EP2496824A1 - Control valve assembly - Google Patents

Control valve assembly

Info

Publication number
EP2496824A1
EP2496824A1 EP10768197A EP10768197A EP2496824A1 EP 2496824 A1 EP2496824 A1 EP 2496824A1 EP 10768197 A EP10768197 A EP 10768197A EP 10768197 A EP10768197 A EP 10768197A EP 2496824 A1 EP2496824 A1 EP 2496824A1
Authority
EP
European Patent Office
Prior art keywords
control valve
actuator
valve arrangement
guide rod
arrangement according
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.)
Granted
Application number
EP10768197A
Other languages
German (de)
French (fr)
Other versions
EP2496824B1 (en
Inventor
Nestor Rodriguez-Amaya
Siegfried Ruthardt
Holger Rapp
Wolfgang Stoecklein
Bernd Berghaenel
Marco Beier
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2496824A1 publication Critical patent/EP2496824A1/en
Application granted granted Critical
Publication of EP2496824B1 publication Critical patent/EP2496824B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/004—Sliding valves, e.g. spool valves, i.e. whereby the closing member has a sliding movement along a seat for opening and closing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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
    • F02D2041/2051—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using voltage control
    • 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
    • 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
    • F02D2041/2058—Output circuits, e.g. for controlling currents in command coils characterised by the control of the circuit using information of the actual current value
    • 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
    • F02D2200/0602—Fuel pressure
    • 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

Definitions

  • the invention relates to control valve arrangements on a control chamber, in particular of a fuel injector, with an electromagnetic actuator actuating the valve arrangement.
  • a nozzle needle is provided for controlling the injectors whose nozzle distal end formed in the manner of a plunger and displaceable in a control chamber which communicates via an inlet throttle with the high pressure side of the fuel injector and a Control valve assembly with the low pressure side of the fuel injector is connectable.
  • the control chamber is connected with the control valve arrangement closed only with the high pressure side of the fuel injector, while the pressure in the control chamber with open control valve assembly as a result of the then existing connection with the low pressure side drops.
  • the nozzle needle is pushed into its closed position.
  • the control chamber has an outlet channel which opens out to the low-pressure side of a valve body and which is controlled by the control valve arrangement.
  • the control valve arrangement has a sleeve-shaped closing body, which is displaceably arranged on a guide shaft which is identical to the outlet channel, wherein the annular gap between the outer circumference of the guide rod and the inner circumference of the sleeve-shaped closing body is designed as a virtually leak-free sealing gap.
  • the sleeve-shaped closing body acts with a seat concentric with the mouth of the outlet channel.
  • the invention provides that the control chamber pressure an elastically deformable or movable against elastic resistance part, which leads or bundles the magnetic field of the actuator loaded, wherein movement or deformation-dependent electrical or magnetic parameters of the actuator for determining correlated with the control chamber pressure operating times or parameters are evaluated.
  • the invention utilizes the insight that the control chamber pressure changes significantly at the beginning and at the end of the injection phase of a fuel injector.
  • an analogous to the control chamber pressure intervention in the magnetic field of the actuator by evaluating the time course of the electrical voltage or the electric current at the actuator of the operation of the fuel injector with high Precision recorded and monitored.
  • the actuator thus assumes a dual function by not only serving to actuate the control valve assembly but also as a sensor for the operating phases of the fuel injector.
  • the control valve arrangement according to the invention has a guide rod on a slidably guided sleeve-shaped closing body, which is connected to an armature of the actuator forming the electromagnet assembly. It is further provided that the fluid pressure present within the sleeve-shaped closing body can be removed via the guide rod to the deformable or movable part.
  • This part may be formed as a deformable or movable part of a rod axis radial bottom of a Polschuhan extract serving as an actuator solenoid. By deformation or displacement of this soil, the relative position of the pole pieces can be changed, at the same time the electrical or magnetic parameters of the electromagnet are changed.
  • 1 is a fragmentary axial section of a fuel injector
  • FIG. 2 is a diagram showing the time course of the nozzle needle stroke and the control chamber pressure
  • FIG. 5 shows an illustration of a further modification
  • FIG. 6 shows a further modified embodiment
  • FIG. 7 shows an additional variant
  • FIG. 8 shows a further variant.
  • a high-pressure chamber 2 and a low-pressure chamber 3 are arranged within an injector body 1. These two spaces are separated from each other by a valve piece 4.
  • the high pressure chamber 2 communicates via an inlet channel 5 with a high pressure fuel source, not shown, for fuel, usually a so-called common rail.
  • the low-pressure space 3 is connected via a non-illustrated return line or the like to a fuel tank or the like.
  • the high pressure chamber 2 is connected via injection nozzles, not shown, with the combustion chamber of an internal combustion engine, also not shown.
  • the injection nozzles are controlled in a known manner by means of a nozzle needle, of which in Fig. 1, only the nozzle-distal end, which is designed as a plunger 6, is shown.
  • the plunger 6 is arranged displacer-effective in a control chamber 7 arranged in the valve piece 4.
  • This control chamber communicates via an inlet throttle 8 with the high-pressure chamber 2 and via an outlet throttle 9 with the low-pressure chamber 3, wherein the outlet throttle 9 is controlled by means of a control valve assembly 10. If the outlet throttle 9 is shut off by means of the control valve arrangement 10 and the nozzle needle is in its closed position, the same high pressure arises in the control chamber 7 as in the high-pressure chamber 2, with the result that the plunger 6 in FIG. 1 is pressed downwards is and the associated nozzle needle is held in its shut-off the injectors closing position.
  • the control valve assembly 10 has a sleeve-shaped closing body 11, which is tensioned by a closing spring 12, which is designed as a helical compression spring against a concentric to the outlet port of the flow channel 9 seat.
  • the seat is designed as a flat surface on which the sleeve-shaped closing body 11 is seated with a line-shaped annular edge. In principle, however, a differently shaped seat may be provided.
  • the sleeve-shaped closing body 11 is axially displaceably guided on a guide axis 13, which is equiaxial to the longitudinal axis 100 of the injector body 1, wherein the annular gap between the inner periphery of the closing body 11 and the outer circumference of the guide rod 13 is formed as a virtually leak-free throttle gap.
