EP1430208B1 - Fuel injection device for internal combustion engine - Google Patents

Fuel injection device for internal combustion engine Download PDF

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Publication number
EP1430208B1
EP1430208B1 EP02764515A EP02764515A EP1430208B1 EP 1430208 B1 EP1430208 B1 EP 1430208B1 EP 02764515 A EP02764515 A EP 02764515A EP 02764515 A EP02764515 A EP 02764515A EP 1430208 B1 EP1430208 B1 EP 1430208B1
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EP
European Patent Office
Prior art keywords
fuel injection
control valve
actuator
voltage
pressure
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.)
Expired - Lifetime
Application number
EP02764515A
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German (de)
French (fr)
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EP1430208A1 (en
Inventor
Juergen Boss
Johannes-Joerg Rueger
Klaus Zimmermann
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1430208A1 publication Critical patent/EP1430208A1/en
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Classifications

    • 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
    • F02D41/2096—Output circuits, e.g. for controlling currents in command coils for controlling piezoelectric injectors
    • 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
    • F02M57/02—Injectors structurally combined with fuel-injection pumps
    • F02M57/022—Injectors structurally combined with fuel-injection pumps characterised by the pump drive
    • F02M57/023—Injectors structurally combined with fuel-injection pumps characterised by the pump drive mechanical
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/20—Varying fuel delivery in quantity or timing
    • F02M59/36—Varying fuel delivery in quantity or timing by variably-timed valves controlling fuel passages to pumping elements or overflow passages
    • F02M59/366—Valves being actuated electrically
    • 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
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric 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
    • F02M65/00—Testing fuel-injection apparatus, e.g. testing injection timing ; Cleaning of 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
    • 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

Definitions

  • the invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.
  • Such a fuel injector is through the DE 198 35 494 A1 known.
  • This fuel injection device has a fuel injection valve, with a Injection valve member, through which at least one Injection opening is controlled.
  • the injection valve member is of that in a pressure room of the Fuel injection valve prevailing pressure in one Opening direction acted upon against a closing force.
  • a high-pressure fuel pump generated by a Cam is driven in a lifting movement. It is a by a piezoelectric actuator actuated control valve provided by an electrical control device is controlled and by the one connection of the Pressure chamber is controlled with a discharge space.
  • the Control valve has a control valve member, on which the Actuator acts via a hydraulic coupler to this between an open position and a closed position To move position.
  • the control valve member in his closed position, so is the pressure chamber of Relief space separated and it may be in this Build up high pressure for a fuel injection.
  • the Time of reaching the closing position of the Control valve member is thus of great importance for the Control of fuel injection. Since that Control valve member from the actuator, however, through the coupler is disconnected, is no information about this date available. In addition, for a proper Function of the control valve also a complete filling required of the coupler.
  • the fuel injection device with the Features according to claim 1 has the advantage that the function of the control valve can be monitored.
  • a pressure on, even after Completion of the charging process on the actuator and back in this with disconnected power supply one for the Pressure conditions in the coupler and consequently also for the Implementation of the drive voltage in the stroke of Control valve member generates characteristic piezoelectric voltage.
  • the voltage between the electrical connections on the piezoelectric actuator can thus without the requirement another sensor as a measurement parameter for the Valve behavior are used.
  • the measured Voltage can be used according to claim 2, to the time of reaching the closing position of Control valve member to determine.
  • the course of the tension can as indicated in claim 3 to the occurrence of a Minimums are monitored in the course of the curve.
  • the pressure in the Coupler takes after charging the actuator in the temporal course first off, as the actor after completion Charging reaches approximately its full stroke has, while the control valve member is at this time still moved to its closed position and the coupler thus relaxed. Once the control valve member the Has reached closing position and due to a Bouncing towards its open position moved back, but there is a compression of the coupler medium, resulting in an increase in the Terminal voltage noticeable.
  • the voltage can also be used to detect the Be filled state of the coupler, since the Pressure curve in the coupler depends on the filling state and thus also effects on the tension Has.
  • the test drive provided according to claim 8 allows verification of the function of the control valve before fuel injection, with correction values can be determined in the following Fuel injection can be used. Of the time interval between the determination of the correction value and the control of the control valve to Fuel injection is thus very low, so that the Fuel injection can be done with high accuracy.
  • FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation and Figure 2 a Fuel injection valve of the fuel injection device in an enlarged view.
  • FIGs 1 and 2 is a Fuel injection device for an internal combustion engine shown for example a motor vehicle.
  • the Fuel injection device has a High-pressure fuel pump 10 and connected to this Fuel injection valve 12 on.
  • the high-pressure fuel pump 10 and the fuel injection valve 12 directly with each other connected and form a so-called pump-nozzle unit. It Alternatively, however, it can also be provided that the High-pressure fuel pump 10 away from Fuel injector 12 is disposed and via a Line is connected to this. It is for every cylinder the internal combustion engine, a fuel injection device with high-pressure fuel pump 10 and Fuel injection valve 12 is provided.
  • the high-pressure fuel pump 10 has a pump body 14 in, in which in a cylinder bore 16, a pump piston 18th slidably guided in the cylinder bore 16th limited a pump working space 20.
  • the pump piston 18 is transmitted through a camshaft of the internal combustion engine a cam 22 against a return spring 24 in one Driven stroke movement.
  • Between the cam 22 and the Pump piston 18 may be a rocker arm as a transmission element 26 may be arranged.
  • the cam 22 has a raised Region 22a, over which the pump piston 18 against the Force of the return spring 24 in the cylinder bore 16 up to an internal dead center is pushed in, and one shallower region 22b, over which the pump piston 18 through the return spring 24 from the cylinder bore 16 up to an outer dead center is pushed out.
  • the fuel injection valve 12 has a valve body 30 on, which can be designed in several parts and in the in a bore 32 an injection valve member 34 is guided.
  • the valve body 30 has at its the combustion chamber of the Cylinder of the engine facing end portion at least one, preferably a plurality of injection openings 36 on, which is distributed over the circumference of the valve body 30 are arranged.
  • the injection valve member 34 has at its the combustion chamber facing end an example approximately conical sealing surface 38, which with a in Valve body 30 facing in the combustion chamber End region formed valve seat 40 cooperates, from or after which discharge the injection openings 36.
  • valve body 30 is between the injection valve member 34 and the bore 32 to the valve seat 40 toward an annular space 42nd formed, in its the valve seat 40 facing away End region by a radial extension of the bore 32 in a pressure space 44 surrounding the injection valve member 34 passes.
