EP2370679A1 - Internal combustion engine - Google Patents

Internal combustion engine

Info

Publication number
EP2370679A1
EP2370679A1 EP09763916A EP09763916A EP2370679A1 EP 2370679 A1 EP2370679 A1 EP 2370679A1 EP 09763916 A EP09763916 A EP 09763916A EP 09763916 A EP09763916 A EP 09763916A EP 2370679 A1 EP2370679 A1 EP 2370679A1
Authority
EP
European Patent Office
Prior art keywords
injection valve
pressure injection
fuel
combustion chamber
internal combustion
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.)
Withdrawn
Application number
EP09763916A
Other languages
German (de)
French (fr)
Inventor
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 EP2370679A1 publication Critical patent/EP2370679A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/101—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on or close to the cylinder centre axis, e.g. with mixture formation using spray guided concepts
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/02—Other engines characterised by special shape or construction of combustion chambers to improve operation 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
    • F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
    • F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
    • F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
    • F02B23/104—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder
    • F02B23/105—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder the fuel is sprayed directly onto or close to the spark plug
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3094—Controlling fuel injection the fuel injection being effected by at least two different injectors, e.g. one in the intake manifold and one in the cylinder
    • 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
    • F02M69/046—Positioning of injectors with respect to engine, e.g. in the air intake conduit for injecting into both the combustion chamber and the intake conduit
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/0002—Controlling intake air
    • F02D41/0007—Controlling intake air for control of turbo-charged or super-charged engines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/30—Controlling fuel injection
    • F02D41/3011—Controlling fuel injection according to or using specific or several modes of combustion
    • F02D41/3017—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used
    • F02D41/3023—Controlling fuel injection according to or using specific or several modes of combustion characterised by the mode(s) being used a mode being the stratified charge spark-ignited mode
    • 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

Definitions

  • the invention relates to an internal combustion engine according to the preamble of claim 1.
  • a known internal combustion engine (WO 2006/095515 A1) has at least one combustion cylinder with a combustion chamber bounded by a cylinder head and a reciprocating piston and a fuel injection device.
  • the combustion chamber is provided with an inlet valve which can be closed by an inlet valve and with an outlet which can be closed by an outlet valve.
  • an air intake duct is guided, while the outlet is connected to an exhaust line.
  • the ignition head of a spark plug projects centrally into the combustion chamber.
  • the fuel injection device has per combustion cylinder or combustion chamber on two injection valves, of which a first injection valve fuel directly into the combustion chamber and a second fuel injection valve in the air intake duct, the
  • Air intake duct with the second injection valve is carried out with low pressure, the advantages of both types of injection can be used by appropriate, operating point-dependent switching. Disclosure of the invention
  • the internal combustion engine according to the invention with the features of claim 1 has the advantage that realize a jet-guided shift operation through the multi-hole high-pressure injection valve and can be expanded to low speeds, whereby the
  • High-pressure injection valve as a result of the very small fuel droplets greatly improves the mixture preparation, which is accompanied by an emission reduction.
  • the split of the fuel injection to two differently designed injectors has the advantage that each injector can be optimized for its preferred mode of operation. Thereby and by optionally separate or joint control of
  • the combustion process in the combustion chamber with prevention of local over-enrichment as a cause of increased pollutant emissions and local extent as a cause of knocking can be easily optimized.
  • At high load can be achieved with the low-pressure injector better homogenization and thus a power or torque increase.
  • Mixture preparation is also achieved a reduced soot emissions.
  • the scavenging function can be used because the multi-hole high-pressure injection valve, the full load quantity can be covered at low speeds. As a result, a significant torque gain is achieved at low speeds.
  • the low-pressure injection valve which injects into the air intake duct is designed for a significantly greater fuel throughput compared with the multi-hole high-pressure injection valve and can cover at least 80% of the full load quantity.
  • the fuel jet cone sprayed off by him has a small cone angle and a large penetration directly into Direction inlet valve.
  • the multi-hole high-pressure valve designed with a much smaller flow rate of less than 1/3 of the full load volume injects a fuel cone with a large cone angle and low penetration.
  • High-pressure injection valve and low-pressure injection valve 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 ranges of the injection valves of the fuel injection device in Fig. 1 in association with by operating speed (n) and load (L) specified operating points of the internal combustion engine.
