EP1321661A2 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1321661A2
EP1321661A2 EP02017114A EP02017114A EP1321661A2 EP 1321661 A2 EP1321661 A2 EP 1321661A2 EP 02017114 A EP02017114 A EP 02017114A EP 02017114 A EP02017114 A EP 02017114A EP 1321661 A2 EP1321661 A2 EP 1321661A2
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EP
European Patent Office
Prior art keywords
valve
valve seat
bore
conical
fuel injection
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
EP02017114A
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German (de)
French (fr)
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EP1321661A3 (en
EP1321661B1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1321661A3 publication Critical patent/EP1321661A3/en
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Publication of EP1321661B1 publication Critical patent/EP1321661B1/en
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    • 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
    • F02M61/16—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
    • 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
    • F02M61/1866—Valve seats or member ends having multiple cones

Definitions

  • the invention relates to a fuel injection valve for Internal combustion engines, as described in DE 199 42 370 A1 is known.
  • a valve needle longitudinally displaceable in the bore of a valve body arranged, being between the wall of the bore and the valve needle can be filled with fuel under high pressure Pressure chamber is formed.
  • On the combustion chamber side At the end of the bore there are several injection openings in the valve body trained through which the bore with the combustion chamber the internal combustion engine is connected.
  • a conical valve seat is formed at the end, on which the valve needle in its closed position with a Valve sealing surface comes to the plant. In the closed position the valve needle cannot deliver the fuel from the pressure chamber flow to the injection ports.
  • Fuel flows out of the pressure chamber from the valve seat between the valve sealing surface and the valve seat to the injection openings and from there into the combustion chamber injected into the internal combustion engine.
  • the valve sealing surface has two conical surfaces, the first conical surface upstream of the second conical Surface is arranged and both conical surfaces directly against each other limits.
  • the opening angle of the first conical Area is smaller than the opening angle of the valve seat, which in turn is smaller than the opening angle the second conical surface. This will make the transition of the two conical surfaces formed a ring edge, which in Closed position of the valve needle on the valve seat to the system comes and due to the relatively high surface pressure a good one Creates tightness.
  • the valve needle is in the bore by the hydraulic Counteracts pressure that acts on parts of the valve sealing surface a closing force directed at the valve seat.
  • the pressure at which the valve needle is just coming from the valve seat takes off, is called opening pressure.
  • This is depending on the hydraulically effective seat diameter of the valve needle on the valve seat, which is described in the above Geometry corresponds to the diameter of the sealing edge. This however only applies as long as there is no deformation of the valve needle and valve seat occur. There is always one in operation elastic and, especially after prolonged use, to one plastic deformation of the valve sealing surface by the Valve needle. So can the hydraulically effective seat diameter the valve needle change over time and thus also the opening pressure.
  • the difference angle between the first conical Area and the conical valve seat larger than that Difference angle between the second conical surface and the valve seat. This ensures the constancy of the hydraulic effective seat diameter further supported.
  • the first Ring groove designed as a flat countersink of the hole.
  • the first ring groove can be done in a simple manner manufacture with high precision. It is particularly advantageous here that the first ring groove always without further action remains connected to the pressure chamber so that the valve sealing surface of the fuel pressure in the pressure chamber at all times is acted upon.
  • FIG. 1 is an embodiment of the invention Fuel injector shown in longitudinal section.
  • a bore 3 is formed, the one Has longitudinal axis 8 and in which a piston-shaped valve needle 5 is arranged to be longitudinally displaceable.
  • On the combustion chamber side is a conical valve seat 9 arranged in which at least one injection opening 11 is formed is in the installed position of the fuel injector opens into the combustion chamber of the internal combustion engine.
