EP2910796B1 - Assemblage avec un dispositif de vanne de commande à position flottante - Google Patents

Assemblage avec un dispositif de vanne de commande à position flottante Download PDF

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Publication number
EP2910796B1
EP2910796B1 EP15153740.4A EP15153740A EP2910796B1 EP 2910796 B1 EP2910796 B1 EP 2910796B1 EP 15153740 A EP15153740 A EP 15153740A EP 2910796 B1 EP2910796 B1 EP 2910796B1
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EP
European Patent Office
Prior art keywords
line
pressure
valve
hydraulic cylinder
control
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Application number
EP15153740.4A
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German (de)
English (en)
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EP2910796A1 (fr
EP2910796B9 (fr
Inventor
Wolfgang Kraft
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Linde Hydraulics GmbH and Co KG
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Linde Hydraulics GmbH and Co KG
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Publication of EP2910796B9 publication Critical patent/EP2910796B9/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
    • 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
    • F15B2013/0412—Valve members; Fluid interconnections therefor with three 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
    • F15B2211/3052—Shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—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
    • 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
    • F15B2211/3144—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
    • F15B2211/329—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
    • F15B2211/50—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
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/575—Pilot 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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6057—Load sensing circuits having valve means between output member and the load sensing circuit using directional control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/635—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements
    • F15B2211/6355—Circuits providing pilot pressure to pilot pressure-controlled fluid circuit elements having valve means
    • 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
    • F15B2211/67—Methods for controlling pilot pressure

Definitions

  • the invention relates to an arrangement with a control valve device for controlling a double-acting hydraulic cylinder of a mobile working machine, wherein the control valve means comprises a throttling in intermediate positions control valve which is connected to a delivery line of a pump, to a container line, to a Anhebe admir, with an elevation side of the hydraulic cylinder in combination is connected, and connected to a lowering line, which communicates with a Absenkseite the hydraulic cylinder in communication, wherein the control valve is a neutral position in which the connection of the pump line and the container line with the lever line and the Absenk effet is shut off, a lifting position in which the Delivery line with the lifting lever and the lowering line is connected to the container line, and has a lowered position, in which the delivery line to the lowering and the Anhebetechnisch is connected to the container line, wherein the Steuerventileinric heht has a floating position for the hydraulic cylinder, wherein in the floating position of the hydraulic cylinder, the control valve is operated in the lowered position in which
  • control valve devices In generic control valve devices is connected to the floating position of the control valve device in which the Absenkseite and the lifting side of the hydraulic cylinder connected to the container, achieved with a corresponding load on the hydraulic cylinder energy-saving lowering of the hydraulic cylinder without pump flow. With the floating position of the control valve device is also allowed that lowered to the bottom surface working equipment of the machine can follow the bumps.
  • a variable in the set pressure Verich ceremoniessventil is provided, which is associated with the Absenktechnisch and is adjusted in the floating position to a minimum set pressure to in the floating position also the Absenkseite the hydraulic cylinder with the Container to connect.
  • the forwarding of the load pressure signal of the hydraulic cylinder to a delivery volume adjusting device of the pump is also interrupted, so that the pump delivers only a minimum delivery flow in the floating position of the control valve device.
  • a generic arrangement is from the DE 103 49 714 A1 known.
  • the present invention has for its object to provide a control valve device of the type mentioned available, which allows a low-cost and low cost a floating position and allows reduction of power loss in the lifting operation of the hydraulic cylinder.
  • This object is achieved in that the control valve device has a arranged in the connection of the delivery line of the pump with the Absenkseite of the hydraulic cylinder pressure compensator, wherein in the floating position of the hydraulic cylinder, the pressure compensator is actuated by a pressure signal in a locking position.
  • the already existing for the floating position relief valve by means of the Absenkseite the hydraulic cylinder, bypassing the control valve is connected to the container is also used to connect the lifting side of the hydraulic cylinder in the lifting operation of the hydraulic cylinder, bypassing the control valve to the container.
