EP2438287B1 - Control valve - Google Patents

Control valve Download PDF

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Publication number
EP2438287B1
EP2438287B1 EP10713926.3A EP10713926A EP2438287B1 EP 2438287 B1 EP2438287 B1 EP 2438287B1 EP 10713926 A EP10713926 A EP 10713926A EP 2438287 B1 EP2438287 B1 EP 2438287B1
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EP
European Patent Office
Prior art keywords
valve
closing body
valve closing
seat surface
piece
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EP10713926.3A
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German (de)
French (fr)
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EP2438287A1 (en
Inventor
Manfred Giel
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2438287A1 publication Critical patent/EP2438287A1/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
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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

Definitions

  • the invention relates to a switching valve, in particular a pressure-balanced 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 releases or closes the injection port is driven by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return in which a closing element is seated or released.
  • 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.
  • a switching valve according to the preamble of claim 1 is known from DE-A-10 2007 009168 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 10 have the advantage that a behavior of the switching valve is improved. Specifically, a consistently stable opening behavior of the switching valve can be achieved over the lifetime.
  • a sealing seat of the switching valve is realized with a cone pairing of different cone angle.
  • a matching of the two cones takes place, so that the sealing seat of the valve can move on the equalized surface of the two cones depending on the applied pressure.
  • This happens a change in the opening behavior of the valve and thus, for example, to a change in the injected amount of fuel.
  • a fuel injection valve of such a construction there is thus a drift of the injection amount over the lifetime.
  • drift is undesirable and there is a desire to minimize such drift.
  • a throttle gap in front of the sealing seat can be realized in the course of time during operation, whereby the voltage applied to the sealing seat system pressure is reduced.
  • the design of the throttle gap is effected by wear between the valve closing body and the valve seat surface, which is caused at least substantially by abrasion and smoothing of the surfaces (geometric adjustment). This also reduces the range in which a displacement of the effective seat diameter can occur and / or the extent of such a displacement of the effective seat diameter. This also reduces the possibility of a change in the opening behavior of the switching valve. Thus, a stable opening behavior is possible.
  • the compensation edge of the valve closing body is arranged in front of the sealing seat in a flow direction. Furthermore, it is advantageous that the compensation edge is designed such that a throttle gap is formed in operation between the compensation edge of the valve closing body and the valve seat surface. In this case, it is also advantageous that the throttle gap formed between the compensation edge of the valve closing body and the valve seat surface during operation is formed by an operational wear between the valve closing body and the valve seat surface of the valve piece. Starting from a newly manufactured valve, the compensation edge in operation, so to speak, strikes against the valve seat surface, resulting in wear due to abrasion and smoothing of the surfaces (geometric adjustment). As a result, a throttle gap is formed in the region of the compensation edge of the valve closing body.
  • the wear-related abrasion can be a few microns of material thickness. This creates a gap in the region of the compensation edge between the valve closing body and the valve seat surface, which acts as a throttle gap during operation.
  • the length of this throttle gap can be considered in the flow direction, corresponding to the wear of a few microns. Since the throttle gap, viewed in the direction of flow, is arranged in front of the sealing seat, the pressure applied to the sealing seat is reduced.
  • a material of the valve closing body and a material of the valve piece are selected on the valve seat surface so that an operational wear between the valve closing body and the valve seat surface of the valve member occurs both on the valve closing body and on the valve piece.
  • the valve closing body and the valve piece on the valve seat surface advantageously adjoin one another.
  • a flow-favorable throttle gap is formed.
  • valve closing body has a contact surface which faces the valve seat surface of the valve piece, that the valve closing body cooperates at its contact surface with the valve seat surface to the sealing seat and that the contact surface viewed in a flow direction as a relatively narrow contact surface and / or as an annular contact surface is designed. Furthermore, it is advantageous that the contact surface of the valve closing body is limited by the compensation edge of the valve closing body. This reduces the possible range in which the sealing seat can vary from the outset.
  • the compensation edge is formed by a bevel provided on the valve closing body.
  • the bevel provided on the valve closing body reduces the range in which the effective seat diameter can vary by the amount of width of the chamfer. This achieves additional stabilization of the opening behavior over the service life.
  • the chamfer can be configured, for example, as a ground chamfer.
  • valve closure member is guided on a bolt-shaped guide portion of the valve piece, wherein the valve seat surface of the valve piece is designed as at least substantially conical, annular valve seat surface.
  • valve piece has an annular recess, that an inner side of the valve closing body defines a fuel space formed by the puncture, and that a fuel channel guided through the valve piece opens into the fuel chamber.
  • Fig. 1 shows an embodiment of a switching valve 1 of a fuel injection valve in a schematic, partial, axial sectional view.
  • the switching valve 1 is particularly suitable for fuel injection valves of fuel injection systems of air-compressing, self-igniting internal combustion engines.
