EP1812715B1 - Systeme de commande hydraulique - Google Patents

Systeme de commande hydraulique Download PDF

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Publication number
EP1812715B1
EP1812715B1 EP05799204A EP05799204A EP1812715B1 EP 1812715 B1 EP1812715 B1 EP 1812715B1 EP 05799204 A EP05799204 A EP 05799204A EP 05799204 A EP05799204 A EP 05799204A EP 1812715 B1 EP1812715 B1 EP 1812715B1
Authority
EP
European Patent Office
Prior art keywords
pressure
pressure compensator
power
control arrangement
beyond
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
EP05799204A
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German (de)
English (en)
Other versions
EP1812715A2 (fr
Inventor
Gerhard Keuper
Peter Stachnik
Heinrich Lödige
Sönke Jessen
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Bosch Rexroth AG
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Bosch Rexroth AG
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Publication of EP1812715A2 publication Critical patent/EP1812715A2/fr
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Publication of EP1812715B1 publication Critical patent/EP1812715B1/fr
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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
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/165—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for adjusting the pump output or bypass in response to demand
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/16—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors
    • F15B11/161—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load
    • F15B11/162—Servomotor systems without provision for follow-up action; Circuits therefor with two or more servomotors with sensing of servomotor demand or load for giving priority to particular servomotors or users
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/205—Systems with pumps
    • F15B2211/2053—Type of pump
    • F15B2211/20546—Type of pump variable capacity
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/20—Fluid pressure source, e.g. accumulator or variable axial piston pump
    • F15B2211/25—Pressure control functions
    • F15B2211/253—Pressure margin control, e.g. pump pressure in relation to load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/30525—Directional control valves, e.g. 4/3-directional control valve
    • F15B2211/3053—In combination with a pressure compensating valve
    • F15B2211/30535—In combination with a pressure compensating valve the pressure compensating valve is arranged between pressure source and directional control valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—Directional control characterised by the positions of the valve element
    • F15B2211/3105—Neutral or centre positions
    • F15B2211/3111—Neutral or centre positions the pump port being closed in the centre position, e.g. so-called closed centre
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/30—Directional control
    • F15B2211/31—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
    • F15B2211/315—Directional control characterised by the connections of the valve or valves in the circuit
    • F15B2211/3157—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line
    • F15B2211/31576—Directional control characterised by the connections of the valve or valves in the circuit being connected to a pressure source, an output member and a return line having a single pressure source and a single output member
    • 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
    • F15B2211/321—Directional control characterised by the type of actuation mechanically
    • F15B2211/324—Directional control characterised by the type of actuation mechanically manually, e.g. by using a lever or pedal
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/605—Load sensing circuits
    • F15B2211/6051—Load sensing circuits having valve means between output member and the load sensing circuit
    • F15B2211/6054—Load sensing circuits having valve means between output member and the load sensing circuit using shuttle valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/6306—Electronic controllers using input signals representing a pressure
    • F15B2211/6313—Electronic controllers using input signals representing a pressure the pressure being a load pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/63—Electronic controllers
    • F15B2211/6303—Electronic controllers using input signals
    • F15B2211/634—Electronic controllers using input signals representing a state of a valve
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6652—Control of the pressure source, e.g. control of the swash plate angle
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback

Definitions

  • the invention relates to a hydraulic control arrangement for controlling a plurality of consumers according to the preamble of patent claim 1 and a control method for such a hydraulic control arrangement.
  • Such hydraulic control arrangements are used in particular in mobile work equipment, such as wheel loaders or tractors to provide their consumers, such as the working hydraulics, the steering or traction drives and accessories with pressure medium.
  • a closed-center system is known in which the pressure medium supply via an electrically controlled variable displacement pump.
  • the variable displacement pump is assigned a bypass valve, via which a connection to a tank can be opened.
  • the adjustment of the variable displacement pump, the bypass valve and the closed-center valves connected upstream of the consumer is carried out electrically via control devices, inter alia as a function of the pump pressure and of the path of one of the valve slides of the closed-center valves.
  • control devices inter alia as a function of the pump pressure and of the path of one of the valve slides of the closed-center valves.
  • a so-called power beyond connection which may have a pressure line, a return line and an LS line.
  • This power-beyond connection makes the load-sensing system of the implement also usable for the attachment.
  • Such solutions are for example from the DE 102 14 850 A1 and the DE 42 39 109 C1 known. From the EP1 245 834 A1 a control arrangement according to the preamble of claim 1 is known.
  • the invention has the object to provide a control method and a hydraulic control arrangement in which at least one power beyond consumer to a power beyond connection a pressure medium supply of all consumers is improved over the known solutions.
  • the hydraulic control arrangement has a pump whose flow rate is adjustable and over which at least one consumer can be supplied with pressure medium.
  • the consumer is connected upstream of a metering orifice, via which the pressure medium volume flow to the consumer is set.
  • the pump is followed by an inlet pressure compensator, via which a connection can be opened to a tank line leading to a tank.
  • the control arrangement further has a power beyond connection to which a power beyond consumer is connected.
  • the control of the inlet pressure compensator in dependence on the largest of those load pressures applied to the consumers of Steueranordung and the power beyond consumers. D.
  • the load pressure of the power beyond consumer is used to adjust the pressure in a pump or supply line determining incoming pressure compensator, so that by their appropriate setting disturbance by the power beyond consumer is almost impossible.
  • Such disorders occur at the beginning of the described Technology especially at low load pressure and high pressure medium volume flow.
  • the pump and / or the metering orifices of the consumers are controlled in such a way that, when the power beyond consumer is supplied via the inlet pressure compensator, a predetermined residual volume flow to the tank is established in order to avoid undersupply.
  • the pump is adjusted depending on the setting of the inlet pressure compensator. This can be done for example by measuring the residual volume flow or by position sensing a slider of the inlet pressure compensator.
  • the pressure medium supply of the power beyond consumers takes place either via the inlet pressure compensator or via power beyond individual pressure compensators.
  • the inlet pressure compensator is preferably acted upon by the largest of the load pressures in the closing direction.
  • the inlet pressure compensator is then designed in a preferred embodiment, that in a spring-biased position the connection to the priority consumer and the tank is shut off and when adjusting the inlet pressure compensator in the opening direction, the connection to the priority consumer and then to the tank is aufêtbar. A sufficient supply of the priority consumer is ensured when the said residual volume flow flows to the tank.
  • a second or more power beyond consumers can be supplied with pressure medium either simultaneously or in a predetermined order of priority via the inlet pressure compensator.
  • a priority for example, the second power beyond consumers a power beyond pressure scale be upstream, in the closing direction of the force of a spring and the same control pressure as the inlet pressure compensator and in the opening direction of the at the entrance of the power beyond Pressure compensator applied pressure applied.
  • This power beyond pressure compensator opens only when the pressure medium supply of the former power beyond consumer is secured.
  • the inlet pressure compensator and the power beyond pressure compensator in the closing direction of the largest of the load pressures applied.
  • the inlet pressure compensator and the power beyond pressure compensator are loaded in the opening direction by the highest of the load pressures.
  • the inlet pressure compensator can also be acted upon in the opening direction by the highest of the load pressures, in which case the pressure downstream of the diaphragm also acts in the opening direction on the power beyond pressure compensator.
  • the pump can be designed as an electrically controllable variable displacement pump or as a variable speed fixed displacement pump.
  • the hydraulic control arrangement is embodied as an LS system, wherein each of the metering orifices assigned to a consumer is preceded by an individual pressure compensator.
  • the springs of the individual pressure compensators assigned to the consumers, the power beyond pressure compensators associated with the power beyond consumers, and the inlet pressure compensator are matched to one another such that either consumers or power beyond consumers are prioritized.
  • the opening pressure difference of the inlet pressure compensator is set to be greater than the opening pressure differential of the individual pressure compensators and the power beyond pressure compensators, wherein the opening pressure difference across the power beyond pressure compensators may be greater or smaller than that via the individual pressure compensators, depending on prioritization.
  • the adjustment of the metering orifices can be done electrically, hydraulically or mechanically.
  • the tapping of the highest of the load pressures is preferably carried out via a shuttle valve, at one input of the highest load pressure of the consumer and at the other input, the highest load pressure of the power beyond consumer is applied, so that at the output of the larger of these load pressures tapped and fed to the inlet pressure compensator can be.
