EP1752587B1 - Agencement hydraulique - Google Patents

Agencement hydraulique Download PDF

Info

Publication number
EP1752587B1
EP1752587B1 EP05112498A EP05112498A EP1752587B1 EP 1752587 B1 EP1752587 B1 EP 1752587B1 EP 05112498 A EP05112498 A EP 05112498A EP 05112498 A EP05112498 A EP 05112498A EP 1752587 B1 EP1752587 B1 EP 1752587B1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
control unit
switching
switching means
valve
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.)
Not-in-force
Application number
EP05112498A
Other languages
German (de)
English (en)
Other versions
EP1752587A1 (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 EP1752587A1 publication Critical patent/EP1752587A1/fr
Application granted granted Critical
Publication of EP1752587B1 publication Critical patent/EP1752587B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • 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
    • F15B1/021—Installations or systems with accumulators used for damping
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
    • F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
    • F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/008—Reduction of noise or vibration
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3144—Directional control characterised by the positions of the valve element the positions being continuously variable, e.g. as realised by proportional valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/329—Directional control characterised by the type of actuation actuated by fluid pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/70—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

Definitions

  • the invention relates to a hydraulic arrangement for a suspension system comprising a hydraulic cylinder having at least one first chamber, a hydraulic tank, at least one conveying a hydraulic fluid, a hydraulic accumulator, a first hydraulic line arranged between the hydraulic accumulator and the first chamber, a first switching valve arranged in the first hydraulic line , a first supply line for the first chamber, a control unit having at least three switching positions, which comprise a lifting position, a lowered position and a neutral position for the hydraulic cylinder, and arranged in the first supply line pipe rupture protection device, which closes in the direction of the control valve check valve and a a first control pressure line auf horrbares pressure relief valve comprises.
  • a hydraulic suspension system that cushions the boom or the rocker to achieve overall on the vehicle improved suspension comfort, especially while driving.
  • the lifting side of a hydraulic cylinder is connected to a hydraulic accumulator to effect a suspension through the hydraulic accumulator.
  • the lowering side of the hydraulic cylinder is connected to a hydraulic tank to prevent on the one hand cavitation on the lower side and on the other to allow free movement of the piston rod during the suspension process.
  • these suspension systems to protect the hydraulic cylinder against hose breaks, with Load holding valves or pipe rupture protection devices provided.
  • a hydraulic arrangement for a suspension system according to the preamble of claim 1 is in the EP 1 157 963 A2 disclosed. It is proposed a suspension system for the boom of a telehandler, which provides for securing the boom against sinking a load-holding valve or a pipe rupture device. On the one hand to obtain a pressurized lowering of the boom, which requires opening the load-holding valve, and on the other hand to provide a suspension function in the neutral position of the hydraulic cylinder, a separate switching valve is arranged. For opening the load-holding valve, a pressure limiting valve is provided which can be opened via a control pressure line connected to the supply line of the lowering side of the hydraulic cylinder.
  • the separate switching valve To open the load-holding valve then the separate switching valve must be closed, so that the supply line to the tank is closed and can build up to the opening of the load-holding valve pressure in the supply line.
  • a disadvantage is that the pressure to be applied to open the pressure limiting valve requires a relatively high hydraulic power, which must be applied each time the hydraulic cylinder is lowered under pressure.
  • precise positioning is achieved when the boom is lowered more difficult because the required opening pressure on the lowering side of the hydraulic cylinder also leads indirectly to a pressure load of the hydraulic accumulator, which then then relaxes again, which in turn is associated with a movement of the hydraulic cylinder.
  • the object underlying the invention is seen to improve a suspension system of the type mentioned in such a way that a pressurized lowering of the hydraulic cylinder can be done at lower hydraulic power and precise positioning of the boom when lowering is enabled with suspension enabled.
  • a hydraulic arrangement of the aforementioned type is designed such that the first control pressure line extends between the pipe rupture protection device and a conveyor and switching means are arranged in the first control pressure line, so that by switching the switching means, the first control pressure line acted upon by a control pressure and the pressure relief valve aufêtbar is.
  • the pipe rupture protection device preferably comprises a check valve closing in the direction of the control device and is arranged in a bypass line bypassing the pressure limiting valve.
  • the pressure limiting valve is via a pressure line from the first supply line forth or via the first control pressure line by means of a control pressure, which by a Pressure generating conveyor is generated, auf queenbar.
  • a control pressure generating conveyor either the supply of the hydraulic cylinder provided funding or a separately provided funding can be used.
  • the pressure relief valve has a first control pressure line, which is not connected to a supply line of the hydraulic cylinder, the pressure relief valve can be operated independently of the pressure prevailing in a second chamber of the hydraulic cylinder pressure, ie be controlled.
  • the separate from a second chamber of the hydraulic cylinder pressurizing the first control pressure line allows a Aufberichtn the pressure relief valve at relatively low hydraulic pressure, so that a pressurized lowering of the hydraulic cylinder can be done at lower hydraulic power, or even without pressurization of a second chamber of the hydraulic cylinder, for example by the Gravity of a boom operated by the hydraulic cylinder.
