EP1527267B1 - Method for improving the true running of an internal combustion engine - Google Patents
Method for improving the true running of an internal combustion engine Download PDFInfo
- Publication number
- EP1527267B1 EP1527267B1 EP03787596A EP03787596A EP1527267B1 EP 1527267 B1 EP1527267 B1 EP 1527267B1 EP 03787596 A EP03787596 A EP 03787596A EP 03787596 A EP03787596 A EP 03787596A EP 1527267 B1 EP1527267 B1 EP 1527267B1
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- European Patent Office
- Prior art keywords
- zgst
- cylinder
- internal combustion
- factor
- injection
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- 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.)
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- 238000002485 combustion reaction Methods 0.000 title claims abstract description 39
- 238000000034 method Methods 0.000 title claims abstract description 24
- 238000002347 injection Methods 0.000 claims abstract description 61
- 239000007924 injection Substances 0.000 claims abstract description 61
- 239000000446 fuel Substances 0.000 claims description 10
- 230000015572 biosynthetic process Effects 0.000 claims description 6
- 238000004590 computer program Methods 0.000 claims description 3
- 239000000203 mixture Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000007789 sealing Methods 0.000 description 3
- 230000002411 adverse Effects 0.000 description 2
- 238000005259 measurement Methods 0.000 description 2
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000001514 detection method Methods 0.000 description 1
- 230000006866 deterioration Effects 0.000 description 1
- 238000006073 displacement reaction Methods 0.000 description 1
- 239000000047 product Substances 0.000 description 1
- 230000008672 reprogramming Effects 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 239000013589 supplement Substances 0.000 description 1
Images
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
- F02D41/008—Controlling each cylinder individually
- F02D41/0085—Balancing of cylinder outputs, e.g. speed, torque or air-fuel ratio
-
- 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
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M51/00—Fuel-injection apparatus characterised by being operated electrically
- F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
- F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/167—Means for compensating clearance or thermal expansion
-
- 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
-
- 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
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
- F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
- F02M61/161—Means for adjusting injection-valve lift
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/0014—Valves characterised by the valve actuating means
- F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
- F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
Definitions
- the invention relates to a method for compensating torque differences of the cylinders of an internal combustion engine, wherein the fuel injection system of the internal combustion engine for each cylinder has a variable displacement injector.
- From the DE 33 36 028 A1 is a device for influencing control variables of an internal combustion engine known, with the help of which the votes of the individual cylinders services are individually controlled and approximated to each other. This results in the desired round run of the internal combustion engine.
- the power control of the individual cylinders of the internal combustion engine takes place by the variation of the injection duration.
- the changes of the valve lift of the injectors are limited to a range within which the valve lift can be controlled with sufficient precision.
- a good concentricity of the internal combustion engine can also be achieved if the tolerances of the internal combustion engine or the injection valves are relatively large.
- the concentricity is improved by changing the stroke of the injectors.
- the small remaining correction range which is outside the maximum value and the minimum value of the cylinder equalization factor, is covered by a change in the injection duration. This change in the duration of injection is relatively low and does not adversely affect the mixture formation and the operating behavior of the internal combustion engine.
- the method according to the invention can be implemented without additional costs, apart from the costs for programming the control unit.
- the conversion of the correction factor into a drive voltage, or a charge can also be done indirectly by z.
- a desired flow rate or a desired needle stroke or a desired Aktorhub is corrected and this target value is then converted into a drive voltage, or a charge.
- the correction of the drive voltage is particularly simple if the drive voltage is corrected by multiplying by the cylinder equalization factor. Even with these embodiments of the method according to the invention, no changes to the injection system are required, with the exception of a reprogramming of the control unit.
- the desired improvement in the smoothness of the internal combustion engine can also be achieved by a computer program or a control device for an internal combustion engine, which operate according to one of the previously described methods.
- Fig. 1 shows a block diagram, based on which a first embodiment of the method according to the invention will be described below.
- an electrically actuated injection valve (not shown) with a drive voltage U drive, i , or a charge Q i is controlled.
- partial torques M i emitted by the cylinders of the internal combustion engine which add up to the total output of the internal combustion engine, are detected.
- the detection of the partial moments M i does not necessarily include a direct measurement, but it may, for example Also, the observation and measurement of the rotational speed of the crankshaft and a correlation of this rotational speed with the ignition timing of the cylinder of the internal combustion engine done.
