EP0611885B1 - Fuel injector valve for an internal combustion piston engine - Google Patents

Fuel injector valve for an internal combustion piston engine Download PDF

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Publication number
EP0611885B1
EP0611885B1 EP93810093A EP93810093A EP0611885B1 EP 0611885 B1 EP0611885 B1 EP 0611885B1 EP 93810093 A EP93810093 A EP 93810093A EP 93810093 A EP93810093 A EP 93810093A EP 0611885 B1 EP0611885 B1 EP 0611885B1
Authority
EP
European Patent Office
Prior art keywords
valve
combustion chamber
cap
seat
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP93810093A
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German (de)
French (fr)
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EP0611885A1 (en
Inventor
Ulrich Staiger
Klaus Heim
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.)
Winterthur Gas and Diesel AG
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Winterthur Gas and Diesel AG
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 Winterthur Gas and Diesel AG filed Critical Winterthur Gas and Diesel AG
Priority to DK93810093.0T priority Critical patent/DK0611885T3/da
Priority to EP93810093A priority patent/EP0611885B1/en
Priority to DE59306670T priority patent/DE59306670D1/en
Priority to KR1019940002524A priority patent/KR100323937B1/en
Priority to JP6018707A priority patent/JPH06317235A/en
Priority to CN94101587A priority patent/CN1050877C/en
Priority to FI940718A priority patent/FI106739B/en
Publication of EP0611885A1 publication Critical patent/EP0611885A1/en
Application granted granted Critical
Publication of EP0611885B1 publication Critical patent/EP0611885B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow

Definitions

  • the invention relates to a fuel injection valve for a reciprocating piston internal combustion engine according to the preamble of claim 1.
  • DE-A-15 26 717 describes an injection nozzle for internal combustion engines.
  • the nozzle contains a needle housing, a valve needle with a valve cone 11 at the end on the combustion chamber side, a nozzle body with a cap and nozzle holes which are arranged in the cap, and a valve seat sleeve which is inserted in the nozzle body.
  • the cap is provided below the valve cone and serves to guide the valve needle within the cap of the nozzle body.
  • An annular channel is provided on the inside of the cap.
  • the end of the valve needle forms a flat cone to displace the fuel remaining under the needle through the annular gap of the cylindrical guide.
  • the nozzle has the disadvantages that after the valve needle is closed on the combustion chamber side of the valve seat there is a volume of fuel which is blown out by the gas flow into the combustion chamber and leads to coking and that the needle stroke is very low to reduce the stress on the valve seat and needle and reduce stop.
  • the invention solves the problem of improving a fuel injector for a reciprocating engine.
  • Another advantage of the injection valve according to the invention is that the stroke of the striker can now be made larger.
  • the injection valve has a housing 1, which consists of an upper part 2 and a lower part 3, which are held together by a union nut 4.
  • the housing 1 rests with a flange 5 on a cylinder head 6, which limits the combustion chamber 7 in the cylinder, not shown, of the reciprocating internal combustion engine of the diesel type.
  • the housing 1 penetrates the Zylin6 and projects into the combustion chamber 7 with a section 3 ′ of the lower part 3 with a diameter.
  • the housing 1 For the supply of fuel (arrow A) to the injection valve, the housing 1 has a channel 10 which initially extends radially into the flange 5 and is then guided essentially in the longitudinal direction of the housing through the upper part 2 and into the lower part 3 , where it opens into a room 11 which is located near the center of the housing.
  • a striker 20 In the center of the housing 1 there is an axially displaceable rod 12 of a striker 20 which carries a mushroom-like valve cone 20 'at its lower end in FIG. 1 and which is held at the upper end in a spring plate 13 which is located on its underside on a Compression spring 14 supports.
  • the upper part 2 To guide the axially displaceable rod 12, the upper part 2 has a bore 9 of constant diameter in its lower half and the lower part throughout.
  • the bore 9 is enlarged in diameter and forms a guide for the spring plate 13 which is axially displaceable with the rod 12.
  • the space 15 formed by the enlarged bore, which also receives the compression spring 14, is directed upwards a screw 16 closed.
  • the diameter of the rod 12 is reduced above the space 11, so that between the thinner rod section 12 'thus formed and the bore 9 there is an annular channel 17 which extends to the lowest end of the section 3'.
  • the end face of section 3 ' is designed as a conical seat surface 18 (FIG. 2) which widens towards the combustion chamber 7.
  • the seat surface 18 interacts with a correspondingly conical sealing surface 19 which is formed on the top of the mushroom-like valve cone 20 '.
  • a threaded cap 8 is screwed onto the housing section 3 'and spans the valve cone 20' with its lower section located in the combustion chamber 7.
  • nozzle channels 21 are provided in the cap 8 which extend transversely to the longitudinal axis of the valve and are used to form fuel jets.
  • the channels 21 have a circular cross section.
  • a raised stop surface 8 ' is formed on the inside thereof, against which the striker 20 rests in its fully open position.
  • the threaded cap 8 forms on its inside below the seat surface 18 a cylindrical surface 8 ′′, which serves as a guide surface for the striker 20, which is also cylindrical below the sealing surface 19.
  • the upper limit of the nozzle channel 21 is offset relative to the seat surface 18 by the distance X from the combustion chamber 7, as a result of which the injection valve receives a preliminary stroke without opening.
  • the valve is normally in the closed position, ie the closing piece 20 lies with its sealing surface 19 close to the seat surface 18, which is accomplished by the compression spring 14.
  • the channel 10 and the annular space 17 are filled with fuel which has a pressure of less than 100 bar.
  • the injection of fuel into the combustion chamber 7 is dependent on the delivery pressure of the injection pump, not shown, connected to the channel 10. At the moment when the opening force generated by the fuel pressure and acting on the valve cone 20 ′ outweighs the closing force of the compression spring 14, the closing piece is displaced downward, so that the fuel can flow from the annular space 17 to the channels 21.
  • the nozzle channels 31 have an essentially rectangular cross section and the seat surface 18 is displaced relative to the upper boundary of the channels 31 towards the combustion chamber 7.
  • the injection process begins immediately when the valve cone 20 'is lifted off the seat 18.
  • the striker 40 there is again a mushroom-like valve cone 40' with a sealing surface 42 which interacts with the seat surface 18 at the lower end of the section 3 '.
  • the valve cone 40 ' is surrounded by a threaded cap 48 which, in terms of the stop surface and the cylindrical guide surface for the striker, is of the same design as the threaded cap 8.
  • the difference is that the highly rectangular channels 41 are larger than in the threaded cap 8 according to FIG. 3 and that a slide plate 45 protrudes into the channels 41, which are attached to the closing piece 40 below the sealing surface 42.
  • each channel 41 measured in the circumferential direction, the threaded cap 48 is provided with a slot of the same width at the top.
  • a leg 43 of a ring 44 which encloses the section 3 ', rests on the upper edge of the threaded cap 48 and can be rotated with the threaded cap.
  • the lower end face 43 'of each leg 43 in FIGS. 4 and 5 thus delimits the beam-forming cross section of the associated channel 41 on its upper side.
  • the mode of operation of the injection valve according to FIGS. 4 and 5 is in principle the same as that described for FIGS. 1 and 2, i.e. if the delivery pressure of the injection pump exceeds the force of the closing spring, the closing piece 40 moves in the direction of the combustion chamber 7, as a result of which fuel can flow from the annular space 17 to the nozzle channels 41.
  • the flow cross section of the jet-forming part of the nozzle channels 41 is determined by the axial distance between the surfaces 43 'and 45'.
  • the number of nozzle channels depends on the application of the injection valve. If the injection valve is used in a four-stroke diesel engine, it is usually located in the center of the combustion chamber and the nozzle channels are distributed evenly over the circumference of the injection valve. If the injection valve is arranged in a two-stroke diesel engine with an outlet valve arranged in the center of the combustion chamber, a plurality of injection valves are usually arranged distributed outside the center. One or more nozzle channels per injection valve can be arranged in such a way that the fuel jets emerging from them are distributed in the combustion chamber as cheaply as possible for combustion.
  • a clamp connection for the cap 8 or 48 can also be used instead of a threaded connection.

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

Description

Die Erfindung bezieht sich auf ein Brennstoffeinspritzventil für eine Hubkolbenbrennkraftmaschine gemäss dem Oberbegriff des Anspruches 1.The invention relates to a fuel injection valve for a reciprocating piston internal combustion engine according to the preamble of claim 1.

