EP1055057B1 - Method for regulating the engine speed in multi-cylinder internal combustion engines - Google Patents
Method for regulating the engine speed in multi-cylinder internal combustion engines Download PDFInfo
- Publication number
- EP1055057B1 EP1055057B1 EP99911589A EP99911589A EP1055057B1 EP 1055057 B1 EP1055057 B1 EP 1055057B1 EP 99911589 A EP99911589 A EP 99911589A EP 99911589 A EP99911589 A EP 99911589A EP 1055057 B1 EP1055057 B1 EP 1055057B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pulses
- speed
- engine speed
- rotational
- sensed
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Images
Classifications
-
- 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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
-
- 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
- F02D41/0097—Electrical control of supply of combustible mixture or its constituents using means for generating speed signals
-
- 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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/1497—With detection of the mechanical response of the engine
- F02D41/1498—With detection of the mechanical response of the engine measuring engine roughness
-
- 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
- F02D41/02—Circuit arrangements for generating control signals
- F02D41/14—Introducing closed-loop corrections
- F02D41/16—Introducing closed-loop corrections for idling
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D2200/00—Input parameters for engine control
- F02D2200/02—Input parameters for engine control the parameters being related to the engine
- F02D2200/10—Parameters related to the engine output, e.g. engine torque or engine speed
- F02D2200/1015—Engines misfires
Definitions
- the invention relates to a method for speed control of multi-cylinder internal combustion engines with crankshaft and Fuel injection, especially slow running Marine diesel engines, in which by at least one transducer the speed and direction of rotation of one of the crankshaft driven pole wheel, which can be scanned by the transducer Generates pulses per revolution, records and deviations of the Speed from a predetermined setpoint by means of a Actuator influencing the engine fuel injection be compensated.
- a disadvantage of this method proves that a control of low speeds of less than about 25 min -1 cannot be carried out satisfactorily.
- the dynamic speed deviations that occur as a result of load surges cannot be compensated better than with conventional speed controllers.
- the load is constant, there are unsteady movements of the filling rod if the injection pumps are not set precisely. In the event of malfunction of individual injection pumps, strong periodic movements of the filler rod can be observed, which result from the "fast" controller constantly trying to correct the resulting drop in the speed of the respective cylinder.
- the invention has for its object a method for Speed control of multi-cylinder internal combustion engines in this regard to continue training, avoiding the previously Disadvantages described in a simple and inexpensive way achieve an accurate and fast detection of the speed lets a stable control to a constant speed with periodic and temporary speed fluctuations allows.
- the task is in a method of the aforementioned Art solved according to the invention in that the time required for a set sequence of successively sampled pulses continuously measured and to form equidistant, uncorrected actual speed values is used, whereby the number of successively sampled pulses in Dependency of the number of cylinders of the engine and the number of impulses generated by the magnet wheel per revolution is that the time required for one complete revolution number of sensed pulses corresponding to the magnet wheel measured and used to form an average speed is that the difference between the average speed and of each uncorrected actual speed value for formation corrected actual speed values smoothed and limited in amount and added to the uncorrected actual speed value and that the corrected actual speed values with a predetermined speed setpoint and compared to a controller are supplied by the output variable, the actuator is controlled.
- the number of consecutive sampled pulses as a rounded quotient Number of pulses that can be generated by the pole wheel per revolution and the number of cylinders in the engine.
- This offers the advantage that a sequence of sampled pulses Allocates cylinders, with the result that the formed Actual speed value of the average speed of the crankshaft over a rotation angle range, according to which two sequentially firing cylinders in the same position, for example top dead center, ingest. That way includes the determined actual speed value none periodically during influences that occur during a work cycle, such as the ignition processes.
- the uncorrected actual speed values at intervals of two successive ones Pulses formed. This means that at a number of more than two pulses of a fixed one Pulse train the formed uncorrected actual speed values assigned overlapping angular ranges of the crankshaft are, so that due to the resulting high Number of actual speed values an exact and fast acquisition the speed can be reached.
- each sequence a measured value memory assigned to sampled pulses, in which the time intervals of the successively sampled Impulses for the formation of an uncorrected actual speed value be summed up.
- This enables in a simple way the simultaneous assignment of each sampled pulse to several pulse sequences, which are due to the overlapping Angular ranges of the crankshaft corresponding to actual speed values result.
- Using a process computer with non-volatile memory this can be done on per se known and easy to implement.
- Expediently after Formation of an uncorrected actual speed value of the content of the measured value memory before deletion and assignment of a new one Obtain a sequence of sampled pulses for at least one revolution. This allows the measured value to be used to calculate the average Use the speed value. Then, too, are on simple way of further evaluations of the speed curve, such as misfire detection or Acceleration processes, possible.
- the pulses are rotated through 90 ° by two offset sensor sampled to the direction of rotation the one that can be reversed, especially in the case of marine diesel engines, Determine crankshaft, and thereby the sign to be determined when counting the pulses. It is also an advantage as a flywheel a gearwheel with a uniform circumference use distributed teeth, so that easy Way a sampling of pulses is ensured.
- both by the front as well as by the rear edge of a rotating gear generates a pulse.
- a particularly advantageous procedure for this results with approximately symmetrical flanks of the teeth, so that there are constant time intervals between the individual measurements let achieve. The measuring accuracy is determined by the arrangement the teeth or recordings are not affected.
- the pulses are expediently sampled equidistantly, so that digital sampling control can be applied and there is a pulse-pause ratio of about 1.
- the pulses using inductive, capacitive or optical position sensors detected.
- non-slip driven, incremental angle encoders or other digital or analog working detector circuits coupled to the crankshaft be used.
- the scanning signals of two sensors A and B can be seen.
- the sensors A and B are one Angle of 90o offset, resulting in a Shift of the rectangular signal sequence of the transducer B compared the sensor A results.
- To evaluate the square wave signals both the rising edge L and the falling edge Edge R used.
- the time required for a fixed Sequence of successively sampled pulses is shown.
- the number of successively sampled pulses corresponds to m and results as the quotient of the number of one pole wheel per revolution and the number of cylinders of an engine. Is the number of teeth not by that If the number of cylinders is divisible, the rounded quotient is used.
- the resulting ripple is caused by a correction scheme according to FIG 2 compensated.
- Using a gear with 60 teeth as a pulse-generating pole wheel consequently takes m in a 6-cylinder two-stroke engine the value of 10. This means 10 consecutive Impulses form a pulse sequence, the time required for the determination of an uncorrected actual speed value is, as shown by the in the lower part of FIG 1 Stretching is made clear.
- the signal flow diagram shown in FIG. 2 contains a link 1, which is the difference of one over a complete revolution a crankshaft averaged speed N and one over an angular range defined by the pulse train Crankshaft averaged, uncorrected actual speed value n smooths over time.
- a link 1 is the difference of one over a complete revolution a crankshaft averaged speed N and one over an angular range defined by the pulse train Crankshaft averaged, uncorrected actual speed value n smooths over time.
