EP2357353B1 - Method for recognising the closing point of an injection valve body in a fuel injection valve and fuel injection valve - Google Patents

Method for recognising the closing point of an injection valve body in a fuel injection valve and fuel injection valve Download PDF

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Publication number
EP2357353B1
EP2357353B1 EP11150104.5A EP11150104A EP2357353B1 EP 2357353 B1 EP2357353 B1 EP 2357353B1 EP 11150104 A EP11150104 A EP 11150104A EP 2357353 B1 EP2357353 B1 EP 2357353B1
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EP
European Patent Office
Prior art keywords
injection valve
coil
fuel injection
magnetic circuit
spring element
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
EP11150104.5A
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German (de)
French (fr)
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EP2357353A3 (en
EP2357353A2 (en
Inventor
Nestor Rodriguez-Amaya
Siegfried Ruthardt
Holger Rapp
Wolfgang Stoecklein
Bernd Berghaenel
Marco Beier
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2357353A2 publication Critical patent/EP2357353A2/en
Publication of EP2357353A3 publication Critical patent/EP2357353A3/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/005—Arrangement of electrical wires and connections, e.g. wire harness, sockets, plugs; Arrangement of electronic control circuits in or on fuel injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M57/00—Fuel-injectors combined or associated with other devices
    • F02M57/005—Fuel-injectors combined or associated with other devices the devices being sensors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0017—Valves characterised by the valve actuating means electrical, e.g. using solenoid using electromagnetic operating means
    • 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
    • F02M63/0073—Pressure balanced 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of fuel-injection apparatus
    • F02M65/005—Measuring or detecting injection-valve lift, e.g. to determine injection timing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D41/00—Electrical control of supply of combustible mixture or its constituents
    • F02D41/20—Output circuits, e.g. for controlling currents in command coils
    • F02D2041/202—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit
    • F02D2041/2055—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit with means for determining actual opening or closing time
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02D—CONTROLLING COMBUSTION ENGINES
    • F02D2200/00—Input parameters for engine control
    • F02D2200/02—Input parameters for engine control the parameters being related to the engine
    • F02D2200/06—Fuel or fuel supply system parameters
    • F02D2200/063—Lift of the valve needle

