EP2481910B1 - Fuel injector component - Google Patents

Fuel injector component Download PDF

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Publication number
EP2481910B1
EP2481910B1 EP11196257.7A EP11196257A EP2481910B1 EP 2481910 B1 EP2481910 B1 EP 2481910B1 EP 11196257 A EP11196257 A EP 11196257A EP 2481910 B1 EP2481910 B1 EP 2481910B1
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EP
European Patent Office
Prior art keywords
guide
radial gap
component
fuel injection
injection component
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.)
Not-in-force
Application number
EP11196257.7A
Other languages
German (de)
French (fr)
Other versions
EP2481910B2 (en
EP2481910A1 (en
Inventor
Frieder Buerkle
Andreas Ellenschlaeger
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/167—Means for compensating clearance or thermal expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"

Definitions

  • the invention relates to a fuel injection component according to the preamble of claim 1.
  • Such a fuel injection component is known from EP 1 653 076 A1 known.
  • the radial gap narrowing in the flow direction of the fuel is produced in the conventional fuel injection component by radially deforming a wall portion of the fuel injection component by attaching an axial clamping force when attaching the fuel injection component to a fuel storage member (rail), the amount of deformation or the radial gap depends on the height of the axial force and the geometry of the component.
  • the fuel injection component is formed as a hydraulic valve for a fuel injector, which has a guide pin slidably guided in a valve sleeve, one end face of which is subjected to a force under high pressure fuel.
  • the high-pressure fuel causes an axial expansion of the valve sleeve radially surrounding the valve sleeve, so that a cone-shaped radial gap is formed, as a result of which increased leakage losses can occur on the hydraulic valve.
  • a conical design of the guide for the valve pin and a corresponding embodiment of the valve sleeve is proposed to avoid the increased leakage losses. It is essential that while the radial gap is constant over the axial length of the guide pin despite hydraulic compressive stress.
  • the present invention seeks to further develop a fuel injection according to the preamble of claim 1 such that a changing in the flow direction radial gap without applying external, deformation-causing forces can be formed easily and reproducibly. This should reduce the tendency to deposits in the guide area of a moving component, despite the increased use of alternative fuels.
  • This object is achieved in a fuel injection component with the features of claim 1 according to the invention that the radial gap is formed by a conical design of the guide bore or the component or by a conical design of the moving member in a cylindrical configuration of the guide member.
  • the component is arranged operatively connected to an actuating element which upon activation, the component in the guide bore in the direction of the larger Pressure moves.
  • a radial gap is provided, which has a maximum of 1 micron at its narrowest point and at the furthest point 10 microns, or that the cone angle over the length of the component or the guide bore is a maximum of about 1.5 ° ,
  • the deposits tend to arise where relatively high component or fuel temperatures prevail or where the narrowest guide gap is formed. Since such boundary conditions occur especially in fuel injectors, it is provided in particular that the fuel injection component is part of a fuel injector.
  • the component and the guide component are part of a hydraulic coupler arranged in a low-pressure region, which is arranged in operative connection with a piezoactuator.
  • the component is an anchor bolt of a solenoid valve and the guide member is an armature guide element.
  • Components that are subjected to pressures of 1600 bar and more under high pressure, meaning more pressurized fuel, are elastically deformed under the pressure load of the fuel. Therefore, it is preferably provided that the size of the radial gap is formed taking into account an elastic deformation of the component due to hydraulic pressure.
  • FIG. 1 an arrangement according to the prior art is shown. Such arrangements are known in particular from fuel injection systems, for example in the field of fuel injectors.
  • the arrangement comprises a component 1 with a pin-shaped, in particular cylindrically shaped region 2, which is arranged in a cylindrical guide bore 3 of a guide component 4 in the direction of the double arrow 5 in its longitudinal axis up and down movable.
  • the component 1 is connected in a manner known per se with an actuating element, not shown, for example an electromagnet or the like, in order to realize the movement of the component 1 in the direction of the double arrow 5.
  • the guide bore 3 has an inner diameter D, while the component 1 has an outer diameter d.
  • a radial gap 6 is formed within the guide bore 3, the sake of better visibility in the Fig. 1 is shown greatly enlarged. It is essential that due to the constant diameter d, D of the region 2 and the guide bore 3 of the radial gap 6 over the guide length of the component 1 within the guide bore 3 is always the same size.
  • At the one end face 7 of the component 1 is in particular under high pressure, for example, a pressure of more than 1600 bar, standing fuel.
  • high pressure for example, a pressure of more than 1600 bar
  • deposits 9a, 9b and 9c occur in the region of the radial gap 6.
  • the deposits 9a, 9b and 9c represent typical locations in the radial gap 6, at which the deposits 9a, 9b and 9c can deposit.
  • the deposits 9a are located in the area of the end face 7 in the radial gap 6, while the deposits 9b are located in the region of the end 8 in the radial gap 6.
  • the deposit 9 c is arranged opposite to the entire axial length of the component 1 in the radial gap 6. It is understood that the said deposits 9a, 9b and 9c are arranged in each case over the entire cross section of the radial gap 6, wherein in the Fig. 1 For the sake of simplicity, all deposits 9a, 9b, 9c are shown simultaneously.
  • Fig. 2 an arrangement according to the invention of a component 10 is shown in a guide member 12.
  • the arrangement differs Fig. 2 from the arrangement according to the Fig. 1 in that the radial gap 13, in contrast to the radial gap 6, viewed over the axial length, is conical.
  • the radial gap 13 in the region of the one end face 14 of the component 10, at which a greater pressure of a pressure medium (fuel) prevails, than on the other side of the component 10 has a larger area or a larger cross-section, as in the exit region 15 of the component 10 from the guide bore 16th
  • the radial gap 13 at its narrowest point (in the exit region 15) a maximum of 1 micron, and at its widest point (in the region of the end face 14) max. 10 ⁇ m wide is formed.
  • a cone angle ⁇ of the radial gap 13 it is provided that, viewed over the length of the component 10 in the region of the guide bore 16 or over the length of the component 10, it is at most approximately 1.5 °.
  • the conical shape of the radial gap 13 is preferably formed by the fact that the guide bore 16 is formed in the guide member 12 is cylindrical, while the component 10 receives its conical shape in particular by grinding. Of course, it is also within the scope of the invention that the component 10 is cylindrical, while the guide bore 16 is conical.
  • the component 10 is arranged in a manner not shown with an actuating element 18, for example a magnetic armature or the like, in operative connection.
  • an actuating element 18 for example a magnetic armature or the like
  • the component 10 is moved along its longitudinal axis 17, i. along the double arrow 19, preferably in the direction of the growing radial gap 13, so that deposits 9a, 9b, 9c are not compacted in the radial gap 13 by the movement of the component 10.
  • restoring means e.g. be provided in the form of compression springs or the like, which move the component 10 back to its original position upon deactivation of the actuating element 18. In other words, this means that the actuating element 18 moves the component 10 in an activation of the actuating element 18 in the direction of the higher pressure.
  • the component 10 and the guide component 12 are part of a fuel injection component 100.
  • the fuel injection component 100 is a fuel injector, which is flowed through with high-pressure fuel.
  • the component 10 may be an anchor bolt of a solenoid valve
  • the guide member 12 may be an armature guide member.
  • the component 10 and the guide member 12 are part of a arranged in a low pressure region of the fuel injector hydraulic coupler, wherein the component 10 is then arranged, for example, in operative connection with a piezoelectric actuator as the actuating element 18.
  • a nip pressure p is understood to mean the pressure of the fuel which prevails in the radial gap 6, 13, as a result of the pressure differences.
  • the length I (0) represents the component 1, 10 at the exit region 15 and the length I (1) the component 1, 10 at the end face 7, 14.
  • dashed lines here are the pressure gradients in the deposits 9a, 9b and 9c according to the prior art according to Fig. 1 shown using an always the same radial gap 6.