- the reciprocal of the value of a complete revolution of the crankshaft averaged speed N apply. That on result formed in this way is by a link 2 in its Amount limited and to form a corrected actual speed value x added to the uncorrected actual speed value n.
- the corrected actual speed value x is then used a predetermined speed setpoint w compared and one Link 3 supplied, which is designed as a PID controller.
- the output variable y of the PID controller 3 is used to control a Actuator
- the mode of operation of the speed detection shown in FIG. 1 and the regulation shown in FIG. 2 is based on the following a 6-cylinder two-stroke diesel engine exemplified.
- the individual cylinders of the diesel engine are used during the compression phase using individual injection pumps Fuel supplied, its amount in relation to the combustion air is determined by the degree of filling. The degree of filling will changed by the control rod of the injection pump, which is controlled by the output variable y of the PID controller.
- to Synchronization of the ignition timing of the individual cylinders is the angle of rotation of the crankshaft is detected by means of position sensors.
- two staggered 90o inductive proximity switches which are used by a pulse generated with the crankshaft rotating gear scan.
- the Determine the speed and direction of rotation of the crankshaft without complex measuring attachments to the diesel engine are required.
- the 60th evenly spaced teeth Gear is connected directly to the crankshaft, see above that the measured speed of the gear with the speed of the Crankshaft matches.
- the two inductive proximity sensors detect both the front and in the direction of rotation also the rear flank of the teeth of the gear, so that overall 240 pulses per complete revolution of the gear to be scanned, which is an accurate and fast detection ensure the speed. Because of the number of 60 teeth of the gear and 6 cylinders of the engine provide 10 pulses a pulse train to form the uncorrected actual speed value n represents.
- the pulse trains are at intervals of successive pulses counted so that with two transducers, 60 teeth and 6 Cylinders 240 actual speed values n and 240 averaged speed values N can be determined per revolution. For every actual speed value n there is a measured value memory in which the time intervals of the associated pulses are summed. The The content of each measured value memory is one revolution long stored so that a measurement value memory is assigned to each pulse is. For the present case there are therefore 240 measured value memory locations needed. Because of the even and equidistant arrangement of the teeth of the gear is the ratio of pulse and pulse pause approximately 1.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Combined Controls Of Internal Combustion Engines (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
Die Erfindung betrifft ein Verfahren zur Drehzahlregelung von mehrzylindrigen Verbrennungsmotoren mit Kurbelwelle und Kraftstoffeinspritzung, insbesondere langsam laufender Schiffsdieselmotoren, bei dem durch wenigstens einen Aufnehmer die Drehzahl und Drehrichtung eines von der Kurbelwelle angetriebenen Polrads, welches für den Aufnehmer abtastbare Impulse je Umdrehung erzeugt, erfaßt und Abweichungen der Drehzahl von einem vorgegebenen Sollwert mittels eines die Kraftstoffeinspritzung des Motors beeinflussenden Stellglieds kompensiert werden.The invention relates to a method for speed control of multi-cylinder internal combustion engines with crankshaft and Fuel injection, especially slow running Marine diesel engines, in which by at least one transducer the speed and direction of rotation of one of the crankshaft driven pole wheel, which can be scanned by the transducer Generates pulses per revolution, records and deviations of the Speed from a predetermined setpoint by means of a Actuator influencing the engine fuel injection be compensated.
Derartige Verfahren finden vor allem bei Dieselmotoren Anwendung, die im Vergleich zu beispielsweise Ottomotoren eine Regelung der Leerlaufdrehzahl und eine Begrenzung der Höchstdrehzahl unweigerlich erfordern. Die hierzu verwendeten Einspritzpumpen spritzen je nach vorhandener Drehzahl mehr oder weniger Kraftstoff in die Zylinder ein, wozu sie über entsprechende Regeleinrichtungen verstellt werden. Bei großen Dieselmotoren, wie beispielsweise Zweitakt-Großmotoren, welche häufig an Bord von Schiffen vorzufinden sind, ist jeder Zylinder mit einer eigenen Einzeleinspritzpumpe versehen, welche wegen der erforderlichen hohen Stellkräfte eine hydraulische Kraftverstärkung erfährt. Die aufgrund ihrer erwiesenen Zuverlässigkeit an Bord von Schiffen eingesetzten Zweitakt-Großmotoren sind in der Regel als Reihenmaschinen mit vier bis zwölf Zylindern ausgeführt und arbeiten in einem Nenndrehzahlbereich von 50 bis 120 min-1. Da Schiffsdieselmotoren umsteuerbar sind, daß heißt in beiden Drehrichtungen laufen können, weisen die Steuerwellen Nocken für Vorwärtsund Rückwärtslauf auf, welche die Einzeleinspritzpumpen betätigen.Such methods are used above all in diesel engines, which in comparison to gasoline engines, for example, inevitably require regulation of the idling speed and limitation of the maximum speed. The injection pumps used for this purpose inject more or less fuel into the cylinders depending on the available speed, for which purpose they are adjusted by means of appropriate control devices. In large diesel engines, such as large two-stroke engines, which are often found on board ships, each cylinder is equipped with its own single injection pump, which is hydraulically amplified due to the high actuating forces required. The large two-stroke engines used on board due to their proven reliability are usually designed as in-line engines with four to twelve cylinders and operate in a nominal speed range of 50 to 120 min -1 . Since marine diesel engines are reversible, that is, they can run in both directions of rotation, the control shafts have cams for forward and reverse running, which actuate the individual injection pumps.
Infolge der niedrigen Nenndrehzahlen ergeben sich Minimaldrehzahlen von 12 bis 25 min-1, die durch einen unruhigen Lauf gekennzeichnet sind. Die Ursache hierfür sind Drehzahlschwankungen, die aus periodischen Störeinflüssen, wie beispielsweise die einzelnen Zündvorgänge, und aus vorübergehenden Unregelmäßigkeiten, wie zum Beispiel Laststöße, Änderungen des Antriebsmomentes, Zündaussetzern oder sonstige Fehlfunktionen der Einspritzpumpen, herrühren. Um einen Stillstand oder ein Überdrehen des Motors zu vermeiden, werden die Drehzahlschwankungen durch Einregeln auf eine konstante Drehzahl kompensiert.As a result of the low nominal speeds, minimum speeds of 12 to 25 min -1 result , which are characterized by an unsteady run. The reason for this is fluctuations in engine speed resulting from periodic interference, such as the individual ignition processes, and from temporary irregularities, such as load surges, changes in drive torque, misfires or other malfunctions of the injection pumps. In order to avoid the motor coming to a standstill or over-revving, the speed fluctuations are compensated for by adjusting to a constant speed.
