EP2052148B1 - Fuel injector with direct needle control and servo valve assistance - Google Patents

Fuel injector with direct needle control and servo valve assistance Download PDF

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Publication number
EP2052148B1
EP2052148B1 EP07730183A EP07730183A EP2052148B1 EP 2052148 B1 EP2052148 B1 EP 2052148B1 EP 07730183 A EP07730183 A EP 07730183A EP 07730183 A EP07730183 A EP 07730183A EP 2052148 B1 EP2052148 B1 EP 2052148B1
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EP
European Patent Office
Prior art keywords
control
piston
valve member
chamber
injection valve
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Not-in-force
Application number
EP07730183A
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German (de)
French (fr)
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EP2052148A1 (en
Inventor
Friedrich Boecking
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP2052148A1 publication Critical patent/EP2052148A1/en
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive 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
    • 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
    • F02M2200/704—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with actuator and actuated element moving in different directions, e.g. in opposite directions

Definitions

  • the invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1 (US Pat. WO-A-96/37698 ).
  • a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having an injector housing having a fuel inlet communicating with a central fuel high pressure source outside the injector housing and with a pressure space within the injector housing depending on the position a control valve is injected with high pressure fuel.
  • the control valve is actuated by means of a piezoelectric actuator.
  • a coupling space is formed between the control valve and the piezoelectric actuator. This acts as a hydraulic translator on the valve piston of the control valve.
  • An inventively designed injector for injecting fuel into a combustion chamber of an internal combustion engine is actuated by means of an actuator and is connected to a fuel inlet, is supplied via the standing under system pressure fuel.
  • at least one injection opening can be opened or closed by an injection valve member, wherein the injection valve member by means of a control piston is controlled via a control chamber, which is exposed to the control piston and a piston portion of the injection valve member with respective pressure surfaces.
  • the control piston is also a valve piston of a control valve.
  • the valve piston and the piston portion of the injection valve member enclose a further control chamber, which is connected with the control valve open with a fuel return and with the control valve closed to the fuel inlet.
  • a first opening phase of the injection valve member the control piston acts via the first control chamber according to the principle of direct control of the injection valve member.
  • a further opening phase of the injection valve member begins when the control piston acts as a valve piston of a servo valve and controls the further control chamber.
  • the essence of the invention lies in a combination of direct control and servo control of the injection valve member, wherein the opening of the injection valve member takes place when the actuator moves the control piston in the direction of the injection openings.
  • a further advantage of the inventively embodied injector is that the stroke of the actuator is translated so that even a short actuator is sufficient to produce a sufficiently large stroke of the injection valve member. This makes it possible to reduce the height of the injector.
  • the opening speed of the injection valve member is increased at the beginning of the opening process in comparison to the fuel injectors known from the prior art by the inventive design of the injector.
  • an annular portion is formed on the control piston, in which the piston portion of the injection valve member is guided.
  • the additional control chamber is limited by the injection valve member and the annular portion.
  • the aring-shaped portion is formed on the piston portion of the injection valve member. In the annular portion of the control piston is guided and the other control chamber is limited by the control piston and the annular portion.
  • the actuator is connected to a booster piston, wherein the booster piston defines with an end face a booster chamber, which is bounded on the opposite side by an upper end face of the control piston.
  • the ratio of the strokes of the booster piston and the control piston is proportional to the ratio the diameter. The larger the diameter of the booster piston compared to the diameter of the control chamber limiting end face of the control piston, the larger the stroke of the control piston compared to the stroke of the booster piston.
  • the control chamber which is bounded by the injection valve member and the control piston, connected by a connecting channel with a valve chamber, the Control spool encloses.
  • the valve chamber is a valve chamber of the control valve.
  • a throttle element is received in the connecting channel, through which the control chamber, which is delimited by the injection valve member and the control piston, is connected to the valve chamber.
  • the throttle element acts as a tolerance limiter in the connecting channel.
  • valve chamber of the control valve which is connected to the further control chamber via the connecting channel, is connected by means of a throttle element to the fuel inlet.
  • the injection valve member in which the injection valve member is guided in an annular portion in the control piston, define a lower end face on the annular portion of the control piston and a shoulder on the piston portion of the injection valve member, the control space.
  • the injection valve member is pushed out of this during a movement of the control piston into the control chamber.
  • This configuration has the effect that, when the actuator is energized, that is to say with an extended actuator, the control piston is moved into the control chamber and the injection valve member moves out of the control chamber through this movement of the control piston, thus lifting it out of its seat and releasing the at least one injection opening.
  • the stroke of the injection valve member in dependence on the stroke of the control piston can be adjusted.
  • the piston portion of the injection valve member has an annular portion in which the control piston is guided, define an end face on the annular portion of the piston portion of the injection valve member and a shoulder on the control piston the control chamber.
  • the function here is the same as in the embodiment in which the annular portion is formed on the control piston, and an injection valve member is guided in this annular portion on the control piston.
  • control piston in an embodiment is connected directly to the actuator.
  • the actuator is preferably housed in a housing which is made of a material whose coefficient of thermal expansion corresponds to that of the actuator. Due to the almost same coefficient of thermal expansion, the housing in which the actuator is received, preferably made of Invar, when the actuator is a piezoelectric actuator.
  • a compensation element is added in a preferred embodiment between the actuator and the housing.
  • the compensating element is made of aluminum or aluminum alloys, for example.
  • the housing is made of a material whose coefficient of thermal expansion corresponds to that of the actuator and in which a compensating element is accommodated between the housings and the actuator, by which a residual error of the coefficient of thermal expansion between actuator and housing is compensated, is particularly preferred when the spool is directly connected to the actuator. This is therefore necessary to ensure a clean closing of the control valve.
  • An optionally occurring residual error in the stroke for generating the tightness at the control valve can be compensated for example electrically.
  • FIG. 1 a fuel injector designed according to the invention is shown in a first embodiment.
  • a fuel injector 1 comprises an injection valve member 3, which is guided in a guide 5 in a lower housing part 7. At the injection valve member 3, a sealing edge 9 is formed, which is in a seat 13 when the injection opening 11 is closed. In addition to the embodiment shown here, in which the fuel injector 1 has an injection opening 11, it is also possible that more than one injection opening 11 is provided.
  • the injection valve member 3 is enclosed by a nozzle chamber 15.
  • the nozzle chamber 15 is connected via an inlet channel 17 with a fuel inlet 19.
  • the fuel inlet 19 is in turn connected to a high-pressure accumulator, not shown here, of a common-rail system.
  • the injection valve member 3 has a piston portion, which is guided in an annular portion 21 of a control piston 23.
  • an end face 57 is formed, which is exposed as a pressure surface of a control chamber 59.
  • a shoulder 61 is formed, which also limits the control space 59 as the other pressure surface on the same side as the end face 57 of the annular portion 21. This leads to that the injection valve member 3 is moved in a movement of the control piston 23 in the opposite direction, so that a stroke reversal of Aktorhubs based on the stroke of the injection valve member 3 is formed.
  • a further control chamber 27 is enclosed.
  • a spring element 29 is received, which is preferably designed as a compression spring coil spring.
  • the control piston 23 simultaneously acts as a valve piston of a control valve 31.
  • a sealing edge 33 is formed on the control piston 23.
  • the control piston 23 is enclosed on the side facing the injection valve member 3 by a valve chamber 37.
  • a connecting channel 39 is formed, through which the valve chamber 37 is connected to the other control chamber 27. Furthermore, a throttle element 41, which connects the valve chamber 37 with the inlet channel 17, opens into the valve chamber 37. As a result, when the control valve 31 is closed, the control chamber 27 is filled via the throttle element 41, the valve chamber 37 and the connecting channel 39 with fuel under system pressure.
  • a plate-shaped portion 43 is formed, which is connected to an actuator 45, preferably with a piezoelectric actuator.
  • an actuator 45 preferably with a piezoelectric actuator.
  • a piezoelectric actuator it is also possible to use any other actuator known to the person skilled in the art, which expands when energized and contracts when the current supply is terminated.
  • the actuator On the opposite side of the control piston 23, the actuator is connected to a disk 47. To achieve the necessary bias of the actuator is enclosed by a spring element 49.
  • the spring element 49 is preferably designed as a tension spring Bourdon tube.
  • the actuator 45 is housed in a housing 51 which is made of a material having a substantially same thermal expansion coefficient as the actuator 45. If the actuator 45 is a piezoelectric actuator is, the housing 51 is preferably made of Invar. To compensate for any residual error due to the different thermal expansion coefficients is in the in FIG. 1 illustrated embodiment between the disc 47, which is connected to the actuator 45, and the housing 51 a compensating element 53 added.
  • the compensating element 53 is made of aluminum, for example.
  • an actuator chamber 55 is formed, which is filled with fuel during operation of the fuel injector 1.
  • the actuator 45 is surrounded by fuel. Due to the good thermal conductivity of the fuel, the heat generated by the actuator 45 during operation is transmitted to the housing 51. Thus, the fuel with which the actuator 45 is lapped, at the same time for cooling the actuator 45th
  • the actuator 45 is energized. As a result, the actuator 45 expands. By expanding the actuator 45, the control piston 23 is moved in the direction of the injection valve member 3. The thus increasing pressure force acts on the shoulder 61 on the piston portion of the injection valve member 3, which moves the injection valve member 3 in the opposite direction to Aktorhub and the injection valve member 3 lifts from its seat 13 and thereby the at least one injection opening 11 releases.
  • the control piston 23 via the control chamber 59 acts directly on the injection valve member 3. At the same time lifts the sealing edge 33 of the control valve 31 from its seat 35 and thus gives a connection from the valve chamber 37 in a fuel return by the movement of the control piston 23 63 free.
  • the pressure in the valve chamber 37 drops to the return pressure. Due to the reduced pressure in the valve chamber 37, fuel flows from the further control chamber 27 via the connecting channel 39 into the valve chamber 37 and from there into the fuel return 63. The pressure in the further control chamber 27 decreases.
  • the control piston 23 acts as a valve piston of a servo-valve and controls the further control chamber 27 at. Due to the decreasing pressure in the control chamber 27, the movement of the injection valve member 3 is facilitated. A quick opening of the injection valve member 3 with a translated actuator stroke is thereby achieved.
  • the energization of the actuator 45 is stopped.
  • the actuator 45 contracts and thereby moves the control piston 23 in the direction of the actuator 45.
  • the end face 57 lifts out of the control chamber 59 and thus increases its volume.
  • the pressure in the control chamber 59 decreases. This results in a lower pressure force acting on the shoulder 61 on the injection valve member 3. Sobad the pressure force acting on the shoulder 61 of the injection valve member 3 is smaller than the pressure force acting on the upper end face 25 of the injection valve member 3, the injection valve member 3 moves into its seat 13 and thereby closes the injection port 11 is supported Movement of the injection valve member 3 characterized in that the sealing edge 33 is placed in its seat 35 by the movement of the control piston 23 and so the control valve 31 is closed.
  • control valve 31 Once the control valve 31 is closed, can under System pressure standing fuel from the inlet channel 17 via the throttle element 41, the valve chamber 37 and the connecting channel 39 in the other control chamber 27 flow.
  • the pressure in the further control chamber 27 increases to system pressure.
  • a further increased pressure force acts on the upper end face 25 of the injection valve member 3. The movement of the injection valve member 3 is accelerated.
  • the housing 51 is made of a material which has approximately the same coefficient of thermal expansion as the actuator 45. Differences in the coefficients of thermal expansion of the actuator 45 and the housing 51 are compensated, for example, by the compensation element 53. Should nevertheless a residual error occur in the stroke, through which the control valve 31 does not close tightly, it is possible to electrically compensate for this error.
  • the actuator is operated, for example bipolar. For this purpose, however, it is necessary to use a bipolar piezoelectric actuator.
  • bipolar piezoelectric actuator contracts when the voltage is reversed.
  • the control valve 31 does not close due to the thermal expansion of the actuator 45 to apply a negative voltage to the actuator 45 and thus cause a contraction of the actuator 45.
  • the control piston 23 is moved further in the direction of the actuator 45 and the sealing edge 33 placed in its seat 35.
  • FIG. 2 a fuel injector designed according to the invention is shown in a second embodiment.
  • FIG. 2 illustrated fuel injector differs from the in FIG. 1 shown fuel injector characterized in that the control piston 23 is not connected to the actuator 45, but limited with an upper end face 65 a booster chamber 67. At the upper end surface 65 opposite side of the booster chamber 67 is bounded by an end face 69 of a booster piston 71. At the booster piston 71, a plate-shaped extension 73 is formed, which is connected to the actuator 45.
  • control piston 23 Since the control piston 23 is not directly connected to the actuator 45, but a hydraulic transmission of the movement of the actuator 45 takes place on the control piston 23, it is in the in FIG. 2 illustrated embodiment, by providing a housing 51 made of a material having a thermal expansion coefficient which corresponds to that of the actuator 45, a occurring due to thermal expansion To compensate for lifting errors. At the same time it is possible to translate the stroke of the actuator 45 to the stroke of the control piston 23 through the translator chamber 67. The transmission ratio is dependent on the diameter d 1 of the booster piston 71 and the diameter d 2 of the control piston 23.
  • the operation of the fuel injector with the in FIG. 2 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that when power to the actuator 45, the actuator 45 expands and thereby the booster piston 71 is moved with the end face 69 in the booster chamber 67. As a result, the volume in the interpreter space 67 decreases. The pressure in the interpreter room 67 increases. Due to the increased pressure, an increased pressure force acts on the upper end surface 65 of the control piston 23. Due to this increased pressure force on the upper end face 65 of the control piston 23, the control piston 23 is moved in the direction of the injection valve member 3. By the movement of the control piston 23, the sealing edge 33 is lifted from its seat 35 and the control valve 31 opens.
  • the energization of the actuator 45 is released.
  • the actuator 45 contracts.
  • the booster piston 71 is moved with the end face 69 from the booster chamber 67.
  • the volume in the translator room 67 increases.
  • the pressure drops in the booster chamber 67 and on the upper end face 65 of the control piston 23 acts a lower pressure force.
  • the control piston 23 is moved in the direction of the booster piston 71 in the booster chamber 67. This movement of the control piston 23 causes the sealing surface 33 is placed in the seat 35 and so the control valve 31 closes the connection from the valve chamber 37 in the fuel return 63.
  • FIG. 3 shows a fuel injector designed according to the invention in a third embodiment.
  • annular portion 75 is formed, in which the control piston 23 is guided.
  • the annular portion 75 and the control piston 23 surround the other control chamber 27.
  • the annular portion 75 on the piston portion of the injection valve member 3 bounded with a face 77 a control chamber 79.
  • a shoulder 81 is formed on the control piston 23, the control chamber 79 on the same Side bounded as the end face 77 of the annular portion 75.
  • a third control chamber 83 which is connected to the fuel inlet 19 via the inlet channel 17, the second control chamber 79 by a ring member 85, which encloses the annular portion 75 on the injection valve member 3, limited ,
  • the ring element 85 is provided with a biting edge 87 against a shoulder 89 on the middle housing part 91.
  • the force required for this purpose is exerted by a spring element 93, which is supported with one side against the ring member 85 and with the other side against the lower housing part 7.
  • the spring element 93 is preferably designed as a compression spring coil spring.
  • a throttle element 95 is formed in the connecting channel 39.
  • FIG. 3 shown fuel injector of the actuator 45 energized.
  • the actuator 45 expands.
  • the booster piston 71 connected to the actuator 45 is moved in the direction of the translator chamber 67.
  • the pressure in the interpreter room 67 increases.
  • an increased pressure force on the upper end surface 65 of the control piston 23 acts.
  • the control piston 23 is moved in the direction of the injection valve member 3.
  • the sealing edge 33 rises from its seat 35.
  • a connection from the other control chamber 27 via the connecting channel 39 with the throttle element 95 in the valve chamber 37 and from there into the fuel return 63 is released.
  • the pressure in the other control chamber 27 decreases.
  • the volume in the control chamber 79 is increased by the movement of the control piston 23, since the shoulder 81 is moved in the direction of the injection valve member. As a result, the pressure in the control chamber 79 decreases.
  • On the end face 77 of the annular portion 75 on the piston portion of the injection valve member 3 acts a lower pressure force. Due to the pressure force in the third control chamber 83, which acts on a second shoulder 99 on the injection valve member 3, the injection valve member is lifted out of its seat 13 and releases the at least one injection opening.
  • the energization of the actuator 45 is canceled.
  • the actuator 45 contracts.
  • the booster piston 71 is moved in the direction of the actuator 45.
  • the volume in the interpreter room 67 increases.
  • On the upper end face 65 of the control piston 23 acts a lower pressure force, whereby the control piston 23 is moved in the direction of the booster chamber 67.
  • the sealing edge 33 is placed back in its seat 35 and thus closes the control valve 31.
  • About the inlet throttle flows under system pressure fuel from the inlet channel into the valve chamber 37 and from there via the throttle element 95 and the connecting channel 39 in the other control chamber 27th Pressure in control room 27 increases.
  • the actuator chamber 55 is connected via a channel 101 to the inlet channel 17.
  • fuel in the actuator chamber 55 under system pressure. This fuel is used to dissipate the heat generated during operation of the actuator to the housing, since the heat transfer coefficient of the fuel is substantially greater than the heat transfer coefficient of a gas.