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

Description

Stand der TechnikState of the art

Die Erfindung betrifft eine Kraftstoffeinspritzkomponente nach dem Oberbegriff des Anspruchs 1.The invention relates to a fuel injection component according to the preamble of claim 1.

Eine derartige Kraftstoffeinspritzkomponente ist aus der EP 1 653 076 A1 bekannt. Der sich in Strömungsrichtung des Kraftstoffs verengende Radialspalt wird bei der aus der Schrift bekannten Kraftstoffeinspritzkomponente dadurch erzeugt, dass beim Befestigen der Kraftstoffeinspritzkomponente an einem Kraftstoffspeicherelement (Rail) eine radiale Verformung eines Wandabschnitts der Kraftstoffeinspritzkomponente durch Aufbringen einer axialen Spannkraft erzeugt wird, wobei die Größe der Verformung bzw. des Radialspalts von der Höhe der Axialkraft sowie der Geometrie des Bauteils abhängt.Such a fuel injection component is known from EP 1 653 076 A1 known. The radial gap narrowing in the flow direction of the fuel is produced in the conventional fuel injection component by radially deforming a wall portion of the fuel injection component by attaching an axial clamping force when attaching the fuel injection component to a fuel storage member (rail), the amount of deformation or the radial gap depends on the height of the axial force and the geometry of the component.