  • a combustion cylinder 11 fragmentary in longitudinal section 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 1 1 axially displaceably guided reciprocating piston 14 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, on which act also the reciprocating piston of 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.
  • an air intake duct 21 for combustion air is guided, which is composed of an intake duct 22 formed in the cylinder head 13 and an intake duct 23 attached to the intake duct 22.
  • Upstream are usually the Suction pipes 23 of a plurality of combustion cylinders 1 1 summarized by means of a Saugrohrkrümmers to an air intake, in which an air control member, preferably a throttle valve, is arranged.
  • 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 1 1 are summarized downstream via an exhaust manifold.
  • a spark plug 35 is inserted into the cylinder head 13, which protrudes with a firing head 351 into the combustion chamber 15.
  • a fuel injection device 27 For fuel supply of 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 per combustion cylinder 11 and combustion chamber 15.
  • the one injection valve is a multi-hole high-pressure injection valve 28, which is connected via a fuel supply line 30 to a high-pressure fuel pump 31, which in turn is connected to a fuel from a fuel tank 32 promotional low-pressure fuel pump 33.
  • the other injection valve is a low-pressure injection valve 29, which is connected via a fuel supply line 34 directly to the low-pressure fuel pump 33.
  • the structure of a multi-hole high-pressure injection valve is known and described for example in EP 1 108 134 B1.
  • the sprayed from the injection valve fuel jets are usually generated with a spray perforated disk, in which a plurality of injection holes are present, the spray hole axes are inclined at an acute angle to the disk axis.
  • the multi-hole high-pressure injection valve 28 is inserted into the cylinder head 13 so as to inject centrally into the combustion chamber 15, and at least one of the fuel jets sprayed from the injection valve 28 is directed toward the ignition head 351 toward the spark plug 35.
  • This fuel jet is preferably bushy, so fanned out very spray-like, and has a low penetration.
  • the spark plug 35 is disposed in close proximity to the multi-hole high-pressure injection valve 28 in the cylinder head 13, and its distance from the spark plug is about 20 mm or less.
  • the multi-hole high-pressure injection valve 28 is designed so that the cone angle of the sprayed fuel jet cone is large and has a lower penetration.
  • the multi-hole high-pressure fuel injection valve 28 is designed for a small fuel flow rate that is less than 1/3 of the full load amount supplied to the combustion chamber 15.
  • the low-pressure injection valve 29 is in the intake passage 21, in the illustrated embodiment, for design reasons in the suction pipe 23, used so that its Abspritzides is directed to the inlet valve 17.
  • the low-pressure injection valve 29 is designed for a large fuel flow rate that is more than 2/3 of that
  • the ejected fuel jet cone has a small cone angle and has a large penetration.
  • the fuel flow rate of the multi-hole high-pressure injection valve 28 is approximately 20% and the fuel flow rate of the low-pressure injection valve 29 is approximately 80%.
  • the two injection valves 28, 29 per combustion chamber 15 are controlled differently by an electronic control unit 36 as a function of the operating points of the internal combustion engine.
  • a diagram is stored in the control unit 36, to which a multiplicity of operating parameters are supplied, as shown diagrammatically in FIG.
  • 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 part load, in which only the multi-hole high-pressure injection valve 28 is used for fuel injection into the combustion chamber 15.
  • the cross-hatched area designated 41 serves the scavenging, in which only the multi-hole high-pressure injection valve 28 is actuated, so that when rinsing the combustion chamber 15 with air only a small amount of fuel is injected into the combustion chamber 15 and reaches the catalyst.
  • both injection valves 28, 29 are activated for force injection.
  • the multi-hole high-pressure injection valve 28 is actuated such that only a small injection quantity is injected into the combustion chamber 15 in order to prevent heating at the central installation location of the multi-hole high-pressure injection valve 28.
  • the operating mode "catalyst heating up” is also covered with fuel injected via the multi-hole high-pressure injection valve 28, a first injection being discontinued for the suction stroke of the piston 14 and a second injection being effected in stratified operation.