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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)
  • Fluid Mechanics (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine. The injector is actuated by an actuator and is connected to a fuel supply line via which fuel is supplied under system pressure. At least one injection opening can be opened or closed off by an injection valve member, which is activated by a control piston via a control chamber to which the control piston and a piston section of the injection valve member are exposed with respective pressure faces. The control piston is a valve piston of a control valve. The pressure face of the control piston and the pressure face of the piston section of the injection valve member are exposed to the control chamber at the same side. The control piston and the piston section of the injection valve member also enclose a further control chamber which is connected to a fuel return line when the control valve is open and to the fuel supply line when the control valve is closed.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine gemäß dem Oberbegriff des Anspruchs 1 ( WO-A-96/37698 ).The invention relates to an injector for injecting fuel into a combustion chamber of an internal combustion engine according to the preamble of claim 1 (US Pat. WO-A-96/37698 ).

Aus DE-A 10 2004 015 744 ist ein Kraftstoffinjektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine bekannt, der ein Injektorgehäuse aufweist, das einen Kraftstoffzulauf aufweist, der mit einer zentralen Kraftstoffhochdruckquelle außerhalb des Injektorgehäuses und mit einem Druckraum innerhalb des Injektorgehäuses in Verbindung steht, aus dem in Abhängigkeit von der Stellung eines Steuerventils mit Hochdruck beaufschlagter Kraftstoff eingespritzt wird. Das Steuerventil wird mittels eines Piezoaktors betätigt. Um einen ausreichend großen Hubweg für das Steuerventil zu erzielen, ist zwischen dem Steuerventil und dem Piezoaktor ein Kopplungsraum ausgebildet. Dieser wirkt als hydraulischer Übersetzer auf den Ventilkolben des Steuerventils.Out DE-A 10 2004 015 744 For example, there is known a fuel injector for injecting fuel into a combustion chamber of an internal combustion engine having an injector housing having a fuel inlet communicating with a central fuel high pressure source outside the injector housing and with a pressure space within the injector housing depending on the position a control valve is injected with high pressure fuel. The control valve is actuated by means of a piezoelectric actuator. In order to achieve a sufficiently large stroke for the control valve, a coupling space is formed between the control valve and the piezoelectric actuator. This acts as a hydraulic translator on the valve piston of the control valve.

Nachteil der aus dem Stand der Technik bekannten Kraftstoffinjektoren, die mit einem Piezoaktor betätigt werden, ist, dass der Piezoaktor sehr lang sein muss, um einen ausreichend großen Weg des Ventilkolbens des Steuerventils zu erzielen. Dies führt zu einer großen Baulänge des Kraftstoffinjektors.Disadvantage of the fuel injectors known from the prior art, which are actuated with a piezoelectric actuator is that the piezoelectric actuator must be very long in order to achieve a sufficiently large path of the valve piston of the control valve. This leads to a large length of the fuel injector.

