EP2644903B1 - Verfahren und hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers - Google Patents

Verfahren und hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers Download PDF

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Publication number
EP2644903B1
EP2644903B1 EP13001388.1A EP13001388A EP2644903B1 EP 2644903 B1 EP2644903 B1 EP 2644903B1 EP 13001388 A EP13001388 A EP 13001388A EP 2644903 B1 EP2644903 B1 EP 2644903B1
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EP
European Patent Office
Prior art keywords
pressure
pressure chamber
pressure medium
valve
chamber
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Active
Application number
EP13001388.1A
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German (de)
English (en)
French (fr)
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EP2644903A3 (de
EP2644903A2 (de
Inventor
Edgar Stamm
Heino Foersterling
Matti Linjama
Lauri Siivonen
Mikko Huova
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2644903A3 publication Critical patent/EP2644903A3/de
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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
    • F15B11/006—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
    • F15B11/04—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed
    • F15B11/042—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in"
    • F15B11/0426—Systems essentially incorporating special features for controlling the speed or actuating force of an output member for controlling the speed by means in the feed line, i.e. "meter in" by controlling the number of pumps or parallel valves switched on
    • 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
    • F15B2211/32—Directional control characterised by the type of actuation
    • F15B2211/327—Directional control characterised by the type of actuation electrically or electronically
    • F15B2211/328—Directional control characterised by the type of actuation electrically or electronically with signal modulation, e.g. pulse width modulation [PWM]
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/405—Flow control characterised by the type of flow control means or valve
    • F15B2211/40576—Assemblies of multiple valves
    • F15B2211/40592—Assemblies of multiple valves with multiple valves in parallel flow paths
    • 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
    • F15B2211/42—Flow control characterised by the type of actuation
    • F15B2211/426—Flow control characterised by the type of actuation electrically or electronically
    • F15B2211/427—Flow control characterised by the type of actuation electrically or electronically with signal modulation, e.g. using pulse width modulation [PWM]
    • 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
    • F15B2211/455—Control of flow in the feed line, i.e. meter-in control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B2211/00—Circuits for servomotor systems
    • F15B2211/40—Flow control
    • F15B2211/46—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
    • F15B2211/63—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
    • F15B2211/6336—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
    • F15B2211/60—Circuit components or control therefor
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6653—Pressure 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6654—Flow rate 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
    • F15B2211/665—Methods of control using electronic components
    • F15B2211/6656—Closed loop control, i.e. control using feedback

