FR2781011A1 - Control of operation of turbo-charged IC, by controlling timing of opening inlet valves before exhaust valves are fully closed - Google Patents
Control of operation of turbo-charged IC, by controlling timing of opening inlet valves before exhaust valves are fully closed Download PDFInfo
- Publication number
- FR2781011A1 FR2781011A1 FR9809021A FR9809021A FR2781011A1 FR 2781011 A1 FR2781011 A1 FR 2781011A1 FR 9809021 A FR9809021 A FR 9809021A FR 9809021 A FR9809021 A FR 9809021A FR 2781011 A1 FR2781011 A1 FR 2781011A1
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- FR
- France
- Prior art keywords
- valves
- exhaust
- control method
- turbo
- pressure
- 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
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0253—Fully variable control of valve lift and timing using camless actuation systems such as hydraulic, pneumatic or electromagnetic actuators, e.g. solenoid valves
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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
- F02B17/00—Engines characterised by means for effecting stratification of charge in cylinders
- F02B17/005—Engines characterised by means for effecting stratification of charge in cylinders having direct injection in the combustion chamber
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02D—CONTROLLING COMBUSTION ENGINES
- F02D13/00—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing
- F02D13/02—Controlling the engine output power by varying inlet or exhaust valve operating characteristics, e.g. timing during engine operation
- F02D13/0261—Controlling the valve overlap
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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
- F02B75/00—Other engines
- F02B75/12—Other methods of operation
- F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
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- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Output Control And Ontrol Of Special Type Engine (AREA)
Abstract
Description
La présente invention concerne le domaine des moteurs àThe present invention relates to the field of motors with
combustion interne à 4 temps, suralimentés. 4-stroke internal combustion, supercharged.
La suralimentation peut être réalisée par un turbo-compresseur ou par Supercharging can be achieved by a turbo-compressor or by
un compresseur entraîné tel qu'un compresseur à vis par exemple. a driven compressor such as a screw compressor for example.
Les moteurs suralimentés permettent des réductions de Supercharged engines allow reductions in
consommation au prix toutefois d'une technologie sophistiquée. consumption at the price, however, of sophisticated technology.
De façon connue, les moteurs turbo-compressés récupèrent une partie de l'énergie perdue dans les gaz d'échappement au moyen d'une turbine placée dans le flux de gaz brûlés. Cette énergie est utilisée positivement, pour comprimer l'air d'admission, ce qui augmente le remplissage en air et accroît donc les performances du moteur. Un In known manner, turbo-compressed engines recover part of the energy lost in the exhaust gases by means of a turbine placed in the flow of burnt gases. This energy is used positively, to compress the intake air, which increases the air filling and therefore increases the engine performance. A
compresseur centrifuge couplé à la turbine peut être utilisé à cet effet. centrifugal compressor coupled to the turbine can be used for this purpose.
Le brevet US 4 909 035 illustre un moteur de ce type. US Patent 4,909,035 illustrates an engine of this type.
La turbo-compression conduit bien à une augmentation du rendement du moteur puisque la puissance fournie au compresseur est récupérée sur The turbo-compression does lead to an increase in the efficiency of the engine since the power supplied to the compressor is recovered on
l'énergie des gaz d'échappement.the energy of the exhaust gases.
La turbo-compression constitue le type de suralimentation le plus utilisé actuellement notamment sur les moteurs de moyenne et grosse Turbo-compression is the most widely used type of supercharging, especially on medium and large engines
cylindrées. Ces moteurs ont de bons rendements. displacement. These engines have good yields.
Toutefois un premier problème réside dans le temps de réponse lors d'une accélération. En outre un manque de pression de suralimentation à bas régime est souvent constaté. Par ailleurs une turbine à l'échappement génère forcément une contre-pression défavorable au fonctionement moteur. Ceci modifie la thermique à l'échappement avec par exemple des However, a first problem lies in the response time during an acceleration. In addition, a lack of boost pressure at low revs is often found. Furthermore, an exhaust turbine necessarily generates a backpressure unfavorable to engine operation. This changes the exhaust thermal with, for example,
incidences défavorables sur le temps de mise en action du pot catalytique. unfavorable effects on the time of activation of the catalytic converter.