- cylinder equalization factor is then formed for each cylinder, so that the smooth running of the engine is improved in consideration of the cylinder equalization factor.
- cylinder equalization factor is designated by F ZGST, i . Also, this cylinder equalization factor F ZGST, i will usually be different for each cylinder Z i .
- the drive voltage U is driving, i , or the charge Q i with the Cylinder equalization factor F ZGST, i multiplied.
- the product of drive voltage U drive, i and cylinder equalization factor F ZGST, i is the corrected drive voltage or the corrected charge.
- a further embodiment of the method according to the invention is shown as a block diagram.
- the essential difference from the embodiment according to Fig. 1 is that the cylinder equalization factor F ZGST, i is limited by a maximum value F ZGST, Max and a minimum value F ZGST, Min in a limiter 1.
- the limiter 1 has the in the Fig. 2 illustrated Characteristic, that is, when the cylinder equalization factor is smaller than the minimum value F ZGST, Min , the cylinder equalization factor F ZGST , i is set equal to the minimum value F ZGST, Min , and if the cylinder equalization factor F ZGST, i is greater than the maximum value F ZGST, Max , the Cylinder equalization factor F ZGST, i equal to the maximum value F ZGST, Max replaced. Otherwise, the cylinder equalization factor F ZGST i remains unchanged.
- the limiter 1 optionally modified cylinder equalization factor F ZGST i , in the same way as based on the Fig. 1 explains, the drive voltage U drive, i , or the charge Q i of the injection valve (not shown) in a corrected drive voltage, or a corrected charge (not shown) converted.
- Fig. 3 A description will be given of the method used when the cylinder equalization factor F ZGST , i is greater than the maximum value F ZGST, Max or less than the minimum value F ZGST, Min .
- the basic idea with this supplement to the method is that the difference of the power of the cylinders Z i, which can not be compensated by the stroke of the injection valve, occurs as a result of a change in the cylinder- specific injection duration F T_injection i .
- a correction factor F T injection i is set equal to 1.0 for the duration of the injection. If the test is positive, the correction factor F T_injection, i , is formed by forming a quotient of the cylinder equalization factor F ZGST, i and the maximum value F ZGST, Max .
- the correction factor F T_ein mousse, i is greater than 1.0 in the case described last.
- the correction factor F T injection i is set equal to 1.0. If this test is positive, the correction factor F T_injection, i is formed from the quotient of cylinder equalization factor F ZGST, i and the minimum value F ZGST , Min . In the case described last, the correction value F T_insprit, i now has a value less than 1.0.
- Fig. 4 is shown how the injection time in response to the correction factor F T_ein mousse, i is corrected.
- an injection valve 3 is shown schematically, which is suitable for carrying out the method according to the invention.
- the injection valve 3 consists of a nozzle body 5 in which a nozzle needle 7 is guided.
- end 9 of the injection valve 3 is a sealing seat (not shown) formed in the nozzle body 5, which cooperates with the nozzle needle 7, that when the nozzle needle 7 is opened, ie in the illustrated position of the injection valve 3 is moved to the left, the nozzle needle 7 lifts off from the sealing seat, not shown.
- a coil spring 11 which is supported at one end on the nozzle body 5 and the other end to the nozzle needle 7, the nozzle needle 7 (not shown) in its sealing seat is moved when the injection valve 3 is de-energized.
- a second coil spring 19 presses the piston 15 against the piezoelectric actuator 13, so that these two components are always connected to each other without play.
- the injection valve 3 is supplied with fuel.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Die Erfindung betrifft ein Verfahren zur Kompensation von Momentenunterschieden der Zylinder einer Brennkraftmaschine, wobei das Kraftstoffeinspritzsystem der Brennkraftmaschine für jeden Zylinder ein Einspritzventil mit variablem Hub aufweist.The invention relates to a method for compensating torque differences of the cylinders of an internal combustion engine, wherein the fuel injection system of the internal combustion engine for each cylinder has a variable displacement injector.