  • the injection valve member 34 points at the level of Pressure chamber 44 by a change in cross section a Pressure shoulder 46, on the in the pressure chamber 44th prevailing pressure a force on the injection valve member 34th generated away from the valve seat 40. Facing away from the combustion chamber End of the injection valve member 34 engages a prestressed Closing spring 48, through which the injection valve member 34th is pressed toward the valve seat 40.
  • the closing spring 48 is in a spring chamber 50 of a part of the valve body 30th forming spring holder 30 a, which adjoins the Bore 32 connects.
  • the pressure chamber 44 of the fuel injection valve 12 is over a channel 52 with the pump chamber 20 of the High-pressure fuel pump 10 connected.
  • prevailing pressure on the pressure shoulder 46 on the Injection valve member 34 generates a larger force than the by the closing spring 48 generated force, so that lifts Injection valve member 34 in the opening direction 35 with its sealing surface 38 from the valve seat 40 and gives the Injection openings 36 free, through the fuel in the Combustion chamber is injected.
  • an electric controlled control valve 54 is provided, through which a Connection of the pump working chamber 20 with a Relief space is controlled.
  • a relief space can For example, the fuel tank 11 of the Be motor vehicle or another area in which a low pressure prevails.
  • the control valve 54 has Control valve member 56, which via a hydraulic Coupler 57 is actuated by a piezoelectric actuator 58 becomes.
  • the actuator 58 is controlled by an electronic Control device 53 with an electrical voltage provided.
  • the actuator 58 has a number of connected in series piezo elements 59 on.
  • the Control valve 54 is, for example, on the pump body 14 arranged.
  • the actuator 58 is on the one hand with a Housing wall 60, through the electrical connections 61 of the Actuator 58 are passed, and on the other hand with a Control piston 62 positively connected.
  • the adjusting piston 62 closes with its end face 63 facing away from the actuator 58 the hydraulic coupler 57 from.
  • the hydraulic coupler 57 in turn acts on one in a connection channel 64 guided adjusting piston 65, at the end of the coupler 57th opposite end of the control valve member 56 is arranged. It can be provided that the control valve member 56 with two Valve seats cooperates, which in a valve chamber 66 are formed, in which the control valve member 56 is arranged is.
  • the control valve member 56 is located in a first End position, which is a tensionless rest position of Actuator 58 corresponds to a first valve seat 68 in Valve space 66 on. In a second end position, the one maximum activation of the actuator 58 corresponds and a Closed position of the control valve member 56 is located Control valve member 56 at a second valve seat 70 in Valve chamber 66 and closes this. It can also be provided that the control valve 54 as double-switching valve is formed, wherein the Control valve member 56 when it is in contact with one of both valve seats 68,70 is respectively closed and only in an intermediate position between the two Valve seats 68,70 is open.
  • valve chamber 66 opens between the two valve seats 68,70 a connection 71 to the discharge room.
  • valve chamber 66 On the second valve seat 70, the valve chamber 66 a Connection with the pump working chamber 20 on. If that is Control valve member 56 in its first end position in Appendix is located on the first valve seat 68, so is the compound of Valve space 66 to the pump working chamber 20 via the second Valve seat 70 is opened, so that the pump working chamber 20 with connected to the discharge room and is not in this Can build up high pressure.
  • connection 71 of the Valve chamber 66 with the discharge space may be a Throttle 67 may be provided.
  • Control valve member 56 in its second end position and thus its closed position in contact with the second valve seat 70th is the connection of the valve space 66 to Pump working chamber 20 via the second valve seat 70th closed, so that the pump working chamber 20 from Relief space is separated and in this high pressure can build, according to the delivery stroke of the pump piston 18.
  • the date of reaching the closing position of Control valve member 56 thus determines the beginning of Fuel injection and the duration of the arrangement of Control valve member 56 in its closed position determines the Fuel quantity injected.
  • the actuator 58 of the control valve 54 is replaced by the Control device 53 depending on operating parameters of Internal combustion engine, such as speed, load, Temperature and others, controlled.
  • Internal combustion engine such as speed, load, Temperature and others
  • For the control of Fuel injection with high accuracy is one Feedback on the start of fuel injection required, at least approximately simultaneously with the Time of reaching the closing position of the Control valve member 56 is.
  • a voltage measuring device 72nd connected which are part of the control device 53 can.
  • To the voltage measuring device 72 may have a Diagnostic device 74 may be connected.
  • the measured data can directly, for example as an analogue voltage signal, be transmitted to the diagnostic device 74. Consequently there is a monitoring of the voltage between the Connections 61 of the actuator 58 as a function of time. It can however, alternatively, the formation of the temporal Derivation of the voltage between the terminals 61 be provided. For this the voltage signals become one associated with the voltage measuring device 72 Differentiator 76 is supplied. The educated there differentiated signals are subsequently sent to the Diagnostic device 74 transmitted. In both alternatives is derived from the time course of the tension between the Terminals 61 of the actuator 58 in the diagnostic device 74th upon reaching the closed position of the control valve member 56 closed.
  • control valve member 56 Once the control valve member 56 its closed position has reached and due to a bounce in the direction however, it moves back to its first end position a compression of the medium in the coupler, the analogously in an increase in the voltage between the Make connections 61 of the actuator 58 noticeable.
  • the im Voltage curve occurring minimum thus identifies the Time at which the control valve member 56 his Has reached closing position.
  • Detecting the timing of the closing of the control valve 54 can provide correction values for control parameters Control device 53 are obtained, which for a subsequent fuel injection can be used and by the accuracy of the fuel injection in terms of timing of fuel injection and Fuel injection quantity can be improved.
  • the test control of the Control valve 54 is preferably carried out during a Time interval, during which also the filling of the Pump workspace 20 during the suction stroke of the pump piston 18 with Fuel as well as the removal of fuel from the Pump work space 20 to terminate the Fuel injection with open control valve 54 is not or is affected as little as possible.
  • the reduction of the voltage also depends on particularly pronounced degree of filling in the coupler 57 from.
  • fully filled coupler 57 is a comparatively pronounced voltage dip of, for example, about 50V detectable.
  • this effect is only partial filled coupler 57 significantly lower, the For example, voltage drop is only about 15V.
  • a Diagnosis statement formed by after the loading phase of Actuator 58 the voltage is measured. After a predefinable Waiting time of about 0.25 ms, for example, becomes the voltage measured again. Then the difference of both measured values formed and compared to a limit. It can do that a fixed limit may be specified, for example can be about 30V. Alternatively, however, a Operating point dependent limit from a by previous Obtained in a data storage module 78 stored map are based. The waiting time is so selectable that the measurement of the voltage immediately before a subsequent tax intervention, namely before a further increase in the voltage takes place.
  • the Setpoint is chosen such that, despite the detected incomplete filling of the coupler 57 after driving the intended stroke of the Control valve member 56 results.

