EP1387939B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1387939B1
EP1387939B1 EP02726069A EP02726069A EP1387939B1 EP 1387939 B1 EP1387939 B1 EP 1387939B1 EP 02726069 A EP02726069 A EP 02726069A EP 02726069 A EP02726069 A EP 02726069A EP 1387939 B1 EP1387939 B1 EP 1387939B1
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EP
European Patent Office
Prior art keywords
valve needle
pressure
piston rod
valve
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.)
Expired - Lifetime
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EP02726069A
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German (de)
French (fr)
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EP1387939A1 (en
Inventor
Peter Boehland
Sebastian Kanne
Godehard Nentwig
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the injection pressure with which the fuel is injected through the fuel injection valve is increased.
  • the number of injection holes of the fuel injection valve is increased, so that the diameter of the individual injection holes can be reduced.
  • the aim of this measure is to increase the beam energy in injection jets while reducing the droplet diameter. If very small quantities are to be pumped, the injection times become very short at high pressures at the fuel injection valve. This has a violent combustion process with correspondingly large noise development.
  • a fuel injection valve with variable injection cross section in which two rows of injection openings are formed.
  • These injection ports are from an inner valve needle and a valve needle controlled surrounding sleeve, wherein both the sleeve and the inner needle are acted upon by closing springs which press them in abutment against a valve seat, whereby the injection openings are closed. If fuel is introduced under high pressure in corresponding pressure chambers, the sleeve and the inner needle are acted upon by the fuel pressure in these pressure chambers.
  • the inner needle Depending on the pressure of the introduced fuel only the inner needle lifts from the valve seat and releases the first row of injection ports or successively lift the inner needle and sleeve away from the valve seat so that both rows of injection ports are sequentially opened.
  • the opening of the inner needle or the sleeve is thus pressure-controlled, so that the successive control of inner needle and outer sleeve is achieved by a clever design of the pressure surfaces and the force of the closing springs.
  • EP 0 978 649 shows another fuel injection valve with variable injection cross-section.
  • stroke-controlled fuel injection systems are known in which a valve needle has a pressure surface which is constantly acted upon by fuel under high pressure in the opening direction.
  • the counterforce is not generated by a closing spring, but hydraulically by a valve piston which acts on the valve needle and in turn by the fuel pressure in a control chamber exerts a closing force on the valve needle.
  • a closing spring which acts on the valve needle and in turn by the fuel pressure in a control chamber exerts a closing force on the valve needle.
  • the closing force on the valve needle changes, so that it is moved by the hydraulic force on the pressure surface.
  • variable injection cross-section ie the variable injection cross-section and the stroke-controlled injection system
  • stroke-controlled injection system would be particularly advantageous for further optimization of the combustion process. So far, however, this was not possible without great effort to transfer the variable injection cross section readily on the stroke-controlled systems. For this purpose, complicated sealing edges or additional control valves are needed, which are expensive to manufacture and expensive.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that with a stroke-controlled injection system, two rows of injection ports are successively als Kunststoffbar and so a Einspritzverlaufsformung is possible without additional control edges or control valves are needed.
  • an inner valve needle is guided, wherein both the outer valve needle and the inner valve needle controls at least one injection port.
  • a fuel-filled control chamber is formed, by the pressure of the valve needles are acted upon at least indirectly in the direction of the valve seat. If the pressure in the control room changed, so does the closing force through the valve needles, so that a control of the injection openings is possible.
  • a throttle connection is formed by the opening stroke of the outer valve needle, so that the inner valve needle is no longer acted upon by the pressure in the control chamber.
  • the outer valve needle is connected to an outer piston rod, whose end face is acted upon by the pressure in the control chamber and thereby generates the closing force on the valve member.
  • the throttle connection between the end face of the piston rod and a stationary base is formed, so that in a simple and thus easy to manufacture manner, the throttle connection can be formed.
  • the inner valve needle is also connected to an inner piston rod whose front side is also acted upon by the pressure in the pressure chamber and thus generates the closing force on the inner valve needle.
  • the inner piston rod is guided in the outer piston rod, so that both piston rods are arranged coaxially to each other.
  • the inner piston rod comes in the opening stroke of the inner valve needle at one on the inside of the outer piston rod trained stop surface to the plant.
  • the stroke stop of the inner valve needle is realized in a simple manner, without a stroke stop must be formed on the housing of the fuel injection valve.
  • the outer piston rod has an inwardly cantilevered region at its end facing away from the combustion chamber.
  • an inner control chamber is bounded by the outer valve needle, the inwardly cantilevered region and the inner valve needle, which is connected to the control chamber, wherein the connection is in the form of a connecting bore.
  • the inner valve needle on a pressure surface which is acted upon by the pressure in the pressure chamber only after the outer valve needle has lifted from the valve seat. This results in an opening force on the inner valve needle only if an injection is to take place. As a result, no opening force acts on the inner valve needle between the injections and the latter always closes the injection openings assigned to it safely.
  • the pressure in the control chamber is adjusted by a controllable by a valve connection with a leakage oil space. So only this one 2/2 valve is necessary for the pressure control, since the inlet throttle remains unchanged.
  • the inlet throttle at least partially. This results in a further reduction of the pressure in the control chamber, so that the closing force on the inner valve needle decreases further.
  • an appropriate design of the opening forces on the valve needles can be achieved that the inner valve needle only after the outer valve needle has closed the inlet throttle performs an opening stroke and so the injection ports are opened successively. In this way, the injection rate at the beginning of the injection is smaller than during the main injection, in which all the injection openings are released, so that a Einspritzverlaufsformung is achieved.
  • the fuel injection valve comprises a housing 1, which may be constructed in several parts.
  • the housing 1 has at its combustion chamber end portion a bore 3, in which a piston-shaped outer valve needle 10 is arranged.
  • the outer valve needle 10 is sealingly guided in a bore away from combustion chamber in the bore 3 and tapers to form a pressure shoulder 9 to the combustion chamber.
  • the outer valve needle 10 passes into a conical pressure surface 101 and finally into a likewise conical valve sealing surface 11, wherein the sealing surface 11 comes into abutment in the closed position of the outer valve needle 10 at a formed on the combustion chamber end of the bore 3 valve seat 13.
  • FIG. 2 shows an enlarged view of the section of FIG.
  • a pressure chamber 5 is formed in the housing 1 at the level of the pressure shoulder 9, which continues as a valve surrounding the outer valve 10 annular channel to the valve seat 13.
  • a plurality of injection openings 7 are formed, which are arranged in a first row of injection openings 107 and in a second row of injection openings 207 arranged offset axially thereto.
  • an inner valve needle 12 is arranged, which is piston-shaped and which has a conical pressure surface 112 and a valve sealing surface 14 at its combustion chamber end.
  • the valve sealing surface 14 contacts the valve seat 13 between the first row of injection openings 107 and the second row of injection openings 207.
  • the interaction of the outer valve needle 10 and the inner valve needle 12, the Einspritzö réelles Herbertn 107, 207 connect to the pressure chamber 5 , If the outer valve needle 10 is in contact with the valve sealing surface 11 on the valve seat 13, then both rows of injection openings 107, 207 are closed against the pressure chamber 5.
  • inlet channel 15 of the pressure chamber 5 is connected to a high-pressure port 17 which is connected to a high-pressure fuel source, not shown in the drawing.
  • the high-pressure fuel source in this case provides during operation of the internal combustion engine, a predetermined high-pressure fuel, so that in the inlet channel 15 and thus also in the pressure chamber 5 always this fuel pressure prevails and forms a high-pressure fuel area.
  • a piston bore 18 embodied as a blind bore is formed in the housing 1 and has a base surface 19.
  • an outer piston rod 20 is arranged longitudinally displaceable, which abuts with its combustion chamber facing end face on the outer valve needle 10 and the combustion chamber facing away from its end face 21 formed at the end of the piston bore 18 control chamber 24.
  • the piston bore 18 is formed at the combustion chamber end portion of the piston rod 20, a spring chamber 8 in the housing 1, in which a spring 42 is arranged under pressure bias.
  • the spring 42 is supported at the end away from the combustion chamber stationary and abuts at its combustion chamber end facing a spring plate 44 which is connected to the outer piston rod 20, so that the spring 42 a force in the direction of the valve seat 13 on the outer piston rod 20 and thus exerts on the outer valve needle 10.
  • an inner piston rod 22 is arranged, which is longitudinally displaceable in the outer piston rod 20. At its end facing the combustion chamber, the inner piston rod 22 abuts on the inner valve needle 12, so that the inner piston rod 22 and the inner valve needle 12 move synchronously.
  • Figure 3 shows an enlargement of Figure 1 in the region of the control chamber 24.
  • the control chamber 24 is bounded by the base 19, the wall of the piston bore 18 and the end face 21 of the outer piston rod 20.
  • the outer piston rod 20 has at its end facing away from the combustion chamber on an inwardly cantilevered region 27, so that an inner control chamber 29 is limited by the outer piston rod 20 and the brennraumabgewandte end face 31 of the inner piston rod 22 via a connecting hole 28 in the outer piston rod 20th is connected to the control room 24.
  • a stop surface 23 is formed which limits the longitudinal movement of the inner piston rod 22.
  • the control chamber 24 is connected via an inlet throttle 25 to the inlet channel 15.
  • the control chamber 24 is connected via an outlet throttle 25 with a formed in the housing 1 leakage oil chamber 30.
  • a longitudinally movable magnet armature 34 is arranged, which has a sealing ball 32 at its end facing the control chamber 24.
  • the armature 34 is acted upon by a closing spring 38, which presses the armature 34 in the direction of the control chamber 24.
  • an electromagnet 36 is arranged, which exerts an attractive force on the magnet armature 34 with appropriate energization and moves it away from the control chamber 24 against the force of the closing spring 38.
  • the magnet armature 34 is pressed by the closing spring 38 in the direction of the control chamber 24, and the sealing ball 32 closes the outlet throttle 26.
  • the electromagnet 36 is energized, the magnet armature 34 is moved away from the control chamber 24 and the sealing ball 32 is present the outlet throttle 26 free. In this position, fuel can flow out of the control chamber 24 into the leakage oil chamber 30 via the outlet throttle 26.
  • the magentanker 34, the sealing ball 32 and the electromagnet 36 thus form a valve 33.
  • the operation of the fuel injection valve is as follows: In the closed state of the fuel injection valve, so if no fuel is injected through the injection openings 7 in the combustion chamber of the internal combustion engine, the sealing ball 32 closes the outlet throttle 26. By the inlet throttle 25 prevails in the control chamber 24, the same fuel pressure as in the inlet channel 15. This results in a hydraulic force on the end face 21 of the outer piston rod 20 and on the end face 31 of the inner piston rod 22, which transmit this to the outer valve needle 10 and the inner valve needle 12, so that the valve needles 10,12 be pressed in contact with the valve seat 13 and close the injection openings 7.
  • the size ratio of the end face 21 to the pressure shoulder 9 and the pressure surface 101 of the outer valve needle 10 is designed so that in this state of the fuel injection valve, the hydraulic force on the end face 21 of the outer piston rod 20 outweighs. If an injection of fuel into the combustion chamber, so the electromagnet 36 is energized, causing the armature 34 and thus also the sealing ball 32 move away from the outlet throttle 26 and connect via the outlet throttle 26 the control chamber 24 with the leakage oil chamber 30.
  • the flow resistances of the inlet throttle 25 and outlet throttle 26 are designed so that the fuel pressure thereby drops in the control chamber 24, to the extent that the outer valve needle 10 through the pressure surface 101 and the pressure shoulder 9 experiences a greater hydraulic force than that now still on the Front side 21 of the outer piston rod 20 acting hydraulic force in the control chamber 24th
  • the inner piston rod 22 moves in the axial direction until it comes to rest on the abutment surface 23 of the outer piston rod 20.
  • an injection progression is achieved in which, at the beginning of the injection, fuel is injected into the combustion chamber of the internal combustion engine at full pressure, but only through part of the injection openings 7, while in the main injection all injection ports 7 of both injection port rows 107 and 207 is injected and thus with a higher injection rate.
  • the energization of the electromagnet 36 is stopped and driven by the closing spring 38 closes the sealing ball 32 on the armature 34, the outlet throttle 26 so that again by the fuel flowing through the inlet throttle 25 fuel pressure of the inlet channel 15 in the control chamber 24th and both pushes the outer piston rod 20 and the inner piston rod 22 in the direction of the valve seat 13, so that the inner valve needle 12 and the outer valve needle 10 are moved back into the closed position.
  • valve 33 which is formed by the electromagnet 34, the armature 34 and the sealing ball 32, again closed before the fuel pressure in the control chamber 24 has dropped so far that the inner valve needle 12 opens.
  • the outlet throttle 26 is then already closed again before the outer piston rod 20 comes to rest with the end face 21 on the base 19 of the piston bore 18. This results between the end face 21 and the base 19, a hydraulic cushion which dampens the opening movement of the outer piston rod 20 and prevents a pressure drop in the control chamber 24, so that the inner piston rod 22 always exerts a sufficient closing force on the inner valve needle 12.
  • the inlet throttle 25 partially covers, so that the cross section of the inlet throttle 25 is reduced, but this is not completely closed. This can be realized for example by a remaining annular gap between the outer piston rod 20 and the wall of the piston bore 18.
  • the connection of the control chamber 24 with the outlet throttle 26 is ensured, for example, by grooves extending in the radial direction on the end face 21 of the outer piston rod 20.