Im Stand der Technik sind zur Einhaltung vorgegebener Drehzahlsollwerte Verfahren bekannt, die sowohl statischen Abweichungen, daß heißt periodischen Drehzahlabweichungen bei konstanter Last, als auch dynamischen Abweichungen, daß heißt vorübergehende Sollwertabweichungen, wie beispielsweise während des Anlaufs zwischen Leerlauf und Vollast, ausregeln. So ist in der EP 0 481 983 B1 ein Verfahren zur Drehzahlregelung eines langsam laufenden, mehrzylindrigen Dieselmotors beschrieben, bei dem für jeden der Zylinder Winkelstellungen der Kurbelwelle definiert werden, die den Anfangswinkel und Endwinkel eines vor dem oberen Totpunkt des Zylinders liegenden Winkelbereiches darstellen. Für diese Winkelbereiche, welche mittels eines Sensors für entsprechende mit der Kurbelwelle rotierende, impulserzeugende Marken erfaßt werden, wird fortlaufend ein Istwert gemessen, welcher die mittlere Geschwindigkeit angibt, mit der die Kurbelwelle diesen Winkelbereich durchläuft. Dieser Istwert wird einem "schnellen", soll heißen proportional wirkenden, Regler zugeführt, welcher auf den Füllgrad des dem entsprechenden Winkelbereich zugeordneten Zylinders einwirkt. Ferner wird eine über mehrere dieser Winkelbereiche gemittelte Geschwindigkeit der Kurbelwelle gemessen und einem "trägen", soll heißen integral oder proportional-integral wirkenden, Regler zugeführt, welcher zur Voreinstellung der Füllgrade aller Zylinder herangezogen wird. Um auftretende Störungen möglichst frühzeitig durch Korrektur des Füllgrades zu kompensieren, wird zudem die durch die Anfangs- und Endwinkel bestimmte Lage der Winkelbereiche in Abhängigkeit von der Drehzahl der Kurbelwelle verstellt.The state of the art requires compliance with specified speed setpoints Known methods that both static deviations, that means periodic speed deviations at constant Load, as well as dynamic deviations, that is temporary setpoint deviations, such as during of the start-up between idling and full load. So is a method for speed control in EP 0 481 983 B1 a slow-running, multi-cylinder diesel engine, with the angular positions for each of the cylinders the crankshaft are defined, the starting angle and End angle of one before the top dead center of the cylinder Represent angular range. For these angular ranges, which by means of a sensor for corresponding with the crankshaft rotating, pulse-generating marks are detected, an actual value is measured continuously, which is the mean Speed indicates at which the crankshaft this angular range passes. This actual value is a "fast", is supposed to be called proportional acting, which controller to the degree of filling of the corresponding angular range Cylinder acts. Furthermore, one is used over several this angular ranges mean speed of the crankshaft measured and a "sluggish" means integral or proportional-integrally acting, controller supplied, which used to preset the filling levels of all cylinders becomes. To deal with any faults as early as possible Correcting the fill level will also compensate position of the angular ranges determined by the start and end angles adjusted depending on the speed of the crankshaft.
Als Nachteil dieses Verfahrens erweist sich, daß eine Regelung geringer Drehzahlen von unter etwa 25 min-1 nicht befriedigend durchführbar ist. Zudem lassen die sich in Folge von Laststößen auftretenden dynamischen Drehzahlabweichungen nicht besser als mit konventionellen Drehzahlreglern ausgleichen. Darüber hinaus sind bei konstanter Last, unruhige Bewegungen des Füllgestänges zu verzeichnen, wenn die Einspritzpumpen nicht exakt eingestellt sind. Bei Fehlfunktion einzelner Einspritzpumpen sind starke periodische Bewegungen des Füllgestänges zu beobachten, die daraus resultieren, daß der "schnelle" Regler den dadurch bedingten Drehzahleinbruch des jeweiligen Zylinders ständig auszuregeln versucht.A disadvantage of this method proves that a control of low speeds of less than about 25 min -1 cannot be carried out satisfactorily. In addition, the dynamic speed deviations that occur as a result of load surges cannot be compensated better than with conventional speed controllers. In addition, when the load is constant, there are unsteady movements of the filling rod if the injection pumps are not set precisely. In the event of malfunction of individual injection pumps, strong periodic movements of the filler rod can be observed, which result from the "fast" controller constantly trying to correct the resulting drop in the speed of the respective cylinder.
Der Erfindung liegt die Aufgabe zugrunde, ein Verfahren zur Drehzahlregelung von mehrzylindrigen Verbrennungsmotoren dahingehend weiterzubilden, daß sich unter Meidung der zuvor beschriebenen Nachteile auf einfache und kostengünstige Weise eine genaue und schnelle Erfassung der Drehzahl erreichen läßt, welche eine stabile Regelung auf eine konstante Drehzahl bei periodischen und vorübergehenden Drehzahlschwankungen ermöglicht.The invention has for its object a method for Speed control of multi-cylinder internal combustion engines in this regard to continue training, avoiding the previously Disadvantages described in a simple and inexpensive way achieve an accurate and fast detection of the speed lets a stable control to a constant speed with periodic and temporary speed fluctuations allows.
Die Aufgabe ist bei einem Verfahren der eingangs genannten Art erfindungsgemäß dadurch gelöst, daß der Zeitbedarf für eine festgelegte Folge aufeinander folgend abgetasteter Impulse kontinuierlich gemessen und zur Bildung von äquidistanten, unkorrigierten Drehzahl-Istwerten herangezogen wird, wobei die Anzahl der aufeinanderfolgend abgetasteten Impulse in Abhängigkeit der Zylinderzahl des Motors und der Anzahl der von dem Polrad je Umdrehung erzeugbaren Impulse festgelegt wird, daß der Zeitbedarf für die einer vollständigen Umdrehung des Polrads entsprechenden Anzahl an abgetasteten Impulsen gemessen und zur Bildung einer mittleren Drehzahl herangezogen wird, daß die Differenz aus mittlerer Drehzahl und eines jeden unkorrigierten Drehzahl-Istwertes zur Bildung korrigierter Drehzahl-Istwerte geglättet und im Betrag begrenzt sowie zum unkorrigierten Drehzahl-Istwert hinzuaddiert wird, und daß die korrigierten Drehzahl-Istwerte mit einem vorgegebenen Drehzahl-Sollwert verglichen und einem Regler zugeführt werden, durch dessen Ausgangsgröße das Stellglied gesteuert wird.The task is in a method of the aforementioned Art solved according to the invention in that the time required for a set sequence of successively sampled pulses continuously measured and to form equidistant, uncorrected actual speed values is used, whereby the number of successively sampled pulses in Dependency of the number of cylinders of the engine and the number of impulses generated by the magnet wheel per revolution is that the time required for one complete revolution number of sensed pulses corresponding to the magnet wheel measured and used to form an average speed is that the difference between the average speed and of each uncorrected actual speed value for formation corrected actual speed values smoothed and limited in amount and added to the uncorrected actual speed value and that the corrected actual speed values with a predetermined speed setpoint and compared to a controller are supplied by the output variable, the actuator is controlled.
Mit einem solchen Verfahren werden sowohl vorübergehend als auch periodisch auftretende Drehzahlschwankungen schnell und genau identifiziert und mittels entsprechender Steuerung des die Krafteinspritzung beeinflussenden Stellglieds durch den Regler kompensiert.With such a procedure, both temporary and also periodically occurring speed fluctuations quickly and precisely identified and controlled accordingly the force influencing actuator by the Controller compensated.
