WO2008000708A1 - Système électrohydraulique, ainsi que dispositif et procédé pour actionner un tel système - Google Patents

Système électrohydraulique, ainsi que dispositif et procédé pour actionner un tel système Download PDF

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Publication number
WO2008000708A1
WO2008000708A1 PCT/EP2007/056285 EP2007056285W WO2008000708A1 WO 2008000708 A1 WO2008000708 A1 WO 2008000708A1 EP 2007056285 W EP2007056285 W EP 2007056285W WO 2008000708 A1 WO2008000708 A1 WO 2008000708A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
switching
proportional
control
valves
Prior art date
Application number
PCT/EP2007/056285
Other languages
German (de)
English (en)
Inventor
Vincent Rieger
Matthias Mueller
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Publication of WO2008000708A1 publication Critical patent/WO2008000708A1/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
    • F15B21/00—Common features of fluid actuator systems; Fluid-pressure actuator systems or details thereof, not covered by any other group of this subclass
    • F15B21/08—Servomotor systems incorporating electrically operated control means
    • 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
    • F15B11/006—Hydraulic "Wheatstone bridge" circuits, i.e. with four nodes, P-A-T-B, and on-off or proportional valves in each link
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/024—Systems essentially incorporating special features for controlling the speed or actuating force of an output member by means of differential connection of the servomotor lines, e.g. regenerative circuits
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B11/00—Servomotor systems without provision for follow-up action; Circuits therefor
    • F15B11/02—Systems essentially incorporating special features for controlling the speed or actuating force of an output member
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/044—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the return line, i.e. "meter out"
    • 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
    • F15B2211/20507—Type of prime mover
    • F15B2211/20515—Electric motor
    • 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
    • F15B2211/20538—Type of pump constant 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
    • F15B2211/30—Directional control
    • F15B2211/305—Directional control characterised by the type of valves
    • F15B2211/3056—Assemblies of multiple valves
    • F15B2211/30565—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve
    • F15B2211/30575—Assemblies of multiple valves having multiple valves for a single output member, e.g. for creating higher valve function by use of multiple valves like two 2/2-valves replacing a 5/3-valve in a Wheatstone Bridge arrangement (also half bridges)
    • 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
    • F15B2211/3122—Special positions other than the pump port being connected to working ports or the working ports being connected to the return line
    • F15B2211/3133—Regenerative position connecting the working ports or connecting the working ports to the pump, e.g. for high-speed approach stroke
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—Control of flow in the return line, i.e. meter-out control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/615—Filtering means
    • 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
    • F15B2211/6336—Electronic controllers using input signals representing a state of the output member, e.g. position, speed or acceleration
    • 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

