EP1056946A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1056946A1
EP1056946A1 EP99966843A EP99966843A EP1056946A1 EP 1056946 A1 EP1056946 A1 EP 1056946A1 EP 99966843 A EP99966843 A EP 99966843A EP 99966843 A EP99966843 A EP 99966843A EP 1056946 A1 EP1056946 A1 EP 1056946A1
Authority
EP
European Patent Office
Prior art keywords
throttle bore
control chamber
fuel
injection 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.)
Granted
Application number
EP99966843A
Other languages
German (de)
French (fr)
Other versions
EP1056946B1 (en
Inventor
Michael Mennicken
Ralf Wirth
Peter Boehland
Christoph Badock
Ralf Hentschel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1056946A1 publication Critical patent/EP1056946A1/en
Application granted granted Critical
Publication of EP1056946B1 publication Critical patent/EP1056946B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/008—Arrangement of fuel passages inside of injectors

Definitions

  • the present invention relates to a fuel injection valve, in particular for high-pressure injection of fuel into combustion chambers of ner internal combustion engines.
  • the fuel for mixture formation is injected into the combustion chamber from a high-pressure chamber via an injection nozzle.
  • Common rail injection systems use the servo principle, among other things, to open and close the injection valves.
  • the injection nozzle is part of a servo valve.
  • a volume flow is switched by a switching valve which is controlled electrically.
  • An open switching valve causes an opening movement of the servo valve via a pressure divider, which is formed by two flow resistors.
  • a closed switching valve causes the servo valve to close.
  • the present invention is therefore based on the object of providing a fuel injection valve with a combination of a switching valve and a servo-hydraulic valve, in which there is a precisely defined flow resistance of the switching valve in the largest possible range of different fuel pressures. This flow resistance must also have the property that only a few geometry parameters influence its size. The precisely defined flow resistance of the switching valve thus defines the opening speed of the servo valve.
  • the fuel injector according to the invention with the features of claim 1 has the advantage that the effective flow cross section of the opening created by the switching valve supports the formation of a cavitating throttle flow.
  • the eccentric position of the inlet throttle bore causes the fuel flow to rotate in the control chamber. This rotation, which accelerates due to the conservation of momentum in the fuel flow after opening the switching valve when flowing through the outlet throttle bore, leads to a reduction in the static pressure in the liquid and thus increases the tendency of the fluid to cavitate when flowing through the outlet throttle bore. Due to the swirling flow within the discharge throttle bore, the tendency to cavitation is extended to a wide pressure range.
  • the inlet throttle bore is aligned tangentially with respect to the control chamber. This ensures that all areas of the flow in the control chamber are set in rotation.
  • the rotation of the flow is not impeded by edges or corners in a cylindrical control chamber.
  • the inlet throttle bore and the outlet throttle bore are preferably aligned perpendicular to one another.
  • the axis of rotation of the generated flow lies parallel to the direction of flow of the fuel into the flow restrictor
  • FIG. 1 shows a sectional view of a switching valve in connection with an inlet throttle bore, a control chamber and an outlet throttle bore;
  • Fig. 2 is a sectional view taken along the line A-A in Fig. 1, which schematically shows the rotation of the flow in the control room.
