EP1165895B1 - Dispositif de commande hydraulique sensible a une charge pour une machine de travail - Google Patents

Dispositif de commande hydraulique sensible a une charge pour une machine de travail Download PDF

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Publication number
EP1165895B1
EP1165895B1 EP00912605A EP00912605A EP1165895B1 EP 1165895 B1 EP1165895 B1 EP 1165895B1 EP 00912605 A EP00912605 A EP 00912605A EP 00912605 A EP00912605 A EP 00912605A EP 1165895 B1 EP1165895 B1 EP 1165895B1
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EP
European Patent Office
Prior art keywords
pressure
valve
load
accumulator
arrangement according
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.)
Expired - Lifetime
Application number
EP00912605A
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German (de)
English (en)
Other versions
EP1165895A1 (fr
Inventor
Alfred Breunig
Jörg GRÜNERT
Edwin Harnischfeger
Georg Rausch
Dieter Roth
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Bosch Rexroth AG
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Bosch Rexroth AG
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/163—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for sharing the pump output equally amongst users or groups of users, e.g. using anti-saturation, pressure compensation
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B66—HOISTING; LIFTING; HAULING
    • B66F—HOISTING, LIFTING, HAULING OR PUSHING, NOT OTHERWISE PROVIDED FOR, e.g. DEVICES WHICH APPLY A LIFTING OR PUSHING FORCE DIRECTLY TO THE SURFACE OF A LOAD
    • B66F9/00—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes
    • B66F9/06—Devices for lifting or lowering bulky or heavy goods for loading or unloading purposes movable, with their loads, on wheels or the like, e.g. fork-lift trucks
    • B66F9/075—Constructional features or details
    • B66F9/20—Means for actuating or controlling masts, platforms, or forks
    • B66F9/22—Hydraulic devices or systems
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2203—Arrangements for controlling the attitude of actuators, e.g. speed, floating function
    • E02F9/2207—Arrangements for controlling the attitude of actuators, e.g. speed, floating function for reducing or compensating oscillations
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2217—Hydraulic or pneumatic drives with energy recovery arrangements, e.g. using accumulators, flywheels
    • E—FIXED CONSTRUCTIONS
    • E02—HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
    • E02F—DREDGING; SOIL-SHIFTING
    • E02F9/00—Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00 - E02F7/00
    • E02F9/20—Drives; Control devices
    • E02F9/22—Hydraulic or pneumatic drives
    • E02F9/2278—Hydraulic circuits
    • E02F9/2296—Systems with a variable displacement pump
    • 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
    • F15B1/00—Installations or systems with accumulators; Supply reservoir or sump assemblies
    • F15B1/02—Installations or systems with accumulators
    • 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
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/21—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge
    • F15B2211/212—Systems with pressure sources other than pumps, e.g. with a pyrotechnical charge the pressure sources being accumulators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30505—Non-return valves, i.e. check valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30555—Inlet and outlet of the pressure compensating valve being connected to the 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
    • F15B2211/32—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
    • 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
    • F15B2211/55—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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/71—Multiple output members, e.g. multiple hydraulic motors or cylinders
    • F15B2211/7114—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators
    • F15B2211/7128—Multiple output members, e.g. multiple hydraulic motors or cylinders with direct connection between the chambers of different actuators the chambers being connected in parallel

Definitions

  • the invention is based on a load-sensing hydraulic control arrangement, which is used in particular for a wheel loader or a forklift.
  • a load sensing hydraulic control arrangement is e.g. from EP 0 566 449 A1 known.
  • an adjusting pump is dependent on the highest load pressure of the actuated hydraulic consumers each set so that the pump pressure is a certain pressure difference above the highest load pressure.
  • Each hydraulic consumers pressure medium flows through an adjustable orifice to.
  • Each metering orifice is followed by a pressure compensator through which is achieved that with sufficient quantity of pressure medium supplied regardless of the load pressures of the hydraulic consumers a certain pressure difference about the respective metering orifice, so that the hydraulic consumer inflow of pressure medium only from the opening cross section of the depends on the respective metering orifice. If a metering orifice is opened further, so more pressure medium has to flow over them in order to produce the determined pressure difference.
  • the variable pump is adjusted so that it has the required amount of pressure medium supplies.
