EP2278152B1 - Fuel injection valve - Google Patents
Fuel injection valve Download PDFInfo
- Publication number
- EP2278152B1 EP2278152B1 EP20100163387 EP10163387A EP2278152B1 EP 2278152 B1 EP2278152 B1 EP 2278152B1 EP 20100163387 EP20100163387 EP 20100163387 EP 10163387 A EP10163387 A EP 10163387A EP 2278152 B1 EP2278152 B1 EP 2278152B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- bore
- pressure pin
- fuel injection
- injection valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Not-in-force
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
- F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
- F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
- F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
- F02M61/042—The valves being provided with fuel passages
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- 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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
- F02M63/0012—Valves
- F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
- F02M63/0071—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059 characterised by guiding or centering means in valves including the absence of any guiding means, e.g. "flying arrangements"
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- 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
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- 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
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- 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
Definitions
- the invention relates to a fuel injection valve for an internal combustion engine having a control valve for controlling an injection valve member which releases or closes at least one injection port, wherein the control valve has a closing element with a central bore for receiving and guiding a pressure pin and an annular sealing edge, the inner diameter of the diameter Bore corresponds, so that the closing element in the closed position, in which the sealing edge sealingly abuts a valve seat, is pressure balanced.
- Fuel injection valves or fuel injectors of the aforementioned type are known from the prior art.
- the control valve has a closing element with a central bore, in which a pressure pin is received, and an annular sealing edge.
- the inner diameter of the sealing edge corresponds substantially to the diameter of the central bore. This has the effect that in the closed position of the control valve, in which the sealing edge is held in contact with a valve seat, little or no axial compressive forces act on the closing element.
- the control valve is thus pressure balanced.
- Pressure compensated control valves have the advantage that, for example, low closing forces required are to hold the closing element in its sealing seat. The use of a pressure compensated valve thus allows lower spring forces, lower magnetic forces, smaller valve lifts and consequently faster switching times. This in turn gives the usability of the valve in the multiple injection.
- the invention has for its object to further develop a fuel injection valve of the type mentioned in such a way that the above-mentioned disadvantages are eliminated.
- the proposed fuel injector should be simple in design and inexpensive to produce.
- the proposed fuel injection valve according to the invention is characterized in that the control valve also has a pressure limiting function by the pressure pin at a defined pressure force on its valve seat facing end surface by changing its axial position causes a hydraulic connection of the bore with a return. Due to the design of the control valve as a pressure balanced valve, the pressure is on the pressure pin, which is guided in the central bore of the closing element of the control valve and thus has at least in a partial area substantially the same diameter as the bore, the system pressure. In order to establish a hydraulic connection of the bore to the return at a faulty pressure in the system for limiting pressure, this faulty system pressure is defined as a compressive force, which causes a change in the axial position of the pressure pin.
- the compressive force is defined as a limit, it must be exceeded to trigger the pressure limiting function.
- a hydraulic connection of the bore to the return and thus to a low pressure region is effected, so that a pressure decrease takes place within the bore.
- the pressure limiting function is also avoided that the control pressure exceeds a certain limit.
- no additional pressure relief valve is required, but only a pressure-balanced control valve with a sleeve-shaped closing element and an internal, loose pressure pin for pressure equalization.
- a fuel injector with such a control valve can therefore be made compact and thus space-saving. In addition, it is inexpensive to produce due to the absence of an additional pressure relief valve.
- a radial expansion at least in a partial region of the bore is provided for producing the hydraulic connection of the bore with the return, which can be released by changing the axial position of the pressure pin.
- the radial expansion circumferentially, for example by execution of the bore as a stepped bore, or only in a over a limited angular range extending portion take place.
- an additional, for example, housing-side guidance of the pressure pin is to be ensured. If such an additional guide, the pressure pin, the guide portion of the bore for making a hydraulic connection of the bore with the return of the guide area also completely leave.
- At least one axially and / or radially guided flow channel may be provided in the wall of the bore, which is releasable by a change in the axial position of the pressure pin.
- a drainage channel in the form of an axially extending groove in the wall of the bore and / or as radial or obliquely guided and branched off from the central bore hole may be formed.
- Also alternatively or additionally may be provided for the hydraulic connection of the bore with the return in the bore radially inwardly extending stop surface which is engageable with a pressure pin formed on the stop surface, so that upon a change in the axial position of the pressure pin, the closing element is carried at least over a section.
- the closing element is lifted out of its sealing seat.