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

Description

Stand der TechnikState of the art

Zur Senkung der Emissionen und zur Steigerung des Wirkungsgrads von Brennkraftmaschinen mit direkter Kraftstoffeinspritzung ist es ein Ziel, den Kraftstoff möglichst fein zerstäubt in den Brennraum der Brennkraftmaschine einzuspritzen. Hierzu wird zum einen der Einspritzdruck erhöht, mit dem der Kraftstoff durch das Kraftstoffeinspritzventil eingespritzt wird. Zum anderen wird die Anzahl der Spritzlöcher des Kraftstoffeinspritzventils erhöht, so daß der Durchmesser der einzelnen Spritzlöcher gesenkt werden kann. Das Ziel dieser Maßnahme ist es, die Strahlenenergie bei Einspritzstrahlen zu erhöhen bei gleichzeitiger Verringerung des Tropfendurchmessers. Sollen sehr kleine Mengen gefördert werden, so werden bei hohen Drücken am Kraftstoffeinspritzventil die Einspritzzeiten sehr kurz. Dies hat einen heftigen Verbrennungsverlauf mit entsprechend großer Geräuschentwicklung zur Folge.To reduce emissions and increase the efficiency of internal combustion engines with direct fuel injection, it is an objective to inject the fuel atomized as finely as possible into the combustion chamber of the internal combustion engine. For this purpose, on the one hand, the injection pressure with which the fuel is injected through the fuel injection valve is increased. On the other hand, the number of injection holes of the fuel injection valve is increased, so that the diameter of the individual injection holes can be reduced. The aim of this measure is to increase the beam energy in injection jets while reducing the droplet diameter. If very small quantities are to be pumped, the injection times become very short at high pressures at the fuel injection valve. This has a violent combustion process with correspondingly large noise development.

