EP2156045B1 - Injector - Google Patents

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Publication number
EP2156045B1
EP2156045B1 EP08736615A EP08736615A EP2156045B1 EP 2156045 B1 EP2156045 B1 EP 2156045B1 EP 08736615 A EP08736615 A EP 08736615A EP 08736615 A EP08736615 A EP 08736615A EP 2156045 B1 EP2156045 B1 EP 2156045B1
Authority
EP
European Patent Office
Prior art keywords
valve
guide element
valve piece
injector
sleeve
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
EP08736615A
Other languages
German (de)
French (fr)
Other versions
EP2156045A1 (en
Inventor
Bernd Streicher
Ralf Nussbaumer
Rudolf Heinz
Michael Mennicken
Holger Rapp
Wolfgang Stoecklein
Christian Faltin
Nadja Eisenmenger
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 EP2156045A1 publication Critical patent/EP2156045A1/en
Application granted granted Critical
Publication of EP2156045B1 publication Critical patent/EP2156045B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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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
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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"
    • 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
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided

Definitions

  • the invention relates to an injector for injecting fuel in a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.
  • Such an injector is from the EP 0 740 068 A2 known.
  • Such an injector has the advantage that the valve sleeve is guided with its outer diameter axially displaceable in a guide element, which is designed as a separate component from the valve member, but is adjacent to this.
  • the guide element can be set only after the manufacture of the valve seat for the valve sleeve on the valve piece, whereby the valve seat can be produced in the usual manner.
  • Additional further advantages are the relatively simple manufacturability of the guide element and in a relatively high strength of the valve piece.
  • the invention has the object, an injector according to the preamble of claim 1 such that a further simplification of the manufacturing process is made possible.
  • This object is achieved in an injector with the features of claim 1.
  • the guide element is fixed to the valve piece by means of a press fit.
  • This embodiment comes along.
  • This type of attachment is particularly suitable for a sleeve-shaped (tubular) formed guide element, which is pressed in the axial direction on the valve piece. It is advantageous if the guide element is elastically deformable in the radial direction, at least in the region of the press fit, in order to improve the clamping effect.
  • the guide element is fixed to a, in particular slightly conical portion of the valve piece.
  • the cone angle of a corresponding inner cone of the guide element before its attachment to the conical portion in particular slightly smaller than the cone angle of the conical portion of the valve piece.
  • the press fit as a so-called Morsekegelpassung, as it is known, for example, for the determination of tools on shafts, formed.
  • the cone angle (angle between the axis of symmetry of the conical portion and the oblique lateral surface of the conical portion) of the conical portion of the valve piece is small, in particular very small, preferably the cone angle is less than about 10 °, in particular less than about 5 ° , Particularly preferably, the cone angle of the conical section is in a range between about 0.5 ° and about 2.5 °.
  • the angle (angle between the axis of symmetry of the inner cone and the oblique inner lateral surface of the inner cone) of the inner cone of the guide element is advantageously about 0.1 ° to about 1.5 °, preferably about 0.25 ° to about 0.75 ° smaller than the cone angle of the conical section of the valve piece.
  • valve seat is arranged on the valve piece directly adjacent to the conical portion of the valve piece on which the guide element is fixed.
  • the valve seat is formed as a convex conical seat, wherein the angle of the conical surface is substantially flatter than the angle of the conical portion for fixing the valve piece.
  • the guide element rests with a continuous contact surface on the valve piece, in particular on the conical portion of the valve piece.
  • the contact surface in particular annularly interrupted, preferably by an exemption, so a non-contacting area on the guide element and / or on the valve piece.
  • two, in particular annular, in the axial direction by the clearance spaced contact areas between the guide member and the valve piece are formed, whereby the clamping action can be improved.
  • an outflow channel has to be provided from the fuel volume within the valve sleeve.
  • the transverse bore does not necessarily extend orthogonally to the longitudinal center axis of the valve sleeve, but may also be arranged obliquely.
  • valve sleeve on its outer circumference and / or the guide element on its inner periphery with at least one mecanicnanschliff to form an axial outflow channel.
  • Fig. 1 is a highly schematic section of a trained as a common rail injector injector 1 for injecting fuel in a combustion chamber, not shown, of an internal combustion engine shown.
  • Fig. 1 is intended to explain only the operation of the injector, wherein the proportions shown do not correspond to the real size ratios.
  • the injector 1 comprises a single-part or multi-part valve element 2 which is shown only in sections and which is adjustable between an open position and a closed position. In its open position (adjusted upward in the plane of the drawing), the valve element 2 releases the fuel flow from a pressure chamber 3 through a nozzle hole arrangement, not shown, into the combustion chamber of an internal combustion engine.
  • valve element 2 delimits a control chamber 5.
  • the latter is arranged radially inside a sleeve-shaped section of a valve piece 6 projecting into the pressure space 3.
  • control chamber 5 opens a introduced into the sleeve-shaped portion of the valve piece 6 inlet throttle 7, via which the control chamber 5 is supplied with fuel from the pressure chamber 3.
  • the pressure chamber 3 is in turn supplied by a fuel supply line 8 under high pressure fuel from a high-pressure fuel storage 9 (Rail).
  • This is powered by a, in particular designed as a radial piston pump high-pressure pump 10 with fuel from a low-pressure reservoir 11.
  • a radial piston pump high-pressure pump 10 with fuel from a low-pressure reservoir 11.
  • valve piece 6 From the control chamber 5 opens an inserted in the axial direction in the valve piece 6 drain channel 14. This is provided with an outlet throttle 15, or designed as such.
  • the drainage channel 14 spreads in his in the plane of the drawing upper portion and terminates in a valve chamber 16 which is bounded radially outwardly by the valve piece 6 and by a valve sleeve 17 adjacent thereto in the axial direction of a control valve 18 (servo valve).
  • the valve chamber 16 of the control valve 18 In the axial upward direction, the valve chamber 16 of the control valve 18 is delimited by an axially displaceably mounted pressure pin 19, which is pressed by befindlichem within the valve chamber 16 fuel in the axial direction in the plane up against a drain pipe 36.
  • the pressure pin 19 passes through a bore 37 in a holding body 20 of an electromagnet assembly 21.
  • a closing spring 23 which is formed on an integrally formed with the valve sleeve 17 anchor plate 24 is supported, is spring-loaded against the outlet nozzle 36.
  • the closing spring 23 acts simultaneously on the armature plate 24 and thus the valve sleeve with a spring force in the axial direction in the plane down to a formed on the valve piece 6, formed as a conical seat valve seat 25 of the control valve 18.
  • the closing spring is supported on an annular shoulder of the holding body 20th the solenoid assembly 21 from.
  • control valve 18 is a servo-pressure-balanced in the axial direction servo valve.
  • a hollow cylindrical, sleeve-shaped guide member 26th intended to guide the valve sleeve 17 on its outer periphery.
  • the guide member 26 is fixed by means of a press fit to a conical portion 27 of the valve piece 6, wherein an outer cone angle ⁇ of the conical portion 27 is shown for reasons of illustration much larger than this is preferably formed in reality.
  • the cone angle ⁇ between a conical surface 28 and an axis parallel to the longitudinal central axis L of the control valve 18 in this embodiment is about 1 °.
  • the conical portion 27 facing away from end face 29 of the guide member 26 is arranged at an axial distance to the underside of the anchor plate 24. How out Fig. 1 can be seen, the valve seat 25 is disposed radially within the conical portion 27 and the conical surface 28 (conical surface).
  • the guide element 26 is fixed by means of a press fit to the conical portion 27 of the valve piece 26.
  • a cone angle ⁇ of an inner cone 30 is like the cone angle ⁇ of the conical portion 27 of the valve member 6 in the mounted state also 1 °. Before assembly, however, the cone angle ⁇ of the inner cone 30 is slightly smaller than the cone angle ⁇ .
  • the inner cone is expanded elastically outward in the radial direction in order to improve the clamping effect.
  • the illustrated non-positive connection between the guide member 26 and the conical portion 27 of the valve member 6 is a kind Morsekegelpassung.
  • the guide member 26 has two opposite arranged at the level of the valve seat 25, slightly inclined transverse bores 31, 32 introduced by the fuel from the valve chamber 16 at the valve seat 25 lifted valve sleeve 17 of the control valve 18 in the guide member 26 surrounding the low pressure region 12 of the Injector can flow. From the low-pressure region 12, the fuel can flow through the injector return 13 to the reservoir 11.
  • valve sleeve 17 from the in Fig. 1 shown displaced position by energizing the solenoid assembly 21 in the plane of the drawing so that fuel via the introduced into the conical section 27, central drain passage 14 into the valve chamber 16 and from there below the valve sleeve in the radial direction and through the transverse bores 31, 32nd through into the low-pressure region 12 and from there to the injector return 13 can flow.
  • transverse bores 31, 32 themselves can be formed as discharge throttles.
  • FIG. 2 illustrated embodiment of an injector 1 substantially corresponds to the embodiment according to Fig. 1 so that to avoid repetition in the following, only the differences will be discussed. With regard to the similarities, reference is made to the preceding description of the figures.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Jellies, Jams, And Syrups (AREA)
  • Glass Compositions (AREA)
  • Disintegrating Or Milling (AREA)

