EP1323908A2 - Method for operating an engine - Google Patents
Method for operating an engine Download PDFInfo
- Publication number
- EP1323908A2 EP1323908A2 EP02450288A EP02450288A EP1323908A2 EP 1323908 A2 EP1323908 A2 EP 1323908A2 EP 02450288 A EP02450288 A EP 02450288A EP 02450288 A EP02450288 A EP 02450288A EP 1323908 A2 EP1323908 A2 EP 1323908A2
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- Prior art keywords
- ignition
- cycle
- stroke
- combustion chamber
- fuel
- 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.)
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/12—Engines characterised by fuel-air mixture compression with compression ignition
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B75/00—Other engines
- F02B75/02—Engines characterised by their cycles, e.g. six-stroke
- F02B75/021—Engines characterised by their cycles, e.g. six-stroke having six or more strokes per cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B1/00—Engines characterised by fuel-air mixture compression
- F02B1/02—Engines characterised by fuel-air mixture compression with positive ignition
- F02B1/04—Engines characterised by fuel-air mixture compression with positive ignition with fuel-air mixture admission into cylinder
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B3/00—Engines characterised by air compression and subsequent fuel addition
- F02B3/06—Engines characterised by air compression and subsequent fuel addition with compression ignition
Definitions
- DE 33 17 128 A1 describes an internal combustion engine, which according to a Six-stroke cycle works.
- a fuel-air mixture embedded in the cylinder which in a first compression stroke is compressed.
- a first power stroke Following the ignition of the compressed fuel-air mixture there is a first power stroke.
- the combustion products are compressed.
- the cylinder content is ignited by a spark plug.
- a second power stroke follows as a result of the expansion of the compressed Combustion products and finally an exhaust stroke, during which the Combustion gases are driven out of the cylinder.
- a method for operating a gasoline-fueled internal combustion engine is known, the engine operating area of which has auto-ignition and spark-ignition areas.
- the internal combustion engine is operated by self-ignition during the partial load, a homogeneous fuel-air mixture being generated in the combustion chamber and the combustion being initiated by self-ignition of this fuel mixture.
- the designated from the English-speaking world as the HCCI process (H omogenous C harge C ompression I gnition) method has particular advantages with regard to the development of emissions.
- AT 5.140 U describes a process with which the self-ignition of the homogeneous fuel-air mixture can be controlled by the residual gas content in the combustion chamber.
- the exhaust gas temperature itself is sufficient, especially at low speeds and loads at extremely high amounts of residual gas, however, no longer enough, so the filling to warm up strongly so that a safe self-ignition is achieved. Moreover the longer cycle times at low speeds have a negative effect on the Filling temperatures because there is more time for heat transfer.
- the object of the invention is to avoid these disadvantages and a method to develop an internal combustion engine, on the one hand high efficiency and low emissions can be achieved can.
- this is achieved in that the injection of the second Subset of petrol in the third stroke, preferably in the second half of the third cycle, there is at least one in the combustion chamber before the second ignition approximately homogeneous fuel-air mixture is formed and that the second ignition by compression ignition of this homogeneous air / fuel mixture he follows.
- the fuel-air mixture formed during the second stroke is lean and stratified and has a large excess of air with an air / fuel ratio of ⁇ > 1.5.
- the excess air ensures that sufficient oxygen is still available for the second combustion.
- the lean stratified combustion produces only very low NO x emissions.
- the temperature of the burned gas is relatively low, but high enough to guarantee safe auto-ignition in the second combustion cycle. It is particularly advantageous if, by adjusting the size of the first subset of the gasoline fuel injected in the second stroke, the combustion that takes place in the fifth stroke following the second ignition is regulated. By simply varying the amount of the first injection or by changing the division between the first and second injection, the composition of the combustion gas and thus the starting condition for the compression ignition can be changed or adapted.
- stratified combustion has the advantage of very high efficiency.
- a pressure adjustment is carried out in the combustion chamber.
- the pressure level regulation in the combustion chamber can be used to control auto-ignition. It is particularly advantageous if the pressure adjustment by a short-term Opening at least one lift valve, preferably an inlet valve becomes.
- a first cycle consisting of the sixth and the first cycle serves to change the gas, that is to say to push out exhaust gas and to draw in fresh fill.
- the second cycle - the second and third clock consists of compression, spark ignition, stratified lean combustion (SCSI - S tratified C harge S pat gnition I) and expansion and forms the first cycle of operation.