  • the Valve needle 5 is in a guide section 23 of the bore 3 sealing led and tapers to the combustion chamber below Formation of a pressure shoulder 13. On its combustion chamber side At the end, the valve needle 5 goes into a valve sealing surface 7 over, in the closed position of the valve needle 5 on the valve seat 9 is present.
  • a pressure chamber 19 is formed, which is at the level of Pressure shoulder 13 is expanded radially.
  • This radial expansion of the pressure chamber 19 opens into the valve body 1 running inlet bore 25 through which the pressure chamber 19 with a high-pressure fuel source is connected in the pressure chamber 19 constant or intermittent high fuel pressure builds.
  • the valve needle 5 is by one in the drawing Applied device, not shown, with a closing force on the valve needle 5 in the direction of the valve seat 9 acts. As a result, the valve needle 5 with the valve sealing surface 7 pressed against the valve seat 9, so that no fuel from the pressure chamber 19 to the injection openings 11 can reach.
  • valve needle 5 then lifts with her Valve sealing surface 7 from the valve seat 9, and it flows Fuel from the pressure chamber 19 between the valve sealing surface 7 and the valve seat 9 through the injection openings 11 and is injected from there into the combustion chamber.
  • the Injection is either by increasing the closing force or by interrupting the fuel supply in the pressure chamber 19 ended.
  • the valve needle 5 slides, driven of the closing force, back into contact with valve seat 9 to its closed position and thus cuts off the fuel supply to the injection openings 11.
  • FIG 2 shows an enlargement of Figure 1 in the area of Valve seat 9.
  • the valve sealing surface 7 is divided into a first conical surface 30 and a second conical surface 32, with a ring edge at the transition of the two surfaces 34 is formed.
  • the opening angle of the first conical Surface 30 is smaller than the opening angle of the conical Valve seat 9, which in turn is smaller than that Opening angle of the second conical surface 32.
  • a first annular groove 36 is formed and one for this parallel second annular groove 38, both annular grooves 36, 38 with respect the longitudinal axis 8 of the bore 3 in a radial plane lie.
  • the first annular groove 36 is a flat countersink of the bore 3, so that a ring shoulder 37 is thereby formed becomes.
  • the ring edge 34 is in Closed position of the valve needle 5 either within this Section of the valve seat 9 or at the level of the second Ring groove 38 arranged.
  • valve needle 9 and the valve body 1 were ideally rigid, the valve needle 5 and the valve seat 9 would only turn on the ring edge 34 or at the transition of the valve seat 9 to touch the second annular groove 38. Because of the occurring elastic Deformations, the valve needle 5 lies on the entire Contact surface 10 on or at least for the most part the same, so that the occurring surface pressures reduce accordingly.
  • the contact surface 10 not over the area delimited by the ring grooves 36, 38 can grow out. This will also reduce the fuel pressure partial area of the first in the pressure chamber 19 conical surface 30 and thus also the opening pressure the valve needle 5, because in addition to the surface of the Pressure shoulder 13 also the corresponding partial surface of the valve sealing surface 7 is decisive.
  • the difference angle d 1 between the first conical surface 30 and the valve seat 9 is smaller than the difference angle d 2 between the second conical surface 32 and the valve seat 9, which corresponds to the so-called inverse seat angle difference. This additionally prevents the hammering of the ring edge 34 into the valve seat 9 from changing the area hydraulically acted upon by the fuel in the pressure chamber 19 and thereby causing a change in the opening pressure.
  • FIG. 1 A further exemplary embodiment is shown in FIG the same section as shown in Figure 2.
  • the Valve seat 9 extends up to the wall of the bore 3 first annular groove 36 is in the same way as the second annular groove 38 formed, but it has a greater depth and includes a larger area of the valve seat 9.
  • Die Contact surface 10 is in turn by the two ring grooves 36,38 limited, with the relatively large first annular groove 36 ensures that it is always connected to the pressure chamber 19 remains hydraulically connected.
  • the opening angle of the valve seat 9 is approximately 55 ° to 65 °, preferably approximately 60 °.
  • the corresponding differential angles d 1 and d 2 to the conical surfaces 30, 32 of the valve sealing surface 7 are a few degrees, preferably 0.5 ° to 3 °.

