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EP1597475A1 - Fuel injection valve for an internal combustion engine - Google Patents

Fuel injection valve for an internal combustion engine

Info

Publication number
EP1597475A1
EP1597475A1 EP03815941A EP03815941A EP1597475A1 EP 1597475 A1 EP1597475 A1 EP 1597475A1 EP 03815941 A EP03815941 A EP 03815941A EP 03815941 A EP03815941 A EP 03815941A EP 1597475 A1 EP1597475 A1 EP 1597475A1
Authority
EP
European Patent Office
Prior art keywords
valve
combustion chamber
bore
blind bore
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.)
Withdrawn
Application number
EP03815941A
Other languages
German (de)
French (fr)
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 EP1597475A1 publication Critical patent/EP1597475A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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
    • F02M61/06—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 furnished at seated ends with pintle or plug shaped extensions
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known from published application DE 198 41 192 AI.
  • a fuel injection valve is shown, which comprises a valve body with a bore formed therein. The bore is tapered at its combustion chamber end
  • Valve seat limited, with a tapped hole adjoining the conical valve seat on the combustion chamber side, from which at least one injection opening opens, which opens into the combustion chamber of the internal combustion engine in the installed position of the fuel injection valve.
  • a cylindrical section is formed in the blind bore, which adjoins the conical valve seat.
  • a piston-shaped valve needle is arranged to be longitudinally displaceable in the bore and has a conical valve sealing surface at its end on the combustion chamber side, which cooperates with the conical valve seat for controlling the fuel inflow to the at least one injection opening. The valve needle is also immersed in the cylindrical section in the blind hole.
  • the known fuel injection valve has the disadvantage that when the fuel enters the blind bore, there is a different throttling of the fuel flow into the blind bore at the transition from the conical valve seat to the blind bore, depending on the stroke of the valve needle.
  • the annular gap between the conical valve sealing surface and the cylindrical portion of the blind bore is formed increases with the stroke of the valve needle, so that the fuel flow that flows into the blind bore between the valve sealing surface and the valve seat also depends on the stroke of the valve needle.
  • the resulting uneven inflow of fuel has an adverse effect on the pressure build-up in the blind bore, since it is difficult to calculate the exact course.
  • the fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the throttling of the fuel flow at the inlet into the blind bore is independent of the stroke of the valve needle at least on an intermediate stroke range of the valve needle.
  • a cylindrical throttle section is formed adjacent to the conical valve sealing surface at the end of the valve needle on the combustion chamber side, which plunges into the cylindrical section of the blind bore when the valve needle is in the closed position, that is to say when the valve sealing surface rests on the valve seat.
  • the cylindrical throttle section is the valve arranged in the closed position of the valve needle within the cylindrical section and emerges from the cylindrical section of the blind bore at the maximum opening stroke of the valve needle. This results in an unthrottled fuel flow into the blind bore at the maximum stroke of the valve needle.
  • a height of the cylindrical section in the blind bore which has proven to be particularly advantageous is 0.01 mm to 0.10 mm.
  • a fuel injection valve according to the invention is shown in the drawing. It shows
  • FIG. 2 an enlargement of the section of FIG. 1 labeled II.
  • a fuel injection valve according to the invention is shown in longitudinal section.
  • a valve body 1 has a bore 3 which is delimited at its combustion chamber end by a conical valve seat 7.
  • a blind bore 22 adjoins this.
  • a plurality of injection openings 11 extend from the blind bore 22 and, in the installed position of the fuel injection valve, into the combustion chamber of the internal combustion engine patronize.
  • a piston-shaped valve needle 5 is arranged so that it can be moved slowly, which is guided in a sealing manner in a section of the bore 3 facing away from the combustion chamber with a guide section 15.
  • valve needle 5 tapers to form a pressure shoulder 13 and merges into a conical valve sealing surface 9 at its end on the combustion chamber side.
  • a pressure chamber 19 is formed, which is radially expanded at the height of the pressure shoulder 13.
  • an inlet channel 25 runs in the valve body 1, via which the pressure chamber 19 can be filled with fuel under high pressure.
  • the valve needle 5 is acted upon at its end facing away from the combustion chamber by a closing force which is exerted by a device not shown in the drawing.
  • a spring or a spring element or a hydraulic device can be used as the device.
  • the fuel flow from the pressure chamber 19 to the injection openings 11 is controlled by the longitudinal movement of the valve needle 5. If the hydraulic force due to the pressure in the pressure chamber 19 on the pressure shoulder 13 and on parts of the valve sealing surface 9 is greater than the closing force which is exerted on the end of the valve needle 5 facing away from the combustion chamber, the valve needle 5 moves away from the valve seat 7 and thus opens one Gap between the valve sealing surface 9 and the valve seat 7. This allows fuel to flow from the pressure chamber 19 into the blind bore 22 and is injected from there through the injection openings 11 into the combustion chamber of the internal combustion engine. By increasing the closing force or reducing the hydraulic pressure in the pressure chamber 19, the valve needle 5 slides back into its closed position, ie in contact with the valve sealing surface 9 on the valve seat 7.
  • FIG. 2 shows an enlargement of the section of FIG. 1 designated II in the region of the valve seat 7.
  • the blind bore 22 has a cylindrical section 24 which directly adjoins the conical valve seat 7.
  • the injection openings 11 start from the rounded section of the blind bore 22, which adjoins the cylindrical section 24 facing towards the burnt finish.
  • the valve needle 5 has a cylindrical throttle section 26 and an end section 28, the cylindrical throttle section 26 directly adjoining the conical valve sealing surface 9.
  • the cylindrical throttle section 26 is arranged such that it is arranged at the same height as the cylindrical section 24 with respect to the longitudinal axis 4 of the bore 3.
  • the end section 28, which adjoins the cylindrical throttle section 26, projects into the throttle bore 22 and thus reduces the volume of the blind bore 22, which lowers the hydrocarbon emissions.
  • Fuel comes into the blind bore 22. This reduces the deflection losses when the fuel flows from the blind bore 22 into the injection openings 11, as long as there is a fuel pressure in the blind bore 22 which is lower than the injection pressure in the pressure chamber 19.
  • the cylindrical throttle section 26 emerges from the cylindrical section 24, so that the fuel can now flow unthrottled from the pressure chamber 19 into the blind bore 22 in order to inject as much fuel as possible through the injection openings 11 in a short time.
  • the cylindrical throttle section 26 has a height H which is somewhat smaller than the height h of the cylindrical section 24, the height H of the cylindrical throttle section 26 being able to determine the point in time at which the inflow of fuel into the blind bore 22 is unthrottled he follows.