  • With the already existing relief valve can thus in the lifting operation of the hydraulic cylinder of the back pressure in the Absenkseite reduced the hydraulic cylinder and thus the energy losses and thus the power loss in lifting operation can be reduced.
  • Due to the multiple use of the relief valve for connecting the Absenkseite the hydraulic cylinder with the container thus a floating position of the hydraulic cylinder and a reduction of the back pressure in the lifting operation of the hydraulic cylinder can be achieved with low construction costs and low cost.
  • the relief valve is designed as a switching valve with a blocking position and a flow position, wherein the relief valve is actuated in the floating position and when lifting the hydraulic cylinder in the flow position.
  • a relief valve has a low construction cost, so that the discharge of the Absenkseite the hydraulic cylinder for the floating position and for reducing the back pressure in lifting operation is achieved with low construction costs.
  • the relief valve is configured as adjustable in the setting pressure and variable safety valve that connects the lowering of the hydraulic cylinder with the container, the safety valve in the floating position and in the lifting operation of the hydraulic cylinder to a minimum set pressure adjustable is.
  • a variable in the setting pressure protection valve can also be achieved with low construction costs to connect the Absenkseite the hydraulic cylinder on the opening safety valve with the container, so that the discharge of the Absenkseite the hydraulic cylinder for the floating position and for reducing the back pressure in lifting operation also with low construction costs are achieved.
  • the safety valve is designed as a pressure limiting valve or combined pressure limiting valve. and Nachsaugeventil formed, wherein the set pressure of the pressure limiting valve is adjustable and variable.
  • the set pressure of the pressure limiting valve is adjustable and variable.
  • the relief valve is particularly advantageously arranged in a bypass line connecting the lowering line to the tank line, a throttle device being arranged downstream of the connection of the bypass line to the tank line in the tank line.
  • generic control valve devices are provided with two relief valves, one of which communicates with the lift line and is disposed in a bypass valve bypassing the control valve, which is connected to the reservoir line connected to the control valve and the other communicates with the drawdown line and disposed in a bypass passage bypassing the control valve, which is also connected to the tank line connected to the control valve.
  • the relief valves serve to protect the maximum operating pressure in the lifting line and the lowering line.
  • the relief valve may be arranged in a branch line guided from the lowering line to the container.
  • an additional relief valve which is arranged in a guided from the Absenkön to the container branch line, the connection of the Absenkseite of the hydraulic cylinder is achieved with the container in the floating position and in lifting operation with little additional construction costs for the relief valve.
  • the relief valve is actuated in response to a control signal acting in the direction of the lifting position control signal and / or in response to a floating position signal in a lowering position of the hydraulic cylinder with the container connecting position.
  • the safety valve in response to the control valve in the direction of the lifting position driving control signal and / or in response to the floating position signal in the direction of a reduction of the set pressure adjustable.
  • the relief valve may be electrically actuated according to an embodiment of the invention.
  • the operating states floating position and lifting operation with reduced back pressure can be detected, for example, by means of appropriate sensors or by the operation of an operating device, such as a joystick, to actuate the relief valve accordingly.
  • an electronic control device is provided for this purpose, which controls the relief valve and is in communication with the sensors or the operating device.
  • the relief valve is hydraulically actuated.
  • the safety valve can advantageously be hydraulically changed in the setting pressure for this purpose.
  • the control signal is expediently designed as a hydraulic control pressure, which is present in a control pressure line of the control valve.
  • the floating position signal is expediently designed as a hydraulic actuating pressure, which is present in a control line.
  • the hydraulic actuation of the relief valve can be achieved with a simple construction, when an actuator of the relief valve is connected to a control line which is connected to the output of a shuttle valve device, wherein a first input of the shuttle valve device is connected to the hydraulic control pressure leading control pressure line and a second input the shuttle valve device is connected to the hydraulic actuation pressure leading control line.
  • a two-position switching valve which controls the admission of the actuating device with the actuating pressure.
  • the two-position switching valve relieves the control line to the container in a first switching position and connects in the second switching position, the control line with an actuating pressure source.