  • FIG. 1 shows a sectional view through a switching valve 40 with a connection to a control chamber 20, in which a piston 50 is movably arranged. is not.
  • the piston 50 is fixedly connected to the valve needle of the actual injection valve.
  • the fuel flows from a central high-pressure supply 1 to the control chamber 20 via an inlet throttle bore 10.
  • an opening 22 on the end face 21 of the control chamber 20 which leads to an outlet throttle bore 30. This results in a preferred perpendicular alignment of the axes of the inlet throttle bore 10 and the outlet throttle bore 30 to one another.
  • the switching valve 40 On the side of the outlet throttle bore 30 facing away from the control chamber 20, the switching valve 40 is arranged, which - depending on the switching position - opens or closes the outlet of the outlet throttle bore 30. The fuel flows from the switching valve 40 back into the low-pressure region of the fuel system.
  • control piston 50 On the side of the control chamber 20 opposite the end face 21 there is the control piston 50, which is connected to the nozzle needle of the actual injection valve. Movements of the control piston 50 correspond to movements of the valve needle of the actual injection valve, which separates the combustion chamber from the high-pressure region 1 of the fuel injection system. Movements of this control piston 50 (indicated by the double arrow in FIG. 1) lead to an opening or closing of the fuel supply in the combustion chamber.
  • the switching valve 40 is controlled electrically.
  • the inlet throttle bore 10 is arranged eccentrically with respect to the control chamber 20.
  • the control room 20 is preferably cylindrical in shape, i.e. the cross section shown in Fig. 2 along the dash-dotted line A-A of Fig. 1 is circular.
  • the orientation of the longitudinal axis of the inlet throttle bore 10 preferably corresponds to a tangent to the circle which is formed by the cross section of the control chamber 20.
  • a vortex flow 60 is formed when the fuel flows into the control chamber 20 whose streamlines are schematically indicated by arrows in FIG. 2.
  • the vortex flow 60 encompasses the entire cross-sectional area of the control chamber 20.
  • this vortex flow 60 enters the opening of the outlet throttle bore 30, which has a substantially smaller cross-sectional area than the control chamber 20.
  • the rotational speed of the vortex flow 60 increases due to the conservation of momentum, so that the static pressure in the flow decreases sharply. This increases the tendency of the flow to cavitate in the area of the outlet throttle bore 30.
  • the onset of cavitation effects means that the total flow resistance of the combination of outlet throttle 30 and switching valve 40 is only dependent on the flow resistance of the outlet throttle 30. This makes it easier to set the size of the flowing volume flow.
  • the speed of movement of the piston 50 is directly dependent on the outflowing volume flow, there is an increase in the accuracy of the speed of movement of the piston 50 due to the increase in the cavitation tendency of the flow in the outlet throttle bore 30. Since the speed of movement of the piston 50 corresponds to the speed of movement of the valve needle Corresponding to the injection valve, the accuracy of the movement of the injection valve and thus the accuracy of the injected fuel quantity also increase. This means that the speed of movement of the valve needle of the injection valve, which should take place as uniformly as possible, can be specifically adjusted via the dimensioning or shape of the outlet throttle bore 30 or can be optimized with regard to the injection conditions.