Aufgrund der unvermeidbaren Herstellungstoleranzen von Komponenten der Kraftstoffeinspritzanlage und der Brennkraftmaschine geben die einzelnen Zylinder der Brennkraftmaschine trotz gleicher Ansteuerung der Einspritzventile eine unterschiedliche Leistung, bzw. ein unterschiedliches Moment ab. Dies äußert sich in einem unrunden Lauf der Brennkraftmaschine, insbesondere im Teillastbereich und im Leerlauf.Due to the unavoidable manufacturing tolerances of components of the fuel injection system and the internal combustion engine give the individual cylinders of the internal combustion engine, despite the same control of the injectors a different performance, or a different moment from. This manifests itself in a non-circular running of the internal combustion engine, in particular in the partial load range and at idle.
Aus der
Aus der
Bei modernen Motorenkonzepten, insbesondere bei Brennkraftmaschinen mit strahlgeführter Benzin-Direkteinspritzung, ist eine Variation der Einspritzdauer nicht ohne weiteres möglich, da die Einspritzdauer Einfluss auf die Gemischbildung hat. Infolgedessen kann durch eine Änderung der Einspritzdauer die Gemischbildung negativ beeinflusst werden und die Zündung des im Brennraum gebildeten Gemischs nicht zum richtigen Zeitpunkt erfolgen.In modern engine concepts, especially in internal combustion engines with spray-guided gasoline direct injection, a variation of the injection duration is not readily possible because the injection duration has an influence on the mixture formation. As a result, the mixture formation can be adversely affected by a change in the injection duration and the ignition of the mixture formed in the combustion chamber can not take place at the correct time.
Das erfindungsgemäße Verfahren zur Kompensation von Momentenunterschieden der Zylinder einer Brennkraftmaschine nach Anspruch 1, erlaubt zunächst eine Verbesserung des Rundlaufs der Brennkraftmaschine, ohne die Einspritzdauer zu verändern. Da die Einspritzdauer unverändert bleibt, ändert sich auch die Gemischbildung in den Brennräumen der Brennkraftmaschine nicht, so dass keine Verschlechterung bei der Gemischbildung und der Zündung des Gemisches eintritt.The inventive method for compensation of torque differences of the cylinder of an internal combustion engine according to claim 1, initially allows an improvement of the concentricity of the internal combustion engine, without changing the injection duration. Since the injection duration remains unchanged, the mixture formation in the combustion chambers of the internal combustion engine does not change, so that no deterioration in the mixture formation and the ignition of the mixture occurs.
Durch die Beschränkung des Zylindergleichstellungsfaktors auf einen Maximalwert und einen Minimalwert, werden die Änderungen des Ventilhubs der Einspritzventile auf einen Bereich, innerhalb dessen der Ventilhub mit ausreichender Präzision steuerbar ist, begrenzt.By restricting the cylinder equalization factor to a maximum value and a minimum value, the changes of the valve lift of the injectors are limited to a range within which the valve lift can be controlled with sufficient precision.
Mit Hilfe des erfindungsgemäßen Verfahrens kann ein guter Rundlauf der Brennkraftmaschine auch dann erreicht werden kann, wenn die Toleranzen der Brennkraftmaschine oder der Einspritzventile relativ groß sind. Dabei wird zunächst der Rundlauf durch eine Änderung des Hubs der Einspritzventile verbessert. Wenn diese Möglichkeit ausgeschöpft wurde, wird der kleine verbleibende Korrekturbereich, der außerhalb des Maximalwerts und des Minimalwerts des Zylindergleichstellungsfaktors liegt, durch eine Änderung der Einspritzdauer abgedeckt. Diese Änderung der Einspritzdauer ist relativ gering und wirkt sich nicht nachteilig auf die Gemischbildung und das Betriebsverhalten der Brennkraftmaschine aus.With the help of the method according to the invention, a good concentricity of the internal combustion engine can also be achieved if the tolerances of the internal combustion engine or the injection valves are relatively large. First, the concentricity is improved by changing the stroke of the injectors. When this possibility has been exhausted, the small remaining correction range, which is outside the maximum value and the minimum value of the cylinder equalization factor, is covered by a change in the injection duration. This change in the duration of injection is relatively low and does not adversely affect the mixture formation and the operating behavior of the internal combustion engine.
Da in der Serienfertigung bereits heute Einspritzventile mit variablem Hub eingesetzt werden, kann das erfindungsgemäße Verfahren ohne zusätzliche Kosten, wenn man von den Kosten für die Programmierung des Steuergeräts absieht, inplementiert werden.Since injection valves with a variable stroke are already used today in mass production, the method according to the invention can be implemented without additional costs, apart from the costs for programming the control unit.