  • a preferred insert is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure and is connected to a plurality of fuel injectors.
  • the switching valve 1 according to the invention and the fuel injection valve according to the invention are also suitable for other applications.
  • the switching valve 1 has a valve piece 1 and a valve closing body 3.
  • the valve closing body 3 may be connected to an armature 4.
  • the valve closing body 3 is designed in one piece with the armature 4.
  • the valve piece 2 has a bolt-shaped guide section 5, on which the armature 4 is guided along an axis 6 of the switching valve 1.
  • the armature 4 is designed axially symmetrical to the axis 6.
  • the valve piece 2 is configured at least substantially axially symmetrically with respect to the axis 6.
  • the valve piece 2 has an annular recess 7.
  • a valve seat surface 8 on the valve piece 2 is formed by the annular recess 7.
  • a surface 9 is thereby formed on the valve piece 2.
  • the valve seat surface 8 is designed as a conical, annular valve seat surface 8.
  • the surface 9 is designed as a conical, annular surface 9.
  • the valve seat surface 8 is at least approximately facing the surface 9.
  • the valve closing body 3 of the armature 4 has an inner side 10, which surrounds the valve piece 2 circumferentially.
  • the inner side 10 of the valve closing body 3 defines an annular fuel space 11 formed by the recess 7.
  • an axial blind bore 12 is configured, from which at least one radial bore 13 branches off.
  • the blind bore 12 and the radial bore 13 form a fuel passage 14 of the switching valve 1.
  • the radial bore 13 of the fuel channel 14 opens at the annular recess 7 in the fuel chamber 11 of the switching valve. 1
  • the valve closing body 3 has a contact surface 20.
  • the contact surface 20 faces the valve seat surface 8.
  • the valve closing body 3 has a compensation edge 21.
  • the compensation edge 21 is directed to the valve seat surface 8.
  • the valve closing body 3 cooperates with the valve seat surface 8 to form a sealing seat.
  • a sealing line, sealing surface or the like of the sealing seat is located in a region 22.
  • the compensation edge 21 is located outside the region 22.
  • the compensation edge 21 of the valve closing body 3 lies in a flow direction 23 in front of the sealing seat, which lies in the region 22.
  • the flow direction 23 is in this case determined such that it at least approximately indicates the flow of the fuel when the sealing seat is open.
  • the contact surface 20 is viewed in the flow direction 23 as a relatively narrow contact surface 20 configured.
  • the contact surface 20 is configured as an annular contact surface 20.
  • the region 22 is set relatively narrow. This favors a constant, stable opening behavior of the switching valve 1 during operation.
  • the compensation edge 21 is formed in this embodiment by a provided on the valve closing body 3 chamfer 24.
  • the chamfer 24 may be configured, for example, by grinding the valve closing body 3.
  • the contact surface 20 is thereby limited by the compensation edge 21.
  • Fig. 2 shows the switching valve 1 after a certain period of operation.
  • a material of the valve closing body 3 and a material of the valve piece 2 on the valve seat surface 8 are selected so that an operational wear between the valve closing body 3 and the valve seat surface 8 of the valve member 2 occurs both on the valve closing body 3 and the valve piece 2.
  • wear occurs in the region of the contact surface 20 of the valve closing body 3 wear, which forms a recess 25.
  • wear occurs on the valve seat surface 8, which leads to a recess 26 on the valve seat surface 8. Further wear occurs in the area of the compensation edge 21.
  • abrasion occurs on the chamfer 24, whereby an abraded chamfer 27 is formed, which is further set back relative to the chamfer 24.
  • a step 28 forms in the valve seat surface 8.
  • the height of the step 28 may be, for example, a few microns.
  • a throttle gap 30 is thereby formed between the abraded chamfer 27 of the valve closing body 3 and the step 28 of the valve seat surface 8.
  • the throttle gap 30 may in the Viewed flow direction 23, be a few microns long.
  • the throttle gap 30 can be configured at least substantially annularly along the valve seat surface 8.
  • the sealing seat formed between the valve closing body 3 and the valve seat surface 8 can come about in the region 22.
  • the instantaneous position is dependent on the pressure in the fuel chamber 11.
  • the sealing seat is at low pressures closer to the compensation edge 21 and at high pressures closer to an outer edge 29 of the recess 26 of the valve seat 8, that is viewed in the flow direction 23 at the end of the recess 26. Since the contact surface 20 set relatively narrow is, even with the occurring wear of the region 22 in which the sealing seat comes about, relatively small. As a result, the opening behavior is relatively stable.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Lift Valve (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Schaltventil, insbesondere ein druckausgeglichenes Ventil 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 pressure-balanced 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 die Einspritzöffnung freigibt oder verschließt, durch ein Steuerventil angesteuert, wobei das Steuerventil eine Verbindung aus einem Steuerraum in einen Kraftstoffrücklauf freigibt oder verschließt, in dem 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 releases or closes the injection port is driven by a control valve, the control valve releasing or closing a connection from a control chamber into a fuel return in which a closing element is seated or released. 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.

Ein Schaltventil gemäß Oberbegriff des Anspruchs 1 ist aus der DE-A- 10 2007 009168 bekannt.A switching valve according to the preamble of claim 1 is known from DE-A-10 2007 009168 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 10 haben den Vorteil, dass ein Verhalten des Schaltventils verbessert ist. Speziell kann ein gleichbleibend stabiles Öffnungsverhalten des Schaltventils über die Lebensdauer erzielt werden.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 10 have the advantage that a behavior of the switching valve is improved. Specifically, a consistently stable opening behavior of the switching valve can be achieved over the lifetime.

