EP1472455B1 - Method and device for controlling a control valve of a pump-nozzle unit - Google Patents

Method and device for controlling a control valve of a pump-nozzle unit Download PDF

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Publication number
EP1472455B1
EP1472455B1 EP03708015A EP03708015A EP1472455B1 EP 1472455 B1 EP1472455 B1 EP 1472455B1 EP 03708015 A EP03708015 A EP 03708015A EP 03708015 A EP03708015 A EP 03708015A EP 1472455 B1 EP1472455 B1 EP 1472455B1
Authority
EP
European Patent Office
Prior art keywords
control valve
pressure
closed
valve
fuel
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
EP03708015A
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German (de)
French (fr)
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EP1472455A1 (en
Inventor
Maximilian Kronberger
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.)
Continental Mechatronic Germany GmbH and Co KG
Original Assignee
Volkswagen Mechatronic GmbH and Co KG
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Publication of EP1472455A1 publication Critical patent/EP1472455A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • 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
    • F02M59/44—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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure

Definitions

  • the invention relates to a method and a device for controlling a control valve of a pump-nozzle unit, wherein the control valve has at least one movable element which is movable to close the control valve in a first end position and to fully open the control valve in a second end position.
  • Pump-nozzle units are used for supplying fuel into a combustion chamber of an internal combustion engine.
  • This may be, for example, a pump-nozzle unit with a controllable and / or controllable fuel pump, a fuel injector, which has a between a closed position and an open position reciprocating nozzle needle, a first pressure chamber of the fuel pump with below a first pressurized fuel is fillable, a second pressure chamber, wherein in the second pressure chamber at a second pressure stationary fuel exerts a closing force on the nozzle needle, and a third pressure chamber communicating with the first pressure chamber, wherein in the third pressure chamber under a third Pressurized fuel exerts an opening force on the nozzle needle.
  • Pump-nozzle units are used in particular in connection with pressure-controlled injection systems.
  • An essential feature of a pressure-controlled injection system is that the fuel injector opens as soon as an opening force, which is influenced at least by currently prevailing pressures, is exerted on the nozzle needle.
  • Such pressure-controlled injection systems are used for fuel metering, fuel preparation, the formation of the course of injection and a seal of the fuel supply against the combustion chamber of the internal combustion engine.
  • pressure controlled Injection systems can be the temporal course of the flow rate during the injection control in an advantageous manner. This can have a positive influence on the engine's performance, fuel consumption and pollutant emission.
  • the fuel pump and the fuel injector are typically formed as an integral component.
  • at least one pump-nozzle unit is provided, which is usually installed in the cylinder head.
  • the fuel pump typically comprises a fuel pump piston which can be moved back and forth in a fuel pump cylinder and which is driven either directly by a tappet or indirectly via rocker arms by a camshaft of the internal combustion engine.
  • the usually the first pressure chamber forming portion of the fuel pump cylinder is connected via a control valve with a fuel low pressure region, wherein sucked with the control valve open fuel from the low-pressure fuel area in the first pressure chamber and pushed back at further open control valve from the first pressure chamber in the low-pressure fuel area becomes.
  • the fuel pump piston compresses the fuel in the first pressure chamber and thus builds up the pressure.
  • the control valve in the form of a solenoid valve.
  • solenoid valves usually have a relatively long response time, which is particularly due to the fact that the magnet armature of a solenoid valve can not be accelerated arbitrarily fast due to the mass inertia forces dependent on its mass.
  • the structure of the magnetic field for generating the tightening force requires time.
  • a pump-nozzle unit equipped with a solenoid valve is known, for example, from EP 0 277 939 B1.
  • pump-nozzle units with a control valve which is operated piezoelectrically.
  • a pump-nozzle unit is known for example from DE 198 35 494 A1 of DE 100 35 814 A1.
  • Optimum combustion processes for example in direct injection diesel engines, require this flexible design of the multiple injection injection pattern, for example, pilot, main, and post injection.
  • a very fast closing and opening of the control valve over its entire stroke is necessary for this purpose, with correspondingly high pressure gradients.
  • high pressure gradients are often undesirable because they trigger pressure fluctuations.
  • the decay time of these pressure fluctuations has an influence on the maximum number and accuracy of the drive processes within a sequence of multiple injections.
  • the low pressure level of the fuel supply of pump-nozzle systems promotes low fuel consumption, but often increases the cavitation tendency. Higher pressure gradients increase this inclination, which increases the engine noise.
  • Control valves in the form of solenoid valves usually have stable stroke positions only in the fully open and in the closed state. These stable layers are usually determined by mechanical stops. The stroke over time depends on the resulting force curve from magnetic, hydraulic and friction forces. With control valves in the form of solenoid valves, there are approaches, the Ab Kunststoffgradienten to reduce by a stepped stroke course. However, such step-shaped strokes show, in principle, strong stochastic and specimen-specific scattering in solenoid valves. Furthermore, the respective duration of Operahubphasen is limited.
  • Control valves in the form of piezo valves allow a relatively stable control of partial strokes, virtually without disturbing time limit.
  • the achievable positioning precision is considered critical, since for example with a total stroke of 200 ⁇ m, a positional accuracy of the valve member strokes of, for example, +/- 5 ⁇ m is considered necessary in order to avoid undesired side effects during the injection process.
  • the invention has the object of developing the generic methods and devices such that Steuerventilteilhübe can be achieved with improved positional accuracy, especially in order to avoid high pressure gradients at lower engine speeds can.
  • the inventive method for controlling a control valve of a pump-nozzle unit is based on the generic state of the art in that for adjusting at least one intermediate position of the at least one movable element at least temporarily a scheme, in particular an adaptive control is used.
  • This solution valve lift strokes are achieved with a high position accuracy, resulting in, for example, to improve the noise and exhaust emissions and the torque curve of the engine.
  • a method provides that at least one intermediate position is set for a predetermined period of time when the at least one movable element for opening the control valve is moved from the second end position to the first end position.
  • control of the control valve by electrical control of an actuator for the at least one movable element takes place.
  • the type of actuator determines the type of control valve, such as solenoid valve or piezo valve.
  • the manipulated variable of the control is an electrical variable with which the actuator is electrically actuated.
  • the electrical variable may be the drive voltage of the piezoelectric element, for example, in the case of a piezo valve.
  • the controlled variable of the control is a resultant force and / or force curve as a result of a pressure within at least one area of the control valve, in particular a pressure and / or pressure curve that occurs during opening of the control valve of the at least one area.
  • the at least one area for example the space filled with fuel before the piezoelectric element and / or a Ab Georgraum, wherein a pressure increase occurring there causes an increase of the pressure force on the piezoceramic, for example via a piston or the like ,
  • the piezoelectric element is part of the actuator or forms this.
  • the pressure and / or pressure curve detected during a current opening operation of the control valve enters the control within the at least one area of the control valve for the current opening operation and / or for at least one subsequent opening operation, in particular in the form of offset values of at least one electrical variable with which the actuator is controlled.
  • an increase in the pressure force on a piezoceramic can be evaluated by an electrical variable measured at the piezoelectric element.
  • the desired partial lifting positions can then be achieved by superimposing corresponding offset values on the value of the piezo control variable present at the time of evaluation.
  • the desired partial lifting positions can assume different values within a multiple control.
  • the inventive device for controlling a control valve of a pump-nozzle unit is based on the generic state of the art in that it performs to adjust at least one intermediate position of the at least one movable element at least temporarily a scheme, in particular an adaptive control.
  • the device adjusts the at least one intermediate position for a predetermined period of time when the at least one movable element for opening the control valve is moved from the second end position to the first end position.
  • embodiments of the device according to the invention are considered advantageous in which it is provided that it performs the control of the control valve by electrical control of an actuator for the at least one movable element.
  • the device it is preferred in this case that it uses an electrical variable as the manipulated variable with which it electrically actuates the actuator in order to carry out the control.
  • the device according to the invention uses a resulting force and / or force curve as a result of a pressure within at least one area of the control valve, in particular a setting when opening the control valve Pressure and / or pressure curve within the at least one area.
  • preferred developments of the device according to the invention provide that the pressure and / or the pressure curve within the at least one region of the control valve is detected via a piezoelectric element.
  • the piezoelectric element is part of the actuator or forms this.
  • the device includes the pressure and / or pressure curve detected during a current opening operation of the control valve within the at least one area of the control valve for the current opening operation and / or for at least one subsequent opening operation, in particular in shape of offset values of at least one electrical quantity with which it drives the actuator.
  • the invention is based on the finding that the noise and exhaust emissions and the torque curve of an internal combustion engine can be improved if a control is used to increase the positional accuracy of partial strokes of the control valve of a pump-nozzle unit.
  • FIG. 1 shows schematically a pump-nozzle unit.
  • the illustrated pump-nozzle unit for supplying fuel 10 into a combustion chamber 12 of an internal combustion engine has a fuel pump 14-22.
  • a fuel pump piston 14 in a fuel pump cylinder 16 is movable back and forth.
  • the fuel pump piston 14 is driven directly or indirectly via a camshaft, not shown, of the internal combustion engine.
  • the compression space of the fuel pump cylinder 16 forms a first pressure chamber 28.
  • the first pressure chamber 28 is connected via a fuel line 20 to the control valve 22 to be triggered according to the invention.
  • the control valve 22 serves either to close the fuel line 20 or to connect it to a low-pressure fuel area 18, from which fuel 10 can be sucked.
  • the illustrated unit injector also includes a total of 24 designated A fuel injector having a reciprocating needle 46 movable between a closed position and an open position.
  • a pressure pin 26 can, in relation to the representation of FIG. 1, in particular exert a downward force on the nozzle needle 46.
  • a shim 40 is provided, which is guided in a second pressure chamber 30, wherein in the second pressure chamber 30 at a second pressure p 30 standing fuel 10 via the pressure pin 26 with respect to the illustration of Figure 1 down directed closing force on the end face 45 of the nozzle needle 46 exerts.
  • a further downwardly directed further closing force is exerted by a first spring 36 on the pressure pin 26 and thus on the nozzle needle 46, wherein the first spring 36 is disposed in the second pressure chamber 30 and is supported with its rear end on the shim 40.
  • a shoulder 44 having a portion of the nozzle needle 46 is surrounded by a third pressure chamber 32 which communicates with the first pressure chamber 28 via a connecting line 42.
  • a third pressure p 32 is built up in the third pressure chamber 32 as a function of the first pressure p 28 prevailing in the first pressure chamber 28.
  • the standing in the third pressure chamber 32 under the third pressure p 32 fuel 10 exerts a reference to the illustration of Figure 1 upward opening force on the nozzle needle 46.
  • the nozzle needle 46 assumes its open position as long as a difference between the opening force caused by the third pressure p 32 and the sum of the closing force generated by the second pressure p 30 and the closing force generated by the first spring 36 exceeds a predetermined value.
  • the nozzle opening pressure can be influenced via the second pressure p 30 in the second pressure chamber 30.
  • it is possible, for example, to provide a pressure limiting and holding valve 34 between the first pressure chamber 28 and the second pressure chamber 30 may be provided.
  • the control valve 22 is driven by an embodiment of the device 80 according to the invention for driving the control valve 22, in particular such that the inventive method results.
  • FIG. 2 shows a schematic partial sectional view of a control valve 22 which can be used with the pump-nozzle unit of Figure 1.
  • the control valve 22 shown has a movable element 48 in the form of a valve needle, which can be moved to close the control valve 22 in the illustrated first end position and fully open the control valve 22 in a second end position, which is shifted relative to the representation to the right ,
  • a valve plate 64 provided on the valve needle 48 cooperates with a housing-side valve seat 62.
  • the low-pressure fuel area 18 is closed relative to a high-pressure chamber 38, which communicates with the fuel line 20 shown in FIG.
  • FIG. 2 is a piezoelectric valve which has a piezoelectric element 76. With suitable control of the piezoelectric element 76, this exerts a force on a pressure piece 54 via an end face 78.
  • the pressure member 54 transmits the force generated by the piezoelectric element 76 in turn to a first lever 56 and a second lever 58, wherein the first lever 56 and the second lever 58 are provided to effect a power transmission.
  • the first lever 56 and the second lever 58 abut against a second axial end surface 72 of the valve needle 48 to transmit the translated force generated by the piezo element 76 to the valve needle 48.
  • the translated force generated by the suitably driven piezoelectric element 76 acting on the valve needle 48 is greater than an opposing force generated by a second spring 66 and exerted via a spring pressure member 68 on a first axial end surface 70 of the valve needle 48.
  • the low-pressure fuel area 18 is connected to a Abêtraum 50 in connection, which is still connected via a balancing bore 52 with an actuator located in front of the piezoelectric element 74 in connection.
  • This actuator chamber 74 is in communication with a return 60, via which fuel can flow back out of the actuator chamber 74.
  • the controlled variable of The resultant is evaluated by means of a measured at the piezoelectric element 76 at this time electrical variable, such as the voltage.
  • This procedure can be used both when the valve needle 48 is moved to complete opening of the control valve in its second end position (total stroke) and when the valve needle 48 is to take an intermediate position (partial stroke).
  • the desired partial displacements within a multiple control can assume different values. If the valve needle 48 via one or more intermediate position, the position according to the invention is regulated, is moved to the second end position, resulting in a slower opening of the valve. In this way, for example, at low engine speeds undesirable high pressure gradients can be at least reduced.
  • FIG. 3 shows a flowchart which illustrates an embodiment of the method according to the invention.
  • the embodiment of the method according to the invention shown in FIG. 3, which can be applied to the piezoelement 76 of FIG. 2, begins in step S1.
  • step S2 an external voltage is applied to the piezoelectric element 76 to close the control valve 22.
  • step S3 the external voltage is removed or lowered by the piezoelectric element 76 to open the control valve 22.
  • the resulting force is detected via an electrical variable on the piezoelectric element 76, for example via the voltage applied to the piezoelectric element 76.
  • step S4 the detected force or the detected force curve in the actuator chamber 74 is compared with a desired force or a desired force curve. Furthermore, a new value for the external voltage is determined, for example by setting offset values appropriately. If the method according to the invention is not to end in step S5, a branch is made back to step S2. Otherwise, the process ends at step S6.
  • the invention can be summarized as follows:
  • the invention relates to a method and a device 80 for controlling the control valve 22 of a pump-nozzle unit.
  • a control in particular an adaptive control.

