WO1997023724A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
WO1997023724A1
WO1997023724A1 PCT/DE1996/001234 DE9601234W WO9723724A1 WO 1997023724 A1 WO1997023724 A1 WO 1997023724A1 DE 9601234 W DE9601234 W DE 9601234W WO 9723724 A1 WO9723724 A1 WO 9723724A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fuel injection
closure plate
face
valve member
Prior art date
Application number
PCT/DE1996/001234
Other languages
German (de)
French (fr)
Inventor
Detlev Potz
Guenter Lewentz
Uwe Gordon
Stefan Haug
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
Priority to EP96922757A priority Critical patent/EP0811119B1/en
Priority to JP9523188A priority patent/JPH11501382A/en
Priority to DE59608146T priority patent/DE59608146D1/en
Publication of WO1997023724A1 publication Critical patent/WO1997023724A1/en

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B05—SPRAYING OR ATOMISING IN GENERAL; APPLYING FLUENT MATERIALS TO SURFACES, IN GENERAL
    • B05B—SPRAYING APPARATUS; ATOMISING APPARATUS; NOZZLES
    • B05B1/00—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means
    • B05B1/30—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages
    • B05B1/3006—Nozzles, spray heads or other outlets, with or without auxiliary devices such as valves, heating means designed to control volume of flow, e.g. with adjustable passages the controlling element being actuated by the pressure of the fluid to be sprayed
    • 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
    • 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
    • F02M61/047—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 being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge orifices

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve known from DE-Gbm G 93 20 433.7
  • the end face of a valve body on the combustion chamber side defines an annular one
  • the pressure chamber into which an inlet line from the fuel injection pump opens.
  • the pressure chamber is delimited radially inwards by a pin projecting axially from the end face of the valve body, the cross section of which tapers conically at the end on the combustion chamber side to form a valve seat.
  • the pressure chamber is delimited by a disk-shaped valve membrane which is fastened to the valve body at its outer edge region with the interposition of a sleeve by means of a clamping nut and which has a central opening, the annular edge of which forms a sealing edge which interacts with the valve seat.
  • valve membrane with its sealing surface lies in the closed NEN state of the fuel injection valve under prestress on the valve seat, so that the pressure chamber is closed in the direction of the combustion chamber of the internal combustion engine to be supplied. If an injection is to take place, the pressure chamber is acted upon by high fuel pressure via the feed line, which, in the process, lifts the resilient valve membrane against the prestressing force with its sealing surface from the valve seat. As a result, the fuel injection takes place via the ring gap on the peg, which is analogous to known throttle pin nozzles. The end of the injection process is controlled by stopping the high pressure supply in the pressure chamber.
  • the known fuel injection valve has the disadvantage that only one injection opening is possible via which the fuel jet can be shaped relatively imprecisely.
  • the possible stroke of the valve membrane and the contact surface between the valve seat and the valve sealing surface acting as a sealing surface are limited due to the clamping on the outer edge.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage, in contrast, that by fixing the disk-shaped valve member in the center
  • valve sealing surface on the radially outer region of the valve member enables a considerably larger contact surface in the sealing region compared to the known solution.
  • Another advantage is achieved by arranging the injection openings in a closure plate delimiting the pressure space, which enables the position and number of the injection openings to be individually adapted to the respective requirements. Since the valve membrane no longer has a direct influence on the shaping of the injection jet, it can be of a very simple design.
  • the fixing of the valve member at its center can alternatively be non-positive, e.g. Clamp between two
  • the injection openings are arranged downstream of the sealing seat between the valve sealing surface and the valve seat, it being possible for the inlet openings to be arranged radially outside of the overlap with the valve member or covered by its radial edge.
  • the overflow of fuel from the pressure chamber into a space enclosed between the valve body end face and the end face of the valve member facing away from the pressure chamber is advantageously prevented by a sealing ring which is designed so that it does not impair the lifting of the valve member from the seat.
  • the necessary opening pressure of the injection valve can be adjusted by dimensioning the thickness of a spacer sleeve between the valve body and the closure plate, via which the distance between the central fixation of the valve member and its contact with the valve seat can be changed in the outer radial area.
  • FIG. 1 shows a longitudinal section through a first exemplary embodiment of the injection valve
  • FIG. 2 shows an enlarged detail from FIG. 1 with the representation of the valve member area essential to the invention
  • FIG. 3 shows a detail from a second exemplary embodiment in which the valve member welds to the pin of the valve body
  • FIG. 4 shows a detail from a third exemplary embodiment, in which the inlet opening of the injection opening is covered by the valve member (valve membrane).
  • the first exemplary embodiment of the fuel injection valve according to the invention shown in an enlarged detail in FIG. 1 and in FIG. 2 has a rotationally symmetrical valve body 1, at the inflow end of which a connection 3 for a fuel injection pump (not shown) leading away
  • the valve body 1 also has one with the fuel injection line connected inlet channel 5, which is formed by an axial through hole which extends from the upper end face in the area of the connection 3 of the valve body 1 to a pin 9 projecting axially from the lower, combustion chamber-side end face 7 of the valve body 1.
  • valve member 11 On the end face of the valve member 11 facing away from the valve body 1, there is a further pin 15 of a closure plate 17 on the central area of the valve member 11, which covers the contact area of the pin 9, so that the valve member 11 is clamped between the pins 9 and 15 and opposite the valve body 1 is fixed in its position.
