EP1574474A2 - Agencement hydraulique - Google Patents

Agencement hydraulique Download PDF

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Publication number
EP1574474A2
EP1574474A2 EP05101767A EP05101767A EP1574474A2 EP 1574474 A2 EP1574474 A2 EP 1574474A2 EP 05101767 A EP05101767 A EP 05101767A EP 05101767 A EP05101767 A EP 05101767A EP 1574474 A2 EP1574474 A2 EP 1574474A2
Authority
EP
European Patent Office
Prior art keywords
hydraulic
valve
pressure
switching
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.)
Withdrawn
Application number
EP05101767A
Other languages
German (de)
English (en)
Other versions
EP1574474A3 (fr
Inventor
Marcus Bitter
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.)
Deere and Co
Original Assignee
Deere and Co
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 Deere and Co filed Critical Deere and Co
Publication of EP1574474A2 publication Critical patent/EP1574474A2/fr
Publication of EP1574474A3 publication Critical patent/EP1574474A3/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Withdrawn legal-status Critical Current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
    • 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
    • B66F9/065—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 non-masted
    • 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
    • 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
    • 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
    • F15B2211/50545—Pressure control characterised by the type of pressure control means the pressure control means controlling a pressure upstream of the pressure control means using braking valves to maintain a back 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
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/705—Output members, e.g. hydraulic motors or cylinders or control therefor characterised by the type of output members or actuators
    • F15B2211/7051—Linear output members
    • F15B2211/7053—Double-acting output members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—Output members, e.g. hydraulic motors or cylinders or control therefor
    • F15B2211/76—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

