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EP1181445A2 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines

Info

Publication number
EP1181445A2
EP1181445A2 EP01909417A EP01909417A EP1181445A2 EP 1181445 A2 EP1181445 A2 EP 1181445A2 EP 01909417 A EP01909417 A EP 01909417A EP 01909417 A EP01909417 A EP 01909417A EP 1181445 A2 EP1181445 A2 EP 1181445A2
Authority
EP
European Patent Office
Prior art keywords
valve
valve member
sealing surface
fuel injection
seat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP01909417A
Other languages
German (de)
French (fr)
Other versions
EP1181445B1 (en
Inventor
Friedrich Boecking
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 EP1181445A2 publication Critical patent/EP1181445A2/en
Application granted granted Critical
Publication of EP1181445B1 publication Critical patent/EP1181445B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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 for internal combustion engines according to the preamble of claim 1.
  • Such a fuel injection valve is known from published patent application DE 196 08 575.
  • An essentially conical tip is formed at the end of the valve member on the combustion chamber side. This tip is divided into two sections, the tip cone angle of the outer section facing the combustion chamber being greater than that of the inner section facing the valve member.
  • a circumferential ring edge is formed as a sealing surface on the outer surface of the valve member tip.
  • valve member is arranged in a bore in the form of a blind bore, the closed end facing the combustion chamber being designed as a valve seat which has a substantially conical shape. At least one injection opening is formed in the valve seat, which opens the inside of the
  • Valve connects to the combustion chamber with the valve member lifted off the valve seat.
  • valve member comes to the valve seat with its valve sealing surface Investment.
  • the cone angle of the valve seat is dimensioned so that the valve member is seated essentially only with the ring edge on the valve seat. This results in a good sealing of the pressure chamber against the injection openings on the one hand, but on the other hand the problem that the high surface pressure leads to deformations of the valve member and valve seat over time.
  • the ring edge and / or the valve seat deform, which changes the effective seat diameter of the valve member. This changes. also the effective passage cross section of the fuel injection valve and the size of the areas exposed to pressure on the valve member, which has a disadvantageous effect on the fuel injection curve and the injection accuracy.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the part of the valve member tip bearing the valve sealing surface is designed as a flexible ring collar, whereby in the closed position of the valve member the part bearing the valve sealing surface rests flat on the valve seat after first contact with the line.
  • the outer edge of the ring collar defines a fixed seat diameter.
  • the increasing contact surface of the valve member on the valve seat results in a relatively low surface pressure in the area of the valve seat, which leads to little wear in this area.
  • the seat diameter thus remains constant over the service life of the fuel injector.
  • valve sealing surface is undercut in part by the annular groove, so that the annular collar is made increasingly lip-shaped and the deformation work of the annular collar is reduced.
  • FIG. 1 shows a longitudinal section through a valve body with valve member
  • FIG. 2 shows an enlarged section of FIG. 1 in the area of the valve seat
  • FIG. 3 shows an enlarged section of FIG. 2 in the area of the valve sealing surface.
  • FIG. 1 shows a longitudinal section through an embodiment of the fuel injection valve according to the invention.
  • a valve body 1 the end face of which faces away from the combustion chamber in the installed position comes to bear at least indirectly on a valve holding body (not shown in the drawing) has a bore 5 designed as a blind bore.
  • the bottom surface is designed as a valve seat 11 and is approximately conical with a cone angle ⁇ , the inside diameter of the valve seat 11 narrowing toward the combustion chamber.
  • At least one injection opening 13 is formed on the valve seat 11 and connects the bore 5 to the combustion chamber.
  • a piston-shaped valve member 7 Arranged in the bore 5 is a piston-shaped valve member 7, which has a larger combustion chamber Section facing away is guided in the bore 5 and which, with the formation of a pressure shoulder 15, merges into the combustion chamber into a valve member shaft 7 1 with a smaller diameter.
  • a pressure chamber 17 is formed between the wall of the bore 5 and the valve member shaft 7 ', which surrounds the valve member 7 and the pressure shoulder 15 and extends to the valve seat 11.
  • An inlet duct 21 formed in the valve body 1 opens into the pressure chamber 17, via which the pressure chamber 17 can be filled with fuel under high pressure.
  • valve member shaft 7 ′ merges into a valve member tip 30, the outer surface of which is approximately conical and forms a valve sealing surface 9, which cooperates with the valve seat 11.