Offenbarung der ErfindungDisclosure of the invention Vorteile der ErfindungAdvantages of the invention

Ein erfindungsgemäß ausgebildeter Injektor zum Einspritzen von Kraftstoff in einen Brennraum einer Verbrennungskraftmaschine wird mittels eines Aktors betätigt und ist mit einem Kraftstoffzulauf verbunden, über den unter Systemdruck stehender Kraftstoff zugeführt wird. Bei dem Injektor ist mindestens eine Einspritzöffnung durch ein Einspritzventilglied freigebbar oder verschließbar, wobei das Einspritzventilglied mittels eines Steuerkolbens über einen Steuerraum angesteuert wird, dem der Steuerkolben und ein Kolbenabschnitt des Einspritzventilglieds mit jeweiligen Druckflächen ausgesetzt ist. Der Steuerkolben ist gleichzeitig ein Ventilkolben eines Steuerventils. Der Ventilkolben und der Kolbenabschnitt des Einspritzventilglieds umschließen einen weiteren Steuerraum, der bei geöffnetem Steuerventil mit einem Kraftstoffrücklauf und bei geschlossenem Steuerventil mit dem Kraftstoffzulauf verbunden ist. In einer ersten Öffnungsphase des Einspritzventilglieds wirkt der Steuerkolben über den ersten Steuerraum nach dem Prinzip einer direkten Ansteuerung auf das Einspritzventilglied. Eine weitere Öffnungsphase des Einspritzventilglieds setzt ein, wenn der Steuerkolben als Ventilkolben eines Servo-Ventils wirkt und den weitere Steuerraum ansteuert. Das Wesen der Erfindung liegt in einer Kombination von direkter Ansteuerung und Servo-Ansteuerung des Einspritzventilglieds, wobei die Öffnung des Einspritzventilglieds erfolgt, wenn der Aktor den Steuerkolben in Richtung der Einspritzöffnungen bewegt. Vorteil des erfindungsgemäß ausgebildeten Injektors ist, dass durch die Ausgestaltung des Steuerkolbens als Ventilkolben für das Steuerventil kein zusätzliches Steuerventil im Injektor ausgebildet sein muss, um den Betrieb des Injektors zu ermöglichten. Aus diesem Grund kann die Baugröße des Injektors reduziert werden. Ein weiterer Vorteil des erfindungsgemäß ausgebildeten Injektors ist, dass der Hub des Aktors so übersetzt wird, dass bereits ein kurzer Aktor ausreichend ist, um einen ausreichend großen Hub des Einspritzventilgliedes zu erzeugen. Hierdurch ist es möglich, die Bauhöhe des Injektors zu reduziercn. Zudem wird durch die erfindungsgemäße Ausgestaltung des Injektors die Öffnungsgeschwindigkeit des Einspritzventilglieds zu Beginn des Öffnungsvorganges im Vergleich zu den aus dem Stand der Technik bekannten Kraftstoffmjektoren erhöht.An inventively designed injector for injecting fuel into a combustion chamber of an internal combustion engine is actuated by means of an actuator and is connected to a fuel inlet, is supplied via the standing under system pressure fuel. In the injector, at least one injection opening can be opened or closed by an injection valve member, wherein the injection valve member by means of a control piston is controlled via a control chamber, which is exposed to the control piston and a piston portion of the injection valve member with respective pressure surfaces. The control piston is also a valve piston of a control valve. The valve piston and the piston portion of the injection valve member enclose a further control chamber, which is connected with the control valve open with a fuel return and with the control valve closed to the fuel inlet. In a first opening phase of the injection valve member, the control piston acts via the first control chamber according to the principle of direct control of the injection valve member. A further opening phase of the injection valve member begins when the control piston acts as a valve piston of a servo valve and controls the further control chamber. The essence of the invention lies in a combination of direct control and servo control of the injection valve member, wherein the opening of the injection valve member takes place when the actuator moves the control piston in the direction of the injection openings. The advantage of the inventively embodied injector is that the design of the control piston as the valve piston for the control valve no additional control valve must be formed in the injector to allow the operation of the injector. For this reason, the size of the injector can be reduced. A further advantage of the inventively embodied injector is that the stroke of the actuator is translated so that even a short actuator is sufficient to produce a sufficiently large stroke of the injection valve member. This makes it possible to reduce the height of the injector. In addition, the opening speed of the injection valve member is increased at the beginning of the opening process in comparison to the fuel injectors known from the prior art by the inventive design of the injector.

Damit der Ventilkolben und das Einspritzventilglied den weiteren Steuerraum umschließen, ist in einer ersten Ausführungsform am Steuerkolben ein ringförmiger Abschnitt ausgebildet, in dem der Kolbenabschnitt des Einspritzventilglieds geführt ist. Der weitere Steuerraum wird dabei durch das Einspritzventilglied und den ringförmigen Abschnitt begrenzt.In order for the valve piston and the injection valve member to surround the further control chamber, in a first embodiment, an annular portion is formed on the control piston, in which the piston portion of the injection valve member is guided. The additional control chamber is limited by the injection valve member and the annular portion.

In einer zweiten Ausführungsform ist der aringförmige Abschnitt am Kolbenabschnitt des Einspritzventilglieds ausgebildet. Im ringförmigen Abschnitt ist der Steuerkolben geführt und der weitere Steuerraum wird durch den Steuerkolben und den ringförmigen Abschnitt begrenzt.In a second embodiment, the aring-shaped portion is formed on the piston portion of the injection valve member. In the annular portion of the control piston is guided and the other control chamber is limited by the control piston and the annular portion.

Um den Hub des Steuerkolbens gegenüber dem Aktorhub weiter zu vergrößern, ist in einer weiteren Ausführungsform der Aktor mit einem Übersetzerkolben verbunden, wobei der Übersetzerkolben mit einer Stirnfläche einen Übersetzerraum begrenzt, der auf der gegenüberliegenden Seite durch eine obere Stirnfläche des Steuerkolbens begrenzt wird. Das Verhältnis der Hübe von Übersetzerkolben und Steuerkolben ist dabei proportional zum Verhältnis der Durchmesser. Je größer der Durchmesser des Übersetzerkolbens im Vergleich zum Durchmesser der den Steuerraum begrenzenden Stirnfläche des Steuerkolbens ist, umso größer ist der Hub des Steuerkolbens im Vergleich zum Hub des Übersetzerkolbens.In order to further increase the stroke of the control piston relative to the Aktorhub, in another embodiment, the actuator is connected to a booster piston, wherein the booster piston defines with an end face a booster chamber, which is bounded on the opposite side by an upper end face of the control piston. The ratio of the strokes of the booster piston and the control piston is proportional to the ratio the diameter. The larger the diameter of the booster piston compared to the diameter of the control chamber limiting end face of the control piston, the larger the stroke of the control piston compared to the stroke of the booster piston.

Um einen ausreichend großen Hub des Einspritzventilgliedes zu ermöglichen und damit eine ausreichend große Menge an Kraftstoff in den Brennraum der Verbrennungskraftmaschine einspritzen zu können, ist der Steuerraum, der durch das Einspritzventilglied und den Steuerkolben begrenzt wird, durch einen Verbindungskanal mit einem Ventilraum verbunden, der den Steuerkolben umschließt. Der Ventilraum ist dabei ein Ventilraum des Steuerventils. Sobald das Steuerventil öffnet, ist der Ventilraum, der den Steuerkolben umschließt, mit einem Kraftstoffrücklauf verbunden. Hierdurch wird der weitere Steuerraum bei geöffnetem Steuerventil druckentlastet. Das Einspritzventilglied kann einen größeren Weg zurücklegen.In order to allow a sufficiently large stroke of the injection valve member and thus to inject a sufficiently large amount of fuel into the combustion chamber of the internal combustion engine, the control chamber, which is bounded by the injection valve member and the control piston, connected by a connecting channel with a valve chamber, the Control spool encloses. The valve chamber is a valve chamber of the control valve. As soon as the control valve opens, the valve space, which encloses the control piston, is connected to a fuel return. As a result, the further control chamber is relieved of pressure when the control valve is open. The injection valve member can travel a greater distance.

In einer bevorzugten Ausführungsform ist in dem Verbindungskanal, durch den der Steuerraum, der durch das Einspritzventilglied und den Steuerkolben begrenzt wird, mit dem Ventilraum verbunden ist, ein Drosselelement aufgenommen. Durch das Drosselelement wird die Druckentlastung bzw. Druckbelastung des Steuerraumes gedämpft. Hierdurch wird ein Rückschlagen des Einspritzventilgliedes vermieden. Zudem wirkt das Drosselelement im Verbindungskanal als Toleranzbegrenzer.In a preferred embodiment, a throttle element is received in the connecting channel, through which the control chamber, which is delimited by the injection valve member and the control piston, is connected to the valve chamber. By the throttle element, the pressure relief or pressure load of the control chamber is attenuated. As a result, a return of the injection valve member is avoided. In addition, the throttle element acts as a tolerance limiter in the connecting channel.

Um den weiteren Steuerraum bei geschlossenem Steuerventil mit unter Systemdruck stehendem Kraftstoff befüllen zu können, ist der Ventilraum des Steuerventils, der mit dem weiteren Steuerraum über den Verbindungskanal verbunden ist, mittels eines Drosselelementes mit dem Kraftstoffzulauf verbunden.To be able to fill the further control chamber with the control valve closed with fuel under system pressure, the valve chamber of the control valve, which is connected to the further control chamber via the connecting channel, is connected by means of a throttle element to the fuel inlet.

Bei einer Ausführungsform des Kraftstoffinjektors, bei der das Einspritzventilglied in einem ringförmigen Abschnitt im Steuerkolben geführt ist, begrenzen eine untere Stirnfläche am ringförmigen Abschnitt des Steuerkolbens und eine Schulter am Kolbenabschnitt des Einspritzventilglieds den Steuerraum. Hierdurch wird bei einer Bewegung des Steuerkolbens in den Steuerraum hinein das Einspritzventilglied aus diesem herausgeschoben. Diese Ausgestaltung führt dazu, dass bei bestromtem Aktor, das heißt bei sich ausgedehntem Aktor, der Steuerkolben in den Steuerraum hineinbewegt wird und sich das Einspritzventilglied durch diese Bewegung des Steuerkolbens aus dem Steuerraum herausbewegt und damit aus seinem Sitz hebt und die mindestens eine Einspritzöffnung freigibt. Durch das Verhältnis der Größe der Stirnfläche am ringförmigen Abschnitt des Steuerkolbens und der Fläche der Schulter, die den Steuerraum begrenzten, lässt sich der Hub des Einspritzventilgliedes in Abhängigkeit vom Hub des Steuerkolbens einstellen. Je kleiner die Fläche der Schulter im Vergleich zur Fläche der Stirnfläche am ringförmigen Abschnitt des Steuerkolbens ist, umso größer ist der Hub des Einspritzventilgliedes im Vergleich zum Hub des Steuerkolbens.In one embodiment of the fuel injector in which the injection valve member is guided in an annular portion in the control piston, define a lower end face on the annular portion of the control piston and a shoulder on the piston portion of the injection valve member, the control space. As a result, the injection valve member is pushed out of this during a movement of the control piston into the control chamber. This configuration has the effect that, when the actuator is energized, that is to say with an extended actuator, the control piston is moved into the control chamber and the injection valve member moves out of the control chamber through this movement of the control piston, thus lifting it out of its seat and releasing the at least one injection opening. By the ratio of the size of the end face on the annular portion of the control piston and the surface of the shoulder, which limited the control chamber, the stroke of the injection valve member in dependence on the stroke of the control piston can be adjusted. The smaller the area of the shoulder in the Compared to the area of the end face on the annular portion of the control piston, the greater is the stroke of the injection valve member in comparison to the stroke of the control piston.