  • Hydraulic arrangement for the realization of a floating position for a hydraulic cylinder, with a first and a second chamber having hydraulic cylinder, a Hydraulic tank, one pumping a hydraulic fluid Conveying, one between the first and the second chamber arranged hydraulic line, one in the hydraulic line arranged switching valve, one in the hydraulic line arranged volume flow dependent controlling valve device, a first supply line for the first Chamber, a second supply line for the second chamber, one arranged in the first supply line Pipe burst protection device and a control unit with at least three switching positions, which are a lifting position, a lowered position and a neutral position for the Include hydraulic cylinder.
  • Hydraulic arrangements with implemented floating positions, whereby a free movement of a hydraulic cylinder allows are known in the art. Both are Connection sides of the hydraulic cylinder with each other as also low pressure or without pressure with a tank or Hydraulic tank connected. Such hydraulic arrangements found in construction or loading vehicles, such.
  • B. Telehandler or front loader vehicles use in which by means of a Lifting cylinder raised a boom or a rocker or can be lowered.
  • the function of the floating position is for example, needed to be independent of the position and location of the vehicle to allow a tool on Boom or on the rocker of the vehicle, the bottom contour can follow the contour. The tool is just pressed to the ground by gravity.
  • Hydraulic arrangements with floating positions are taking shape especially then as very expensive if a load-holding valve is provided, which for safety reasons at emergence a leakage in the connection between cylinder and Control unit unintentional lowering of the boom or the swingarm should prevent or slow down much.
  • a control pressure through which the valve is opened.
  • In the Floating position is a non-pressurized state of the hydraulic Consumer, so that without additives no tax pressure is buildable.
  • To build up this control pressure anyway can, such hydraulic arrangements are to additional switching valves and / or hydraulic lines extended. By this extension should then if necessary a Connection of the rod side of the hydraulic cylinder with the Hydraulic tank to be made or separated.
  • DE 100 06 908 A1 discloses a hydraulic Piston-cylinder unit for agricultural machines with a load-holding valve, in which a working position is reached, in which a constant pressure in the piston bottom side cylinder space is adjustable. This can a boom or a tool located there always rest on the ground with preselected contact force.
  • These Working position is achieved by the pressure chambers of Piston-cylinder unit to be associated with each other And via a pressure control valve, a pressure equalization between the both pressure chambers takes place. If the pressure drops below one preselected value, closes the pressure control valve.
  • a Floating position is only possible if the preselected Value is set to zero, so no pressure control he follows. The disadvantage is that when switching under load, the boom or the tool uncontrolled would sink.
  • the object underlying the invention is seen therein a hydraulic arrangement of the type mentioned to improve that the effort to realize a "lowering function" under load reducible and at the same time a fully functional floating position is feasible. In particular, switching relationships less complex and the risk of incorrect operation and unwanted switching states can be reduced.
  • a hydraulic arrangement of the above mentioned type designed such that the control unit, a has further switching position, which is a floating position represents, in which by the control unit at least the second supply line is connectable to the tank and at the same time connections of both supply lines to Subsidies are interrupted.
  • the controller has a fourth switching position, can on a second Switching valve for connecting the second chamber of Hydraulic cylinder with a tank, as in previous ones Solutions provided is waived. With it reduced the technical effort is considerable, especially because of because an additional hydraulic arrangement for the realization one of the "lowering function" under load is eliminated.
  • a fourth shift position provides the Advantage that in addition to the lifting position and the lowering position furthermore a neutral position for the hydraulic cylinder can be provided in both supply lines are closed.
  • the connection should between the lower side of the hydraulic cylinder and the Hydraulic tank should preferably be closed, as there are applications with wheel loaders, telescopic loaders and also front loaders are at which a certain contact pressure under one on the boom attached tool is to be produced, resulting in a permanent connection to the tank would not be possible and so on would lead to a disadvantage compared to competing products. It is therefore an advantage of a fourth invention To add switching position and both the lifting and To provide lowering and neutral position.
  • the control unit may be designed such that in the fourth switching position, the first supply line with the second supply line interconnected and both Supply lines are connected to the hydraulic tank, the second input to the controller being closed, so that there is no supply from the subsidy.
  • a such fourth switching position as floating position is not mandatory, it is sufficient if the fourth Switch position only the second supply line of the Hydraulic cylinder connects to the hydraulic tank.
  • control unit In the floating position, the control unit connects the second Supply line or the second and the first Supply line directly to the hydraulic tank, i. it No additional valves or means are required (except one) Connecting line from the control unit to the tank).
  • the control unit can be designed manually or electrically operated, Of course, other methods are conceivable are, for example, pneumatic or hydraulic methods, which, however, should not be explained in detail.
  • the switching valve preferably has a closed position and an open position, wherein the switching valve in the Closing position preferably closes in both flow directions and opens in the open position in both directions of flow, so that a floating position for the hydraulic cylinder entry.
