WO2004046539A1 - Fuel injection valve of a fuel injection device for an engine - Google Patents
Fuel injection valve of a fuel injection device for an engine Download PDFInfo
- Publication number
- WO2004046539A1 WO2004046539A1 PCT/DE2003/001764 DE0301764W WO2004046539A1 WO 2004046539 A1 WO2004046539 A1 WO 2004046539A1 DE 0301764 W DE0301764 W DE 0301764W WO 2004046539 A1 WO2004046539 A1 WO 2004046539A1
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- chamber
- valve
- control
- connection
- fuel injection
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Classifications
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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
- 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
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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
- F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
- F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
Definitions
- the invention relates to a fuel injection valve of a fuel injection device for an internal combustion engine according to the preamble of claim 1.
- Such a fuel injection valve is known from EP 0 976 924 A.
- This fuel injection valve has an injection valve member, through which at least one injection opening is controlled.
- Injection valve member is acted upon by the pressure prevailing in a control pressure chamber in a closing direction.
- the pressure prevailing in the control pressure chamber is controlled by a control valve which has a valve chamber which has a connection to the control pressure chamber in which a throttle point is arranged.
- the control valve has a control valve member, by means of which connections of the valve chamber with a high-pressure area and with a low-pressure area are controlled.
- the control pressure chamber has, in addition to the connection to the high-pressure region which is established via the valve chamber and controlled by the control valve member, a direct connection to the high-pressure region in which a further throttle point is arranged.
- control valve member If no fuel injection is to take place, the control valve member is brought into a position in which, through this, the connection of the valve chamber opened with the high pressure area and the connection of the valve chamber with the relief area is closed. If fuel injection is to take place, the control valve member is brought into a position in which the connection of the valve chamber to the relief region is opened and the connection of the valve chamber to the high pressure region is closed.
- a disadvantage of this known fuel injection valve is that even during fuel injection, when the connection of the valve chamber to the relief region is opened and the connection of the valve chamber to the high-pressure region is closed by the control valve member, the direct connection of the control pressure chamber to the high-pressure region leads to fuel under high pressure in the Control pressure chamber flows in, so that the pressure in the control pressure chamber drops only slowly and the injection valve member opens only slowly. As a result, pollutant emissions, in particular high particle emissions, occur during combustion. In addition, the production of the
- Fuel injection valve is expensive due to the additional direct connection of the control pressure chamber to the high pressure area and the throttle point arranged in it.
- the fuel injection valve according to the invention with the features according to claim 1 has the advantage that due to the connection of the control pressure chamber to the high pressure area only via the connection controlled by the control valve member at the start of fuel injection, a rapid pressure drop in the control pressure chamber, so that the fuel injection valve opens quickly and the injection a large amount of fuel is made possible at the start of fuel injection. This leads to a reduction in pollutant emissions during combustion, especially particle emission.
- the manufacture of the fuel injector is simplified because there is only one throttle point.
- the embodiment according to claim 3 enables the pressure curve in the high pressure region to be influenced.
- the embodiment according to claim 4 enables a quick filling of the control pressure chamber and thus a quick closing of the injection valve member to end the fuel injection.
- Fuel injection device for an internal combustion engine in a schematic representation, Figure 2 a
- Fuel injection valve of the fuel injection device in an enlarged schematic illustration with a control valve member in a first position, FIG. 3 the fuel injection valve with the control valve member in a second position, FIG. 4 the fuel injection valve with the control valve member in a third position and FIG. 5 a throttle point in an enlarged illustration.
- FIG. 1 shows a fuel injection device for an internal combustion engine of a motor vehicle.
- the internal combustion engine is preferably a self-igniting internal combustion engine and has a plurality of cylinders.
- the fuel injection device has a feed pump 10, through which fuel flows from a reservoir 12 Suction side of a high pressure pump 14 is promoted.
- High-pressure pump 14 delivers fuel under high pressure to a reservoir 16.
- With the memory 16 are the hydraulic lines on the cylinders
- Internal combustion engine arranged fuel injection valves 18 connected.
- An electrically operated control valve 20 is arranged on each fuel injection valve 18, by means of which the fuel injection valve 18 can be opened for a fuel injection or can be closed for ending a fuel injection.
- the control valves 20 of the fuel injection valves 18 have an electrical actuator, for example an electromagnet or a piezo actuator, which is connected to an electronic control device 22 and is controlled by the latter as a function of operating parameters of the internal combustion engine.
- a fuel injection valve 18 with a control valve 20 is shown enlarged in each of FIGS.
- the fuel injection valve 18 has a multi-part valve body 26, in which an injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30.
- the valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine.
- the injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 lead away.
- valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which in its end region facing away from the valve seat 36 by a radial expansion of the bore 30 into a pressure chamber 40 surrounding the injection valve member 28 transforms.
- the injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 due to a change in cross section.
- the pressure chamber 40 is connected to the accumulator 16 via a channel 44 and a line running through the valve body 26. The pressure prevailing in the pressure chamber 40 generates a force on the injection valve member 28 in the opening direction, that is to say away from the valve seat 36, via the pressure shoulder 42.
- a spring chamber 46 through which the injection valve member 28 passes, adjoins the bore 30 in the valve body 26 facing away from the combustion chamber.
- a control pressure chamber 48 which is separate from the spring chamber 46, adjoins the combustion chamber 46 in the valve body 26, facing away from the combustion chamber.