Bei der Ausgestaltung eines Schaltventils ist es denkbar, dass ein Dichtsitz des Schaltventils mit einer Kegelpaarung unterschiedlicher Kegelwinkel realisiert wird. Dabei findet allerdings im Betrieb im Laufe der Zeit durch Verschleiß und Glättung ein Angleich der beiden Kegel statt, so dass sich der Dichtsitz des Ventils auf der angeglichenen Fläche der beiden Kegel je nach anliegendem Druck verschieben kann. Hierdurch kommt es zu einer Änderung des Öffnungsverhaltens des Ventils und damit beispielsweise zu einer Änderung der eingespritzten Brennstoffmenge. Bei einem Brennstoffeinspritzventil mit solch einer Konstruktion kommt es somit zu einer Drift der Einspritzmenge über die Lebensdauer. Solch eine Drift ist allerdings unerwünscht und es besteht das Bestreben, solch eine Drift möglichst gering zu halten.In the embodiment of a switching valve, it is conceivable that a sealing seat of the switching valve is realized with a cone pairing of different cone angle. However, during operation over time due to wear and smoothing, a matching of the two cones takes place, so that the sealing seat of the valve can move on the equalized surface of the two cones depending on the applied pressure. This is what happens a change in the opening behavior of the valve and thus, for example, to a change in the injected amount of fuel. In a fuel injection valve of such a construction, there is thus a drift of the injection amount over the lifetime. However, such drift is undesirable and there is a desire to minimize such drift.

Durch die Ausgestaltung der Kompensationskante am Ventilschließkörper, die beispielsweise durch Anschleifen ausgebildet werden kann, kann im Laufe der Zeit im Betrieb ein Drosselspalt vor dem Dichtsitz realisiert werden, wodurch der an dem Dichtsitz anliegende Systemdruck reduziert wird. Die Ausgestaltung des Drosselspalts erfolgt hierbei durch einen Verschleiß zwischen dem Ventilschließkörper und der Ventilsitzfläche, der zumindest im Wesentlichen durch Abrieb und Glättung der Oberflächen (geometrischer Angleich) verursacht ist. Hierdurch wird auch der Bereich, in dem eine Verschiebung des wirksamen Sitzdurchmessers erfolgen kann und/oder das Ausmaß solch einer Verschiebung des wirksamen Sitzdurchmessers verringert. Dadurch ist auch die Möglichkeit einer Änderung des Offnungsverhaltens des Schaltventils verringert. Somit ist ein stabiles Öffnungsverhalten möglich.Due to the design of the compensation edge on the valve closing body, which can be formed, for example, by grinding, a throttle gap in front of the sealing seat can be realized in the course of time during operation, whereby the voltage applied to the sealing seat system pressure is reduced. The design of the throttle gap is effected by wear between the valve closing body and the valve seat surface, which is caused at least substantially by abrasion and smoothing of the surfaces (geometric adjustment). This also reduces the range in which a displacement of the effective seat diameter can occur and / or the extent of such a displacement of the effective seat diameter. This also reduces the possibility of a change in the opening behavior of the switching valve. Thus, a stable opening behavior is possible.

Erfindungsgemäß ist die Kompensationskante des Ventilschließkörpers in einer Strömungsrichtung betrachtet vor dem Dichtsitz angeordnet. Ferner ist es vorteilhaft, dass die Kompensationskante so ausgestaltet ist, dass im Betrieb zwischen der Kompensationskante des Ventilschließkörpers und der Ventilsitzfläche ein Drosselspalt ausgebildet ist. Hierbei ist es auch vorteilhaft, dass der zwischen der Kompensationskante des Ventilschließkörpers und der Ventilsitzfläche im Betrieb ausgebildete Drosselspalt durch einen betriebsbedingten Verschleiß zwischen dem Ventilschließkörper und der Ventilsitzfläche des Ventilstücks gebildet ist. Ausgehend von einem neu hergestellten Ventil schlägt die Kompensationskante im Betrieb sozusagen gegen die Ventilsitzfläche, wodurch es zu einem Verschleiß durch Abrieb und Glättung der Oberflächen (geometrischer Angleich) kommt. Dadurch bildet sich ein Drosselspalt im Bereich der Kompensationskante des Ventilschließkörpers aus. Beispielsweise kann der verschleißbedingte Abrieb einige Mikrometer an Materialstärke betragen. Dadurch bildet sich ein Spalt im Bereich der Kompensationskante zwischen dem Ventilschließkörper und der Ventilsitzfläche, der im Betrieb als Drosselspalt wirkt. Die Länge dieses Drosselspalts kann in Strömungsrichtung betrachtet, entsprechend dem Verschleiß einige Mikrometer betragen. Da der Drosselspalt in Strömungsrichtung betrachtet vor dem Dichtsitz angeordnet ist, ergibt sich eine Reduzierung des Druckes, der am Dichtsitz anliegt.According to the invention, the compensation edge of the valve closing body is arranged in front of the sealing seat in a flow direction. Furthermore, it is advantageous that the compensation edge is designed such that a throttle gap is formed in operation between the compensation edge of the valve closing body and the valve seat surface. In this case, it is also advantageous that the throttle gap formed between the compensation edge of the valve closing body and the valve seat surface during operation is formed by an operational wear between the valve closing body and the valve seat surface of the valve piece. Starting from a newly manufactured valve, the compensation edge in operation, so to speak, strikes against the valve seat surface, resulting in wear due to abrasion and smoothing of the surfaces (geometric adjustment). As a result, a throttle gap is formed in the region of the compensation edge of the valve closing body. For example, the wear-related abrasion can be a few microns of material thickness. This creates a gap in the region of the compensation edge between the valve closing body and the valve seat surface, which acts as a throttle gap during operation. The length of this throttle gap can be considered in the flow direction, corresponding to the wear of a few microns. Since the throttle gap, viewed in the direction of flow, is arranged in front of the sealing seat, the pressure applied to the sealing seat is reduced.