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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)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Abstract

A fuel injection system having a fuel injection valve in which an injection valve member is urged in an opening direction counter to a closing force by pressure in a pressure chamber which generated by a high-pressure fuel pump driven by a cam. A control valve is actuated by a piezoelectric actuator triggered by an electric control unit by which a communication of the pressure chamber with a relief chamber is controlled. When the control valve is closed, the pressure chamber is disconnected from the relief chamber. The control valve has a control valve member coupled with the actuator via a hydraulic coupler. The actuator, after a charging phase, communicates with an associated voltage meter, and the voltage between the electrical terminals of the actuator is monitored for detecting the function of the control valve.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine nach der Gattung des Anspruchs 1.The invention is based on a Fuel injection device for an internal combustion engine according to the preamble of claim 1.

Eine solche Kraftstoffeinspritzeinrichtung ist durch die DE 198 35 494 A1 bekannt. Diese Kraftstoffeinspritzeinrichtung weist ein Kraftstoffeinspritzventil auf, mit einem Einspritzventilglied, durch das wenigstens eine Einspritzöffnung gesteuert wird. Das Einspritzventilglied ist von dem in einem Druckraum des Kraftstoffeinspritzventils herrschenden Druck in einer Öffnungsrichtung gegen eine Schließkraft beaufschlagt. Der im Druckraum herrschende Druck wird durch einen Pumpenkolben einer Kraftstoffhochdruckpumpe erzeugt, der durch einen Nocken in einer Hubbewegung angetrieben wird. Es ist ein durch einen piezoelektrischen Aktor betätigtes Steuerventil vorgesehen, das durch eine elektrische Steuereinrichtung angesteuert wird und durch das eine Verbindung des Druckraums mit einem Entlastungsraum gesteuert wird. Das Steuerventil weist ein Steuerventilglied auf, auf das der Aktor über einen hydraulischen Koppler wirkt, um dieses zwischen einer geöffneten Stellung und einer geschlossenen Stellung zu bewegen. Wenn das Steuerventilglied in seiner geschlossenen Stellung ist, so ist der Druckraum vom Entlastungsraum getrennt und es kann sich in diesem Hochdruck für eine Kraftstoffeinspritzung aufbauen. Der Zeitpunkt des Erreichens der Schließposition des Steuerventilglieds ist somit von großer Bedeutung für die Steuerung der Kraftstoffeinspritzung. Da das Steuerventilglied vom Aktor jedoch durch den Koppler getrennt ist, ist keine Information über diesen Zeitpunkt vorhanden. Darüberhinaus ist für eine ordnungsgemäße Funktion des Steuerventils auch eine vollständige Befüllung des Kopplers erforderlich.Such a fuel injector is through the DE 198 35 494 A1 known. This fuel injection device has a fuel injection valve, with a Injection valve member, through which at least one Injection opening is controlled. The injection valve member is of that in a pressure room of the Fuel injection valve prevailing pressure in one Opening direction acted upon against a closing force. Of the pressure prevailing in the pressure chamber is through a pump piston a high-pressure fuel pump generated by a Cam is driven in a lifting movement. It is a by a piezoelectric actuator actuated control valve provided by an electrical control device is controlled and by the one connection of the Pressure chamber is controlled with a discharge space. The Control valve has a control valve member, on which the Actuator acts via a hydraulic coupler to this between an open position and a closed position To move position. When the control valve member in his closed position, so is the pressure chamber of Relief space separated and it may be in this Build up high pressure for a fuel injection. Of the Time of reaching the closing position of the Control valve member is thus of great importance for the Control of fuel injection. Since that Control valve member from the actuator, however, through the coupler is disconnected, is no information about this date available. In addition, for a proper Function of the control valve also a complete filling required of the coupler.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Kraftstoffeinspritzeinrichtung mit den Merkmalen gemäß Anspruch 1 hat demgegenüber den Vorteil, daß die Funktion des Steuerventils überwacht werden kann. Während der Aufladephase des piezoelektrischen Aktors baut sich im hydraulischen Koppler ein Druck auf, der auch nach Beendigung des Ladevorgangs auf den Aktor zurückwirkt und in diesem bei abgetrennter Spannungsversorgung eine für die Druckverhältnisse im Koppler und demzufolge auch für die Umsetzung der Ansteuerspannung in den Hub des Steuerventilglieds charakteristische Piezospannung erzeugt. Die Spannung zwischen den elektrischen Anschlüssen am piezoelektrischen Aktor kann somit ohne das Erfordernis eines weiteren Sensors als Meßparameter für das Ventilverhalten herangezogen werden.The fuel injection device according to the invention with the Features according to claim 1 has the advantage that the function of the control valve can be monitored. During the charging phase of the piezoelectric actuator builds in the hydraulic coupler, a pressure on, even after Completion of the charging process on the actuator and back in this with disconnected power supply one for the Pressure conditions in the coupler and consequently also for the Implementation of the drive voltage in the stroke of Control valve member generates characteristic piezoelectric voltage. The voltage between the electrical connections on the piezoelectric actuator can thus without the requirement another sensor as a measurement parameter for the Valve behavior are used.

In den abhängigen Ansprüchen sind vorteilhafte Ausgestaltungen und Weiterbildungen der erfindungsgemäßen Kraftstoffeinspritzeinrichtung angegeben. Die gemessene Spannung kann gemäß Anspruch 2 dazu herangezogen werden, um den Zeitpunkt des Erreichens der Schließposition des Steuerventilglieds zu ermitteln. Der Verlauf der Spannung kann wie im Anspruch 3 angegeben auf das Auftreten eines Minimums im Kurvenverlauf hin überwacht werden. Der Druck im Koppler nimmt nach erfolgter Aufladung des Aktors im zeitlichen Verlauf zunächst ab, da der Aktor nach Beendigung des Ladevorgangs annähernd seinen vollständigen Hub erreicht hat, während das Steuerventilglied sich zu diesem Zeitpunkt noch auf seine Schließposition zubewegt und der Koppler somit entspannt wird. Sobald das Steuerventilglied die Schließposition erreicht hat und sich aufgrund eines Prellens in Richtung auf seine Öffnungsposition zurückbewegt, erfolgt jedoch eine Kompression des im Koppler befindlichen Mediums, die sich in einem Anstieg der Klemmenspannung bemerkbar macht. Das im Spannungsverlauf auftretende Minimum identifiziert somit den Zeitpunkt, zu dem das Steuerventilglied seine Schließposition erreicht hat. Alternativ kann auch wie im Anspruch 4 angegeben die zeitliche Ableitung der Klemmenspannung gebildet und auf einen Nulldurchgang hin überwacht werden. Der Nulldurchgang des zeitlich abgeleiteten Spannungssignals identifiziert dabei ebenfalls das Minimum im zeitlichen Verlauf der Klemmenspannung und somit das Erreichen der Schließposition durch das Steuerventilglied. In weiterer vorteilhafter Ausgestaltung wird gemäß Anspruch 5 aus dem ermittelten Zeitpunkt des Erreichens der Schließposition des Steuerventilglieds ein Korrekturwert für einen Steuerparameter der Steuereinrichtung abgeleitet. Dabei kann insbesondere ein Korrekturwert für die Ansteuerspannung des Aktors und/oder für den Ansteuerzeitpunkt und/oder für die Dauer des Ladevorgangs bereitgestellt werden. Gemäß Anspruch 6 kann die Spannung auch zur Erkennung des Befüllungszustands des Kopplers herangezogen werden, da der Druckverlauf im Koppler vom Befüllungszustand abhängig ist und somit ebenfalls Rückwirkungen auf die Spannung zur Folge hat. Die gemäß Anspruch 8 vorgesehene Testansteuerung ermöglicht eine Überprüfung der Funktion des Steuerventils vor einer Kraftstoffeinspritzung, wobei dabei Korrekturwerte ermittelt werden können, die bei der nachfolgenden Kraftstoffeinspritzung verwendet werden können. Der zeitliche Abstand zwischen der Ermittlung des Korrekturwerts und der Ansteuerung des Steuerventils zur Kraftstoffeinspritzung ist somit sehr gering, so daß die Kraftstoffeinspritzung mit hoher Genauigkeit erfolgen kann.In the dependent claims are advantageous Embodiments and developments of the invention Fuel injector specified. The measured Voltage can be used according to claim 2, to the time of reaching the closing position of Control valve member to determine. The course of the tension can as indicated in claim 3 to the occurrence of a Minimums are monitored in the course of the curve. The pressure in the Coupler takes after charging the actuator in the temporal course first off, as the actor after completion Charging reaches approximately its full stroke has, while the control valve member is at this time still moved to its closed position and the coupler thus relaxed. Once the control valve member the Has reached closing position and due to a Bouncing towards its open position moved back, but there is a compression of the coupler medium, resulting in an increase in the Terminal voltage noticeable. This in the voltage curve occurring minimum thus identifies the time, too the control valve member reaches its closed position Has. Alternatively, as indicated in claim 4 the time derivative of the terminal voltage formed and on a zero crossing to be monitored. The zero crossing identified the time-derived voltage signal while also the minimum in the time course of Terminal voltage and thus reaching the closed position through the control valve member. In a further advantageous Embodiment is determined according to claim 5 from the Time of reaching the closing position of the Control valve member a correction value for a Derived control parameters of the control device. It can in particular a correction value for the drive voltage of Actuator and / or for the Ansteuerzeitpunkt and / or for the Charging time can be provided. According to claim 6, the voltage can also be used to detect the Be filled state of the coupler, since the Pressure curve in the coupler depends on the filling state and thus also effects on the tension Has. The test drive provided according to claim 8 allows verification of the function of the control valve before fuel injection, with correction values can be determined in the following Fuel injection can be used. Of the time interval between the determination of the correction value and the control of the control valve to Fuel injection is thus very low, so that the Fuel injection can be done with high accuracy.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine in schematischer Darstellung und Figur 2 ein Kraftstoffeinspritzventil der Kraftstoffeinspritzeinrichtung in vergrößerter Darstellung.An embodiment of the invention is in the drawing shown and in the following description in more detail explained. FIG. 1 shows a Fuel injection device for an internal combustion engine in a schematic representation and Figure 2 a Fuel injection valve of the fuel injection device in an enlarged view.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In den Figuren 1 und 2 ist eine Kraftstoffeinspritzeinrichtung für eine Brennkraftmaschine beispielsweise eines Kraftfahrzeugs dargestellt. Die Kraftstoffeinspritzeinrichtung weist eine Kraftstoffhochdruckpumpe 10 und ein mit dieser verbundenes Kraftstoffeinspritzventil 12 auf. Beim dargestellten Ausführungsbeispiel sind die Kraftstoffhochdruckpumpe 10 und das Kraftstoffeinspritzventil 12 direkt miteinander verbunden und bilden eine sogenannte Pumpe-Düse-Einheit. Es kann alternativ jedoch auch vorgesehen sein, daß die Kraftstoffhochdruckpumpe 10 entfernt vom Kraftstoffeinspritzventil 12 angeordnet ist und über eine Leitung mit diesem verbunden ist. Es ist für jeden Zylinder der Brennkraftmaschine eine Kraftstoffeinspritzeinrichtung mit Kraftstoffhochdruckpumpe 10 und Kraftstoffeinspritzventil 12 vorgesehen.In Figures 1 and 2 is a Fuel injection device for an internal combustion engine shown for example a motor vehicle. The Fuel injection device has a High-pressure fuel pump 10 and connected to this Fuel injection valve 12 on. When presented Embodiment are the high-pressure fuel pump 10 and the fuel injection valve 12 directly with each other connected and form a so-called pump-nozzle unit. It Alternatively, however, it can also be provided that the High-pressure fuel pump 10 away from Fuel injector 12 is disposed and via a Line is connected to this. It is for every cylinder the internal combustion engine, a fuel injection device with high-pressure fuel pump 10 and Fuel injection valve 12 is provided.