Les compresseurs entraînés tels que décrits par exemple dans la demande EP 249718 génèrent une bonne pression de suralimentation à bas régime avec un temps de réponse quasi nul. De plus leur implantation est aisée. Les inconvénients classiquement connus des compresseurs mécaniques sont un mauvais rendement notamment à haut régime, un coût The driven compressors as described for example in application EP 249718 generate a good boost pressure at low speed with an almost zero response time. In addition, their implementation is easy. The conventionally known drawbacks of mechanical compressors are poor efficiency, especially at high speed, a cost
important, la génération de bruit. important, the generation of noise.
Par ailleurs, on sait que dans les moteurs suralimentés à allumage commandé et injection indirecte (c'est-à-dire dans le circuit d'admission et non pas dans la chambre de combustion), tout croisement des soupapes est néfaste au fonctionnement du moteur. En effet, un croisement des soupapes signifie une ouverture simultanée des soupapes d'admission et d'échappement, ouverture pendant laquelle une partie du carburant peut être directement court-circuité à l'échappement, sans avoir été brûlé si la pression d'admission est supérieure à celle de l'échappement. Ceci génère Furthermore, it is known that in supercharged engines with positive ignition and indirect injection (that is to say in the intake circuit and not in the combustion chamber), any crossing of the valves is harmful to the operation of the engine. . Indeed, a crossing of the valves means a simultaneous opening of the intake and exhaust valves, opening during which a part of the fuel can be directly short-circuited to the exhaust, without having been burned if the intake pressure is greater than that of the exhaust. This generates
surconsommation et pollution.overconsumption and pollution.
On a donc cherché à éviter ce croisement, à "décroiser" les soupapes c'est-à-dire à ouvrir I'admission uniquement lorsque l'échappement est fermé. Ceci conduit à avoir des taux importants de gaz résiduels dans les chambres de combustion, notamment à bas régime, pleine charge, ce qui We have therefore sought to avoid this crossing, to "uncross" the valves, that is to say to open the intake only when the exhaust is closed. This leads to high levels of residual gases in the combustion chambers, especially at low speed, full load, which
favorise l'apparition de cliquetis sur les moteurs à allumage commandé. promotes the appearance of rattling on spark ignition engines.
Pour éviter le cliquetis, une solution consiste à régler le moteur en "sous avance" à l'allumage ce qui conduit à une perte de rendement du moteur. En outre, le décroisement des soupapes impliquant que des gaz résiduels occupent tout le volume mort cylindre, ce dernier ne peut être utilisé comme volume utile pour la performance. Le remplissage en air du To avoid rattling, one solution is to set the engine to "advance" upon ignition which leads to a loss of engine performance. In addition, the uncrossing of the valves implying that residual gases occupy the entire dead cylinder volume, the latter can not be used as useful volume for performance. The air filling of the
cylindre n'est donc pas optimal.cylinder is therefore not optimal.
La présente invention a notamment pour objectifs - de réduire le taux de gaz résiduels et d'augmenter simultanément le remplissage dans un moteur à allumage commandé, suralimenté. - d'éviter tout risque de rejet de carburant directement dans la ligne d'échappement. Le domaine d'application de l'invention est donc préférentiellement celui des moteurs suralimentés, et plus précisément dans les zones de fonctionnement o la pression de l'air à l'admission (P2) est supérieure à la The objectives of the present invention are in particular to - reduce the rate of residual gases and simultaneously increase the filling in a positive-ignition, supercharged ignition engine. - to avoid any risk of fuel being discharged directly into the exhaust line. The field of application of the invention is therefore preferably that of supercharged engines, and more precisely in the operating zones where the air pressure at the intake (P2) is greater than the
pression (P3) régnant dans la (ou les) tubulures d'échappement. pressure (P3) prevailing in the exhaust manifold (s).