  • High-pressure injection valve 28 is driven, and only if at low temperatures over the multi-hole high-pressure injection valve 28 ejected fuel amount is no longer sufficient, the low-pressure injector 29 is driven assistive.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention specifies an internal combustion engine comprising at least one combustion chamber (15) with an inlet (18) which can be closed off by an inlet valve (17) and upstream of which is connected an air intake duct (21), comprising a spark plug (35) which is inserted into the combustion chamber (15), and comprising a fuel injection device (27) which, per combustion chamber (15), has one high-pressure injection valve (28) which injects directly into the combustion chamber (15) and one low-pressure injection valve (29) which injects fuel into the air intake duct (21). To realize a jet-controlled stratified-charge mode, which is extended toward low engine speeds, for the purpose of lowering fuel consumption and achieving stable idle running, the high-pressure injection valve (28) is designed as a multi-hole high-pressure injection valve (28) which discharges a plurality of fuel jets and is arranged such that it injects centrally into the combustion chamber (15) and, in this way, at least one fuel jet is directed toward the spark plug (35).

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.
Eine bekannte Brennkraftmaschine (WO 2006/095515 A1 ) weist mindestens einen Verbrennungszylinder mit einem von einem Zylinderkopf und einem Hubkolben begrenzten Brennraum sowie eine Kraftstoffeinspritzvorrichtung auf. Der Brennraum ist mit einem von einem Einlassventil verschließbaren Einlass und mit einem von einem Auslassventil verschließbaren Auslass versehen. Zu dem Ein- lass ist ein Luftansaugkanal geführt, während der Auslass an einem Abgasstrang angeschlossen ist. Zum Einleiten eines Verbrennungsprozesses im Brennraum ragt der Zündkopf einer Zündkerze zentral in den Brennraum hinein. Die Kraftstoffeinspritzvorrichtung weist pro Verbrennungszylinder bzw. Brennraum zwei Einspritzventile auf, von denen ein erstes Einspritzventil Kraftstoff direkt in den Brennraum und ein zweites Einspritzventil Kraftstoff in den Luftansaugkanal, demA known internal combustion engine (WO 2006/095515 A1) has at least one combustion cylinder with a combustion chamber bounded by a cylinder head and a reciprocating piston and a fuel injection device. The combustion chamber is provided with an inlet valve which can be closed by an inlet valve and with an outlet which can be closed by an outlet valve. To the inlet an air intake duct is guided, while the outlet is connected to an exhaust line. To initiate a combustion process in the combustion chamber, the ignition head of a spark plug projects centrally into the combustion chamber. The fuel injection device has per combustion cylinder or combustion chamber on two injection valves, of which a first injection valve fuel directly into the combustion chamber and a second fuel injection valve in the air intake duct, the
Einlassventil vorgelagert, abspritzt.Inlet valve upstream, cums.
Bei Brennkraftmaschinen mit einer solchen dualen Kraftstoffeinspritzvorrichtung, auch Dual-Injection-System genannt, bei dem die Direkteinspritzung in den Brennraum mit dem ersten Einspritzventil mit Hochdruck und die sog. Saugrohreinspritzung in denIn internal combustion engines with such a dual fuel injection device, also called dual-injection system, in which the direct injection into the combustion chamber with the first injection valve with high pressure and the so-called. Intake manifold injection in the
Luftansaugkanal mit dem zweiten Einspritzventil mit Niederdruck erfolgt, können die Vorteile beider Einspritzarten durch entsprechende, betriebspunktabhängige Umschal- tung genutzt werden. Offenbarung der ErfindungAir intake duct with the second injection valve is carried out with low pressure, the advantages of both types of injection can be used by appropriate, operating point-dependent switching. Disclosure of the invention
Die erfindungsgemäße Brennkraftmaschine mit den Merkmalen des Anspruchs 1 hat den Vorteil, dass durch das Mehrloch-Hochdruckeinspritzventil sich ein strahlgeführter Schichtbetrieb realisieren und zu kleinen Drehzahlen hin erweitern lässt, wodurch derThe internal combustion engine according to the invention with the features of claim 1 has the advantage that realize a jet-guided shift operation through the multi-hole high-pressure injection valve and can be expanded to low speeds, whereby the