Die Kraftstoffhochdruckpumpe 10 weist einen Pumpenkörper 14 auf, in dem in einer Zylinderbohrung 16 ein Pumpenkolben 18 verschiebbar geführt ist, der in der Zylinderbohrung 16 einen Pumpenarbeitsraum 20 begrenzt. Der Pumpenkolben 18 wird durch eine Nockenwelle der Brennkraftmaschine über einen Nocken 22 gegen eine Rückstellfeder 24 in einer Hubbewegung angetrieben. Zwischen dem Nocken 22 und dem Pumpenkolben 18 kann als Übertragungselement ein Kipphebel 26 angeordnet sein. Der Nocken 22 weist einen erhabenen Bereich 22a auf, über den der Pumpenkolben 18 gegen die Kraft der Rückstellfeder 24 in die Zylinderbohrung 16 bis zu einem inneren Totpunkt hineingedrückt wird, und einen flacheren Bereich 22b, über den der Pumpenkolben 18 durch die Rückstellfeder 24 aus der Zylinderbohrung 16 bis zu einem äußeren Totpunkt herausgedrückt wird. Bei der Hubbewegung des Pumpenkolbens 18 in die Zylinderbohrung 16 hinein führt dieser einen Förderhub aus, bei dem Kraftstoff im Pumpenarbeitsraum 20 verdichtet wird. Bei der Hubbewegung des Pumpenkolbens 18 aus der Zylinderbohrung 16 heraus führt dieser einen Saughub aus, bei dem Kraftstoff in den Pumpenarbeitsraum 20 angesaugt wird.The high-pressure fuel pump 10 has a pump body 14 in, in which in a cylinder bore 16, a pump piston 18th slidably guided in the cylinder bore 16th limited a pump working space 20. The pump piston 18 is transmitted through a camshaft of the internal combustion engine a cam 22 against a return spring 24 in one Driven stroke movement. Between the cam 22 and the Pump piston 18 may be a rocker arm as a transmission element 26 may be arranged. The cam 22 has a raised Region 22a, over which the pump piston 18 against the Force of the return spring 24 in the cylinder bore 16 up to an internal dead center is pushed in, and one shallower region 22b, over which the pump piston 18 through the return spring 24 from the cylinder bore 16 up to an outer dead center is pushed out. In the Lifting movement of the pump piston 18 in the cylinder bore 16th in this leads out a delivery stroke, the fuel is compressed in the pump working chamber 20. In the stroke movement the pump piston 18 leads out of the cylinder bore 16 out this one suction stroke, the fuel in the Pump working chamber 20 is sucked.

Das Kraftstoffeinspritzventil 12 weist einen Ventilkörper 30 auf, der mehrteilig ausgebildet sein kann und in dem in einer Bohrung 32 ein Einspritzventilglied 34 geführt ist. Der Ventilkörper 30 weist an seinem dem Brennraum des Zylinders der Brennkraftmaschine zugewandten Endbereich wenigstens eine, vorzugsweise mehrere Einspritzöffnungen 36 auf, die über den Umfang des Ventilkörpers 30 verteilt angeordnet sind. Das Einspritzventilglied 34 weist an seinem dem Brennraum zugewandten Endbereich eine beispielsweise etwa kegelförmige Dichtfläche 38 auf, die mit einem im Ventilkörper 30 in dessen dem Brennraum zugewandten Endbereich ausgebildeten Ventilsitz 40 zusammenwirkt, von dem oder nach dem die Einspritzöffnungen 36 abführen. Im Ventilkörper 30 ist zwischen dem Einspritzventilglied 34 und der Bohrung 32 zum Ventilsitz 40 hin ein Ringraum 42 gebildet, der in seinem dem Ventilsitz 40 abgewandten Endbereich durch eine radiale Erweiterung der Bohrung 32 in einen das Einspritzventilglied 34 umgebenden Druckraum 44 übergeht. Das Einspritzventilglied 34 weist auf Höhe des Druckraums 44 durch eine Querschnittsänderung eine Druckschulter 46 auf, über die der im Druckraum 44 herrschende Druck eine Kraft auf das Einspritzventilglied 34 vom Ventilsitz 40 weg erzeugt. Am dem Brennraum abgewandten Ende des Einspritzventilglieds 34 greift eine vorgespannte Schließfeder 48 an, durch die das Einspritzventilglied 34 zum Ventilsitz 40 hin gedrückt wird. Die Schließfeder 48 ist in einem Federraum 50 eines einen Teil des Ventilkörpers 30 bildenden Federhalters 30a angeordnet, der sich an die Bohrung 32 anschließt.The fuel injection valve 12 has a valve body 30 on, which can be designed in several parts and in the in a bore 32 an injection valve member 34 is guided. The valve body 30 has at its the combustion chamber of the Cylinder of the engine facing end portion at least one, preferably a plurality of injection openings 36 on, which is distributed over the circumference of the valve body 30 are arranged. The injection valve member 34 has at its the combustion chamber facing end an example approximately conical sealing surface 38, which with a in Valve body 30 facing in the combustion chamber End region formed valve seat 40 cooperates, from or after which discharge the injection openings 36. in the Valve body 30 is between the injection valve member 34 and the bore 32 to the valve seat 40 toward an annular space 42nd formed, in its the valve seat 40 facing away End region by a radial extension of the bore 32 in a pressure space 44 surrounding the injection valve member 34 passes. The injection valve member 34 points at the level of Pressure chamber 44 by a change in cross section a Pressure shoulder 46, on the in the pressure chamber 44th prevailing pressure a force on the injection valve member 34th generated away from the valve seat 40. Facing away from the combustion chamber End of the injection valve member 34 engages a prestressed Closing spring 48, through which the injection valve member 34th is pressed toward the valve seat 40. The closing spring 48 is in a spring chamber 50 of a part of the valve body 30th forming spring holder 30 a, which adjoins the Bore 32 connects.