La présente invention a pour objet un procédé de contrôle du fonctionnement d'un moteur à allumage commandé suralimenté et à injection directe d'essence dans la (ou les) chambre(s) de combustion lorsque la pression de l'air dans le circuit d'admission est supérieure à la The present invention relates to a method for controlling the operation of a supercharged spark ignition engine and with direct injection of petrol into the combustion chamber (s) when the air pressure in the circuit d admission is greater than
pression à l'échappement.exhaust pressure.
Selon un mode de réalisation de l'invention, le procédé consiste à réaliser un croisement des soupapes et à asservir le début de l'injection à la quasi-fermeture de l'une au moins des soupapes d'échappement ce qui According to one embodiment of the invention, the method consists in carrying out a crossing of the valves and in controlling the start of the injection to the quasi-closing of at least one of the exhaust valves which
permet d'éviter le court-circuitage du carburant. prevents fuel short-circuiting.
Conformément à un mode de réalisation de l'invention, la In accordance with one embodiment of the invention, the
suralimentation peut être réalisée grâce à un turbo-compresseur. supercharging can be achieved through a turbo-compressor.
Selon un autre mode de réalisation de l'invention, la suralimentation According to another embodiment of the invention, overeating
est réalisée par un compresseur mécanique entraîné. is performed by a driven mechanical compressor.
Préférentiellement, on utilise une distribution variable de type mécanique tel que par exemple, un déphaseur d'arbres à cames, pour Preferably, a mechanical type variable distribution is used such as, for example, a camshaft phase shifter, for
réaliser le croisement des soupapes. cross the valves.
Sans sortir du cadre de l'invention, on peut utiliser un moyen électrohydraulique ou électromagnétique pour réaliser le croisement des soupapes. Ce type de distribution permet d'adapter le fonctionnement Without departing from the scope of the invention, an electro-hydraulic or electromagnetic means can be used to cross the valves. This type of distribution makes it possible to adapt the operation
moteur aux caractéristiques de la suralimentation. engine with turbocharging characteristics.
De façon avantageuse, I'invention est mise en oeuvre pour le Advantageously, the invention is implemented for the
fonctionnement à forte charge et bas régime moteur lorsqu'un turbo- operation at high load and low engine speed when a turbo
compresseur est utilisé.compressor is used.
Dans le cas o un compresseur mécanique est utilisé, le procédé est alors mis en oeuvre pour le fonctionnement à forte charge, quel que soit le In the case where a mechanical compressor is used, the process is then implemented for operation at high load, whatever the
régime moteur.engine speed.
D'autres caractéristiques, détails, avantages de l'invention Other characteristics, details, advantages of the invention
apparaîtront mieux à la lecture de la description qui va suivre, faite à titre will appear better on reading the description which follows, made as
illustratif et nullement limitatif en référence aux planches annexées, sur lesquelles: - La figure 1 est un diagramme pression-volume cylindre obtenu selon l'art antérieur; - La figure 2 est une courbe donnant la levée des soupapes selon l'art antérieur; - La figure 3 est un diagramme pression-volume cylindre obtenu selon l'invention; et - La figure 4 est une courbe donnant la levée des soupapes selon illustrative and in no way limitative with reference to the attached plates, in which: - Figure 1 is a cylinder pressure-volume diagram obtained according to the prior art; - Figure 2 is a curve giving the lifting of the valves according to the prior art; - Figure 3 is a cylinder pressure-volume diagram obtained according to the invention; and - Figure 4 is a curve showing the valve lift according to
I'invention.The invention.
Les figures 1 et 2 concernent donc l'art antérieur. Figures 1 and 2 therefore relate to the prior art.