  • the actuating device is preferably designed as a setting pressure changing device.
  • the two-position switching valve can be made electrically or hydraulically actuated.
  • the pressure signal is formed by the delivery pressure of the pump.
  • the pressure balance in normal operation of the load pressure and a spring in the direction the blocking position and is actuated by the delivery pressure of the pump in the direction of the flow position can be operated for the floating position in a simple manner in the blocking position, when instead of the load pressure of the delivery pressure of the pump is guided to an acting in the blocking position control surface of the pressure compensator.
  • the application of the force acting in the direction of the blocking position control surface of the pressure balance of the load pressure or the delivery pressure can be controlled with low construction costs, if the pressure compensator has a control position acting in the direction of a blocking position, with a load pressure signal line is in communication, wherein the two-position switching valve in the first switching position connects the load pressure signal line with a load pressure signaling line, which is guided to a flow control of a load-sensing variable displacement pump, and in the second switching position connects the load pressure signal line with a signal line carrying the pressure signal.
  • the pressure compensator In the first switching position of the two-position switching valve thus the pressure compensator is controlled in the direction of the blocking position of the load pressure signal and operates in the normal manner for load-independent operation of the hydraulic cylinder.
  • the two-position switching valve is actuated in the second switching position, so that the connection of the delivery line of the pump to the Absenkseite of the hydraulic cylinder is shut off by means of the operated in the blocking position pressure compensator.
  • the signal line is connected to the delivery line of the pump.
  • FIG. 1 shows the circuit diagram of a load-sensing controlled drive system AS, for example, designed as an excavator or wheel loader mobile machine with a control valve device SV according to the invention.
  • the drive system AS comprises an adjustable in the delivery volume pump 1, which is operated in the illustrated embodiment in the open circuit and the input side is in communication with a container 2 and the output promotes in a delivery line 3, to which several consumers are connected.
  • a designed as a double-acting hydraulic cylinder 4 consumer is shown, for the control of a control valve device SV according to the invention is provided.
  • the control valve device SV comprises a control valve 5 which throttles in intermediate positions.
  • the lifting side A is connected to the control valve 5 by means of a lifting line 6a.
  • the Absenkseite B is connected by means of a lowering line 6b to the control valve 5.
  • the control valve 5 is further connected to the delivery line 3 of the pump 1 and communicates by means of container branch lines 8a, 8b, which are connected to a container line 8, with the container 2 in connection.
  • the lifting side A is formed by the piston-side pressure chamber of the hydraulic cylinder 4 and the Absenkseite B from the piston rod-side pressure chamber of the hydraulic cylinder 4th
  • the control valve 5 designed as a directional control valve has a neutral position N, in which the connection of the delivery line 3 of the pump 1 and the connection of the container line 8 to the lifting line 6a and the lowering line 6b are shut off.
  • a lifting position H of the control valve 5 the conveying line 3 is connected to the lifting line 6a and the lowering line 6b is connected to the container branch line 8b.
  • a lowering position S of the control valve 5 the lowering line 6b is connected to the conveying line 3 and the lifting line 6a is connected to the container branch line 8a.
  • the control valve 5 has in the lifting position H an orifice plate, not shown, and is provided with a downstream of the orifice arranged pressure compensator 11a.
  • the control valve 5 also has in the Suction position S an orifice plate, not shown, and is provided with a downstream of the orifice arranged pressure compensator 11b.
  • valves control valves for controlling other consumers of the drive system are connected to the delivery line 3, the container line 8 and the load pressure signaling line 21 accordingly.
  • the construction of the pressure compensators 11a and 11b is based on the FIG. 2 described in more detail, in which the control valve SV of the FIG. 1 is shown in an enlarged view.
  • the pressure compensator 11a arranged in the lifting position H in the flow path from the conveying line 3 to the lifting line 6a has a flow-through position 12a and a blocking position 12b.
  • the pressure compensator 11a In the direction of the flow position 12a, the pressure compensator 11a is acted upon by the delivery pressure present downstream of the metering orifice.
