EP3940246A1 - Agencement de soupape et procédé pour commander un dispositif de levage ou un appareil porté - Google Patents

Agencement de soupape et procédé pour commander un dispositif de levage ou un appareil porté Download PDF

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Publication number
EP3940246A1
EP3940246A1 EP21185034.2A EP21185034A EP3940246A1 EP 3940246 A1 EP3940246 A1 EP 3940246A1 EP 21185034 A EP21185034 A EP 21185034A EP 3940246 A1 EP3940246 A1 EP 3940246A1
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EP
European Patent Office
Prior art keywords
pressure
lowering
valve
directional control
active
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.)
Granted
Application number
EP21185034.2A
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German (de)
English (en)
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EP3940246B1 (fr
Inventor
Peter Schmuttermair
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP3940246A1 publication Critical patent/EP3940246A1/fr
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0402—Valve members; Fluid interconnections therefor for linearly sliding valves, e.g. spool 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
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/05—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed specially adapted to maintain constant speed, e.g. pressure-compensated, load-responsive
    • 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
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B2013/0413—Valve members; Fluid interconnections therefor with four or more positions
    • 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
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F15B2211/30515—Load holding 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
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—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
    • 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
    • F15B2211/31—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
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • 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
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • F15B2211/30—Directional control
    • F15B2211/365—Directional control combined with flow control and pressure 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
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40515—Flow control characterised by the type of flow control means or valve with variable throttles or orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/505—Pressure control characterised by the type of pressure control means
    • F15B2211/50509—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means
    • F15B2211/50518—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using pressure relief 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
    • F15B2211/50—Pressure control
    • F15B2211/515—Pressure control characterised by the connections of the pressure control means in the circuit
    • F15B2211/5159—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a 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
    • F15B2211/50—Pressure control
    • F15B2211/55—Pressure control for limiting a pressure up to a maximum pressure, e.g. by using a pressure relief 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
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—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
    • F15B2211/70—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
    • F15B2211/77—Control of direction of movement of the output member
    • F15B2211/7741—Control of direction of movement of the output member with floating mode, e.g. using a direct connection between both lines of a double-acting cylinder

