EP2438288B1 - Switching valve - Google Patents

Switching valve Download PDF

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Publication number
EP2438288B1
EP2438288B1 EP10713929.7A EP10713929A EP2438288B1 EP 2438288 B1 EP2438288 B1 EP 2438288B1 EP 10713929 A EP10713929 A EP 10713929A EP 2438288 B1 EP2438288 B1 EP 2438288B1
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EP
European Patent Office
Prior art keywords
valve
guide
seat
guide section
seat surface
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.)
Active
Application number
EP10713929.7A
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German (de)
French (fr)
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EP2438288A1 (en
Inventor
Wolfgang Stoecklein
Andreas Rettich
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2438288A1 publication Critical patent/EP2438288A1/en
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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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • 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
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • F02M63/0019—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means characterised by the arrangement of electromagnets or fixed armatures
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/003—Valve inserts containing control chamber and valve piston
    • 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
    • F02M63/0078—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 a switching valve, in particular a solenoid valve for fuel injection valves, and a fuel injection valve with such a switching valve.
  • the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.
  • a fuel injector with a pressure compensated control valve is known.
  • an injection valve member which opens or closes an injection port, is driven by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return by placing or releasing a closing element in a seat.
  • the hydraulic forces are minimized via a pressure compensation.
  • the spring force can be reduced with less stroke and larger cross-sectional area. As a result, short switching times and advantageous dynamics are possible.
  • the from the DE 10 2006 021 741 A1 known fuel injector has the disadvantage that it may come to a seat leakage due to a misalignment of an anchor and a lack of centering due to a formed flat seat. Furthermore, the control valve is relatively sensitive to particles, since the support effect is limited. In addition, the seat limitation can only be done via the anchor, with very small seat lengths with two functional edges, which also adversely affects the coating and particle impacts.
  • a switching valve according to the preamble of claim 1 is known from DE 102 007 009 165 known.
  • the switching valve according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 12 have the advantage that an operation is improved. Specifically, there is the advantage that a robust switching valve can be created, which is also suitable for high pressures.
  • the space into which the channel of the valve piece opens between the guide section and the sealing seat is formed at least partially in the guide opening.
  • a puncture is provided on the valve piece between the guide portion and the valve seat surface, and that the space into which opens the channel of the valve piece between the guide portion and the sealing seat, at least substantially predetermined by the puncture, wherein an inner wall of the guide opening bounded by the recess space.
  • the guide opening is designed as a guide bore, in particular as a continuous guide bore, and that at least the guide section of the valve piece is configured axially symmetrical to an axis of the guide bore.
  • a guide between the valve piece and the valve closing body is ensured, so that a leak on the sealing seat is prevented by misalignment of the valve closing body.
  • a relatively large guide play is predetermined between the guide section and the guide bore. In this way, a tensile load between the guide portion and the rest of the valve piece can be reduced. About the relatively large leadership game targeted leakage is possible.
  • a lateral bevel is provided on the guide section, on which a leakage gap is formed between the guide section and the guide bore.
  • About the leakage gap can also be a tensile load between the guide portion and the rest of the valve piece can be reduced.
  • the channel which opens into the space between the guide portion and the sealing seat, designed as a throttled channel.
  • the channel can be realized through the channel, in particular an outlet throttle.
  • valve closing body has a sealing edge which faces the valve seat surface, that the sealing seat between the sealing edge and the valve seat surface is formed and that a predetermined by the sealing edge seat diameter of the sealing seat is at least approximately equal to a diameter of the guide portion of the valve piece.
  • valve seat surface is designed as a conical valve seat surface and that an opening angle of the conical valve seat surface is selected from a range of about 80 ° to about 120 °.
  • sealing edge is configured on a conical end face of the valve closing body and that an opening angle of the conical end face is greater than the opening angle of the conical valve seat surface. This allows an advantageous centering effect of the valve closing body with respect to the valve seat surface of the valve piece. Thus, leakage at the sealing seat by misalignment or the like can be prevented.
  • a seat limitation may be mounted in or on the valve piece.
  • the seat diameter of the sealing seat is not greater than 2 mm, in particular approximately equal to 1.8 mm.
  • a relatively large leakage which may occur, for example, with a seat diameter of 2.5 mm, be prevented and a high pressure resistance for very high pressures, especially for pressures of more than 160 MPa (1600 bar), created.
  • Fig. 1 shows an embodiment of a fuel injection valve 1 with a switching valve 2 in a schematic, excerpt, axial sectional view.
  • the fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred use of the fuel injector 1 is for a fuel injection system having a fuel rail which supplies diesel fuel under high pressure to a plurality of fuel injectors 1.
  • the fuel injection valve according to the invention 1 and the switching valve 2 according to the invention are also suitable for other applications.
  • the switching valve 2 has a valve piece 3, on which a valve seat surface 4 is formed. Furthermore, the switching valve 2 has a valve closing body 5, which cooperates with the valve seat surface 4 to a sealing seat.