  • the closure plate having the second pin 15 is disc-shaped and is clamped axially by a clamping nut 19 encompassing its radially outer edge against the combustion-chamber-side end face 7 of the valve body 1, a spacer sleeve 21 being clamped between the closure plate and the end face 7 of the valve member 1.
  • the pin 15 of the closure plate 17 has a connecting channel 23 which, starting from its end overlap with the passage opening 13 in the valve member 11, opens into a pressure chamber 25 formed between the valve member 11 and the closure plate 17.
  • Connection channel 23 is preferably by an axial Blind bore and a transverse bore leading away from this.
  • valve sealing surface 27 which, under prestress (internal stress of the valve membrane), bears sealingly against an annular valve seat surface 29 formed by part of the end face of the closure plate 17 facing away from the combustion chamber.
  • Injection openings 31 can be freely selected and can be adapted to the respective conditions. To avoid an overflow of fuel in an enclosed between the end of the valve member 11 facing away from the pressure chamber 25 and the end face 7 of the valve body 1
  • Space 33 is a sealing ring 35 clamped between the radially outer edge of the closure plate 17 and the spacer sleeve 21, which rests on the edge of the valve member 11 facing away from the pressure chamber and is designed such that it does not impair the lifting movement of the free end of the valve member 11.
  • an annular shoulder 37 is preferably provided on the radially outward-pointing edge region of the closure plate 17, via which the thickness of the closure plate 17 increases on the outer circumference in the direction of the valve body 1.
  • the fuel injection valve for internal combustion engines works in the following manner.
  • the injection valve is supplied with high-pressure fuel in a known manner from the injection pump via the injection line, which continues through the inlet channel 5 into the fuel-filled pressure chamber 25.
  • the fuel under high pressure lifts the free outer edge of the valve member 11 with the valve sealing surface 27 against the biasing force of the resilient valve member 11 (valve membrane) from the valve seat 29, so that an opening cross section is opened, via which the fuel from the pressure chamber 25 to the Injection openings 31 flows through which it continues into the combustion chamber
  • the sealing ring 35 which is preferably made of temperature-resistant and fuel-resistant rubber, prevents fuel from flowing into the space 33.
  • the fuel injection is terminated by the high-pressure fuel supply to the injection valve being interrupted and, as a result, the pressure in the pressure chamber 25 falling below the necessary injection pressure, so that the valve member 11 with its valve sealing surface 27 is in contact with the
  • Valve seat surface 29 returns and the injector closes.
  • the valve Function and the reset function integrated in one component, namely the valve member 11.
  • the injection pressure can be adjusted via the dimensioning of the thickness of the spacer sleeve 21, via which the axial distance between the central fixation and the outer contact of the valve member 11 and thus its pretensioning force can be adjusted.
  • the second exemplary embodiment shown in a detail in FIG. 3 differs from the first exemplary embodiment in the design of the central fixing and fastening of the valve member 11 on the pin 9 of the valve body 1, the valve member 11 being welded to the pin 9 here, preferably laser-welded .
  • This fastening of the valve member 11 has the advantage that there is no need for a pin on the closure plate 17, which considerably simplifies its construction.
  • Closure plate 17 which is formed here in one piece with the spacer sleeve.

Abstract

A fuel injection valve for internal combustion engines with a valve body (1) at the combustion chamber side of which there is an annular pressure chamber (25) connected to a supply channel (5) and bounded by an elastic valve member (11) which bears under its own tension via a valve sealing surface (27) on a fixed valve seat (29), from which it can be lifted by pressure in the pressure chamber (25). The aperture cross-section thereby controlled is downstream of at least one injection aperture (31) into the combustion chamber of the internal combustion engine. Here, the centre of the elastic valve member (11), which takes the form of a diaphragm, is secured against the valve body (1) and its radially outwardly directed edge region forms the elastic sealing surface (27) which can be elastically raised from the valve seat (29).