Von besonderem Vorteil ist es, wenn die Anzahl der aufeinanderfolgend abgetasteten Impulse als gerundeter Quotient die Anzahl der von dem Polrad je Umdrehung erzeugbaren Impulse und der Zylinderzahl des Motors festgelegt wird. Dies bietet den Vorteil, daß sich eine Folge abgetasteter Impulse einem Zylinder zuordnen läßt, mit der Folge, daß der gebildete Drehzahl-Istwert der gemittelten Drehzahl der Kurbelwelle über einen Drehwinkelbereich entspricht, nach welchem zwei nacheinander zündende Zylinder die gleiche Stellung, beispielsweise oberer Totpunkt, einnehmen. Auf diese Weise beinhaltet der ermittelte Drehzahl-Istwert keine periodisch während eines Arbeitsspieles auftretende Einflüsse, wie beispielsweise die Zündvorgänge.It is particularly advantageous if the number of consecutive sampled pulses as a rounded quotient Number of pulses that can be generated by the pole wheel per revolution and the number of cylinders in the engine. This offers the advantage that a sequence of sampled pulses Allocates cylinders, with the result that the formed Actual speed value of the average speed of the crankshaft over a rotation angle range, according to which two sequentially firing cylinders in the same position, for example top dead center, ingest. That way includes the determined actual speed value none periodically during influences that occur during a work cycle, such as the ignition processes.
Gemäß einer vorteilhaften Weiterbildung der Erfindung werden die unkorrigierten Drehzahl-Istwerte im Abstand zweier aufeinanderfolgenden Impulse gebildet. Dies bedeutet, daß bei einer Anzahl von mehr als zwei Impulsen einer festgelegten Impulsfolge die gebildeten unkorrigierten Drehzahl-Istwerte überlappenden Winkelbereichen der Kurbelwelle zugeordnet sind, so daß sich infolge der sich daraus ergebenden hohen Anzahl an Drehzahl-Istwerten eine genaue und schnelle Erfassung der Drehzahl erreichen läßt.According to an advantageous development of the invention the uncorrected actual speed values at intervals of two successive ones Pulses formed. This means that at a number of more than two pulses of a fixed one Pulse train the formed uncorrected actual speed values assigned overlapping angular ranges of the crankshaft are, so that due to the resulting high Number of actual speed values an exact and fast acquisition the speed can be reached.
Gemäß einem weiteren Merkmal der Erfindung wird jeder Folge von abgetasteten Impulsen ein Meßwertspeicher zugeordnet, in welchem die Zeitabstände der aufeinanderfolgend abgetasteten Impulse zur Bildung eines unkorrigierten Drehzahl-Istwertes summiert werden. Dies ermöglicht auf einfache Art und Weise die gleichzeitige Zuordnung eines jeden abgetasteten Impulses zu mehreren Impulsfolgen, die sich aufgrund der den überlappenden Winkelbereichen der Kurbelwelle entsprechenden Drehzahl-Istwerten ergeben. Mittels eines Prozeßrechners mit nichtflüchtigem Speicher läßt sich dies auf an sich bekannte und einfache Weise realisieren. Zweckmäßigerweise wird nach Bildung eines unkorrigierten Drehzahl-Istwertes der Inhalt des Meßwertspeichers vor Löschung und Zuordnung einer neuen Folge abgetasteter Impulse mindestens für eine Umdrehung erhalten. Dadurch läßt sich der Meßwert zur Berechnung des gemitelten Drehzahlwertes heranziehen. Außerdem sind dann auf einfache Weise weitere Auswertungen des Drehzahlverlaufes, wie beispielsweise hinsichtlich Fehlzündungserfassung oder Beschleunigungsvorgängen, möglich.According to another feature of the invention, each sequence a measured value memory assigned to sampled pulses, in which the time intervals of the successively sampled Impulses for the formation of an uncorrected actual speed value be summed up. This enables in a simple way the simultaneous assignment of each sampled pulse to several pulse sequences, which are due to the overlapping Angular ranges of the crankshaft corresponding to actual speed values result. Using a process computer with non-volatile memory this can be done on per se known and easy to implement. Expediently after Formation of an uncorrected actual speed value of the content of the measured value memory before deletion and assignment of a new one Obtain a sequence of sampled pulses for at least one revolution. This allows the measured value to be used to calculate the average Use the speed value. Then, too, are on simple way of further evaluations of the speed curve, such as misfire detection or Acceleration processes, possible.
Vorteilhafterweise werden die Impulse mittels zwei um 90º versetzt angeordneten Aufnehmer abgetastet, um die Drehrichtung der, insbesondere bei Schiffsdieselmotoren umsteuerbaren, Kurbelwelle festzustellen, und dadurch das Vorzeichen bei der Zählung der Impulse festzulegen. Von Vorteil ist ferner, als Polrad ein Zahnrad mit gleichmäßig an seinem Umfang verteilt angeordneten Zähnen einzusetzen, so daß auf einfache Art und Weise ein Abtasten von Impulsen sichergestellt ist. Um eine hohe Anzahl an abtastbaren Impulsen zu erhalten, wird gemäß einem weiteren vorteilhaften Merkmal der Erfindung sowohl durch die in Drehrichtung vordere als auch durch die hintere Flanke eines sich drehenden Zahnrads ein Impuls erzeugt. Eine besonders vorteilhafte Verfahrensführung hierzu ergibt sich bei annähernd symmetrischen Flanken der Zähne, so daß sich gleichbleibende Zeitabstände der einzelnen Messungen erzielen lassen. Die Meßgenauigkeit wird durch die Anordnung der Zähne bzw. Aufnahmen nicht beeinflußt.Advantageously, the pulses are rotated through 90 ° by two offset sensor sampled to the direction of rotation the one that can be reversed, especially in the case of marine diesel engines, Determine crankshaft, and thereby the sign to be determined when counting the pulses. It is also an advantage as a flywheel a gearwheel with a uniform circumference use distributed teeth, so that easy Way a sampling of pulses is ensured. In order to obtain a high number of scannable pulses according to another advantageous feature of the invention both by the front as well as by the rear edge of a rotating gear generates a pulse. A particularly advantageous procedure for this results with approximately symmetrical flanks of the teeth, so that there are constant time intervals between the individual measurements let achieve. The measuring accuracy is determined by the arrangement the teeth or recordings are not affected.
Zweckmäßigerweise werden die Impulse äquidistant abgetastet, so daß eine digitale Abtastregelung angewendet werden kann und sich ein Impuls-Pausen-Verhältnis von etwa 1 ergibt. Zu diesem Zweck wird vorteilhafterweise weiterhin vorgeschlagen, ein Zahnrad mit einem Verhältnis von Zahndicke zu Lückenweite im Teilkreis von annähernd 1 einzusetzen.The pulses are expediently sampled equidistantly, so that digital sampling control can be applied and there is a pulse-pause ratio of about 1. To for this purpose it is furthermore advantageously proposed a gear with a ratio of tooth thickness to gap width to be used in the pitch circle of approximately 1.