  • FIG. 1 shows a hydraulic control arrangement 1 of a mobile implement, such as a tractor.
  • This control arrangement can be formed for example by a mobile control block, via which the hydraulic consumers of the working hydraulics of the working device, in the present case two double-acting cylinders 2, 4 are supplied with pressure medium, which is supplied by a pump 6 and returned by the consumers to a tank T.
  • the pump 6 is in the illustrated embodiment as electrically controllable variable displacement pump whose pivot angle is adjustable via a pump regulator 8.
  • a variable speed fixed displacement pump or the like can be used.
  • the sucked by the pump 6 from the tank T pressure fluid is conveyed into a pump line 10, which branches into two supply lines 12, 14, wherein the supply line 12 to the cylinder 2 and the supply line 14 is assigned to the cylinder 4.
  • the pressure medium volume flow Q VW delivered by the pump 6 is branched into partial pressure medium volume flows Q VW1 and Q VW2 .
  • the supply lines 12, 14 are each connected to an input port P of a continuously variable directional control valve 16 or 18, through which the pressure medium flow direction to or from the consumer and the pressure medium volume flow can be adjusted.
  • the actuation of the two-way valves 16, 18 via one or more pilot control devices 36, via the control spaces of the directional control valves 16, 18 are acted upon with a control pressure to the valve spool from its illustrated locking position (closed center) in the indicated positions (a) or ( b) to adjust, in which either the cylinder chamber 28, 30 or the annulus 32, 34 is supplied with pressure medium, while the pressure medium is then displaced from the respective other pressure chamber.
  • a Zulaufmeßblende is controlled via an inlet control edge, whose opening cross-section determines the pressure medium volume flow to the cylinder 2, 4.
  • the pressure medium flowing back from the cylinder 2, 4 is returned to the tank T via a tank connection T and a tank line 38 connected thereto.
  • FIG. 1 is characterized by the flow lines 20, 22 inflowing pressure medium flow with Q A1 , Q A2 and the outflowing pressure medium flow with Q B1 and Q B2 .
  • the indicated pressures p A1 , p B1 , p A2 and p B2 are then in each case in the lines.
  • each directional control valve 16, 18 Upstream of each directional control valve 16, 18 is in the corresponding flow line 12 and 14, a LS or individual pressure compensator 40, 42 is provided, which is acted upon in the opening direction respectively by the force of a pressure compensator spring 44 and 46 and the load applied to the respective load 2, 4 , In the closing direction acts on the pressure compensator slide of the individual pressure compensators 40, 42 respectively, the pressure in the pressure medium flow path between the output of the respective individual pressure compensator 40, 42 and the input of the downstream directional control valve 16, 18.
  • a flow regulator is formed over which the pressure drop across the orifice can be kept constant independent of the load.
  • the control arrangement further has an inlet pressure compensator 52, which is arranged in a branch line 54 branching off from the pump line 10. Via the inlet pressure compensator 52, a connection to the tank T can be opened.
  • control arrangement 1 substantially corresponds to the structure as described in the aforementioned prior art.
  • power beyond consumer 50 To connect a device with an additional hydraulic consumer to the mobile implement, such as a loading wagon or a potato harvester, the system is provided with a power beyond port to which this additional consumer, hereinafter referred to as power beyond consumer 50, can be connected.
  • the inlet pressure compensator 52 is designed as a 3/3-way pressure balance, the slide in the closing direction of the force of a spring 56 and the pressure applied to the output of a pressure compensating valve 58 pressure and in the closing direction of the pressure in the branch line 54 and thus the pressure in the pump line 10 is applied.
  • the pressure compensator exchange valve 58 At the inputs of the pressure compensator exchange valve 58, on the one hand, the highest load pressure of the two consumers 2, 4, which is tapped via a shuttle valve 48 and corresponding load reporting lines from the directional control valves 16, 18.
  • the load pressure of the power beyond consumer 50 is applied, which is tapped via a power-beyond-Lastmelde effet 68.
  • the pressure slide of the inlet pressure compensator 52 is acted upon in the closing direction of the highest of the load pressures at the consumers 2, 4 and the power beyond consumer 50 abut.
  • the power beyond consumer 50 is connected via an inlet channel 60 to a working port A of the 3/3-way pressure compensator.
  • the flowing away from the power beyond consumer 50 pressure medium is passed through a drain passage 64 in the tank line 38.
  • a tank channel 62 leading to the tank T is connected.
  • the opening pressure difference ⁇ PEDW which must be applied to fully open the inlet pressure compensator 52, is determined by the force of the spring 56.
  • the path of the valve spool of the input pressure compensator 52 is detected via a displacement sensor 66 and converted into a signal which is applied to a signal input of the pump controller 8, so that the adjustment of the pump in response to the path of the pressure compensator slide of the inlet pressure compensator 52 takes place.
  • the inlet pressure compensator 52 When the power beyond consumer 50 is not actuated or not connected, the inlet pressure compensator 52 is closed and the working hydraulics of the tractor (cylinders 2, 4) are supplied with pressure medium. Upon actuation of the power beyond consumer 3, the inlet pressure compensator 52 is adjusted in the opening direction, so that it can be supplied with pressure medium. The pump 6 is adjusted in response to the path of the pressure compensator slide of the inlet pressure compensator 52 so that a small residual volume flow flows through the tank port T - (the inlet pressure compensator 52 is then open to the power beyond consumer 50 and the tank T out). This ensures that all consumers 2, 4 and the power beyond consumer 50 are adequately supplied with pressure medium.