Beispielsweise aus der europäischen Patentanmeldung EP 0 470 348 A1 ist ein Kraftstoffeinspritzventil mit variablem Einspritzquerschnitt bekannt, bei dem zwei Reihen von Einspritzöffnungen ausgebildet sind. Diese Einspritzöffnungen werden von einer inneren Ventilnadel und einer die Ventilnadel umgebenden Hülse gesteuert, wobei sowohl die Hülse als auch die Innennadel von Schließfedern beaufschlagt sind, die diese in Anlage an einen Ventilsitz drücken, wodurch die Einspritzöffnungen verschlossen werden. Wird Kraftstoff unter hohem Druck in entsprechende Druckräume eingebracht, so werden die Hülse und die Innennadel vom Kraftstoffdruck in diesen Druckräumen beaufschlagt. Je nach Druck des eingeführten Kraftstoffs hebt nur die Innennadel vom Ventilsitz ab und gibt die erste Reihe von Einspritzöffnungen frei oder es heben sukzessiv die Innennadel und die Hülse vom Ventilsitz ab, so daß beide Reihen von Einspritzöffnungen nacheinander aufgesteuert werden. Das Öffnen der Innennadel bzw. der Hülse erfolgt also druckgesteuert, so daß das sukzessive Aufsteuern von Innennadel und äußerer Hülse durch eine geschickte Auslegung der Druckflächen und der Kraft der Schließfedern erreicht wird.For example, from the European patent application EP 0 470 348 A1 is known a fuel injection valve with variable injection cross section, in which two rows of injection openings are formed. These injection ports are from an inner valve needle and a valve needle controlled surrounding sleeve, wherein both the sleeve and the inner needle are acted upon by closing springs which press them in abutment against a valve seat, whereby the injection openings are closed. If fuel is introduced under high pressure in corresponding pressure chambers, the sleeve and the inner needle are acted upon by the fuel pressure in these pressure chambers. Depending on the pressure of the introduced fuel only the inner needle lifts from the valve seat and releases the first row of injection ports or successively lift the inner needle and sleeve away from the valve seat so that both rows of injection ports are sequentially opened. The opening of the inner needle or the sleeve is thus pressure-controlled, so that the successive control of inner needle and outer sleeve is achieved by a clever design of the pressure surfaces and the force of the closing springs.

EP 0 978 649 zeigt ein anderes kraftstoffeinspritzventil mit variablem Einspritzquerschnitt. EP 0 978 649 shows another fuel injection valve with variable injection cross-section.

Darüber hinaus sind aus dem Stand der Technik hubgesteuerte Kraftstoffeinspritzsysteme bekannt, bei denen eine Ventilnadel eine Druckfläche aufweist, die ständig mit Kraftstoff unter hohem Druck in Öffnungsrichtung beaufschlagt wird. Die Gegenkraft wird nicht durch eine Schließfeder erzeugt, sondern hydraulisch durch einen Ventilkolben, der auf die Ventilnadel wirkt und der durch den Kraftstoffdruck in einem Steuerraum wiederum eine Schließkraft auf die Ventilnadel ausübt. Als Beispiel sei hier die Schrift DE 198 27 267 A1 genannt. Durch Veränderung des Kraftstoffdrucks im Steuerraum ändert sich die Schließkraft auf die Ventilnadel, so daß diese durch die hydraulische Kraft auf die Druckfläche bewegt wird. Solche hubgesteuerten Kraftstoffeinspritzsysteme werden in vielen modernen Brennkraftmaschinen eingesetzt, insbesondere für selbstzündende Brennkraftmaschinen in Personenkraftwagen.In addition, from the prior art stroke-controlled fuel injection systems are known in which a valve needle has a pressure surface which is constantly acted upon by fuel under high pressure in the opening direction. The counterforce is not generated by a closing spring, but hydraulically by a valve piston which acts on the valve needle and in turn by the fuel pressure in a control chamber exerts a closing force on the valve needle. As an example, here is the font DE 198 27 267 A1 called. By changing the fuel pressure in the control chamber, the closing force on the valve needle changes, so that it is moved by the hydraulic force on the pressure surface. Such stroke-controlled fuel injection systems are used in many modern internal combustion engines, in particular for self-igniting internal combustion engines in passenger cars.

Eine Verbindung beider Systeme, also des variablen Einspritzquerschnitts und des hubgesteuerten Einspritzsystems, wäre für eine weitere Optimierung des Verbrennungsprozesses besonders vorteilhaft. Bisher war dies jedoch nicht ohne großen Aufwand möglich, den variablen Einspritzquerschnitt ohne weiteres auf die hubgesteuerten Systeme zu übertragen. Hierzu sind komplizierte Dichtkanten oder zusätzliche Steuerventile nötig, die aufwendig zu fertigen und kostenintensiv sind.A combination of both systems, ie the variable injection cross-section and the stroke-controlled injection system, would be particularly advantageous for further optimization of the combustion process. So far, however, this was not possible without great effort to transfer the variable injection cross section readily on the stroke-controlled systems. For this purpose, complicated sealing edges or additional control valves are needed, which are expensive to manufacture and expensive.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, daß mit einem hubgesteuerten Einspritzsystem zwei Reihen von Einspritzöffnungen sukzessiv aufsteuerbar sind und so eine Einspritzverlaufsformung möglich ist, ohne daß zusätzliche Steuerkanten oder Steuerventile nötig sind. In der äußeren Ventilnadel ist eine innere Ventilnadel geführt, wobei sowohl die äußere Ventilnadel als auch die innere Ventilnadel wenigstens eine Einspritzöffnung steuert. Im Kraftstoffeinspritzventil ist ein kraftstoffgefüllter Steuerraum ausgebildet, durch dessen Druck die Ventilnadeln zumindest mittelbar in Richtung des Ventilsitzes beaufschlagt werden. Wird der Druck im Steuerraum verändert, so verändert sich auch die Schließkraft durch die Ventilnadeln, so daß eine Ansteuerung der Einspritzöffnungen möglich ist.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that with a stroke-controlled injection system, two rows of injection ports are successively aufsteuerbar and so a Einspritzverlaufsformung is possible without additional control edges or control valves are needed. In the outer valve needle, an inner valve needle is guided, wherein both the outer valve needle and the inner valve needle controls at least one injection port. In the fuel injection valve, a fuel-filled control chamber is formed, by the pressure of the valve needles are acted upon at least indirectly in the direction of the valve seat. If the pressure in the control room changed, so does the closing force through the valve needles, so that a control of the injection openings is possible.

In einer vorteilhaften Ausgestaltung der Erfindung wird durch die Öffnungshubbewegung der äußeren Ventilnadel eine Drosselverbindung gebildet, so daß die innere Ventilnadel nicht mehr vom Druck im Steuerraum beaufschlagt wird. Hierdurch wird die Schließkraft auf die innere Ventilnadel in einfacher Weise reduziert, ohne daß eine Steuerkante oder ein weiteres Ventil notwendig wäre.In an advantageous embodiment of the invention, a throttle connection is formed by the opening stroke of the outer valve needle, so that the inner valve needle is no longer acted upon by the pressure in the control chamber. As a result, the closing force on the inner valve needle in easily reduced, without a control edge or another valve would be necessary.

In einer vorteilhaften Ausgestaltung ist die äußere Ventilnadel mit einer äußeren Kolbenstange verbunden, deren Stirnfläche vom Druck im Steuerraum beaufschlagt ist und dadurch die Schließkraft auf das Ventilglied erzeugt. Hierdurch lassen sich die Funktion der Ventilnadel und der druckbeaufschlagten Kolbenstange in vorteilhafter Weise voneinander trennen und so jeweils optimal gestalten.In an advantageous embodiment, the outer valve needle is connected to an outer piston rod, whose end face is acted upon by the pressure in the control chamber and thereby generates the closing force on the valve member. As a result, the function of the valve needle and the pressurized piston rod can be separated from each other in an advantageous manner and thus optimally designed.

In einer weiteren vorteilhaften Ausgestaltung wird die Drosselverbindung zwischen der Stirnseite der Kolbenstange und einer ortsfesten Grundfläche gebildet, so daß in einfacher und damit gut zu fertigenden Weise die Drosselverbindung ausgebildet werden kann.In a further advantageous embodiment, the throttle connection between the end face of the piston rod and a stationary base is formed, so that in a simple and thus easy to manufacture manner, the throttle connection can be formed.