  • the pressure compensators are downstream of the metering orifices and are opened in the opening direction by the pressure after the respective metering orifice and in the closing direction of one in a rear control room Control pressure applied, which is usually the highest load pressure of all of corresponds to the same hydraulic pump supplied hydraulic consumer. If with simultaneous actuation of several hydraulic consumers, the metering orifices be opened so far that the adjusted from the stop Hydraulic pump delivered quantity of pressure medium is smaller than the total required amount of pressure medium, the individual hydraulic consumers inflowing pressure medium quantities regardless of the respective load pressure of the hydraulic consumer reduced proportionally.
  • LUDV control Control with load-independent flow distribution
  • Controlled hydraulic consumers are called LUDV consumers for short. Because with a LUDV control the highest load pressure is sensed and from the pressure medium source by a certain pressure difference above the highest LUDV control is a load pressure lying supply pressure is generated Special case of a load-sensing or load-sensing control (LS control).
  • LS control load-sensing or load-sensing control
  • Wheel loaders or forklifts and similar mobile work machines tend to be, in particular when they are loaded, when driving faster to so-called pitching vibrations.
  • pitching vibrations of wheel loaders with a damping system dampen, which is part of the hydraulic control arrangement of the wheel loader.
  • the two hydraulic lift cylinders are generally used to dampen vibrations for lifting and lowering the loading bucket via a check valve to a hydraulic accumulator connectable from a hydraulic pump via a filling line to the front the directional control valve block branches off from the pump line and in the Filling valve can be charged.
  • pressure medium can be freely between the lift cylinders and the hydraulic accumulator flow back and forth so that the loading shovel is no longer rigid with the vehicle body is connected and the pitching vibrations are damped.
  • the branching of the filling line in front of the directional control valve block entails that the hydraulic accumulator not only when the lift cylinder is assigned Directional control valve, but when any directional control valve is actuated, the leads to a pressure build-up in the pump line, is charged.
  • the hydraulic accumulator can also operate the hydraulic steering of the working machine associated steering valve to an inflow of pressure medium to the hydraulic accumulator to lead. If the check valve is then opened, an uncontrolled movement can occur the lift cylinder take place.
  • a control arrangement is also known from DE 39 09 205 C1 known to dampen pitching vibrations in the filling line from the consumer line between the directional control valve block and the lift cylinders branches.
  • the aim of the invention is the known hydraulic components for pitch vibration damping of a mobile machine within to arrange a load-sensing hydraulic control arrangement so that the uncontrolled movements of the hydraulic cylinders described above largely avoided.
  • a load-sensing hydraulic control arrangement the filling line from the intermediate section branches off the main line.
  • This intermediate section is when the directional valve not actuated, i.e. the metering orifice is closed, fluidically neither directly connected to the hydraulic consumer still with the pressure medium source. Therefore, when the directional control valve is not actuated, neither the load pressure nor the Inlet pressure has a direct influence on the storage pressure. at most If a certain condition is maintained for a longer period, internal leaks may occur the state of charge of the memory can be changed. However, this is rare because the operating state during the operation of a mobile machine constantly changing.
  • Tax arrangement can be found in the subclaims.
  • the filling valve should have a large opening cross section for the have pressure medium flowing into the hydraulic accumulator and is therefore corresponding to dimension large. So that a spring that the filling valve piston in the opening direction of the filling valve and its preload force the closing pressure determined by which the filling valve is closed, not one to one voluminous filling valve must have leading size is according to claim 7 provided that the filling valve piston on a measuring surface that is much smaller than the cross section of the valve bore receiving the fill valve piston is from Closing pressure is applied in the closing direction. Like such a small measuring area can be created in an advantageous manner is in the claims 8 and 9 indicated.
  • check valve between the hydraulic accumulator and the pressure chamber of the hydraulic cylinder should have a large opening cross-section. It is therefore in accordance with Claim 10 piloted by a pilot valve and has a control surface on, which is relieved of pressure in a switching position of the pilot valve and in a second switching position of the pilot valve with one acting in the closing direction Closing pressure is applied.
  • shut-off valve and the filling valve form a single control piston Control valve are summarized, one with the hydraulic accumulator connected memory port, one to the consumer section of the main line connected consumer connection and one with the intermediate section the main line connected filling connection and three valve positions, wherein in a first valve position assumed under the action of a valve spring the hydraulic accumulator with the filling connection and the storage connection Pressure medium can be filled in a second valve position into which the control valve arrives when the storage pressure or the consumer pressure a certain amount reached, all three connections are cordoned off and in the third Valve position consumer connection and storage connection connected are.
