EP1828582B1 - Method and device for offsetting bounce effects in a piezo-actuated injection system of an internal combustion engine - Google Patents
Method and device for offsetting bounce effects in a piezo-actuated injection system of an internal combustion engine Download PDFInfo
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- EP1828582B1 EP1828582B1 EP05822186.2A EP05822186A EP1828582B1 EP 1828582 B1 EP1828582 B1 EP 1828582B1 EP 05822186 A EP05822186 A EP 05822186A EP 1828582 B1 EP1828582 B1 EP 1828582B1
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- piezo
- control valve
- bounce
- piezo actuator
- piezoelectric
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- 238000000034 method Methods 0.000 title claims description 42
- 238000002485 combustion reaction Methods 0.000 title claims description 20
- 230000000694 effects Effects 0.000 title claims description 19
- 238000002347 injection Methods 0.000 title claims description 19
- 239000007924 injection Substances 0.000 title claims description 19
- 238000001514 detection method Methods 0.000 claims description 14
- 230000001105 regulatory effect Effects 0.000 claims description 2
- 238000007599 discharging Methods 0.000 claims 1
- 230000001276 controlling effect Effects 0.000 description 5
- 230000002123 temporal effect Effects 0.000 description 5
- 239000000446 fuel Substances 0.000 description 4
- 238000011161 development Methods 0.000 description 3
- 230000018109 developmental process Effects 0.000 description 3
- OKTJSMMVPCPJKN-UHFFFAOYSA-N Carbon Chemical compound [C] OKTJSMMVPCPJKN-UHFFFAOYSA-N 0.000 description 2
- 230000002411 adverse Effects 0.000 description 2
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2034—Control of the current gradient
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2037—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit for preventing bouncing of the valve needle
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D41/00—Electrical control of supply of combustible mixture or its constituents
- F02D41/20—Output circuits, e.g. for controlling currents in command coils
- F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
- F02D2041/2051—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using voltage control
Definitions
- the invention relates to a method and a device for compensating bouncing effects in a piezo-controlled injection system of an internal combustion engine according to patent claims 1 and 8.
- Pump-nozzle units with a control valve actuated by a piezoactuator as an actuator are used in particular in pressure-controlled injection systems in internal combustion engines.
- the control valve is used for controlling a fuel flow from a low-pressure fuel area into a pressure chamber of the pump-nozzle unit and for controlling a pressure curve within the pump-nozzle unit.
- Affected system parameters may include, for example, a hydraulic delivery start, a pressure build-up behavior and scatters within the pump-nozzle unit. This can, inter alia, adversely affect an injection quantity accuracy of the fuel into the pressure chamber. Disadvantageous effects of the bounce may further include unstable pressure build-up behavior as well as undefined transitions between switching states of the control valve. Under certain circumstances it is possible by bouncing that unwanted pressure waves are introduced into the injection system.
- the DE 199 21 456 A1 describes a method and apparatus for avoiding overshoot and bounce of a high pressure injector equipped with a piezoelectric actuator.
- a circuit arrangement for driving the piezoelectric actuator is designed so that it initially reloads the actuator only over a partial stroke with a maximum slope and loads after a break with a different pitch to reach the final stroke.
- the residual charge phase is selected such that an aperiodic transition to the final value is approximated for the mechanical system consisting of actuator valve needle hydraulics.
- the DE 103 11 269 A1 describes a method for driving a piezoelectric element, wherein a drive variable is variable and for determining the drive quantity is dependent on the control variable hingeutton for the transient response of a controlled state variable of the piezoelectric element is minimized.
- the method is particularly suitable for driving a piezoelectric element which is used as an actuator in a fuel injection nozzle in an internal combustion engine.
- the method according to the invention is characterized in that an actual bounce behavior of the control valve is detected and a deviation between the actual bounce behavior and a desired bounce behavior of the control valve is determined and corrected.
- a speed of movement of the needle of the control valve can be minimized or largely eliminated according to a difference between the actual bounce behavior and the target bounce behavior.
- a timely detection and compensation of bounce images of the piezo-controlled injection system is thus advantageously supported, whereby changes in the bounce images, which are caused by long and short-term effects, can be compensated.
- a preferred development of the method according to the invention provides that the speed characteristic of the needle is determined by an embodiment of a holding phase in a loading and / or unloading process of the piezoactuator.
- the holding phase divides the charging process of the piezoactuator into two phases, which is interrupted by the holding phase.
- An amplitude of the holding phase represents a controlled Vorhubparameter, by means of which the speed characteristics of the needle of the control valve can be influenced in an advantageous manner.
- a further preferred embodiment of the method according to the invention provides that when compensating the deviation between the actual bounce behavior and the desired bounce behavior of the control valve, a minimization of areas between maxima in the capacitance curve of the piezoactuator and a reference line connecting the maxima is performed.
- the bouncing of the control valve is imaged by the piezoelectric effect in electrical signals of the piezoactuator, the bouncing in a capacity curve of the piezoactuator can be evaluated.
- the bouncing of the control valve is reflected in the capacity curve of the piezoactuator, and can thus be minimized by minimizing the areas between the reference line connecting the capacity maxima and the capacity maxima.
- This is done by an optimized control the piezo actuator in the charging process, whereby a speed profile of the needle of the piezoelectric actuator is designed such that the needle when closing the control valve at the optimum speed on the valve seat and thereby bouncing is minimized.
- the minimized bounce is shown in minimized areas between the reference line connecting the capacity maxima and the capacity maxima of the piezoactuator.
- FIG. 1 shows in three figures temporal courses of electrical signals and characteristics of a piezo actuator for controlling a control valve in a pump-nozzle unit of an internal combustion engine.
- 1a shows a curve of a piezoelectric voltage u piezo
- 1b a curve of a piezoelectric current i piezo with which the piezoactuator is driven.
- a time characteristic of the piezo voltage u piezo and the piezoelectric current i piezo- computationally determined characteristics of the piezoactuator is plotted.
- 1c denotes a time course of a piezoelectric charge q piezo and 1d a time profile of a piezoelectric capacitance C piezo , which is determined from a division of the piezoelectric charge q piezo by the piezoelectric voltage u piezo .
