EP2667038A2 - Agencement de circuit hydraulique - Google Patents

Agencement de circuit hydraulique Download PDF

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Publication number
EP2667038A2
EP2667038A2 EP13002648.7A EP13002648A EP2667038A2 EP 2667038 A2 EP2667038 A2 EP 2667038A2 EP 13002648 A EP13002648 A EP 13002648A EP 2667038 A2 EP2667038 A2 EP 2667038A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
valve
line
circuit arrangement
load
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.)
Withdrawn
Application number
EP13002648.7A
Other languages
German (de)
English (en)
Other versions
EP2667038A3 (fr
Inventor
Holger Jongebloed
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wessel-Hydraulik GmbH
Wessel Hydraulik GmbH
Original Assignee
Wessel-Hydraulik GmbH
Wessel Hydraulik GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wessel-Hydraulik GmbH, Wessel Hydraulik GmbH filed Critical Wessel-Hydraulik GmbH
Publication of EP2667038A2 publication Critical patent/EP2667038A2/fr
Publication of EP2667038A3 publication Critical patent/EP2667038A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • F15B11/0445—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out" with counterbalance valves, e.g. to prevent overrunning or for braking
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66D—CAPSTANS; WINCHES; TACKLES, e.g. PULLEY BLOCKS; HOISTS
    • B66D1/00—Rope, cable, or chain winding mechanisms; Capstans
    • B66D1/28—Other constructional details
    • B66D1/40—Control devices
    • B66D1/42—Control devices non-automatic
    • B66D1/44—Control devices non-automatic pneumatic of hydraulic
    • 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
    • F15B2211/50563—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure
    • F15B2211/50581—Pressure control characterised by the type of pressure control means the pressure control means controlling a differential pressure using counterbalance 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
    • F15B2211/5153—Pressure control characterised by the connections of the pressure control means in the circuit being connected to an output member and a directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/526—Pressure 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
    • F15B2211/50—Pressure control
    • F15B2211/52—Pressure control characterised by the type of actuation
    • F15B2211/528—Pressure control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—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
    • F15B2211/665—Methods of control using electronic components
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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
    • F15B2211/70—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
    • F15B2211/7058—Rotary 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
    • F15B2211/76—Control of force or torque of the output member
    • F15B2211/761—Control of a negative load, i.e. of a load generating hydraulic energy