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 comprising a valve body (1) having a bore (3) whose end on a combustion chamber side is embodied in the form of a conical valve seat (7) on which a blind hole (22) is supported on the combustion chamber side, at least one injection orifice (11) extending away from said blind hole (22). The blind hole (22) is fitted with a cylindrical section (24) which is supported by the conical valve seat (7). The bore (3) comprises a valve niddle (5) which is arranged in such a way that it is longitudinally slidable and provided with a conical valve sealing surface (9) on the combustion chamber side, thereby allowing said valve niddle (5) to interact with the conical valve seat (7). A throttling cylindrical section (26) is supported on the conical valve sealing surface (9) of the valve niddle (5), on the combustion chamber side.

Description

Kraftstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es aus der Offenlegungsschrift DE 198 41 192 AI bekannt ist. In dieser Schrift ist ein Kraftstoffeinspritzventil gezeigt, das einen Ventilkörper mit einer darin ausgebildeten Bohrung umfasst. Die Bohrung wird an ihrem brennraumseitigen Ende von einem konischenThe invention is based on a fuel injection valve for internal combustion engines, as is known from published application DE 198 41 192 AI. In this document, a fuel injection valve is shown, which comprises a valve body with a bore formed therein. The bore is tapered at its combustion chamber end
Ventilsitz begrenzt, wobei sich an den konischen Ventilsitz brennraumseitig eine Sackbohrung anschließt, von der wenigstens eine Einspritzöffnung abgeht, die in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraft- maschine mündet. In der Sackbohrung ist ein zylindrischer Abschnitt ausgebildet, der an den konischen Ventilsitz angrenzt. Eine kolbenförmige Ventilnadel ist in der Bohrung längsverschiebbar angeordnet, die an ihrem brennraumseitigen Ende eine konische Ventildichtflache aufweist, die mit dem konischen Ventilsitz zur Steuerung des KraftstoffZuflusses zu der wenigstens einen Einspritzöffnung zusammenwirkt. Die Ventilnadel taucht hierbei auch in den zylindrischen Abschnitt in der Sackbohrung ein.Valve seat limited, with a tapped hole adjoining the conical valve seat on the combustion chamber side, from which at least one injection opening opens, which opens into the combustion chamber of the internal combustion engine in the installed position of the fuel injection valve. A cylindrical section is formed in the blind bore, which adjoins the conical valve seat. A piston-shaped valve needle is arranged to be longitudinally displaceable in the bore and has a conical valve sealing surface at its end on the combustion chamber side, which cooperates with the conical valve seat for controlling the fuel inflow to the at least one injection opening. The valve needle is also immersed in the cylindrical section in the blind hole.
Das bekannte Kraftstoffeinspritzventil weist den Nachteil auf, dass es beim Einlauf des Kraftstoffs in die Sackbohrung zu einer unterschiedlichen Drosselung des Kraftstoffstroms in die Sackbohrung am Übergang des konischen Ventilsitzes der Sackbohrung kommt, je nach Hub der Ventilnadel. Der Ringspalt, der zwischen der konischen Ventildichtflache und dem zylindrischen Abschnitt der Sackbohrung gebildet wird, vergrößert sich mit dem Hub der Ventilnadel, so dass auch der Kraftstoffström, der zwischen der Ventildichtflache und dem Ventilsitz hindurch in die Sackbohrung strömt, vom Hub der Ventilnadel abhängt. Das hierdurch bewirkte ungleichmäßige Einströmen des Kraftstoffs wirkt sich auf den Druckaufbau in der Sackbohrung nachteilig aus, da sich der genaue Verlauf nur schwer berechnen lässt.The known fuel injection valve has the