  • the pressure compensator 11a In the direction of the blocking position 12b, the pressure compensator 11a is acted upon by the highest load pressure of the driven consumers.
  • the lift side A load pressure signal path formed by the load pressure signal line 20a starts downstream of the pressure compensator 11a at a branch where the load pressure signal line 20a branches off from the lift side A lift path. From the load pressure signal line 20a, a control line 13a branches off to a control pressure surface of the pressure compensator 11a which acts in the direction of the blocking position 12b.
  • the pressure compensator 11b arranged in the lowering position S in the flow path from the delivery line 3 to the lowering line 6b has a throughflow position 12a and a blocking position 12b.
  • the Pressure compensator 11a acted upon by the pending downstream of the metering orifice delivery pressure.
  • the pressure compensator 11a is acted upon by the highest load pressure of the driven consumers.
  • the load pressure signal path of the lowering side B formed by the load pressure signal line 20b starts downstream of the pressure compensator 11a at a branch where the load pressure signal line 20b branches off from the flow path of the lowering side B. From the load pressure signal line 20b, a control line 13b branches off to a control pressure surface of the pressure compensator 11b which acts in the direction of the blocking position 12b.
  • the pump 1 has an adjusting device 25 for controlling the delivery quantity, for example an inclinable swashplate of an axial piston pump which is operatively connected to an actuating piston device 26 for actuation.
  • the adjusting piston device 26 has a control pressure chamber 26a which acts in the direction of an increase in the delivery rate of the pump 1 and which is acted upon by the delivery pressure of the pump 1.
  • a guided to the delivery line 3 control line 3b is provided.
  • a spring device 27 can continue to act.
  • a control pressure space 26b of the control piston line 26 which acts in the direction of a reduction in the delivery rate of the pump 1 can be controlled by means of a delivery flow regulator 30 designed as a demand flow control valve.
  • the delivery flow regulator 30 connects the control pressure chamber 26b to the container 2.
  • the control pressure chamber 26b is connected to the delivery line of the pump 1 and thus acted upon by the delivery pressure of the pump 1.
  • the delivery flow regulator 30 is acted upon by the delivery pressure of the pump 1 in the direction of the second control position 30b.
  • the first control position 30a of the flow controller 30 is acted upon by the present in the load pressure reporting line 21 highest load pressure of the driven loads and a spring means 31 whose bias corresponds to the control pressure difference of the load-sensing system.
  • the control valve 5 can be actuated by means of a drive signal X in the direction of the lifting position H and by means of a drive signal Y in the direction of the lowering position S.
  • the Drive signal X is formed by a hydraulic control pressure, which is present in a control pressure line 35 a, which is in communication with a corresponding control surface of the control valve 5.
  • the drive signal Y is correspondingly formed by a hydraulic control pressure, which is present in a control pressure line 35b which is in communication with a corresponding control surface of the control valve 5.
  • the control valve device SV is provided for maximum pressure protection of the hydraulic cylinder with safety valves 40a, 40b.
  • the check valve 40a is disposed in a bypass line 41a connecting the lift line 6a to the tank branch line 8a, bypassing the control valve 5.
  • the check valve 40b is disposed in a bypass passage 41b connecting the lowering passage 6b to the tank branch passage 8b and bypassing the control valve 5. Downstream of the connection of the bypass line 41b to the container line 8 and downstream of the connection of the bypass line 41a to the container line 8, a throttle device 42 is arranged in the container line 8.
  • the hedging valves 40a, 40b are formed in the illustrated embodiment as a combined pressure relief and Nachsaugeventile.
  • the control valve device SV further has a floating position for the hydraulic cylinder 4, in which the lifting side A and the Absenkseite B of the hydraulic cylinder 4 are connected to the container 2.
  • the control valve 5 is actuated in the lowering position S, in which the lifting line 6a connected to the container branch line 8a and thus the container line 8.
  • connection of the pump 1 with the Absenkseite B of the hydraulic cylinder 4 is also ineffective.