In einer weiteren vorteilhaften Ausgestaltung ist auch die innere Ventilnadel mit einer inneren Kolbenstange verbunden, deren Stirnseite ebenfalls vom Druck im Druckraum beaufschlagt ist und so die Schließkraft auf die innere Ventilnadel erzeugt. Dadurch läßt sich auch hier die Funktion von Ventilnadel und Kolbenstange trennen.In a further advantageous embodiment, the inner valve needle is also connected to an inner piston rod whose front side is also acted upon by the pressure in the pressure chamber and thus generates the closing force on the inner valve needle. As a result, the function of valve needle and piston rod can be separated here as well.

In einer weiteren vorteilhaften Ausgestaltung ist die innere Kolbenstange in der äußeren Kolbenstange geführt, so daß beide Kolbenstangen koaxial zueinander angeordnet sind. Hierdurch läßt sich die Verbindung der äußeren Kolbenstange zur äußeren Ventilnadel und der inneren Ventilnadel zur inneren Kolbenstange in vorteilhafter Weise einfach realisieren.In a further advantageous embodiment, the inner piston rod is guided in the outer piston rod, so that both piston rods are arranged coaxially to each other. As a result, the connection of the outer piston rod to the outer valve needle and the inner valve needle to the inner piston rod can be realized in an advantageous manner in an advantageous manner.

In einer weiteren vorteilhaften Ausgestaltung kommt die innere Kolbenstange bei der Öffnungshubbewegung der inneren Ventilnadel an einer an der Innenseite der äußeren Kolbenstange ausgebildeten Anschlagfläche zur Anlage. Hierdurch wird der Hubanschlag der inneren Ventilnadel in einfacher Art und Weise realisiert, ohne daß ein Hubanschlag am Gehäuse des Kraftstoffeinspritzventils ausgebildet sein muß.In a further advantageous embodiment, the inner piston rod comes in the opening stroke of the inner valve needle at one on the inside of the outer piston rod trained stop surface to the plant. As a result, the stroke stop of the inner valve needle is realized in a simple manner, without a stroke stop must be formed on the housing of the fuel injection valve.

In einer weiteren vorteilhaften Ausgestaltung weist die äußere Kolbenstange an ihrem brennraumabgewandten Ende einen nach innen kragenden Bereich auf. Hierdurch wird durch die äußere Ventilnadel, den nach innen kragenden Bereich und die innere Ventilnadel ein innerer Steuerraum begrenzt, der mit dem Steuerraum verbunden, wobei die Verbindung in Form einer Verbindungsbohrung ausgebildet ist. Hierdurch läßt sich der Druckausgleich zwischen dem Steuerraum und dem inneren Steuerraum und damit die Schließkraft auf die innere Ventilnadel bei der Öffnungshubbewegung durch Gestaltung der Verbindungsbohrung abstimmen, so daß ein definiertes sukzessives Öffnen von äußerer Ventilnadel und innerer Ventilnadel stattfindet und damit die gewünschte Einspritzverlaufsformung.In a further advantageous embodiment, the outer piston rod has an inwardly cantilevered region at its end facing away from the combustion chamber. As a result, an inner control chamber is bounded by the outer valve needle, the inwardly cantilevered region and the inner valve needle, which is connected to the control chamber, wherein the connection is in the form of a connecting bore. As a result, the pressure equalization between the control chamber and the inner control chamber and thus the closing force on the inner valve needle in the opening stroke can be tuned by design of the connecting hole, so that a defined successive opening of the outer valve needle and inner valve needle takes place and thus the desired Einspritzverlaufsformung.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung weist die innere Ventilnadel eine Druckfläche auf, die erst nachdem die äußere Ventilnadel vom Ventilsitz abgehoben hat vom Druck im Druckraum beaufschlagt wird. Hierdurch ergibt sich nur dann eine Öffnungskraft auf die innere Ventilnadel, wenn eine Einspritzung erfolgen soll. Dadurch wirkt zwischen den Einspritzungen keine Öffnungskraft auf die innere Ventilnadel und diese verschließt die ihr zugeordneten Einspritzöffnungen stets sicher.In a further advantageous embodiment of the invention, the inner valve needle on a pressure surface which is acted upon by the pressure in the pressure chamber only after the outer valve needle has lifted from the valve seat. This results in an opening force on the inner valve needle only if an injection is to take place. As a result, no opening force acts on the inner valve needle between the injections and the latter always closes the injection openings assigned to it safely.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung wird der Druck im Steuerraum durch eine durch ein Ventil steuerbare Verbindung mit einem Leckölraum eingestellt. So ist nur dieses eine 2/2-Ventil für die Drucksteuerung notwendig, da die Zulaufdrossel unverändert bleibt.In a further advantageous embodiment of the invention, the pressure in the control chamber is adjusted by a controllable by a valve connection with a leakage oil space. So only this one 2/2 valve is necessary for the pressure control, since the inlet throttle remains unchanged.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung verschließt die äußere Kolbenstange bei der Öffnungshubbewegung der äußeren Ventilnadel die Zulaufdrossel zumindest teilweise. Hierdurch kommt es zu einer weiteren Absenkung des Drucks im Steuerraum, so daß die Schließkraft auf die innere Ventilnadel weiter abnimmt. Durch eine entsprechende Auslegung der öffnenden Kräfte auf die Ventilnadeln läßt sich erreichen, daß die innere Ventilnadel erst nachdem die äußere Ventilnadel die Zulaufdrossel verschlossen hat, eine Öffnungshubbewegung ausführt und so die Einspritzöffnungen sukzessiv aufgesteuert werden. Auf diese Weise ist die Einspritzrate zu Beginn der Einspritzung kleiner als während der Haupteinspritzung, bei der sämtliche Einspritzöffnungen freigegeben sind, so daß eine Einspritzverlaufsformung erreicht wird.In a further advantageous embodiment of the invention closes the outer piston rod at the opening stroke of the outer valve needle, the inlet throttle at least partially. This results in a further reduction of the pressure in the control chamber, so that the closing force on the inner valve needle decreases further. By an appropriate design of the opening forces on the valve needles can be achieved that the inner valve needle only after the outer valve needle has closed the inlet throttle performs an opening stroke and so the injection ports are opened successively. In this way, the injection rate at the beginning of the injection is smaller than during the main injection, in which all the injection openings are released, so that a Einspritzverlaufsformung is achieved.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention are the description of the drawing and the claims removed.