disadvantage that when the fuel enters the blind bore, there is a different throttling of the fuel flow into the blind bore at the transition from the conical valve seat to the blind bore, depending on the stroke of the valve needle. The annular gap between the conical valve sealing surface and the cylindrical portion of the blind bore is formed increases with the stroke of the valve needle, so that the fuel flow that flows into the blind bore between the valve sealing surface and the valve seat also depends on the stroke of the valve needle. The resulting uneven inflow of fuel has an adverse effect on the pressure build-up in the blind bore, since it is difficult to calculate the exact course.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass die Drosselung des Kraftstoff- stroms am Einlauf in die Sackbohrung zumindest an einem Zwi- schenhubbereich der Ventilnadel unabhängig vom Hub der Ventilnadel ist. Hierzu ist angrenzend an die konische Ventildichtflache am brennraumseitigen Ende der Ventilnadel ein zylindrischer Drosselabschnitt ausgebildet, der in Schließ- Stellung der Ventilnadel, also wenn die Ventildichtflache auf dem Ventilsitz aufliegt, in den zylindrischen Abschnitt der Sackbohrung eintaucht. Bei der Hubbewegung der Ventilnadel vom Ventilsitz weg ergibt sich so ein Ringspalt zwischen dem zylindrischen Abschnitt der Sackbohrung und dem zylind- rischen Drosselabschnitt der Ventilnadel, der zumindest in einem Zwischenhubbereich der Ventilnadel unabhängig vom Hub der Ventilnadel ist. Dadurch erreicht man ein gleichförmiges Einströmen des Kraftstoffs in die Sackbohrung und einen e- bensolchen Druckaufbau in der Sackbohrung.The fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the throttling of the fuel flow at the inlet into the blind bore is independent of the stroke of the valve needle at least on an intermediate stroke range of the valve needle. For this purpose, a cylindrical throttle section is formed adjacent to the conical valve sealing surface at the end of the valve needle on the combustion chamber side, which plunges into the cylindrical section of the blind bore when the valve needle is in the closed position, that is to say when the valve sealing surface rests on the valve seat. During the stroke movement of the valve needle away from the valve seat, there is an annular gap between the cylindrical section of the blind bore and the cylindrical throttle section of the valve needle, which is independent of the stroke of the valve needle at least in an intermediate stroke area of the valve needle. This achieves a uniform inflow of fuel into the blind bore and the same pressure build-up in the blind bore.
Durch die abhängigen Ansprüche sind vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung möglich.The dependent claims enable advantageous refinements of the subject matter of the invention.
In einer ersten vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist der zylindrische Drosselabschnitt der Ven- tilnadel in Schließstellung der Ventilnadel innerhalb des zylindrischen Abschnitts angeordnet und taucht bei maximalem Öffnungshub der Ventilnadel aus dem zylindrischen Abschnitt der Sackbohrung aus. Dadurch erhält man bei Maximalhub der Ventilnadel einen ungedrosselten Kraftstoffstrom in die Sackbohrung.In a first advantageous embodiment of the subject matter of the invention, the cylindrical throttle section is the valve arranged in the closed position of the valve needle within the cylindrical section and emerges from the cylindrical section of the blind bore at the maximum opening stroke of the valve needle. This results in an unthrottled fuel flow into the blind bore at the maximum stroke of the valve needle.