Eine weitere Kraftstoffeinspritzkomponente ist aus der DE 10 2007 025 964 A1 der Anmelderin bekannt. In dieser Schrift ist die Kraftstoffeinspritzkomponente als Hydraulikventil für einen Kraftstoffinjektor ausgebildet, das einen in einer Ventilhülse gleitend geführten Führungsbolzen aufweist, dessen eine Stirnfläche mit unter Hochdruck stehendem Kraftstoff kraftbeaufschlagt ist. Der unter Hochdruck stehende Kraftstoff bewirkt eine axiale Aufweitung der dem Ventilbolzen radial umgebenden Ventilhülse, so dass sich ein konusförmiger Radialspalt ausbildet, in dessen Folge erhöhte Leckageverluste an dem Hydraulikventil auftreten können. In der vorbenannten Schrift wird daher zur Vermeidung der erhöhten Leckageverluste eine konusförmige Ausgestaltung der Führung für den Ventilbolzen sowie eine entsprechende Ausgestaltung der Ventilhülse vorgeschlagen. Wesentlich dabei ist, dass dabei der Radialspalt trotz hydraulischer Druckbeanspruchung über die axiale Länge des Führungsbolzens konstant ist.Another fuel injection component is out of the DE 10 2007 025 964 A1 the applicant known. In this document, the fuel injection component is formed as a hydraulic valve for a fuel injector, which has a guide pin slidably guided in a valve sleeve, one end face of which is subjected to a force under high pressure fuel. The high-pressure fuel causes an axial expansion of the valve sleeve radially surrounding the valve sleeve, so that a cone-shaped radial gap is formed, as a result of which increased leakage losses can occur on the hydraulic valve. In the above-mentioned document therefore a conical design of the guide for the valve pin and a corresponding embodiment of the valve sleeve is proposed to avoid the increased leakage losses. It is essential that while the radial gap is constant over the axial length of the guide pin despite hydraulic compressive stress.

Neben der angesprochenen Problematik von Leckageverlusten kommt es durch den zunehmenden Einsatz von alternativen Kraftstoffen, insbesondere von Biodiesel, bei Kraftstoffeinspritzkomponenten, die in selbstzündenden Brennkraftmaschinen eingesetzt werden, zu einer erhöhten Tendenz der Bildung von Ablagerungen in dem Führungsspalt zwischen einem entlang einer Längsachse verschiebbar angeordneten Bauteil und der Führungsbohrung eines das Bauteil aufnehmenden Führungsbauteils. Mit dem aus der DE 10 2007 025 964 A1 bekannten, unter hydraulischer Druckbelastung über die axiale Länge konstanten Radialspalt ist die angesprochene Problematik der Ablagerungen nicht zufriedenstellend gelöst.In addition to the problem of leakage losses mentioned above, the increasing use of alternative fuels, in particular biodiesel, in fuel injection components used in self-igniting internal combustion engines leads to an increased tendency for the formation of deposits in the guide gap between a component displaceable along a longitudinal axis the guide bore of a component receiving the guide member. With the from the DE 10 2007 025 964 A1 known, under hydraulic pressure load over the axial length constant radial gap, the problem of deposits mentioned is not satisfactorily solved.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine Kraftstoffeinspritzkomponente nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass sich ein in Durchströmungsrichtung ändernder Radialspalt ohne Aufbringen von äußeren, eine Verformung bewirkenden Kräften einfach und reproduzierbar ausbilden lässt. Dadurch soll trotz des erhöhten Einsatzes alternativer Kraftstoffe die Tendenz zu Ablagerungen im Führungsbereich eines bewegten Bauteils reduziert werden. Diese Aufgabe wird bei einer Kraftstoffeinspritzkomponente mit den Merkmalen des Anspruchs 1 erfindungsgemäß dadurch gelöst, dass der Radialspalt durch eine konische Ausbildung der Führungsbohrung bzw. des Bauteils oder durch eine konische Ausbildung des bewegten Bauteils bei einer zylindrischen Ausbildung der Führungsbauteils ausgebildet ist.Based on the illustrated prior art, the present invention seeks to further develop a fuel injection according to the preamble of claim 1 such that a changing in the flow direction radial gap without applying external, deformation-causing forces can be formed easily and reproducibly. This should reduce the tendency to deposits in the guide area of a moving component, despite the increased use of alternative fuels. This object is achieved in a fuel injection component with the features of claim 1 according to the invention that the radial gap is formed by a conical design of the guide bore or the component or by a conical design of the moving member in a cylindrical configuration of the guide member.

Vorteilhafte Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzkomponente sind in den Unteransprüchen angegeben.Advantageous developments of the fuel injection component according to the invention are specified in the subclaims.

Um zu vermeiden, dass es bei einer Betätigung des bewegten Bauteils zu einer Verdichtung der Ablagerungen kommt, ist es darüber hinaus ganz bevorzugt vorgesehen, dass das Bauteil mit einem Betätigungselement wirkverbunden angeordnet ist, das bei einer Aktivierung das Bauteil in der Führungsbohrung in Richtung des größeren Drucks bewegt.In order to avoid that during an actuation of the moving component comes to a compression of the deposits, it is also very preferably provided that the component is arranged operatively connected to an actuating element which upon activation, the component in the guide bore in the direction of the larger Pressure moves.