Description

Kraftstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einem derartigen aus dem DE-Gbm G 93 20 433.7 be¬ kannten Kraftstoffeinspritzventil begrenzt die brennraumsei- tige Stirnfläche eines Ventilkörpers einen ringförmigenThe invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. In such a fuel injection valve known from DE-Gbm G 93 20 433.7, the end face of a valve body on the combustion chamber side defines an annular one
Druckraum, in den eine Zulaufleitung von der Kraftstoffein- spritzpumpe mündet. Der Druckraum ist radial einwärts von einem axial von der Stirnfläche des Ventilkörpers vorstehen¬ den Zapfen begrenzt, dessen Querschnitt sich am brennraum- seitigen Ende unter Bildung eines Ventilsitzes konisch ver¬ jüngt. An seinem brennraumseitigen Ende wird der Druckraum von einer scheibenförmigen Ventilmembran begrenzt, die an ihrem Außenrandbereich unter Zwischenschaltung einer Hülse mittels einer Spannmutter am Ventilkörper befestigt ist und die eine zentrale Öffnung aufweist, deren Ringkante eine mit dem Ventilsitz zusammenwirkende Dichtkante bildet. Dabei liegt die Ventilmembran mit ihrer Dichtfläche im geschlosse- nen Zustand des Kraftstoffeinspritzventils unter Vorspannung dichtend am Ventilsitz an, so daß der Druckraum in Richtung Brennraum der zu versorgenden Brennkraftmaschine verschlos¬ sen ist. Soll eine Einspritzung erfolgen, wird der Druckraum über die Zulaufleitung mit hohem Kraftstoffdruck beauf¬ schlagt, der dabei die federnde Ventilmembran entgegen der Vorspannkraft mit ihrer Dichtfläche vom Ventilsitz abhebt. Über den dabei aufgesteuerten Ringspalt am Zapfen erfolgt in Folge die Kraftstoffeinspritzung analog zu bekannten Dros- seizapfendüsen. Das Ende des Einspritzvorganges wird durch das Beenden der Hochdruckzufuhr in den Druckraum gesteuert. Dabei weist das bekannte Kraftstoffeinspritzventil jedoch den Nachteil auf, daß nur eine Einspritzöffnung möglich ist, über die sich der Kraftstoffstrahl relativ ungenau formen läßt. Zudem sind der mögliche Hub der Ventilmembran und die als Dichtfläche wirkende Kontaktfläche zwischen Ventilsitz und Ventildichtfläche aufgrund der Einspannung am äußeren Rand begrenzt.Pressure chamber into which an inlet line from the fuel injection pump opens. The pressure chamber is delimited radially inwards by a pin projecting axially from the end face of the valve body, the cross section of which tapers conically at the end on the combustion chamber side to form a valve seat. At its end on the combustion chamber side, the pressure chamber is delimited by a disk-shaped valve membrane which is fastened to the valve body at its outer edge region with the interposition of a sleeve by means of a clamping nut and which has a central opening, the annular edge of which forms a sealing edge which interacts with the valve seat. The valve membrane with its sealing surface lies in the closed NEN state of the fuel injection valve under prestress on the valve seat, so that the pressure chamber is closed in the direction of the combustion chamber of the internal combustion engine to be supplied. If an injection is to take place, the pressure chamber is acted upon by high fuel pressure via the feed line, which, in the process, lifts the resilient valve membrane against the prestressing force with its sealing surface from the valve seat. As a result, the fuel injection takes place via the ring gap on the peg, which is analogous to known throttle pin nozzles. The end of the injection process is controlled by stopping the high pressure supply in the pressure chamber. However, the known fuel injection valve has the disadvantage that only one injection opening is possible via which the fuel jet can be shaped relatively imprecisely. In addition, the possible stroke of the valve membrane and the contact surface between the valve seat and the valve sealing surface acting as a sealing surface are limited due to the clamping on the outer edge.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil für Brenn¬ kraftmaschinen mit den kennzeichnenden Merkmalen des Patent¬ anspruchs 1 hat demgegenüber den Vorteil, daß durch das mittige Fixieren des scheibenförmigen VentilgliedesThe fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage, in contrast, that by fixing the disk-shaped valve member in the center
{Ventilmembran) eine größere freie Biegelänge und damit ein größerer darstellbarer Hub am Ventilglied zur Verfügung steht, was sich vorteilhaft auf die Membranbeanspruchung und somit auf deren Lebensdauer auswirkt. Zudem ermöglicht das Vorsehen der Ventildichtfläche am radial äußeren Bereich des Ventilgliedes gegenüber der bekannten Lösung eine erheblich größere Kontaktfläche im Dichtbereich. Ein weiterer Vorteil wird durch das Anordnen der Einspritzöffnungen in einer den Druckraum begrenzenden Verschlußplatte erreicht, was eine individuelle Anpassung der Lage und Anzahl der Einspritzöffnungen an die jeweiligen Erfordernisse ermöglicht. Da die Ventilmembran nunmehr keinen direkten Einfluß mehr auf die Formung des Einspritzstrahles ausübt, kann sie sehr einfach ausgebildet sein.{Valve membrane) a larger free bending length and thus a larger representable stroke is available on the valve member, which has an advantageous effect on the membrane stress and thus on its service life. In addition, the provision of the valve sealing surface on the radially outer region of the valve member enables a considerably larger contact surface in the sealing region compared to the known solution. Another advantage is achieved by arranging the injection openings in a closure plate delimiting the pressure space, which enables the position and number of the injection openings to be individually adapted to the respective requirements. Since the valve membrane no longer has a direct influence on the shaping of the injection jet, it can be of a very simple design.
Die Fixierung des Ventilgliedes an seiner Mitte kann dabei alternativ kraftschlüssig, z.B. Einspannen zwischen zweiThe fixing of the valve member at its center can alternatively be non-positive, e.g. Clamp between two
Anschlägen oder stoffschlüssig, z.B. Verschweißen an einem Anschlag erfolgen.Stops or cohesively, e.g. Welding done at a stop.
Die Einspritzöffnungen sind dem Dichtsitz zwischen Ventildichtfläche und Ventilsitz stromabwärts nachgeordnet, wobei die Eintrittsöffnungen radial außerhalb der Überdeckung mit dem Ventilglied oder von dessen radialem Rand überdeckt angeordnet sein können.The injection openings are arranged downstream of the sealing seat between the valve sealing surface and the valve seat, it being possible for the inlet openings to be arranged radially outside of the overlap with the valve member or covered by its radial edge.