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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)

Abstract

The invention relates to a method and device (80) for controlling the control valve (22) of a pump-nozzle unit. The positional accuracy of the valve lifts is increased by means of an automatic control, especially an adaptive automatic control, in order to avoid high pressure gradients at low engine speeds during the shut-off of the valve.

Description

Die Erfindung betrifft ein Verfahren und eine Vorrichtung zur Ansteuerung eines Steuerventils einer Pumpe-Düse-Einheit, wobei das Steuerventil zumindest ein bewegliches Element aufweist, das zum Schließen des Steuerventils in eine erste Endstellung und zum vollständigen Öffnen des Steuerventils in eine zweite Endstellung bewegbar ist.The invention relates to a method and a device for controlling a control valve of a pump-nozzle unit, wherein the control valve has at least one movable element which is movable to close the control valve in a first end position and to fully open the control valve in a second end position.

Pumpe-Düse-Einheiten dienen zum Zuführen von Kraftstoff in einen Verbrennungsraum einer Brennkraftmaschine. Dabei kann es sich beispielsweise um eine Pumpe-Düse-Einheit mit einer Steuer- und/oder regelbaren Kraftstoffpumpe, einer Kraftstoffeinspritzdüse, die eine zwischen einer Schließstellung und einer Öffnungsstellung hin und her bewegliche Düsennadel aufweist, einem ersten Druckraum, der von der Kraftstoffpumpe mit unter einem ersten Druck stehenden Kraftstoff befüllbar ist, einem zweiten Druckraum, wobei in dem zweiten Druckraum unter einem zweiten Druck stehender Kraftstoff eine Schließkraft auf die Düsennadel ausübt, und einem dritten Druckraum, der mit dem ersten Druckraum kommuniziert, wobei in den dritten Druckraum unter einem dritten Druck stehender Kraftstoff eine Öffnungskraft auf die Düsennadel ausübt, handeln.Pump-nozzle units are used for supplying fuel into a combustion chamber of an internal combustion engine. This may be, for example, a pump-nozzle unit with a controllable and / or controllable fuel pump, a fuel injector, which has a between a closed position and an open position reciprocating nozzle needle, a first pressure chamber of the fuel pump with below a first pressurized fuel is fillable, a second pressure chamber, wherein in the second pressure chamber at a second pressure stationary fuel exerts a closing force on the nozzle needle, and a third pressure chamber communicating with the first pressure chamber, wherein in the third pressure chamber under a third Pressurized fuel exerts an opening force on the nozzle needle.

