EP2370687A1 - Internal combustion engine - Google Patents

Internal combustion engine

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Publication number
EP2370687A1
EP2370687A1 EP09756322A EP09756322A EP2370687A1 EP 2370687 A1 EP2370687 A1 EP 2370687A1 EP 09756322 A EP09756322 A EP 09756322A EP 09756322 A EP09756322 A EP 09756322A EP 2370687 A1 EP2370687 A1 EP 2370687A1
Authority
EP
European Patent Office
Prior art keywords
valve
injection
inlet
internal combustion
injection valve
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.)
Granted
Application number
EP09756322A
Other languages
German (de)
French (fr)
Other versions
EP2370687B1 (en
Inventor
Michael Baeuerle
Alexander Schenck Zu Schweinsberg
Klaus Ries-Mueller
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2370687A1 publication Critical patent/EP2370687A1/en
Application granted granted Critical
Publication of EP2370687B1 publication Critical patent/EP2370687B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/043—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit upstream of an air throttle valve
    • 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
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/042—Positioning of injectors with respect to engine, e.g. in the air intake conduit
    • F02M69/044—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into the intake conduit downstream of an air throttle valve

Definitions

  • the invention relates to an internal combustion engine, according to the preamble of claim 1.
  • JP-10196440 A injects the first injection valve upstream of a throttle inserted into the intake duct for air flow control and the second injection valve downstream of the throttle valve respectively in the intake passage of the internal combustion engine, wherein the injection of the second injection valve in time before Injection is made by the first injection valve.
  • the internal combustion engine according to the invention with the features of claim 1 has the advantage that with the two injected into the intake passage of the at least one combustion cylinder, differently designed injection valves, the fuel input in the direction of intake valve can be performed in different ways, in different
  • the injection valves are electrically controllable solenoid valves.
  • Such solenoid valves are significantly less expensive than commonly used piezoelectric injectors.
  • Fig. 1 detail a longitudinal section of a combustion cylinder a
  • Fig. 2 is a diagram for driving areas of the injection valves of
  • FIG. 3 shows a detail of a plan view in the direction of arrow III in FIG. 2 with injection valves inserted into an intake passage of the internal combustion engine
  • FIG. 6 is a similar view as in Fig. 3 of another embodiment of a combustion cylinder
  • Fig. 8 is a section along the line VIII - VIII in Figure 6.
  • a combustion cylinder 11 is shown in fragmentary longitudinal section in Fig. 1 schematically.
  • the outside of a cooling water jacket 12 surrounded combustion cylinder 11 is frontally covered by a cylinder head 13 gas-tight.
  • a in the combustion cylinder 11 axially displaceable guided reciprocating piston 14 is limited together with the cylinder head 13, a combustion chamber 15.
  • the reciprocating piston 14 is connected via a connecting rod 16 with a crankshaft, not shown here, act on the piston and the other combustion cylinder.
  • the combustion chamber 15 has an inlet 18 closable with an inlet valve 17 and an outlet 20 closable with an outlet valve 19.
  • a combustion air intake duct 21 is guided, which is composed of an inlet duct 22 formed in the cylinder head 13 and a suction duct 23 attached to the inlet duct 22.
  • the suction pipes 23 of a plurality of combustion cylinders 11 are combined by means of a Saugrohrkrümmers to an air intake in which an air quantity control member, preferably a throttle valve is arranged to regulate the air flow.
  • the throttle valve 36 is shown in the suction tube 23 of a combustion cylinder 11 only for clarity.
  • an exhaust duct 24 is removed, which consists of an exhaust duct 25 formed in the cylinder head 13 and an exhaust pipe 26 attached to the exhaust duct 25.
  • the exhaust pipes 26 of a plurality of combustion cylinders 11 are combined downstream via an exhaust manifold.
  • a fuel injection device 27 For fuel supply to the combustion chamber 15 of the at least one combustion cylinder 11, a fuel injection device 27 is provided which has two electromagnetic injection valves 28, 29 per combustion cylinder 11 or per combustion chamber 15.
  • the two injection valves 28, 29 are supplied with fuel by a fuel pump 31 which delivers fuel from a fuel tank 30 and is controlled by an electronic control unit 32, which is supplied with a plurality of parameters defining the operating points of the internal combustion engine.
  • the two injection valves 28, 29 are downstream of the throttle valve 36 in the intake passage 21, here in the suction tube 23, held insertion 33,37 (Fig. 3 to 5) inserted so that they can inject fuel into the intake passage 21, wherein the fuel sprayed in the form of spray cones from the injection valves 28, 29 is sprayed.
  • the two injectors 28, 29 arranged as close as possible to the inlet valve 17 are aligned so that their spray cones are directed towards the inlet valve 17.
  • the two injection valves 28, 29 are formed differently both in terms of fuel flow and in terms of the formation of the sprayed-off fuel spray cone.
  • the first injection valve 28 injects a wide-spread spray cone 34 (FIG. 5) with a large cone angle and the second injection valve 29 clearly sprays a spray cone 35 (FIG. 4) which is only slightly fanned out smaller cone angle.
  • the spray cone 35 of the second injection valve 29 has a much greater penetration, so it can penetrate much deeper into the combustion chamber 15 with open inlet valve 17 as the spray cone 34 of the first injection valve 28 with much smaller penetration.
  • the second injection valve 29 is also designed in comparison to the first injection valve 28 for a significantly larger fuel flow and can, for. B at least 70% of the full load amount.
  • the Einstecköffhung 33 for the first injection valve 28 has a slightly greater distance from the inlet 18, as the Einstecgroffhung 37 for the second injection valve 29 so that the Abspritzöffhung the first injector 28 is slightly further away from the inlet valve 17 as the Abspritzöffhung the second Injector 29.
  • An equal spacing arrangement of the two Einstecköffhungen 33, 37 from the inlet 18 is also possible.
  • the combustion chamber 15 with cylinder head 13 is modified to the extent that two inlets 18, 18 'are present, each of which is provided by an inlet valve 17 or 17'. are closable.
  • a first combustion air intake duct 21 is guided (FIG. 7)
  • a second combustion air intake duct 21' is guided (FIG. 8).
  • the fuel supply of the combustion chamber 15 takes place in the same manner as described above in connection with FIG. 1.
  • the first injection valve 28 is inserted in the same manner near the inlet valve 17 into an insertion opening 33 held in the first intake passage 21, again here in the intake pipe 23, in order to inject fuel into the first intake passage 21.
  • the second injection valve 29 is inserted in the same manner near the second inlet valve 17 'in a in the second intake passage 21', here again in the intake pipe 23 'held insertion opening 37 to inject fuel into the second intake passage 21'.