Das Überströmen von Kraftstoff aus dem Druckraum in einen zwischen der Ventilkörperstirnfläche und der dem Druckraum abgewandten Stirnfläche des Ventilgliedes eingeschlossenen Raum wird dabei in vorteilhafter Weise durch einen Dichtring verhindert, der dabei so ausgebildet ist, daß er das Abheben des Ventilgliedes vom Sitz nicht beeinträchtigt. Der notwendige Öffnungsdruck des Einspritzventils ist durch die Dimensionierung der Stärke einer Distanzhülse zwischen dem Ventilkörper und der Verschlußplatte einstellbar, über die der Abstand zwischen der mittigen Fixierung des Ventilgliedes und dessen Anlage am Ventilsitz im äußeren radialen Bereich veränderbar ist. Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Ansprüchen entnehmbar.The overflow of fuel from the pressure chamber into a space enclosed between the valve body end face and the end face of the valve member facing away from the pressure chamber is advantageously prevented by a sealing ring which is designed so that it does not impair the lifting of the valve member from the seat. The necessary opening pressure of the injection valve can be adjusted by dimensioning the thickness of a spacer sleeve between the valve body and the closure plate, via which the distance between the central fixation of the valve member and its contact with the valve seat can be changed in the outer radial area. Further advantages and advantageous embodiments of the subject matter of the invention can be found in the drawing, the description and the claims.
Zeichnungdrawing
Drei Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen sind in der Zeichnung dargestellt und werden im folgenden näher erläutert.Three exemplary embodiments of the fuel injection valve for internal combustion engines according to the invention are shown in the drawing and are explained in more detail below.
Es zeigen die Figur 1 einen Längsschnitt durch ein erstes Ausführungsbeispiel des Einspritzventils, die Figur 2 einen vergrößerten Ausschnitt aus der Figur 1 mit der Darstellung des erfindungswesentlichen Ventilgliedbereiches, die Figur 3 einen Ausschnitt aus einem zweiten Ausführungsbeispiel, bei dem das Ventilglied am Zapfen des Ventilkörpers verschweißt ist und die Figur 4 einen Ausschnitt aus einem dritten Ausführungsbeispiel, bei dem die Eintrittsöffnung der Einspritzöffnung vom Ventilglied (Ventilmembran) überdeckt wird.FIG. 1 shows a longitudinal section through a first exemplary embodiment of the injection valve, FIG. 2 shows an enlarged detail from FIG. 1 with the representation of the valve member area essential to the invention, and FIG. 3 shows a detail from a second exemplary embodiment in which the valve member welds to the pin of the valve body and FIG. 4 shows a detail from a third exemplary embodiment, in which the inlet opening of the injection opening is covered by the valve member (valve membrane).
Beschreibung der AusführungsbeispieleDescription of the embodiments
Das in der Figur 1 und in der Figur 2 in einem vergrößerten Ausschnitt dargestellte erste Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils weist einen rotationssyτnmetrischen Ventilkörper 1 auf, an dessen Zulaufende ein Anschluß 3 für eine nicht dargestellte, von einer Kraftstoffeinspritzpumpe abführendeThe first exemplary embodiment of the fuel injection valve according to the invention shown in an enlarged detail in FIG. 1 and in FIG. 2 has a rotationally symmetrical valve body 1, at the inflow end of which a connection 3 for a fuel injection pump (not shown) leading away
Kraftstoffeinspritzleitung vorgesehen ist. Der Ventilkörper 1 weist weiterhin einen mit der Kraftstoffeinspritzleitung verbundenen Zulaufkanal 5 auf, der durch eine axiale Durchgangsbohrung gebildet ist, die sich von der oberen Stirnseite im Bereich des Anschlusses 3 des Ventilkörpers 1 bis in einen axial von der unteren, brennraumseitigen Stirnfläche 7 des Ventilkörpers 1 vorstehenden Zapfen 9 erstreckt. An der Stirnfläche des Zapfens 9 des Ventilkörpers 1 liegt ein als gewölbte Ventilmembran ausgebildetes scheibenförmiges Ventilglied 11 aus einem federnden Werkstoff mit seinem mittigen Bereich an, wobei im Bereich der Überdeckung mit dem Zulaufkanal 5 im Zapfen 9 eine Durchgangsδffnung 13 im Ventilglied 11 angeordnet ist. An der dem Ventilkörper l abgewandten Stirnfläche des Ventilgliedes 11 liegt ein weiterer Zapfen 15 einer Verschlußplatte 17 am mittigen Bereich des Ventilgliedes 11 an, der den Anlagebereich des Zapfens 9 überdeckt, so daß das Ventilglied 11 zwischen den Zapfen 9 und 15 eingespannt und gegenüber dem Ventilkörper 1 in seiner Lage fixiert ist. Die den zweiten Zapfen 15 aufweisende Verschlußplatte ist dabei scheibenförmig ausgebildet und wird von einer ihren radial äußeren Rand umgreifenden Spannmutter 19 axial gegen die brennraumseitige Stirnfläche 7 des Ventilkorpers 1 verspannt, wobei zwischen der Verschlußplatte und der Stirnfläche 7 des Ventilgliedes 1 eine Distanzhülse 21 eingespannt ist.Fuel injection line is provided. The valve body 1 also has one with the fuel injection line connected inlet channel 5, which is formed by an axial through hole which extends from the upper end face in the area of the connection 3 of the valve body 1 to a pin 9 projecting axially from the lower, combustion chamber-side end face 7 of the valve body 1. On the end face of the pin 9 of the valve body 1, there is a disk-shaped valve member 11 made of a resilient material with a central area formed as a curved valve membrane, a passage opening 13 being arranged in the valve member 11 in the area of the overlap with the inlet channel 5 in the pin 9. On the end face of the valve member 11 facing away from the valve body 1, there is a further pin 15 of a closure plate 17 on the central area of the valve member 11, which covers the contact area of the pin 9, so that the valve member 11 is clamped between the pins 9 and 15 and opposite the valve body 1 is fixed in its position. The closure plate having the second pin 15 is disc-shaped and is clamped axially by a clamping nut 19 encompassing its radially outer edge against the combustion-chamber-side end face 7 of the valve body 1, a spacer sleeve 21 being clamped between the closure plate and the end face 7 of the valve member 1.