Als günstige Dimensionierung des Radialspalts unter herstellungstechnisch wirtschaftlichen Randbedingungen ist ein Radialspalt vorgesehen, der an seiner engsten Stelle maximal 1µm und an der weitesten Stelle maximal 10µm aufweist, bzw. dass der Konuswinkel über die Länge des Bauteils oder der Führungsbohrung maximal etwa 1,5° beträgt.As a favorable dimensioning of the radial gap under manufacturing conditions economic boundary conditions a radial gap is provided, which has a maximum of 1 micron at its narrowest point and at the furthest point 10 microns, or that the cone angle over the length of the component or the guide bore is a maximum of about 1.5 ° ,

Es hat sich herausgestellt, dass die Ablagerungen tendenziell dort entstehen, wo relativ hohe Bauteil- bzw. Kraftstofftemperaturen herrschen bzw. wo der engste Führungsspalt ausgebildet ist. Da derartige Randbedingungen insbesondere auch bei Kraftstoffinjektoren vorkommen, ist es insbesondere vorgesehen, dass die Kraftstoffeinspritzkomponente Bestandteil eines Kraftstoffinjektors ist.It has been found that the deposits tend to arise where relatively high component or fuel temperatures prevail or where the narrowest guide gap is formed. Since such boundary conditions occur especially in fuel injectors, it is provided in particular that the fuel injection component is part of a fuel injector.

In einer ersten konstruktiven Umsetzung der Erfindung kann es vorgesehen sein, dass das Bauteil und das Führungsbauteil Bestandteil eines in einem Niederdruckbereich angeordneten hydraulischen Kopplers sind, der in Wirkverbindung mit einem Piezoaktuator angeordnet ist.In a first design implementation of the invention, it can be provided that the component and the guide component are part of a hydraulic coupler arranged in a low-pressure region, which is arranged in operative connection with a piezoactuator.

Alternativ ist es auch denkbar, dass das Bauteil ein Ankerbolzen eines Magnetventils und das Führungsbauteil ein Ankerführungselement ist.Alternatively, it is also conceivable that the component is an anchor bolt of a solenoid valve and the guide member is an armature guide element.

Bauteile, die mit unter hohem Druck, gemeint sind hier Drücke von 1600bar und mehr stehendem Kraftstoff ausgesetzt sind, werden unter der Druckbelastung des Kraftstoffs elastisch verformt. Daher ist es bevorzugt vorgesehen, dass die Größe des Radialspalts unter Berücksichtigung einer elastischen Verformung des Bauteils aufgrund hydraulischen Drucks ausgebildet ist.Components that are subjected to pressures of 1600 bar and more under high pressure, meaning more pressurized fuel, are elastically deformed under the pressure load of the fuel. Therefore, it is preferably provided that the size of the radial gap is formed taking into account an elastic deformation of the component due to hydraulic pressure.

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnung.Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawing.

Diese zeigt in:

Fig. 1
ein in einem Führungsbauteil verschiebbar angeordnetes Bauteil gemäß dem Stand der Technik in einer teilweise geschnittenen Seitenansicht,
Fig. 2
eine erfindungsgemäße Anordnung eines in einem Führungsbauteil angeordneten Bauteils unter Verwendung eines konisch ausgebildeten Radialspalts und
Fig. 3
ein Diagramm zur Verdeutlichung der Druckverläufe in den Radialspalten gemäß Anordnungen in den Fig. 1 und 2 in Verbindung mit in den Radialspalten befindlichen Ablagerungen.
This shows in:
Fig. 1
a slidably arranged in a guide member component according to the prior art in a partially sectioned side view,
Fig. 2
an inventive arrangement of a arranged in a guide member component using a conical radial gap and
Fig. 3
a diagram illustrating the pressure gradients in the radial gaps according to arrangements in the Fig. 1 and 2 in connection with deposits in the radial gaps.