  • the hydraulic arrangement according to the invention is also suitable as a hydraulic suspension system for a single-acting hydraulic cylinder.
  • the hydraulic arrangement has coupling means which couple the first switching means to the control unit in such a way that a switching position of the first switching means, in which pressurization of the first control pressure line is effected, occurs synchronously with a lowering position of the control unit. This ensures that as soon as the control unit is switched to a lowered position, the pressure limiting valve opens and the hydraulic oil located in the first chamber can escape when the hydraulic cylinder is lowered.
  • control unit is hydraulically switchable and is also connected via control pressure lines.
  • the coupling means can then be designed as a second control pressure line extending between the first control pressure line and the control device, so that pressurization of the second control pressure line takes place by pressurizing the first control pressure line.
  • the first switching means are coupled to the control unit, so that the control pressure generated to open the pressure relief valve is also the applied to switch the control unit in the lowering position control pressure.
  • the hydraulically switchable control device preferably has a third control pressure line, by means of which it can be switched into the lifting position.
  • second switching means are provided in the third control pressure line, via which the third control pressure line can be acted upon with pressure.
  • the switching means are designed as proportional switching valves, in particular pressure reducing valves, by which either a connection of the control pressure lines to the hydraulic tank or to a conveyor can be produced, wherein the switching means mechanically, electrically, hydraulically or pneumatically actuated or can be controlled and proportional to a control signal From a preferably closed first switching position, are switched or moved in an open second switching position.
  • the second switching position is variable or controllable proportional to the control signal, so that a pressure reduction proportional to the control signal can take place.
  • the switching means may also be designed as a hydraulic actuating device in the form of a joystick, wherein a simultaneous hydraulic supply of the first and second control pressure line is established as soon as the joystick is moved into a position provided for the lowering position of the control unit.
  • a simultaneous hydraulic supply of the first and second control pressure line is established as soon as the joystick is moved into a position provided for the lowering position of the control unit.
  • the third control pressure line of the control unit is pressurized and at the same time the hydraulic supply of the first and second control pressure line is interrupted.
  • the hydraulic supply of the first, second and third control pressure lines is interrupted, so that the control unit can assume the neutral position, for example by prestressed control springs.
  • the coupling means comprise an actuator for the first Switching means.
  • the switching means are brought into an open or in a closed position in dependence on the switching position of the control device.
  • a third control pressure line for example in the case of an electrically or mechanically connected control unit, so that only the switching means for the first control pressure line have to be actuated.
  • the actuating device for the first switching means may be designed, for example, mechanically, via a pushbutton / plunger combination, or also electrically, for example via a switch or sensor.
  • an angle or position sensor can be used, which detects the switching position of the control device or the hydraulic actuator or a joystick and generates a signal for switching the first switching means.
  • other controls should be considered, which would result for a person skilled in the art of hydraulic controls and cause the first switching means are automatically and synchronously connected to the control unit such that when switched into the lowering position of the control unit, a pressurization the first control pressure line for opening the pressure relief valve of the pipe rupture protection device takes place.
  • control device is preferably designed as a valve spool exhibiting slide valve having three switch positions, each with two inputs and outputs.
  • the supply lines in different ways according to the switching positions (lifting, lowering and neutral position (holding)) with the Conveyor or connected to the hydraulic tank or closed.
  • the first switching means are switched in response to the switching positions of the control unit via the actuating device.
  • the valve slide may be connected to a switching element, for example with a button, a control arm, a lever, a lock slider or the like, which actuates a switch provided on the first switching means actuating plunger or switch.
  • the switching means can for example also be connected via a cable with the valve spool, through which, when moving the valve spool, the adjusting means from a biased position (for example, by a spring) is moved.
  • the control unit can be designed as a hydraulically, electrically or mechanically operable control device, wherein the valve spool can be hydraulically, electrically or mechanically displaceable in a known manner.
  • a hydraulic arrangement according to the invention with suspension function is, as already mentioned above, both for a hydraulic cylinder acting on one side, ie for a hydraulic cylinder with only one pressurizable chamber, and for a double-acting or double-acting hydraulic cylinder, ie for a hydraulic cylinder with two pressurizable chambers , advantageously usable.
  • the hydraulic cylinder may have a second chamber which is supplied by a second supply line.
  • a second hydraulic line is then arranged between the second chamber and the hydraulic tank. In a spring movement of the hydraulic cylinder can then in the second chamber located hydraulic oil flow into the hydraulic tank.
  • the hydraulic assembly may further include a second switching valve disposed in the second hydraulic line.
  • the second switching valve can be used to close the second hydraulic line to the tank, so that the second chamber can be pressurized by the control unit, both with activated and deactivated suspension. This is advantageous if, for example, one wishes to generate a contact pressure for a working tool fastened to a boom actuated by the hydraulic cylinder or to lower the hydraulic cylinder or the arm under pressure.