Zeichnungdrawing

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

  • Figur 1 einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
  • Figur 2 eine Vergrößerung von Figur 1 im mit II bezeichneten Bereich,
  • Figur 3 eine Vergrößerung von Figur 1 im mit III bezeichneten Bereich,
  • Figur 4 den gleichen Ausschnitt wie Figur 3, wobei die äußere Kolbenstange in einer anderen Schaltstellung ist.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
  • 1 shows a longitudinal section through a fuel injection valve according to the invention,
  • FIG. 2 shows an enlargement of FIG. 1 in the area denoted by II,
  • FIG. 3 shows an enlargement of FIG. 1 in the area designated III,
  • Figure 4 shows the same section as Figure 3, wherein the outer piston rod is in a different switching position.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils im Längsschnitt dargestellt. Das Kraftstoffeinspritzventil umfaßt ein Gehäuse 1, das mehrteilig aufgebaut sein kann. Das Gehäuse 1 weist an seinem brennraumseitigen Endbereich eine Bohrung 3 auf, in der eine kolbenförmige äußere Ventilnadel 10 angeordnet ist. Die äußere Ventilnadel 10 wird in einem brennraumabgewandten Abschnitt in der Bohrung 3 dichtend geführt und verjüngt sich unter Bildung einer Druckschulter 9 dem Brennraum zu. Am brennraumseitigen Ende geht die äußere Ventilnadel 10 in eine konische Druckfläche 101 und schließlich in eine ebenfalls konische Ventildichtfläche 11 über, wobei die Dichtfläche 11 in Schließstellung der äußeren Ventilnadel 10 an einem am brennraumseitigen Ende der Bohrung 3 ausgebildeten Ventilsitz 13 zur Anlage kommt. In Figur 2 ist eine vergrößerte Darstellung des mit II bezeichneten Ausschnitts von Figur 1 im Bereich des Ventilsitzes 13 dargestellt. Durch eine radiale Erweiterung der Bohrung 3 ist auf Höhe der Druckschulter 9 ein Druckraum 5 im Gehäuse 1 ausgebildet, der sich als ein die äußere Ventilnadel 10 umgebender Ringkanal bis zum Ventilsitz 13 fortsetzt. Im Ventilsitz 13 sind mehrere Einspritzöffnungen 7 ausgebildet, die in einer ersten Einspritzöffnungsreihe 107 und in einer axial dazu versetzt angeordneten zweiten Einspritzöffnungsreihe 207 angeordnet sind. Bei Anlage der äußeren Ventilnadel 10 am Ventilsitz 13 verschließt diese alle Einspritzöffnungen 7 gegen den Druckraum 5, so daß aus diesem kein Kraftstoff zu den Einspritzöffnungen 7 gelangen kann.1 shows an embodiment of the fuel injection valve according to the invention is shown in longitudinal section. The fuel injection valve comprises a housing 1, which may be constructed in several parts. The housing 1 has at its combustion chamber end portion a bore 3, in which a piston-shaped outer valve needle 10 is arranged. The outer valve needle 10 is sealingly guided in a bore away from combustion chamber in the bore 3 and tapers to form a pressure shoulder 9 to the combustion chamber. At the combustion chamber end, the outer valve needle 10 passes into a conical pressure surface 101 and finally into a likewise conical valve sealing surface 11, wherein the sealing surface 11 comes into abutment in the closed position of the outer valve needle 10 at a formed on the combustion chamber end of the bore 3 valve seat 13. FIG. 2 shows an enlarged view of the section of FIG. 1 designated by II in the region of the valve seat 13. By a radial extension of the bore 3, a pressure chamber 5 is formed in the housing 1 at the level of the pressure shoulder 9, which continues as a valve surrounding the outer valve 10 annular channel to the valve seat 13. In the valve seat 13 a plurality of injection openings 7 are formed, which are arranged in a first row of injection openings 107 and in a second row of injection openings 207 arranged offset axially thereto. When the outer valve needle 10 abuts the valve seat 13, it closes all the injection openings 7 against the pressure chamber 5, so that no fuel can reach the injection openings 7 from it.

In der äußeren Ventilnadel 10 ist eine innere Ventilnadel 12 angeordnet, die kolbenförmig ausgebildet ist und die an ihrem brennraumseitigen Ende eine konische Druckfläche 112 und eine Ventildichtfläche 14 aufweist. Kommt die innere Ventilnadel 12 am Ventilsitz 13 zur Anlage, so berührt die Ventildichtfläche 14 den Ventilsitz 13 zwischen der ersten Einspritzöffnungsreihe 107 und der zweiten Einspritzöffnungsreihe 207. Durch das Zusammenspiel der äußeren Ventilnadel 10 und der innerer Ventilnadel 12 lassen sich die Einspritzöffnungsreihen 107, 207 mit dem Druckraum 5 verbinden. Liegt die äußere Ventilnadel 10 mit der Ventildichtfläche 11 am Ventilsitz 13 an, so werden beide Einspritzöffnungsreihen 107, 207 gegen den Druckraum 5 verschlossen. Hebt nur die äußere Ventilnadel 10 vom Ventilsitz 13 ab, während die innere Ventilnadel 12 mit der Ventildichtfläche 14 am Ventilsitz 13 anliegt, so wird nur die erste Einspritzöffnungsreihe 107 mit dem Druckraum 5 verbunden, während die zweite Einspritzöffnungsreihe 207 durch die innere Ventilnadel 12 verschlossen bleibt. Erst wenn auch die innere Ventilnadel 12 vom Ventilsitz 13 abhebt, wird die zweite Einspritzöffnungsreihe 207 mit dem Druckraum 5 verbunden.In the outer valve needle 10, an inner valve needle 12 is arranged, which is piston-shaped and which has a conical pressure surface 112 and a valve sealing surface 14 at its combustion chamber end. Comes the inner valve needle 12 on the valve seat 13 to the system, the valve sealing surface 14 contacts the valve seat 13 between the first row of injection openings 107 and the second row of injection openings 207. The interaction of the outer valve needle 10 and the inner valve needle 12, the Einspritzöffnungsreihen 107, 207 connect to the pressure chamber 5 , If the outer valve needle 10 is in contact with the valve sealing surface 11 on the valve seat 13, then both rows of injection openings 107, 207 are closed against the pressure chamber 5. Only lifts the outer valve needle 10 from the valve seat 13, while the inner valve needle 12 abuts with the valve sealing surface 14 on the valve seat 13, so only the first row of injection openings 107 is connected to the pressure chamber 5, while the second row of injection 207 closed by the inner valve needle 12 , Only when the inner valve needle 12 lifts off from the valve seat 13, the second injection opening row 207 is connected to the pressure chamber 5.

Über einen im Gehäuse 1 verlaufenden Zulaufkanal 15 ist der Druckraum 5 mit einem Hochdruckanschluß 17 verbunden, der mit einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle verbunden ist. Die Kraftstoffhochdruckquelle liefert hierbei bei Betrieb der Brennkraftmaschine einen vorgegebenen Kraftstoffhochdruck, so daß im Zulaufkanal 15 und somit auch im Druckraum 5 stets dieser Kraftstoffdruck herrscht und einen Kraftstoffhochdruckbereich bildet.About a running in the housing 1 inlet channel 15 of the pressure chamber 5 is connected to a high-pressure port 17 which is connected to a high-pressure fuel source, not shown in the drawing. The high-pressure fuel source in this case provides during operation of the internal combustion engine, a predetermined high-pressure fuel, so that in the inlet channel 15 and thus also in the pressure chamber 5 always this fuel pressure prevails and forms a high-pressure fuel area.

Brennraumabgewandt zur Bohrung 3 ist im Gehäuse 1 eine als Sackbohrung ausgeführte Kolbenbohrung 18 ausgebildet, die eine Grundfläche 19 aufweist. In der Kolbenbohrung 18 ist eine äußere Kolbenstange 20 längsverschiebbar angeordnet, die mit ihrer dem Brennraum zugewandten Stirnseite an der äußeren Ventilnadel 10 anliegt und die mit ihrer brennraumabgewandten Stirnseite 21 einen am Ende der Kolbenbohrung 18 ausgebildeten Steuerraum 24 begrenzt. Durch eine radiale Erweiterung der Kolbenbohrung 18 ist am brennraumseitigen Endbereich der Kolbenstange 20 ein Federraum 8 im Gehäuse 1 ausgebildet, in dem eine Feder 42 unter Druckvorspannung angeordnet ist. Die Feder 42 stützt sich am brennraumabgewandten Ende ortsfest ab und liegt an ihrem brennraumzugewandten Ende an einem Federteller 44 an, der mit der äußeren Kolbenstange 20 verbunden ist, so daß die Feder 42 eine Kraft in Richtung auf den Ventilsitz 13 auf die äußere Kolbenstange 20 und damit auch auf die äußere Ventilnadel 10 ausübt.Facing away from the combustion chamber to the bore 3, a piston bore 18 embodied as a blind bore is formed in the housing 1 and has a base surface 19. In the piston bore 18, an outer piston rod 20 is arranged longitudinally displaceable, which abuts with its combustion chamber facing end face on the outer valve needle 10 and the combustion chamber facing away from its end face 21 formed at the end of the piston bore 18 control chamber 24. Through a radial extension the piston bore 18 is formed at the combustion chamber end portion of the piston rod 20, a spring chamber 8 in the housing 1, in which a spring 42 is arranged under pressure bias. The spring 42 is supported at the end away from the combustion chamber stationary and abuts at its combustion chamber end facing a spring plate 44 which is connected to the outer piston rod 20, so that the spring 42 a force in the direction of the valve seat 13 on the outer piston rod 20 and thus exerts on the outer valve needle 10.