In der DE-A-15 26 717 ist eine Einspritzdüse für Brennkraftmaschinen beschrieben. Die Düse enthält ein Nadelgehäuse, eine Ventilnadel mit einem Ventilkegel 11 am brennraumseitigen Ende, einen Düsenkörper mit einer Kappe und Düsenlöchern, die in der Kappe angeordnet sind und eine Ventilsitzbüchse, die im Düsenkörper eingesetzt ist. Unterhalb des Ventilkegels ist die Kappe vorgesehen, die zur Führung der Ventilnadel innerhalb der Kappe des Düsenkörpers dient. An der Innenseite der Kappe ist ein Ringkanal vorgesehen. Das Ende der Ventilnadel bildet ein Flachkegel, um den unter der Nadel verbleibenden Kraftstoff durch den Ringspalt der zylindrischen Führung zu verdrängen.DE-A-15 26 717 describes an injection nozzle for internal combustion engines. The nozzle contains a needle housing, a valve needle with a valve cone 11 at the end on the combustion chamber side, a nozzle body with a cap and nozzle holes which are arranged in the cap, and a valve seat sleeve which is inserted in the nozzle body. The cap is provided below the valve cone and serves to guide the valve needle within the cap of the nozzle body. An annular channel is provided on the inside of the cap. The end of the valve needle forms a flat cone to displace the fuel remaining under the needle through the annular gap of the cylindrical guide.

Die Düse hat die Nachteile, dass nach dem Schliessen der Ventilnadel auf der Brennraumseite des Ventilsitzes ein Brennstoffvolumen vorhanden ist, das durch die Gasströmung in den Verbrennungsraum ausgeblasen wird und zu Verkokungen führt und dass der Nadelhub sehr gering ist, um die Beanspruchung von Ventilsitz, Nadel und Anschlag zu vermindern.The nozzle has the disadvantages that after the valve needle is closed on the combustion chamber side of the valve seat there is a volume of fuel which is blown out by the gas flow into the combustion chamber and leads to coking and that the needle stroke is very low to reduce the stress on the valve seat and needle and reduce stop.

Die Erfindung, wie sie in den Ansprüchen gekennzeichnet ist, löst die Aufgabe ein Brennstoffeinspritzventil für eine Hubkolbenmaschine zu verbessern.The invention, as characterized in the claims, solves the problem of improving a fuel injector for a reciprocating engine.

Diese Aufgabe wird erfindungsgemäß durch die Merkmale des Kennzeichens von Anspruch 1 gelöst. Damit ergibt sich die Möglichkeit, die Querschnittsgröße des zu bildenden Strahls abhängig vom Hub des Schliessstückes zu verändern, wobei der Hub mit Hilfe des Einspritzdrucks oder mittels einer Verstellvorrichtung für das Schliessstück eingestellt wird.This object is achieved by the features of the characterizing part of claim 1. This results in the possibility of changing the cross-sectional size of the jet to be formed depending on the stroke of the striker, the stroke being adjusted with the aid of the injection pressure or by means of an adjusting device for the striker.

Ein weiterer Vorteil des erfindungsgemässen Einspritzventils besteht darin, dass der Hub des Schliessstückes nunmehr grösser bemessen werden kann.Another advantage of the injection valve according to the invention is that the stroke of the striker can now be made larger.

Wird am Ventilkegel ein Vorsprung vorgesehen, der in den Düsenkanal ragt, kann der Austrittsquerschnitt des Brennstoffstrahles verändert werden. Damit wird die höchste Strömungsgeschwindigkeit am Austritt des Düsenkanals erreicht.If a projection is provided on the valve cone, which protrudes into the nozzle channel, the outlet cross section of the fuel jet can be changed. The highest flow velocity at the outlet of the nozzle channel is thus achieved.

Einige Ausführungsbeispiele der Erfindung sind in der folgenden Beschreibung anhand der Zeichnung näher erläutert.
Es zeigen:

Fig. 1
einen axialen Schnitt durch ein Einspritzventil nach der Erfindung,
Fig. 2
das untere Ende des Einspritzventils nach Fig. 1 im grösseren Massstab,
Fig. 3
das untere Ende eines gegenüber Fig. 2 abgewandelten Einspritzventils,
Fig. 4
das untere Ende eines weiteren abgewandelten Einspritzventils und
Fig. 5
eine Ansicht des unteren Endes des Einspritzventils nach Fig. 4.
Some embodiments of the invention are explained in more detail in the following description with reference to the drawing.
Show it:
Fig. 1
an axial section through an injection valve according to the invention,
Fig. 2
the lower end of the injection valve of FIG. 1 on a larger scale,
Fig. 3
the lower end of a modified injection valve compared to FIG. 2,
Fig. 4
the lower end of another modified injector and
Fig. 5
a view of the lower end of the injection valve of FIG. 4th

Gemäss Fig. 1 weist das Einspritzventil ein Gehäuse 1 auf, das aus einem oberen Teil 2 und einem unteren Teil 3 besteht, die durch eine Ueberwurfmutter 4 zusammengehalten werden. Das Gehäuse 1 ruht mit einem Flansch 5 auf einem Zylinderkopf 6, der den Brennraum 7 im nicht gezeichneten Zylinder der Hubkolbenbrennkraftmaschine der Dieselbauart nach oben begrenzt. Das Gehäuse 1 durchdringt den Zylin6 und ragt mit einem im Durchmesser abgesetzten Abschnitt 3' des unteren Teils 3 in den Brennraum 7.1, the injection valve has a housing 1, which consists of an upper part 2 and a lower part 3, which are held together by a union nut 4. The housing 1 rests with a flange 5 on a cylinder head 6, which limits the combustion chamber 7 in the cylinder, not shown, of the reciprocating internal combustion engine of the diesel type. The housing 1 penetrates the Zylin6 and projects into the combustion chamber 7 with a section 3 ′ of the lower part 3 with a diameter.