- the lean exhaust gas from this first work cycle is not pushed out but remains in the cylinder and serves as a filling for the following third cycle (fourth and fifth stroke).
- This third cycle is the second work cycle and is characterized by homogeneous compression ignition (HCCI). This is followed by the exhaust of the first cycle.
- HCCI homogeneous compression ignition
- the invention is illustrated by the figure.
- the figure shows the valve strokes h of the exhaust valves and the intake valves, wherein with reference number 1 the exhaust valve lift and with reference number 2 the intake valve lift is designated.
- Line 3 shows the injection events in the combustion chamber.
- the working process has six bars I, II, III, IV, V, VI, two each Bars belong to a cycle A, B, C.
- the first cycle A is used to change the gas and consists of the clock VI for pushing out the exhaust gas and the clock I for Sucking in air.
- the second cycle B consists of the clock II, in which the Air is compressed in the cylinder and a first subset of petrol is injected, as well as stroke III, the first working stroke of the piston.
- the first subset of petrol is injected, such as is indicated with reference number 3a.
- an igniter such as is indicated by reference numeral 5. This leads to a lean stratified combustion.
- the lean exhaust gas from the first work cycle B is not pushed out, but remains in the cylinder and serves as a filling for the next one third cycle C, the second cycle.
- the second cycle has the stroke IV, during which the cylinder content is recompressed, and the Cycle V, the second working stroke of the piston.
- a short opening can at least of an intake valve may be provided to regulate the pressure level in the cylinder.
- This brief opening of the inlet valve is indicated by reference number 2a.
- the pressure adjustment by briefly opening the inlet valve in the area bottom dead center between cycle III and cycle IV can be for the Control of the auto ignition can be used.
- the stratified lean combustion in the cycle B works with high air surplus and produced especially for very little fuel injected very low NO x emissions.
- the temperature of the burned gas is also relatively low, but high enough to guarantee reliable auto-ignition in the following working cycle C.
- the composition of the combustion gas and thus the starting condition for the compression ignition 6 can be changed or adapted. Both stratified combustion and homogeneous self-ignition are characterized by high efficiency.
- Compression ignition 6 offers significant advantages, particularly with regard to NO x and soot emissions.
- the fact that any soot or hydrocarbon emissions from the first work cycle B are fed to a further combustion and thus burned also has a positive effect on the emissions.
Abstract
Description
Die Erfindung betrifft ein Verfahren zum Betreiben einer Brennkraftmaschine nach einem Sechstakt-Verfahren mit folgender Taktfolge:
- 1.Takt: Ansaugen von Luft in einen Brennraum,
- 2. Takt: Verdichten der Luft und Einspritzen einer ersten Teilmenge von Otto-Kraftstoff in den Brennraum,
- 3. Takt: Erster Arbeitshub mit vorangegangener erster Zündung des Gemisches, wobei die erste Zündung durch eine Zündeinrichtung eingeleitet wird,
- 4. Takt: Neuverdichtung des Brennrauminhaltes,
- 5. Takt: Zweiter Arbeitshub mit vorangegangener zweiter Zündung des im Brennraum befindlichen Kraftstoff-Luftgemisches,
- 6. Takt: Ausschieben der Abgase aus dem Brennraum,
- 1st cycle: sucking air into a combustion chamber,
- 2nd stroke: compressing the air and injecting a first subset of petrol into the combustion chamber,
- 3rd cycle: first working stroke with previous first ignition of the mixture, the first ignition being initiated by an ignition device,
- 4th cycle: recompression of the combustion chamber contents,
- 5th cycle: second working stroke with previous second ignition of the fuel-air mixture in the combustion chamber,
- 6th cycle: pushing the exhaust gases out of the combustion chamber,
Aus der DE 34 06 732 A1 ist ein Arbeitsverfahren für Hubkolbenverbrennungskraftmaschinen mit innerer Verbrennung bekannt, bei dem die Zündung des Kraftstoff-Luftgemisches durch eine Zündeinrichtung oder mittels Selbstzündung erfolgt. Das Arbeitstaktverfahren läuft dabei in sechs Takten mit der folgenden Taktweise ab:
- 1. Takt: Ansaugen,
- 2. Takt: Verdichten und Einspritzen einer Kraftstoffteilmenge,
- 3. Takt: erster Arbeitstakt,
- 4. Takt: Neu verdichten der Abgase, die noch ungebundenen Sauerstoff enthalten und Einspritzen einer zweiten Kraftstoffteilmenge,
- 5. Takt: Zweiter Arbeitstakt,
- 6. Takt: Ausschieben.