- a prestressed spring 50 is arranged in the spring chamber 46, which is supported on the injection valve member 28 via a spring plate 52 and generates a force on the injection valve member 28 in the closing direction, that is to say toward the valve seat 36.
- the spring chamber 46 is connected to the channel 44, so that the same high pressure prevails in the spring chamber as in the pressure chamber 40.
- the end of the injection valve member 28 extends into the control pressure chamber 48 and is acted upon on its end face by the pressure prevailing in the control pressure chamber 48, through which a force in the closing direction towards the valve seat 36 is generated on the injection valve member 28. It can also be provided that the injection valve member 28 is connected to a separate piston which is supported on the injection valve member 28, which projects into the control pressure chamber 48 and which is acted upon by the pressure prevailing in the control pressure chamber 48.
- a valve chamber 54 of the control valve 20 connects to the control pressure chamber 48 facing away from the combustion chamber and has a connection 56 to the control pressure chamber 48, in which a throttle point 58 is arranged.
- the valve chamber 54 also has a connection 60 to the spring chamber 46 and a connection 62 with a relief area, which can serve, for example, as a return flow at least indirectly into the fuel tank.
- the control valve 20 has a control valve member 64 which, as stated above, can be moved in the direction of its longitudinal axis 65 by means of an electrical actuator and by which the connection 60 of the valve chamber 54 with the spring chamber 46 and the connection 62 of the valve chamber 54 with the relief region is controlled.
- the control valve member 64 has, at its end projecting into the valve chamber 54, an at least approximately flat surface 66 arranged perpendicular to its longitudinal axis 65, with which it acts as a valve seat with the boundary 55 of the valve chamber 54, from which the connection 60 leads to the spring chamber 46 cooperates to control the connection 60.
- the control valve member 64 also has, at its end facing away from the surface 66 in the valve chamber 54, a further, for example convexly curved or conical surface 68, with which it is connected to a valve seat 63 formed at the mouth of the connection 62 to the relief region in the valve chamber 54 for controlling the Connection 62 interacts.
- the control valve member 64 is shown in FIG. 2 in a first end position, in which its surface 68 abuts the valve seat 63, so that the valve chamber 54 is separated from the relief area.
- the control valve member 64 is raised with its surface 66 from the boundary 55 of the valve chamber 54, so that the connection 60 to the spring chamber 46 is released.
- the same high pressure prevails in the valve chamber 54 as in the spring chamber 46.
- This high pressure also prevails in the control pressure chamber 48 via the connection 56 and generates such a force in the closing direction on the injection valve member 28 that the injection valve member 28 rests with its sealing surface 34 on the valve seat 36 and none Fuel injection takes place. If a fuel injection is to take place, the control device 22 moves the control valve member 64 into a second position shown in FIG.
- the control valve member 64 lies with its surface 66 on the boundary 55 of the valve chamber 54, so that the valve chamber 54 is separated from the spring chamber 46 and thus from the high-pressure region.
- the surface 68 of the control valve member 64 is raised from the valve seat 63, so that the connection 62 of the valve chamber 54 with the relief region is released. High pressure can therefore no longer prevail in the valve chamber 54 because of its released connection 62 to the relief region, the control pressure chamber 48 also being relieved via the connection 56.
- control pressure chamber 48 Due to the lower pressure prevailing in the control pressure chamber 48, only a small force is generated in the closing direction on the injection valve member 28, so that the force generated in the opening direction by the pressure prevailing in the pressure chamber 40 via the pressure shoulder 42 is greater than the force acting in the closing direction and itself the injection valve member 28 moves in the opening direction according to arrow 29 and lifts off with its sealing surface 34 from the valve seat 36 and opens the injection openings 32. Since the control pressure chamber 48 only has a connection 60 to the spring chamber 46 and thus the high pressure region via the valve chamber 54 and this connection 60 is closed by the control valve member 64, a rapid pressure drop occurs in the control pressure chamber 48 and thus a quick opening of the injection valve member 28 a large amount of fuel is injected at the beginning of a fuel injection cycle.
- the throttle point 58 can, as shown in FIG. 5, be designed such that it offers a greater resistance to the flow in the flow direction from the valve space 54 into the control pressure space 48 than in the reverse flow direction from the control pressure space 48 into the valve space 54 54 have a gradual reduction in cross-section, for example due to a rounding, while the inlet from the control pressure chamber 48 has a discontinuous reduction in cross-section. This enables both a quick opening of the injection valve member 28 and a quick closing of the injection valve member 28, since the control pressure chamber 48 can be quickly filled with fuel.
- control valve member 64 can also be brought into an intermediate position shown in FIG. 4 between the two end positions and held in this position by means of the actuator. In this intermediate position, the connection 60 of the valve chamber 54 to the spring chamber 46 and thus to the high-pressure region and the connection 62 to the relief region is released by the control valve member 64. If that Control valve member 64 is in its intermediate position, there is an increased pressure in the control pressure chamber 48 which is sufficient to move the injection valve member 28 into its closed position or to hold the injection valve member 28 in its closed position, so that no fuel injection takes place.