  • the pressure chamber 14 formed within the closing body 11 which communicates with the control chamber 7 via the outlet channel 9, and accordingly the same fluid pressure as the control raum 7 has shut off from the low-pressure chamber 3.
  • a star-shaped armature 15 of an electromagnet arrangement 16 is arranged, which is provided as an actuator for actuating the control valve arrangement 10.
  • the solenoid assembly 16 has in a known manner a magnetic coil 17, which is arranged within a concentric to the guide rod 13 Polschuhan extract with an annular outer pole 18 and an annular inner pole 19. If the magnetic coil 17 is energized electrically, the armature 15 is magnetically attracted by the poles 18 and 19, so that the closing body 11 is lifted against the force of the closing spring 12 from its seat and the control valve assembly 10 is opened.
  • the electromagnetic parameters of the solenoid assembly 16 changes such that the closing times of the nozzle needle by appropriate evaluation of the electric current-voltage curve at the solenoid 17 can be detected.
  • the electromagnet arrangement 16 also takes over
  • the guide rod 13 has the task of a control element for changing parameters of the electromagnet arrangement 16.
  • FIG. 3 shows a first embodiment of a possibility of changing the parameters of the solenoid assembly 16.
  • the pressure of the pressure chamber 14 dependent axial force of the guide rod 13 is removed to an elastically bendable bottom 21, which forms part of the Polschuhan extract and with the poles 18 and 19 is connected.
  • the air gap between the inner pole 19 and the armature 15 changes, that is, with an increase in the pressure in the control chamber 7 and the associated increase in pressure in the pressure chamber 14, the air gap between the armature 15 and inner pole 19 is increased.
  • the control chamber pressure increases immediately after the closing time of the nozzle needle, at this time increases the force acting on the bottom 21 axial force of the guide rod 13 and causes an increase in the air gap between the inner pole 19 and armature 15. If there is a residual flux in the magnetic circuit at this time, Thus, the enlargement of the aforementioned air gap causes a change in the coil voltage (at vanishing coil current) or a change in the coil current (at vanishing coil voltage). If there is no sufficient residual magnetic flux, the solenoid 12 is energized weakly before the expected closing time of the nozzle needle to re-establish magnetic flux. The degree of energization is chosen so low that the closing body 11 remains in its closed position.
  • the bottom 21 is supported stationary on its side remote from the inner pole 19 side.
  • the outer pole 18 is arranged separately from the bottom 21 stationary in the injector body 1, wherein between the bottom 21 and the outer pole 18, an air gap 22 remains. This air gap changes as a function of the axial force of the guide rod 13.
  • the associated changes in the magnetic flux of the solenoid assembly 16 thus in turn open up the possibility of accurately detecting the closing time of the nozzle needle.
  • the inner pole 19 and the outer pole 18 form a pole shoe arrangement which is separate from the flexible base 21 and whose bridge region is formed between the poles 18 and 19 with a comparatively small cross-section.
  • the embodiment of FIG. 6 differs from the embodiment of FIG. 5 essentially only in that the flexible bottom 21 rests on a ring land on the back of the inner pole 19 and an elastic gap 24 is changed in elastic bending of the bottom 21. Functionally, the embodiments of the embodiment of FIG. 5 thus apply to the embodiment of FIG. 6.
  • This web 25 is provided in the example of FIG. 7 on the side facing away from the armature 15 end face of the magnetic coil 17.
  • the flexible bottom 21 is arranged and designed such that it rests on vanishing axial force of the guide rod 13, that is at a correspondingly low pressure in the control chamber 7 and in the pressure chamber 14, on the facing end faces of the poles 18 and 19.
  • FIG. 8 A functionally similar embodiment is shown in Fig. 8. This embodiment differs from the embodiment according to FIG. 7 only in that the non-magnetic web 25 'is arranged on the side of the magnet coil 17 facing the armature 15. If the guide rod 13 is axially free of force, the bottom 21 is again on the facing end faces of the poles 18 and 19, and with a corresponding axial force of the guide rod 13, the air gap 26 'is formed at the inner pole.

Abstract

The control valve assembly, which is preferably associated with a control chamber of a fuel injector, comprises an electromagnetic actuator, which is arranged such that the electromagnetic parameters thereof are varied by the pressure in the control chamber. It is thus possible to detect predefined operating times, in particular the closing times of the injection nozzles, by detecting the electrical voltages or currents at the actuator.

Description

Beschreibung  description
Steuerventilanordnung Control valve assembly
Die Erfindung steht im Zusammenhang mit Steuerventilanordnungen an einem Steuerraum, insbesondere eines Kraftstoffinjektors, mit einem die Ventilanordnung betätigenden elektromagnetischen Aktor. The invention relates to control valve arrangements on a control chamber, in particular of a fuel injector, with an electromagnetic actuator actuating the valve arrangement.