La figure 1 montre le diagramme classique de la pression dans un cylindre en fonction du volume du cylindre, pour les différents temps d'un cycle moteur. Les 4 temps sont respectivement référencés: (1) admission, (2) compression, (3) détente et (4) échappement. La pression P2 à Figure 1 shows the classic diagram of the pressure in a cylinder as a function of the cylinder volume, for the different times of an engine cycle. The 4 times are respectively referenced: (1) intake, (2) compression, (3) rebound and (4) exhaust. The pressure P2 at
l'admission est ici supérieure à la pression à l'échappement P3. the intake here is greater than the exhaust pressure P3.
La figure 2 montre la levée correspondante des soupapes d'échappement (courbe E) et d'admission (courbe A). On remarque que l'ouverture de l'admission coïncide approximativement avec la fermeture de l'échappement, ceci afin notamment d'éviter le court-circuitage de gaz Figure 2 shows the corresponding lift of the exhaust (curve E) and intake (curve A) valves. It is noted that the opening of the intake coincides approximately with the closing of the exhaust, this in particular in order to avoid the short-circuiting of gas.
imbrûlés à l'échappement comme indiqué en tête de la description. unburnt at the exhaust as indicated at the beginning of the description.
La figure 3 illustre la mise en oeuvre de l'invention. Les phases de détente (3) et de compression (4) sont inchangées vis-à-vis de l'art Figure 3 illustrates the implementation of the invention. The expansion (3) and compression (4) phases are unchanged with respect to the art
antérieur, de même que l'échappement. anterior, as well as the exhaust.
Cependant, la fin de l'échappement (4) et le début de l'admission (1) sont modifiées. Ceci est dû au croisement des soupapes associé à un début However, the end of the exhaust (4) and the start of the intake (1) are modified. This is due to the crossing of the valves associated with a start
d'injection asservi à la fin de l'échappement. injection control at the end of the exhaust.
La figure 4 illustre cette mise en ceuvre: lorsque l'échappement (courbe E') n'est pas encore terminé, l'admission (courbe A') débute; en outre, l'injection I ne débute que lorsque la (ou les) soupapes Figure 4 illustrates this implementation: when the exhaust (curve E ') is not yet finished, the intake (curve A') begins; furthermore, injection I does not start until the valve (s)
d'échappement sont fermées.are closed.
Le croisement des soupapes peut être opéré en retardant l'échappement et/ou en avançant l'admission vis-à-vis du fonctionnement connu. Selon l'invention, c'est-à-dire lorsque la pression d'admission est supérieure à la pression d'échappement, les gaz résiduels sont balayés vers l'échappement lors de la phase de croisement. Par ailleurs, aucun carburant n'est rejeté directement vers l'échappement puisque le début de l'injection n'est réalisé qu'à la fin de la phase de croisement, soit après la fermeture de l'échappement. Le croisement des soupapes selon l'invention, pourra être permanent mais il sera préférentiellement réalisé dans le cadre d'une distribution The crossing of the valves can be operated by delaying the exhaust and / or by advancing the intake with respect to the known operation. According to the invention, that is to say when the intake pressure is higher than the exhaust pressure, the residual gases are swept towards the exhaust during the crossing phase. Furthermore, no fuel is discharged directly to the exhaust since the start of the injection is only carried out at the end of the crossing phase, that is to say after the exhaust is closed. The crossing of the valves according to the invention may be permanent, but it will preferably be carried out within the framework of a distribution.
variable, sur certaines zones de fonctionnement. variable, on certain operating zones.
La distribution variable peut être de type mécanique: elle sera alors The variable distribution can be mechanical: it will then be
par exemple obtenue grâce à un déphaseur d'arbre à cames. for example obtained by means of a camshaft phase shifter.
Sans sortir du cadre de l'invention, la distribution pourra être Without departing from the scope of the invention, the distribution may be
totalement variable: des systèmes électrohydrauliques ou électro- fully variable: electrohydraulic or electro-
magnétiques peuvent alors être utilisés. magnetic can then be used.