In der Fig. 1 ist eine Anordnung gemäß dem Stand der Technik dargestellt. Derartige Anordnungen sind insbesondere aus Kraftstoffeinspritzsystemen, zum Beispiel im Bereich von Kraftstoffinjektoren, bekannt. Die Anordnung umfasst ein Bauteil 1 mit einem stiftförmigen, insbesondere zylindrisch ausgebildeten Bereich 2, der in einer zylindrischen Führungsbohrung 3 eines Führungsbauteils 4 in Richtung des Doppelpfeils 5 in seiner Längsachse auf- und abbeweglich angeordnet ist. Das Bauteil 1 ist in an sich bekannter Art und Weise mit einem nicht dargestellten Betätigungselement, beispielsweise einem Elektromagneten oder ähnlichem verbunden, um die Bewegung des Bauteils 1 in Richtung des Doppelpfeils 5 zu realisieren. Die Führungsbohrung 3 weist einen Innendurchmesser D auf, während das Bauteil 1 einen Außendurchmesser d aufweist. Zwischen dem Bauteil 1 und der Führungsbohrung 3 des Führungsbauteils 4 ist ein Radialspalt 6 innerhalb der Führungsbohrung 3 ausgebildet, der der besseren Erkennbarkeit halber in der Fig. 1 stark vergrößert dargestellt ist. Wesentlich dabei ist, dass aufgrund der konstanten Durchmesser d, D des Bereichs 2 bzw. der Führungsbohrung 3 der Radialspalt 6 über die Führungslänge des Bauteils 1 innerhalb der Führungsbohrung 3 stets gleich groß ist.In the Fig. 1 an arrangement according to the prior art is shown. Such arrangements are known in particular from fuel injection systems, for example in the field of fuel injectors. The arrangement comprises a component 1 with a pin-shaped, in particular cylindrically shaped region 2, which is arranged in a cylindrical guide bore 3 of a guide component 4 in the direction of the double arrow 5 in its longitudinal axis up and down movable. The component 1 is connected in a manner known per se with an actuating element, not shown, for example an electromagnet or the like, in order to realize the movement of the component 1 in the direction of the double arrow 5. The guide bore 3 has an inner diameter D, while the component 1 has an outer diameter d. Between the component 1 and the guide bore 3 of the guide member 4, a radial gap 6 is formed within the guide bore 3, the sake of better visibility in the Fig. 1 is shown greatly enlarged. It is essential that due to the constant diameter d, D of the region 2 and the guide bore 3 of the radial gap 6 over the guide length of the component 1 within the guide bore 3 is always the same size.

An der einen Stirnfläche 7 des Bauteils 1 steht insbesondere unter Hochdruck, beispielsweise einem Druck von mehr als 1600bar, stehender Kraftstoff an. Demgegenüber herrscht an dem der Stirnseite 7 gegenüberliegenden Ende 8 des Bauteils 1 ein geringerer Druck, beispielsweise ein Rücklaufdruck zu einem Kraftstoffvorratsbehälter, so dass der unter hohem Druck stehende Kraftstoff die Führungsbohrung 3 aus Richtung der Stirnfläche 7 in Richtung des Endes 8 des Bauteils 1 durchströmt. Insbesondere bei Verwendung alternativer Kraftstoffe, genannt sei hier beispielhaft, aber nicht einschränkend Biodiesel, kommt es im Bereich des Radialspalts 6 zu Ablagerungen 9a, 9b und 9c. Hierbei repräsentieren die Ablagerungen 9a, 9b und 9c typische Stellen im Radialspalt 6, an denen sich die Ablagerungen 9a, 9b und 9c ablagern können. So befinden sich die einen Ablagerungen 9a im Bereich der Stirnfläche 7 im Radialspalt 6, während die Ablagerungen 9b sich im Bereich des Endes 8 im Radialspalt 6 befinden. Die Ablagerung 9c ist entgegen über die gesamte axiale Länge des Bauteils 1 im Radialspalt 6 angeordnet. Es versteht sich, dass die genannten Ablagerungen 9a, 9b und 9c hierbei jeweils über den gesamten Querschnitt des Radialspalts 6 angeordnet sind, wobei in der Fig. 1 der Einfachheit halber alle Ablagerungen 9a, 9b, 9c gleichzeitig dargestellt sind.At the one end face 7 of the component 1 is in particular under high pressure, for example, a pressure of more than 1600 bar, standing fuel. In contrast, there is a lower pressure at the opposite end face 8 of the component 1, for example, a return pressure to a fuel tank, so that the fuel under high pressure the Guide bore 3 from the direction of the end face 7 in the direction of the end 8 of the component 1 flows through. In particular, when using alternative fuels, which may be mentioned here by way of example but not restricting biodiesel, deposits 9a, 9b and 9c occur in the region of the radial gap 6. In this case, the deposits 9a, 9b and 9c represent typical locations in the radial gap 6, at which the deposits 9a, 9b and 9c can deposit. Thus, the deposits 9a are located in the area of the end face 7 in the radial gap 6, while the deposits 9b are located in the region of the end 8 in the radial gap 6. The deposit 9 c is arranged opposite to the entire axial length of the component 1 in the radial gap 6. It is understood that the said deposits 9a, 9b and 9c are arranged in each case over the entire cross section of the radial gap 6, wherein in the Fig. 1 For the sake of simplicity, all deposits 9a, 9b, 9c are shown simultaneously.