- the flow connection to the return can thus be effected by the closing element is transferred via an axial displacement of the pressure pin in an open position and / or via the axial displacement of the pressure pin, a further flow connection is released.
- the entrainment of the closing element at least over a partial route can be provided on the closing element in the bore radially inwardly extending annular shoulder, a stop surface for a corresponding formed on the pressure pin stop surface, for example in the form of a annular paragraph, forms.
- the entrainment of the closing element over only a partial distance requires that the pressure pin initially undergoes an axial displacement relative to the closing element over a first partial section until it abuts against the annular shoulder of the bore. Only then is the closing element carried over a further section. Here it lifts off from the sealing seat, so that a pressure equalization takes place via the valve seat.
- the pressure pin is supported on the housing side.
- a stop disc may be provided which breaks at a defined pressure force on the valve seat facing end face of the pressure pin to allow an axial displacement of the pressure pin. The breakage of the stopper disc occurs only when exceeding a predetermined limit, which corresponds to a faulty overpressure in the system.
- the housing side support may preferably also cause additional guidance of the pressure pin, for example, when the pressure pin for making a hydraulic connection of the bore with the return leaves the guide region of the bore.
- the pressure pin is indirectly or directly acted upon by the pressure force of a spring, which is preferably supported on the housing side.
- the spring causes a pressure equalization, so that the pressure pin is held in a specific axial position.
- the spring force can be overcome, so that the pressure pin changes its axial position, that is, moves in the direction of the spring.
- the spring force thus determines the limit whose exceeding causes a change in the axial position of the pressure pin and thus a pressure limit.
- the setting is therefore made on the spring force of the spring and the pressure surface formed on the pressure pin.
- a coil spring, a spring sleeve or a plate spring can be used, which acts on the pressure pin on its end facing away from the valve seat directly or indirectly with a compressive force which is opposite to the system pressure.
- the spring can be supported on the one hand on the housing, on the other hand on a plate which at the same time forms an abutment or abutment surface for the pressure pin.
- a pressure plate is arranged between the pressure pin and the spring.
- the control valve is a solenoid valve and has a movable armature via an electromagnet, which is connected to the closing element.
- the armature can be designed as a closing element of the control valve.
- the anchor preferably has an anchor plate with a valve seat side arranged, sleeve-shaped approach.
- the sleeve body encloses a bore which serves to receive and guide the pressure pin and on whose front side an annular sealing edge is formed, which cooperates sealingly with a valve seat.
- the sealing edge is linear, that is, the annular surface has a small radial extent in order to increase the sealing force.
- the sealing edge may be designed as a biting edge.
- the valve seat is this preferably cone-shaped or formed as a flat seat.
- FIG. 1 illustrated first embodiment of a fuel injection valve according to the invention has a solenoid valve as a control valve 1.
- the solenoid valve comprises an electromagnet 14, which acts on energizing an armature 15 of the solenoid valve, so that it is moved in the direction of the electromagnet 14. Since the armature 15 is also formed as a closing element 4, which cooperates with a valve seat 8 on a valve piece 16, the energization of the solenoid valve causes a lifting of the closing element 4 and thus opening of the valve. In an open position of the valve, fuel can flow out of a control chamber 18 via an outlet throttle 17, so that the pressure in the control chamber 18 drops.
- an injection valve member 2 in the form of a single or multi-part valve needle moves from a closed position to an open position, so that at least one injection port 3 of the fuel injection valve is released.
- the energization of the solenoid valve causes an applied to the armature 15 valve closing spring 19 that a return of the armature is in the closed position of the valve, in which the closing element 4 sealingly abuts with its annular sealing edge 7 on the valve seat 8 of the valve member 16.
- Fuel is supplied to the control chamber 18 via an inlet, so that the pressure in the control chamber 18 rises again to a pressure which finally causes the closing of the nozzle needle, whereby the injection process is terminated.
- the sleeve-shaped closing element 4 of the solenoid valve forms a bore 5, in which a pressure pin 6 is received and guided high pressure-tight.
- the pressure pin 6 thus has - at least in a guide area - the same diameter as the bore 5.
- the sealing edge 7 of the closing element 4 is formed radially inwardly, the inner diameter of the sealing edge 7 also corresponds to the diameter of the bore 5. The valve is thus pressure balanced.
- the closing element 4 of the control valve 1 has at least one radially guided outflow channel 20 for the hydraulic connection the bore 5 with a return on.