Definitions

  • the invention relates to a method for controlling a consumer with two pressure chambers and a hydraulic control arrangement for controlling such a consumer.
  • proportionally adjustable valves are used whose valve member is designed to be hydraulically or electrically continuously adjustable in order to set an opening cross section for the pressure medium volume flow.
  • Pulse Width Modulation can be used to adjust the current on the actuating magnet.
  • the frequency of the pulse width modulation is set higher than a maximum switching frequency of the valve.
  • the PWM pulses are smoothed in a coil of the actuating magnet to an average value.
  • the valve spool is acted upon by a spring counter to the effective direction of the actuating magnet.
  • the adjusting spring force during adjustment corresponds to a force at which the spring and thus the valve slide travel along a path corresponding to the current.
  • the spring is designed so that it can be adjusted at a maximum current to a position corresponding to the maximum opening position of the valve spool.
  • switching valve should be understood in particular a valve having a movable valve member which is biased by a spring in the direction of a basic position (for example, closed) and in a switching position (open) is adjustable. This switching position is occupied by energizing an actuating magnet. It is assumed that the spring biasing the valve member in the direction of the basic position in comparison to the force of the actuating magnet at Nennbestromung is very low, so that only a comparatively short time (with fast switching valves 2ms) is required to apply the current to the actuating magnet to connect the switching valve in the switching position. By choosing the pulse frequency and the pulse duration, a pressure medium volume flow can be adjusted via such a switching valve, similar to a proportionally adjustable valve.
  • binary coded parallel architecture pulse code modulation (PCM) and pulse width modulation (PWM) with individual switching valves to distinguish, but can also be combined.
  • PCM pulse code modulation
  • PWM pulse width modulation
  • multiple DFCUs can be implemented with these switching valves in parallel, ideally doubling from one valve to the next, the maximum achievable flow through such a DFCU
  • the resolution of the volume flow through such a DFCU is predetermined by the number of switching valves
  • An increase in resolution can be achieved by using additional switching valves in a DFCU or by pulse-width-modulated control, whereby a ballistic PWM control is also possible the switching valves is possible.
  • a generic hydraulic control arrangement for controlling a hydraulic cylinder in which a piston rod side annular space of the hydraulic cylinder is acted upon by a predetermined pressure, such as a pump pressure, while the other, bottom pressure chamber via a switching valve arrangement with the pump or a pressure medium sink (tank) is connectable.
  • a predetermined pressure such as a pump pressure
  • the desired cylinder position is set, in which the bottom pressure chamber on the Switching valve arrangement supplied a pressure medium volume flow or from this bottom-side pressure chamber, a pressure medium volume flow is discharged, the adjustment then takes place in each case against the pressure in the annular space.
  • pamphlets US 2002 002 68 69 A1 and WO 2007 028 863 A1 each show a generic method and a generic control arrangement for controlling a consumer.
  • the invention has for its object to provide a method for driving a consumer with two pressure chambers and a hydraulic control arrangement, by which a positioning accuracy of a consumer, in particular the fine control is improved.
  • the inventive method is used to control a consumer with two pressure chambers, of which one can be shut off at least via a switching valve arrangement or with a pressure medium source or with a pressure medium sink connectable.
  • a pressure medium volume is determined which is to be supplied to or removed from the one pressure chamber in order to set a predetermined nominal chamber pressure in one of the pressure chambers, preferably in the other, preferably blocked pressure chamber, or by a predetermined desired consumer position, For example, set a piston position of a cylinder.
  • the switching valve arrangement is then controlled such that the predetermined pressure medium volume is supplied to a pressure chamber or discharged from this pressure space.
  • the thereby adjusting actual chamber pressure or the actual consumer position is then compared with the corresponding predetermined desired value and, if necessary, the two aforementioned steps are repeated until the desired state is present.
  • the compressibility of the pressure medium is thus utilized to perform a fine control. It is in contrast to the prior art, no volume flow but a volume regulated, the duty cycle of the switching valves is determined in advance.
  • each pressure chamber is assigned a switching valve arrangement.
  • the opening duration of the switching valves can be changed in order to supply or remove the pressure medium volume.
  • the respective other pressure chamber is preferably shut off, so that the compressibility of the pressure medium in each shut off pressure chamber is utilized to realize the smallest positioning steps of a consumer.
  • each pressure chamber is assigned at least one inlet and one outlet switching valve. If the pressure chamber is blocked with the smaller pressure medium volume and the other pressure chamber is connected to the larger volume via the valve arrangement with the pressure medium source or the pressure medium sink, a smaller change in the nominal chamber pressure or the setpoint pressure results for a specific, increased or decreased pressure medium volume. Consumer position, as in the opposite case, when the pressure chamber locked with the larger volume and the pressure fluid volume is supplied to the pressure chamber of smaller volume or discharged from this. In the former way, the higher compressibility in the pressure chamber with the larger Volume used for fine adjustment.
  • the pressure chamber with the smaller volume is connected via the valve arrangement to the pressure medium source or the pressure medium sink and the other pressure chamber is blocked by the larger volume, the lower compressibility in the pressure chamber with the smaller volume can be used to change the setpoint chamber pressure or Target consumer position to achieve with little pressure medium volume.
  • an inlet valve of one chamber and an outlet valve of the other chamber can be controlled offset in time to regulate the consumer position.
  • control of the switching valves can be carried out according to a pulse combination which is selected from a table provided or stored in a data memory of pulse combinations with different pulse duration.
  • the opening duration of the switching valves is below the switching time for the respective switching valve - d. h., there is a ballistic control.
  • the hydraulic control arrangement for controlling a consumer with two pressure chambers, it is provided that at least one of these pressure chambers is associated with an inlet and outlet valve designed as a switching valve, via which the pressure chamber can be connected to a pressure medium source or a pressure medium sink.
  • the control arrangement further has a control unit for controlling the inlet and outlet valves such that a chamber pressure of one or the other pressure chamber or a consumer position by compression or decompression of the pressure medium in the other pressure chamber by supplying or removing a pressure medium volume via the one pressure chamber associated Inlet or outlet valve is adjustable.
  • the control unit according to the invention is designed so that the Switching valve arrangements in the sense of the pre-discussed method claims can be controlled.
  • each of the pressure chambers is associated with an inlet and an outlet valve.
  • the inlet valve of the one pressure chamber and the outlet valve of the other pressure chamber are controlled alternately or overlapping each other.