  • the switching valve is preferably electric actuated. It is of course also conceivable that other types of actuation of the switching valve are used, for example, a manual, pneumatic or hydraulic Activity.
  • the floating position to be activated it will Switching valve in its open position and the control unit in its fourth switching position switched to the first and the second chamber of the hydraulic cylinder with each other and with the Hydraulic tank to connect. So that the hydraulic arrangement as easy to use and the possibilities for a Operator error is minimized the switching valve is preferably always opened automatically, d. H. brought into open position when the control unit in its floating position. Preferably, they are Provided with funds to determine whether the Control unit is in its floating position or not. This can be implemented, for example, in the form of a switch be in connection or depending on the Floating position is switched on the control unit.
  • the boom or the rocker to hold under load or with a certain contact pressure. This is from a lifting or lowering position directly into the Neutral position switched and by the lifting or Lowering built contact pressure held. As a result of that the switching valve in the lifting, neutral and lowered position always automatically held in the closed position, no Pressure equalization between the chambers occur.
  • the functions for lifting and lowering of the hydraulic cylinder carried at closed switching valve by switching the control unit in Lifting or lowering in a known manner.
  • the control device is preferably as a slide valve formed, which four switch positions, each with two Has inputs and outputs. In the individual positions are the supply lines in different ways according to the actuating functions (lifting, lowering, Neutral position (holding) and floating position) of the control unit connected to the conveyor or to the tank or closed.
  • the pipe rupture protection device preferably comprises a in Direction of the control unit closing check valve and a pressure relief valve, wherein the pressure relief valve through prevailing in the connecting lines pressures is controllable.
  • the control is done by Pilot pressure lines, which of the pressure relief valve in lead the first and the second supply line.
  • the Check valve is in a pressure relief valve arranged bypass bypass, wherein the Check valve opens towards the first chamber.
  • Other Possibilities for pipe burst protection are also conceivable.
  • pressure switches can also be used in case of pressure drop, actuate a switching valve.
  • a volume flow dependent controlling valve device has the Advantage that regardless of the hydraulic pressure in the Hydraulic line the volume flow is controllable, so that both at low and high hydraulic load only a certain flow through the hydraulic line and thus a security function is offered. Becomes for example, while the first chamber of the Hydraulic cylinder is pressurized, the hydraulic Arrangement brought into floating position by the switching valve by moving the control unit into the floating position in Flow position is switched, then ensures the Volume flow dependent controlling valve device that the flow rate is only in., regardless of the level of pressure does not change certain limits or a certain value will exceed.
  • the valve device preferably includes a Flow opening changing adjusting means, for example a slider or closing elements, on the one hand a Pressure of the first chamber and on the other hand a pressure of the Container and optionally exposed to a spring force is. Depending on a pressure difference between the two flow sides, which correspond to one prevailing volumetric flow, changed or closes the flow opening of the actuating means.
  • a Flow opening changing adjusting means for example a slider or closing elements
  • the valve device preferably has means that with rising (falling) pressure drop over the Valve device reduce the flow area (expand). If due to increasing pressure in the Hydraulic line increases the flow, so does the Pressure gradient between the flow inlet and Flow outlet side on. At the same time then reduces the flow area across the valve means, so that the pressure gradient drops again. As a result of the declining Pressure gradient is reduced again Flow cross-section of the valve device, so that a controlling state that sets the Volume flow in the presence of a pressure gradient keeps as far as possible or within certain limits constant.
  • the valve device may include a flow control valve, which changes the volume flow as a function of flow and on limits a predefinable maximum value.
  • Flow control valves are, for example, from the company "HYDAC International. "An exact description of the DIN-ISO 1219 are removed.
  • a flow control valve has via a differential pressure controller, the volume flow dependent on a control piston, a compression spring, a control panel and over a set screw for adjusting the control pressure difference the Flow controls or regulates. With increasing volume flow or increasing flow d. H. increasing pressure gradient is the cross section of the control panel according to the increased Reduced pressure drop until again Force balance is present.
  • the control direction preferably the outflow direction of the hydraulic fluid the pressurized chamber of the Hydraulic cylinder, preferably the lifting side of the Hydraulic cylinder, in the direction of the container corresponds.
  • the valve can be flowed through unregulated.
  • Such a valve has the advantage that even at extreme high pressure loads always one of the control pressure difference adjusts corresponding volume flow, the Control pressure difference can be specified via the adjusting screw. This As a result, when switching from operating position in Floating position under load a controlled pressure decrease, largely independent of the amount of the prevailing Pressure, takes place and thus a safety precaution in Switching to the floating position is given.
  • the valve means includes a parallel to Flow control valve arranged check valve, which in Direction of the first chamber opens. This will ensure that flowing in the direction of the container Hydraulic fluid is forced through the flow control valve to flow and accordingly controlled from the high Pressure applied chamber drains, whereas an inflow from the opposite direction can take place unhindered.