  • control of the pump 6 takes place in dependence on the path of the Pressure compensator valve of the inlet pressure compensator 52, alternatively, the residual volume flow flowing out to the tank T could also be detected and used to set the pump 6.
  • the actual path of the pressure compensator valve corresponding signal Y EDWist is compared with a stored in a data storage setpoint - the adjustment of the pump 6 then takes place in response to this control difference via a control algorithm.
  • the opening pressure difference of the input pressure compensator 52 will generally be greater than the opening pressure difference of the individual pressure compensators 40, 42, d. h.,
  • the spring 56 is stronger than the pressure compensator springs 44, 46th
  • FIG. 2 illustrated embodiment corresponds in principle to in Fig. 1 illustrated solution, but instead of a single consumer two power beyond consumers 50, 70 are driven.
  • the inlet pressure compensator 52 is designed as a 4/4-way pressure compensator, wherein the input terminal P of the inlet pressure compensator 52 is connected to the branch line 54, while the pressure medium supply of the two power beyond consumers 50, 70 via the Inlet passage 60 and a further inlet channel 72 takes place, which are connected to two output terminals A, B of the pressure compensator 52.
  • the inlet pressure compensator 52 is again acted upon in the closing direction by the force of the spring 56 and the highest load pressure of the consumers 2, 4 and the two power beyond consumers 50, 70, wherein the greater of the load pressures of the two power beyond consumers 50, 70 is tapped via a power beyond shuttle valve 73. In the opening direction, the inlet pressure compensator 52 in turn is acted upon by the pressure at the inlet port P.
  • the inlet pressure compensator 52 is designed so that when inoperative or disconnected power beyond consumers 50, 70, the inlet pressure compensator 52 is shut off. Upon actuation of both power beyond consumers 50, 70, the power beyond consumer 50 is first supplied with pressure medium and on a further displacement of the pressure compensator slide the connection to the other power beyond consumer 70 aufteil.
  • the power beyond consumer 50 is prioritized over the power beyond consumer 70.
  • the inlet pressure compensator 52 is completely open, a residual volume flow flows via the tank channel 62 to the tank T.
  • the path of the pressure compensator slide is detected as in the above embodiment via the transducer 66 and guided via a signal line 74 to a signal port of the pump controller 8 and processed in the manner described above - the adjustment of the pump 6 is again such that a predetermined residual flow to the tank T. flows out, so that a sufficient supply of all consumers and the power beyond consumers 50, 70 is ensured.
  • dargestellen embodiment is the same inlet pressure compensator 52 as in Embodiment according to Fig. 1 used, but over which two power beyond consumers 50, 70 can be supplied with pressure medium.
  • the connected to the output terminal A inlet channel 60 branches into two Zulaufzweigkanäle 76, 78, via which the pressure medium to the power beyond consumer 50 or 70 is performed.
  • a power beyond pressure compensator 80 is provided, which is acted upon in the closing direction by the force of a pressure compensator spring 82 and the highest of the occurring load pressures, which is tapped from the output of the pressure compensator shuttle valve 58.
  • In the opening direction of the power beyond pressure compensator 80 is acted upon by the pressure at its input terminal P.
  • This power beyond pressure compensator 80 is smaller than that of the inlet pressure compensator 52 and the individual pressure compensators 40, 42 chosen.
  • the pressure medium supply of the power beyond consumer 50, 70 always via the inlet pressure compensator 52, which is located in the pressure fluid flow path between the pump line 10 and the associated load 50, 70.
  • the pressure medium supply to the consumer takes place directly, d. h., When bypassing the inlet pressure compensator 52 via associated power beyond pressure compensators.
  • Fig. 4 shows a variant of the control arrangement 1, in which the inlet pressure compensator 52 is designed as a 2/2-way pressure compensator, wherein the input terminal P as in the above-described embodiments is connected to the branch line 54 and the tank port T opens via the tank passage 62 into the tank.
  • the inlet pressure compensator 52 is acted upon by the pressure at the inlet port P in the opening direction and by the force of the spring 56 and the highest applied to the output of the pressure compensating valve 58, the load pressures in the closing direction.
  • the path of the pressure compensator valve spool is in turn detected by a displacement sensor 66 and used to control the pump 6.
  • the pressure medium supply of the power beyond consumer 50 takes place according to Fig. 4 via the power beyond pressure compensator 80, which is acted upon in the opening direction by the pressure in the pump line 10 and in the closing direction by the force of the pressure balance spring 82 and the highest of the load pressures tapped at the outlet of the pressure balance changeover valve 58.
  • the power beyond pressure compensator 80 is arranged in a power beyond feed 84 branching off from the pump line 10.
  • the inlet pressure compensator 52 and the power beyond pressure compensator 80 are arranged in parallel and each designed as a 2/2-way pressure compensator.
  • the opening pressure ⁇ p EDW of the inlet pressure compensator is greater than that of the power beyond pressure compensator 80 ( ⁇ p IDW3 ) and the two individual pressure compensators 40, 42 ( ⁇ p IDW1 , 2), whereby either the opening pressure of the two individual pressure compensators 40, 42 or that of the power Beyond-Druckwaage 80 can be selected larger to set a prioritization. That is, it can first the power beyond consumer 50 or the working hydraulics of the tractor (cylinder 2, 4) are supplied with pressure medium. Also in this embodiment, a supply of all consumers 2, 4, 50 is ensured when the pump 6 is set so that a residual volume flow flows through the inlet pressure compensator 52 to the tank T out.
  • Fig. 5 is a variant of in Fig. 4 shown embodiment, wherein the inlet pressure compensator 52 is not - as in Fig. 4 - parallel, but in series with the power beyond pressure scale 80 is connected. That is, the branch line 54 leading to the input port P of the input pressure compensator 52 does not branch from the pump line 10 but from the inlet port 60 connecting the output port A of the power beyond pressure compensator 80 and the power beyond consumer 50.