Um einen einfachen und kostengünstigen Meßaufbau zu erreichen, werden gemäß einem Merkmal der Erfindung die Impulse mittels induktiven, kapazitiven oder optischen Positionssensoren erfaßt. Alternativ können auch schlupflos angetriebene, inkrementale Winkelgeber oder andere digital oder analog arbeitende, an die Kurbelwelle gekoppelte Detektorschaltungen eingesetzt werden.In order to achieve a simple and inexpensive measurement setup, according to a feature of the invention, the pulses using inductive, capacitive or optical position sensors detected. Alternatively, non-slip driven, incremental angle encoders or other digital or analog working detector circuits coupled to the crankshaft be used.
Um eine stabile Regelung auf konstante Drehzahlen zu erzielen, wird gemäß einer Weiterbildung der Erfindung ein proportional-integral wirkender Regler mit Vorhaltezeit verwendet, der die auftretenden Drehzahlabweichungen ausregelt. Schließlich wird vorgeschlagen, eine adaptive Regelung einzusetzen, um beispielsweise umgebungsbedingte Einflüsse zu berücksichtigen.In order to achieve stable control at constant speeds, is a proportional-integral according to a development of the invention acting controller with derivative time used, which corrects the speed deviations that occur. Finally it is proposed to use adaptive control, to take environmental influences into account, for example.
Weitere Einzelheiten, Merkmale und Vorteile des Gegenstandes der Erfindung ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispieles, welches in den zugehörigen Zeichnungen dargestellt ist, und zwar zeigen:
- FIG 1
- mittels zwei Aufnehmern aufgenommene Impulse und der Zeitbedarf einer festgelegten Impulsfolge und
- FIg 2
- ein Signalflußplan für eine Drehzahlregelung.
- FIG. 1
- impulses recorded by means of two sensors and the time required for a defined pulse sequence and
- FIg 2
- a signal flow plan for a speed control.
Im oberen Teil der FIG 1 sind die Abtastsignale zweier Aufnehmer A und B zu erkennen. Die Aufnehmer A und B sind um einen Winkel von 90º versetzt angeordnet, wodurch sich eine Verschiebung der Rechtecksignalfolge des Aufnehmers B gegenüber dem Aufnehmer A ergibt. Zur Auswertung der Rechtecksignale werden sowohl die steigende Flanke L als auch die fallende Flanke R herangezogen.In the upper part of FIG 1, the scanning signals of two sensors A and B can be seen. The sensors A and B are one Angle of 90º offset, resulting in a Shift of the rectangular signal sequence of the transducer B compared the sensor A results. To evaluate the square wave signals both the rising edge L and the falling edge Edge R used.
Im unteren Teil der FIG 1 ist der Zeitbedarf für eine festgelegte Folge aufeinanderfolgend abgetasteter Impulse dargestellt. Die Anzahl der aufeinanderfolgend abgetasteten Impulse entspricht m und ergibt sich als Quotient der Anzahl von einem Polrad je Umdrehung erzeugbaren Impulse und der Zylinderzahl eines Motors. Ist die Zahl der Zähne nicht durch die Zahl der Zylinder teilbar, wird der gerundete Quotient verwendet. Die hierdurch verursachte Restwelligkeit wird durch eine Korrekturregelung nach FIG 2 ausgeglichen. Bei Verwendung eines Zahnrades mit 60 Zähnen als impulserzeugendes Polrad nimmt demzufolge bei einem 6-Zylinder-Zweitakt-Motor m den Wert von 10 ein. Dies bedeutet, daß 10 aufeinanderfolgende Impulse eine Impulsfolge bilden, deren Zeitbedarf zur Ermittlung eines unkorrigierten Drehzahl-Istwertes herangezogen wird, wie durch die im unteren Teil der FIG 1 dargestellten Strecken verdeutlicht wird.In the lower part of FIG 1, the time required for a fixed Sequence of successively sampled pulses is shown. The number of successively sampled pulses corresponds to m and results as the quotient of the number of one pole wheel per revolution and the number of cylinders of an engine. Is the number of teeth not by that If the number of cylinders is divisible, the rounded quotient is used. The resulting ripple is caused by a correction scheme according to FIG 2 compensated. Using a gear with 60 teeth as a pulse-generating pole wheel consequently takes m in a 6-cylinder two-stroke engine the value of 10. This means 10 consecutive Impulses form a pulse sequence, the time required for the determination of an uncorrected actual speed value is, as shown by the in the lower part of FIG 1 Stretching is made clear.
Der in FIG 2 abgebildete Signalflußplan enthält ein Glied 1,
welches die Differenz aus einer über eine vollständige Umdrehung
einer Kurbelwelle gemittelten Drehzahl N und einer über
einen durch die Impulsfolge festgelegten Winkelbereich der
Kurbelwelle gemittelten, unkorrigierten Drehzahl-Istwert n
zeitkonstant glättet. Als Glättungsfunktion kann hierzu der
reziproke Wert der über eine vollständige Umdrehung der Kurbelwelle
gemittelten Drehzahl N Anwendung finden. Das auf
diese Weise gebildete Ergebnis wird durch ein Glied 2 in seinem
Betrag begrenzt und zur Bildung eines korrigierten Drehzahl-Istwertes
x dem unkorrigierten Drehzahl-Istwert n hinzuaddiert.
Der korrigierte Drehzahl-Istwert x wird sodann mit
einem vorgegebenen Drehzahl-Sollwert w verglichen und einem
Glied 3 zugeführt, welches als PID-Regler ausgebildet ist.