  • pressure compensator 11b is actuated by a pressure signal in the blocking position 12b.
  • the load pressure signal line 20b which is connected in the lowering position S of the control valve 5 with the acting in the direction of the blocking position 12b control surface of the pressure compensator 11b, connected to a two-position switching valve 50.
  • the Switching valve 50 has a first switching position 50a, in which the load pressure signal line 20b is connected to the load pressure signaling line 21, which is guided to the flow regulator 30 of the load-sensing variable displacement pump 1.
  • the switching valve 50 has a second switching position 50b, in which the load pressure signal line 20b is connected to a signal line 51 carrying the pressure signal.
  • the pressure signal is formed by the delivery pressure of the pump 1, to which the signal line 51 is connected to the delivery line 3 of the pump 1.
  • the two-position switching valve 50 is actuated by means of a spring 52 in the first switching position 50a and can be switched by means of an actuator 53 in the second switching position 50b. In the floating position of the control valve SV, the two-position switching valve 50 is actuated in the second switching position 50b.
  • the two-position switching valve 50 is electrically actuated, for which the actuator 53 is formed by a magnet, such as a solenoid, which is in communication with an electronic control device not shown in detail.
  • control valve device 5 In order to connect the lowering line 6b to the container 2 in the floating position, the control valve device 5 is provided with a relief valve 60, by means of which in the floating position the Absenkseite B of the hydraulic cylinder 4, bypassing the control valve 5 is connected to the container 2.
  • the control valve 5 is actuated in the lifting position H, in which the conveying line 3 is connected to the lifting line 6a.
  • the Absenkseite B of the hydraulic cylinder 4 is connected to the container 2 in the lifting operation of the hydraulic cylinder 4, so that the Absenktechnisch 6 b of the hydraulic cylinder 4 via the relief valve 60 communicates with the container 2 and from the Absenkseite B of the hydraulic cylinder 4 flowing out pressure medium flow through the relief valve 60 and thus flows, bypassing the control valve 5 to the container 2.
  • the relief valve 60 is arranged in a branch line 6c guided from the lowering line 6b to the container 2.
  • the relief valve 60 is configured as a variable pressure setting valve 61 which connects the lowering passage 6b of the hydraulic cylinder 4 to the reservoir 2.
  • the safety valve 61 is adjustable to a minimum setting pressure both in the floating position and in the lifting operation of the hydraulic cylinder 4.
  • the safety valve 61 is formed in the illustrated embodiment as a combined pressure limiting and Nachsaugeventil 62, wherein the set pressure of the pressure relief valve is adjustable and variable.
  • the safety valve 61 is set by means of a spring device 63 to a maximum setting pressure.
  • the bias of the spring device 63 is variable and thus the set pressure of the safety valve 61 adjustable.
  • the safety valve 61 In order to adjust the safety valve 61 to the minimum setting pressure both in the floating position and in the lifting operation, the safety valve 61 is in the direction of a reduction as a function of the control signal X driving the control valve 5 in the lifting position and / or in response to a floating position signal Z. the set pressure adjustable.
  • the safety valve 61 is hydraulically variable in the set pressure.
  • the drive signal X is designed as a hydraulic drive pressure, which is present in the control pressure line 35a.
  • the floating position signal Z is designed as a hydraulic actuating pressure which is present in a control line 70.
  • the control line 70 is in this case with an actuating pressure source 71 in Connection, for example, a control pressure pump or feed pump of the drive system AS.
  • the actuator 65 of the safety valve 61 is connected to a control line 75 which is connected to the output of a shuttle valve 76 ,
  • a first input of the shuttle valve device 76 is connected by means of a branch line 77 to the hydraulic control pressure and thus the drive signal X leading control pressure line 35a.
  • a second input of the shuttle valve device 76 is connected to the hydraulic actuation pressure Z leading control line 70.
  • the actuation of the actuator 65 is formed by the actuating pressure in the control line 70 floating position signal Z by means of the two-position switching valve 50 controllable.