  • Both injectors 28, 29 are formed as described above and in turn aligned so that their spray cone 34, 35 is directed to the respectively associated inlet valve 17 and 17 '. As can be seen from FIGS.
  • the opening cross-section of the two inlets 18, 18 'in the combustion chamber 15 of the combustion cylinder 11 varies in size.
  • the first injection valve 28 is assigned to the first intake passage 21 leading to the smaller-diameter first intake 18, while the second injection valve 29 is injected into the second intake passage 21 'leading to the larger-cross-sectional second intake 18'.
  • the cross sections of the two intake passages 21, 21 ', more precisely the cross sections of the intake passages 22, 22 'in the cylinder head 13, can be the same size, but - as shown in Fig. 6 to 8 - also be different sizes, wherein the first intake passage 21, in which injects the first injection valve 28, the smaller diameter having.
  • the two inlet valves 17, 17 ' may have a different valve lift.
  • the assignment of the two injection valves 28, 29 to the intake valves 17, 17 ' is then made such that the first injection valve 28 is associated with the intake valve 17 with the smaller valve lift and the second injection valve 29 with the intake valve 17' with the larger valve lift.
  • one of the inlet valves 17, 17 ' is provided with a valve mask and the first injection valve 28 injects into the intake passage leading to the intake valve with valve masking.
  • the two injection valves 28, 29 at different distances from the respective associated inlet valve 17 or 17 'in the intake channel 21 or in the exemplary embodiment in FIGS. 21 ' may be arranged.
  • the first injection valve 28 has a slightly greater distance from the first inlet valve 17 than the second injection valve 29 from the second inlet valve 17 '.
  • the two injection valves 28, 29 are controlled differently per combustion cylinder 11 by the electronic control unit 32 as a function of the operating points of the internal combustion engine.
  • a diagram is stored in the control unit 32, as shown schematically in FIG.
  • the hatched area marked 40 in the diagram shows the range of small partial load, in which only the first injection valve 28 is used for fuel introduction into the combustion chamber 15.
  • the cross-hatched area marked 41 serves for scavenging, in which only the second injection valve 29 with a small spray cone 35 and high penetration is activated, which does not generate any appreciable wall film in front of the inlet 18 of the combustion chamber 15.
  • both injection valves 28, 29 are activated for fuel injection.
  • the two intake valves 17, 17 'per combustion chamber 15 on time staggered opening phases.
  • the injectors 28, 29 are then associated with the intake valves 17, 17 'in such a manner that the first intake valve 28 is disposed in the intake passage 21 leading to the earlier-opening intake valve 17 and the second injection valve 29 is disposed in the later-opening intake valve 17' ,
  • the first injection valve 17 can be controlled by the control electronics 32 so that it sprays fuel only at a time to which the second inlet valve 17 'public, so an overlap of the open inlet 13, 13' and Outlet 20 of the combustion chamber 15 is safely excluded.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

The invention relates to an internal combustion engine that comprises at least one combustion chamber (15), which can be closed by an intake valve (17), at least one air intake channel (21), which leads to the intake valve (17), and a fuel injection device (27), which in association with the at least one combustion chamber (15) has a first and a second injection valve (28, 29) for injecting fuel into at least one intake channel (21) in a metered manner. In order to achieve a significantly improved mixture preparation and combustion of the fuel-air mixture in the combustion chamber (15), the two injection valves (28, 29) are designed so that the first injection valve (28) sprays a widely spread spray cone (34) having a large cone angle and the second injection valve (29) sprays an only slightly spread spray cone (35) having a significantly smaller cone angle.

Description

Beschreibung description
Titel BrennkraftmaschineTitle internal combustion engine
Stand der TechnikState of the art
Die Erfindung geht aus von einer Brennkraftmaschine, nach dem Oberbegriff des Anspruchs 1.The invention relates to an internal combustion engine, according to the preamble of claim 1.
Bei einer bekannten Kraftstoffeinspritzvorrichtung für eine Brennkraftmaschine (JP-10196440 A) spritzt das erste Einspritzventil stromaufwärts einer in den Ansaugkanal zur Luftmengenregelung eingesetzten Drosselklappe und das zweite Einspritzventil stromabwärts der Drosselklappe jeweils in den Ansaugkanal der Brennkraftmaschine ein, wobei die Einspritzung des zweiten Einspritzventils zeitlich vor der Einspritzung durch das erste Einspritzventil vorgenommen wird.In a known fuel injection device for an internal combustion engine (JP-10196440 A) injects the first injection valve upstream of a throttle inserted into the intake duct for air flow control and the second injection valve downstream of the throttle valve respectively in the intake passage of the internal combustion engine, wherein the injection of the second injection valve in time before Injection is made by the first injection valve.