  • the valve member 7 is pressed by the force of a closing spring (not shown in the drawing) with the valve sealing surface 9 against the valve seat 11, so that in this closed position the injection opening 13 is sealed against the pressure chamber 17 by the valve sealing surface 9.
  • the pressure chamber 17 In the open position of the valve member 7, that is, when the valve sealing surface 9 lifts against an closing force by an axial movement of the valve member 7 from the combustion chamber away from the valve seat 11 under the action of the fuel supplied to the pressure chamber 17 under high pressure, the pressure chamber 17 is above the one - Spray opening 13 connected to the combustion chamber and fuel is injected into the combustion chamber.
  • FIG. 2 shows an enlargement of the fuel injection valve shown in FIG. 1 in the region of the valve seat 11 in the closed position.
  • the outer surface of the valve member tip 30 is divided into two sections which are separated from one another by an annular groove 25.
  • the first valve member section 30a forming the end of the valve member 7 has a conical lateral surface with a cone angle ⁇
  • the second valve member section 30b, which to the side of the valve member shaft 7 'connects to the annular groove 25, has a truncated cone-shaped outer surface with a cone angle ⁇ .
  • the cone angle ⁇ is larger than the cone angle ⁇ , and the two sections of the valve member tip 30 are designed such that only the outer surface of the second, frustoconical valve member section 30b carries the valve sealing surface 9.
  • annular groove 23 is formed, which releases the second valve member section 30b carrying the valve sealing surface 9 and is preferably designed such that it partially undercuts the section 30b.
  • annular collar 28 is formed, which is resilient and can thus adapt to the valve seat 11 by deforming when it is in contact with the valve seat 11 under the action of the closing force.
  • the annular groove 25 arranged at the transition of the two valve member sections 30a, 30b of the valve member tip 30 ensures a better fuel distribution in the volume between the valve member tip 30 and the valve seat 11, if it is provided to arrange more than one injection opening 13 on the valve seat 11.
  • the annular groove 25 is located upstream of the discharge injection openings 13.
  • FIG. 3 shows an enlargement of the valve member 7 in the area of the valve sealing surface 9.
  • the lateral surface of the annular collar 28 has an opening angle ß, which is not the same, but is slightly larger than the cone angle ⁇ of the valve seat 11.
  • the difference angle ⁇ is dimensioned such that the annular collar 28, which is in the closed position of the valve member 7 by the force of the Closing spring is pressed against the valve seat 11, can spring purely elastically perpendicular to the surface of the valve seat 11 to the inside and thus rests flat against the valve seat 11.
  • the feathering is supported by that part of the valve sealing surface 9 is undercut by the annular groove 23, so that a reduced cross section is formed at the base of the annular collar.
  • Valve sealing surface 9 forms, is not pressed into the valve seat 11 by this configuration, since the full force of the closing spring only acts on the valve seat 11 after the deformation.
  • the diameter of the first contact of the valve member 7 with the valve seat 11 remains unchanged.
  • the difference angle ⁇ between the cone angles of the valve sealing surface 9 and the valve seat 11 must be less than 1 degree, preferably 0.25 to 0.75 Degree.
  • valve member 7 During the closing movement of the valve member 7 towards the valve seat 11, the sealing edge 34 comes into contact with the valve seat 11 first. Due to the force of the closing spring, the valve member 7 is pressed further onto the valve seat 11, so that the annular collar 28 is pressed inwards until the entire, frustoconical valve sealing surface 9 comes into contact with the valve seat 11.
  • valve member tip 30 By dividing the valve member tip 30 by an annular groove into two valve member sections 30a, 30b, it can also be provided that the annular groove 25 is omitted, as a result of the different cone angle of the two valve member sections 30a, 30b forming an annular edge at their transition.