  • Valve means means that when exceeding a predeterminable pressure gradient reduce the volume flow or interrupt. This will ensure that when it reaches a volume flow, the predetermined pressure drop causes the connection is interrupted, so that the Pressure in the pressurized first chamber or is held in the first hydraulic line. If the pressure falls Once again, the connection is restored as soon as that specifiable pressure gradient is reached or a Volume flow that causes a pressure gradient, which is less than or equal to the predeterminable pressure gradient.
  • the valve device includes a Rohbruchtechnischsventil, which when reaching or Exceeding a predefinable pressure gradient closes or falls below the predetermined pressure gradient opens.
  • Rohbruchtechnischsventile be for example of offered by the company "HYDAC International” detailed in a company catalog “HYDAC INTERNATIONAL - FLUTEC Pipe Fittings RBE “described.” Flutec "Pipe Fuses are volume flow dependent switching Flat seat valves, the impermissible and uncontrolled Avoid movements of a consumer under load.
  • a pipe rupture valve has a closing element, For example, a closing piston in the form of a Poppet valve, which is an open in normal operating condition Has switching position.
  • the closing element is preferably held by a spring in the open state, as long as the Spring force is greater than that through the flow resistance When flowing through force caused on the closing element or on the plate surface of the poppet valve.
  • the valve stays opened and can be flowed through in both directions. exceeds the prevailing volumetric flow when flowing through the valve in a predeterminable direction by the predetermined Pressure drop defined, maximum allowable value is through the flow resistance increase the spring force overcome and the closing element abruptly pressed on the valve seat, so that the flow is interrupted.
  • the valve opens automatically, as soon as a pressure equalization takes place and the Pressure force in front of the valve resulting from spring force and Compressive force behind the valve composing force below.
  • the valve device has a parallel to the pipe rupture valve arranged throttle or orifice, which allows a reduced volume flow when the pipe rupture valve is closed. This ensures that always a certain proportion of the volume flow is passed on, so that the pressure in front of the valve device can not build up.
  • the throttle or orifice can be arranged in a bypass line parallel to the pipe break safety valve or be formed, for example, in the form of a bore directly on the pipe rupture valve, in particular directly on the poppet valve. At high flow rates is thus ensured that the closing of the pipe rupture valve much of the flow is intercepted and only a small portion of the hydraulic fluid passes through the throttle, so that a total of controlled pressure decrease is achieved when switching to the floating position.
  • a telescopic loader in each Operating position also under load with raised boom, in Floating position to be switched.
  • a floating position without described volume flow control would cause with increasing load of the boom more or less uncontrolled Shut down, causing a heightened security risk represents.
  • the floating position is made possible to use when working on the soil surface.
  • the hydraulic cylinder with raised boom through corresponding control via the control valve with the side Pressure to apply, so an accelerated Shutting down the boom entry. In all Operating positions is a secure switch to a Floating position given.
  • the circuit diagram shown in Fig. 1 shows Embodiment of a hydraulic arrangement 10 for Realization of a floating position.
  • the hydraulic arrangement 10 includes a switchable controller 12, for example a Slide valve, which via hydraulic lines 14, 16 with a pump 18 and a hydraulic tank 20 is connected, wherein the control unit 12 in three operating positions, lifting, neutral and Lowering, switchable.
  • the switching of the control unit 12 is preferably done by hand, but can also electrically, hydraulically or pneumatically.
  • first and second supply line 22, 24 is the Control unit 12 connected to a hydraulic cylinder 26, wherein the first supply line 22 into a first chamber 28 of the Hydraulic cylinder 26 and the second supply line 24 in a second chamber 30 of the hydraulic cylinder 26 leads.
  • One Piston 29 separates the two chambers 26, 28 from each other.
  • the first chamber 28 of the hydraulic cylinder 26 provides the piston-side or lift-side chamber, whereas the second chamber 30, the piston rod side and the lower side Represents chamber of the hydraulic cylinder.
  • the Pipe burst protection device 32 includes a pressure and spring-controlled pressure relief valve 34, and a for Hydraulic cylinder side opening check valve 36, which via a bypass line 38 parallel to the pressure relief valve 34 is arranged.
  • a first pressure line 40 is a Pressure connection from the pressure relief valve 34 to Hydraulic cylinder side portion of the first supply line 22 produced.
  • a second pressure line 42 is another pressure connection from the pressure relief valve 34 to second supply line 24 made. Furthermore, holds a spring 44, the pressure relief valve 34 in Closed position.
  • a hydraulic line 46 connects the first chamber 28 and the first supply line 22 to the second chamber 30 and with the second supply line 24, one with the first Supply line 22 connected end 48 of the hydraulic line 46 between the first chamber 28 and the Pipe rupture protection device 32 is arranged.
  • a switching valve 50 In the hydraulic line 46 is a switching valve 50 and a in the direction of the second supply line 24 behind the Switching valve 50 connected volume flow dependent controlling Valve device 52 is arranged.
  • the switching valve 50 is turned on electrically switchable seat valve, which has a Stellfeder 54 is held in the closed position and a Solenoid 56 is brought into an open passage position can be.
  • the switching valve 50 seals in both Directions leak-free.