  • the valve closing body 5 is a part of an armature 6. In this case, the valve closing body 5 is formed integrally with the armature 6. However, the valve closing body 5 can also be connected to the armature 6.
  • a solenoid 8 is arranged, which serves to generate a magnetic field for actuating the valve closing body 5 of the armature 6 by means of the magnetic core 7. As a result, the sealing seat formed between the valve closing body 5 and the valve seat surface 4 can be opened and closed.
  • the armature 6 is in this case guided on a pressure pin 9, which is supported on a support element 10. Further, a valve spring 11 is provided, which is arranged between the support member 10 and the armature 6, to bias the armature 6 against a magnetic attraction of the magnetic core 7, which is controllable by a current through the magnetic coil 8. In this case, the force of the valve spring 11 influences the contact force of an edge 12 of the valve closing body 5 against the valve seat surface 4 when the sealing seat is closed.
  • valve piece 3 is inserted into a further housing part 13 of the fuel injection valve 1.
  • the valve member 3 is supported on a shoulder 14 of the housing part 13.
  • the valve piece 3 has a bore 15 in which a control chamber 16 is delimited by a valve piston 17.
  • In the control chamber 16 performs an inlet throttle 18, which connects the control chamber 16 with a high-pressure chamber 19 in the interior of the housing part 13.
  • the switching valve 2 has an axis 25, on which the armature 6 and the valve piece 3 are aligned.
  • the armature 6 is designed axially symmetrical to the axis 25.
  • the valve piece 3 is designed substantially axially symmetrical to the axis 25.
  • the valve piece 3 has a guide portion 26 which is guided in a guide bore 27 of the armature 6.
  • the guide bore 27 is configured here as a continuous guide bore 27.
  • In the guide bore 27 also extends the pressure pin 9 to guide the armature 6 on the pressure pin 9.
  • a recess 28 is provided on the valve piece 3.
  • a fuel chamber 29 is formed, which is bounded by an inner wall 30 of the guide bore 27 of the armature 6. The fuel room 29 is thus formed between the guide portion 26 and the valve seat surface 4.
  • the valve piece 3 has an axial blind bore 31, from which a channel 32 and a channel 33 branch off. About the blind bore 31 and the channels 32, 33 of the control chamber 16 is connected to the fuel chamber 29.
  • the channels 32, 33 are designed as throttled channels 32, 33.
  • the channels 32, 33 both open into the fuel chamber 29 between the guide portion 26 and the sealing seat, which is formed at the edge 12 between the valve closing body 5 and the valve seat surface 4.
  • the fuel space 29 is formed in the guide bore 27.
  • the edge 12 of the valve closing body 5 is designed as a sealing edge on which the sealing seat between the valve closing body 5 and the valve seat surface 4 comes about.
  • the sealing edge 12 faces the valve seat surface 4.
  • a diameter 34 of the sealing edge 12 is at least approximately the same size as a diameter 35 of the guide portion 26. This is in relation to the fuel chamber 29, a pressure equalization allows.
  • the diameter 34 is very small, so that a seat diameter of the sealing seat is also very small.
  • the diameter 34 and thus the seat diameter at the sealing edge 12 can not be greater than 2 mm, in particular approximately equal to 1.8 mm.
  • the armature 6 has an end face 36 which faces the valve seat surface 4 of the valve piece 3.
  • the sealing edge 12 is formed between the end face 36 and the inner wall 30 of the guide bore 27.
  • the conical valve seat surface 4 for example, has an opening angle which is equal to 90 °.
  • An opening angle of the conical end face 36 of the valve closing body 5 is greater than the opening angle of the conical valve seat surface 4, that is, in this embodiment, greater than 90 ° selected.
  • the opening angle of the conical valve seat surface 4 is determined by the required centering and may be in a range of less than 120 °. It is particularly advantageous if it is in a range of about 80 ° to about 120 °.
  • the opening angle the conical end face 36 of the valve closing body 5 is then selected to be greater than the opening angle of the conical valve seat surface 4.
  • the valve seat surface 4 is limited by a step 37. In this way, a maximum diameter 38 of the valve seat surface 4 can be predetermined for seat limitation.
  • the seat limitation can be attached to the valve member 3 through the step 37 or in other ways.
  • the guide section 26 is preferably made relatively short along the axis 25. This short guide section 26 essentially serves for centering during assembly. The leadership of the armature 6 via the pressure pin 9. The pressure forces from the seat diameter are preferably absorbed by the pressure pin 9. About the support member 10 thus takes place a support to a magnet group. In this case, the guide section 26 does not seal against the high pressure in the fuel chamber 29. This ensures that the valve member 3 in the region of the recess 28 and in particular at the mouths of the channels 32, 33 is not loaded on train and thus in this area no or only very small tensile stresses in the valve piece 3 occur. Here it is possible to provide a further strain relief.
  • a bevel 39 may be provided on one side of the guide section 26, which forms a leakage gap between the guide section 26 and the inner wall 30 of the guide bore 27.
  • the guide portion 26 in which no bevel 39 or the like is provided.
  • the guide portion 26 is thereby configured axially symmetrical to the axis 25. In this way, a certain amount of guidance can be achieved in order to achieve a reliable closing of the sealing seat between the sealing edge 12 and the valve seat surface 4. Specifically, a tilting between the valve closing body 5 and the valve member 3 is prevented or at least reduced, whereby a self-centering of the sealing edge 12 is supported on the conical valve seat surface 4.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Schaltventil, insbesondere ein Magnetventil für Brennstoffeinspritzventile, und ein Brennstoffeinspritzventil mit solch einem Schaltventil. Speziell betrifft die Erfindung das Gebiet der Injektoren für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen.The invention relates to a switching valve, in particular a solenoid valve for fuel injection valves, and a fuel injection valve with such a switching valve. Specifically, the invention relates to the field of injectors for fuel injection systems of air compressing, self-igniting internal combustion engines.