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 relates to a fuel injection valve for internal combustion engines. The inventive valve comprises a valve body (1). A valve member (7) is arranged in said body and in a bore (5) against a closing force and in an axially moveable manner. The valve member (7) is provided with an essentially conical valve member point (30) on the end thereof. Said point rests on a valve seat (11) with a component of the lateral area thereof, whereby said component serves as valve sealing surface (9). Said valve seat is configured on an end of the bore (5), whereby said end faces the combustion chamber. A ring groove (23) is configured in the transitional area between the valve member (7) and the valve member point (30). Said groove partially undercuts the valve sealing surface (9) and thus forms an annular collar (28) which is springy and elastic. When the valve member (7) is in the opening position, the conical angle ( beta ) of the valve sealing surface (9) is slightly greater than the conical angle ( alpha ) of the valve seat (11) so that the annular collar (28) first contacts the valve seat (11) with the outer edge when the valve member (7) performs a closing movement and is further formed towards the inside by means of the additional closing movement, whereby said edge is designed as a sealing edge (34). The sealing edge (34) is thus not pressed into the valve seat (11) and the diameter of the seat thus remains unchanged throughout the service life of the fuel injection valve.

Description

Kraftstoffeinspritzventil für Brenn raft aschinen Fuel injection valve for fuel rafts
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Ein derartiges Kraftstoffeinspritzventil ist aus der Offenlegungsschrift DE 196 08 575 bekannt. Am brennraumseitigen Ende des Ventilgliedes ist eine im wesentlichen kegelförmige Spitze ausgebildet. Diese Spitze ist in zwei Ab- schnitte unterteilt, wobei der Spitzenkegelwinkel des äußeren, brennraumzugewandten Abschnitts größer als der des inneren, dem Ventilglied zugewandten Abschnitts ist. Dadurch ist an der Mantelfläche der Ventilgliedspitze eine umlaufende Ringkante als Dichtfläche ausgebildet.The invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is known from published patent application DE 196 08 575. An essentially conical tip is formed at the end of the valve member on the combustion chamber side. This tip is divided into two sections, the tip cone angle of the outer section facing the combustion chamber being greater than that of the inner section facing the valve member. As a result, a circumferential ring edge is formed as a sealing surface on the outer surface of the valve member tip.
Das Ventilglied ist in einer als Sackbohrung ausgeführten Bohrung angeordnet, wobei das brennraumzugewandte, geschlossene Ende als Ventilsitz ausgebildet ist, der im wesentlichen eine konische Form aufweist. Im Ventilsitz ist wenig- stens eine Einspritzöffnung ausgebildet, die das Innere desThe valve member is arranged in a bore in the form of a blind bore, the closed end facing the combustion chamber being designed as a valve seat which has a substantially conical shape. At least one injection opening is formed in the valve seat, which opens the inside of the
Ventils bei vom Ventilsitz abgehobenen Ventilglied mit dem Brennraum verbindet .Valve connects to the combustion chamber with the valve member lifted off the valve seat.
In Schließstellung des Kraftstoffeinspritzventil kommt das Ventilglied mit seiner Ventildichtfläche am Ventilsitz zur Anlage. Der Konuswinkel des Ventilsitzes ist dabei so bemessen, daß das Ventilglied im wesentlichen nur mit der Ringkante am Ventilsitz aufsitzt. Dadurch ergibt sich einerseits eine gute Abdichtung des Druckraums gegen die Einspritzöff- nngen aber andererseits das Problem, daß es durch die hohe Flächenpressung im Laufe der Zeit zu Verformungen an Ventilglied und Ventilsitz kommt. Die Ringkante und/oder der Ventilsitz verformen sich, wodurch sich der effektive Sitzdurchmesser des Ventilgliedes ändert. Dadurch ändert sich. auch der effektive Durchlaßquerschnitt des Kraftstoffeinspritzventils und die Größe der druckausgesetzten Flächen am Ventilglied, was sich auf den Kraftstoffeinspritzverlauf und die Einspritzgenauigkeit nachteilig auswirkt.In the closed position of the fuel injection valve, the valve member comes to the valve seat with its valve sealing surface Investment. The cone angle of the valve seat is dimensioned so that the valve member is seated essentially only with the ring edge on the valve seat. This results in a good sealing of the pressure chamber against the injection openings on the one hand, but on the other hand the problem that the high surface pressure leads to deformations of the valve member and valve seat over time. The ring edge and / or the valve seat deform, which changes the effective seat diameter of the valve member. This changes. also the effective passage cross section of the fuel injection valve and the size of the areas exposed to pressure on the valve member, which has a disadvantageous effect on the fuel injection curve and the injection accuracy.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß der die Ventildichtfläche tragende Teil der Ventilgliedspitze als nachgiebiger Ringkragen ausgebildet ist, wodurch in Schließstellung des Ventilgliedes der die Ventildichtfläche tragende Teil nach zunächst erfolgter Lά- nienberührung flächig am Ventilsitz anliegt. Die äußere Kante des Ringkragens definiert einen festen Sitzdurchmesser. Durch die sich vergrößernde Auflagefläche des Ventilgliedes am Ventilsitz ist eine relativ geringe Flächenpressung im Bereich des Ventilsitzes gegeben, was zu geringem Verschleiß in diesem Bereich führt. Der Sitzdurchmesser bleibt somit über die Lebensdauer des Kraftstoffeinspritzventils kon- stant.The fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the part of the valve member tip bearing the valve sealing surface is designed as a flexible ring collar, whereby in the closed position of the valve member the part bearing the valve sealing surface rests flat on the valve seat after first contact with the line. The outer edge of the ring collar defines a fixed seat diameter. The increasing contact surface of the valve member on the valve seat results in a relatively low surface pressure in the area of the valve seat, which leads to little wear in this area. The seat diameter thus remains constant over the service life of the fuel injector.
