EP1478840B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1478840B1
EP1478840B1 EP03704252A EP03704252A EP1478840B1 EP 1478840 B1 EP1478840 B1 EP 1478840B1 EP 03704252 A EP03704252 A EP 03704252A EP 03704252 A EP03704252 A EP 03704252A EP 1478840 B1 EP1478840 B1 EP 1478840B1
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EP
European Patent Office
Prior art keywords
pressure
valve
chamber
control
valve needle
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03704252A
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German (de)
French (fr)
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EP1478840A1 (en
Inventor
Detlev Potz
Peter Boehland
Thomas Kuegler
Andreas Koeninger
Predrag Nunic
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1478840A1 publication Critical patent/EP1478840A1/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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/21—Fuel-injection apparatus with piezoelectric or magnetostrictive elements
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve is for example from the published patent application DE 41 15 477 A1 known.
  • a housing there is an outer valve needle and an inner valve needle guided therein. Both valve needles cooperate with their combustion chamber-side end with a valve seat surface in which two rows of injection openings are formed.
  • the outer injection opening row is controlled by the outer valve needle, the inner row of injection openings correspondingly by the inner valve needle.
  • fuel is supplied under high pressure to the injection openings, which discharges under the control of the valve needles through the injection openings and is injected from there into the combustion chamber of the internal combustion engine.
  • a control chamber In the housing of the fuel injection valve, a control chamber is formed, the pressure of which acts on the end face of a pressure piston which is connected to the inner valve needle. In this way, results from the pressure in the control chamber, a closing force on the inner valve needle, which holds them in contact with the valve seat surface.
  • the control room can over a control valve connected to the injection pressure or be relieved in a leakage oil space, so that in this way the pressure in the control room can be controlled.
  • the opening force on the inner and outer valve needle is generated in the cited prior art by application of fuel pressure of each formed on the valve needles pressure surface, wherein the pressure at which open the valve needles, is referred to as the opening pressure.
  • the known fuel injection valve has the disadvantage that the closing force on the outer valve needle is not generated hydraulically, but via a firmly biased closing spring. Therefore, the opening pressure of the outer valve needle is not controllable, and it can be injected through the outer Einspritzö réelles #2 only with a minimum pressure corresponding to the opening pressure of the outer valve needle.
  • the prior art has the disadvantage that the control valve, which regulates the pressure in the control chamber, is designed as a 3/2-way valve with slide seat, so that it is relatively complicated and therefore expensive to manufacture. It is thus not possible in the known fuel injection valve to control the injection cross section as desired.
  • an injection valve with an outer and an inner valve needle is known, which are guided into each other and each control an injection opening row.
  • a first control chamber which acts on the outer valve needle
  • a second control chamber which acts on the inner valve needle, formed, wherein both control chambers are interconnected.
  • the control chamber Via a solenoid valve, the control chamber can be connected to a leakage oil space, so that the pressure in the first control chamber is lowered and - depending on the duration that opens the solenoid valve - in the second control chamber.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that both the inner and the outer valve needle via only one control valve can be controlled.
  • a control chamber is formed, which is connected to the high pressure passage and beyond with a control pressure chamber. Due to the pressure in the control chamber, a closing force is exerted on the outer valve needle, at least indirectly.
  • a control valve is formed, through which the control chamber is connectable to a leakage oil chamber, so that the pressure in the control chamber and, because of the connection with the control chamber, also in the control pressure chamber via the control valve can be lowered well below the injection pressure, so that the closing force can be controlled to the inner and the outer valve needle.
  • the control valve has a valve space connected to the control space and a valve member which is controlled by an actuator.
  • the actuator is designed here as an electrical piezo actuator. As a result, the valve member can be precisely controlled and drive the valve member directly to the desired position.
  • valve member cooperates in a first switching position with a first valve seat and in a second switching position with a second valve seat, wherein the valve chamber is sealed in the first switching position against the leakage oil chamber and is connected in the second switching position with the leakage oil space.
  • valve chamber of the control valve can be connected to the high-pressure passage via a connecting channel, with the valve member closing the connecting channel when it rests against the second valve seat.
  • connection channel is ineffective and does not interfere with the further function of the pressure control in the control room.
  • the high-pressure passage is released, and it can flow fuel at the injection pressure in the valve chamber and from there into the control chamber.
  • an outer pressure piston is arranged in the housing, which is connected to the outer valve needle and whose end face defines the control chamber. In this way, a hydraulic force results from the pressure in the control chamber on the end face of the outer pressure piston, so that a closing force is exerted on the outer valve needle.
  • the outer pressure piston comes in the opening stroke of the outer valve needle to a wall of the control chamber to the system, so that the connection of the control chamber is interrupted to the high-pressure channel.
  • control pressure chamber is formed in the outer pressure piston and connected by a bore in the outer pressure piston with the control chamber.
  • the leakage oil space compared to the injection pressure significantly lower pressure, preferably atmospheric pressure.
  • FIG. 1 is a longitudinal section through an inventive fuel injection valve shown.
  • the fuel injection valve has a housing 1, which comprises a valve body 3, an intermediate body 7, an intermediate disk 9, a control body 12 and a holding body 14, wherein these components abut each other in the enumerated sequence. All these parts of the housing 1 are hereby pressed together by a clamping nut 5 with their contact surfaces.
  • a high-pressure passage 10 is formed, which is connected at one end to a high-pressure fuel source, not shown in the drawing and extends through the holding body 14, the control body 12, the washer 9 and the intermediate body 7 into the valve body 3.
  • the high pressure passage 10 opens into a pressure chamber 26, which is designed as a radial extension of a bore 16 formed in the valve body 3.
  • the bore 16 is closed at its combustion chamber end by a seat surface 24, wherein in the seat 24 injection openings 30 are formed, which connect the bore 16 with the combustion chamber of the internal combustion engine.
  • a piston-shaped, outer valve needle 20 is arranged, which is sealingly guided in a combustion chamber remote from the bore 16.
  • the outer valve needle 20 tapers from the guided portion to the combustion chamber to form a pressure shoulder 27 and merges at its combustion chamber end in a valve sealing surface 32, with which it bears against the seat surface 24 in the closed position.
  • annular channel 28 is formed, which connects the pressure chamber 26 with the seat surface 24, wherein the pressure shoulder 27 is disposed at the level of the pressure chamber 26.
  • the outer valve needle 20 closes the injection openings 30 against the fuel in the annular channel 28, so that fuel can flow into the injection openings 30 only when the outer valve needle 20 lifted from the seat surface 24.
  • the outer valve needle 20 is designed as a hollow needle and has a longitudinal bore 21.
  • an inner valve needle 22 is longitudinally displaceable, which also comes with its combustion chamber end end to the seat surface 24 in the closed position to the plant.
  • FIG. 2 is an enlargement of the section marked II FIG. 1 shown, so the area of the seat 24.
  • the injection openings 30 in the seat surface 24 are grouped in an outer injection opening row 130 and an inner injection opening row 230.