In der äußeren Kolbenstange 20 ist eine innere Kolbenstange 22 angeordnet, die in der äußeren Kolbenstange 20 längsverschiebbar ist. An ihrem brennraumzugewandten Ende liegt die innere Kolbenstange 22 an der inneren Ventilnadel 12 an, so daß sich die innere Kolbenstange 22 und die innere Ventilnadel 12 synchron bewegen. Figur 3 zeigt eine Vergrößerung von Figur 1 im Bereich des Steuerraums 24. Der Steuerraum 24 wird von der Grundfläche 19, der Wand der Kolbenbohrung 18 und der Stirnseite 21 der äußeren Kolbenstange 20 begrenzt. Die äußere Kolbenstange 20 weist an ihrem brennraumabgewandten Ende einen nach innen kragenden Bereich 27 auf, so daß durch die äußere Kolbenstange 20 und die brennraumabgewandte Stirnseite 31 der inneren Kolbenstange 22 ein innerer Steuerraum 29 begrenzt wird, der über eine Verbindungsbohrung 28 in der äußeren Kolbenstange 20 mit dem Steuerraum 24 verbunden ist. Im Inneren der äußeren Kolbenstange 20 ist eine Anschlagfläche 23 ausgebildet, die die Längsbewegung der inneren Kolbenstange 22 begrenzt. In Schließstellung des Kraftstoffeinspritzventils, also wenn sowohl die innere Ventilnadel 12 als auch die äußere Ventilnadel 10 am Ventilsitz 13 anliegen, verbleibt ein axialer Abstand zwischen der Anschlagfläche 23 und der brennraumabgewandten Stirnseite 31 der inneren Kolbenstange 22.In the outer piston rod 20, an inner piston rod 22 is arranged, which is longitudinally displaceable in the outer piston rod 20. At its end facing the combustion chamber, the inner piston rod 22 abuts on the inner valve needle 12, so that the inner piston rod 22 and the inner valve needle 12 move synchronously. Figure 3 shows an enlargement of Figure 1 in the region of the control chamber 24. The control chamber 24 is bounded by the base 19, the wall of the piston bore 18 and the end face 21 of the outer piston rod 20. The outer piston rod 20 has at its end facing away from the combustion chamber on an inwardly cantilevered region 27, so that an inner control chamber 29 is limited by the outer piston rod 20 and the brennraumabgewandte end face 31 of the inner piston rod 22 via a connecting hole 28 in the outer piston rod 20th is connected to the control room 24. Inside the outer piston rod 20, a stop surface 23 is formed which limits the longitudinal movement of the inner piston rod 22. In the closed position of the fuel injection valve, so when both the inner valve needle 12 and the outer valve needle 10 abut the valve seat 13, an axial distance between the stop surface 23 and the combustion chamber facing away from the end face 31 of the inner piston rod 22 remains.

Der Steuerraum 24 ist über eine Zulaufdrossel 25 mit dem Zulaufkanal 15 verbunden. Darüber hinaus ist der Steuerraum 24 über eine Ablaufdrossel 25 mit einem im Gehäuse 1 ausgebildeten Leckölraum 30 verbunden. Im Leckölraum 30 ist ein längsbeweglicher Magnetanker 34 angeordnet, der an seinem dem Steuerraum 24 zugewandten Ende eine Dichtkugel 32 aufweist. Der Magnetanker 34 wird durch eine Schließfeder 38 beaufschlagt, die den Magnetanker 34 in Richtung des Steuerraums 24 drückt. Weiter ist im Leckölraum 30 ein Elektromagnet 36 angeordnet, der bei geeigneter Bestromung eine anziehende Kraft auf den Magnetanker 34 ausübt und ihn vom Steuerraum 24 entgegen der Kraft der Schließfeder 38 wegbewegt. Ist der Elektromagnet 36 nicht bestromt, so wird der Magnetanker 34 von der Schließfeder 38 in Richtung des Steuerraums 24 gedrückt, und die Dichtkugel 32 verschließt die Ablaufdrossel 26. Bei Bestromung des Elektromagneten 36 wird der Magnetanker 34 vom Steuerraum 24 wegbewegt und die Dichtkugel 32 gibt die Ablaufdrossel 26 frei. In dieser Stellung kann Kraftstoff aus dem Steuerraum 24 in den Leckölraum 30 über die Ablaufdrossel 26 abfließen. Der Magentanker 34, die Dichtkugel 32 und der Elektromagnet 36 bilden so ein Ventil 33.The control chamber 24 is connected via an inlet throttle 25 to the inlet channel 15. In addition, the control chamber 24 is connected via an outlet throttle 25 with a formed in the housing 1 leakage oil chamber 30. In the leakage oil chamber 30, a longitudinally movable magnet armature 34 is arranged, which has a sealing ball 32 at its end facing the control chamber 24. The armature 34 is acted upon by a closing spring 38, which presses the armature 34 in the direction of the control chamber 24. Further, in the leakage oil chamber 30, an electromagnet 36 is arranged, which exerts an attractive force on the magnet armature 34 with appropriate energization and moves it away from the control chamber 24 against the force of the closing spring 38. If the electromagnet 36 is not energized, then the magnet armature 34 is pressed by the closing spring 38 in the direction of the control chamber 24, and the sealing ball 32 closes the outlet throttle 26. When the electromagnet 36 is energized, the magnet armature 34 is moved away from the control chamber 24 and the sealing ball 32 is present the outlet throttle 26 free. In this position, fuel can flow out of the control chamber 24 into the leakage oil chamber 30 via the outlet throttle 26. The magentanker 34, the sealing ball 32 and the electromagnet 36 thus form a valve 33.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Im geschlossenen Zustand des Kraftstoffeinspritzventils, also wenn kein Kraftstoff durch die Einspritzöffnungen 7 in den Brennraum der Brennkraftmaschine eingespritzt wird, verschließt die Dichtkugel 32 die Ablaufdrossel 26. Durch die Zulaufdrossel 25 herrscht im Steuerraum 24 der gleiche Kraftstoffdruck wie im Zulaufkanal 15. Hierdurch ergibt sich eine hydraulische Kraft auf die Stirnseite 21 der äußeren Kolbenstange 20 und auf die Stirnseite 31 der inneren Kolbenstange 22, die diese auf die äußere Ventilnadel 10 bzw. der innere Ventilnadel 12 übertragen, so daß die Ventilnadeln 10,12 in Anlage am Ventilsitz 13 gedrückt werden und die Einspritzöffnungen 7 verschließen. Das Größenverhältnis der Stirnseite 21 zu der Druckschulter 9 bzw. der Druckfläche 101 der äußeren Ventilnadel 10 ist so ausgelegt, daß in diesem Zustand des Kraftstoffeinspritzventils die hydraulische Kraft auf die Stirnseite 21 der äußeren Kolbenstange 20 überwiegt. Soll eine Einspritzung von Kraftstoff in den Brennraum geschehen, so wird der Elektromagnet 36 bestromt, wodurch sich der Magnetanker 34 und damit auch die Dichtkugel 32 von der Ablaufdrossel 26 wegbewegen und über die Ablaufdrossel 26 den Steuerraum 24 mit dem Leckölraum 30 verbinden. Die Durchflußwiderstände von Zulaufdrossel 25 und Ablaufdrossel 26 sind so ausgelegt, daß der Kraftstoffdruck hierdurch im Steuerraum 24 abfällt, und zwar so weit, daß die äußere Ventilnadel 10 durch die Druckfläche 101 und die Druckschulter 9 eine größere hydraulische Kraft erfährt als die jetzt noch auf die Stirnseite 21 der äußeren Kolbenstange 20 wirkende hydraulische Kraft im Steuerraum 24.The operation of the fuel injection valve is as follows: In the closed state of the fuel injection valve, so if no fuel is injected through the injection openings 7 in the combustion chamber of the internal combustion engine, the sealing ball 32 closes the outlet throttle 26. By the inlet throttle 25 prevails in the control chamber 24, the same fuel pressure as in the inlet channel 15. This results in a hydraulic force on the end face 21 of the outer piston rod 20 and on the end face 31 of the inner piston rod 22, which transmit this to the outer valve needle 10 and the inner valve needle 12, so that the valve needles 10,12 be pressed in contact with the valve seat 13 and close the injection openings 7. The size ratio of the end face 21 to the pressure shoulder 9 and the pressure surface 101 of the outer valve needle 10 is designed so that in this state of the fuel injection valve, the hydraulic force on the end face 21 of the outer piston rod 20 outweighs. If an injection of fuel into the combustion chamber, so the electromagnet 36 is energized, causing the armature 34 and thus also the sealing ball 32 move away from the outlet throttle 26 and connect via the outlet throttle 26 the control chamber 24 with the leakage oil chamber 30. The flow resistances of the inlet throttle 25 and outlet throttle 26 are designed so that the fuel pressure thereby drops in the control chamber 24, to the extent that the outer valve needle 10 through the pressure surface 101 and the pressure shoulder 9 experiences a greater hydraulic force than that now still on the Front side 21 of the outer piston rod 20 acting hydraulic force in the control chamber 24th