Bei einer weiteren Ausführungsform des Kraftstoffinjektors, bei der der Kolbenabschnitt des Einspritzventilglieds einen ringförmigen Abschnitt aufweist, in dem der Steuerkolben geführt ist, begrenzen eine Stirnfläche am ringförmigen Abschnitt des Kolbenabschnitts des Einspritzventilglieds und eine Schulter am Steuerkolben den Steuerraum. Die Funktion ist hierbei die gleiche wie bei der Ausführungsförm, bei der der ringförmige Abschnitt am Steuerkolben ausgeführt ist, und ein Einspritzventilglied in diesem ringförmigen Abschnitt am Steuerkolben geführt ist. Auch hier ist die Übersetzung der Bewegung des Einspritzventilgliedes im Vergleich zum Steuerkolben abhängig von der Querschnittsfläche der Stirnfläche des Kolbenabschnitts des Einspritzventilglieds und der Fläche der Schulter, die den Steuerraum begrenzen.In a further embodiment of the fuel injector, wherein the piston portion of the injection valve member has an annular portion in which the control piston is guided, define an end face on the annular portion of the piston portion of the injection valve member and a shoulder on the control piston the control chamber. The function here is the same as in the embodiment in which the annular portion is formed on the control piston, and an injection valve member is guided in this annular portion on the control piston. Again, the translation of the movement of the injection valve member in relation to the control piston is dependent on the cross-sectional area of the end face of the piston portion of the injection valve member and the surface of the shoulder which define the control space.

Um den Steuerkolben mit Hilfe des Aktors, vorzugsweise ein Piezoaktor, betätigen zu können, ist der Steuerkolben in einer Ausführungsförm direkt mit dem Aktor verbunden.In order to be able to actuate the control piston by means of the actuator, preferably a piezoactuator, the control piston in an embodiment is connected directly to the actuator.

Um Hubunterschiede auszugleichen, die aufgrund der Wärmeausdehnung des Aktors entstehen können, ist der Aktor vorzugsweise in einem Gehäuse aufgenommen, das aus einem Material gefertigt ist, dessen Wärmeausdehnungskoeffizient dem des Aktors entspricht. Aufgrund des nahezu gleichen Wärmeausdehnungskoeffizienten ist das Gehäuse, in dem der Aktor aufgenommen ist, vorzugsweise aus Invar gefertigt, wenn der Aktor ein Piezoaktor ist.To compensate Hubunterschiede, which may arise due to the thermal expansion of the actuator, the actuator is preferably housed in a housing which is made of a material whose coefficient of thermal expansion corresponds to that of the actuator. Due to the almost same coefficient of thermal expansion, the housing in which the actuator is received, preferably made of Invar, when the actuator is a piezoelectric actuator.

Um einen eventuell auftretenden Restfehler im Wärmeausdehnungskoeffizienten zwischen Aktor und Gehäuse zu kompensieren, ist in einer bevorzugten Ausführungsform zwischen dem Aktor und dem Gehäuse ein Ausgleichselement aufgenommen. Das Ausgleichselement ist zum Beispiel aus Aluminium oder Aluminiumlegierungen gefertigt.To compensate for any residual error in the coefficient of thermal expansion between the actuator and the housing, a compensation element is added in a preferred embodiment between the actuator and the housing. The compensating element is made of aluminum or aluminum alloys, for example.

Die Ausführungsform, bei der das Gehäuse aus einem Material gefertigt ist, dessen Wärmeausdehnungskoeffizient dem des Aktors entspricht und bei dem zwischen dem Gehäusen und dem Aktor ein Ausgleichselement aufgenommen ist, durch welches ein Restfehler des Wärmeausdehnungskoeffizienten zwischen Aktor und Gehäuse kompensiert wird, ist insbesondere dann bevorzugt, wenn der Steuerkolben direkt mit dem Aktor verbunden ist. Dies ist deshalb erforderlich, um ein sauberes Schließen des Steuerventils zu gewährleisten. Ein gegebenenfalls auftretender Restfehler im Hub zur Erzeugung der Dichtheit am Steuerventil kann zum Beispiel elektrisch kompensiert werden. Hierzu ist es möglich, den Aktor zum Beispiel bipolar zu betreiben.The embodiment in which the housing is made of a material whose coefficient of thermal expansion corresponds to that of the actuator and in which a compensating element is accommodated between the housings and the actuator, by which a residual error of the coefficient of thermal expansion between actuator and housing is compensated, is particularly preferred when the spool is directly connected to the actuator. This is therefore necessary to ensure a clean closing of the control valve. An optionally occurring residual error in the stroke for generating the tightness at the control valve can be compensated for example electrically. For this purpose, it is possible to operate the actuator, for example, bipolar.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Ausführungsbeispiele der Erfindung sind in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert.Embodiments of the invention are illustrated in the drawings and explained in more detail in the following description.

Es zeigen

Figur 1
einen erfindungsgemäß ausgebildeten Kraftstoffinjektor in einer ersten Ausführungsform,
Figur 2
einen erfindungsgemäß ausgebildeten Kraftstoffinjektor in einer zweiten Ausführungsform,
Figur 3
einen erfindungsgemäß ausgebildeten Kraftstoffinjektor in einer dritten Ausführungsform.
Show it
FIG. 1
a fuel injector designed according to the invention in a first embodiment,
FIG. 2
a fuel injector designed according to the invention in a second embodiment,
FIG. 3
an inventively designed fuel injector in a third embodiment.

Ausführungsformen der ErfindungEmbodiments of the invention

In Figur 1 ist ein erfindungsgemäß ausgebildeter Kraftstoffinjektor in einer ersten Ausführungsform dargestellt.In FIG. 1 a fuel injector designed according to the invention is shown in a first embodiment.

Ein Kraftstoffinjektor 1 umfasst ein Einspritzventilglied 3, welches in einer Führung 5 in einem unterem Gehäuseteil 7 geführt ist. Am Einspritzventilglied 3 ist eine Dichtkante 9 ausgebildet, welche bei geschlossener Einspritzöffnung 11 in einem Sitz 13 steht. Neben der hier dargestellten Ausführungsform, bei der der Kraftstoffinjektor 1 eine Einspritzöffnung 11 aufweist, ist es auch möglich, dass mehr als eine Einspritzöffnung 11 vorgesehen ist.A fuel injector 1 comprises an injection valve member 3, which is guided in a guide 5 in a lower housing part 7. At the injection valve member 3, a sealing edge 9 is formed, which is in a seat 13 when the injection opening 11 is closed. In addition to the embodiment shown here, in which the fuel injector 1 has an injection opening 11, it is also possible that more than one injection opening 11 is provided.

Das Einspritzventilglied 3 ist von einem Düsenraum 15 umschlossen. Der Düsenraum 15 ist über einen Zulaufkanal 17 mit einem Kraftstoffzulauf 19 verbunden. Der Kraftstoffzulauf 19 ist wiederum mit einem hier nicht dargestellten Hochdruckspeicher eines Common-Rail-Systems verbunden.The injection valve member 3 is enclosed by a nozzle chamber 15. The nozzle chamber 15 is connected via an inlet channel 17 with a fuel inlet 19. The fuel inlet 19 is in turn connected to a high-pressure accumulator, not shown here, of a common-rail system.

An seinem der Einspritzöffnung 11 abgewandten Ende weist das Einspritzventilglied 3 einen Kolbenabschnitt auf, der in einem ringförmigen Abschnitt 21 eines Steuerkolbens 23 geführt ist. Am ringförmigen Abschnitt 21 ist eine Stirnfläche 57 ausgebildet, die als Druckfläche einem Steuerraum 59 ausgesetzt ist. Am Kolbenabschnitt des Einspritzventilglieds 3 ist eine Schulter 61 ausgebildet, die als weitere Druckfläche ebenfalls dem Steuerraum 59 auf der gleichen Seite begrenzt wie die Stirnfläche 57 des ringförmigen Abschnittes 21. Dies führt dazu, dass das Einspritzventilglied 3 bei einer Bewegung des Steuerkolbens 23 in die entgegengesetzte Richtung bewegt wird, so dass eine Hubumkehr des Aktorhubs bezogen auf den Hub des Einspritzventilglieds 3 entsteht. Durch den ringförmigen Abschnitt 21 und eine obere Stirnfläche 25 des Einspritzventilgliedes 3 wird ein weiterer Steuerraum 27 umschlossen. Im weiteren Steuerraum 27 ist ein Federelement 29 aufgenommen, welches vorzugsweise eine als Druckfeder ausgebildete Spiralfeder ist.At its end facing away from the injection opening 11, the injection valve member 3 has a piston portion, which is guided in an annular portion 21 of a control piston 23. On the annular portion 21, an end face 57 is formed, which is exposed as a pressure surface of a control chamber 59. At the piston portion of the injection valve member 3, a shoulder 61 is formed, which also limits the control space 59 as the other pressure surface on the same side as the end face 57 of the annular portion 21. This leads to that the injection valve member 3 is moved in a movement of the control piston 23 in the opposite direction, so that a stroke reversal of Aktorhubs based on the stroke of the injection valve member 3 is formed. Through the annular portion 21 and an upper end face 25 of the injection valve member 3, a further control chamber 27 is enclosed. In the further control chamber 27, a spring element 29 is received, which is preferably designed as a compression spring coil spring.

Der Steuerkolben 23 fungiert gleichzeitig als Ventilkolben eines Steuerventils 31. Hierzu ist am Steuerkolben 23 eine Dichtkante 33 ausgebildet. Bei geschlossenem Steuerventil 31 steht die Dichtkante 33 in einem Sitz 35 des Steuerventils 31. Der Steuerkolben 23 wird auf der dem Einspritzventilglied 3 zuweisenden Seite von einem Ventilraum 37 umschlossen.The control piston 23 simultaneously acts as a valve piston of a control valve 31. For this purpose, a sealing edge 33 is formed on the control piston 23. When the control valve 31 is closed, the sealing edge 33 is in a seat 35 of the control valve 31. The control piston 23 is enclosed on the side facing the injection valve member 3 by a valve chamber 37.