Aus der DE 10 2006 021 741 A1 ist ein Kraftstoffinjektor mit einem druckausgeglichenen Steuerventil bekannt. Bei dem bekannten Injektor wird ein Einspritzventilglied, welches eine Einspritzöffnung freigibt oder verschließt, durch ein Steuerventil angesteuert, wobei das Steuerventil eine Verbindung aus einem Steuerraum in einen Kraftstoffrücklauf freigibt oder verschließt, indem ein Schließelement in einen Sitz gestellt wird oder diesen freigibt. Bei dem Steuerventil werden die hydraulischen Kräfte über einen Druckausgleich minimiert. Dadurch kann die Federkraft bei gleichzeitig weniger Hub und größerer Querschnittsfläche reduziert werden. Hierdurch sind kurze Schaltzeiten und eine vorteilhafte Dynamik möglich.From the DE 10 2006 021 741 A1 For example, a fuel injector with a pressure compensated control valve is known. In the known injector, an injection valve member, which opens or closes an injection port, is driven by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return by placing or releasing a closing element in a seat. In the control valve, the hydraulic forces are minimized via a pressure compensation. As a result, the spring force can be reduced with less stroke and larger cross-sectional area. As a result, short switching times and advantageous dynamics are possible.

Der aus der DE 10 2006 021 741 A1 bekannte Kraftstoffinjektor hat den Nachteil, dass es durch eine Schiefstellung eines Ankers und eine fehlende Zentrierwirkung auf Grund eines gebildeten Flachsitzes zu einer Undichtheit am Sitz kommen kann. Ferner ist das Steuerventil relativ empfindlich gegenüber Partikel, da die Stützwirkung begrenzt ist. Außerdem kann die Sitzbegrenzung nur über den Anker erfolgen, wobei sehr kleine Sitzlängen mit zwei Funktionskanten bestehen, was sich auch beim Beschichten und bei Partikeleinschlägen nachteilig auswirkt.The from the DE 10 2006 021 741 A1 known fuel injector has the disadvantage that it may come to a seat leakage due to a misalignment of an anchor and a lack of centering due to a formed flat seat. Furthermore, the control valve is relatively sensitive to particles, since the support effect is limited. In addition, the seat limitation can only be done via the anchor, with very small seat lengths with two functional edges, which also adversely affects the coating and particle impacts.

Ein Schaltventil gemäß Oberbegriff der Anspruchs 1 ist aus der DE 102 007 009 165 bekannt.A switching valve according to the preamble of claim 1 is known from DE 102 007 009 165 known.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Schaltventil mit den Merkmalen des Anspruchs 1 und das erfindungsgemäße Brennstoffeinspritzventil mit den Merkmalen des Anspruchs 12 haben den Vorteil, dass eine Funktionsweise verbessert ist. Speziell besteht der Vorteil, dass ein robustes Schaltventil geschaffen werden kann, das auch für hohe Drücke geeignet ist.The switching valve according to the invention with the features of claim 1 and the fuel injection valve according to the invention with the features of claim 12 have the advantage that an operation is improved. Specifically, there is the advantage that a robust switching valve can be created, which is also suitable for high pressures.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen des im Anspruch 1 angegebenen Schaltventils und des im Anspruch 11 angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous refinements of the specified in claim 1 switching valve and the fuel injection valve specified in claim 11 are possible.

Vorteilhaft ist es, dass der Raum, in den der Kanal des Ventilstücks zwischen dem Führungsabschnitt und dem Dichtsitz mündet, zumindest teilweise in der Führungsöffnung ausgebildet ist. Hierbei ist es ferner vorteilhaft, dass an dem Ventilstück zwischen dem Führungsabschnitt und der Ventilsitzfläche ein Einstich vorgesehen ist, und dass der Raum, in den der Kanal des Ventilstücks zwischen dem Führungsabschnitt und dem Dichtsitz mündet, zumindest im Wesentlichen durch den Einstich vorgegeben ist, wobei eine Innenwand der Führungsöffnung den durch den Einstich vorgegebenen Raum begrenzt. Dadurch ist eine kompakte Ausgestaltung eines zumindest im Wesentlichen druckausgeglichenen Schaltventils möglich.It is advantageous that the space into which the channel of the valve piece opens between the guide section and the sealing seat is formed at least partially in the guide opening. In this case, it is further advantageous that a puncture is provided on the valve piece between the guide portion and the valve seat surface, and that the space into which opens the channel of the valve piece between the guide portion and the sealing seat, at least substantially predetermined by the puncture, wherein an inner wall of the guide opening bounded by the recess space. As a result, a compact embodiment of an at least substantially pressure balanced switching valve is possible.

Vorteilhaft ist es auch, dass die Führungsöffnung als Führungsbohrung, insbesondere als durchgehende Führungsbohrung, ausgestaltet ist, und dass zumindest der Führungsabschnitt des Ventilstücks axialsymmetrisch zu einer Achse der Führungsbohrung ausgestaltet ist. Hierdurch ist eine Führung zwischen dem Ventilstück und dem Ventilschließkörper gewährleistet, so dass eine Undichtigkeit am Dichtsitz durch Schiefstellung des Ventilschließkörpers verhindert ist. Hierbei ist es ferner vorteilhaft, dass zwischen dem Führungsabschnitt und der Führungsbohrung ein relativ großes Führungsspiel vorgegeben ist. Hierdurch kann eine Zugbelastung zwischen dem Führungsabschnitt und dem übrigen Ventilstück reduziert werden. Über das relativ große Führungsspiel ist eine gezielte Leckage möglich.It is also advantageous that the guide opening is designed as a guide bore, in particular as a continuous guide bore, and that at least the guide section of the valve piece is configured axially symmetrical to an axis of the guide bore. As a result, a guide between the valve piece and the valve closing body is ensured, so that a leak on the sealing seat is prevented by misalignment of the valve closing body. In this case, it is also advantageous that a relatively large guide play is predetermined between the guide section and the guide bore. In this way, a tensile load between the guide portion and the rest of the valve piece can be reduced. About the relatively large leadership game targeted leakage is possible.