Definitions

  • the invention relates to a method for detecting the closing time of an injection valve member in a fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine and a suitable fuel injection valve.
  • the closing time of the injection valve member allows conclusions about the injection duration, wherein the injection duration and the injection pressure determine the injected amount of fuel.
  • factors such as manufacturing tolerances, wear of components and pressure waves occurring in the system, which can lead to inaccuracies in the amount of fuel injected.
  • These influencing variables gain in importance, in particular, when the actuation of the injection valve member takes place indirectly via an actuator-operated servo valve.
  • deviations often occur which have an influence on the opening duration of the injection valve member and thus on the injection duration.
  • a decisive factor is the dynamic behavior of the servo valve.
  • a fuel injector with a measuring device for detecting the end of an injection process or the detection of the stop of an opening stroke of a nozzle needle is known.
  • the measuring device is designed as an eddy current sensor with a measuring body.
  • the measuring body surrounds a movement device, in particular a nozzle needle, which has a magnetization at least in the area of its enclosure by the measuring body.
  • the measuring device is operated with constant direct current or with a constant direct voltage, wherein a deviation from the direct current or the direct current serves as a measuring signal.
  • the change in the periodic nozzle needle movement results in a change in the measuring signal output by means of the measuring device in the form of a discontinuity.
  • the Hubanschlags- or closing times of periodically consecutive opening or closing cycles are determined.
  • the proposed measuring device is an additional component, which applies to be integrated into a housing part of the injector.
  • separate electrical connections for the measuring device are required. The design effort is therefore high.
  • the invention has for its object to provide a simple method and a simple design fuel injector, which allow the detection of the closing time of the nozzle needle and consequently a high accuracy in the determination of the injection quantity.
  • a fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine with a solenoid valve for driving an injection valve member, wherein opening or closing of the solenoid valve, the injection valve member in the closing direction acting hydraulic pressure is changed in a control room.
  • the solenoid valve of the proposed fuel injection valve comprises an axially displaceably mounted and supported on a spring element anchor bolt, which is acted upon by an axial force which is proportional to the hydraulic pressure in the control chamber.
  • coupling means are provided, via which the spring element and a coil of at least one magnetic circuit are coupled and which cause a detectable parameter change, preferably a change in the coil voltage or the coil current, in at least one magnetic circuit during an elastic deformation of the spring element.
  • the solenoid valve is also preferably a pressure balanced solenoid valve, wherein the pressure compensation takes place via the anchor bolt, which is guided in a guide bore of the armature.
  • the guide diameter of the armature and the seat diameter of the solenoid valve is approximately the same.
  • the proposed fuel injection valve allows the implementation of one of the above-described method according to the invention, apply in the Related to the advantages described also for the fuel injection valve.
  • the proposed fuel injection valve is simple and inexpensive to produce.
  • the spring element and the coil of the magnetic circuit are mechanically coupled via the coupling means.
  • An elastic deformation of the spring element also causes a change in position of the coil relative to a magnetic core and consequently a detectable parameter change in the magnetic circuit.
  • a mechanical coupling is easy to produce, for example via rod-shaped coupling elements, which are connected on the one hand with the coil and on the other hand with the spring element.
  • rod-shaped coupling elements which are connected on the one hand with the coil and on the other hand with the spring element.
  • the coupling means may for example be designed such that they bring about a reversal of direction and / or a path translation.
  • the position change of the coil can therefore be set counter to the direction of movement of the anchor bolt and / or the path of the coil may be greater or smaller than the path of the anchor bolt. It is essential that the coil is arranged such that it can also change its position. Preferably, therefore, the coil is mounted at least axially displaceable.
  • a second magnetic circuit with a second coil is provided as the coupling means, and an elastic deformation of the spring element causes a detectable parameter change at least in the second magnetic circuit.
  • the coil of the second magnetic circuit can be arranged in or on the spring element, for example as a printed flat coil fastened by gluing, or in or on the magnetic core of the primary circuit.
  • an air gap is formed between the coil and the magnetic core or the coil and the spring element, which changes with elastic deformation of the spring element and thus leads to a change in the inductance of the magnetic circuit.
  • the second coil of the second magnetic circuit and the first coil of the first magnetic circuit are connected in parallel or in series. These measures make the arrangement of other electrical lines outside the fuel injector dispensable.
  • the solenoid valve of a fuel injection valve according to the invention is substantially balanced.
  • the armature pin of the solenoid valve is received in a guide bore of an armature, wherein the diameter of the guide bore and the diameter of a valve seat cooperating with the armature are approximately equal.
  • the hydraulic force does not act on the movable armature via the surface enclosed by the seat line of the valve as an opening force, but on the anchor bolt supported on the spring element.
  • the spring element can be designed as an elastically deformable support plate. To increase the elasticity of the support plate may be provided in this recesses. These are to be designed such that the magnetic flux is not affected in the second magnetic circuit.
  • the inventive method utilizes the fact that the solenoid valve is closed during the closing phase of the fuel injection valve and in the pressure chamber of the solenoid valve, the control chamber pressure prevails. This control chamber pressure - and consequently the force acting on the anchor bolt Axiakraft floc to a clear minimum. Immediately after closing the injection valve member, there is a rapid increase in the control chamber pressure, which also causes an increase in the force acting on the anchor bolt axial force.
  • This change in force results in a fuel injector according to the invention to an elastic deformation of the spring element, wherein the provided coupling means translate the elastic deformation of the spring element in a change in position of a coil of a magnetic circuit and / or in a change in size of an air gap, which in turn a parameter change in which the coil and / or the air gap Magnetic circuit entails. Based on this parameter change, the closing time of the injection valve member can then be determined.
  • a known fuel injection valve has a in a first housing part 16 (nozzle body) liftably guided injection valve member 1 in the form of a nozzle needle, to which a valve piston 15 is attached as an extension.
  • the valve piston 15 is also guided in a liftable manner in a second housing part 16 (injector body) and received in a valve piece 18 at its end facing away from the nozzle needle.
  • a control chamber 3 Inside the valve piece 18 is limited by the valve piston 15, a control chamber 3, in which in the closed position of a solenoid valve 2, a valve piston 15 and thus the injection valve member 1 in the closing direction acting hydraulic pressure prevails.
  • the hydraulic pressure in the control chamber 3 that acts on the injection valve member 1 in the closing direction is ensured by an inlet throttle 21, which is in communication with a high-pressure port 20 for the supply of fuel under high pressure.
  • the high pressure port 20 is further in communication with a high pressure bore 17 through which the high pressure fuel is supplied to at least one injection port of the fuel injection valve.
  • the control chamber 3 a further throttle, namely an outlet throttle 22, via which a hydraulic connection of the control chamber 3 is made with a pressure chamber 24 of the solenoid valve 2 (see also Fig. 4 and 5 ).
  • a further throttle namely an outlet throttle 22
  • fuel can flow out of the control chamber 3 and the pressure chamber 24 of the solenoid valve 2 via the outlet throttle 22 and the valve seat 14 in the pressure chamber 24 of the solenoid valve 2.
  • the result is a pressure drop in the control chamber 3, which has an opening stroke of the injection valve member 1 result.
  • this is energized, so that cooperating with the valve seat 14 armature 13 of the solenoid valve 2 is lifted from its sealing seat and the valve seat 14 opens.
  • an electrical connection 19 is provided on the fuel injection valve (see Fig. 1 ).
  • control chamber pressure reaches its minimum immediately before the start of the opening stroke of the injection valve member.
  • the spring element 4 is formed as a plate spring and supported on a serving as a support plate housing part 16.
  • the anchor bolt 5 is surrounded by a magnetic core 11 in which a coil 7 is received.
  • coupling means 6 are provided which mechanically connect the coil 7 with the spring element 4 in such a way that an elastic deformation of the spring element 4 causes a change in position of the coil 7 relative to the magnetic core 11.
  • the coil 7 is axially displaceable for this purpose received in the magnetic core 11 and the magnetic core 11 via a clamping element 23 which biases the magnetic core 11 relative to a radial shoulder on the housing part 16, fixed in position.
  • the change in position of the coil 7 leads to a parameter change, for example a change in the coil voltage or the coil current, in the existing magnetic circuit 9, so that the closing time of the injection valve member 1 can be reliably detected via the detection of the parameter change.
  • FIG. 5 An alternative embodiment is from the Fig. 5 out.
  • the spring element 4 is designed differently and the mechanical coupling of the spring element 4 with the coil 7 via the coupling means 6 in such a way that the change in position of the coil 7 takes place in the opposite direction to the movement of the anchor bolt 5. It can thus be effected a direction reversal.
  • the path of the coil 7 differ from the path of the anchor bolt 5, so that further a path translation is realized.
  • FIG. 6 Another alternative embodiment is in Fig. 6 shown.
  • a coupling means 6 a further magnetic circuit 10 with a further coil. 8 used.
  • the housing-side support plate forms the spring element 4, which is therefore designed elastically deformable.
  • the second coil 8 is received in the magnetic core 11 and between the magnetic core 11 and the spring element 4, an air gap 25 is formed, which changes in an elastic deformation of the spring element 4, in this case enlarged.
  • This has the consequence that the inductance in the magnetic circuit 10 changes.
  • There is a parameter change which in turn is detectable and allows a conclusion on the closing time of the injection valve member 1.
  • the Fig. 7 shows a modification of the embodiment of the Fig. 6 , The difference is that the second coil 8 is integrated into the spring element 4. In the case of an elastic deformation of the spring element 4, a change in the position of the coil 8 takes place, which likewise results in the air gap 25 being enlarged.
  • the respective second coil 8 is connected in parallel or in series with the coil 7 of the primary circuit.
  • the parallel connection is exemplary for the embodiment of the Fig. 7 in Fig. 8 shown.
  • Fig. 9 shows the corresponding series connection. While in parallel connection, the inductance of the second coil 8 must be selected to be high in comparison to the first coil 7 in order not to impair the function of the primary circuit, it is the other way round in the series connection. That is, in the series connection, the number of turns of the second coil 8 may be smaller than that of the first coil 7.
  • the invention By detecting the closing time of the injection valve member, not only the dynamic behavior of the servo valve is taken into account in the determination of the injection duration, but all possible inaccuracies within the entire switching chain from the actuator to the nozzle needle or to the injection valve member.
  • the invention is capable of compensating for example scattering of similar valves, as well as their drift over the life and the influence of variable influencing variables, such as the influence of pressure oscillations.
  • the injected amount of fuel is therefore determinable and adjustable with higher accuracy.

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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)
  • Analytical Chemistry (AREA)
  • Fluid Mechanics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Description

Die Erfindung betrifft ein Verfahren zur Erkennung des Schließzeitpunktes eines Einspritzventilgliedes in einem Kraftstoffeinspritzventil zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine sowie ein hierzu geeignetes Kraftstoffeinspritzventil.The invention relates to a method for detecting the closing time of an injection valve member in a fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine and a suitable fuel injection valve.