Die Ausgangsgröße y des PID-Reglers 3 dient zur Steuerung eines
Stellgliedes, welches im vorliegenden Fall ein den Füllgrad
eines Motorzylinders beeinflussendes Füllungsgestänge
einer Einspritzpumpe ist.The signal flow diagram shown in FIG. 2 contains a
Die Funktionsweise der in FIG 1 gezeigten Drehzahlerfassung und der in FIG 2 gezeigten Regelung sei im folgenden anhand eines 6-Zylinder-Zweitakt-Dieselmotors beispielhaft erläutert. Die einzelnen Zylinder des Dieselmotors werden während der Verdichtungsphase mittels Einzeleinspritzpumpen mit Kraftstoff versorgt, dessen Menge im Verhältnis zur Verbrennungsluft durch den Füllgrad bestimmt ist. Der Füllgrad wird durch die Regelstange der Einspritzpumpe verändert, welche durch die Ausgangsgröße y des PID-Reglers gesteuert wird. Zur Syncronisation der Zündzeitpunkte der einzelnen Zylinder wird der Drehwinkel der Kurbelwelle mittels Positionssensoren erfaßt. Zu diesem Zweck werden zwei um 90º versetzt angeordnete, induktive Nährungsschalter verwendet, welche die durch ein sich mit der Kurbelwelle drehenden Zahnrad erzeugten Impulse abtasten. Auf diese Weise läßt sich gleichzeitig die Drehzahl und Drehrichtung der Kurbelwelle ermitteln, ohne daß es aufwendiger Meßanbauten an dem Dieselmotor bedarf. Das 60 gleichmäßig und gleich voneinander beabstandete Zähne aufweisende Zahnrad ist direkt mit der Kurbelwelle verbunden, so daß die gemessene Drehzahl des Zahnrades mit der Drehzahl der Kurbelwelle übereinstimmt. Die beiden induktiven Nährungssenoren detektieren sowohl die in Drehrichtung vordere als auch die hintere Flanke der Zähne des Zahnrades, so daß insgesamt 240 Impulse pro vollständiger Umdrehung des Zahnrades abgetastet werden, welche eine genaue und schnelle Erfassung der Drehzahl gewährleisten. Aufgrund der Anzahl von 60 Zähnen des Zahnrades und 6 Zylindern des Motors stellen 10 Impulse eine Impulsfolge zur Bildung des unkorrigierten Drehzahl-Istwertes n dar.The mode of operation of the speed detection shown in FIG. 1 and the regulation shown in FIG. 2 is based on the following a 6-cylinder two-stroke diesel engine exemplified. The individual cylinders of the diesel engine are used during the compression phase using individual injection pumps Fuel supplied, its amount in relation to the combustion air is determined by the degree of filling. The degree of filling will changed by the control rod of the injection pump, which is controlled by the output variable y of the PID controller. to Synchronization of the ignition timing of the individual cylinders is the angle of rotation of the crankshaft is detected by means of position sensors. For this purpose, two staggered 90º inductive proximity switches, which are used by a pulse generated with the crankshaft rotating gear scan. In this way, the Determine the speed and direction of rotation of the crankshaft without complex measuring attachments to the diesel engine are required. The 60th evenly spaced teeth Gear is connected directly to the crankshaft, see above that the measured speed of the gear with the speed of the Crankshaft matches. The two inductive proximity sensors detect both the front and in the direction of rotation also the rear flank of the teeth of the gear, so that overall 240 pulses per complete revolution of the gear to be scanned, which is an accurate and fast detection ensure the speed. Because of the number of 60 teeth of the gear and 6 cylinders of the engine provide 10 pulses a pulse train to form the uncorrected actual speed value n represents.
Die Impulsfolgen werden im Abstand aufeinanderfolgender Impulse
gezählt, so daß bei zwei Aufnehmern, 60 Zähnen und 6
Zylindern 240 Drehzahl-Istwerte n und 240 gemittelte Drehzahlwerte
N pro Umdrehung ermittelt werden. Für jeden Drehzahl-Istwert
n ist ein Meßwertspeicher vorhanden, in welchem
die Zeitabstände der zugehörigen Impulse summiert werden. Der
Inhalt eines jeden Meßwertspeichers wird eine Umdrehung lang
gespeichert, so daß jedem Impuls ein Meßwertspeicher zugeordnet
ist. Für den vorliegenden Fall werden daher 240 Meßwertspeicherplätze
benötigt. Aufgrund der gleichmäßigen und
gleich beabstandeten Anordnung der Zähne des Zahnrades beträgt
das Verhältnis von Impuls und Impulspause annähernd 1.
Das Verhältnis von Impuls und Impulspause sowie auch der Abstand
der beiden Aufnehmer A und B und etwaige Asymmetrien
der ermittelten Rechtecksignalfolgen, die beispielsweise aus
Fertigungsungenauigkeiten des Zahnrades herrühren, beeinflussen
jedoch nicht das Meßergebnis. Dies ist darauf zurückzuführen,
daß Meßungenauigkeiten, periodische Fehler im Drehzahl-Istwert
n oder eine Restwelligkeit, die sich bei einer
nicht durch die Zähnezahl teilbaren Zylinderzahl ergeben würde,
durch die Korrektur mittels der Glieder 1 und 2 eliminiert
werden. Auf diese Weise beeinflussen schlecht eingestellte,
abgenutzte oder gar ausgefallene Einspritzpumpen den
Drehzahl-Istwert n lediglich im Moment der Änderung. Solange
der Fehler nicht größer als durch das Glied 2 vorgegeben ist,
ist er nach Ablauf der dreifachen Glättungszeit von Glied 1
korrigiert.The pulse trains are at intervals of successive pulses
counted so that with two transducers, 60 teeth and 6
Cylinders 240 actual speed values n and 240 averaged speed values
N can be determined per revolution. For every actual speed value
n there is a measured value memory in which
the time intervals of the associated pulses are summed. The
The content of each measured value memory is one revolution long
stored so that a measurement value memory is assigned to each pulse
is. For the present case there are therefore 240 measured value memory locations
needed. Because of the even and
equidistant arrangement of the teeth of the gear is
the ratio of pulse and pulse pause approximately 1.
The ratio of impulse and impulse pause as well as the distance
of the two sensors A and B and any asymmetries
of the ascertained square-wave signal sequences, which for example consist of
Manufacturing inaccuracies of the gear wheel originate, influence
but not the measurement result. This is due to,
that measurement inaccuracies, periodic errors in the actual speed value
n or a ripple that occurs at a
would not result in the number of cylinders divisible by the number of teeth,
eliminated by the correction by means of
Mit dem zuvor beschriebenen Verfahren läßt sich auf einfache Art und Weise eine schnelle und genaue Erfassung der Drehzahl realisieren. Darüber hinaus wird die Drehzahl des Dieselmotors mit einer hohen Genauigkeit konstant gehalten, selbst wenn schnelle Lastwechsel vorliegen, wie diese beispielsweise bei Schiffsdieselmotoren auftreten, wenn der Schiffspropeller bei rauhem Seegang aus dem Wasser auftaucht. Nicht zuletzt ergibt sich ein stabiles Regelverhalten bei konstanter Last, welches ein unruhiges Bewegen der Regelstange der Einspritzpumpen verhindert.With the method described above it is easy to Way a fast and accurate detection of the speed realize. In addition, the speed of the diesel engine kept constant with high accuracy, even when there are rapid load changes, such as these in marine diesel engines occur when the marine propeller emerges from the water during rough seas. Not least this results in a stable control behavior with constant load, which is a restless movement of the control rod of the injection pumps prevented.
Claims (14)
- Method for regulating the engine speed in multicylinder internal combustion engines with a crankshaft and fuel injection, in particular slow-running ships diesel engines, in which the rotational speed and direction of rotation of a pole wheel, which is driven by the crankshaft and generates, on each revolution, pulses which can be sensed by the pickup (A, B), are detected by at least one pickup (A, B) and deviations of the rotational speed from a predefined set point value (w) are compensated for by means of an actuator element which influences the fuel injection of the engine, characterized in that the time required for a defined sequence of successively sensed pulses is continuously measured and used to form equidistant, uncorrected rotational-speed actual values (n), the number of successive sensed pulses being defined as a function of the cylinder number of the engine and the number of pulses which can be generated per revolution by the pole wheel, in that the time required for the number of sensed pulses corresponding to one complete revolution of the pole wheel is measured and used to form an average rotational speed (N), in that the difference between an average rotational speed (N) and each uncorrected rotational-speed actual value (n) is smoothed in order to form corrected rotational-speed actual values (x) and limited in absolute value and added to the uncorrected rotational-speed actual value (n), and in that the corrected rotational-speed actual values (x) are compared with the predefined rotational-speed set point value (w) and fed to a regulator (3) by whose output variable (y) the actuator element is controlled.