Offenbarung der ErfindungDisclosure of the invention
Die erfindungsgemäße Brennkraftmaschine mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass mit den beiden in den Ansaugkanal des mindestens einen Verbrennungszylinders einspritzenden, unterschiedlich konzipierten Einspritzventile der Kraftstoffeintrag in Richtung Einlassventil in unterschiedlicher Weise durchgeführt werden kann, die in unterschiedlichenThe internal combustion engine according to the invention with the features of claim 1 has the advantage that with the two injected into the intake passage of the at least one combustion cylinder, differently designed injection valves, the fuel input in the direction of intake valve can be performed in different ways, in different
Betriebsbereichen der Brennkraftmaschine zu einer deutlich verbesserten Gemischaufbereitung und Verbrennung führt. So ist es von Vorteil, bei betriebswarmer Brennkraftmaschine und hoher Last den Kraftstoff mit hoher Penetration bei geöffnetem Einlassventil direkt in den Brennraum einzuspritzen, während bei kalter Brennkraftmaschine eine starke Wandbenetzung des dem Einlassventil unmittelbar vorgeordneten Wandbereichs des Ansaugkanals zu einer besserenOperating areas of the internal combustion engine leads to a significantly improved mixture preparation and combustion. Thus, it is advantageous to inject the fuel with high penetration at an open inlet valve directly into the combustion chamber at high operating temperature engine and high load, while in cold engine strong wall wetting of the inlet valve immediately upstream wall portion of the intake duct to a better
Verbrennung führt, da der Wandfilm erst zeitlich versetzt in den Brennraum gelangt. Durch die erfindungsgemäß unterschiedliche Konzeption der beiden Einspritzventile lässt sich diese betriebspunktabhängige Optimierung der Verbrennung durch unterschiedliche Ansteuerung der beiden Einspritzventile in unterschiedlichen Betriebsbreichen der Brennkraftmaschine in einfacher Weise erreichen. So kann durch die Nutzung der beiden Einspritzventile in unterschiedlicher Weise in unterschiedlichen Betriebsbereichen die Lambda- Verteilung im Brennraum optimiert, lokale Überfettung, die verbunden ist mit hohen Kohlenwasserstoff (HC)-Anfall, und lokale Ausmagerung, die ein Klopfen der Brennkraftmaschine begünstigt, vermieden, sowie ein reduzierter Kraftstoffverbrauch erzielt werden. So kann z.B. im Kaltstart durch Einsatz des ersten Einspritzventils infolge der kleineren Kraftstofftröpfchen in dessen Spraykegel die Gemischaufbereitung verbessert und die HC-Emissionen reduziert werden. Bei Volllast wird durch stärke Nutzung des zweiten Einspritzventils mit der größeren Penetration bis in den Brennraum und mit minimierter Wandfilmerzeugung im Ansaugkanal die Verdampfungswärme des Kraftstoffs stärker der Zylinderladung als der Wandung des Ansaugkanals entnommen, womit die Zylinderladung stärker abkühlt und die Klopfempfindlichkeit abnimmt.Combustion results because the wall film only reaches the combustion chamber at a later stage. By virtue of the different conception of the two injection valves according to the invention, this operating point-dependent optimization of the combustion can be simplified by different activation of the two injection valves in different operating ranges of the internal combustion engine Reach way. Thus, by using the two injectors differently in different operating ranges optimizes the Lambda distribution in the combustion chamber, local superfatting, which is associated with high hydrocarbon (HC) incidence, and local Ausmagerung, which favors a knocking of the internal combustion engine, avoided and a reduced fuel consumption can be achieved. For example, in the cold start by using the first injection valve as a result of the smaller fuel droplets in the spray cone, the mixture preparation improved and the HC emissions can be reduced. At full load is used by strong use of the second injector with the greater penetration into the combustion chamber and minimized Wandfilhmzeugung in the intake manifold, the heat of vaporization of the fuel more of the cylinder charge than the wall of the intake channel, whereby the cylinder charge cools more and the knock sensitivity decreases.
Bei aufgeladenen Brennkraftmaschinen ist die Nutzung des sog. Scavenging ohne eines direkt in den Brennraum einspritzenden Einspritzventils möglich, da das zweite Einspritzventil angesichts des kleinen Kegelwinkels seines Spraykegels keinen oder eines nur minimalen Wandfilm imIn supercharged internal combustion engines, the use of the so-called. Scavenging is possible without injecting directly into the combustion chamber injection valve, since the second injection valve in view of the small cone angle of its spray cone no or a minimal wall film in
Ansaugkanal erzeugt. Beim Spülen des Brennraums mit Luft (Scavenging) gelangt damit kein oder nur wenig Kraftstoff in den Brennraum in Richtung Katalysator. Scavenging ist mit erträglicher Belastung für den Katalysator realisierbar und führt in Verbindung mit Turboaufladung zu einem deutlichen Drehmomentgewinn bei kleinen Drehzahlen.Intake channel generated. When flushing the combustion chamber with air (scavenging) so that little or no fuel enters the combustion chamber in the direction of the catalyst. Scavenging can be realized with tolerable load for the catalytic converter and, in conjunction with turbocharging, leads to a significant torque gain at low speeds.
Im Motorauslauf kann durch Heranziehen des zweiten Einspritzventils der Wandfilm im Ansaugkanal minimiert werden, so dass beim Neustart der Brennkraftmaschine, insbesondere bei Start/Stopp-Anwendungen, die Schadstoffemissionen reduziert werden.In the engine outlet can be minimized by using the second injection valve of the wall film in the intake passage, so that when restarting the internal combustion engine, especially in start / stop applications, the pollutant emissions are reduced.
Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Kraftstoffeinspritzvorrichtung möglich.The measures listed in the further claims advantageous refinements and improvements of the claim 1 fuel injection device are possible.
Mit den in diesen Ansprüchen angegebenen unterschiedlichen Ausführungen der Einspritzventile und/oder der Einlassventile bei einem Brennraum mit zwei jeweils einen Einlass verschließenden Einlassventilen und durch die spezielle Zuordnung von Einlassventil und Einspritzventil können in Verbindung mit einer getrennten Ansteuerung der Einspritzventile die vorstehend beschriebenen Effekte der Reduzierung der Klopfneigung, Optimierung des Verbrennungsgemischs mit Vermeidung lokaler Überfettung und lokaler Ausmagerung und Verbrauchsreduzierung graduell verbessert werden. Gemäß einer vorteilhaften Ausführungsform der Erfindung sind die Einspritzventile elektrisch ansteuerbare Magnetventile. Solche Magnetventile sind deutlich kostengünstiger als häufig verwendete piezoelektrische Einspritzventile.With the different embodiments of the injection valves and / or the intake valves in a combustion chamber with two inlet valves closing each inlet and by the special allocation of inlet valve and injection valve, the above-described effects of the reduction of the injection valves can be described in connection with a separate activation of the injection valves Tapping tendency, optimization of the combustion mixture with prevention of local over-greasing and local Ausmagerung and consumption reduction gradually improved. According to an advantageous embodiment of the invention, the injection valves are electrically controllable solenoid valves. Such solenoid valves are significantly less expensive than commonly used piezoelectric injectors.
Kurze Beschreibung der ZeichnungenBrief description of the drawings
Die Erfindung ist anhand eines in den Zeichnungen dargestellten Ausführungsbeispiels in der nachfolgenden Beschreibung näher erläutert. Es zeigen in schematischer Darstellung:The invention is explained in more detail in the following description with reference to an embodiment shown in the drawings. In a schematic representation:
Fig. 1 ausschnittweise einen Längsschnitt eines Verbrennungszylinders einerFig. 1 detail a longitudinal section of a combustion cylinder a
Brennkraftmaschine in Verbindung mit einer Kraftstoffeinspritzvorrichtung,Internal combustion engine in conjunction with a fuel injection device,
Fig. 2 ein Diagramm für Ansteuerungsbereiche der Einspritzventile derFig. 2 is a diagram for driving areas of the injection valves of
Kraftstoffeinspritzvorrichtung in Fig. 1 in Zuordnung zu durch Drehzahl (n) und Last (L) festgelegten Betriebspunkten der Brennkraftmaschine,1 in association with operating points of the internal combustion engine defined by rotational speed (n) and load (L),
Fig. 3 ausschnittweise eine Draufsicht in Richtung Pfeil III in Fig. 2 bei in einen Ansaugkanal der Brennkraftmaschine eingesetzten Einspritzventilen,3 shows a detail of a plan view in the direction of arrow III in FIG. 2 with injection valves inserted into an intake passage of the internal combustion engine, FIG.