In vorteilhafter Weise sind ein Werkstoff des Ventilschließkörpers und ein Werkstoff des Ventilstücks an der Ventilsitzfläche so gewählt, dass ein betriebsbedingter Verschleiß zwischen dem Ventilschließkörper und der Ventilsitzfläche des Ventilstücks sowohl an dem Ventilschließkörper als auch an dem Ventilstück auftritt. Dadurch passen sich der Ventilschließkörper und das Ventilstück an der Ventilsitzfläche in vorteilhafter Weise aneinander an. Dadurch wird insbesondere ein strömungsgünstiger Drosselspalt ausgebildet.Advantageously, a material of the valve closing body and a material of the valve piece are selected on the valve seat surface so that an operational wear between the valve closing body and the valve seat surface of the valve member occurs both on the valve closing body and on the valve piece. As a result, the valve closing body and the valve piece on the valve seat surface advantageously adjoin one another. As a result, in particular a flow-favorable throttle gap is formed.

Vorteilhaft ist es, dass der Ventilschließkörper eine Kontaktfläche aufweist, die der Ventilsitzfläche des Ventilstücks zugewandt ist, dass der Ventilschließkörper an seiner Kontaktfläche mit der Ventilsitzfläche zu dem Dichtsitz zusammenwirkt und dass die Kontaktfläche in einer Strömungsrichtung betrachtet als relativ schmale Kontaktfläche und/oder als ringförmige Kontaktfläche ausgestaltet ist. Ferner ist es vorteilhaft, dass die Kontaktfläche des Ventilschließkörpers durch die Kompensationskante des Ventilschließkörpers begrenzt ist. Hierdurch wird der mögliche Bereich, in dem der Dichtsitz variieren kann, von vornherein verringert.It is advantageous that the valve closing body has a contact surface which faces the valve seat surface of the valve piece, that the valve closing body cooperates at its contact surface with the valve seat surface to the sealing seat and that the contact surface viewed in a flow direction as a relatively narrow contact surface and / or as an annular contact surface is designed. Furthermore, it is advantageous that the contact surface of the valve closing body is limited by the compensation edge of the valve closing body. This reduces the possible range in which the sealing seat can vary from the outset.

Vorteilhaft ist es auch, dass die Kompensationskante durch eine an dem Ventilschließkörper vorgesehene Fase gebildet ist. Durch die an dem Ventilschließkörper vorgesehene Fase verringert sich der Bereich, in dem der wirksame Sitzdurchmesser schwanken kann, um das Maß der Breite der Fase. Dadurch wird eine zusätzliche Stabilisierung des Offnungsverhaltens über die Lebensdauer erzielt. Die Fase kann beispielsweise als eingeschliffene Fase ausgestaltet sein.It is also advantageous that the compensation edge is formed by a bevel provided on the valve closing body. The bevel provided on the valve closing body reduces the range in which the effective seat diameter can vary by the amount of width of the chamfer. This achieves additional stabilization of the opening behavior over the service life. The chamfer can be configured, for example, as a ground chamfer.

In vorteilhafter Weise ist der Ventilschließkörper an einem bolzenförmigen Führungsabschnitt des Ventilstücks geführt, wobei die Ventilsitzfläche des Ventilstücks als zumindest im Wesentlichen konische, ringförmige Ventilsitzfläche ausgestaltet ist. Außerdem ist es vorteilhaft, dass das Ventilstück einen ringförmigen Einstich aufweist, dass eine Innenseite des Ventilschließkörpers einen durch den Einstich gebildeten Brennstoffraum begrenzt und dass in den Brennstoffraum ein durch das Ventilstück geführter Brennstoffkanal mündet. Hierdurch kann eine vorteilhafte Positionierung, insbesondere Zentrierung, des Ventilschließkörpers in Bezug auf das Ventilstück und somit der Kompensationskante in Bezug auf die Ventilsitzfläche erzielt werden. Außerdem kann in vorteilhafter Weise eine druckausgeglichene Ausgestaltung des Ventils erzielt werden.Advantageously, the valve closure member is guided on a bolt-shaped guide portion of the valve piece, wherein the valve seat surface of the valve piece is designed as at least substantially conical, annular valve seat surface. Moreover, it is advantageous that the valve piece has an annular recess, that an inner side of the valve closing body defines a fuel space formed by the puncture, and that a fuel channel guided through the valve piece opens into the fuel chamber. In this way, an advantageous positioning, in particular centering, of the valve closing body with respect to the valve piece and thus the compensation edge with respect to the valve seat surface can be achieved. In addition, advantageously, a pressure-balanced configuration of the valve can be achieved.