Kraftstoffverbrauch gesenkt und ein stabilerer Leerlauf erzielt wird. Durch den die Zündkerze erfassenden, buschigen Strahl des Mehrloch-Hochdruckeinspritzventils mit einem großen Strahlkegel und geringer Penetration ist eine gezielte Schichteinspritzung möglich. Gleichzeitig wird das Anspritzen der Brennraumwand stark verringert, mit dem Vorteil einer geringeren Ölverdünnung. Im Kaltstart wird mittels des Mehrloch-Fuel consumption is reduced and a more stable idle is achieved. By the spark plug detecting, bushy jet of multi-hole high-pressure injection valve with a large beam cone and low penetration targeted layering is possible. At the same time, the injection of the combustion chamber wall is greatly reduced, with the advantage of a lower oil dilution. In cold start, the multi-hole
Hochdruckeinspritzventils infolge der sehr kleine Kraftstofftröpfchen die Gemischaufbereitung stark verbessert, womit eine Emissionsreduktion einhergeht. Die Aufteilung der Kraftstoffeinspritzung auf zwei unterschiedlich ausgelegte Einspritzventile hat den Vorteil, dass jedes Einspritzventil für seine bevorzugte Betriebsweise optimiert werden kann. Dadurch und durch wahlweise getrennte oder gemeinsame Ansteuerung derHigh-pressure injection valve as a result of the very small fuel droplets greatly improves the mixture preparation, which is accompanied by an emission reduction. The split of the fuel injection to two differently designed injectors has the advantage that each injector can be optimized for its preferred mode of operation. Thereby and by optionally separate or joint control of
Einspritzventile lässt sich der Verbrennungsprozess im Brennraum mit Vermeidung lokaler Überfettung als Ursache für vergrößerte Schadstoffemission und lokaler Ausma- gerung als Ursache des Klopfens in einfacher Weise optimieren. Bei hoher Last lässt sich mit dem Niederdruckeinspritzventil eine bessere Homogenisierung und damit ein Leistungs- bzw. Drehmomentzuwachs erreichen. Durch die insgesamt verbesserteInjectors, the combustion process in the combustion chamber with prevention of local over-enrichment as a cause of increased pollutant emissions and local extent as a cause of knocking can be easily optimized. At high load can be achieved with the low-pressure injector better homogenization and thus a power or torque increase. By the overall improved
Gemischaufbereitung wird auch eine verringerte Rußemission erreicht. Bei aufgeladenen Brennkraftmaschinen kann die Scavenging-Funktion genutzt werden, da mit dem Mehrloch-Hochdruckeinspritzventil die Volllastmenge bei kleinen Drehzahlen abgedeckt werden kann. Dadurch wird bei kleinen Drehzahlen ein deutlicher Drehmoment- gewinn erzielt.Mixture preparation is also achieved a reduced soot emissions. In supercharged internal combustion engines, the scavenging function can be used because the multi-hole high-pressure injection valve, the full load quantity can be covered at low speeds. As a result, a significant torque gain is achieved at low speeds.
Durch die in den weiteren Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Anspruch 1 angegebenen Brennkraftmaschine möglich.The measures listed in the further claims advantageous refinements and improvements of claim 1 internal combustion engine are possible.
Gemäß einer vorteilhaften Ausführungsform der Erfindung ist das in den Luftansaugkanal einspritzende Niederdruckeinspritzventil für einen im Vergleich zum Mehrloch- Hochdruckeinspritzventil deutlich größeren Kraftstoffdurchfluss ausgelegt und kann mindestens 80% der Volllastmenge abdecken. Der von ihm abgespritzte Kraftstoff- Strahlkegel besitzt einen kleinen Kegelwinkel und eine große Penetration direkt in Richtung Einlassventil. Das mit einem deutlich kleineren Durchfluss von weniger als 1/3 der Volllastmenge konzipierte Mehrloch-Hochdruckventil spritzt dagegen einen Kraftstoff-Strahlkegel mit großem Kegelwinkel und geringer Penetration ab.According to an advantageous embodiment of the invention, the low-pressure injection valve which injects into the air intake duct is designed for a significantly greater fuel throughput compared with the multi-hole high-pressure injection valve and can cover at least 80% of the full load quantity. The fuel jet cone sprayed off by him has a small cone angle and a large penetration directly into Direction inlet valve. On the other hand, the multi-hole high-pressure valve designed with a much smaller flow rate of less than 1/3 of the full load volume injects a fuel cone with a large cone angle and low penetration.