In der Fig. 2 ist eine erfindungsgemäße Anordnung eines Bauteils 10 in einem Führungsbauteil 12 dargestellt. Hierbei unterscheidet sich die Anordnung der Fig. 2 von der Anordnung gemäß der Fig. 1 dadurch, dass der Radialspalt 13, im Gegensatz zum Radialspalt 6, über die axiale Länge betrachtet, konusförmig ausgebildet ist. Insbesondere ist es vorgesehen, dass der Radialspalt 13 im Bereich der einen Stirnfläche 14 des Bauteils 10, an der ein größerer Druck eines Druckmittels (Kraftstoff) herrscht, als an der anderen Seite des Bauteils 10, eine größere Fläche bzw. einen größeren Querschnitt aufweist, als im Austrittsbereich 15 des Bauteils 10 aus der Führungsbohrung 16.In the Fig. 2 an arrangement according to the invention of a component 10 is shown in a guide member 12. Here, the arrangement differs Fig. 2 from the arrangement according to the Fig. 1 in that the radial gap 13, in contrast to the radial gap 6, viewed over the axial length, is conical. In particular, it is provided that the radial gap 13 in the region of the one end face 14 of the component 10, at which a greater pressure of a pressure medium (fuel) prevails, than on the other side of the component 10, has a larger area or a larger cross-section, as in the exit region 15 of the component 10 from the guide bore 16th

Bevorzugt ist es vorgesehen, dass der Radialspalt 13 an seiner engsten Stelle (im Austrittsbereich 15) maximal 1µm, und an seiner weitesten Stelle (im Bereich der Stirnfläche 14) max. 10µm breit ausgebildet ist. Bezüglich eines Konuswinkels α des Radialspalts 13 ist es vorgesehen, dass dieser über die Länge des Bauteils 10 im Bereich der Führungsbohrung 16 bzw. über die Länge des Bauteils 10 betrachtet maximal etwa 1,5° beträgt.Preferably, it is provided that the radial gap 13 at its narrowest point (in the exit region 15) a maximum of 1 micron, and at its widest point (in the region of the end face 14) max. 10μm wide is formed. With respect to a cone angle α of the radial gap 13, it is provided that, viewed over the length of the component 10 in the region of the guide bore 16 or over the length of the component 10, it is at most approximately 1.5 °.

Die konusförmige Ausbildung des Radialspalts 13 wird bevorzugt dadurch ausgebildet, dass die Führungsbohrung 16 in Führungsbauteil 12 zylindrisch ausgebildet ist, während das Bauteil 10 insbesondere durch Schleifen seine konusförmige Form erhält. Selbstverständlich liegt es auch im Rahmen der Erfindung, dass das Bauteil 10 zylindrisch ausgebildet ist, während die Führungsbohrung 16 konusförmig ist.The conical shape of the radial gap 13 is preferably formed by the fact that the guide bore 16 is formed in the guide member 12 is cylindrical, while the component 10 receives its conical shape in particular by grinding. Of course, it is also within the scope of the invention that the component 10 is cylindrical, while the guide bore 16 is conical.

Das Bauteil 10 ist auf nicht mehr dargestellte Art und Weise mit einem Betätigungselement 18, beispielsweise einem Magnetanker oder ähnlichem, in Wirkverbindung angeordnet. Bei einer Betätigung des Betätigungselements 18, z.B. bei einer Bestromung einer Magnetspule, wird das Bauteil 10 entlang seiner Längsachse 17, d.h. entlang des Doppelpfeils 19, vorzugsweise in Richtung des größer werdenden Radialspalts 13 bewegt, damit Ablagerungen 9a, 9b, 9c im Radialspalt 13 durch die Bewegung des Bauteils 10 nicht verdichtet werden. Üblicherweise können Rückstellmittel, z.B. in Form von Druckfedern oder ähnlichem vorgesehen sein, die bei einer Deaktivierung des Betätigungselements 18 das Bauteil 10 wieder in seine ursprüngliche Lage bewegen. Mit anderen Worten gesagt bedeutet dies, dass das Betätigungselement 18 das Bauteil 10 bei einer Aktivierung des Betätigungselements 18 in Richtung des höheren Drucks bewegt.The component 10 is arranged in a manner not shown with an actuating element 18, for example a magnetic armature or the like, in operative connection. Upon actuation of the actuator 18, e.g. when a solenoid is energized, the component 10 is moved along its longitudinal axis 17, i. along the double arrow 19, preferably in the direction of the growing radial gap 13, so that deposits 9a, 9b, 9c are not compacted in the radial gap 13 by the movement of the component 10. Usually, restoring means, e.g. be provided in the form of compression springs or the like, which move the component 10 back to its original position upon deactivation of the actuating element 18. In other words, this means that the actuating element 18 moves the component 10 in an activation of the actuating element 18 in the direction of the higher pressure.