  • the first and the second switching valve preferably have a closed position and an open position, wherein the first and the second switching valve close in the closed position in one or both flow directions, but open in the open position in both flow directions, so that a suspension function in conjunction with the Hydraulic accumulator or enters with the hydraulic tank.
  • the first and the second switching valve may be formed such that they close in the closed position only in the direction of the hydraulic accumulator or the hydraulic tank.
  • the first and the second switching valve are preferably electrically actuated. It is of course also conceivable that other types of actuation are used for the first and second switching valve, for example a manual, pneumatic or hydraulic actuation.
  • a hydraulic arrangement according to the invention with a suspension function is suitable, for example, for lifting and Lowering a boom of a charger, such as a wheel loader, front loader, crane or telescopic loader, such chargers are found in agriculture, construction or in forestry.
  • a charger such as a wheel loader, front loader, crane or telescopic loader, such chargers are found in agriculture, construction or in forestry.
  • the suspension should be activated, which can be done by means of a switch that operates in the cab of the charger, or for example, by a speed signal, the first and the second switching valve is brought into their open positions to the first chamber of the hydraulic cylinder to connect with the hydraulic accumulator and the second chamber of the hydraulic cylinder to the hydraulic tank.
  • jerky accelerations can be damped by the free swinging of the jib or the rocker, so that an increase in driving comfort can be achieved.
  • the first control pressure line is automatically pressurized, so that the pipe rupture device or the pressure relief valve is opened, which is essential for lowering the boom or rocker.
  • FIG. 1 illustrated hydraulic arrangement 10 shows an inventive embodiment for the realization of a suspension.
  • the hydraulic arrangement 10 comprises a hydraulically switchable control unit 12, which, for example, as a Slider valve formed with a valve spool 13 and is connected via hydraulic lines 14, 16 with a pump 18 and a hydraulic tank 20, wherein the control unit 12 in three operating positions, lifting, neutral and lowered position, can be switched.
  • a hydraulically switchable control unit 12 which, for example, as a Slider valve formed with a valve spool 13 and is connected via hydraulic lines 14, 16 with a pump 18 and a hydraulic tank 20, wherein the control unit 12 in three operating positions, lifting, neutral and lowered position, can be switched.
  • the control unit 12 Via a first and second supply line 22, 24, the control unit 12 is connected to a hydraulic cylinder 26, wherein the first supply line 22 leads into a first chamber 28 of the hydraulic cylinder 26 and the second supply line 24 into a second chamber 30 of the hydraulic cylinder 26.
  • a piston 29 separates the two chambers 26, 28 from each other.
  • the first chamber 28 of the hydraulic cylinder 26 represents the piston bottom side and the stroke side chamber, whereas the second chamber 30 represents the piston rod side and the lower side chamber of the hydraulic cylinder.
  • a load-holding valve arrangement or pipe rupture protection device 32 is provided in the first supply line 22.
  • the pipe burst protection device 32 includes a pressure and spring-controlled pressure limiting valve 34, and a check valve 36 which opens to the hydraulic cylinder side and which is arranged via a bypass line 38 parallel to the pressure limiting valve 34.
  • a pressure line 40 a pressure connection from the pressure relief valve 34 to the hydraulic cylinder side portion of the first supply line 22 is made.
  • a first control pressure line 42 a pressure connection from the pressure relief valve 34 to the pump 18 is established.
  • a spring 44 holds the pressure relief valve 34 in the closed position.
  • a first hydraulic line 46 connects the first chamber 28 and the first supply line 22 to a hydraulic accumulator 48, wherein the not connected to the hydraulic accumulator 48 end 50 of the first hydraulic line 46 between the first chamber 28 and the pipe rupture protection device 32 is arranged.
  • a first switching valve 52 is arranged in the first hydraulic line 46.
  • the first switching valve 52 is an electrically switchable seat valve, which is held by a spring 54 in the closed position and can be brought via a solenoid 56 in an open position.
  • the first switching valve 52 seals in the closed position in the direction of the hydraulic accumulator 48.
  • the first switching valve 52 may also be designed such that it seals leak-free in both directions. In the open position, a hydraulic flow in both directions is ensured to produce a suspension function between the hydraulic cylinder 26 and the hydraulic accumulator 48.
  • a second hydraulic line 46 ' connects the second chamber 30 and the second supply line 24 to the hydraulic tank 20.
  • a second switching valve 52' is arranged in the second hydraulic line 46 '.
  • the second switching valve 52 ' is an electrically switchable seat valve, which is held in the closed position by a spring 54' and can be brought into a open position via a magnetic coil 56 '.
  • the second switching valve 52 ' may also be designed such that it seals leak-free in both directions. In the open position is ensures a hydraulic flow in both directions to establish a connection between the second chamber 30 of the hydraulic cylinder 26 and hydraulic tank 20.
  • first switching means 58 are arranged, which have a first switching position and at least a second switching position, wherein in the at least second switching position, a pressure reduction is infinitely variable.
  • the first switching means 58 are preferably connected electronically, wherein the first control pressure line 42 in the first switching position (as in FIG. 1 shown) with the tank 20 and in the second switching position with the pump 18 is connectable.
  • the hydraulic arrangement according to the invention also has coupling means which couple or connect the first switching means 58 and the control unit 12 or synchronize their switching operations.
  • the coupling means are in the form of a second control pressure line 60, which extends from the first control pressure line 42 to the control unit 12, so that upon pressurization of the first control pressure line 42 and the second control pressure line 60 is pressurized.
