WO2001014714A1 - Method for controlling fuel injection valves - Google Patents

Method for controlling fuel injection valves Download PDF

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Publication number
WO2001014714A1
WO2001014714A1 PCT/DE2000/002671 DE0002671W WO0114714A1 WO 2001014714 A1 WO2001014714 A1 WO 2001014714A1 DE 0002671 W DE0002671 W DE 0002671W WO 0114714 A1 WO0114714 A1 WO 0114714A1
Authority
WO
WIPO (PCT)
Prior art keywords
valve member
fuel
stroke
valve
pressure
Prior art date
Application number
PCT/DE2000/002671
Other languages
German (de)
French (fr)
Inventor
Katsuoki Itoh
Original Assignee
Robert Bosch Gmbh
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch Gmbh filed Critical Robert Bosch Gmbh
Priority to EP00962211A priority Critical patent/EP1210514A1/en
Priority to JP2001518563A priority patent/JP2003507640A/en
Publication of WO2001014714A1 publication Critical patent/WO2001014714A1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/24—Fuel-injection apparatus with sensors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a method for controlling
  • the device used for this purpose has a valve element actuated by a piezo, which closes or opens a control chamber to a drain container.
  • Characteristic of such a device are always an inlet throttle upstream of the valve member and an outlet throttle arranged in the connection between the valve member and an outlet container.
  • the geometric design of the inlet and outlet throttle and their relationship to each other can be used to influence the opening speed of the fuel metering valve needle, which is indirectly connected to the valve member via the control chamber, when the control chamber is relieved.
  • the closing speed of the valve needle is determined by the design of the inlet throttle.
  • valve member serves essentially as a blocking member towards the drain tank, the valve member only having to assume two positions, an open and a closed position.
  • valve member acts as a variable throttle, which serves to influence the rising edge of the injection valve member stroke as a function of operating conditions and thus to generate optimal stroke profiles of the injection valve member.
  • the method according to the invention is particularly advantageous when it works as a closed control loop, so that a comparison between the optimal and actual stroke profile is made possible.
  • the method according to the invention can serve to compensate for temperature-dependent leakages in the hydraulic translator.
  • FIG. 1 shows a schematic illustration of a fuel injection device
  • FIG. 2 shows a part of an injection valve in longitudinal section
  • 3 shows a representation of the stroke profiles of a valve body as a function of the control voltage of a piezo.
  • FIG. 1 shows a fuel injection valve 10 in a simplified representation, which has an injection valve housing 12 with a stepped bore 13 in which one
  • Valve needle is guided as an injection valve member 15. This has at one end a conical sealing surface 16 which cooperates with a conical valve seat 17 at the end of the stepped bore 13. Fuel injection openings 18 are arranged downstream of the valve seat 17 and are separated from a pressure chamber 19 when the sealing surface 16 is placed on the valve seat 17. The pressure chamber 19 extends over an annular space 22 which is formed around the part 21 of the injection valve sleeve 15 which adjoins the sealing surface 16 upstream and is provided with a smaller diameter, up to the valve seat 17.
  • the pressure chamber 19 is connected via a pressure line 23 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 24, which is supplied, for example, by a high-pressure pump 25, which delivers a variable delivery rate, from a reservoir 27 with fuel which is brought to the injection pressure.
  • the high-pressure fuel reservoir 24 supplies several of the fuel injection valves 10 shown.
  • Such a fuel injection system is referred to as a “common rail system”.
  • the part 21 of the injection valve sleeve 15 with a smaller diameter merges with a pressure shoulder 28 facing the valve seat 17 part 29 of the injector valve part 15 with a larger diameter, which is in the stepped Bore 13 guided tightly and settles on the side facing away from the pressure shoulder 28 in an intermediate part 30 up to a piston-shaped end 31 of the
  • Injector güeds 15 continued. In the area of the intermediate part 30, this has a spring plate 32, between which and the injection valve housing 12 a compression spring 33 is clamped, which acts on the injection valve member 15 in the closed position.
  • a displacement or stroke sensor 26 is arranged between the spring plate 32 and the part 29 at the level of the intermediate part 30 in the bore 13, which detects the stroke h of the injection valve member 15 and feeds it to a control device as an input value.
  • the piston-shaped end 31 of the injector 15 delimits an end face 34, the area of which is larger than that of the pressure shoulder 28 in the injector housing 12, a control chamber 35.
  • the control chamber 35 is in constant communication with the inlet throttle 36
  • control chamber 35 is connected to a relief chamber 39, which can also be the reservoir 27, for example, via an outlet channel 38 and an outlet throttle 37.
  • the passage of the drain channel 38 is controlled by a control valve 40, which is designed as a 2/2 way valve.
  • the fuel injection valve 10 is shown in more detail in FIG.
  • the control valve 40 is at least partially integrated in the injection valve housing 12.
  • the control valve 40 has a valve tappet 42 which is slidably guided in a bore 43 aligned with the bore 13.
  • the drain channel 38 also branches off from the bore 43.
  • the end of the valve tappet 42 facing the control chamber 35 has a valve member 44 with a conical sealing surface 45 on.
  • the valve member 44 is arranged in a spring chamber 46, which is connected to the control chamber 35 via a connecting channel 47.
  • the outlet throttle 37 is also arranged in the connecting channel 47.