  • the input pressure compensator 52 is thus supplied with pressure medium only after the control of the power beyond pressure compensator 80.
  • Both pressure compensators 52, 80 are designed as a 2/2-way pressure compensator and are biased over the highest of the load pressures in the closed position and by the pressure applied in each case at the input P in the open position.
  • the power beyond consumer 50 or the consumers 2, 4 can be prioritized.
  • the opening pressure difference of the inlet pressure compensator 52 is again greater than the opening pressure difference of the individual pressure compensators 40, 42 and the power beyond pressure compensator 80 selected. Otherwise, the function corresponds to that of the embodiment Fig. 4 ,
  • FIG. 6 an embodiment is shown in which two power beyond consumers 50, 70 to be supplied with pressure medium. These are each associated with a power beyond pressure compensator 80 or 86, which are each connected via branching off from the pump line 10 power beyond supply lines 84, 88 with the associated power beyond consumers 50, 70.
  • the two Power Beyond pressure compensators 80, 86 and the inlet pressure compensator 52 are each designed as 2/2-way pressure compensators.
  • the input pressure compensator 52 is biased in this embodiment by the tapped via the pressure compensating valve 58 highest of the load pressures in the opening direction, while in the closing direction, only the spring 56 acts.
  • the output port of the inlet pressure compensator 52 is connected via the tank channel 62 to the tank T.
  • the two power beyond pressure scales 80, 86 are biased only by the force of a pressure compensator spring 82 and 90 in the closing direction, while in the opening direction in this embodiment, the highest of the load pressures acts, which is tapped at the output of the pressure compensator shuttle valve 58.
  • This embodiment allows a variety of functional processes, since depending on the spring selection of the individual pressure compensators 40, 42 and the power beyond pressure scales 80, 86 either the working hydraulics of the tractor (consumers 2, 4) and then the power beyond consumers 50, 70 or vice versa or initially only one of the power beyond consumers, then the working hydraulics and then the other power beyond consumers 70, 50 can be supplied with pressure medium.
  • a residual volume flow will occur when the inlet pressure compensator 52 is open and the pump 6 is actuated in dependence on this residual volume flow or on the position of the pressure compensator piston of the inlet pressure compensator 52 in order to avoid undersupply.
  • Fig. 7 an embodiment is shown with the connection of a power beyond consumer 50, that in the basic structure of that Fig. 4 equivalent.
  • the power beyond consumer 50 is supplied with pressure medium via a power beyond pressure compensator 80 arranged in the power beyond supply line 84.
  • the inlet pressure compensator 52 is arranged in the branch line 54 and acted upon in the opening direction by the pressure in this branch line 54, while in the closing direction, the force of the spring 56 and the tapped on the pressure compensating valve 58 highest load pressure act.
  • the residual volume flow through the inlet pressure compensator 52 to avoid undesirable high pressure drops at the aperture 92 via a parallel to the aperture 92 switched bias valve to the tank.
  • the opening pressure of the individual pressure compensators 40, 42 of Working hydraulics set greater than the opening pressure of the power beyond pressure compensator 80 and the opening pressure of the inlet pressure compensator 52 is - as in all embodiments - preferably greater than that of the individual or power beyond pressure scales selected.
  • Fig. 8 shows an embodiment in which the basis Fig. 7 explained principle for controlling a plurality of power beyond consumers 50, 70 is used.
  • Each of the two power beyond consumers 50, 70 is in each case assigned a power beyond pressure compensator 80, 86, which are arranged in branching off from the pump line 10 power beyond supply lines 84 and 88 and over which the two power Beyond Consumers 50, 70 are supplied with pressure medium.
  • the inlet pressure compensator 52 is formed and interconnected as in the above-described embodiment, wherein the aperture 92 is again provided in the tank channel 62, which generates a control pressure for controlling the two power beyond pressure compensators 80, 86.
  • a pressure medium supply of the two power beyond consumers 50, 70 takes place only when a sufficient control pressure is built up before the aperture 92.
  • the two power beyond consumers 50, 70 can be prioritized by a suitable choice of the pressure balance springs 82, 90 with each other.
  • the concept according to the invention makes it possible to easily connect power beyond consumers and to ensure a desired pressure medium supply of all consumers even under unfavorable operating conditions (for example low load pressure, high pressure medium volume flow).
  • DW pressure compensator
  • PB power beyond consumer
  • ⁇ p the respective opening pressure of the pressure compensators
  • Pressure compensators 52, 80, 86 1P B 2PB Opening pressure ratios of the EDW (52) and IDWs (40, 42, 80, 86) 1 1x3 / 3 DW x ⁇ p EDW > ⁇ p IDW1,2 2 1x4 / 4 DW x ⁇ p EDW > ⁇ p IDW1,2 3 1x3 / 3 12/2 DW x ⁇ p EDW > ⁇ p IW1,2 > ⁇ p IDW3 4 2x2 / 2 DW parallel x ⁇ p EDW > ⁇ p IDW3 > ⁇ p IDW1,2 ⁇ p EDW> ⁇ p IDW1,2 > ⁇ p IDW> ⁇ p IDW1,2 > ⁇ p IDW3 5 2x2 / 2 DW row x ⁇ p EDW> ⁇ p IDW3 ⁇ p IDW1,2 ⁇ p EDW > ⁇ p IDW1,2 > ⁇ p IDW3 6 3x2 / 2 DW parallel x ⁇ p EDW >
  • the use of the invention is possible with the use of electrically adjustable control pumps and variable speed constant displacement pumps, in particular in conjunction with open center and LS valves, which are operated mechanically, electrically or electro-hydraulically.
  • the invention is suitable for all working hydraulic applications of mobile hydraulics whose consumers are not fixed from the outset.
  • a hydraulic control arrangement for controlling a plurality of consumers, in particular a mobile working device, wherein in addition to the consumers of the control arrangement, a power beyond consumer should be connectable to a power beyond port. All consumers and power beyond consumers are supplied by a pump with pressure medium, downstream of the pump, an inlet pressure compensator is provided at the control terminal of the greater of the load pressures of the consumer or the at least one power beyond consumer is present.