Sobald die äußere Ventilnadel 10 vom Ventilsitz 13 abhebt gibt sie die erste Einspritzöffnungsreihe 107 frei, durch die jetzt Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt wird. Dadurch wird nun auch die Druckfläche 112 der inneren Ventilnadel 12 vom Kraftstoffdruck des Druckraums 5 beaufschlagt, so daß die innere Ventilnadel 12 eine Öffnungskraft erfährt. Der verbleibende Kraftstoffdruck im Steuerraum 24 ist jedoch so hoch, daß die hydraulische Kraft auf die Stirnseite 31 der inneren Kolbenstange 22 weiterhin ausreicht, die innere Ventilnadel 12 entgegen der Öffnungskraft in Schließstellung zu halten. Im Zuge der Öffnungshubbewegung kommt die äußere Kolbenstange 20 schließlich an der Grundfläche 19 zur Anlage, wodurch der Steuerraum 24 durch eine zusätzliche Drosselstelle 45, die sich zwischen der Stirnseite 21 der äußeren Kolbenstange 20 und der Grundfläche 19 bildet, weitgehend gegen die Ablaufdrossel 26 verschlossen wird. Diese Stellung der äußeren Kolbenstange 20 ist in der Figur 4 dargestellt. Hierdurch wird der weitere Zufluß von Kraftstoff aus dem Steuerraum 24 zur Ablaufdrossel 26 vermindert, und der Druck im inneren Steuerraum 29 fällt weiter ab. Aufgrund des jetzt niedrigeren hydraulischen Drucks im inneren Steuerraum 29 bewegt sich, getrieben durch die hydraulische Kraft auf die Druckfläche 112, auch die innere Ventilnadel 12 und damit auch die innere Kolbenstange 22 vom Ventilsitz 13 weg, so daß die zweite Einspritzöffnungsreihe 207 aufgesteuert wird. Die innere Kolbenstange 22 bewegt sich dabei in axialer Richtung, bis sie an der Anschlagfläche 23 der äußeren Kolbenstange 20 zur Anlage kommt. Durch das sukzessive Aufsteuern der beiden Einspritzöffnungsreihen 107 und 207 erreicht man so eine Einspritzverlaufsformung, bei der zu Beginn der Einspritzung zwar mit vollem Druck, jedoch nur durch ein Teil der Einspritzöffnungen 7 Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt-wird, während bei der Haupteinspritzung durch sämtliche Einspritzöffnungen 7 beider Einspritzöffnungsreihen 107 und 207 eingespritzt wird und damit auch mit einer höheren Einspritzrate. Um den Einspritzvorgang zu beenden, wird die Bestromung des Elektromagneten 36 beendet und angetrieben durch die Schließfeder 38 verschließt die Dichtkugel 32 am Magnetanker 34 die Ablaufdrossel 26, so daß sich durch den durch die Zulaufdrossel 25 nachströmenden Kraftstoff erneut der Kraftstoffdruck des Zulaufkanals 15 im Steuerraum 24 aufbaut und sowohl die äußere Kolbenstange 20 als auch die innere Kolbenstange 22 in Richtung des Ventilsitzes 13 drückt, so daß die innere Ventilnadel 12 und die äußere Ventilnadel 10 zurück in die Schließstellung bewegt werden.As soon as the outer valve needle 10 lifts off from the valve seat 13, it releases the first row of injection openings 107, through which fuel is now injected into the combustion chamber of the internal combustion engine. As a result, the pressure surface 112 of the inner valve needle 12 is now acted upon by the fuel pressure of the pressure chamber 5, so that the inner valve needle 12 experiences an opening force. However, the remaining fuel pressure in the control chamber 24 is so high that the hydraulic force on the end face 31 of the inner piston rod 22 is still sufficient to keep the inner valve needle 12 against the opening force in the closed position. In the course of the opening stroke, the outer piston rod 20 finally comes to the base 19 to the system, whereby the control chamber 24 is largely closed by an additional restrictor 45, which forms between the end 21 of the outer piston rod 20 and the base 19 against the outlet throttle 26 , This position of the outer piston rod 20th is shown in FIG. As a result, the further inflow of fuel from the control chamber 24 is reduced to the outlet throttle 26, and the pressure in the inner control chamber 29 drops further. Due to the now lower hydraulic pressure in the inner control chamber 29, driven by the hydraulic force on the pressure surface 112, the inner valve needle 12 and thus also the inner piston rod 22 moves away from the valve seat 13 so that the second injection opening row 207 is opened. The inner piston rod 22 moves in the axial direction until it comes to rest on the abutment surface 23 of the outer piston rod 20. By the successive opening up of the two rows of injection openings 107 and 207, an injection progression is achieved in which, at the beginning of the injection, fuel is injected into the combustion chamber of the internal combustion engine at full pressure, but only through part of the injection openings 7, while in the main injection all injection ports 7 of both injection port rows 107 and 207 is injected and thus with a higher injection rate. To end the injection process, the energization of the electromagnet 36 is stopped and driven by the closing spring 38 closes the sealing ball 32 on the armature 34, the outlet throttle 26 so that again by the fuel flowing through the inlet throttle 25 fuel pressure of the inlet channel 15 in the control chamber 24th and both pushes the outer piston rod 20 and the inner piston rod 22 in the direction of the valve seat 13, so that the inner valve needle 12 and the outer valve needle 10 are moved back into the closed position.

Es kann auch vorgesehen sein, nur durch die erste Einspritzöffnungsreihe 107 Kraftstoff einzuspritzen. Hierzu wird das Ventil 33, das durch den Elektromagneten 34, den Magnetanker 34 und die Dichtkugel 32 gebildet wird, wieder geschlossen, ehe der Kraftstoffdruck im Steuerraum 24 so weit abgesunken ist, daß sich die innere Ventilnadel 12 öffnet. Die Ablaufdrossel 26 ist dann bereits wieder geschlossen ehe die die äußere Kolbenstange 20 mit der Stirnfläche 21 an der Grundfläche 19 der Kolbenbohrung 18 zur Anlage kommt. Hierdurch ergibt sich zwischen der Stirnfläche 21 und der Grundfläche 19 ein hydraulisches Polster, das die Öffnungsbewegung der äußeren Kolbenstange 20 dämpft und einen Druckabfall im Steuerraum 24 verhindert, so daß die innere Kolbenstange 22 stets eine ausreichende Schließkraft auf die innere Ventilnadel 12 ausübt.It can also be provided to inject fuel only through the first row of injection openings 107. For this purpose, the valve 33, which is formed by the electromagnet 34, the armature 34 and the sealing ball 32, again closed before the fuel pressure in the control chamber 24 has dropped so far that the inner valve needle 12 opens. The outlet throttle 26 is then already closed again before the outer piston rod 20 comes to rest with the end face 21 on the base 19 of the piston bore 18. This results between the end face 21 and the base 19, a hydraulic cushion which dampens the opening movement of the outer piston rod 20 and prevents a pressure drop in the control chamber 24, so that the inner piston rod 22 always exerts a sufficient closing force on the inner valve needle 12.