  • a seat edge 48 (a conical seat surface is also conceivable) is formed between the spring chamber 46 and the bore 43 and forms a sealing seat with the sealing surface 45.
  • a compression spring 50 is arranged which acts on the valve member 44 in the direction of the seat edge 48.
  • valve tappet 42 opens into a pressure medium chamber 54 which acts as a hydraulic booster 53 and is filled with fuel.
  • the valve tappet 42 is sealingly guided in the bore 43 except for temperature-dependent leaks, while between the seat edge 48 and the drain channel 38, for example, a gap or an annular space 51 between the valve tappet 42 and the
  • the pressure medium space 54 has a diameter that is larger than the diameter of the bore 43.
  • a plunger 56 which is coupled to a piezo 57, plunges into the open end face of the pressure medium space 54 opposite the bore 43.
  • the control valve 40 is mainly formed from the valve member 44, the hydraulic booster 53 and the piezo 57.
  • the control of the fuel injection valve 10 via the control valve 40 or the piezo 57 takes place via a control unit 58 which controls the control valves 40 of the individual fuel injection valves 10 as a function of operating parameters, and also the pressure p in the high-pressure fuel accumulator 24 with a pressure sensor 59 detected and controls the variable delivery high pressure pump 25 according to the deviation from a desired setpoint.
  • a pressure limiting valve 60 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply.
  • the high-pressure pump 25 can also continuously deliver in the same quantity and the pressure p in the high-pressure fuel accumulator 24 can be regulated via the pressure-limiting valve 60, which is to be regarded here explicitly as a pressure control valve.
  • control valve 40 With control valve 40 closed, i.e. When the piezo 57 is not actuated, the compression spring 50 presses the valve member 44 with its sealing surface 45 against the seat edge 48. Due to the constant connection of the control chamber 35 to the high-pressure fuel accumulator 24, the pressure prevailing in the control chamber 35 is at a high level. Because the area of the end face 34 is larger than the area of the pressure shoulder 28, and the pressure acting on both areas is the same at the moment, there is a resulting force supported by the compression spring 33, which
  • Injection valve member 15 holds in the closed position with respect to the fuel injection openings 18.
  • the piezo 57 is controlled by the control unit 58. This control of the piezo 57 takes place by means of a rectangular voltage pulse U, the duration of which is t.
  • the control of the piezo 57 causes the plunger 56 to be immersed more in the hydraulic intensifier 53 or the pressure medium chamber 54.
  • the valve member 44 begins in the direction of Control chamber 35 to move When lifting the sealing surface 45 of the valve güed 44 from the seat edge 48, an annular gap is formed.
  • the size of the annular gap and thus the amount of fuel flowing out through the annular gap to the drain channel 38 is proportional to the stroke of the valve güed 44 46 outflowing fuel, the control chamber 35 can be relieved to the relief chamber 39, so that, decoupled from the high-pressure fuel reservoir 24 by the inlet throttle 36, s ch in the control chamber 35 sets a lower pressure level.
  • the pressure forces acting on the pressure shoulder 28 m opening opening predominate and the fuel injection valve 10 is opened for injection by the injection valve member 15 executing a stroke h and thereby lifting off the valve seat 17.
  • the stroke movement of the injection valve member 15, ie the stroke h, is detected by the stroke sensor 26 and fed to the control device 58 as an input value.
  • the control device 58 is supplied with other operating parameters, such as the pressure p in the high-pressure fuel reservoir 24 (by means of the pressure sensor 59), the engine speed n, the load 1, etc., as input variables.
  • the control unit 58 uses these input variables to determine an optimal stroke profile h of the injection valve member 15, reference being made to FIG. 3 for a more detailed explanation: there are two different stroke profiles h1 and h2 of the injection valve member 15 for each injection process and the corresponding voltage pulses U1 and U2 through the Control device 58 shown on the piezo 57.
  • Each stroke course hl, h2 is divided into three sections a, b and c.
  • Section a identifies the rising flank during the opening of the injection valve member 15, section b the fully opened injection valve member 15 and section c the Closing movement of the injection valve member 15. While the size of the stroke h in section b and the course of section c cannot be changed or can hardly be changed for geometric or fluidic reasons (because of the flow restrictor 37), the course of section a is via a variation of the voltage U and the time period t can be changed, it being assumed in FIG. 3 for simplicity that the injection valve member 15 opens completely in each case with the stroke profiles h1 and h2.
  • the end of the injection process is initiated by not energizing the piezo 57 (end of the Voltage pulse U).
  • the control valve 40 or the piezo 57 By reclosing the control valve 40 or the piezo 57, the original high fuel pressure is quickly restored in the control chamber 35, since the fuel can continue to flow via the inlet throttle 36. As a result, the injection valve member 15 returns to its initial position or closed position to terminate the

Abstract

The invention relates to a method for controlling fuel injection valves, particularly for use in diesel internal combustion engines. The device used for carrying out the method has fuel injection valves (10) that are supplied with fuel by a high pressure fuel accumulator (24). Each fuel injection valve (10) has a needle-shaped injection valve mechanism (15) which is coupled with a control chamber (35), said control chamber being connected to the high pressure fuel accumulator by a supply throttle (36). The control chamber (35) is able to drain into a draining container (39) by means of a valve mechanism (44) that is actuated by a piezo actuator (57). According to the invention, the characteristic of the leading edge (a) of the stroke course (h) of the injection valve mechanism (15) is regulated by controlling the piezo actuator (57). A closed regulating circuit is formed with a stroke sensor (26) and a control device (58). The inventive method enables e.g. temperature-related leakage on a hydraulic transmission mechanism (53) to be compensated.