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

Abstract

L'invention concerne un système de commande hydraulique (1) pour assurer la commande de plusieurs consommateurs (2, 4), notamment d'un engin mobile, outre les consommateurs du système de commande, un consommateur additionnel (50) devant pouvoir être raccordé à une connexion de type power-beyond. Tous les consommateurs et les consommateurs de type power-beyond sont alimentés en fluide hydraulique par une pompe (6), une balance de pression d'entrée étant prévue en aval de la pompe. La plus grande des pressions de charge des consommateurs ou du consommateur de type power-beyond (au moins au nombre de un) se situe au niveau de la borne de commande de la balance de pression d'entrée.

Claims (20)

  1. Système de commande hydraulique servant à commander plusieurs consommateurs (2, 4), en particulier un engin mobile, sachant que ledit système de commande hydraulique présente une pompe (6), par l'intermédiaire de laquelle les multiples consommateurs (2, 4) peuvent être alimentés en milieu sous pression, sachant que la pompe (6) est disposée en amont d'une balance de pression d'entrée (52) appartenant au système de commande hydraulique, par l'intermédiaire de laquelle une liaison vers le réservoir (T) peut être commandée, sachant qu'un diaphragme de dosage (16, 18) pouvant être ajusté est associé à chaque consommateur (2, 4), et sachant que le système de commande comporte un raccordement de type power-beyond, auquel au moins un consommateur de type power-beyond (50, 70) peut être raccordé, sachant que le réglage de la balance de pression d'entrée (52) a lieu en fonction de la plus grande pression de charge des consommateurs (2, 4) et du consommateur de type power-beyond (50, 70) au moins au nombre de un, caractérisé en ce que la pompe (6) est une pompe présentant un refoulement réglable, laquelle peut être commandée en fonction du réglage de la balance de pression d'entrée (52).
  2. Système de commande selon la revendication 1, sachant que le consommateur de type power-beyond (50, 70) peut être alimentée en milieu sous pression par l'intermédiaire de la balance de pression d'entrée (52) et que la plus grande pression de charge sollicite la balance de pression d'entrée (52) dans la direction de fermeture.
  3. Système de commande selon la revendication 2, sachant que la balance de pression d'entrée (52) bloque dans une position de base précontrainte par ressort, la liaison avec le consommateur de type power-beyond (50, 70) et avec le réservoir (T) et commande lors du passage dans la direction d'ouverture dans un premier temps la liaison avec le consommateur de type power-beyond (50, 70) puis la liaison avec le réservoir (T).
  4. Système de commande selon la revendication 3, sachant qu'un deuxième consommateur du type power-beyond (70) peut être raccordé, lequel peut être alimenté en milieu sous pression par l'intermédiaire de la balance de pression d'entrée (52) de manière simultanée avec le premier consommateur de type power-beyond (50) ou de manière ultérieure à ce dernier.
  5. Système de commande hydraulique selon la revendication 4, sachant que le deuxième consommateur de type power-beyond (70) est placé en aval de la balance de pression de type power-beyond (80) appartenant au système de commande hydraulique, laquelle balance de pression de type power-beyond est sollicitée dans la direction de fermeture par la force d'un ressort (82) et par la même pression de commande que le balance de pression d'entrée (52) et est sollicitée dans la direction d'ouverture par la pression au niveau de son raccordement d'entrée (P).
  6. Système de commande hydraulique selon la revendication 1, sachant qu'au moins un consommateur de type power-beyond (50, 70) peut être alimenté en milieu sous pression, en contournant la balance de pression d'entrée (52), par l'intermédiaire d'une balance de pression de type power-beyond (80, 86).
  7. Système de commande selon la revendication 6, sachant que la balance de pression d'entrée (52) est sollicitée dans la direction de fermeture par la plus grande pression de charge et par la force d'un ressort (56) et est sollicitée dans la direction d'ouverture par la pression au niveau de son entrée (P).
  8. Système de commande selon la revendication 7, sachant que la balance de pression de type power-beyond est sollicitée dans la direction de fermeture par la plus grande pression de charge et par la force d'un ressort (82).