Es hat sich als besonders vorteilhaft erwiesen, wenn als Einspritzventile elektrisch gesteuerte Einspritzventile, insbesondere Piezoventile mit nach außen öffnenden Einspritzdüsen, eingesetzt werden, da bei diesen die Einspritzmenge je Zeiteinheit durch eine Korrektur des Hubs des Einspritzventils in Abhängigkeit eines Zylindergleichstellungsfaktors erfolgen kann. Die Korrektur des Hubs kann durch eine Korrektur der Ansteuerspannung oder der Ladung mit der der Piezo-Aktor beaufschlagt wird erfolgen. Nachfolgend wird im Zusammenhang mit der Erfindung immer nur von einer Korrektur der Ansteuerspannung gesprochen. Damit ist immer auch eine Korrektur der Ladung gemeint.It has proved to be particularly advantageous if electrically controlled injection valves, in particular piezo valves with outwardly opening injection nozzles, are used as injection valves, since in these the injection quantity per unit time can be effected by a correction of the stroke of the injection valve as a function of a cylinder equalization factor. The correction of the stroke can be done by a correction of the drive voltage or the charge with which the piezo actuator is acted upon. In the following, only a correction of the drive voltage will be discussed in connection with the invention. This always means a correction of the load.
Die Umrechnung des Korrekturfaktors in eine Ansteuerspannung, bzw. eine Ladung kann auch indirekt erfolgen, indem z. B. ein Soll-Durchflußwert oder ein Soll-Nadelhub oder ein Soll-Aktorhub korrigiert wird und dieser Soll-Wert dann in ein Ansteuerspannung, bzw. eine Ladung umgerechnet wird.The conversion of the correction factor into a drive voltage, or a charge can also be done indirectly by z. B. a desired flow rate or a desired needle stroke or a desired Aktorhub is corrected and this target value is then converted into a drive voltage, or a charge.
Besonders einfach ist die Korrektur der Ansteuerspannung, wenn die Ansteuerspannung durch Multiplikation mit dem Zylindergleichstellungsfaktor korrigiert wird. Auch bei diesen Ausgestaltungen des erfindungsgemäßen Verfahrens werden keine Änderungen an der Einspritzanlage erforderlich, mit Ausnahme einer Umprogrammierung des Steuergeräts.The correction of the drive voltage is particularly simple if the drive voltage is corrected by multiplying by the cylinder equalization factor. Even with these embodiments of the method according to the invention, no changes to the injection system are required, with the exception of a reprogramming of the control unit.
Es hat sich als vorteilhaft erwiesen, wenn die erforderliche Einspritzmenge des Zylinders mit dem Korrekturfaktor multipliziert wird und anschließend in eine zylinderindividuelle Einspritzzeit umgerechnet wird.It has proved to be advantageous if the required injection quantity of the cylinder is multiplied by the correction factor and then converted into a cylinder-specific injection time.
Die angestrebte Verbesserung der Laufruhe der Brennkraftmaschine kann auch durch ein Computerprogramm oder ein Steuergerät für eine Brennkraftmaschine, welche nach einem der vorher beschriebenen Verfahren arbeiten, erreicht werden.The desired improvement in the smoothness of the internal combustion engine can also be achieved by a computer program or a control device for an internal combustion engine, which operate according to one of the previously described methods.
Weitere Vorteile und vorteilhafte Ausgestaltungen der Erfindung sind der nachfolgenden Zeichnung, deren Beschreibung und den Patentansprüchen entnehmbar.Further advantages and advantageous embodiments of the invention are the following drawings, the description and the claims removable.
In der Zeichnung zeigen:
- Fig. 1:
- ein Blockschaltbild eines ersten Ausführungsbeispiels;
- Fig. 2:
- ein Blockschaltbild eines zweiten Ausführungsbeispiels;
- Fig. 3:
- ein Blockschaltbild der Aufteilung des Zylindergleichstellungsfaktors in eine Änderung der Ladung, bzw. Spannung und eine Änderung der Einspritzdauer;
- Fig. 4:
- ein Blockschaltbild der Änderung der Einspritzdauer des erfindungsgemäßen Verfahrens; und
- Fig. 5:
- ein Beispiel eines mit einer mittels Piezoaktor betätigten Hochdruckeinspritzventils mit variablem Hub.