Stand der Technik State of the art
Bei einem aus der DE 10 2007 060 395 AI bekannten Kraftstoffinjektor ist zur Steuerung der Einspritzdüsen eine Düsennadel vorgesehen, deren düsenfernes Ende nach Art eines Plungers ausgebildet und verdrängerwirksam in einem Steuerraum angeordnet ist, der über eine Zulaufdrossel mit der Hochdruckseite des Kraftstoffinjektors kommuniziert und über eine Steuerventilanordnung mit der Niederdruckseite des Kraftstoffinjektors verbindbar ist. Dabei ist der Steuerraum bei geschlossener Steuerventilanordnung nur mit der Hochdruckseite des Kraftstoffinjektors verbunden, während der Druck im Steuerraum bei geöffneter Steuerventilanordnung infolge der dann vorhandenen Verbindung mit der Niederdruckseite absinkt. Bei Hochdruck im Steuerraum wird die Düsennadel in ihre Schließlage geschoben. Dagegen wird die Düsennadel vom Druck an den Düsen in ihre Offenlage geschoben, wenn das Schaltventil geöffnet ist. Bei dem Kraftstoffinjektor der DE 10 2007 060 395 AI besitzt der Steuerraum einen zur Niederdruckseite eines Ventilkörpers ausmündenden Auslasskanal, welcher durch die Steuerventilanordnung gesteuert wird. Zu diesem Zweck besitzt die Steuerventilanordnung einen hülsenförmigen Schließkörper, welcher auf einer zum Auslasskanal glei- chachsigen Führungsstange verschiebbar angeordnet ist, wobei der Ringspalt zwischen dem Außenumfang der Führungsstange und dem Innenumfang des hülsenförmigen Schließkörpers als praktisch leckagefreier Dichtspalt ausgebildet ist. Der hülsenförmige Schließkörper wirkt mit einem zur Mündung des Auslasskanals konzentrischen Sitz zu- sammen und ist mit einem Anker verbunden, der seinerseits mit einer zur Führungsstange gleichachsigen Elektromagnetanordnung zusammenwirkt. Bei elektrischer Bestromung der Elektromagnetanordnung wird der Anker zusammen mit dem hülsen- förmigen Schließkörper in Richtung der Elektromagnetanordnung gezogen, so dass der Schließkörper von seinem Sitz abhebt. Im elektrisch nicht bestromten Zustand der Elektromagnetanordnung wird der Schließkörper von einer Schließfeder in seine Schließlage gestellt, wobei sich der Anker von der Elektromagnetanordnung entfernt. In a fuel injector known from DE 10 2007 060 395 AI a nozzle needle is provided for controlling the injectors whose nozzle distal end formed in the manner of a plunger and displaceable in a control chamber which communicates via an inlet throttle with the high pressure side of the fuel injector and a Control valve assembly with the low pressure side of the fuel injector is connectable. In this case, the control chamber is connected with the control valve arrangement closed only with the high pressure side of the fuel injector, while the pressure in the control chamber with open control valve assembly as a result of the then existing connection with the low pressure side drops. At high pressure in the control room, the nozzle needle is pushed into its closed position. In contrast, the nozzle needle is pushed by the pressure at the nozzle in its open position when the switching valve is open. In the case of the fuel injector of DE 10 2007 060 395 A1, the control chamber has an outlet channel which opens out to the low-pressure side of a valve body and which is controlled by the control valve arrangement. For this purpose, the control valve arrangement has a sleeve-shaped closing body, which is displaceably arranged on a guide shaft which is identical to the outlet channel, wherein the annular gap between the outer circumference of the guide rod and the inner circumference of the sleeve-shaped closing body is designed as a virtually leak-free sealing gap. The sleeve-shaped closing body acts with a seat concentric with the mouth of the outlet channel. together and is connected to an armature, which in turn cooperates with an equiaxed to the guide rod electromagnet assembly. When electrical current is applied to the electromagnet arrangement, the armature is pulled together with the sleeve-shaped closing body in the direction of the electromagnet arrangement, so that the closing body lifts off from its seat. In the electrically non-energized state of the electromagnet arrangement of the closing body is placed by a closing spring in its closed position, wherein the armature away from the electromagnet assembly.
Grundsätzlich ist es erwünscht, die Betriebsphasen eines Kraftstoffinjektors genau erfassen zu können, um eine optimale Motorsteuerung zu ermöglichen. Durch Verschleißerscheinungen am Kraftstoffinjektor wird eine Drift der Schließzeitpunkte der Düsennadel verursacht, mit der Folge, dass sich die Einspritzmengen des Kraftstoffes entsprechend verändern und der jeweilige Motor nicht mehr optimal arbeitet. Ebenso weisen die Injektoren auf Grund unvermeidlicher Bauteilstreuungen auch eine Exemplarstreuung der Einspritzmenge bei gleicher Ansteuerung auf. In principle, it is desirable to be able to detect the operating phases of a fuel injector precisely in order to enable optimum engine control. Due to signs of wear on the fuel injector drift of the closing times of the nozzle needle is caused, with the result that the injection quantities of the fuel change accordingly and the respective engine is no longer working optimally. Likewise, due to unavoidable component scattering, the injectors also exhibit a copy spread of the injection quantity with the same activation.
Offenbarung der Erfindung Disclosure of the invention
Mit der Erfindung soll nun bei geringem konstruktivem Aufwand eine Erfassung der Schließzeiten ermöglicht werden. With the invention, a detection of the closing times is now to be made possible with little design effort.
Hierzu ist erfindungsgemäß vorgesehen, dass der Steuerraumdruck ein elastisch verformbares oder gegen elastischen Widerstand bewegliches Teil, welches das Magnetfeld des Aktors führt oder bündelt, belastet, wobei bewegungs- bzw. verformungsabhängige elektrische oder magnetische Parameter des Aktors zur Ermittlung von mit dem Steuerraumdruck korrelierten Betriebszeitpunkten oder -parametern ausgewertet werden. For this purpose, the invention provides that the control chamber pressure an elastically deformable or movable against elastic resistance part, which leads or bundles the magnetic field of the actuator loaded, wherein movement or deformation-dependent electrical or magnetic parameters of the actuator for determining correlated with the control chamber pressure operating times or parameters are evaluated.
Die Erfindung nutzt die Erkenntnis, dass sich der Steuerraumdruck am Beginn und am Ende der Einspritzphase eines Kraftstoffinjektors signifikant ändert. Indem nun erfindungsgemäß ein zum Steuerraumdruck analoger Eingriff in das Magnetfeld des Aktors erfolgt, kann durch Auswertung des zeitlichen Verlaufs der elektrischen Spannung oder des elektrischen Stroms am Aktor der Betriebsablauf des Kraftstoffinjektors mit hoher Präzision erfasst und überwacht werden. Der Aktor übernimmt also eine Doppelfunktion, indem er nicht nur zur Betätigung der Steuerventilanordnung sondern auch als Sensor für die Betriebsphasen des Kraftstoffinjektors dient. Gemäß einer konstruktiv bevorzugten Ausführungsform der Erfindung besitzt die erfindungsgemäße Steuerventilanordnung einen auf einer Führungsstange verschiebbar geführten hülsenförmigen Schließkörper, welcher mit einem Anker einer den Aktor bildenden Elektromagnetanordnung verbunden ist. Dabei ist des weiteren vorgesehen, dass der innerhalb des hülsenförmigen Schließkörpers vorliegende Fluiddruck über die Füh- rungsstange auf das verformbare bzw. bewegliche Teil abtragbar ist. The invention utilizes the insight that the control chamber pressure changes significantly at the beginning and at the end of the injection phase of a fuel injector. By now according to the invention an analogous to the control chamber pressure intervention in the magnetic field of the actuator, by evaluating the time course of the electrical voltage or the electric current at the actuator of the operation of the fuel injector with high Precision recorded and monitored. The actuator thus assumes a dual function by not only serving to actuate the control valve assembly but also as a sensor for the operating phases of the fuel injector. According to a structurally preferred embodiment of the invention, the control valve arrangement according to the invention has a guide rod on a slidably guided sleeve-shaped closing body, which is connected to an armature of the actuator forming the electromagnet assembly. It is further provided that the fluid pressure present within the sleeve-shaped closing body can be removed via the guide rod to the deformable or movable part.