Definitions

  • the invention relates to a hydraulic circuit arrangement for a hydraulically operated machine.
  • Hoisting winches are hydraulically operated on many lifting vehicles, in particular by hydraulic motors.
  • the hoisting winches are used for lifting and lowering loads.
  • the hydraulic motor Via hose lines, the hydraulic motor is connected to a control valve, which doses a coming from a pump hydraulic fluid flow in the amount and determines its direction for lowering or lifting the load.
  • lowering brake valves which are locked in a normal position and are opened, for example by the pressure in a supply line to the hydraulic motor.
  • a volume flow is conducted via a check valve to the hydraulic motor for lifting the load and from there to a tank. The lifting thus happens almost lossless, since only the unavoidable throttle losses incurred in the valve.
  • the hydraulic fluid is then passed from the control valve to the hydraulic motor. From this line also a control pressure is tapped, which acts on a valve spool opening. Only then can the hoist winch be set in motion to lower the load. The load pressure of the winch is thus supported on the lowering brake valve.
  • the present invention seeks to provide a hydraulic circuit arrangement for a hydraulically operated machine, which reduces the power losses with high security against uncontrolled lowering of a load.
  • a hydraulic circuit arrangement for a hydraulically operated machine comprising at least one hydraulic load for selectively lifting or lowering a load, and a first and a second connected to the hydraulic consumer hydraulic line, wherein for lifting the load a hydraulic fluid inlet for the hydraulic consumer via the first hydraulic line is carried out and a hydraulic fluid return from the hydraulic consumer via the second hydraulic line, and wherein for lowering the load is a hydraulic fluid inlet for the hydraulic consumer via the second hydraulic line and takes place a hydraulic fluid return from the hydraulic consumer via the first hydraulic line, at least one drain control valve, which in the open state a flow of when lowering the load as return from the hydraulic consumer coming Hydraulikflü liquid and in a closed ground state for one such flow of hydraulic fluid blocks, at least one connected to the second hydraulic line pilot valve, wherein the pilot valve, a pilot pressure at a first control input of the drain control valve for opening the drain control valve is controllable, a pressure measuring device that measures the pressure in the second hydraulic line, at least when lowering the load ,
  • the work machine may be a lift truck, e.g. a crane, act.
  • the work machine may e.g. comprise a hoisting winch with which a load is raised or lowered, the hoisting winch being driven by the hydraulic consumer, e.g. a hydraulic motor, is driven.
  • the circuit arrangement comprises a main control valve which selectively connects the first hydraulic line to the pump and the second hydraulic line to the tank for lifting a load or connects the second hydraulic line to the pump and the first hydraulic line to the tank for lowering a load.
  • the hydraulic fluid may be hydraulic oil in a manner known per se.
  • the pump flow is passed through the main control valve through the second hydraulic line to the hydraulic consumer and from there into the first hydraulic line, from which it reaches the drain control valve.
  • This is initially closed in a basic position, so that the hydraulic fluid can not flow through the drain control valve.
  • the pressure increases in the second hydraulic line serving as an inlet.
  • the pressure measuring device comprises at least one pressure sensor, which measures the pressure in the second hydraulic line when lowering the load and possibly also when lifting the load.
  • the pressure in the second hydraulic line is regulated on this basis to a defined predetermined pressure, that is, a target pressure.
  • a pilot valve which is controlled by the control device.
  • the pilot pressure acting on the first control input of the drain control valve is set in a suitable manner for opening the drain control valve.
  • On the first control input of the drain control valve thus acts a mediated by the pilot valve control pressure, which then leads to the opening of the drain control valve.
  • hydraulic fluid can flow to the tank via the drain control valve.
  • control of the opening cross section of the pilot valve is carried out by means of the control device in such a way that such an opening cross section is provided by the drain control valve that the set pressure prevails as precisely as possible in the second hydraulic line.
  • the pilot valve is supplied by the second hydraulic line serving as a supply line to the hydraulic consumer when lowering the load. If the hydraulic consumer, for example a hydraulic motor, becomes too fast and over-revving due to a very large load to be lowered, this leads to a drop in the inlet pressure in the second hydraulic line. This in turn automatically causes the pressure in the pilot control line to the drain control valve to decrease and the drain control valve to close.
  • the inventive circuit arrangement at low inlet pressures automatically to a classic lowering brake valve, which prevents over-rotation and cavitation of the hydraulic load, such as a Windernnotors.
  • At least the drain control valve is in its basic state in a closed position.
  • the pilot valve may also be in its basic state in a closed position according to an embodiment. But it is also possible in principle that the pilot valve is open in its basic position and is influenced by the control device in the course of pressure control of the opening cross section in a suitable manner.
  • the function of lowering the load according to the invention corresponds to a supply pressure control.
  • the supply pressure to the hydraulic consumer is regulated to a specific desired value with the aid of the drain control valve.
  • the inlet pressure opens the drain control valve directly. This often causes vibrations in the system, which can only be prevented by high damping measures. Often only a high hydraulic clamping of the consumer of 60 bar and more leads to success.
  • the hydraulic circuit arrangement according to the invention effects a decoupling of the second hydraulic line serving as a supply line during lowering from the drain control valve, since the inlet pressure does not immediately open the drain control valve, but the pilot valve is interposed.
  • the pressure required for the vibration-free lowering of a load is achieved by the hydraulic circuit arrangement according to the invention therefore considerably reduced. This reduces power losses. In addition, it is possible to provide targeted further vibration-reducing measures by the control device.
  • the pilot valve may open according to an embodiment in the open state, a connection between the second hydraulic line and the first control input of the drain control valve for opening the drain control valve and close in a closed state, this connection.
  • the pilot valve may be arranged in particular in a connecting line between the second hydraulic line and the first control input of the drain control valve.