- Fig. 1:
- a block diagram of a first embodiment;
- Fig. 2:
- a block diagram of a second embodiment;
- 3:
- a block diagram of the division of the cylinder equalization factor in a change in the charge or voltage and a change in the Injection duration;
- 4:
- a block diagram of the change in the injection duration of the method according to the invention; and
- Fig. 5:
- an example of a variable-stroke high pressure injector actuated by a piezoactuator.
Abhängig von den Lastanforderungen an die nicht dargestellte Brennkraftmaschine wird ein elektrisch betätigtes Einspritzventil (nicht dargestellt) mit einer Ansteuerspannung UAnsteuer, i, bzw. einer Ladung Qi angesteuert. Der Index 'i' steht dabei für die Nummer eines Zylinders. Es gilt i = 1 bis n, wenn 'n' die Zahl der Zylinder der Brennkraftmaschine ist Damit soll zum Ausdruck gebracht werden, dass die Ansteuerspannung UAnsteuer, bzw. die Ladung Qi in Abhängigkeit von weiteren Parametern, auf die im Zusammenhang mit der Erfindung nicht weiter angegangen werden soll, für jeden Zylinder Zi individuell festgelegt werden kann.Depending on the load requirements of the internal combustion engine, not shown, an electrically actuated injection valve (not shown) with a drive voltage U drive, i , or a charge Q i is controlled. The index 'i' stands for the number of a cylinder. It is i = 1 to n, if 'n' is the number of cylinders of the internal combustion engine This is to be expressed that the drive voltage U drive , or the charge Q i as a function of other parameters, in connection with the Invention should not be addressed, for each cylinder Z i can be set individually.
Während des Betriebs der Brennkraftmaschine werden von den Zylindern der Brennkraftmaschine abgegebenen Teilmomente Mi, die sich zu der Gesamtleistungsabgabe der Brennkraftmaschine addieren, erfasst. Dabei muss die Erfassung der Teilmomente Mi nicht notwendigerweise eine direkte Messung beinhalten, sondern es kann beispielsweise auch die Beobachtung und Messung der Drehgeschwindigkeit der Kurbelwelle und einer Korrelation dieser Drehgeschwindigkeit mit den Zündzeitpunkten der Zylinder der Brennkraftmaschine erfolgen. Wenn sich die Teilmomente Mi der Zylinder Zi innerhalb eines Arbeitshubs der Brennkraftmaschine voneinander unterscheiden, wird anschließend Zylindergleichstellungsfaktor für jeden Zylinder gebildet, so dass unter Berücksichtigung des Zylindergleichstellungsfaktors die Laufruhe der Brennkraftmaschine verbessert wird.During operation of the internal combustion engine, partial torques M i emitted by the cylinders of the internal combustion engine, which add up to the total output of the internal combustion engine, are detected. In this case, the detection of the partial moments M i does not necessarily include a direct measurement, but it may, for example Also, the observation and measurement of the rotational speed of the crankshaft and a correlation of this rotational speed with the ignition timing of the cylinder of the internal combustion engine done. When the partial torques M i of the cylinders Z i differ from each other within an engine operating stroke, cylinder equalization factor is then formed for each cylinder, so that the smooth running of the engine is improved in consideration of the cylinder equalization factor.
In
Um zu einer korrigierten Ansteuerspannung UAnsteuer, i, bzw. einer Ladung Qi des nicht dargestellten Einspritzventils des Zylinders Zi und infolgedessen zu einem korrigierten Hub des Einspritzventils zu gelangen, wird die Ansteuerspannung UAnsteuer, i, bzw. die Ladung Qi mit dem Zylindergleichstellungsfaktor FZGST, i multipliziert. Das Produkt aus Ansteuerspannung UAnsteuer, i und Zylindergleichstellungsfaktor FZGST, i ist die korrigierte Ansteuerspannung, bzw. die korrigierte Ladung.In order to arrive at a corrected drive voltage U drive, i , or a charge Q i of the injection valve of the cylinder Zi, not shown, and consequently to a corrected stroke of the injection valve, the drive voltage U is driving, i , or the charge Q i with the Cylinder equalization factor F ZGST, i multiplied. The product of drive voltage U drive, i and cylinder equalization factor F ZGST, i is the corrected drive voltage or the corrected charge.