Als besonders vorteilhaft hat sich eine Höhe des zylindrischen Abschnitts in der Sackbohrung erwiesen, die 0,01 mm bis 0,10 mm beträgt. Bei den üblichen Druckverhältnissen in einem Kraftstoffeinspritzventil, wie es für schnelllaufende, selbstzündende Brennkraftmaschinen verwendet wird, ergibt sich bei einem Einspritzdruck von 100 MPa und mehr bei den normalerweise verwendeten Kraftstoffen eine optimale Drosse- lung des KraftstoffStroms .A height of the cylindrical section in the blind bore which has proven to be particularly advantageous is 0.01 mm to 0.10 mm. With the usual pressure conditions in a fuel injection valve, such as is used for high-speed, self-igniting internal combustion engines, with an injection pressure of 100 MPa and more, the fuel flow is optimally restricted for the fuels normally used.
Zeichnungdrawing
In der Zeichnung ist ein erfindungsgemäßes Kraftstoffein- spritzventil dargestellt. Es zeigtA fuel injection valve according to the invention is shown in the drawing. It shows
Figur 1 einen Längsschnitt durch ein erfindungsgemäßes1 shows a longitudinal section through an inventive
Kraftstoffeinspritzventil und Figur 2 eine Vergrößerung des mit II bezeichneten Ausschnitts der Figur 1.Fuel injection valve and FIG. 2 an enlargement of the section of FIG. 1 labeled II.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt. Ein Ventilkörper 1 weist eine Bohrung 3 auf, die an ihrem brennraumseitigen Ende von einem konischen Ventilsitz 7 begrenzt wird. Brennraumzuge- wandt zum konischen Ventilsitz 7 schließt sich an diesen eine Sackbohrung 22 an. Von der Sackbohrung 22 gehen mehrere Einspritzöffnungen 11 ab, die in Einbaulage des Kraftstoff- einspritzventils in den Brennraum der Brennkraftmaschine munden. In der Bohrung 3 ist eine kolbenförmige Ventilnadel 5 langsverschiebbar angeordnet, die in einem brennraumabge- wandten Abschnitt der Bohrung 3 mit einem Fuhrungsabschnitt 15 dichtend gefuhrt ist. Ausgehend vom Fuhrungsabschnitt 15 verjungt sich die Ventilnadel 5 unter Bildung einer Druckschulter 13 und geht an ihrem brennraumseitigen Ende in eine konische Ventildichtflache 9 über. Zwischen der Ventilnadel 5 und der Wand der Bohrung 3 ist ein Druckraum 19 ausgebildet, der auf Hohe der Druckschulter 13 radial erweitert ist. In die radiale Erweiterung des Druckraums 19 mundet ein im Ventilkorper 1 verlaufender Zulaufkanal 25, über den der Druckraum 19 mit Kraftstoff unter hohem Druck befullbar ist. Die Ventilnadel 5 wird an ihrem brennraumabgewandten Ende von einer Schließkraft beaufschlagt, die von einer in der Zeichnung nicht dargestellten Vorrichtung ausgeübt wird. Als Vorrichtung kommen beispielsweise eine Feder bzw. ein Federelement oder eine hydraulische Vorrichtung in Frage.In Figure 1, a fuel injection valve according to the invention is shown in longitudinal section. A valve body 1 has a bore 3 which is delimited at its combustion chamber end by a conical valve seat 7. Coming towards the combustion chamber toward the conical valve seat 7, a blind bore 22 adjoins this. A plurality of injection openings 11 extend from the blind bore 22 and, in the installed position of the fuel injection valve, into the combustion chamber of the internal combustion engine patronize. In the bore 3, a piston-shaped valve needle 5 is arranged so that it can be moved slowly, which is guided in a sealing manner in a section of the bore 3 facing away from the combustion chamber with a guide section 15. Starting from the guide section 15, the valve needle 5 tapers to form a pressure shoulder 13 and merges into a conical valve sealing surface 9 at its end on the combustion chamber side. Between the valve needle 5 and the wall of the bore 3, a pressure chamber 19 is formed, which is radially expanded at the height of the pressure shoulder 13. In the radial expansion of the pressure chamber 19, an inlet channel 25 runs in the valve body 1, via which the pressure chamber 19 can be filled with fuel under high pressure. The valve needle 5 is acted upon at its end facing away from the combustion chamber by a closing force which is exerted by a device not shown in the drawing. For example, a spring or a spring element or a hydraulic device can be used as the device.