In einer vorteilhaften Ausgestaltung ist die Ventildichtfläche durch die Ringnut zum Teil hinterschnitten, so daß der Ringkragen verstärkt lippenförmig ausgebildet ist und die Verformarbeit des Ringkragens verringert wird. Durch eine Variation der Form der Ringnut kann die Nachgiebigkeit des Ringkragens an das jeweilige Material von Ventilglied und Ventilkörper angepaßt werden.In an advantageous embodiment, the valve sealing surface is undercut in part by the annular groove, so that the annular collar is made increasingly lip-shaped and the deformation work of the annular collar is reduced. By a Varying the shape of the annular groove allows the flexibility of the annular collar to be adapted to the respective material of the valve member and valve body.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung, der Beschreibung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be found in the drawing, the description and the claims.
Zeichnungdrawing
In der Zeichnung ist ein Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigen die Figur 1 einen Längsschnitt durch einen Ventilkörper mit Ventilglied, Figur 2 einen vergrößerten Ausschnitt von Figur 1 im Bereich des Ventilsitzes und Figur 3 einen vergrößerten Ausschnitt von Figur 2 im Bereich der Ventildichtfläche .In the drawing, an embodiment of a fuel injection valve according to the invention is shown. 1 shows a longitudinal section through a valve body with valve member, FIG. 2 shows an enlarged section of FIG. 1 in the area of the valve seat and FIG. 3 shows an enlarged section of FIG. 2 in the area of the valve sealing surface.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist ein Längsschnitt durch ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils gezeigt. Ein Ventilkörper 1, dessen brennraumabgewandte Stirnfläche in Einbaulage zumindest mittelbar an einem in der Zeichnung nicht dargestellten Ventilhaltekörper zur Anlage kommt, weist eine als Sackbohrung ausgeführte Bohrung 5 auf. Die Bodenfläche ist als Ventilsitz 11 ausgebildet und näherungsweise konisch mit einem Konuswinkel α, wobei sich der Innendurchmesser des Ventilsitzes 11 zum Brennraum hin ver- kleinert . Am Ventilsitz 11 ist wenigstens eine Einspritzöffnung 13 ausgebildet, die die Bohrung 5 mit dem Brennraum verbindet .FIG. 1 shows a longitudinal section through an embodiment of the fuel injection valve according to the invention. A valve body 1, the end face of which faces away from the combustion chamber in the installed position comes to bear at least indirectly on a valve holding body (not shown in the drawing) has a bore 5 designed as a blind bore. The bottom surface is designed as a valve seat 11 and is approximately conical with a cone angle α, the inside diameter of the valve seat 11 narrowing toward the combustion chamber. At least one injection opening 13 is formed on the valve seat 11 and connects the bore 5 to the combustion chamber.