Für die Zufuhr von Brennstoff (Pfeil A) zum Einspritzventil weist das Gehäuse 1 einen Kanal 10 auf, der sich zunächst radial in den Flansch 5 erstreckt und dann im wesentlichen in Längsrichtung des Gehäuses durch den oberen Teil 2 und in den unteren Teil 3 geführt ist, wo er in einem Raum 11 mündet, der sich nahe dem Zentrum des Gehäuses befindet. Im Zentrum des Gehäuses 1 ist eine axial verschiebbare Stange 12 eines Schliessstücks 20 vorhanden, die an ihrem in Fig. 1 unteren Ende einen pilzartigen Ventilkegel 20' trägt und die am oberen Ende in einem Federteller 13 gehalten ist, der sich auf seiner Unterseite auf einer Druckfeder 14 abstützt. Zum Führen der axial verschiebbaren Stange 12 weisen der obere Teil 2 in seiner unteren Hälfte und der untere Teil durchgehend eine Bohrung 9 von konstantem Durchmesser auf. In der oberen Hälfte des oberen Teils 2 ist die Bohrung 9 im Durchmesser erweitert und bildet eine Führung für den mit der Stange 12 axial verschiebbaren Federteller 13. Der durch die erweiterte Bohrung gebildete Raum 15, der auch die Druckfeder 14 aufnimmt, ist nach oben durch eine Schraube 16 verschlossen.For the supply of fuel (arrow A) to the injection valve, the housing 1 has a channel 10 which initially extends radially into the flange 5 and is then guided essentially in the longitudinal direction of the housing through the upper part 2 and into the lower part 3 , where it opens into a room 11 which is located near the center of the housing. In the center of the housing 1 there is an axially displaceable rod 12 of a striker 20 which carries a mushroom-like valve cone 20 'at its lower end in FIG. 1 and which is held at the upper end in a spring plate 13 which is located on its underside on a Compression spring 14 supports. To guide the axially displaceable rod 12, the upper part 2 has a bore 9 of constant diameter in its lower half and the lower part throughout. In the upper half of the upper part 2, the bore 9 is enlarged in diameter and forms a guide for the spring plate 13 which is axially displaceable with the rod 12. The space 15 formed by the enlarged bore, which also receives the compression spring 14, is directed upwards a screw 16 closed.

Die Stange 12 ist oberhalb des Raumes 11 in ihrem Durchmesser verringert, so dass sich zwischen dem so gebildeten dünneren Stangenabschnitt 12' und der Bohrung 9 ein Ringkanal 17 ergibt, der sich bis zum untersten Ende des Abschnitts 3' erstreckt. Die Stirnfläche des Abschnitts 3' ist als kegelige, sich gegen den Brennraum 7 erweiternde Sitzfläche 18 (Fig. 2) ausgebildet. Die Sitzfläche 18 wirkt mit einer entsprechend kegeligen Dichtfläche 19 zusammen, die an der Oberseite des pilzartigen Ventilkegels 20' ausgebildet ist.The diameter of the rod 12 is reduced above the space 11, so that between the thinner rod section 12 'thus formed and the bore 9 there is an annular channel 17 which extends to the lowest end of the section 3'. The end face of section 3 'is designed as a conical seat surface 18 (FIG. 2) which widens towards the combustion chamber 7. The seat surface 18 interacts with a correspondingly conical sealing surface 19 which is formed on the top of the mushroom-like valve cone 20 '.