Bevorzugte Ausführungsbeispiele der Erfindung sind in der nachfolgenden Beschreibung unter Bezugnahme auf die beigefügten Zeichnungen, in denen sich entsprechende Elemente mit übereinstimmenden Bezugszeichen versehen sind, näher erläutert. Es zeigt:

  • Fig. 1 ein Schaltventil in einer auszugsweisen, schematischen Schnittdarstellung entsprechend einem Ausführungsbeispiel der Erfindung im Neuzustand und
  • Fig. 2 den in Fig. 1 dargestellten Ausschnitt nach einer gewissen Betriebsdauer.
Preferred embodiments of the invention are explained in more detail in the following description with reference to the accompanying drawings, in which corresponding elements are provided with identical reference numerals. It shows:
  • Fig. 1 a switching valve in an excerpt, schematic sectional view according to an embodiment of the invention in the new state and
  • Fig. 2 the in Fig. 1 shown section after a certain period of operation.

Fig. 1 zeigt ein Ausführungsbeispiel eines Schaltventils 1 eines Brennstoffeinspritzventils in einer schematischen, auszugsweisen, axialen Schnittdarstellung. Das Schaltventil 1 eignet sich besonders für Brennstoffeinspritzventile von Brennstoffeinspritzanlagen von luftverdichtenden, selbstzündenden Brennkraftmaschinen. Ein bevorzugter Einsatz besteht für eine Brennstoffeinspritzanlage mit einer Brennstoffverteilerleiste, die Dieselbrennstoff unter hohem Druck speichert und mit mehreren Brennstoffeinspritzventilen verbunden ist. Das erfindungsgemäße Schaltventil 1 und das erfindungsgemäße Brennstoffeinspritzventil eignen sich jedoch auch für andere Anwendungsfälle. Fig. 1 shows an embodiment of a switching valve 1 of a fuel injection valve in a schematic, partial, axial sectional view. The switching valve 1 is particularly suitable for fuel injection valves of fuel injection systems of air-compressing, self-igniting internal combustion engines. A preferred insert is for a fuel injection system having a fuel rail which stores diesel fuel under high pressure and is connected to a plurality of fuel injectors. However, the switching valve 1 according to the invention and the fuel injection valve according to the invention are also suitable for other applications.

Das Schaltventil 1 weist ein Ventilstück 1 und einen Ventilschließkörper 3 auf. Der Ventilschließkörper 3 kann mit einem Anker 4 verbunden sein. In diesem Ausführungsbeispiel ist der Ventilschließkörper 3 einstückig mit dem Anker 4 ausgestaltet.The switching valve 1 has a valve piece 1 and a valve closing body 3. The valve closing body 3 may be connected to an armature 4. In this embodiment, the valve closing body 3 is designed in one piece with the armature 4.

Das Ventilstück 2 weist einen bolzenförmigen Führungsabschnitt 5 auf, an dem der Anker 4 entlang einer Achse 6 des Schaltventils 1 geführt ist. Der Anker 4 ist dabei axialsymmetrisch zu der Achse 6 ausgestaltet. Ferner ist das Ventilstück 2 zumindest im Wesentlichen axialsymmetrisch zu der Achse 6 ausgestaltet.The valve piece 2 has a bolt-shaped guide section 5, on which the armature 4 is guided along an axis 6 of the switching valve 1. The armature 4 is designed axially symmetrical to the axis 6. Furthermore, the valve piece 2 is configured at least substantially axially symmetrically with respect to the axis 6.

Das Ventilstück 2 weist einen ringförmigen Einstich 7 auf. Durch den ringförmigen Einstich 7 ist einerseits eine Ventilsitzfläche 8 an dem Ventilstück 2 ausgebildet. Andererseits ist dadurch an dem Ventilstück 2 eine Fläche 9 ausgebildet. Die Ventilsitzfläche 8 ist als konische, ringförmige Ventilsitzfläche 8 ausgestaltet. Ferner ist die Fläche 9 als konische, ringförmige Fläche 9 ausgestaltet. Die Ventilsitzfläche 8 ist der Fläche 9 zumindest näherungsweise zugewandt.The valve piece 2 has an annular recess 7. On the one hand, a valve seat surface 8 on the valve piece 2 is formed by the annular recess 7. On the other hand, a surface 9 is thereby formed on the valve piece 2. The valve seat surface 8 is designed as a conical, annular valve seat surface 8. Furthermore, the surface 9 is designed as a conical, annular surface 9. The valve seat surface 8 is at least approximately facing the surface 9.