Gemäß einer vorteilhaften Ausführungsform der Erfindung sind Mehrloch-According to an advantageous embodiment of the invention, multi-hole
Hochdruckeinspritzventil und Niederdruckeinspritzventil elektrisch ansteuerbare Magnetventile. Solche Magnetventile sind deutlich kostengünstiger als häufig verwendete piezoelektrische Einspritzventile.High-pressure injection valve and low-pressure injection valve 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:The invention is explained in more detail in the following description with reference to an embodiment shown in the drawings. Show it:
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 der Kraftstoffeinspritzvorrichtung in Fig. 1 in Zuordnung zu durch Drehzahl (n) und Last (L) festgelegten Betriebspunkten der Brennkraftmaschine.Fig. 2 is a diagram for driving ranges of the injection valves of the fuel injection device in Fig. 1 in association with by operating speed (n) and load (L) specified operating points of the internal combustion engine.
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 1 1 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 conventional multi-cylinder internal combustion engine for e.g. Motor vehicles is shown in Fig. 1, only a combustion cylinder 11 fragmentary in longitudinal section 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 1 1 axially displaceably guided reciprocating piston 14 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, on which act also the reciprocating piston of the other combustion cylinder.
Der Brennraum 15 weist einen mit einem Einlassventil 17 verschließbaren Einlass 18 und einen mit einem Auslassventil 19 verschließbaren Auslass 20 auf. Zu dem Einlass 18 ist ein Luftansaugkanal 21 für Verbrennungsluft geführt, der aus einem im Zylinderkopf 13 ausgeformten Einlasskanal 22 und einem an den Einlasskanal 22 ange- setzten Saugrohr 23 zusammengesetzt ist. Stromaufwärts sind üblicherweise die Saugrohre 23 mehrerer Verbrennungszylinder 1 1 mittels eines Saugrohrkrümmers zu einem Luftansaugstutzen zusammengefasst, in dem ein Luftsteuerorgan, vorzugsweise eine Drosselklappe, angeordnet ist. 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 1 1 sind stromabwärts über einen Abgaskrümmer zusammengefasst. Zur Einleitung des Verbrennungsprozesses im Brennraum 15 ist in den Zylinderkopf 13 eine Zündkerze 35 eingesetzt, die mit einem Zündkopf 351 in den Brennraum 15 hineinragt.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, an air intake duct 21 for combustion air is guided, which is composed of an intake duct 22 formed in the cylinder head 13 and an intake duct 23 attached to the intake duct 22. Upstream are usually the Suction pipes 23 of a plurality of combustion cylinders 1 1 summarized by means of a Saugrohrkrümmers to an air intake, in which an air control member, preferably a throttle valve, is arranged. 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 1 1 are summarized downstream via an exhaust manifold. To initiate the combustion process in the combustion chamber 15, a spark plug 35 is inserted into the cylinder head 13, which protrudes with a firing head 351 into the combustion chamber 15.
Zur Kraftstoffversorgung des Brennraums 15 des mindestens einen Verbrennungszylinders 11 ist eine Kraftstoffeinspritzvorrichtung 27 vorgesehen, die pro Verbrennungszylinder 11 bzw. Brennraum 15 zwei elektromagnetische Einspritzventile aufweist. Das eine Einspritzventil ist ein Mehrloch-Hochdruckeinspritzventil 28, das über eine Kraftstoffzuleitung 30 an einer Kraftstoff-Hochdruckpumpe 31 angeschlossen ist, die ihrerseits mit einer Kraftstoff aus einem Kraftstofftank 32 fördernden Kraftstoff- Niederdruckpumpe 33 verbunden ist. Das andere Einspritzventil ist ein Niederdruckeinspritzventil 29, das über eine Kraftstoffzuleitung 34 unmittelbar an die Kraftstoff- Niederdruckpumpe 33 angeschlossen ist. Der Aufbau eines Mehrloch- Hochdruckeinspritzventils ist bekannt und beispielsweise in der EP 1 108 134 B1 beschrieben. Die von dem Einspritzventil abgespritzten Kraftstoffstrahlen werden dabei üblicherweise mit einer Spritzlochscheibe