In
Der Begrenzer 1 hat die in der
In
Dazu wird geprüft, ob der Zylindergleichstellungsfaktor FZGST, größer als der Maximalwert FZGST, Max ist. Wenn diese Prüfung negativ ist, wird ein Korrekturfaktor FT_einspritz, i für die Dauer der Einspritzung gleich 1,0 gesetzt. Wenn die Prüfung positiv ausfällt, wird der Korrekturfaktor FT_einspritz, i, durch die Bildung eines Quotienten aus dem Zylindergleichstellungsfaktor FZGST, i und dem Maximalwert FZGST, Max gebildet.For this purpose, it is checked whether the cylinder equalization factor F ZGST , greater than the maximum value F ZGST , Max . If this check is negative, a correction factor F T injection, i is set equal to 1.0 for the duration of the injection. If the test is positive, the correction factor F T_injection, i , is formed by forming a quotient of the cylinder equalization factor F ZGST, i and the maximum value F ZGST, Max .
Durch diese Maßnahme wird der Teil des Zylindergleichstellungsfaktors, der nicht durch eine Änderung des Hubs des Einspritzventils berücksichtigt werden kann, durch eine Erhöhung der Einspritzdauer genommen. Der Korrekturfaktor FT_einspritz, i ist in dem zuletzt beschriebenen Fall größer 1,0.By this measure, the part of the cylinder equalization factor, not by a Changing the stroke of the injector can be considered, taken by increasing the injection duration. The correction factor F T_einspritz, i is greater than 1.0 in the case described last.
Parallel dazu wird geprüft, ob der Zylindergleichstellungsfaktor FZGST, i kleiner als der Minimalwert FZGST, Min ist. Wenn diese Prüfung negativ ausfällt, wird der Korrekturfaktor FT_einspritz, i gleich 1,0 gesetzt. Wenn diese Prüfung positiv ausfällt, wird der Korrekturfaktor FT_einspritz, i aus dem Quotient aus Zylindergleichstellungsfaktor FZGST, i und dem Minimalwert FZGST, Min gebildet. In dem zuletzt beschriebenen Fall hat der Korrekturwert FT_einsprit, i jetzt einen Wert kleiner 1,0.In parallel, it is checked whether the cylinder equalization factor F ZGST, i is smaller than the minimum value F ZGST, Min . If this test fails, the correction factor F T injection, i is set equal to 1.0. If this test is positive, the correction factor F T_injection, i is formed from the quotient of cylinder equalization factor F ZGST, i and the minimum value F ZGST , Min . In the case described last, the correction value F T_insprit, i now has a value less than 1.0.
In
Dabei wird davon ausgegangen, dass aufgrund der Lastanforderungen an die Brennkraftmaschine und anderer Betriebsparameter eine bestimmte geforderte Kraftstoffmenge vom Steuergerät der Brennkraftmaschine berechnet wird. Diese geforderte Kraftstoffmenge wird mit dem Korrekturfaktor FT_einspritz, i multipliziert, und anschließend wird aus dieser multiplizierten geforderten Kraftstoffmenge eine Einspritzzeit für den betroffenen Zylinder Zi berechnet. Somit kann auch bei Zylindern, deren Betriebsverhalten durch Herstellungstoleranzen große Unterschiede aufweist, ein sehr ruhiger Lauf erzielt werden, indem nämlich ein Teil der Unterschiede durch eine zylinderindividuelle Variation des Ventilhubs der Einspritzventile und der verbleibende Teil durch eine zylinderindividuelle Variation der Einspritzdauer der Einspritzventile kompensiert wird.It is assumed that due to the load requirements of the internal combustion engine and other operating parameters, a certain required amount of fuel is calculated by the control unit of the internal combustion engine. This required fuel quantity is multiplied by the correction factor F T_injection, i , and then an injection time for the cylinder Z i concerned is calculated from this multiplied required fuel quantity. Thus, even with cylinders whose operating behavior by manufacturing tolerances has great differences, a very smooth running can be achieved by namely a part of the differences is compensated by a cylinder-individual variation of the valve lift of the injectors and the remaining part by a cylinder-individual variation of the injection duration of the injectors.