Abstract

The invention relates to an injector (1) for injecting fuel into a combustion chamber of an internal combustion engine, particularly a common rail injector, comprising a control valve (18) having an axially adjustable valve sleeve (17) that is guided on the outer circumference, the control valve being used to release and block the fuel flow through a discharge duct (14) introduced in a valve piece in the direction of a low-pressure region (12) of the injector (1) from a control chamber (5), which is operatively connected to an axially adjustable valve element (2). According to the invention, the valve sleeve (17) is guided on the outer circumference by a guide element (26), the element being formed as a component that is separate from the valve piece (6) and fixed to the valve piece (6).

Description

Stand der TechnikState of the art

Die Erfindung betrifft einen Injektor zum Einspritzen von Kraftstoff in einem Brennraum einer Brennkraftmaschine, insbesondere einen Common-Rail-Injektor, nach dem Oberbegriff des Anspruchs 1.The invention relates to an injector for injecting fuel in a combustion chamber of an internal combustion engine, in particular a common rail injector, according to the preamble of claim 1.

Ein derartiger Injektor ist aus der EP 0 740 068 A2 bekannt. Ein derartiger Injektor hat den Vorteil, dass die Ventilhülse mit ihrem Außendurchmesser axial verschieblich in einem Führungselement geführt ist, welches als von dem Ventilstück separates Bauteil ausgebildet, jedoch an diesem anliegend ist. Dadurch kann das Führungselement erst nach der Fertigung des Ventilsitzes für die Ventilhülse am Ventilstück festgelegt werden, wodurch der Ventilsitz in üblicher Weise herstellbar ist. Zusätzliche weitere Vorteile liegen in der relativ einfachen Herstellbarkeit des Führungselementes sowie in einer relativ hohen Festigkeit des Ventilstückes.Such an injector is from the EP 0 740 068 A2 known. Such an injector has the advantage that the valve sleeve is guided with its outer diameter axially displaceable in a guide element, which is designed as a separate component from the valve member, but is adjacent to this. As a result, the guide element can be set only after the manufacture of the valve seat for the valve sleeve on the valve piece, whereby the valve seat can be produced in the usual manner. Additional further advantages are the relatively simple manufacturability of the guide element and in a relatively high strength of the valve piece.