Der Ventilschließkörper 3 des Ankers 4 weist eine Innenseite 10 auf, die das Ventilstück 2 umfänglich umschließt. Die Innenseite 10 des Ventilschließkörpers 3 begrenzt einen durch den Einstich 7 gebildeten ringförmigen Brennstoffraum 11. In dem Ventilstück 2 ist eine axiale Sackbohrung 12 ausgestaltet, von der zumindest eine radiale Bohrung 13 abzweigt. Die Sackbohrung 12 und die radiale Bohrung 13 bilden einen Brennstoffkanal 14 des Schaltventils 1 aus. Die radiale Bohrung 13 des Brennstoffkanals 14 mündet an dem ringförmigen Einstich 7 in den Brennstoffraum 11 des Schaltventils 1.The valve closing body 3 of the armature 4 has an inner side 10, which surrounds the valve piece 2 circumferentially. The inner side 10 of the valve closing body 3 defines an annular fuel space 11 formed by the recess 7. In the valve piece 2, an axial blind bore 12 is configured, from which at least one radial bore 13 branches off. The blind bore 12 and the radial bore 13 form a fuel passage 14 of the switching valve 1. The radial bore 13 of the fuel channel 14 opens at the annular recess 7 in the fuel chamber 11 of the switching valve. 1

Der Ventilschließkörper 3 weist eine Kontaktfläche 20 auf. Die Kontaktfläche 20 ist der Ventilsitzfläche 8 zugewandt. Im Bereich der Kontaktfläche 20 weist der Ventilschließkörper 3 eine Kompensationskante 21 auf. Die Kompensationskante 21 ist auf die Ventilsitzfläche 8 gerichtet. Der Ventilschließkörper 3 wirkt mit der Ventilsitzfläche 8 zu einem Dichtsitz zusammen. Eine Dichtlinie, Dichtfläche oder dergleichen des Dichtsitzes liegt in einem Bereich 22. Die Kompensationskante 21 liegt außerhalb des Bereichs 22. Hierbei liegt die Kompensationskante 21 des Ventilschließkörpers 3 in einer Strömungsrichtung 23 betrachtet vor dem Dichtsitz, der im Bereich 22 liegt. Die Strömungsrichtung 23 ist hierbei so bestimmt, dass diese zumindest näherungsweise den Fluss des Brennstoffs bei geöffnetem Dichtsitz angibt.The valve closing body 3 has a contact surface 20. The contact surface 20 faces the valve seat surface 8. In the area of the contact surface 20, the valve closing body 3 has a compensation edge 21. The compensation edge 21 is directed to the valve seat surface 8. The valve closing body 3 cooperates with the valve seat surface 8 to form a sealing seat. A sealing line, sealing surface or the like of the sealing seat is located in a region 22. The compensation edge 21 is located outside the region 22. In this case, the compensation edge 21 of the valve closing body 3 lies in a flow direction 23 in front of the sealing seat, which lies in the region 22. The flow direction 23 is in this case determined such that it at least approximately indicates the flow of the fuel when the sealing seat is open.

Die Kontaktfläche 20 ist in der Strömungsrichtung 23 betrachtet als relativ schmale Kontaktfläche 20 ausgestaltet. Außerdem ist die Kontaktfläche 20 als ringförmige Kontaktfläche 20 ausgestaltet. Hierdurch ist der Bereich 22 relativ schmal vorgegeben. Dies begünstigt im Betrieb ein konstantes, stabiles Öffnungsverhalten des Schaltventils 1.The contact surface 20 is viewed in the flow direction 23 as a relatively narrow contact surface 20 configured. In addition, the contact surface 20 is configured as an annular contact surface 20. As a result, the region 22 is set relatively narrow. This favors a constant, stable opening behavior of the switching valve 1 during operation.

Die Kompensationskante 21 ist in diesem Ausführungsbeispiel durch eine an dem Ventilschließkörper 3 vorgesehene Fase 24 gebildet. Die Fase 24 kann beispielsweise durch Anschleifen des Ventilschließkörpers 3 ausgestaltet sein. Die Kontaktfläche 20 ist dadurch durch die Kompensationskante 21 begrenzt.The compensation edge 21 is formed in this embodiment by a provided on the valve closing body 3 chamfer 24. The chamfer 24 may be configured, for example, by grinding the valve closing body 3. The contact surface 20 is thereby limited by the compensation edge 21.