- a mechanical stroke of an external reference sensor which is arranged for measurement purposes within the control valve is shown. It can be seen that the course of the mechanical stroke 1f has pronounced extrema with maxima and minima, resulting from a bouncing of the control valve, in particular a needle of the control valve.
- a time profile of the capacitance C piezo of the piezoactuator is shown. It can be seen that the course of the piezoelectric capacitance C piezo essentially correlates with the course 1f of the mechanical stroke of the reference sensor.
- a closing behavior of the piezo-controlled control valve can be determined by the in FIG. 1 describe described electrical signal waveforms.
- the relationship between the individual variables can be used for a qualitative assessment of a bump characteristic of the valve needle.
- FIG. 2 shows in two figures determined by a simulation waveforms of a force input F piezo in the piezoelectric actuator and thereby caused mechanical strokes.
- 2a denotes a time profile of the force input F piezo in the piezoactuator.
- 2b shows a resulting time course of a mechanical stroke of the piezo actuator.
- 2c plotted a time course of a mechanical stroke of a needle of the control valve.
- the differences in the courses 2b and 2c result from the fact that between the piezo actuator and the control valve needle a Mattertragerumble is arranged, which dampens the mechanical stroke of the piezo actuator.
- FIG. 3 shows in two figures by means of a sampling process time-sampled electrical variables of the piezoelectric actuator and a calculated therefrom over time the piezoelectric capacitance C piezo of the piezoelectric actuator.
- 3a shows a time profile of the sampled piezo voltage u piezo .
- 3b is a piezo voltage corresponding to the piezo voltage sampled course of the piezoelectric charge q piezo referred to, which is determined from an integration of the piezoelectric current i piezo .
- a time profile of the piezoelectric capacitance C piezo of the piezoactuator which is determined from the sampled values of the piezoelectric voltage u piezo and the piezoelectric charge q piezo, is shown.
- FIG. 4 shows an enlarged view of the lower figure of FIG. 3 , It is the sampled course of the piezoelectric capacitance C piezo shown, 4a with a first maximum of the piezoelectric capacitance C piezo is designated. This first maximum results from a first striking of the needle of the control valve to the valve seat upon closure of the control valve.
- 4b is exemplified a sampled, discrete value from the course of the piezoelectric capacitance C piezo .
- FIG. 4c illustrates a temporal detection window in which the course of the piezoelectric capacitance C piezo is detected in the method according to the invention.
- Denoted at 4d is a reference line connecting individual maxima in the course of the piezocapacitance C piezo within the detection window 4c and used to define areas between the reference line and the path of the piezocapacitance C piezo .
- A1, A2 and A3 areas are referred to, which are detected according to the invention between the reference line 4d and maxima in the course of the piezoelectric capacitance C piezo .
- the reference line is formed between adjacent maxima of the course of the piezoelectric capacitance as a straight line.
- the areas A1 and A3 are located below the reference line and the area A2 above the reference line.
- the bouncing of the needle of the control valve in the course of the piezoelectric capacitance C piezo reflects such that the areas A1, A2 and A3 are greater, the more pronounced the bouncing of the needle.
- the extent of the area A2, which may be caused by an overshoot of the needle after impact with the valve seat, is in the illustration of FIG. 4 essentially zero.
- the size of the areas between the course of the piezocapacitance and the reference line between maximum values, ie local maxima The piezocapacity within a fixed time acquisition window is used as a controlled variable to reduce bouncing of the needle.
- control valve is controlled in such a way that the areas between the reference line and the course of the piezoelectric capacitance are minimized within the temporal detection window.
- the detection window starts and ends preferably at a local maximum of the piezo capacitance.
- FIG. 5 shows a schematic block diagram of an apparatus with which the inventive method is performed.
- a detection device 13 By means of a detection device 13, the in FIG. 4 shown areas between the reference line 4d and the maxima in the course of the piezoelectric capacitance C detected piezo summarily and fed to an absolute value of the total area a summation point 15 with a negative sign.
- a setpoint presetting device 12 is used to establish a minimized extent of the detected areas, wherein a value of substantially zero is desired.
- the output value of the setpoint input device 12 therefore essentially corresponds to a nominal value of the total area which is likewise fed to the summation point 15.
- the output value of the summation point 15 is thus a difference value between the area sum detected by the detection device 13 and a setpoint of the total area in the course of the piezoelectric capacitance C piezo .
- the output value at the summation point 15 thus essentially corresponds to a control difference which is fed to a control device 11.
- the control device 11 regulates the supplied control difference and generates for this purpose a timing control information for the piezoelectric actuator.
- the timing control information may include, for example, a number of charging steps in a charging of the piezo actuator.
- the generated control information is supplied to a limiter 14, which essentially performs a plausibility check represents.
- the control information generated by the control device 11 and limited by means of the limiter 14 control information is then supplied to an adder 16.
- a pilot control device 10 is supplied with a first operating parameter 17 of the internal combustion engine, a second operating parameter 18 of the internal combustion engine and a third operating parameter 19 of the internal combustion engine.
- the first operating parameter 17, the second operating parameter 18 and the third operating parameter 19 model a system state of the internal combustion engine by means of characteristic map data.
- the first operating parameter 17 may comprise a closing time of the control valve, the second operating parameter 18 a rotational speed of the internal combustion engine, and the third operating parameter 19 various physical environmental variables of the internal combustion engine.
- the pilot control device 10 a pilot value or initial value for the time control information of the piezoactuator is generated and likewise fed to the adder 16 via an output of the pilot control device 10.
- the control information generated by the pilot control device 10 can represent, for example, a rough estimate for the design of the holding phase during the charging process of the piezoactuator.
- a time information for the first load time until the hold phase can thus be generated. This must always be smaller than the closing time of the control valve.
- the time control information generated by the pilot control device 10 and the control device 11 are added and are available at the output of the adder 16 as the fourth operating parameter 20 of the internal combustion engine for controlling the piezoelectric actuator available.
- the fourth operating parameter 20 thus represents an end value of a number of loading steps in the first phase during the charging process of the piezo actuator until the holding phase.