- the representation in Fig. 1 are two radially outflow channels 20 to remove in the form of holes that open into the bore 5.
- the axial position of the drainage channels 20 is selected such that their release for establishing a hydraulic connection of the bore 5 with a return requires an axial displacement of the pressure pin 6.
- This in turn requires that the pressure force of a spring 12 is overcome, which acts on the pressure pin 6 and is supported on the housing side.
- An axial displacement of the pressure pin 6 is thus possible only when a definable limit value is exceeded, the determination of the setting of the spring force.
- the spring 12 is also supported on a plate 13 which is arranged between the spring 12 and the pressure pin 6.
- the pressure pin 6 can also rest directly on the spring 12.
- the in Fig. 1 illustrated embodiment of a fuel injection valve according to the invention further axially guided drainage channels 20 in the form of grooves 21 (shown by means of broken lines). These can be arranged as an alternative or in addition to radial run-off channels 20.
- the grooves 21 open into the radially guided flow channels 20.
- the grooves 21 may also be arranged at an axial distance from the radially guided flow channels 20, so that the exposure of the grooves 21 requires a greater axial displacement of the pressure pin 6.
- the grooves 21 may be arranged offset over a certain angular range to the radially guided flow channels 20.
- the number of grooves 21 as well as the number of radially guided drainage channels 20 can be selected according to the respective requirements.
- Fig.2 illustrated embodiment of a fuel injection valve according to the invention differs from that of Fig. 1 in particular characterized in that the closing element 4 of the control valve 1 for implementing the pressure limiting function has an annular, in the bore 5 radially inwardly extending stop surface 10 which is engageable in abutment with a pressure pin 6 correspondingly shaped stop surface 11.
- the bore 5 in the present case is designed as a stepped bore.
- the pressure pin 6, however, has a circumferential radial recess, so that the pressure pin in a has a smaller diameter adjacent to the recess section.
- FIG.2 Another distinguishing feature of the embodiment of the Fig.2 opposite to the Fig.1 shows the use of a plate spring as a spring 12, which is arranged in a housing-side recess of the fuel injection valve.
- Both exemplified embodiments of the present invention show simple and compact fuel injection valves that require little space and are also inexpensive to produce. In addition, the benefits of a pressure balanced valve come into play.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Description
Die Erfindung betrifft ein Kraftstoffeinspritzventil für eine Brennkraftmaschine mit einem Steuerventil zur Steuerung eines Einspritzventilgliedes, das wenigstens eine Einspritzöffnung freigibt oder verschließt, wobei das Steuerventil ein Schließelement mit einer zentralen Bohrung zur Aufnahme und Führung eines Druckstiftes sowie eine ringförmige Dichtkante besitzt, deren Innendurchmesser dem Durchmesser der Bohrung entspricht, so dass das Schließelement in der Schließstellung, in der die Dichtkante dichtend an einem Ventilsitz anliegt, druckausgeglichen ist.The invention relates to a fuel injection valve for an internal combustion engine having a control valve for controlling an injection valve member which releases or closes at least one injection port, wherein the control valve has a closing element with a central bore for receiving and guiding a pressure pin and an annular sealing edge, the inner diameter of the diameter Bore corresponds, so that the closing element in the closed position, in which the sealing edge sealingly abuts a valve seat, is pressure balanced.
Kraftstoffeinspritzventile bzw. Kraftstoffinjektoren der vorstehend genannten Art sind aus dem Stand der Technik bekannt. Als Beispiel wird auf die Druckschrift
Als nachteilig erweist sich jedoch bei den aus dem Stand der Technik bekannten druckausgeglichenen Ventilen, dass sie bei einem fehlerhaften Überdruck im System nicht selbständig öffnen. Aus diesem Grund ist daher in der Regel zusätzlich ein Druckbegrenzungsventil vorgesehen, das sich jedoch ungünstig auf den erforderlichen Bauraum und die Kosten auswirkt.However, it proves to be disadvantageous in the pressure-balanced valves known from the prior art that they do not open automatically in the event of a faulty overpressure in the system. For this reason, therefore, a pressure relief valve is usually provided in addition, however, which has an unfavorable effect on the required space and the cost.
Der Erfindung liegt die Aufgabe zugrunde, ein Kraftstoffeinspritzventil der eingangs genannten Art derart weiter zu entwickeln, dass die vorstehend genannten Nachteile beseitigt werden. Insbesondere soll der vorgeschlagene Kraftstoffinjektor einfach aufgebaut und kostengünstig herstellbar sein.The invention has for its object to further develop a fuel injection valve of the type mentioned in such a way that the above-mentioned disadvantages are eliminated. In particular, the proposed fuel injector should be simple in design and inexpensive to produce.