Fig. 2 zeigt das Schaltventil 1 nach einer gewissen Betriebsdauer. Ein Werkstoff des Ventilschließkörpers 3 und ein Werkstoff des Ventilstücks 2 an der Ventilsitzfläche 8 sind so gewählt, dass ein betriebsbedingter Verschleiß zwischen dem Ventilschließkörper 3 und der Ventilsitzfläche 8 des Ventilstücks 2 sowohl an dem Ventilschließkörper 3 als auch dem Ventilstück 2 auftritt. Somit tritt im Bereich der Kontaktfläche 20 des Ventilschließkörpers 3 ein Verschleiß auf, der eine Vertiefung 25 bildet. Außerdem tritt auch ein Verschleiß an der Ventilsitzfläche 8 auf, der zu einer Vertiefung 26 an der Ventilsitzfläche 8 führt. Eine weitere Abnutzung tritt im Bereich der Kompensationskante 21 auf. An der in der Fig. 1 dargestellten Fase 24 tritt im Betrieb ein Abrieb auf, wodurch sich eine abgeriebene Fase 27 ausbildet, die gegenüber der Fase 24 weiter zurückgesetzt ist. Entsprechend kommt es auch im Bereich der Ventilsitzfläche 8 zu einem Verschleiß, wodurch sich eine Stufe 28 in der Ventilsitzfläche 8 bildet. Die Höhe der Stufe 28 kann beispielsweise einige Mikrometer betragen. Im geschlossenen Zustand des Dichtsitzes, in dem der Ventilschließkörper 3 an seiner Vertiefung 25 an der Vertiefung 26 der Ventilsitzfläche 8 anliegt, ist dadurch zwischen der abgeriebenen Fase 27 des Ventilschließkörpers 3 und der Stufe 28 der Ventilsitzfläche 8 ein Drosselspalt 30 gebildet. Der Drosselspalt 30 kann in der Strömungsrichtung 23 betrachtet, einige Mikrometer lang sein. Der Drosselspalt 30 kann in diesem Ausführungsbeispiel zumindest im Wesentlichen ringförmig entlang der Ventilsitzfläche 8 ausgestaltet sein. Fig. 2 shows the switching valve 1 after a certain period of operation. A material of the valve closing body 3 and a material of the valve piece 2 on the valve seat surface 8 are selected so that an operational wear between the valve closing body 3 and the valve seat surface 8 of the valve member 2 occurs both on the valve closing body 3 and the valve piece 2. Thus occurs in the region of the contact surface 20 of the valve closing body 3 wear, which forms a recess 25. In addition, wear occurs on the valve seat surface 8, which leads to a recess 26 on the valve seat surface 8. Further wear occurs in the area of the compensation edge 21. At the in the Fig. 1 During operation, abrasion occurs on the chamfer 24, whereby an abraded chamfer 27 is formed, which is further set back relative to the chamfer 24. Accordingly, wear occurs in the region of the valve seat surface 8, as a result of which a step 28 forms in the valve seat surface 8. The height of the step 28 may be, for example, a few microns. In the closed state of the sealing seat, in which the valve closing body 3 rests against its depression 25 on the depression 26 of the valve seat surface 8, a throttle gap 30 is thereby formed between the abraded chamfer 27 of the valve closing body 3 and the step 28 of the valve seat surface 8. The throttle gap 30 may in the Viewed flow direction 23, be a few microns long. In this exemplary embodiment, the throttle gap 30 can be configured at least substantially annularly along the valve seat surface 8.

Somit entsteht über die Betriebsdauer ein Drosselspalt 30 vor dem Dichtsitz, der den Druck an dieser Stelle drosselt. Somit kann ein stabiles Öffnungsverhalten erzielt werden. Ferner besteht der Vorteil, dass die Kompensationskante 21 relativ stumpf wird, wodurch eine gegebenenfalls vorgesehene Beschichtung vereinfacht ist.Thus arises over the operating time, a throttle gap 30 in front of the sealing seat, which throttles the pressure at this point. Thus, a stable opening behavior can be achieved. Furthermore, there is the advantage that the compensation edge 21 becomes relatively dull, whereby an optionally provided coating is simplified.

Im Betrieb kann der zwischen dem Ventilschließkörper 3 und der Ventilsitzfläche 8 gebildete Dichtsitz in dem Bereich 22 zustande kommen. Hierbei ist die momentane Position von dem Druck in dem Brennstoffraum 11 abhängig. In der Regel liegt der Dichtsitz bei niedrigen Drücken näher an der Kompensationskante 21 und bei hohen Drücken näher an einer äußeren Kante 29 der Vertiefung 26 der Ventilsitzfläche 8, das heißt in Strömungsrichtung 23 betrachtet am Ende der Vertiefung 26. Da die Kontaktfläche 20 relativ schmal vorgegeben ist, bleibt auch bei dem auftretenden Verschleiß der Bereich 22, in dem der Dichtsitz zustande kommt, relativ klein. Dadurch ist auch das Öffnungsverhalten relativ stabil.During operation, the sealing seat formed between the valve closing body 3 and the valve seat surface 8 can come about in the region 22. In this case, the instantaneous position is dependent on the pressure in the fuel chamber 11. In general, the sealing seat is at low pressures closer to the compensation edge 21 and at high pressures closer to an outer edge 29 of the recess 26 of the valve seat 8, that is viewed in the flow direction 23 at the end of the recess 26. Since the contact surface 20 set relatively narrow is, even with the occurring wear of the region 22 in which the sealing seat comes about, relatively small. As a result, the opening behavior is relatively stable.

Somit kommt es zu einer vorteilhaften Zusammenwirkung der Wirkung des Drosselspalts 30 und des relativ schmalen Bereichs 22, in dem der Dichtsitz liegt. Denn durch den Drosselspalt 30 wird der Hochdruck im Brennstoffraum 11 in Bezug auf den Dichtsitz gedrosselt, so dass eine druckbedingte Variation des Dichtsitzes verringert ist, und zugleich ist der Bereich 22 für den Dichtsitz relativ schmal. Durch den Drosselspalt 30 kann hierbei einer verschleißbedingten Vergrößerung des Bereichs 22 im Betrieb entgegen gewirkt werden, so dass eine zumindest teilweise Kompensation auftritt.Thus, there is an advantageous interaction of the effect of the throttle gap 30 and the relatively narrow portion 22 in which the sealing seat is located. Because through the throttle gap 30, the high pressure in the fuel chamber 11 is throttled with respect to the sealing seat, so that a pressure-related variation of the sealing seat is reduced, and at the same time the region 22 for the sealing seat is relatively narrow. Through the throttle gap 30, a wear-induced enlargement of the region 22 can be counteracted during operation, so that an at least partial compensation occurs.