Im ringförmigen Abschnitt 21 des Steuerkolbens 23 ist ein Verbindungskanal 39 ausgebildet, durch welchen der Ventilraum 37 mit dem weiteren Steuerraum 27 verbunden ist. Weiterhin mündet in den Ventilraum 37 ein Drosselelement 41, welches den Ventilraum 37 mit dem Zulaufkanal 17 verbindet. Hierdurch wird bei geschlossenem Steuerventil 31 der Steuerraum 27 über das Drosselelement 41, den Ventilraum 37 und den Verbindungskanal 39 mit unter Systemdruck stehendem Kraftstoff befüllt.In the annular portion 21 of the control piston 23, a connecting channel 39 is formed, through which the valve chamber 37 is connected to the other control chamber 27. Furthermore, a throttle element 41, which connects the valve chamber 37 with the inlet channel 17, opens into the valve chamber 37. As a result, when the control valve 31 is closed, the control chamber 27 is filled via the throttle element 41, the valve chamber 37 and the connecting channel 39 with fuel under system pressure.

Am Steuerkolben 23 ist ein tellerförmiger Abschnitt 43 ausgebildet, der mit einem Aktor 45, vorzugsweise mit einem Piezoaktor, verbunden ist. Anstelle eines Piezoaktors ist auch jeder andere dem Fachmann bekannte Aktor einsetzbar, der sich bei Bestromung ausdehnt und bei Beendigung der Bestromung zusammenzieht.On the control piston 23, a plate-shaped portion 43 is formed, which is connected to an actuator 45, preferably with a piezoelectric actuator. Instead of a piezoelectric actuator, it is also possible to use any other actuator known to the person skilled in the art, which expands when energized and contracts when the current supply is terminated.

Auf der dem Steuerkolben 23 gegenüberliegenden Seite ist der Aktor mit einer Scheibe 47 verbunden. Zur Erzielung der notwendigen Vorspannung ist der Aktor von einem Federelement 49 umschlossen. Das Federelement 49 ist vorzugsweise eine als Zugfeder ausgebildete Rohrfeder.On the opposite side of the control piston 23, the actuator is connected to a disk 47. To achieve the necessary bias of the actuator is enclosed by a spring element 49. The spring element 49 is preferably designed as a tension spring Bourdon tube.

Um Fehlfunktionen zu vermeiden, die aufgrund der Wärmeausdehnung des Aktors 45 auftreten können, ist der Aktor 45 in einem Gehäuse 51 aufgenommen, welches aus einem Material gefertigt ist, das einen im Wesentlichen gleichen Wärmeausdehnungskoeffzienten aufweist wie der Aktor 45. Wenn der Aktor 45 ein Piezoaktor ist, ist das Gehäuse 51 vorzugsweise aus Invar gefertigt. Zum Ausgleich eines eventuell auftretenden Restfehlers aufgrund der unterschiedlichen Wärmeausdehnungskoeffizienten ist in der in Figur 1 dargestellten Ausführungsform zwischen der Scheibe 47, die mit dem Aktor 45 verbunden ist, und dem Gehäuse 51 ein Ausgleichselement 53 aufgenommen. Das Ausgleichselement 53 ist zum Beispiel aus Aluminium gefertigt.To avoid malfunctions that may occur due to the thermal expansion of the actuator 45, the actuator 45 is housed in a housing 51 which is made of a material having a substantially same thermal expansion coefficient as the actuator 45. If the actuator 45 is a piezoelectric actuator is, the housing 51 is preferably made of Invar. To compensate for any residual error due to the different thermal expansion coefficients is in the in FIG. 1 illustrated embodiment between the disc 47, which is connected to the actuator 45, and the housing 51 a compensating element 53 added. The compensating element 53 is made of aluminum, for example.

Durch das Gehäuse 51 wird ein Aktorraum 55 ausgebildet, der bei Betrieb des Kraftstoffjektors 1 mit Kraftstoff befüllt ist. Hierdurch wird der Aktor 45 von Kraftstoff umspült. Aufgrund der guten Wärmeleitfähigkeit des Kraftstoffs wird die Wärme, die im Betrieb vom Aktor 45 erzeugt wird, an das Gehäuse 51 übertragen. Somit dient der Kraftstoff, mit dem der Aktor 45 umspült wird, gleichzeitig zur Kühlung des Aktors 45.Through the housing 51, an actuator chamber 55 is formed, which is filled with fuel during operation of the fuel injector 1. As a result, the actuator 45 is surrounded by fuel. Due to the good thermal conductivity of the fuel, the heat generated by the actuator 45 during operation is transmitted to the housing 51. Thus, the fuel with which the actuator 45 is lapped, at the same time for cooling the actuator 45th

Um den Einspritzvorgang zu starten, wird der Aktor 45 bestromt. Hierdurch dehnt sich der Aktor 45 aus. Durch das Ausdehnen des Aktors 45 wird der Steuerkolben 23 in Richtung des Einspritzventilgliedes 3 bewegt. Durch die Bewegung des Steuerkolbens 23 erhöht sich der Druck im Steuerraum 59. Die dadurch zunehmende Druckkraft wirkt auf die Schulter 61 am Kolbenabschnitt des Einspritzventilglieds 3, die des Einspritzventilglied 3 in entgegengesetzte Richtung zum Aktorhub bewegt und das Einspritzventilglied 3 aus seinem Sitz 13 hebt und dadurch die mindestens eine Einspritzöffnung 11 freigibt. In dieser Öffnungsphase des Einspritzventilglieds 3 wirkt der Steuerkolben 23 über den Steuerraum 59 direkt auf das Einspritzventilglied 3. Gleichzeitig hebt sich durch die Bewegung des Steuerkolbens 23 die Dichtkante 33 des Steuerventils 31 aus ihrem Sitz 35 und gibt so eine Verbindung vom Ventilraum 37 in einen Kraftstoffrücklauf 63 frei. Hierdurch fällt der Druck im Ventilraum 37 auf den Rücklaufdruck. Aufgrund des gesunkenen Druckes im Ventilraum 37 strömt Kraftstoff aus dem weiteren Steuerraum 27 über den Verbindungskanal 39 in den Ventilraum 37 und von dort weiter in den Kraftstoffrücklauf 63. Der Druck im weiteren Steuerraum 27 nimmt ab. In dieser weiteren Öffnungsphase des Einspritzventilglieds 3 wirkt der Steuerkolben 23 als Ventilkolben eines Servo-Ventils und steuert den weitere Steuerraum 27 an. Durch den abnehmenden Druck im Steuerraum 27 wird die Bewegung des Einspritzventilgliedes 3 erleichtert. Ein schnelles Öffnen des Einspritzventilgliedes 3 mit einem überset/ten Aktorhub wird dadurch erzielt.To start the injection process, the actuator 45 is energized. As a result, the actuator 45 expands. By expanding the actuator 45, the control piston 23 is moved in the direction of the injection valve member 3. The thus increasing pressure force acts on the shoulder 61 on the piston portion of the injection valve member 3, which moves the injection valve member 3 in the opposite direction to Aktorhub and the injection valve member 3 lifts from its seat 13 and thereby the at least one injection opening 11 releases. In this opening phase of the injection valve member 3, the control piston 23 via the control chamber 59 acts directly on the injection valve member 3. At the same time lifts the sealing edge 33 of the control valve 31 from its seat 35 and thus gives a connection from the valve chamber 37 in a fuel return by the movement of the control piston 23 63 free. As a result, the pressure in the valve chamber 37 drops to the return pressure. Due to the reduced pressure in the valve chamber 37, fuel flows from the further control chamber 27 via the connecting channel 39 into the valve chamber 37 and from there into the fuel return 63. The pressure in the further control chamber 27 decreases. In this further opening phase of the injection valve member 3, the control piston 23 acts as a valve piston of a servo-valve and controls the further control chamber 27 at. Due to the decreasing pressure in the control chamber 27, the movement of the injection valve member 3 is facilitated. A quick opening of the injection valve member 3 with a translated actuator stroke is thereby achieved.

Um den Einspritzvorgang wieder zu beenden, wird die Bestromung des Aktors 45 beendet. Der Aktor 45 zieht sich zusammen und bewegt dadurch den Steuerkolben 23 in Richtung des Aktors 45. Durch diese Bewegung hebt sich die Stirnfläche 57 aus dem Steuerraum 59 und vergrößert so dessen Volumen. Der Druck im Steuerraum 59 nimmt ab. Dies führt dazu, dass eine geringere Druckkraft auf die Schulter 61 am Einspritzventilglied 3 wirkt. Sobad die Druckkraft, die auf die Schulter 61 des Einspritzventilgliedes 3 wirkt, kleiner ist als die Druckkraft, die auf die obere Stirnfläche 25 des Einspritzventilgliedes 3 wirkt, bewegt sich das Einspritzventilglied 3 in seinen Sitz 13 und verschließt hierdurch die Einspritzöffnung 11. Unterstützt wird die Bewegung des Einspritzventilgliedes 3 dadurch, dass durch die Bewegung des Steuerkolbens 23 die Dichtkante 33 in ihren Sitz 35 gestellt wird und so das Steuerventil 31 geschlossen wird. Sobald das Steuerventil 31 geschlossen ist, kann unter Systemdruck stehender Kraftstoff aus dem Zulaufkanal 17 über das Drosselelement 41, den Ventilraum 37 und den Verbindungskanal 39 in den weiteren Steuerraum 27 strömen. Der Druck im weiteren Steuerraum 27 steigt auf Systemdruck an. Hierdurch wirkt eine weiter vergrößerte Druckkraft auf die obere Stirnfläche 25 des Einspritzventilgliedes 3. Die Bewegung des Einspritzventilgliedes 3 wird beschleunigt.To end the injection process again, the energization of the actuator 45 is stopped. The actuator 45 contracts and thereby moves the control piston 23 in the direction of the actuator 45. By this movement, the end face 57 lifts out of the control chamber 59 and thus increases its volume. The pressure in the control chamber 59 decreases. This results in a lower pressure force acting on the shoulder 61 on the injection valve member 3. Sobad the pressure force acting on the shoulder 61 of the injection valve member 3 is smaller than the pressure force acting on the upper end face 25 of the injection valve member 3, the injection valve member 3 moves into its seat 13 and thereby closes the injection port 11 is supported Movement of the injection valve member 3 characterized in that the sealing edge 33 is placed in its seat 35 by the movement of the control piston 23 and so the control valve 31 is closed. Once the control valve 31 is closed, can under System pressure standing fuel from the inlet channel 17 via the throttle element 41, the valve chamber 37 and the connecting channel 39 in the other control chamber 27 flow. The pressure in the further control chamber 27 increases to system pressure. As a result, a further increased pressure force acts on the upper end face 25 of the injection valve member 3. The movement of the injection valve member 3 is accelerated.