  • the directional valve section contains a directional control valve 15, which can be controlled by means of two pilot valves controlled by proportional solenoids 16 and 17, which are designed as pressure reducing valves, are proportional can be operated.
  • proportional solenoids 16 and 17 which are designed as pressure reducing valves, are proportional can be operated.
  • the directional control valve 15 has one Inlet port 19 to which one of a port P of the control block 10 outgoing inlet channel 20 leads.
  • a tank chamber 21 is through with the block 10 leading tank channel 22 connected.
  • a first consumer chamber 23 of the directional valve 15 is with a first consumer connection 24 and one second consumer chamber 25 with a second consumer connection 26
  • Directional valve section 11 connected.
  • a consumer line leads from the consumer connection 24 27 to the bottom pressure chambers 28 and from the consumer connection 26 a consumer line 29 to the rod-side pressure chambers 30 of the two lift cylinders 14.
  • the metering orifice 18 is located between the inlet chamber 19 and a first intermediate chamber 35.
  • the control piston of the pressure compensator 36 is in the direction of closing the connection between the inlet and the outlet of the pressure compensator from pressure in one Load signaling line 39, the highest load pressure of all at the same time actuated hydraulic load of the wheel loader corresponds. In the closing direction also acts a weak compression spring 40.
  • Control piston of the pressure compensator 36 is acted upon by the pressure at the inlet of the pressure compensator.
  • the highest load pressure is also applied to a regulator of the adjustable hydraulic pump 9 reported that each promotes so much pressure medium that in the supply line 20 there is an inlet pressure which is around a certain pressure difference of e.g. 20 bar above the highest load pressure.
  • pressure medium flows from the inlet channel 20 via the inlet chamber 19, the metering orifice 18, the intermediate chamber 35, the pressure compensator 36, the load holding valve 37, the intermediate chamber 38, the consumer chamber 23, the consumer connection 24 and via the consumer line 27 to the pressure rooms 28 of the two lift cylinders 14. From the pressure rooms 30 is on the consumer line 29, the consumer connection 26, the Consumer chamber 25 and the tank chamber 21 pressure medium in the tank channel 22 repressed. As described, the pressure medium initially flows through the metering orifice 18 and then via the pressure compensator 36. This is therefore connected downstream of the metering orifice.
  • the throttles Pressure compensator 36 the flowing pressure medium so strongly that the pressure on it Input on the control piston generates such a force acting in the opening direction, that the sum of the force generated by the load pressure and the force of the spring 40th the balance is maintained.
  • the pressure compensator is almost completely open, though the lift cylinders are operated alone or have the highest load pressure. is this e.g. 100 bar and are equivalent to the force of the compression spring 40 0.5 bar a pressure of 100.5 bar builds up at the inlet of the pressure compensator 36.
  • the inlet pressure is 120 bar, so that a pressure difference of 19.5 bar. Is the load pressure of the lift cylinder 14 e.g.
  • the channels and lines through the pressure medium from the variable displacement pump 9 to the Pressure spaces 28 or to the pressure spaces 30 of the lift cylinder 14 flows are generally referred to as the main line.
  • the section of this main between the variable displacement pump 9 and the inlet chamber 19 of the directional valve 15 the inlet section.
  • the section between the consumer chamber 23 and the Pressure chambers 28 or between the consumer chamber 25 and the pressure chambers 30 the lift cylinder is the consumer section.
  • Between the intermediate chamber 35 of the directional valve 15 and the intermediate chamber 38 is located an intermediate section of the main line, which is in the middle position of the directional valve 15 fluidly neither with the variable displacement pump 9 nor with one of the pressure chambers Lift cylinder 14 is connected.
  • the control arrangement has a hydraulic damping system for damping pitching vibrations of the wheel loader.
  • Essential elements of this damping system are one or more hydraulic accumulators 40, a filling valve 42 and one Blocking valve 50.
  • the filling valve 42 is a pilot operated 3/2-way valve, which in a Filling line 41 is arranged between the load holding valve 37 and the Intermediate chamber 38 of the directional control valve 17 from the intermediate section of the main line going on. From this, the said input of the filling valve 42, its output and via a check valve 43, which blocks the outlet of the filling valve 42, pressure medium in the hydraulic accumulator 40 flow to charge this to the load pressure of the lift cylinder 14.