Offenbarung der ErfindungDisclosure of the invention

Ausgehend von dem dargestellten Stand der Technik liegt der Erfindung die Aufgabe zugrunde, einen Injektor nach dem Oberbegriff des Anspruchs 1 derart weiterzubilden, dass eine weitere Vereinfachung des Herstellungsprozesses ermöglicht wird. Diese Aufgabe wird bei einem Injektor mit den Merkmalen des Anspruchs 1 gelöst. Durch das erfindungsgemäße Vorsehen einer Hülse können dabei insbesondere Fertigungsschwankungen der Ventilhülse und des Ventilstücks ausgeglichen werden bzw. diese Bauteile können mit größeren Toleranzen gefertigt werden.Starting from the illustrated prior art, the invention has the object, an injector according to the preamble of claim 1 such that a further simplification of the manufacturing process is made possible. This object is achieved in an injector with the features of claim 1. By providing a sleeve according to the invention, in particular manufacturing fluctuations of the valve sleeve and the valve piece can be compensated or these components can be manufactured with larger tolerances.

Vorteilhafte Weiterbildungen des erfindungsgemäßen Injektors sind in den Unteransprüchen angegeben. In den Rahmen der Erfindung fallen sämtliche Kombinationen aus zumindest zwei von in den Ansprüchen, der Beschreibung und/oder den Figuren offenbarten Merkmalen.Advantageous developments of the injector according to the invention are specified in the subclaims. All combinations of at least two of the features disclosed in the claims, the description and / or the figures fall within the scope of the invention.

In Ausgestaltung der Erfindung ist mit Vorteil vorgesehen, dass das Führungselement an dem Ventilstück mittels einer Presspassung festgelegt ist. Diese Ausfuhrungsform kommt mit. Vorteil ohne zusätzliche Befestigungsmittel aus. Diese Art der Befestigung eignet sich insbesondere für ein hülsenförmig (rohrförmig) ausgebildetes Führungselement, welches in axialer Richtung auf das Ventilstück aufgepresst wird. Dabei ist es von Vorteil, wenn das Führungselement zumindest im Bereich der Presspassung in radialer Richtung elastisch verformbar ist, um die Klemmwirkung zu verbessern.In an embodiment of the invention is advantageously provided that the guide element is fixed to the valve piece by means of a press fit. This embodiment comes along. Advantage without additional fasteners. This type of attachment is particularly suitable for a sleeve-shaped (tubular) formed guide element, which is pressed in the axial direction on the valve piece. It is advantageous if the guide element is elastically deformable in the radial direction, at least in the region of the press fit, in order to improve the clamping effect.

Um einen optimalen Halt des Führungselementes an dem Ventilstück zu gewährleisten, ist in Ausgestaltung der Erfindung vorgesehen, dass das Führungselement an einem, insbesondere leicht konischen Abschnitt des Ventilstücks festgelegt ist. Zur Erzielung einer Presspassung ist es von Vorteil, wenn der Konuswinkel eines entsprechenden Innenkonus des Führungselementes vor dessen Befestigung an den konischen Abschnitt, insbesondere geringfügig kleiner ist als der Konuswinkel des konischen Abschnitt des Ventilstücks. Bevorzugt ist die Presspassung als sogenannte Morsekegelpassung, wie sie beispielsweise zur Festlegung von Werkzeugen an Schäften bekannt ist, ausgebildet.In order to ensure optimum hold of the guide element on the valve piece, it is provided in an embodiment of the invention that the guide element is fixed to a, in particular slightly conical portion of the valve piece. To achieve a press fit, it is of Advantage, when the cone angle of a corresponding inner cone of the guide element before its attachment to the conical portion, in particular slightly smaller than the cone angle of the conical portion of the valve piece. Preferably, the press fit as a so-called Morsekegelpassung, as it is known, for example, for the determination of tools on shafts, formed.

Wie bereits erläutert, ist der Konuswinkel (Winkel zwischen der Symmetrieachse des konischen Abschnitts und der schrägen Mantelfläche des konischen Abschnitts) des konischen Abschnitts des Ventilstückes klein, insbesondere sehr klein, bevorzugt ist der Konuswinkel kleiner als etwa 10°, insbesondere kleiner als etwa 5°. Besonders bevorzugt liegt der Konuswinkel des konischen Abschnitts in einem Bereich zwischen etwa 0,5° und etwa 2,5°. Dabei ist der Winkel (Winkel zwischen der Symmetrieachse des Innenkonus und der schrägen inneren Mantelfläche des Innenkonus) des Innenkonus des Führungselementes mit Vorteil etwa um 0,1° bis etwa 1,5°, vorzugsweise um etwa 0,25° bis etwa 0,75° kleiner als der Konuswinkel des konischen Abschnittes des Ventilstückes.As already explained, the cone angle (angle between the axis of symmetry of the conical portion and the oblique lateral surface of the conical portion) of the conical portion of the valve piece is small, in particular very small, preferably the cone angle is less than about 10 °, in particular less than about 5 ° , Particularly preferably, the cone angle of the conical section is in a range between about 0.5 ° and about 2.5 °. The angle (angle between the axis of symmetry of the inner cone and the oblique inner lateral surface of the inner cone) of the inner cone of the guide element is advantageously about 0.1 ° to about 1.5 °, preferably about 0.25 ° to about 0.75 ° smaller than the cone angle of the conical section of the valve piece.