- 1st cycle: suction,
- 2nd stroke: compression and injection of a partial fuel quantity,
- 3rd bar: first work bar,
- 4th stroke: recompress the exhaust gases that still contain unbound oxygen and inject a second sub-quantity of fuel,
- 5th bar: second work bar,
- 6th measure: Extend.
Dieses Verfahren wird sowohl für den Diesel-Motor, bei dem die Zündung des Kraftstoffes durch Kompressionszündung erfolgt, als auch für den Otto-Motor, bei dem die Zündung des Kraftstoffes durch eine Zündeinrichtung erfolgt, beschrieben.This procedure is used for both the diesel engine, in which the ignition of the Fuel is made by compression ignition, as well as for the Otto engine which is the ignition of the fuel by an ignition device described.
Die DE 33 17 128 A1 beschreibt eine Brennkraftmaschine, welche nach einem Sechstakt-Zyklus arbeitet. Während eines Einlasshubes wird ein Treibstoff-Luftgemisch in den Zylinder eingelassen, welches in einem ersten Kompressionshub komprimiert wird. Im Anschluss an die Zündung des komprimierten Treibstoff-Luftgemisches erfolgt ein erster Krafthub. In einem darauffolgenden zweiten Kompressionshub werden die Verbrennungsprodukte komprimiert. Am Ende des zweiten Kompressionshubes wird der Zylinderinhalt durch eine Zündkerze gezündet. Es folgt ein zweiter Krafthub in Folge der Expansion der komprimierten Verbrennungsprodukte und schließlich ein Auslasshub, währenddessen die Verbrennungsgase aus dem Zylinder herausgetrieben werden.DE 33 17 128 A1 describes an internal combustion engine, which according to a Six-stroke cycle works. During an intake stroke, a fuel-air mixture embedded in the cylinder, which in a first compression stroke is compressed. Following the ignition of the compressed fuel-air mixture there is a first power stroke. In a subsequent second Compression stroke, the combustion products are compressed. At the end of second compression stroke, the cylinder content is ignited by a spark plug. A second power stroke follows as a result of the expansion of the compressed Combustion products and finally an exhaust stroke, during which the Combustion gases are driven out of the cylinder.
Bei den bekannten Sechstakt-Brennkraftmaschinen liegt zu Beginn des ersten und des zweiten Arbeitshubes entweder Kompressionszündung von Diesel- oder Fremdzündung von Otto-Kraftstoff vor.In the known six-stroke internal combustion engines is the beginning of the first and the second stroke either compression ignition of diesel or Spark ignition of petrol.
Brennkraftmaschinen, welche zumindest teilweise und mit homogener Fremdzündung von Benzin betrieben werden, benötigen für eine sichere Zündung des Luft-Kraftstoff-Restgasgemisches hohe Füllungstemperaturen, sowie hohe Restgasmengen.Internal combustion engines, which are at least partially and with homogeneous spark ignition operated by petrol, need for a safe ignition of the Air-fuel-residual gas mixture high filling temperatures, as well as high residual gas quantities.
Aus der AT 3.135 U ist ein Verfahren zum Betreiben einer Otto-Kraftstoffbetriebenen Brennkraftmaschine bekannt, deren Motorbetriebsbereich Selbstzündungsund Fremdzündungsbereiche aufweist. Während der Teillast wird die Brennkraftmaschine selbstgezündet betrieben, wobei ein homogenes Kraftstoff-Luftgemisch im Brennraum erzeugt wird und die Verbrennung durch Selbstzündung dieses Kraftstoffgemisches eingeleitet wird. Das aus dem englischen Sprachraum als HCCI-Verfahren (Homogenous Charge Compression Ignition) bezeichnete Verfahren hat besondere Vorteile hinsichtlich der Entstehung von Emissionen. In der AT 5.140 U wird ein Verfahren beschrieben, mit welchem die Selbstzündung des homogenen Kraftstoff-Luftgemisches durch den Restgasgehalt im Brennraum gesteuert werden kann. From AT 3.135 U a method for operating a gasoline-fueled internal combustion engine is known, the engine operating area of which has auto-ignition and spark-ignition areas. The internal combustion engine is operated by self-ignition during the partial load, a homogeneous fuel-air mixture being generated in the combustion chamber and the combustion being initiated by self-ignition of this fuel mixture. The designated from the English-speaking world as the HCCI process (H omogenous C harge C ompression I gnition) method has particular advantages with regard to the development of emissions. AT 5.140 U describes a process with which the self-ignition of the homogeneous fuel-air mixture can be controlled by the residual gas content in the combustion chamber.