  • the second control pressure line 60 is arranged such that when pressure is applied, the control unit 12 or the valve slide 13 is switched or moved into the lowered position.
  • the control unit 12 is further provided with a third control pressure line 62.
  • the third control pressure line 62 formed as a pressure reducing valve second switching means 64 are arranged, which a first Switching position and have at least a second switching position, wherein in the at least second switching position, a pressure reduction is infinitely variable.
  • the second switching means 64 are preferably switched electronically, wherein the third control pressure line 62 in the first switching position (as in FIG. 1 shown) with the tank 20 and in the second switching position with the pump 18 connects.
  • the third control pressure line 62 is arranged such that, when pressure is applied, the control unit 12 or the valve slide 13 is switched or moved into the lifting position.
  • the individual operating states can now be controlled as follows via the control unit 12 and via the switching valves 52, 52 '.
  • the control unit 12 is held in neutral position by adjusting springs 70, 72, wherein the first and second switching means 58, 64 are each in their first switching position.
  • the connection of the first supply line 22 to the pump 18 and the connection of the second supply line 24 to the hydraulic tank 20 is made.
  • a corresponding switching signal is generated by the control device 76, whereby the second switching means 64 are switched and a controlled according to the control signal pressurization of the third control pressure line 62 takes place.
  • the control unit 12 and the valve slide 13 is brought into the lifting position.
  • the first chamber 28 of the hydraulic cylinder 26 is then filled via the first supply line 22 and via the check valve 36 of the pipe rupture protection device 32 (the pressure relief valve 34 of the load-holding arrangement 32 is in the closed position).
  • the piston 29 moves in the direction of the second chamber 30 and presses the oil present there through the second supply line 24 out into the hydraulic tank 20.
  • a corresponding switching signal for switching to the neutral position (holding position) can be generated , whereby the second switching means 64 are moved back into their first switching position, a pressure relief of the third control pressure line 62 to the tank takes place and the control unit 12 assumes the neutral position (holding position).
  • the controller 12 interrupts the connections to the pump 18 and the hydraulic tank 20, so that the pressure in the two chambers 28, 30 of the hydraulic cylinder 26 is maintained and the movement of the piston 29 is released.
  • the piston 29 stops or is held.
  • the connection of the first supply line 22 to the tank 20 and the connection of the second supply line 24 to the pump 18 is made.
  • a corresponding switching signal is generated by the control device 76, whereby the first switching means 58 are switched and a controlled according to the control signal pressurization of the first and second control pressure line 42, 60 takes place.
  • the control unit 12 or the valve slide 13 is brought into the lowered position.
  • the second chamber 30 of the hydraulic cylinder 26 is then filled via the second supply line 24.
  • the pressure relief valve 34 is opened.
  • the piston 29 moves in the direction of the first chamber 28 and pushes the existing there oil via the open pressure relief valve 34 through the second supply line 22 out in the hydraulic tank 20.
  • a corresponding switching signal for switching to the neutral position (Stop position) are generated, whereby the first switching means 58 are moved back to their first switching position, a pressure relief of the first and second control pressure line 42, 60 takes place towards the tank and the control unit 12 assumes the neutral position (holding position).
  • the controller 12 interrupts the connections to the pump 18 and the hydraulic tank 20, so that the pressure in the two chambers 28, 30 of the hydraulic cylinder 26 is maintained and the movement of the piston 29 is released.
  • the piston 29 stops or is held.
  • the pipe rupture device 32 thus ensures that the hydraulic cylinder 26 maintains its position in the neutral position or escape oil in the lifting and neutral position from the pressurized first chamber 28 and that in the lowered position, the oil from the first chamber 28 can flow through the open pressure relief valve 34 ,
  • the pipe rupture protection device 32 should or should be arranged on the lifting side of the hydraulic cylinder 26, as shown, with the lifting side being the side of the hydraulic cylinder 26 in which a pressure for lifting a load is built up.
  • the lifting side is the first chamber 28 of the hydraulic cylinder 26, wherein the second chamber 30 could serve as a lifting side.
  • the excess pressure line 40 is an overload protection, so that at excessive operating pressures in the first chamber 28 of the hydraulic cylinder 26, which may be caused by excessive loads, for example, in the pressure line 40, a limiting pressure is reached, which opens the pressure relief valve 34 to reduce pressure.
  • the positions of the controller 12 can be detected and a signal to the electronic control device 76 are sent.
  • the control unit 76 is connected to the first and second switching valves 52, 52 '.
  • the activation of the suspension via an activation switch 82, which outputs an activation signal to the control unit 76.
  • the piston 29 When activated suspension function, the piston 29 can spring freely. If it moves downwards by a shock transmitted to it, the oil from the first chamber 28 in the Hydraulic accumulator 48 pushed. The pressure building up in the hydraulic accumulator 48 causes the oil to flow back into the first chamber 28, so that the piston 29 moves upward again. This resilient movement is repeated, if necessary, until the shock has been completely compensated.
  • FIG. 2 shows a mobile telescopic loader 83 with a on a housing 84 or frame of the telehandler 83 pivotally hinged, telescopically extendable, boom 86. Between boom 86 and housing 84, a hydraulic cylinder 26 for raising and lowering of the boom 86 is arranged. The hydraulic cylinder 26 is pivoted to a first and a second bearing 88, 90, wherein the piston rod side 92 is hinged to the second bearing point 90 on the arm 86 and the piston bottom side 94 at the first bearing 88 on the housing 84.