Description

VERFAHREN ZUM STEUERN VON KRAFTSTOFFEINSPRITZVENTILENMETHOD FOR CONTROLLING FUEL INJECTION VALVES
Stand der TechnikState of the art
Die Erfindung betrifft ein Verfahren zum Steuern vonThe invention relates to a method for controlling
Flüssigkeiten nach dem Oberbegriff des Anspruchs 1, wie es aus der DE 198 26 339 AI bekannt ist. Die dazu verwendete Vorrichtung weist ein von einem Piezo betätigtes Ventilglied auf, das einen Steuerraum zu einem Abflußbehälter hin verschließt oder öffnet. Charakteristisch für eine derartige Vorrichtung sind stets eine dem Ventilglied vorgeschaltete Zulaufdrossel sowie eine in der Verbindung zwischen dem Ventilglied und einem Abflußbehälter angeordnete Ablaufdrossel . Über die geometrische Ausbildung der Zulauf- und Ablaufdrossel und deren Verhältnis zueinander lässt sich beim Entlasten des Steuerraums die Öffnungsgeschwindigkeit der den Kraftstoff dosierenden, über den Steuerraum mit dem Ventilglied mittelbar verbundenen Ventilnadel beeinflussen. Ferner wird durch die Ausbildung der Zulaufdrossel die Schließgeschwindigkeit der Ventilnadel bestimmt. DasLiquids according to the preamble of claim 1, as is known from DE 198 26 339 AI. The device used for this purpose has a valve element actuated by a piezo, which closes or opens a control chamber to a drain container. Characteristic of such a device are always an inlet throttle upstream of the valve member and an outlet throttle arranged in the connection between the valve member and an outlet container. The geometric design of the inlet and outlet throttle and their relationship to each other can be used to influence the opening speed of the fuel metering valve needle, which is indirectly connected to the valve member via the control chamber, when the control chamber is relieved. Furthermore, the closing speed of the valve needle is determined by the design of the inlet throttle. The
Ventilglied dient bei dem bekannten Verfahren zum Steuern von Flüssigkeiten im wesentlichen als Sperrglied zum Abflußbehälter hin, wobei das Ventilglied lediglich zwei Stellungen einnehmen muß, eine Öffnungs- und eine Schließstellung. Vorteile der ErfindungIn the known method for controlling liquids, valve member serves essentially as a blocking member towards the drain tank, the valve member only having to assume two positions, an open and a closed position. Advantages of the invention
Das erfindungsgemäße Verfahren zum Steuern von Flüssigkeiten mit den kennzeichnenden Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß das Ventilglied als variable Drossel wirkt, die dazu dient, die Anstiegsflanke des Einspritzventilgliedhubes in Abhängigkeit von Betriebszuständen zu beeinflussen um somit optimale Hubverläufe des Einspritzventilgliedes zu erzeugen.The method according to the invention for controlling liquids with the characterizing features of claim 1 has the advantage that the valve member acts as a variable throttle, which serves to influence the rising edge of the injection valve member stroke as a function of operating conditions and thus to generate optimal stroke profiles of the injection valve member.
Weitere vorteilhafte Weiterbildungen des erfindungsgemäßen Verfahrens zum Steuern von Flüssigkeiten sind in den Unteransprüchen angegeben.Further advantageous developments of the method according to the invention for controlling liquids are specified in the subclaims.
Besonders vorteilhaft ist das erfindungsgemäße Verfahren wenn es als geschlossener Regelkreis arbeitet, so daß ein Vergleich zwischen optimalem und tatsächlichem Hubverlauf ermöglicht wird.The method according to the invention is particularly advantageous when it works as a closed control loop, so that a comparison between the optimal and actual stroke profile is made possible.