Hier bleibt also die aus der DE 10 2007 060 395 AI an sich bekannte Konstruktion der Steuerventilanordnung weitestgehend unverändert, im Wesentlichen erhält nur die Führungsstange eine Doppelfunktion, indem sie auch die Übertragung der fluidischen Druckkräfte auf ein das Magnetfeld des Aktors führendes bzw. bündelndes, mittels derHere, therefore, the known from DE 10 2007 060 395 AI per se construction of the control valve assembly remains largely unchanged, essentially receives only the guide rod a double function by also the transmission of the fluidic pressure forces on the magnetic field of the actuator leading or bundling, means of the
Druckkräfte verformbares oder bewegbares Teil übernimmt. Compressive forces deformable or movable part takes over.
Dieses Teil kann als verformbares oder bewegliches Teil eines zur Stangenachse radialen Bodens einer Polschuhanordnung des als Aktor dienenden Elektromagnets aus- gebildet sein. Durch Verformung bzw. Verlagerung dieses Bodens kann die Relativlage der Polschuhe verändert werden, wobei gleichzeitig die elektrischen bzw. magnetischen Parameter des Elektromagnets verändert werden. This part may be formed as a deformable or movable part of a rod axis radial bottom of a Polschuhanordnung serving as an actuator solenoid. By deformation or displacement of this soil, the relative position of the pole pieces can be changed, at the same time the electrical or magnetic parameters of the electromagnet are changed.
Im übrigen wird hinsichtlich bevorzugter Merkmale der Erfindung auf die Ansprüche und die nachfolgende Erläuterung der Zeichnung verwiesen, anhand der besonders bevorzugte Ausführungsformen der Erfindung näher beschrieben werden. Moreover, reference is made to the claims and the following explanation of the drawing with regard to preferred features of the invention, are described in detail with reference to the particularly preferred embodiments of the invention.
Schutz wird nicht nur für angegebene oder dargestellte Merkmalskombinationen sondern auch für prinzipiell beliebige Kombinationen der angegebenen oder dargestellten Einzelmerkmale beansprucht. Protection is claimed not only for specified or illustrated feature combinations but also for any combinations of the specified or illustrated individual features.
Kurze Beschreibung der Zeichnung In der Zeichnung zeigt: Short description of the drawing In the drawing shows:
Fig. 1 einen ausschnittsweisen Axialschnitt eines Kraftstoffinjektors, 1 is a fragmentary axial section of a fuel injector,
Fig. 2 ein Diagramm, welches den zeitlichen Verlauf des Düsennadelhubs sowie des Steuerraumdrucks darstellt, 2 is a diagram showing the time course of the nozzle needle stroke and the control chamber pressure,
Fig. 3 einen Axialschnitt des Kraftstoffinjektors im Bereich des elektromagnetischen Aktors, 3 shows an axial section of the fuel injector in the region of the electromagnetic actuator,
Fig. 4 eine der Fig. 3 entsprechende Darstellung einer abgewandelten Ausführungsform, 4 a of FIG. 3 corresponding representation of a modified embodiment,
Fig. 5 eine Darstellung einer weiteren Abwandlung, Fig. 6 eine nochmals abgewandelte Ausführungsform, Fig. 7 eine zusätzliche Variante und Fig. 8 eine weitere Variante. Ausführungsformen der Erfindung 5 shows an illustration of a further modification, FIG. 6 shows a further modified embodiment, FIG. 7 shows an additional variant and FIG. 8 shows a further variant. Embodiments of the invention
Gemäß Fig. 1 ist innerhalb eines Injektorkörpers 1 ein Hochdruckraum 2 sowie ein Niederdruckraum 3 angeordnet. Diese beiden Räume sind voneinander durch ein Ventilstück 4 getrennt. According to FIG. 1, a high-pressure chamber 2 and a low-pressure chamber 3 are arranged within an injector body 1. These two spaces are separated from each other by a valve piece 4.