Zur Lösung der Aufgabe wird ein Kraftstoffeinspritzventil mit den Merkmalen des Anspruchs 1 vorgeschlagen. Vorteilhafte Weiterbildungen der Erfindung werden in den Unteransprüchen beschrieben.To solve the problem, a fuel injection valve with the features of claim 1 is proposed. Advantageous developments of the invention are described in the subclaims.
Das vorgeschlagene Kraftstoffeinspritzventil zeichnet sich erfindungsgemäß dadurch aus, dass das Steuerventil zudem eine Druckbegrenzungsfunktion besitzt, indem der Druckstift bei einer definierten Druckkraft an seiner dem Ventilsitz zugewandten Stirnfläche durch Veränderung seiner axialen Lage eine hydraulische Verbindung der Bohrung mit einem Rücklauf bewirkt. Aufgrund der Ausführung des Steuerventils als druckausgeglichenes Ventil, liegt am Druckstift, der hochdruckdicht in der zentralen Bohrung des Schließelementes des Steuerventils geführt ist und damit zumindest in einem Teilbereich im Wesentlichen den gleichen Durchmesser wie die Bohrung besitzt, der Systemdruck an. Um bei einem fehlerhaften Überdruck im System zur Druckbegrenzung eine hydraulische Verbindung der Bohrung zum Rücklauf herzustellen, wird dieser fehlerhafte Systemdruck als Druckkraft definiert, die eine Veränderung der axialen Lage des Druckstiftes bewirkt. Vorzugsweise wird die Druckkraft als Grenzwert definiert, den es zur Auslösung der Druckbegrenzungsfunktion zu überschreiten gilt. Durch die Veränderung der axialen Lage des Druckstiftes wird dann eine hydraulische Verbindung der Bohrung zum Rücklauf und damit zu einem Niederdruckbereich bewirkt, so dass eine Druckabnahme innerhalb der Bohrung erfolgt. Da die Bohrung über Drosseln in Verbindung mit einem als Steuerraum ausgelegten Druckraum steht, wird durch die Druckbegrenzungsfunktion zugleich vermieden, dass der Steuerdruck einen bestimmten Grenzwert übersteigt. Zur Druckbegrenzung ist somit kein zusätzliches Druckbegrenzungsventil erforderlich, sondern lediglich ein druckausgeglichenes Steuerventil mit einem hülsenförmigen Schließelement und einem innen liegenden, losen Druckstift zum Druckausgleich. Ein Kraftstoffinjektor mit einem solchen Steuerventil kann demnach kompakt und damit bauraumschonend ausgeführt werden. Zudem ist es aufgrund des Verzichtes auf ein zusätzliches Druckbegrenzungsventil kostengünstig herstellbar.The proposed fuel injection valve according to the invention is characterized in that the control valve also has a pressure limiting function by the pressure pin at a defined pressure force on its valve seat facing end surface by changing its axial position causes a hydraulic connection of the bore with a return. Due to the design of the control valve as a pressure balanced valve, the pressure is on the pressure pin, which is guided in the central bore of the closing element of the control valve and thus has at least in a partial area substantially the same diameter as the bore, the system pressure. In order to establish a hydraulic connection of the bore to the return at a faulty pressure in the system for limiting pressure, this faulty system pressure is defined as a compressive force, which causes a change in the axial position of the pressure pin. Preferably, the compressive force is defined as a limit, it must be exceeded to trigger the pressure limiting function. By changing the axial position of the pressure pin, a hydraulic connection of the bore to the return and thus to a low pressure region is effected, so that a pressure decrease takes place within the bore. Since the bore via throttles is in connection with a designed as a control chamber pressure chamber, the pressure limiting function is also avoided that the control pressure exceeds a certain limit. For pressure relief, therefore, no additional pressure relief valve is required, but only a pressure-balanced control valve with a sleeve-shaped closing element and an internal, loose pressure pin for pressure equalization. A fuel injector with such a control valve can therefore be made compact and thus space-saving. In addition, it is inexpensive to produce due to the absence of an additional pressure relief valve.