Im Zusammenhang mit einem hydraulischen Übersetzer kann das erfindungsgemäße Verfahren dazu dienen, temperaturabhängige Leckagen des hydraulischen Übersetzers zu kompensieren.In connection with a hydraulic translator, the method according to the invention can serve to compensate for temperature-dependent leakages in the hydraulic translator.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung dargestellt und wird nachfolgend näher erläutert. Es zeigen:An embodiment of the invention is shown in the drawing and is explained in more detail below. Show it:
Figur 1 eine schematische Darstellung einer Kraftstoffeinspritzvorrichtung, Figur 2 einen Teil eines Einspritzventils im Längs- schnitt und Figur 3 eine Darstellung von Hubverläufen eines Ventilkörpers in Abhängigkeit von der Ansteuerspannung eines Piezos.1 shows a schematic illustration of a fuel injection device, FIG. 2 shows a part of an injection valve in longitudinal section and 3 shows a representation of the stroke profiles of a valve body as a function of the control voltage of a piezo.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Figur 1 zeigt ein Kraftstoffeinspritzventil 10 in vereinfachter Darstellung, das ein Einspritzventilgehäuse 12 mit einer gestuften Bohrung 13 aufweist, in der eineFIG. 1 shows a fuel injection valve 10 in a simplified representation, which has an injection valve housing 12 with a stepped bore 13 in which one
Ventilnadel als Einspritzventilglied 15 geführt ist. Dieses weist an seinem einen Ende eine kegelförmige Dichtfläche 16 auf, die mit einem kegelförmigen Ventilsitz 17 am Ende der gestuften Bohrung 13 zusammenwirkt. Stromabwärts des Ventilsitzes 17 sind Kraftstoffeinspritzöffnungen 18 angeordnet, die beim Aufsetzen der Dichtfläche 16 auf dem Ventilsitz 17 von einem Druckraum 19 getrennt werden. Der Druckraum 19 erstreckt sich über einen um den sich an die Dichtfläche 16 stromaufwärts anschließenden, mit kleinerem Durchmesser versehenen Teil 21 des Einspritzventilgüeds 15 herum gebildeten Ringraum 22 bis zum Ventilsitz 17 hin. Der Druckraum 19 ist über eine Druckleitung 23 mit einer Kraftstoffhochdruckquelle in Form eines Kraftstoffhochdruckspeichers 24 verbunden, der zum Beispiel von einer mit variabler Förderrate fördernden Hochdruckpumpe 25 aus einem Vorratsbehälter 27 mit Kraftstoff, der auf Einspritzdruck gebracht ist, versorgt wird. Der Kraftstoffhochdruckspeicher 24 versorgt dabei mehrere der gezeigten Kraftstoffeinspritzventile 10. Es derartiges Kraftstoffeinspritzsystem wird als „Common-Rail-System" bezeichnet. Im Bereich des Druckraums 19 geht der im Durchmesser kleinere Teil 21 des Einspritzventilgüeds 15 mit einer zum Ventilsitz 17 weisenden Druckschulter 28 in einen im Durchmesser größeren Teil 29 des Einspritzventilgüeds 15 über. Dieser ist in der gestuften Bohrung 13 dicht geführt und setzt sich auf der der Druckschulter 28 abgewandten Seite in einem Zwischenteil 30 bis hin zu einem kolbenförmigen Ende 31 desValve needle is guided as an injection valve member 15. This has at one end a conical sealing surface 16 which cooperates with a conical valve seat 17 at the end of the stepped bore 13. Fuel injection openings 18 are arranged downstream of the valve seat 17 and are separated from a pressure chamber 19 when the sealing surface 16 is placed on the valve seat 17. The pressure chamber 19 extends over an annular space 22 which is formed around the part 21 of the injection valve sleeve 15 which adjoins the sealing surface 16 upstream and is provided with a smaller diameter, up to the valve seat 17. The pressure chamber 19 is connected via a pressure line 23 to a high-pressure fuel source in the form of a high-pressure fuel reservoir 24, which is supplied, for example, by a high-pressure pump 25, which delivers a variable delivery rate, from a reservoir 27 with fuel which is brought to the injection pressure. The high-pressure fuel reservoir 24 supplies several of the fuel injection valves 10 shown. Such a fuel injection system is referred to as a “common rail system”. In the area of the pressure chamber 19, the part 21 of the injection valve sleeve 15 with a smaller diameter merges with a pressure shoulder 28 facing the valve seat 17 part 29 of the injector valve part 15 with a larger diameter, which is in the stepped Bore 13 guided tightly and settles on the side facing away from the pressure shoulder 28 in an intermediate part 30 up to a piston-shaped end 31 of the
Einspritzventilgüeds 15 fort. Im Bereich des Zwischenteils 30 hat dieses einen Federteller 32, zwischen dem und dem Einspritzventilgehäuse 12 eine Druckfeder 33 eingespannt ist, die das Einspritzventilglied 15 in Schließstellung beaufschlagt .Injector güeds 15 continued. In the area of the intermediate part 30, this has a spring plate 32, between which and the injection valve housing 12 a compression spring 33 is clamped, which acts on the injection valve member 15 in the closed position.
Weiterhin ist zwischen dem Federteller 32 und dem Teil 29 in Höhe des Zwischenteils 30 in der Bohrung 13 ein Weg- bzw. Hubsensor 26 angeordnet, der den Hub h des Einspritzventilgliedes 15 erfasst und einer Steuereinrichtung als Eingangswert zuführt.Furthermore, a displacement or stroke sensor 26 is arranged between the spring plate 32 and the part 29 at the level of the intermediate part 30 in the bore 13, which detects the stroke h of the injection valve member 15 and feeds it to a control device as an input value.
Das kolbenförmige Ende 31 des Einspritzventilgüeds 15 begrenzt mit einer Stirnseite 34, deren Fläche größer ist als die der Druckschulter 28 im Einspritzventilgehäuse 12 einen Steuerraum 35. Der Steuerraum 35 ist über eine Zulaufdrossel 36 in ständiger Verbindung mit demThe piston-shaped end 31 of the injector 15 delimits an end face 34, the area of which is larger than that of the pressure shoulder 28 in the injector housing 12, a control chamber 35. The control chamber 35 is in constant communication with the inlet throttle 36
Kraftstoffhochdruckspeicher 24. Gleichzeitig ist der Steuerraum 35 über einen Abflußkanal 38 und eine Ablaufdrossel 37 mit einem Entlastungsraum 39 verbunden, der zum Beispiel auch der Vorratsbehälter 27 sein kann. Der Durchgang des Abflußkanals 38 wird durch ein Steuerventil 40, das als 2/2 -Wegeventil ausgebildet ist, gesteuert.High-pressure fuel reservoir 24. At the same time, the control chamber 35 is connected to a relief chamber 39, which can also be the reservoir 27, for example, via an outlet channel 38 and an outlet throttle 37. The passage of the drain channel 38 is controlled by a control valve 40, which is designed as a 2/2 way valve.