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- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
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Abstract
Description
KRAFTSTOFFEINSPRITZVENTIL EINER KRAFTSTOFFEINSPRITZEINRICHTUNG FÜR EINE BRENNKR AFTMAS CHINEFUEL INJECTION VALVE OF A FUEL INJECTION DEVICE FOR A COMBUSTION ENGINE
Stand der TechnikState of the art
Die Erfindung geht aus von einem Kraftstoffeinspritzventil einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention relates to a fuel injection valve of a fuel injection device for an internal combustion engine according to the preamble of claim 1.
Ein solches Kraftstoffeinspritzventil ist durch die EP 0 976 924 A bekannt. Dieses Kraftstoffeinspritzventil weist ein Einspritzventilglied auf, durch das wenigstens eine Einspritzöffnung gesteuert wird. DasSuch a fuel injection valve is known from EP 0 976 924 A. This fuel injection valve has an injection valve member, through which at least one injection opening is controlled. The
Einspritzventilglied ist von dem in einem Steuerdruckraum herrschenden Druck in einer Schließrichtung beaufschlagt ist. Der im Steuerdruckraum herrschende Druck wird durch ein Steuerventil gesteuert, das einen Ventilraum aufweist, der eine Verbindung mit dem Steuerdruckraum aufweist, in der eine Drosselstelle angeordnet ist. Das Steuerventil weist ein Steuerventilglied auf, durch das Verbindungen des Ventilraums mit einem Hochdruckbereich und mit einem Niederdruckbereich gesteuert werden. Der Steuerdruckraum weist zusätzlich zu der über den Ventilraum erfolgenden und durch das Steuerventilglied gesteuerten Verbindung mit dem Hochdruckbereich eine direkte Verbindung mit dem Hochdruckbereich auf, in der eine weitere Drosselstelle angeordnet ist. Wenn keine Kraftstoffeinspritzung erfolgen soll, so wird das Steuerventilglied in eine Stellung gebracht, in der durch dieses die Verbindung des Ventilraums mit dem Hochdruckbereich geöffnet und die Verbindung des Ventilraums mit dem Entlastungsbereich verschlossen wird. Wenn eine Kraftstoffeinspritzung erfolgen soll, so wird das Steuerventilglied in eine Stellung gebracht, in der durch dieses die Verbindung des Ventilraums mit dem Entlastungsbereich geöffnet und die Verbindung des Ventilraums mit dem Hochdruckbereich verschlossen wird. Nachteilig bei diesem bekannten Kraftstoffeinspritzventil ist, dass auch während der Kraftstoffeinspritzung, wenn durch das Steuerventilglied die Verbindung des Ventilraums mit dem Entlastungsbereich geöffnet und die Verbindung des Ventilraums mit dem Hochdruckbereich verschlossen ist, durch die direkte Verbindung des Steuerdruckraums mit dem Hochdruckbereich Kraftstoff unter Hochdruck in den Steuerdruckraum einströmt, so dass der Druck im Steuerdruckraum nur langsam sinkt und das Einspritzventilglied nur langsam öffnet. Dies führt dazu, dass bei der Verbrennung eine Schadstoffemission, insbesondere eine hohe Partikelemission erfolgt. Darüberhinaus ist die Fertigung desInjection valve member is acted upon by the pressure prevailing in a control pressure chamber in a closing direction. The pressure prevailing in the control pressure chamber is controlled by a control valve which has a valve chamber which has a connection to the control pressure chamber in which a throttle point is arranged. The control valve has a control valve member, by means of which connections of the valve chamber with a high-pressure area and with a low-pressure area are controlled. The control pressure chamber has, in addition to the connection to the high-pressure region which is established via the valve chamber and controlled by the control valve member, a direct connection to the high-pressure region in which a further throttle point is arranged. If no fuel injection is to take place, the control valve member is brought into a position in which, through this, the connection of the valve chamber opened with the high pressure area and the connection of the valve chamber with the relief area is closed. If fuel injection is to take place, the control valve member is brought into a position in which the connection of the valve chamber to the relief region is opened and the connection of the valve chamber to the high pressure region is closed. A disadvantage of this known fuel injection valve is that even during fuel injection, when the connection of the valve chamber to the relief region is opened and the connection of the valve chamber to the high-pressure region is closed by the control valve member, the direct connection of the control pressure chamber to the high-pressure region leads to fuel under high pressure in the Control pressure chamber flows in, so that the pressure in the control pressure chamber drops only slowly and the injection valve member opens only slowly. As a result, pollutant emissions, in particular high particle emissions, occur during combustion. In addition, the production of the
Kraftstoffeinspritzventils wegen der zusätzlichen direkten Verbindung des Steuerdruckraums mit dem Hochdruckbereich und der in dieser angeordneten Drosselstelle aufwendig.Fuel injection valve is expensive due to the additional direct connection of the control pressure chamber to the high pressure area and the throttle point arranged in it.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, dass infolge der Verbindung des Steuerdruckraums mit dem Hochdruckbereich nur über die durch das Steuerventilglied gesteuerte Verbindung zum Beginn der Kraftstoffeinspritzung ein schneller Druckabfall im Steuerdruckraum, damit ein schnelles Öffnen des Kraftstoffeinspritzventils und die Einspritzung einer grossen Kraftstoffmenge zu Beginn der Kraftstoffeinspritzung ermöglicht ist. Dies führt zu einer Verringerung der Schadstoffemission bei der Verbrennung, insbesondere der Partikelemission. Darüberhinaus ist die Fertigung des Kraftstoffeinspritzventils vereinfacht, da nur eine Drosselstelle vorhanden ist.The fuel injection valve according to the invention with the features according to claim 1 has the advantage that due to the connection of the control pressure chamber to the high pressure area only via the connection controlled by the control valve member at the start of fuel injection, a rapid pressure drop in the control pressure chamber, so that the fuel injection valve opens quickly and the injection a large amount of fuel is made possible at the start of fuel injection. This leads to a reduction in pollutant emissions during combustion, especially particle emission. In addition, the manufacture of the fuel injector is simplified because there is only one throttle point.