  • the outer valve needle 20 has at its combustion chamber end, a conical valve sealing surface 32, which has a larger opening angle than the likewise conical seat 24. As a result, at the outer edge of the sealing surface 32, a sealing edge 34 is formed in the closed position of the outer valve needle 20 at the seat 24 comes to rest.
  • the sealing edge 34 is in this case arranged upstream of the outer injection opening row 130, so that upon contact of the sealing edge 34 on the seat surface 24, the injection openings of the outer injection opening row 130 are sealed against the annular channel 28.
  • a conical pressure surface 36 is formed, which in turn adjoins an also conical conical surface 38, which forms the end of the inner valve needle 22.
  • a sealing edge 37 is formed, which comes into abutment in the closed position of the inner valve needle 22 on the seat surface 24.
  • the installation of the sealing edge 37 in this case takes place between the outer injection opening row 130 and the inner injection opening 230, so that when the inner valve needle 22 on the seat 24 only the inner row of injection openings 230 is sealed against the annular space 28, but not the outer row of injection openings 130th
  • FIG. 3 shows an enlargement of FIG. 1
  • a piston bore 45 is formed, in which a pressure piston 40 is arranged, which abuts with its end facing the combustion chamber on the outer valve needle 20 in the designated III section, ie in the region of the intermediate body 7, intermediate disc 9 and control body.
  • a spring chamber 43 is formed, in which between a contact surface 41 of the spring chamber 43 and an annular surface 39 of the outer pressure piston 40 a closing spring 44 is arranged under pressure bias, which surrounds the outer pressure piston 40 on a part of its length.
  • the outer pressure piston 40 is pressed in the direction of the valve body 3 and thus also the outer valve needle 20 in the direction of the seat 24.
  • a guide bore 47 is formed in the longitudinal direction, in which an inner pressure piston 42 is guided , which rests with its combustion chamber end on the inner valve needle 22.
  • the inner pressure piston 42 is longitudinally displaceable in the outer pressure piston 40 and moves synchronously with the inner valve needle 22.
  • a control chamber 50 is limited, via a in the outer pressure piston 40th formed connecting bore 55 is connected to a control pressure chamber 52 which is bounded by the guide bore 47 and the combustion chamber facing away from end face 53 of the inner pressure piston 42.
  • the control chamber 50 is connected via an inlet throttle 70 to the high-pressure passage 10 and via an outlet throttle 72 with a formed in the control body 12 valve chamber 68.
  • a valve member 60 is arranged, which is formed substantially hemispherical and forms a control valve 58.
  • the flattened side faces the intermediate disk 9, while the hemispherical side of the valve member 60 is connected to a pressure piece 48, which is guided in a receiving body 13 arranged in the holding body 14.
  • the pressure piece 48 is in this case longitudinally displaceable by an actuator 46 and thereby also moves the valve member 60 in the valve chamber 68, wherein the actuator is designed here as a piezoelectric actuator.
  • the pressure member 48 is surrounded by a leakage oil chamber 78, which always has a low pressure because of its connection with a drain oil system, not shown in the drawing.
  • the intermediate disc 9 faces away in the valve chamber 68 a first valve seat 62 is formed, on which the valve member 60 can come with its spherical valve sealing surface 66 to the plant.
  • FIG. 4 shows a cross section through FIG. 3 along the line IV-IV.
  • the course of the transverse channel 76 as a semicircular groove on the abutment surface 7 of the intermediate disc 9 facing the intermediate body 7 becomes clear here.
  • the inlet throttle 70, the outlet throttle 72, the connecting channel 74 and the high-pressure passage 10 are also visible.
  • the function of the fuel injection valve is as follows: At the beginning of the injection cycle, the fuel injection valve is in the closed position, ie both the outer valve needle 20 and the inner valve needle 22 are in contact with the seat surface 24 and close both the inner injection opening row 230 and the outer injection opening row 130. Since the valve member 60 rests against the first valve seat 62, both the control chamber 50 and the control pressure chamber 52 are connected via the inlet throttle 70 to the high pressure passage 10, so that both the control chamber 50 and the control pressure chamber 52, the high fuel pressure of the high pressure passage 10 prevails which corresponds to the injection pressure.
  • the end face 51 of the outer pressure piston 40 has a larger hydraulically effective area than the pressure shoulder 27 of the outer valve needle 20, so that the outer valve needle 20 remains in the closed position.
  • the force of the closing spring 44 plays only a minor role; the closing spring 44 is mainly used to hold the outer valve needle 20 in the closed position, when the internal combustion engine is not working. Also in the valve chamber 68 prevails through the connection via the connecting channel 74 and also via the outlet throttle 72, the pressure in the high-pressure passage 10. In the leakage oil chamber 78, however, there is a low pressure, which generally corresponds approximately to the atmospheric pressure.
  • the actuator 46 is actuated, and the valve member 60 moves together with the pressure piece 48 from the first valve seat 62 away to the second valve seat 64.
  • the valve chamber 68 is connected to the leakage oil chamber 78, so that the valve chamber 68 and also the control chamber 50 are relieved of pressure via the outlet throttle 72.
  • the connecting channel 74 is closed, so that no more fuel can flow into the valve chamber 68 via the transverse channel 76.
  • the inlet throttle 70 and the outlet throttle 72 are dimensioned such that the pressure in the control chamber 50 drops, but not to the level of the leakage oil chamber 78.
  • valve member 60 If it is intended, for example for a pilot injection, to inject fuel into the combustion chamber of the internal combustion engine only through the outer injection opening row 130, then, by actuating the actuator 46, the valve member 60 must be moved again so that the connection of the valve space 68 to the leakage oil space 78 is interrupted. As a result, the connection of the high-pressure passage 10 via the connecting channel 74 to the valve chamber 68 is restored, so that fuel flows with injection pressure from the high-pressure passage 10 via the outlet throttle 72 and via the inlet throttle 70 into the control chamber 50. There again, a high fuel pressure level builds up, which presses the outer pressure piston 40 and thus also the outer valve needle 20 back into the closed position.
  • valve member 60 remains in abutment with the second valve seat 64.
  • the feed throttle 70 is closed by abutment of the end face 51 of the outer pressure piston 40 on the intermediate disk 9.
  • the pressure in the control pressure chamber 52 can thus further drop via the outlet throttle 72 and the connection of the valve chamber 68 to the leakage oil chamber 78 until the hydraulic force on the pressure surface 36 of the inner valve needle 22 is greater than the hydraulic force on the end face 53 of the inner pressure piston 42nd
  • the inner valve needle 22 now lifts with the sealing edge 37 from the seat surface 24, and fuel is additionally injected through the inner injection port row 230.
  • a selective opening can also be achieved by means of a middle position of the control valve 58.
  • the valve member 60 is moved by means of the piezo-actuator 48 in a middle position between the first valve seat 62 and the second valve seat 64, so that all connections to the valve chamber 68 are opened.
  • fuel flows from the valve chamber 68 into the leakage oil chamber 78, on the other hand via the connecting channel 74 constantly in the valve chamber 68, so that only a certain pressure drop in the valve chamber 68 sets, which is still significantly above the pressure of the leakage oil chamber 78.
  • This pressure is sufficient to hold the inner valve needle 22 in its closed position, but the closing force on the outer valve needle 20 is reduced to the extent that it opens.
  • the injection is also terminated here again in the manner already described above by switching the control valve 58.
  • the actuator 46 is a piezoelectric actuator in this embodiment.
  • the valve member 60 in the valve chamber 68 requires only a small stroke for its function, as it can usually be applied by a piezoelectric actuator. If necessary, a hydraulic translator can be provided with which larger strokes can be realized and which is well known from the prior art.
  • piezo actuators have the advantage that they can switch extremely fast. It is thus possible without any problems in the manner described above to carry out a precise pre-injection only through the outer injection opening row 130.