Der Zapfen 15 der Verschlußplatte 17 weist einen Verbindungskanal 23 auf, der ausgehend von seiner stirnseitigen Überdeckung mit der Durchgangsδffnung 13 im Ventilglied 11 in einen zwischen dem Ventilglied 11 und der Verschlußplatte 17 gebildeten Druckraum 25 mündet. DerThe pin 15 of the closure plate 17 has a connecting channel 23 which, starting from its end overlap with the passage opening 13 in the valve member 11, opens into a pressure chamber 25 formed between the valve member 11 and the closure plate 17. The
Verbindungskanal 23 ist dabei vorzugsweise durch eine axiale Sackbohrung und eine von dieser abführenden Querbohrung gebildet.Connection channel 23 is preferably by an axial Blind bore and a transverse bore leading away from this.
Der zwischen dem gewölbten Ventilglied 11 und der brennraumabgewandten Stirnseite der Verschlußplatte 17 begrenzte Druckraum 25 ist durch die federnde Anlage des freien, radial auswärts weisenden Randbereiches des Ventilgliedes 11 an der Verschlußplatte 17 abgedichtet. Dabei bildet der radiale Außenwandbereich der Brennraumzugewandten Stirnfläche des Ventilgliedes 11 eine Ventildichtfläche 27 die unter Vorspannung (Eigenspannung der Ventilmembran) an einer durch einen Teil der brennraumabgewandten Stirnfläche der Verschlußplatte 17 gebildeten ringförmigen Ventilsitzfläche 29 dichtend anliegt. Dabei sind diesem an der Anlage von Ventilsitz 29 und Ventildichtfläche 27 gebildeten Dichtsitz stromabwärts Einspritzöffnungen 31 nachgeordnet, die als radial auswärts des Dichtsitzes liegende Bohrungen in der Verschlußplatte 17 ausgebildet sind. Die Anzahl und Anordnung dieser in den Brennraum der zu versorgenden Brennkraftmaschine mündendenThe pressure space 25 limited between the curved valve member 11 and the end of the closure plate 17 facing away from the combustion chamber is sealed by the resilient contact of the free, radially outward-pointing edge region of the valve member 11 on the closure plate 17. The radial outer wall region of the end face of the valve member 11 facing the combustion chamber forms a valve sealing surface 27 which, under prestress (internal stress of the valve membrane), bears sealingly against an annular valve seat surface 29 formed by part of the end face of the closure plate 17 facing away from the combustion chamber. Injection openings 31, which are formed as bores in the closure plate 17 lying radially outward of the sealing seat, are arranged downstream of this sealing seat formed on the system of valve seat 29 and valve sealing surface 27. The number and arrangement of these open into the combustion chamber of the internal combustion engine to be supplied
Einspritzöffnungen 31 ist dabei frei wählbar und kann an die jeweiligen Verhältnisse angepaßt werden. Zur Vermeidung eines Überströmens von Kraftstoff in einen zwischen der dem Druckraum 25 abgewandten Stirnseite des Ventilgliedes 11 und der Stirnfläche 7 des Ventilkorpers 1 eingeschlossenenInjection openings 31 can be freely selected and can be adapted to the respective conditions. To avoid an overflow of fuel in an enclosed between the end of the valve member 11 facing away from the pressure chamber 25 and the end face 7 of the valve body 1
Raumes 33 ist ein Dichtring 35 zwischen dem radial äußeren Rand der Verschlußplatte 17 und der Distanzhülse 21 eingespannt, der am druckraumabgewandten Rand des Ventilgliedes 11 anliegt und so ausgebildet ist, daß er die Abhebbewegung des freien Endes des Ventilgliedes 11 nicht beeinträchtigt. Dabei ist am radial auswärts weisenden Randbereich der Verschlußplatte 17 vorzugsweise ein Ringabsatz 37 vorgesehen, über den sich die Stärke der Verschlußplatte 17 am äußeren Umfang in Richtung Ventilkörper 1 hin vergrößert.Space 33 is a sealing ring 35 clamped between the radially outer edge of the closure plate 17 and the spacer sleeve 21, which rests on the edge of the valve member 11 facing away from the pressure chamber and is designed such that it does not impair the lifting movement of the free end of the valve member 11. In this case, an annular shoulder 37 is preferably provided on the radially outward-pointing edge region of the closure plate 17, via which the thickness of the closure plate 17 increases on the outer circumference in the direction of the valve body 1.
Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen arbeitet in folgender Weise.The fuel injection valve for internal combustion engines works in the following manner.