Fig. 4 einen Schnitt längs der Linie IV - IV in Fig. 3,4 is a section along the line IV - IV in Fig. 3,
Fig. 5 einen Schnitt längs der Linie V - V in Fig. 3,5 shows a section along the line V - V in Fig. 3,
Fig. 6 eine gleiche Darstellung wie in Fig. 3 eines weiteren Ausführungsbeispiels eines Verbrennungszylinders,6 is a similar view as in Fig. 3 of another embodiment of a combustion cylinder,
Fig. 7 einen Schnitt längs der Linie VII - VII in Fig. 6,7 is a section along the line VII - VII in Fig. 6,
Fig. 8 einen Schnitt längs der Linie VIII - VIII in Fig.6.Fig. 8 is a section along the line VIII - VIII in Figure 6.
Von einer üblicherweise mehrzylindrigen Brennkraftmaschine für z.B. Kraftfahrzeuge ist in Fig. 1 lediglich ein Verbrennungszylinder 11 ausschnittweise im Längsschnitt schematisiert dargestellt. Der außen mit einem Kühlwassermantel 12 umgebene Verbrennungszylinder 11 ist stirnseitig von einem Zylinderkopf 13 gasdicht abgedeckt. Ein im Verbrennungszylinder 11 axial verschieblich geführter Hubkolben 14 begrenzt zusammen mit dem Zylinderkopf 13 einen Brennraum 15. Der Hubkolben 14 ist über ein Pleuel 16 mit einer hier nicht dargestellten Kurbelwelle verbunden, auf die auch die Hubkolben der anderen Verbrennungszylinder wirken.From a usually mehrzylindrigen engine for eg motor vehicles, only a combustion cylinder 11 is shown in fragmentary longitudinal section in Fig. 1 schematically. The outside of a cooling water jacket 12 surrounded combustion cylinder 11 is frontally covered by a cylinder head 13 gas-tight. A in the combustion cylinder 11 axially displaceable guided reciprocating piston 14 is limited together with the cylinder head 13, a combustion chamber 15. The reciprocating piston 14 is connected via a connecting rod 16 with a crankshaft, not shown here, act on the piston and the other combustion cylinder.
Der Brennraum 15 weist in einem in Verbindung mit Fig. 1 in Fig. 3 bis 5 illustrierten ersten Ausführungsbeispiel einen mit einem Einlassventil 17 verschließbaren Einlass 18 und einen mit einem Auslassventil 19 verschließbaren Auslass 20 auf. Zu dem Einlass 18 ist ein Ansaugkanal 21 für Verbrennungsluft geführt, der aus einem im Zylinderkopf 13 ausgeformten Einlasskanal 22 und einem an den Einlasskanal 22 angesetzten Saugrohr 23 zusammengesetzt ist. Stromaufwärts sind üblicherweise die Saugrohre 23 mehrerer Verbrennungszylinder 11 mittels eines Saugrohrkrümmers zu einem Luftansaugstutzen zusammengefasst, in dem ein Luftmengensteuerorgan, vorzugsweise eine Drosselklappe, zur Luftmengenregulierung angeordnet ist. In Fig. 1 ist lediglich zur Verdeutlichung die Drosselklappe 36 in das Saugrohr 23 des einen Verbrennungszylinders 11 eingezeichnet. Vom Auslass 20 ist ein Abgaskanal 24 abgeführt, der aus einem im Zylinderkopf 13 ausgebildeten Auslasskanal 25 und einem an den Auslasskanal 25 angesetzten Abgasrohr 26 besteht. Die Abgasrohre 26 mehrerer Verbrennungszylinder 11 sind stromabwärts über einen Abgaskrümmer zusammengefasst.In a first exemplary embodiment illustrated in conjunction with FIG. 1 in FIGS. 3 to 5, the combustion chamber 15 has an inlet 18 closable with an inlet valve 17 and an outlet 20 closable with an outlet valve 19. To the inlet 18 a combustion air intake duct 21 is guided, which is composed of an inlet duct 22 formed in the cylinder head 13 and a suction duct 23 attached to the inlet duct 22. Upstream usually the suction pipes 23 of a plurality of combustion cylinders 11 are combined by means of a Saugrohrkrümmers to an air intake in which an air quantity control member, preferably a throttle valve is arranged to regulate the air flow. In Fig. 1, the throttle valve 36 is shown in the suction tube 23 of a combustion cylinder 11 only for clarity. From the outlet 20, an exhaust duct 24 is removed, which consists of an exhaust duct 25 formed in the cylinder head 13 and an exhaust pipe 26 attached to the exhaust duct 25. The exhaust pipes 26 of a plurality of combustion cylinders 11 are combined downstream via an exhaust manifold.