Der Schließzeitpunkt des Einspritzventilgliedes lässt Rückschlüsse auf die Einspritzdauer zu, wobei die Einspritzdauer und der Einspritzdruck die eingespritzte Kraftstoffmenge bestimmen. Darüber hinaus gibt es weitere Einflussgrößen, wie beispielsweise Fertigungstoleranzen, Verschleiß von Bauteilen und im System auftretende Druckwellen, die zu Ungenauigkeiten in Bezug auf die eingespritzte Kraftstoffmenge führen können. Diese Einflussgrößen gewinnen insbesondere dann an Bedeutung, wenn die Betätigung des Einspritzventilgliedes indirekt über ein aktorbetätigtes Servoventil erfolgt. Denn innerhalb der Schaltkette vom Aktor, über das Servoventil und die Hochdruckhydraulik bis hin zum Einspritzventilglied kommt es oftmals zu Abweichungen, die Einfluss auf die Öffnungsdauer des Einspritzventilgliedes und damit auf die Einspritzdauer haben. Einen mitbestimmenden Faktor stellt dabei auch das dynamische Verhalten des Servoventils dar.The closing time of the injection valve member allows conclusions about the injection duration, wherein the injection duration and the injection pressure determine the injected amount of fuel. In addition, there are other factors, such as manufacturing tolerances, wear of components and pressure waves occurring in the system, which can lead to inaccuracies in the amount of fuel injected. These influencing variables gain in importance, in particular, when the actuation of the injection valve member takes place indirectly via an actuator-operated servo valve. Within the switching chain from the actuator, via the servo valve and the high-pressure hydraulics to the injection valve member, deviations often occur which have an influence on the opening duration of the injection valve member and thus on the injection duration. A decisive factor is the dynamic behavior of the servo valve.

Stand der TechnikState of the art

Aus dem Stand der Technik sind bereits verschiedene Verfahren und/oder Vorrichtungen zur Bestimmung der Öffnungsdauer eines Einspritzventilgliedes bekannt, um die Genauigkeit der eingespritzten Kraftstoffmenge zu optimieren.Various methods and / or devices for determining the opening duration of an injection valve member are already known from the prior art in order to optimize the accuracy of the injected fuel quantity.

Aus der Offenlegungsschrift DE 10 2007 031 552 A1 ist beispielsweise ein Verfahren zum Ermitteln der Position eines Ankers in einem Magnetventil sowie eine Vorrichtung zum Betreiben eines Magnetventils mit einem Anker bekannt. Da bei Kraftstoffinjektoren, die mittels eines Magnetventils betrieben werden, die Öffnungsdauer des Magnetventils einen entscheidenden Einfluss auf die eingespritzte Menge Kraftstoff hat, wird die Öffnungsdauer über die Ansteuerdauer einer Magnetspule des Magnetventils mittelbar eingestellt. Um die geeignete Ansteuerdauer zu ermitteln, müssen die Verzugszeit und die Schließzeit des Magnetventils unter den aktuellen Bedingungen bekannt sein. Während die Verzugszeit mit guter Genauigkeit vorhersagbar ist, hängt die Schließzeit von vielen Faktoren ab, die Schwankungen bewirken können, und ist daher nur unzureichend vorhersagbar. Die Schließzeit wird daher über die Position des Ankers des Magnetventils ermittelt. Über die Erkennung des Schließzeitpunktes des Magnetventils lassen sich jedoch keine Fehler und/oder Streuungen innerhalb der Hochdruckhydraulik erkennen.From the publication DE 10 2007 031 552 A1 For example, a method for determining the position of an armature in a solenoid valve and a device for operating a solenoid valve with an armature is known. There at Fuel injectors, which are operated by means of a solenoid valve, the opening duration of the solenoid valve has a decisive influence on the injected amount of fuel, the opening duration is set indirectly over the drive duration of a solenoid of the solenoid valve. In order to determine the appropriate drive time, the delay time and the closing time of the solenoid valve must be known under the current conditions. While the delay time is predictable with good accuracy, the closing time depends on many factors that can cause fluctuations and is therefore insufficiently predictable. The closing time is therefore determined by the position of the armature of the solenoid valve. By detecting the closing time of the solenoid valve, however, no errors and / or variations within the high-pressure hydraulics can be detected.

Aus der Offenlegungsschrift DE 10 2006 051 206 A1 ist des Weiteren ein Kraftstoffinjektor mit einer Messeinrichtung zur Erfassung des Endes eines Einspritzvorgangs bzw. der Erfassung des Anschlags eines Öffnungshubes einer Düsennadel bekannt. Die Messeinrichtung ist als Wirbelstromsensor mit einem Messkörper ausgeführt. Der Messkörper umgibt eine Bewegungseinrichtung, insbesondere eine Düsennadel, welche wenigstens im Bereich ihrer Umschließung durch den Messkörper eine Magnetisierung aufweist. Die Messeinrichtung wird mit konstantem Gleichstrom oder mit einer konstanten Gleichspannung betrieben, wobei eine Abweichung von der Gleichspannung bzw. vom Gleichstrom als Messsignal dient. Insbesondere ergibt sich aus der Änderung der periodischen Düsennadelbewegung eine Änderung des mittels der Messeinrichtung ausgegebenen Messsignals in Form einer Unstetigkeit. Mittels dieser Unstetigkeit werden die Hubanschlags- oder Schließzeitpunkte periodisch aufeinander folgender Öffnungs- oder Schließzyklen ermittelt. Die vorgesehene Messeinrichtung stellt jedoch ein zusätzliches Bauteil dar, das es in einen Gehäuseteil des Injektors zu integrieren gilt. Zudem sind separate elektrische Anschlüsse für die Messeinrichtung erforderlich. Der konstruktive Aufwand ist dementsprechend hoch.From the publication DE 10 2006 051 206 A1 Furthermore, a fuel injector with a measuring device for detecting the end of an injection process or the detection of the stop of an opening stroke of a nozzle needle is known. The measuring device is designed as an eddy current sensor with a measuring body. The measuring body surrounds a movement device, in particular a nozzle needle, which has a magnetization at least in the area of its enclosure by the measuring body. The measuring device is operated with constant direct current or with a constant direct voltage, wherein a deviation from the direct current or the direct current serves as a measuring signal. In particular, the change in the periodic nozzle needle movement results in a change in the measuring signal output by means of the measuring device in the form of a discontinuity. By means of this discontinuity, the Hubanschlags- or closing times of periodically consecutive opening or closing cycles are determined. However, the proposed measuring device is an additional component, which applies to be integrated into a housing part of the injector. In addition, separate electrical connections for the measuring device are required. The design effort is therefore high.

Der Erfindung liegt die Aufgabe zugrunde, ein einfaches Verfahren und einen einfach aufgebauten Kraftstoffinjektor bereit zu stellen, welche die Erkennung des Schließzeitpunktes der Düsennadel und demzufolge eine hohe Genauigkeit in der Bestimmung der Einspritzmenge ermöglichen.The invention has for its object to provide a simple method and a simple design fuel injector, which allow the detection of the closing time of the nozzle needle and consequently a high accuracy in the determination of the injection quantity.

Die Aufgabe wird gelöst von einem Kraftstoffeinspritzventil gemäß Anspruch 1 und einem Verfahren gemäß Anspruch 7. Vorteilhafte Weiterbildungen der Erfindung sind in den jeweiligen Unteransprüchen angegeben.The object is achieved by a fuel injection valve according to claim 1 and a method according to claim 7. Advantageous developments of the invention are specified in the respective subclaims.