Soll eine Kraftstoffeinspritzung am Einspritzventil erfolgen, wird dem Einspritzventil in bekannter Weise von der Einspritzpumpe über die Einspritzleitung ein Kraftstoffhochdruck zugeführt, der sich über den Zulaufkanal 5 in den kraftstoffgefüllten Druckraum 25 fortsetzt. Dort hebt der unter hohem Druck stehende Kraftstoff den freien Außenrand des Ventilgliedes 11 mit der Ventildichtfläche 27 entgegen der Vorspannkraft des federnden Ventilgliedes 11 (Ventilmembran) vom Ventilsitz 29 ab, so daß ein Öffnungsquerschnitt aufgesteuert wird, über den der Kraftstoff aus dem Druckraum 25 zu den Einspritzδffnungen 31 strömt, über die er weiter in den Brennraum derIf fuel injection is to take place at the injection valve, the injection valve is supplied with high-pressure fuel in a known manner from the injection pump via the injection line, which continues through the inlet channel 5 into the fuel-filled pressure chamber 25. There, the fuel under high pressure lifts the free outer edge of the valve member 11 with the valve sealing surface 27 against the biasing force of the resilient valve member 11 (valve membrane) from the valve seat 29, so that an opening cross section is opened, via which the fuel from the pressure chamber 25 to the Injection openings 31 flows through which it continues into the combustion chamber
Brennkraftmaschine gelangt. Dabei unterbindet der vorzugsweise aus temperatur- und kraftstoffbeständigem Gummi ausgebildete Dichtring 35 ein Überströmen von Kraftstoff in den Raum 33.Comes to the internal combustion engine. The sealing ring 35, which is preferably made of temperature-resistant and fuel-resistant rubber, prevents fuel from flowing into the space 33.
Die Kraftstoffeinspritzung wird beendet indem die Kraftstoffhochdruckzufuhr zum Einspritzventil unterbrochen wird und in Folge der Druck im Druckraum 25 unter den notwendigen Einspritzdruck absinkt, so daß das Ventilglied 11 mit seiner Ventildichtfläche 27 zur Anlage an dieThe fuel injection is terminated by the high-pressure fuel supply to the injection valve being interrupted and, as a result, the pressure in the pressure chamber 25 falling below the necessary injection pressure, so that the valve member 11 with its valve sealing surface 27 is in contact with the
Ventilsitzfläche 29 zurückkehrt und das Einspritzventil schließt. Dabei sind in vorteilhafter Weise die Ventil- Funktion und die Rückstell-Funktion in einem Bauteil, nämlich dem Ventilglied 11 integriert.Valve seat surface 29 returns and the injector closes. In this case, the valve Function and the reset function integrated in one component, namely the valve member 11.
Der Einspritzdruck läßt sich dabei über die Dimensionierung der Dicke der Distanzhülse 21 einstellen, über die der axiale Abstand zwischen mittiger Fixierung und äußerer Anlage des Ventilgliedes 11 und somit seine Vorspannkraft einstellbar ist.The injection pressure can be adjusted via the dimensioning of the thickness of the spacer sleeve 21, via which the axial distance between the central fixation and the outer contact of the valve member 11 and thus its pretensioning force can be adjusted.
Das in der Figur 3 in einem Ausschnitt dargestellte zweite Ausführungsbeispiel unterscheidet sich zum ersten Ausführungsbeispiel in der Ausbildung der mittigen Fixierung und Befestigung des Ventilgliedes 11 am Zapfen 9 des Ventilkörpers 1, wobei das Ventilglied 11 hier mit dem Zapfen 9 verschweißt, vorzugsweise Laser-verschweißt ist. Dabei hat diese Befestigung des Ventilgliedes 11 den Vorteil, daß auf einen Zapfen an der Verschlußplatte 17 verzichtet werden kann, was deren Aufbau wesentlich vereinfacht.The second exemplary embodiment shown in a detail in FIG. 3 differs from the first exemplary embodiment in the design of the central fixing and fastening of the valve member 11 on the pin 9 of the valve body 1, the valve member 11 being welded to the pin 9 here, preferably laser-welded . This fastening of the valve member 11 has the advantage that there is no need for a pin on the closure plate 17, which considerably simplifies its construction.
Bei dem in der Figur 4 in einem weiteren Ausschnitt dargestellten dritten Ausführungsbeispiel überdeckt das federnde Ventilglied 11 mit seinem äußeren, die Ventildichtfläche 27 tragenden Rand vollständig die Eintrittsöffnung der Einspritzöffnung 31 in derIn the third exemplary embodiment shown in a further detail in FIG. 4, the resilient valve member 11, with its outer edge carrying the valve sealing surface 27, completely covers the inlet opening of the injection opening 31 in FIG
Verschlußplatte 17, die hier einstückig mit der Distanzhülse ausgebildet ist.Closure plate 17, which is formed here in one piece with the spacer sleeve.