  • the check valve 43 prevents the pressure in the hydraulic accumulator 40 can drop during a work cycle with the lift cylinders 14.
  • the hydraulic accumulator 40 is therefore the highest in the pressure rooms of the lift cylinders 14 charged load pressure occurring during a work cycle. This applies until to a maximum load pressure caused by the preload force of a spring on the pilot valve of the fill valve 42 is determined.
  • This pilot valve opens as soon as this maximum load pressure to be placed in the accumulator is reached becomes. This is due to the input of the fill valve 42 to a control side outgoing control line 47 indicated.
  • the pilot valve of the filling valve responds and the filling valve switches to its second switching position. In this the entrance is blocked off.
  • the Outlet is relieved to the tank, so that it is ensured that no pressure medium more in the hydraulic accumulator 40.
  • a pressure relief valve 60 is additionally provided.
  • a compensating line 44 in which the check valve 50 is located.
  • This is structured like a logic element.
  • Such one has two connections that are shut off from one another like a poppet valve can as well as different control areas, at which different pressures act can.
  • the one in the pressure chambers 28 acts on a first control surface 51 the lift cylinder 14 prevailing load pressure in the opening direction of the valve.
  • the accumulator pressure acts in the opening direction.
  • a weak spring 56 acts due to which the valve closes movable valve element of the shutoff valve 50 a closed rest position takes place when the pressure forces cancel each other out.
  • a third control surface 53 of the check valve 50 is exactly the same size as the control surfaces 51 and 52 taken together.
  • a pilot valve 54 is on the control surface 53 the highest of the two pressures load pressure and accumulator pressure at or the control surface 53 is relieved of pressure towards a leakage line 46.
  • the highest of the two pressures, load pressure and accumulator pressure is achieved by a shuttle valve 55 selected.
  • the pilot valve 54 takes the one in FIG 1 shown rest position in which the control surface 53 is loaded by pressure.
  • the check valve 50 is in its locked position. If the mobile work machine exceeds a certain driving speed or if the The driver actuates an electrical switch arbitrarily, the electromagnet becomes of the pilot valve 54 energized so that this in its second switching position arrives, in which the control surface 53 is relieved of pressure. Under the action of The accumulator pressure and load pressure, the check valve 50 reaches its second position, in which a wide open connection between the pressure chambers 28 of the lift cylinder 14 and the hydraulic accumulator 40. Pressure medium can be drawn from the pressure chambers 28 be displaced towards the memory 40. Conversely, pressure medium from the Memory 40 flow into the pressure chambers 28. This is that of the lift cylinders 14 Loaded bucket of the wheel loader no longer firmly with the vehicle body connected so that pitch vibrations are damped.
  • Another logic element 58 with a pilot valve 59 is between the pressure spaces 30 of the lift cylinder 14 and the tank channel 22 are arranged.
  • the pilot valve 59 is in the rest position shown in FIG. 1, in which the logic element 58 is closed. If pitch vibrations should be damped, is simultaneously with the electromagnet of the pilot valve 54 of the check valve 50, the solenoid of the pilot valve 59 is energized, so that a Control room at logic element 58 is relieved of pressure and the logic element already opened from a low pressure in the pressure chambers 30 of the lift cylinder 14 can be.
  • pressure medium from the pressure chambers 30 via the Logic element 58 are displaced into the tank channel 22. Conversely, can Pressure medium from the tank channel 22 via the logic element 58 into the pressure chambers 30 be sucked up.
  • a pilot-operated as a filling valve Pressure reducing valve 65 arranged by the pressure on its storage side Output is controlled. So it closes when the memory pressure reaches a maximum value reached.
  • the check valve 43 is in the embodiment according to FIG. 2 arranged between the filling valve and the intermediate section of the main line. It fulfills the same function as in the embodiment according to FIG. 1.
  • check valve provided with the reference number 66 are two lockable Check valves 67 are used, which are antiparallel in the between the hydraulic accumulator 40 and the pressure chambers 28 extending compensating line 44 are arranged.
  • the two check valves 67 are pilot-controlled by a pilot valve 68 which can assume two switching positions and has four connections. Of this one is cordoned off. A connection is connected to the leakage line 46. On the second connection is at the output of the also in the embodiment according to FIG existing shuttle valve 55, the highest of the two pressures load pressure selects the lift cylinder 14 and accumulator pressure in the pressure rooms 28.