  • the valve device 52 includes a Flow control valve 58, which in parallel to a Check valve 60 is arranged, wherein the check valve 60 opens in the hydraulic cylinder direction.
  • the valve device 52 in the direction of the second Supply line 24 to be arranged in front of the switching valve 50.
  • the individual operating states can now via the Controlled control unit 12 and via the switching valve 50 become.
  • the control unit 12th held in neutral position by adjusting springs 62, 64.
  • the Switching valve 50 is in a closed position. about a control signal or by manual operation is the Control unit 12 by means of an actuator 66 from the Neutral position out in the lifting, lowering or floating position brought. It can be a manual, electrical, hydraulic or pneumatic actuator 66 act.
  • control unit 70 When switching the controller 12 in the floating position detects a connected to the actuator 66 Switch or sensor 68, the floating position of the controller 12th and sends a signal to a control unit 70.
  • the Control unit 70 is connected to the switching valve 50 and stops or brings the switching valve 50 in the closed position, if the controller 12 is in the floating position.
  • the control logic is the Control unit 70 is preferably designed so that at each Switching position of the controller 12 from the floating position deviates a corresponding signal to close the Switching valve 50 is generated, wherein the switch or sensor 68 the switching positions of the control unit 12 detected or detected and a corresponding switching position signal to the Control unit 70 outputs.
  • the controller 12 interrupts the connections to the pump 18 and the hydraulic tank 20, so that the pressure in the retained two chambers 28, 30 of the hydraulic cylinder 26 and the movement of the piston 29 is canceled.
  • the switching valve 50 is closed.
  • the piston 29 stops.
  • the pipe rupture device 32 thus ensures that the hydraulic cylinder 26 in neutral position maintains or in lifting and neutral position no oil from the pressurized first chamber 28 can escape and that in lowering position, the oil from the first chamber 28 via the opened pressure relief valve 34 can drain.
  • the lifting side of the side of the Hydraulic cylinder 26 is in which a pressure for lifting a load is built.
  • the stroke side is the first chamber 28 of the hydraulic cylinder 26, by turning the hydraulic cylinder 26 and the second Chamber 30 could serve as a lifting side.
  • the first pressure line 40 represents an overload protection, so that too high Operating pressures in the first chamber 28 of the hydraulic cylinder 26, for example, caused by excessive loads can, in the first pressure line 40 reaches a limit pressure is that opens the pressure relief valve 34 to reduce pressure.
  • the controller 12 can from any Switch position out or in any operating position in the floating position (from above the fourth switching position of Control unit 12 of Figure 1) are switched. It will by the switching signal generated by the control unit 70 Switching valves 50 controlled so that the solenoid 56 of the Spring force of the spring 54 counteracts and the switching valve 50th brought out of the closed position in the open position becomes. This has the consequence that the first chamber 28 and the second chamber 30 with each other and with the other Hydraulic tank 20 can be associated, so that a Replacement of the hydraulic fluid or the oil take place and the piston 29 can be moved freely floating. Finds Switching to the floating position from an operating position under load, the oil flows under elevated pressure from the pressurized first chamber 28 out, resulting in a would lead to accelerated piston movement.
  • Flow control valve 58 in force, which limits the flow or the flow of the oil controls or regulates. exceeds the volume flow is an approved value, the Passage cross section of the flow control valve 58, so that the Volume flow does not increase any further. This will be uncontrolled movements of the piston 29 effectively avoided.
  • FIG. 2 is another volume flow dependent controlling Valve device shown, based on an alternative Embodiment will be explained.
  • valve device shown in FIG. 2 shown valve device can be used.
  • the rest Components or their functions are according to the in the manner shown in Figure 1 and according to the previous description used.
  • 2 is for the valve means 52 in place of the flow control valve 58 and of the check valve 60 a pipe rupture valve 72 in Combination with a throttle 74 connected in parallel used.
  • a throttle 74 may also be a equivalent aperture can be used. Is through switching of the controller 12 is switched to the floating position causes the pipe rupture valve 72 also a flow-dependent reduction or limitation of the Volume flow.
  • FIG. 3 shows a mobile one Telescopic loader 82 with a housing 84 and a frame of the Telescopic loader 82 pivotally hinged, telescopic extendible, cantilever 86.
  • a hydraulic cylinder 26 for raising and lowering the boom 86 arranged.
  • the hydraulic cylinder 26 is at one first and a second bearing 88, 90 pivotally hinged, wherein the piston rod side 92 at the second Bearing 90 on the boom 86 and the piston bottom side 94 at the first bearing 88 is hinged to the housing 84.
  • the hydraulic tank 20, the pump 18 and the Control unit 12 is positioned on or in the housing 84 and over Hydraulic lines 14, 16 connected to each other.
  • Valve block 96 are in particular the pipe rupture protection 32, the Switching valve 50 and the valve device 52 integrated.
  • electrical or mechanical control Control or switching signals are generated with which the Control unit 12 or the switching valve 50 (see FIG. 1) be operated or switched.
  • Float position it is possible in Float position to switch so that the piston freely movable and thus also the boom 86 is floating.
  • the floating position ensures that a on Boom 86 fixed and lowered to the ground tool 98 floating, following the contour of the ground, over the Ground surface can be moved.
  • the contact pressure of the Tool 98 relative to the ground is thereby substantially by the weight of the boom 86 and the tool 98 certainly.
  • a safety function is thereby given, lowering the boom 86 is volume controlled under load can be done so no unintentional, sudden Movement changes occur. Is z. B.