Definitions

  • the invention relates to a valve arrangement for controlling a lifting mechanism or attachment according to the preamble of patent claim 1 and a method for controlling such a lifting mechanism or attachment.
  • valve arrangements are used, for example, to control the working function of mobile working devices, in particular agricultural vehicles such as tractors with power lifts, combine harvesters with a mower deck control, forage harvesters with a head control or municipal machines with power lifts.
  • tractors are designed with a rear linkage and a front linkage, with the pressure medium often being supplied according to an LS control, i.e. depending on the highest load pressure of the consumers.
  • the rear or the front linkage can each be double-acting, with the pressure chambers of a lifting cylinder of the linkage, which are effective in the "lift"/"support” or “lower”/”press” direction, for example, being connected to a pressure medium source or Can be connected to a return in order to implement the respective functions (lowering, pushing, lifting, supporting, neutral position or floating position).
  • the continuously adjustable directional valve is controlled via an electrical control unit of the work machine, with the setpoint values being set, for example, via a front control panel or a rear control panel of the work machine.
  • the two pamphlets DE 10 2017 219 942 A1 and EP 2 884 118 A1 each show generic valve arrangements in which the pressure is limited by means of a pressure-reducing valve.
  • a similar solution is in the US10321621B2 disclosed.
  • a continuously adjustable (double-acting) directional control valve suitable for controlling such hoists is in DE 10 2013 207 299 A1 shown with the directional control valve having intermediate positions for passive movement, ie movement due to gravity or the like.
  • the invention is based on the object of creating a valve arrangement and a method for controlling a mobile working device in which the pressure limitation is simplified compared to the solutions described at the outset.
  • the valve arrangement according to the invention and the method according to the invention are designed to control a lifting cylinder of a lifting gear or attachment of a mobile working device, in particular an agricultural vehicle, and has a proportionally/continuously adjustable directional control valve.
  • This has a first working connection, which is in fluid communication with a first Actuating direction (e.g. lifting) is effective pressure chamber of the lifting cylinder.
  • Another working port is in fluid communication with a second pressure chamber of the lifting cylinder that is effective in a second actuating device (e.g. lowering).
  • the directional control valve also has a return/tank connection and a pressure connection, with opening cross-sections (measuring orifices) between the connections being able to be opened or closed by adjusting a slide of the directional control valve in order to control the pressure medium supply to or from the lifting cylinder.
  • the slide is designed with two active lowering control edges, via which, when the slide is adjusted, an inflow cross section in the direction of one of the pressure chambers can be opened and at the same time, preferably in opposite directions, an outflow cross section in the pressure medium flow path from the pressure chamber in the direction of the return connection (tank). - or is controllable.
  • the slide assumes its own pressure control position, in which a dynamic pressure balance is established, which is dependent on the inflow and outflow cross-sections opened via the active-lowering control edges.
  • the pressure chamber of the cylinder that is effective in the "press"/"lower” direction is subjected to an inflowing pressure medium volume flow, with a defined outflow cross-section also being present at the same time, so that a predictable "block pressure” sets, whereby the consumer volume flow is equal to zero.
  • the “block pressure” is increased by increasing the volume flow from the pressure chamber (outflow cross section opened). If the pressure medium volume flow to the consumer is increased (enlargement of the inlet cross section), the "block pressure” is reduced accordingly.
  • the directional control valve is designed with adjustment ranges “float position” and/or “neutral” and/or “passive lowering” and/or “raise” in addition to the “active lowering” slide adjustment range described above.
  • the “active lowering” slide adjustment range can be configured adjacent to the “passive lowering” slide adjustment range. This makes it possible to form a continuous, overlapping transition between the two adjustment ranges.
  • a load-pressure-independent volume flow can be formed by configuring the valve arrangement as an LS valve arrangement with an LS pressure compensator connected upstream of the directional control valve and an LS pressure regulator of the pump.
  • a pressure-limiting valve can be provided in a pressure medium flow path between one or both working connections and the pressure chamber/pressure chambers connected thereto.
  • This pressure-limiting valve (secondary pressure-limiting valve) can intercept overpressure situations induced by disturbances, so that in such a situation pressure medium can be routed in the direction of return. This can be necessary, for example, if the lifting gear has to move upwards due to a contour in the ground.