Es ist vorgesehen, dass das Bauteil 10 sowie das Führungsbauteil 12 Bestandteil einer Kraftstoffeinspritzkomponente 100 sind. Insbesondere ist es dabei denkbar, dass die Kraftstoffeinspritzkomponente 100 ein Kraftstoffinjektor ist, der mit unter Hochdruck stehendem Kraftstoff durchströmt ist. Z. B. kann es sich bei dem Bauteil 10 dabei um einen Ankerbolzen eines Magnetventils, und bei dem Führungsbauteil 12 um ein Ankerführungselement handeln. Es ist jedoch auch denkbar, dass das Bauteil 10 und das Führungsbauteil 12 Bestandteil eines in einem Niederdruckbereich des Kraftstoffinjektors angeordneten hydraulischen Kopplers sind, wobei das Bauteil 10 dann beispielsweise in Wirkverbindung mit einem Piezoaktuator als Betätigungselement 18 angeordnet ist.It is provided that the component 10 and the guide component 12 are part of a fuel injection component 100. In particular, it is conceivable that the fuel injection component 100 is a fuel injector, which is flowed through with high-pressure fuel. For example, the component 10 may be an anchor bolt of a solenoid valve, and the guide member 12 may be an armature guide member. However, it is also conceivable that the component 10 and the guide member 12 are part of a arranged in a low pressure region of the fuel injector hydraulic coupler, wherein the component 10 is then arranged, for example, in operative connection with a piezoelectric actuator as the actuating element 18.

Bei den insbesondere in Kraftstoffinjektoren während des Betriebs herrschenden relativ hohen Drücken des Kraftstoffs, gemeint sind hier Drücke von 1600bar und mehr, kann es zu einer elastischen Verformung des Bauteils 10 bzw. des Führungsbauteils 12 kommen. Es ist daher bevorzugt vorgesehen, dass eine derartige elastische Verformung des Bauteils 10 bzw. des Führungsbauteils 12 bei einer Bemaßung des Radialspalts 13 bzw. bei der Herstellung des Bauteils 10 sowie des Führungsbauteils 12 beachtet bzw. berücksichtigt wird.In the case of the relatively high pressures of the fuel, which prevail in particular in fuel injectors during operation, pressures of 1600 bar and more are meant here, elastic deformation of the component 10 or of the guide component 12 may occur. Therefore, it is preferably provided that such an elastic deformation of the component 10 or of the guide component 12 is taken into account or taken into account when dimensioning the radial gap 13 or when producing the component 10 and the guide component 12.

In der Fig. 3 sind über die Länge I des Bauteils 1, 10 innerhalb des Radialspalts 6, 13 die Spaltdrücke p dargestellt. Hierbei wird unter einem Spaltdruck p der in dem Radialspalt 6, 13 herrschende, in Folge der Druckunterschiede sich einstellende Druck des Kraftstoffs verstanden. Die Länge I(0) repräsentiert dabei die das Bauteil 1, 10 am Austrittsbereich 15 und die Länge I(1) das Bauteil 1, 10 an der Stirnfläche 7, 14. Durch gestrichelte Linien sind hierbei die Druckverläufe bei den Ablagerungen 9a, 9b und 9c gemäß dem Stand der Technik nach Fig. 1 unter Verwendung eines stets gleichen Radialspaltes 6 dargestellt. Demgegenüber wird durch die durchgezogenen Linien der Druckverlauf bei den Ablagerungen 9a, 9b und 9c bei einem Radialspalt 13 dargestellt, wenn dieser gemäß der Erfindung konusförmig ausgebildet ist, wobei ansonsten die Bauteile 1, 10 und die Führungsbauteile 4, 12 dieselbe Dimensionierung aufweisen. Man erkennt, dass jeweils bei direktem Vergleich zwischen den Ablagerungen 9a, 9b und 9c gemäß dem Stand der Technik und der Erfindung bei der Erfindung mit dem Radialspalt 13 stets ein größerer Druck innerhalb des Radialspaltes 13 im Vergleich zum Radialspalt 6 herrscht. Durch den jeweils höheren Druck wird dabei die Tendenz zu Ablagerungen im Radialspalt 13 verringert, bzw. das Ablösen von Ablagerungen 9a, 9b, 9c von den Bauteiloberflächen des Bauteils 10 bzw. des Führungsbauteils 12 beim Spülen bzw. Durchströmen der Radialspalte 6, 13 erleichtert.In the Fig. 3 the gap pressures p are shown over the length I of the component 1, 10 within the radial gap 6, 13. In this case, a nip pressure p is understood to mean the pressure of the fuel which prevails in the radial gap 6, 13, as a result of the pressure differences. The length I (0) represents the component 1, 10 at the exit region 15 and the length I (1) the component 1, 10 at the end face 7, 14. By dashed lines here are the pressure gradients in the deposits 9a, 9b and 9c according to the prior art according to Fig. 1 shown using an always the same radial gap 6. In contrast, the pressure curve in the deposits 9a, 9b and 9c at a radial gap 13 is shown by the solid lines, if this is cone-shaped according to the invention, otherwise the components 1, 10 and the guide members 4, 12 have the same dimensions. It can be seen that each time a direct comparison between the deposits 9a, 9b and 9c according to the prior art and the invention in the invention with the radial gap 13 always a greater pressure within the radial gap 13 in comparison to the radial gap 6 prevails. The higher pressure in each case reduces the tendency for deposits in the radial gap 13, or facilitates the detachment of deposits 9a, 9b, 9c from the component surfaces of the component 10 or the guide component 12 during flushing or passage through the radial gaps 6, 13.