In der Figur 2 ist das Kraftstoffeinspritzventil 10 näher dargestellt. Das Steuerventil 40 ist dabei wenigstens teilweise in das Einspritzventilgehäuse 12 integriert. Das Steuerventil 40 weist einen Ventilstößel 42 auf, der in einer zur Bohrung 13 fluchtenden Bohrung 43 gleitend geführt ist. Von der Bohrung 43 zweigt auch der Abflußkanal 38 ab. Das dem Steuerraum 35 zugewandte Ende des Ventilstößels 42 weist ein Ventilglied 44 mit einer kegelförmigen Dichtfläche 45 auf. Das Ventilglied 44 ist in einem Federraum 46 angeordnet, der über einen Verbindungskanal 47 mit dem Steuerraum 35 verbunden ist. In dem Verbindungskanal 47 ist auch die Ablaufdrossel 37 angeordnet. Zwischen dem Federraum 46 und der Bohrung 43 ist eine Sitzkante 48 (es ist auch eine kegelförmige Sitzfläche denkbar) ausgebildet, die mit der Dichtfläche 45 einen Dichtsitz bildet. Zwischen der dem Steuerraum 35 zugewandten Stirnseite des Ventilglieds 44 und dem dem Verbindungskanal 47 zugewandten Boden 49 des Federraums 46 ist eine Druckfeder 50 angeordnet, die das Ventilglied 44 in Richtung der Sitzkante 48 beaufschlagt.The fuel injection valve 10 is shown in more detail in FIG. The control valve 40 is at least partially integrated in the injection valve housing 12. The control valve 40 has a valve tappet 42 which is slidably guided in a bore 43 aligned with the bore 13. The drain channel 38 also branches off from the bore 43. The end of the valve tappet 42 facing the control chamber 35 has a valve member 44 with a conical sealing surface 45 on. The valve member 44 is arranged in a spring chamber 46, which is connected to the control chamber 35 via a connecting channel 47. The outlet throttle 37 is also arranged in the connecting channel 47. A seat edge 48 (a conical seat surface is also conceivable) is formed between the spring chamber 46 and the bore 43 and forms a sealing seat with the sealing surface 45. Between the end face of the valve member 44 facing the control chamber 35 and the bottom 49 of the spring compartment 46 facing the connecting channel 47, a compression spring 50 is arranged which acts on the valve member 44 in the direction of the seat edge 48.
Die dem Ventilglied 44 gegenüberliegende Stirnfläche 52 des Ventilstößels 42 mündet in einen als hydraulischen Übersetzer 53 wirkenden Druckmittelraum 54, der mit Kraftstoff gefüllt ist. In diesem Bereich ist der Ventilstößel 42 bis auf temperaturabhängige Leckagen dichtend in der Bohrung 43 geführt, während zwischen der Sitzkante 48 und dem Abflußkanal 38 zum Beispiel ein Spalt oder ein Ringraum 51 zwischen dem Ventilstößel 42 und derThe end face 52 of the valve tappet 42 opposite the valve member 44 opens into a pressure medium chamber 54 which acts as a hydraulic booster 53 and is filled with fuel. In this area, the valve tappet 42 is sealingly guided in the bore 43 except for temperature-dependent leaks, while between the seat edge 48 and the drain channel 38, for example, a gap or an annular space 51 between the valve tappet 42 and the
Bohrung 43 ausgebildet ist, um das Abfließen von Kraftstoff zu ermöglichen. Der Druckmittelraum 54 weist einen Durchmesser auf, der größer ist als der Durchmesser der Bohrung 43. In die der Bohrung 43 gegenüberliegende offene Stirnseite des Druckmittelraums 54 taucht ein Stößel 56 ein, der mit einem Piezo 57 gekoppelt ist. Somit wird das Steuerventil 40 hauptsächlich gebildet aus dem Ventilglied 44, dem hydraulischen Übersetzer 53 und dem Piezo 57.Bore 43 is formed to allow fuel to flow away. The pressure medium space 54 has a diameter that is larger than the diameter of the bore 43. A plunger 56, which is coupled to a piezo 57, plunges into the open end face of the pressure medium space 54 opposite the bore 43. Thus, the control valve 40 is mainly formed from the valve member 44, the hydraulic booster 53 and the piezo 57.