Abstract

A fuel injection valve for internal combustion engines, having a housing in which an outer valve needle and an inner valve needle guided in it are disposed in a bore. The outer valve needle controls an outer row of injection openings, and the inner valve needle controls an inner row of injection openings, to which rows of injection openings fuel is delivered at an injection pressure through a high-pressure conduit embodied in the housing. A control pressure chamber in the housing can be made to communicate with the high-pressure conduit, and by means of its pressure, a closing force is exerted at least indirectly on the inner valve needle. The high-pressure conduit communicates with a control chamber, by whose pressure a closing force is exerted at least indirectly on the outer valve needle, and the control chamber communicates with the control pressure chamber. A control valve is disposed in a housing, and by means of the control valve, the control chamber can be made to communicate with a leak fuel chamber.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Ein derartiges Kraftstoffeinspritzventil ist beispielsweise aus der Offenlegungsschrift DE 41 15 477 A1 bekannt. In einem Gehäuse befindet sich eine äußere Ventilnadel und eine darin geführte innere Ventilnadel. Beide Ventilnadeln wirken mit ihrem brennraumseitigen Ende mit einer Ventilsitzfläche zusammen, in der zwei Reihen von Einspritzöffnungen ausgebildet sind. Die äußere Einspritzöffnungsreihe wird hierbei von der äußeren Ventilnadel gesteuert, die innere Einspritzöffnungsreihe entsprechend von der inneren Ventilnadel. Durch einen im Gehäuse ausgebildeten Hochdruckkanal wird den Einspritzöffnungen Kraftstoff unter hohem Druck zugeleitet, der gesteuert von den Ventilnadeln durch die Einspritzöffnungen austritt und von dort in den Brennraum der Brennkraftmaschine eingespritzt wird.The invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1. Such a fuel injection valve is for example from the published patent application DE 41 15 477 A1 known. In a housing there is an outer valve needle and an inner valve needle guided therein. Both valve needles cooperate with their combustion chamber-side end with a valve seat surface in which two rows of injection openings are formed. In this case, the outer injection opening row is controlled by the outer valve needle, the inner row of injection openings correspondingly by the inner valve needle. By means of a high-pressure channel formed in the housing, fuel is supplied under high pressure to the injection openings, which discharges under the control of the valve needles through the injection openings and is injected from there into the combustion chamber of the internal combustion engine.