Pumpe-Düse-Einheiten werden insbesondere im Zusammenhang mit druckgesteuerten Einspritzsystemen verwendet. Ein wesentliches Merkmal eines druckgesteuerten Einspritzsystems besteht darin, dass die Kraftstoffeinspritzdüse öffnet, sobald eine zumindest von aktuell herrschenden Drücken beeinflusste Öffnungskraft auf die Düsennadel ausgeübt wird. Derartige druckgesteuerte Einspritzsysteme dienen der Kraftstoffdosierung, der Kraftstoffaufbereitung, der Formung des Einspritzverlaufs und einer Abdichtung der Kraftstoffzuführung gegen den Verbrennungsraum der Brennkraftmaschine. Mit druckgesteuerten Einspritzsystemen lässt sich der zeitliche Verlauf des Mengenstroms während der Einspritzung in vorteilhafter Weise steuern. Damit kann ein positiver Einfluss auf die Leistung, den Kraftstoffverbrauch und die Schadstoffemission des Motors genommen werden.Pump-nozzle units are used in particular in connection with pressure-controlled injection systems. An essential feature of a pressure-controlled injection system is that the fuel injector opens as soon as an opening force, which is influenced at least by currently prevailing pressures, is exerted on the nozzle needle. Such pressure-controlled injection systems are used for fuel metering, fuel preparation, the formation of the course of injection and a seal of the fuel supply against the combustion chamber of the internal combustion engine. With pressure controlled Injection systems can be the temporal course of the flow rate during the injection control in an advantageous manner. This can have a positive influence on the engine's performance, fuel consumption and pollutant emission.

Bei Pumpe-Düse-Einheiten sind die Kraftstoffpumpe und die Kraftstoffeinspritzdüse in der Regel als integriertes Bauteil ausgebildet. Für jeden Verbrennungsraum der Brennkraftmaschine wird zumindest eine Pumpe-Düse-Einheit vorgesehen, die in der Regel in den Zylinderkopf eingebaut wird. Die Kraftstoffpumpe umfasst dabei typischerweise einen in einem Kraftstoffpumpenzylinder hin und her beweglichen Kraftstoffpumpenkolben, der entweder direkt über einen Stößel oder indirekt über Kipphebel von einer Nockenwelle der Brennkraftmaschine angetrieben wird. Der üblicherweise den ersten Druckraum bildende Abschnitt des Kraftstoffpumpenzylinders ist über ein Steuerventil mit einem Kraftstoff-Niederdruckbereich verbindbar, wobei bei geöffnetem Steuerventil Kraftstoff von dem Kraftstoff-Niederdruckbereich in den ersten Druckraum angesaugt und bei weiterhin geöffnetem Steuerventil von dem ersten Druckraum in den Kraftstoff-Niederdruckbereich zurückgedrückt wird. Sobald das Steuerventil geschlossen wird, erfolgt durch den Kraftstoffpumpenkolben eine Komprimierung des in dem ersten Druckraum befindlichen Kraftstoffs und somit ein Druckaufbau. Es ist bekannt, das Steuerventil in Form eines Magnetventils vorzusehen. Magnetventile weisen jedoch üblicherweise eine relativ lange Ansprechzeit auf, was insbesondere dadurch bedingt ist, dass der Magnetanker eines Magnetventils aufgrund der von seiner Masse abhängigen Massenträgheitskräfte nicht beliebig schnell beschleunigt werden kann. Weiterhin erfordert auch der Aufbau des Magnetfeldes zur Erzeugung der Anzugskraft Zeit. Eine mit einem Magnetventil ausgestattete Pumpe-Düse-Einheit ist beispielsweise aus der EP 0 277 939 B1 bekannt.In unit injectors, the fuel pump and the fuel injector are typically formed as an integral component. For each combustion chamber of the internal combustion engine, at least one pump-nozzle unit is provided, which is usually installed in the cylinder head. The fuel pump typically comprises a fuel pump piston which can be moved back and forth in a fuel pump cylinder and which is driven either directly by a tappet or indirectly via rocker arms by a camshaft of the internal combustion engine. The usually the first pressure chamber forming portion of the fuel pump cylinder is connected via a control valve with a fuel low pressure region, wherein sucked with the control valve open fuel from the low-pressure fuel area in the first pressure chamber and pushed back at further open control valve from the first pressure chamber in the low-pressure fuel area becomes. As soon as the control valve is closed, the fuel pump piston compresses the fuel in the first pressure chamber and thus builds up the pressure. It is known to provide the control valve in the form of a solenoid valve. However, solenoid valves usually have a relatively long response time, which is particularly due to the fact that the magnet armature of a solenoid valve can not be accelerated arbitrarily fast due to the mass inertia forces dependent on its mass. Furthermore, the structure of the magnetic field for generating the tightening force requires time. A pump-nozzle unit equipped with a solenoid valve is known, for example, from EP 0 277 939 B1.

Um die durch die Verwendung von Magnetventilen hervorgerufenen Probleme zu vermeiden, ist es weiterhin bereits bekannt, Pumpe-Düse-Einheiten mit einem Steuerventil auszustatten, das piezoelektrisch betrieben wird. Eine derartige Pumpe-Düse-Einheit ist beispielsweise aus der DE 198 35 494 A1 der DE 100 35 814 A1 bekannt.In order to avoid the problems caused by the use of solenoid valves, it is also known to provide pump-nozzle units with a control valve which is operated piezoelectrically. Such a pump-nozzle unit is known for example from DE 198 35 494 A1 of DE 100 35 814 A1.

Um bei einem Einspritzvorgang neben einer Haupteinspritzmenge eine zusätzliche Voreinspritzmenge und/oder eine zusätzliche Nacheinspritzmenge in den Verbrennungsraum einzubringen, ist es weiterhin bekannt, während eines Einspritzzyklus mehrere in kurzen Zeitabständen aufeinanderfolgende Einspritzimpulse auszulösen.In order to introduce an additional pre-injection quantity and / or an additional post-injection quantity into the combustion chamber during an injection process in addition to a main injection quantity, it is also known to trigger a plurality of injection pulses consecutive in short time intervals during one injection cycle.

Optimale Brennverfahren, beispielsweise bei direkt einspritzenden Dieselmotoren, erfordern diese flexible Gestaltung des Einspritzverlaufs mit Mehrfacheinspritzung, beispielsweise Vor-, Haupt- und Nacheinspritzung. Bei höheren Drehzahlen ist zu diesem Zweck ein sehr schnelles Schließen und Öffnen des Steuerventils über dessen gesamten Hub notwendig, mit entsprechend hohen Druckgradienten. Insbesondere bei niedrigen Drehzahlen sind solche hohen Druckgradienten häufig unerwünscht, da sie Druckschwankungen auslösen. Die Abklingzeit dieser Druckschwankungen hat Einfluss auf die maximale Anzahl und Genauigkeit der Ansteuervorgänge innerhalb einer Sequenz von Mehrfacheinspritzungen. Das niedrige Druckniveau der Kraftstoffversorgung von Pumpe-Düse-Systemen begünstigt einen niedrigen Kraftstoffverbrauch, erhöht jedoch häufig die Kavitationsneigung. Höhere Druckgradienten verstärken diese Neigung, was das Motorgeräusch erhöht.Optimum combustion processes, for example in direct injection diesel engines, require this flexible design of the multiple injection injection pattern, for example, pilot, main, and post injection. At higher speeds, a very fast closing and opening of the control valve over its entire stroke is necessary for this purpose, with correspondingly high pressure gradients. Especially at low speeds such high pressure gradients are often undesirable because they trigger pressure fluctuations. The decay time of these pressure fluctuations has an influence on the maximum number and accuracy of the drive processes within a sequence of multiple injections. The low pressure level of the fuel supply of pump-nozzle systems promotes low fuel consumption, but often increases the cavitation tendency. Higher pressure gradients increase this inclination, which increases the engine noise.