Die Ansteuerung des Kraftstoffeinspritzventils 10 über das Steuerventil 40 bzw. den Piezo 57 erfolgt über ein Steuergerät 58, das in Abhängigkeit von Betriebsparametern die Steuerventile 40 der einzelnen Kraftstoffeinspritzventile 10 ansteuert, ferner mit einem Drucksensor 59 den Druck p im Kraftstoffhochdruckspeicher 24 erfaßt und entsprechend der Abweichung von einem gewünschten Sollwert die variabel fördernde Hochdruckpumpe 25 steuert. Parallel zu dieser kann ein Druckbegrenzungsventil 60 vorgesehen sein, das auch als Drucksteuerventil in Abhängigkeit von Betriebsparametern steuerbar ist, je nach Konzeption der Kraftstoffhochdruckmengenversorgung . Auch kann die Hochdruckpumpe 25 ständig in gleicher Menge fördern und über das Druckbegrenzungsventil 60, das hier explizit als Drucksteuerventil anzusehen ist, der Druck p im Kraftstoffhochdruckspeicher 24 eingeregelt werden.The control of the fuel injection valve 10 via the control valve 40 or the piezo 57 takes place via a control unit 58 which controls the control valves 40 of the individual fuel injection valves 10 as a function of operating parameters, and also the pressure p in the high-pressure fuel accumulator 24 with a pressure sensor 59 detected and controls the variable delivery high pressure pump 25 according to the deviation from a desired setpoint. In parallel with this, a pressure limiting valve 60 can be provided, which can also be controlled as a pressure control valve depending on operating parameters, depending on the design of the high-pressure fuel supply. The high-pressure pump 25 can also continuously deliver in the same quantity and the pressure p in the high-pressure fuel accumulator 24 can be regulated via the pressure-limiting valve 60, which is to be regarded here explicitly as a pressure control valve.
Die oben beschriebene Kraftstoffeinspritzvorrichtung, die insbesondere Bestandteil einer Dieselbrennkraftmaschine ist, arbeitet wie folgt:The fuel injection device described above, which is in particular part of a diesel engine, works as follows:
Bei geschlossenem Steuerventil 40, d.h. nicht betätigtem Piezo 57 drückt die Druckfeder 50 das Ventilglied 44 mit seiner Dichtfläche 45 gegen die Sitzkante 48. Aufgrund der ständigen Verbindung des Steuerraums 35 mit dem Kraftstoffhochdruckspeicher 24 ist der im Steuerraum 35 herrschende Druck auf hohem Niveau. Weil die Fläche der Stirnseite 34 größer ist als die Fläche der Druckschulter 28, und der auf beiden Flächen wirkende Druck in dem Moment gleich groß ist, ergibt sich eine resultierende, durch die Druckfeder 33 unterstützte Kraft, die dasWith control valve 40 closed, i.e. When the piezo 57 is not actuated, the compression spring 50 presses the valve member 44 with its sealing surface 45 against the seat edge 48. Due to the constant connection of the control chamber 35 to the high-pressure fuel accumulator 24, the pressure prevailing in the control chamber 35 is at a high level. Because the area of the end face 34 is larger than the area of the pressure shoulder 28, and the pressure acting on both areas is the same at the moment, there is a resulting force supported by the compression spring 33, which
Einspritzventilglied 15 in geschlossener Stellung in bezug auf die Kraftstoffeinspritzöffnungen 18 hält.Injection valve member 15 holds in the closed position with respect to the fuel injection openings 18.
Zur Auslösung einer Einspritzung wird der Piezo 57 vom Steuergerät 58 angesteuert. Diese Ansteuerung des Piezos 57 erfolgt mittels eines rechteckförmigen Spannungsimpulses U, dessen Dauer t beträgt. Die Ansteuerung des Piezos 57 bewirkt, daß der Stößel 56 stärker in den hydraulischen Übersetzer 53 bzw. den Druckmittelraum 54 eintaucht. Infolge dessen beginnt auch das Ventilglied 44 sich in Richtung des Steuerraums 35 zu bewegen Beim Abheben der Dichtflache 45 des Ventilgüeds 44 von der Sitzkante 48 wird dabei ein Ringspalt gebildet Die Große des Ringspalts und somit die durch den Ringspalt zum Abflußkanal 38 abströmende Kraftstoffmenge ist dabei proportional zum Hub des Ventilgüeds 44. Durch den über den Federraum 46 abströmenden Kraftstoff kann der Steuerraum 35 zum Entlastungsraum 39 entlastet werden, so daß, abgekoppelt vom Kraftstoffhochdruckspeicher 24 durch die Zulaufdrossel 36, s ch im Steuerraum 35 ein Druck niedrigeren Niveaus einstellt. In diesem Fall überwiegen d e auf die Druckschulter 28 m Offnungsπchtung wirkenden Druckkräfte und das Kraftstoffemspπtzventil 10 wird zur Einspritzung geöffnet, indem das Emspritzventilglied 15 einen Hub h ausfuhrt und dabei von dem Ventilsitz 17 abhebt.To trigger an injection, the piezo 57 is controlled by the control unit 58. This control of the piezo 57 takes place by means of a rectangular voltage pulse U, the duration of which is t. The control of the piezo 57 causes the plunger 56 to be immersed more in the hydraulic intensifier 53 or the pressure medium chamber 54. As a result, the valve member 44 begins in the direction of Control chamber 35 to move When lifting the sealing surface 45 of the valve güed 44 from the seat edge 48, an annular gap is formed. The size of the annular gap and thus the amount of fuel flowing out through the annular gap to the drain channel 38 is proportional to the stroke of the valve güed 44 46 outflowing fuel, the control chamber 35 can be relieved to the relief chamber 39, so that, decoupled from the high-pressure fuel reservoir 24 by the inlet throttle 36, s ch in the control chamber 35 sets a lower pressure level. In this case, the pressure forces acting on the pressure shoulder 28 m opening opening predominate and the fuel injection valve 10 is opened for injection by the injection valve member 15 executing a stroke h and thereby lifting off the valve seat 17.