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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)

Abstract

Fuel injection valve comprises a valve body (1) having a valve seat (9) with a first annular groove (36) running in a radial plane of a bore (3), and a parallel second annular groove (38) arranged downstream of the first annular groove. <??>Preferred Features: An annular edge (34) lies within the second annular groove when the valve needle is in the closed position. The angle (d2) between a second conical surface (32) and the conical valve seat is greater than the angle (d1) between a first conical surface (30) and the valve seat.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es aus der Schrift DE 199 42 370 A1 bekannt ist. Bei diesem Kraftstoffeinspritzventil ist eine Ventilnadel in der Bohrung eines Ventilkörpers längsverschiebbar angeordnet, wobei zwischen der Wand der Bohrung und der Ventilnadel ein mit Kraftstoff unter hohem Druck befüllbarer Druckraum ausgebildet ist. Am brennraumseitigen Ende der Bohrung ist im Ventilkörper mehrere Einspritzöffnungen ausgebildet, durch die die Bohrung mit dem Brennraum der Brennkraftmaschine verbunden ist. Ebenfalls am brennraumseitigen Ende ist ein konischer Ventilsitz ausgebildet, an dem die Ventilnadel in ihrer Schließstellung mit einer Ventildichtfläche zur Anlage kommt. In der Schließstellung der Ventilnadel kann der Kraftstoff aus dem Druckraum nicht zu den Einspritzöffnungen fließen. Durch Abheben der Ventilnadel vom Ventilsitz fließt Kraftstoff aus dem Druckraum zwischen der Ventildichtfläche und dem Ventilsitz hindurch den Einspritzöffnungen zu und wird von dort in den Brennraum der Brennkraftmaschine eingespritzt. The invention relates to a fuel injection valve for Internal combustion engines, as described in DE 199 42 370 A1 is known. With this fuel injector a valve needle longitudinally displaceable in the bore of a valve body arranged, being between the wall of the bore and the valve needle can be filled with fuel under high pressure Pressure chamber is formed. On the combustion chamber side At the end of the bore there are several injection openings in the valve body trained through which the bore with the combustion chamber the internal combustion engine is connected. Also on the combustion chamber side A conical valve seat is formed at the end, on which the valve needle in its closed position with a Valve sealing surface comes to the plant. In the closed position the valve needle cannot deliver the fuel from the pressure chamber flow to the injection ports. By lifting the valve needle Fuel flows out of the pressure chamber from the valve seat between the valve sealing surface and the valve seat to the injection openings and from there into the combustion chamber injected into the internal combustion engine.

Um eine sichere Abdichtung am Ventilsitz zu erreichen weist die Ventildichtfläche zwei konische Flächen auf, wobei die erste konische Fläche stromaufwärts der zweiten konischen Fläche angeordnet ist und beide konischen Flächen direkt aneinander grenzen. Der Öffnungswinkel der ersten konischen Fläche ist hierbei kleiner als der Öffnungswinkel des Ventilsitzes, welcher wiederum kleiner ist als der Öffnungswinkel der zweiten konischen Fläche. Dadurch wird am Übergang der beiden konischen Flächen eine Ringkante gebildet, die in Schließstellung der Ventilnadel am Ventilsitz zur Anlage kommt und durch die relativ hohe Flächenpressung eine gute Dichtheit erzeugt.To achieve a secure seal on the valve seat points the valve sealing surface has two conical surfaces, the first conical surface upstream of the second conical Surface is arranged and both conical surfaces directly against each other limits. The opening angle of the first conical Area is smaller than the opening angle of the valve seat, which in turn is smaller than the opening angle the second conical surface. This will make the transition of the two conical surfaces formed a ring edge, which in Closed position of the valve needle on the valve seat to the system comes and due to the relatively high surface pressure a good one Creates tightness.