  • the functionality of the method according to the invention and the valve arrangement according to the invention can be further improved if a position sensor is provided, via which the position of the lifting mechanism/attachment is detected.
  • the position sensor can detect the stroke of the lifting cylinder, a lifting gear angle or the like.
  • the signal from this position sensor can be used to calculate the theoretical volume flow or, alternatively, the speed of the hoist, so that control can be intervened if there are deviations from the target values. This will be discussed later.
  • a further or additional possibility for making interventions in the regulation that are necessary due to disturbances is to use a pressure sensor, via which the pressure in the respective pressure chamber of the lifting cylinder or in the pressure medium flow path leading to it is detected. Depending on the signal from this pressure sensor, the slide position can then be corrected in accordance with the control deviation via a control algorithm using a control unit. This concept is also explained in more detail in the specific description.
  • the control of the directional control valve is particularly simple if it is designed to be controlled electrohydraulically.
  • the support of the lifting cylinder in a predetermined desired position is improved if a non-return valve that can be opened is assigned to the pressure chamber that is effective in the support direction. This can be brought into the open position mechanically or hydraulically in order to allow the pressure medium to flow out. In this case, for example, the stroke of the slide can be transmitted to the check valve via a coupling mechanism in order to open it.
  • valve arrangement according to the invention can also be used with other double-acting consumers of a mobile working device.
  • lifting mechanism 2 which has a double-acting lifting cylinder 4 (also called lifting mechanism cylinder) which is controlled via a valve arrangement 6 according to the invention.
  • the lifting cylinder 4 is designed as a differential cylinder with a bottom-side pressure chamber 8 and an annular space 10 which has the Valve assembly 6 with a variable displacement pump 12 or a pressure medium sink, in the present case a tank T can be connected.
  • the lifting mechanism 2 is designed as a rear lifting mechanism, with a piston rod 14 of the lifting cylinder 4 actuating an arm 18 pivotably mounted on a lifting shaft 16 and other coupling elements on which, for example, an attachment such as a packer roller 20, a seed drill or a plow is attached .
  • the illustrated valve arrangement 6 for controlling the hoist 2 is designed as an LS control with a continuously adjustable directional control valve 22 forming a metering orifice and an LS pressure compensator 24 connected upstream thereof.
  • a continuously adjustable directional control valve 22 forming a metering orifice and an LS pressure compensator 24 connected upstream thereof.
  • LS control ensures that the pressure in front of the measuring orifice that is opened in each case is only a specific pressure difference above the individual load pressure, regardless of the pump pressure.
  • the invention in no way presupposes such an LS control.
  • the pressure connection of the variable displacement pump 12 embodied, for example, as an axial piston pump, connected via an inlet channel 26 to a pressure connection P′ of the pressure compensator 24 .
  • This is biased by a spring 28 into a basic position in which an output port D of the pressure compensator 24 is shut off.
  • the pressure in the inlet channel 26 is tapped off via a control channel 30 and guided to a control surface of the pressure compensator 24 which acts in the opening direction against the force of the spring 18 .
  • the spring 28 and the pressure in an LS channel 32 act in the opposite direction.
  • the pressure compensator 24 adjusts to a control position in which the pressure drop across the measuring orifice is kept constant and approximately corresponds to the pressure equivalent of the force of the spring 28, so that a constant pressure medium volume flow through the measuring orifice (directional valve 22) is guaranteed is.
  • the delivery pressure of the variable displacement pump 4 present in the inlet channel 26 is set in an LS control as a function of the highest load pressure present at the consumers of the tractor.
  • This load pressure--in the illustrated embodiment the load pressure on the lifting cylinder 4-- is reported to an LS pressure regulator 34, via which the variable displacement pump is set in a manner known per se.
  • an LS control in which the delivery flow of the pump is adjusted as a function of the highest load pressure, is not a prerequisite for the system according to the invention.
  • An outlet port D of the pressure compensator 24 is connected to a pressure port P of the directional control valve 22 via an inlet line 36 .
  • This also has a return port T, an LS relief port LSE and a further pressure port P′, with this and the LS relief port LSE being in fluid communication with the LS line 32 .
  • the LS discharge connection LSE is assigned an LS outlet connection LSR, which in turn is connected to the tank T via an LS return line 43 .