Zur Kraftstoffversorgung des Brennraums 15 des mindestens einen Verbrennungszylinders 11 ist eine Kraftstoffeinspritzvorrichtung 27 vorgesehen, die pro Verbrennungszylinder 11 bzw. pro Brennraum 15 zwei elektromagnetische Einspritzventile 28, 29 aufweist. Die beiden Einspritzventile 28, 29 werden von einer Kraftstoff aus einem Kraftstofftank 30 fördernden Kraftstoffpumpe 31 mit Kraftstoff versorgt und von einer elektronischen Steuereinheit 32, der eine Vielzahl von die Betriebspunkte der Brennkraftmaschine festlegende Parameter zugeführt sind, gesteuert. Die beiden Einspritzventile 28, 29 sind stromabwärts der Drosselklappe 36 in in dem Ansaugkanal 21, hier im Saugrohr 23, vorgehaltene Einstecköffhungen 33,37 (Fig. 3 bis 5) so eingesetzt, dass sie Kraftstoff in den Ansaugkanal 21 einzuspritzen vermögen, wobei der Kraftstoff zerstäubt in Form von Spraykegeln von den Einspritzventilen 28, 29 abgespritzt wird. Die beiden möglichst nahe des Einlassventils 17 angeordneten Einspritzventile 28, 29 sind so ausgerichtet, dass ihre Spraykegel auf das Einlassventil 17 gerichtet sind. Die beiden Einspritzventile 28, 29 sind sowohl hinsichtlich des Kraftstoffdurchflusses als auch hinsichtlich der Ausbildung des abgespritzten Kraftstoff-Spraykegels unterschiedlich ausgebildet. Das erste Einspritzventil 28 spritzt einen breit aufgefächerten Spraykegel 34 (Fig. 5) mit einem großen Kegelwinkel und das zweite Einspritzventil 29 einen nur wenig aufgefächerten Spraykegel 35 (Fig. 4) mit deutlich kleinerem Kegelwinkel ab. Dabei hat der Spraykegel 35 des zweiten Einspritzventils 29 eine deutlich größere Penetration, kann also bei geöffnetem Einlassventil 17 wesentlich tiefer in den Brennraum 15 eindringen als der Spraykegel 34 des ersten Einspritzventils 28 mit deutlich kleinerer Penetration. Das zweite Einspritzventils 29 ist außerdem im Vergleich zum ersten Einspritzventil 28 für einen deutlich größeren Kraftstoffdurchfluss ausgelegt und vermag z. B mindestens 70% der Volllastmenge abzuspritzen. Im dargestellten Ausführungsbeispiel hat die Einstecköffhung 33 für das erste Einspritzventil 28 einen etwas größeren Abstand vom Einlass 18, als die Einstecköffhung 37 für das zweite Einspritzventil 29, so dass die Abspritzöffhung des ersten Einspritzventils 28 vom Einlassventil 17 etwas weiter entfernt ist als die Abspritzöffhung des zweiten Einspritzventils 29. Eine gleiche Abstandsanordnung der beiden Einstecköffhungen 33, 37 vom Einlass 18 ist ebenfalls möglich.For fuel supply to the combustion chamber 15 of the at least one combustion cylinder 11, a fuel injection device 27 is provided which has two electromagnetic injection valves 28, 29 per combustion cylinder 11 or per combustion chamber 15. The two injection valves 28, 29 are supplied with fuel by a fuel pump 31 which delivers fuel from a fuel tank 30 and is controlled by an electronic control unit 32, which is supplied with a plurality of parameters defining the operating points of the internal combustion engine. The two injection valves 28, 29 are downstream of the throttle valve 36 in the intake passage 21, here in the suction tube 23, held insertion 33,37 (Fig. 3 to 5) inserted so that they can inject fuel into the intake passage 21, wherein the fuel sprayed in the form of spray cones from the injection valves 28, 29 is sprayed. The two injectors 28, 29 arranged as close as possible to the inlet valve 17 are aligned so that their spray cones are directed towards the inlet valve 17. The two injection valves 28, 29 are formed differently both in terms of fuel flow and in terms of the formation of the sprayed-off fuel spray cone. The first injection valve 28 injects a wide-spread spray cone 34 (FIG. 5) with a large cone angle and the second injection valve 29 clearly sprays a spray cone 35 (FIG. 4) which is only slightly fanned out smaller cone angle. In this case, the spray cone 35 of the second injection valve 29 has a much greater penetration, so it can penetrate much deeper into the combustion chamber 15 with open inlet valve 17 as the spray cone 34 of the first injection valve 28 with much smaller penetration. The second injection valve 29 is also designed in comparison to the first injection valve 28 for a significantly larger fuel flow and can, for. B at least 70% of the full load amount. In the illustrated embodiment, the Einstecköffhung 33 for the first injection valve 28 has a slightly greater distance from the inlet 18, as the Einstecköffhung 37 for the second injection valve 29 so that the Abspritzöffhung the first injector 28 is slightly further away from the inlet valve 17 as the Abspritzöffhung the second Injector 29. An equal spacing arrangement of the two Einstecköffhungen 33, 37 from the inlet 18 is also possible.
In einem in Fig. 6 bis 8 illustrierten weiteren Ausführungsbeispiel des Verbrennungszylinders 12 einer Brennkraftmaschine gemäß Fig. 1 ist der Brennraum 15 mit Zylinderkopf 13 insoweit modifiziert, als zwei Einlasse 18, 18' vorhanden sind, die von jeweils einem Einlassventil 17 bzw. 17' verschließbar sind. Zu dem ersten Einlass 18 ist ein erster Ansaugkanal 21 für Verbrennungsluft geführt (Fig. 7), und zu dem zweiten Einlass 18' ist ein zweiter Ansaugkanal 21 ' für Verbrennungsluft geführt (Fig. 8). Beide Ansaugkanäle 21, 21 ' bestehen jeweils aus einem im Zylinderkopf 13 ausgeformten Einlasskanal 22 bzw. 22' und einem an den Einlasskanal 22 bzw. 22' angesetzten Saugrohr 23 bzw. 23'. Die Kraftstoffversorgung des Brennraums 15 erfolgt in der gleichen Weise wie vorstehend in Verbindung mit Fig. 1 beschrieben worden ist. Das erste Einspritzventil 28 ist nahe dem Einlassventil 17 in eine in dem ersten Ansaugkanal 21, hier wiederum im Saugrohr 23, vorgehaltene Einstecköffhung 33 in gleicher Weise eingesetzt, um Kraftstoff in den ersten Ansaugkanal 21 einzuspritzen. Das zweite Einspritzventil 29 ist nahe dem zweiten Einlassventil 17' in eine in dem zweiten Ansaugkanal 21', hier wiederum im Saugrohr 23', vorgehaltene Einstecköffhung 37 in gleicher Weise eingesetzt, um Kraftstoff in den zweiten Ansaugkanal 21 ' einzuspritzen. Beide Einspritzventile 28, 29 sind wie vorstehend beschrieben ausgebildet und wiederum so ausgerichtet, dass ihre Spraykegel 34, 35 auf das jeweils zugeordnete Einlassventil 17 bzw. 17' gerichtet ist. Wie aus Fig. 6 bis 8 ersichtlich ist, ist der Öffhungsquerschnitt der beiden Einlasse 18, 18' im Brennraum 15 des Verbrennungszylinders 11 unterschiedlich groß. Das erste Einspritzventil 28 ist dem zum querschnittskleineren ersten Einlass 18 führenden ersten Ansaugkanal 21 zugeordnet, während das zweite Einspritzventil 29 in den zum querschnittsgrößeren zweiten Einlass 18' führenden zweiten Ansaugkanal 21 ' einspritzt. Die Querschnitte der beiden Ansaugkanäle 21, 21 ', genauer gesagt die Querschnitte der Einlasskanäle 22, 22' im Zylinderkopf 13, können dabei gleich groß sein, können aber - wie dies in Fig. 6 bis 8 dargestellt ist - ebenfalls unterschiedlich groß sein, wobei der erste Ansaugkanal 21, in den das erste Einspritzventil 28 einspritzt, den kleineren Durchmesser aufweist.In a further embodiment of the combustion cylinder 12 of an internal combustion engine according to FIG. 1 illustrated in FIGS. 6 to 8, the combustion chamber 15 with cylinder head 13 is modified to the extent that two inlets 18, 18 'are present, each of which is provided by an inlet valve 17 or 17'. are closable. To the first inlet 18, a first combustion air intake duct 21 is guided (FIG. 7), and to the second inlet 18 ', a second combustion air intake duct 21' is guided (FIG. 8). Both intake ports 21, 21 'each consist of an intake port 22, 22' formed in the cylinder head 13 and an intake pipe 23, 23 'attached to the intake port 22, 22', respectively. The fuel supply of the combustion chamber 15 takes place in the same manner as described above in connection with FIG. 1. The first injection valve 28 is inserted in the same manner near the inlet valve 17 into an insertion opening 33 held in the first intake passage 21, again here in the intake pipe 23, in order to inject fuel into the first intake passage 21. The second injection valve 29 is inserted in the same manner near the second inlet valve 17 'in a in the second intake passage 21', here again in the intake pipe 23 'held insertion opening 37 to inject fuel into the second intake passage 21'. Both injectors 28, 29 are formed as described above and in turn aligned so that their spray cone 34, 35 is directed to the respectively associated inlet valve 17 and 17 '. As can be seen from FIGS. 6 to 8, the opening cross-section of the two inlets 18, 18 'in the combustion chamber 15 of the combustion cylinder 11 varies in size. The first injection valve 28 is assigned to the first intake passage 21 leading to the smaller-diameter first intake 18, while the second injection valve 29 is injected into the second intake passage 21 'leading to the larger-cross-sectional second intake 18'. The cross sections of the two intake passages 21, 21 ', more precisely the cross sections of the intake passages 22, 22 'in the cylinder head 13, can be the same size, but - as shown in Fig. 6 to 8 - also be different sizes, wherein the first intake passage 21, in which injects the first injection valve 28, the smaller diameter having.