Steuerventile in Form von Magnetventilen haben in der Regel nur im vollständig geöffneten und im geschlossenen Zustand stabile Hublagen. Diese stabilen Lagen sind in der Regel durch mechanische Anschläge bestimmt. Der Hubverlauf über der Zeit hängt vom resultierenden Kraftverlauf aus Magnet-, Hydraulik- und Reibungskräften ab. Bei Steuerventilen in Form von Magnetventilen gibt es Ansätze, die Absteuerdruckgradienten durch einen stufenförmigen Hubverlauf zu vermindern. Derartige stufenförmige Hubverläufe zeigen bei Magnetventilen jedoch prinzipbedingt starke stochastische und exemplarspezifische Streuungen. Weiterhin ist die jeweilige Dauer der Teilhubphasen eng begrenzt.Control valves in the form of solenoid valves usually have stable stroke positions only in the fully open and in the closed state. These stable layers are usually determined by mechanical stops. The stroke over time depends on the resulting force curve from magnetic, hydraulic and friction forces. With control valves in the form of solenoid valves, there are approaches, the Absteuerdruckgradienten to reduce by a stepped stroke course. However, such step-shaped strokes show, in principle, strong stochastic and specimen-specific scattering in solenoid valves. Furthermore, the respective duration of Teilhubphasen is limited.

Steuerventile in Form von Piezoventilen ermöglichen eine relativ stabile Ansteuerung von Teilhüben, praktisch ohne störende zeitliche Begrenzung. Allerdings gilt die dabei erreichbare Stellgenauigkeit als kritisch, da man beispielsweise bei einem Gesamthub von 200 µm eine Lagegenauigkeit der Ventilteilhübe von beispielsweise +/- 5 µm für erforderlich hält, um unerwünschte Nebenwirkungen im Einspritzverlauf zu vermeiden.Control valves in the form of piezo valves allow a relatively stable control of partial strokes, virtually without disturbing time limit. However, the achievable positioning precision is considered critical, since for example with a total stroke of 200 μm, a positional accuracy of the valve member strokes of, for example, +/- 5 μm is considered necessary in order to avoid undesired side effects during the injection process.

Der Erfindung liegt die Aufgabe zugrunde, die gattungsgemäßen Verfahren und Vorrichtungen derart weiterzubilden, dass Steuerventilteilhübe mit verbesserter Lagegenauigkeit erzielt werden können, insbesondere um bei niedrigeren Motordrehzahlen hohe Druckgradienten vermeiden zu können.The invention has the object of developing the generic methods and devices such that Steuerventilteilhübe can be achieved with improved positional accuracy, especially in order to avoid high pressure gradients at lower engine speeds can.

Diese Aufgabe wird durch die Merkmale der unabhängigen Ansprüche 1 und 6 gelöst.This object is solved by the features of independent claims 1 and 6.

Vorteilhafte Ausgestaltungen und Weiterbildungen der Erfindung ergeben sich aus den abhängigen Ansprüchen.Advantageous embodiments and modifications of the invention will become apparent from the dependent claims.

Das erfindungsgemäße Verfahren zur Ansteuerung eines Steuerventils einer Pumpe-Düse-Einheit baut auf dem gattungsgemäßen Stand der Technik dadurch auf, dass zur Einstellung von zumindest einer Zwischenstellung des zumindest einen beweglichen Elements zumindest zeitweise eine Regelung, insbesondere eine adaptive Regelung eingesetzt wird. Durch diese Lösung werden Ventilteilhübe mit einer hohen Lagegenauigkeit erreicht, was beispielsweise zu einer Verbesserung der Geräusch- und Abgasemissionen sowie des Drehmomentenverlaufs des Motors führt.The inventive method for controlling a control valve of a pump-nozzle unit is based on the generic state of the art in that for adjusting at least one intermediate position of the at least one movable element at least temporarily a scheme, in particular an adaptive control is used. This solution valve lift strokes are achieved with a high position accuracy, resulting in, for example, to improve the noise and exhaust emissions and the torque curve of the engine.

Ein Verfahren sieht vor, dass zumindest eine Zwischenstellung für eine vorgegebene Zeitspanne eingestellt wird, wenn das zumindest eine bewegliche Element zum Öffnen des Steuerventils von der zweiten Endstellung in die erste Endstellung bewegt wird. Durch das Einstellen von einer oder mehreren definierten Zwischenstellungen für eine oder mehrere vorgegebene Zeitspannen kann der Öffnungsvorgang des Steuerventils gezielt und definiert verlangsamt werden, beispielsweise um bei niedrigeren Motordrehzahlen hohe Druckgradienten zu vermeiden.A method provides that at least one intermediate position is set for a predetermined period of time when the at least one movable element for opening the control valve is moved from the second end position to the first end position. By setting one or more defined intermediate positions for one or more predetermined periods of time, the opening operation of the control valve can be slowed down in a targeted and defined manner, for example in order to avoid high pressure gradients at lower engine speeds.

Dabei ist vorzugsweise weiterhin vorgesehen, dass die Ansteuerung des Steuerventils durch elektrische Ansteuerung eines Stellgliedes für das zumindest eine bewegliche Element erfolgt. Der Typ des Stellgliedes legt dabei den Typ des Steuerventils fest, beispielsweise Magnetventil oder Piezoventil.It is preferably further provided that the control of the control valve by electrical control of an actuator for the at least one movable element takes place. The type of actuator determines the type of control valve, such as solenoid valve or piezo valve.

Hinsichtlich der eigentlichen Regelung wird bevorzugt, dass die Stellgröße der Regelung eine elektrische Größe ist, mit der das Stellglied elektrisch angesteuert wird. Die elektrische Größe kann beispielsweise bei einem Piezoventil die Ansteuerspannung des Piezoelements sein.With regard to the actual control, it is preferred that the manipulated variable of the control is an electrical variable with which the actuator is electrically actuated. The electrical variable may be the drive voltage of the piezoelectric element, for example, in the case of a piezo valve.

Bei einer erstern Ausführungsform des erfindungsgemäßen Verfahrens ist vorgesehen, dass die Regelgröße der Regelung eine resultierende Kraft und/oder ein resultierender Kraftverlauf in Folge eines Drucks innerhalb zumindest eines Bereichs des Steuerventils ist, insbesondere ein sich beim Öffnen des Steuerventils einstellender Druck und/oder Druckverlauf innerhalb des zumindest einen Bereichs. Sofern es sich um ein Piezoventil handelt, kann der zumindest eine Bereich, beispielsweise der mit Kraftstoff gefüllte Raum vor dem Piezoelement und/oder ein Absteuerraum sein, wobei ein dort auftretender Druckanstieg einen Anstieg der Druckkraft an der Piezokeramik bewirkt, beispielsweise über einen Kolben oder ähnliches.In a first embodiment of the method according to the invention, it is provided that the controlled variable of the control is a resultant force and / or force curve as a result of a pressure within at least one area of the control valve, in particular a pressure and / or pressure curve that occurs during opening of the control valve of the at least one area. If it is a piezoelectric valve, the at least one area, for example the space filled with fuel before the piezoelectric element and / or a Absteuerraum, wherein a pressure increase occurring there causes an increase of the pressure force on the piezoceramic, for example via a piston or the like ,

Dadurch ergibt sich, dass der Druck und/oder der Druckverlauf innerhalb des zumindest einen Bereichs des Steuerventils über ein Piezoelement erfasst wird.This results in that the pressure and / or the pressure curve within the at least one region of the control valve is detected via a piezoelectric element.

In diesem Zusammenhang ist vorzugsweise weiterhin vorgesehen, dass das Piezoelement Bestandteil des Stellgliedes ist oder dieses bildet.In this context, it is preferably further provided that the piezoelectric element is part of the actuator or forms this.