Auf den Gehäuseabschnitt 3' ist eine Gewindekappe 8 aufgeschraubt, die mit ihrem unteren, im Brennraum 7 befindlichen Abschnitt den Ventilkegel 20' überspannt. Im Bereich der Sitzfläche 18 sind in der Kappe 8 sich quer zur Längsachse des Ventils erstreckende Düsenkanäle 21 vorgesehen, die zum Bilden von Brennstoffstrahlen dienen. Wie links von Fig. 2 angedeutet ist, haben die Kanäle 21 kreisrunden Querschnitt. Im Zentrum der Kappe 8 ist auf deren Innenseite eine erhöhte Anschlagfläche 8' ausgebildet, an der das Schliessstück 20 in seiner voll geöffneten Stellung anliegt. Wie Fig. 2 weiter zeigt, bildet die Gewindekappe 8 auf ihrer Innenseite unterhalb der Sitzfläche 18 eine Zylinderfläche 8'', die als Führungsfläche für das Schliessstück 20 dient, das unterhalb der Dichtfläche 19 ebenfalls zylindrisch ausgebildet ist. Die obere Begrenzung des Düsenkanals 21 ist relativ zur Sitzfläche 18 um den Abstand X zum Brennraum 7 hin versetzt, wodurch das Einspritzventil einen Vorhub ohne Oeffnung erhält.A threaded cap 8 is screwed onto the housing section 3 'and spans the valve cone 20' with its lower section located in the combustion chamber 7. In the area of the seat surface 18, nozzle channels 21 are provided in the cap 8 which extend transversely to the longitudinal axis of the valve and are used to form fuel jets. As indicated on the left of FIG. 2, the channels 21 have a circular cross section. In the center of the cap 8, a raised stop surface 8 'is formed on the inside thereof, against which the striker 20 rests in its fully open position. As further shown in FIG. 2, the threaded cap 8 forms on its inside below the seat surface 18 a cylindrical surface 8 ″, which serves as a guide surface for the striker 20, which is also cylindrical below the sealing surface 19. The upper limit of the nozzle channel 21 is offset relative to the seat surface 18 by the distance X from the combustion chamber 7, as a result of which the injection valve receives a preliminary stroke without opening.

Das Einspritzventil gemäss Fig. 1 und 2 funktioniert wie folgt: Das Ventil ist normalerweise in geschlossener Stellung, d.h. das Schliessstück 20 liegt mit seiner Dichtfläche 19 dicht an der Sitzfläche 18 an, was durch die Druckfeder 14 bewerkstelligt wird. Der Kanal 10 und der Ringraum 17 sind mit Brennstoff gefüllt, der einen Druck von weniger als 100 bar aufweist. Das Einspritzen von Brennstoff in den Brennraum 7 ist abhängig vom Förderdruck der nicht gezeigten, am Kanal 10 angeschlossenen Einspritzpumpe. In dem Moment, in dem die vom Brennstoffdruck erzeugte, auf den Ventilkegel 20' wirkende Oeffnungskraft die Schliesskraft der Druckfeder 14 überwiegt, wird das Schliessstück abwärtsverschoben, so dass der Brennstoff aus dem Ringraum 17 zu den Kanälen 21 strömen kann. Beim Durchströmen der Kanäle 21 werden Brennstoffstrahlen gebildet, die beim Eintritt in den Brennraum 7 zerstäuben und sich dort mit der komprimierten Luft vermischen, wobei der Brennstoff gezündet wird und verbrennt. Dadurch dass die obere Begrenzung der Kanäle 21 gegenüber der Sitzfläche 18 versetzt ist, beginnt das Durchströmen der Kanäle 21 etwas später als das Abheben des Ventilkegels von der Sitzfläche 18. Wenn der Förderdruck der Einspritzpumpe nachlässt, wird der Ventilkegel 20' durch die Druckfeder 14 wieder in die Schliessstellung zurückbewegt und der Einspritzvorgang ist beendet. Der jeweilige Hub des Schliessstücks ist vom Förderdruck der Einspritzpumpe und damit von der Last des Motors abhängig. Bei Vollast öffnet das Schliesstück bis zum Anliegen an der Anschlagfläche 8'.1 and 2 works as follows: The valve is normally in the closed position, ie the closing piece 20 lies with its sealing surface 19 close to the seat surface 18, which is accomplished by the compression spring 14. The channel 10 and the annular space 17 are filled with fuel which has a pressure of less than 100 bar. The injection of fuel into the combustion chamber 7 is dependent on the delivery pressure of the injection pump, not shown, connected to the channel 10. At the moment when the opening force generated by the fuel pressure and acting on the valve cone 20 ′ outweighs the closing force of the compression spring 14, the closing piece is displaced downward, so that the fuel can flow from the annular space 17 to the channels 21. When flowing through the channels 21, fuel jets are formed which atomize when entering the combustion chamber 7 and mix there with the compressed air, the fuel being ignited and combusted. As a result of that the upper limit of the channels 21 is offset from the seat surface 18, the flow through the channels 21 begins somewhat later than the lifting of the valve cone from the seat surface 18. When the delivery pressure of the injection pump decreases, the valve cone 20 'is pushed back into the pressure spring 14 Moves the closed position back and the injection process is finished. The stroke of the striker depends on the delivery pressure of the injection pump and thus on the load of the engine. At full load, the striker opens up to the abutment surface 8 '.