Im Gehäuse des Kraftstoffeinspritzventils ist ein Steuerraum ausgebildet, dessen Druck auf die Stirnseite eines Druckkolbens wirkt, der mit der inneren Ventilnadel verbunden ist. Auf diese Weise ergibt sich über den Druck im Steuerraum eine Schließkraft auf die innere Ventilnadel, die diese in Anlage an der Ventilsitzfläche hält. Der Steuerraum kann über ein Steuerventil mit dem Einspritzdruck verbunden oder auch in einen Leckölraum entlastet werden, so dass auf diese Weise der Druck im Steuerraum gesteuert werden kann. Die Öffnungskraft auf die innere bzw. äußere Ventilnadel wird im genannten Stand der Technik durch Beaufschlagung mit Kraftstoffdruck einer jeweils an den Ventilnadeln ausgebildeten Druckfläche erzeugt, wobei der Druck, bei dem die Ventilnadeln öffnen, als Öffnungsdruck bezeichnet wird.In the housing of the fuel injection valve, a control chamber is formed, the pressure of which acts on the end face of a pressure piston which is connected to the inner valve needle. In this way, results from the pressure in the control chamber, a closing force on the inner valve needle, which holds them in contact with the valve seat surface. The control room can over a control valve connected to the injection pressure or be relieved in a leakage oil space, so that in this way the pressure in the control room can be controlled. The opening force on the inner and outer valve needle is generated in the cited prior art by application of fuel pressure of each formed on the valve needles pressure surface, wherein the pressure at which open the valve needles, is referred to as the opening pressure.

Das bekannte Kraftstoffeinspritzventil weist hierbei jedoch den Nachteil auf, dass die Schließkraft auf die äußere Ventilnadel nicht hydraulisch erzeugt wird, sondern über eine fest vorgespannte Schließfeder. Deshalb ist der Öffnungsdruck der äußeren Ventilnadel nicht regelbar, und es kann durch die äußere Einspritzöffnungsreihe nur mit einem Mindestdruck, der dem Öffnungsdruck der äußeren Ventilnadel entspricht, eingespritzt werden. Darüber hinaus weist der Stand der Technik den Nachteil auf, dass das Steuerventil, welches den Druck im Steuerraum regelt, als 3/2-Wege-Ventil mit Schiebersitz ausgebildet ist, so dass es relativ kompliziert und damit teuer in der Herstellung ist. Es ist bei dem bekannten Kraftstoffeinspritzventil somit nicht möglich, den Einspritzquerschnitt beliebig zu steuern.However, the known fuel injection valve has the disadvantage that the closing force on the outer valve needle is not generated hydraulically, but via a firmly biased closing spring. Therefore, the opening pressure of the outer valve needle is not controllable, and it can be injected through the outer Einspritzöffnungsreihe only with a minimum pressure corresponding to the opening pressure of the outer valve needle. In addition, the prior art has the disadvantage that the control valve, which regulates the pressure in the control chamber, is designed as a 3/2-way valve with slide seat, so that it is relatively complicated and therefore expensive to manufacture. It is thus not possible in the known fuel injection valve to control the injection cross section as desired.

Aus der DE 101 22 241 A1 ist ein Einspritzventil mit einer äußeren und einer inneren Ventilnadel bekannt, die ineinander geführt sind und jeweils eine Einspritzöffnungsreihe steuern. Im Einspritzventil ist ein erster Steuerraum, der die äußere Ventilnadel beaufschlagt, und ein zweiter Steuerraum, der die innere Ventilnadel beaufschlagt, ausgebildet, wobei beide Steuerräume miteinander verbunden sind. Über ein Magnetventil kann der Steuerraum mit einem Leckölraum verbunden werden, so dass sich der Druck im ersten Steuerraum erniedrigt und - je nach Dauer, die das Magnetventil öffnet - auch im zweiten Steuerraum.From the DE 101 22 241 A1 an injection valve with an outer and an inner valve needle is known, which are guided into each other and each control an injection opening row. In the injection valve, a first control chamber, which acts on the outer valve needle, and a second control chamber, which acts on the inner valve needle, formed, wherein both control chambers are interconnected. Via a solenoid valve, the control chamber can be connected to a leakage oil space, so that the pressure in the first control chamber is lowered and - depending on the duration that opens the solenoid valve - in the second control chamber.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass sowohl die innere als auch die äußere Ventilnadel über lediglich ein Steuerventil ansteuerbar sind. Im Gehäuse ist ein Steuerraum ausgebildet, der mit dem Hochdruckkanal und darüber hinaus mit einem Steuerdruckraum verbunden ist. Durch den Druck im Steuerraum wird eine Schließkraft auf die äußere Ventilnadel zumindest mittelbar ausgeübt. Im Gehäuse ist ein Steuerventil ausgebildet, durch das der Steuerraum mit einem Leckölraum verbindbar ist, so dass der Druck im Steuerraum und, wegen der Verbindung mit dem Steuerraum, auch im Steuerdruckraum über das Steuerventil deutlich unter den Einspritzdruck absenkbar ist, so dass sich die Schließkraft auf die innere bzw. die äußere Ventilnadel steuern lässt. Über eine geeignete Schaltcharakteristik des Steuerventils und durch geeignet dimensionierte Zu- bzw. Abläufe des Steuerraums und dessen Verbindung mit dem Steuerdruckraum lässt sich eine separate Ansteuerung der äußeren Ventilnadel oder wahlweise beider Ventilnadeln erreichen.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that both the inner and the outer valve needle via only one control valve can be controlled. In the housing, a control chamber is formed, which is connected to the high pressure passage and beyond with a control pressure chamber. Due to the pressure in the control chamber, a closing force is exerted on the outer valve needle, at least indirectly. In the housing, a control valve is formed, through which the control chamber is connectable to a leakage oil chamber, so that the pressure in the control chamber and, because of the connection with the control chamber, also in the control pressure chamber via the control valve can be lowered well below the injection pressure, so that the closing force can be controlled to the inner and the outer valve needle. By means of a suitable switching characteristic of the control valve and by suitably dimensioned inflows and outflows of the control chamber and its connection to the control pressure chamber, a separate actuation of the outer valve needle or alternatively of both valve needles can be achieved.