Die Ventilnadel wird in der Bohrung durch den hydraulischen Druck, der auf Teile der Ventildichtfläche wirkt, entgegen einer auf den Ventilsitz gerichteten Schließkraft bewegt. Der Druck, bei dem die Ventilnadel gerade eben vom Ventilsitz abhebt, wird als Öffnungsdruck bezeichnet. Dieser ist abhängig vom hydraulisch wirksamen Sitzdurchmesser der Ventilnadel am Ventilsitz, welcher bei der oben beschriebenen Geometrie dem Durchmesser der Dichtkante entspricht. Dies gilt jedoch nur, solange keine Verformungen von Ventilnadel und Ventilsitz auftreten. Im Betrieb kommt es stets zu einer elastischen und, insbesondere nach längerem Betrieb, zu einer plastischen Verformung der Ventildichtfläche durch die Ventilnadel. So kann sich der hydraulisch wirksame Sitzdurchmesser der Ventilnadel mit der Zeit ändern und damit auch der Öffnungsdruck. Um dem entgegenzuwirken ist es aus der Schrift DE 196 34 933 A1 bekannt, zwischen den beiden konischen Flächen der Ventildichtfläche eine Ringnut in die Ventilnadel einzubringen. Dies hat jedoch den Nachteil, dass die Steifigkeit der Ventilnadel vermindert wird, was im Bereich der Ringnut zu einer Verformung der Ventilnadel führen kann. Dadurch wäre die Funktionsfähigkeit des gesamten Kraftstoffeinspritzventils in Frage gestellt. The valve needle is in the bore by the hydraulic Counteracts pressure that acts on parts of the valve sealing surface a closing force directed at the valve seat. The pressure at which the valve needle is just coming from the valve seat takes off, is called opening pressure. This is depending on the hydraulically effective seat diameter of the valve needle on the valve seat, which is described in the above Geometry corresponds to the diameter of the sealing edge. This however only applies as long as there is no deformation of the valve needle and valve seat occur. There is always one in operation elastic and, especially after prolonged use, to one plastic deformation of the valve sealing surface by the Valve needle. So can the hydraulically effective seat diameter the valve needle change over time and thus also the opening pressure. It is over to counteract this the document DE 196 34 933 A1 known between the two conical surfaces of the valve sealing surface an annular groove in the Insert valve needle. However, this has the disadvantage that the rigidity of the valve needle is reduced, which is in the area the annular groove lead to deformation of the valve needle can. This would make the whole work Fuel injector questioned.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass der hydraulisch wirksame Durchmesser der Ventilnadel am Ventilsitz über die gesamte Lebensdauer erhalten bleibt, ohne dass die Steifigkeit der Ventilnadel vermindert wird. Hierzu sind im Ventilsitz zwei zueinander parallele Ringnuten ausgebildet, die jeweils in Radialebenen zur Längsachse der Bohrung verlaufen. Die Ventilnadel liegt hierbei zwischen den beiden Ringnuten am Ventilsitz an. Hierdurch wird die Fläche des Ventilsitzes, an der die Ventilnadel anliegt, begrenzt und damit auch der hydraulisch wirksame Sitzdurchmesser der Ventilnadel.The fuel injector according to the invention with the characteristic Features of claim 1, however, points the advantage of the hydraulically effective diameter the valve needle on the valve seat over the entire service life is retained without the rigidity of the Valve needle is reduced. For this there are two in the valve seat mutually parallel annular grooves each formed in Radial planes run to the longitudinal axis of the bore. The valve needle lies between the two ring grooves on the valve seat on. This causes the surface of the valve seat to the valve needle abuts, and therefore also hydraulically effective seat diameter of the valve needle.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist der Differenzwinkel zwischen der ersten konischen Fläche und dem konischen Ventilsitz größer als der Differenzwinkel zwischen der zweiten konischen Fläche und dem Ventilsitz. Dadurch wird die Konstanz des hydraulisch wirksamen Sitzdurchmessers weiter unterstützt.In an advantageous embodiment of the subject of Invention is the difference angle between the first conical Area and the conical valve seat larger than that Difference angle between the second conical surface and the valve seat. This ensures the constancy of the hydraulic effective seat diameter further supported.

In einer weiteren vorteilhaften Ausgestaltung ist die erste Ringnut als Flachsenkung der Bohrung ausgestaltet. Auf diese Weise lässt sich die erste Ringnut in einfacher Art und Weise mit hoher Präzision herstellen. Besonders vorteilhaft ist hier, dass die erste Ringnut ohne weitere Maßnahmen stets mit dem Druckraum verbunden bleibt, damit die Ventildichtfläche vom Kraftstoffdruck im Druckraum zu jedem Zeitpunkt beaufschlagt ist.In a further advantageous embodiment, the first Ring groove designed as a flat countersink of the hole. To this The first ring groove can be done in a simple manner manufacture with high precision. It is particularly advantageous here that the first ring groove always without further action remains connected to the pressure chamber so that the valve sealing surface of the fuel pressure in the pressure chamber at all times is acted upon.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar. Further advantages and advantageous configurations of the object the invention are the description and the drawing removable.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt

  • Figur 1 einen Längsschnitt durch ein Kraftstoffeinspritzventil,
  • Figur 2 eine Vergrößerung von Figur 1 im Bereich des Ventilsitzes und
  • Figur 3 denselben Ausschnitt wie Figur 2 eines weiteren Ausführungsbeispiels.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
  • FIG. 1 shows a longitudinal section through a fuel injection valve,
  • Figure 2 is an enlargement of Figure 1 in the region of the valve seat and
  • Figure 3 shows the same section as Figure 2 of another embodiment.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils im Längsschnitt dargestellt. In einem Ventilkörper 1 ist eine Bohrung 3 ausgebildet, die eine Längsachse 8 aufweist und in der eine kolbenförmige Ventilnadel 5 längsverschiebbar angeordnet ist. Am brennraumseitigen Ende der Bohrung 3 ist ein konischer Ventilsitz 9 angeordnet, in dem wenigstens eine Einspritzöffnung 11 ausgebildet ist, die in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraftmaschine mündet. Die Ventilnadel 5 ist in einem Führungsabschnitt 23 der Bohrung 3 dichtend geführt und verjüngt sich dem Brennraum zu unter Bildung einer Druckschulter 13. An ihrem brennraumseitigen Ende geht die Ventilnadel 5 in eine Ventildichtfläche 7 über, die in Schließstellung der Ventilnadel 5 am Ventilsitz 9 anliegt. Zwischen der Ventilnadel 5 und der Wand der Bohrung 3 ist ein Druckraum 19 ausgebildet, der auf Höhe der Druckschulter 13 radial erweitert ist. In diese radiale Erweiterung des Druckraums 19 mündet eine im Ventilkörper 1 verlaufende Zulaufbohrung 25, über die der Druckraum 19 mit einer Kraftstoffhochdruckquelle verbunden ist, die im Druckraum 19 ständig oder zeitweise einen hohen Kraftstoffdruck aufbaut. Die Ventilnadel 5 wird durch eine in der Zeichnung nicht dargestellte Vorrichtung mit einer Schließkraft beaufschlagt, die auf die Ventilnadel 5 in Richtung des Ventilsitzes 9 wirkt. Dadurch wird die Ventilnadel 5 mit der Ventildichtfläche 7 gegen den Ventilsitz 9 gepresst, so dass kein Kraftstoff aus dem Druckraum 19 zu den Einspritzöffnungen 11 gelangen kann. Soll eine Einspritzung von Kraftstoff in den Brennraum der Brennkraftmaschine stattfinden, so wird der Druck im Druckraum 19 soweit erhöht, bis bei Erreichen eines Öffnungsdrucks die hydraulische Kraft auf die Druckschulter 13 und auf Teile der Ventildichtfläche 7 die Schließkraft übersteigt. Die Ventilnadel 5 hebt dann mit ihrer Ventildichtfläche 7 vom Ventilsitz 9 ab, und es fließt Kraftstoff aus dem Druckraum 19 zwischen der Ventildichtfläche 7 und dem Ventilsitz 9 hindurch den Einspritzöffnungen 11 zu und wird von dort in den Brennraum eingespritzt. Die Einspritzung wird entweder durch eine Erhöhung der Schließkraft oder durch eine Unterbrechung der Kraftstoffzufuhr in den Druckraum 19 beendet. Die Ventilnadel 5 gleitet, getrieben von der Schließkraft, zurück in Anlage am Ventilsitz 9 in ihre Schließstellung und unterbricht so die Kraftstoffzufuhr zu den Einspritzöffnungen 11.In Figure 1 is an embodiment of the invention Fuel injector shown in longitudinal section. In a valve body 1, a bore 3 is formed, the one Has longitudinal axis 8 and in which a piston-shaped valve needle 5 is arranged to be longitudinally displaceable. On the combustion chamber side The end of the bore 3 is a conical valve seat 9 arranged in which at least one injection opening 11 is formed is in the installed position of the fuel injector opens into the combustion chamber of the internal combustion engine. The Valve needle 5 is in a guide section 23 of the bore 3 sealing led and tapers to the combustion chamber below Formation of a pressure shoulder 13. On its combustion chamber side At the end, the valve needle 5 goes into a valve sealing surface 7 over, in the closed position of the valve needle 5 on the valve seat 9 is present. Between the valve needle 5 and the wall of the bore 3, a pressure chamber 19 is formed, which is at the level of Pressure shoulder 13 is expanded radially. In this radial expansion of the pressure chamber 19 opens into the valve body 1 running inlet bore 25 through which the pressure chamber 19 with a high-pressure fuel source is connected in the pressure chamber 19 constant or intermittent high fuel pressure builds. The valve needle 5 is by one in the drawing Applied device, not shown, with a closing force on the valve needle 5 in the direction of the valve seat 9 acts. As a result, the valve needle 5 with the valve sealing surface 7 pressed against the valve seat 9, so that no fuel from the pressure chamber 19 to the injection openings 11 can reach. Should be an injection of fuel take place in the combustion chamber of the internal combustion engine, so the pressure in the pressure chamber 19 is increased until it is reached of an opening pressure the hydraulic force on the pressure shoulder 13 and on parts of the valve sealing surface 7 Closing force exceeds. The valve needle 5 then lifts with her Valve sealing surface 7 from the valve seat 9, and it flows Fuel from the pressure chamber 19 between the valve sealing surface 7 and the valve seat 9 through the injection openings 11 and is injected from there into the combustion chamber. The Injection is either by increasing the closing force or by interrupting the fuel supply in the pressure chamber 19 ended. The valve needle 5 slides, driven of the closing force, back into contact with valve seat 9 to its closed position and thus cuts off the fuel supply to the injection openings 11.