  • the hydraulic tank 20, the pump 18 and the control unit 12 are positioned on or in the housing 84 and connected to each other via hydraulic lines 14, 16, 96. Furthermore, the supply lines 22, 24 between the control unit 12 and hydraulic cylinder 26 in Fig. 2 to see.
  • the pipe burst protection device 32 and the switching valve 52 are located in a common valve block directly on the hydraulic cylinder 26.
  • the hydraulic accumulator 48 is preferably also disposed directly on the hydraulic cylinder 26, so that between the common valve block and the hydraulic accumulator 48, the first hydraulic line 46 can be formed as a rigid connection that does not require a separate breakaway device. According to the switching positions described above, the hydraulic cylinder 26 can be operated such that the boom 86 can be raised, held and lowered and possibly perform resilient movements.
  • FIG. 3 an alternative embodiment is shown, which, in contrast to the in FIG. 1 illustrated embodiment, an electronically controllable or switchable control unit 112, wherein the control unit 112 also includes a slide valve with a valve spool 113.
  • the control unit 112 may also be designed as a hydraulically or mechanically controllable control unit.
  • the control unit can also be actuated here via an electronic control device 76 or via a joystick or a similar control device.
  • the hydraulic arrangement 110 shown here further corresponds to the in FIG. 1 illustrated arrangement 10 described above, unless it is pointed to corresponding differences.
  • In the FIG. 3 also has a first control pressure line 42 which extends between the pressure relief valve 34 of a pipe rupture device 32 and a conveyor or pump 18.
  • first switching means 114 are also arranged, which are designed as a switching valve, in particular pressure reducing valve.
  • An essential difference to that in FIG. 1 illustrated embodiment is that in FIG. 3 the first switching means 58 from FIG. 1 be replaced by first switching means 114 and mechanical coupling means between the first switching means 114 and the control unit 112 are arranged.
  • the control unit 112 according to the in FIG.
  • the coupling means are formed as a mechanical actuator 116 for the first switching means 114, wherein the actuating means 116 bring the first switching means 114 in response to or proportional to the switching position of the controller 112 and the valve spool 113 in a first or second switching position, wherein in the second Switching one of the movement of the controller 112 and the valve spool 113 proportional pressure reduction in the first control pressure line is carried out.
  • a connection of the control pressure line 42 to the pump 18 is interrupted, in the second switching position, a connection of the control pressure line 42 is made to the pump 18, so that the control pressure line 42 is pressurized.
  • the dependence on the switching position of the controller 112 and the valve spool 113 is such that when the controller 112 and the valve spool 113 is brought into the lowered position (lowermost switching position of the controller 112 in FIG. 3 ), the actuating device 116 brings the first switching means 114 in the second switching position, so that the control pressure line 42 is pressurized and the Pressure relief valve 34 is opened.
  • the first switching means 114 are returned to the first switching position.
  • the actuating device 116 has a locking slide 118 which is in contact or interacts with an actuating tappet 120 arranged on the first switching means 114.
  • the actuating push rod 120 is pressed or actuated, whereby the first switching means 114 are brought into the second switching position.
  • the actuating push rod 120 is relieved of the control slide 118 or moves back again, so that the first switching means 114 again assume their first switching position.
  • the actuating device 116 By the coupling of the movement or the switching operation of the control device 112 and the valve spool 113, which is given by the actuating device 116, it is thus ensured that, as soon as the lowering position is assumed for the hydraulic cylinder 26, the pressure relief valve 34 synchronous and proportional to the movement the control valve is turned on, so that the oil can escape from the first chamber 28 when lowering the piston 29. At the same time, however, a pipe rupture protection function is ensured. Furthermore, it is conceivable to form the actuating device 116 also electrically. For example, by the sensor 80, the position of the control device 112 and the valve spool 113 can be detected. A corresponding to the position proportional signal can then be generated by the electronic control device 76 and used to control the first switching means 114, wherein the first switching means 114 are then formed as electronically controllable switching means or pressure reducing valve.
  • FIG. 3 illustrated embodiment may according to the in FIG. 1 illustrated embodiment also on the in FIG. 2 Telehandlers 83 are used.
  • the inventive arrangement of the first control pressure line 42 for the pressure relief valve 34 of the pipe rupture protection device 32, based on two embodiments with respect to the FIGS. 1 and 3 has been described, it is ensured that the boom can be lowered independently of a pressure prevailing in the second chamber, whereby a better power output, in particular with respect to a hydraulic power at idle speed of the telehandler 83, can be achieved. Furthermore, a more precise positioning can be achieved when lowering the boom when the suspension is activated.
  • first and second switching means 58, 114, 64 can be actuated or controlled mechanically, electrically, hydraulically or pneumatically and in proportion to a switching signal or control signal from a preferably closed first switching position to an opened second switching position be switched or moved.
  • the second switching position is variable proportional to the switching signal or control signal or controllable, so that a pressure reduction proportional to the switching signal or control signal can take place.
  • hydraulic arrangement can also be applied to other vehicles, for example to wheel loaders or front loaders or to excavators or cranes, which have hydraulically actuated components that can be raised or lowered and where a suspension seems useful.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Civil Engineering (AREA)
  • Structural Engineering (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Mining & Mineral Resources (AREA)
  • Fluid-Pressure Circuits (AREA)
  • Vehicle Body Suspensions (AREA)
  • Lubricants (AREA)