In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen des erfindungsgemäßen Kraftstoffeinspritzventils angegeben. Die Ausbildung gemäß Anspruch 3 ermöglicht eine Beeinflussung des Druckverlaufs im Hochdruckbereich. Die Ausbildung gemäß Anspruch 4 ermöglicht eine schnelle Befüllung des Steuerdruckraums und damit ein schnelles Schließen des Einspritzventilglieds zur Beendigung der Kraftstoffeinspritzung.Advantageous refinements and developments of the fuel injection valve according to the invention are specified in the dependent claims. The embodiment according to claim 3 enables the pressure curve in the high pressure region to be influenced. The embodiment according to claim 4 enables a quick filling of the control pressure chamber and thus a quick closing of the injection valve member to end the fuel injection.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eineAn embodiment of the invention is shown in the drawing and explained in more detail in the following description. 1 shows a
Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung, Figur 2 einFuel injection device for an internal combustion engine in a schematic representation, Figure 2 a
Kraftstoffeinspritzventil der Kraftstoffeinspritzeinrichtung in vergrößerter schematischer Darstellung mit einem Steuerventilglied in einer ersten Stellung, Figur 3 das Kraftstoffeinspritzventil mit dem Steuerventilglied in einer zweiten Stellung, Figur 4 das Kraftstoffeinspritzventil mit dem Steuerventilglied in einer dritten Stellung und Figur 5 eine Drosselstelle in vergrößerter Darstellung.Fuel injection valve of the fuel injection device in an enlarged schematic illustration with a control valve member in a first position, FIG. 3 the fuel injection valve with the control valve member in a second position, FIG. 4 the fuel injection valve with the control valve member in a third position and FIG. 5 a throttle point in an enlarged illustration.
Beschreibung des AusführungsbeispielsDescription of the embodiment
In Figur 1 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine eines Kraftfahrzeugs dargestellt. Die Brennkraftmaschine ist vorzugsweise eine selbstzündende Brennkraftmaschine und weist mehrere Zylinder auf. Die Kraftstoffeinspritzeinrichtung weist eine Förderpumpe 10 auf, durch die Kraftstoff aus einem Vorratsbehälter 12 zur Saugseite einer Hochdruckpumpe 14 gefördert wird. Durch die Hochdruckpumpe 14 wird Kraftstoff unter Hochdruck in einen Speicher 16 gefördert. Mit dem Speicher 16 sind über hydraulische Leitungen an den Zylindern derFIG. 1 shows a fuel injection device for an internal combustion engine of a motor vehicle. The internal combustion engine is preferably a self-igniting internal combustion engine and has a plurality of cylinders. The fuel injection device has a feed pump 10, through which fuel flows from a reservoir 12 Suction side of a high pressure pump 14 is promoted. High-pressure pump 14 delivers fuel under high pressure to a reservoir 16. With the memory 16 are the hydraulic lines on the cylinders
Brennkraftmaschine angeordnete Kraftstoffeinspritzventile 18 verbunden. An jedem Kraftstoffeinspritzventil 18 ist jeweils ein elektrisch betätigtes Steuerventil 20 angeordnet, mittels dem das Kraftstoffeinspritzventil 18 zu einer Kraftstoffeinspritzung geöffnet werden kann bzw. zur Beendigung einer Kraftstoffeinspritzung geschlossen werden kann. Die Steuerventile 20 der Kraftstoffeinspritzventile 18 weisen einen elektrischen Aktor, beispielsweise einen Elektromagneten oder einen Piezoaktor auf, der mit einer elektronischen Steuereinrichtung 22 verbunden ist und durch diese abhängig von Betriebsparametern der Brennkraftmaschine angesteuert wird.Internal combustion engine arranged fuel injection valves 18 connected. An electrically operated control valve 20 is arranged on each fuel injection valve 18, by means of which the fuel injection valve 18 can be opened for a fuel injection or can be closed for ending a fuel injection. The control valves 20 of the fuel injection valves 18 have an electrical actuator, for example an electromagnet or a piezo actuator, which is connected to an electronic control device 22 and is controlled by the latter as a function of operating parameters of the internal combustion engine.