Offenbarung der ErfindungDisclosure of the invention

Es wird ein Kraftstoffeinspritzventil zum Einspritzen von Kraftstoff in den Brennraum einer Brennkraftmaschine mit einem Magnetventil zum Ansteuern eines Einspritzventilgliedes vorgeschlagen, wobei durch Öffnen oder Schließen des Magnetventils ein das Einspritzventilglied in Schließrichtung beaufschlagender hydraulischer Druck in einem Steuerraum verändert wird. Das Magnetventil des vorgeschlagenen Kraftstoffeinspritzventils umfasst einen axial verschiebbar gelagerten und an einem Federelement abgestützten Ankerbolzen, der von einer Axialkraft beaufschlagbar ist, die proportional zum hydraulischen Druck im Steuerraum ist. Erfindungsgemäß sind Kupplungsmittel vorgesehen, über welche das Federelement und eine Spule wenigstens eines Magnetkreises gekoppelt sind und welche bei einer elastischen Verformung des Federelementes eine detektierbare Parameteränderung, vorzugsweise eine Änderung der Spulenspannung oder des Spulenstroms, in zumindest einem Magnetkreis bewirken.It is proposed a fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine with a solenoid valve for driving an injection valve member, wherein opening or closing of the solenoid valve, the injection valve member in the closing direction acting hydraulic pressure is changed in a control room. The solenoid valve of the proposed fuel injection valve comprises an axially displaceably mounted and supported on a spring element anchor bolt, which is acted upon by an axial force which is proportional to the hydraulic pressure in the control chamber. According to the invention, coupling means are provided, via which the spring element and a coil of at least one magnetic circuit are coupled and which cause a detectable parameter change, preferably a change in the coil voltage or the coil current, in at least one magnetic circuit during an elastic deformation of the spring element.

Wesentliches Merkmal des erfindungsgemäßen Kraftstoffeinspritzventils sind demnach die Kopplungsmittel, welche die Durchführung des vorstehend beschriebenen erfindungsgemäßen Verfahrens ermöglichen. Bei dem Magnetventil handelt es sich zudem bevorzugt um ein druckausgeglichenes Magnetventil, wobei der Druckausgleich über den Ankerbolzen erfolgt, der in einer Führungsbohrung des Ankers geführt. Dabei ist der Führungsdurchmesser des Ankers und der Sitzdurchmesser des Magnetventils näherungsweise gleich gewählt. Dadurch wirkt die hydraulische Kraft über die von der Sitzlinie des Ventils umschlossene Fläche nicht als Öffnungskraft auf den beweglichen Anker, sondern auf den am Federelement abgestützten Ankerbolzen. Das Federelement kann beispielsweise auch eine elastisch verformbare Abstützplatte sein.An essential feature of the fuel injection valve according to the invention are therefore the coupling means, which allow the implementation of the method according to the invention described above. The solenoid valve is also preferably a pressure balanced solenoid valve, wherein the pressure compensation takes place via the anchor bolt, which is guided in a guide bore of the armature. The guide diameter of the armature and the seat diameter of the solenoid valve is approximately the same. As a result, the hydraulic force does not act on the movable armature via the surface enclosed by the seat line of the valve as an opening force, but on the anchor bolt supported on the spring element. The spring element may for example also be an elastically deformable support plate.

Da das vorgeschlagene Kraftstoffeinspritzventil die Durchführung eines der vorstehend beschriebenen erfindungsgemäßen Verfahren ermöglicht, gelten die im Zusammenhang mit den Verfahren beschriebenen Vorteile auch für das Kraftstoffeinspritzventil. Darüber hinaus ist das vorgeschlagene Kraftstoffeinspritzventil einfach aufgebaut und kostengünstig herstellbar.Since the proposed fuel injection valve allows the implementation of one of the above-described method according to the invention, apply in the Related to the advantages described also for the fuel injection valve. In addition, the proposed fuel injection valve is simple and inexpensive to produce.

Gemäß einer ersten bevorzugten Ausführungsform sind das Federelement und die Spule des Magnetkreises über die Kopplungsmittel mechanisch gekoppelt. Eine elastische Verformung des Federelementes bewirkt zudem eine Positionsänderung der Spule gegenüber einem Magnetkern und demzufolge eine detektierbare Parameteränderung im Magnetkreis. Eine mechanische Kopplung ist einfach herzustellen, beispielsweise über stangenförmige Kopplungselemente, das einerseits mit der Spule und andererseits mit dem Federelement verbunden sind. Darüber hinaus besteht eine Vielzahl an weiteren Kopplungsmöglichkeiten.According to a first preferred embodiment, the spring element and the coil of the magnetic circuit are mechanically coupled via the coupling means. An elastic deformation of the spring element also causes a change in position of the coil relative to a magnetic core and consequently a detectable parameter change in the magnetic circuit. A mechanical coupling is easy to produce, for example via rod-shaped coupling elements, which are connected on the one hand with the coil and on the other hand with the spring element. In addition, there are a variety of other coupling options.

Die Kopplungsmittel können beispielsweise derart ausgebildet sein, dass sie eine Richtungsumkehr und/oder eine Wegübersetzung bewirken. Die Positionsänderung der Spule kann demnach der Bewegungsrichtung des Ankerbolzens entgegen gesetzt sein und/oder der Weg der Spule kann größer oder kleiner als der Weg des Ankerbolzens sein. Wesentlich ist, dass die Spule derart angeordnet ist, dass sie ihre Position auch ändern kann. Vorzugsweise ist die Spule daher zumindest axial verschiebbar gelagert.The coupling means may for example be designed such that they bring about a reversal of direction and / or a path translation. The position change of the coil can therefore be set counter to the direction of movement of the anchor bolt and / or the path of the coil may be greater or smaller than the path of the anchor bolt. It is essential that the coil is arranged such that it can also change its position. Preferably, therefore, the coil is mounted at least axially displaceable.

Gemäß einer bevorzugten weiteren Ausführungsform ist als Kopplungsmittel ein zweiter Magnetkreis mit einer zweiten Spule vorgesehen und eine elastische Verformung des Federelementes bewirkt eine detektierbare Parameteränderung zumindest im zweiten Magnetkreis. Die Spule des zweiten Magnetkreises kann hierzu im bzw. am Federelement, beispielsweise als gedruckte und mittels Kleben befestigte Flachspule, oder im bzw. am Magnetkern des Primärkreises angeordnet sein. Hierbei wird - in Abhängigkeit von der gewählten Anordnung - ein Luftspalt zwischen der Spule und dem Magnetkern oder der Spule und dem Federelement ausgebildet, der sich bei einer elastischen Verformung des Federelementes verändert und somit zu einer Änderung der Induktivität des Magnetkreises führt.According to a preferred further embodiment, a second magnetic circuit with a second coil is provided as the coupling means, and an elastic deformation of the spring element causes a detectable parameter change at least in the second magnetic circuit. For this purpose, the coil of the second magnetic circuit can be arranged in or on the spring element, for example as a printed flat coil fastened by gluing, or in or on the magnetic core of the primary circuit. Here, depending on the selected arrangement, an air gap is formed between the coil and the magnetic core or the coil and the spring element, which changes with elastic deformation of the spring element and thus leads to a change in the inductance of the magnetic circuit.