Das Steuerventil weist einen mit dem Steuerraum verbundenen Ventilraum auf und ein Ventilglied, das durch einen Aktor gesteuert wird. Der Aktor ist hierbei als elektrischer Piezo Aktor ausgebildet. Hierdurch lässt sich das Ventilglied präzise steuern und das Ventilglied unmittelbar auf die gewünschte Position fahren.The control valve has a valve space connected to the control space and a valve member which is controlled by an actuator. The actuator is designed here as an electrical piezo actuator. As a result, the valve member can be precisely controlled and drive the valve member directly to the desired position.

In einer vorteilhaften Ausgestaltung wirkt das Ventilglied in einer ersten Schaltstellung mit einem ersten Ventilsitz zusammen und in einer zweiten Schaltstellung mit einem zweiten Ventilsitz, wobei der Ventilraum in der ersten Schaltstellung gegen den Leckölraum abgedichtet ist und in der zweiten Schaltstellung mit dem Leckölraum verbunden ist. Durch dieses Ventilglied lässt sich der Druck im Steuerraum präzise und ohne nennenswerte zeitliche Verzögerung steuern.In an advantageous embodiment, the valve member cooperates in a first switching position with a first valve seat and in a second switching position with a second valve seat, wherein the valve chamber is sealed in the first switching position against the leakage oil chamber and is connected in the second switching position with the leakage oil space. By means of this valve member, the pressure in the control room can be controlled precisely and without appreciable time delay.

In einer weiteren vorteilhaften Ausgestaltung ist der Ventilraum des Steuerventils über einen Verbindungskanal mit dem Hochdruckkanal verbindbar, wobei das Ventilglied bei seiner Anlage am zweiten Ventilsitz den Verbindungskanal verschließt. Bei Entlastung des Steuerraums wird somit der Verbindungskanal unwirksam und stört die weitere Funktion der Druckregelung im Steuerraum nicht. Bei Betätigung des Steuerventils und Bewegung des Ventilgliedes zum ersten Ventilsitz wird der Hochdruckkanal freigegeben, und es kann Kraftstoff mit dem Einspritzdruck in den Ventilraum und von dort in den Steuerraum strömen. Hierdurch wird nach Beendigung der Einspritzung sehr schnell ein hoher Druck im Steuerraum aufgebaut, so dass sich eine starke Schließkraft auf die äußere Ventilnadel und damit auch auf die innere Ventilnadel ergibt.In a further advantageous embodiment, the valve chamber of the control valve can be connected to the high-pressure passage via a connecting channel, with the valve member closing the connecting channel when it rests against the second valve seat. Upon discharge of the control chamber thus the connection channel is ineffective and does not interfere with the further function of the pressure control in the control room. Upon actuation of the Control valve and movement of the valve member to the first valve seat, the high-pressure passage is released, and it can flow fuel at the injection pressure in the valve chamber and from there into the control chamber. As a result, a high pressure in the control chamber is very quickly built after completion of the injection, so that there is a strong closing force on the outer valve needle and thus also on the inner valve needle.

In einer weiteren vorteilhaften Ausgestaltung ist im Gehäuse ein äußerer Druckkolben angeordnet, der mit der äußeren Ventilnadel verbunden ist und dessen Stirnfläche den Steuerraum begrenzt. Auf diese Weise ergibt sich eine hydraulische Kraft durch den Druck im Steuerraum auf die Stirnfläche des äußeren Druckkolbens, so dass eine Schließkraft auf die äußere Ventilnadel ausgeübt wird. Durch die Trennung der Funktion der druckbeaufschlagten Druckfläche und der Ventilnadel lassen sich beide Teile getrennt voneinander optimieren.In a further advantageous embodiment, an outer pressure piston is arranged in the housing, which is connected to the outer valve needle and whose end face defines the control chamber. In this way, a hydraulic force results from the pressure in the control chamber on the end face of the outer pressure piston, so that a closing force is exerted on the outer valve needle. By separating the function of the pressurized pressure surface and the valve needle, both parts can be optimized separately.