- the fourth operating parameter 20 it is possible to variably form the length of the holding phase and / or the partial lift level of the holding phase and thereby to influence a speed characteristic of the needle of the control valve.
- the design of the holding phase within the charging process of the piezoelectric actuator can, in addition to the aforementioned amplitude, also comprise a time duration of the holding phase.
- a speed profile of the needle of the control valve can be optimized in this way insofar as an impact of the needle in the valve seat on the one hand well defined and on the other hand designed substantially bounce-free.
- the device represents the FIG.
- the inventive device of FIG. 5 thus implements a strategy for designing the holding phase.
- the control algorithm implemented by the control unit 11 determines a residual error value from the supplied area information and adds this to the precontrol value.
- FIG. 6A shows principal time courses of the piezoelectric voltage u piezo and the piezoelectric capacitance C piezo in a closing operation of the control valve according to the prior art.
- 6d denotes a curve of the piezo voltage u piezo , which undergoes a change of the gradient at a point 6a of a closing of the control valve as a result of the piezoelectric effect. It can be clearly seen that, starting from this point in time, the piezo voltage u piezo is steeper than before the time when the control valve closed.
- a curve of the piezoelectric capacitance C piezo is designated, based on the basis of FIG. 3 explained Way is determined.
- a curve of the piezo voltage u piezo during the holding phase is essentially constant.
- the amplitude of the holding phase is variable according to the invention and is denoted by 6g. It can be seen that due to the insertion of the holding phase in the charging process of the piezo actuator from the time 6 a of the closing of the control valve, the gradient of the piezoelectric voltage u piezo is substantially continuous. Furthermore, it can be seen in the course of the piezo capacitance C piezor that the areas between the reference line 6f and the extremes in the course of the piezoelectric capacitance C piezo in the detection window 6c are minimized or reduced.
- the charging phase for the piezoactuator is influenced such that a speed profile of the control valve is achieved, with which the bouncing of the control valve is compensated.
- This can be done, for example, in that no energization of the piezoelectric actuator is performed during the holding phase, whereby a decrease in the speed of the needle of the control valve is achieved.
- This results a prevention of further acceleration of the needle of the control valve, so that at the time of impact of the control valve needle in the valve seat bouncing or Nachprellen is largely eliminated.
- the holding phase can also be inserted into a discharge process of the piezoactuator.
- FIG. 7 shows a schematic representation of a control valve 22, with which the invention can be performed.
- the control valve 22 is controlled by means of a piezo actuator 21, which acts on a needle 23 in terms of power.
- a piezo actuator 21 acts on a needle 23 in terms of power.
- the needle 23 is pressed into a valve seat 24, according to the invention bouncing of the needle 23 is minimized as a result of being impacted in the valve seat 24.
- the invention relates to a device for compensating for bounce effects in a piezo-controlled injection system of an internal combustion engine, wherein the injection system comprises a controlled by a piezo actuator 21 control valve 22, wherein the device comprises a detection device 13 for detecting an actual bounce of the control valve 22 and a Deviation between the actual bounce and the target bounce of the control valve 22 includes, wherein the device further comprises a control device 11 for compensating the deviation between the actual bounce and the target bounce behavior, wherein a control information for the control valve 22 is generated, when adjusting the deviation between the actual bounce behavior and the desired bounce behavior of the control valve are minimized in a time acquisition window areas between a capacity curve of the piezoelectric actuator and a reference line, wherein the reference line is formed between local maxima of the capacitance curve as a straight line.
Description
Die Erfindung betrifft ein Verfahren und eine Vorrichtung zur Kompensation von Prelleffekten in einem piezogesteuerten Einspritzsystem einer Verbrennungskraftmaschine gemäß den Patentansprüchen 1 und 8.The invention relates to a method and a device for compensating bouncing effects in a piezo-controlled injection system of an internal combustion engine according to
Pumpe-Düse-Einheiten (PDE) mit einem von einem Piezoaktuator als Stellantrieb angesteuerten Steuerventil werden insbesondere in druckgesteuerten Einspritzsystemen in Verbrennungskraftmaschinen verwendet. Dabei wird das Steuerventil zum Steuern eines Kraftstoffflusses von einem Kraftstoff-Niederdruckbereich in einen Druckraum der Pumpe-Düse-Einheit sowie zum Steuern eines Druckverlaufs innerhalb der Pumpe-Düse-Einheit verwendet.Pump-nozzle units (PDE) with a control valve actuated by a piezoactuator as an actuator are used in particular in pressure-controlled injection systems in internal combustion engines. In this case, the control valve is used for controlling a fuel flow from a low-pressure fuel area into a pressure chamber of the pump-nozzle unit and for controlling a pressure curve within the pump-nozzle unit.
Durch Untersuchungen wurde festgestellt, dass Prelleffekte innerhalb des Steuerventils negative Auswirkungen auf Systemparameter der piezogesteuerten Einspritzsysteme haben können. Davon betroffene Systemparameter können beispielsweise einen hydraulischen Förderbeginn, ein Druckaufbauverhalten und Streuungen innerhalb der Pumpe-Düse-Einheit umfassen. Dies kann sich unter anderem nachteilig auf eine Einspritzmengengenauigkeit des Kraftstoffs in den Druckraum auswirken. Nachteilige Auswirkungen des Prellens können ferner ein instabiles Druckaufbauverhalten sowie undefinierte Übergänge zwischen Schaltzuständen des Steuerventils umfassen. Unter Umständen ist es durch das Prellen möglich, dass unerwünschte Druckwellen in das Einspritzsystem eingebracht werden.Investigations have found that bouncing effects within the control valve can have a negative impact on system parameters of the piezo-controlled injection systems. Affected system parameters may include, for example, a hydraulic delivery start, a pressure build-up behavior and scatters within the pump-nozzle unit. This can, inter alia, adversely affect an injection quantity accuracy of the fuel into the pressure chamber. Disadvantageous effects of the bounce may further include unstable pressure build-up behavior as well as undefined transitions between switching states of the control valve. Under certain circumstances it is possible by bouncing that unwanted pressure waves are introduced into the injection system.