In der Bohrung 5 ist ein kolbenförmiges Ventilglied 7 ange- ordnet, das mit einem im Durchmesser größeren, dem Brennraum abgewandten Abschnitt in der Bohrung 5 geführt ist und das unter Bildung einer Druckschulter 15 dem Brennraum zu in einen im Durchmesser kleineren Ventilgliedschaft 71 übergeht. Zwischen der Wand der Bohrung 5 und dem Ventilgliedschaft 7' ist ein Druckraum 17 ausgebildet, der das Ventilglied 7 und die Druckschulter 15 umgibt und bis zum Ventilsitz 11 reicht. In den Druckraum 17 mündet ein im Ventilkörper 1 ausgebildeter Zulaufkanal 21, über den der Druckraum 17 mit Kraftstoff unter hohem Druck befüllt werden kann.Arranged in the bore 5 is a piston-shaped valve member 7, which has a larger combustion chamber Section facing away is guided in the bore 5 and which, with the formation of a pressure shoulder 15, merges into the combustion chamber into a valve member shaft 7 1 with a smaller diameter. A pressure chamber 17 is formed between the wall of the bore 5 and the valve member shaft 7 ', which surrounds the valve member 7 and the pressure shoulder 15 and extends to the valve seat 11. An inlet duct 21 formed in the valve body 1 opens into the pressure chamber 17, via which the pressure chamber 17 can be filled with fuel under high pressure.
Am brennraumseitigen Ende geht der Ventilgliedschaft 7' in eine Ventilgliedspitze 30 über, deren Außenmantelfläche näherungsweise konusförmig ist und eine Ventildichtfläche 9 bildet, die mit dem Ventilsitz 11 zusammenwirkt. Das Ventil- glied 7 wird durch die Kraft einer in der Zeichnung nicht dargestellten Schließfeder mit der Ventildichtfläche 9 gegen den Ventilsitz 11 gepreßt, so daß in dieser Schließstellung die Einspritzöffnung 13 durch die Ventildichtfläche 9 gegen den Druckraum 17 abdichtet wird. In geöffneter Stellung des Ventilgliedes 7, das ist, wenn die Ventildichtfläche 9 durch eine axiale Bewegung des Ventilgliedes 7 vom Brennraum weg vom Ventilsitz 11 unter Einwirkung des dem Druckraum 17 unter hohem Druck zugeführten Kraftstoffs entgegen einer Schließkraft abhebt, ist der Druckraum 17 über die Ein- spritzöffnung 13 mit dem Brennraum verbunden und Kraftstoff wird in den Brennraum eingespritzt.At the end on the combustion chamber side, the valve member shaft 7 ′ merges into a valve member tip 30, the outer surface of which is approximately conical and forms a valve sealing surface 9, which cooperates with the valve seat 11. The valve member 7 is pressed by the force of a closing spring (not shown in the drawing) with the valve sealing surface 9 against the valve seat 11, so that in this closed position the injection opening 13 is sealed against the pressure chamber 17 by the valve sealing surface 9. In the open position of the valve member 7, that is, when the valve sealing surface 9 lifts against an closing force by an axial movement of the valve member 7 from the combustion chamber away from the valve seat 11 under the action of the fuel supplied to the pressure chamber 17 under high pressure, the pressure chamber 17 is above the one - Spray opening 13 connected to the combustion chamber and fuel is injected into the combustion chamber.
In Figur 2 ist eine Vergrößerung des in Figur 1 dargestellten Kraftstoffeinspritzventils im Bereich des Ventilsitzes 11 in Schließstellung gezeigt. Die Mantelfläche der Ventilgliedspitze 30 ist in zwei Abschnitte geteilt, die durch eine Ringrille 25 voneinander getrennt sind. Der das Ende des Ventilgliedes 7 bildende erste Ventilgliedabschnitt 30a weist eine kegelförmige Mantelfläche mit einem Konuswinkel γ auf, während der zweite Ventilgliedabschnitt 30b, der sich zur Seite des Ventilgliedschafts 7 ' an die Ringrille 25 anschließt, eine kegelstumpfförmige Mantelfläche aufweist mit einem Konuswinkel ß. Der Konuswinkel γ ist dabei größer als der Konuswinkel ß, und die beiden Abschnitte der Ventil- gliedspitze 30 sind so ausgebildet, daß nur die Mantelfläche des zweiten, kegelstumpfförmigen Ventilgliedabschnitts 30b die Ventildichtfläche 9 trägt.FIG. 2 shows an enlargement of the fuel injection valve shown in FIG. 1 in the region of the valve seat 11 in the closed position. The outer surface of the valve member tip 30 is divided into two sections which are separated from one another by an annular groove 25. The first valve member section 30a forming the end of the valve member 7 has a conical lateral surface with a cone angle γ, while the second valve member section 30b, which to the side of the valve member shaft 7 'connects to the annular groove 25, has a truncated cone-shaped outer surface with a cone angle β. The cone angle γ is larger than the cone angle β, and the two sections of the valve member tip 30 are designed such that only the outer surface of the second, frustoconical valve member section 30b carries the valve sealing surface 9.