  • the pilot valve thus establishes in its open state via its working channel a connection between the second hydraulic line and a first control input of the drain control valve. Achieved, for example, when starting the hydraulic consumer, the pressure in the second hydraulic line, the target pressure, the control device controls the pilot valve in such a way that it is brought from a closed state to an open state and thus also opens the drain control valve.
  • the pilot valve is arranged in a branched off from the connecting line between the second hydraulic line and the first control input of the drain control valve bypass line.
  • the bypass line forms a bypass to the drain control valve.
  • the pilot pressure to the first control input of the drain control valve is thus influenced by the open-arranged in the bypass line pilot valve is opened or closed.
  • the drain control valve may be, for example, a 2/2-way valve.
  • the pilot valve may be, for example, a 3/2-way valve.
  • the drain control valve may be closed leak-free in its basic position.
  • the pilot valve may have a connection for leak oil.
  • the pilot valve may be an electrically controllable pilot valve, which is electrically controlled by the control device.
  • the controller may include a microcontroller. The evaluation of the measuring signals of the pressure measuring device and the control of the pilot valve and thus the control to a constant inlet pressure in the second hydraulic line when lowering a load are then carried out by the microcontroller. By such, for example, as "onboard electronics" designed microcontroller extensive control rules can be implemented in a simple and cost-effective manner.
  • the drain control valve and / or the pilot valve may be a proportional valve.
  • the pilot valve may in particular be an electrohydraulic valve with proportional solenoids.
  • a spring force biasing the drain control valve in a closed position for example, a constant spring force.
  • the control device can act on a first control input of the pilot valve, wherein a spring force, for example a constant spring force acts on the second control input of the pilot valve. This can bias the pilot valve in a closed position.
  • the second control inputs of the drain control valve and / or the pilot control valve may each be connected to the tank. By acting on the second control inputs spring forces is ensured in a particularly simple and reliable manner that the pilot valve and the drain control valve are biased in the closed position.
  • the control device only activates the pilot control valve for opening the drain control valve when a predetermined limit pressure is measured by the pressure measuring device.
  • a predetermined limit pressure is measured by the pressure measuring device.
  • the pressure measuring device comprises at least one pressure sensor, which measures the pressure in the second hydraulic line at least when lowering the load.
  • the pressure measuring device may comprise at least two pressure sensors, each measuring the pressure in the second hydraulic line at least when lowering the load.
  • the measured values of both pressure sensors are present as inputs to the control device and can for example be compared with one another by the control device. For example, when a predetermined limit difference between the pressure measured values compared with one another is exceeded, an error message can then be output by the control device and / or the lowering of the load can be stopped.
  • the pressure sensors are different pressure sensors.
  • the pressure sensors can be designed for different pressure ranges. Hereby are Also, to rule out systematic errors that can occur in certain configurations of load and pressure sensors.
  • a non-return valve which opens in the direction of flow when the load is lowered as a return from the hydraulic consumer and opens in the opposite direction of flow can be provided. This ensures that when lifting the load a hydraulic fluid supply is possible at any time, and that when lowering the load, a hydraulic fluid return is only possible via the drain control valve.
  • the check valve can be integrated into the drain control valve.
  • the hydraulic fluid flow passes via the branch into the third hydraulic line to the drain control valve arranged therein.
  • An outflow via the first hydraulic line downstream of the branch into the third hydraulic line is not possible.
  • the check valve in the first hydraulic line in the flow direction of the hydraulic fluid when lowering the load downstream of the branch is arranged in the third hydraulic line.
  • the third hydraulic line can branch off at a branch point from the first hydraulic line and open at a mouth location back into the first hydraulic line.
  • the check valve may then be disposed between the tap site and the mouth location in the first hydraulic line.
  • the third hydraulic line forms in this embodiment, a bypass line for bypassing the in the first hydraulic line arranged check valve.
  • the drain control valve is thus arranged parallel to the check valve.
  • the hydraulic consumer can be a hydraulic motor. It can then be further provided a speed measuring device which measures the speed of the hydraulic motor and gives the measured values to the control device.
  • the control device may be designed to take into account individual application parameters for the control process, in particular the weight of the load, a setpoint and / or maximum speed when lowering the load and / or a setpoint and / or maximum speed of the hydraulic load when Lowering the load.
  • the control device for example a microcontroller of the control device, can therefore be provided with additional signals for the evaluation in addition to the pressure measurement values.
  • the microcontroller can detect the speed of the wind when lowering the load and depending on wind speed, for example, use different target pressures for the control.
  • a central crane control data to the control device such as a microcontroller of the control device, could be passed.
  • An example in this regard would be a setpoint for the lowering speed of a load.
  • the inventive circuit arrangement according to the in FIG. 1 has a main control valve 10 and a first hydraulic line 12 and second hydraulic line 14 connected to the main control valve 10. Between the first and second hydraulic line 12, 14 there is a hydraulic consumer, in the present case a hydraulic motor 16.
  • the hydraulic motor 16 serves to raise or lower a load by a hydraulic working machine, for example a lifting vehicle with a hoist winch driven by the hydraulic motor 16.
  • a third hydraulic line 20 branches off from the first hydraulic line 12.
  • the third hydraulic line 20 opens again into the first hydraulic line 12.
  • a check valve 24th in the first hydraulic line 12.
  • a drain control valve 26 in the present case a 2/2-way proportional valve, is located in the third hydraulic line 20. In the basic position shown in the figure, which is also assumed when lifting a load, the drain control valve 26 blocks for a flow of hydraulic fluid through the third hydraulic line 20.