Claims (19)

  1. Système hydraulique pour un système de suspension, comportant un vérin hydraulique (26), qui contient au moins une première chambre (28), une cuve hydraulique (20), au moins un moyen de transport (18) transportant le liquide hydraulique, un réservoir hydraulique (48), une première conduite hydraulique (46) disposée entre le réservoir hydraulique (48) et la première chambre (28), une première vanne de commande (52), montée dans la première conduite hydraulique (46), une première conduite d'alimentation (22) pour la première chambre (28), un dispositif de commande (12, 112) avec au moins trois positions de commande, à savoir une position de levage, une position d'abaissement et une position neutre pour le vérin hydraulique (26), et un dispositif anti-rupture de tube (32), qui est monté dans la première conduite d'alimentation (22) et qui comporte un clapet de non-retour (36) fermant vers le dispositif de commande (12, 112) et un limiteur de pression (34) dont l'ouverture est commandée par une première conduite de pression de commande (42), caractérisé en ce que la première conduite de pression de commande (42) est disposée entre le dispositif anti-rupture de tube (32) et un moyen de transport (18), et des premiers moyens de commande (58, 114) sont disposés dans la première conduite de pression de commande (42), de telle sorte que, sous l'effet de la commande des premiers moyens de commande (58, 114), la première conduite de pression de commande (42) peut recevoir une pression de commande et le limiteur de pression (34) peut s'ouvrir.
  2. Système hydraulique selon la revendication 1, caractérisé en ce qu'il est prévu des moyens de couplage, par lesquels les premiers moyens de commande (58, 114) sont couplés au dispositif de commande (12, 112) de telle sorte qu'une position de commande des premiers moyens de commande (58, 114), dans laquelle la première conduite de pression de commande (42) est alimentée en pression, se produit de manière synchrone à une position d'abaissement du dispositif de commande (12, 112).
  3. Système hydraulique selon la revendication 1 ou 2, caractérisé en ce que le dispositif de commande (12, 112) peut être commandé par voie hydraulique et les moyens de couplage comportent une deuxième conduite de pression de commande (60) qui est disposée entre la première conduite de pression de commande (42) et le dispositif de commande (12, 112), de telle sorte qu'une admission de pression dans la deuxième conduite de pression de commande (60) est effectuée sous l'effet d'une admission de pression dans la première conduite de pression de commande (42).
  4. Système hydraulique selon l'une quelconque des revendications 1 à 3, caractérisé en ce que le dispositif de commande (12, 112) comporte une troisième conduite de pression de commande (62), prévue pour commander le dispositif de commande (12, 112) dans la position de levage, des deuxièmes moyens de commande (64) étant disposés dans la troisième conduite de pression de commande (62).
  5. Système hydraulique selon la revendication 4, caractérisé en ce que les deuxièmes moyens de commande (64) comportent une vanne de commande proportionnelle, en particulier une vanne de diminution de pression, qui permet d'établir au choix une liaison entre la troisième conduite de pression de commande (62) et la cuve hydraulique (20) ou un moyen de transport (18).
  6. Système hydraulique selon l'une quelconque des revendications 1 à 5, caractérisé en ce que les premiers moyens de commande (58, 114) comportent une vanne de commande proportionnelle, en particulier une vanne de diminution de pression, qui permet d'établir au choix une liaison entre la première conduite de pression de commande (42) et la cuve hydraulique (20) ou un moyen de transport (18).
  7. Système hydraulique selon l'une quelconque des revendications 1 à 6, caractérisé en ce que les moyens de commande (58, 114, 64) peuvent être actionnés par voie mécanique, électrique, hydraulique ou pneumatique.
  8. Système hydraulique selon l'une quelconque des revendications 1 à 7, caractérisé en ce que les premiers moyens de commande (58, 114) sont réalisés sous la forme d'un joystick hydraulique, une alimentation hydraulique de la première et de la deuxième conduites de pression de commande (42, 60) pouvant être établie dès que les premiers moyens de commande (58, 114) sont déplacés dans une position prévue pour la position d'abaissement du dispositif de commande (12, 112).
  9. Système hydraulique selon l'une quelconque des revendications 4 à 8, caractérisé en ce que les deuxièmes moyens de commande (64) sont réalisés sous la forme d'un joystick hydraulique, une alimentation hydraulique de la troisième conduite de pression de commande (62) pouvant être établie dès que les deuxièmes moyens de commande (64) sont déplacés dans une position prévue pour la position de levage du dispositif de commande (12, 112).
  10. Système hydraulique selon l'une quelconque des revendications 2 à 9, caractérisé en ce que les moyens de couplage comportent un dispositif d'actionnement (116) pour les premiers moyens de commande (114), lequel, en fonction de la position de commande ou proportionnellement à la position de commande du dispositif de commande (112), amène les premiers moyens de commande (114) dans une première ou une deuxième position de commande.
  11. Système hydraulique selon la revendication 10, caractérisé en ce que le dispositif d'actionnement (116) comporte un capteur angulaire ou capteur de position.
  12. Système hydraulique selon la revendication 10 ou 11, caractérisé en ce que le dispositif de commande (112) comporte un tiroir de vanne (113), et le dispositif d'actionnement (116) comporte un élément de commande (118), relié au tiroir de vanne (113), et un poussoir (120) réalisé sur le premier moyen de commande (114), le poussoir (120) pouvant être actionné par l'élément de commande (118) sous l'effet d'un déplacement du tiroir de vanne (113).
  13. Système hydraulique selon l'une quelconque des revendications 1 à 12, caractérisé en ce que le vérin hydraulique (26) comporte une deuxième chambre (30), et il est prévu une deuxième conduite d'alimentation (24) pour la deuxième chambre (30), et en ce qu'une deuxième conduite hydraulique (46') est disposée entre la deuxième chambre (30) et la cuve hydraulique (20).
  14. Système hydraulique selon la revendication 13, caractérisé en ce qu'il est prévu une deuxième vanne de commande (52'), montée dans la deuxième conduite hydraulique (46').
  15. Système hydraulique selon l'une quelconque des revendications 1 à 13, caractérisé en ce que la première et la deuxième vannes de commande (52, 52') ont une position de fermeture et une position d'ouverture.
  16. Système hydraulique selon l'une quelconque des revendications 1 à 15, caractérisé en ce que la première vanne de commande (52) dans la position de fermeture ferme la liaison vers le réservoir hydraulique (48).
  17. Système hydraulique selon l'une quelconque des revendications 14 à 16, caractérisé en ce que la deuxième vanne de commande (52') dans la position de fermeture ferme la liaison vers la cuve hydraulique (20).
  18. Système hydraulique selon l'une quelconque des revendications 14 à 17, caractérisé en ce qu'il est prévu des moyens (76, 80), qui amènent la deuxième vanne de commande (52') dans une position de fermeture lorsque le dispositif de commande (12, 112) est amené dans une position d'abaissement.
  19. Chargeuse, en particulier chargeuse télescopique (83), comportant un bras (86) et un système hydraulique (10, 110) selon une des revendications précédentes pour relever et abaisser le bras (86).
EP05112498A 2005-08-11 2005-12-20 Agencement hydraulique Not-in-force EP1752587B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102005038333A DE102005038333A1 (de) 2005-08-11 2005-08-11 Hydraulische Anordnung