Durch das Prellen des Steuerventils kann eine Instabilität eines Betriebsverhaltens der Pumpe-Düse-Einheit nachteilig erhöht sein, wobei die Instabilität umso höher ist, je größer eine Intensität des Prellens ausgeprägt ist. Elementare Anforderungen bei einer Regelung der piezogesteuerten Einspritzsysteme, wie beispielsweise eine Gleichstellung unter den einzelnen Zylindern der Verbrennungskraftmaschine und/oder eine Kompensation von Alterungserscheinungen und Toleranzen an Einspritzelementen können ferner durch das Prellen des Steuerventils in nachteiliger Weise erschwert sein.By bouncing the control valve, an instability of a performance of the unit injector may be adversely increased, the larger the instability is an intensity of the bounce is pronounced. Furthermore, elementary requirements for controlling the piezo-controlled injection systems, such as equality between the individual cylinders of the internal combustion engine and / or compensation of aging phenomena and tolerances on injection elements, may disadvantageously be hindered by the bouncing of the control valve.
Die
Die
Es ist daher die Aufgabe der vorliegenden Erfindung, ein Verfahren bereitzustellen, mit dem die geschilderten nachteiligen Effekte innerhalb der piezogesteuerten Einspritzsysteme reduziert werden. Die Aufgabe wird gelöst mit einem Verfahren gemäß Patentanspruch 1 sowie mit einer Vorrichtung gemäß Patentanspruch 8. Bevorzugte Weiterbildungen des erfindungsgemäßen Verfahrens sind in abhängigen Ansprüchen angegeben.It is therefore the object of the present invention to provide a method with which the described disadvantageous effects are reduced within the piezo-controlled injection systems. The object is achieved with a method according to
Das erfindungsgemäße Verfahren ist zur Kompensation von Prelleffekten in einem piezogesteuerten Einspritzsystem einer Verbrennungskraftmaschine vorgesehen, wobei das Einspritzsystem ein von einem Piezoaktuator angesteuertes Steuerventil umfasst. Das Verfahren weist folgende Verfahrensschritte auf:
- Erfassen eines Ist-Prellverhaltens des Steuerventils, und
- Ermitteln und Ausregeln einer Abweichung zwischen dem Ist-Prellverhalten und einem Soll-Prellverhalten des Steuerventils, wobei eine Ansteuerinformation für das Steuerventil generiert wird, durch die eine Geschwindigkeitscharakteristik einer Nadel des Steuerventils beeinflusst wird.
- Detecting an actual bounce behavior of the control valve, and
- Determining and compensating a deviation between the actual bounce behavior and a desired bounce behavior of the control valve, wherein a control information for the control valve is generated, by which a speed characteristic of a needle of the control valve is influenced.
Das erfindungsgemäße Verfahren zeichnet sich dadurch aus, dass ein Ist-Prellverhalten des Steuerventils erfasst und eine Abweichung zwischen dem Ist-Prellverhalten und einem Soll-Prellverhalten des Steuerventils ermittelt und ausgeregelt wird. Zu diesem Zweck wird eine Geschwindigkeitscharakteristik einer Nadel des Steuerventils beeinflusst. Auf diese Art und Weise kann eine Geschwindigkeit einer Bewegung der Nadel des Steuerventils entsprechend einer Differenz zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten minimiert bzw. weitestgehend eliminiert werden. Eine zeitnahe Erfassung und Kompensation von Prellbildern des piezogesteuerten Einspritzsystems ist somit vorteilhaft unterstützt, wobei Änderungen der Prellbilder, die durch Lang- und Kurzzeiteffekte verursacht sind, kompensiert werden können.The method according to the invention is characterized in that an actual bounce behavior of the control valve is detected and a deviation between the actual bounce behavior and a desired bounce behavior of the control valve is determined and corrected. For this purpose, a speed characteristic a needle of the control valve influenced. In this way, a speed of movement of the needle of the control valve can be minimized or largely eliminated according to a difference between the actual bounce behavior and the target bounce behavior. A timely detection and compensation of bounce images of the piezo-controlled injection system is thus advantageously supported, whereby changes in the bounce images, which are caused by long and short-term effects, can be compensated.
Eine bevorzugte Weiterbildung des erfindungsgemäßen Verfahrens sieht vor, dass die Geschwindigkeitscharakteristik der Nadel durch eine Ausgestaltung einer Haltephase in einem Lade- und/oder Entladevorgang des Piezoaktuators festgelegt wird. Durch die Haltephase wird der Ladevorgang des Piezoaktuators in zwei Phasen unterteilt, die durch die Haltephase unterbrochen ist. Eine Amplitude der Haltephase stellt dabei einen geregelten Vorhubparameter dar, mit dessen Hilfe die Geschwindigkeitscharakteristik der Nadel des Steuerventils in vorteilhafter Weise beeinflussbar ist.A preferred development of the method according to the invention provides that the speed characteristic of the needle is determined by an embodiment of a holding phase in a loading and / or unloading process of the piezoactuator. The holding phase divides the charging process of the piezoactuator into two phases, which is interrupted by the holding phase. An amplitude of the holding phase represents a controlled Vorhubparameter, by means of which the speed characteristics of the needle of the control valve can be influenced in an advantageous manner.
Eine weitere bevorzugte Ausgestaltung des erfindungsgemäßen Verfahrens sieht vor, dass beim Ausregeln der Abweichung zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten des Steuerventils ein Minimieren von Flächen zwischen Maxima im Kapazitätsverlauf des Piezoaktuators und einer die Maxima verbindenden Bezugslinie durchgeführt wird.A further preferred embodiment of the method according to the invention provides that when compensating the deviation between the actual bounce behavior and the desired bounce behavior of the control valve, a minimization of areas between maxima in the capacitance curve of the piezoactuator and a reference line connecting the maxima is performed.