In den Figuren 2 bis 4 ist jeweils vergrößert ein Kraftstoffeinspritzventil 18 mit Steuerventil 20 dargestellt. Das Kraftstoffeinspritzventil 18 weist einen mehrteiligen Ventilkörper 26 auf, in dem ein Einspritzventilglied 28 in einer Bohrung 30 längsverschiebbar geführt ist. Der Ventilkörper 26 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 32 auf. Das Einspritzventilglied 28 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 34 auf, die mit einem im Ventilkörper 26 in dessen dem Brennraum zugewandtem Endbereich ausgebildeten Ventilsitz 36 zusammenwirkt, von dem oder nach dem die Einspritzöffnungen 32 abführen. Im Ventilkörper 26 ist zwischen dem Einspritzventilglied 28 und der Bohrung 30 zum Ventilsitz 36 hin ein Ringraum 38 vorhanden, der in seinem dem Ventilsitz 36 abgewandten Endbereich durch eine radiale Erweiterung der Bohrung 30 in einen das Einspritzventilglied 28 umgebenden Druckraum 40 übergeht. Das Einspritzventilglied 28 weist auf Höhe des Druckraums 40 durch eine Querschnittsänderung eine Druckschulter 42 auf. Der Druckraum 40 ist über einen durch den Ventilkörper 26 verlaufenden Kanal 44 und eine Leitung mit dem Speicher 16 verbunden. Durch den im Druckraum 40 herrschenden Druck wird über die Druckschulter 42 eine in Öffnungsrichtung, das heißt vom Ventilsitz 36 weggerichtete Kraft auf das Einspritzventilglied 28 erzeugt.A fuel injection valve 18 with a control valve 20 is shown enlarged in each of FIGS. The fuel injection valve 18 has a multi-part valve body 26, in which an injection valve member 28 is guided so as to be longitudinally displaceable in a bore 30. The valve body 26 has at least one, preferably a plurality of injection openings 32 at its end region facing the combustion chamber of the cylinder of the internal combustion engine. The injection valve member 28 has, for example, an approximately conical sealing surface 34 on its end region facing the combustion chamber, which cooperates with a valve seat 36 formed in the valve body 26 in its end region facing the combustion chamber, from or after which the injection openings 32 lead away. In the valve body 26 there is an annular space 38 between the injection valve member 28 and the bore 30 towards the valve seat 36, which in its end region facing away from the valve seat 36 by a radial expansion of the bore 30 into a pressure chamber 40 surrounding the injection valve member 28 transforms. The injection valve member 28 has a pressure shoulder 42 at the level of the pressure chamber 40 due to a change in cross section. The pressure chamber 40 is connected to the accumulator 16 via a channel 44 and a line running through the valve body 26. The pressure prevailing in the pressure chamber 40 generates a force on the injection valve member 28 in the opening direction, that is to say away from the valve seat 36, via the pressure shoulder 42.
An die Bohrung 30 schließt sich im Ventilkörper 26 dem Brennraum abgewandt ein Federraum 46 an, durch den das Einspritzventilglied 28 hindurchtritt. An den Federraum 46 schließt sich dem Brennraum abgewandt im Ventilkörper 26 ein Steuerdruckraum 48 an, der vom Federraum 46 getrennt ist. Im Federraum 46 ist eine vorgespannte Feder 50 angeordnet, die sich über einen Federteller 52 am Einspritzventilglied 28 abstützt und auf dieses eine in Schließrichtung, das heißt zum Ventilsitz 36 hin gerichtete Kraft erzeugt. Der Federraum 46 ist mit dem Kanal 44 verbunden, so dass im Federraum derselbe Hochdruck herrscht wie im Druckraum 40. Das Einspritzventilglied 28 ragt mit seinem Ende bis in den Steuerdruckraum 48 und ist auf seiner Stirnseite von dem im Steuerdruckraum 48 herrschenden Druck beaufschlagt, durch den auf das Einspritzventilglied 28 eine Kraft in Schließrichtung zum Ventilsitz 36 hin erzeugt wird. Es kann auch vorgesehen sein, dass das Einspritzventilglied 28 mit einem separaten Kolben verbunden ist, der sich am Einspritzventilglied 28 abstützt, der in den Steuerdruckraum 48 ragt und der von dem im Steuerdruckraum 48 herrschenden Druck beaufschlagt ist.A spring chamber 46, through which the injection valve member 28 passes, adjoins the bore 30 in the valve body 26 facing away from the combustion chamber. A control pressure chamber 48, which is separate from the spring chamber 46, adjoins the combustion chamber 46 in the valve body 26, facing away from the combustion chamber. A prestressed spring 50 is arranged in the spring chamber 46, which is supported on the injection valve member 28 via a spring plate 52 and generates a force on the injection valve member 28 in the closing direction, that is to say toward the valve seat 36. The spring chamber 46 is connected to the channel 44, so that the same high pressure prevails in the spring chamber as in the pressure chamber 40. The end of the injection valve member 28 extends into the control pressure chamber 48 and is acted upon on its end face by the pressure prevailing in the control pressure chamber 48, through which a force in the closing direction towards the valve seat 36 is generated on the injection valve member 28. It can also be provided that the injection valve member 28 is connected to a separate piston which is supported on the injection valve member 28, which projects into the control pressure chamber 48 and which is acted upon by the pressure prevailing in the control pressure chamber 48.