Bei dem Ausführungsbeispiel gemäss Fig. 3 haben die Düsenkanäle 31 im wesentlichen rechteckigen Querschnitt und die Sitzfläche 18 ist relativ zur oberen Begrenzung der Kanäle 31 gegen den Brennraum 7 hin verschoben. Abweichend von der Funktionsbeschreibung des Einspritzventils nach Fig. 1 und 2 setzt also sofort mit dem Abheben des Ventilkegels 20' von der Sitzfläche 18 der Einspritzvorgang ein.3, the nozzle channels 31 have an essentially rectangular cross section and the seat surface 18 is displaced relative to the upper boundary of the channels 31 towards the combustion chamber 7. In a departure from the functional description of the injection valve according to FIGS. 1 and 2, the injection process begins immediately when the valve cone 20 'is lifted off the seat 18.

Gemäss dem Ausführungsbeispiel nach Fig. 4 und 5 befindet sich am unteren Ende des Stangenabschnitts 12' des Schliesstücks 40 wiederum ein pilzartiger Ventilkegel 40' mit Dichtfläche 42, die mit der Sitzfläche 18 am unteren Stirnende des Abschnitts 3' zusammenwirkt. Der Ventilkegel 40' ist von einer Gewindekappe 48 umgeben, die hinsichtlich der Anschlagfläche und der zylindrischen Führungsfläche für das Schliessstück gleich ausgebildet ist wie die Gewindekappe 8. Abweichend ist dagegen, dass die hochrechteckigen Kanäle 41 grösser dimensioniert sind als in der Gewindekappe 8 gemäss Fig. 3 und dass in die Kanäle 41 je eine Schieberplatte 45 ragt, die unterhalb der Dichtfläche 42 am Schliessstück 40 befestigt sind. Die in Fig. 4 und 5 obere Seite 45' jeder Schieberplatte 45 begrenzt also nach unten den strahlbildenden Querschnitt des Düsenkanals. Die zur Längsachse parallelen Begrenzungsflächen der Schieberplatte 45 sind dichtend an den benachbarten Begrenzungsflächen jedes Kanals 41 geführt. Entsprechend der in Umfangsrichtung gemessenen Breite jedes Kanals 41 ist die Gewindekappe 48 nach oben mit einem gleichbreiten Schlitz versehen. In jedem dieser Schlitze ragt ein Schenkel 43 eines Ringes 44, der den Abschnitt 3' umschliesst, auf dem oberen Rand der Gewindekappe 48 ruht und mit der Gewindekappe gedreht werden kann. Die in Fig. 4 und 5 untere Stirnfläche 43' jedes Schenkels 43 begrenzt also den strahlbildenden Querschnitt des zugehörigen Kanals 41 auf dessen Oberseite.According to the exemplary embodiment according to FIGS. 4 and 5, at the lower end of the rod section 12 'of the striker 40 there is again a mushroom-like valve cone 40' with a sealing surface 42 which interacts with the seat surface 18 at the lower end of the section 3 '. The valve cone 40 'is surrounded by a threaded cap 48 which, in terms of the stop surface and the cylindrical guide surface for the striker, is of the same design as the threaded cap 8. The difference, however, is that the highly rectangular channels 41 are larger than in the threaded cap 8 according to FIG. 3 and that a slide plate 45 protrudes into the channels 41, which are attached to the closing piece 40 below the sealing surface 42. The upper side 45 'of each slide plate 45 in FIGS. 4 and 5 thus limits the jet-forming cross section of the nozzle channel at the bottom. The boundary surfaces of the slide plate 45 parallel to the longitudinal axis are sealing against the neighboring ones Boundary surfaces of each channel 41 out. In accordance with the width of each channel 41 measured in the circumferential direction, the threaded cap 48 is provided with a slot of the same width at the top. In each of these slots a leg 43 of a ring 44, which encloses the section 3 ', rests on the upper edge of the threaded cap 48 and can be rotated with the threaded cap. The lower end face 43 'of each leg 43 in FIGS. 4 and 5 thus delimits the beam-forming cross section of the associated channel 41 on its upper side.