Der Hochdruckraum 2 kommuniziert über einen Zulaufkanal 5 mit einer nicht dargestellten Hochdruckquelle für Kraftstoff, in der Regel ein so genanntes Common Rail. Der Niederdruckraum 3 ist über eine nicht dargestellte Rücklaufleitung oder dergleichen mit einem Kraftstofftank oder dergleichen verbunden. Der Hochdruckraum 2 ist über nicht dargestellte Einspritzdüsen mit dem Brennraum eines ebenfalls nicht dargestellten Verbrennungsmotors verbindbar. Die Einspritzdüsen werden in bekannter Weise mittels einer Düsennadel gesteuert, von der in Fig. 1 nur das düsenferne Ende, welches als Plunger 6 ausgebildet ist, dargestellt ist. Der Plunger 6 ist verdrängerwirksam in einem im Ventilstück 4 angeordneten Steuerraum 7 angeordnet. Dieser Steuerraum kommuniziert über eine Zulaufdrossel 8 mit dem Hochdruckraum 2 und über eine Ablaufdrossel 9 mit dem Niederdruckraum 3, wobei die Ablaufdrossel 9 mittels einer Steuerventilanordnung 10 gesteuert wird. Wenn die Ablaufdrossel 9 mittels der Steuerventilanordnung 10 abgesperrt wird und die Düsennadel sich in ihrer Schließlage befindet, stellt sich im Steuerraum 7 der gleiche Hochdruck wie im Hochdruckraum 2 ein, mit der Folge, dass der Plunger 6 in Fig. 1 nach abwärts ge- presst wird und die damit verbundene Düsennadel in ihrer die Einspritzdüsen absperrenden Schließlage gehalten wird. Wird der Ablaufkanal 9 mittels der Steuerventilanordnung 10 geöffnet, stellt sich im Steuerraum 7 ein gegenüber dem Hochdruck im Hochdruckraum 2 stark verminderter Druck ein, und der Plunger 6 verschiebt sich zusammen mit der Düsennadel in Fig. 1 in Aufwärtsrichtung, das heißt die Düsennadel wird in deren Offenlage gestellt, so dass Kraftstoff durch die Einspritzdüsen in den Brennraum eingespritzt wird. The high pressure chamber 2 communicates via an inlet channel 5 with a high pressure fuel source, not shown, for fuel, usually a so-called common rail. The low-pressure space 3 is connected via a non-illustrated return line or the like to a fuel tank or the like. The high pressure chamber 2 is connected via injection nozzles, not shown, with the combustion chamber of an internal combustion engine, also not shown. The injection nozzles are controlled in a known manner by means of a nozzle needle, of which in Fig. 1, only the nozzle-distal end, which is designed as a plunger 6, is shown. The plunger 6 is arranged displacer-effective in a control chamber 7 arranged in the valve piece 4. This control chamber communicates via an inlet throttle 8 with the high-pressure chamber 2 and via an outlet throttle 9 with the low-pressure chamber 3, wherein the outlet throttle 9 is controlled by means of a control valve assembly 10. If the outlet throttle 9 is shut off by means of the control valve arrangement 10 and the nozzle needle is in its closed position, the same high pressure arises in the control chamber 7 as in the high-pressure chamber 2, with the result that the plunger 6 in FIG. 1 is pressed downwards is and the associated nozzle needle is held in its shut-off the injectors closing position. If the outlet channel 9 is opened by means of the control valve arrangement 10, a pressure which is greatly reduced in relation to the high pressure in the high-pressure chamber 2 sets in the control chamber 7, and the plunger 6 shifts in the upward direction together with the nozzle needle in FIG. 1, that is to say the nozzle needle is in their open position provided so that fuel is injected through the injectors into the combustion chamber.
Die Steuerventilanordnung 10 besitzt einen hülsenförmigen Schließkörper 11, der von einer Schließfeder 12, die als Schraubendruckfeder ausgebildet ist, gegen einen zur Auslassmündung des Ablaufkanals 9 konzentrischen Sitz gespannt wird. Im Beispiel der Fig. 1 ist der Sitz als Planfläche ausgebildet, auf der der hülsenförmige Schließkörper 11 mit einer linienförmigen Ringkante aufsitzt. Grundsätzlich kann jedoch auch ein anders geformter Sitz vorgesehen sein. The control valve assembly 10 has a sleeve-shaped closing body 11, which is tensioned by a closing spring 12, which is designed as a helical compression spring against a concentric to the outlet port of the flow channel 9 seat. In the example of Fig. 1, the seat is designed as a flat surface on which the sleeve-shaped closing body 11 is seated with a line-shaped annular edge. In principle, however, a differently shaped seat may be provided.
Der hülsenförmige Schließkörper 11 ist auf einer zur Längsachse 100 des Injektorkörpers 1 gleichachsigen Führungsstange 13 axial verschiebbar geführt, wobei der Ringspalt zwischen dem Innenumfang des Schließkörpers 11 und dem Außenumfang der Führungsstange 13 als praktisch leckagefreier Drosselspalt ausgebildet ist. Wenn der Schließkörper 11 die in Fig. 1 dargestellte Schließlage einnimmt, wird der innerhalb des Schließkörpers 11 gebildete Druckraum 14, welcher über den Ablaufkanal 9 mit dem Steuerraum 7 kommuniziert und dementsprechend gleichen Fluiddruck wie der Steuer- räum 7 aufweist, gegenüber dem Niederdruckraum 3 abgesperrt. Am Schließkörper 11 ist ein sternförmiger Anker 15 einer Elektromagnetanordnung 16 angeordnet, der als Aktor zur Betätigung der Steuerventilanordnung 10 vorgesehen ist. Die Elektromagnetanordnung 16 besitzt in bekannter Weise eine Magnetspule 17, die innerhalb einer zur Führungsstange 13 konzentrischen Polschuhanordnung mit einem ringförmigen Außenpol 18 und einem ringförmigen Innenpol 19 angeordnet ist. Wird die Magnetspule 17 elektrisch bestromt, wird der Anker 15 von den Polen 18 und 19 magnetisch angezogen, so dass der Schließkörper 11 gegen die Kraft der Schließfeder 12 von seinem Sitz abgehoben und die Steuerventilanordnung 10 geöffnet wird. The sleeve-shaped closing body 11 is axially displaceably guided on a guide axis 13, which is equiaxial to the longitudinal axis 100 of the injector body 1, wherein the annular gap between the inner periphery of the closing body 11 and the outer circumference of the guide rod 13 is formed as a virtually leak-free throttle gap. When the closing body 11 assumes the closed position shown in FIG. 1, the pressure chamber 14 formed within the closing body 11, which communicates with the control chamber 7 via the outlet channel 9, and accordingly the same fluid pressure as the control raum 7 has shut off from the low-pressure chamber 3. On the closing body 11, a star-shaped armature 15 of an electromagnet arrangement 16 is arranged, which is provided as an actuator for actuating the control valve arrangement 10. The solenoid assembly 16 has in a known manner a magnetic coil 17, which is arranged within a concentric to the guide rod 13 Polschuhanordnung with an annular outer pole 18 and an annular inner pole 19. If the magnetic coil 17 is energized electrically, the armature 15 is magnetically attracted by the poles 18 and 19, so that the closing body 11 is lifted against the force of the closing spring 12 from its seat and the control valve assembly 10 is opened.