Vorteilhaft ist es allerdings auch, dass an dem Führungsabschnitt ein seitlicher Anschliff vorgesehen ist, an dem zwischen dem Führungsabschnitt und der Führungsbohrung ein Leckagespalt ausgebildet ist. Über den Leckagespalt kann ebenfalls eine Zugbelastung zwischen dem Führungsabschnitt und dem übrigen Ventilstück verringert werden.However, it is also advantageous that a lateral bevel is provided on the guide section, on which a leakage gap is formed between the guide section and the guide bore. About the leakage gap can also be a tensile load between the guide portion and the rest of the valve piece can be reduced.

In vorteilhafter Weise ist der Kanal, der in den Raum zwischen dem Führungsabschnitt und dem Dichtsitz mündet, als gedrosselter Kanal ausgestaltet. Hierbei kann durch den Kanal, insbesondere eine Ablaufdrossel, realisiert werden.Advantageously, the channel, which opens into the space between the guide portion and the sealing seat, designed as a throttled channel. In this case, can be realized through the channel, in particular an outlet throttle.

Vorteilhaft ist es auch, dass der Ventilschließkörper eine Dichtkante aufweist, die der Ventilsitzfläche zugewandt ist, dass der Dichtsitz zwischen der Dichtkante und der Ventilsitzfläche gebildet ist und dass ein durch die Dichtkante vorgegebener Sitzdurchmesser des Dichtsitzes zumindest näherungsweise gleich groß ist wie ein Durchmesser des Führungsabschnitts des Ventilstücks. Hierdurch kann ein sehr kleiner Sitzdurchmesser realisiert werden, wobei eine ausreichende Hochdruckfestigkeit ermöglicht ist. Durch den kleinen Sitzdurchmesser kann eine zuverlässige Dichtheit des geschlossenen Dichtsitzes auch bei sehr hohen Drücken gewährleistet werden.It is also advantageous that the valve closing body has a sealing edge which faces the valve seat surface, that the sealing seat between the sealing edge and the valve seat surface is formed and that a predetermined by the sealing edge seat diameter of the sealing seat is at least approximately equal to a diameter of the guide portion of the valve piece. This allows a very small seat diameter can be realized, with a sufficient high-pressure resistance is possible. Due to the small seat diameter, a reliable tightness of the closed sealing seat can be ensured even at very high pressures.

Vorteilhaft ist es hierbei außerdem, dass die Ventilsitzfläche als konische Ventilsitzfläche ausgestaltet ist und dass ein Öffnungswinkel der konischen Ventilsitzfläche aus einem Bereich von etwa 80° bis etwa 120° gewählt ist. Hierbei ist es ferner vorteilhaft, dass die Dichtkante an einer konischen Stirnfläche des Ventilschließkörpers ausgestaltet ist und dass ein Öffnungswinkel der konischen Stirnfläche größer als der Öffnungswinkel der konischen Ventilsitzfläche ist. Dies ermöglicht eine vorteilhafte Zentrierwirkung des Ventilschließkörpers in Bezug auf die Ventilsitzfläche des Ventilstücks. Somit kann eine Undichtheit am Dichtsitz durch Schiefstellung oder dergleichen verhindert werden. Außerdem kann eine Sitzbegrenzung im oder am Ventilstück angebracht sein.It is also advantageous here that the valve seat surface is designed as a conical valve seat surface and that an opening angle of the conical valve seat surface is selected from a range of about 80 ° to about 120 °. Here, it is also advantageous that the sealing edge is configured on a conical end face of the valve closing body and that an opening angle of the conical end face is greater than the opening angle of the conical valve seat surface. This allows an advantageous centering effect of the valve closing body with respect to the valve seat surface of the valve piece. Thus, leakage at the sealing seat by misalignment or the like can be prevented. In addition, a seat limitation may be mounted in or on the valve piece.

Speziell ist es vorteilhaft, dass der Sitzdurchmesser des Dichtsitzes nicht größer als 2 mm, insbesondere näherungsweise gleich 1,8 mm, ist. Somit kann eine relativ große Leckage, die beispielsweise bei einem Sitzdurchmesser von 2,5 mm auftreten kann, verhindert werden und eine Hochdruckfestigkeit für sehr hohe Drücke, insbesondere für Drücke von mehr als 160 MPa (1600 bar), geschaffen werden.Specifically, it is advantageous that the seat diameter of the sealing seat is not greater than 2 mm, in particular approximately equal to 1.8 mm. Thus, a relatively large leakage, which may occur, for example, with a seat diameter of 2.5 mm, be prevented and a high pressure resistance for very high pressures, especially for pressures of more than 160 MPa (1600 bar), created.

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügte Zeichnung näher erläutert. ES zeigt:

  • Fig. 1 ein Schaltventil eines Brennstoffeinspritzventils in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings. It shows:
  • Fig. 1 a switching valve of a fuel injection valve in a partial, schematic sectional view according to an embodiment of the invention.