Wesentlich dabei ist, daß die Hubbewegung des Emspritzventilgliedes 15, d.h. der Hub h von dem Hubsensor 26 erfasst, und dem Steuergerat 58 als Eingangswert zugeführt wird. Weiterhin werden dem Steuergerat 58 andere Betriebsparameter, wie beispielsweise der Druck p im Kraftstoffhochdruckspeicher 24 (mittels des Drucksensors 59), die Drehzahl n des Motors, die Last 1 usw. als Eingangsgrößen zugeführt. Mittels dieser Eingangsgroßen ermittelt das Steuergerät 58 einen optimalen Hubverlauf h des Emspritzventilgliedes 15, wobei zur näheren Erläuterung auf die Figur 3 verwiesen wird: Dort sind zwei verschiedene Hubverlaufe hl und h2 des Emspritzventilgliedes 15 für jeweils einen Einspritzvorgang sowie die entsprechenden SpannungsImpulse Ul und U2 durch das Steuergerat 58 an den Piezo 57 dargestellt. Jeder Hubverlauf hl, h2 gliedert sich m drei Abschnitte a, b und c. Der Abschnitt a kennzeichnet die Anstiegstlanke wahrend des Öffnens des Emspritzventilgliedes 15, der Abschnitt b das vollständig geöffnete Emspritzventilglied 15 und der Abschnitt c die Schließbewegung des Einspritzventilgliedes 15. Während die Größe des Hubes h im Abschnitt b sowie der Verlauf des Abschnitts c aus geometrischen bzw. strömungstechnischen Gründen (der Ablaufdrossel 37 wegen) nicht oder kaum veränderbar sind, ist der Verlauf des Abschnitts a über eine Variation der Spannung U und der Zeitspanne t veränderbar, wobei in der Figur 3 der Einfachheit davon ausgegangen wird, daß das Einspritzventilglied 15 bei den Hubverläufen hl und h2 jeweils vollständig öffnet. Es ist ersichtlich, daß beim Hubverlauf h2 , bei dem der Spannungsimpuls U größer ist und länger andauert, die Anstiegstlanke steiler verläuft und der Maximalhub früher erreicht wird und länger andauert. Dabei wird der jeweils erreichte Hubverlauf h, insbesondere der Abschnitt a, mittels des Hubsensors 26 erfasst und infolge des geschlossenen Regelkreises vom Steuergerät 58 auf den Sollverlauf eingeregelt .It is essential here that the stroke movement of the injection valve member 15, ie the stroke h, is detected by the stroke sensor 26 and fed to the control device 58 as an input value. Furthermore, the control device 58 is supplied with other operating parameters, such as the pressure p in the high-pressure fuel reservoir 24 (by means of the pressure sensor 59), the engine speed n, the load 1, etc., as input variables. The control unit 58 uses these input variables to determine an optimal stroke profile h of the injection valve member 15, reference being made to FIG. 3 for a more detailed explanation: there are two different stroke profiles h1 and h2 of the injection valve member 15 for each injection process and the corresponding voltage pulses U1 and U2 through the Control device 58 shown on the piezo 57. Each stroke course hl, h2 is divided into three sections a, b and c. Section a identifies the rising flank during the opening of the injection valve member 15, section b the fully opened injection valve member 15 and section c the Closing movement of the injection valve member 15. While the size of the stroke h in section b and the course of section c cannot be changed or can hardly be changed for geometric or fluidic reasons (because of the flow restrictor 37), the course of section a is via a variation of the voltage U and the time period t can be changed, it being assumed in FIG. 3 for simplicity that the injection valve member 15 opens completely in each case with the stroke profiles h1 and h2. It can be seen that in the course of the stroke h2, in which the voltage pulse U is greater and lasts longer, the rising flank is steeper and the maximum stroke is reached earlier and lasts longer. The stroke progression h achieved in each case, in particular section a, is detected by means of the stroke sensor 26 and adjusted to the target progression by the control unit 58 as a result of the closed control loop.
Die Beeinflußungsmöglichkeit des Abschnitts a des Hubverlaufes h des Einspritzventilgliedes 15 ist besonders vorteilhaft anwendbar bei der Verwendung des hydraulischen Übersetzers 53. Dieser besitzt eine temperaturabhängige Leckage aufgrund der Toleranzen der in den hydraulischen Übersetzer 53 eintauchenden Stößel 56 und Ventilstößel 42. Daraus ergibt sich, daß bei einer größeren Leckage die Anstiegsflanke bzw. der Abschnitt a flacher verläuft. Dieser Effekt kann nunmehr durch eine Erhöhung des Spannungsimpulses U, und falls erforderlich durch eine Variation der Zeitdauer t, kompensiert werden. Wichtig dabei ist, daß über die Rückkopplung mittels des Hubsensors 26 an das Steuergerät 58 ein geschlossener Regelkreis ausgebildet wird. Somit können temperaturunabhängig optimale Abschnittsverläufe a erzeugt werden.The possibility of influencing the section a of the stroke profile h of the injection valve member 15 can be used particularly advantageously when using the hydraulic booster 53. This has a temperature-dependent leakage due to the tolerances of the plunger 56 and valve plunger 42 immersed in the hydraulic booster 53. This results in that at a larger leak, the rising flank or section a runs flatter. This effect can now be compensated for by increasing the voltage pulse U and, if necessary, by varying the time period t. It is important here that a closed control loop is formed via the feedback by means of the stroke sensor 26 to the control device 58. In this way, optimum section profiles a can be generated regardless of the temperature.