Es kann auch vorgesehen sein, daß die äußere Kolbenstange 20 bei der Öffnungshubbewegung der äußeren Ventilnadel 10 die Zulaufdrossel 25 teilweise überdeckt, so daß der Querschnitt der Zulaufdrossel 25 reduziert wird, diese aber nicht völlig verschlosse wird. Dies kann beispielsweise durch einen verbleibenden Ringspalt zwischen der äußeren Kolbenstange 20 und der Wand der Kolbenbohrung 18 realisiert werden. Die Verbindung des Steuerraum 24 mit der Ablaufdrossel 26 wird beispielsweise durch in radialer Richtung verlaufende Nuten an der Stirnseite 21 der äußeren Kolbenstange 20 sichergestellt. Hierdurch ist der Kraftstoffzufluß durch die Zulaufdrossel 25 in den Steuerraum 24 deutlich verringert, so daß der Kraftstoffdruck im Steuerraum 24 und, über die Verbindungsbohrung 28, auch im inneren Steuerraum 29 weiter abfällt und die innere Kolbenstange 22 und damit die innere Ventilnadel 12 in der oben beschriebenen Weise öffnet.It can also be provided that the outer piston rod 20 during the opening stroke of the outer valve needle 10, the inlet throttle 25 partially covers, so that the cross section of the inlet throttle 25 is reduced, but this is not completely closed. This can be realized for example by a remaining annular gap between the outer piston rod 20 and the wall of the piston bore 18. The connection of the control chamber 24 with the outlet throttle 26 is ensured, for example, by grooves extending in the radial direction on the end face 21 of the outer piston rod 20. As a result, the fuel flow through the inlet throttle 25 in the control chamber 24 is significantly reduced, so that the fuel pressure in the control chamber 24 and, via the connecting bore 28, in the inner control chamber 29 further drops and the inner piston rod 22 and thus the inner valve needle 12 in the above described manner opens.

Claims (12)

  1. Fuel injection valve for internal combustion engines having a housing (1) in which a piston-shaped outer valve needle (10) is arranged in a longitudinally moveable manner in a bore (3), which outer valve needle (10) interacts with a valve seat (13), which is formed at the combustion-chamber-side end of the bore (3), in order to control at least one injection opening (7), and having a control space (24) which is formed in the housing (1), wherein the pressure in the control space (24) can be regulated by means of a valve (33), and wherein a closing force in the direction of the valve seat (13) is exerted on the outer valve needle (10) at least indirectly by means of the pressure in the control space (24), and having at least one pressure face (9; 101) formed on the outer valve needle (10), which pressure face (9; 101) is acted on by the pressure in a pressure space (5) which is formed between the outer valve needle (10) and the wall of the bore (3) and extends up to the valve seat (13), such that there is a resulting opening force, which is aligned counter to the closing force, on the outer valve needle (1), characterized in that an inner valve needle (12) is guided in the outer valve needle (10), which inner valve needle (12) controls at least one additional injection opening (7) on the valve seat (13), and which inner valve needle (12) is acted on at least indirectly in the direction of the valve seat (13) by the pressure in the control space (24) in order to actuate the injection opening.
  2. Fuel injection valve according to Claim 1, characterized in that a throttle connection (45) is formed by the opening lift movement of the outer valve needle (10), such that the inner valve needle (12) is no longer acted on at least indirectly by the pressure in the control space (24).
  3. Fuel injection valve according to Claim 2, characterized in that the outer valve needle (10) is connected to an outer piston rod (20) which moves synchronously with the outer valve needle (10) and has an end face (21) which faces away from the outer valve needle (10), which end face (21) is acted on by the pressure in the control space (24) and thus generates the closing force on the outer valve needle (10).
  4. Fuel injection valve according to Claim 3, characterized in that the throttle connection (45) is formed between the end side (21) of the outer piston rod (20) and a positionally fixed base face (19).
  5. Fuel injection valve according to Claim 3, characterized in that the inner valve needle (12) is connected to an inner piston rod (22) which moves synchronously with the inner valve needle (12) and has an end face (31) which is acted on by the pressure in the control space (24) in the closing direction of the inner valve needle (12) and thus generates the closing force on the inner valve needle (12).
  6. Fuel injection valve according to Claim 5, characterized in that the outer piston rod (20) is embodied as a sleeve and the inner piston rod (22) is guided in the outer piston rod (20).
  7. Fuel injection valve according to Claim 6, characterized in that, during the opening movement caused by the opening force on a pressure face (112) of the inner valve needle (12), the inner piston rod (22) comes into contact with a lift stop face (23) formed on the inner side of the outer piston rod (20).
  8. Fuel injection valve according to Claim 6, characterized in that an inwardly protruding region (27) is formed on the combustion-chamber-remote end of the outer piston rod (20), such that the inner side of the outer piston rod (20), the inwardly protruding region (27) and the end side (21) of the inner piston rod (22) delimit an inner control space (29) which is connected only by means of a connecting bore (28) in the outer piston rod (20) to the control space (24).
  9. Fuel injection valve according to Claim 1, characterized in that the inner valve needle (12) has a pressure face (112) which is acted on by the pressure in the pressure space (5), such that there is a resulting opening force on the inner valve needle (12), only after the outer valve needle (10) has lifted from the valve seat (13).
  10. Fuel injection valve according to Claim 1, characterized in that the control space (24) is connected by means of an inflow throttle (25) to a high-pressure fuel region and by means of an outflow throttle (26) to a leakage oil space (30) in which a lower fuel pressure prevails than in the high-pressure fuel region, wherein the outflow throttle (26) can be closed off by means of a valve (33).
  11. Fuel injection valve according to Claim 10, characterized in that, during the opening movement of the outer valve needle (10), the outer piston rod (20) partially closes off the inflow throttle (25), and thus sets a reduced inflow cross section from the high-pressure fuel region into the control space (24).
  12. Fuel injection valve according to Claim 11, characterized in that a first injection opening row (107) and a second injection opening row (207), which is arranged offset in the axial direction with respect to said first injection opening row (107), are formed on the valve seat (13), wherein the second injection opening row (207) can be closed off with respect to the pressure space (5) by means of the inner valve needle (12), while the outer valve needle (10) can close off both the second injection opening row (207) and also the first injection opening row (107) with respect to the pressure space (5).
EP02726069A 2001-05-08 2002-03-22 Fuel injection valve for internal combustion engines Expired - Lifetime EP1387939B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10122241 2001-05-08
DE10122241A DE10122241A1 (en) 2001-05-08 2001-05-08 Fuel injection valve for internal combustion engines
PCT/DE2002/001036 WO2002090754A1 (en) 2001-05-08 2002-03-22 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1387939A1 EP1387939A1 (en) 2004-02-11
EP1387939B1 true EP1387939B1 (en) 2008-01-16

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EP02726069A Expired - Lifetime EP1387939B1 (en) 2001-05-08 2002-03-22 Fuel injection valve for internal combustion engines

Country Status (5)

Country Link
US (1) US7117842B2 (en)
EP (1) EP1387939B1 (en)
JP (1) JP4116448B2 (en)
DE (2) DE10122241A1 (en)
WO (1) WO2002090754A1 (en)

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Also Published As

Publication number Publication date
US20050199753A1 (en) 2005-09-15
US7117842B2 (en) 2006-10-10
DE50211554D1 (en) 2008-03-06
DE10122241A1 (en) 2002-12-05
EP1387939A1 (en) 2004-02-11
JP2004519597A (en) 2004-07-02
WO2002090754A1 (en) 2002-11-14
JP4116448B2 (en) 2008-07-09

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