Fig. 1 zeigt ein Ausführungsbeispiel eines Brennstoffeinspritzventils 1 mit einem Schaltventil 2 in einer schematischen, auszugsweisen, axialen Schnittdarstellung. Das Brennstoffeinspritzventil 1 kann insbesondere als Injektor für Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen dienen. Ein bevorzugter Einsatz des Brennstoffeinspritzventils 1 besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, die Dieselbrennstoff unter hohem Druck zu mehreren Brennstoffeinspritzventilen 1 führt. Das erfindungsgemäße Brennstoffeinspritz-ventil 1 und das erfindungsgemäße Schaltventil 2 eignen sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows an embodiment of a fuel injection valve 1 with a switching valve 2 in a schematic, excerpt, axial sectional view. The fuel injection valve 1 can serve in particular as an injector for fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred use of the fuel injector 1 is for a fuel injection system having a fuel rail which supplies diesel fuel under high pressure to a plurality of fuel injectors 1. The fuel injection valve according to the invention 1 and the switching valve 2 according to the invention, however, are also suitable for other applications.

Das Schaltventil 2 weist ein Ventilstück 3 auf, an dem eine Ventilsitzfläche 4 ausgebildet ist. Ferner weist das Schaltventil 2 einen Ventilschließkörper 5 auf, der mit der Ventilsitzfläche 4 zu einem Dichtsitz zusammenwirkt. In diesem Ausführungsbeispiel ist der Ventilschließkörper 5 ein Teil eines Ankers 6. Dabei ist der Ventilschließkörper 5 einstückig mit dem Anker 6 ausgebildet. Der Ventilschließkörper 5 kann allerdings auch mit dem Anker 6 verbunden sein. In einem Magnetkern 7 des Brennstoffeinspritzventils 1 ist eine Magnetspule 8 angeordnet, die zum Erzeugen eines Magnetfelds zum Betätigen des Ventilschließkörpers 5 des Ankers 6 mittels des Magnetkerns 7 dient. Hierdurch kann der zwischen dem Ventilschließkörper 5 und der Ventilsitzfläche 4 gebildete Dichtsitz geöffnet und geschlossen werden. Der Anker 6 ist hierbei an einem Druckbolzen 9 geführt, der sich an einem Stützelement 10 abstützt. Ferner ist eine Ventilfeder 11 vorgesehen, die zwischen dem Stützelement 10 und dem Anker 6 angeordnet ist, um den Anker 6 entgegen einer magnetischen Anzugskraft des Magnetkerns 7, die durch einen Strom durch die Magnetspule 8 steuerbar ist, zu beaufschlagen. Die Kraft der Ventilfeder 11 beeinflusst hierbei die bei geschlossenem Dichtsitz wirkende Anlagekraft einer Kante 12 des Ventilschließkörpers 5 an der Ventilsitzfläche 4.The switching valve 2 has a valve piece 3, on which a valve seat surface 4 is formed. Furthermore, the switching valve 2 has a valve closing body 5, which cooperates with the valve seat surface 4 to a sealing seat. In this embodiment, the valve closing body 5 is a part of an armature 6. In this case, the valve closing body 5 is formed integrally with the armature 6. However, the valve closing body 5 can also be connected to the armature 6. In a magnetic core 7 of the fuel injection valve 1, a solenoid 8 is arranged, which serves to generate a magnetic field for actuating the valve closing body 5 of the armature 6 by means of the magnetic core 7. As a result, the sealing seat formed between the valve closing body 5 and the valve seat surface 4 can be opened and closed. The armature 6 is in this case guided on a pressure pin 9, which is supported on a support element 10. Further, a valve spring 11 is provided, which is arranged between the support member 10 and the armature 6, to bias the armature 6 against a magnetic attraction of the magnetic core 7, which is controllable by a current through the magnetic coil 8. In this case, the force of the valve spring 11 influences the contact force of an edge 12 of the valve closing body 5 against the valve seat surface 4 when the sealing seat is closed.

In diesem Ausführungsbeispiel ist das Ventilstück 3 in ein weiteres Gehäuseteil 13 des Brennstoffeinspritzventils 1 eingesetzt. Hierbei stützt sich das Ventilstück 3 an einem Absatz 14 des Gehäuseteils 13 ab. Das Ventilstück 3 weist eine Bohrung 15 auf, in der ein Steuerraum 16 durch einen Ventilkolben 17 begrenzt ist. In den Steuerraum 16 führt eine Zulaufdrossel 18, die den Steuerraum 16 mit einem Hochdruckraum 19 im Inneren des Gehäuseteils 13 verbindet.In this embodiment, the valve piece 3 is inserted into a further housing part 13 of the fuel injection valve 1. In this case, the valve member 3 is supported on a shoulder 14 of the housing part 13. The valve piece 3 has a bore 15 in which a control chamber 16 is delimited by a valve piston 17. In the control chamber 16 performs an inlet throttle 18, which connects the control chamber 16 with a high-pressure chamber 19 in the interior of the housing part 13.

Das Schaltventil 2 weist eine Achse 25 auf, an der der Anker 6 und das Ventilstück 3 ausgerichtet sind. Der Anker 6 ist dabei axialsymmetrisch zu der Achse 25 ausgestaltet. Das Ventilstück 3 ist im Wesentlichen axialsymmetrisch zu der Achse 25 ausgestaltet. Das Ventilstück 3 weist einen Führungsabschnitt 26 auf, der in einer Führungsbohrung 27 des Ankers 6 geführt ist. Die Führungsbohrung 27 ist hierbei als durchgehende Führungsbohrung 27 ausgestaltet. In die Führungsbohrung 27 erstreckt sich außerdem der Druckbolzen 9, um den Anker 6 an dem Druckbolzen 9 zu führen. Zwischen dem Führungsabschnitt 26 und der Ventilsitzfläche 4 ist ein Einstich 28 an dem Ventilstück 3 vorgesehen. Durch den Einstich 28 ist ein Brennstoffraum 29 gebildet, der durch eine Innenwand 30 der Führungsbohrung 27 des Ankers 6 begrenzt ist. Der Brennstoffraum 29 ist somit zwischen dem Führungsabschnitt 26 und der Ventilsitzfläche 4 ausgebildet.The switching valve 2 has an axis 25, on which the armature 6 and the valve piece 3 are aligned. The armature 6 is designed axially symmetrical to the axis 25. The valve piece 3 is designed substantially axially symmetrical to the axis 25. The valve piece 3 has a guide portion 26 which is guided in a guide bore 27 of the armature 6. The guide bore 27 is configured here as a continuous guide bore 27. In the guide bore 27 also extends the pressure pin 9 to guide the armature 6 on the pressure pin 9. Between the guide portion 26 and the valve seat surface 4, a recess 28 is provided on the valve piece 3. By the recess 28, a fuel chamber 29 is formed, which is bounded by an inner wall 30 of the guide bore 27 of the armature 6. The fuel room 29 is thus formed between the guide portion 26 and the valve seat surface 4.