An den Steuerdruckraum 48 schließt sich dem Brennraum abgewandt ein Ventilraum 54 des Steuerventils 20 an, der mit dem Steuerdruckraum 48 eine Verbindung 56 aufweist, in der eine Drosselstelle 58 angeordnet ist. Der Ventilraum 54 weist ausserdem eine Verbindung 60 mit dem Federraum 46 auf und eine Verbindung 62 mit einem Entlastungsbereich, als der beispielsweise ein Rucklauf zumindest mittelbar in den Kraftstoffvorratsbehalter dienen kann. Das Steuerventil 20 weist ein Steuerventilglied 64 auf, das wie vorstehend angegeben mittels eines elektrischen Aktors in Richtung seiner Langsachse 65 bewegbar ist und durch das die Verbindung 60 des Ventilraums 54 mit dem Federraum 46 und die Verbindung 62 des Ventilraums 54 mit dem Entlastungsbereich gesteuert wird. Das Steuerventilglied 64 weist an seinem in den Ventilraum 54 ragenden Ende eine zumindest annähernd ebene und senkrecht zu dessen Langsachse 65 angeordnete Flache 66 auf, mit der es mit der Begrenzung 55 des Ventilraums 54, von der die Verbindung 60 zum Federraum 46 abfuhrt, als Ventilsitz zur Steuerung der Verbindung 60 zusammenwirkt. Das Steuerventilglied 64 weist ausserdem an seinem der Flache 66 abgewandten Ende im Ventilraum 54 eine weitere, beispielsweise konvex gewölbte oder konische Flache 68 auf, mit der es mit einem an der Mundung der Verbindung 62 zum Entlastungsbereich in den Ventilraum 54 ausgebildeten Ventilsitz 63 zur Steuerung der Verbindung 62 zusammenwirkt.A valve chamber 54 of the control valve 20 connects to the control pressure chamber 48 facing away from the combustion chamber and has a connection 56 to the control pressure chamber 48, in which a throttle point 58 is arranged. The valve chamber 54 also has a connection 60 to the spring chamber 46 and a connection 62 with a relief area, which can serve, for example, as a return flow at least indirectly into the fuel tank. The control valve 20 has a control valve member 64 which, as stated above, can be moved in the direction of its longitudinal axis 65 by means of an electrical actuator and by which the connection 60 of the valve chamber 54 with the spring chamber 46 and the connection 62 of the valve chamber 54 with the relief region is controlled. The control valve member 64 has, at its end projecting into the valve chamber 54, an at least approximately flat surface 66 arranged perpendicular to its longitudinal axis 65, with which it acts as a valve seat with the boundary 55 of the valve chamber 54, from which the connection 60 leads to the spring chamber 46 cooperates to control the connection 60. The control valve member 64 also has, at its end facing away from the surface 66 in the valve chamber 54, a further, for example convexly curved or conical surface 68, with which it is connected to a valve seat 63 formed at the mouth of the connection 62 to the relief region in the valve chamber 54 for controlling the Connection 62 interacts.
Das Steuerventilglied 64 ist in Figur 2 in einer ersten Endstellung dargestellt, in der dieses mit seiner Flache 68 am Ventilsitz 63 anliegt, so dass der Ventilraum 54 vom Entlastungsbereich getrennt ist. Das Steuerventilglied 64 ist dabei mit seiner Flache 66 von der Begrenzung 55 des Ventilraums 54 abgehoben, so dass die Verbindung 60 zum Federraum 46 freigegeben ist. Im Ventilraum 54 herrscht somit derselbe Hochdruck wie im Federraum 46. Dieser Hochdruck herrscht über die Verbindung 56 auch im Steuerdruckraum 48 und erzeugt auf das Einspritzventilglied 28 eine so große Kraft in Schliessrichtung, dass das Einspritzventilglied 28 mit seiner Dichtflache 34 am Ventilsitz 36 anliegt und keine Kraftstoffeinspritzung erfolgt. Wenn eine Kraftstoffeinspritzung erfolgen soll, so wird durch die Steuereinrichtung 22 durch entsprechende Ansteuerung des Aktors des Steuerventils 20 das Steuerventilglied 64 in eine in Figur 3 dargestellte zweite Stellung bewegt. Das Steuerventilglied 64 liegt dabei mit seiner Fläche 66 an der Begrenzung 55 des Ventilraums 54 an, so dass der Ventilraum 54 vom Federraum 46 und damit vom Hochdruckbereich getrennt ist. Das Steuerventilglied 64 ist mit seiner Fläche 68 vom Ventilsitz 63 abgehoben, so dass die Verbindung 62 des Ventilraums 54 mit dem Entlastungsbereich freigegeben ist. Im Ventilraum 54 kann somit wegen dessen freigegebener Verbindung 62 mit dem Entlastungsbereich kein Hochdruck mehr herrschen, wobei über die Verbindung 56 auch der Steuerdruckraum 48 entlastet ist. Durch den im Steuerdruckraum 48 herrschenden geringeren Druck wird nur noch eine geringe Kraft in Schließrichtung auf das Einspritzventilglied 28 erzeugt, so dass die durch den im Druckraum 40 herrschenden Druck über die Druckschulter 42 in Öffnungsrichtung erzeugte Kraft größer ist als die in Schließrichtung wirkende Kraft und sich das Einspritzventilglied 28 in Öffnungsrichtung gemäß Pfeil 29 bewegt und mit seiner Dichtfläche 34 vom Ventilsitz 36 abhebt und die Einspritzöffnungen 32 freigibt. Da der Steuerdruckraum 48 nur über den Ventilraum 54 eine Verbindung 60 mit dem Federraum 46 und damit dem Hochdruckbereich aufweist und diese Verbindung 60 durch das Steuerventilglied 64 verschlossen ist, erfolgt im Steuerdruckraum 48 ein schneller Druckabfall und somit ein schnelles Öffnen des Einspritzventilglieds 28. Somit kann bereits zu Beginn eines Kraftstoffeinspritzzyklus eine große Kraftstoffmenge eingespritzt werden. Bei der Öffnungsbewegung des Einspritzventilglieds 28 wird durch dieses