Die Beendigung des Einspritzvorganges wird durch ein Nichtbestromen des Piezos 57 eingeleitet (Ende des Spannungsimpulses U) . Durch Wiederschließen des Steuerventils 40 bzw. des Piezos 57 stellt sich im Steuerraum 35 sehr schnell der ursprüngliche hohe Kraftstoffdruck wieder ein, da der Kraftstoff über die Zulaufdrossel 36 weiterhin zufließen kann. Dadurch gelangt das Einspritzventilglied 15 wieder in seine Ausgangsstellung bzw. Schließstellung zur Beendigung derThe end of the injection process is initiated by not energizing the piezo 57 (end of the Voltage pulse U). By reclosing the control valve 40 or the piezo 57, the original high fuel pressure is quickly restored in the control chamber 35, since the fuel can continue to flow via the inlet throttle 36. As a result, the injection valve member 15 returns to its initial position or closed position to terminate the
Hochdruckeinspritzung zurück (Abschnitt c) , bei der das Einspritzventilglied 15 auf dem Ventilsitz 17 aufsitzt. High pressure injection back (section c), in which the injection valve member 15 is seated on the valve seat 17.

Claims

Ansprüche Expectations
1. Verfahren zum Steuern von Flüssigkeiten, bei dem in einem Druckraum (19) unter Hochdruck stehender Kraftstoff mittels eines von einem Ventilsitz (17) abhebbaren Ventilkörpers (15) durch Spritzöffnungen (18) einer Brennkraftmaschine zugeführt wird, wobei die Bewegung des Ventilkörpers (15) über einen ebenfalls unter dem Hochdruck des Kraftstoffs stehenden Steuerraum (35) gesteuert wird, der über ein Ventilglied (44) mit einer dem Ventilglied (44) vorgeschalteten Zulaufdrossel (36) und einer Ablaufdrossel (37) zu einem Abflußbehälter (39) verbindbar ist und wobei das Ventilglied (44) zumindest mittelbar von einem Piezo (57) betätigt wird, dadurch gekennzeichnet, daß die Bewegung des Ventilgliedes (44) und die Anstiegsflanke (a) des Hubverlaufes (h) des Einspritzventilgliedes (15) in Abhängigkeit von Betriebsparametern (p, n, 1) veränderbar ist .1. A method for controlling liquids, in which fuel under high pressure in a pressure chamber (19) is supplied to an internal combustion engine through spray openings (18) by means of a valve body (15) which can be lifted off from a valve seat (17), the movement of the valve body (15 ) is controlled via a control chamber (35) which is also under the high pressure of the fuel and which can be connected via a valve member (44) to an inlet throttle (36) upstream of the valve member (44) and an outlet throttle (37) to form an outlet tank (39) and wherein the valve member (44) is actuated at least indirectly by a piezo (57), characterized in that the movement of the valve member (44) and the rising edge (a) of the stroke course (h) of the injection valve member (15) as a function of operating parameters ( p, n, 1) is changeable.
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, daß der Hubverlauf (h) des Einspritzventilgliedes (15) von einem Hubsensor (26) erfasst und einem Steuergerät (58) als Eingangsgröße zugeleitet wird, daß die Ansteuerung des Piezos (57) mittels eines Spannungsimpulses (U) erfolgt und daß der Spannungsimpuls (U) aufgrund des Hubverlaufs (h) regelbar ist. 2. The method according to claim 1, characterized in that the stroke profile (h) of the injection valve member (15) is detected by a stroke sensor (26) and fed to a control device (58) as an input variable that the control of the piezo (57) by means of a voltage pulse (U) takes place and that the voltage pulse (U) can be regulated on the basis of the stroke profile (h).
3. Verfahren nach Anspruch 2, dadurch gekennzeichnet, daß der Spannungsimpuls ein Rechteckimpuls (U) ist und daß die Regelung des Rechteckimpulses (U) über dessen Höhe und Zeitdauer (t) erfolgt.3. The method according to claim 2, characterized in that the voltage pulse is a square-wave pulse (U) and that the regulation of the square-wave pulse (U) takes place over its level and duration (t).
4. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, daß die Bewegung vom Piezo (57) zum Ventilkörper (15) mittels eines hydraulischen Übersetzers4. The method according to any one of claims 1 to 3, characterized in that the movement from the piezo (57) to the valve body (15) by means of a hydraulic translator
(53) übertragen wird. (53) is transferred.
PCT/DE2000/002671 1999-08-20 2000-08-10 Method for controlling fuel injection valves WO2001014714A1 (en)

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JP2001518563A JP2003507640A (en) 1999-08-20 2000-08-10 Liquid control method

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DE102007033469A1 (en) * 2007-07-18 2009-01-22 Continental Automotive Gmbh Method and device for shaping an electrical control signal for an injection pulse

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WO2003040534A2 (en) * 2001-11-09 2003-05-15 Volkswagen Mechatronic Gmbh & Co. Internal combustion engine injection system and related operating method
WO2003040534A3 (en) * 2001-11-09 2003-09-04 Siemens Ag Internal combustion engine injection system and related operating method
DE102007033469A1 (en) * 2007-07-18 2009-01-22 Continental Automotive Gmbh Method and device for shaping an electrical control signal for an injection pulse
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DE102007033469B4 (en) * 2007-07-18 2017-06-14 Continental Automotive Gmbh Method and device for shaping an electrical control signal for an injection pulse

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