Aufgrund der Tatsache, dass das Prellen des Steuerventils durch den piezoelektrischen Effekt in elektrischen Signalen des Piezoaktuators abgebildet wird, kann das Prellen in einem Kapazitätsverlauf des Piezoaktuators evaluiert werden. Das Prellen des Steuerventils spiegelt sich im Kapazitätsverlauf des Piezoaktuators wider, und kann somit durch eine Minimierung der Flächen zwischen der die Kapazitätsmaxima verbindenden Bezugslinie und den Kapazitätsmaxima entsprechend minimiert werden. Dies geschieht durch eine optimierte Ansteuerung des Piezoaktuators im Ladevorgang, wodurch ein Geschwindigkeitsverlauf der Nadel des Piezoaktuators derart ausgebildet ist, dass die Nadel beim Schließen des Steuerventils mit optimaler Geschwindigkeit am Ventilsitz aufschlägt und dadurch das Prellen minimiert ist. Das minimierte Prellen ist in minimierten Flächen zwischen der die Kapazitätsmaxima verbindenden Bezugslinie und den Kapazitätsmaxima des Piezoaktuators abgebildet.Due to the fact that the bouncing of the control valve is imaged by the piezoelectric effect in electrical signals of the piezoactuator, the bouncing in a capacity curve of the piezoactuator can be evaluated. The bouncing of the control valve is reflected in the capacity curve of the piezoactuator, and can thus be minimized by minimizing the areas between the reference line connecting the capacity maxima and the capacity maxima. This is done by an optimized control the piezo actuator in the charging process, whereby a speed profile of the needle of the piezoelectric actuator is designed such that the needle when closing the control valve at the optimum speed on the valve seat and thereby bouncing is minimized. The minimized bounce is shown in minimized areas between the reference line connecting the capacity maxima and the capacity maxima of the piezoactuator.
Ein Ausführungsbeispiel der Erfindung wird nachfolgend anhand von mehreren Figuren detailliert beschrieben. Dabei zeigt:
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zeitliche Verläufe von elektrischen Signalen und Kenngrößen eines Piezoaktuators,Figur 1 -
Figur 2 zwei Graphen, die einen Zusammenhang zwischen einem Krafteintrag in den Piezoaktuator und einem mechanischen Hub des Piezoaktuators bzw. einer vom Piezoaktuator angesteuerten Steuerventilnadel darstellen, -
Figur 3 zwei Graphen, die abgetastete elektrische Signale des Piezoaktuators und einen daraus ermittelten Kapazitätsverlauf des Piezoaktuators darstellen, -
Figur 4 eine vergrößerte Darstellung des Kapazitätsverlaufs der unteren Abbildung vonFigur 3 , -
ein Ausführungsbeispiel einer Vorrichtung, mit der das erfindungsgemäße Verfahren durchführbar ist,Figur 5 -
Figur 6A Verläufe der Piezospannung und der Piezokapazität eines Piezoaktuators beim Prellen gemäß Stand der Technik, -
Figur 6B Verläufe der Piezospannung und der Piezokapazität eines Piezoaktuators, bei dem das Prellen erfindungsgemäß minimiert ist, und -
eine prinzipielle Darstellung eines von einem Piezoaktuator als Stellantrieb angesteuerten Steuerventils.Figur 7
-
FIG. 1 temporal courses of electrical signals and characteristics of a piezoactuator, -
FIG. 2 two graphs illustrating a relationship between a force input into the piezo actuator and a mechanical stroke of the piezo actuator or a control valve needle controlled by the piezo actuator, -
FIG. 3 two graphs representing sampled electrical signals of the piezo actuator and a capacity curve of the piezoactuator determined therefrom; -
FIG. 4 an enlarged view of the capacity curve of the lower figure ofFIG. 3 . -
FIG. 5 An embodiment of a device with which the method according to the invention is feasible, -
FIG. 6A Characteristics of the piezoelectric voltage and the piezo capacity of a piezoactuator when bouncing according to the prior art, -
FIG. 6B Characteristics of the piezoelectric voltage and the piezoelectric capacity of a piezoelectric actuator, in which the bouncing is minimized according to the invention, and -
FIG. 7 a schematic representation of a controlled by a piezo actuator as an actuator control valve.
In der unteren Abbildung der
Dies lässt sich damit begründen, dass das Prellen des Steuerventils über den piezoelektrische Effekt im Kapazitätsverlauf des Piezoaktuators abgebildet wird. Bei ungefähr 0,25 ms ist in der unteren Abbildung ein erstes Anschlagen des Referenzsensors an einen Ventilsitz des Steuerventils dadurch erkennbar, dass der Signalverlauf 1f zu diesem Zeitpunkt ein erstes Maximum aufweist. In Entsprechung dazu ist in der oberen Abbildung der
Ein Schließverhalten des piezogesteuerten Steuerventils lässt sich anhand der in
Dabei haben die Parameter folgende Bedeutungen:
- f(t)
- Kraft des Piezoaktuators
- s(t)
- mechanischer Hub des Piezoaktuators
- S
- Kleinsignalelastizität des Piezoaktuators
- d
- piezoelektrische Ladungskonstante
- C0
- Kleinsignalkapazität des Piezoaktuators
- qpiezo
- Piezoladung
- upiezo
- Piezospannung
- f (t)
- Force of the piezoactuator
- s (t)
- mechanical stroke of the piezoactuator
- S
- Low-signal elasticity of the piezoactuator
- d
- piezoelectric charge constant
- C 0
- Small signal capacity of the piezo actuator
- q piezo
- piezo charge
- u piezo
- piezovoltage
Aus den mathematischen Beziehungen erkennt man, dass bei einer Messung der Piezoladung qpiezo, der Piezospannung upiezo und der Kleinsignalkapazität Co unter Berücksichtigung piezoelektrischer Ladungs- und Elastizitätsverhältnisse die Kraft und der mechanische Hub des Piezoaktuators berechnet werden können.It can be seen from the mathematical relationships that, when measuring the piezoelectric charge q piezo , the piezo voltage u piezo and the small signal capacitance C o taking into account the piezoelectric charge and elasticity conditions, the force and the mechanical stroke of the piezo actuator can be calculated.