Claims (7)

  1. Fuel injection component (100), having a part (10) which is arranged so as to be displaceable along a longitudinal axis (17) and which is arranged in a guide bore (16) of a guide part (12) such that a radial gap (13) is formed, wherein different pressures of a pressure medium, in particular of a fuel, prevail on the two opposite sides of the guide bore (16), wherein the pressure medium flows through the radial gap (13) in the direction of the lower pressure, wherein the radial gap (13) between the part (10) and the guide part (12) is configured so as to vary in size over the axial length of the guide bore (16), and wherein the radial gap (13) decreases in size in the direction of the lower pressure of the part (10) in the guide bore (16),
    characterized
    in that the radial gap (13) is formed by a conical configuration of the guide bore (16) or of the part (10) or is formed by a conical configuration of the part (10) with a cylindrical configuration of the guide bore (16) in the guide part (12).
  2. Fuel injection component according to Claim 1,
    characterized
    in that the part (10) is arranged so as to be operatively connected to an actuation element (18) which, upon an activation, moves the part (10) in the guide bore (16) in the direction of the higher pressure.
  3. Fuel injection component according to Claim 1 or 2,
    characterized
    in that the radial gap (13) is at most 1 µm at its narrowest point and at most 10 µm at the widest point, and/or in that the cone angle (α) is at most approximately 1.5° over the length of the part (10) or of the guide bore (16).
  4. Fuel injection component according to one of Claims 1 to 3,
    characterized
    in that said fuel injection component is a constituent part of a fuel injector.
  5. Fuel injection component according to Claim 4,
    characterized
    in that the part (10) and the guide part (12) are constituent parts of a hydraulic coupler which is arranged in a low-pressure region and which is arranged so as to be operatively connected to a piezo actuator.
  6. Fuel injection component according to Claim 4,
    characterized
    in that the part (10) is an armature pin of a solenoid valve, and the guide part (12) is an armature guide element.
  7. Fuel injection component according to one of Claims 4 to 6,
    characterized
    in that the size of the radial gap (13) is configured taking into consideration an elastic deformation of the part (10) and/or of the guide part (12) owing to fuel at high hydraulic pressure.
EP11196257.7A 2011-02-01 2011-12-30 Fuel injector component Not-in-force EP2481910B2 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102011003452A DE102011003452A1 (en) 2011-02-01 2011-02-01 Fuel injection component

Publications (3)

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EP2481910A1 EP2481910A1 (en) 2012-08-01
EP2481910B1 true EP2481910B1 (en) 2013-08-28
EP2481910B2 EP2481910B2 (en) 2020-11-25

Family

ID=45581723

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11196257.7A Not-in-force EP2481910B2 (en) 2011-02-01 2011-12-30 Fuel injector component

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EP (1) EP2481910B2 (en)
CN (1) CN102628415B (en)
DE (1) DE102011003452A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB201402535D0 (en) * 2014-02-13 2014-04-02 Delphi Int Operations Luxembourg Sarl Fuel pump
SE545024C2 (en) * 2019-10-01 2023-02-28 Scania Cv Ab Fuel injector arrangement for an internal combustion engine and method for operating said arrangement

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59130070U (en) * 1983-02-18 1984-08-31 ダイハツ工業株式会社 internal combustion engine fuel injection valve
JPH07103106A (en) * 1993-09-30 1995-04-18 Hino Motors Ltd Fuel injection device
DE10045281C1 (en) † 2000-09-13 2002-05-23 Orange Gmbh High pressure fuel pump has reduced diameter of piston head corresponding with spacing of heat input from compression cavity
JP4119812B2 (en) * 2003-09-19 2008-07-16 ボッシュ株式会社 Fuel injection valve
DE102004002299A1 (en) * 2004-01-16 2005-08-04 Robert Bosch Gmbh Fuel injector with directly controlled injection valve member
DE102004012950A1 (en) † 2004-03-17 2005-10-13 Man B & W Diesel Ag High-pressure pump piston-cylinder unit
JP4100393B2 (en) * 2004-10-29 2008-06-11 株式会社デンソー Flow damper
DE102007025964A1 (en) 2007-06-04 2008-12-11 Robert Bosch Gmbh Hydraulic valve for a fuel injector

Also Published As

Publication number Publication date
CN102628415A (en) 2012-08-08
EP2481910B2 (en) 2020-11-25
EP2481910A1 (en) 2012-08-01
DE102011003452A1 (en) 2012-08-02
CN102628415B (en) 2017-03-01

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