Das Ventilstück 3 weist eine axiale Sackbohrung 31 auf, aus der ein Kanal 32 und ein Kanal 33 abzweigen. Über die Sackbohrung 31 und die Kanäle 32, 33 ist der Steuerraum 16 mit dem Brennstoffraum 29 verbunden. Die Kanäle 32, 33 sind dabei als gedrosselte Kanäle 32, 33 ausgestaltet. Die Kanäle 32, 33 münden beide in den Brennstoffraum 29 zwischen dem Führungsabschnitt 26 und dem Dichtsitz, der an der Kante 12 zwischen dem Ventilschließkörper 5 und der Ventilsitzfläche 4 gebildet ist. In diesem Ausführungsbeispiel ist der Brennstoffraum 29 in der Führungsbohrung 27 ausgebildet.The valve piece 3 has an axial blind bore 31, from which a channel 32 and a channel 33 branch off. About the blind bore 31 and the channels 32, 33 of the control chamber 16 is connected to the fuel chamber 29. The channels 32, 33 are designed as throttled channels 32, 33. The channels 32, 33 both open into the fuel chamber 29 between the guide portion 26 and the sealing seat, which is formed at the edge 12 between the valve closing body 5 and the valve seat surface 4. In this embodiment, the fuel space 29 is formed in the guide bore 27.

In diesem Ausführungsbeispiel ist die Kante 12 des Ventilschließkörpers 5 als Dichtkante ausgestaltet, an der der Dichtsitz zwischen dem Ventilschließkörper 5 und der Ventilsitzfläche 4 zustande kommt. Die Dichtkante 12 ist der Ventilsitzfläche 4 zugewandt. Dabei ist ein Durchmesser 34 der Dichtkante 12 zumindest näherungsweise gleich groß wie ein Durchmesser 35 des Führungsabschnitts 26. Dadurch ist in Bezug auf den Brennstoffraum 29 ein Druckausgleich ermöglicht. Außerdem ist der Durchmesser 34 sehr klein, so dass ein Sitzdurchmesser des Dichtsitzes ebenfalls sehr klein ist. Beispielsweise kann der Durchmesser 34 und somit der Sitzdurchmesser an der Dichtkante 12 nicht größer als 2 mm, insbesondere näherungsweise gleich 1,8 mm, sein.In this embodiment, the edge 12 of the valve closing body 5 is designed as a sealing edge on which the sealing seat between the valve closing body 5 and the valve seat surface 4 comes about. The sealing edge 12 faces the valve seat surface 4. In this case, a diameter 34 of the sealing edge 12 is at least approximately the same size as a diameter 35 of the guide portion 26. This is in relation to the fuel chamber 29, a pressure equalization allows. In addition, the diameter 34 is very small, so that a seat diameter of the sealing seat is also very small. For example, the diameter 34 and thus the seat diameter at the sealing edge 12 can not be greater than 2 mm, in particular approximately equal to 1.8 mm.

In diesem Ausführungsbeispiel weist der Anker 6 eine Stirnfläche 36 auf, die der Ventilsitzfläche 4 des Ventilstücks 3 zugewandt ist. Die Dichtkante 12 ist zwischen der Stirnfläche 36 und der Innenwand 30 der Führungsbohrung 27 gebildet. Dadurch liegt die Dichtkante 12 noch an der Stirnfläche 36, hat aber einen minimalen Durchmesser 34. Die konische Ventilsitzfläche 4 hat beispielsweise einen Öffnungswinkel, der gleich 90° ist. Hierdurch wird eine vorteilhafte Zentrierung des Ventilschließkörpers 5 mit seiner Dichtkante 12 an der Ventilsitzfläche 4 ermöglicht. Ein Öffnungswinkel der konischen Stirnfläche 36 des Ventilschließkörpers 5 ist größer als der Öffnungswinkel der konischen Ventilsitzfläche 4, das heißt in diesem Ausführungsbeispiel größer als 90°, gewählt.In this embodiment, the armature 6 has an end face 36 which faces the valve seat surface 4 of the valve piece 3. The sealing edge 12 is formed between the end face 36 and the inner wall 30 of the guide bore 27. As a result, the sealing edge 12 is still on the end face 36, but has a minimum diameter 34. The conical valve seat surface 4, for example, has an opening angle which is equal to 90 °. As a result, an advantageous centering of the valve closing body 5 is made possible with its sealing edge 12 on the valve seat surface 4. An opening angle of the conical end face 36 of the valve closing body 5 is greater than the opening angle of the conical valve seat surface 4, that is, in this embodiment, greater than 90 ° selected.