  • an LS pressure relief can be carried out by opening the LS return line.
  • the directional control valve 22 also has an outlet port P′′′, which is connected via a channel 38 to the pressure port P′ and thus also to the LS line 32 .
  • a working port A is connected via a working line 40 to the bottom pressure chamber 8 of the lifting cylinder 4 .
  • Another working connection B is connected via a working line 42 to the annular space 10 of the lifting cylinder 4 through which the piston rod 14 passes.
  • the directional control valve 22 is adjusted via a pilot valve arrangement 50, which is shown in accordance with FIG figure 1 is formed by two electro-hydraulic pilot elements 52, 54.
  • the control of the pilot valve arrangement 54 takes place by means of a control unit 56, which is designed with suitable control software.
  • the control oil required to control the pilot valve arrangement 50 is provided via a control oil supply 58 which is connected to the two pilot control elements 52 , 54 via a pilot line 60 .
  • the control oil required for actuating the pilot valve assembly 50 can be discharged to the tank T via the LS return line 43 .
  • the position of the slide 44 is detected by a displacement sensor 62 and reported to the control unit 56, so that the pilot valve arrangement 50 is also actuated as a function of the signal from the displacement sensor 62.
  • the spool 44 of the directional control valve 22 is biased into a neutral position N by the two centering springs 46, 48, in which the ports P, P", P'" and A are shut off.
  • the working connection B is connected to the tank connection T, so that the pressure medium can flow from the working line 42 to the tank T via a tank channel 64 .
  • the LS relief connections LSE and LSR are connected to one another, so that the LS line to tank T is also relieved.
  • a metering orifice 65 connecting the two ports P and P'" is opened, so that pressure medium can flow from the pressure port P via the port P'" and the channel 38 to the pressure port P" and then from there via the Working port A and the working line 40 in the bottom Pressure chamber 8 of the lifting cylinder 4 is funded.
  • Its annular space 10 is connected to the tank T via the working line 42, the working connection B, the tank connection T and the tank channel 64, so that the pressure medium can flow out of the decreasing annular space 10.
  • the piston of the lifting cylinder 4 extends and the implement is raised or at least supported accordingly.
  • valve slide 44 When the valve slide 44 is adjusted from its in figure 2 If the basic position shown is moved to the right, it is moved into a "sink passive (S passive ) area" in which the connections P, P'" and P" are blocked.
  • the two working ports A, B are both connected to the tank port T.
  • the LS pressure relief is also open to the LS return line 43, so that the attachment, in the present case the packer roller 20, is subjected to the lifting cylinder 4 in the retracting direction due to its own weight, so that the pressure medium from the decreasing pressure chamber 8 to the tank T is pushed out. From this, pressure medium can flow into the expanding annular space 10 .
  • the "lowering active (S active ) area” is reached, in which, similar to the lifting area, the two ports P and P′′′ are connected to one another, so that pressure medium from the supply line 36 is guided into the channel 38 via the orifice plate 65.
  • a control edge of the slide 44 opens an inflow cross section 66 between the connections P" and B.
  • a drain cross section 68 is opened via a further control edge, through which the working connection B and thus the flow in the direction " Lowering / pressing "effective annular space 10 is connected to the tank T.
  • the adjustment of the cross sections 66, 68 is preferably carried out in opposite directions.
  • a defined pressure drop occurs over this discharge cross section 68 in a specific slide deflection, with varying the slide deflection, ie by opening or closing
  • This defined pressure drop can be varied by controlling the inlet cross section 66 or the outlet cross section 68 .
  • the inflow cross section 66 and the outflow cross section 68 preferably change in opposite directions, so that when the volume flow from the consumer increases, the “block pressure” is increased, while when the volume flow to the consumer decreases, the “block pressure” is reduced.
  • a dynamic pressure equilibrium is established, as a result of which a fine adjustment of the pressure on the lifting cylinder 4 in the "lowering" direction is possible.
  • a pilot operated check valve 70 which prevents pressure medium from flowing out of the pressure chamber 8 in its closed position.
  • the check valve 70 can be opened mechanically, electrically or hydraulically when the slide 44 is moved into the “float” and “ active/passive lowering” ranges. This can be done, for example, by the slide 44 being mechanically coupled to the check valve 70 so that this is opened when the slide 44 is moved into the aforementioned ranges.
  • hydraulic or electromechanical actuation is also possible.
  • check valve 70 instead of the check valve 70, corresponding check valves can also be integrated into the directional control valve 22. These serve in particular to prevent the attachment/power lift from lowering due to a leak.