  • the inlet and outlet valves assigned to one pressure chamber can also be controlled alternately or overlapping, while the other pressure chamber is shut off by the associated inlet and outlet valves, so that the compressibility of the pressure medium in this pressure chamber is utilized for the adjustment.
  • FIG. 1 An in FIG. 1 its piston 4 divides the hydraulic cylinder 2 in a bottom-side pressure chamber 6 and a piston rod side annular space 8, which are connectable via the control arrangement 1 with a pump P or a tank T. to set the piston position or a piston speed or a chamber pressure.
  • a digital hydraulic control arrangement 1 consists of a multiplicity of so-called digital volume flow units (DFCU) which are used in the illustrated embodiment by a respective switching valve 10, 12, 14 and 16 are formed.
  • the switching valves 10, 12 the pressure chamber 6 and the switching valves 14, 16 associated with the annular space 8.
  • the pressure connection of the pump P is connected via a respective working line 18, 20 to the respective pressure chamber 6 or the annular space 8.
  • the two switching valves 12, 14 are arranged in the pressure medium flow path between the pump P and the respective pressure chamber 6, 8.
  • the respective working line 18, 20 can be connected to the tank T via the two other switching valves 10, 16 so that pressure medium can flow out of the associated pressure chamber 6 or the annular space 8.
  • the two switching valves 12, 14 are thus inlet valves, while the two other switching valves 10, 16 represent exhaust valves.
  • FIG. 1 are the two pressure ports of the hydraulic cylinder 2 denoted by the reference numeral A, B, accordingly, the two inlet valves 12, 14 control the pressure medium connection from the pump P to port A and from the pump P to port B, while the two exhaust valves 10, 16 control the pressure medium connection from port A to tank T or from working port B to tank T.
  • the switching valves are biased in each case via the aforementioned weak spring 22, 24, 26, 28 in the direction of a closed position and can be adjusted via a respective actuating magnet 30, 32, 34, 36 in the direction of a flow position.
  • the respective volumetric flow paths from the pump P to the pressure chambers 6, 8 or from these to the tank T can thus be controlled independently of one another. Due to these resolved control edges an exact fine control is possible.
  • the control of the valve members of the switching valves 10, 12, 14, 16 takes place after a pulse width modulation (PWM), wherein preferably a ballistic PWM is used.
  • PWM pulse width modulation
  • the respective switching valve is not completely switched through, but the respective actuating magnet 30, 32, 34, 36 is momentarily energized so that with the introduced energy, the valve member performs only a partial stroke and returns according to its ballistic trajectory back to the closed position.
  • the ballistic drive pulse has a PWM fundamental frequency which is below the maximum switching frequency of the respective switching valve. In other words, a period of the ballistic drive pulse is shorter than a minimum switching time of the respective switching valve 10, 12, 14, 16.
  • the pressure medium supply of the hydraulic cylinder 2 via the control arrangement shown is carried out according to the so-called Meterlnn MeterOut- (MIMO) method, where there are in principle two options. Common to both options is that the hydraulic cylinder 2 supplied or discharged pressure medium volume, which is necessary to achieve a desired chamber pressure or a cylinder position, is known or can be approximately determined depending on the current pressures and positions.
  • the duty cycle of the switching valves 10, 12, 14, 16 then depends on the pressure medium volume required for setting the cylinder position. In this case, the switching valves 10, 12, 14, 16 are operated for the smallest required pressure fluid volumes in said ballistic mode. For larger volumes of pressure medium, activation can also take place after the "normal" PWM or in another way.
  • the DFCUs as in the embodiment according to FIG. 3 are shown, more than a prescribed switching valve on.
  • the switching valves of each DFCU can be operated alternatively or in addition to the "normal" PWM in pulse code mode.
  • control unit 40 which is connected via signal lines 42, 44, 46, 48 with the actuating magnet 30, 32, 34, 36 in order to switch these to energize or de-energized.
  • this metered addition or release of pressure medium takes place over the opening duration of the switching valves 10, 12, 14, 16, via which a pressure space is shut off, while pressure medium volume is supplied to the other pressure space or is discharged from this pressure medium volume.
  • D. h. The piston 4 is then supported, so to speak, on the shut-off oil volume, wherein the pressure in this pressure chamber changes depending on the supplied or discharged volume.
  • the movement of the piston 4 is carried out according to the compression or decompression of the pressure medium in the shut-off pressure chamber. This results in a very finely controllable movement of the piston. 4
  • an inlet valve on one side of the hydraulic consumer and an outlet valve on the other side of the hydraulic consumer it is possible to use an inlet valve on one side of the hydraulic consumer and an outlet valve on the other side of the hydraulic consumer.
  • the switching valves 14 and 10 are controlled while the other two switching valves 12, 16 remain in their locked position.
  • the two switching valves 10, 14 controlling the pressure medium connection of P ⁇ B and of A ⁇ T can be actuated offset in time from one another.
  • the pressure medium connection to the tank controlling switching valve does not trigger.
  • the second option which is preferred here, is to control the intake and exhaust valves associated with a pressure chamber.
  • the annular space 8 is to be supplied with a volume of pressure medium or be discharged therefrom, so that correspondingly, as in FIG. 1 indicated the switching valves 14, 16 are actuated, while the two the pressure chamber 6 associated switching valves 10, 12 are de-energized and thus remain in its closed position.
  • the drive pulses are in FIG. 1 symbolically drawn with u P and u T. It is assumed that this control takes place after the ballistic mode. In this case, it is preferred if the supply or removal of pressure medium to or from the pressure chamber takes place with the currently larger volume of pressure medium, since this can be compressed more strongly, and thus more sensitive fluid metering is possible.
  • this selected valve switching combination generates, for example, an algorithm based on predetermined parameters opening pulses of different duration and from it pulse combinations for controlling the two switching valves 14, 16.
  • the pulse combinations can also be specified manually.
  • a temporal offset of the opening pulses is conceivable for the selected switching valves, i. h., the valves are not synchronized.
  • the pulse length t pulse can be specified as a multiple of a time unit t 1 .
  • the volume which this particular combination is expected to produce is calculated. Subsequently, that pulse combination is selected whose calculated volume corresponds to the required fluid volume Vol ref , which is supplied to the hydraulic cylinder 2 or is discharged therefrom in order to set the desired cylinder position. This pulse combination determined in this way is then output to the actuating magnets 14, 16 via the control unit 40.
  • both the inlet valve and the outlet valve can be actuated offset from one another.
  • each DFCU is implemented only with a switching valve 10,12, 14, 16, which are controlled according to the strategy explained above.
  • FIG. 3 shows a variant in which each DFCU of a plurality of parallel connected Switching valves exists, with the single flow rate of each switching valve to the next switching valve of a DFCU ideally doubles.
  • the maximum achievable flow which can be controlled via such a DFCU, then results from the sum of the individual flows of the individual switching valves.
  • An increase in the resolution is possible by using additional switching valves or by the pulse width modulated control (up to the ballistic control) of individual switching valves.
  • the "smallest" switching valves 10, 12, 14, 16 of each DFCU are correspondingly used for activation.