Am Übergang des Ventilgliedschaftes 71 zur Ventilgliedspitze 30 beziehungsweise zum zweiten kegelförmigen Abschnitt 30b ist eine Ringnut 23 ausgebildet, die den die Ventildichtfläche 9 tragenden zweiten Ventilgliedabschnitt 30b freistellt und vorzugsweise so ausgeführt ist, daß sie den Abschnitt 30b teilweise hinterschneidet. Dadurch wird ein Ringkragen 28 gebildet, der federnd nachgiebig ist und sich so bei Anlage an den Ventilsitz 11 unter der Einwirkung der Schließkraft verformend dem Ventilsitz 11 anpassen kann. Die am Übergang der beiden Ventilgliedabschnitte 30a, 30b der Ventilgliedspitze 30 angeordnete Ringrille 25 sorgt für eine bessere Kraftstoffverteilung im Volumen zwischen der Ventil- gliedspitze 30 und dem Ventilsitz 11, falls vorgesehen ist, mehr als eine Einspritzöffnung 13 am Ventilsitz 11 anzuordnen. Die Ringrille 25 liegt stromaufwärts der abführenden Einspritzöffnungen 13.At the transition of the valve member shaft 7 1 to the valve member tip 30 or to the second conical section 30b, an annular groove 23 is formed, which releases the second valve member section 30b carrying the valve sealing surface 9 and is preferably designed such that it partially undercuts the section 30b. As a result, an annular collar 28 is formed, which is resilient and can thus adapt to the valve seat 11 by deforming when it is in contact with the valve seat 11 under the action of the closing force. The annular groove 25 arranged at the transition of the two valve member sections 30a, 30b of the valve member tip 30 ensures a better fuel distribution in the volume between the valve member tip 30 and the valve seat 11, if it is provided to arrange more than one injection opening 13 on the valve seat 11. The annular groove 25 is located upstream of the discharge injection openings 13.
In Figur 3 ist eine Vergrößerung des Ventilgliedes 7 im Bereich der Ventildichtfläche 9 gezeigt. Die Mantelfläche des Ringkragens 28 weist einen Öffnungswinkel ß auf, der nicht gleich, sondern etwas größer ist als der Konuswinkel α des Ventilsitzes 11. Der Differenzwinkel φ ist dabei so bemessen, daß der Ringkragen 28, der in Schließstellung des Ventilgliedes 7 durch die Kraft der Schließfeder gegen den Ventilsitz 11 gepreßt wird, rein elastisch senkrecht zur Fläche des Ventilsitzes 11 nach innen federn kann und so flächig am Ventilsitz 11 anliegt. Das Federn wird dadurch unterstützt, daß ein Teil der Ventildichtfläche 9 durch die Ringnut 23 hinterschnitten wird, so daß sich an der Basis des Ringkra- gens ein verringerter Querschnitt bildet.FIG. 3 shows an enlargement of the valve member 7 in the area of the valve sealing surface 9. The lateral surface of the annular collar 28 has an opening angle ß, which is not the same, but is slightly larger than the cone angle α of the valve seat 11. The difference angle φ is dimensioned such that the annular collar 28, which is in the closed position of the valve member 7 by the force of the Closing spring is pressed against the valve seat 11, can spring purely elastically perpendicular to the surface of the valve seat 11 to the inside and thus rests flat against the valve seat 11. The feathering is supported by that part of the valve sealing surface 9 is undercut by the annular groove 23, so that a reduced cross section is formed at the base of the annular collar.