Fertigungstechnisch ist eine Ausführungsform von Vorteil, bei der Ventilsitz am Ventilstück unmittelbar benachbart zu dem konischen Abschnitt des Ventilstücks angeordnet ist, an dem das Führungselement festgelegt ist. Bevorzugt ist der Ventilsitz als konvexer Kegelsitz ausgebildet, wobei der Winkel der Kegelfläche wesentlich flacher ist, als der Winkel des konischen Abschnitts zur Festlegung des Ventilstücks. Daneben ist es denkbar, den Ventilsitz als Flachsitz, oder sogar als konkaven Kegelsitz auszubilden.In terms of production technology, an embodiment is advantageous in which the valve seat is arranged on the valve piece directly adjacent to the conical portion of the valve piece on which the guide element is fixed. Preferably, the valve seat is formed as a convex conical seat, wherein the angle of the conical surface is substantially flatter than the angle of the conical portion for fixing the valve piece. In addition, it is conceivable to design the valve seat as a flat seat, or even as a concave conical seat.

Zur Realisierung der Presspassung zwischen dem Führungselement und dem Ventilstück gibt es verschiedene Möglichkeiten. Gemäß einer ersten Variante ist vorgesehen, dass das Führungselement mit einer durchgehenden Kontaktfläche an dem Ventilstück, insbesondere an dem konischen Abschnitt des Ventilstücks anliegt.There are various possibilities for realizing the interference fit between the guide element and the valve piece. According to a first variant it is provided that the guide element rests with a continuous contact surface on the valve piece, in particular on the conical portion of the valve piece.

Alternativ dazu ist es denkbar, dass die Kontaktfläche, insbesondere ringförmig unterbrochen ist, vorzugsweise durch eine Freistellung, also einen nicht kontaktierenden Bereich am Führungselement und/oder am Ventilstück. Bei dieser Ausführungsform sind zwei, insbesondere ringförmige, in axialer Richtung durch die Freistellung beabstandete Kontaktbereiche zwischen dem Führungselement und dem Ventilstück ausgebildet, wodurch die Klemmwirkung noch verbessert werden kann.Alternatively, it is conceivable that the contact surface, in particular annularly interrupted, preferably by an exemption, so a non-contacting area on the guide element and / or on the valve piece. In this embodiment, two, in particular annular, in the axial direction by the clearance spaced contact areas between the guide member and the valve piece are formed, whereby the clamping action can be improved.

Damit bei geöffnetem Steuerventil, also bei angehobener Ventilhülse die aus der Steuerkammer nachströmende Kraftstoffmenge (Steuermenge) frei in Richtung des Niederdruckbereichs des Injektors abströmen kann, muss ein Abströmungskanal aus dem Kraftstoffvolumen innerhalb der Ventilhülse bereitgestellt werden. Hierzu ist es von Vorteil in dem Führungselement mindestens eine Querbohrung vorzusehen. Dabei muss die Querbohrung nicht zwangsweise orthogonal zur Längsmittelachse der Ventilhülse verlaufen, sondern kann auch schräg angeordnet sein. Zusätzlich oder alternativ ist es denkbar, die Ventilhülse an ihrem Außenumfang und/oder das Führungselement an seinem Innenumfang mit mindestens einem Flächenanschliff zur Bildung eines axialen Abströmkanals auszustatten. Ebenso ist es möglich eine Abströmbohrung oder ein Abströmkanal am Ventilstück vorzusehen, über die bzw. den die Steuermenge, insbesondere nach unten, unterhalb des Führungselementes hindurch nach außen in den Niederdruckbereich fließen kann.In order for the fuel quantity (control quantity) flowing out of the control chamber to be able to flow freely in the direction of the low-pressure region of the injector when the control valve is open, ie when the valve sleeve is raised, an outflow channel has to be provided from the fuel volume within the valve sleeve. For this purpose, it is advantageous to provide at least one transverse bore in the guide element. In this case, the transverse bore does not necessarily extend orthogonally to the longitudinal center axis of the valve sleeve, but may also be arranged obliquely. Additionally or alternatively, it is conceivable to equip the valve sleeve on its outer circumference and / or the guide element on its inner periphery with at least one Flächenanschliff to form an axial outflow channel. Likewise, it is possible to provide an outlet bore or a discharge channel on the valve piece, via which or the control quantity, in particular down, below the guide element can flow through the outside in the low pressure area.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Weitere Vorteile, Merkmale und Einzelheiten der Erfindung ergeben sich aus der nachfolgenden Beschreibung bevorzugter Ausführungsbeispiele sowie anhand der Zeichnungen; diese zeigen in:

Fig. 1:
eine stark schematisierte Teilansicht eines als Common-Rail-Injektor ausgebildeten Injektors und
Fig. 2:
eine alternative Ausführungsform eines Injektors in einer ebenfalls stark schematisierten Teilansicht.
Further advantages, features and details of the invention will become apparent from the following description of preferred embodiments and from the drawings; these show in:
Fig. 1:
a highly schematic partial view of a trained as a common rail injector injector and
Fig. 2:
an alternative embodiment of an injector in a likewise highly schematic partial view.

Ausführungsformen der ErfindungEmbodiments of the invention

In den Figuren sind gleiche Bauteile und Bauteile mit der gleichen Funktion mit den gleichen Bezugszeichen gekennzeichnet.In the figures, the same components and components with the same function with the same reference numerals.