In einer weiteren Modifikation des Ausführungsbeispiels gemäß Fig. 6 bis 8 können die beiden Einlassventile 17, 17' einen unterschiedlich großen Ventilhub aufweisen. Die Zuordnung der beiden Einspritzventile 28, 29 zu den Einlassventilen 17, 17' ist dann so getroffen, dass das erste Einspritzventil 28 dem Einlassventil 17 mit dem kleineren Ventilhub und das zweite Einspritzventil 29 dem Einlassventil 17' mit dem größeren Ventilhub zugeordnet ist.In a further modification of the embodiment according to FIGS. 6 to 8, the two inlet valves 17, 17 'may have a different valve lift. The assignment of the two injection valves 28, 29 to the intake valves 17, 17 'is then made such that the first injection valve 28 is associated with the intake valve 17 with the smaller valve lift and the second injection valve 29 with the intake valve 17' with the larger valve lift.
In einer weiteren konstruktiven Ausführung ist eines der Einlassventile 17, 17' mit einer Ventilmaskierung versehen und das erste Einspritzventil 28 spritzt in den Ansaugkanal ein, der zu dem Einlassventil mit Ventilmaskierung führt.In another constructive embodiment, one of the inlet valves 17, 17 'is provided with a valve mask and the first injection valve 28 injects into the intake passage leading to the intake valve with valve masking.
Ebenso wie dies in dem Ausführungsbeispiel gemäß Fig. 3 bis 5 illustriert ist, können auch bei dem Ausführungsbeispiel in Fig. 6 bis 8 die beiden Einspritzventile 28, 29 mit unterschiedlichem Abstand zu dem jeweils zugeordneten Einlassventil 17 bzw. 17' im Ansaugkanal 21 bzw. 21 ' angeordnet sein. Bevorzugt hat dabei das erste Einspritzventil 28 einen etwas größeren Abstand vom ersten Einlassventil 17 als das zweite Einspitzventil 29 vom zweiten Einlassventil 17'.As is illustrated in the exemplary embodiment according to FIGS. 3 to 5, the two injection valves 28, 29 at different distances from the respective associated inlet valve 17 or 17 'in the intake channel 21 or in the exemplary embodiment in FIGS. 21 'may be arranged. Preferably, the first injection valve 28 has a slightly greater distance from the first inlet valve 17 than the second injection valve 29 from the second inlet valve 17 '.
Bei allen beschriebenen Ausführungsbeispielen werden die beiden Einspritzventile 28, 29 pro Verbrennungszylinder 11 von der elektronischen Steuereinheit 32 abhängig von den Betriebspunkten der Brennkraftmaschine unterschiedlich angesteuert. Hierzu ist in der Steuereinheit 32 ein Diagramm abgespeichert, wie es in Fig. 2 schematisiert dargestellt ist. Zu einem bestimmten Betriebspunkt der Brennkraftmaschine, der durch die Drehzahl n und die von der Brennkraftmaschine abgeforderte Last L festgelegt ist, wird das eine oder andere der beiden Einspritzventile 28, 29 oder werden beide Einspritzventile 28, 29 angesteuert. Der mit 40 gekennzeichnete, schraffierte Bereich im Diagramm weist den Bereich kleiner Teillast aus, in dem nur das erste Einspritzventil 28 zur Kraftstoffeinbringung in den Brennraum 15 herangezogen wird. Der mit 41 gekennzeichnete, kreuzschraffierte Bereich dient dem Scavenging, in dem nur das zweite Einspritzventil 29 mit kleinem Spraykegel 35 und großer Penetration angesteuert wird, das keinen nennenswerten Wandfilm vor dem Einlass 18 des Brennraums 15 erzeugt. In dem verbleibenden, mit 42 gekennzeichneten Bereich werden beide Einspritzventile 28, 29 zur Kraftstoffeinspritzung angesteuert. Zur Verbesserang der Gemischaufbereitung und Tramblebewegung in den verschiedenen Betriebspunkten weisen die beiden Einlassventile 17, 17' pro Brennraum 15 zeitlich versetzte Öffnungsphasen auf. Die Einspritzventile 28, 29 sind dann den Einlassventilen 17, 17' in der Weise zugeordnet, dass das erste Einlassventil 28 in dem zu den früher öffnenden Einlassventil 17 führenden Ansaugkanal 21 und das zweite Einspritzventil 29 in dem zu dem später öffnenden Einlassventil 17' angeordnet ist. In einem bestimmten Betriebsmodus der Brennkraftmaschine, kann dann das erste Einspritzventil 17 von der Steuerelektronik 32 so angesteuert werden, dass es Kraftstoff erst zu einem Zeitpunkt abspritzt, zu dem das zweite Einlassventil 17' öffent, also eine Überschneidung von geöffnetem Einlass 13, 13' und Auslaß 20 des Brennraums 15 sicher ausgeschlossen ist. In all described embodiments, the two injection valves 28, 29 are controlled differently per combustion cylinder 11 by the electronic control unit 32 as a function of the operating points of the internal combustion engine. For this purpose, a diagram is stored in the control unit 32, as shown schematically in FIG. At a specific operating point of the internal combustion engine, which is determined by the rotational speed n and the load L requested by the internal combustion engine, one or the other of the two injection valves 28, 29 or both injection valves 28, 29 are actuated. The hatched area marked 40 in the diagram shows the range of small partial load, in which only the first injection valve 28 is used for fuel introduction into the combustion chamber 15. The cross-hatched area marked 41 serves for scavenging, in which only the second injection valve 29 with a small spray cone 35 and high penetration is activated, which does not generate any appreciable wall film in front of the inlet 18 of the combustion chamber 15. In the remaining region marked 42, both injection valves 28, 29 are activated for fuel injection. To improve the mixture preparation and tramble movement in the various operating points, the two intake valves 17, 17 'per combustion chamber 15 on time staggered opening phases. The injectors 28, 29 are then associated with the intake valves 17, 17 'in such a manner that the first intake valve 28 is disposed in the intake passage 21 leading to the earlier-opening intake valve 17 and the second injection valve 29 is disposed in the later-opening intake valve 17' , In a certain operating mode of the internal combustion engine, then the first injection valve 17 can be controlled by the control electronics 32 so that it sprays fuel only at a time to which the second inlet valve 17 'public, so an overlap of the open inlet 13, 13' and Outlet 20 of the combustion chamber 15 is safely excluded.