  • a first control input 28 of the drain control valve 26 is connected to the output of a pilot valve 30, in this case one 3/2-way proportional valve, in particular an electrically controllable pilot valve 30.
  • a second control input 32 of the drain control valve 26 is at tank pressure level, with a spring force acting on the second control input 32.
  • the first control input 34 as mentioned, electrically controllable.
  • the second control input 36 in turn is at tank pressure level, with a spring force also acting on the second control input 36 of the pilot control valve 30.
  • the pilot valve 30 is biased in the closed basic position shown in the figure. In this basic position, the pilot valve 30 connects the first control input 28 of the drain control valve 26 with tank pressure level.
  • the hydraulic circuit arrangement according to the first embodiment further comprises a pressure measuring device with two pressure sensors 38, 40, which in each case control the pressure in the second hydraulic line 14 measure, for example at regular intervals or continuously.
  • the measurement results are given by the pressure sensors 38, 40 to a control device 42 of the hydraulic circuit arrangement according to the invention.
  • the control device 42 includes a microcontroller, which is electrically supplied via a line 44. Via an electrical line 46, the control device 42, the first control input 34 of the pilot valve 30 to open the pilot valve 30 to control.
  • a compensation line 48 which is connectable via a pressure relief valve 50 to the tank.
  • the pressure relief valve 50 By the pressure relief valve 50, the maximum inlet pressure in the second hydraulic line is limited.
  • the pressure limiting valve 50 and sudden supply pressure changes can be limited, whereby the first existing control error (target-actual error) can be limited even at high attenuation.
  • the hydraulic circuit arrangement according to the first embodiment operates as follows: The lifting of a load with the circuit arrangement according to the invention has been explained above. To lower a load, hydraulic fluid is conveyed from the tank into the second hydraulic line 14 via the main control valve 10 by means of a pump. Due to the check valve 24, a drainage of the hydraulic fluid via the first hydraulic line 12 to the main control valve 10 and thus to the tank is not possible. Rather, the hydraulic fluid at the branch point 18 enters the third hydraulic line 20. As long as the drain control valve 26 and the pilot valve 30 are in their closed position, the drain control valve 26 also blocks a drainage of the hydraulic fluid through the third hydraulic line 20. On the inlet side of the hydraulic motor 16 increases So the pressure on.
  • the pressure sensors 38, 40 measure, for example, at regular intervals or continuously the pressure in the second hydraulic line 14 and give their measured values to the control device 42.
  • the control device 42 is now to regulate the pressure in the second hydraulic line 14 to a desired pressure. Purely by way of example, it is assumed that this target pressure is 30 bar.
  • the pilot valve 30 is actuated by the control device 42 via the line 46, so that it assumes an open state. In this open state, the pilot valve 30 establishes a connection via the line 52 between the second hydraulic line 14 and the first control input 28 of the drain control valve 26.
  • hydraulic fluid can flow via the third hydraulic line 20 and the mouth 22 through the first hydraulic line 12 to the main control valve 10 and thus to the tank.
  • the control device 42 controls the opening cross section of the pilot valve 30 and also the opening cross section of the drain control valve 26 so that in the now taking place lowering the load in the second hydraulic line 14 as accurately as possible, the target pressure of for example 30 bar.
  • the target pressure of for example 30 bar.
  • a comparison of the measured values of the two pressure sensors 38, 40 can take place in the control device 42. If critical deviations are detected, this indicates an error of at least one of the pressure sensors 38, 40. It can then be taken by the control device 42 suitable countermeasures, for example, a stop of the lowering process and / or an error message. It is also possible that the two pressure sensors are designed differently in order to rule out systematic errors.
  • FIG. 2 shown second embodiment of a hydraulic circuit arrangement according to the invention corresponds in structure and function as far as possible in Fig. 1 shown embodiment.
  • the pilot valve 30 'at the in Fig. 2 in contrast to the embodiment according to Fig. 1 is the pilot valve 30 'at the in Fig. 2 however, in the second embodiment shown in FIG Fig. 2 shown basic state, thus establishes a connection between the second hydraulic line 14 and the first control input 28 of the drain control valve 26.
  • the pilot valve 30 ' is controlled by the control device 42 via the line 46, so that in turn the first control input 28 of the drain control valve 26 supplied pilot pressure is controlled in a suitable manner for pressure control, as in principle above to Fig. 1 was explained.
  • FIG. 3 shown third embodiment of the circuit arrangement according to the invention corresponds in structure and function as far as possible in Fig. 1 shown first embodiment. Unlike the ones in the FIGS. 1 and 2 shown first and second embodiments of the invention is in the third embodiment after Fig. 3
  • the pilot valve 30 "not in a connecting line between the second hydraulic line 14 and the first control passage 28 of the drain control valve 26, but in a bypass line 52 branching off from this connecting line, through which the drain control valve 26 can be bypassed .
  • the bypass line 52 is connected to tank pressure level.
  • the pressure acting on the first control input 28 of the drain control valve 26 acts via a throttle point 54 of the pressure acting in the second hydraulic line 14.
  • the pilot control valve 30 "of the pressure control device 42 via the line 46 are brought into an open state, so that in turn the on the first control gear 28 of the drain control valve 26 acting pilot pressure can be influenced.
  • the pilot valves 30 and 30 'from the FIGS. 1 and 2 it is also in the pilot valve 30 "off Fig. 3 around a proportional valve, in this case a 2/2-way proportional valve.
  • the pressure required to lower a load can be significantly reduced. This results in a considerable energy saving potential.
  • the hydraulic oscillating circuit can be decoupled and, if necessary, vibration-reducing measures can be taken via the microcontroller of the regulating device 52.
  • the intake pressure drops, for example, if the hydraulic motor 16 overruns with a very large driving load
  • the pilot valve 30, 30 ', 30 "and the drain control valve 26 move in their closed position, so that an uncontrolled fall of the load is excluded.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • General Engineering & Computer Science (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
EP13002648.7A 2012-05-25 2013-05-21 Agencement de circuit hydraulique Withdrawn EP2667038A3 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012010266.6A DE102012010266B4 (de) 2012-05-25 2012-05-25 Hydraulische Schaltungsanordnung