Der Druckraum 44 des Kraftstoffeinspritzventils 12 ist über einen Kanal 52 mit dem Pumpenarbeitsraum 20 der Kraftstoffhochdruckpumpe 10 verbunden. Wenn der im Druckraum 44 herrschende Druck über die Druckschulter 46 auf das Einspritzventilglied 34 eine größere Kraft erzeugt als die durch die Schließfeder 48 erzeugte Kraft, so hebt das Einspritzventilglied 34 in dessen Öffnungsrichtung 35 mit seiner Dichtfläche 38 vom Ventilsitz 40 ab und gibt die Einspritzöffnungen 36 frei, durch die Kraftstoff in den Brennraum eingespritzt wird. Wenn der im Druckraum 44 herrschende Druck über die Druckschulter 46 auf das Einspritzventilglied 34 eine geringere Kraft erzeugt als die durch die Schließfeder 48 erzeugte Kraft, so bewegt sich das Einspritzventilglied 34 entgegen dessen Öffnungsrichtung 35 mit seiner Dichtfläche 38 zum Ventilsitz 40 hin und verschließt bei Anlage am Ventilsitz 40 die Einspritzöffnungen 36, so daß kein Kraftstoff in den Brennraum eingespritzt wird.The pressure chamber 44 of the fuel injection valve 12 is over a channel 52 with the pump chamber 20 of the High-pressure fuel pump 10 connected. When in the pressure room 44 prevailing pressure on the pressure shoulder 46 on the Injection valve member 34 generates a larger force than the by the closing spring 48 generated force, so that lifts Injection valve member 34 in the opening direction 35 with its sealing surface 38 from the valve seat 40 and gives the Injection openings 36 free, through the fuel in the Combustion chamber is injected. When the pressure in the room 44th prevailing pressure on the pressure shoulder 46 on the Injection valve member 34 generates a lower force than the force generated by the closing spring 48, so that moves Injection valve member 34 opposite to its opening direction 35th with its sealing surface 38 to the valve seat 40 and closes at installation on the valve seat 40 the Injection openings 36, so that no fuel in the Combustion chamber is injected.

Zur Steuerung der Kraftstoffeinspritzung ist ein elektrisch angesteuertes Steuerventil 54 vorgesehen, durch das eine Verbindung des Pumpenarbeitsraums 20 mit einem Entlastungsraum gesteuert wird. Als Entlastungsraum kann beispielsweise der Kraftstoffvorratsbehälter 11 des Kraftfahrzeugs oder ein anderer Bereich sein, in dem ein geringer Druck herrscht. Das Steuerventil 54 weist ein Steuerventilglied 56 auf, das über einen hydraulischen Koppler 57 durch einen piezoelektrischen Aktor 58 betätigt wird. Der Aktor 58 wird durch eine elektronische Steuereinrichtung 53 mit einer elektrischen Spannung versorgt. Der Aktor 58 weist eine Anzahl von hintereinandergeschalteten Piezoelementen 59 auf. Das Steuerventil 54 ist beispielsweise am Pumpenkörper 14 angeordnet. Der Aktor 58 ist einerseits mit einer Gehäusewand 60, durch die elektrische Anschlüsse 61 des Aktors 58 hindurchgeführt sind, und andererseits mit einem Stellkolben 62 kraftschlüssig verbunden. Der Stellkolben 62 schließt mit seiner vom Aktor 58 abgewandten Stirnfläche 63 den hydraulischen Koppler 57 ab. Der hydraulische Koppler 57 wirkt seinerseits auf einen in einem Verbindungskanal 64 geführten Stellkolben 65, an dessen vom Koppler 57 abgewandtem Ende das Steuerventilglied 56 angeordnet ist. Es kann vorgesehen sein, daß das Steuerventilglied 56 mit zwei Ventilsitzen zusammenwirkt, die in einem Ventilraum 66 ausgebildet sind, in dem das Steuerventilglied 56 angeordnet ist. Das Steuerventilglied 56 liegt in einer ersten Endposition, die einer spannungslosen Ruheposition des Aktors 58 entspricht, an einem ersten Ventilsitz 68 im Ventilraum 66 an. In einer zweiten Endposition, die einer maximalen Ansteuerung des Aktors 58 entspricht und eine Schließposition des Steuerventilglieds 56 ist, liegt das Steuerventilglied 56 an einem zweiten Ventilsitz 70 im Ventilraum 66 an und verschließt diesen. Es kann auch vorgesehen sein, daß das Steuerventil 54 als doppelschaltendes Ventil ausgebildet ist, wobei das Steuerventilglied 56 wenn es sich in Anlage an einem der beiden Ventilsitze 68,70 befindet jeweils geschlossen ist und nur in einer Zwischenposition zwischen den beiden Ventilsitzen 68,70 geöffnet ist. To control the fuel injection is an electric controlled control valve 54 is provided, through which a Connection of the pump working chamber 20 with a Relief space is controlled. As a relief space can For example, the fuel tank 11 of the Be motor vehicle or another area in which a low pressure prevails. The control valve 54 has Control valve member 56, which via a hydraulic Coupler 57 is actuated by a piezoelectric actuator 58 becomes. The actuator 58 is controlled by an electronic Control device 53 with an electrical voltage provided. The actuator 58 has a number of connected in series piezo elements 59 on. The Control valve 54 is, for example, on the pump body 14 arranged. The actuator 58 is on the one hand with a Housing wall 60, through the electrical connections 61 of the Actuator 58 are passed, and on the other hand with a Control piston 62 positively connected. The adjusting piston 62 closes with its end face 63 facing away from the actuator 58 the hydraulic coupler 57 from. The hydraulic coupler 57 in turn acts on one in a connection channel 64 guided adjusting piston 65, at the end of the coupler 57th opposite end of the control valve member 56 is arranged. It can be provided that the control valve member 56 with two Valve seats cooperates, which in a valve chamber 66 are formed, in which the control valve member 56 is arranged is. The control valve member 56 is located in a first End position, which is a tensionless rest position of Actuator 58 corresponds to a first valve seat 68 in Valve space 66 on. In a second end position, the one maximum activation of the actuator 58 corresponds and a Closed position of the control valve member 56 is located Control valve member 56 at a second valve seat 70 in Valve chamber 66 and closes this. It can also be provided that the control valve 54 as double-switching valve is formed, wherein the Control valve member 56 when it is in contact with one of both valve seats 68,70 is respectively closed and only in an intermediate position between the two Valve seats 68,70 is open.

In den Ventilraum 66 mündet zwischen den beiden Ventilsitzen 68,70 eine Verbindung 71 zu dem Entlastungsraum. Über den zweiten Ventilsitz 70 weist der Ventilraum 66 eine Verbindung mit dem Pumpenarbeitsraum 20 auf. Wenn sich das Steuerventilglied 56 in seiner ersten Endposition in Anlage am ersten Ventilsitz 68 befindet, so ist die Verbindung des Ventilraums 66 zum Pumpenarbeitsraum 20 über den zweiten Ventilsitz 70 geöffnet, so daß der Pumpenarbeitsraum 20 mit dem Entlastungsraum verbunden ist und sich in diesem kein Hochdruck aufbauen kann. In der Verbindung 71 des Ventilraums 66 mit dem Entlastungsraum kann eine Drosselstelle 67 vorgesehen sein. Wenn sich das Steuerventilglied 56 in seiner zweiten Endposition und damit seiner Schließposition in Anlage am zweiten Ventilsitz 70 befindet, so ist die Verbindung des Ventilraums 66 zum Pumpenarbeitsraum 20 über den zweiten Ventilsitz 70 geschlossen, so daß der Pumpenarbeitsraum 20 vom Entlastungsraum getrennt ist und sich in diesem Hochdruck aufbauen kann, entsprechend dem Förderhub des Pumpenkolbens 18. Der Zeitpunkt des Erreichens der Schließposition des Steuerventilglieds 56 bestimmt somit den Beginn der Kraftstoffeinspritzung und die Dauer der Anordnung des Steuerventilglieds 56 in seiner Schließposition bestimmt die Kraftstoffmenge, die eingespritzt wird.In the valve chamber 66 opens between the two valve seats 68,70 a connection 71 to the discharge room. On the second valve seat 70, the valve chamber 66 a Connection with the pump working chamber 20 on. If that is Control valve member 56 in its first end position in Appendix is located on the first valve seat 68, so is the compound of Valve space 66 to the pump working chamber 20 via the second Valve seat 70 is opened, so that the pump working chamber 20 with connected to the discharge room and is not in this Can build up high pressure. In the connection 71 of the Valve chamber 66 with the discharge space may be a Throttle 67 may be provided. If that is Control valve member 56 in its second end position and thus its closed position in contact with the second valve seat 70th is the connection of the valve space 66 to Pump working chamber 20 via the second valve seat 70th closed, so that the pump working chamber 20 from Relief space is separated and in this high pressure can build, according to the delivery stroke of the pump piston 18. The date of reaching the closing position of Control valve member 56 thus determines the beginning of Fuel injection and the duration of the arrangement of Control valve member 56 in its closed position determines the Fuel quantity injected.