Publications (2)

Publication Number Publication Date
EP1752587A1 EP1752587A1 (fr) 2007-02-14
EP1752587B1 true EP1752587B1 (fr) 2008-06-11

Family

ID=36190729

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05112498A Not-in-force EP1752587B1 (fr) 2005-08-11 2005-12-20 Agencement hydraulique

Country Status (4)

Country Link
US (1) US7337610B2 (fr)
EP (1) EP1752587B1 (fr)
AT (1) ATE398213T1 (fr)
DE (2) DE102005038333A1 (fr)

Families Citing this family (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102004056418B4 (de) * 2004-11-23 2013-02-28 Deere & Company Hydraulische Anordnung
DE102005033154A1 (de) * 2005-07-13 2007-01-18 Deere & Company, Moline Hydraulische Anordnung
FR2903155B1 (fr) * 2006-07-03 2008-10-17 Poclain Hydraulics Ind Soc Par Circuit hydraulique de recuperation d'energie
TWI490513B (zh) * 2006-12-29 2015-07-01 Intest Corp 用於使負載沿平移軸線平移之負載定位系統以及使負載達到平衡之方法
US8267004B2 (en) * 2009-05-20 2012-09-18 Lifetime Enterprises, Llc Adaptable hydraulic control system
CN104254694B (zh) * 2012-01-05 2017-05-10 派克汉尼芬公司 带有浮动功能的电液***
DE102012106185B3 (de) * 2012-07-10 2013-11-21 Fsp Fluid Systems Partners Holding Ag Steueranordnung für ein hydropneumatisches Federungssystem sowie hydropneumatisches Federungssystem mit einer solchen Steueranordnung
CN102979778A (zh) * 2012-12-07 2013-03-20 中联重科股份有限公司 三位六通换向阀、液压控制***及工程车辆
US20150047331A1 (en) * 2013-08-14 2015-02-19 Caterpillar Inc. Hydraulic system for machine
DE102014216682A1 (de) * 2014-08-21 2016-02-25 Jungheinrich Aktiengesellschaft Nachrüstung eines Sicherheitsventils bei einem gewerblichen Fahrzeug zur Erfüllung von Sicherheitsanforderungen betreffend den Senkbetrieb einer Hubvorrichtung und ein entsprechendes gewerbliches Fahrzeug
CN104278703B (zh) * 2014-09-28 2017-01-11 中外合资沃得重工（中国）有限公司 挖掘机动臂减震液压控制装置
CN107131168A (zh) * 2017-05-19 2017-09-05 青神格林维尔流体动力控制技术有限公司 一种差动油缸控制的插装式集成块
WO2019198579A1 (fr) * 2018-04-09 2019-10-17 イーグル工業株式会社 Circuit de pression de fluide
EP3951073A4 (fr) * 2019-04-05 2022-12-07 Volvo Construction Equipment AB Machine hydraulique
KR20210136086A (ko) 2019-04-05 2021-11-16 볼보 컨스트럭션 이큅먼트 에이비 유압기계
US20200399859A1 (en) * 2019-06-18 2020-12-24 Deere & Company Hydraulic Accumulator Assembly
CN111677702B (zh) * 2020-06-29 2024-05-03 广西玉柴机器股份有限公司 一种重型油缸行程可调***及安全可调控制方法
CN111997947B (zh) * 2020-08-31 2023-08-29 徐州徐工矿业机械有限公司 一种正铲挖掘机开闭斗的液压***
DE102020131046A1 (de) 2020-11-24 2022-05-25 Buchholz Hydraulik Gmbh Hydraulisches Hubsystem
CN112780627B (zh) * 2021-03-03 2022-12-20 徐州威世泽机电设备有限公司 一种多路阀及液压***