Bevorzugt sind die zweite Spule des zweiten Magnetkreises und die erste Spule des ersten Magnetkreises parallel oder in Reihe geschaltet. Diese Maßnahmen machen die Anordnung weiterer elektrischer Leitungen außerhalb des Kraftstoffeinspritzventils entbehrlich.Preferably, the second coil of the second magnetic circuit and the first coil of the first magnetic circuit are connected in parallel or in series. These measures make the arrangement of other electrical lines outside the fuel injector dispensable.

Vorteilhafterweise ist das Magnetventil eines erfindungsgemäßen Kraftstoffeinspritzventils im Wesentlichen durckausgeglichen. Hierzu ist der Ankerbolzen des Magnetventils in einer Führungsbohrung eines Ankers aufgenommen, wobei der Durchmesser der Führungsbohrung und der Durchmesser eines mit dem Anker zusammenwirkenden Ventilsitzes näherungsweise gleich sind. Dadurch wirkt die hydraulische Kraft über die von der Sitzlinie des Ventils umschlossene Fläche nicht als Öffnungskraft auf den beweglichen Anker, sondern auf den am Federelement abgestützten Ankerbolzen. Das Federelement kann hierzu als elastisch verformbare Abstützplatte ausgebildet sein. Um die Elastizität der Abstützplatte zu erhöhen, können in dieser Aussparungen vorgesehen sein. Diese sind derart zu gestalten, dass der Magnetfluss im zweiten Magnetkreis nicht beeinträchtigt wird.Advantageously, the solenoid valve of a fuel injection valve according to the invention is substantially balanced. For this purpose, the armature pin of the solenoid valve is received in a guide bore of an armature, wherein the diameter of the guide bore and the diameter of a valve seat cooperating with the armature are approximately equal. As a result, the hydraulic force does not act on the movable armature via the surface enclosed by the seat line of the valve as an opening force, but on the anchor bolt supported on the spring element. For this purpose, the spring element can be designed as an elastically deformable support plate. To increase the elasticity of the support plate may be provided in this recesses. These are to be designed such that the magnetic flux is not affected in the second magnetic circuit.

Das erfindungsgemäße Verfahren nutzt die Tatsache, dass das Magnetventil während der Schließphase des Kraftstoffeinspritzventils geschlossen ist und in der Druckkammer des Magnetventils der Steuerraumdruck herrscht. Dieser Steuerraumdruck - und folglich die auf den Ankerbolzen wirkende Axiakraftweisen im Schließzeitpunkt des Einspritzventils ein deutliches Minimum auf. Unmittelbar nach dem Schließen des Einspritzventilgliedes kommt es zu einem schnellen Anstieg des Steuerraumdrucks, der ferner einen Anstieg der auf den Ankerbolzen wirkenden Axialkraft bewirkt. Diese Kraftänderung führt bei einem erfindungsgemäßen Kraftstoffinjektor zu einer elastischen Verformung des Federelementes, wobei die vorgesehenen Kopplungsmittel die elastische Verformung des Federelementes in eine Positionsänderung einer Spule eines Magnetkreises und/oder in eine Größenveränderung eines Luftspaltes übersetzen, was wiederum eine Parameteränderung in dem die Spule und/oder den Luftspalt aufweisenden Magnetkreis zur Folge hat. Anhand dieser Parameteränderung kann dann der Schließzeitpunkt des Einspritzventilgliedes bestimmt werden.The inventive method utilizes the fact that the solenoid valve is closed during the closing phase of the fuel injection valve and in the pressure chamber of the solenoid valve, the control chamber pressure prevails. This control chamber pressure - and consequently the force acting on the anchor bolt Axiakraftweisen at the closing time of the injector to a clear minimum. Immediately after closing the injection valve member, there is a rapid increase in the control chamber pressure, which also causes an increase in the force acting on the anchor bolt axial force. This change in force results in a fuel injector according to the invention to an elastic deformation of the spring element, wherein the provided coupling means translate the elastic deformation of the spring element in a change in position of a coil of a magnetic circuit and / or in a change in size of an air gap, which in turn a parameter change in which the coil and / or the air gap Magnetic circuit entails. Based on this parameter change, the closing time of the injection valve member can then be determined.

Bevorzugte Ausführungsformen der Erfindung werden nachfolgend anhand der Zeichnungen näher beschrieben. Diese zeigen:

  • Fig. 1 einen Längsschnitt durch ein Kraftstoffeinspritzventil gemäß dem Stand der Technik,
  • Fig. 2 einen Detailausschnitt aus Fig. 1 im Bereich des Steuerraums,
  • Fig. 3 ein Diagramm zur Darstellung des zeitlichen Verlaufs und der Zusammenhänge des Hubes des Einspritzventilgliedes und des Steuerraumdrucks,
  • Fig. 4 einen Längsschnitt durch ein erstes erfindungsgemäßes Kraftstoffeinspritzventil im Bereich des Magnetventils,
  • Fig. 5 einen Längsschnitt durch ein zweites erfindungsgemäßes Kraftstoffeinspritzventil im Bereich des Magnetventils,
  • Fig. 6 einen Längsschnitt durch ein Magnetventil eines dritten erfindungsgemäßen Kraftstoffeinspritzventils,
  • Fig. 7 einen Längsschnitt durch ein Magnetventil eines vierten erfindungsgemäßen Kraftstoffeinspritzventils und
  • Fig. 8 und 9 jeweils ein Schaltschema eines Magnetventils gemäß der Fig. 7.
Preferred embodiments of the invention are described below with reference to the drawings. These show:
  • Fig. 1 a longitudinal section through a fuel injection valve according to the prior art,
  • Fig. 2 a detail from Fig. 1 in the area of the control room,
  • Fig. 3 a diagram showing the time course and the relationships of the stroke of the injection valve member and the control chamber pressure,
  • Fig. 4 a longitudinal section through a first inventive fuel injection valve in the region of the solenoid valve,
  • Fig. 5 a longitudinal section through a second inventive fuel injection valve in the region of the solenoid valve,
  • Fig. 6 a longitudinal section through a solenoid valve of a third fuel injection valve according to the invention,
  • Fig. 7 a longitudinal section through a solenoid valve of a fourth fuel injection valve according to the invention and
  • 8 and 9 in each case a circuit diagram of a solenoid valve according to the Fig. 7 ,