Nach einer bevorzugten Ausführungsform der Erfindung ist zur Herstellung der hydraulischen Verbindung der Bohrung mit dem Rücklauf eine radiale Aufweitung zumindest in einem Teilbereich der Bohrung vorgesehen, die durch eine Veränderung der axialen Lage des Druckstiftes freigebbar ist. In dem Bereich der radialen Aufweitung wird somit die hochdruckdichte Führung des Druckstiftes innerhalb der Bohrung aufgegeben. Dabei kann die radiale Aufweitung umlaufend, beispielsweise durch Ausführung der Bohrung als Stufenbohrung, oder lediglich in einem sich über einen begrenzten Winkelbereich erstreckenden Teilabschnitt erfolgen. Gegebenenfalls ist bei einer umlaufenden ringförmigen Aufweitung der zentralen Bohrung des Schließelementes für eine zusätzliche, beispielsweise gehäuseseitige Führung des Druckstiftes zu sorgen. Besteht eine solche zusätzliche Führung kann der Druckstift den Führungsbereich der Bohrung zur Herstellung einer hydraulischen Verbindung der Bohrung mit dem Rücklauf den Führungsbereich auch vollständig verlassen.According to a preferred embodiment of the invention, a radial expansion at least in a partial region of the bore is provided for producing the hydraulic connection of the bore with the return, which can be released by changing the axial position of the pressure pin. In the area of the radial expansion thus the high-pressure-tight leadership of the pressure pin is abandoned within the bore. In this case, the radial expansion circumferentially, for example by execution of the bore as a stepped bore, or only in a over a limited angular range extending portion take place. Optionally, in the case of a peripheral annular widening of the central bore of the closing element, an additional, for example, housing-side guidance of the pressure pin is to be ensured. If such an additional guide, the pressure pin, the guide portion of the bore for making a hydraulic connection of the bore with the return of the guide area also completely leave.
Alternativ oder ergänzend kann zur Herstellung der hydraulischen Verbindung der Bohrung mit dem Rücklauf wenigstens ein axial und/oder radial geführter Ablaufkanal in der Wandung der Bohrung vorgesehen sein, der durch eine Veränderung der axialen Lage des Druckstiftes freigebbar ist. Beispielsweise kann ein solcher Ablaufkanal in Form einer axial verlaufenden Nut in der Wandung der Bohrung und/oder als radial oder schräg geführte und von der zentralen Bohrung abzweigende Bohrung ausgebildet sein.Alternatively or additionally, for the preparation of the hydraulic connection of the bore with the return at least one axially and / or radially guided flow channel may be provided in the wall of the bore, which is releasable by a change in the axial position of the pressure pin. For example, such a drainage channel in the form of an axially extending groove in the wall of the bore and / or as radial or obliquely guided and branched off from the central bore hole may be formed.
Ebenfalls alternativ oder ergänzend kann zur hydraulischen Verbindung der Bohrung mit dem Rücklauf eine sich in die Bohrung nach radial innen erstreckende Anschlagfläche vorgesehen sein, die in Anlage mit einer am Druckstift ausgebildeten Anschlagfläche bringbar ist, so dass bei einer Veränderung der axialen Lage des Druckstiftes das Schließelement zumindest über eine Teilstrecke mitgeführt wird. Dabei wird das Schließelement aus seinem Dichtsitz gehoben. Die Strömungsverbindung zum Rücklauf kann demnach dadurch bewirkt werden, dass das Schließelement über eine axiale Verschiebung des Druckstiftes in eine Offenstellung überführt wird und/oder über die axiale Verschiebung des Druckstiftes eine weitere Strömungsverbindung freigegeben wird. Die einzelnen Maßnahmen sind somit auch kumulativ anwendbar. Soll bei einer axialen Verschiebung des Druckstiftes die Mitnahme des Schließelementes zumindest über eine Teilstrecke erfolgen, kann hierzu am Schließelement ein sich in die Bohrung nach radial innen erstreckender ringförmiger Absatz vorgesehen sein, der eine Anschlagfläche für eine korrespondierend am Druckstift ausgebildete Anschlagfläche, beispielsweise in Form eines ringförmigen Absatzes, bildet. Die Mitnahme des Schließelementes über lediglich eine Teilstrecke setzt voraus, dass der Druckstift zunächst über eine erste Teilstrecke eine axiale Verschiebung gegenüber dem Schließelement erfährt, bis er am ringförmigen Absatz der Bohrung anschlägt. Erst dann wird das Schließelement über eine weitere Teilstrecke mitgeführt. Hierbei hebt es vom Dichtsitz ab, so dass ein Druckausgleich über den Ventilsitz erfolgt.Also alternatively or additionally may be provided for the hydraulic connection of the bore with the return in the bore radially inwardly extending stop surface which is engageable with a pressure pin formed on the stop surface, so that upon a change in the axial position of the pressure pin, the closing element is carried at least over a section. The closing element is lifted out of its sealing seat. The flow connection to the return can thus be effected by the closing element is transferred via an axial displacement of the pressure pin in an open position and / or via the axial displacement of the pressure pin, a further flow connection is released. The individual measures are therefore also cumulatively applicable. If at an axial displacement of the pressure pin, the entrainment of the closing element at least over a partial route, this can be provided on the closing element in the bore radially inwardly extending annular shoulder, a stop surface for a corresponding formed on the pressure pin stop surface, for example in the form of a annular paragraph, forms. The entrainment of the closing element over only a partial distance requires that the pressure pin initially undergoes an axial displacement relative to the closing element over a first partial section until it abuts against the annular shoulder of the bore. Only then is the closing element carried over a further section. Here it lifts off from the sealing seat, so that a pressure equalization takes place via the valve seat.