erzeugt, in der mehrere Spritzlöcher vorhanden sind, deren Spritzlochachsen unter einem spitzen Winkel zur Scheibenachse geneigt sind. Das Mehrloch-Hochdruckeinspritzventil 28 ist in den Zylinderkopf 13 so eingesetzt, dass es zentral in den Brennraum 15 einspritzt, wobei mindestens einer der von dem Einspritzventil 28 abgespritzten Kraftstoffstrahlen zum Zündkopf 351 der zur Zündkerze 35 hin gerichtet ist. Dieser Kraftstoffstrahl ist vorzugsweise buschig, also stark sprayartig aufgefächert, und besitzt eine nur geringe Penetration. Die Zündkerze 35 ist in räumlicher Nähe zum Mehrloch-Hochdruckeinspritzventil 28 im Zylinderkopf 13 angeordnet, wobei ihr Abstand von der Zündkerze ca. 20 mm oder weniger beträgt. Das Mehrloch-Hochdruckeinspritzventil 28 ist so konzipiert, dass der Kegelwinkel des abgespritzten Kraftstoffstrahlkegels groß ist und eine geringere Penetration aufweist. Außerdem ist das Mehrloch-Hochdruckeinspritzventil 28 für einen kleinen Kraftstoff durchf I uss ausgelegt, der weniger als 1/3 der dem Brennraum 15 zugeführten Volllastmenge beträgt. Das Niederdruckeinspritzventil 29 ist in den Ansaugkanal 21 , im dargestellten Ausführungsbeispiel aus konstruktiven Gründen in das Saugrohr 23, so eingesetzt, dass seine Abspritzrichtung hin zum Einlassventil 17 gerichtet ist. Das Niederdruckein- spritzventil 29 ist für einen großen Kraftstoff durchf I uss ausgelegt, der mehr als 2/3 derFor fuel supply of 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 per combustion cylinder 11 and combustion chamber 15. The one injection valve is a multi-hole high-pressure injection valve 28, which is connected via a fuel supply line 30 to a high-pressure fuel pump 31, which in turn is connected to a fuel from a fuel tank 32 promotional low-pressure fuel pump 33. The other injection valve is a low-pressure injection valve 29, which is connected via a fuel supply line 34 directly to the low-pressure fuel pump 33. The structure of a multi-hole high-pressure injection valve is known and described for example in EP 1 108 134 B1. The sprayed from the injection valve fuel jets are usually generated with a spray perforated disk, in which a plurality of injection holes are present, the spray hole axes are inclined at an acute angle to the disk axis. The multi-hole high-pressure injection valve 28 is inserted into the cylinder head 13 so as to inject centrally into the combustion chamber 15, and at least one of the fuel jets sprayed from the injection valve 28 is directed toward the ignition head 351 toward the spark plug 35. This fuel jet is preferably bushy, so fanned out very spray-like, and has a low penetration. The spark plug 35 is disposed in close proximity to the multi-hole high-pressure injection valve 28 in the cylinder head 13, and its distance from the spark plug is about 20 mm or less. The multi-hole high-pressure injection valve 28 is designed so that the cone angle of the sprayed fuel jet cone is large and has a lower penetration. In addition, the multi-hole high-pressure fuel injection valve 28 is designed for a small fuel flow rate that is less than 1/3 of the full load amount supplied to the combustion chamber 15. The low-pressure injection valve 29 is in the intake passage 21, in the illustrated embodiment, for design reasons in the suction pipe 23, used so that its Abspritzrichtung is directed to the inlet valve 17. The low-pressure injection valve 29 is designed for a large fuel flow rate that is more than 2/3 of that
Volllastmenge beträgt. Der von ihm abgespritzte Kraftstoffstrahlkegel weist einen kleinen Kegelwinkel auf und besitzt eine große Penetration. Beispielsweise ist der Kraftstoffdurchfluss des Mehrloch-Hochdruckeinspritzventils 28 mit ca. 20% und der Kraftstoffdurchfluss des Niederdruckeinspritzventils 29 mit ca. 80% bemessen.Full load amount is. The ejected fuel jet cone has a small cone angle and has a large penetration. For example, the fuel flow rate of the multi-hole high-pressure injection valve 28 is approximately 20% and the fuel flow rate of the low-pressure injection valve 29 is approximately 80%.