Damit das Steuerventil 31 dicht schließt, damit bei geschlossenem Steuerventil 31 kein Kraftstoff aus dem Ventilraum 37 in den Kraftstoffrücklauf 63 strömen kann, ist es notwendig, dass gegebenenfalls auftretende Längenänderungen des Aktors aufgrund von zunehmender Temperatur kompensiert werden. Dies erfolgt zum einen dadurch, dass das Gehäuse 51 aus einem Material gefertigt ist, welches in etwa den gleichen Wärnleausdehnungskoeffizienten aufweist wie der Aktor 45. Unterschiede in den Wärmeausdehnungskoeffizienten von Aktor 45 und Gehäuse 51 werden zum Beispiel durch das Ausgleichselement 53 kompensiert. Sollte trotzdem ein Restfehler im Hub auftreten, durch welchen das Steuerventil 31 nicht dicht schließt, ist es möglich, diesen Fehler elektrisch zu kompensieren. Hierzu wird der Aktor zum Beispiel bipolar betrieben. Hierzu ist es jedoch notwendig, einen bipolaren Piezoaktor einzusetzen. Vorteil des bipolaren Piezoaktors ist, dass sich dieser bei Spannungsumkehr zusammenzieht. Somit ist es möglich, wenn das Steuerventil 31 aufgrund der Wärmeausdehnung des Aktors 45 nicht schließt, eine negative Spannung am Aktor 45 anzulegen und so ein Zusammenziehen des Aktors 45 herbeizuführen. Hierdurch wird der Steuerkolben 23 weiter in Richtung des Aktors 45 bewegt und die Dichtkante 33 in ihren Sitz 35 gestellt.In order for the control valve 31 to close tightly, so that no fuel can flow from the valve chamber 37 into the fuel return 63 when the control valve 31 is closed, it is necessary that any changes in length of the actuator occurring due to increasing temperature be compensated. This is done on the one hand in that the housing 51 is made of a material which has approximately the same coefficient of thermal expansion as the actuator 45. Differences in the coefficients of thermal expansion of the actuator 45 and the housing 51 are compensated, for example, by the compensation element 53. Should nevertheless a residual error occur in the stroke, through which the control valve 31 does not close tightly, it is possible to electrically compensate for this error. For this purpose, the actuator is operated, for example bipolar. For this purpose, however, it is necessary to use a bipolar piezoelectric actuator. The advantage of the bipolar piezoelectric actuator is that it contracts when the voltage is reversed. Thus, it is possible if the control valve 31 does not close due to the thermal expansion of the actuator 45 to apply a negative voltage to the actuator 45 and thus cause a contraction of the actuator 45. As a result, the control piston 23 is moved further in the direction of the actuator 45 and the sealing edge 33 placed in its seat 35.

In Figur 2 ist ein erfindungsgemäß ausgebildeter Kraftstoffinjektor in einer zweiten Ausführungsform dargestellt.In FIG. 2 a fuel injector designed according to the invention is shown in a second embodiment.

Der in Figur 2 dargestellte Kraftstoffinjektor unterscheidet sich von dem in Figur 1 dargestellten Kraftstoffinjektor dadurch, dass der Steuerkolben 23 nicht mit dem Aktor 45 verbunden ist, sondern mit einer oberen Stirnfläche 65 einen Übersetzerraum 67 begrenzt. An der der oberen Stirnfläche 65 gegenüberliegenden Seite ist der Übersetzerraum 67 von einer Stirnfläche 69 eines Übersetzerkolbens 71 begrenzt. Am Übersetzerkolben 71 ist eine tellerförmige Erweiterung 73 ausgebildet, die mit dem Aktor 45 verbunden ist.The in FIG. 2 illustrated fuel injector differs from the in FIG. 1 shown fuel injector characterized in that the control piston 23 is not connected to the actuator 45, but limited with an upper end face 65 a booster chamber 67. At the upper end surface 65 opposite side of the booster chamber 67 is bounded by an end face 69 of a booster piston 71. At the booster piston 71, a plate-shaped extension 73 is formed, which is connected to the actuator 45.

Da der Steuerkolben 23 nicht direkt mit dem Aktor 45 verbunden ist, sondern eine hydraulische Übertragung der Bewegung des Aktors 45 auf den Steuerkolben 23 erfolgt, ist es bei der in Figur 2 dargestellten Ausführungsform nicht notwendig, durch Vorsehen eines Gehäuses 51 aus einem Material, welches einen Wärmeausdehnungskoeffizienten aufweist, welcher dem des Aktors 45 entspricht, einen aufgrund von Wärmeausdehnung auftretenden Hubfehler auszugleichen. Der Ausgleich des Hubfehlers erfolgt durch den Übersetzerraum 67. Gleichzeitig ist es möglich, durch den Übersetzerraum 67 den Hub des Aktors 45 auf den Hub des Steuerkolbens 23 zu übersetzen. Das Übersetzungsverhältnis ist dabei abhängig vom Durchmesser d1 des Übersetzerkolbens 71 und dem Durchmesser d2 des Steuerkolbens 23. Sobald der Durchmesser d1 des Übersetzerkolbens 71 größer ist als der Durchmesser d2 der oberen Stirnfläche 65 des Steuerkolbens 23, ist der Hub des Steuerkolbens 23 größer als der Hub des Übersetzerkolbens 71. Hierdurch ist es möglich, die Bauhöhe des Aktors 45 zu reduzieren, da ein kleinerer Hub des Aktors 45 erforderlich ist.Since the control piston 23 is not directly connected to the actuator 45, but a hydraulic transmission of the movement of the actuator 45 takes place on the control piston 23, it is in the in FIG. 2 illustrated embodiment, by providing a housing 51 made of a material having a thermal expansion coefficient which corresponds to that of the actuator 45, a occurring due to thermal expansion To compensate for lifting errors. At the same time it is possible to translate the stroke of the actuator 45 to the stroke of the control piston 23 through the translator chamber 67. The transmission ratio is dependent on the diameter d 1 of the booster piston 71 and the diameter d 2 of the control piston 23. As soon as the diameter d 1 of the booster piston 71 is greater than the diameter d 2 of the upper end face 65 of the control piston 23, the stroke of the control piston 23rd larger than the stroke of the booster piston 71. This makes it possible to reduce the height of the actuator 45, since a smaller stroke of the actuator 45 is required.

Der Betrieb des Kraftstoffinjektors mit der in Figur 2 dargestellten Ausführungsform unterscheidet sich von der in Figur 1 dargestellten Ausführungsform dadurch, dass bei Stromzufuhr zum Aktor 45 sich der Aktor 45 ausdehnt und dadurch der Übersetzerkolben 71 mit der Stirnfläche 69 in den Übersetzerraum 67 bewegt wird. Hierdurch nimmt das Volumen im Übersetzerraum 67 ab. Der Druck im Übersetzerraum 67 steigt an. Aufgrund des ansteigenden Druckes wirkt eine erhöhte Druckkraft auf die obere Stirnfläche 65 des Steuerkolbens 23. Aufgrund dieser erhöhten Druckkraft auf die obere Stirnfläche 65 des Steuerkolbens 23 wird der Steuerkolben 23 in Richtung des Einspritzventilgliedes 3 bewegt. Durch die Bewegung des Steuerkolbens 23 wird die Dichtkante 33 aus ihrem Sitz 35 gehoben und das Steuerventil 31 öffnet sich. Gleichzeitig wird die Stirnfläche 67 des ringförmigen Abschnittes 21 in den Steuerraum 59 bewegt, wodurch sich das Volumen im zweiten Steuerraum 59 verringert und dadurch eine größere Druckkraft auf die Schulter 61 am Einspritzventilglied 3 wirkt. Das Einspritzventilglied 3 wird aus seinem Sitz gehoben. Durch das Öffnen des Steuerventils 31 wird der Druck im weiteren Steuerraum 27 verringert, da Kraftstoff aus dem Steuerraum 27 über den Verbindungskanal 39 und den Ventilraum 37 in den Kraftstoffrücklauf 63 strömen kann. Aufgrund des abfallenden Druckes im Steuerraum 27 ist ein schnelles Öffnen des Einspritzventilgliedes 3 und damit ein schnelles Freigeben der mindestens einen Einspritzöffnung 11 möglich.The operation of the fuel injector with the in FIG. 2 illustrated embodiment differs from the in FIG. 1 illustrated embodiment in that when power to the actuator 45, the actuator 45 expands and thereby the booster piston 71 is moved with the end face 69 in the booster chamber 67. As a result, the volume in the interpreter space 67 decreases. The pressure in the interpreter room 67 increases. Due to the increased pressure, an increased pressure force acts on the upper end surface 65 of the control piston 23. Due to this increased pressure force on the upper end face 65 of the control piston 23, the control piston 23 is moved in the direction of the injection valve member 3. By the movement of the control piston 23, the sealing edge 33 is lifted from its seat 35 and the control valve 31 opens. At the same time the end face 67 of the annular portion 21 is moved into the control chamber 59, whereby the volume in the second control chamber 59 is reduced and thereby a greater compressive force acts on the shoulder 61 on the injection valve member 3. The injection valve member 3 is lifted out of its seat. By opening the control valve 31, the pressure in the further control chamber 27 is reduced, since fuel from the control chamber 27 via the connecting channel 39 and the valve chamber 37 can flow into the fuel return 63. Due to the falling pressure in the control chamber 27 is a quick opening of the injection valve member 3 and thus a quick release of the at least one injection port 11 is possible.