  • the fourth The pilot valve 68 is connected to the control chambers of the check valves 67 connected. The pilot valve 68 assumes a rest position under the action of a compression spring one in which the control chambers of the check valves 67 to the leakage line 46 are relieved of pressure.
  • One check valve 67 can therefore the other check valve 67 from the hydraulic accumulator from the pressure chambers 28 40 ago are flowed through by pressure medium. There is an open connection between the pressure chambers 28 and the hydraulic accumulator 40. The system for Damping of pitching vibrations is then switched on. If the pilot valve 68 brought into its second switching position by energizing an electromagnet, in which the control chambers of the two check valves 67 with the highest of the both pressures load pressure and accumulator pressure selected via the shuttle valve 55 is acted upon. The check valves 67 are then blocked. How in the embodiment according to FIG. 1, the logic element is also used in the embodiment according to FIG 58 with pilot valve 59 and the pressure relief valve 60 available. The In principle, the embodiment according to FIG. 2 functions in exactly the same way as that according to FIG 1, so that reference is made here to the corresponding description of the first embodiment can be.
  • the embodiment according to FIG. 3 also corresponds with respect to the directional valve 15 Pressure compensator 36, the load holding valve 37, the logic element 58 together with the pilot valve 59 and the pressure relief valve 60 of the embodiment according to FIG. 1.
  • the shut-off valve and the filling valve are now combined into a single control valve 70, the check valve 43 in the filling line also the control valve 70 is integrated.
  • the control valve 70 has three connections, namely a filling connection 71 which is connected via the filling line 41 between the load holding valve 37 and the intermediate chamber 38 of the directional control valve 15 to the intermediate section the main line is connected, a consumer connection 72, the connected to the pressure chambers 28 of the lift cylinder 14 via the compensating line 44 is, and a storage port 73, which is connected to the hydraulic accumulator 40 is.
  • a filling connection 71 which is connected via the filling line 41 between the load holding valve 37 and the intermediate chamber 38 of the directional control valve 15 to the intermediate section the main line is connected
  • a consumer connection 72 the connected to the pressure chambers 28 of the lift cylinder 14 via the compensating line 44 is
  • a storage port 73 which is connected to the hydraulic accumulator 40 is.
  • the consumer connection is in the other side switch position 72 and the memory port 73 connected to each other and there can be an exchange of pressure medium between the pressure chambers 28 of the lift cylinders 14 and the hydraulic accumulator 40 take place.
  • the control valve 70 thus fulfills the function of the check valve.
  • the control valve 70 is in the sense of a connection of the storage port 73 with the filling connection 71 acted upon by a compression spring 74, by the pretensioning force thereof the accumulator pressure is determined, the maximum occurring in the hydraulic accumulator 40 should.
  • the control valve 70 is on a first control surface 75 acted upon by consumer pressure.
  • the pressure on a second control surface 76 which acts in the same direction as consumer pressure, is electromagnetic actuable pilot valve 77 controllable. In the rest position of the pilot valve 77, the control surface 76 is relieved of pressure towards the leak oil line 46. In the other switching position of the pilot valve 77 is with that in the control pressure line 78 prevailing maximum pilot pressure for the directional valve 15 is applied.
  • a switchable stroke limitation is provided for the control valve 70, which essentially consists of a stop piston 79 which is in the rest position of the pilot valve 77 is acted upon by the maximum pilot pressure and then a switching of the control valve 70 only from the first switching position to the Allows middle position.
  • the stop piston is in the second switching position of the pilot valve 77 79 relieved of pressure, so that the control valve 70 to the second lateral switching position can be switched.
  • the pilot valve 77 is in its rest position, in which the control surface 76 is relieved of pressure and the stop piston 79 is loaded with pilot pressure.
  • the control valve 70 is due to the effect the spring 74 in the first lateral switching position, in the pressure medium from Filling port 71 can flow to the storage port 73. A pressure medium flow in reverse direction is prevented by the check valve 43. So is the hydraulic accumulator 40 to the highest consumer pressure that has occurred charged.
  • the pilot valve 77 is switched to dampen pitch vibrations.
  • the stop piston 79 is relieved of pressure and the control surface 76 with pressure loaded.
  • the control valve 70 therefore safely reaches its second side Switch position in which the consumer connection 72 and the storage connection 73 are interconnected so that a free flow of pressure medium between the Pressure rooms 28 of the lift cylinder 14 and the pressure accumulator 40 is possible.