Es ist somit mit dem erfindungsgemäßen Kraftstoffeinspritzventil auf konstruktiv einfache Weise möglich erhebliche Vorteile gegenüber bekannten sogenannten Membrandüsen hinsichtlich Beanspruchung und Spritzlochanordnung- und Geometrie zu erreichen. It is thus possible with the fuel injection valve according to the invention in a structurally simple manner, considerable advantages over known so-called To achieve membrane nozzles with regard to stress and spray hole arrangement and geometry.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkorper (1) , an dessen brennraumseitigen Ende ein mit einem Zulaufkanal (5) verbundener ringförmiger Druckraum1. Fuel injection valve for internal combustion engines with a valve body (1), at the combustion chamber end of which an annular pressure chamber connected to an inlet channel (5)
(25) vorgesehen ist, der von einem federnden Ventilglied (11) begrenzt wird, das unter Eigenspannung mit einer(25) is provided, which is limited by a resilient valve member (11) which is under internal tension with a
Ventildichtfläche (27) an einem ortsfesten Ventilsitz (29) anliegt und vom Druck im Druckraum (25) von diesem abhebbar ist, wobei dem dabei aufgesteuerten Öffnungsquerschnitt wenigstens eine Einspritzöffnung (31) in den Brennraum der Brennkraftmaschine nachgeordnet ist, dadurch gekennzeichnet, daß das als Membran ausgebildete federnde Ventilglied (11) in seiner Mitte gegenüber dem Ventilkörper (1) fixiert ist und mit seinem radial auwärts weisenden Randbereich die federnd vom Ventilsitz (29) abhebbare Ventildichtfläche (27) bildet.Valve sealing surface (27) bears against a stationary valve seat (29) and can be lifted off from the pressure in the pressure chamber (25), the opening cross section being controlled being followed by at least one injection opening (31) in the combustion chamber of the internal combustion engine, characterized in that the as Membrane-type resilient valve member (11) is fixed in its center with respect to the valve body (1) and forms with its radially outward-facing edge region the valve sealing surface (27) which can be lifted off the valve seat (29).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das federnde Ventilglied (11) in seinem mittigen Bereich zwischen einem axial von der brennraumseitigen Stirnfläche (7) des Ventilkörpers (1) vorstehenden Zapfen (9) und einem weiteren axial von der brennraumabgewandten Stirnfläche einer am Ventilkörper (1) befestigten Verschlußplatte (17) vorstehenden zweiten Zapfen (15) eingespannt ist.2. Fuel injection valve according to claim 1, characterized in that the resilient valve member (11) in its central region between an axially from the combustion chamber end face (7) of the valve body (1) projecting pin (9) and another axially from the combustion chamber facing end face one on the valve body (1) attached closure plate (17) projecting second pin (15) is clamped.
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der zwischen der Verschlußplatte (17) und dem federnden Ventilglied (11) eingeschlossene Ringraum den Druckraum (25) bildet.3. Fuel injection valve according to claim 2, characterized in that the annular space enclosed between the closure plate (17) and the resilient valve member (11) forms the pressure space (25).
4. Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß der Zulaufkanal (5) im Ventilkörper (1) an der Stirnfläche des Zapfens (9) an eine Durchgangsδffnung (13) im mittigen Bereich des Ventilgliedes (11) angrenzt, an die sich andererseits ein Verbindungskanal (23) im Zapfen (15) der Verschlußplatte (17) anschließt, der in den Druckraum (25) mündet.4. Fuel injection valve according to claim 3, characterized in that the inlet channel (5) in the valve body (1) on the end face of the pin (9) adjoins a Durchgangsδffnung (13) in the central region of the valve member (11), which on the other hand Connecting channel (23) in the pin (15) of the closure plate (17) connects, which opens into the pressure chamber (25).
5. Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß der Verbindungskanal (23) im Zapfen (15) der Verschlußkappe (17) durch eine axiale Sackbohrung gebildet ist, die von einer Querbohrung angeschnitten wird.5. Fuel injection valve according to claim 4, characterized in that the connecting channel (23) in the pin (15) of the closure cap (17) is formed by an axial blind bore which is cut by a transverse bore.
6. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß die Verschlußplatte (17) mittels einer ihren radial äußeren Rand umgreifenden Spannmutter (19) axial gegen den Ventilkörper (1) verspannt ist, wobei zwischen der Stirnfläche (7) des Ventilkörpers (1) und der Verschlußplatte (17) eine Distanzhülse (21) eingespannt ist.6. Fuel injection valve according to claim 2, characterized in that the closure plate (17) is clamped axially against the valve body (1) by means of a clamping nut (19) encompassing its radially outer edge, between the end face (7) of the valve body (1) and the closure plate (17) a spacer sleeve (21) is clamped.
7. Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß an einem radial äußeren Bereich der dem Druckraum (25) zugewandten Stirnfläche der Verschlußplatte (17) eine kreisringförmiger Ventilsitzfläche (29) gebildet ist, an dem das Ventilglied (11) mit seiner am freien radial äußeren Randbereich angeordneten Ventildichtfläche (27) unter Vorspannung anliegt.7. Fuel injection valve according to claim 3, characterized in that an annular valve seat surface (29) is formed on a radially outer region of the end face of the closure plate (17) facing the pressure chamber (25) against which the valve member (11) with its valve sealing surface (27) arranged on the free, radially outer edge area rests under prestress.
8. Kraftstoffeinspritzventil nach Anspruch 7, dadurch gekennzeichnet, daß die Verschlußplatte (17) an ihrem radial äußeren Randbereich der druckraumzugewandten Stirnfläche einen Ringabsatz (37) aufweist, über den sich die Stärke der Verschlußplatte (17) im Randbereich in Richtung Ventilkörper (1) vergrößert, wobei zwischen dem Rand des Ventilgliedes (11) und dem Ringabsatz (37) ein Spiel verbleibt.8. Fuel injection valve according to claim 7, characterized in that the closure plate (17) at its radially outer edge region of the end face facing the pressure chamber has a ring shoulder (37) over which the thickness of the closure plate (17) increases in the edge region in the direction of the valve body (1) , A game remains between the edge of the valve member (11) and the ring shoulder (37).