Ausführliche Beschreibung der ZeichnungenDetailed description of the drawings

Das in der Fig. 1 dargestellte bekannte Kraftstoffeinspritzventil weist ein in einem ersten Gehäuseteil 16 (Düsenkörper) hubbeweglich geführtes Einspritzventilglied 1 in Form einer Düsennadel auf, an welche ein Ventilkolben 15 als Verlängerung angesetzt ist. Der Ventilkolben 15 ist in einem zweiten Gehäuseteil 16 (Injektorkörper) ebenfalls hubbeweglich geführt und an seinem der Düsennadel abgewandtem Ende in einem Ventilstück 18 aufgenommen. Innerhalb des Ventilstücks 18 wird durch den Ventilkolben 15 ein Steuerraum 3 begrenzt, in welchem in Schließstellung eines Magnetventils 2 ein den Ventilkolben 15 und damit das Einspritzventilglied 1 in Schließrichtung beaufschlagender hydraulischer Druck herrscht. Der das Einspritzventilglied 1 in Schließrichtung beaufschlagende hydraulische Druck im Steuerraum 3 wird durch eine Zulaufdrossel 21 sichergestellt, welche in Verbindung mit einem Hochdruck-Anschluss 20 für die Zuleitung von unter hohem Druck stehenden Kraftstoff steht. Der Hochdruck-Anschluss 20 steht ferner in Verbindung mit einer Hochdruckbohrung 17, über welche der unter hohem Druck stehende Kraftstoff wenigstens einer Einspritzöffnung des Kraftstoffeinspritzventils zugeführt wird.That in the Fig. 1 shown known fuel injection valve has a in a first housing part 16 (nozzle body) liftably guided injection valve member 1 in the form of a nozzle needle, to which a valve piston 15 is attached as an extension. The valve piston 15 is also guided in a liftable manner in a second housing part 16 (injector body) and received in a valve piece 18 at its end facing away from the nozzle needle. Inside the valve piece 18 is limited by the valve piston 15, a control chamber 3, in which in the closed position of a solenoid valve 2, a valve piston 15 and thus the injection valve member 1 in the closing direction acting hydraulic pressure prevails. The hydraulic pressure in the control chamber 3 that acts on the injection valve member 1 in the closing direction is ensured by an inlet throttle 21, which is in communication with a high-pressure port 20 for the supply of fuel under high pressure. The high pressure port 20 is further in communication with a high pressure bore 17 through which the high pressure fuel is supplied to at least one injection port of the fuel injection valve.

Wie aus Fig. 2 ersichtlich weist der Steuerraum 3 eine weitere Drossel, nämlich eine Ablaufdrossel 22 auf, über welche eine hydraulische Verbindung des Steuerraums 3 mit einer Druckkammer 24 des Magnetventils 2 hergestellt wird (siehe auch Fig. 4 und 5). In der Druckkammer 24 des Magnetventils 2 herrscht somit bei geschlossenem Magnetventil 2 der hydraulische Druck des Steuerraums 3. Wird nun das Magnetventil 2 geöffnet, kann über die Ablaufdrossel 22 und den Ventilsitz 14 Kraftstoff aus dem Steuerraum 3 und der Druckkammer 24 des Magnetventils 2 abströmen. Die Folge ist ein Druckabfall im Steuerraum 3, der einen Öffnungshub des Einspritzventilgliedes 1 zur Folge hat. Zum Öffnen des Magnetventils 2 wird dieses bestromt, so dass ein mit dem Ventilsitz 14 zusammenwirkender Anker 13 des Magnetventils 2 aus seinem Dichtsitz gehoben wird und den Ventilsitz 14 öffnet. Zur Bestromung des Magnetventils 2 ist am Kraftstoffeinspritzventil ein elektrischer Anschluss 19 vorgesehen (siehe Fig. 1).How out Fig. 2 it can be seen, the control chamber 3, a further throttle, namely an outlet throttle 22, via which a hydraulic connection of the control chamber 3 is made with a pressure chamber 24 of the solenoid valve 2 (see also Fig. 4 and 5 ). If the solenoid valve 2 is opened, fuel can flow out of the control chamber 3 and the pressure chamber 24 of the solenoid valve 2 via the outlet throttle 22 and the valve seat 14 in the pressure chamber 24 of the solenoid valve 2. The result is a pressure drop in the control chamber 3, which has an opening stroke of the injection valve member 1 result. To open the solenoid valve 2, this is energized, so that cooperating with the valve seat 14 armature 13 of the solenoid valve 2 is lifted from its sealing seat and the valve seat 14 opens. For energizing the solenoid valve 2, an electrical connection 19 is provided on the fuel injection valve (see Fig. 1 ).

Die Zusammenhänge zwischen dem Steuerraumdruck und dem Öffnungshub der Düsennadel bzw. des Einspritzventilgliedes 1 gehen aus dem Diagramm der Fig. 3 hervor. Die Rückwirkung von Öffnen und Schließen des Einspritzventilgliedes 1 auf den Steuerraumdruck sind deutlich zu sehen. So erreicht der Steuerraumdruck sein Minimum unmittelbar vor Beginn des Öffnungshubes des Einspritzventilgliedes 1.The relationships between the control chamber pressure and the opening stroke of the nozzle needle or the injection valve member 1 go from the diagram of Fig. 3 out. The reaction of opening and closing of the injection valve member 1 to the control chamber pressure can be clearly seen. Thus, the control chamber pressure reaches its minimum immediately before the start of the opening stroke of the injection valve member. 1

Diese Zusammenhänge kommen insbesondere zum Tragen, wenn ein druckausgeglichenes Magnetventil 2 zur Ansteuerung des Einspritzventilgliedes 1 Verwendung findet (siehe Fig. 4 und 5). Der Druckausgleich erfolgt über einen Ankerbolzen 5, der in einer Führungsbohrung 12 des Ankers 13 axial verschiebbar geführt ist, wobei der Durchmesser der Führungsbohrung 12 zumindest näherungsweise gleich dem Durchmesser des Ventilsitzes 14 gewählt ist. Dadurch wirkt keine hydraulische Kraft auf den Anker 13, sondern lediglich auf den Ankerbolzen 5, der an einem Federelement 4 abgestützt ist. Dabei wird der Ankerbolzen 5 von einer Axialkraft beaufschlagt, die proportional zum hydraulischen Druck im Steuerraum 3 ist. Die Axialkraft bewirkt, dass der Ankerbolzen 5 in Richtung des Federelementes 4 axial verschoben wird, wobei das Federelement 4 eine elastische Verformung erfährt.These relationships are particularly relevant when a pressure balanced solenoid valve 2 is used to control the injection valve member 1 (see Fig. 4 and 5 ). The pressure equalization takes place via an anchor bolt 5, which is axially displaceable in a guide bore 12 of the armature 13 is guided, wherein the diameter of the guide bore 12 is at least approximately equal to the diameter of the valve seat 14 is selected. As a result, no hydraulic force acts on the armature 13, but only on the anchor bolt 5, which is supported on a spring element 4. In this case, the anchor bolt 5 is acted upon by an axial force which is proportional to the hydraulic pressure in the control chamber 3. The axial force causes the anchor bolt 5 is axially displaced in the direction of the spring element 4, wherein the spring element 4 experiences an elastic deformation.