Abstract

A fuel injection valve for high pressure injection of fuel from a high-pressure central fuel tank (1) into the combustion chambers of an internal combustion engine. The high pressure fuel tank (1) interacts with a control chamber via an inlet throttle hole (10), whereby said control chamber controls the opening and closing of the injector nozzle and the control chamber (20) communicates with a switch valve via an outlet throttle hole (30). The inlet throttle hole (10) is oriented in an eccentric position with respect to the control chamber (20).

Description

Kraftstoffeinspritzventil Fuel injector
Die vorliegende Erfindung betrifft eine Kraftstoffeinspritzventil insbesondere zur Hochdruckeinspritzung von Kraftstoff in Brennräume von Nerbrennungskraft- maschinen.The present invention relates to a fuel injection valve, in particular for high-pressure injection of fuel into combustion chambers of ner internal combustion engines.
Stand der TechnikState of the art
In Verbrennungskraftmaschinen mit Kraftstoffeinspritzung wird der Kraftstoff zur Gemischbildung aus einer Hochdruckkammer über eine Einspritzdüse in den Brennraum eingespritzt. Zum Öffnen und Schließen der Einspritzventile wird bei Common-Rail-Einspritzsystemen unter anderem auf das Servoprinzip zurückgegriffen. Die Einspritzdüse ist dabei Teil eines Servoventils. Durch ein Schaltventil, welches elektrisch angesteuert wird, wird ein Volumenstrom geschaltet. Über einen Druckteiler, der durch zwei Durchflußwiderstände gebildet wird, bewirkt ein geöffnetes Schaltventil eine Öffnungsbewegung des Servoventils. Ein geschlossenes Schaltventil bewirkt eine Schließbewegung des Servoventils.In internal combustion engines with fuel injection, the fuel for mixture formation is injected into the combustion chamber from a high-pressure chamber via an injection nozzle. Common rail injection systems use the servo principle, among other things, to open and close the injection valves. The injection nozzle is part of a servo valve. A volume flow is switched by a switching valve which is controlled electrically. An open switching valve causes an opening movement of the servo valve via a pressure divider, which is formed by two flow resistors. A closed switching valve causes the servo valve to close.
Für einen optimalen Verbrennungsprozeß in der Brennkammer ist es erforderlich, den Zeitpunkt, die Dauer des Einspritzens, die gesamte eingespritzte Kraftstoff- masse und den zeitlichen Verlauf der Einspritzrate genauestens zu kontrollieren, da die Brennraumgeometrie auf diese Parameter zur Minimierung des Kraftstoffverbrauchs und der Abgasemmissionen genau abgestimmt ist. Der vorliegenden Erfindung liegt daher die Aufgabe zugrunde, ein Kraftstoffeinspritzventil mit einer Kombination aus Schaltventil und servohydraulischem Ventil zu schaffen, bei der ein genau definierter Durchflußwiderstand des Schaltventils in einem möglichst großen Bereich unterschiedlicher Kraftstoffdrücke vor- handen ist. Dieser Durchflußwiderstand muß darüber hinaus die Eigenschaft aufweisen, daß nur wenige Geometrieparameter seine Größe beeinflussen. Der genau definierte Durchflußwiderstand des Schaltventils legt damit die Öffnungsgeschwindigkeit des Servoventils fest.For an optimal combustion process in the combustion chamber, it is necessary to control the point in time, the duration of the injection, the total injected fuel mass and the temporal course of the injection rate, since the combustion chamber geometry is precisely matched to these parameters to minimize fuel consumption and exhaust gas emissions is. The present invention is therefore based on the object of providing a fuel injection valve with a combination of a switching valve and a servo-hydraulic valve, in which there is a precisely defined flow resistance of the switching valve in the largest possible range of different fuel pressures. This flow resistance must also have the property that only a few geometry parameters influence its size. The precisely defined flow resistance of the switching valve thus defines the opening speed of the servo valve.