  • a pressure sensor 72 can be provided, via which the pressure in the annular space 10 or in the working line 42 is recorded and reported to the control unit 56 . If the signal from the pressure sensor 72 deviates from setpoint values, for example due to an inaccurate deflection of the slide 44 or other disturbances, the slide position can then be corrected via the control algorithm of the control unit 56 according to the control deviation.
  • the " passive lowering" area can be included in this control in order to use only one control edge opening in the "tank/return" direction without the pressure medium flowing in. This is necessary, for example, when the attachment has to move out of the way due to a rising ground contour while the pressure/ground immersion depth remains the same.
  • a secondary pressure-limiting valve 74, 76 can be provided according to the invention, via which the pressure in working line 42 or working line 40 is limited, so that the pressure medium is released when the pressure set at pressure-limiting valve 74, 76 is exceeded drains towards tank T. This can be necessary, for example, when the lifting mechanism 2 has to give way due to a ground contour, so that the pressure-limiting valve 74 in the working line 42 then opens.
  • a further option consists in detecting the deflection of the lifting cylinder 4 using a position sensor 78 .
  • this is designed as an angle sensor with which the angle of attack of the arm 18 is detected.
  • This makes it possible, for example, to increase the theoretical volume flow the "push side" (alternatively the cylinder speed/hoist speed, which are approximately proportional over large ranges). With knowledge of this theoretical volume flow, the following improvements of the system can be brought about, for example.
  • the associated advantage is better filling of the lifting cylinder 4, so that the transition to pressure control is continuous.
  • a further advantage is that when lowering the slider 44 can be deflected further without building up pressure. In this way, the single-acting lowering speed can possibly be maximized, since the control edge determining the outflow cross section 68 is then completely open.
  • a further improvement is that when evading through a ground contour, the tank drain can be opened in a controlled manner on the "push side" depending on the theoretical pressure medium volume flow and the target pressure.
  • the advantage of this is that the pressure rises only moderately when evading, even without "closed-loop pressure control", or in a system with pressure control, the controller is supported by the pilot control.
  • the upper cross-sectional course shows the opening cross-section in the above-described adjustment ranges of the slide 44 between the pressure chamber 8 ("carrying") and the return (T). Accordingly, this cross-section is opened in the two "sink areas” and is then open in the "Float".
  • the opening cross-section of the pump 12 in the direction of the pressure chamber 8 ("carrying") is only opened in the "lifting" area and decreases with increasing adjustment of the slide 44 in the "neutral” direction.
  • a defined flow cross section 68 is opened from the annular space 10 (“press”) to the return (T). This cross-section is then closed again at the transition from the "Sinking active " area to the "Float” area.
  • block pressure As shown in the detail view in FIG. 4, without a movement of the lifting mechanism 2 (consumer volume flow 0), a predictable pressure occurs in the “lowering active ” area, which is referred to as “block pressure” in this application. As mentioned above, increasing the flow of fluid from the consumer (lift cylinder 4) to the tank T increases the “block pressure”, while decreasing the flow of fluid to the consumer reduces the "block pressure”.
  • the increase in the "block pressure” can be influenced with increasing deflection and thus increasing pump quantity. This is quite evident in figure 5 shown, from which it can be seen that with increasing inflow volume and simultaneous increase in the outflow cross section 68 towards the tank T, the increase in the “block pressure” compared to the increase according to FIG figure 4 can be flattened so that the "block pressure” increases only moderately.
  • the course of the cross section when the pressure medium connection is opened from the pressure chamber 8 ("carry") to the return (T) and the course of the opening cross section from the annular space 10 ("press") to the return (T) can also be varied .
  • the full outflow cross section 68 effective in the "lowering" direction ie the cross section determining the pressure medium connection from the pressure chamber 8 to the tank T, must already be set to a maximum before the in figure 6 pressure control range indicated by dashed lines is reached.
  • these areas can also overlap each other more or less.
  • a valve arrangement and a method for controlling a lifting mechanism or attachment of a mobile working device are disclosed, with a double-acting lifting cylinder being controlled via a directional control valve.
  • This is designed with two control edges, which simultaneously change an inflow cross section and an outflow cross section, so that, for example, a pressure setting on the lifting cylinder in the "lowering" direction is possible.