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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)
  • Magnetically Actuated Valves (AREA)
  • Supply Devices, Intensifiers, Converters, And Telemotors (AREA)
EP13001388.1A 2012-03-27 2013-03-18 Verfahren und hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers Active EP2644903B1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102012006219A DE102012006219A1 (de) 2012-03-27 2012-03-27 Verfahren und hydraulische Steueranordnung zur Ansteuerung eines Verbrauchers

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EP2644903A2 EP2644903A2 (de) 2013-10-02
EP2644903A3 EP2644903A3 (de) 2017-12-06
EP2644903B1 true EP2644903B1 (de) 2019-11-13

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EP (1) EP2644903B1 (zh)
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CN106224312B (zh) * 2016-07-27 2018-01-09 华侨大学 一种单柱塞泵矩阵式布置液压驱动系统
CN106224310B (zh) * 2016-07-27 2018-08-24 华侨大学 一种闭式多单柱塞泵重组控制液压缸系统
CN106224323B (zh) * 2016-09-13 2017-12-01 华侨大学 一种多单柱塞泵重组控制非对称液压缸的闭式液压系统
CN107366647B (zh) * 2017-09-05 2018-10-02 河海大学常州校区 一种槽式聚光器支架的调节方法
CN109323469A (zh) * 2017-09-05 2019-02-12 河海大学常州校区 一种不同反射面适应型槽式集热器及调试方法
DE102018003728A1 (de) 2018-05-07 2019-11-07 Hydac Mobilhydraulik Gmbh Ventilanordnung zur Druckmittelversorgung eines hydraulischen Verbrauchers
US11048281B2 (en) * 2018-06-12 2021-06-29 Robert Bosch Gmbh Real-time capable control strategy for hydraulic systems while systematically taking into consideration control (rate) and state variable constraints
CN109441904B (zh) * 2018-12-26 2020-07-14 燕山大学 一种数字阀组pwm与pcm复合控制装置及其控制方法
DE102021108081B4 (de) 2021-03-30 2023-02-02 Andreas Lupold Hydrotechnik Gmbh Vorrichtung zum Regeln einer Hydraulikpumpe oder eines Hydraulikmotors
CN114483724B (zh) * 2021-12-28 2022-12-23 南京航空航天大学 一种提高阵列高速开关阀使用寿命的pwm控制方法与系统

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EP2644903A3 (de) 2017-12-06
CN103362894A (zh) 2013-10-23
CN103362894B (zh) 2016-12-28
DE102012006219A1 (de) 2013-10-02
EP2644903A2 (de) 2013-10-02

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