In einer weiteren vorteilhaften Ausgestaltung kommt der äußere Druckkolben bei der Öffnungshubbewegung der äußeren Ventilnadel an einer Wand des Steuerraums zur Anlage, so dass die Verbindung des Steuerraums zum Hochdruckkanal unterbrochen wird. Hierdurch strömt bei geöffnetem Kraftstoffeinspritzventil kein Kraftstoff mehr in den Steuerraum, so dass die Leckölverluste des Kraftstoffeinspritzventils minimiert werden.In a further advantageous embodiment, the outer pressure piston comes in the opening stroke of the outer valve needle to a wall of the control chamber to the system, so that the connection of the control chamber is interrupted to the high-pressure channel. As a result, fuel no longer flows into the control chamber when the fuel injection valve is open, so that the leakage oil losses of the fuel injection valve are minimized.

In einer weiteren vorteilhaften Ausgestaltung ist der Steuerdruckraum im äußeren Druckkolben ausgebildet und durch eine Bohrung im äußeren Druckkolben mit dem Steuerraum verbunden. Diese Konstruktion erlaubt eine direkte Ansteuerung der inneren Ventilnadel, die sich in der äußeren Ventilnadel befindet, und ergibt darüber hinaus eine sehr platzsparende Konstruktion.In a further advantageous embodiment, the control pressure chamber is formed in the outer pressure piston and connected by a bore in the outer pressure piston with the control chamber. This design allows a direct control of the inner valve needle, which is located in the outer valve needle, and also results in a very space-saving design.

In einer vorteilhaften Ausgestaltung herrscht im Leckölraum ein gegenüber dem Einspritzdruck deutlich niedrigerer Druck, vorzugsweise Atmosphärendruck. Je niedriger der Druck im Leckölraum, desto größer sind die Druckunterschiede gegenüber dem Einspritzdruck, so dass sich entsprechend auch größere Kräfte auf die innere bzw. äußere Ventilnadel realisieren lassen und damit kürzere Schaltzeiten.In an advantageous embodiment prevails in the leakage oil space compared to the injection pressure significantly lower pressure, preferably atmospheric pressure. The lower the pressure in the leakage oil space, the greater the pressure differences compared to the injection pressure, so that correspondingly larger forces can be realized on the inner or outer valve needle and thus shorter switching times.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Zeichnung und der Beschreibung entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be taken from the drawing and the description.

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils gezeigt. Es zeigt

  • Figur 1 einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil in seinem wesentlichen Bereich,
  • Figur 2 eine Vergrößerung von Figur 1 im Bereich des brennraumseitigen Endes des Einspritzventils, wobei dieser Ausschnitt in Figur 1 mit II bezeichnet ist,
  • Figur 3 eine Vergrößerung von Figur 1 im mit III bezeichneten Bereich und
  • Figur 4 einen Querschnitt durch den in Figur 3 gezeigten Ausschnitt entlang der Linie IV-IV.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
  • FIG. 1 a longitudinal section through a fuel injection valve according to the invention in its essential area,
  • FIG. 2 an enlargement of FIG. 1 in the region of the combustion chamber end of the injection valve, wherein this cutout in FIG. 1 denoted by II,
  • FIG. 3 an enlargement of FIG. 1 in the area designated III and
  • FIG. 4 a cross section through the in FIG. 3 shown section along the line IV-IV.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das einen Ventilkörper 3, einem Zwischenkörper 7, eine Zwischenscheibe 9, einen Steuerkörper 12 und einen Haltekörper 14 umfasst, wobei diese Bauteile in der aufgezählten Reihenfolge jeweils aneinander anliegen. Alle diese Teile des Gehäuses 1 werden hierbei durch eine Spannmutter 5 mit ihren Anlageflächen aneinander gepresst. Im Gehäuse 1 ist ein Hochdruckkanal 10 ausgebildet, der an einem Ende mit einer in der Zeichnung nicht dargestellten Kraftstoffhochdruckquelle verbunden ist und durch den Haltekörper 14, den Steuerkörper 12, die Zwischenscheibe 9 und den Zwischenkörper 7 bis in den Ventilkörper 3 reicht. Im Ventilkörper 3 mündet der Hochdruckkanal 10 in einen Druckraum 26, der als radiale Erweiterung einer im Ventilkörper 3 ausgebildeten Bohrung 16 ausgeführt ist. Die Bohrung 16 wird an ihrem brennraumseitigen Ende von einer Sitzfläche 24 verschlossen, wobei in der Sitzfläche 24 Einspritzöffnungen 30 ausgebildet sind, die die Bohrung 16 mit dem Brennraum der Brennkraftmaschine verbinden. In der Bohrung 16 ist eine kolbenförmige, äußere Ventilnadel 20 angeordnet, die in einem brennraumabgewandten Abschnitt der Bohrung 16 dichtend geführt ist. Die äußere Ventilnadel 20 verjüngt sich ausgehend vom geführten Abschnitt dem Brennraum zu unter Bildung einer Druckschulter 27 und geht an ihrem brennraumseitigen Ende in eine Ventildichtfläche 32 über, mit der sie an der Sitzfläche 24 in Schließstellung anliegt. Zwischen der äußeren Ventilnadel 20 und der Wand der Bohrung 16 ist ein Ringkanal 28 ausgebildet, der den Druckraum 26 mit der Sitzfläche 24 verbindet, wobei die Druckschulter 27 auf Höhe des Druckraums 26 angeordnet ist. In Schließstellung verschließt die äußere Ventilnadel 20 die Einspritzöffnungen 30 gegen den Kraftstoff im Ringkanal 28, so dass nur bei von der Sitzfläche 24 abgehobener äußerer Ventilnadel 20 Kraftstoff den Einspritzöffnungen 30 zuströmen kann.In FIG. 1 is a longitudinal section through an inventive fuel injection valve shown. The fuel injection valve has a housing 1, which comprises a valve body 3, an intermediate body 7, an intermediate disk 9, a control body 12 and a holding body 14, wherein these components abut each other in the enumerated sequence. All these parts of the housing 1 are hereby pressed together by a clamping nut 5 with their contact surfaces. In the housing 1, a high-pressure passage 10 is formed, which is connected at one end to a high-pressure fuel source, not shown in the drawing and extends through the holding body 14, the control body 12, the washer 9 and the intermediate body 7 into the valve body 3. In the valve body 3, the high pressure passage 10 opens into a pressure chamber 26, which is designed as a radial extension of a bore 16 formed in the valve body 3. The bore 16 is closed at its combustion chamber end by a seat surface 24, wherein in the seat 24 injection openings 30 are formed, which connect the bore 16 with the combustion chamber of the internal combustion engine. In the bore 16, a piston-shaped, outer valve needle 20 is arranged, which is sealingly guided in a combustion chamber remote from the bore 16. The outer valve needle 20 tapers from the guided portion to the combustion chamber to form a pressure shoulder 27 and merges at its combustion chamber end in a valve sealing surface 32, with which it bears against the seat surface 24 in the closed position. Between the outer valve needle 20 and the wall of the bore 16, an annular channel 28 is formed, which connects the pressure chamber 26 with the seat surface 24, wherein the pressure shoulder 27 is disposed at the level of the pressure chamber 26. In the closed position, the outer valve needle 20 closes the injection openings 30 against the fuel in the annular channel 28, so that fuel can flow into the injection openings 30 only when the outer valve needle 20 lifted from the seat surface 24.