Die Funktionsweise des Einspritzventils gemäss Fig. 4 und 5 ist im Prinzip gleich wie zu Fig. 1 und 2 beschrieben, d.h. wenn der Förderdruck der Einspritzpumpe die Kraft der Schliessfeder übersteigt, verschiebt sich das Schliessstück 40 in Richtung zum Brennraum 7, wodurch Brennstoff aus dem Ringraum 17 zu den Düsenkanälen 41 strömen kann. Der Strömungsquerschnitt des strahlbildenden Teils der Düsenkanäle 41 wird dabei durch den axialen Abstand der Flächen 43' und 45' bestimmt.The mode of operation of the injection valve according to FIGS. 4 and 5 is in principle the same as that described for FIGS. 1 and 2, i.e. if the delivery pressure of the injection pump exceeds the force of the closing spring, the closing piece 40 moves in the direction of the combustion chamber 7, as a result of which fuel can flow from the annular space 17 to the nozzle channels 41. The flow cross section of the jet-forming part of the nozzle channels 41 is determined by the axial distance between the surfaces 43 'and 45'.

Bei allen beschriebenen Beispielen richtet sich die Zahl der Düsenkanäle nach dem Anwendungsfall des Einspritzventils. Wird das Einspritzventil in einem Viertakt-Dieselmotor verwendet, so befindet es sich meistens im Zentrum des Brennraums und die Düsenkanäle sind gleichmässig über den Umfang des Einspritzventils verteilt angeordnet. Bei einer Anordnung des Einspritzventils in einem Zweitakt-Dieselmotor mit im Zentrum des Brennraums angeordnetem Auslassventil werden meistens mehrere Einspritzventile ausserhalb des Zentrums verteilt angeordnet. Dabei können ein oder mehrere Düsenkanäle pro Einspritzventil so angeordnet sein, dass die aus ihnen austretenden Brennstoffstrahlen sich möglichst verbrennungsgünstig im Brennraum verteilen.In all of the examples described, the number of nozzle channels depends on the application of the injection valve. If the injection valve is used in a four-stroke diesel engine, it is usually located in the center of the combustion chamber and the nozzle channels are distributed evenly over the circumference of the injection valve. If the injection valve is arranged in a two-stroke diesel engine with an outlet valve arranged in the center of the combustion chamber, a plurality of injection valves are usually arranged distributed outside the center. One or more nozzle channels per injection valve can be arranged in such a way that the fuel jets emerging from them are distributed in the combustion chamber as cheaply as possible for combustion.

Abweichend von den beschriebenen Ausführungsbeispielen kann statt einer Gewindeverbindung auch eine Klemmverbindung für die Kappe 8 oder 48 verwendet werden.In a departure from the exemplary embodiments described, a clamp connection for the cap 8 or 48 can also be used instead of a threaded connection.

Claims (7)

  1. A fuel injection valve for a reciprocating internal combustion engine, having a valve housing (1) protruding into the combustion chamber (7) of a cylinder of the engine, which on its end face faced towards the combustion chamber comprises a seat (18), and having a moveable closing part (20, 40) extending through the valve housing, which on its end faced towards the combustion chamber is provided with a mushroom-head-shaped valve cone (20', 40') protruding from the valve housing and comprising a sealing surface (18) cooperating with the seat, and which opens in the direction of flow of the fuel flowing through the valve housing, with fuel being injected under elevated pressure into the combustion chamber (7), with at the valve housing (1) a cap (8, 48) spanning the mushroom-head-shaped valve cone of the closing part being provided and with the cap (8, 48) comprising at least one nozzle duct (21, 41) for forming a fuel jet in the region of the seat (18), characterised in that the sealing surface (19, 42) of the valve cone merges into a cylindrical surface at its outer periphery and the edge between the sealing surface (42) and the cylindrical surface controls the size of the inlet cross section of the nozzle duct (21, 41).
  2. A valve according to Claim 1,
    characterised in that the mushroom-head-shaped valve cone (20', 40') of the closing part (20, 40) is guided tightly along the inside of the cap (8, 48).
  3. A valve according to Claim 1 or 2,
    characterised in that the boundary of the nozzle duct (21) faced away from the combustion chamber (7) is connected to the seat (18) of the valve housing (1).
  4. A valve according to Claim 1 or 2,
    characterised in that the boundary of the nozzle duct (31) faced away from the combustion chamber is displaced towards the combustion chamber relative to the seat (18) of the valve housing (1).
  5. A valve according to one of Claims 1 to 4,
    characterised in that at least one projection (45) is provided at the valve cone (40), which protrudes into the nozzle duct (41).
  6. A valve according to one of Claims 1 to 5,
    characterised in that the cap (8, 48) is provided detachably screwed to the valve body (3, 3').
  7. A valve according to one of Claims 1 to 6,
    characterised in that a stop face (8'), which determines the maximum travel of the closing part (20, 40), is constructed on the inside of the cap (8, 48).
EP93810093A 1993-02-17 1993-02-17 Fuel injector valve for an internal combustion piston engine Expired - Lifetime EP0611885B1 (en)