Die beiden Einspritzventile 28, 29 pro Brennraum 15 werden von einer elektronischen Steuereinheit 36 abhängig von den Betriebspunkten der Brennkraftmaschine unterschiedlich angesteuert. Hierzu ist in der Steuereinheit 36, der eine Vielzahl von Betriebsparametern zugeführt werden, 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 Mehrloch-Hochdruckeinspritzventil 28 zur Kraftstoffeinspritzung in den Brennraum 15 herangezogen wird. Der mit 41 gekennzeichnete, kreuzschraffierte Bereich dient dem Scavenging, in dem wiederum nur das Mehrloch-Hochdruckeinspritzventil 28 angesteuert wird, so dass beim Spülen des Brennraums 15 mit Luft nur wenig Kraftstoff in den Brennraum 15 eingespritzt wird und in Richtung Katalysator gelangt. In dem verbleibenden, mit 42 gekennzeichneten Bereich, also bei hohen Drehzahlen und großer Last werden beide Einspritzventile 28, 29 zur Krafteinspritzung angesteuert. Die Ansteuerung des Mehrloch-Hochdruckeinspritzventils 28 erfolgt dabei so, dass nur eine geringe Einspritzmenge in den Brennraum 15 eingespritzt wird, um eine Erhitzung am zentralen Einbauort des Mehrloch-Hochdruckeinspritzventils 28 zu ver- hindern.The two injection valves 28, 29 per combustion chamber 15 are controlled differently by an electronic control unit 36 as a function of the operating points of the internal combustion engine. For this purpose, a diagram is stored in the control unit 36, to which a multiplicity of operating parameters are supplied, as shown diagrammatically 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 part load, in which only the multi-hole high-pressure injection valve 28 is used for fuel injection into the combustion chamber 15. The cross-hatched area designated 41 serves the scavenging, in which only the multi-hole high-pressure injection valve 28 is actuated, so that when rinsing the combustion chamber 15 with air only a small amount of fuel is injected into the combustion chamber 15 and reaches the catalyst. In the remaining region marked 42, ie at high rotational speeds and high load, both injection valves 28, 29 are activated for force injection. The multi-hole high-pressure injection valve 28 is actuated such that only a small injection quantity is injected into the combustion chamber 15 in order to prevent heating at the central installation location of the multi-hole high-pressure injection valve 28.
Auch die Betriebsart „Katalysator aufheizen" wird mit über das Mehrloch- Hochdruckeinspritzventil 28 eingespritztem Kraftstoff abgedeckt, wobei eine erste Einspritzung zum Saughub des Hubkolbens 14 und eine zweite Einspritzung im Schichtbetrieb abgesetzt wird. Im Startvorgang wird ebenfalls das Mehrloch- Hochdruckeinspritzventil 28 angesteuert, und nur dann, wenn bei geringen Temperaturen die über das Mehrloch-Hochdruckeinspritzventil 28 abgespritzte Kraftstoffmenge nicht mehr ausreicht, wird das Niederdruckeinspritzventil 29 unterstützend angesteuert. The operating mode "catalyst heating up" is also covered with fuel injected via the multi-hole high-pressure injection valve 28, a first injection being discontinued for the suction stroke of the piston 14 and a second injection being effected in stratified operation. High-pressure injection valve 28 is driven, and only if at low temperatures over the multi-hole high-pressure injection valve 28 ejected fuel amount is no longer sufficient, the low-pressure injector 29 is driven assistive.

Claims

Ansprüche claims
1. Brenkraftmaschine mit mindestens einem Brennraum (15), der ein von einem Einlassventil (17) verschließbaren Einlass (18) mit vorgeordnetem Luftansaugkanal (21 ) aufweist, mit einer in den Brennraum (15) eingeführten Zündkerze (35) und mit einer Kraftstoffeinspritzvorrichtung (27), die proA gasoline engine having at least one combustion chamber (15) having an inlet (18) with an upstream air intake duct (21) which can be closed by an inlet valve (17), a spark plug (35) inserted into the combustion chamber (15) and a fuel injection device ( 27), the pro
Brennraum (15) ein unter Hochdruck stehenden Kraftstoff direkt in den Brennraum (15) einspritzendes Hochdruckeinspritzventil (28) und ein unter Niederdruck stehenden Kraftstoff in den Luftansaugkanal (21 ) einspritzendes Niederdruckeinspritzventil (29) aufweist, dadurch gekennzeichnet, dass das Hochdruckeinspritzventil (28) als ein mehrere Kraftstoffstrahlen abspritzendes Mehrloch-Hochdruckeinspritzventil (28) ausgebildet und so angeordnet ist, dass es zentral in den Brennraum (15) einspritzt und dabei mindestens ein Kraftstoffstrahl zur Zündkerze (35) gerichtet ist.Combustion chamber (15) has a high pressure fuel directly into the combustion chamber (15) injecting high pressure injection valve (28) and a low pressure fuel in the air intake passage (21) injecting low pressure injection valve (29), characterized in that the high pressure injection valve (28) as a multi-hole high pressure injection valve (28) having multiple fuel jets is formed and arranged to inject centrally into the combustion chamber (15) while directing at least one jet of fuel toward the spark plug (35).