In
Betätigt wird die Düsennadel 7 und damit das Einspritzventil 3 durch einen Piezoaktor 13. Zwischen dem Piezoaktor 13 und der Düsennadel 7 ist ein Zwischenkolben 15 angeordnet, der ebenso wie die Düsennadel 7 im Düsenkörper 5 geführt wird. Der durch den gestrichelten Kreis 5 angedeutete Bereich 17 des Düsenkörpers 5 in dem sowohl die Düsennadel 7 als auch der Zwischenkolben 15 geführt werden, dient gleichzeitig auch als hydraulischer Koppler zwischen Kolben 15 und Düsennadel 7. Der Zwischenraum zwischen dem Kolben 15 und der Düsennadel 7 ist mit Kraftstoff gefüllt und überträgt die schnellen Steuerbewegungen, welche vom Piezoaktor 13 auf den Zwischenkolben 15 übertragen werden, direkt auf die Düsennadel 7.Actuates the nozzle needle 7 and thus the
Wenn sich der Abstand zwischen Düsennadel 7 und Zwischenkolben 15 langsam ändert, tritt eine gewisse Leckage von Kraftstoff zwischen Düsennadel 7 und Zwischenkolben 15 einerseits und Düsenkörper 5 in dem Bereich 17 auf, so dass die Änderungen des Abstands zwischen Düsennadel 7 und Zwischenkolben 15 kompensiert werden. Ursache für Längenänderungen des Einspritzventils 3 und in Folge dessen auch des Abstands zwischen Düsennadel 7 und Zwischenkolben 15 können Temperaturänderungen des Einspritzventils 3 sein.When the distance between the nozzle needle 7 and
Eine zweite Spiralfeder 19 presst den Kolben 15 an den Piezoaktor 13, so dass diese beiden Bauelemente stets spielfrei miteinander verbunden sind.A
Über eine Kraftstoffzufuhr 21 wird das Einspritzventil 3 mit Kraftstoff versorgt.Via a
Claims (8)
- Method for compensating for differences in torque between the cylinders (Zi, where i = l to m) of an internal combustion engine, wherein the fuel injection system of the internal combustion engine has an injection valve (3) with a variable stroke for each cylinder (Zi), characterized by the following method steps:- sensing of the partial torques (Mi) which are output by the cylinders (Zi) of the internal combustion engine,- formation of a cylinder equalization factor (FZGST,i) for each cylinder (Zi), wherein the cylinder equalization factor (FZGST,i) is limited to a maximum value (FZGST,max) in the upward direction and to a minimum value (FZGST,Min) in the downward direction,- correction of the stroke of the injection valve (3) assigned to the cylinder (Zi), as a function of the cylinder equalization factor (FZGST,i) and- determination of a correction factor (FT_einspritz,i) for the injection period,wherein the correction factor (FT_einspritz,i) is equal to 1.0 if the cylinder equalization factor (FZGST,i) is smaller than the maximum value (FZGST,Max) and larger than the minimum value (FZGST,Min),
wherein the correction factor (FT_einspritz,i) is equal to the quotient of the cylinder equalization factor (FZGST,i) and the maximum value (FZGST,Max) when the cylinder equalization factor (FZGST,i) is larger than the maximum value (FZGST,Max), and
wherein the correction factor (FT_einspritz,i) is equal to the quotient of the cylinder equalization factor (FZGST,i) and the minimum value (FZGST,Min) when the cylinder equalization factor (FZGST,i) is smaller than the minimum value (FZGST,Min). - Method according to Claim 1, characterized in that the stroke of the injection valve (3) is corrected by correcting an actuation voltage (UAnsteuer, i) or an electrical charge of the injection valve (3) as a function of the cylinder equalization factor (FZGST,i).
- Method according to Claim 2, characterized in that the actuation voltage (UAnsteuer,i) or the electrical charge is corrected by multiplication by the cylinder equalization factor (FZGST,i).
- Method according to one of the preceding claims, characterized in that the required injection quantity of the cylinder (Zi) is multiplied by the correction factor (FT_einspritz,i) and is subsequently converted into a cylinder-specific injection time (TEinspritz,i).
- Method according to one of the preceding claims, characterized in that it is provided for use in internal combustion engines with petrol direct injection, in particular with jet-controlled petrol direct injection.
- Computer program, characterized in that it operates according to one of the preceding methods.
- Computer program according to Claim 6, characterized in that it can be stored on a storage medium.
- Control unit for an internal combustion engine, characterized in that it operates according to one of the methods according to one of Claims 1 to 5.