Claims (5)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
FR9809021A FR2781011B1 (en) | 1998-07-13 | 1998-07-13 | METHOD FOR CONTROLLING THE OPERATION OF A DIRECT FUEL INJECTION FUEL ENGINE |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
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FR9809021A FR2781011B1 (en) | 1998-07-13 | 1998-07-13 | METHOD FOR CONTROLLING THE OPERATION OF A DIRECT FUEL INJECTION FUEL ENGINE |
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FR2781011A1 true FR2781011A1 (en) | 2000-01-14 |
FR2781011B1 FR2781011B1 (en) | 2001-01-12 |
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FR9809021A Expired - Fee Related FR2781011B1 (en) | 1998-07-13 | 1998-07-13 | METHOD FOR CONTROLLING THE OPERATION OF A DIRECT FUEL INJECTION FUEL ENGINE |
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Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2841294A1 (en) | 2002-06-21 | 2003-12-26 | Inst Francais Du Petrole | Control method for motor vehicle supercharged fuel injection internal combustion engine involves two staged air and fuel air feed into combustion chamber |
WO2004055347A1 (en) * | 2002-12-17 | 2004-07-01 | Siemens Aktiengesellschaft | Method for heating an exhaust gas catalyst for an internal combustion engine operating with direct fuel injection |
EP1489280A1 (en) * | 2003-06-18 | 2004-12-22 | Institut Francais Du Petrole | Engine and operating method for a supercharged four stroke engine |
WO2005035958A1 (en) * | 2003-10-06 | 2005-04-21 | Fev Motorentechnik Gmbh | Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range |
EP1591646A1 (en) * | 2004-04-27 | 2005-11-02 | GM Global Technology Operations, Inc. | Operating method for Ottomotor with valve overlap |
FR2879258A1 (en) * | 2004-12-13 | 2006-06-16 | Renault Sas | Supercharged external injection internal combustion engine controlling method, involves increasing fuel injection pressure at engine`s high load and low speed state relative to stable functioning state of engine at heat and partial load |
US7783410B2 (en) * | 2007-07-18 | 2010-08-24 | Curtis O. Anderson | Engine process |
US8100099B2 (en) | 2004-05-13 | 2012-01-24 | Audi, Ag | Method for operating an internal combustion engine, and internal combustion engine for carrying out said method |
CN101042085B (en) * | 2006-03-20 | 2013-10-30 | 福特环球技术公司 | System and method for boosted direct injection engine |
US9010111B2 (en) | 2009-04-29 | 2015-04-21 | Fev Gmbh | Compressor comprising a swirl generator, for a motor vehicle |
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EP0249718A2 (en) | 1986-06-20 | 1987-12-23 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Turbo-charged internal-combustion engine and intake air cooling arrangement |
US4909035A (en) | 1985-02-25 | 1990-03-20 | Mazda Motor Corporation | Control system for a turbo-supercharger of an internal combustion engine |
JPH0486355A (en) * | 1990-07-30 | 1992-03-18 | Toyota Motor Corp | Fuel injection internal combustion engine |
JPH04183945A (en) * | 1990-11-19 | 1992-06-30 | Toyota Motor Corp | Cylinder direct injection type spark ignition engine |
WO1997013063A1 (en) * | 1995-10-02 | 1997-04-10 | Hitachi, Ltd. | Control device for an internal combustion engine |
JPH09287487A (en) * | 1996-04-25 | 1997-11-04 | Nissan Motor Co Ltd | Cylinder direct injection internal combustion engine |
-
1998
- 1998-07-13 FR FR9809021A patent/FR2781011B1/en not_active Expired - Fee Related