Speziell bei niedrigen Drehzahlen und Lasten reicht die Abgastemperatur selbst bei extrem hohen Restgasmengen allerdings nicht mehr aus, um die Füllung so stark zu erwärmen, dass eine sichere Selbstzündung erreicht wird. Außerdem wirken sich die längeren Zykluszeiten bei niedrigen Drehzahlen negativ auf die Füllungstemperaturen aus, da mehr Zeit für den Wärmeübergang vorhanden ist.The exhaust gas temperature itself is sufficient, especially at low speeds and loads at extremely high amounts of residual gas, however, no longer enough, so the filling to warm up strongly so that a safe self-ignition is achieved. Moreover The longer cycle times at low speeds have a negative effect on the Filling temperatures because there is more time for heat transfer.
Aufgabe der Erfindung ist es, diese Nachteile zu vermeiden und ein Verfahren zum Betreiben einer Brennkraftmaschine zu entwickeln, mit welchem einerseits ein hoher Wirkungsgrad und andererseits niedrige Emissionen erreicht werden können.The object of the invention is to avoid these disadvantages and a method to develop an internal combustion engine, on the one hand high efficiency and low emissions can be achieved can.
Erfindungsgemäß wird dies dadurch erreicht, dass die Einspritzung der zweiten Teilmenge von Otto-Kraftstoff im dritten Takt, vorzugsweise in der zweiten Hälfte des dritten Taktes, erfolgt, dass im Brennraum vor der zweiten Zündung ein zumindest annähernd homogenes Kraftstoff-Luftgemisch gebildet wird und dass die zweite Zündung durch Kompressionszündung dieses homogenen Kraftstoff-Luftgemisches erfolgt.According to the invention, this is achieved in that the injection of the second Subset of petrol in the third stroke, preferably in the second half of the third cycle, there is at least one in the combustion chamber before the second ignition approximately homogeneous fuel-air mixture is formed and that the second ignition by compression ignition of this homogeneous air / fuel mixture he follows.
Vorzugsweise ist dabei vorgesehen, dass das während dem zweiten Takt gebildete Kraftstoff-Luftgemisch mager und geschichtet ist und einen hohen Luftüberschuss mit einem Luft/Kraftstoffverhältnis von λ > 1,5 aufweist. Der Luftüberschuss gewährleistet, dass für die zweite Verbrennung noch ausreichend Sauerstoff zur Verfügung steht. Speziell bei sehr geringen eingespritzten Kraftstoffmengen werden durch die magere Schichtverbrennung nur sehr geringe NOx-Emissionen gebildet. Die Temperatur des verbrannten Gases ist relativ niedrig, aber hoch genug, um damit eine sichere Selbstzündung im zweiten Verbrennungszyklus zu garantieren. Besonders vorteilhaft ist es, wenn durch Einstellen der Größe der ersten Teilmenge des im zweiten Takt eingespritzten Otto-Kraftstoffes die im Anschluss an die zweite Zündung im fünften Takt stattfindende Verbrennung geregelt wird. Durch einfaches Variieren der Menge der ersten Einspritzung oder durch Verändern der Aufteilung zwischen erster und zweiter Einspritzung kann die Zusammensetzung des Verbrennungsgases und somit die Ausgangsbedingung für die Kompressionszündung verändert beziehungsweise angepasst werden.It is preferably provided that the fuel-air mixture formed during the second stroke is lean and stratified and has a large excess of air with an air / fuel ratio of λ> 1.5. The excess air ensures that sufficient oxygen is still available for the second combustion. Especially with very small amounts of fuel injected, the lean stratified combustion produces only very low NO x emissions. The temperature of the burned gas is relatively low, but high enough to guarantee safe auto-ignition in the second combustion cycle. It is particularly advantageous if, by adjusting the size of the first subset of the gasoline fuel injected in the second stroke, the combustion that takes place in the fifth stroke following the second ignition is regulated. By simply varying the amount of the first injection or by changing the division between the first and second injection, the composition of the combustion gas and thus the starting condition for the compression ignition can be changed or adapted.