Es ist deutlich erkennbar, dass der Verlauf der Piezokapazität Cpiezo aufgrund des Prellens des Steuerventils, das sich über einen Rückkopplungseffekt in elektrischen Signalen des Piezoaktuators abbildet, ausgeprägte Extrema aufweist. Die untere Abbildung der
Der
Die Regelungseinrichtung 11 regelt die zugeführte Regeldifferenz aus und generiert zu diesem Zweck eine zeitliche Ansteuerinformation für den Piezoaktuator. Die zeitliche Ansteuerinformation kann beispielsweise eine Anzahl von Ladeschritten in einem Ladevorgang des Piezoaktuators umfassen. Dabei wird die generierte Ansteuerinformation einem Begrenzer 14 zugeführt, der im Wesentlichen eine Plausibilitätsüberprüfung darstellt. Die von der Regelungseinrichtung 11 erzeugte und mittels des Begrenzers 14 begrenzte Ansteuerinformation wird sodann einer Addiereinrichtung 16 zugeführt.The
Einer Vorsteuereinrichtung 10 werden ein erster Betriebsparameter 17 der Verbrennungskraftmaschine, ein zweiter Betriebsparameter 18 der Verbrennungskraftmaschine und ein dritter Betriebsparameter 19 der Verbrennungskraftmaschine zugeführt. Der erste Betriebsparameters 17, der zweite Betriebsparameter 18 und der dritte Betriebsparameter 19 modellieren dabei einen Systemzustand der Verbrennungskraftmaschine mittels Kennfelddaten. Beispielsweise kann der erste Betriebsparameter 17 eine Schließzeit des Steuerventils, der zweite Betriebsparameter 18 eine Drehzahl der Verbrennungskraftmaschine und der dritte Betriebsparameter 19 verschiedene physikalische Umgebungsvariablen der Verbrennungskraftmaschine umfassen. Mittels der Vorsteuereinrichtung 10 wird ein Vorsteuer- bzw. Initialwert für die zeitliche Ansteuerinformation des Piezoaktuators geniert und über einen Ausgang der Vorsteuereinrichtung 10 ebenfalls der Addiereinrichtung 16 zugeführt.A
Die von der Vorsteuereinrichtung 10 generierte Ansteuerinformation kann beispielsweise einen groben Schätzwert für die Ausgestaltung der Haltephase im Ladevorgang des Piezoaktuators darstellen. Mittels eines in der Vorsteuereinrichtung 10 implementierten Vorsteueralgorithmus kann somit eine Zeitinformation für die erste Ladezeit bis zur Haltephase generiert werden. Diese muss stets kleiner als die Schließzeit des Steuerventils sein.The control information generated by the
Mittels der Addiereinrichtung 16 werden die von der Vorsteuereinrichtung 10 und der Regelungseinrichtung 11 erzeugten zeitlichen Ansteuerinformationen addiert und stehen am Ausgang der Addiereinrichtung 16 als vierter Betriebsparameter 20 der Verbrennungskraftmaschine zur Ansteuerung des Piezoaktuators zur Verfügung. Der vierte Betriebsparameter 20 repräsentiert somit einen Endwert einer Anzahl von Ladeschritten in der ersten Phase im Ladevorgang des Piezoaktuators bis zur Haltephase.By means of the
Mit dem vierten Betriebsparameter 20 ist es möglich, die Länge der Haltephase und/oder das Teilhubniveau der Haltephase variierbar auszubilden und dadurch eine Geschwindigkeitscharakteristik der Nadel des Steuerventils zu beeinflussen. Die Ausgestaltung der Haltephase innerhalb des Ladevorgangs des Piezoaktuators kann außer der genannten Amplitude noch eine zeitliche Dauer der Haltephase umfassen. Ein Geschwindigkeitsverlauf der Nadel des Steuerventils kann auf diese Weise insofern optimiert werden, als ein Auftreffen der Nadel im Ventilsitz einerseits wohldefiniert und andererseits im Wesentlichen prellfrei ausgestaltet ist. In ihrer Grundstruktur repräsentiert die Vorrichtung der
Die erfindungsgemäße Vorrichtung der
In
In
Als besonders vorteilhaft wird bei der vorliegenden Erfindung angesehen, dass durch eine Variation der Amplitude der Haltephase die Ladephase für den Piezoaktuator derart beeinflusst wird, dass ein Geschwindigkeitsverlauf des Steuerventils erreicht wird, mit dem das Prellen des Steuerventils kompensiert ist. Dies kann beispielsweise dadurch erfolgen, dass während der Haltephase keine Bestromung des Piezoaktuators durchgeführt wird, wodurch eine Abnahme der Geschwindigkeit der Nadel des Steuerventils erreicht wird. Daraus resultiert eine Verhinderung einer weiteren Beschleunigung der Nadel des Steuerventils, sodass zum Auftreffzeitpunkt der Steuerventilnadel im Ventilsitz ein Prellen bzw. Nachprellen weitgehend eliminiert ist.It is considered to be particularly advantageous in the present invention that by varying the amplitude of the holding phase, the charging phase for the piezoactuator is influenced such that a speed profile of the control valve is achieved, with which the bouncing of the control valve is compensated. This can be done, for example, in that no energization of the piezoelectric actuator is performed during the holding phase, whereby a decrease in the speed of the needle of the control valve is achieved. This results a prevention of further acceleration of the needle of the control valve, so that at the time of impact of the control valve needle in the valve seat bouncing or Nachprellen is largely eliminated.
Weiterhin wird als vorteilhaft angesehen, dass durch eine zeitnahe Erfassung der elektrischen Signale und Kenngrößen des Piezoaktuators und deren Auswertung während einer Steuerventilschließ-/Öffnungsphase, das Prellverhalten jeder einzelnen Pumpe-Düse-Einheit individuell beobachtbar ist und über eine Ansteuerungs- bzw. Regelungseinrichtung, wie sie beispielsweise in
Mittels der inhärenten sensorischen Eigenschaften des Piezoaktuators durch Ausnutzung des piezoelektrischen Effekts kann vorteilhaft eine aufwendige und kostenintensive Sensorik zur Erfassung der elektrischen Signale und Kenngrößen eingespart werden. Es versteht sich von selbst, dass zum erfindungsgemäßen Kompensieren des Prellens die Haltephase auch in einen Entladevorgang des Piezoaktuators eingefügt werden kann.By means of the inherent sensory properties of the piezoactuator by utilizing the piezoelectric effect, it is advantageously possible to save a complex and cost-intensive sensor system for detecting the electrical signals and parameters. It goes without saying that for compensating the bounce according to the invention, the holding phase can also be inserted into a discharge process of the piezoactuator.