Bei besonders bevorzugten Ausführungsformen des erfindungsgemäßen Verfahrens ist weiterhin vorgesehen, dass der während eines aktuellen Öffnungsvorganges des Steuerventils erfasste Druck und/oder Druckverlauf innerhalb des zumindest einen Bereichs des Steuerventils für den aktuellen Öffnungsvorgang und/oder für zumindest einen nachfolgenden Öffnungsvorgang in die Regelung eingeht, insbesondere in Form von Offsetwerten zumindest einer elektrischen Größe, mit der das Stellglied angesteuert wird. Beispielsweise kann ein Anstieg der Druckkraft an einer Piezokeramik durch eine an dem Piezoelement gemessene elektrische Größe ausgewertet werden. Während des aktuellen Einspritzvorgangs, vorzugsweise spätestens ab dem nächsten Einspritzvorgang, können die gewünschten Teilhublagen dann durch Überlagerung entsprechender Offsetwerte auf den zum Auswertungszeitpunkt vorliegenden Wert der Piezo-Steuergröße erreicht werden. Die Soll-Teilhublagen können dabei innerhalb einer Mehrfachansteuerung unterschiedliche Werte' annehmen.In particularly preferred embodiments of the method according to the invention, it is further provided that the pressure and / or pressure curve detected during a current opening operation of the control valve enters the control within the at least one area of the control valve for the current opening operation and / or for at least one subsequent opening operation, in particular in the form of offset values of at least one electrical variable with which the actuator is controlled. For example, an increase in the pressure force on a piezoceramic can be evaluated by an electrical variable measured at the piezoelectric element. During the current injection process, preferably at the latest from the next injection process, the desired partial lifting positions can then be achieved by superimposing corresponding offset values on the value of the piezo control variable present at the time of evaluation. The desired partial lifting positions can assume different values within a multiple control.

Die erfindungsgemäße Vorrichtung zur Ansteuerung eines Steuerventils einer Pumpe-Düse-Einheit baut auf dem gattungsgemäßen Stand der Technik dadurch auf, dass sie zur Einstellung von zumindest einer Zwischenstellung des zumindest einen beweglichen Elements zumindest zeitweise eine Regelung, insbesondere eine adaptive Regelung durchführt. Dadurch ergeben sich die im Zusammenhang mit dem erfindungsgemäßen Verfahren erläuterten Vorteile in gleicher oder ähnlicher Weise, weshalb zur Vermeidung von Wiederholungen auf die entsprechenden Ausführungen verwiesen wird.The inventive device for controlling a control valve of a pump-nozzle unit is based on the generic state of the art in that it performs to adjust at least one intermediate position of the at least one movable element at least temporarily a scheme, in particular an adaptive control. This results in the advantages explained in connection with the method according to the invention in the same or a similar way, which is why to avoid repetition, reference is made to the relevant statements.

Gleiches gilt sinngemäß für die folgenden bevorzugten Ausführungsformen der erfindungsgemäßen Vorrichtung, wobei auch bezüglich der durch diese Ausführungsformen erzielbaren Vorteile auf die entsprechenden Ausführungen im Zusammenhang mit dem erfindungsgemäßen Verfahren verwiesen wird.The same applies mutatis mutandis to the following preferred embodiments of the device according to the invention, wherein also with respect to the advantages achievable by these embodiments, reference is made to the corresponding statements in connection with the inventive method.

Auch bei vorteilhaften Ausführungsformen der erfindungsgemäßen Vorrichtung ist vorgesehen, dass sie die zumindest eine Zwischenstellung für eine vorgegebene Zeitspanne einstellt, wenn das zumindest eine bewegliche Element zum Öffnen des Steuerventils von der zweiten Endstellung in die erste Endstellung bewegt wird.Also in advantageous embodiments of the device according to the invention it is provided that it adjusts the at least one intermediate position for a predetermined period of time when the at least one movable element for opening the control valve is moved from the second end position to the first end position.

Weiterhin werden Ausführungsformen der erfindungsgemäßen Vorrichtung als vorteilhaft erachtet, bei denen vorgesehen ist, dass sie die Ansteuerung des Steuerventils durch elektrische Ansteuerung eines Stellgliedes für das zumindest eine bewegliche Element durchführt.Furthermore, embodiments of the device according to the invention are considered advantageous in which it is provided that it performs the control of the control valve by electrical control of an actuator for the at least one movable element.

Für die erfindungsgemäße Vorrichtung wird in diesem Fall bevorzugt, dass sie zur Durchführung der Regelung eine elektrische Größe als Stellgröße verwendet, mit der sie das Stellglied elektrisch ansteuert.For the device according to the invention, it is preferred in this case that it uses an electrical variable as the manipulated variable with which it electrically actuates the actuator in order to carry out the control.

Ähnlich wie bei dem erfindungsgemäßen Verfahren ist auch bei der erfindungsgemäßen Vorrichtung vorzugsweise vorgesehen, dass sie als Regelgröße der Regelung eine resultierende Kraft und/oder einen resultierenden Kraftverlauf in Folge eines Drucks innerhalb zumindest eines Bereichs des Steuerventils verwendet, insbesondere einen sich beim Öffnen des Steuerventils einstellenden Druck und/oder Druckverlauf innerhalb des zumindest einen Bereichs.Similar to the method according to the invention, it is also preferably provided in the device according to the invention that it uses a resulting force and / or force curve as a result of a pressure within at least one area of the control valve, in particular a setting when opening the control valve Pressure and / or pressure curve within the at least one area.

Insbesondere in diesem Zusammenhang sehen bevorzugte Weiterbildungen der erfindungsgemäßen Vorrichtung vor, dass der Druck und/oder der Druckverlauf innerhalb des zumindest einen Bereichs des Steuerventils über ein Piezoelement erfasst wird.In particular in this connection, preferred developments of the device according to the invention provide that the pressure and / or the pressure curve within the at least one region of the control valve is detected via a piezoelectric element.

Dabei wird weiterhin bevorzugt, dass das Piezoelement Bestandteil des Stellgliedes ist oder dieses bildet.It is further preferred that the piezoelectric element is part of the actuator or forms this.

Auch für die erfindungsgemäße Vorrichtung wird bevorzugt, dass sie den während eines aktuellen Öffnungsvorganges des Steuerventils erfassten Druck und/oder Druckverlauf innerhalb des zumindest einen Bereichs des Steuerventils für den aktuellen Öffnungsvorgang und/oder für zumindest einen nachfolgenden Öffnungsvorgang in die Regelung einbezieht, insbesondere in Form von Offsetwerten zumindest einer elektrischen Größe, mit der sie das Stellglied ansteuert.It is also preferred for the device according to the invention that it includes the pressure and / or pressure curve detected during a current opening operation of the control valve within the at least one area of the control valve for the current opening operation and / or for at least one subsequent opening operation, in particular in shape of offset values of at least one electrical quantity with which it drives the actuator.

Der Erfindung liegt die Erkenntnis zugrunde, dass sich die Geräusch- und Abgasemissionen sowie der Drehmomentverlauf eines Verbrennungsmotors verbessern lassen, wenn zur Erhöhung der Lagegenauigkeit von Teilhüben des Steuerventils einer Pumpe-Düse-Einheit eine Regelung verwendet wird.The invention is based on the finding that the noise and exhaust emissions and the torque curve of an internal combustion engine can be improved if a control is used to increase the positional accuracy of partial strokes of the control valve of a pump-nozzle unit.

Die Erfindung wird nun unter Bezugnahme auf die beigefügten Zeichnungen anhand bevorzugter Ausführungsformen beispielhaft erläutert.The invention will now be described by way of example with reference to the accompanying drawings with reference to preferred embodiments.

Es zeigen:

Figur 1
eine schematische Ausführungsform einer Pumpe-Düse-Einheit bei beziehungsweise mit der das erfindungsgemäße Verfahren beziehungsweise die erfindungsgemäße Vorrichtung angewendet werden kann;
Figur 2
eine schematische Teil-Schnittansicht eines Steuerventils, das mit der Pumpe-Düse-Einheit nach Figur 1 verwendet werden kann; und
Figur 3
ein Flussdiagramm, das eine Ausführungsform des erfindungsgemäßen Verfahrens veranschaulicht.
Show it:
FIG. 1
a schematic embodiment of a pump-nozzle unit at or with which the method according to the invention or the device according to the invention can be applied;
FIG. 2
a schematic partial sectional view of a control valve, which can be used with the pump-nozzle unit of Figure 1; and
FIG. 3
a flow chart illustrating an embodiment of the method according to the invention.