  • the section of the control line 70 which is in communication with the actuating pressure source 71 is shut off and the section of the control line 70 communicating with the second input of the shuttle valve device 76 is relieved to the container 2.
  • the control line 70 is opened, so that the floating position signal Z is present at the second input of the shuttle valve device 76.
  • control valve 5 is arranged together with the safety valves 40a, 40b in a control valve housing 80.
  • the required for activating and deactivating the floating position two-position switching valve 50 is disposed in a housing or a mounting plate 81 which is flanged to the control valve housing 80.
  • the relief valve 60 is disposed in a housing or mounting plate 82 which is also flanged to the control valve housing 80.
  • FIG. 3 a second embodiment of the invention is shown.
  • the same components are provided with the same reference numbers.
  • the inventive control valve SV of the FIGS. 1 to 3 works as follows.
  • the two-position switching valve 50 is not activated and is in the first switching position 50 a, in which the floating position is deactivated.
  • the control signal X acts on the control valve 5 in the direction of the lifting position H and is via the shuttle valve 76 in the An Kunststoff 75, whereby the adjusting pressure adjustable in the check valve 40 b ( FIG. 3 ) or 61 ( FIGS. 1 and 2 ) is adjusted by the drive signal X in the direction of a reduction of the set pressure.
  • the safety valve 40b or 61 is open, a bypass circuit can be achieved with which the lowering side B of the hydraulic cylinder 4 is connected to the container 2, bypassing the control valve 5.
  • the control valve 5 is actuated by the drive signal Y in the lowering position S and the two-position switching valve 50 is actuated in the second switching position 50b.
  • the in the delivery line 3 of the pump. 1 Pending discharge pressure is thus in the load pressure signal line 20b and acts on the pressure compensator 11b in the blocking position 12b.
  • the forwarding of the load pressure of the hydraulic cylinder 4 to the load pressure signaling line 21 and thus to the flow controller 30 of the pump 1 is interrupted in the second switching position 50b of the two-position switching valve 50, so that the pump 1 remains in a position with a minimum flow.
  • the invention is not limited to the illustrated embodiments.
  • the two-position switching valve 50 may alternatively be operated hydraulically, for example by a hydraulic pilot pressure.
  • the drive signal X and the floating position signal Z can be detected by sensors or the operation of the relief valve 60 for the floating position or in the lifting operation of the hydraulic cylinder 4th directly from the actuation and the actuating signals of an operating device, for example a joystick, with which the lifting operation and the floating position can be controlled, can be detected.

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

Claims (21)

  1. Assemblage avec une pompe (1), un réservoir (2), un cylindre hydraulique à double effet (4) et un dispositif de vanne de commande (SV) pour la commande du cylindre hydraulique à double effet (4) d'une machine de travail mobile, dans lequel le dispositif de vanne de commande (SV) comprend une vanne de commande (5) à étranglement dans des positions intermédiaires, qui est raccordée à une conduite de refoulement (3) de la pompe (1), à une conduite de réservoir (8), à une conduite d'élévation (6a), qui est en communication avec un côté d'élévation (A) du cylindre hydraulique (4), et avec une conduite de descente (6b), qui est en communication avec un côté de descente (B) du cylindre hydraulique (4), dans lequel la vanne de commande (5) présente une position neutre (N), dans laquelle la communication de la conduite de pompe (3) et de la conduite de réservoir (8) avec la conduite d'élévation (6a) et avec la conduite de descente (6b) est fermée, une position d'élévation (H), dans laquelle la conduite de refoulement (3) est reliée à la conduite d'élévation (6a) et la conduite de descente (6b) est reliée à la conduite de réservoir (8), et une position de descente (S), dans laquelle la conduite de refoulement (3) est reliée à la conduite de descente (6b) et la conduite d'élévation (6a) est reliée à la conduite de réservoir (8), dans lequel le dispositif de vanne de commande (SV) présente une position flottante