  • control block 10 is even more schematic than in Figures 1 to 3 represented as a mere rectangle. It contains several directional valve segments related to 1 to 3 described type with a directional valve, a pressure compensator and a load holding valve. Also in the execution According to FIG. 4, a filling line goes from an intermediate section of the main line 41, in which a filling valve 85 is located. This is as a 2/2-way pressure reducing valve trained that the fluidic connection between his Input 86 and its with the hydraulic accumulator 40 via a check valve 43 connectable outlet 87 can close leakage-free like a seat valve.
  • the filling valve 85 has one Control piston 88, which is a stepped piston with a small area difference is formed and located in a correspondingly stepped valve bore 89 Valve housing 90 is located.
  • the control piston has a first piston collar 91 large diameter, which has a guiding function and which in the valve bore 89 opening 86 opening from an axially spaced therefrom into the valve bore opening leakage hole 92 separates. Closes the piston collar 91 a piston neck extends towards the inlet bore 86 and a closing cone 93 thereon of the control piston 88.
  • the spring chamber is all over the Control piston 88 passed through axial bore 98 with the outlet 87 at the other end of the control piston 88 connected.
  • the same pressure namely the accumulator pressure.
  • This pressure therefore only acts on an area that is the difference area between the Cross-sectional areas of the piston collars 91 and 95 is in the closing direction on the Control piston 88.
  • the spring 97 can therefore be relatively small and weak.
  • Figure 4 is the cross-sectional area of the piston collar 91 with 101, the smaller Cross-sectional area of the piston collar 95 with 102 and that for the leakage bore 92 pressure-relieved differential area designated by the reference number 103.
  • the filling valve 85 is kept open by the compression spring 97 as long as the accumulator pressure on an active surface which corresponds in size to the surface 103, one Generates force that is less than the force of the compression spring 97. Here is the preload the compression spring to the desired maximum storage pressure. If this storage pressure is reached, the filling valve 85 can close it close so that the memory 40 is protected from higher pressures. For protection of the hydraulic accumulator 40 is additionally the pressure relief valve 60 intended.
  • the surface 101 and 102 do not act Storage pressure, but the pressure present at the inlet 86 of the filling valve 85 from the intermediate section of the main line. This can be done easily in that the inlet valve 86 shown in FIG. 6 and output 87 are interchanged.
  • Solenoid direct operated check valve 110 used as a 4/2-way valve is trained. in the rest position of the valve is between the Pressure chambers 28 of the lift cylinder 14 and the hydraulic accumulator 40 extending compensation line 44 interrupted. There is also a broken connection between the pressure chambers 30 of the lift cylinder 14 and a tank line 22. If the electromagnet 111 of the check valve 110 is energized, it passes into its second Switch position in which the pressure chambers 30 with the tank and the pressure chambers 28 Lift cylinders 14 are connected to the hydraulic accumulator 40. In this switch position of the check valve 110, pitching vibrations are damped.
  • the exemplary embodiments are described with reference to a wheel loader.
  • the hydraulic control arrangements shown can, however, also be used without difficulty e.g. be used with a forklift.
  • the hydraulic accumulator 40 is also filled when the directional control valve 15, the pressure chambers 30 of the lift cylinders 14 with the pressure medium source 9 connects. However, this happens during the actuation of the lift cylinder and not while other consumers are operating. Regarding the lift cylinder but is the driver on a delayed pressure build-up or on a Movement when switching on the damping system after previous Working cycle set.