2. Brennkraftmaschine nach Anspruch 1 , dadurch gekennzeichnet, dass das2. Internal combustion engine according to claim 1, characterized in that the
Niederdruckeinspritzventil (29) für einen im Vergleich zum Mehrloch- Hochdruckeinspritzventil (28) deutlich größeren Kraftstoffdurchfluss ausgelegt ist.Low-pressure injection valve (29) for a compared to the multi-hole high-pressure injection valve (28) significantly larger fuel flow is designed.
3. Brennkraftmaschine nach Anspruch 2, dadurch gekennzeichnet, dass der maximale Kraftstoffdurchfluss des Mehrloch-Hochdruckeinspritzventils (28) weniger als 1/3 und der des Niederdruckeinspritzventils (29) mehr als 2/3 der dem Brennraum (15) zugeführten Volllastmenge beträgt.3. Internal combustion engine according to claim 2, characterized in that the maximum fuel flow of the multi-hole high-pressure injection valve (28) is less than 1/3 and that of the low-pressure injection valve (29) more than 2/3 of the combustion chamber (15) supplied full load amount.
4. Brennkraftmaschine nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass das Mehrloch-Hochdruckeinspritzventil (28) zur Abspritzung eines weit aufgespreizten Kraftstoffstrahlkegels mit großem Kegelwinkel ausgebildet ist.4. Internal combustion engine according to one of claims 1 to 3, characterized in that the multi-hole high-pressure injection valve (28) is designed for the injection of a widely spread fuel jet cone with a large cone angle.
5. Brennkraftmaschine nach einem der Ansprüche 1 bis 4, dadurch gekennzeichnet, dass das Niederdruckeinspritzventil (29) zum Abspritzen eines we- nig aufgespreizten Kraftstoffstrahlkegels mit kleinem Kegelwinkel ausgebildet ist.5. Internal combustion engine according to one of claims 1 to 4, characterized in that the low-pressure injection valve (29) for spraying a we- nig spread fuel jet cone is designed with a small cone angle.
6. Brennkraftmaschine nach einem der Ansprüche 1 bis 5, dadurch gekenn- zeichnet, dass das Mehrloch-Hochdruck- und das Niederdruckeinspritzventil6. Internal combustion engine according to any one of claims 1 to 5, characterized in that the multi-hole high-pressure and the low-pressure injection valve
(28, 29) elektrisch ansteuerbare Magnetventile sind.(28, 29) are electrically controllable solenoid valves.
7. Brennkraftmaschine nach einem der Ansprüche 1 bis 6, dadurch gekennzeichnet, dass das Hochdruckeinspritzventil (28) einen nur geringen Abstand von der Zündkerze (35) aufweist, der vorzugsweise gleich oder kleiner7. Internal combustion engine according to one of claims 1 to 6, characterized in that the high-pressure injection valve (28) has only a small distance from the spark plug (35), which is preferably equal to or smaller
20 mm ist. 20 mm.
EP09763916A 2008-12-01 2009-11-24 Internal combustion engine Withdrawn EP2370679A1 (en)

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JP6111899B2 (en) * 2013-06-28 2017-04-12 三菱自動車工業株式会社 Engine control device
DE102015200455B4 (en) * 2015-01-14 2018-01-25 Ford Global Technologies, Llc Engine, motor vehicle, injection process
DE102020117001A1 (en) 2020-06-29 2021-12-30 Dr. Ing. H.C. F. Porsche Aktiengesellschaft Injection device of an internal combustion engine and method for operating an internal combustion engine
CN115750067B (en) * 2022-11-09 2024-04-12 重庆长安汽车股份有限公司 Combustion system and combustion method of hybrid gasoline engine, engine and vehicle

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