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE10233778 | 2002-07-25 | ||
DE2002133778 DE10233778A1 (en) | 2002-07-25 | 2002-07-25 | Compensation method for moment differences of cylinders of combustion engine involves correcting hub of injection valve allocated to cylinder depending on cylinder coordination factor |
PCT/DE2003/002005 WO2004016931A1 (en) | 2002-07-25 | 2003-06-17 | Method for improving the true running of an internal combustion engine |
Publications (2)
Publication Number | Publication Date |
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EP1527267A1 EP1527267A1 (en) | 2005-05-04 |
EP1527267B1 true EP1527267B1 (en) | 2008-02-27 |
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EP03787596A Expired - Lifetime EP1527267B1 (en) | 2002-07-25 | 2003-06-17 | Method for improving the true running of an internal combustion engine |
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EP (1) | EP1527267B1 (en) |
JP (1) | JP4327721B2 (en) |
DE (2) | DE10233778A1 (en) |
WO (1) | WO2004016931A1 (en) |
Families Citing this family (9)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102004006294B3 (en) * | 2004-02-09 | 2005-10-13 | Siemens Ag | Method for equalizing the injection quantity differences between the cylinders of an internal combustion engine |
DE102004006297B4 (en) * | 2004-02-09 | 2007-05-16 | Siemens Ag | Method for controlling an injection valve of an internal combustion engine |
DE102005004442B4 (en) * | 2005-01-31 | 2006-11-16 | Siemens Ag | Method and device for controlling an internal combustion engine |
DE102005010028B4 (en) | 2005-03-04 | 2007-04-26 | Siemens Ag | Regulator device for compensation of scattering of injectors |
WO2007090228A1 (en) * | 2006-02-06 | 2007-08-16 | Orbital Australia Pty Limited | Fuel injection apparatus |
DE102006039523A1 (en) * | 2006-08-23 | 2008-02-28 | Siemens Ag | Method for controlling a fuel injection device |
DE102009045723A1 (en) | 2009-10-15 | 2011-04-21 | Robert Bosch Gmbh | Method for operating internal-combustion engine, involves detecting lambda value in exhaust gas of cylinders, and controlling spin flap or adjusting device in inlet channel of cylinder depending on lambda value |
US20150039208A1 (en) * | 2013-07-30 | 2015-02-05 | GM Global Technology Operations LLC | System and method for controlling air flow through an engine based on a fuel injection duration limit |
DE102016112335A1 (en) * | 2016-07-06 | 2018-01-11 | Knorr-Bremse Systeme für Schienenfahrzeuge GmbH | Device and method for valve control |
Family Cites Families (5)
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DE3336028C3 (en) * | 1983-10-04 | 1997-04-03 | Bosch Gmbh Robert | Device for influencing control variables of an internal combustion engine |
DE19642653C5 (en) * | 1996-10-16 | 2008-02-21 | Daimler Ag | Process for forming an ignitable fuel / air mixture |
DE19700711C2 (en) * | 1997-01-10 | 1999-05-12 | Siemens Ag | Method for compensating for the systematic error in injection devices for an internal combustion engine |
DE10026274A1 (en) * | 2000-05-26 | 2001-12-06 | Siemens Ag | Method for cylinder equalization in an internal combustion engine |
DE10206906C1 (en) * | 2002-02-19 | 2003-11-06 | Siemens Ag | Method for controlling an amount of fuel injected by a pieno injector |
-
2002
- 2002-07-25 DE DE2002133778 patent/DE10233778A1/en not_active Ceased
-
2003
- 2003-06-17 JP JP2004528313A patent/JP4327721B2/en not_active Expired - Fee Related
- 2003-06-17 WO PCT/DE2003/002005 patent/WO2004016931A1/en active IP Right Grant
- 2003-06-17 DE DE50309265T patent/DE50309265D1/en not_active Expired - Lifetime
- 2003-06-17 EP EP03787596A patent/EP1527267B1/en not_active Expired - Lifetime
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WO2004016931A1 (en) | 2004-02-26 |
JP4327721B2 (en) | 2009-09-09 |
DE10233778A1 (en) | 2004-02-05 |
JP2005533969A (en) | 2005-11-10 |
EP1527267A1 (en) | 2005-05-04 |
DE50309265D1 (en) | 2008-04-10 |
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