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den Merkmalen gemäß Anspruchs 1 hat den Vorteil, daß der effektive Strömungsquerschnitt der durch das Schaltventil erzeugten Öffnung die Ausbildung einer kavitierenden Drosselströmung unterstützt. Durch die exzentrische Position der Zulaufdrosselbohrung wird im Steuerraum eine Rotation der Kraftstoffströmung verursacht. Diese Rotation, die sich aufgrund der Impulserhaltung der Kraftstoffströmung nach Öffnen des Schaltventils beim Durchströmen der Ablaufdrosselbohrung beschleunigt, führt zu einer Absenkung des statischen Drucks in der Flüssigkeit und verstärkt damit die Kavitationsneigung des Fluides beim Durchströmen der Ablaufdrosselbohrung. Aufgrund der drallbehafteten Strömung innerhalb der Ablaufdrosselbohrung wird die Kavitationsneigung auf einen weiten Druckbereich ausgedehnt. Schon bei geringen Druckdifferenzen über die Ablaufdrosselbohrung hinweg und bei hohen Drücken im Niederdruckbereich hinter der Ablaufdrosselbohrung treten Kavitationseffekte auf und bewirken, daß der effektive Öffnungsquerschnitt, der aus der Kombination von Magnetventil 40 und Ablaufdrosselbohrung 30 gebildet wird, nur noch von der Geometrie der Ablaufdrosselbohrung beeinflußt wird. Hierdurch kann mit Hilfe der Größe der Ablaufdrosselbohrung ein exakt definierter Durchflußquerschnitt eingestellt werden, ohne den Einfluß des Magnetventils 40 berücksichtigen zu müssen. In den abhängigen Ansprüchen aufgeführte Maßnahmen definieren vorteilhafte Weiterbildungen und Verbesserungen des in Anspruch 1 angegebenen Kraftstoffeinspritzventils .The fuel injector according to the invention with the features of claim 1 has the advantage that the effective flow cross section of the opening created by the switching valve supports the formation of a cavitating throttle flow. The eccentric position of the inlet throttle bore causes the fuel flow to rotate in the control chamber. This rotation, which accelerates due to the conservation of momentum in the fuel flow after opening the switching valve when flowing through the outlet throttle bore, leads to a reduction in the static pressure in the liquid and thus increases the tendency of the fluid to cavitate when flowing through the outlet throttle bore. Due to the swirling flow within the discharge throttle bore, the tendency to cavitation is extended to a wide pressure range. Even at low pressure differences across the outlet throttle bore and at high pressures in the low-pressure area behind the outlet throttle bore, cavitation effects occur and have the effect that the effective opening cross section, which is formed from the combination of solenoid valve 40 and outlet throttle bore 30, is only influenced by the geometry of the outlet throttle bore . As a result, an exactly defined flow cross-section can be set with the aid of the size of the outlet throttle bore without having to take into account the influence of the solenoid valve 40. Measures specified in the dependent claims define advantageous developments and improvements of the fuel injection valve specified in claim 1.
Gemäß einer bevorzugten Ausführungsform ist die Zulaufdrosselbohrung tangen- tial gegenüber dem Steuerraum ausgerichtet. Dadurch wird erreicht, daß alle Bereiche der Strömung im Steuerraum in Rotation versetzt werden.According to a preferred embodiment, the inlet throttle bore is aligned tangentially with respect to the control chamber. This ensures that all areas of the flow in the control chamber are set in rotation.
Gemäß einer weiteren Ausführungsform ist bei einem zylindrisch ausgebildeten Steuerraum das Rotieren der Strömung nicht durch Kanten oder Ecken behindert. Vorzugsweise sind die Zulaufdrosselbohrung und die Ablaufdrosselbohrung senk- recht zueinander ausgerichtet. Dadurch liegt die Rotationsachse der erzeugten Strömung parallel zur Einströmrichtung des Kraftstoffs in die Ablaufdrosselboh-According to a further embodiment, the rotation of the flow is not impeded by edges or corners in a cylindrical control chamber. The inlet throttle bore and the outlet throttle bore are preferably aligned perpendicular to one another. As a result, the axis of rotation of the generated flow lies parallel to the direction of flow of the fuel into the flow restrictor
Zeichnungdrawing
Die Erfindung ist anhand einer in der Zeichnung dargestellten Ausfuhrungsform in der folgenden detaillierten Beschreibung näher erläutert. Es zeigen:The invention is explained in more detail with reference to an embodiment shown in the drawing in the following detailed description. Show it:
Fig. 1: eine Schnittansicht eines Schaltventils in Verbindung mit einer Zulauf- drosselbohrung, einem Steuerrraum und einer Ablaufdrosselbohrung; und1 shows a sectional view of a switching valve in connection with an inlet throttle bore, a control chamber and an outlet throttle bore; and
Fig. 2: eine Schnittansicht entlang der Linie A-A in Fig. 1, die schematisch die Rotation der Strömung im Steuerrraum zeigt.Fig. 2 is a sectional view taken along the line A-A in Fig. 1, which schematically shows the rotation of the flow in the control room.
Detaillierte Beschreibung der bevorzugten AusführungsformDetailed description of the preferred embodiment
In Fig. 1 ist eine Schnittansicht durch ein Schaltventil 40 mit einer Verbindung zu einem Steuerraum 20 dargestellt, in welchem ein Kolben 50 beweglich angeord- net ist. Der Kolben 50 ist fest mit der Ventilnadel des eigentlichen Einspritzventils verbunden. Über eine Zulaufdrosselbohrung 10 strömt der Kraftstoff von einer zentralen Hochdruckversorgung 1 zu dem Steuerraum 20. Vorzugsweise an der Stirnseite 21 des Steuerraumes 20 befindet sich eine Öffnung 22, die zu einer Ablaufdrosselbohrung 30 führt. Damit ergibt sich eine bevorzugte rechtwinklige Ausrichtung der Achsen der Zulaufdrosselbohrung 10 und der Ablaufdrosselbohrung 30 zueinander.1 shows a sectional view through a switching valve 40 with a connection to a control chamber 20, in which a piston 50 is movably arranged. is not. The piston 50 is fixedly connected to the valve needle of the actual injection valve. The fuel flows from a central high-pressure supply 1 to the control chamber 20 via an inlet throttle bore 10. Preferably, there is an opening 22 on the end face 21 of the control chamber 20, which leads to an outlet throttle bore 30. This results in a preferred perpendicular alignment of the axes of the inlet throttle bore 10 and the outlet throttle bore 30 to one another.
Auf der dem Steuerraum 20 abgewandten Seite der Ablaufdrosselbohrung 30 ist das Schaltventil 40 angeordnet, das - je nach Schaltposition - den Ausgang der Ablaufdrosselbohrung 30 öffnet oder verschließt. Vom Schaltventil 40 fließt der Kraftstoff zurück in den Niederdruckbereich des Kraftstoff Systems.On the side of the outlet throttle bore 30 facing away from the control chamber 20, the switching valve 40 is arranged, which - depending on the switching position - opens or closes the outlet of the outlet throttle bore 30. The fuel flows from the switching valve 40 back into the low-pressure region of the fuel system.
Auf der der Stirnseite 21 gegenüberliegenden Seite des Steuerraums 20 befindet sich der Steuerkolben 50, der mit der Düsennadel des eigentlichen Einspritzventils verbunden ist. Bewegungen des Steuerkolbens 50 entsprechen Bewegungen der Ventilnadel des eigentlichen Einspritzventils, welches den Brennraum vom Hochdruckbereich 1 des Kraftstoffeinspritzsystems trennt. Bewegungen dieses Steuerkolbens 50 (angedeutet durch den Doppelpfeil in Fig. 1) führen zu einem Öffnen beziehungsweise Schließen der Kraftstoffzufuhr in den Brennraum. Das Schaltventil 40 wird elektrisch angesteuert.On the side of the control chamber 20 opposite the end face 21 there is the control piston 50, which is connected to the nozzle needle of the actual injection valve. Movements of the control piston 50 correspond to movements of the valve needle of the actual injection valve, which separates the combustion chamber from the high-pressure region 1 of the fuel injection system. Movements of this control piston 50 (indicated by the double arrow in FIG. 1) lead to an opening or closing of the fuel supply in the combustion chamber. The switching valve 40 is controlled electrically.
Unter Bezugnahme auf Fig. 2 ist die Zulaufdrosselbohrung 10 exzentrisch in be- zug auf den Steuerraum 20 angeordnet. Der Steuerraum 20 hat vorzugsweise eine zylindrische Gestalt, d.h. der in Fig. 2 gezeigte Querschnitt entlang der strichpunktierten Linie A-A aus Fig. 1 ist kreisförmig. Bevorzugt entspricht die Orientierung der Längsachse der Zulaufdrosselbohrung 10 einer Tangente an den Kreis, der durch den Querschnitt des Steuerraumes 20 gebildet wird.With reference to FIG. 2, the inlet throttle bore 10 is arranged eccentrically with respect to the control chamber 20. The control room 20 is preferably cylindrical in shape, i.e. the cross section shown in Fig. 2 along the dash-dotted line A-A of Fig. 1 is circular. The orientation of the longitudinal axis of the inlet throttle bore 10 preferably corresponds to a tangent to the circle which is formed by the cross section of the control chamber 20.