pour le cylindre hydraulique (4), dans lequel, dans la position flottante du cylindre hydraulique (4), la vanne de commande (5) est actionnée dans la position de descente (S), dans laquelle la conduite d'élévation (6a) est reliée à la conduite de réservoir (8), et la communication de la pompe (1) avec le côté de descente (B) du cylindre hydraulique (4) est connectée sans effet, dans lequel il est prévu une vanne de délestage (60), au moyen de laquelle le côté de descente (B) du cylindre hydraulique (4) peut être relié au réservoir (2) avec contournement de la vanne de commande (5), dans lequel dans la position flottante le côté de descente (B) du cylindre hydraulique (4) est relié au réservoir (2) au moyen de la vanne de délestage (60), dans lequel en fonctionnement d'élévation du cylindre hydraulique (4) la vanne de commande (5) est actionnée dans la position d'élévation (H), dans laquelle la conduite de refoulement (3) est reliée à la conduite d'élévation (6a), et en fonctionnement d'élévation du cylindre hydraulique (4) le côté de descente (B) du cylindre hydraulique (4) peut être relié au réservoir (2) au moyen de la vanne de délestage (60), de telle manière que la conduite de descente (6b) du cylindre hydraulique (4) soit en communication avec le réservoir (2) par l'intermédiaire de la vanne de délestage (60) et que le courant volumétrique de fluide sous pression s'écoulant hors du côté de descente (B) du cylindre hydraulique (4) s'écoule vers le réservoir (2) par l'intermédiaire de la vanne de délestage (60), caractérisé en ce que le dispositif de vanne de commande (5) présente une balance de pression (11b) disposée dans la communication de la conduite de refoulement (3) de la pompe (1) avec le côté de descente (B) du cylindre hydraulique (4), dans lequel, dans la position flottante du cylindre hydraulique (4), la balance de pression (11b) est actionnée dans une position d'arrêt (12b) au moyen d'un signal de pression.
  2. Assemblage selon la revendication 1, caractérisé en ce que la vanne de délestage (60) est formée par une vanne de commutation avec une position d'arrêt et une position de passage, dans lequel la vanne de délestage est actionnée dans la position de passage dans la position flottante et lors de l'élévation du cylindre hydraulique (4).
  3. Assemblage selon la revendication 1, caractérisé en ce que la vanne de délestage (60) est formée par une vanne de protection (40b; 61) réglable en pression de réglage et variable, qui relie la conduite de descente (6b) du cylindre hydraulique (4) au réservoir (2), dans lequel la vanne de protection (40b; 61) peut être réglée à une pression de réglage minimale dans la position flottante et en fonctionnement d'élévation du cylindre hydraulique (4).
  4. Assemblage selon la revendication 3, caractérisé en ce que la vanne de protection (40b; 61) est formée par une vanne de limitation de pression ou une vanne combinée de limitation de pression et de réaspiration (62), dans lequel la pression de réglage de la vanne de limitation de pression est réglable et variable.
  5. Assemblage selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la vanne de délestage (60) est disposée dans une conduite de contournement (41b) reliant la conduite de descente (6b) à la conduite de réservoir (8), dans lequel un dispositif d'étranglement (42) est disposé dans la conduite de réservoir (8) en aval du raccord de la conduite de contournement (41b) à la conduite de réservoir (8).
  6. Assemblage selon l'une quelconque des revendications 1 à 4, caractérisé en ce que la vanne de délestage (60) est disposée dans une conduite de branchement (6c) menée de la conduite de descente (6b) au réservoir (2).
  7. Assemblage selon l'une quelconque des revendications 1 à 6, caractérisé en ce que la vanne de délestage (60) peut être actionnée dans une position reliant le côté de descente (B) du cylindre hydraulique (4) au réservoir (8) en fonction d'un signal de commande (X) agissant sur la vanne de commande (5) en direction de la position d'élévation (H) et/ou en fonction d'un signal de position flottante (Z).
  8. Assemblage selon la revendication 7 et la revendication 3 ou 4, caractérisé en ce que la vanne de protection (40b; 61) peut être déplacée en direction d'une diminution de la pression de réglage en fonction du signal de commande (X) commandant la vanne de commande (5) en direction de la position d'élévation (H) et/ou en fonction du signal de position flottante (Z).