In Fig. 1 ist stark schematisiert ein Ausschnitt eines als Common-Rail-Injektor ausgebildeten Injektors 1 zum Einspritzen von Kraftstoff in einen nicht gezeigten Brennraum einer Brennkraftmaschine gezeigt. Fig. 1 soll lediglich die Funktionsweise des Injektors erläutern, wobei die gezeigten Größenverhältnisse nicht den realen Größenverhältnissen entsprechen.In Fig. 1 is a highly schematic section of a trained as a common rail injector injector 1 for injecting fuel in a combustion chamber, not shown, of an internal combustion engine shown. Fig. 1 is intended to explain only the operation of the injector, wherein the proportions shown do not correspond to the real size ratios.

Der Injektor 1 umfasst ein lediglich ausschnittsweise dargestelltes, ein- oder mehrteiliges Ventilelement 2, das zwischen einer Öffnungsstellung und einer Schließstellung verstellbar ist. In seiner Öffnungsstellung (in der Zeichnungsebene nach oben verstellt) gibt das Ventilelement 2 den Kraftstofffluss aus einem Druckraum 3 durch eine nicht gezeigte Düsenlochanordnung in den Brennraum einer Brennkraftmaschine frei.The injector 1 comprises a single-part or multi-part valve element 2 which is shown only in sections and which is adjustable between an open position and a closed position. In its open position (adjusted upward in the plane of the drawing), the valve element 2 releases the fuel flow from a pressure chamber 3 through a nozzle hole arrangement, not shown, into the combustion chamber of an internal combustion engine.

Mit einer oberen Stirnfläche 4 begrenzt das Ventilelement 2 eine Steuerkammer 5. Diese ist radial innerhalb eines in den Druckraum 3 hineinragenden, hülsenförmigen Abschnitts eines Ventilstückes 6 angeordnet.With an upper end face 4, the valve element 2 delimits a control chamber 5. The latter is arranged radially inside a sleeve-shaped section of a valve piece 6 projecting into the pressure space 3.

In die Steuerkammer 5 mündet eine in den hülsenförmigen Abschnitt des Ventilstückes 6 eingebrachte Zulaufdrossel 7, über die die Steuerkammer 5 mit Kraftstoff aus dem Druckraum 3 versorgt wird. Der Druckraum 3 wird wiederum von einer Kraftstoffversorgungsleitung 8 mit unter Hochdruck stehendem Kraftstoff aus einem Kraftstoffhochdruckspeicher 9 (Rail) versorgt. Dieser wird von einer, insbesondere als Radialkolbenpumpe ausgebildeten Hochdruckpumpe 10 mit Kraftstoff aus einem auf Niederdruck liegenden Vorratsbehälter 11 versorgt. In den Vorratsbehälter 11 strömt auch eine später noch zu erläuternde Steuermenge an Kraftstoff aus einem Niederdruckbereich 12 des Injektors über einen Injektorrücklauf 13.In the control chamber 5 opens a introduced into the sleeve-shaped portion of the valve piece 6 inlet throttle 7, via which the control chamber 5 is supplied with fuel from the pressure chamber 3. The pressure chamber 3 is in turn supplied by a fuel supply line 8 under high pressure fuel from a high-pressure fuel storage 9 (Rail). This is powered by a, in particular designed as a radial piston pump high-pressure pump 10 with fuel from a low-pressure reservoir 11. In the reservoir 11 also flows later to be explained control amount of fuel from a low pressure region 12 of the injector via an injector return 13th

Aus der Steuerkammer 5 mündet ein in axialer Richtung in das Ventilstück 6 eingebrachter Ablaufkanal 14 aus. Dieser ist mit einer Ablaufdrossel 15 versehen, oder als solche ausgebildet. Der Ablaufkanal 14 verbreitet sich in seinem in der Zeichnungsebene oberen Abschnitt und mündet in eine Ventilkammer 16, die radial außen von dem Ventilstück 6 sowie von einer in axialer Richtung daran angrenzenden Ventilhülse 17 eines Steuerventils 18 (Servoventil) begrenzt wird. In axialer Richtung nach oben wird die Ventilkammer 16 des Steuerventils 18 von einem axial verschieblich gelagerten Druckstift 19 begrenzt, der von innerhalb der Ventilkammer 16 befindlichem Kraftstoff in axialer Richtung in der Zeichnungsebene nach oben gegen einen Ablaufstutzen 36 gepresst wird. Hierzu durchsetzt der Druckstift 19 eine Bohrung 37 in einen Haltekörper 20 einer Elektromagnetanordnung 21. In seinem in der Zeichnungsebene oberen Bereich ist der Druckstift 19 von einer Hülse 22 geführt, die von einer Schließfeder 23, die sich an einer einstückig mit der Ventilhülse 17 ausgebildeten Ankerplatte 24 abstützt, gegen den Ablaufstutzen 36 federkraftbeaufschlagt wird. Die Schließfeder 23 beaufschlagt gleichzeitig die Ankerplatte 24 und damit die Ventilhülse mit einer Federkraft in axialer Richtung in der Zeichnungsebene nach unten auf einen am Ventilstück 6 ausgebildeten, als Kegelsitz ausgeformten Ventilsitz 25 des Steuerventils 18. Alternativ stützt sich die Schließfeder an einer Ringschulter des Haltekörpers 20 der Elektromagnetanordnung 21 ab.From the control chamber 5 opens an inserted in the axial direction in the valve piece 6 drain channel 14. This is provided with an outlet throttle 15, or designed as such. The drainage channel 14 spreads in his in the plane of the drawing upper portion and terminates in a valve chamber 16 which is bounded radially outwardly by the valve piece 6 and by a valve sleeve 17 adjacent thereto in the axial direction of a control valve 18 (servo valve). In the axial upward direction, the valve chamber 16 of the control valve 18 is delimited by an axially displaceably mounted pressure pin 19, which is pressed by befindlichem within the valve chamber 16 fuel in the axial direction in the plane up against a drain pipe 36. For this purpose, the pressure pin 19 passes through a bore 37 in a holding body 20 of an electromagnet assembly 21. In its upper plane in the drawing area of the pressure pin 19 is guided by a sleeve 22, by a closing spring 23 which is formed on an integrally formed with the valve sleeve 17 anchor plate 24 is supported, is spring-loaded against the outlet nozzle 36. The closing spring 23 acts simultaneously on the armature plate 24 and thus the valve sleeve with a spring force in the axial direction in the plane down to a formed on the valve piece 6, formed as a conical seat valve seat 25 of the control valve 18. Alternatively, the closing spring is supported on an annular shoulder of the holding body 20th the solenoid assembly 21 from.