  • Electrohydraulic system as well as apparatus and method for actuating such
  • the invention relates to an electrohydraulic system, in particular a convertible top in a motor vehicle, and to an apparatus and a method for operating such a system.
  • Proportional valves are used, which are all controlled independently, the control unit must have a correspondingly high number of amplifier stages. But this is quite costly for an application in the vehicle.
  • the electrohydraulic system according to the invention as well as the device and the method for operating such with the features of the independent claims have the advantage that the number of required amplifier stages is halved by the common control of a switching valve and a proportional valve via exactly one amplifier stage. This allows the corresponding control unit be made cheaper and space-saving. In addition, this can reduce energy consumption.
  • Adjustment of the piston are controlled accordingly.
  • the double-acting cylinder can be controlled in an application-optimized manner with a single output stage.
  • Control signal provides.
  • the switching valve and the proportional valve are connected by means of a parallel circuit with the amplifier stage.
  • the proportional valve has a higher total electrical resistance than the proportional valve, which is actuated together with the switching valve.
  • the electromagnets and their series resistors are designed accordingly for the switching or proportional valve.
  • transistors as an amplifier stage, preferably field emission transistors (FET), which may be connected, for example via a bus system with the corresponding valves.
  • FET field emission transistors
  • both the switching and the proportional valves are designed as 2/2-way valves, which saves space in common valve blocks can be arranged.
  • 2/2-way valves By using a total of four 2/2-way valves for a double-acting hydraulic cylinder it can be controlled speed-dependent in both directions.
  • the switching valves and the proportional valves each have a return spring which places the valves in a non-energized state in a certain rest position, the valves need only be actively supplied with power during the adjustment process. If, for example, the first and the third valve are open in the rest position and the second and fourth valves are closed, it is also easy to realize an emergency operation in the event of a power failure.
  • the switching valve remains unchanged in its deviating from the rest position switching position.
  • the proportional valve can be set individually to a desired flow position over the entire proportional control range.
  • the switching valve and the proportional valve are particularly suitable as a control variable, an electrical voltage and / or current, which are tapped at the amplifier stage. If the proportional valve has a higher resistance than the switching valve, it can be above the switching voltage of the switching valve - A -
  • a setting range can be realized in which the position of the proportional valve is set proportionally to the applied voltage and / or current value.
  • Figure 1 is a hydraulic circuit diagram of a device according to the invention for
  • FIG. 2 is a schematic diagram of the driving method of the hydraulic system according to the invention.
  • Figure 3 is an electrical circuit diagram for the common control of the switching valve with the proportional valve.
  • the illustrated in Fig. 1 hydraulic actuator comprises a hydraulic cylinder 2, in which a piston 3 is arranged longitudinally displaceable.
  • the piston 3 has a first piston surface 5, which limits a first control pressure chamber 6 in the hydraulic cylinder 2.
  • a second piston surface 7 is formed on the piston 3, which limits a corresponding second actuating pressure chamber 8 in the hydraulic cylinder 2.
  • the pressure in the first control pressure chamber 6 can be changed via a first control pressure line 9 and the pressure in the second control pressure chamber 8 can be changed via a second control pressure line 10.
  • the first actuating pressure line 9 branches into a first line branch 11 and a second line branch 12.
  • the second positioning pressure line 10 branches into a third line branch 13 and a fourth line branch 14. Via the first line branch 11, the first signal pressure chamber 6 is connected to a first valve 15 , About the second leg 12 is the first
  • the second control pressure chamber 8 is connected via a third line branch 13 with a third valve 17 and via the fourth line branch 14 with a fourth valve 18.
  • the first control pressure chamber 6 and the second control pressure chamber 8 are connected via the second valve 16 and the fourth valve 18 with a pressure medium source 19.
  • a pressure medium source 19th used in the illustrated embodiment a hydraulic pump 19, which is preferably designed as a fixed displacement pump.
  • the hydraulic pump 19 is provided for conveying in only one direction and is driven by an electric motor 20 which is connected to the hydraulic pump 19 via a shaft 21.
  • the hydraulic pump 19 sucks pressure medium via a suction line 22 and a filter 23 arranged therein from a
  • the pressure fluid sucked by the hydraulic pump 19 is conveyed by the hydraulic pump 19 into a working pressure line 25.
  • the working pressure line 25 branches into a first working pressure line branch 26 and a second working pressure line branch 27.
  • the first working pressure line branch 26 is connected to the second valve 16.
  • the second working pressure line branch 27 is connected to the fourth valve 18. Via the second valve 16, a flow-through connection between the first working pressure line branch 26 and the second line branch 12 can be produced, so that the pressure medium conveyed by the hydraulic pump 19 into the working pressure line 25 via the first working pressure line branch 26, the second line branch 12 and the first
  • Stelltiktechnisch 9 flows into the first control pressure chamber 6 and there applied to the first piston surface 5 with a hydraulic force.