Publications (2)

Publication Number Publication Date
EP2667038A2 true EP2667038A2 (fr) 2013-11-27
EP2667038A3 EP2667038A3 (fr) 2015-07-15

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP13002648.7A Withdrawn EP2667038A3 (fr) 2012-05-25 2013-05-21 Agencement de circuit hydraulique

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EP (1) EP2667038A3 (fr)
DE (1) DE102012010266B4 (fr)

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EP3104022A1 (fr) * 2015-06-12 2016-12-14 National Oilwell Varco Norway AS Améliorations apportées à la commande d'actionneurs hydrauliques
WO2017116573A1 (fr) * 2015-12-31 2017-07-06 Westinghouse Electric Company Llc Appareil hydraulique et machine hydraulique utilisable en son sein
DE102016201971A1 (de) * 2016-02-10 2017-08-10 Robert Bosch Gmbh Hydraulische Antriebsvorrichtung mit lastabhängigem Druckteiler
IT201800002731A1 (it) * 2018-02-15 2019-08-15 Magni Telescopic Handlers S R L Apparecchiatura per regolarizzare la corsa di attuatori oleodinamici a doppio effetto

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DE102014222326B4 (de) * 2014-10-31 2016-06-09 Tadano Faun Gmbh Hydraulikanordnung
DE102016212389A1 (de) * 2016-07-07 2018-01-11 Robert Bosch Gmbh Hydraulisches Antriebssystem mit gleichförmigem Lauf
DE102017130485B4 (de) 2017-12-19 2024-05-08 Wessel-Hydraulik Gmbh Hydraulische Schaltungsanordnung zum Heben und Senken einer Last

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EP3104022A1 (fr) * 2015-06-12 2016-12-14 National Oilwell Varco Norway AS Améliorations apportées à la commande d'actionneurs hydrauliques
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