Figur 2 zeigt eine Vergrößerung der Figur 1 im Bereich des Ventilsitzes 9. Die Ventildichtfläche 7 unterteilt sich in eine erste konische Fläche 30 und eine zweite konische Fläche 32, wobei am Übergang der beiden Flächen eine Ringkante 34 ausgebildet ist. Der Öffnungswinkel der ersten konischen Fläche 30 ist hierbei kleiner als der Öffnungswinkel des konischen Ventilsitzes 9, welcher wiederum'kleiner ist als der Öffnungswinkel der zweiten konischen Fläche 32. Im Ventilsitz 9 ist eine erste Ringnut 36 ausgebildet und eine dazu parallele zweite Ringnut 38, wobei beide Ringnuten 36,38 bezüglich der Längsachse 8 der Bohrung 3 in einer Radialebene liegen. Die erste Ringnut 36 ist als Flachsenkung der Bohrung 3 ausgeführt, so dass dadurch ein Ringabsatz 37 gebildet wird. Die am Übergang des Ringabsatzes 37 zur Ventildichtfläche 9 gebildete Kante 40 und die zweite Ringnut 38 begrenzen den Teil des Ventilsitzes 9, der als Anlagefläche 10 für die Ventilnadel 5 dient. Die Ringkante 34 ist in Schließstellung der Ventilnadel 5 entweder innerhalb dieses Abschnitts des Ventilsitzes 9 oder auf Höhe der zweiten Ringnut 38 angeordnet.Figure 2 shows an enlargement of Figure 1 in the area of Valve seat 9. The valve sealing surface 7 is divided into a first conical surface 30 and a second conical surface 32, with a ring edge at the transition of the two surfaces 34 is formed. The opening angle of the first conical Surface 30 is smaller than the opening angle of the conical Valve seat 9, which in turn is smaller than that Opening angle of the second conical surface 32. In the valve seat 9, a first annular groove 36 is formed and one for this parallel second annular groove 38, both annular grooves 36, 38 with respect the longitudinal axis 8 of the bore 3 in a radial plane lie. The first annular groove 36 is a flat countersink of the bore 3, so that a ring shoulder 37 is thereby formed becomes. The at the transition of the ring shoulder 37 to the valve sealing surface 9 formed edge 40 and the second annular groove 38 limit the part of the valve seat 9 that serves as a contact surface 10 serves for the valve needle 5. The ring edge 34 is in Closed position of the valve needle 5 either within this Section of the valve seat 9 or at the level of the second Ring groove 38 arranged.

Wären die Ventilnadel 9 und der Ventilkörper 1 ideal starr, so würden sich die Ventilnadel 5 und der Ventilsitz 9 nur an der Ringkante 34 oder am Übergang des Ventilsitzes 9 zur zweiten Ringnut 38 berühren. Aufgrund der auftretenden elastischen Verformungen liegt die Ventilnadel 5 auf der gesamten Anlagefläche 10 auf oder zumindest auf dem größten Teil derselben, so dass sich die auftretenden Flächenpressungen entsprechend reduzieren. Durch die beiden Ringnuten 36,38 ist auf jeden Fall sichergestellt, dass die Anlagefläche 10 nicht über die durch die Ringnuten 36,38 begrenzte Fläche hinaus anwachsen kann. Dadurch wird auch die vom Kraftstoffdruck im Druckraum 19 beaufschlagte Teilfläche der ersten konischen Fläche 30 festgelegt und damit auch der Öffnungsdruck der Ventilnadel 5, da hierfür neben der Fläche der Druckschulter 13 auch die entsprechende Teilfläche der Ventildichtfläche 7 bestimmend ist.If the valve needle 9 and the valve body 1 were ideally rigid, the valve needle 5 and the valve seat 9 would only turn on the ring edge 34 or at the transition of the valve seat 9 to touch the second annular groove 38. Because of the occurring elastic Deformations, the valve needle 5 lies on the entire Contact surface 10 on or at least for the most part the same, so that the occurring surface pressures reduce accordingly. Through the two ring grooves 36.38 it is ensured in any case that the contact surface 10 not over the area delimited by the ring grooves 36, 38 can grow out. This will also reduce the fuel pressure partial area of the first in the pressure chamber 19 conical surface 30 and thus also the opening pressure the valve needle 5, because in addition to the surface of the Pressure shoulder 13 also the corresponding partial surface of the valve sealing surface 7 is decisive.