  • the second working pressure line branch 27 can be connected to the fourth line branch 14 in a flow-through manner. The funded by the hydraulic pump 19 in the working pressure line 25 pressure fluid then flows through the second working pressure line branch 27, the fourth
  • Tank volume 24 can be produced.
  • the first control pressure chamber 6 is expanded into the tank volume 24 via the first control pressure line 9 and the first line branch 11. If the third valve 17 is in a corresponding actuating position, the third line branch 13 is connected to the tank volume 24 and the second signal pressure chamber 8 is connected via the second Set pressure line 10 and the third leg 13 in the tank volume 24 relaxed.
  • the valves 15 to 18 are preferably 2/2-way valves, which are each held by a spring held in its rest position.
  • the first valve 15 is replaced by a first
  • the second valve 16 which is arranged parallel to the first valve 15, acted upon by the force of a second spring 29 in the direction of the first switching position as a rest position. As long as a second electromagnet acting in the opposite direction 32 is not energized, so no through-flow connection between the first working pressure line branch 26 and the second leg 12 is made. Only when the second solenoid 33 is energized, the second valve
  • the third valve 17 corresponds in its construction to the first valve 15, wherein it is replaced by a third spring 30 in its second position.
  • Valve 18 is as in the second valve 16, the first switching position of the valve in which the flow is blocked. Contrary to the force of the fourth spring 31, a fourth electromagnet 35 is arranged on the fourth valve 18, which brings the fourth valve 18 in its second switching position at a corresponding applied signal. In the second switching position of the fourth valve 18, the second control pressure chamber 8 is depressed by the hydraulic pump 19.
  • the second valve 16 and the fourth valve 18 in its first switching position, it is achieved that the pressure in the first control pressure chamber 6 and in the second control pressure chamber 8 corresponds to the pressure level of the tank volume 24.
  • the hydraulic cylinder 2 is thus pressureless.
  • the respective other switching position of the valves 15-18 it is also conceivable to choose the respective other switching position of the valves 15-18 as a rest position. It is only important that the pairs of a control pressure chamber associated valves 15, 16 and 17, 18 each have different switching positions as rest position.
  • the switching positions of the first and second valves 15, 16 and the third and fourth valves 17, 18 match in pairs, so that the rest position of the first valve 15 of the rest position of the third valve 17 and the rest position of the second valve 16 of the rest position of the fourth valve 18 corresponds.
  • the four electromagnets 32-35 for actuating the valves 15-18 are controlled via an electrical line 36.
  • the electrical line 36 may, for. B. may be part of a bus system over which the electromagnets 32-35 can be controlled individually and independently.
  • the electrical line 36 is connected to a
  • Control unit 37 connected. Via the control unit 37, the switching positions of the electromagnets 32-35 are defined and, accordingly, a power dimensioned individually for each electromagnet 32-35 is supplied. To z. B. to start the opening or closing operation of a convertible top of a convertible, the control unit 37 is transmitted by an actuating switch 38, a corresponding start signal. To the end of a
  • a signal line 39 is connected to an input of the control device 37, via which the control unit 37 is supplied with a voltage signal of a displacement meter 41.
  • the displacement sensor 41 By the displacement sensor 41, the respective position of the piston rod 4 can be detected, so that for example towards the end of an actuating movement, the speed of the electric motor 20 can be reduced.
  • Speed reduction of the electric motor 20 is promoted by the designed as a fixed displacement pump 19 hydraulic pump 19 a smaller volume flow in the working pressure line 25.
  • the adjusting movement slows down therefore.
  • the control unit 37 Via inputs / outputs 40, the control unit 37 communicates with other components of the vehicle. One of these outputs can z. B. control the speed of the electric motor 20.
  • the first valve 15 and the third valve 17 are designed as proportional valves, whose forward current is variably adjustable via the control unit 37.
  • the rest position of the first and the third valve 15, 17 in this case represents an open, through-flow connection between the control room 6 and the tank volume 24, so that in a de-energized valve 15, 17, the control pressure chambers 6, 8 is at the same pressure level with the tank volume 24 ,
  • the two valves 15, 17 are directly and directly connected to the tank volume 24, wherein in particular no further control valves between the valves 15, 17 and the tank volume 24 are arranged.
  • the output 49 of the first and third valves 15, 17 is in each case by a separate
  • the second valve 16 and the fourth valve 18 are each formed as switching valves having a locking state and a transmitting state.
  • the blocking state is formed as a rest position, so that in case of power failure, the connection between the pressure medium source 19 and the control pressure chambers 6, 8 is interrupted.
  • the arrangement with two proportional valves, which are each connected to the tank volume 24, and two switching valves which are connected to the pressure medium source 19 is particularly advantageous for 2/2-way valves 15 to 18 to produce, since in this case all four 2/2 Directional valves, or optionally further four units for additional piston 3 are low in a common valve block to produce.
  • the hydraulic circuit has one or more pressure sensors 54, as shown in dashed lines in FIG.
  • the pressure sensor 54 is arranged between the control pressure chamber 8 and the parallel-connected valves 17, 18 in the control pressure line 10. In this case, the pressure on the cylinder output side of the positioning space 8 is detected and a pressure signal 56 is forwarded to the evaluation unit 58.