Um den Einspritzvorgang zu beenden, wird die Bestromung des Aktors 45 aufgehoben. Der Aktor 45 zieht sich zusammen. Hierdurch wird der Übersetzerkolben 71 mit der Stirnfläche 69 aus dem Übersetzerraum 67 bewegt. Das Volumen im Übersetzerraum 67 vergrößert sich. Hierdurch fällt der Druck im Übersetzerraum 67 ab und auf die obere Stirnfläche 65 des Steuerkolbens 23 wirkt eine geringere Druckkraft. Hierdurch wird der Steuerkolben 23 in Richtung des Übersetzerkolbens 71 in den Übersetzerraum 67 hineinbewegt. Diese Bewegung des Steuerkolbens 23 führt dazu, dass die Dichtfläche 33 in den Sitz 35 gestellt wird und so das Steuerventil 31 die Verbindung vom Ventilraum 37 in den Kraftstoffrücklauf 63 verschließt. Gleichzeitig wird durch die Bewegung des Steuerkolbens 23 die Stirnfläche 57 des ringförmigen Abschnittes 21 aus dem zweiten Steuerraum 59 gehoben und so das Volumen im Steuerraum 59 vergrößert. Hierdurch nimmt die Druckkraft, die auf die Schulter 61 des Einspritzventilgliedes 3 wirkt, ab. Da aufgrund des geschlossenen Steuerventils 31 über die Zulaufdrossel 41, den Ventilraum 37 und den Verbindungskanal 39 unter System stehender Kraftstoff in den weiteren Steuerraum 27 strömt und dadurch der Druck im weiteren Steuerraum 27 zunimmt, wirkt eine erhöhte Druckkraft auf die obere Stirnfläche 25 des Einspritzventilgliedes 3. Das Einspritzventilglied 3 wird mit der Dichtkante in seinen Sitz 13 gestellt und verschließt so die mindestens eine Einspritzöffnung 11. Der Einspritzvorgang ist beendet. Durch den Druckaufbau im weiteren Steuerraum 27 wird die Schließbewegung des Einspritzventilgliedes 3 erhöht.To end the injection process, the energization of the actuator 45 is released. The actuator 45 contracts. As a result, the booster piston 71 is moved with the end face 69 from the booster chamber 67. The volume in the translator room 67 increases. As a result, the pressure drops in the booster chamber 67 and on the upper end face 65 of the control piston 23 acts a lower pressure force. As a result, the control piston 23 is moved in the direction of the booster piston 71 in the booster chamber 67. This movement of the control piston 23 causes the sealing surface 33 is placed in the seat 35 and so the control valve 31 closes the connection from the valve chamber 37 in the fuel return 63. At the same time, the end face 57 of the annular section 21 is lifted out of the second control chamber 59 by the movement of the control piston 23 and so on the volume in the control chamber 59 increases. As a result, the pressure force acting on the shoulder 61 of the injection valve member 3 decreases. Since due to the closed control valve 31 via the inlet throttle 41, the valve chamber 37 and the connecting channel 39 under system fuel in the further control chamber 27 flows and thereby the pressure in the further control chamber 27 increases, an increased pressure force acts on the upper end face 25 of the injection valve member. 3 The injection valve member 3 is placed with the sealing edge in its seat 13 and thus closes the at least one injection opening 11. The injection process is completed. Due to the pressure build-up in the further control chamber 27, the closing movement of the injection valve member 3 is increased.

Figur 3 zeigt einen erfindungsgemäß ausgebildeten Kraftstoffinjektor in einer dritten Ausführungsform. FIG. 3 shows a fuel injector designed according to the invention in a third embodiment.

Im Unterschied zu dem in Figur 2 dargestellten Kraftstoffinjektor ist bei dem in Figur 3 dargestellten Kraftstoffinjektor am Kolbenabschnitt des Einspritzventilglieds 3 ein ringförmiger Abschnitt 75 ausgebildet, in welchem der Steuerkolben 23 geführt ist. Dabei umschließen der ringförmige Abschnitt 75 und der Steuerkolben 23 den weiteren Steuerraum 27. Der ringförmige Abschnitt 75 am Kolbenabschnitt des Einspritzventilglieds 3 begrenzt mit einer Stirnfläche 77 einen Steuerraum 79. Weiterhin ist am Steuerkolben 23 eine Schulter 81 ausgebildet, die den Steuerraum 79 auf der gleichen Seite begrenzt wie die Stirnfläche 77 des ringförmigen Abschnittes 75. Gegen einen dritten Steuerraum 83, der mit dem Kraftstoffzulauf 19 über den Zulaufkanal 17 verbunden ist, ist der zweite Steuerraum 79 durch ein Ringelement 85, welches den ringförmigen Abschnitt 75 am Einspritzventilglied 3 umschließt, begrenzt. Hierzu wird das Ringelement 85 mit einer Beißkante 87 gegen eine Schulter 89 am mittleren Gehäuseteil 91 gestellt. Die hierfür erforderliche Kraft wird durch ein Federelement 93 ausgeübt, welches sich mit einer Seite gegen das Ringelement 85 und mit der anderen Seite gegen das untere Gehäuseteil 7 abstützt. Das Federelement 93 ist vorzugsweise eine als Druckfeder ausgebildete Spiralfeder.Unlike the in FIG. 2 shown fuel injector is in the in FIG. 3 illustrated fuel injector on the piston portion of the injection valve member 3, an annular portion 75 is formed, in which the control piston 23 is guided. In this case, the annular portion 75 and the control piston 23 surround the other control chamber 27. The annular portion 75 on the piston portion of the injection valve member 3 bounded with a face 77 a control chamber 79. Furthermore, a shoulder 81 is formed on the control piston 23, the control chamber 79 on the same Side bounded as the end face 77 of the annular portion 75. Against a third control chamber 83 which is connected to the fuel inlet 19 via the inlet channel 17, the second control chamber 79 by a ring member 85, which encloses the annular portion 75 on the injection valve member 3, limited , For this purpose, the ring element 85 is provided with a biting edge 87 against a shoulder 89 on the middle housing part 91. The force required for this purpose is exerted by a spring element 93, which is supported with one side against the ring member 85 and with the other side against the lower housing part 7. The spring element 93 is preferably designed as a compression spring coil spring.

Um gegebenenfalls auftretende Druckschwankungen im Steuerraum 27 zu dämpfen, ist im Verbindungskanal 39 ein Drosselelement 95 ausgebildet.In order to damp any pressure fluctuations occurring in the control chamber 27, a throttle element 95 is formed in the connecting channel 39.

Neben der in Figur 3 dargestellten Ausführungsform ist es auch bei den in den Figuren 1 und 2 dargestellten Ausführungsformen möglich, im Verbindungskanal 39, mit dem der weitere Steuerraum 27 mit dem Ventilraum 37 verbunden ist, ein Drosselelement vorzusehen.In addition to the in FIG. 3 illustrated embodiment, it is also in the in the FIGS. 1 and 2 illustrated embodiments possible, in the connecting channel 39, with which the further control chamber 27 is connected to the valve chamber 37 to provide a throttle element.

Damit unter Systemdruck stehender Kraftstoff aus dem dritten Steuerraum 83 in den Düsenraum 15 strömen kann, ist bei der in Figur 3 dargestellten Ausführungsform im Bereich der Führung 5 am Einspritzventilglied 3 mindestens eine Freifläche 97 ausgebildet. Der unter Systemdruck stehende Kraftstoff kann dann vom Kraftstoffzulauf 19 über den Zulaufkanal 17 zunächst in den dritten Steuerraum 83 und von dort entlang der Freifläche 97 in den Düsenraum 15 strömen.In order for fuel under system pressure to be able to flow from the third control chamber 83 into the nozzle chamber 15, in the case of the in FIG. 3 illustrated embodiment in the area the guide 5 on the injection valve member 3 at least one free surface 97 is formed. The fuel under system pressure can then flow from the fuel inlet 19 via the inlet channel 17 first into the third control chamber 83 and from there along the free surface 97 into the nozzle chamber 15.

Um den Einspritzvorgang zu starten, wird auch bei dem in Figur 3 dargestellten Kraftstoffinjektor der Aktor 45 bestromt. Hierdurch dehnt sich der Aktor 45 aus. Der mit dem Aktor 45 verbundene Übersetzerkolben 71 wird in Richtung des Übersetzerraumes 67 bewegt. Hierdurch verkleinert sich das Volumen im Übersetzerraum 67. Der Druck im Übersetzerraum 67 steigt an. Somit wirkt eine vergrößerte Druckkraft auf die obere Stirnfläche 65 des Steuerkolbens 23. Der Steuerkolben 23 wird in Richtung des Einspritzventilgliedes 3 bewegt. Durch die Bewegung des Steuerkolbens 23 hebt sich die Dichtkante 33 aus ihrem Sitz 35. Eine Verbindung vom weiteren Steuerraum 27 über den Verbindungskanal 39 mit dem Drosselelement 95 in den Ventilraum 37 und von dort in den Kraftstoffrücklauf 63 wird freigegeben. Der Druck im weiteren Steuerraum 27 nimmt ab. Gleichzeitig wird durch die Bewegung des Steuerkolbens 23 das Volumen im Steuerraum 79 vergrößert, da die Schulter 81 in Richtung des Einspritzventilgliedes bewegt wird. Hierdurch nimmt der Druck im Steuerraum 79 ab. Auf die Stirnfläche 77 des ringförmigen Abschnittes 75 am Kolbenabschnitt des Einspritzventilglieds 3 wirkt eine geringere Druckkraft. Das Einspritzventilglied wird aufgrund der Druckkraft im dritten Steuerraum 83, die auf eine zweite Schulter 99 am Einspritzventilglied 3 wirkt, aus seinem Sitz 13 gehoben und gibt die mindestens eine Einspritzöffnung frei.To start the injection process, the in FIG. 3 shown fuel injector of the actuator 45 energized. As a result, the actuator 45 expands. The booster piston 71 connected to the actuator 45 is moved in the direction of the translator chamber 67. This reduces the volume in the interpreter room 67. The pressure in the interpreter room 67 increases. Thus, an increased pressure force on the upper end surface 65 of the control piston 23 acts. The control piston 23 is moved in the direction of the injection valve member 3. By the movement of the control piston 23, the sealing edge 33 rises from its seat 35. A connection from the other control chamber 27 via the connecting channel 39 with the throttle element 95 in the valve chamber 37 and from there into the fuel return 63 is released. The pressure in the other control chamber 27 decreases. At the same time, the volume in the control chamber 79 is increased by the movement of the control piston 23, since the shoulder 81 is moved in the direction of the injection valve member. As a result, the pressure in the control chamber 79 decreases. On the end face 77 of the annular portion 75 on the piston portion of the injection valve member 3 acts a lower pressure force. Due to the pressure force in the third control chamber 83, which acts on a second shoulder 99 on the injection valve member 3, the injection valve member is lifted out of its seat 13 and releases the at least one injection opening.