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

Claims (10)

  1. Switching valve (1), in particular pressure-balanced valve for fuel injection valves of air-compressing, auto-ignition internal combustion engines, having a valve piece (2) on which a valve seat surface (8) is formed and having a valve closing body (3) which interacts with the valve seat surface (8) to form a sealing seat, wherein the valve closing body (3) has a compensation edge (21) and the compensation edge (21) delimits a contact surface (20) of the valve closing body (3) and is situated outside a region (22) for the sealing seat, characterized in that the compensation edge (21) of the valve closing body (3) is arranged upstream of the region (22) for the sealing seat as viewed in a flow direction (23).
  2. Switching valve according to Claim 1, characterized in that the compensation edge (21) is designed such that, during operation, a throttle gap (30) is formed between the compensation edge (21) of the valve closing body (3) and the valve seat surface (8).
  3. Switching valve according to Claim 2, characterized in that the throttle gap (30) formed between the compensation edge (21) of the valve closing body (3) and the valve seat surface (8) during operation is formed by operation-induced wear between the valve closing body (3) and the valve seat surface (8) of the valve piece (2).
  4. Switching valve according to one of Claims 1 to 3, characterized in that a material of the valve closing body (3) and a material of the valve piece (2) at the valve seat surface (8) are selected such that operation-induced wear between the valve closing body (3) and the valve seat surface (8) of the valve piece (2) occurs both on the valve closing body (3) and also on the valve piece (2).
  5. Switching valve according to one of Claims 1 to 4, characterized in that the valve closing body (3) has a contact surface (20) which faces towards the valve seat surface (8) of the valve piece (2), in that the valve closing body (3) interacts, at its contact surface (20), with the valve seat surface (8) to form the sealing seat, and in that the contact surface (20) is formed as a relatively narrow contact surface (20), and/or as an annular contact surface (20), as viewed in a flow direction (23).
  6. Switching valve according to one of Claims 1 to 5, characterized in that the contact surface (20) of the valve closing body (3) is delimited by the compensation edge (21) of the valve closing body (3).
  7. Switching valve according to one of Claims 1 to 6, characterized in that the compensation edge (21) is formed by a chamfer (24) provided on the valve closing body (3).
  8. Switching valve according to one of Claims 1 to 7, characterized in that the valve closing body (3) is guided on a pin-shaped guide portion (5) of the valve piece (2), and in that the valve seat surface (8) of the valve piece (2) is formed as an at least substantially conical, annular valve seat surface (8).
  9. Switching valve according to Claim 8, characterized in that the valve piece (2) has an annular recess (7), in that the inner side (10) of the valve closing body (3) delimits a fuel chamber (11) formed by the recess (7), and in that a fuel duct (14) which leads through the valve piece (2) issues into the fuel chamber (11).
  10. Fuel injection valve, in particular injector for fuel injection systems of air-compressing, auto-ignition internal combustion engines, having a switching valve according to one of Claims 1 to 9.
EP10713926.3A 2009-06-05 2010-04-13 Control valve Active EP2438287B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200910026778 DE102009026778A1 (en) 2009-06-05 2009-06-05 switching valve
PCT/EP2010/054798 WO2010139500A1 (en) 2009-06-05 2010-04-13 Control valve

Publications (2)

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EP2438287A1 EP2438287A1 (en) 2012-04-11
EP2438287B1 true EP2438287B1 (en) 2013-06-19

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EP10713926.3A Active EP2438287B1 (en) 2009-06-05 2010-04-13 Control valve

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EP (1) EP2438287B1 (en)
DE (1) DE102009026778A1 (en)
WO (1) WO2010139500A1 (en)

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DE102022122501A1 (en) 2022-09-06 2024-03-07 Zf Cv Systems Europe Bv Valve of a compressor or pump

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006021741A1 (en) 2006-05-10 2007-11-15 Robert Bosch Gmbh Fuel injector with pressure compensated control valve
DE102007009168A1 (en) * 2007-02-26 2008-08-28 Robert Bosch Gmbh Pressure-compensated control valve, has seat limiting surface running between valve element and valve piece, where seat limiting surface is limited by seat disposing edge, which is guided at valve element or at valve piece
DE102007013245A1 (en) * 2007-03-20 2008-09-25 Robert Bosch Gmbh Pressure compensated switching valve
DE102007044357A1 (en) * 2007-06-21 2008-12-24 Robert Bosch Gmbh Control valve for a fuel injection valve
DE102008040639A1 (en) * 2007-10-04 2009-04-09 Robert Bosch Gmbh Pressure-balanced control valve for internal combustion engine, has high pressure chamber loaded with fuel through hole under system pressure, and another high pressure chamber formed in region between valve piece and valve element

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WO2010139500A1 (en) 2010-12-09
EP2438287A1 (en) 2012-04-11

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