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Claims (19)

  1. Un dispositif de commande hydraulique avec saisie de la charge pour une machine productrice à travail mobile, en particulier pour une pelleteuse ou un char à fourche,
    doté d'au moins un vérin (14) hydraulique, à l'aide duquel un outil de travail peut être amené à bouger,
    doté d'une conduite principale, qui mène d'une source (9) de fluide de pression vers une chambre (28) de pression du vérin (14) hydraulique,
    doté d'un dispositif de valves, disposé dans la conduite principale, qui pour la commande du sens de déplacement et de la vitesse de déplacement du vérin (14) hydraulique présente au moins un orifice (18) d'étranglement réglable, une balance (36) de pression individuelle, disposée en série avec le précédent, et un distributeur (15) et qui permet d'isoler une section intermédiaire de la conduite principale d'une section des récepteurs, laquelle est reliée à la chambre (28) de pression du vérin (14) hydraulique, et d'une section d'alimentation de la conduite principale, laquelle est reliée à la source (9) de fluide de pression,
    doté d'un accumulateur (40) hydraulique, dont la pression d'accumulateur peut être augmentée par une alimentation en fluide de pression au travers d'une valve (42 ; 65 ; 70 ; 85) de remplissage, disposée dans une conduite (41) de remplissage, et doté d'une valve (50 ; 66 ; 70 ; 110) de fermeture, qui peut être amenée dans une position de passage, dans laquelle du fluide de pression peut parcourir une conduite (44) d'équilibrage dans le sens allant de l'accumulateur (40) hydraulique vers la chambre (28) de pression du vérin (14) hydraulique et dans le sens inverse,
    caractérisé en ce que
    la conduite (41) de remplissage dérive de la section intermédiaire de la conduite principale.
  2. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 1, caractérisé en ce que la valve de remplissage (42 ; 65 ; 70 ; 85) ferme la conduite (41) de remplissage, lorsque la pression de l'accumulateur atteint une valeur prédéterminée.
  3. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 1 ou n° 2, caractérisé en ce que la balance de pression individuelle est disposée en amont de l'orifice d'étranglement réglable.
  4. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 1 ou n° 2, caractérisé en ce que la balance (36) de pression individuelle est disposée en aval de l'orifice (18) d'étranglement réglable et que la conduite (41) de remplissage dérive de la section intermédiaire de la conduite principale, en aval de la balance (36) de pression.
  5. Un dispositif de commande hydraulique avec saisie de la charge conforme à une revendication précédente, caractérisé en ce que la pression régnant au niveau de l'entrée (86) de la valve (42 ; 85) de remplissage, qui est raccordée à la section intermédiaire de la conduite principale, est saisie et la valve (42 ; 85) de remplissage ferme lorsque la pression saisie dépasse une valeur prédéterminée.
  6. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 5, caractérisé en ce que la valve (42 ; 85) de remplissage présente une surface de commande, sur laquelle agit, contre un ressort (97) et dans le sens de la fermeture de la conduite (41) de remplissage, la pression régnant au niveau de l'entrée (86) de la valve de remplissage, qui est raccordée à la section intermédiaire de la conduite principale.
  7. Un dispositif de commande hydraulique avec saisie de la charge conforme à une revendication précédente, caractérisé en ce que un tiroir (88) de valve de remplissage de la valve (85) de remplissage, qui est guidé dans un alésage (89) de valve et qui peut être amené à coulisser dans la direction axiale, est sollicité dans le sens de l'ouverture par un ressort (97) et est sollicité dans le sens de la fermeture par la pression de fermeture au niveau d'une surface de mesure, laquelle est nettement plus petite que la section transversale de l'alésage (89) de valve.
  8. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 7, caractérisé en ce que le tiroir (88) de valve de remplissage est un tiroir étagé avec deux diamètres de guidage différents et la surface de mesure est déterminée par la différence de surface entre les deux surfaces (101, 102), lesquelles sont déterminées par les deux diamètres.
  9. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 8, caractérisé en ce que le tiroir (88) de valve de remplissage présente un alésage (98) axial le traversant, qui relie l'une à l'autre les deux chambres (87, 96) de pression, aisposees devantcnacune uesaeux faces extrêmes du tiroir (88) de valve de remplissage et soumises à la pression de fermeture, et que l'épaulement au niveau du tiroir (88) de valve de remplissage est déchargé de toute pression.
  10. Un dispositif de commande hydraulique avec saisie de la charge conforme à une revendication précédente, caractérisé en ce que la valve (50 ; 66 ; 70) de fermeture est pilotée par une valve (54 ; 68 ; 77) de pilotage et présente une surface de commande, qui est déchargée de toute pression dans une position de commutation de la valve (54 ; 68 ; 77) de pilotage et qui est soumise à une pression de fermeture, agissant dans le sens de la fermeture, dans une seconde position de commutation de la valve (54 ; 68 ; 77) de pilotage.
  11. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 10, caractérisé en ce que la pression de fermeture est la pression d'alimentation pour le pilotage électro-hydraulique du distributeur (15).
  12. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 10, caractérisé en ce que la pression de fermeture est la supérieure des deux pressions que sont la pression de l'accumulateur et la pression des récepteurs.