Der Aktor 58 des Steuerventils 54 wird durch die Steuereinrichtung 53 abhängig von Betriebsparametern der Brennkraftmaschine, wie beispielsweise Drehzahl, Last, Temperatur und weiteren, angesteuert. Für die Steuerung der Kraftstoffeinspritzung mit hoher Genauigkeit ist eine Rückmeldung über den Beginn der Kraftstoffeinspritzung erforderlich, der zumindest annähernd gleichzeitig mit dem Zeitpunkt des Erreichens der Schließposition des Steuerventilglieds 56 ist. Zur Erkennung, ob das Steuerventilglied 56 seine Schließposition erreicht hat, wird nach erfolgtem Ladevorgang, das ist nach erfolgter Ansteuerung des Aktors 58 zum Schließen des Steuerventils 54, für eine vorgebbare Zeitdauer eines Meßfensters an die Anschlüsse 61 des Aktors 58 eine Spannungsmeßeinrichtung 72 angeschlossen, die Bestandteil der Steuereinrichtung 53 sein kann. An die Spannungsmeßeinrichtung 72 kann eine Diagnoseinrichtung 74 angeschlossen sein. Die Meßdaten können direkt, beispielsweise als analoges Spannungssignal, an die Diagnoseeinrichtung 74 übermittelt werden. Somit erfolgt eine Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 als Funktion der Zeit. Es kann jedoch alternativ zunächst auch die Bildung der zeitlichen Ableitung der Spannung zwischen den Anschlüssen 61 vorgesehen werden. Dazu werden die Spannungssignale einem der Spannungsmeßeinrichtung 72 zugeordneten Differenzierglied 76 zugeführt. Die dort gebildeten differenzierten Signale werden anschließend an die Diagnoseeinrichtung 74 übermittelt. In beiden Alternativen wird aus dem zeitlichen Verlauf der Spannung zwischen den Anschlüssen 61 des Aktors 58 in der Diagnoseeinrichtung 74 auf das Erreichen der Schließposition des Steuerventilglieds 56 geschlossen.The actuator 58 of the control valve 54 is replaced by the Control device 53 depending on operating parameters of Internal combustion engine, such as speed, load, Temperature and others, controlled. For the control of Fuel injection with high accuracy is one Feedback on the start of fuel injection required, at least approximately simultaneously with the Time of reaching the closing position of the Control valve member 56 is. To detect if that Control valve member 56 has reached its closed position, will after loading, which is after successful Actuation of the actuator 58 to close the control valve 54, for a predetermined period of a measuring window to the Connections 61 of the actuator 58, a voltage measuring device 72nd connected, which are part of the control device 53 can. To the voltage measuring device 72 may have a Diagnostic device 74 may be connected. The measured data can directly, for example as an analogue voltage signal, be transmitted to the diagnostic device 74. Consequently there is a monitoring of the voltage between the Connections 61 of the actuator 58 as a function of time. It can however, alternatively, the formation of the temporal Derivation of the voltage between the terminals 61 be provided. For this the voltage signals become one associated with the voltage measuring device 72 Differentiator 76 is supplied. The educated there differentiated signals are subsequently sent to the Diagnostic device 74 transmitted. In both alternatives is derived from the time course of the tension between the Terminals 61 of the actuator 58 in the diagnostic device 74th upon reaching the closed position of the control valve member 56 closed.

Zur Erkennung der Schließposition des Steuerventilglieds 56 wird der zeitliche Verlauf der Spannung zwischen den Anschlüssen 61 des Aktors 58 auf das Auftreten eines Minimums im Kurvenverlauf hin überwacht. Bei der Auswertung der zeitlichen Ableitung der Spannung mittels des Differenzierglieds 76 wird dementsprechend das Auftreten eines Nulldurchgangs überprüft. Wie festgestellt wurde baut sich nach Beendigung der Ladephase des Aktors 58 der Druck im hydraulischen Koppler 57 zunächst ab, da der Aktor 58 nach Beendigung des Ladevorgangs annähernd seinen vollständigen Hub erreicht hat, während das Steuerventilglied 56 sich zu diesem Zeitpunkt noch auf seine Schließposition zubewegt und der Koppler 57 somit entspannt wird. Dieser Druckabfall ist über die Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 in der Form einer als Funktion der Zeit eintretenden Reduzierung der Spannung nachweisbar.For detecting the closing position of the control valve member 56th is the time course of the tension between the Connections 61 of the actuator 58 to the occurrence of a Minimums monitored in the course of the curve. In the evaluation the time derivative of the voltage by means of Differentiating member 76 is accordingly the occurrence a zero crossing checked. As stated was building After completion of the loading phase of the actuator 58, the pressure in the hydraulic coupler 57 first off, since the actuator 58th after completion of the charging approximately its has reached full stroke while the Control valve member 56 at this time still on his Closing moved closed position and the coupler 57 thus relaxed becomes. This pressure drop is about monitoring the Voltage between the terminals 61 of the actuator 58 in the Form of a reduction occurring as a function of time the voltage detectable.

Sobald das Steuerventilglied 56 seine Schließposition erreicht hat und sich aufgrund eines Prellens in Richtung auf seine erste Endposition zurückbewegt, erfolgt jedoch eine Kompression des im Koppler befindlichen Mediums, die sich analog in einem Anstieg der Spannung zwischen den Anschlüssen 61 des Aktors 58 bemerkbar macht. Das im Spannungsverlauf auftretende Minimum identifiziert somit den Zeitpunkt, zu dem das Steuerventilglied 56 seine Schließposition erreicht hat. Auf der Grundlage der Erkennung des Zeitpunkts des Schließens des Steuerventils 54 können Korrekturwerte für Steuerparameter der Steuereinrichtung 53 gewonnen werden, die für eine nachfolgende Kraftstoffeinspritzung verwendet werden können und durch die die Genauigkeit der Kraftstoffeinspritzung hinsichtlich Zeitpunkt der Kraftstoffeinspritzung und Kraftstoffeinspritzmenge verbessert werden kann.Once the control valve member 56 its closed position has reached and due to a bounce in the direction however, it moves back to its first end position a compression of the medium in the coupler, the analogously in an increase in the voltage between the Make connections 61 of the actuator 58 noticeable. The im Voltage curve occurring minimum thus identifies the Time at which the control valve member 56 his Has reached closing position. On the basis of Detecting the timing of the closing of the control valve 54 can provide correction values for control parameters Control device 53 are obtained, which for a subsequent fuel injection can be used and by the accuracy of the fuel injection in terms of timing of fuel injection and Fuel injection quantity can be improved.

Es kann vorgesehen sein, daß die vorstehend erläuterte Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 jeweils während einer erfolgenden Kraftstoffeinspritzung durchgeführt wird. Die dabei gewonnenen Korrekturwerte können dann für die Steuerung der nachfolgenden Kraftstoffeinspritzung verwendet werden.It can be provided that the above-explained Monitoring the voltage between the terminals 61 of the Actuator 58 each during a successful Fuel injection is performed. The case obtained correction values can then be used for the control of subsequent fuel injection can be used.