Der Kraftstoffström aus dem Druckraum 19 zu den Einspritz- Öffnungen 11 wird durch die Langsbewegung der Ventilnadel 5 gesteuert. Ist die hydraulische Kraft durch den Druck im Druckraum 19 auf die Druckschulter 13 und auf Teile der Ventildichtflache 9 großer als die Schließkraft, die auf das brennraumabgewandte Ende der Ventilnadel 5 ausgeübt wird, so bewegt sich die Ventilnadel 5 vom Ventilsitz 7 weg und öffnet so einen Spalt zwischen der Ventildichtflache 9 und dem Ventilsitz 7. Dadurch kann Kraftstoff aus dem Druckraum 19 in die Sackbohrung 22 strömen und wird von dort durch die Einspritzoffnungen 11 in den Brennraum der Brennkraftmaschi- ne eingespritzt. Durch eine Erhöhung der Schließkraft oder eine Verminderung des hydraulischen Drucks im Druckraum 19 gleitet die Ventilnadel 5 zurück in ihre Schließstellung, d.h. in Anlage der Ventildichtflache 9 am Ventilsitz 7. Dadurch wird der Kraftstoffstrom vom Druckraum 19 in die Sack- bohrung 22 unterbrochen. In Figur 2 ist eine Vergrößerung des mit II bezeichneten Ausschnitts der Figur 1 im Bereich des Ventilsitzes 7 gezeigt. Die Sackbohrung 22 weist einen zylindrischen Ab- schnitt 24 auf, der sich direkt an den konischen Ventilsitz 7 anschließt. Die Einspritzöffnungen 11 gehen vom gerundeten Abschnitt der Sackbohrung 22 aus, der sich brennrau zuge- wandt an den zylindrischen Abschnitt 24 anschließt. Die Ventilnadel 5 weist neben der konischen Ventildichtflache 9 ei- nen zylindrischen Drosselabschnitt 26 und einen Endabschnitt 28 auf, wobei der zylindrische Drosselabschnitt 26 direkt an die konische Ventildichtfl che 9 grenzt. Der zylindrische Drosselabschnitt 26 ist in Schließstellung der Ventilnadel 5 so angeordnet, dass er bezüglich der Längsachse 4 der Boh- rung 3 auf derselben Höhe wie der zylindrische Abschnitt 24 angeordnet ist. Der Endabschnitt 28, der sich an den zylindrischen Drosselabschnitt 26 anschließt, ragt in die Drosselbohrung 22 hinein und vermindert so das Volumen der Sackbohrung 22, was die Kohlenwasserstoffemissionen senkt.The fuel flow from the pressure chamber 19 to the injection openings 11 is controlled by the longitudinal movement of the valve needle 5. If the hydraulic force due to the pressure in the pressure chamber 19 on the pressure shoulder 13 and on parts of the valve sealing surface 9 is greater than the closing force which is exerted on the end of the valve needle 5 facing away from the combustion chamber, the valve needle 5 moves away from the valve seat 7 and thus opens one Gap between the valve sealing surface 9 and the valve seat 7. This allows fuel to flow from the pressure chamber 19 into the blind bore 22 and is injected from there through the injection openings 11 into the combustion chamber of the internal combustion engine. By increasing the closing force or reducing the hydraulic pressure in the pressure chamber 19, the valve needle 5 slides back into its closed position, ie in contact with the valve sealing surface 9 on the valve seat 7. As a result, the fuel flow from the pressure chamber 19 into the blind bore 22 is interrupted. FIG. 2 shows an enlargement of the section of FIG. 1 designated II in the region of the valve seat 7. The blind bore 22 has a cylindrical section 24 which directly adjoins the conical valve seat 7. The injection openings 11 start from the rounded section of the blind bore 22, which adjoins the cylindrical section 24 facing towards the burnt finish. In addition to the conical valve