Die äußere Ventilnadel 20 ist als Hohlnadel ausgeführt und weist eine Längsbohrung 21 auf. In der Längsbohrung 21 ist eine innere Ventilnadel 22 längsverschiebbar angeordnet, die mit ihrem brennraumseitigen Ende ebenfalls an der Sitzfläche 24 in Schließstellung zur Anlage kommt. In Figur 2 ist eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1 dargestellt, also der Bereich der Sitzfläche 24. Die Einspritzöffnungen 30 in der Sitzfläche 24 sind in einer äußeren Einspritzöffnungsreihe 130 und einer inneren Einspritzöffnungsreihe 230 gruppiert. Die äußere Ventilnadel 20 weist an ihrem brennraumseitigen Ende eine konische Ventildichtfläche 32 auf, die einen größeren Öffnungswinkel aufweist als die ebenfalls konisch ausgebildete Sitzfläche 24. Hierdurch ist an der äußeren Kante der Dichtfläche 32 eine Dichtkante 34 ausgebildet, die in Schließstellung der äußeren Ventilnadel 20 an der Sitzfläche 24 zur Anlage kommt. Die Dichtkante 34 ist hierbei stromaufwärts zur äußeren Einspritzöffnungsreihe 130 angeordnet, so dass bei Anlage der Dichtkante 34 an der Sitzfläche 24 die Einspritzöffnungen der äußeren Einspritzöffnungsreihe 130 gegen den Ringkanal 28 abgedichtet werden. Am brennraumseitigen Ende der inneren Ventilnadel 22 ist eine konische Druckfläche 36 ausgebildet, welche ihrerseits an eine ebenfalls konische Konusfläche 38 grenzt, die das Ende der inneren Ventilnadel 22 bildet. Am Übergang der Druckfläche 36 zur Konusfläche 38 ist eine Dichtkante 37 ausgebildet, die in Schließstellung der inneren Ventilnadel 22 an der Sitzfläche 24 zur Anlage kommt. Die Anlage der Dichtkante 37 erfolgt hierbei zwischen der äußeren Einspritzöffnungsreihe 130 und der inneren Einspritzöffnungsreihe 230, so dass bei Anlage der inneren Ventilnadel 22 an der Sitzfläche 24 nur die innere Einspritzöffnungsreihe 230 gegen den Ringraum 28 abgedichtet wird, nicht jedoch die äußere Einspritzöffnungsreihe 130.The outer valve needle 20 is designed as a hollow needle and has a longitudinal bore 21. In the longitudinal bore 21, an inner valve needle 22 is longitudinally displaceable, which also comes with its combustion chamber end end to the seat surface 24 in the closed position to the plant. In FIG. 2 is an enlargement of the section marked II FIG. 1 shown, so the area of the seat 24. The injection openings 30 in the seat surface 24 are grouped in an outer injection opening row 130 and an inner injection opening row 230. The outer valve needle 20 has at its combustion chamber end, a conical valve sealing surface 32, which has a larger opening angle than the likewise conical seat 24. As a result, at the outer edge of the sealing surface 32, a sealing edge 34 is formed in the closed position of the outer valve needle 20 at the seat 24 comes to rest. The sealing edge 34 is in this case arranged upstream of the outer injection opening row 130, so that upon contact of the sealing edge 34 on the seat surface 24, the injection openings of the outer injection opening row 130 are sealed against the annular channel 28. At the combustion chamber end of the inner valve needle 22, a conical pressure surface 36 is formed, which in turn adjoins an also conical conical surface 38, which forms the end of the inner valve needle 22. At the transition of the pressure surface 36 to the conical surface 38, a sealing edge 37 is formed, which comes into abutment in the closed position of the inner valve needle 22 on the seat surface 24. The installation of the sealing edge 37 in this case takes place between the outer injection opening row 130 and the inner injection opening 230, so that when the inner valve needle 22 on the seat 24 only the inner row of injection openings 230 is sealed against the annular space 28, but not the outer row of injection openings 130th