Priority Applications (7)

Application Number Priority Date Filing Date Title
DK93810093.0T DK0611885T3 (en) 1993-02-17 1993-02-17
EP93810093A EP0611885B1 (en) 1993-02-17 1993-02-17 Fuel injector valve for an internal combustion piston engine
DE59306670T DE59306670D1 (en) 1993-02-17 1993-02-17 Fuel injection valve for a reciprocating piston internal combustion engine
KR1019940002524A KR100323937B1 (en) 1993-02-17 1994-02-14 Fuel injection valve of reciprocating internal combustion engine
JP6018707A JPH06317235A (en) 1993-02-17 1994-02-15 Fuel injection nozzle for reciprocating type internal combustion engine
CN94101587A CN1050877C (en) 1993-02-17 1994-02-16 A fuel injection valve for a reciprocating internal combustion engine
FI940718A FI106739B (en) 1993-02-17 1994-02-16 Fuel injection valve for percussion internal combustion engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP93810093A EP0611885B1 (en) 1993-02-17 1993-02-17 Fuel injector valve for an internal combustion piston engine

Publications (2)

Publication Number Publication Date
EP0611885A1 EP0611885A1 (en) 1994-08-24
EP0611885B1 true EP0611885B1 (en) 1997-06-04

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP93810093A Expired - Lifetime EP0611885B1 (en) 1993-02-17 1993-02-17 Fuel injector valve for an internal combustion piston engine

Country Status (7)

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EP (1) EP0611885B1 (en)
JP (1) JPH06317235A (en)
KR (1) KR100323937B1 (en)
CN (1) CN1050877C (en)
DE (1) DE59306670D1 (en)
DK (1) DK0611885T3 (en)
FI (1) FI106739B (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4440369A1 (en) * 1994-11-11 1996-05-15 Bosch Gmbh Robert Fuel injection valve for IC engine
DE19929473B4 (en) * 1999-06-26 2005-12-08 Robert Bosch Gmbh Fuel injection valve
EP1854798A3 (en) 2000-09-19 2007-11-28 Bristol-Myers Squibb Company Fused heterocyclic succinimide compounds and analogs thereof, modulators of nuclear hormone receptor function
JP2002130087A (en) * 2000-10-23 2002-05-09 Toyota Motor Corp Fuel injection valve for cylinder injection type internal combustion engine
US20040087548A1 (en) 2001-02-27 2004-05-06 Salvati Mark E. Fused cyclic succinimide compounds and analogs thereof, modulators of nuclear hormone receptor function
JP4127703B2 (en) * 2005-09-07 2008-07-30 三菱電機株式会社 Fuel injection device
EP2397683B1 (en) * 2010-06-18 2014-12-03 Caterpillar Motoren GmbH & Co. KG Injection Nozzle System
DE102016215637A1 (en) * 2016-08-19 2018-02-22 Robert Bosch Gmbh fuel Injector
EP3404235A1 (en) * 2017-05-19 2018-11-21 Winterthur Gas & Diesel AG Large diesel motor and method for operating same
CN113623108B (en) * 2021-09-04 2022-09-09 重庆红江机械有限责任公司 Needle valve coupling part of oil sprayer of marine low-speed machine

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Publication number Priority date Publication date Assignee Title
US2351965A (en) * 1939-03-01 1944-06-20 Ex Cell O Corp Nozzle
DE1526717A1 (en) * 1966-09-06 1970-02-26 Maschf Augsburg Nuernberg Ag Injection nozzle for internal combustion engines
GB8410749D0 (en) * 1984-04-26 1984-05-31 Lumber P M P Fuel injection nozzles
US4862857A (en) * 1988-02-12 1989-09-05 Outboard Marine Corporation Fuel injection system for multi cylinder two-stroke engine
DE4034203C2 (en) * 1990-10-27 1995-02-09 Rinsum Cornelis Van Dipl Ing Fuel injection nozzle for internal combustion engines

Also Published As

Publication number Publication date
FI106739B (en) 2001-03-30
CN1050877C (en) 2000-03-29
CN1092504A (en) 1994-09-21
KR940019986A (en) 1994-09-15
DE59306670D1 (en) 1997-07-10
KR100323937B1 (en) 2002-06-20
FI940718A0 (en) 1994-02-16
DK0611885T3 (en) 1997-06-30
FI940718A (en) 1994-08-18
JPH06317235A (en) 1994-11-15
EP0611885A1 (en) 1994-08-24

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