Der Differenzwinkel d1 zwischen der ersten konischen Fläche 30 und dem Ventilsitz 9 ist kleiner als der Differenzwinkel d2 zwischen der zweiten konischen Fläche 32 und dem Ventilsitz 9, was der sogenannten inversen Sitzwinkeldifferenz entspricht. Dadurch wird zusätzlich verhindert, dass durch das Einhämmern der Ringkante 34 in den Ventilsitz 9 die hydraulisch vom Kraftstoff im Druckraum 19 beaufschlagte Fläche verändert wird und dadurch eine Änderung des Öffnungsdrucks bewirkt. The difference angle d 1 between the first conical surface 30 and the valve seat 9 is smaller than the difference angle d 2 between the second conical surface 32 and the valve seat 9, which corresponds to the so-called inverse seat angle difference. This additionally prevents the hammering of the ring edge 34 into the valve seat 9 from changing the area hydraulically acted upon by the fuel in the pressure chamber 19 and thereby causing a change in the opening pressure.

In Figur 3 ist ein weiteres Ausführungsbeispiel gezeigt, wobei derselbe Ausschnitt wie in Figur 2 dargestellt ist. Der Ventilsitz 9 reicht hierbei bis zur Wand der Bohrung 3. Die erste Ringnut 36 ist in gleicher Weise wie die zweite Ringnut 38 ausgebildet, jedoch weist sie eine größere Tiefe auf und umfasst einen größeren Bereich des Ventilsitzes 9. Die Anlagefläche 10 wird wiederum durch die beiden Ringnuten 36,38 begrenzt, wobei durch die relativ große erste Ringnut 36 sichergestellt ist, dass diese stets mit dem Druckraum 19 hydraulisch verbunden bleibt.A further exemplary embodiment is shown in FIG the same section as shown in Figure 2. The Valve seat 9 extends up to the wall of the bore 3 first annular groove 36 is in the same way as the second annular groove 38 formed, but it has a greater depth and includes a larger area of the valve seat 9. Die Contact surface 10 is in turn by the two ring grooves 36,38 limited, with the relatively large first annular groove 36 ensures that it is always connected to the pressure chamber 19 remains hydraulically connected.

Der Öffnungswinkel des Ventilsitzes 9 beträgt etwa 55° bis 65°, vorzugsweise etwa 60°. Die entsprechenden Differenzwinkel d1 und d2 zu den konischen Flächen 30,32 der Ventildichtfläche 7 betragen wenige Grad, vorzugsweise 0,5° bis 3°.The opening angle of the valve seat 9 is approximately 55 ° to 65 °, preferably approximately 60 °. The corresponding differential angles d 1 and d 2 to the conical surfaces 30, 32 of the valve sealing surface 7 are a few degrees, preferably 0.5 ° to 3 °.

Claims (7)

Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkörper (1), in dem in einer Bohrung (3) eine kolbenförmige Ventilnadel (5) längsverschiebbar angeordnet ist, wobei zwischen der Ventilnadel (5) und der Wand der Bohrung (3) ein mit Kraftstoff befüllbarer Druckraum (19) angeordnet ist, aus dem Kraftstoff wenigstens einer am brennraumseitigen Ende der Bohrung (3) ausgebildeten Einspritzöffnung (11) zufließen kann, und mit einem am brennraumseitigen Ende der Bohrung (3) ausgebildeten konischen Ventilsitz (9), mit dem die Ventilnadel (5) mit einer an ihrem brennraumseitigen Ende ausgebildeten Ventildichtfläche (7) zur Steuerung der wenigstens einen Einspritzöffnung (11) zusammenwirkt, wobei an der Ventildichtfläche eine erste konische Fläche (30) und eine zweite konische Fläche (32) ausgebildet sind, wobei die erste konische Fläche (30) einen Öffnungswinkel aufweist, der kleiner als der Öffnungswinkel des Ventilsitzes (9) ist, welcher wiederum kleiner als der Öffnungswinkel der zweiten konischen Fläche (32) ist, und dass zwischen den beiden konischen Flächen (30; 32) eine Ringkante (34) ausgebildet ist, dadurch gekennzeichnet, dass im Ventilsitz (9) eine in einer Radialebene der Bohrung (3) verlaufende erste Ringnut (36) ausgebildet ist und eine stromabwärts der ersten Ringnut (36) und parallel zu dieser angeordneten zweiten Ringnut (38). Fuel injection valve for internal combustion engines with a valve body (1), in which a piston-shaped valve needle (5) is arranged so as to be longitudinally displaceable in a bore (3), a pressure chamber (19) that can be filled with fuel between the valve needle (5) and the wall of the bore (3) ) from which fuel can flow in at least one injection opening (11) formed at the combustion chamber end of the bore (3), and with a conical valve seat (9) formed at the combustion chamber end of the bore (3), with which the valve needle (5) cooperates with a valve sealing surface (7) formed on its combustion chamber end for controlling the at least one injection opening (11), a first conical surface (30) and a second conical surface (32) being formed on the valve sealing surface, the first conical surface ( 30) has an opening angle which is smaller than the opening angle of the valve seat (9), which in turn is smaller than that Opening angle of the second conical surface (32), and that between the two conical surfaces (30; 32) an annular edge (34) is formed, characterized in that a first annular groove (36) extending in a radial plane of the bore (3) is formed in the valve seat (9) and one arranged downstream of the first annular groove (36) and parallel to it second ring groove (38). Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Ringkante (34) in Schließstellung der Ventilnadel (5) innerhalb der zweiten Ringnut (38) liegt.Fuel injection valve according to claim 1, characterized in that the ring edge (34) in the closed position of the valve needle (5) lies within the second ring groove (38). Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass der Differenzwinkel (d2) der zweiten konischen Fläche (32) mit dem konischen Ventilsitz (9) größer ist als der Differenzwinkel (d2) zwischen der ersten konischen Fläche (30) und dem Ventilsitz (9).Fuel injection valve according to Claim 1, characterized in that the differential angle (d2) of the second conical surface (32) with the conical valve seat (9) is greater than the differential angle (d2) between the first conical surface (30) and the valve seat (9) , Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die erste Ringnut (36) als Flachsenkung der Bohrung (3) ausgebildet ist.Fuel injection valve according to claim 1, characterized in that the first annular groove (36) is designed as a flat countersink of the bore (3). Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass der Öffnungswinkel des konischen Ventilsitzes (9) zumindest näherungsweise 60° beträgt.Fuel injection valve according to claim 1, characterized in that the opening angle of the conical valve seat (9) is at least approximately 60 °. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Einspritzöffnungen (11) stromabwärts der zweiten Ringnut (38) in den Ventilsitz (9) münden.Fuel injection valve according to Claim 1, characterized in that the injection openings (11) open into the valve seat (9) downstream of the second annular groove (38). Kraftstoffeinspritzventil nach einem der vorstehenden Ansprüche, dadurch gekennzeichnet, dass die erste Ringnut (36) stets mit den Druckraum (19) hydraulisch verbunden ist.Fuel injection valve according to one of the preceding claims, characterized in that the first annular groove (36) is always hydraulically connected to the pressure chamber (19).
EP02017114A 2001-12-22 2002-07-30 Fuel injection valve for internal combustion engines Expired - Lifetime EP1321661B1 (en)

Applications Claiming Priority (2)

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DE10163908 2001-12-22
DE10163908A DE10163908A1 (en) 2001-12-22 2001-12-22 Fuel injection valve for internal combustion engines

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Also Published As

Publication number Publication date
JP2003201938A (en) 2003-07-18
US20030132413A1 (en) 2003-07-17
EP1321661A3 (en) 2005-07-13
DE50213847D1 (en) 2009-10-29
DE10163908A1 (en) 2003-07-03
US6789783B2 (en) 2004-09-14
EP1321661B1 (en) 2009-09-16

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