Alternativ kann auch vorgesehen sein, daß die vorstehend erläuterte Überwachung der Spannung während einer Testansteuerung des Steuerventils 54 durch die Steuereinrichtung 53 in einem Zeitintervall erfolgt, während dem keine Kraftstoffeinspritzung erfolgt. Dies ist insbesondere während einer Hubphase des Pumpenkolbens 18 der Fall, bei der dieser sich aus der Zylinderbohrung 16 zu seinem äußeren Totpunkt hin bewegt. Der Nocken 18 befindet sich dann in seinem flacheren Bereich 22b in Anlage am Kipphebel 26. Während dieser Hubphase des Pumpenkolbens 18 wird durch diesen im Pumpenarbeitsraum 20 und damit im Druckraum 44 des Kraftstoffeinspritzventils 12 kein für eine Kraftstoffeinspritzung ausreichender Druck erzeugt, so daß auch beim Schließen des Steuerventils 54 keine Kraftstoffeinspritzung erfolgt. Die Testansteuerung des Steuerventils 54 erfolgt vorzugsweise während eines Zeitintervalls, während dem auch die Befüllung des Pumpenarbeitsraums 20 beim Saughub des Pumpenkolbens 18 mit Kraftstoff sowie die Absteuerung von Kraftstoff aus dem Pumpenarbeitsraum 20 zur Beendigung der Kraftstoffeinspritzung bei geöffnetem Steuerventil 54 nicht oder nur geringstmöglich beeinflußt wird.Alternatively, it can also be provided that the above explained monitoring the voltage during a Test activation of the control valve 54 by the Control means 53 takes place in a time interval while no fuel injection takes place. This is in particular during a stroke phase of the pump piston 18 of the Case in which this from the cylinder bore 16 to moved to its outer dead center. The cam 18 is located then in his shallower area 22b in Appendix on Rocker 26. During this stroke phase of the pump piston 18th is characterized by this in the pump chamber 20 and thus in the Pressure chamber 44 of the fuel injection valve 12 none for a Fuel injection generates sufficient pressure, so that even when closing the control valve 54 no Fuel injection takes place. The test control of the Control valve 54 is preferably carried out during a Time interval, during which also the filling of the Pump workspace 20 during the suction stroke of the pump piston 18 with Fuel as well as the removal of fuel from the Pump work space 20 to terminate the Fuel injection with open control valve 54 is not or is affected as little as possible.

Bei der Testansteuerung des Steuerventils 54 können Korrekturparameter gewonnen werden, die bereits bei der Steuerung der nachfolgenden Kraftstoffeinspritzung verwendet werden können. Der zeitliche Versatz zwischen der Gewinnung der Korrekturwerte und der Steuerung der Kraftstoffeinspritzung ist bei der Testansteuerung des Steuerventils 54 nur etwa halb so groß wie bei der Gewinnung der Korrekturwerte bei der tatsächlich erfolgenen Kraftstoffeinspritzung. Die Genauigkeit der Steuerung der Kraftstoffeinspritzung kann somit nochmals wesentlich erhöht werden. Bei der Testansteuerung des Steuerventils 54 werden direkt vor der Ansteuerung zur Kraftstoffeinspritzung die Korrekturwerte ermittelt.In the test drive of the control valve 54 can Correction parameters are already obtained at the Control of the subsequent fuel injection used can be. The time lag between the extraction the correction values and the control of the Fuel injection is in the test drive of the Control valve 54 only about half as large as in the extraction the correction values in the actually done Fuel injection. The accuracy of the control of Fuel injection can thus be significantly increased again become. In the test drive of the control valve 54 are just before the fuel injection control Correction values determined.

Über Leckspalte wird bei der Bewegung des Stellkolbens 62 ein Teil des im hydraulischen Koppler 57 befindlichen Mediums, das vorzugsweise Kraftstoff ist, herausgedrückt. Für einen bestimmungsgemäßen Zusammenhang zwischen Ansteuerspannung des Aktors 58 und eingespritzter Kraftstoffmenge ist jedoch eine ordnungsgemäße Befüllung des Kopplers 57 erforderlich. Daher ist zwischen zwei Einspritzungen eine Wiederbefüllung des Kopplers 57 über einen nicht dargestellten Kanal vorgesehen. Für eine Überprüfung, ob der Koppler 57 auch tatsächlich ordnungsgemäß wiederbefüllt wurde, kann wiederum die Spannung zwischen den Anschlüssen 61 des Aktors 58 herangezogen werden. Nach erfolgtem Ladevorgang des Aktors 58 wird wiederum durch die Spannunsmeßeinrichtung 72 der zeitliche Verlauf der Spannung zwischen den Anschlüssen 61 des Aktors 58 überwacht. Es wurde festgestellt, daß nach Beendigung des Ladevorgangs des Aktors 58 der Druck im hydraulischen Koppler 57 infolge abströmenden Mediums sich wieder abbaut. Dieser Druckabfall ist über die Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 in Form einer als Funktion der Zeit eintretenden Reduzierung der Spannung nachweisbar. Das Ausmaß dieses zeitlichen Abfalls der Spannung ist dabei auch abhängig vom sogenannten Übersetzungsverhältnis im Koppler 57, also dem Verhältnis der Querschnittsfläche des Stellkolbens 62 zur Querschnittsfläche des Stellkolbens 65 und außerdem vom Verhältnis aus dem erzeugbaren Hub des Steuerventilglieds 56 zu der auf den Koppler 57 einwirkenden Längenänderung des Aktors 58. Die Reduzierung der Spannung hängt zudem in besonders ausgeprägtem Maße vom Befüllungsgrad im Koppler 57 ab. Bei voll befülltem Koppler 57 ist ein vergleichsweise ausgeprägter Spannungseinbruch von beispielsweise etwa 50 V nachweisbar. Dagegen ist dieser Effekt bei nur teilweise befülltem Koppler 57 deutlich geringer, wobei der Spannungseinbruch beispielsweise nur etwa 15 V beträgt.About leakage gaps is 62 in the movement of the actuating piston a part of the located in the hydraulic coupler 57 Medium, which is preferably fuel, pushed out. For a proper relationship between Drive voltage of the actuator 58 and injected Fuel quantity, however, is a proper filling of the Kopplers 57 required. Therefore, between two Injections a refill of the coupler 57 via provided a channel, not shown. For one Check if the coupler 57 actually can be refilled properly, in turn, the Voltage between the terminals 61 of the actuator 58th be used. After the charging process of the actuator 58 is again by the Spannunsmeßeinrichtung 72 of time course of the voltage between the terminals 61 of the actuator 58 monitored. It was found that after Termination of the charging process of the actuator 58, the pressure in hydraulic coupler 57 as a result of effluent itself degrades again. This pressure drop is above the monitoring the voltage between the terminals 61 of the actuator 58 in Form of a reduction occurring as a function of time the voltage detectable. The extent of this temporal Waste of the voltage is also dependent on the so-called Transmission ratio in the coupler 57, so the ratio the cross-sectional area of the actuating piston 62 to Cross-sectional area of the actuating piston 65 and also from Ratio of the producible stroke of the control valve member 56th to the force acting on the coupler 57 change in length of the Aktors 58. The reduction of the voltage also depends on particularly pronounced degree of filling in the coupler 57 from. When fully filled coupler 57 is a comparatively pronounced voltage dip of, for example, about 50V detectable. By contrast, this effect is only partial filled coupler 57 significantly lower, the For example, voltage drop is only about 15V.

Aus der Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 wird somit in der Diagnoseeinrichtung 74 eine Diagnoseaussage gebildet, indem nach erfolgter Ladephase des Aktors 58 die Spannung gemessen wird. Nach einer vorgebbaren Wartezeit von beispielsweise etwa 0,25 ms wird die Spannung erneut gemessen. Sodann wird die Differenz beider Meßwerte gebildet und mit einem Grenzwert verglichen. Es kann dabei ein fester Grenzwert vorgegeben sein, der beispielsweise etwa 30 V betragen kann. Alternativ kann jedoch auch ein betriebspunktabhängiger Grenzwert aus einem durch vorherige Eichung gewonnenen, in einem Datenspeichermodul 78 hinterlegten Kennfeld zugrundegelegt werden. Die Wartezeit ist dabei derart wählbar, daß die Messung der Spannung unmittelbar vor einem darauffolgenden Steuereingriff, nämlich vor einer weiteren Anhebung der Spannung, erfolgt.From the monitoring of the voltage between the terminals 61 of the actuator 58 is thus in the diagnostic device 74 a Diagnosis statement formed by after the loading phase of Actuator 58, the voltage is measured. After a predefinable Waiting time of about 0.25 ms, for example, becomes the voltage measured again. Then the difference of both measured values formed and compared to a limit. It can do that a fixed limit may be specified, for example can be about 30V. Alternatively, however, a Operating point dependent limit from a by previous Obtained in a data storage module 78 stored map are based. The waiting time is so selectable that the measurement of the voltage immediately before a subsequent tax intervention, namely before a further increase in the voltage takes place.