Figur 1 zeigt schematisch eine Pumpe-Düse-Einheit. Die dargestellte Pumpe-Düse-Einheit zum Zuführen von Kraftstoff 10 in einen Verbrennungsraum 12 einer Brennkraftmaschine weist eine Kraftstoffpumpe 14-22 auf. Dabei ist ein Kraftstoffpumpenkolben 14 in einem Kraftstoffpumpenzylinder 16 hin und her bewegbar. Der Kraftstoffpumpenkolben 14 wird direkt oder indirekt über eine nicht dargestellte Nockenwelle der Brennkraftmaschine angetrieben. Der Kompressionsraum des Kraftstoffpumpenzylinders 16 bildet einen ersten Druckraum 28. Der erste Druckraum 28 ist über eine Kraftstoffleitung 20 mit dem erfindungsgemäß anzusteuernden Steuerventil 22 verbunden. Das Steuerventil 22 dient dazu, die Kraftstoffleitung 20 entweder zu verschließen oder mit einem Kraftstoff-Niederdruckbereich 18 zu verbinden, aus dem Kraftstoff 10 angesaugt werden kann. In der geöffneten Ruhestellung des Steuerventils 22 wird bei einer bezogen auf Figur 1 nach oben gerichteten Bewegung des Kraftstoffpumpenkolbens 14 Kraftstoff 10 aus dem Kraftstoff-Niederdruckbereich 18 in den ersten Druckraum 28 angesaugt. Sofern das Steuerventil 22 sich bei einer bezogen auf Figur 1 nach unten gerichteten Bewegung des Kraftstoffpumpenkolbens 14 noch in seiner geöffneten Ruhestellung befindet, kann vorher in den ersten Druckraum 28 angesaugter Kraftstoff 10 wieder zurück in den Kraftstoff-Niederdruckbereich 18 gedrückt werden. Bei einer geeigneten Ansteuerung des Steuerventils 22 verschließt dieses die Kraftstoffleitung 20. Dadurch wird der in den ersten Druckraum 28 angesaugte Kraftstoff 10 bei einer nach unten gerichteten Bewegung des Kraftstoffpumpenkolbens 14 komprimiert, wodurch ein erster Druck p28 in dem ersten Druckraum 28 erzeugt wird. Die dargestellte Pumpe-Düse-Einheit umfasst weiterhin eine insgesamt mit 24 bezeichnete Kraftstoffeinspritzdüse, die eine zwischen einer Schließstellung und einer Öffnungsstellung hin und her bewegliche Düsennadel 46 aufweist. Ein Druckstift 26 kann, bezogen auf die Darstellung von Figur 1, insbesondere eine nach unten gerichtete Kraft auf die Düsennadel 46 ausüben. Am oberen Ende des Druckstifts 26 ist eine Einstellscheibe 40 vorgesehen, die in einem zweiten Druckraum 30 geführt ist, wobei in dem zweiten Druckraum 30 unter einem zweiten Druck p30 stehender Kraftstoff 10 über den Druckstift 26 eine bezogen auf die Darstellung von Figur 1 nach unten gerichtete Schließkraft auf die Stirnfläche 45 der Düsennadel 46 ausübt. Eine ebenfalls nach unten gerichtete weitere Schließkraft wird durch eine erste Feder 36 auf den Druckstift 26 und somit auf die Düsennadel 46 ausgeübt, wobei die erste Feder 36 in dem zweiten Druckraum 30 angeordnet ist und sich mit ihrem hinteren Ende an der Einstellscheibe 40 abstützt. Ein eine Schulter 44 aufweisender Abschnitt der Düsennadel 46 ist von einem dritten Druckraum 32 umgeben, der mit dem ersten Druckraum 28 über eine Verbindungsleitung 42 kommuniziert. In Abhängigkeit von der Drosselwirkung der Verbindungsleitung 42 und gegebenenfalls weiterer nicht dargestellter Drosseleinrichtungen wird in Abhängigkeit von dem in dem ersten Druckraum 28 herrschenden ersten Druck p28 in dem dritten Druckraum 32 ein dritter Druck p32 aufgebaut. Der in dem dritten Druckraum 32 unter dem dritten Druck p32 stehende Kraftstoff 10 übt eine bezogen auf die Darstellung von Figur 1 nach oben gerichtete Öffnungskraft auf die Düsennadel 46 aus. Die Düsennadel 46 nimmt ihre Öffnungsstellung ein, solange eine Differenz zwischen der durch den dritten Druck p32 verursachten Öffnungskraft und der Summe aus der durch den zweiten Druck p30 erzeugten Schließkraft und der durch die erste Feder 36 erzeugten Schließkraft einen vorgegebenen Wert überschreitet. Über den zweiten Druck p30 in dem zweiten Druckraum 30 kann somit der Düsenöffnungsdruck beeinflusst werden. Um den zweiten Druck p30 im zweiten Druckraum 30 auf jeweils geeignet Werte zu begrenzen und zu halten kann beispielsweise ein Druckbegrenzungs- und -halteventil 34 zwischen dem ersten Druckraum 28 und dem zweiten Druckraum 30 vorgesehen sein. Das Steuerventil 22 wird durch eine Ausführungsform der erfindungsgemäßen Vorrichtung 80 zum Ansteuern des Steuerventils 22 angesteuert, insbesondere derart, dass sich das erfindungsgemäße Verfahren ergibt.Figure 1 shows schematically a pump-nozzle unit. The illustrated pump-nozzle unit for supplying fuel 10 into a combustion chamber 12 of an internal combustion engine has a fuel pump 14-22. In this case, a fuel pump piston 14 in a fuel pump cylinder 16 is movable back and forth. The fuel pump piston 14 is driven directly or indirectly via a camshaft, not shown, of the internal combustion engine. The compression space of the fuel pump cylinder 16 forms a first pressure chamber 28. The first pressure chamber 28 is connected via a fuel line 20 to the control valve 22 to be triggered according to the invention. The control valve 22 serves either to close the fuel line 20 or to connect it to a low-pressure fuel area 18, from which fuel 10 can be sucked. In the open rest position of the control valve 22, fuel 10 is sucked from the low-pressure fuel area 18 into the first pressure chamber 28 in a movement of the fuel pump piston 14 directed upward in relation to FIG. If the control valve 22 is still in its open rest position with respect to a downwardly directed with respect to Figure 1 movement of the fuel pump piston 14, previously sucked into the first pressure chamber 28 fuel 10 can be pressed back into the low-pressure fuel area 18. With a suitable control of the control valve 22 closes, this is the fuel line 20. This compresses the sucked into the first pressure chamber 28, fuel 10 at a downwardly directed movement of the fuel pump plunger 14, whereby a first pressure p is produced in the first pressure chamber 28 28th The illustrated unit injector also includes a total of 24 designated A fuel injector having a reciprocating needle 46 movable between a closed position and an open position. A pressure pin 26 can, in relation to the representation of FIG. 1, in particular exert a downward force on the nozzle needle 46. At the upper end of the pressure pin 26, a shim 40 is provided, which is guided in a second pressure chamber 30, wherein in the second pressure chamber 30 at a second pressure p 30 standing fuel 10 via the pressure pin 26 with respect to the illustration of Figure 1 down directed closing force on the end face 45 of the nozzle needle 46 exerts. A further downwardly directed further closing force is exerted by a first spring 36 on the pressure pin 26 and thus on the nozzle needle 46, wherein the first spring 36 is disposed in the second pressure chamber 30 and is supported with its rear end on the shim 40. A shoulder 44 having a portion of the nozzle needle 46 is surrounded by a third pressure chamber 32 which communicates with the first pressure chamber 28 via a connecting line 42. Depending on the throttling action of the connecting line 42 and possibly other throttle devices, not shown, a third pressure p 32 is built up in the third pressure chamber 32 as a function of the first pressure p 28 prevailing in the first pressure chamber 28. The standing in the third pressure chamber 32 under the third pressure p 32 fuel 10 exerts a reference to the illustration of Figure 1 upward opening force on the nozzle needle 46. The nozzle needle 46 assumes its open position as long as a difference between the opening force caused by the third pressure p 32 and the sum of the closing force generated by the second pressure p 30 and the closing force generated by the first spring 36 exceeds a predetermined value. Thus, the nozzle opening pressure can be influenced via the second pressure p 30 in the second pressure chamber 30. In order to limit and maintain the second pressure p 30 in the second pressure chamber 30 at respectively suitable values, it is possible, for example, to provide a pressure limiting and holding valve 34 between the first pressure chamber 28 and the second pressure chamber 30 may be provided. The control valve 22 is driven by an embodiment of the device 80 according to the invention for driving the control valve 22, in particular such that the inventive method results.