Kraftstoff aus dem Steuerdruckraum 48 verdrängt, der über die Verbindung 56 mit der Drosselstelle 58 und den Ventilraum 54 in den Entlastungsbereich gelangt. Zur Beendigung der Kraftstoffeinspritzung wird das Steuerventilglied 64 wieder in seine erste Endstellung gebracht, so dass der Ventilraum 54 mit dem Federraum 46 und damit dem Hochdruckbereich verbunden und vom Entlastungsbereich getrennt ist. Dabei herrscht auch im Steuerdruckraum 48 wieder Hochdruck, so dass das Einspritzventilglied 28 in seine Schließstellung bewegt wird und mit seiner Dichtfläche 34 am Ventilsitz 36 anliegt. In den Steuerdruckraum 48 strömt dabei aus dem Federraum 46 über den Ventilraum 54 und die Verbindung 56 mit der Drosselstelle 58 Kraftstoff ein.The control valve member 64 is shown in FIG. 2 in a first end position, in which its surface 68 abuts the valve seat 63, so that the valve chamber 54 is separated from the relief area. The control valve member 64 is raised with its surface 66 from the boundary 55 of the valve chamber 54, so that the connection 60 to the spring chamber 46 is released. The same high pressure prevails in the valve chamber 54 as in the spring chamber 46. This high pressure also prevails in the control pressure chamber 48 via the connection 56 and generates such a force in the closing direction on the injection valve member 28 that the injection valve member 28 rests with its sealing surface 34 on the valve seat 36 and none Fuel injection takes place. If a fuel injection is to take place, the control device 22 moves the control valve member 64 into a second position shown in FIG. 3 by means of appropriate control of the actuator of the control valve 20. The control valve member 64 lies with its surface 66 on the boundary 55 of the valve chamber 54, so that the valve chamber 54 is separated from the spring chamber 46 and thus from the high-pressure region. The surface 68 of the control valve member 64 is raised from the valve seat 63, so that the connection 62 of the valve chamber 54 with the relief region is released. High pressure can therefore no longer prevail in the valve chamber 54 because of its released connection 62 to the relief region, the control pressure chamber 48 also being relieved via the connection 56. Due to the lower pressure prevailing in the control pressure chamber 48, only a small force is generated in the closing direction on the injection valve member 28, so that the force generated in the opening direction by the pressure prevailing in the pressure chamber 40 via the pressure shoulder 42 is greater than the force acting in the closing direction and itself the injection valve member 28 moves in the opening direction according to arrow 29 and lifts off with its sealing surface 34 from the valve seat 36 and opens the injection openings 32. Since the control pressure chamber 48 only has a connection 60 to the spring chamber 46 and thus the high pressure region via the valve chamber 54 and this connection 60 is closed by the control valve member 64, a rapid pressure drop occurs in the control pressure chamber 48 and thus a quick opening of the injection valve member 28 a large amount of fuel is injected at the beginning of a fuel injection cycle. During the opening movement of the injection valve member 28, fuel is displaced from the control pressure chamber 48, which reaches the relief region via the connection 56 with the throttle point 58 and the valve chamber 54. To end the fuel injection, the control valve member 64 is brought back into its first end position, so that the valve chamber 54 is connected to the spring chamber 46 and thus to the high-pressure region and is separated from the relief region. High pressure prevails again in the control pressure chamber 48, so that the injection valve member 28 is moved into its closed position and rests with its sealing surface 34 on the valve seat 36. Fuel flows into the control pressure chamber 48 from the spring chamber 46 via the valve chamber 54 and the connection 56 with the throttle point 58.
Die Drosselstelle 58 kann wie in Figur 5 dargestellt derart ausgebildet sein, dass diese der Strömung in Strömungsrichtung vom Ventilraum 54 in den Steuerdruckraum 48 einen größeren Widerstand bietet als in umgekehrter Strömungsrichtung vom Steuerdruckraum 48 in den Ventilraum 54. Hierzu kann der Einlauf der Drosselstelle vom Ventilraum 54 her eine allmähliche Querschnittsverringerung, beispielsweise durch eine Verrundung aufweisen, während der Einlauf vom Steuerdruckraum 48 her eine unstetige Querschnittsverringerung aufweist. Dies ermöglicht sowohl ein schnelles Öffnen des Einspritzventilglieds 28 als auch ein schnelles Schließen des Einspritzventilglieds 28, da der Steuerdruckraum 48 schnell mit Kraftstoff befüllt werden kann.The throttle point 58 can, as shown in FIG. 5, be designed such that it offers a greater resistance to the flow in the flow direction from the valve space 54 into the control pressure space 48 than in the reverse flow direction from the control pressure space 48 into the valve space 54 54 have a gradual reduction in cross-section, for example due to a rounding, while the inlet from the control pressure chamber 48 has a discontinuous reduction in cross-section. This enables both a quick opening of the injection valve member 28 and a quick closing of the injection valve member 28, since the control pressure chamber 48 can be quickly filled with fuel.