Bei dem in der Fig. 4 dargestellten ersten erfindungsgemäßen Kraftstoffeinspritzventil ist das Federelement 4 als Tellerfeder ausgebildet und an einem als Abstützplatte dienenden Gehäuseteil 16 abgestützt. Der Ankerbolzen 5 ist von einem Magnetkern 11 umgeben, in dem eine Spule 7 aufgenommen ist. Ferner sind Kopplungsmittel 6 vorgesehen, welche die Spule 7 mit dem Federelement 4 in der Weise mechanisch verbinden, dass eine elastische Verformung des Federelementes 4 eine Positionsänderung der Spule 7 gegenüber dem Magnetkern 11 bewirkt. Die Spule 7 ist hierzu axial verschiebbar im Magnetkern 11 aufgenommen und der Magnetkern 11 über ein Spannelement 23, das den Magnetkern 11 gegenüber einem radialen Absatz am Gehäuseteil 16 vorspannt, lagefixiert. Die Positionsänderung der Spule 7 führt zu einer Parameteränderung, beispielsweise einer Änderung der Spulenspannung oder des Spulenstroms, im vorhandenen Magnetkreis 9, so dass über die Detektion der Parameteränderung der Schließzeitpunkt des Einspritzventilgliedes 1 zuverlässig erkannt werden kann.In the in the Fig. 4 shown first fuel injection valve according to the invention, the spring element 4 is formed as a plate spring and supported on a serving as a support plate housing part 16. The anchor bolt 5 is surrounded by a magnetic core 11 in which a coil 7 is received. Further, coupling means 6 are provided which mechanically connect the coil 7 with the spring element 4 in such a way that an elastic deformation of the spring element 4 causes a change in position of the coil 7 relative to the magnetic core 11. The coil 7 is axially displaceable for this purpose received in the magnetic core 11 and the magnetic core 11 via a clamping element 23 which biases the magnetic core 11 relative to a radial shoulder on the housing part 16, fixed in position. The change in position of the coil 7 leads to a parameter change, for example a change in the coil voltage or the coil current, in the existing magnetic circuit 9, so that the closing time of the injection valve member 1 can be reliably detected via the detection of the parameter change.

Eine alternative Ausführungsform geht aus der Fig. 5 hervor. Diese unterscheidet sich von der der Fig. 4 dadurch, dass das Federelement 4 unterschiedlich ausgebildet ist und die mechanische Kopplung des Federelementes 4 mit der Spule 7 über die Kopplungsmittel 6 in der Weise erfolgt, dass die Positionsänderung der Spule 7 in entgegengesetzter Richtung zur Bewegung des Ankerbolzens 5 erfolgt. Es kann somit eine Richtungsumkehr bewirkt werden. Zudem unterscheiden sich der Weg der Spule 7 vom Weg des Ankerbolzens 5, so dass ferner eine Wegübersetzung realisiert wird.An alternative embodiment is from the Fig. 5 out. This is different from the one of Fig. 4 in that the spring element 4 is designed differently and the mechanical coupling of the spring element 4 with the coil 7 via the coupling means 6 in such a way that the change in position of the coil 7 takes place in the opposite direction to the movement of the anchor bolt 5. It can thus be effected a direction reversal. In addition, the path of the coil 7 differ from the path of the anchor bolt 5, so that further a path translation is realized.

Eine weitere alternative Ausführungsform ist in der Fig. 6 gezeigt. Hier werden als Kopplungsmittel 6 ein weiterer Magnetkreis 10 mit einer weiteren Spule 8 eingesetzt. Zudem bildet die gehäuseseitige Abstützplatte das Federelement 4 aus, welche demnach elastisch verformbar ausgeführt ist. Die zweite Spule 8 ist in dem Magnetkern 11 aufgenommen und zwischen dem Magnetkern 11 und dem Federelement 4 ist ein Luftspalt 25 ausgebildet, der sich bei einer elastischen Verformung des Federelementes 4 verändert, vorliegend vergrößert. Dies hat zur Folge, dass sich die Induktivität im Magnetkreis 10 ändert. Es erfolgt eine Parameteränderung, die wiederum detektierbar ist und einen Rückschluss auf den Schließzeitpunkt des Einspritzventilgliedes 1 zulässt.Another alternative embodiment is in Fig. 6 shown. Here, as a coupling means 6, a further magnetic circuit 10 with a further coil. 8 used. In addition, the housing-side support plate forms the spring element 4, which is therefore designed elastically deformable. The second coil 8 is received in the magnetic core 11 and between the magnetic core 11 and the spring element 4, an air gap 25 is formed, which changes in an elastic deformation of the spring element 4, in this case enlarged. This has the consequence that the inductance in the magnetic circuit 10 changes. There is a parameter change, which in turn is detectable and allows a conclusion on the closing time of the injection valve member 1.

Die Fig. 7 zeigt eine Abwandlung der Ausführungsform der Fig. 6. Der Unterschied besteht darin, dass die zweite Spule 8 in das Federelement 4 integriert ist. Bei einer elastischen Verformung des Federelementes 4 erfolgt demnach eine Positionsänderung der Spule 8, die ebenfalls dazu führt, dass der Luftspalt 25 eine Vergrößerung erfährt.The Fig. 7 shows a modification of the embodiment of the Fig. 6 , The difference is that the second coil 8 is integrated into the spring element 4. In the case of an elastic deformation of the spring element 4, a change in the position of the coil 8 takes place, which likewise results in the air gap 25 being enlarged.

Um weitere elektrische Leitungen bzw. einen weiteren elektrischen Anschluss 19 zu vermeiden, ist die jeweils zweite Spule 8 parallel oder in Reihe mit der Spule 7 des Primärkreises geschaltet. Die Parallelschaltung ist beispielhaft für die Ausführungsform der Fig. 7 in Fig. 8 dargestellt. Fig. 9 zeigt die entsprechende Reihenschaltung. Während bei der Parallelschaltung die Induktivität der zweiten Spule 8 im Vergleich zur ersten Spule 7 hoch gewählt sein muss, um die Funktion des Primärkreises nicht zu beeinträchtigen, verhält es sich bei der Reihenschaltung anders herum. Das heißt, dass bei der Reihenschaltung die Windungszahl der zweiten Spule 8 geringer als die der ersten Spule 7 sein kann.In order to avoid further electrical lines or a further electrical connection 19, the respective second coil 8 is connected in parallel or in series with the coil 7 of the primary circuit. The parallel connection is exemplary for the embodiment of the Fig. 7 in Fig. 8 shown. Fig. 9 shows the corresponding series connection. While in parallel connection, the inductance of the second coil 8 must be selected to be high in comparison to the first coil 7 in order not to impair the function of the primary circuit, it is the other way round in the series connection. That is, in the series connection, the number of turns of the second coil 8 may be smaller than that of the first coil 7.