Der Öffnungswinkel der konischen Ventilsitzfläche 4 ist durch die erforderliche Zentrierung bestimmt und kann in einem Bereich von weniger als 120° liegen. Besonders günstig ist es, wenn er in einem Bereich von etwa 80° bis etwa 120° liegt. Der Öffnungswinkel der konischen Stirnfläche 36 des Ventilschließkörpers 5 ist dann größer als der Öffnungswinkel der konischen Ventilsitzfläche 4 gewählt.The opening angle of the conical valve seat surface 4 is determined by the required centering and may be in a range of less than 120 °. It is particularly advantageous if it is in a range of about 80 ° to about 120 °. The opening angle the conical end face 36 of the valve closing body 5 is then selected to be greater than the opening angle of the conical valve seat surface 4.

Die Ventilsitzfläche 4 ist durch eine Stufe 37 begrenzt. Hierdurch kann ein maximaler Durchmesser 38 der Ventilsitzfläche 4 zur Sitzbegrenzung vorgegeben sein. Die Sitzbegrenzung kann hierbei an dem Ventilstück 3 durch die Stufe 37 oder auch auf andere Weise angebracht werden.The valve seat surface 4 is limited by a step 37. In this way, a maximum diameter 38 of the valve seat surface 4 can be predetermined for seat limitation. The seat limitation can be attached to the valve member 3 through the step 37 or in other ways.

Der Führungsabschnitt 26 ist entlang der Achse 25 vorzugsweise relativ kurz ausgestaltet. Dieser kurze Führungsabschnitt 26 dient im Wesentlichen zur Zentrierung bei einer Montage. Die Führung des Ankers 6 erfolgt über den Druckbolzen 9. Die Druckkräfte vom Sitzdurchmesser werden vorzugsweise vom Druckbolzen 9 aufgenommen. Über das Stützelement 10 erfolgt somit eine Abstützung an einer Magnetgruppe. Der Führungsabschnitt 26 dichtet in diesem Fall nicht gegen den Hochdruck im Brennstoffraum 29 ab. Dadurch ist gewährleistet, dass das Ventilstück 3 im Bereich des Einstichs 28 und insbesondere an den Mündungen der Kanäle 32, 33 nicht auf Zug belastet wird und somit in diesem Bereich keine oder nur sehr geringe Zugspannungen im Ventilstück 3 auftreten. Hierbei ist es möglich, eine weitere Zugentlastung zu schaffen. Dies kann beispielsweise durch ein relativ großes Führungsspiel zwischen dem Führungsabschnitt 26 und der Führungsbohrung 27 des Ankers 6 erzielt werden. Außerdem kann zusätzlich oder alternativ ein Anschliff 39 an einer Seite des Führungsabschnitts 26 vorgesehen sein, der einen Leckagespalt zwischen dem Führungsabschnitt 26 und der Innenwand 30 der Führungsbohrung 27 ausbildet. Durch solch eine gezielte Leckage wird eine Angleichung des Drucks in der Führungsbohrung 27 zwischen dem Führungsabschnitt 26 und dem Druckbolzen 9 an den Druck im Brennstoffraum 29 ermöglicht.The guide section 26 is preferably made relatively short along the axis 25. This short guide section 26 essentially serves for centering during assembly. The leadership of the armature 6 via the pressure pin 9. The pressure forces from the seat diameter are preferably absorbed by the pressure pin 9. About the support member 10 thus takes place a support to a magnet group. In this case, the guide section 26 does not seal against the high pressure in the fuel chamber 29. This ensures that the valve member 3 in the region of the recess 28 and in particular at the mouths of the channels 32, 33 is not loaded on train and thus in this area no or only very small tensile stresses in the valve piece 3 occur. Here it is possible to provide a further strain relief. This can be achieved, for example, by a relatively large guide play between the guide section 26 and the guide bore 27 of the armature 6. In addition, additionally or alternatively, a bevel 39 may be provided on one side of the guide section 26, which forms a leakage gap between the guide section 26 and the inner wall 30 of the guide bore 27. By such a targeted leakage, an approximation of the pressure in the guide bore 27 between the guide portion 26 and the pressure pin 9 to the pressure in the fuel chamber 29 is made possible.

Vorteilhaft ist allerdings auch eine Ausgestaltung des Führungsabschnitts 26, bei der kein Anschliff 39 oder dergleichen vorgesehen ist. Der Führungsabschnitt 26 ist dadurch axialsymmetrisch zu der Achse 25 ausgestaltet. Hierdurch kann auch eine gewisse Führung erzielt werden, um ein zuverlässiges Schließen des Dichtsitzes zwischen der Dichtkante 12 und der Ventilsitzfläche 4 zu erzielen. Speziell wird ein Verkippen zwischen dem Ventilschließkörper 5 und dem Ventilstück 3 verhindert oder zumindest verringert, wodurch eine Selbstzentrierung der Dichtkante 12 an der konischen Ventilsitzfläche 4 unterstützt ist.However, it is also advantageous embodiment of the guide portion 26, in which no bevel 39 or the like is provided. The guide portion 26 is thereby configured axially symmetrical to the axis 25. In this way, a certain amount of guidance can be achieved in order to achieve a reliable closing of the sealing seat between the sealing edge 12 and the valve seat surface 4. Specifically, a tilting between the valve closing body 5 and the valve member 3 is prevented or at least reduced, whereby a self-centering of the sealing edge 12 is supported on the conical valve seat surface 4.

Die Erfindung ist nicht auf die beschriebenen Ausführungsbeispiele beschränkt.The invention is not limited to the described embodiments.