sealing surface 9, the valve needle 5 has a cylindrical throttle section 26 and an end section 28, the cylindrical throttle section 26 directly adjoining the conical valve sealing surface 9. In the closed position of the valve needle 5, the cylindrical throttle section 26 is arranged such that it is arranged at the same height as the cylindrical section 24 with respect to the longitudinal axis 4 of the bore 3. The end section 28, which adjoins the cylindrical throttle section 26, projects into the throttle bore 22 and thus reduces the volume of the blind bore 22, which lowers the hydrocarbon emissions.
Beim Öffnungshub der Ventilnadel 5, also wenn die Ventilnadel 5 vom Ventilsitz 7 abhebt, strömt Kraftstoff aus dem Druckraum 19 zwischen dem Ventilsitz 7 und der Ventildichtflache 9 hindurch in die Sackbohrung 22. Durch den zylindri- sehen Abschnitt 24 und den zylindrischen Drosselabschnitt 26 wird ein Ringspalt gebildet, durch den der Kraftstoff hindurchströmt. Durch die zylindrische Ausprägung der Abschnitte 24, 26 ändert sich der Querschnitt dieses Ringspalts zu Beginn der Öffnungshubbewegung der Ventilnadel 5 nicht, so dass es zu einem gleichmäßig gedrosselten Einströmen vonDuring the opening stroke of the valve needle 5, that is to say when the valve needle 5 lifts off the valve seat 7, fuel flows out of the pressure space 19 between the valve seat 7 and the valve sealing surface 9 into the blind bore 22. Through the cylindrical section 24 and the cylindrical throttle section 26 a Annular gap is formed through which the fuel flows. Due to the cylindrical shape of the sections 24, 26, the cross section of this annular gap does not change at the beginning of the opening stroke movement of the valve needle 5, so that there is a uniformly throttled inflow of
Kraftstoff in die Sackbohrung 22 kommt. Dies vermindert die Umlenkverluste beim Einströmen des Kraftstoffs aus der Sackbohrung 22 in die Einspritzöffnungen 11, solange in der Sackbohrung 22 ein Kraftstoffdruck herrscht, der geringer als der Einspritzdruck im Druckraum 19 ist. Im weiteren Ver- lauf der Öffnungshubbewegung taucht der zylindrische Drosselabschnitt 26 aus dem zylindrischen Abschnitt 24 aus, so dass jetzt der Kraftstoff ungedrosselt aus dem Druckraum 19 in die Sackbohrung 22 einströmen kann, um möglichst viel Kraftstoff in kurzer Zeit durch die Einspritzöffnungen 11 einzuspritzen.Fuel comes into the blind bore 22. This reduces the deflection losses when the fuel flows from the blind bore 22 into the injection openings 11, as long as there is a fuel pressure in the blind bore 22 which is lower than the injection pressure in the pressure chamber 19. In the further sales During the opening stroke movement, the cylindrical throttle section 26 emerges from the cylindrical section 24, so that the fuel can now flow unthrottled from the pressure chamber 19 into the blind bore 22 in order to inject as much fuel as possible through the injection openings 11 in a short time.
Besonders vorteilhaft ist eine Höhe h des zylindrischen Abschnitts 24, die 0,01 mm bis 0,10 mm beträgt, vorzugsweise 0,01 mm bis 0,70 mm. Der zylindrische Drosselabschnitt 26 weist eine Höhe H auf, die etwas kleiner als die Höhe h des zylindrischen Abschnitts 24 ausgebildet ist, wobei über die Höhe H des zylindrischen Drosselabschnitts 26 der Zeitpunkt bestimmt werden kann, zu dem die Einströmung von Kraftstoff in die Sackbohrung 22 ungedrosselt erfolgt. A height h of the cylindrical section 24, which is 0.01 mm to 0.10 mm, preferably 0.01 mm to 0.70 mm, is particularly advantageous. The cylindrical throttle section 26 has a height H which is somewhat smaller than the height h of the cylindrical section 24, the height H of the cylindrical throttle section 26 being able to determine the point in time at which the inflow of fuel into the blind bore 22 is unthrottled he follows.