Claims

Ansprüche claims
1. Brennkraftmaschine mit mindestens einen Brennraum (15), der mindestens einen von einem Einlassventil (17; 17, 17') verschließbaren Einlass (18; 18, 18') mit vorgeordnetem Ansaugkanal (21; 21, 21 ') zum Ansaugen von Verbrennungsluft aufweist, und mit einer Kraftstoffeinspritzvorrichtung (27), die in Zuordnung zu dem mindestens einen Brennraum (15) ein erstes und ein zweites Einspritzventil (28, 29) zum dosierten Einspritzen von Kraftstoff in mindestens einen Ansaugkanal (21; 21, 21 ') aufweist, wobei die Einspritzventile (28, 29) den Kraftstoff zerstäubt in Form von Spraykegeln (34, 35) abspritzen, dadurch gekennzeichnet, dass das erste Einspritzventil (28) zur Abspritzung eines breit aufgefächerten Spraykegels (34) mit großem Kegelwinkel und das zweite Einspritzventil (29) zur Abspritzung eines nur wenig aufgefächerten Spraykegels (35) mit deutlich kleinerem Kegelwinkel ausgebildet ist.1. Internal combustion engine having at least one combustion chamber (15), the at least one of an inlet valve (17; 17, 17 ') closable inlet (18; 18, 18') with upstream intake duct (21; 21, 21 ') for the intake of combustion air and a fuel injection device (27) having in association with the at least one combustion chamber (15) a first and a second injection valve (28, 29) for the metered injection of fuel into at least one intake passage (21, 21, 21 ') in which the injection valves (28, 29) atomize the fuel atomized in the form of spray cones (34, 35), characterized in that the first injection valve (28) is for spraying a wide fan cone (34) with a large cone angle and the second injection valve ( 29) is designed for the injection of a spray fan (35) with only a small fan-out, with a significantly smaller cone angle.
2. Brennkraftmaschine nach Anspruch 1, dadurch gekennzeichnet, dass das zweite Einspritzventil (29) eine gegenüber dem ersten Einspritzventil (28) deutlich größere Spritzreichweite aufweist.2. Internal combustion engine according to claim 1, characterized in that the second injection valve (29) has a relation to the first injection valve (28) significantly larger spray range.
3. Brennkraftmaschine nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass das zweite3. Internal combustion engine according to claim 1 or 2, characterized in that the second
Einspritzventil (29) für einen im Vergleich zum ersten Einspritzventil (29) deutlich größeren Kraftstoffdurchfluss ausgelegt ist.Injection valve (29) is designed for a compared to the first injection valve (29) significantly larger fuel flow.
4. Brennkraftmaschine nach Anspruch 3, dadurch gekennzeichnet, dass das Verhältnis des Kraftstoffdurchflusses zwischen zweitem Einspritzventil (29) und erstem Einspritzventil (28) ungefähr 7:3 beträgt.4. Internal combustion engine according to claim 3, characterized in that the ratio of the fuel flow between the second injection valve (29) and the first injection valve (28) is approximately 7: 3.
5. Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass bei nur einem Einlassventil (17) pro Brennraum (15) beide Einspritzventile (28, 29) in dem zu dem Einlass (18) führenden Ansaugkanal (21) nahe dem Einlassventil (17) so angeordnet sind, dass ihre Spraykegel (34, 35) auf das Einlassventil (17) gerichtet sind.5. Internal combustion engine according to one of claims 1 to 4, characterized in that with only one inlet valve (17) per combustion chamber (15) both injectors (28, 29) in the inlet (18) leading to the intake passage (21) near the inlet valve (17) are arranged so that their spray cone (34, 35) are directed to the inlet valve (17).
6. Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass bei zwei Einlassventilen (17, 17') pro Brennraum (15) jeweils ein Einspritzventil (28, 29) in einem zu einem der Einlassventile (17, 17') führenden Ansaugkanal (21, 21') nahe dem jeweiligen Einlassventil (17, 17') so angeordnet ist, dass sein Spraykegel (34, 35) auf das Einlassventil (17, 17') gerichtet ist.6. Internal combustion engine according to one of claims 1 to 4, characterized in that in two intake valves (17, 17 ') per combustion chamber (15) each have an injection valve (28, 29) in one an intake passage (21, 21 ') leading to the intake valves (17, 17') is disposed near the respective intake valve (17, 17 ') so that its spray cone (34, 35) is directed to the intake valve (17, 17') ,
7. Brennkraftmaschine nach Anspruch 6, dadurch gekennzeichnet, dass die Öffnungsquerschnitte der beiden Einlasse (18, 18') im Brennraum (15) des Verbrennungszylinders (11) unterschiedlich groß sind und dass das erste Einspritzventil (28) dem zum querschnittskleineren Einlass (18) führenden Ansaugkanal (21) und das zweite Einspritzventil (29) dem zum querschnittsgrößeren Einlass (18') führenden Ansaugkanal (21 ') zugeordnet ist.7. Internal combustion engine according to claim 6, characterized in that the opening cross sections of the two inlets (18, 18 ') in the combustion chamber (15) of the combustion cylinder (11) are different in size and that the first injection valve (28) to the smaller cross-section inlet (18) leading intake passage (21) and the second injection valve (29) to the larger-cross-section inlet (18 ') leading intake passage (21') is associated.