Darüber hinaus hat die Schichtverbrennung den Vorteil eines sehr hohen Wirkungsgrades.In addition, stratified combustion has the advantage of very high efficiency.
Aber auch die homogene Selbstzündung zeichnet sich durch einen guten Wirkungsgrad aus. Speziell hinsichtlich NOx- und Ruß-Emissionen bietet die Kompressionszündung wesentliche Vorteile. Auch der Umstand, dass eventuell entstehender Ruß beziehungsweise Kohlenwasserstoffemissionen aus dem ersten Arbeitszyklus einer weiteren Verbrennung zugeführt und damit verbrannt werden, wirkt sich positiv auf die Emissionen aus.But the homogeneous self-ignition is also characterized by good efficiency. Compression ignition offers significant advantages, particularly with regard to NO x and soot emissions. The fact that any soot or hydrocarbon emissions from the first work cycle are fed to a further combustion and thus burned also has a positive effect on the emissions.
In einer besonders bevorzugten Ausführungsvarianten der Erfindung ist vorgesehen, dass im Bereich des Überganges zwischen dem dritten und dem vierten Takt eine Druckanpassung im Brennraum durchgeführt wird. Die Druckniveauregulierung im Brennraum kann für die Steuerung der Selbstzündung genutzt werden. Besonders vorteilhaft ist es, wenn die Druckanpassung durch ein kurzfristiges Öffnen zumindest eines Hubventils, vorzugsweise eines Einlassventils durchgeführt wird.In a particularly preferred embodiment of the invention, that in the area of the transition between the third and fourth A pressure adjustment is carried out in the combustion chamber. The pressure level regulation in the combustion chamber can be used to control auto-ignition. It is particularly advantageous if the pressure adjustment by a short-term Opening at least one lift valve, preferably an inlet valve becomes.
Dabei dient ein aus dem sechsten und dem ersten Takt bestehender erster Zyklus dem Gaswechsel, das heißt dem Ausschieben von Abgas, sowie dem Ansaugen von Frischfüllung. Der zweite Zyklus - zweiter und dritter Takt- besteht aus Kompression, fremdgezündeter, magerer Schichtverbrennung (SCSI - Stratified Charge Spat Ignition) und Expansion und bildet den ersten Arbeitszyklus. Das magere Abgas aus diesem ersten Arbeitszyklus wird nicht ausgeschoben sondern verbleibt im Zylinder und dient als Füllung für den folgenden dritten Zyklus (vierter und fünfter Takt). Dieser dritte Zyklus ist der zweite Arbeitszyklus und wird durch eine homogene Kompressionszündung (HCCI) charakterisiert. Darauf folgt wieder das Ausschieben des Abgases des ersten Zyklus.Here, a first cycle consisting of the sixth and the first cycle serves to change the gas, that is to say to push out exhaust gas and to draw in fresh fill. The second cycle - the second and third clock consists of compression, spark ignition, stratified lean combustion (SCSI - S tratified C harge S pat gnition I) and expansion and forms the first cycle of operation. The lean exhaust gas from this first work cycle is not pushed out but remains in the cylinder and serves as a filling for the following third cycle (fourth and fifth stroke). This third cycle is the second work cycle and is characterized by homogeneous compression ignition (HCCI). This is followed by the exhaust of the first cycle.
Die niedrigen Ladungswechselverluste und die Kombination der beiden Brennverfahren SCSI und HCCI, so wie die Tatsache, dass bei diesem Sechstakt-Arbeitsverfahren zwei Arbeitszyklen einem Ladungswechselzyklus gegenüber stehen, garantieren hohes Verbrauchspotential bei niedrigsten Emissionen.The low gas exchange losses and the combination of the two combustion processes SCSI and HCCI, like the fact that this six-stroke process two working cycles are opposed to one charge cycle, guarantee high consumption potential with lowest emissions.
Die Erfindung wird anhand der Figur näher erläutert.The invention is illustrated by the figure.
Die Figur zeigt die Ventilhübe h der Auslassventile und der Einlassventile, wobei
mit Bezugszeichen 1 der Auslassventilhub und mit Bezugszeichen 2 der Einlassventilhub
bezeichnet ist.The figure shows the valve strokes h of the exhaust valves and the intake valves, wherein
with
Die Linie 3 zeigt die Einspritzereignisse in den Brennraum.