  9. Système de commande selon la revendication 8, sachant que la balance de pression d'entrée (52) est placée en aval de manière alignée par rapport à la balance de pression de type power-beyond (80).
  10. Système de commande selon la revendication 6, sachant que la balance de pression d'entrée (52) est sollicitée par la plus grande de toutes les pressions de charge dans la direction d'ouverture.
  11. Système de commande selon la revendication 10, sachant que la balance de pression de type power-beyond (80, 86) au moins au nombre de une est sollicitée dans la direction d'ouverture par la plus grande de toutes les pressions de charge et est sollicitée dans la direction de fermeture par la force d'un ressort (82, 90).
  12. Système de commande selon la revendication 7 ou 10, sachant qu'en aval de la balance de pression d'entrée (52), un diaphragme (92) est disposé dans une conduite de réservoir (62) menant au réservoir (T) et la pression agissant dans la direction d'ouverture sur la balance de pression de type power-beyond (80, 86) au moins au nombre de une est mesurée entre le diaphragme (92) et la balance de pression d'entrée (52), sachant que la balance de pression de type power-beyond (80, 86) est sollicitée dans la direction de fermeture par la force d'un ressort (82, 90).
  13. Système de commande selon l'une quelconque des revendications précédentes, sachant que la pompe (6) est une pompe à cylindrée variable pouvant être commandée électriquement ou une pompe à cylindrée constante avec réglage de vitesse.
  14. Système de commande selon l'une quelconque des revendications précédentes, sachant qu'une balance de pression individuelle (40, 42) est placée en amont de chaque diaphragme de dosage (16, 18), laquelle est sollicitée dans la direction d'ouverture par un ressort de balance de pression (44) et par la plus grande pression de charge des consommateurs (2, 4) et est sollicitée dans la direction de fermeture par la pression à la sortie de la balance de pression individuelle (40, 42).
  15. Système de commande selon la revendication 14, sachant que les ressorts de balance de pression (44, 46) des balances de pression individuelles (40, 42) et des balances de pression de type power-beyond (80, 86) ou de la balance de pression d'entrée (52) sont calés les uns sur les autres de telle manière que soit les consommateurs (2, 4) soit les consommateurs de type power-beyond (50, 70) sont prioritaires.
  16. Système de commande selon la revendication 15, sachant que la différence de pression d'ouverture de la balance de pression d'entrée (52) est choisie de manière à être plus grande que la différence de pression d'ouverture des balances de pression individuelles (40, 42) ou des balances de pression de type power-beyond (80, 86).
  17. Système de commande selon l'une quelconque des revendications précédentes, sachant que les diaphragmes de dosage sont formés par des valves de balancement (16, 18) pouvant être réglés de manière électrique, hydraulique ou mécanique.
  18. Système de commande selon l'une quelconque des revendications précédentes, comportant un sélecteur de circuit de balance de pression (58), à l'entrée duquel est présente d'un côté la plus grande pression de charge des consommateurs (2, 4) et d'un autre côté la plus grande pression de charge du ou des consommateurs de type power-beyond (50) et la sortie duquel est reliée à une chambre de commande de la balance de pression d'entrée (52).
  19. Procédé de réglage pour un système de commande hydraulique selon la revendication 1, caractérisé en ce que la pompe (6) et/ou les diaphragmes de dosage (16, 18) des consommateurs (2, 4) sont commandés de telle manière qu'il résulte un flux volumique restant prédéterminé en direction du réservoir (T) lorsque le consommateur de type power-beyond (50, 70) au moins au nombre de un est alimenté en milieu sous pression par l'intermédiaire de la balance de pression d'entrée (52).
  20. Procédé de réglage selon la revendication 19, sachant que la pompe (6) est réglée en fonction du flux volumique restant ou en fonction de la position d'un tiroir de balance de pression de la balance de pression d'entrée (52).
EP05799204A 2004-10-06 2005-10-06 Systeme de commande hydraulique Not-in-force EP1812715B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004048684A DE102004048684A1 (de) 2004-10-06 2004-10-06 Hydraulische Steueranordnung
PCT/DE2005/001792 WO2006037318A1 (fr) 2004-10-06 2005-10-06 Systeme de commande hydraulique

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EP1812715A2 EP1812715A2 (fr) 2007-08-01
EP1812715B1 true EP1812715B1 (fr) 2012-07-04