- Method according to Claim 1, characterized in that the number of successively sensed pulses is defined as a rounded quotient of the number of pulses which can be generated per revolution by the pole wheel and of the cylinder number of the engine.
- Method according to Claim 1 to 2, characterized in that uncorrected rotational-speed actual values (n) are formed with the spacing of two successive pulses.
- Method according to one of Claims 1 to 3, characterized in that each sequence of sensed pulses is assigned a measured value memory in which the time intervals of the successively sensed pulses are summed in order to form an uncorrected rotational-speed actual value (n).
- Method according to Claim 4, characterized in that, after the formation of an uncorrected rotational-speed actual value (n), the content of the measured value memory is retained for at least one revolution before the deletion and assignment of a new sequence of sensed pulses.
- Method according to one of Claims 1 to 5, characterized in that the pulses are sensed by means of two pickups (A, B) which are offset by 90°.
- Method according to one of Claims 1 to 6, characterized in that a gear wheel with teeth arranged distributed uniformly over its circumference is used as pole wheel.
- Method according to Claim 7, characterized in that a pulse is generated by both the front and rear edges, in the direction of rotation, of the teeth of the rotating gear wheel.
- Method according to Claim 7 or 8, characterized by approximately symmetrical edges of the teeth.
- Method according to one of Claims 1 to 9, characterized in that the pulses are sensed equidistantly.
- Method according to one of Claims 7 to 10, characterized by the use of a gear wheel with a ratio of tooth thickness to gap width in the pitch circle of approximately 1.
- Method according to one of Claims 1 to 11, characterized in that the pulses are sensed by means of inductive, capacitive or optical position sensors.
- Method according to one of Claims 1 to 10, characterized by a regulator with a proportional-integral action and a derivative action time.
- Method according to one of the preceding claims, characterized in that an adaptive regulating method is used.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE19805113 | 1998-02-09 | ||
| DE19805113 | 1998-02-09 | ||
| PCT/DE1999/000335 WO1999040308A1 (en) | 1998-02-09 | 1999-02-08 | Method for regulating the engine speed in multi-cylinder internal combustion engines |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| EP1055057A1 EP1055057A1 (en) | 2000-11-29 |
| EP1055057B1 true EP1055057B1 (en) | 2002-05-08 |
Family
ID=7857088
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP99911589A Expired - Lifetime EP1055057B1 (en) | 1998-02-09 | 1999-02-08 | Method for regulating the engine speed in multi-cylinder internal combustion engines |
Country Status (11)
| Country | Link |
|---|---|
| US (1) | US6363912B1 (en) |
| EP (1) | EP1055057B1 (en) |
| JP (1) | JP2002502934A (en) |
| KR (1) | KR100404241B1 (en) |
| CN (1) | CN1102201C (en) |
| CA (1) | CA2320179A1 (en) |
| DE (1) | DE59901397D1 (en) |
| DK (1) | DK1055057T3 (en) |
| ES (1) | ES2177262T3 (en) |
| NO (1) | NO323169B1 (en) |
| WO (1) | WO1999040308A1 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6640777B2 (en) * | 2000-10-12 | 2003-11-04 | Kabushiki Kaisha Moric | Method and device for controlling fuel injection in internal combustion engine |
| JP4270534B2 (en) | 2000-10-12 | 2009-06-03 | ヤマハモーターエレクトロニクス株式会社 | Internal combustion engine load detection method, control method, ignition timing control method, and ignition timing control device |
| DE10327563A1 (en) * | 2003-06-18 | 2005-01-05 | Robert Bosch Gmbh | Method for operating an internal combustion engine |
| US7138623B2 (en) * | 2004-12-13 | 2006-11-21 | Magna Powertrain Usa, Inc. | Power transfer device with contactless optical encoder and color reflective surface |
| JP4339347B2 (en) * | 2006-10-30 | 2009-10-07 | 本田技研工業株式会社 | Crank angular velocity detection device for internal combustion engine |
| GB2478989A (en) * | 2010-03-26 | 2011-09-28 | Gm Global Tech Operations Inc | Determining speed of a multi-tooth wheel |
Family Cites Families (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE2625971C2 (en) * | 1976-06-10 | 1984-08-23 | Robert Bosch Gmbh, 7000 Stuttgart | Method and device for the detection of malfunctions in individual cylinders of internal combustion engines |
| JPS5979856A (en) * | 1982-10-30 | 1984-05-09 | Diesel Kiki Co Ltd | Apparatus for detecting change amount in rotating speed of internal combustion engine |
| US4575800A (en) * | 1983-04-08 | 1986-03-11 | Optimizer Control Corporation | System for optimizing the timing of diesel or spark ignition engines |
| US5222022A (en) * | 1986-12-01 | 1993-06-22 | Woodward Governor Company | Method and apparatus for iterated determinations of sensed speed and speed governing |
| JPH0315645A (en) * | 1989-06-13 | 1991-01-24 | Hitachi Ltd | Engine control device |
| JPH04506389A (en) * | 1989-07-07 | 1992-11-05 | シーメンス アクチエンゲゼルシヤフト | Method and device for adjusting the rotation speed of a multi-cylinder diesel engine rotating at low speed |
| US5268842A (en) * | 1990-12-03 | 1993-12-07 | Cummins Engine Company, Inc. | Electronic control of engine fuel injection based on engine duty cycle |
| JP2916271B2 (en) * | 1990-12-10 | 1999-07-05 | ヤマハ発動機株式会社 | Engine fuel injection control method |
| US5377537A (en) * | 1993-09-01 | 1995-01-03 | Ford Motor Company | System and method to compensate for torsional disturbances in measured crankshaft velocities for engine misfire detection |
| FR2723400B1 (en) * | 1994-08-03 | 1996-10-11 | Magneti Marelli France | METHOD FOR CORRECTING A SIZE RELATED TO THE ROTATION OF AN INTERNAL COMBUSTION ENGINE AS A FUNCTION OF THE DISSYMETRIES OF A TARGET LINKED TO THE ROTATION |
| JP3478318B2 (en) * | 1996-08-27 | 2003-12-15 | 三菱自動車工業株式会社 | Control device for in-cylinder injection spark ignition internal combustion engine |
-
1999
- 1999-02-08 DK DK99911589T patent/DK1055057T3/en active
- 1999-02-08 DE DE59901397T patent/DE59901397D1/en not_active Expired - Lifetime
- 1999-02-08 CA CA002320179A patent/CA2320179A1/en not_active Abandoned
- 1999-02-08 JP JP2000530699A patent/JP2002502934A/en not_active Abandoned
- 1999-02-08 EP EP99911589A patent/EP1055057B1/en not_active Expired - Lifetime
- 1999-02-08 KR KR10-2000-7008689A patent/KR100404241B1/en not_active IP Right Cessation
- 1999-02-08 WO PCT/DE1999/000335 patent/WO1999040308A1/en active IP Right Grant
- 1999-02-08 CN CN99801292A patent/CN1102201C/en not_active Expired - Fee Related
- 1999-02-08 ES ES99911589T patent/ES2177262T3/en not_active Expired - Lifetime
- 1999-02-08 US US09/601,853 patent/US6363912B1/en not_active Expired - Fee Related
-
2000
- 2000-08-09 NO NO20004017A patent/NO323169B1/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| CA2320179A1 (en) | 1999-08-12 |
| EP1055057A1 (en) | 2000-11-29 |
| NO323169B1 (en) | 2007-01-08 |
| NO20004017L (en) | 2000-08-09 |
| KR20010040795A (en) | 2001-05-15 |
| NO20004017D0 (en) | 2000-08-09 |
| ES2177262T3 (en) | 2002-12-01 |
| US6363912B1 (en) | 2002-04-02 |
| CN1274408A (en) | 2000-11-22 |
| KR100404241B1 (en) | 2003-11-01 |
| CN1102201C (en) | 2003-02-26 |
| DK1055057T3 (en) | 2002-09-02 |
| DE59901397D1 (en) | 2002-06-13 |
| WO1999040308A1 (en) | 1999-08-12 |