Im unteren Teil des Diagramms ist der Zylinderdruck p über dem Kurbelwinkel
KW aufgetragen. Diese Kurve ist mit Bezugszeichen 4 bezeichnet.In the lower part of the diagram, the cylinder pressure p is above the crank angle
KW applied. This curve is designated by
Das Arbeitsverfahren weist sechs Takte I, II, III, IV, V, VI auf, wobei jeweils zwei
Takte einem Zyklus A, B, C angehören. Der erste Zyklus A dient dem Gaswechsel
und besteht aus dem Takt VI zum Ausschieben des Abgases und dem Takt I zum
Ansaugen von Luft. Der zweite Zyklus B besteht aus dem Takt II, bei dem die
Luft im Zylinder verdichtet wird und eine erste Teilmenge von Otto-Kraftstoff
eingespritzt wird, sowie den Takt III dem ersten Arbeitshub des Kolbens. Am
Ende des Taktes II wird die erste Teilmenge von Otto-Kraftstoff eingespritzt, wie
mit Bezugszeichen 3a angedeutet ist. Gleich darauf wird am Ende des Taktes II
das magere und geschichtete Gemisch durch eine Zündeinrichtung gezündet, wie
durch Bezugszeichen 5 angedeutet ist. Dabei erfolgt eine magere Schichtverbrennung.
Das magere Abgas aus dem ersten Arbeitszyklus B wird nicht ausgeschoben,
sondern verbleibt im Zylinder und dient als Füllung für den darauffolgenden
dritten Zyklus C, dem zweiten Arbeitszyklus. Der zweite Arbeitszyklus
weist den Takt IV, während dem der Zylinderinhalt neu verdichtet wird, und den
Takt V, den zweiten Arbeithub des Kolbens, auf.The working process has six bars I, II, III, IV, V, VI, two each
Bars belong to a cycle A, B, C. The first cycle A is used to change the gas
and consists of the clock VI for pushing out the exhaust gas and the clock I for
Sucking in air. The second cycle B consists of the clock II, in which the
Air is compressed in the cylinder and a first subset of petrol
is injected, as well as stroke III, the first working stroke of the piston. At the
At the end of cycle II, the first subset of petrol is injected, such as
is indicated with
In der zweiten Hälfte des Taktes III wird eine zweite Teilmenge von Otto-Kraftstoff
in den Brennraum eingespritzt. Durch diese frühe Einspritzung wird bis zum
durch Bezugszeichen 6 angedeuteten Zeitpunkt der zweiten Zündung eine Homogenisierung
des Gemisches erreicht. Die zweite Zündung 6 ist eine Kompressionszündung.
Danach erfolgt im Takt VI wieder das Ausschieben des Abgases.In the second half of measure III there is a second subset of petrol
injected into the combustion chamber. By this early injection until
Homogenization, indicated by
Zwischen den beiden Arbeitszyklen B und C kann ein kurzes Öffnen zumindest
eines Einlassventils vorgesehen sein, um das Druckniveau im Zylinder zu regulieren.
Dieses kurze Öffnen des Einlassventils ist mit Bezugszeichen 2a angedeutet.
Die Duckanpassung durch kurzes Öffnen des Einlassventils im Bereich
des unteren Totpunktes zwischen dem Zyklus III und dem Zyklus IV kann für die
Steuerung der Selbstzündung genutzt werden.Between the two working cycles B and C, a short opening can at least
of an intake valve may be provided to regulate the pressure level in the cylinder.
This brief opening of the inlet valve is indicated by
Die magere Schichtverbrennung im Arbeitszyklus B funktioniert mit hohem Luft-überschuss
und produziert speziell bei sehr wenig eingespritztem Kraftstoff sehr
geringe NOx-Emissionen. Auch die Temperatur des verbrannten Gases ist relativ
gering, jedoch aber hoch genug, um damit eine sichere Selbstzündung im folgenden
Arbeitszyklus C zu garantieren. Durch einfaches Variieren der Einspritzmenge
kann die Zusammensetzung des Verbrennungsgases und somit die Ausgangsbedingung
für die Kompressionszündung 6 verändert beziehungsweise angepasst
werden. Sowohl die Schichtverbrennung als auch die homogene Selbstzündung
zeichnen sich durch einen hohen Wirkungsgrad aus.The stratified lean combustion in the cycle B works with high air surplus and produced especially for very little fuel injected very low NO x emissions. The temperature of the burned gas is also relatively low, but high enough to guarantee reliable auto-ignition in the following working cycle C. By simply varying the injection quantity, the composition of the combustion gas and thus the starting condition for the
Speziell hinsichtlich der NOx- und Ruß-Emissionen bietet die Kompressionszündung
6 deutliche Vorteile. Auch der Umstand, dass eventuell entstehender Ruß
beziehungsweise Kohlenwasserstoffemissionen aus dem ersten Arbeitszyklus B
einer weiteren Verbrennung zugeführt und damit verbrannt werden, wirkt sich
positiv auf die Emissionen aus.