Um den Einspritzvorgang zu beenden, wird die Bestromung des Aktors 45 wieder aufgehoben. Der Aktor 45 zieht sich zusammen. Hierdurch wird der Übersetzerkolben 71 in Richtung des Aktors 45 bewegt. Dies führt dazu, dass sich das Volumen im Übersetzerraum 67 vergrößert. Auf die obere Stirnfläche 65 des Steuerkolbens 23 wirkt eine geringere Druckkraft, wodurch der Steuerkolben 23 in Richtung des Übersetzerraums 67 bewegt wird. Die Dichtkante 33 wird wieder in ihren Sitz 35 gestellt und verschließt so das Steuerventil 31. Über die Zulaufdrossel strömt unter Systemdruck stehender Kraftstoff aus dem Zulaufkanal in den Ventilraum 37 und von dort über das Drosselelement 95 und den Verbindungskanal 39 in den weiteren Steuerraum 27. Der Druck in Steuerraum 27 steigt an. Gleichzeitig wird durch die Bewegung des Steuerkolbens 23 die Schulter 81 am Steuerkolben 23 in den Steuerraum 79 hineinbewegt. Das Volumen im Steuerraum 79 nimmt ab. Hierdurch wirkt eine vergrößerte Druckkraft auf die Stirnfläche 77 am ringförmigen Abschnitt 75 des Kolbenabschnitts des Einspritzventilglieds 3. Durch die auf das Einspritzventilglied 3 wirkenden Druckkräfte wird dieses in Richtung der Einspritzöffnung bewegt, bis es mit der Dichtkante 9 im Sitz 13 steht. Die Einspritzöffnung 11 ist verschlossen und der Einspritzvorgang beendet.To end the injection process, the energization of the actuator 45 is canceled. The actuator 45 contracts. As a result, the booster piston 71 is moved in the direction of the actuator 45. As a result, the volume in the interpreter room 67 increases. On the upper end face 65 of the control piston 23 acts a lower pressure force, whereby the control piston 23 is moved in the direction of the booster chamber 67. The sealing edge 33 is placed back in its seat 35 and thus closes the control valve 31. About the inlet throttle flows under system pressure fuel from the inlet channel into the valve chamber 37 and from there via the throttle element 95 and the connecting channel 39 in the other control chamber 27th Pressure in control room 27 increases. At the same time, the shoulder 81 on the control piston 23 is moved into the control chamber 79 by the movement of the control piston 23. The volume in the control room 79 decreases. As a result, an increased pressure force acts on the end face 77 on the annular portion 75 of the piston portion of the injection valve member 3. By acting on the injection valve member 3 compressive forces this is moved in the direction of the injection port until it with the sealing edge 9 in the seat 13 stands. The injection opening 11 is closed and the injection process is completed.

Bei der in Figur 3 dargestellten Ausführungsform ist der Aktorraum 55 über einen Kanal 101 mit dem Zulaufkanal 17 verbunden. Hierdurch befindet sich im Aktorraum 55 unter Systemdruck stehender Kraftstoff. Dieser Kraftstoff dient zur Abfuhr der beim Betrieb des Aktors entstehenden Wärme an das Gehäuse, da der Wärmeübertragungskoeffizient des Kraftstoffes wesentlich größer ist als der Wärmeübertragungskoeffizient eines Gases.At the in FIG. 3 illustrated embodiment, the actuator chamber 55 is connected via a channel 101 to the inlet channel 17. As a result, there is fuel in the actuator chamber 55 under system pressure. This fuel is used to dissipate the heat generated during operation of the actuator to the housing, since the heat transfer coefficient of the fuel is substantially greater than the heat transfer coefficient of a gas.

Claims (12)

  1. Injector for injecting fuel into a combustion chamber of an internal combustion engine, with the injector (1) being actuated by means of an actuator (45) and being connected to a fuel inlet (19) via which fuel at system pressure is supplied, and in which injector at least one injection opening (11) can be opened up or closed off by means of an injection valve member (3), with the injection valve member (3) being controlled by means of a control piston (23) via a control chamber (59, 79) to which respective pressure surfaces (57, 81) and (61, 77) of the control piston (23) and of a piston section of the injection valve member (3) are exposed, with the control piston (23) being a valve piston of a control valve (31) and the pressure surface (57, 81) of the control piston (23) and the pressure surface (61, 77) of the piston section of the injection valve member (3) delimiting the control chamber (59, 79) on the same side, characterized in that the control piston (23) and the piston section of the injection valve member (3) enclose a further control chamber (27) which is connected to a fuel return line (63) when the control valve (31) is open and to the fuel inlet (19) when the control valve (31) is closed.
  2. Injector according to Claim 1, characterized in that an annular section (21) is formed on the control piston (23), in which annular section (21) the piston section of the injection valve member (3) is guided, with the further control chamber (27) being delimited by the piston section of the injection valve member (3) and the annular section (21) of the control piston (23).
  3. Injector according to Claim 1 or 2, characterized in that the pressure surface of the control piston (23) is formed by a lower end surface (57) on the annular section (21) and the pressure surface of the piston section of the injection valve member (3) is formed by a shoulder (61).
  4. Injector according to one of Claims 1 to 3, characterized in that the further control chamber (27), which is delimited by the injection valve member (3) and by the control piston (23), is connected by means of a connecting duct (39) to a valve chamber (37) which surrounds the control piston (23).
  5. Injector according to Claim 4, characterized in that a throttle element (95) is held in the connecting duct (39) which serves to connect the further control chamber (27), which is delimited by the injection valve member (3) and the control piston (23), to the valve chamber (37).
  6. Injector according to Claim 4 or 5, characterized in that the valve chamber (37) is connected by means of a throttle element (41) to the fuel inlet (19).
  7. Injector according to Claim 1, characterized in that an annular section (75) is formed on the piston section of the injection valve member (3), in which annular section (75) the control piston (23) is guided, with the further control chamber (27) being delimited by the control piston (23) and the annular section (75).
  8. Injector according to Claim 7, characterized in that an end surface (77) on the annular section (75) of the piston section of the injection valve member (3) and a shoulder (81) on the control piston (23) delimit the control chamber (79) on the same side.
  9. Injector according to one of the preceding claims, characterized in that the actuator (45) is connected to the control piston (23).
  10. Injector according to one of the preceding claims, characterized in that the actuator (45) is connected to a booster piston (71), with an end surface (69) of the booster piston (71) delimiting a booster chamber (67) which is delimited on the opposite side by an upper end surface (65) of the control piston (23).
  11. Injector according to one of the preceding claims, characterized in that a compensating element (53) is held between the actuator (45) and the housing (51), which compensating element (53) serves to compensate the residual error in coefficients of thermal expansion between actuator (45) and housing (51).
  12. Injector according to one of the preceding claims, characterized in that the actuator (45) is held in a housing (51) which is produced from a material whose coefficient of thermal expansion corresponds to that of the actuator (45).
EP07730183A 2006-08-07 2007-06-15 Fuel injector with direct needle control and servo valve assistance Not-in-force EP2052148B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006036780A DE102006036780A1 (en) 2006-08-07 2006-08-07 Fuel injector with direct needle control and servo valve support
PCT/EP2007/055939 WO2008017538A1 (en) 2006-08-07 2007-06-15 Fuel injector with direct needle control and servo valve assistance

Publications (2)

Publication Number Publication Date
EP2052148A1 EP2052148A1 (en) 2009-04-29
EP2052148B1 true EP2052148B1 (en) 2010-05-12

Family

ID=38516142

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07730183A Not-in-force EP2052148B1 (en) 2006-08-07 2007-06-15 Fuel injector with direct needle control and servo valve assistance

Country Status (6)

Country Link
US (1) US7946509B2 (en)
EP (1) EP2052148B1 (en)
CN (1) CN101501324A (en)
AT (1) ATE467758T1 (en)
DE (2) DE102006036780A1 (en)
WO (1) WO2008017538A1 (en)

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DE102009000181A1 (en) * 2009-01-13 2010-07-15 Robert Bosch Gmbh Fuel injector
FR2941746A1 (en) * 2009-02-02 2010-08-06 Renault Sas DEVICE FOR INJECTING LIQUID, IN PARTICULAR FUEL, WITH ELECTROACTIVE ACTUATOR.
FR2941745A3 (en) * 2009-02-02 2010-08-06 Renault Sas Liquid i.e. fuel, injecting device, has electroactive material actuator triggering movement of head of needle, needle piston carried by end of needle, and hydraulic chamber connected to duct to maintain chamber supplied with liquid
DE102009002897A1 (en) * 2009-05-07 2010-11-11 Robert Bosch Gmbh fuel injector
FR2947200B1 (en) * 2009-06-25 2011-08-19 Prospection & Inventions INSTALLATION TOOL FOR FIXING ELEMENTS WITH FUEL INJECTOR
DE102010023698A1 (en) 2010-06-14 2011-12-15 Continental Automotive Gmbh Injector with direct and servo drive
DE102012005319A1 (en) * 2012-03-19 2013-09-19 L'orange Gmbh Injector assembly for fuel injector of motor vehicle, has actuating element that generates pressure in fluid, which is increased with respect to system high pressure, where injector assembly is formed to be effective against pressure force
US9309846B2 (en) * 2012-11-12 2016-04-12 Mcalister Technologies, Llc Motion modifiers for fuel injection systems
DK177782B1 (en) * 2013-05-29 2014-06-30 Man Diesel & Turbo Deutschland Internal combustion engine and a water-in-fuel emulsion creation and injection pump for it
DE102014209961A1 (en) * 2014-05-26 2015-11-26 Robert Bosch Gmbh Nozzle assembly for a fuel injector and fuel injector
DE102014215774B4 (en) * 2014-08-08 2016-06-30 Continental Automotive Gmbh Device for a high-pressure pump for a motor vehicle
JP6674799B2 (en) * 2015-06-05 2020-04-01 株式会社Ｓｏｋｅｎ Fuel injection valve and control device for fuel injection valve
JP6926693B2 (en) * 2017-06-06 2021-08-25 株式会社Ｓｏｋｅｎ Fuel injection device, control device and fuel injection system
JP6993900B2 (en) * 2018-02-26 2022-01-14 株式会社Soken Fuel injection device
JP7014637B2 (en) * 2018-02-26 2022-02-01 株式会社Soken Fuel injection device
CN114151255B (en) * 2021-11-19 2023-02-14 哈尔滨工程大学 Electromagnetic valve direct-drive oil injection-pressurization double-acting oil injector

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Also Published As

Publication number Publication date
DE102006036780A1 (en) 2008-02-21
US7946509B2 (en) 2011-05-24
CN101501324A (en) 2009-08-05
US20090179086A1 (en) 2009-07-16
WO2008017538A1 (en) 2008-02-14
DE502007003775D1 (en) 2010-06-24
ATE467758T1 (en) 2010-05-15
EP2052148A1 (en) 2009-04-29

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