Durch die exzentrische Orientierung der Zulaufdrosselbohrung 10 bildet sich beim Einströmen des Kraftstoffs in den Steuerraum 20 eine Wirbelströmung 60 aus, deren Stromlinien in Fig. 2 schematisch durch Pfeile angedeutet sind. Die Wirbelströmung 60 umfaßt bei der bevorzugten tangentialen Anordnung der Zu- laufbohrung 10 die gesamte Querschnittfläche des Steuerraums 20.Due to the eccentric orientation of the inlet throttle bore 10, a vortex flow 60 is formed when the fuel flows into the control chamber 20 whose streamlines are schematically indicated by arrows in FIG. 2. In the preferred tangential arrangement of the inlet bore 10, the vortex flow 60 encompasses the entire cross-sectional area of the control chamber 20.
Wird das Schaltventil 40 geöffnet, tritt diese Wirbelströmung 60 in die Öffnung der Ablaufdrosselbohrung 30 ein, die eine wesentlich kleinere Querschnittfläche als der Steuerraum 20 aufweist. Durch das Abfließen des Fluides durch die Ablaufdrosselbohrung 30 erhöht sich dabei aufgrund der Impulserhaltung die Drehgeschwindigkeit der Wirbelströmung 60, so daß der statische Druck in der Strömung stark abnimmt. Dies erhöht die Neigung der Strömung zum Kavitieren im Bereich der Ablaufdrosselbohrung 30. Das Einsetzen von Kavitationseffekten führt dazu, daß der gesamte Durchflußwiderstand der Kombination aus Ablaufdrossel 30 und Schaltventil 40 nur noch von dem Durchflußwiderstand der Ablaufdrossel 30 abhängig ist. Dies erleichtert die Einstellung der Größe des abfließenden Volumenstroms. Da die Bewegungsgeschwindigkeit des Kolbens 50 di- rekt von dem abfließenden Volumenstrom abhängig ist, ergibt sich aufgrund der Erhöhung der Kavitationsneigung der Strömung in der Ablaufdrosselbohrung 30 eine Erhöhung der Genauigkeit der Bewegungsgeschwindigkeit des Kolbens 50. Da die Bewegungsgeschwindigkeit des Kolbens 50 der Bewegungsgeschwindigkeit der Ventilnadel des Einspritzventils entspricht, erhöht sich somit auch die Genauigkeit der Bewegung des Einspritzventils und damit die Genauigkeit der eingespritzten Kraftstoffmenge. Das bedeutet, daß die Bewegungsgeschwindigkeit der Ventilnadel des Einspritzventils, welche möglichst gleichmäßig erfolgen soll, über die Dimensionierung bzw. Gestalt der Ablaufdrosselbohrung 30 zielgerichtet einstellbar bzw. hinsichtlich der Einspritzbedingungen optimierbar ist. If the switching valve 40 is opened, this vortex flow 60 enters the opening of the outlet throttle bore 30, which has a substantially smaller cross-sectional area than the control chamber 20. As a result of the fluid flowing through the outlet throttle bore 30, the rotational speed of the vortex flow 60 increases due to the conservation of momentum, so that the static pressure in the flow decreases sharply. This increases the tendency of the flow to cavitate in the area of the outlet throttle bore 30. The onset of cavitation effects means that the total flow resistance of the combination of outlet throttle 30 and switching valve 40 is only dependent on the flow resistance of the outlet throttle 30. This makes it easier to set the size of the flowing volume flow. Since the speed of movement of the piston 50 is directly dependent on the outflowing volume flow, there is an increase in the accuracy of the speed of movement of the piston 50 due to the increase in the cavitation tendency of the flow in the outlet throttle bore 30. Since the speed of movement of the piston 50 corresponds to the speed of movement of the valve needle Corresponding to the injection valve, the accuracy of the movement of the injection valve and thus the accuracy of the injected fuel quantity also increase. This means that the speed of movement of the valve needle of the injection valve, which should take place as uniformly as possible, can be specifically adjusted via the dimensioning or shape of the outlet throttle bore 30 or can be optimized with regard to the injection conditions.