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US4909035A (en) | 1985-02-25 | 1990-03-20 | Mazda Motor Corporation | Control system for a turbo-supercharger of an internal combustion engine |
EP0249718A2 (en) | 1986-06-20 | 1987-12-23 | Dr.Ing.h.c. F. Porsche Aktiengesellschaft | Turbo-charged internal-combustion engine and intake air cooling arrangement |
JPH0486355A (en) * | 1990-07-30 | 1992-03-18 | Toyota Motor Corp | Fuel injection internal combustion engine |
JPH04183945A (en) * | 1990-11-19 | 1992-06-30 | Toyota Motor Corp | Cylinder direct injection type spark ignition engine |
WO1997013063A1 (en) * | 1995-10-02 | 1997-04-10 | Hitachi, Ltd. | Control device for an internal combustion engine |
EP0854280A1 (en) * | 1995-10-02 | 1998-07-22 | Hitachi, Ltd. | Control device for an internal combustion engine |
JPH09287487A (en) * | 1996-04-25 | 1997-11-04 | Nissan Motor Co Ltd | Cylinder direct injection internal combustion engine |
Non-Patent Citations (3)
Title |
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PATENT ABSTRACTS OF JAPAN vol. 16, no. 311 (M - 1277) 8 July 1992 (1992-07-08) * |
PATENT ABSTRACTS OF JAPAN vol. 16, no. 498 (M - 1325) 15 October 1992 (1992-10-15) * |
PATENT ABSTRACTS OF JAPAN vol. 98, no. 3 27 February 1998 (1998-02-27) * |
Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
FR2841294A1 (en) | 2002-06-21 | 2003-12-26 | Inst Francais Du Petrole | Control method for motor vehicle supercharged fuel injection internal combustion engine involves two staged air and fuel air feed into combustion chamber |
WO2004055347A1 (en) * | 2002-12-17 | 2004-07-01 | Siemens Aktiengesellschaft | Method for heating an exhaust gas catalyst for an internal combustion engine operating with direct fuel injection |
US7155899B2 (en) | 2002-12-17 | 2007-01-02 | Siemens Aktiengesellschaft | Method for heating an exhaust gas catalyst for an internal combustion engine operating with direct fuel injection |
EP1489280A1 (en) * | 2003-06-18 | 2004-12-22 | Institut Francais Du Petrole | Engine and operating method for a supercharged four stroke engine |
FR2856429A1 (en) * | 2003-06-18 | 2004-12-24 | Inst Francais Du Petrole | METHOD FOR COMBUSTION OF A FUEL-FOUR-STROKE ENGINE AND ENGINE USING SUCH A METHOD |
US7159560B2 (en) | 2003-06-18 | 2007-01-09 | Institut Francais Du Petrole | Supercharged four-stroke engine combustion method and engine using such a method |
WO2005035958A1 (en) * | 2003-10-06 | 2005-04-21 | Fev Motorentechnik Gmbh | Method for optimizing the operation of a charged reciprocating internal combustion engine in the lower engine speed range |
EP1591646A1 (en) * | 2004-04-27 | 2005-11-02 | GM Global Technology Operations, Inc. | Operating method for Ottomotor with valve overlap |
US8100099B2 (en) | 2004-05-13 | 2012-01-24 | Audi, Ag | Method for operating an internal combustion engine, and internal combustion engine for carrying out said method |
FR2879258A1 (en) * | 2004-12-13 | 2006-06-16 | Renault Sas | Supercharged external injection internal combustion engine controlling method, involves increasing fuel injection pressure at engine`s high load and low speed state relative to stable functioning state of engine at heat and partial load |
CN101042085B (en) * | 2006-03-20 | 2013-10-30 | 福特环球技术公司 | System and method for boosted direct injection engine |
US7783410B2 (en) * | 2007-07-18 | 2010-08-24 | Curtis O. Anderson | Engine process |
US9010111B2 (en) | 2009-04-29 | 2015-04-21 | Fev Gmbh | Compressor comprising a swirl generator, for a motor vehicle |
Also Published As
Publication number | Publication date |
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