9. Kraftstoffeinspritzventil nach Anspruch 7, dadurch gekennzeichnet, daß eine Vielzahl von Einspritzöffnungen (31) in der Verschlußplatte (17) vorgesehen sind, die radial auswärts der ringförmigen Ventilsitzfläche (29) von der den Druckraum (25) begrenzenden Stirnfläche der Verschlußplatte (17) abführen und in den Brennraum der Brennkraftmaschine münden.9. Fuel injection valve according to claim 7, characterized in that a plurality of injection openings (31) in the closure plate (17) are provided, which radially outward of the annular valve seat surface (29) from the pressure space (25) delimiting the end face of the closure plate (17) dissipate and open into the combustion chamber of the internal combustion engine.
10. Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß zwischen der Verschlußplatte (17) und der Distanzhülse (21) ein Dichtring (35) vorgesehen ist, der an der druckraumabgewandten Stirnfläche des Ventilgliedes (11) anliegend, ein Überströmen von Kraftstoff in einen zwischen dem Ventilglied (11) und der Stirnfläche (7) des Ventilkörpers (1) gebildeten Raum (33) verhindert.10. Fuel injection valve according to claim 6, characterized in that between the closure plate (17) and the spacer sleeve (21) a sealing ring (35) is provided, which rests on the end face of the valve member (11) facing away from the pressure chamber, an overflow of fuel into one between the valve member (11) and the end face (7) of the valve body (1) formed space (33) prevented.
11. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das federnde Ventilglied (11) als gewölbte Scheibe aus federndem Material ausgebildet ist. 11. Fuel injection valve according to claim 1, characterized in that the resilient valve member (11) is designed as a curved disc made of resilient material.
12. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß das federnde Ventilglied (11) in seinem mittigen Bereich mit einem axial von der brennraumseitigen Stirnfläche (7) des Ventilkörpers (1) vorstehenden Zapfen (5) verschweißt ist. 12. Fuel injection valve according to claim 1, characterized in that the resilient valve member (11) is welded in its central region with a pin (5) projecting axially from the combustion chamber-side end face (7) of the valve body (1).
PCT/DE1996/001234 1995-12-23 1996-07-09 Fuel injection valve for internal combustion engines WO1997023724A1 (en)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP96922757A EP0811119B1 (en) 1995-12-23 1996-07-09 Fuel injection valve for internal combustion engines
JP9523188A JPH11501382A (en) 1995-12-23 1996-07-09 Fuel injection valve for internal combustion engine
DE59608146T DE59608146D1 (en) 1995-12-23 1996-07-09 FUEL INJECTION VALVE FOR INTERNAL COMBUSTION ENGINES

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19548540.8 1995-12-23
DE19548540A DE19548540A1 (en) 1995-12-23 1995-12-23 Fuel injection valve for internal combustion engines

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WO1997023724A1 true WO1997023724A1 (en) 1997-07-03

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EP (1) EP0811119B1 (en)
JP (1) JPH11501382A (en)
KR (1) KR19980702022A (en)
CN (1) CN1075871C (en)
DE (2) DE19548540A1 (en)
RU (1) RU2161723C2 (en)
WO (1) WO1997023724A1 (en)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10064802A1 (en) * 2000-12-22 2002-06-27 Bosch Gmbh Robert Fuel injection valve for combustion engine has valve sealing surface on radially outer edge of valve element biased in center section by holding element with respect to contact with valve seat
DE102014215475A1 (en) * 2014-08-05 2016-02-11 Robert Bosch Gmbh Injector, in particular injection injector for gaseous fuel
CN105396717B (en) * 2015-12-24 2017-10-24 上海震界自动化设备制造有限公司 Gas control diaphragm type nozzle
CN110538754B (en) * 2019-09-10 2021-06-08 魏新 Wood spraying device
CN111016434B (en) * 2019-12-25 2021-07-27 西安交通大学 Thin film type ink-jet printing head based on extrusion mode

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1595624A (en) * 1924-03-17 1926-08-10 Scott Philip Lane Atomizer valve
US4635849A (en) * 1984-05-03 1987-01-13 Nippon Soken, Inc. Piezoelectric low-pressure fuel injector
DE9320433U1 (en) * 1993-04-10 1994-09-29 Bosch Gmbh Robert Fuel injection nozzle for internal combustion engines

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1595624A (en) * 1924-03-17 1926-08-10 Scott Philip Lane Atomizer valve
US4635849A (en) * 1984-05-03 1987-01-13 Nippon Soken, Inc. Piezoelectric low-pressure fuel injector
DE9320433U1 (en) * 1993-04-10 1994-09-29 Bosch Gmbh Robert Fuel injection nozzle for internal combustion engines

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KR19980702022A (en) 1998-07-15
CN1075871C (en) 2001-12-05
DE59608146D1 (en) 2001-12-13
EP0811119B1 (en) 2001-11-07
CN1173911A (en) 1998-02-18
JPH11501382A (en) 1999-02-02
DE19548540A1 (en) 1997-06-26
EP0811119A1 (en) 1997-12-10
RU2161723C2 (en) 2001-01-10

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