In einer alternativen Ausführungsform der Erfindung ist es auch denkbar, dass statt der als Regelgröße verwendeten Flächensummendifferenz die über den piezoelektrischen Effekt ermittelte Kraft und/oder der mechanische Hub des Piezoaktuators verwendet werden.In an alternative embodiment of the invention, it is also conceivable that, instead of the surface difference used as a control variable, the force determined via the piezoelectric effect and / or the mechanical stroke of the piezoactuator are used.
Durch den Krafteintrag des Piezoaktuators 21 in die Nadel 23 wird die Nadel 23 in einen Ventilsitz 24 gedrückt, wobei erfindungsgemäß ein Prellen der Nadel 23 in Folge des Aufschlagens in den Ventilsitz 24 minimiert ist.
As a result of the force input of the
Die in der Beschreibung, den Patentansprüchen und den Zeichnungen offenbarten Merkmale der Erfindung können sowohl einzeln als auch in beliebiger Kombination für die Durchführung der Erfindung wesentlich sein.The features of the invention disclosed in the specification, the claims and the drawings may be essential to the practice of the invention both individually and in any combination.
In einer Weiterbildung betrifft die Erfindung ein Verfahren zur Kompensation von Prelleffekten in einem piezogesteuerten Einspritzsystem einer Verbrennungskraftmaschine, mit einem von einem Piezoaktuator angesteuerten Steuerventil, mit folgenden Verfahrensschritten:
- Erfassen eines Ist-Prellverhaltens des Steuerventils; und
- Ermitteln und Ausregeln einer Abweichung zwischen dem Ist-Prellverhalten und einem Soll-Prellverhalten des Steuerventils, wobei für das Steuerventil in der Weise angesteuert wird, dass die Geschwindigkeit der Nadel des Steuerventils beeinflusst wird, wobei beim Ausregeln der Abweichung zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten der Nadel Flächen zwischen einem Kapazitätsverlauf des Piezoaktuators und einer Maxima des Kapazitätsverlaufs verbindenden Bezugslinie minimiert werden.
- Detecting an actual bounce behavior of the control valve; and
- Determining and compensating for a deviation between the actual bounce behavior and a desired bouncing behavior of the control valve, wherein the control valve is controlled in such a way that the speed of the needle of the control valve is influenced, wherein when compensating the deviation between the actual bounce and the Target bounce behavior of the needle surfaces between a capacitance curve of the piezo actuator and a maximum capacity curve connecting the reference line are minimized.
In einer weiteren Ausführungsform betrifft die Erfindung eine Vorrichtung zur Kompensation von Prelleffekten in einem piezogesteuerten Einspritzsystems einer Verbrennungskraftmaschine, wobei das Einspritzsystem ein von einem Piezoaktuator 21 angesteuertes Steuerventil 22 umfasst, wobei die Vorrichtung eine Erfassungseinrichtung 13 zum Erfassen eines Ist-Prellverhaltens des Steuerventils 22 und einer Abweichung zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten des Steuerventils 22 umfasst, wobei die Vorrichtung ferner eine Regelungseinrichtung 11 zum Ausregeln der Abweichung zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten umfasst, wobei eine Ansteuerinformation für das Steuerventil 22 generiert wird, wobei beim Ausregeln der Abweichung zwischen dem Ist-Prellverhalten und dem Soll-Prellverhalten des Steuerventils in einem zeitlichen Erfassungsfenster Flächen zwischen einem Kapazitätsverlauf des Piezoaktuators und einer Bezugslinie minimiert werden, wobei die Bezugslinie zwischen lokalen Maxima des Kapazitätsverlaufs als Gerade ausgebildet ist.In a further embodiment, the invention relates to a device for compensating for bounce effects in a piezo-controlled injection system of an internal combustion engine, wherein the injection system comprises a controlled by a
Claims (7)
- Method for compensating bounce effects in a piezo-controlled injection system of an internal combustion engine, having a control value which is actuated by a piezo actuator, having the following method steps:- detecting an actual bounce behaviour of the control value, and- determining and compensating a deviation between the actual bounce behaviour and a setpoint bounce behaviour of the control valve,wherein actuation information for the control valve, by which a speed characteristic of a needle of the control valve is influenced, is generated, wherein the speed characteristic of the needle is defined by a configuration of a holding phase in a charging and/or discharging process of the piezo actuator.
- Method according to Claim 1, where charge values and voltage values of the piezo actuator are sampled, and a capacitant profile of the piezo actuator is determined on the basis of the charge values and voltage values.
- Method according to Claim 2, wherein the configuration of the holding phase in the charging process of the piezo actuator is determined by means of the following method steps:- determining a pilot-control value of the holding phase; and- adding the generated actuation information to the pilot-control value.
- Method according to Claim 3, wherein the holding phase is defined by a corresponding number of charging steps of the piezo actuator.
- Method according to one of Claims 1 to 4, wherein during the compensation of the deviation between the actual bounce behaviour and the setpoint bounce behaviour of the control valve an extent of areas between the maximum values in the capacitance profile of the piezo actuator and a reference line connecting the maximum values is minimized.
- Method according to one of Claims 1 to 5, wherein the method is carried out adaptively during operation of the internal combustion engine.
- Device for compensating bounce effects in a piezo-controlled injection system of an internal combustion engine, wherein the injection system comprises a control valve (22) which is actuated by a piezo actuator (21) wherein the device comprises a detection apparatus (13) for detecting an actual bounce behaviour of the control valve (22) on the basis of a capitance profile of the piezo actuator and for determining a deviation between the actual bounce behaviour and the setpoint bounce behaviour of the control valve (22), wherein the device also comprises a regulating apparatus (11) for compensating the deviation between the actual bounce behaviour and the setpoint bounce behaviour, wherein actuation information for the control valve (22) is generated, wherein the device can be used for carrying out the method according to one of Claims 1 to 6.