Gemäß einer weiteren vorteilhaften Ausführungsform ist der Druckstift gehäuseseitig abgestützt. Zur Abstützung kann beispielsweise eine Anschlagscheibe vorgesehen sein, die bei Überschreiten einer definierten Druckkraft an der dem Ventilsitz zugewandten Stirnfläche des Druckstiftes bricht, um eine axiale Verschiebung des Druckstiftes zuzulassen. Der Sollbruch der Anschlagscheibe erfolgt erst bei Überschreiten eines vorher festgelegten Grenzwertes, der einem fehlerhaften Überdruck im System entspricht. Die gehäuseseitge Abstützung kann vorzugsweise auch eine zusätzliche Führung des Druckstiftes bewirken, wenn zum Beispiel der Druckstift zur Herstellung einer hydraulischen Verbindung der Bohrung mit dem Rücklauf den Führungsbereich der Bohrung verlässt.According to a further advantageous embodiment, the pressure pin is supported on the housing side. To support, for example, a stop disc may be provided which breaks at a defined pressure force on the valve seat facing end face of the pressure pin to allow an axial displacement of the pressure pin. The breakage of the stopper disc occurs only when exceeding a predetermined limit, which corresponds to a faulty overpressure in the system. The housing side support may preferably also cause additional guidance of the pressure pin, for example, when the pressure pin for making a hydraulic connection of the bore with the return leaves the guide region of the bore.
Gemäß einer weiteren Ausführungsform ist alternativ vorgesehen, dass der Druckstift mittelbar oder unmittelbar durch die Druckkraft einer Feder beaufschlagt wird, die vorzugsweise gehäuseseitig abgestützt ist. Dabei bewirkt die Feder einen Druckausgleich, so dass der Druckstift in einer bestimmten axialen Lage gehalten wird. Steigt jedoch der Systemdruck an, kann die Federkraft überwunden werden, so dass der Druckstift seine axiale Lage verändert, das heißt, sich in Richtung der Feder bewegt. Die Federkraft bestimmt demnach den Grenzwert, dessen Überschreiten eine Veränderung der axialen Lage des Druckstiftes und damit eine Druckbegrenzung bewirkt. Die Einstellung erfolgt demnach über die Federkraft der Feder und die am Druckstift ausgebildete Druckfläche. Als Feder eigenen sich verschiedene Arten von Federelementen. Beispielsweise kann eine Schraubenfeder, eine Federhülse oder eine Tellerfeder eingesetzt werden, die den Druckstift an seiner dem Ventilsitz abgewandten Stirnseite unmittelbar oder mittelbar mit einer Druckkraft beaufschlagt, die dem Systemdruck entgegengesetzt ist. Zur mittelbaren Druckkraftbeaufschlagung kann die Feder einerseits am Gehäuse, andererseits an einer Platte abgestützt sein, die zugleich eine Anlage- bzw. Anschlagfläche für den Druckstift bildet. Gemäß einer vorteilhaften Ausführungsform ist daher zwischen Druckstift und Feder eine Druckplatte angeordnet.According to another embodiment, it is alternatively provided that the pressure pin is indirectly or directly acted upon by the pressure force of a spring, which is preferably supported on the housing side. The spring causes a pressure equalization, so that the pressure pin is held in a specific axial position. However, if the system pressure increases, the spring force can be overcome, so that the pressure pin changes its axial position, that is, moves in the direction of the spring. The spring force thus determines the limit whose exceeding causes a change in the axial position of the pressure pin and thus a pressure limit. The setting is therefore made on the spring force of the spring and the pressure surface formed on the pressure pin. As spring own different types of spring elements. For example, a coil spring, a spring sleeve or a plate spring can be used, which acts on the pressure pin on its end facing away from the valve seat directly or indirectly with a compressive force which is opposite to the system pressure. For indirect pressure force application, the spring can be supported on the one hand on the housing, on the other hand on a plate which at the same time forms an abutment or abutment surface for the pressure pin. According to an advantageous embodiment, therefore, a pressure plate is arranged between the pressure pin and the spring.