Der niedrige Ladungswechselverlust und die Kombination der beiden Brennverfahren, sowie die Tatsache, dass bei dem beschriebenen Sechstakt-Verfahren zwei Arbeitszyklen B, C einem Ladungswechselzyklus A gegenüberstehen, garantieren hohes Verbrauchspotential bei niedrigsten Emissionen.The low gas exchange loss and the combination of the two combustion processes, and the fact that with the six-stroke method described guarantee two working cycles B, C against a charge exchange cycle A. high consumption potential with lowest emissions.
Claims (5)
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| AT0097901U AT5937U1 (en) | 2001-12-27 | 2001-12-27 | METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE |
| AT9792001U | 2001-12-27 |
Publications (3)
| Publication Number | Publication Date |
|---|---|
| EP1323908A2 true EP1323908A2 (en) | 2003-07-02 |
| EP1323908A3 EP1323908A3 (en) | 2003-10-29 |
| EP1323908B1 EP1323908B1 (en) | 2006-06-21 |
Family
ID=3504152
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| EP02450288A Expired - Fee Related EP1323908B1 (en) | 2001-12-27 | 2002-12-19 | Method for operating an engine |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US6758174B1 (en) |
| EP (1) | EP1323908B1 (en) |
| AT (1) | AT5937U1 (en) |
| DE (1) | DE50207286D1 (en) |
Families Citing this family (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US7165391B2 (en) | 2004-03-19 | 2007-01-23 | Ford Global Technologies, Llc | Method to reduce engine emissions for an engine capable of multi-stroke operation and having a catalyst |
| US7059281B2 (en) * | 2004-07-12 | 2006-06-13 | General Motors Corporation | Four stroke engine auto-ignition combustion |
| US6966309B1 (en) * | 2004-08-09 | 2005-11-22 | Southwest Research Institute | In-cylinder reburn method for emissions reduction |
| GB2431202B (en) * | 2005-09-01 | 2007-09-05 | Lotus Car | An engine which operates repeatedly with a multi-stage combustion process |
| US7398758B2 (en) * | 2005-10-25 | 2008-07-15 | Gm Global Technology Operations, Inc. | Combustion control method for a direct-injection controlled auto-ignition combustion engine |
| US7418928B2 (en) | 2006-04-28 | 2008-09-02 | Caterpillar Inc. | Engine and method for operating an engine |
| US20080022657A1 (en) * | 2006-07-28 | 2008-01-31 | Caterpillar Inc. | Power source thermal management and emissions reduction system |
| US7426916B2 (en) * | 2006-10-30 | 2008-09-23 | Ford Global Technologies, Llc | Multi-stroke internal combustion engine for facilitation of auto-ignition operation |
| JP2011508131A (en) * | 2007-12-20 | 2011-03-10 | ルノー・トラックス | 6-stroke internal combustion engine, method of operating such an engine and vehicle equipped with such an engine |
| CN102325976A (en) * | 2008-12-22 | 2012-01-18 | 卡特彼勒公司 | Engine control system implementing lean burn 6-stroke cycle |
| US20100212300A1 (en) * | 2009-02-25 | 2010-08-26 | Caterpillar Inc. | Exhaust Purification With On-Board Ammonia Production |
| CN102155311A (en) * | 2011-05-27 | 2011-08-17 | 华北水利水电学院 | Secondary combustion working method of six-stroke internal-combustion engine |
| US9133764B2 (en) | 2012-12-12 | 2015-09-15 | Caterpillar Inc. | Six-stroke engine system with blowdown exhaust recirculation |
| US9181830B2 (en) | 2012-12-12 | 2015-11-10 | Caterpillar Inc. | After-treatment system and method for six-stroke combustion cycle |
| US8978603B2 (en) | 2012-12-12 | 2015-03-17 | Caterpillar Inc. | Six-stroke internal combustion engine valve activation system and method for operating such engine |