Claims (11)

  1. Switching valve (2), in particular solenoid valve for fuel injection valves of air-compressing, auto-ignition internal combustion engines, having a valve piece (3) on which there is formed a valve seat surface (4), and having a valve closing body (5) which is part of an armature (4) and which interacts with the valve seat surface (4) to form a sealing seat, wherein the valve piece (3) has a guide section (26) on which the valve closing body (5) is guided by way of a guide opening (27), and in that the valve piece (3) has at least one duct (32, 33) which issues into a fuel chamber (29) between the guide section (26) and the sealing seat,
    characterized in that
    the armature (6) is guided on a pressure pin (9) which is supported on a support element (10), and in that a leakage gap is formed between the guide section (26) and the guide bore (27) such that the pressure in the guide bore (27) between the guide section (26) and the pressure pin (9) is brought into alignment with the pressure in the fuel chamber (29).
  2. Switching valve according to Claim 1, characterized in that the chamber (29) into which the duct (32, 33) of the valve piece (3) issues between the guide section (26) and the sealing seat is formed at least partially in the guide opening (27).
  3. Switching valve according to Claim 1 or 2, characterized in that an indentation (28) is provided on the valve piece (3) between the guide section (26) and the valve seat surface (4), and in that the chamber (29) into which the duct (32, 33) of the valve piece (3) issues between the guide section (26) and the sealing seat is defined at least substantially by the indentation (28), wherein an internal wall (30) of the guide opening (27) delimits the chamber (29) defined by the indentation (28).
  4. Switching valve according to one of Claims 1 to 3, characterized in that the guide opening (27) is in the form of a guide bore (27), in particular in the form of a continuous guide bore (27), and in that at least the guide section (26) of the valve piece (3) is formed so as to be axially symmetrical with respect to an axis (25) of the guide bore (27).
  5. Switching valve according to one of Claims 1 to 3, characterized in that a lateral ground portion (39) is provided on the guide section (26).
  6. Switching valve according to one of Claims 1 to 5, characterized in that the duct (32, 33) that issues into the chamber (29) between the guide section (26) and the sealing seat is in the form of a throttled duct (32, 33).
  7. Switching valve according to one of Claims 1 to 6, characterized in that the valve closing body (5) has a sealing edge (12) which faces toward the valve seat surface (4), in that the sealing seat is formed between the sealing edge (12) and the valve seat surface (4), and in that a seat diameter (34), defined by the sealing edge (12), of the sealing seat is at least approximately equal to a diameter (35) of the guide section (26) of the valve piece (3).
  8. Switching valve according to Claim 7, characterized in that the valve seat surface (4) is in the form of a conical valve seat surface (4), and in that an opening angle of the conical valve seat surface (4) is selected from a range of approximately 80° to approximately 120°.
  9. Switching valve according to Claim 8, characterized in that the sealing edge (12) is formed on a conical end surface (36) of the valve closing body (5), and in that an opening angle of the conical end surface (36) is greater than the opening angle of the conical valve seat surface (4).
  10. Switching valve according to one of Claims 7 to 9, characterized in that the seat diameter (34) of the sealing seat is no greater than 2 mm, in particular is at least approximately equal to 1.8 mm.
  11. Fuel injection valve (1), in particular injector for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a switching valve (2) according to one of Claims 1 to 10.
EP10713929.7A 2009-06-05 2010-04-13 Switching valve Active EP2438288B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910026774 DE102009026774A1 (en) 2009-06-05 2009-06-05 switching valve
PCT/EP2010/054810 WO2010139501A1 (en) 2009-06-05 2010-04-13 Switching valve

Publications (2)

Publication Number Publication Date
EP2438288A1 EP2438288A1 (en) 2012-04-11
EP2438288B1 true EP2438288B1 (en) 2014-11-12

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ID=42313859

Family Applications (1)

Application Number Title Priority Date Filing Date
EP10713929.7A Active EP2438288B1 (en) 2009-06-05 2010-04-13 Switching valve

Country Status (4)

Country Link
EP (1) EP2438288B1 (en)
CN (1) CN102803704B (en)
DE (1) DE102009026774A1 (en)
WO (1) WO2010139501A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
IT201600070056A1 (en) * 2016-07-06 2018-01-06 Magneti Marelli Spa FUEL PUMP WITH A MAXIMUM PRESSURE VALVE PERFECTED FOR A DIRECT INJECTION SYSTEM
CN106014740B (en) * 2016-07-25 2018-12-11 成都威特电喷有限责任公司 Eliminate the control valve of valve rod axial force

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE602005021310D1 (en) * 2005-03-14 2010-07-01 Fiat Ricerche Adjustable metering valve of an injector and its adjustment method
DE102006021741A1 (en) 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102007009165A1 (en) * 2007-02-26 2008-08-28 Robert Bosch Gmbh Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, has output choke arranged in area of passage from riser bore into ring chamber, where amount of fuel guided by riser bore flows through choke
DE102007013248A1 (en) * 2007-03-20 2008-09-25 Robert Bosch Gmbh Fuel injector, has pressure-balanced switching valve actuated by solenoid valve and seat surface formed in area of valve seat, where seat surface increases outwards in radial direction
DE102007018005A1 (en) * 2007-04-17 2008-10-23 Robert Bosch Gmbh injector
DE102007044361A1 (en) * 2007-09-17 2009-03-19 Robert Bosch Gmbh Control valve for a fuel injector

Also Published As

Publication number Publication date
CN102803704B (en) 2015-08-12
CN102803704A (en) 2012-11-28
WO2010139501A1 (en) 2010-12-09
EP2438288A1 (en) 2012-04-11
DE102009026774A1 (en) 2010-12-09

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