Figur 2 zeigt eine schematische Teil-Schnittansicht eines Steuerventils 22, das mit der Pumpe-Düse-Einheit nach Figur 1 verwendet werden kann. Das dargestellte Steuerventil 22 weist ein bewegliches Element 48 in Form einer Ventilnadel auf, die zum Schließen des Steuerventils 22 in die dargestellte erste Endstellung und zum vollständigen Öffnen des Steuerventils 22 in eine zweite Endstellung bewegt werden kann, die bezogen auf die Darstellung nach rechts verschoben ist. Wenn sich die Ventilnadel 48 in ihrer dargestellten ersten Endstellung befindet, wirkt ein an der Ventilnadel 48 vorgesehener Ventilteller 64 mit einem gehäuseseitigen Ventilsitz 62 zusammen. Dadurch wird der Kraftstoff-Niederdruckbereich 18 gegenüber einer Hochdruckkammer 38 verschlossen, die mit der in Figur 1 dargestellten Kraftstoffleitung 20 in Verbindung steht. Bei dem in Figur 2 dargestellten Steuerventil 22 handelt es sich um ein Piezoventil, das ein Piezoelement 76 aufweist. Bei geeigneter Ansteuerung des Piezoelementes 76 übt dieses über eine Stirnfläche 78 eine Kraft auf ein Druckstück 54 aus. Das Druckstück 54 überträgt die von dem Piezoelement 76 erzeugte Kraft seinerseits auf einen ersten Hebel 56 und einen zweiten Hebel 58, wobei der erste Hebel 56 und der zweite Hebel 58 dazu vorgesehen sind, eine Kraftübersetzung zu bewirken. Der erste Hebel 56 und der zweite Hebel 58 liegen an einer zweiten axialen Endfläche 72 der Ventilnadel 48 an, um die von dem Piezoelement 76 erzeugte, übersetzte Kraft auf die Ventilnadel 48 zu übertragen. Die von dem geeignet angesteuerten Piezoelement 76 erzeugte, übersetzte Kraft, die auf die Ventilnadel 48 wirkt, ist größer als eine entgegengesetzte Kraft, die von einer zweiten Feder 66 erzeugt und über ein Federdruckstück 68 auf eine erste axiale Endfläche 70 der Ventilnadel 48 ausgeübt wird. Der Kraftstoff-Niederdruckbereich 18 steht mit einem Absteuerraum 50 in Verbindung, der über eine Ausgleichsbohrung 52 weiterhin mit einem vor dem Piezoelement befindlichen Aktorraum 74 in Verbindung steht. Dieser Aktorraum 74 steht mit einem Rücklauf 60 in Verbindung, über den Kraftstoff aus dem Aktorraum 74 zurückströmen kann.Figure 2 shows a schematic partial sectional view of a control valve 22 which can be used with the pump-nozzle unit of Figure 1. The control valve 22 shown has a movable element 48 in the form of a valve needle, which can be moved to close the control valve 22 in the illustrated first end position and fully open the control valve 22 in a second end position, which is shifted relative to the representation to the right , When the valve needle 48 is in its illustrated first end position, a valve plate 64 provided on the valve needle 48 cooperates with a housing-side valve seat 62. As a result, the low-pressure fuel area 18 is closed relative to a high-pressure chamber 38, which communicates with the fuel line 20 shown in FIG. The control valve 22 shown in FIG. 2 is a piezoelectric valve which has a piezoelectric element 76. With suitable control of the piezoelectric element 76, this exerts a force on a pressure piece 54 via an end face 78. The pressure member 54 transmits the force generated by the piezoelectric element 76 in turn to a first lever 56 and a second lever 58, wherein the first lever 56 and the second lever 58 are provided to effect a power transmission. The first lever 56 and the second lever 58 abut against a second axial end surface 72 of the valve needle 48 to transmit the translated force generated by the piezo element 76 to the valve needle 48. The translated force generated by the suitably driven piezoelectric element 76 acting on the valve needle 48 is greater than an opposing force generated by a second spring 66 and exerted via a spring pressure member 68 on a first axial end surface 70 of the valve needle 48. The low-pressure fuel area 18 is connected to a Absteuerraum 50 in connection, which is still connected via a balancing bore 52 with an actuator located in front of the piezoelectric element 74 in connection. This actuator chamber 74 is in communication with a return 60, via which fuel can flow back out of the actuator chamber 74.

Bei Öffnungsbeginn des Steuerventils 22 (in der Regel zu dem Zeitpunkt, zu dem eine Kraftstoffeinspritzung in den Verbrennungsraum beendet ist "Förderende") entsteht in dem Absteuerraum 50 durch dessen Verbindung mit der Hochdruckkammer 38 ein Druckanstieg. Die Bohrung 52 leitet diesen Druckanstieg ungefähr mit Schallgeschwindigkeit in den mit Kraftstoff gefüllten Aktorraum 74 vor dem Piezoelement 76, was einen Anstieg der Druckkraft an der Piezokeramik bewirkt. Der im Aktorraum 76 entstehende Druckanstieg wirkt des weiteren über die als Kolben ausgebildete Ventilnadel 48 mit der Kraftübersetzung der Hebel 56 und 58 als zusätzliche Kraft über das Druckstück 54 auf die Stirnfläche 78 des Piezoelements 76. Die Resultierende dieser Kräfte stellt bei dieser Ausführungsform die Regelgröße der erfindungsgemäßen Regelung dar. Die Resultierende wird mittels einer am Piezoelement 76 zu diesem Zeitpunkt gemessenen elektrischen Größe, beispielsweise der Spannung, ausgewertet. Diese Vorgehensweise kann sowohl dann angewendet werden, wenn die Ventilnadel 48 zum vollständigen Öffnen des Steuerventils in ihre zweite Endstellung bewegt wird (Gesamthub) als auch wenn die Ventilnadel 48 eine Zwischenstellung einnehmen soll (Teilhub). Während des aktuellen Einspritzvorganges, vorzugsweise spätestens ab dem nächsten Einspritzvorgang, werden die gewünschten Teilhublagen durch Überlagerung entsprechender Offsetwerte auf den zum Auswertungszeitpunkt (= Kraftstoffförderende) vorliegenden Wert der Steuergröße der Regelung (beispielsweise der Piezospannung) erreicht. Es ist zu beachten, dass die Soll-Teilhublagen innerhalb einer Mehrfachansteuerung unterschiedliche Werte annehmen können. Wenn die Ventilnadel 48 über eine oder mehrere Zwischenstellung, deren Lage erfindungsgemäß geregelt wird, in die zweite Endstellung bewegt wird, ergibt sich ein verlangsamtes Öffnen des Ventils. Auf diese Weise können beispielsweise bei niedrigeren Motordrehzahlen unerwünschte hohe Druckgradienten zumindest verringert werden.At the start of opening of the control valve 22 (usually at the time when fuel injection into the combustion chamber is finished "end of delivery") arises in the Absteuerraum 50 by its connection with the high-pressure chamber 38, a pressure increase. The bore 52 conducts this pressure increase approximately at the speed of sound into the fuel-filled actuator chamber 74 in front of the piezoelectric element 76, which causes an increase in the pressure force on the piezoceramic. The resulting in the actuator chamber 76 pressure increase further acts on the trained as a piston valve needle 48 with the force translation of the lever 56 and 58 as an additional force on the pressure member 54 on the end face 78 of the piezoelectric element 76. The resultant of these forces in this embodiment, the controlled variable of The resultant is evaluated by means of a measured at the piezoelectric element 76 at this time electrical variable, such as the voltage. This procedure can be used both when the valve needle 48 is moved to complete opening of the control valve in its second end position (total stroke) and when the valve needle 48 is to take an intermediate position (partial stroke). During the current injection process, preferably at the latest from the next injection process, the desired partial displacements are achieved by superimposing corresponding offset values on the value of the control variable of the control (for example the piezoelectric voltage) present at the evaluation time (= fuel delivery end). It should be noted that the desired partial displacements within a multiple control can assume different values. If the valve needle 48 via one or more intermediate position, the position according to the invention is regulated, is moved to the second end position, resulting in a slower opening of the valve. In this way, for example, at low engine speeds undesirable high pressure gradients can be at least reduced.