  • the evaluation unit 58 has a pressure regulator 60, by means of which a control signal 62 is generated with which the proportional valves 15, 17 are actuated.
  • the evaluation unit 58 is integrated, for example, in the control unit 37. Information about the positions of the speed of the piston rod 4 can be obtained in the evaluation unit 58, whereby a control circuit can be created via the electrical control of the proportional valves 15, 17.
  • a control signal 62 for the proportional valve 17 can be generated via the indicated pressure sensor 54, which directly regulates the adjustment speed of the piston rod 4 via the outlet speed of the pressure medium from the control chamber 8 into the tank volume 24 ,
  • the adjustment of the piston rod 4 is completely independent of the Pressure medium source 19 applied power, or constructed in the control pressure chamber 6 pressure.
  • a further pressure sensor 54 are installed to control the insertion movement of the piston rod 4 according to the proportional valve 15.
  • the second valve 16 and the fourth valve 18 as a proportional valve and the first valve 15 and the third valve 17 is formed as a switching valve.
  • the adjustment of the piston rod 4 is not controlled via the outflow of the pressure medium from the control pressure chambers 6 and 8, as was the case in the circuit of Figure 1, but via the supply of the pressure medium and the pressure medium source 19 via the proportional valves 16, 18 in the control pressure chambers 6, 8 inside.
  • Valves 16 and 18 are controlled.
  • the described actuating device 1 is not limited to the application with only one hydraulic cylinder 2.
  • a plurality of pistons 3 can be controlled in the circuits at the same time or several circuits for a plurality of pistons 3 can be built next to one another. Rather, an application together with a plurality of hydraulic cylinders 42 is possible. If the further hydraulic cylinders 42 are in each case in turn designed as double-acting hydraulic cylinders 42, then each of the actuating pressure chambers thus created is the further one
  • Hydraulic cylinder 42 associated with a pair of valves, as shown for the hydraulic cylinder 2 in Fig. 1.
  • the circuits described can be used particularly advantageously for the adjustment of the convertible top, in which the individual mutually movably arranged hood parts are each connected to a piston rod 4 in order to adjust them automatically.
  • the individual mutually movably arranged hood parts are each connected to a piston rod 4 in order to adjust them automatically.
  • FIG. 2 the simultaneous control of the switching valve 66 and the proportional valve 68 is shown schematically, the two are connected in parallel.
  • An amplifier stage 70 supplies as a control signal 72, for example, a control voltage 74, which is applied simultaneously to the switching valve 66 and the proportional valve 68.
  • the control voltage 74 available at the amplifier stage 70 is on the x-axis
  • the current 78 resulting from application of the control voltage 74 of the corresponding electromagnets 32-35 of the valves 66, 68.
  • the control voltage 74 an analog voltage signal or an AC voltage, or a pulse width modulated (PWM) Voltage signal 74 are applied.
  • PWM pulse width modulated
  • the switching valve 66 for example, is switched from a "closed position" to a "open position.”
  • the electromagnet 33, 35 of the switching valve 66 has a lower resistance than the electromagnet 32, 34 of the proportional valve 68, so that at the switching valve 66, the switching operation of the switching valve 66 takes place even at a lower voltage 76. If the voltage 76 is further increased above the switching threshold 80, is in a
  • Proportional adjustment range 82 of the proportional valve 68 of this variable moves in a corresponding flow position.
  • the electromagnet 32, 34 of the proportional valve 68 to a higher resistance, so that the proportional valve 68 is adjusted only at higher currents 78 in a corresponding adjustment position.
  • the proportional valve 68 has by its higher total resistance a lower power consumption (flat curve 88) than the switching valve 66.
  • the proportional control range 82 overlaps with the area below the switching threshold 80 of the switching valve 66.
  • the switching threshold 80 is, for example, the pressure and / or the volume flow of the system and can be influenced by the design of the resistances of the two valves 66, 68.
  • the proportional valve 68 has a "open position" as the rest position (without current), so that the proportional valve 68 is closed practically after the opening of the switching valve 68 when the control signal 72 (control voltage 74) is increased further corresponding different
  • the electromagnet 33, 35 of the switching valve 66 is designed such that it is also for longer times with currents can be loaded, which are well above the switching threshold 80.
  • a control current or an electrical power can be used as the control signal 72, whereby, for example, temperature effects of the coil current can be compensated.
  • FIG. 3 shows an electrical circuit diagram according to the invention, in which an amplifier stage 70 supplies a control signal for the parallel actuation of the switching valve 66 and of the proportional valve 68.
  • the amplifier stage is designed, for example, as a transistor 71, preferably as an FET.
  • the amplifier stage 70 is constructed as part of the control unit 37 of the still further Verstäkerchn 70 for controlling additional valve
  • Pairs 66, 68 may be arranged. To realize a higher resistance of the proportional valve 68, this is preceded by a series resistor 90 in series.
  • an identically designed magnetic coil for the electromagnets 32 to 35 can then expediently be used for both valve types 68, 68. Due to the different total resistance of the two valves 66 and 68, they have a different level of current consumption, as shown by curves 86 and 88 in FIG.