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Ventilkörper (1) , in dem eine Bohrung (3) ausgebildet ist, an deren brennraumseitigen Ende ein konischer Ventilsitz (7) ausgebildet ist, an den sich brennraumseitig eine Sackbohrung (22) anschließt, wobei in der Sackbohrung (22) ein zylindrischer Abschnitt (24) ausgebildet ist und von der Sackbohrung (22) wenigstens eine Ein- spritzöffnung (11) abgeht, die in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraftmaschine mündet, und mit einer Ventilnadel (5) , die in der Bohrung (3) längsverschiebbar geführt ist und die an ihrem brennraumseitigen Ende eine konische Ventildichtflä- ehe (9) aufweist, mit der die Ventilnadel (5) mit dem konischen Ventilsitz (7) zusammenwirkt, dadurch gekennzeichnet, dass sich an die konische Ventildichtflache (9) der Ventilnadel (5) brennraumseitig ein zylindrischer Drosselabschnitt (26) anschließt.1. Fuel injection valve for internal combustion engines with a valve body (1), in which a bore (3) is formed, at the combustion chamber end of which a conical valve seat (7) is formed, to which a blind bore (22) is connected on the combustion chamber side, in the blind bore (22) a cylindrical section (24) is formed and from the blind bore (22) there is at least one injection opening (11) which opens into the combustion chamber of the internal combustion engine in the installed position of the fuel injection valve, and with a valve needle (5) which the bore (3) is longitudinally displaceable and has a conical valve sealing surface (9) on its combustion chamber end, with which the valve needle (5) interacts with the conical valve seat (7), characterized in that the conical valve sealing surface ( 9) of the valve needle (5) on the combustion chamber side is connected to a cylindrical throttle section (26).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass bei Anlage der Ventilnadel (5) am Ventilsitz (7) der zylindrische Abschnitt (24) der Sackbohrung (22) wenigstens annähernd bezüglich der Längsachse (4) der Bohrung (3) auf derselben Höhe wie der zylindri- sehe Drosselabschnitt (26) angeordnet ist.2. Fuel injection valve according to claim 1, characterized in that when the valve needle (5) abuts the valve seat (7) the cylindrical section (24) of the blind bore (22) is at least approximately at the same height with respect to the longitudinal axis (4) of the bore (3) how the cylindrical throttle section (26) is arranged.
3. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass der zylindrische Drosselabschnitt (26) der Ventilnadel (5) bei maximalem Hub der Ventilnadel (5) aus dem zylindrischen Abschnitt (24) der Sackbohrung (22; austaucht.3. Fuel injection valve according to claim 1, characterized in that the cylindrical throttle section (26) of the valve needle (5) at maximum stroke of the valve needle (5) emerges from the cylindrical section (24) of the blind bore (22;
4. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Höhe (h) des zylindrischen Abschnitts (24) der Sackbohrung (22) 0,01 mm bis 0,10 mm beträgt. 4. Fuel injection valve according to claim 1, characterized in that the height (h) of the cylindrical portion (24) of the blind bore (22) is 0.01 mm to 0.10 mm.
EP03815941A 2003-02-18 2003-08-21 Fuel injection valve for an internal combustion engine Withdrawn EP1597475A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10306700 2003-02-18
DE2003106700 DE10306700A1 (en) 2003-02-18 2003-02-18 Fuel injection valve for IC engine has a cylindrical section of the dosing needle and the injector bore to maintain an even aperture over part of the needle displacement
PCT/DE2003/002789 WO2004074676A1 (en) 2003-02-18 2003-08-21 Fuel injection valve for an internal combustion engine