Es kann vorgesehen sein, dass das Steuerventilglied 64 mittels des Aktors auch in eine in Figur 4 dargestellte Zwischenstellung zwischen den beiden Endstellungen gebracht und in dieser gehalten werden kann. In dieser Zwischenstellung ist durch das Steuerventilglied 64 die Verbindung 60 des Ventilraums 54 zum Federraum 46 und damit zum Hochdruckbereich und die Verbindung 62 zum Entlastungsbereich freigegeben. Wenn sich das Steuerventilglied 64 in seiner Zwischenstellung befindet, so herrscht im Steuerdruckraum 48 ein erhöhter Druck, der ausreicht, um das Einspritzventilglied 28 in seine Schließstellung zu bewegen bzw. das Einspritzventilglied 28 in seiner Schließstellung zu halten, so dass keine Kraftstoffeinspritzung erfolgt. In der Zwischenstellung des Steuerventilglieds 64 wird im Ventilraum 54 und im Steuerdruckraum 48 ein Druckabfall erzeugt, durch den eine Verdünnungswelle induziert wird, die sich zum Speicher 16 hin bewegt. Am Speicher 16 wird diese Verdünnungswelle als Verdichtungswelle reflektiert und erzeugt somit im Druckraum 40 des Kraftstoffeinspritzventils 18 eine Druckerhöhung, welche zu einer Formung des Einspritzdruckverlaufs genutzt werden kann. It can be provided that the control valve member 64 can also be brought into an intermediate position shown in FIG. 4 between the two end positions and held in this position by means of the actuator. In this intermediate position, the connection 60 of the valve chamber 54 to the spring chamber 46 and thus to the high-pressure region and the connection 62 to the relief region is released by the control valve member 64. If that Control valve member 64 is in its intermediate position, there is an increased pressure in the control pressure chamber 48 which is sufficient to move the injection valve member 28 into its closed position or to hold the injection valve member 28 in its closed position, so that no fuel injection takes place. In the intermediate position of the control valve member 64, a pressure drop is generated in the valve chamber 54 and in the control pressure chamber 48, by means of which a dilution wave is induced which moves toward the accumulator 16. This dilution wave is reflected on the accumulator 16 as a compression wave and thus generates a pressure increase in the pressure chamber 40 of the fuel injection valve 18, which pressure increase can be used to shape the injection pressure curve.
Claims
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE10254300.3 | 2002-11-21 | ||
| DE2002154300 DE10254300A1 (en) | 2002-11-21 | 2002-11-21 | Fuel injection valve of a fuel injection device for an internal combustion engine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| WO2004046539A1 true WO2004046539A1 (en) | 2004-06-03 |
Family
ID=32240228
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| PCT/DE2003/001764 Ceased WO2004046539A1 (en) | 2002-11-21 | 2003-05-30 | Fuel injection valve of a fuel injection device for an engine |
Country Status (2)
| Country | Link |
|---|---|
| DE (1) | DE10254300A1 (en) |
| WO (1) | WO2004046539A1 (en) |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4406901A1 (en) * | 1994-03-03 | 1995-09-14 | Daimler Benz Ag | Electromagnetically controlled fuel injector for i.c. engine |
| WO1995025888A1 (en) * | 1994-03-24 | 1995-09-28 | Siemens Aktiengesellschaft | Injection valve for internal combustion engines |
| JPH07332200A (en) * | 1994-06-08 | 1995-12-22 | Hino Motors Ltd | Fuel injection device for diesel engine |
| EP1126160A2 (en) * | 2000-02-17 | 2001-08-22 | Siemens Aktiengesellschaft | Injector for injecting fuel in an internal combustion engine |
| EP1184563A2 (en) * | 2000-08-30 | 2002-03-06 | Toyota Jidosha Kabushiki Kaisha | Fuel injector |
| FR2824874A1 (en) * | 2001-05-16 | 2002-11-22 | Bosch Gmbh Robert | Fuel injector, for a common rail fuel injection system at an IC motor, has a single flow throttle with a greater throttle action towards the control valve |
-
2002
- 2002-11-21 DE DE2002154300 patent/DE10254300A1/en not_active Withdrawn
-
2003
- 2003-05-30 WO PCT/DE2003/001764 patent/WO2004046539A1/en not_active Ceased
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4406901A1 (en) * | 1994-03-03 | 1995-09-14 | Daimler Benz Ag | Electromagnetically controlled fuel injector for i.c. engine |
| WO1995025888A1 (en) * | 1994-03-24 | 1995-09-28 | Siemens Aktiengesellschaft | Injection valve for internal combustion engines |
| JPH07332200A (en) * | 1994-06-08 | 1995-12-22 | Hino Motors Ltd | Fuel injection device for diesel engine |
| EP1126160A2 (en) * | 2000-02-17 | 2001-08-22 | Siemens Aktiengesellschaft | Injector for injecting fuel in an internal combustion engine |
| EP1184563A2 (en) * | 2000-08-30 | 2002-03-06 | Toyota Jidosha Kabushiki Kaisha | Fuel injector |
| FR2824874A1 (en) * | 2001-05-16 | 2002-11-22 | Bosch Gmbh Robert | Fuel injector, for a common rail fuel injection system at an IC motor, has a single flow throttle with a greater throttle action towards the control valve |
Non-Patent Citations (1)
| Title |
|---|
| PATENT ABSTRACTS OF JAPAN vol. 1996, no. 04 30 April 1996 (1996-04-30) * |
Also Published As
| Publication number | Publication date |
|---|---|
| DE10254300A1 (en) | 2004-06-03 |
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