8. Brennkraftmaschine nach Anspruch 6 oder 7, dadurch gekennzeichnet, dass die zu den Einlassventilen (17, 17') führenden Ansaugkanäle (21, 21 ') unterschiedlich große Durchmesser aufweisen und dass das erste Einspritzventil (28) dem durchmesserkleineren Ansaugkanal (21) und das zweite Einspritzventil (29) dem durchmessergrößeren Ansaugkanal (21 ') zugeordnet ist.8. Internal combustion engine according to claim 6 or 7, characterized in that the inlet valves (17, 17 ') leading intake ports (21, 21') have different sized diameter and that the first injection valve (28) the smaller diameter intake passage (21) and the second injection valve (29) is associated with the larger diameter intake passage (21 ').
9. Brennkraftmaschine nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, dass mindestens ein Einlassventil (17, 18) eine Ventilmaskierung aufweist und dass das erste Einspritzventil (28) den zu dem Einlassventil (17) mit Ventilmaskierung führenden Ansaugkanal (21) zugeordnet ist.9. Internal combustion engine according to one of claims 6 to 8, characterized in that at least one inlet valve (17, 18) has a Ventilmaskierung and that the first injection valve (28) is associated with the inlet valve (17) with valve masking leading intake passage (21) ,
10. Brennkraftmaschine nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass die beiden Einlassventile (18, 18') einen unterschiedlich großen Ventilhub aufweisen und dass das erste Einspritzventil (28) in den zum Einlassventil (17) mit dem kleineren Ventilhub führenden Ansaugkanal (21) und das zweite Einspritzventil (29) in den zum Einlassventil (17') mit dem größeren Ventilhub führenden Ansaugkanal (21 ') einspritzt.10. Internal combustion engine according to one of claims 6 to 9, characterized in that the two inlet valves (18, 18 ') have a different sized valve lift and that the first injection valve (28) in the intake valve (17) with the smaller valve lift leading intake (21) and injects the second injection valve (29) in the intake passage (21 ') leading to the intake valve (17') with the larger valve lift.
11. Brennkraftmaschine nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, dass die beiden Einlassventile (17, 17') zeitlich versetzte Öffhungsphasen aufweisen und dass das erste Einspritzventil (28) dem zu dem zuerst öffnenden Einlassventil (17) führenden Ansaugkanal11. Internal combustion engine according to one of claims 6 to 9, characterized in that the two inlet valves (17, 17 ') have time-shifted Öffhungsphasen and that the first injection valve (28) leading to the first opening inlet valve (17) intake passage
(21) und das zweite Einspritzventil (17') dem zu dem später öffnenden Einlassventil (17') führenden Ansaugkanal (21 ') zugeordnet ist. (21) and the second injection valve (17 ') is assigned to the inlet channel (21') leading to the later-opening inlet valve (17 ').
12. Brennkraftmaschine nach Anspruch 11, dadurch gekennzeichnet, dass das erste Einspritzventil (28) erst beim Öffnen des später öffnenden Einlassventils (17') zur Einspritzung angesteuert ist.12. Internal combustion engine according to claim 11, characterized in that the first injection valve (28) is only activated when opening the later opening inlet valve (17 ') for injection.
13. Brennkraftmaschine nach einem der Ansprüche 1 bis 12, dadurch gekennzeichnet, dass das erste Einspritzventil (28) gegenüber dem zweiten Einspitzventil (29) in einem größeren Abstand von dem zugeordneten Einlassventil (17) angeordnet ist.13. Internal combustion engine according to one of claims 1 to 12, characterized in that the first injection valve (28) relative to the second Einspitzventil (29) is arranged at a greater distance from the associated inlet valve (17).
14. Brennkraftmaschine nach einem der Ansprüche 1 bis 13, dadurch gekennzeichnet, dass der mindestens eine Ansaugkanal (21; 21, 21 ') einen in einem den Brennraum (15) begrenzenden14. Internal combustion engine according to one of claims 1 to 13, characterized in that the at least one intake passage (21, 21, 21 ') in a combustion chamber (15) delimiting
Zylinderkopf (13) eines Verbrennungszylinders (11) ausgebildeten Einlasskanal (22; 22, 22') und ein daran angesetztes Saugrohr (23) umfasst und dass die Einspritzventile (28, 29) so in das Saugrohr (23; 23, 23') eingesetzt sind, dass die Kraftstoffabspritzung durch den Einlasskanal (22; 22, 22') hindurch zum Einlassventil (17; 17, 17') erfolgt.Cylinder head (13) of a combustion cylinder (11) formed inlet channel (22; 22, 22 ') and an attached suction pipe (23) and that the injection valves (28, 29) so in the suction pipe (23; 23, 23') used in that the fuel injection takes place through the inlet channel (22; 22, 22 ') to the inlet valve (17; 17, 17').
15. Brennkraftmaschine nach einem der Ansprüche 1 bis 14, dadurch gekennzeichnet, dass die Einspritzventile elektrisch ansteuerbare Magnetventile sind. 15. Internal combustion engine according to one of claims 1 to 14, characterized in that the injection valves are electrically controllable solenoid valves.
EP09756322A 2008-12-01 2009-11-24 Internal combustion engine Not-in-force EP2370687B1 (en)

Applications Claiming Priority (2)

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DE102008044244A DE102008044244A1 (en) 2008-12-01 2008-12-01 Internal combustion engine
PCT/EP2009/065708 WO2010063615A1 (en) 2008-12-01 2009-11-24 Internal combustion engine

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EP2370687A1 true EP2370687A1 (en) 2011-10-05
EP2370687B1 EP2370687B1 (en) 2013-01-23

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JP (1) JP5362028B2 (en)
KR (1) KR101623358B1 (en)
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DE (1) DE102008044244A1 (en)
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WO2010063615A1 (en) 2010-06-10
JP2012510589A (en) 2012-05-10
KR101623358B1 (en) 2016-05-23
KR20110095876A (en) 2011-08-25
CN102232143A (en) 2011-11-02
JP5362028B2 (en) 2013-12-11
US20110283974A1 (en) 2011-11-24
EP2370687B1 (en) 2013-01-23
US9169818B2 (en) 2015-10-27
DE102008044244A1 (en) 2010-06-02
CN102232143B (en) 2014-10-29
ES2398879T3 (en) 2013-03-22

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