Aufgrund der Tatsache, dass die Ventilhülse 17 keine in axialer Richtung wirkende Druckangriffsfläche für Kraftstoff innerhalb der Ventilkammer aufweist, handelt es sich bei dem Steuerventil 18 um ein in axialer Richtung druckausgeglichenes Servoventil.Due to the fact that the valve sleeve 17 has no axially acting pressure application surface for fuel within the valve chamber, the control valve 18 is a servo-pressure-balanced in the axial direction servo valve.

Zur Führung der Ventilhülse 17 an ihrem Außenumfang ist ein hohlzylindrisches, hülsenförmiges Führungselement 26 vorgesehen. Das Führungselement 26 ist mittels einer Presspassung an einem konischen Abschnitt 27 des Ventilstücks 6 festgelegt, wobei ein äußerer Konuswinkel α des konischen Abschnittes 27 aus Veranschaulichungsgründen wesentlich größer dargestellt ist, als dieser in der Realität bevorzugt ausgebildet ist. In der Realität beträgt der Konuswinkel α zwischen einer Konusfläche 28 und einer zur Längsmittelachse L des Steuerventils 18 parallelen Achse in diesem Ausführungsbeispiel etwa 1°.To guide the valve sleeve 17 on its outer periphery is a hollow cylindrical, sleeve-shaped guide member 26th intended. The guide member 26 is fixed by means of a press fit to a conical portion 27 of the valve piece 6, wherein an outer cone angle α of the conical portion 27 is shown for reasons of illustration much larger than this is preferably formed in reality. In reality, the cone angle α between a conical surface 28 and an axis parallel to the longitudinal central axis L of the control valve 18 in this embodiment is about 1 °.

Die dem konischen Abschnitt 27 abgewandte Stirnseite 29 des Führungselementes 26 ist mit Axialabstand zur Unterseite der Ankerplatte 24 angeordnet. Wie aus Fig. 1 zu erkennen ist, ist der Ventilsitz 25 radial innerhalb des konischen Abschnittes 27 bzw. der Konusfläche 28 (Kegelfläche) angeordnet.The conical portion 27 facing away from end face 29 of the guide member 26 is arranged at an axial distance to the underside of the anchor plate 24. How out Fig. 1 can be seen, the valve seat 25 is disposed radially within the conical portion 27 and the conical surface 28 (conical surface).

Das Führungselement 26 ist mittels einer Presspassung an dem konischen Abschnitt 27 des Ventilstückes 26 festgelegt. Ein Konuswinkel β eines Innenkonus 30 beträgt wie der Konuswinkel α des konusförmigen Abschnittes 27 des Ventilstückes 6 im montierten Zustand ebenfalls 1°. Vor der Montage ist der Konuswinkel β des Innenkonus 30 jedoch etwas kleiner als der Konuswinkel α. Bei dem Aufpressen des Führungselementes 26 auf den konischen Abschnitt 27 wird der Innenkonus in radialer Richtung nach außen elastisch aufgeweitet, um die Klemmwirkung zu verbessern. Bei der gezeigten kraftschlüssigen Verbindung zwischen dem Führungselement 26 und dem konusförmigen Abschnitt 27 des Ventilstückes 6 handelt es sich um eine Art Morsekegelpassung.The guide element 26 is fixed by means of a press fit to the conical portion 27 of the valve piece 26. A cone angle β of an inner cone 30 is like the cone angle α of the conical portion 27 of the valve member 6 in the mounted state also 1 °. Before assembly, however, the cone angle β of the inner cone 30 is slightly smaller than the cone angle α. When the guide element 26 is pressed onto the conical section 27, the inner cone is expanded elastically outward in the radial direction in order to improve the clamping effect. In the illustrated non-positive connection between the guide member 26 and the conical portion 27 of the valve member 6 is a kind Morsekegelpassung.

In das Führungselement 26 sind zwei gegenüberliegende auf Höhe des Ventilsitzes 25 angeordnete, leicht schräg verlaufende Querbohrungen 31, 32 eingebracht, durch die Kraftstoff aus der Ventilkammer 16 bei von dem Ventilsitz 25 abgehobener Ventilhülse 17 des Steuerventils 18 in den das Führungselement 26 umgebenden Niederdruckbereich 12 des Injektors strömen kann. Aus dem Niederdruckbereich 12 kann der Kraftstoff durch den Injektorrücklauf 13 zu dem Vorratsbehälter 11 strömen.In the guide member 26 has two opposite arranged at the level of the valve seat 25, slightly inclined transverse bores 31, 32 introduced by the fuel from the valve chamber 16 at the valve seat 25 lifted valve sleeve 17 of the control valve 18 in the guide member 26 surrounding the low pressure region 12 of the Injector can flow. From the low-pressure region 12, the fuel can flow through the injector return 13 to the reservoir 11.