Während der geschlossenen Phase der mit dem Plunger 6 verbundenen Düsennadel, das heißt bei geschlossenen Einspritzdüsen, ist die Steuerventilanordnung 10 geschlossen, und im Druckraum 14 sowie im Steuerraum 7 liegen gleiche Fluiddrucke vor. Unmittelbar vor dem Schließzeitpunkt der Düsennadel sinkt der Druck im Steuerraum 7 wegen des zu diesem Zeitpunkt geringen Drucks unter dem Düsensitz der Düsennadel und der damit einhergehenden Schließbewegung des Plungers 6 unter den Hochdruck im Zulaufkanal 5 ab. Unmittelbar nach dem Schließen der Düsennadel kommt es wegen des nun stillstehenden Plungers 6 zu einem steilen Anstieg des Drucks im Steuerraum 7, wobei der Steuerraumdruck auf den Druck im Zulaufkanal 5 ansteigt. Der Druck im Steuerraum 7 und der damit praktisch identische Druck im Druckraum 14 weisen folglich zum Schließzeitpunkt der Düsennadel ein ausgeprägtes Minimum auf. In Fig. 2 ist der Verlauf des Düsennadelhubs im Diagramm A und der Verlauf des Steuerraumdrucks im Diagramm B beispielhaft dargestellt. Da der Druck des Steuerraums 7 auch im Druckraum 14 vorliegt, wird die Führungsstange 13 innerhalb des Schließkörpers 11 bei geschlossener Steuerventilanordnung 10 stirnseitig immer vom Steuerraumdruck belastet. During the closed phase of the nozzle needle connected to the plunger 6, that is with closed injection nozzles, the control valve assembly 10 is closed, and in the pressure chamber 14 and in the control chamber 7 are the same fluid pressures. Immediately before the closing time of the nozzle needle, the pressure in the control chamber 7 drops because of the low pressure under the nozzle seat of the nozzle needle and the associated closing movement of the plunger 6 under the high pressure in the inlet channel 5. Immediately after closing the nozzle needle occurs because of the now stationary plunger 6 to a steep increase in pressure in the control chamber 7, wherein the control chamber pressure increases to the pressure in the inlet channel 5. The pressure in the control chamber 7 and thus virtually identical pressure in the pressure chamber 14 thus have a pronounced minimum at the closing time of the nozzle needle. In Fig. 2 the course of the nozzle needle stroke in the diagram A and the course of the control chamber pressure in the diagram B is exemplified. Since the pressure of the control chamber 7 is also present in the pressure chamber 14, the guide rod 13 is always loaded within the closing body 11 with closed control valve assembly 10 frontally from the control chamber pressure.
Erfindungsgemäß ist nun vorgesehen, den Steuerraumdruck mittels der Führungsstange 13 auf eine in Fig. 1 nur schematisch dargestellte Übertragung 20 abzutragen, die elektromagnetische Parameter der Elektromagnetanordnung 16 verändert, derart, dass die Schließzeitpunkte der Düsennadel durch entsprechende Auswertung des elektrischen Strom-Spannungsverlaufs an der Magnetspule 17 erkannt werden können. Damit übernimmt die Elektromagnetanordnung 16 zusätzlich zu ihrer Aktorfunktion auch Sen- sorfunktionen, und die Führungsstange 13 hat zusätzlich zu ihrer Führungsfunktion für den Schließkörper 11 die Aufgabe eines Steuerelements zur Veränderung von Parametern der Elektromagnetanordnung 16. According to the invention it is now provided to remove the control chamber pressure by means of the guide rod 13 to a transmission 20 shown only schematically in Fig. 1, the electromagnetic parameters of the solenoid assembly 16 changes such that the closing times of the nozzle needle by appropriate evaluation of the electric current-voltage curve at the solenoid 17 can be detected. In this way, in addition to its actuator function, the electromagnet arrangement 16 also takes over In addition to their guiding function for the closing body 11, the guide rod 13 has the task of a control element for changing parameters of the electromagnet arrangement 16.
Die Fig. 3 zeigt nun ein erstes Ausführungsbeispiel für eine Möglichkeit der Veränderung der Parameter der Elektromagnetanordnung 16. Die vom Druck im Druckraum 14 abhängige Axialkraft der Führungsstange 13 wird auf einen elastisch biegbaren Boden 21 abgetragen, der einen Teil der Polschuhanordnung bildet und mit den Polen 18 und 19 verbunden ist. Entsprechend der Verbiegung des Bodens 21 ändert sich der Luftspalt zwischen dem Innenpol 19 und dem Anker 15, das heißt bei einer Erhöhung des Drucks im Steuerraum 7 und der damit einhergehenden Erhöhung des Drucks im Druckraum 14 wird der Luftspalt zwischen Anker 15 und Innenpol 19 vergrößert. Wenn nun der Steuerraumdruck unmittelbar nach dem Schließzeitpunkt der Düsennadel ansteigt, steigt zu diesem Zeitpunkt auch die auf den Boden 21 wirkende Axialkraft der Führungsstange 13 und bewirkt eine Erhöhung des Luftspalts zwischen Innenpol 19 und Anker 15. Ist zu diesem Zeitpunkt ein Restfluss im Magnetkreis vorhanden, so bewirkt die Vergrößerung des vorgenannten Luftspalts eine Veränderung der Spulenspannung (bei verschwindendem Spulenstrom) oder eine Änderung des Spulenstroms (bei verschwindender Spulenspannung). Sollte kein hinreichender magnetischer Restfluss vorhanden sein, so wird vor dem erwarteten Schließzeitpunkt der Düsennadel die Magnetspule 12 schwach bestromt, um erneut Magnetfluss aufzubauen. Dabei wird das Maß der Bestromung so gering gewählt, dass der Schließkörper 11 in seiner Schließlage bleibt. 3 shows a first embodiment of a possibility of changing the parameters of the solenoid assembly 16. The pressure of the pressure chamber 14 dependent axial force of the guide rod 13 is removed to an elastically bendable bottom 21, which forms part of the Polschuhanordnung and with the poles 18 and 19 is connected. Corresponding to the bending of the bottom 21, the air gap between the inner pole 19 and the armature 15 changes, that is, with an increase in the pressure in the control chamber 7 and the associated increase in pressure in the pressure chamber 14, the air gap between the armature 15 and inner pole 19 is increased. Now, if the control chamber pressure increases immediately after the closing time of the nozzle needle, at this time increases the force acting on the bottom 21 axial force of the guide rod 13 and causes an increase in the air gap between the inner pole 19 and armature 15. If there is a residual flux in the magnetic circuit at this time, Thus, the enlargement of the aforementioned air gap causes a change in the coil voltage (at vanishing coil current) or a change in the coil current (at vanishing coil voltage). If there is no sufficient residual magnetic flux, the solenoid 12 is energized weakly before the expected closing time of the nozzle needle to re-establish magnetic flux. The degree of energization is chosen so low that the closing body 11 remains in its closed position.