Publications (1)

Publication Number Publication Date
EP1597475A1 true EP1597475A1 (en) 2005-11-23

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ID=32747967

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EP03815941A Withdrawn EP1597475A1 (en) 2003-02-18 2003-08-21 Fuel injection valve for an internal combustion engine

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EP (1) EP1597475A1 (en)
DE (1) DE10306700A1 (en)
WO (1) WO2004074676A1 (en)

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Publication number Priority date Publication date Assignee Title
DE102008039920A1 (en) * 2008-08-27 2010-03-04 Continental Automotive Gmbh Nozzle body, nozzle assembly and fuel injector, and method of making a nozzle body
DE102009042155A1 (en) 2009-09-21 2011-04-07 Continental Automotive Gmbh Fuel injection valve for an internal combustion engine
DE102010030934A1 (en) 2010-07-05 2012-01-05 Robert Bosch Gmbh Injector i.e. common-rail fuel injector, for common-rail fuel injection system of motor car, has seat surface designed as cone-shaped surface, where bent angles of surface are between preset ranges, and sealing portion forming sealing seat

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Publication number Priority date Publication date Assignee Title
IT1167325B (en) * 1983-04-11 1987-05-13 Roberto Bosio PULVERIZER FOR DIESEL ENGINE FUEL INJECTORS
EP0283154A1 (en) * 1987-03-14 1988-09-21 LUCAS INDUSTRIES public limited company Fuel injection nozzle
JPH07286570A (en) * 1994-04-19 1995-10-31 Shin A C Ii:Kk Fuel injection nozzle for diesel engine

Non-Patent Citations (1)

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Title
See references of WO2004074676A1 *

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DE10306700A1 (en) 2004-08-26
WO2004074676A1 (en) 2004-09-02

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