Figur 3 zeigt ein Flussdiagramm, das eine Ausführungsform des erfindungsgemäßen Verfahrens veranschaulicht. Die in Figur 3 dargestellte Ausführungsform des erfindungsgemäßen Verfahrens, die auf das Piezoelement 76 von Figur 2 angewendet werden kann, beginnt beim Schritt S1. Anschließend wird beim Schritt S2 einen externe Spannung an das Piezoelement 76 angelegt, um das Steuerventil 22 zu schließen. Sobald das Kraftstoffförderende erreicht ist wird beim Schritt S3 fortgefahren. Im Schritt S3 wird die externe Spannung vom Piezoelement 76 entfernt oder gesenkt, um das Steuerventil 22 zu öffnen. Anschließend wird die resultierende Kraft über eine elektrische Größe am Piezoelement 76 erfasst, beispielsweise über die am Piezoelement 76 anliegende Spannung. Anschließend wird im Schritt S4 die erfasste Kraft oder der erfasste Kraftverlauf im Aktorraum 74 mit einer Sollkraft oder einem Sollkraftverlauf verglichen. Weiterhin wird ein neuer Wert für die externe Spannung bestimmt, beispielsweise indem Offsetwerte geeignet festgelegt werden. Sofern das erfindungsgemäße Verfahren beim Schritt S5 nicht enden soll wird zurück zum Schritt S2 verzweigt. Anderenfalls endet das Verfahren beim Schritt S6.FIG. 3 shows a flowchart which illustrates an embodiment of the method according to the invention. The embodiment of the method according to the invention shown in FIG. 3, which can be applied to the piezoelement 76 of FIG. 2, begins in step S1. Subsequently, at step S2, an external voltage is applied to the piezoelectric element 76 to close the control valve 22. As soon as the fuel delivery end has been reached, the process continues with step S3. In step S3, the external voltage is removed or lowered by the piezoelectric element 76 to open the control valve 22. Subsequently, the resulting force is detected via an electrical variable on the piezoelectric element 76, for example via the voltage applied to the piezoelectric element 76. Subsequently, in step S4, the detected force or the detected force curve in the actuator chamber 74 is compared with a desired force or a desired force curve. Furthermore, a new value for the external voltage is determined, for example by setting offset values appropriately. If the method according to the invention is not to end in step S5, a branch is made back to step S2. Otherwise, the process ends at step S6.

Die Erfindung lässt sich wie folgt zusammenfassen: Die Erfindung betrifft ein Verfahren und eine Vorrichtung 80 zur Ansteuerung des Steuerventils 22 einer Pumpe-Düse-Einheit. Insbesondere um bei niedrigen Motordrehzahlen hohe Druckgradienten bei der Ventilabsteuerung zu vermeiden, wird die Lagegenauigkeit von Ventilteilhüben durch eine Regelung, insbesondere eine adaptive Regelung, verbessert.The invention can be summarized as follows: The invention relates to a method and a device 80 for controlling the control valve 22 of a pump-nozzle unit. In particular, in order to avoid high pressure gradients in valve deactivation at low engine speeds, the positional accuracy of valve part strokes is improved by a control, in particular an adaptive control.

Die in der vorstehenden Beschreibung, in den Zeichnungen sowie in den Ansprüchen offenbarten Merkmale der Erfindung können sowohl einzeln als auch in beliebiger Kombination für die Verwirklichung der Erfindung wesentlich sein.The features of the invention disclosed in the foregoing description, in the drawings and in the claims may be essential to the realization of the invention both individually and in any combination.

Claims (9)

  1. Method for controlling a control valve (22) of a pump-nozzle unit, the control valve (22) having at least one movable element (48) which can be moved into a first end position in order to close the control valve (22), and can be moved into a second end position in order to completely open the control valve (22), a closed-loop control process, in particular an adaptive closed-loop control process, being used to set at least one intermediate position of the at least one movable element (48), at least temporarily, characterized in that a resulting force and/or a resulting force profile owing to a pressure within at least one region (50, 74) of the control valve (22), in particular a pressure and/or pressure profile which occurs within the at least one region (50, 74) when the control valve (22) opens, is used as the closed-loop control variable for performing closed-loop control, and in that the pressure and/or the pressure profile within the at least one region (50, 74) of the control valve (22) is sensed by means of a piezo element (76).
  2. Method according to Claim 1, characterized in that the control valve (22) is actuated by electrical actuation of a piezo element (76) for the at least one movable element (48).
  3. Method according to Claim 2, characterized in that the pressure is sensed by means of a voltage which is applied to the piezo element (76).
  4. Method according to Claim 3, characterized in that the manipulated variable for the closed-loop control process is an electrical variable with which the actuator element (76) is electrically actuated.
  5. Method according to one of Claims 1 to 4, characterized in that the pressure and/or pressure profile which is sensed within the at least one region (50, 74) of the control valve (22) during a current opening process of the control valve (22), for the current opening process and/or for at least one subsequent opening process, is included in the closed-loop control process, in particular in the form of offset values of at least one electrical variable with which an electrical actuator element (76) of the control valve is actuated.
  6. Device for controlling a control valve (22) of a pump-nozzle unit, the control valve (22) having at least one movable element (48) which can be moved into a first end position in order to close the control valve (22), and can be moved into a second end position in order to completely open the control valve (22), the device having a closed-loop control process, in particular an adaptive closed-loop control process, for setting at least one intermediate position of the at least one movable element (48), at least temporarily, characterized in that a resulting force and/or a resulting force profile owing to a pressure within at least one region (50, 74) of the control valve (22), in particular a pressure and/or pressure profile which occurs within the at least one region (50, 74) when the control valve (22) opens, is used as the closed-loop control variable for performing closed-loop control, and in that the pressure and/or the pressure profile within the at least one region (50, 74) of the control valve (22) is sensed by means of a piezo element (76).
  7. Device according to Claim 6, characterized in that the control valve (22) can be actuated by electrically actuating a piezo element (76) for the at least one movable element (48).
  8. Device according to Claim 7, characterized in that in order to carry out the closed-loop control process it is possible to use an electrical variable as the manipulated variable with which the actuator element (76) can be electrically actuated.
  9. Device according to one of Claims 6 to 8, characterized in that it can include the pressure and/or pressure profile sensed within the at least one region (50, 74) of the control valve (22) during a current opening process of the control valve (22), for the current opening process and/or for at least one subsequent opening process, in the closed-loop control process, in particular in the form of offset values of at least one electrical variable with which the actuator element (76) can be actuated.
EP03708015A 2002-02-07 2003-02-03 Method and device for controlling a control valve of a pump-nozzle unit Expired - Lifetime EP1472455B1 (en)

Applications Claiming Priority (3)

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DE10205112 2002-02-07
DE10205112 2002-02-07
PCT/DE2003/000298 WO2003067074A1 (en) 2002-02-07 2003-02-03 Method and device for controlling a control valve of a pump-nozzle unit

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EP1472455A1 EP1472455A1 (en) 2004-11-03
EP1472455B1 true EP1472455B1 (en) 2006-10-04

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DE102004024926A1 (en) 2004-05-19 2005-12-15 Volkswagen Mechatronic Gmbh & Co. Kg Pump-nozzle unit

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DE10024662A1 (en) * 2000-05-18 2001-12-06 Siemens Ag Injection valve, has control circuit for actuator that is also used as sensor to measure pressure in control chamber that controls nozzle needle to adjust operation state of injection valve

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JPS62150070A (en) * 1985-12-24 1987-07-04 Nippon Denso Co Ltd Fuel injection device
JPH07117012B2 (en) * 1986-09-05 1995-12-18 トヨタ自動車株式会社 Unit Injector
JP2523759B2 (en) 1987-02-04 1996-08-14 フエスト − アルピネ オウトモチブ ゲゼルシャフト ミットベシュレンクテル ハフツンク Fuel injection nozzle
JP2636379B2 (en) * 1988-11-07 1997-07-30 トヨタ自動車株式会社 Fuel injection device
DE19835494C2 (en) 1998-08-06 2000-06-21 Bosch Gmbh Robert Pump-nozzle unit
DE19939457A1 (en) * 1999-08-20 2001-03-01 Bosch Gmbh Robert Hydraulic control device
GB9923823D0 (en) * 1999-10-09 1999-12-08 Lucas Industries Ltd Fuel injector
DE10035814A1 (en) * 2000-07-22 2002-01-31 Bosch Gmbh Robert Method for controlling an injection valve for fuel injection into an internal combustion engine

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DE10024662A1 (en) * 2000-05-18 2001-12-06 Siemens Ag Injection valve, has control circuit for actuator that is also used as sensor to measure pressure in control chamber that controls nozzle needle to adjust operation state of injection valve

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