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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)
EP21185034.2A 2020-07-16 2021-07-12 Agencement de soupape et procédé pour commander un dispositif de levage ou un appareil porté Active EP3940246B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102020208922.1A DE102020208922B3 (de) 2020-07-16 2020-07-16 Ventilanordnung

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EP3940246B1 EP3940246B1 (fr) 2025-02-26

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Families Citing this family (3)

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Publication number Priority date Publication date Assignee Title
DE102022202288A1 (de) 2022-03-08 2023-09-14 Robert Bosch Gesellschaft mit beschränkter Haftung Arbeitsvorrichtung mit einem Ventil, welches wenigstens eine gesonderte Entleerstellung hat
DE102022211400A1 (de) 2022-10-27 2024-05-02 Robert Bosch Gesellschaft mit beschränkter Haftung Verfahren zum Betreiben eines hydraulischen Antriebssystems
CN115407647B (zh) * 2022-10-31 2023-01-24 艾坦姆流体控制技术(山东)有限公司 一种优化控制方法及使用该方法的三级打孔阀控制系统

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DE19510331A1 (de) * 1994-03-29 1995-10-05 Bucher Gmbh Ansteuerung für ein Wegeventil in einem hydraulischen Antriebssystem
EP1281872A1 (fr) * 2001-08-04 2003-02-05 Robert Bosch Gmbh Dispositif electro-hydraulique pour le contrôle d'un moteur à double effet
DE102004033315A1 (de) 2004-07-09 2006-02-09 Bosch Rexroth Aktiengesellschaft Hubwerksventilanordnung
EP2064933A1 (fr) * 2007-11-28 2009-06-03 Robert Bosch GmbH Entraînement de roulement pour appareils de travail
DE102013207299A1 (de) 2013-04-23 2014-10-23 Robert Bosch Gmbh Hydraulisches Wegeventil für das Hubwerk eines landwirtschaftlichen Fahrzeugs
EP2884118A1 (fr) 2013-10-30 2015-06-17 AGCO International GmbH Système d'alimentation hydraulique
DE102006004423B4 (de) 2006-01-31 2018-08-02 Robert Bosch Gmbh Ventilanordnung zur Ansteuerung eines Hubwerkes oder Anbaugerätes sowie Verfahren zur Ansteuerung dieser
DE102017219942A1 (de) 2017-11-09 2019-05-09 Robert Bosch Gmbh Ventilanordung für Hubwerkssteuerung mit einer Druckregelvorrichtung
US10321621B2 (en) 2016-08-11 2019-06-18 Deere & Company Electronic latching circuit

Family Cites Families (1)

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Publication number Priority date Publication date Assignee Title
EP2597210B1 (fr) 2011-11-23 2016-03-16 HAWE Hydraulik SE Dispositif de commande hydroélectrique

Patent Citations (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19510331A1 (de) * 1994-03-29 1995-10-05 Bucher Gmbh Ansteuerung für ein Wegeventil in einem hydraulischen Antriebssystem
EP1281872A1 (fr) * 2001-08-04 2003-02-05 Robert Bosch Gmbh Dispositif electro-hydraulique pour le contrôle d'un moteur à double effet
DE10138389A1 (de) 2001-08-04 2003-02-20 Bosch Gmbh Robert Elektrohydraulische Einrichtung zur Steuerung eines doppelt wirkenden Motors
DE102004033315A1 (de) 2004-07-09 2006-02-09 Bosch Rexroth Aktiengesellschaft Hubwerksventilanordnung
DE102006004423B4 (de) 2006-01-31 2018-08-02 Robert Bosch Gmbh Ventilanordnung zur Ansteuerung eines Hubwerkes oder Anbaugerätes sowie Verfahren zur Ansteuerung dieser
EP2064933A1 (fr) * 2007-11-28 2009-06-03 Robert Bosch GmbH Entraînement de roulement pour appareils de travail
DE102013207299A1 (de) 2013-04-23 2014-10-23 Robert Bosch Gmbh Hydraulisches Wegeventil für das Hubwerk eines landwirtschaftlichen Fahrzeugs
EP2884118A1 (fr) 2013-10-30 2015-06-17 AGCO International GmbH Système d'alimentation hydraulique
US10321621B2 (en) 2016-08-11 2019-06-18 Deere & Company Electronic latching circuit
DE102017219942A1 (de) 2017-11-09 2019-05-09 Robert Bosch Gmbh Ventilanordung für Hubwerkssteuerung mit einer Druckregelvorrichtung

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