Claims

Patentansprüche claims
1. Kraftstoffeinspritzventil für eine Hochdruckeinspritzung von Kraftstoff aus einem zentralen Hochdruckspeicher (1) in Brennräume einer Verbrennungs- kraftmaschine, wobei der Hochdruckspeicher (1) über eine Zulaufdrosselbohrung (10) mit einem Steuerraum (20) in Wirkverbindung steht, welcher das Öffnen und Verschließen der Einspritzdüse steuert, wobei der Steuerraum (20) über eine Ablaufdrosselbohrung (30) mit einem Schaltventil (40) kommuniziert, dadurch gekennzeichnet, daß die Zulaufdrosselbohrung (10) gegenüber dem Steuerraum (20) exzentrisch ausgerichtet ist.1. Fuel injection valve for high-pressure injection of fuel from a central high-pressure accumulator (1) into combustion chambers of an internal combustion engine, the high-pressure accumulator (1) being operatively connected to a control chamber (20) via an inlet throttle bore (10), which controls the opening and closing of the Injection nozzle controls, the control chamber (20) communicating with a switching valve (40) via an outlet throttle bore (30), characterized in that the inlet throttle bore (10) is aligned eccentrically with respect to the control chamber (20).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Zulaufdrosselbohrung (10) gegenüber dem Steuerraum (20) tangential aus- gerichtet ist.2. Fuel injection valve according to claim 1, characterized in that the inlet throttle bore (10) is aligned tangentially with respect to the control chamber (20).
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß die Zulaufdrosselbohrung (10) und die Ablaufdrosselbohrung (30) senkrecht zueinander angeordnet sind.3. Fuel injection valve according to claim 2, characterized in that the inlet throttle bore (10) and the outlet throttle bore (30) are arranged perpendicular to each other.
4. Kraftstoffeinspritzventil nach Anspruch 3. dadurch gekennzeichnet, daß der Steuerraum (20) eine zylindrische Gestalt aufweist.4. Fuel injection valve according to claim 3, characterized in that the control chamber (20) has a cylindrical shape.
5. Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß die Ablaufdrosselbohrung (30) so dimensioniert ist, daß beim Betätigen des Schaltventiles (40) Kavitationseffekte in der Ablaufdrosselbohrung (30) auftreten. 5. Fuel injection valve according to claim 4, characterized in that the discharge throttle bore (30) is dimensioned such that cavitation effects occur in the discharge throttle bore (30) when the switching valve (40) is actuated.
EP99966843A 1998-12-22 1999-12-08 Fuel injection valve Expired - Lifetime EP1056946B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19859592 1998-12-22
DE19859592A DE19859592C1 (en) 1998-12-22 1998-12-22 Fuel injection valve for high pressure injection of fuel into the combustion chambers of internal combustion engines
PCT/DE1999/003914 WO2000037794A1 (en) 1998-12-22 1999-12-08 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP1056946A1 true EP1056946A1 (en) 2000-12-06
EP1056946B1 EP1056946B1 (en) 2004-03-17

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP99966843A Expired - Lifetime EP1056946B1 (en) 1998-12-22 1999-12-08 Fuel injection valve

Country Status (5)

Country Link
US (1) US6382185B1 (en)
EP (1) EP1056946B1 (en)
JP (1) JP2002533608A (en)
DE (2) DE19859592C1 (en)
WO (1) WO2000037794A1 (en)

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Publication number Priority date Publication date Assignee Title
DE10055267B4 (en) * 2000-11-08 2004-07-29 Robert Bosch Gmbh Pressure-controlled injector for high injection with slide throttles
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DE59908888D1 (en) 2004-04-22
JP2002533608A (en) 2002-10-08
US6382185B1 (en) 2002-05-07
EP1056946B1 (en) 2004-03-17
WO2000037794A1 (en) 2000-06-29
DE19859592C1 (en) 2000-05-04

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