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DE102004062073.3A DE102004062073B4 (en) | 2004-12-23 | 2004-12-23 | Method and device for compensation of bounce effects in a piezo-controlled injection system of an internal combustion engine |
PCT/EP2005/013959 WO2006069750A1 (en) | 2004-12-23 | 2005-12-22 | Method and device for offsetting bounce effects in a piezo-actuated injection system of an internal combustion engine |
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EP1828582A1 EP1828582A1 (en) | 2007-09-05 |
EP1828582B1 true EP1828582B1 (en) | 2015-02-25 |
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US (1) | US8239115B2 (en) |
EP (1) | EP1828582B1 (en) |
DE (1) | DE102004062073B4 (en) |
WO (1) | WO2006069750A1 (en) |
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DE102007005360B3 (en) * | 2007-02-02 | 2008-07-24 | Siemens Ag | Method for operation of fluid measuring device, involves supplying electric power to solid body actuator by charging pulses and power is discharged to actuator by discharging pulses |
DE102008040412A1 (en) | 2008-03-18 | 2009-09-24 | Robert Bosch Gmbh | Method for bounce suppression of a valve connected by a piezoactuator |
DE102010022536A1 (en) * | 2010-06-02 | 2011-12-08 | Continental Automotive Gmbh | Method and device for controlling a valve |
DE102010040306B4 (en) | 2010-09-07 | 2020-06-25 | Continental Automotive Gmbh | Method for controlling a piezo injector of a fuel injection system |
DE102011004613A1 (en) * | 2011-02-23 | 2012-08-23 | Continental Automotive Gmbh | Method for monitoring the state of a piezo injector of a fuel injection system |
DE102011005934A1 (en) | 2011-03-23 | 2012-09-27 | Continental Automotive Gmbh | Method for determining the force relationships on the nozzle needle of a directly driven piezo injector |
DE102011075269B4 (en) * | 2011-05-04 | 2014-03-06 | Continental Automotive Gmbh | Method and device for controlling a valve |
DE102013224385B3 (en) * | 2013-11-28 | 2015-03-12 | Continental Automotive Gmbh | Method for operating an injector of an injection system of an internal combustion engine |
DE102014212010A1 (en) * | 2014-06-23 | 2015-12-24 | Robert Bosch Gmbh | Method for operating a fuel injection system of an internal combustion engine |
JP6463638B2 (en) | 2015-01-20 | 2019-02-06 | 株式会社Soken | Control device for fuel injection valve |
DE102016218515A1 (en) * | 2016-09-27 | 2018-03-29 | Robert Bosch Gmbh | Method for controlling switchable valves, in particular injection valves of an internal combustion engine of a motor vehicle |
JP2019039323A (en) * | 2017-08-23 | 2019-03-14 | 株式会社デンソー | Fuel injection control device |
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US6128754A (en) * | 1997-11-24 | 2000-10-03 | Schlumberger Technologies, Inc. | Tester having event generation circuit for acquiring waveform by supplying strobe events for waveform acquisition rather than using strobe events specified by the test program |
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JP2000023474A (en) | 1998-07-01 | 2000-01-21 | Isuzu Motors Ltd | Piezoelectric actuator and fuel injector using the same |
JP3855473B2 (en) * | 1998-07-08 | 2006-12-13 | いすゞ自動車株式会社 | Common rail fuel injection system |
JP3767199B2 (en) * | 1998-09-16 | 2006-04-19 | 日産自動車株式会社 | Differential pressure type fuel injection valve and control method thereof |
US6128175A (en) * | 1998-12-17 | 2000-10-03 | Siemens Automotive Corporation | Apparatus and method for electronically reducing the impact of an armature in a fuel injector |
DE19921456A1 (en) * | 1999-05-08 | 2000-11-16 | Bosch Gmbh Robert | Method and device for controlling a piezoelectric actuator |
DE19939421A1 (en) * | 1999-08-20 | 2001-03-01 | Bosch Gmbh Robert | Combined stroke / pressure controlled fuel injection method and system for an internal combustion engine |
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DE10155391A1 (en) * | 2001-11-10 | 2003-05-22 | Bosch Gmbh Robert | Method of loading and unloading a piezoelectric element |
EP1488089B1 (en) * | 2002-03-28 | 2005-12-21 | Volkswagen Mechatronic GmbH & Co. KG | Method and device for controlling the piezo-actuator of a piezo-control valve of a pump nozzle unit |
DE10222196A1 (en) * | 2002-05-18 | 2003-11-27 | Bosch Gmbh Robert | Fuel injection valve for combustion engine, has control valve with valve chamber and valve member that is moveable between two end positions for opening or closing connections to certain chambers |
CN1671961A (en) * | 2002-07-29 | 2005-09-21 | 罗伯特·博世有限公司 | Fuel injector with and without pressure amplification with a controllable needle speed and method for the control thereof |
DE10311269A1 (en) | 2003-03-14 | 2004-09-23 | Conti Temic Microelectronic Gmbh | Method for controlling a piezoelectric element or actuator based on a measure of quality of the oscillating behavior to provide a control parameter |
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DE102004049288A1 (en) * | 2004-10-09 | 2006-04-20 | Robert Bosch Gmbh | Fuel injector with molded valve seat to reduce the anchor stroke |
DE102005002242A1 (en) * | 2005-01-18 | 2006-07-20 | Robert Bosch Gmbh | Method for operating a fuel injection device of an internal combustion engine |
US20070069043A1 (en) * | 2005-08-17 | 2007-03-29 | Axial Vector Engine Corporation | Piezoelectric liquid injector |
-
2004
- 2004-12-23 DE DE102004062073.3A patent/DE102004062073B4/en not_active Expired - Fee Related
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- 2005-12-22 EP EP05822186.2A patent/EP1828582B1/en active Active
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US20100063709A1 (en) | 2010-03-11 |
US8239115B2 (en) | 2012-08-07 |
EP1828582A1 (en) | 2007-09-05 |
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