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  • Engineering & Computer Science (AREA)
  • Transportation (AREA)
  • Structural Engineering (AREA)
  • Mechanical Engineering (AREA)
  • Civil Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Geology (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Operation Control Of Excavators (AREA)
  • Transplanting Machines (AREA)
EP20050101767 2004-03-13 2005-03-08 Agencement hydraulique Withdrawn EP1574474A3 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004012382 2004-03-13
DE102004012382.9A DE102004012382B4 (de) 2004-03-13 2004-03-13 Hydraulische Anordnung

Publications (2)

Publication Number Publication Date
EP1574474A2 true EP1574474A2 (fr) 2005-09-14
EP1574474A3 EP1574474A3 (fr) 2006-10-04

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP20050101767 Withdrawn EP1574474A3 (fr) 2004-03-13 2005-03-08 Agencement hydraulique

Country Status (5)

Country Link
US (1) US7448309B2 (fr)
EP (1) EP1574474A3 (fr)
AU (1) AU2005201083B2 (fr)
CA (1) CA2500609C (fr)
DE (1) DE102004012382B4 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007048697A1 (de) * 2007-10-11 2009-04-16 Deere & Company, Moline Hydraulische Hubeinrichtung
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DE102007048697A1 (de) * 2007-10-11 2009-04-16 Deere & Company, Moline Hydraulische Hubeinrichtung
EP2196682A1 (fr) * 2008-12-15 2010-06-16 Bosch Rexroth Oil Control S.p.A. Dispositif hydraulique pour la commande d'un actionneur d'engin de travaux.
EP2786958A1 (fr) * 2013-04-05 2014-10-08 Bosch Rexroth Oil Control S.p.A. Dispositif de commande pour la descente d'une charge
EP2786959A1 (fr) * 2013-04-05 2014-10-08 Bosch Rexroth Oil Control S.p.A. Dispositif d'anti-cavitation pour vérin hydraulique
ITUA20162376A1 (it) * 2016-04-07 2017-10-07 Atlantic Fluid Tech S R L Dispositivo di controllo di un attuatore
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WO2019210341A1 (fr) * 2018-05-04 2019-11-07 Palfinger Ag Système hydraulique
IT201900005056A1 (it) * 2019-04-04 2020-10-04 Nem S R L Circuito idraulico di azionamento per macchina operatrice con articolazione meccanica dotata di funzione flottante.

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EP1574474A3 (fr) 2006-10-04
CA2500609A1 (fr) 2005-09-13
DE102004012382B4 (de) 2014-03-13
AU2005201083A1 (en) 2005-09-29
DE102004012382A1 (de) 2005-09-29
AU2005201083B2 (en) 2011-03-10
US20050199120A1 (en) 2005-09-15
CA2500609C (fr) 2007-05-22
US7448309B2 (en) 2008-11-11

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