  9. Assemblage selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la vanne de délestage (60) peut être actionnée électriquement.
  10. Assemblage selon l'une quelconque des revendications 1 à 8, caractérisé en ce que la vanne de délestage (60) peut être actionnée hydrauliquement.
  11. Assemblage selon l'une quelconque des revendications 3 à 8 ou 10, caractérisé en ce que la vanne de protection (40b; 61) peut être modifiée hydrauliquement au niveau de la pression de réglage.
  12. Assemblage selon l'une quelconque des revendications 7 à 11, caractérisé en ce que le signal de commande (X) se présente sous la forme d'une pression de commande hydraulique, qui règne dans une conduite de pression de commande (35a) de la vanne de commande (5).
  13. Assemblage selon l'une quelconque des revendications 7 à 12, caractérisé en ce que le signal de position flottante (Z) se présente sous la forme d'une pression d'actionnement hydraulique, qui règne dans une conduite de commande (70).
  14. Assemblage selon la revendication 12 ou 13, caractérisé en ce qu'un dispositif d'actionnement (65) de la vanne de délestage (60) est relié à une conduite de commande (75), qui est raccordée à la sortie d'un dispositif de vanne de sélection (76), dans lequel une première entrée du dispositif de vanne de sélection (76) est raccordée à la conduite de pression de commande (35a) conduisant la pression de commande hydraulique (X) et une seconde entrée du dispositif de vanne de sélection (76) est raccordée à la conduite de commande (70) conduisant la pression d'actionnement hydraulique (Z).
  15. Assemblage selon la revendication 14, caractérisé en ce qu'il est prévu une vanne de commutation à deux positions (50), qui dans une première position de commutation (50a) déleste la conduite de commande (70) vers le réservoir (2) et dans une seconde position de commutation (50b) relie la conduite de commande (70) à une source de pression d'actionnement (71).
  16. Assemblage selon la revendication 15, caractérisé en ce que la vanne de commutation à deux positions (70) dans la position flottante est actionnée dans la seconde position de commutation (50b).
  17. Assemblage selon l'une quelconque des revendications 14 à 16 et la revendication 3 ou 4, caractérisé en ce que le dispositif d'actionnement (65) de la vanne de protection (40b; 61) est formée par un dispositif de variation de la pression de réglage.
  18. Assemblage selon l'une quelconque des revendications 15 à 17, caractérisé en ce que la vanne de commutation à deux positions (50) peut être actionnée électriquement ou hydrauliquement.
  19. Assemblage selon l'une quelconque des revendications 1 à 18, caractérisé en ce que le signal de pression est formé par la pression de refoulement de la pompe (1).
  20. Assemblage selon la revendication 19, caractérisé en ce que la balance de pression (11b) présente une face de commande agissant en direction d'une position d'arrêt (12b), qui est en communication avec une conduite de signal de pression de charge (20b), dans lequel la vanne de commutation à deux positions (50) relie dans la première position de commutation (50) la conduite de signal de pression de charge (20b) à une conduite d'annonce de pression de charge (21), qui est menée à un régulateur de flux de refoulement (30) d'une pompe à cylindrée variable (1) à régulation par détection de charge, et dans la seconde position de commutation (50b) relie la conduite de signal de pression de charge (20b) à une conduite de signal (51) transportant le signal de pression.
  21. Assemblage selon la revendication 20, caractérisé en ce que la conduite de signal (51) est raccordée à la conduite de refoulement (3) de la pompe (2).
EP15153740.4A 2014-02-24 2015-02-04 Assemblage avec un dispositif de vanne de commande à position flottante Active EP2910796B9 (fr)

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EP2910796A1 (fr) 2015-08-26
DE102014102336A1 (de) 2015-08-27
EP2910796B9 (fr) 2018-10-10
CN104863913B (zh) 2018-06-12
CN104863913A (zh) 2015-08-26

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