Allen dargestellten Ausführungsformen eines erfindungsgemäßen Kraftstoffeinspritzventils gemeinsam ist, dass das Magnetventil 2 jeweils derart ausgelegt und konstruiert ist, dass das Schließen des Einspritzventilgliedes 1 eine detektierbare Parameteränderung in einem Magnetkreis des Magnetventils 2 zur Folge hat. Über die Parameteränderung kann demnach in zuverlässiger Weise der Schließzeitpunkt des Einspritzventilgliedes 1 ermittelt werden.All illustrated embodiments of a fuel injection valve according to the invention is common that the solenoid valve 2 is designed and constructed in each case such that the closing of the injection valve member 1 has a detectable parameter change in a magnetic circuit of the solenoid valve 2 result. Accordingly, the closing time of the injection valve member 1 can be determined in a reliable manner via the parameter change.

Zur Durchführung des Verfahrens ist es erforderlich, das ein ausreichender Restfluss im jeweiligen Magnetkreis vorhanden ist. Sofern dies nicht der Fall ist, wird vorgeschlagen, das Magnetventil 2 erneut kurz zu bestromen, um einen ausreichenden Magnetfluss zu gewährleisten. Dabei ist jedoch Sorge zu tragen, dass das Magnetventil 2 nicht erneut öffnet. Denn dies hätte einen Druckabfall im Steuerraum 3 und ggf. einen erneuten Öffnungshub des Einspritzventilgliedes 1 zur Folge.To carry out the method, it is necessary that a sufficient residual flux is present in the respective magnetic circuit. If this is not the case, it is proposed again to briefly energize the solenoid valve 2 in order to ensure a sufficient magnetic flux. However, care must be taken to ensure that the solenoid valve 2 does not open again. Because this would have a pressure drop in the control chamber 3 and possibly a renewed opening stroke of the injection valve member 1 result.

Indem der Schließzeitpunkt des Einspritzventilgliedes erfasst wird, findet bei der Ermittlung der Einspritzdauer nicht nur das dynamische Verhalten des Servoventils Berücksichtigung, sondern sämtliche etwaige Ungenauigkeiten innerhalb der gesamten Schaltkette vom Aktor bis zur Düsennadel bzw. bis zum Einspritzventilglied. Die Erfindung vermag sowohl Exemplarstreuungen gleichartiger Ventile auszugleichen, als auch deren Drift über die Lebensdauer sowie den Einfluss variabler Einflussgrößen, wie beispielsweise den Einfluss von Druckschwingungen. Die eingespritzte Kraftstoffmenge ist demnach mit höherer Genauigkeit bestimmbar und einstellbar.By detecting the closing time of the injection valve member, not only the dynamic behavior of the servo valve is taken into account in the determination of the injection duration, but all possible inaccuracies within the entire switching chain from the actuator to the nozzle needle or to the injection valve member. The invention is capable of compensating for example scattering of similar valves, as well as their drift over the life and the influence of variable influencing variables, such as the influence of pressure oscillations. The injected amount of fuel is therefore determinable and adjustable with higher accuracy.

Claims (7)

  1. Fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine, having a solenoid valve (2) which serves for actuating an injection valve element (1) in that a hydraulic pressure in a control chamber (3), which hydraulic pressure acts on the injection valve element (1) in a closing direction, can be varied by opening or closing the solenoid valve (2), and wherein the solenoid valve (2) comprises an armature pin (5) which is mounted in axially displaceable fashion and which is supported on a spring element (4) and which can be acted on by an axial force which is proportional to the hydraulic pressure in the control chamber (3),
    characterized in that coupling means (6) are provided by means of which the spring element (4) and a coil (7, 8) of at least one magnetic circuit (9, 10) are coupled and which, in the event of an elastic deformation of the spring element (4), effect a detectable parameter change, preferably a change in the coil voltage or in the coil current, in at least one magnetic circuit (9, 10).
  2. Fuel injection valve according to Claim 1,
    characterized in that the spring element (4) and the coil (7) of the magnetic circuit (9) are mechanically coupled by the coupling means (6), and an elastic deformation of the spring element (4) effects a change in position of the coil (7) relative to a magnet core (11) and accordingly a detectable parameter change in the magnetic circuit (9).
  3. Fuel injection valve according to Claim 1 or 2,
    characterized in that the coupling means (6) effect a direction reversal and/or a stroke-boosting action.
  4. Fuel injection valve according to one of Claims 1 to 3, characterized in that a second magnetic circuit (10) with a second coil (8) is provided as coupling means (6), and an elastic deformation of the spring element (4) effects a detectable parameter change at least in the second magnetic circuit (10).
  5. Fuel injection valve according to Claim 4,
    characterized in that the second coil (8) of the second magnetic circuit (10) and the first coil (7) of the first magnetic circuit (9) are connected in parallel or in series.
  6. Fuel injection valve according to one of Claims 1 to 5,
    characterized in that the armature pin of the solenoid valve (2) is received in a guide bore (12) of an armature (13), wherein the diameter of the guide bore (12) and the diameter of a valve seat (14) which interacts with the armature (13) are approximately equal, such that the solenoid valve (2) is substantially pressure-balanced.
  7. Method for identifying the closing time of an injection valve element (1) in a fuel injection valve according to one of Claims 1 to 6, characterized in that the parameter change in a magnetic circuit (9, 10) is determined in the presence of a residual flux, and/or a magnetic flux adequate for determining the parameter change is built up by renewed energization of the solenoid valve (2) prior to the expected closing time of the injection valve element (1).
EP11150104.5A 2010-02-16 2011-01-04 Method for recognising the closing point of an injection valve body in a fuel injection valve and fuel injection valve Active EP2357353B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102010001960A DE102010001960A1 (en) 2010-02-16 2010-02-16 Method for detecting the closing time of an injection valve member in a fuel injection valve and fuel injection valve

Publications (3)

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EP2357353A2 EP2357353A2 (en) 2011-08-17
EP2357353A3 EP2357353A3 (en) 2015-08-26
EP2357353B1 true EP2357353B1 (en) 2017-08-09

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EP11150104.5A Active EP2357353B1 (en) 2010-02-16 2011-01-04 Method for recognising the closing point of an injection valve body in a fuel injection valve and fuel injection valve

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DE (1) DE102010001960A1 (en)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102014210605A1 (en) 2013-09-17 2015-03-19 Robert Bosch Gmbh fuel injector

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006051206A1 (en) 2006-10-30 2008-05-08 Robert Bosch Gmbh Fuel injector for internal combustion engine, has sensor with measuring body, which partially encloses moving device, where device exhibits magnetization in enclosing region over body
DE102007031552A1 (en) 2007-07-06 2009-01-08 Robert Bosch Gmbh Method for determining a position of an armature in a solenoid valve and device for operating a solenoid valve with an armature
DE102008001425A1 (en) * 2008-04-28 2009-10-29 Robert Bosch Gmbh Fuel injector

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EP2357353A3 (en) 2015-08-26
DE102010001960A1 (en) 2011-08-18
EP2357353A2 (en) 2011-08-17

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