| JP2002502934A (en) | 2002-01-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| EP0563347B1 (en) | Process for adapting mechanical tolerances of a pick-up wheel | |
| DE4122139C2 (en) | Method for cylinder equalization with regard to the fuel injection quantities in an internal combustion engine | |
| DE2507138C2 (en) | Method and device for obtaining a measured variable which indicates the approximation of a predetermined lean running limit during the operation of an internal combustion engine | |
| EP0929794B1 (en) | Method and device for correcting margins of error of an indicating wheel | |
| DE102004054711A1 (en) | Internal combustion engine e.g. diesel engine, controlling method for motor vehicle, involves determining top dead center of crankshaft from structural noise signal according to phase relation obtained between noise signal and dead center | |
| DE3704837A1 (en) | CYLINDER PRESSURE SENSOR OUTPUT COMPENSATION METHOD FOR INTERNAL COMBUSTION ENGINES | |
| EP2148070A2 (en) | Method for determining the injected fuel mass of a single injection and device for carrying out the method | |
| DE19814732B4 (en) | Speed detection method, in particular for misfire detection | |
| DE19622042C2 (en) | Method for recognizing and correcting errors in the time measurement on rotating shafts | |
| DE102005014920A1 (en) | Method to adjust injection times of individual cylinders of an internal combustion engine depending on their dimensions derived from the crank shaft rotations to compensate for fluctuations in injection quantities | |
| DE4215581B4 (en) | System for controlling a solenoid-controlled fuel metering device | |
| DE4021886A1 (en) | FUEL INJECTION SYSTEM FOR AN INTERNAL COMBUSTION ENGINE | |
| EP1055057B1 (en) | Method for regulating the engine speed in multi-cylinder internal combustion engines | |
| DE19941171B4 (en) | Method for determining the torque applied by an internal combustion engine | |
| EP0661433B1 (en) | Method for calibrating a control system of an internal combustion engine | |
| DE3421640C2 (en) | ||
| AT516669B1 (en) | Method for controlling an internal combustion engine | |
| DE2434743C2 (en) | Method and device for regulating the operating behavior of an internal combustion engine | |
| DE4240917C2 (en) | Control device and control method for internal combustion engines | |
| EP0406765B1 (en) | Method and apparatus for regulating the rotational speed of a slow-running multi-cylinder diesel engine | |
| DE102009046759B4 (en) | Uneven running-based compensation of air ratio differences between different combustion chambers of an internal combustion engine | |
| DE3339231A1 (en) | Device for determining the change in value of the speed of an internal combustion engine | |
| DE19802109C2 (en) | Process for adapting mechanical tolerances when measuring time on rotating shafts | |
| WO2003023412A1 (en) | Method for detecting rotational speed | |
| DE19804327B4 (en) | Method for accurate speed detection |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
| 17P | Request for examination filed |
Effective date: 20000417 |
|
| AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): BE CH DE DK ES FI FR GB GR IT LI NL SE |
|
| GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
| GRAG | Despatch of communication of intention to grant |
Free format text: ORIGINAL CODE: EPIDOS AGRA |
|
| GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
| 17Q | First examination report despatched |
Effective date: 20010817 |
|
| REG | Reference to a national code |
Ref country code: GB Ref legal event code: IF02 |
|
| GRAH | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOS IGRA |
|
| GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
| AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): BE CH DE DK ES FI FR GB GR IT LI NL SE |
|
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: NV Representative=s name: SIEMENS SCHWEIZ AG Ref country code: CH Ref legal event code: EP |
|
| REF | Corresponds to: |
Ref document number: 59901397 Country of ref document: DE Date of ref document: 20020613 |
|
| GBT | Gb: translation of ep patent filed (gb section 77(6)(a)/1977) |
Effective date: 20020731 |
|
| REG | Reference to a national code |
Ref country code: DK Ref legal event code: T3 |
|
| REG | Reference to a national code |
Ref country code: GR Ref legal event code: EP Ref document number: 20020402408 Country of ref document: GR |
|
| ET | Fr: translation filed | ||
| REG | Reference to a national code |
Ref country code: ES Ref legal event code: FG2A Ref document number: 2177262 Country of ref document: ES Kind code of ref document: T3 |
|
| PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
| STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
| 26N | No opposition filed |
Effective date: 20030211 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20060228 Year of fee payment: 8 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: CH Payment date: 20060505 Year of fee payment: 8 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FI Payment date: 20070111 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: SE Payment date: 20070208 Year of fee payment: 9 Ref country code: GB Payment date: 20070208 Year of fee payment: 9 Ref country code: DK Payment date: 20070208 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: NL Payment date: 20070212 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20070219 Year of fee payment: 9 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070228 Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070228 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: ES Payment date: 20070315 Year of fee payment: 9 |
|
| REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: GR Payment date: 20070117 Year of fee payment: 9 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20070216 Year of fee payment: 9 |
|
| BERE | Be: lapsed |
Owner name: SIEMENS A.G. Effective date: 20080228 |
|
| REG | Reference to a national code |
Ref country code: DK Ref legal event code: EBP |
|
| EUG | Se: european patent has lapsed | ||
| GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20080208 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080208 |
|
| NLV4 | Nl: lapsed or anulled due to non-payment of the annual fee |
Effective date: 20080901 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080901 |
|
| REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20081031 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080209 Ref country code: DK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080229 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080228 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080229 |
|
| REG | Reference to a national code |
Ref country code: ES Ref legal event code: FD2A Effective date: 20080209 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080903 Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080208 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080209 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20070208 |
|
| PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20130419 Year of fee payment: 15 |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59901397 Country of ref document: DE |
|
| REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 59901397 Country of ref document: DE Effective date: 20140902 |
|
| PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140902 |