Zum Öffnen des Ventilelements 2 muss der Druck in der Steuerkammer 5 abgesenkt werden. Hierzu wird die Ventilhülse 17 aus der in Fig. 1 gezeigten Position durch Bestromung der Elektromagnetanordnung 21 in der Zeichnungsebene nach oben verstellt, so dass Kraftstoff über den in den konischen Abschnitt 27 eingebrachten, zentrischen Ablaufkanal 14 in die Ventilkammer 16 und von dort aus unterhalb der Ventilhülse in radialer Richtung und durch die Querbohrungen 31, 32 hindurch in den Niederdruckbereich 12 und von dort aus zum Injektorrücklauf 13 strömen kann.To open the valve element 2, the pressure in the control chamber 5 must be lowered. For this purpose, the valve sleeve 17 from the in Fig. 1 shown displaced position by energizing the solenoid assembly 21 in the plane of the drawing so that fuel via the introduced into the conical section 27, central drain passage 14 into the valve chamber 16 and from there below the valve sleeve in the radial direction and through the transverse bores 31, 32nd through into the low-pressure region 12 and from there to the injector return 13 can flow.

Zusätzlich oder Alternativ zur Ausbildung einer Ablaufdrossel 15 im Ablaufkanal 14 können die Querbohrungen 31, 32 selbst als Ablaufdrosseln ausgebildet werden.In addition or as an alternative to the formation of a discharge throttle 15 in the discharge channel 14, the transverse bores 31, 32 themselves can be formed as discharge throttles.

Da der Durchflussquerschnitt der Ablaufdrossel 15 größer ist als der Durchflussquerschnitt der Zulaufdrossel 7 resultiert bei geöffnetem Steuerventil 18 ein Nettoabfluss von Kraftstoff aus der Steuerkammer 5, wodurch die auf das Ventilelement 2 wirkende Schließkraft reduziert wird und das Ventilelement 2 von seinem nicht gezeigten Ventilsitz abhebt und den Kraftstofffluss freigibt. Zum Schließen des Ventilelementes 2 wird die Bestromung der Elektromagnetanordnung 21 unterbrochen, wodurch die Ventilhülse 17 federkraftunterstützt durch die Schließfeder 23 in axialer Richtung nach unten auf ihren Ventilsitz 25 bewegt wird, so dass kein Kraftstoff mehr aus der Ventilkammer 16 in den Niederdruckbereich abströmen kann. Durch den weiterhin durch die Zulaufdrossel 7 in die Steuerkammer 5 strömenden Kraftstoff steigt der Druck in der Steuerkammer 5 und somit die auf das Ventilelement 2 wirkende Schließkraft.Since the flow cross section of the outlet throttle 15 is greater than the flow cross section of the inlet throttle 7 results in open control valve 18, a net outflow of fuel from the control chamber 5, whereby the force acting on the valve element 2 closing force is reduced and the valve element 2 lifts from its valve seat, not shown, and the Fuel flow releases. To close the Valve element 2, the energization of the solenoid assembly 21 is interrupted, whereby the valve sleeve 17 is spring assisted by the closing spring 23 in the axial direction down to its valve seat 25 is moved, so that no more fuel can flow out of the valve chamber 16 in the low pressure region. By continuing to flow through the inlet throttle 7 in the control chamber 5 fuel increases the pressure in the control chamber 5 and thus acting on the valve element 2 closing force.

Die in Fig. 2 dargestellte Ausführungsform eines Injektors 1 entspricht im Wesentlichen der Ausführungsform gemäß Fig. 1, so dass zur Vermeidung von Wiederholungen im Folgenden nur auf die Unterschiede eingegangen wird. Bezüglich der Gemeinsamkeiten wird auf die vorangehende Figurenbeschreibung verwiesen.In the Fig. 2 illustrated embodiment of an injector 1 substantially corresponds to the embodiment according to Fig. 1 so that to avoid repetition in the following, only the differences will be discussed. With regard to the similarities, reference is made to the preceding description of the figures.

Der einzige Unterschied zu dem Ausführungsbeispiel gemäß Fig. 1 besteht darin, dass die Presspassung zwischen dem Führungselement 26 und dem konischen Abschnitt 27 des Ventilstückes 6 unterschiedlich realisiert ist. In den Innenkonus 30 des Führungselementes 26 ist eine ringförmige Freistellung 33 eingebracht, so dass das Führungselement an zwei in axialer Richtung beabstandeten Kontaktflächen 34, 35 an den konischen Abschnitt 27 des Ventilstückes 6 anliegt. Hierdurch kann die Klemmwirkung zwischen dem Führungselement 26 und dem Ventilstück 6 weiter verbessert werden.The only difference from the embodiment according to Fig. 1 is that the interference fit between the guide member 26 and the conical portion 27 of the valve member 6 is realized differently. In the inner cone 30 of the guide member 26, an annular release position 33 is introduced, so that the guide element rests against two axially spaced contact surfaces 34, 35 to the conical portion 27 of the valve member 6. Thereby, the clamping action between the guide member 26 and the valve member 6 can be further improved.

Anstelle von den gezeigten Querbohrungen 31, 32 im Führungselement 26 können zur Ableitung von Kraftstoff aus der Ventilkammer 16 bei geöffnetem Steuerventil 18, bevorzugt in axialer Richtung verlaufende Flächenanschliffe am Außenumfang der Ventilhülse 17 und/oder am Innenumfang des Führungselementes 26 vorgesehen werden.Instead of the illustrated transverse bores 31, 32 in the guide element 26, for discharging fuel from the valve chamber 16 when the control valve 18 is open, Preferably in the axial direction extending Flächenanschliffe be provided on the outer circumference of the valve sleeve 17 and / or on the inner circumference of the guide member 26.