Im Ausführungsbeispiel der Fig. 4 ist der Boden 21 auf seiner vom Innenpol 19 abgewandten Seite stationär abgestützt. Außerdem ist der Außenpol 18 separat vom Boden 21 stationär im Injektorkörper 1 angeordnet, wobei zwischen dem Boden 21 und dem Außenpol 18 ein Luftspalt 22 verbleibt. Dieser Luftspalt verändert sich in Abhängigkeit von der Axialkraft der Führungsstange 13. Die damit einhergehenden Änderungen des magnetischen Flusses der Elektromagnetanordnung 16 eröffnen somit wiederum die Möglichkeit, den Schließzeitpunkt der Düsennadel genau zu erfassen. Bei der Ausführungsform der Fig. 5 bilden der Innenpol 19 sowie der Außenpol 18 eine vom biegsamen Boden 21 getrennte Polschuhanordnung, deren Brückenbereich zwischen den Polen 18 und 19 mit vergleichsweise kleinem Querschnitt ausgebildet ist. Am Außenumfang liegt der aus ferromagnetischem Material bestehende Boden 21 an einem zugewandten Ringsteg der Polschuhanordnung an, derart, dass ein Luftspalt 23 erzeugt wird. Dieser Luftspalt verändert sein Spaltmaß in Abhängigkeit von der elastischen Verbiegung des Bodens 21 und dementsprechend in Abhängigkeit von der Axialkraft der Führungsstange 13. Damit verändert sich der magnetische Widerstand, der dem magnetischen Fluss zwischen den Polen 19 und 20 entgegensteht. Die damit verbundenen Rückwirkungen auf den elektrischen Strom-Spannungsverlauf an der Magnetspule 17 bieten wiederum die Möglichkeit, den Schließzeitpunkt der Düsennadel zu erkennen. In the embodiment of Fig. 4, the bottom 21 is supported stationary on its side remote from the inner pole 19 side. In addition, the outer pole 18 is arranged separately from the bottom 21 stationary in the injector body 1, wherein between the bottom 21 and the outer pole 18, an air gap 22 remains. This air gap changes as a function of the axial force of the guide rod 13. The associated changes in the magnetic flux of the solenoid assembly 16 thus in turn open up the possibility of accurately detecting the closing time of the nozzle needle. In the embodiment of FIG. 5, the inner pole 19 and the outer pole 18 form a pole shoe arrangement which is separate from the flexible base 21 and whose bridge region is formed between the poles 18 and 19 with a comparatively small cross-section. At the outer periphery of the existing ferromagnetic material bottom 21 abuts a facing annular web of the pole piece, such that an air gap 23 is generated. This air gap changes its gap as a function of the elastic deflection of the bottom 21 and accordingly in dependence on the axial force of the guide rod 13. This changes the magnetic resistance, which opposes the magnetic flux between the poles 19 and 20. The associated repercussions on the electric current-voltage curve at the magnetic coil 17 in turn provide the opportunity to detect the closing time of the nozzle needle.
Die Ausführungsform der Fig. 6 unterscheidet sich von der Ausführungsform der Fig. 5 im Wesentlichen nur dadurch, dass der biegsame Boden 21 auf einem Ringsteg auf der Rückseite des Innenpols 19 aufliegt und bei elastischer Verbiegung des Bodens 21 ein Luftspalt 24 verändert wird. Funktionsmäßig gelten somit für die Ausführungsform der Fig. 6 die Ausführungen zur Ausführungsform der Fig. 5. The embodiment of FIG. 6 differs from the embodiment of FIG. 5 essentially only in that the flexible bottom 21 rests on a ring land on the back of the inner pole 19 and an elastic gap 24 is changed in elastic bending of the bottom 21. Functionally, the embodiments of the embodiment of FIG. 5 thus apply to the embodiment of FIG. 6.
Bei der Ausführungsform der Fig. 7 sind der Innenpol 19 und der Außenpol 18, die jeweils aus einem magnetisierbaren, insbesondere ferromagnetischen Material bestehen, miteinander über einen Steg 25 aus amagnetischem Material verbunden. Dieser Steg 25 ist im Beispiel der Fig. 7 auf der von dem Anker 15 abgewandten Stirnseite der Magnetspule 17 vorgesehen. Der biegsame Boden 21 ist derart angeordnet und ausgebildet, dass er bei verschwindender Axialkraft der Führungsstange 13, das heißt bei entsprechend geringem Druck im Steuerraum 7 bzw. im Druckraum 14, auf den zugewandten Stirnseiten der Pole 18 und 19 aufliegt. Damit bildet der Boden 21, welcher aus einem magnetisch gut leitfähigem Material besteht, eine magnetisch gut leitfähige Verbindung zwischen den Polen 18 und 19. Sobald die Führungsstange 13 mit größerer Axialkraft gegen den Boden 21 gespannt wird, hebt dieser vom Innenpol 19 unter Bildung eines Luftspalts 26 ab, so dass der magnetische Widerstand für den magnetischen Fluss zwischen den Polen 18 und 19 signifikant vergrößert wird. Eine funktional gleichartige Ausführungsform ist in Fig. 8 dargestellt. Diese Ausfüh- rungsform unterscheidet sich von der Ausführungsform nach Fig. 7 lediglich dadurch, dass der amagnetische Steg 25' auf der dem Anker 15 zugewandten Seite der Magnetspule 17 angeordnet ist. Wenn die Führungsstange 13 axial kraftfrei ist, liegt der Boden 21 wiederum auf den zugewandten Stirnseiten der Pole 18 und 19 auf, und bei entsprechender Axialkraft der Führungsstange 13 wird am Innenpol der Luftspalt 26' gebildet. In the embodiment of Fig. 7, the inner pole 19 and the outer pole 18, each consisting of a magnetizable, in particular ferromagnetic material, connected to each other via a web 25 of non-magnetic material. This web 25 is provided in the example of FIG. 7 on the side facing away from the armature 15 end face of the magnetic coil 17. The flexible bottom 21 is arranged and designed such that it rests on vanishing axial force of the guide rod 13, that is at a correspondingly low pressure in the control chamber 7 and in the pressure chamber 14, on the facing end faces of the poles 18 and 19. Thus, the bottom 21, which consists of a magnetically good conductive material, a magnetically good conductive connection between the poles 18 and 19. Once the guide rod 13 is stretched with greater axial force against the bottom 21, this lifts from the inner pole 19 to form an air gap 26, so that the magnetic resistance for the magnetic flux between the poles 18 and 19 is significantly increased. A functionally similar embodiment is shown in Fig. 8. This embodiment differs from the embodiment according to FIG. 7 only in that the non-magnetic web 25 'is arranged on the side of the magnet coil 17 facing the armature 15. If the guide rod 13 is axially free of force, the bottom 21 is again on the facing end faces of the poles 18 and 19, and with a corresponding axial force of the guide rod 13, the air gap 26 'is formed at the inner pole.