| US8978602B2 (en) | 2012-12-12 | 2015-03-17 | Caterpillar Inc. | Six-stroke engine power density matching system and method |
| US9151222B2 (en) | 2012-12-12 | 2015-10-06 | Caterpillar Inc. | Six-stroke combustion cycle engine and process |
| US8978601B2 (en) | 2012-12-12 | 2015-03-17 | Caterpillar Inc. | Six-stroke engine system with blowdown exhaust system |
| US9057324B2 (en) | 2012-12-12 | 2015-06-16 | Caterpillar Inc. | Six-stroke engine system with blowdown turbocharger |
| CN103835825B (en) * | 2014-02-27 | 2016-06-29 | 长城汽车股份有限公司 | Six-stroke gasoline oil machine and control method thereof and control device |
| CN104005862B (en) * | 2014-05-30 | 2017-11-14 | 长城汽车股份有限公司 | Control method, system and the vehicle of internal combustion engine |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3317128A1 (en) | 1983-05-06 | 1984-11-08 | Leonhard Johann Gerhard Umina New South Wales Pal | Combustion engine |
| DE3406732A1 (en) | 1984-02-24 | 1985-08-29 | Reinhard 3501 Ahnatal Bennedik | Operating process for reciprocating piston internal-combustion engines and combustion engine for this |
| AT3135U1 (en) | 1998-06-18 | 1999-10-25 | Avl List Gmbh | METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE OPERATING WITH ANY ALTERNATIVE, OR ALSO AUTO, IGNITION |
| AT5140U1 (en) | 2000-10-03 | 2002-03-25 | Avl List Gmbh | METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE |
Family Cites Families (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB465507A (en) * | 1934-09-25 | 1937-05-07 | Tito Brunetti | Feeding process for combustion motors by fuel injection in comburent partially pre-carburetted |
| US2249997A (en) * | 1938-11-12 | 1941-07-22 | Cities Service Oil Co | Internal combustion method |
| JP3906941B2 (en) | 1997-03-17 | 2007-04-18 | 株式会社日本自動車部品総合研究所 | Control device for internal combustion engine |
| JP2000314318A (en) | 1999-04-30 | 2000-11-14 | Nissan Motor Co Ltd | Combustion control device for internal combustion engine |
| JP2001336435A (en) * | 2000-05-24 | 2001-12-07 | Mitsubishi Motors Corp | Six-cycle internal combustion engine |
| JP4134492B2 (en) * | 2000-06-08 | 2008-08-20 | 三菱自動車工業株式会社 | In-cylinder internal combustion engine |
| US6561139B2 (en) * | 2001-10-04 | 2003-05-13 | Evan Guy Enterprises, Inc. | Method and apparatus for reducing emissions of internal combustion engines |
-
2001
- 2001-12-27 AT AT0097901U patent/AT5937U1/en not_active IP Right Cessation
-
2002
- 2002-12-19 EP EP02450288A patent/EP1323908B1/en not_active Expired - Fee Related
- 2002-12-19 DE DE50207286T patent/DE50207286D1/en not_active Expired - Lifetime
- 2002-12-31 US US10/334,153 patent/US6758174B1/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3317128A1 (en) | 1983-05-06 | 1984-11-08 | Leonhard Johann Gerhard Umina New South Wales Pal | Combustion engine |
| DE3406732A1 (en) | 1984-02-24 | 1985-08-29 | Reinhard 3501 Ahnatal Bennedik | Operating process for reciprocating piston internal-combustion engines and combustion engine for this |
| AT3135U1 (en) | 1998-06-18 | 1999-10-25 | Avl List Gmbh | METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE OPERATING WITH ANY ALTERNATIVE, OR ALSO AUTO, IGNITION |
| AT5140U1 (en) | 2000-10-03 | 2002-03-25 | Avl List Gmbh | METHOD FOR OPERATING AN INTERNAL COMBUSTION ENGINE |
Also Published As
| Publication number | Publication date |
|---|---|
| US6758174B1 (en) | 2004-07-06 |
| EP1323908A3 (en) | 2003-10-29 |
| EP1323908B1 (en) | 2006-06-21 |
| US20040123822A1 (en) | 2004-07-01 |
| DE50207286D1 (en) | 2006-08-03 |
| AT5937U1 (en) | 2003-01-27 |
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