  13. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 12, caractérisé en ce que la valve (50) de fermeture présente un tiroir de fermeture, qui est sollicité dans le sens de l'ouverture de la conduite (44) d'équilibrage par la pression de l'accumulateur et / ou par la pression des récepteurs.
  14. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 13, caractérisé en ce que le tiroir de fermeture est sollicité dans le sens de l'ouverture par la pression des récepteurs au niveau d'une première surface (51) de commande et par la pression de l'accumulateur au niveau d'une deuxième surface (52) de commande et dans le sens de la fermeture par un ressort (56) et que la pression de fermeture agit sur une troisième surface (53) de commande, qui est exactement aussi grande que les deux premières surfaces de commande réunies.
  15. Un dispositif de commande hydraulique avec saisie de la charge conforme à une des revendications n° 10 à n° 12, caractérisé en ce que la valve (66) de fermeture est constituée de deux clapets (67) anti-retour verrouillables, qui sont disposés en parallèle et dans des sens opposés dans la conduite (44) d'équilibrage.
  16. Un dispositif de commande hydraulique avec saisie de la charge conformé à une des revendications n° 10 à n° 14, caractérisé en ce que la valve de fermeture et la valve de remplissage sont réunies en une valve (70) de commande unique, pourvue d'un tiroir de commande, qui présente un raccord (73) d'accumulateur relié à l'accumulateur (40) hydraulique, un raccord (72) de récepteur relié à la section des récepteurs de la conduite principale et un raccord (71) de remplissage relié à la section intermédiaire de la conduite principale, ainsi que trois positions de commutation de la valve, cependant que, dans une première position de commutation, prise sous l'effet d'un ressort (74) de valve, l'accumulateur (40) hydraulique peut être rempli de fluide de pression au travers du raccord (74) de remplissage et du raccord (73) d'accumulateur, dans une deuxième position de commutation, que vient prendre la valve (70) de commande lorsque la pression de l'accumulateur ou la pression des récepteurs, selon le cas, atteint une valeur prédéterminée, tous les trois raccords (71, 72, 73) sont isolés les uns par rapport aux autres et, dans la troisième position de commutation, le raccord (72) de récepteur et le raccord (73) d'accumulateur sont reliés l'un à l'autre.
  17. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 16, caractérisé en ce que la valve (70) de commande passe de la deuxième dans la troisième position de commutation sous l'effet d'une force additionnelle, qui est indépendante de la pression des récepteurs et de la pression de l'accumulateur.
  18. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 16 ou n° 17, caractérisé en ce que la valve (70) de commande présente une butée (79) réglable pour le tiroir de commande, qui permet de limiter la course du tiroir de commande dans la deuxième position de commutation et qui peut être amené à coulisser pour la commutation dans la troisième position de commutation.
  19. Un dispositif de commande hydraulique avec saisie de la charge conforme à la revendication n° 18, caractérisé en ce que la butée est constituée d'un piston (79), qui est sollicité par la pression ou déchargé de toute pression au niveau d'une surface de commande, en fonction de la position d'une valve (77) de pilotage.
EP00912605A 1999-03-26 2000-03-15 Dispositif de commande hydraulique sensible a une charge pour une machine de travail Expired - Lifetime EP1165895B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19913784 1999-03-26
DE19913784A DE19913784A1 (de) 1999-03-26 1999-03-26 Lastfühlende hydraulische Steueranordnung für eine mobile Arbeitsmaschine
PCT/EP2000/002263 WO2000058570A1 (fr) 1999-03-26 2000-03-15 Dispositif de commande hydraulique sensible a une charge pour une machine de travail

Publications (2)

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EP1165895A1 EP1165895A1 (fr) 2002-01-02
EP1165895B1 true EP1165895B1 (fr) 2003-04-23

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EP (1) EP1165895B1 (fr)
AT (1) ATE238465T1 (fr)
DE (2) DE19913784A1 (fr)
WO (1) WO2000058570A1 (fr)

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DE10253131B4 (de) * 2002-10-31 2014-03-13 Linde Hydraulics Gmbh & Co. Kg Zylinderanbauventil
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DE50001872D1 (de) 2003-05-28
ATE238465T1 (de) 2003-05-15
EP1165895A1 (fr) 2002-01-02
WO2000058570A1 (fr) 2000-10-05
DE19913784A1 (de) 2000-09-28

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