Weiterhin vorzugsweise ist das Steuerventil ein Magnetventil und besitzt einen über einen Elektromagneten bewegbaren Anker, der mit dem Schließelement verbunden ist. Alternativ kann auch der Anker als Schließelement des Steuerventils ausgebildet sein. Hierzu weist der Anker vorzugsweise eine Ankerplatte mit einem ventilsitzseitig angeordneten, hülsenförmigen Ansatz auf. Der Hülsenkörper umschließt eine Bohrung, die der Aufnahme und Führung des Druckstiftes dient und an dessen Stirnseite eine ringförmige Dichtkante ausgebildet ist, die mit einem Ventilsitz dichtend zusammenwirkt. Vorzugsweise ist die Dichtkante linienförmig, das heißt, dass die Ringfläche eine geringe radiale Erstreckung aufweist, um die Dichtkraft zu erhöhen. Beispielsweise kann die Dichtkante als Beißkante ausgeführt sein. Der Ventilsitz ist hierzu bevorzugt kegelförmig oder als Flachsitz ausgebildet.Further preferably, the control valve is a solenoid valve and has a movable armature via an electromagnet, which is connected to the closing element. Alternatively, the armature can be designed as a closing element of the control valve. For this purpose, the anchor preferably has an anchor plate with a valve seat side arranged, sleeve-shaped approach. The sleeve body encloses a bore which serves to receive and guide the pressure pin and on whose front side an annular sealing edge is formed, which cooperates sealingly with a valve seat. Preferably, the sealing edge is linear, that is, the annular surface has a small radial extent in order to increase the sealing force. For example, the sealing edge may be designed as a biting edge. The valve seat is this preferably cone-shaped or formed as a flat seat.
Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der Zeichnungen näher erläutert. Diese zeigen:
- Fig. 1
- eine Schnittansicht längs durch ein Kraftstoffeinspritzventil gemäß einer ersten Ausführungsform und
- Fig. 2
- eine Schnittansicht längs durch ein Kraftstoffeinspritzventil gemäß einer zwei- ten Ausführungsform der Erfindung.
- Fig. 1
- a sectional view along through a fuel injection valve according to a first embodiment and
- Fig. 2
- a sectional view along through a fuel injection valve according to a second embodiment of the invention.
Das in
Das hülsenförmige Schließelement 4 des Magnetventils bildet eine Bohrung 5 aus, in der ein Druckstift 6 aufgenommen und hochdruckdicht geführt ist. Der Druckstift 6 weist somit - zumindest in einem Führungsbereich - den gleichen Durchmesser wie die Bohrung 5 auf. Indem die Dichtkante 7 des Schließelementes 4 radial innenliegend ausgebildet ist, entspricht der Innendurchmesser der Dichtkante 7 ebenfalls dem Durchmesser der Bohrung 5. Das Ventil ist somit druckausgeglichen.The sleeve-shaped
Zur Umsetzung der Druckbegrenzungsfunktion weist das Schließelement 4 des Steuerventils 1 wenigstens einen radial geführten Ablaufkanal 20 zur hydraulischen Verbindung der Bohrung 5 mit einem Rücklauf auf. Der Darstellung in
Zur Umsetzung der Druckbegrenzungsfunktion weist das in
Das in der
Ein weiteres unterscheidendes Merkmal der Ausführungsform der
Beide beispielhaft gezeigten Ausführungsformen der vorliegenden Erfindung zeigen einfach und kompakt aufgebaute Kraftstoffeinspritzventile, die wenig Bauraum beanspruchen und ferner kostengünstig herstellbar sind. Zudem kommen die Vorteile eines druckausgeglichenen Ventils zum Tragen.Both exemplified embodiments of the present invention show simple and compact fuel injection valves that require little space and are also inexpensive to produce. In addition, the benefits of a pressure balanced valve come into play.