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE68918930T2 (de) * 1989-02-06 1995-03-23 Kobe Steel Ltd Vorrichtung zur Unterdrückung von Vibrationen für Baumaschinen auf Rädern.
JPH0815998B2 (ja) * 1989-10-14 1996-02-21 株式会社神戸製鋼所 ホイール式クレーンの振動抑制装置
JPH08302753A (ja) * 1995-05-12 1996-11-19 Hitachi Constr Mach Co Ltd 油圧建設機械
DE19734658A1 (de) * 1997-08-11 1999-02-18 Mannesmann Rexroth Ag Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader
DE19754828C2 (de) * 1997-12-10 1999-10-07 Mannesmann Rexroth Ag Hydraulische Steueranordnung für eine mobile Arbeitsmaschine, insbesondere für einen Radlader, zur Dämpfung von Nickschwingungen
US6357230B1 (en) * 1999-12-16 2002-03-19 Caterpillar Inc. Hydraulic ride control system
GB2365407B (en) * 2000-05-25 2003-10-08 Bamford Excavators Ltd Hydraulic system for wheeled loader
US7204086B2 (en) * 2000-05-25 2007-04-17 J.C Bamford Excavators Limited Method of operating a hydraulic system for a loader machine
DE10133616A1 (de) * 2001-07-13 2003-01-30 Bosch Rexroth Ag Hydraulische Steueranordnung
ES2289436T3 (es) * 2003-07-05 2008-02-01 DEERE & COMPANY Suspension hidraulica.
DE10330344A1 (de) * 2003-07-05 2005-02-24 Deere & Company, Moline Hydraulische Federung
DE102004012362A1 (de) * 2004-03-13 2005-09-22 Deere & Company, Moline Hydraulische Anordnung

Also Published As

Publication number Publication date
ATE398213T1 (de) 2008-07-15
US20070033933A1 (en) 2007-02-15
US7337610B2 (en) 2008-03-04
DE502005004413D1 (de) 2008-07-24
EP1752587A1 (fr) 2007-02-14
DE102005038333A1 (de) 2007-02-15

Similar Documents

Publication Publication Date Title
EP1752587B1 (fr) Agencement hydraulique
EP1574626B1 (fr) Système hydraulique de suspension passive
EP1743981A1 (fr) Agencement hydraulique
DE102004056418B4 (de) Hydraulische Anordnung
EP0615583B1 (fr) Recuperateur d'energie
EP1897847B1 (fr) Appareil de chargement
DE102004012382B4 (de) Hydraulische Anordnung
DE102009025827A1 (de) Hydraulikschaltvorrichtung für die Mobilhydraulik, mobile Hydraulikmaschine und Ventileinheit
DE4438899C1 (de) Energierückgewinnungsvorrichtung
EP1003939B1 (fr) Dispositif de commande hydraulique destine a une machine de travail mobile, notamment a une chargeuse a roues
DE19951498B4 (de) Vorrichtung und Verfahren zur Steuerung eines strömungsmittelbetätigten Schnellkupplungssystems
DE102013102069A1 (de) Proportional-Wegeventil sowie hydraulische Schaltung und hydropneumatisches Federungssystem mit einem derartigen Ventil
DE202004017743U1 (de) Fahrsteuerschaltung für eine Arbeitsmaschine
EP2108746B1 (fr) Outil de travail et système d'évacuation d'urgence
DE3739525C2 (fr)
DE102006024731B3 (de) Verfahren zur lagegerechten Ausrichtung einer an einem heb- und senkbaren Hubgerüst einer Arbeitsmaschine kippbar angeordeten Arbeitausrüstung sowie Arbeitsmaschine
EP3305611B1 (fr) Dispositif de freinage
EP4367405A1 (fr) Dispositif d'actionnement pour au moins une charge entraînée par fluide
DE2723305A1 (de) Verriegelbare hydropneumatische federung, insbesondere fuer die vorderachse von radladern o.dgl.
EP2157319B1 (fr) Commande hydraulique pour un moteur hydraulique
DE2834480C2 (de) Steuereinrichtung eines Schaufelladers od.dgl.
DE10331533B4 (de) Steuer- und Stellsystem für ein Hub- und Kippwerk eines Arbeitswerkzeugs in einer mobilen Arbeitsmaschine
DE102016224401A1 (de) Arbeitshydrauliksystem und Fahrzeug mit dem Arbeitshydrauliksystem
EP3213941A1 (fr) Dispositif de commande d'un arbre oscillant, bloc d'arbre oscillant et machine de travail mobile comprenant au moins un arbre oscillant
WO2005052266A1 (fr) Systeme de commande hydraulique pour engin mobile

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

AX Request for extension of the european patent

Extension state: AL BA HR MK YU

17P Request for examination filed

Effective date: 20070814

AKX Designation fees paid

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU LV MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

RIN1 Information on inventor provided before grant (corrected)

Inventor name: BITTER, MARCUS

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REF Corresponds to:

Ref document number: 502005004413

Country of ref document: DE

Date of ref document: 20080724

Kind code of ref document: P

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: LV

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

NLV1 Nl: lapsed or annulled due to failure to fulfill the requirements of art. 29p and 29m of the patents act
PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081011

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080911

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080922

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081111

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080911

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

26N No opposition filed

Effective date: 20090312

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20081212

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20081220

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080611

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20080912

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20091231

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20131227

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: IT

Payment date: 20131220

Year of fee payment: 9

Ref country code: FR

Payment date: 20131217

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: BE

Payment date: 20131227

Year of fee payment: 9

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20141119

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141231

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20141220

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20150831

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141231

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20141220

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005004413

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20160701