Claims

Ansprüche claims
1. Steuerventilanordnung (10) für einen Steuerraum (7) eines Kraftstoffinjektors, mit einem die Ventilanordnung (10) betätigenden elektromagnetischen Aktor (15, 16), 1. control valve arrangement (10) for a control chamber (7) of a fuel injector, with a valve arrangement (10) actuated electromagnetic actuator (15, 16),
dadurch gekennzeichnet,  characterized,
dass der Steuerraumdruck auf ein elastisch verformbares Teil (21) abtragbar ist, welches ein elektromagnetisches Feld des Aktors (15, 16) führt bzw. bündelt, wobei verformungsabhängige elektromagnetische Parameter des Aktors (15, 16) zur Ermittlung von mit dem Steuerraumdruck korrelierten Zeitpunkten mittels einer Auswerteeinrichtung erfassbar sind.  the control chamber pressure can be ablated on an elastically deformable part (21) which guides or bundles an electromagnetic field of the actuator (15, 16), wherein deformation-dependent electromagnetic parameters of the actuator (15, 16) are used to determine times correlated to the control chamber pressure An evaluation device can be detected.
2. Steuerventilanordnung nach Anspruch 1, 2. Control valve arrangement according to claim 1,
dadurch gekennzeichnet,  characterized,
dass ein auf einer Führungsstange (13) verschiebbar geführter hülsenförmi- ger Schließkörper (11) vorgesehen ist, welcher mit einem Anker (15) einer als Aktor vorgesehenen Elektromagnetanordnung (16) verbunden ist, und dass ein innerhalb des hülsenförmigen Schließkörpers (11) auftretender Flu- iddruck über die Führungsstange (13) auf das verformbare Teil (21) abtragbar ist.  in that a sleeve-shaped closing body (11) which is displaceably guided on a guide rod (13) is provided, which is connected to an armature (15) of an electromagnet arrangement (16) provided as an actuator, and in that a flow occurring within the sleeve-shaped closing body (11) - iddruck on the guide rod (13) on the deformable part (21) is ablatable.
3. Steuerventilanordnung nach Anspruch 1 oder 2, 3. control valve arrangement according to claim 1 or 2,
dadurch gekennzeichnet,  characterized,
dass die Elektromagnetanordnung (16) eine elektrische Magnetspule (17) mit durch die Führungsstange (13) verformbarer Polschuhanordnung (18, 19) aufweist.  in that the electromagnet arrangement (16) has an electric magnet coil (17) with pole shoe arrangement (18, 19) which can be deformed by the guide rod (13).
4. Steuerventilanordnung nach Anspruch 3, 4. control valve arrangement according to claim 3,
dadurch gekennzeichnet,  characterized,
dass ein Luftspalt zwischen der Polschuhanordnung (18, 19) und dem Anker (15) durch Verformung der Polschuhanordnung veränderbar ist. Steuerventilanordnung nach einem der Ansprüche 2 bis 4, an air gap between the pole piece arrangement (18, 19) and the armature (15) can be changed by deformation of the pole piece arrangement. Control valve arrangement according to one of claims 2 to 4,
dadurch gekennzeichnet, characterized,
dass ein ringförmiger Innenpol (19) und ein ringförmiger Außenpol (18) einem gemeinsamen Boden (21) zugeordnet sind. in that an annular inner pole (19) and an outer annular pole (18) are assigned to a common base (21).
Steuerventilanordnung nach Anspruch 5, Control valve arrangement according to claim 5,
dadurch gekennzeichnet, characterized,
dass die Führungsstange (13) auf einem Zentralbereich des Bodens (21) abgestützt ist. in that the guide rod (13) is supported on a central region of the base (21).
Steuerventilanordnung nach einem der Ansprüche 2 bis 6, Control valve arrangement according to one of claims 2 to 6,
dadurch gekennzeichnet, characterized,
dass zwischen dem Boden und einem der Pole (18, 19) ein durch Verformung des Bodens veränderbarer Luftspalt (23, 24, 26, 26') angeordnet ist. in that an air gap (23, 24, 26, 26 ') which is variable by deformation of the bottom is arranged between the bottom and one of the poles (18, 19).
Verfahren zum Betrieb einer Steuerventilanordnung nach einem der Ansprüche 1 bis 7, Method for operating a control valve arrangement according to one of Claims 1 to 7,
dadurch gekennzeichnet, characterized,
dass das elektromagnetische Feld des Aktors fluiddruckabhängig verändert wird und that the electromagnetic field of the actuator is changed fluid pressure dependent and
dass mit der Auswerteeinrichtung elektrische Ströme und/oder Spannungen am Aktor erfasst und ausgewertet werden. that the evaluation device detects and evaluates electrical currents and / or voltages at the actuator.
EP10768197.5A 2009-11-03 2010-09-30 Control valve assembly Active EP2496824B1 (en)

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DE102012206586A1 (en) * 2012-04-20 2013-10-24 Robert Bosch Gmbh Method for operating a fuel injector
DE102012223244A1 (en) 2012-12-14 2014-06-18 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
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DE19930309C2 (en) * 1999-07-01 2001-12-06 Siemens Ag Method and device for regulating the injection quantity in a fuel injection valve with a piezo element actuator
DE102007060395A1 (en) 2007-12-03 2009-06-04 Robert Bosch Gmbh Switching valve for injectors

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