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US (1) US7870728B2 (fr)
EP (1) EP1812715B1 (fr)
DE (1) DE102004048684A1 (fr)
WO (1) WO2006037318A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019092206A1 (fr) 2017-11-10 2019-05-16 Syn Trac Gmbh Système hydraulique pour véhicule et véhicule équipé d'un tel système hydraulique

Families Citing this family (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006008940A1 (de) 2006-02-23 2007-08-30 Robert Bosch Gmbh Hydraulische Steueranordnung
EP2025948A3 (fr) * 2007-08-16 2013-03-27 Robert Bosch GmbH Agencement de commande hydraulique
DE102007045802A1 (de) * 2007-08-16 2009-02-19 Robert Bosch Gmbh Hydraulische Steueranordnung
DE102007045803A1 (de) * 2007-08-22 2009-02-26 Robert Bosch Gmbh Hydraulische Steueranordnung
EP2028376B1 (fr) * 2007-08-22 2013-11-27 Robert Bosch GmbH Agencement de commande hydraulique
KR101595116B1 (ko) * 2008-03-10 2016-02-18 파커-한니핀 코포레이션 다중 액추에이터를 구비한 유압 시스템 및 관련 제어 방법
DE102009028816A1 (de) * 2009-08-21 2011-02-24 Deere & Company, Moline Hydraulische Anordnung
DE102010027964A1 (de) * 2010-04-20 2011-10-20 Deere & Company Hydraulische Anordnung
SE1350633A1 (sv) * 2013-05-24 2014-11-25 BAE Systems Hägglunds Aktiebolag Förfarande och system för styrning av hydraulanordning
DE102013214734A1 (de) * 2013-07-29 2015-01-29 Robert Bosch Gmbh Hydraulische Steueranordnung und Verfahren zur Versorgung mehrere Verbraucher damit
MX2016004277A (es) * 2013-10-03 2016-10-12 Transocean Innovation Labs Ltd Dispositivos hidraulicos y metodos para activar los mismos.
DE102013223288A1 (de) 2013-11-15 2015-05-21 Robert Bosch Gmbh Hydraulische Steueranordnung

Family Cites Families (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4335577A (en) * 1980-06-19 1982-06-22 Deere & Company Hydraulic system having variable displacement pumps controlled by power beyond flow
US4400937A (en) * 1982-09-29 1983-08-30 Deere & Company Control for quickly effecting displacement changes in a pump supplying fluid to primary and secondary function control valves
DE3629471A1 (de) * 1986-08-29 1988-03-03 Bosch Gmbh Robert Hydraulische steuereinrichtung
JPH02107802A (ja) * 1988-08-31 1990-04-19 Hitachi Constr Mach Co Ltd 油圧駆動装置
DE69004789T3 (de) 1989-01-18 1997-12-18 Hitachi Construction Machinery Hydraulische antriebseinheit für baumaschinen.
US4977928A (en) * 1990-05-07 1990-12-18 Caterpillar Inc. Load sensing hydraulic system
JP2828490B2 (ja) 1990-06-19 1998-11-25 日立建機株式会社 ロードセンシング油圧駆動回路の制御装置
DE4127342C2 (de) 1991-08-19 1995-02-16 Danfoss As Hydraulisches System mit einer Pumpe
DE4239109C1 (de) * 1992-11-20 1994-06-30 Danfoss As Hydraulisches System
DE4433633C1 (de) * 1994-09-21 1995-12-07 Wessel Hydraulik Hydraulische Schaltungseinheit zur Betätigung von auswechselbaren Zusatzgeräten an Hydraulikbaggern und ähnlichen Vorrichtungen
US5540049A (en) 1995-08-01 1996-07-30 Caterpillar Inc. Control system and method for a hydraulic actuator with velocity and force modulation control
GB2352275B (en) * 1999-07-17 2004-02-18 Agco Gmbh & Co Hydraulic system for utility vehicles
DE10115650A1 (de) * 2001-03-29 2002-10-02 Bosch Gmbh Robert Hydraulische Steuereinrichtung
DE10214850A1 (de) * 2002-04-04 2003-10-30 Cnh Oesterreich Gmbh Hydrauliksystem eines Schleppers mit Anbaugerät
JP4081487B2 (ja) * 2004-12-28 2008-04-23 東芝機械株式会社 油圧制御弁

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2019092206A1 (fr) 2017-11-10 2019-05-16 Syn Trac Gmbh Système hydraulique pour véhicule et véhicule équipé d'un tel système hydraulique
DE102017126505B4 (de) 2017-11-10 2023-06-15 Syn Trac Gmbh Hydrauliksystem für ein Fahrzeug sowie ein Fahrzeug mit einem solchen Hydrauliksystem

Also Published As

Publication number Publication date
US20080202110A1 (en) 2008-08-28
WO2006037318A1 (fr) 2006-04-13
EP1812715A2 (fr) 2007-08-01
DE102004048684A1 (de) 2006-04-13
US7870728B2 (en) 2011-01-18

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