Die Dichtkante 34, die den brennraumabge andten Rand derThe sealing edge 34, the edge of the combustion chamber and the
Ventildichtfläche 9 bildet, wird durch diese Ausgestaltung nicht in den Ventilsitz 11 eingedrückt, da die volle Kraft der Schließfeder erst nach der Verforπiung auf den Ventilsitz 11 wirkt. Der Durchmesser der ersten Berührung des Ventil- gliedes 7 mit dem Ventilsitz 11 bleibt unverändert. Um die Verformungsarbeit des Ringkragens 28 zu verringern mit dem Ziel, daß eine große Ventildichtfläche 9 flächig am Ventilsitz 11 anliegt, muß der Differenzwinkel φ zwischen den Konuswinkeln von Ventildichtfläche 9 und Ventilsitz 11 kleiner als 1 Grad sein, vorzugsweise 0,25 bis 0,75 Grad.Valve sealing surface 9 forms, is not pressed into the valve seat 11 by this configuration, since the full force of the closing spring only acts on the valve seat 11 after the deformation. The diameter of the first contact of the valve member 7 with the valve seat 11 remains unchanged. In order to reduce the work of deformation of the annular collar 28 with the aim that a large valve sealing surface 9 lies flat against the valve seat 11, the difference angle φ between the cone angles of the valve sealing surface 9 and the valve seat 11 must be less than 1 degree, preferably 0.25 to 0.75 Degree.
Bei der Schließbewegung des Ventilgliedes 7 auf den Ventilsitz 11 zu kommt zuerst die Dichtkante 34 am Ventilsitz 11 zur Anlage. Durch die Kraft der Schließfeder wird das Ven- tilglied 7 weiter auf den Ventilsitz 11 gepreßt, so daß der Ringkragen 28 nach innen gedrückt wird, bis die gesamte, kegelstumpfförmige Ventildichtfläche 9 am Ventilsitz 11 zur Anlage kommt .During the closing movement of the valve member 7 towards the valve seat 11, the sealing edge 34 comes into contact with the valve seat 11 first. Due to the force of the closing spring, the valve member 7 is pressed further onto the valve seat 11, so that the annular collar 28 is pressed inwards until the entire, frustoconical valve sealing surface 9 comes into contact with the valve seat 11.
Statt die Ventilgliedspitze 30 durch eine Ringrille in zwei Ventilgliedabschnitte 30a, 30b zu unterteilen, kann es auch vorgesehen sein, daß die Ringrille 25 entfällt, wodurch sich durch den unterschiedlichen Konuswinkel der beiden Ventilgliedabschnitte 30a, 30b eine Ringkante an deren Übergang bildet. Instead of dividing the valve member tip 30 by an annular groove into two valve member sections 30a, 30b, it can also be provided that the annular groove 25 is omitted, as a result of the different cone angle of the two valve member sections 30a, 30b forming an annular edge at their transition.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkörper (1) , in dem in einer Bohrung (5) ein kolbenförmiges Ventilglied (7) entgegen einer Ξchließ- kraft axial beweglich angeordnet ist, welches Ventilglied1. Fuel injection valve for internal combustion engines with a valve body (1), in which a piston-shaped valve member (7) is arranged in a bore (5) axially movable against a closing force, which valve member
(7) in einem brennraumabgewandten Abschnitt in der Bohrung (5) geführt ist und das brennraumseitig durch eine Querschnittsverringerung in einen Ventilgliedschaft (7') übergeht, der in den als Druckraum (17) ausgebildeten Ringraum zwischen der Bohrung (5) und dem Ventilgliedschaft (7') ragt, und einer am brennrau seitigen Ende des Ventilgliedschaftes (7') ausgebildeten Ventilgliedspitze (30) , die im wesentlichen konisch ist und deren Außendurchmesser sich vom Ventilgliedschaft (7') weg verrin- gert, und einem Ventilsitz (11) , der am brennraumseitigen(7) is guided in a section in the bore (5) facing away from the combustion chamber and which on the combustion chamber side merges into a valve member shaft (7 ') by reducing the cross section, which valve chamber (7) is designed as a pressure chamber (17) between the bore (5) and the valve member shaft ( 7 '), and a valve member tip (30) which is formed on the combustion-gray end of the valve member shaft (7') and is essentially conical and whose outer diameter is reduced away from the valve member shaft (7 '), and a valve seat (11), the one on the combustion chamber side
Ende der Bohrung (5) ausgebildet ist und eine im wesentlichen konische Fläche aufweist, auf der eine Mantelfläche der Ventilgliedspitze (30) als Ventildichtfläche (9) bei Bewegung des Ventilgliedes (7) in Richtung der Schließkraft zur Anlage kommt und so wenigstens eine Ein- spritzöffnung (13) gegen den Druckraum (17) abdichtet, dadurch gekennzeichnet, daß zwischen dem Übergang des Ventilgliedschaftes (71) zur Ventilgliedspitze (30) und der Ventildichtfläche (9) eine umlaufende Ringnut (23) angeordnet ist, derart, daß der die Ventildichtfläche (9) tragende Teil der Ventilgliedspitze (30) federnd ausgebildet ist und senkrecht zur konischen Fläche des Ventilsitzes (11) elastisch verforbar ist.End of the bore (5) is formed and has a substantially conical surface on which a lateral surface of the valve member tip (30) as a valve sealing surface (9) comes to rest when the valve member (7) moves in the direction of the closing force and thus at least one Spray opening (13) seals against the pressure chamber (17), characterized in that a circumferential annular groove (23) is arranged between the transition of the valve member shaft (7 1 ) to the valve member tip (30) and the valve sealing surface (9), such that the Valve sealing surface (9) supporting part of the valve member tip (30) is resilient and is elastically deformable perpendicular to the conical surface of the valve seat (11).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Ringnut (23) die Ventildichtfläche (9) zumindest zum Teil hinterschneidet.2. Fuel injection valve according to claim 1, characterized in that the annular groove (23) at least partially undercuts the valve sealing surface (9).
3. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge- kennzeichnet, daß an der Ventilgliedspitze (30) eine3. Fuel injection valve according to claim 1, characterized in that on the valve member tip (30)
Ringrille (25) ausgebildet ist, wobei die Ventildicht läche (9) auf der kegelstumpfförmigen Fläche zwischen Ringnut (23) und Ringrille (25) ausgebildet wird.An annular groove (25) is formed, the valve sealing surface (9) being formed on the frustoconical surface between the annular groove (23) and the annular groove (25).
4. Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß der Konuswinkel (ß) der Ventildichtfläche (9) größer als der Konuswinkel (α) des Ventilsitzes (11) ist.4. Fuel injection valve according to claim 3, characterized in that the cone angle (β) of the valve sealing surface (9) is greater than the cone angle (α) of the valve seat (11).
5. Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß die Differenz (φ) der Konuswinkel (o,ß) von Ventilsitz (11) und Ventildichtfläche (9) weniger als 1 Grad beträgt.5. Fuel injection valve according to claim 4, characterized in that the difference (φ) of the cone angle (o, ß) of the valve seat (11) and valve sealing surface (9) is less than 1 degree.
6. Kraftstoffeinspritzventil nach Anspruch 5, dadurch gekennzeichnet, daß die Differenz (φ) der Konuswinkel (oc,ß) von Ventilsitz (11) und Ventildichtfläche (9) 0,25 bis 0 , 75 Grad beträgt . 6. Fuel injection valve according to claim 5, characterized in that the difference (φ) of the cone angle (oc, ß) of the valve seat (11) and valve sealing surface (9) is 0.25 to 0.75 degrees.
EP01909417A 2000-01-08 2001-01-05 Fuel injection valve for internal combustion engines Expired - Lifetime EP1181445B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10000501A DE10000501A1 (en) 2000-01-08 2000-01-08 Fuel injection valve for internal combustion engines
DE10000501 2000-01-08
PCT/DE2001/000003 WO2001051804A2 (en) 2000-01-08 2001-01-05 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1181445A2 true EP1181445A2 (en) 2002-02-27
EP1181445B1 EP1181445B1 (en) 2005-04-06

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ID=7626967

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EP01909417A Expired - Lifetime EP1181445B1 (en) 2000-01-08 2001-01-05 Fuel injection valve for internal combustion engines

Country Status (6)

Country Link
US (1) US6669117B2 (en)
EP (1) EP1181445B1 (en)
JP (1) JP2003519756A (en)
DE (2) DE10000501A1 (en)
PL (1) PL350824A1 (en)
WO (1) WO2001051804A2 (en)

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Also Published As

Publication number Publication date
EP1181445B1 (en) 2005-04-06
US20030057298A1 (en) 2003-03-27
JP2003519756A (en) 2003-06-24
WO2001051804A3 (en) 2001-12-06
PL350824A1 (en) 2003-02-10
DE50105813D1 (en) 2005-05-12
DE10000501A1 (en) 2001-07-19
WO2001051804A2 (en) 2001-07-19
US6669117B2 (en) 2003-12-30

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