Claims (7)
- Fuel injection valve for an internal combustion engine, having a control valve (1) for controlling an injection valve member (2) which opens up or closes off at least one injection opening (3), wherein the control valve (1) has a closing element (4) with a central bore (5) for receiving and guiding a pressure pin (6) and has an annular sealing edge (7), the diameter of which substantially corresponds to the diameter of the bore (5), such that the closing element (4) is substantially pressure-balanced when in the closed position in which the sealing edge (7) bears sealingly against a valve seat (8),
characterized in that the control valve (1) also has a pressure-limiting function in that the pressure pin (6), when acted on with a defined pressure force on its end surface (9) facing toward the valve seat (8), produces a hydraulic connection of the bore (5) to a return line as a result of a change in the axial position of said pressure pin. - Fuel injection valve according to Claim 1,
characterized in that, to produce the hydraulic connection of the bore (5) to the return line, a radial widening is provided at least in a sub-region of the bore, which radial widening can be opened up as a result of a change in the axial position of the pressure pin (6). - Fuel injection valve according to Claim 1 or 2,
characterized in that, to produce the hydraulic connection of the bore (5) to the return line, at least one axially and/or radially extending outflow duct (20) is provided in the wall of the bore (5), which outflow duct can be opened up as a result of a change in the axial position of the pressure pin (6). - Fuel injection valve according to one of the preceding claims,
characterized in that, for the hydraulic connection of the bore (5) to the return line, an abutment surface (10) is provided which extends radially inward into the bore (5) and which can be placed in contact with an abutment surface (11) formed on the pressure pin (6), such that, during a change in the axial position of the pressure pin (6), the closing element (4) is driven along at least over a section of travel. - Fuel injection valve according to one of the preceding claims,
characterized in that the pressure pin (6) is acted on indirectly or directly by the pressure force of a spring (12) which is preferably supported on the housing. - Fuel injection valve according to Claim 5,
characterized in that a pressure plate (13) is arranged between the pressure pin (6) and spring (12). - Fuel injection valve according to one of the preceding claims,
characterized in that the control valve (1) is a solenoid valve and has an armature (15) which can be moved by means of an electromagnet (14), which armature is connected to the closing element (4) or is formed as a closing element.
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200910027841 DE102009027841A1 (en) | 2009-07-20 | 2009-07-20 | Fuel injection valve |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2278152A1 EP2278152A1 (en) | 2011-01-26 |
EP2278152B1 true EP2278152B1 (en) | 2014-01-22 |
Family
ID=42813120
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP20100163387 Not-in-force EP2278152B1 (en) | 2009-07-20 | 2010-05-20 | Fuel injection valve |
Country Status (2)
Country | Link |
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EP (1) | EP2278152B1 (en) |
DE (1) | DE102009027841A1 (en) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9297473B2 (en) | 2011-09-28 | 2016-03-29 | Nabtesco Corporation | Solenoid valve with armature guide |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102012224403A1 (en) * | 2012-12-27 | 2014-07-03 | Robert Bosch Gmbh | Pressure control valve for a fuel injection system |
DE102014225323A1 (en) | 2014-12-09 | 2016-06-09 | Robert Bosch Gmbh | Shift or pressure control valve for a fuel injection system |
DE102016224208A1 (en) * | 2016-12-06 | 2018-06-07 | Robert Bosch Gmbh | Electromagnetically actuable control valve for a fuel injector, fuel injector |
Family Cites Families (3)
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 |
DE102007047152A1 (en) * | 2007-10-02 | 2009-04-09 | Robert Bosch Gmbh | Injector with an annulus separate anchor space |
DE102007047129A1 (en) * | 2007-10-02 | 2009-04-09 | Robert Bosch Gmbh | Injector with sleeve-shaped control valve element |
-
2009
- 2009-07-20 DE DE200910027841 patent/DE102009027841A1/en not_active Withdrawn
-
2010
- 2010-05-20 EP EP20100163387 patent/EP2278152B1/en not_active Not-in-force
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9297473B2 (en) | 2011-09-28 | 2016-03-29 | Nabtesco Corporation | Solenoid valve with armature guide |
Also Published As
Publication number | Publication date |
---|---|
EP2278152A1 (en) | 2011-01-26 |
DE102009027841A1 (en) | 2011-01-27 |
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