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  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Analytical Chemistry (AREA)
  • Fluid-Pressure Circuits (AREA)

Abstract

L'invention concerne un dispositif et un procédé servant à actionner un système électrohydraulique (1) comprenant au moins un cylindre hydraulique (2), notamment une capote de cabriolet (100) sur un véhicule automobile. Le cylindre hydraulique (2) est hydrauliquement relié à au moins une soupape de commande (66) et à au moins une soupape proportionnelle (68). La soupape de commande (66) et la soupape proportionnelle (68) sont commandées électriquement par une unité de commande qui présente au moins un étage d'amplification (70) pour l'actionnement de la soupape de commande (66) et de la soupape proportionnelle (68). Selon l'invention, la soupape de commande (66) et la soupape proportionnelle (68) sont commandées conjointement par un seul étage d'amplification (70).
PCT/EP2007/056285 2006-06-28 2007-06-22 Système électrohydraulique, ainsi que dispositif et procédé pour actionner un tel système WO2008000708A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200610029623 DE102006029623A1 (de) 2006-06-28 2006-06-28 Elektrohydraulisches System, sowie Vorrichtung und Verfahren zum Betätigen eines solchen
DE102006029623.0 2006-06-28

Publications (1)

Publication Number Publication Date
WO2008000708A1 true WO2008000708A1 (fr) 2008-01-03

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PCT/EP2007/056285 WO2008000708A1 (fr) 2006-06-28 2007-06-22 Système électrohydraulique, ainsi que dispositif et procédé pour actionner un tel système

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WO (1) WO2008000708A1 (fr)

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4723107A (en) * 1986-01-28 1988-02-02 Steinbock Gmbh Hydraulic lifting mechanism
EP0546300A1 (fr) * 1991-12-07 1993-06-16 Robert Bosch Gmbh Dispositif de commande électrohydraulique
EP0872645A2 (fr) * 1997-04-14 1998-10-21 Brevini Hydraulics S.p.A. Dispositif d'entraínement électro-hydraulique pour commander à distance un distributeur hydraulique
DE10023959A1 (de) * 2000-05-16 2001-11-22 Bosch Gmbh Robert Hydraulische Steuereinrichtung für einen Hubantrieb
DE10296739T5 (de) 2001-05-02 2004-04-22 Husco International Inc., Waukesha Hydraulikkreislauf mit Rückführleitungsdosierventil und Betriebsverfahren

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4723107A (en) * 1986-01-28 1988-02-02 Steinbock Gmbh Hydraulic lifting mechanism
EP0546300A1 (fr) * 1991-12-07 1993-06-16 Robert Bosch Gmbh Dispositif de commande électrohydraulique
EP0872645A2 (fr) * 1997-04-14 1998-10-21 Brevini Hydraulics S.p.A. Dispositif d'entraínement électro-hydraulique pour commander à distance un distributeur hydraulique
DE10023959A1 (de) * 2000-05-16 2001-11-22 Bosch Gmbh Robert Hydraulische Steuereinrichtung für einen Hubantrieb
DE10296739T5 (de) 2001-05-02 2004-04-22 Husco International Inc., Waukesha Hydraulikkreislauf mit Rückführleitungsdosierventil und Betriebsverfahren

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