en)

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JP2009001137A (en) * 2007-06-21 2009-01-08 Shin Meiwa Ind Co Ltd Cargo handling device for container cargo handling vehicle
DE102016106616B4 (en) 2016-04-11 2023-07-06 Schwing Gmbh Electrohydraulic control circuit for a large manipulator
DE102018004769A1 (en) * 2018-06-13 2019-12-19 Hydac Mobilhydraulik Gmbh control device
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