Ist die ermittelte Differenz der Spannung größer als der Grenzwert, so wird als Diagnose auf eine vollständige und ordnungsgemäße Wiederbefüllung des Kopplers 57 geschlossen und es wird keine weitere Maßnahme eingeleitet. Ist die ermittelte Differenz der Spannung jedoch kleiner als der Grenzwert, so wird als Diagnose auf eine unvollständige und mangelhafte Wiederbefüllung des Kopplers 57 geschlossen. In diesem Fall wird ein weiterer Vergleich der Differenz der Spannungen mit einem zweiten Grenzwert oder Minimalwert vorgenommen. Durch diesen Vergleich wird noch eine Unterscheidung nach Auswirkungen des Fehlers vorgenommen. Unterschreitet die Differenz der Spannungen auch den zweiten, noch geringeren Grenzwert oder Minimalwert, so wird ein wesentlicher Fehler diagnostiziert, der beispielsweise eine sofortige Stillegung der Brennkraftmaschine zur Folge hat. Liegt die Differenz der Spannungen hingegen zwar unterhalb des ersten aber oberhalb des zweiten Grenzwertes, so wird ein leichter Fehler diagnostiziert, der zwar einen weiteren Betrieb der Brennkraftmaschine erlaubt, der jedoch für spätere Diagnosezwecke im Datenspeichermodul 78 hinterlegt wird.Is the determined difference of the voltage greater than that Limit value, so as a diagnosis to a complete and proper refilling of the coupler 57 closed and no further action will be taken. Is the However, the difference of the voltage determined is smaller than that Limit value, so as a diagnosis is incomplete and Inadequate refilling of the coupler 57 is closed. In In this case, another comparison of the difference of Voltages with a second limit or minimum value performed. This comparison will add another Distinction made according to the effects of the error. If the difference of the voltages falls below the second, even lower limit or minimum value, so will diagnosed a major mistake, for example an immediate shutdown of the internal combustion engine result Has. On the other hand, the difference of the voltages is indeed below the first but above the second threshold, so a slight mistake is diagnosed, although one further operation of the internal combustion engine allowed, however for later diagnostic purposes in the data storage module 78 is deposited.

Bei Feststellung eines leichten Fehlers in der Diagnoseeinrichtung 74 wird zudem ein Sollwert für die Ansteuerspannung des Aktors 58 vorgegeben, wobei der Sollwert derart gewählt wird, daß sich trotz der festgestellten nicht vollständigen Befüllung des Kopplers 57 nach einer Ansteuerung der vorgesehene Hub des Steuerventilglieds 56 ergibt. Die vorstehend erläuterte Überwachung der Spannung zwischen den Anschlüssen 61 des Aktors 58 wird vorzugsweise während einer Testansteuerung des Steuerventils 54 in einer Phase durchgeführt, während derer keine Kraftstoffeinspritzung erfolgt.Upon detection of a slight error in the Diagnostic device 74 is also a setpoint for the Drive voltage of the actuator 58 given, the Setpoint is chosen such that, despite the detected incomplete filling of the coupler 57 after driving the intended stroke of the Control valve member 56 results. The above explained Monitoring the voltage between the terminals 61 of the Actuator 58 is preferably during a test drive of the control valve 54 in a phase while which no fuel injection takes place.

Claims (10)

  1. Fuel injection device, having a control device, for an internal combustion engine having a fuel injection valve (12) which has at least one injection valve element (34) by means of which at least one injection opening (36) is controlled, pressure which prevails in a pressure space (44) of the fuel injection valve (12) being applied to the injection valve element (34) in an opening direction (35) counter to a closing force, the pressure prevailing in the pressure space (44) being generated by a pump piston (18) of a fuel high pressure pump (10), said pump piston (18) being driven by a cam (22) in a reciprocating movement and the control valve (54) which is activated by a piezo-electric actuator (58), which can be actuated by the electric control device (53), being provided, and it being possible to control a connection (71) between the pressure space (44) and a relief space at least indirectly by means of the control valve, the pressure space (44) being separated from the relief space when the control valve (54) is closed and the control valve (54) having a control valve element (56) which is coupled to the actuator (58) via a hydraulic coupler (57), characterized in that the control device comprises means with which the actuator (58) is connected to an assigned voltage measuring device (72) after a charging phase, and in that the voltage between the electrical terminals (61) of the actuator (58) is monitored in order to detect the function of the control valve (54).
  2. Fuel injection device according to Claim 1, characterized in that the voltage between the electrical terminals (61) of the actuator (58) is used to detect when a closing position of the control valve element (56) is reached.
  3. Fuel injection device according to Claim 2, characterized in that the time profile of the voltage is monitored for the occurrence of a minimum in the curve profile.
  4. Fuel injection device according to Claim 2, characterized in that the derivation of the voltage over time is formed and is monitored for a zero crossover.
  5. Fuel injection device according to one of Claims 2 to 4, characterized in that a correction value for a control parameter of the control device (53) is formed from the time determined when the closing position of the control valve element (56) is reached, said correction value being taken into account during a subsequent fuel injection.
  6. Fuel injection device according to one of the preceding claims, characterized in that the voltage between the electrical terminals (61) of the actuator (58) is used to detect the filling state of the coupler (57).
  7. Fuel injection device according to Claim 6, characterized in that a difference between a voltage measured directly after the termination of the charging phase of the actuator (58) and a voltage measured after a predefinable waiting time has expired is compared with a limiting value.
  8. Fuel injection device according to one of the preceding claims, characterized in that the voltage between the electrical terminals (61) of the actuator (58) is monitored in order to detect the function of the control valve (54) during a test actuation of the control valve (54), during which actuation fuel is not injected.
  9. Fuel injection device according to Claim 8, characterized in that the test actuation of the control valve (54) takes place in a reciprocating phase of the pump piston (18) during which the latter does not generate sufficient pressure in the pressure space (44) of the fuel injection valve (12) to open the injection valve element (34).
  10. Fuel injection device according to one of the preceding claims, characterized in that it has a separate fuel high pressure pump (10) for each fuel injection valve (12), said fuel high pressure pump (10) having a pump piston (18) which is driven by a cam (22).
EP02764515A 2001-09-22 2002-07-13 Fuel injection device for internal combustion engine Expired - Lifetime EP1430208B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10146747 2001-09-22
DE10146747A DE10146747A1 (en) 2001-09-22 2001-09-22 Fuel injection device for an internal combustion engine
PCT/DE2002/002574 WO2003027468A1 (en) 2001-09-22 2002-07-13 Fuel injection device for internal combustion engine

Publications (2)

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EP1430208A1 EP1430208A1 (en) 2004-06-23
EP1430208B1 true EP1430208B1 (en) 2005-01-26

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EP02764515A Expired - Lifetime EP1430208B1 (en) 2001-09-22 2002-07-13 Fuel injection device for internal combustion engine

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US (1) US6807950B2 (en)
EP (1) EP1430208B1 (en)
JP (1) JP4116552B2 (en)
AT (1) ATE288031T1 (en)
DE (2) DE10146747A1 (en)
HU (1) HUP0301402A2 (en)
PL (1) PL360659A1 (en)
WO (1) WO2003027468A1 (en)

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EP1430208A1 (en) 2004-06-23
JP4116552B2 (en) 2008-07-09
US6807950B2 (en) 2004-10-26
DE50202146D1 (en) 2005-03-03
ATE288031T1 (en) 2005-02-15
DE10146747A1 (en) 2003-04-10
HUP0301402A2 (en) 2007-11-28
PL360659A1 (en) 2004-09-20
US20040065301A1 (en) 2004-04-08
WO2003027468A1 (en) 2003-04-03
JP2005504211A (en) 2005-02-10

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