Claims (9)

  1. Injector for injecting fuel into a combustion chamber of an internal combustion engine, in particular common rail injector, having a control valve (18) which has guided on its outer circumference an axially adjustable valve sleeve (17), by means of which valve sleeve (17) the fuel flows through an outflow duct (14), which is formed in a valve piece (6), in the direction of the low-pressure region (12) of the injector (1) from a control chamber (5) operatively connected to an axially adjustable valve element (2) can be enabled and shut off, with a valve seat (25) of the valve sleeve (17) being formed on the valve piece (6), with the valve sleeve (17) being guided, on its outer circumference, by a guide element (26) which is formed as a component separate from the valve piece (6), and with the guide element (26) bearing against the valve piece (6), characterized in that the guide element (26) is formed as an in particular cylindrical sleeve whose inner diameter corresponds to the outer diameter of the valve sleeve (17) plus a guide play.
  2. Injector according to Claim 1,
    characterized
    in that the guide element (26) is fixed to the valve piece (6) by means of an interference fit.
  3. Injector according to one of the preceding claims,
    characterized
    in that the guide element (26) is fixed to a conical section (27) of the valve piece (6).
  4. Injector according to Claim 3,
    characterized
    in that a cone angle (β) of an internal cone (30) of the guide element (26) is in particular slightly smaller than the cone angle (α) of the conical section (27) of the valve piece.
  5. Injector according to one of Claims 3 or 4,
    characterized
    in that the conical section (27) of the valve piece (6) has a cone angle (α) in a range between approximately 0.5° and approximately 10°, preferably of less than 7°, preferably of less than 5°, in particular of less than 3°, particularly preferably of less than 2°, particularly preferably of approximately 1°.
  6. Injector according to one of Claims 3 to 5,
    characterized
    in that a valve seat (25) of the valve sleeve (17) is formed radially within the conical section (27).
  7. Injector according to one of the preceding claims,
    characterized
    in that the guide element (26) bears areally against the valve piece (6) in the region of contact with the latter.
  8. Injector according to one of Claims 1 to 6,
    characterized
    in that an in particular annular recess (33) is provided on the guide element (26) and/or on the valve piece (6) in the region of contact between the guide element (26) and the valve piece (6).
  9. Injector according to one of the preceding claims,
    characterized
    in that a transverse bore (31, 32) for discharging fuel out of the outflow duct (14) into the low-pressure region (12) is formed in the guide element (26).
EP08736615A 2007-05-14 2008-04-29 Injector Not-in-force EP2156045B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102007022586A DE102007022586A1 (en) 2007-05-14 2007-05-14 injector
PCT/EP2008/055206 WO2008138743A1 (en) 2007-05-14 2008-04-29 Injector

Publications (2)

Publication Number Publication Date
EP2156045A1 EP2156045A1 (en) 2010-02-24
EP2156045B1 true EP2156045B1 (en) 2010-11-24

Family

ID=39811713

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08736615A Not-in-force EP2156045B1 (en) 2007-05-14 2008-04-29 Injector

Country Status (6)

Country Link
EP (1) EP2156045B1 (en)
CN (1) CN101680405B (en)
AT (1) ATE489551T1 (en)
DE (2) DE102007022586A1 (en)
RU (1) RU2469206C2 (en)
WO (1) WO2008138743A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007044356A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh injector
DE102007044362A1 (en) 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector
DE102007044361A1 (en) 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector
DE102014226258A1 (en) * 2014-12-17 2016-06-23 Robert Bosch Gmbh fuel injector

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD122574A1 (en) * 1975-10-24 1976-10-12 Karl Marx Stadt Automobilbau
FR2580728B1 (en) * 1985-04-19 1989-05-05 Alsacienne Constr Meca FUEL INJECTION SYSTEM FOR DIESEL ENGINE
JPH0286953A (en) * 1988-09-21 1990-03-27 Kanesaka Gijutsu Kenkyusho:Kk Fuel injection valve
US5191867A (en) * 1991-10-11 1993-03-09 Caterpillar Inc. Hydraulically-actuated electronically-controlled unit injector fuel system having variable control of actuating fluid pressure
GB9508623D0 (en) * 1995-04-28 1995-06-14 Lucas Ind Plc "Fuel injection nozzle"
DE19650900A1 (en) * 1996-12-07 1998-06-10 Bosch Gmbh Robert Piezoelectric actuator
IT1289794B1 (en) * 1996-12-23 1998-10-16 Elasis Sistema Ricerca Fiat IMPROVEMENTS TO AN ELECTROMAGNETICALLY OPERATED DOSING VALVE FOR A FUEL INJECTOR.
ES2277229T3 (en) 2004-06-30 2007-07-01 C.R.F. Societa Consortile Per Azioni SERVOVALVULA TO CONTROL THE FUEL INJECTOR OF AN INTERNAL COMBUSTION ENGINE.
DE102006055548A1 (en) * 2006-11-24 2008-05-29 Robert Bosch Gmbh fuel injector

Also Published As

Publication number Publication date
RU2469206C2 (en) 2012-12-10
RU2009146123A (en) 2011-06-20
EP2156045A1 (en) 2010-02-24
WO2008138743A1 (en) 2008-11-20
ATE489551T1 (en) 2010-12-15
DE102007022586A1 (en) 2008-11-27
CN101680405B (en) 2012-03-21
CN101680405A (en) 2010-03-24
DE502008001904D1 (en) 2011-01-05

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