Figur 3 zeigt eine Vergrößerung von Figur 1 im mit III bezeichneten Ausschnitt, also im Bereich von Zwischenkörper 7, Zwischenscheibe 9 und Steuerkörper 12. Im Zwischenkörper 7 ist eine Kolbenbohrung 45 ausgebildet, in der ein Druckkolben 40 angeordnet ist, der mit seinem brennraumzugewandten Ende an der äußeren Ventilnadel 20 anliegt. Durch eine radiale Erweiterung der Kolbenbohrung 45 ist ein Federraum 43 ausgebildet, in dem zwischen einer Anlagefläche 41 des Federraums 43 und einer Ringfläche 39 des äußeren Druckkolbens 40 eine Schließfeder 44 unter Druckvorspannung angeordnet ist, die den äußeren Druckkolben 40 auf einem Teil seiner Länge umgibt. Durch die Vorspannung der Schließfeder 44 wird der äußere Druckkolben 40 in Richtung des Ventilkörpers 3 gedrückt und damit auch die äußere Ventilnadel 20 in Richtung der Sitzfläche 24. Im äußeren Druckkolben 40 ist eine Führungsbohrung 47 in Längsrichtung ausgebildet, in der ein innerer Druckkolben 42 geführt ist, der mit seinem brennraumseitigen Ende an der inneren Ventilnadel 22 anliegt. Der innere Druckkolben 42 ist im äußeren Druckkolben 40 längsverschiebbar und bewegt sich synchron mit der inneren Ventilnadel 22. Durch die Kolbenbohrung 45, die brennraumabgewandte Stirnseite 51 des äußeren Druckkolbens 40 und die Zwischenscheibe 9 wird ein Steuerraum 50 begrenzt, der über eine im äußeren Druckkolben 40 ausgebildete Verbindungsbohrung 55 mit einem Steuerdruckraum 52 verbunden ist, der von der Führungsbohrung 47 und der brennraumabgewandten Stirnseite 53 des inneren Druckkolbens 42 begrenzt wird. Der Steuerraum 50 ist über eine Zulaufdrossel 70 mit dem Hochdruckkanal 10 verbunden und über eine Ablaufdrossel 72 mit einem im Steuerkörper 12 ausgebildeten Ventilraum 68. Im Ventilraum 68 ist ein Ventilglied 60 angeordnet, das im wesentlichen halbkugelförmig ausgebildet ist und ein Steuerventil 58 bildet. Die abgeflachte Seite ist der Zwischenscheibe 9 zugewandt, während die halbkugelförmige Seite des Ventilglieds 60 mit einem Druckstück 48 verbunden ist, das in einem im Haltekörper 14 angeordneten Aufnahmekörper 13 geführt ist. Das Druckstück 48 ist hierbei durch einen Aktor 46 längsverschiebbar und bewegt dadurch auch das Ventilglied 60 im Ventilraum 68, wobei der Aktor hierbei als Piezo-Aktor ausgebildet ist. Das Druckstück 48 wird von einem Leckölraum 78 umgeben, der wegen seiner Verbindung mit einem in der Zeichnung nicht dargestellten Leckölsystem stets einen niedrigen Druck aufweist. Der Zwischenscheibe 9 abgewandt ist im Ventilraum 68 ein erster Ventilsitz 62 ausgebildet, an dem das Ventilglied 60 mit seiner kugeligen Ventildichtfläche 66 zur Anlage gelangen kann. Dem ersten Ventilsitz 62 gegenüberliegend ist im Ventilraum 68 ein zweiter Ventilsitz 64 ausgebildet, an dem das Ventilglied 60 mit der abgeflachten Seite zur Anlage kommen kann. Durch Anlage des Ventilglieds 60 am zweiten Ventilsitz 64 wird ein Verbindungskanal 74 verschlossen, der ebenfalls in den Ventilraum 68 mündet und der über einen Querkanal 76 mit dem Hochdruckkanal 10 verbunden ist. Figur 4 zeigt einen Querschnitt durch Figur 3 entlang der Linie IV-IV. Der Verlauf des Querkanals 76 als eine halbkreisförmige Nut an der dem Zwischenkörper 7 zugewandten Anlagefläche der Zwischenscheibe 9 wird hier deutlich. In dem dort dargestellten Querschnitt ist auch gut die Zulaufdrossel 70, die Ablaufdrossel 72, der Verbindungskanal 74 und der Hochdruckkanal 10 sichtbar. Die Funktion des Kraftstoffeinspritzventils ist wie folgt: Zu Beginn des Einspritzzyklus befindet sich das Kraftstoffeinspritzventil in Schließstellung, d.h. sowohl die äußere Ventilnadel 20 als auch die innere Ventilnadel 22 sind in Anlage an der Sitzfläche 24 und verschließen sowohl die innere Einspritzöffnungsreihe 230 als auch die äußere Einspritzöffnungsreihe 130. Da das Ventilglied 60 am ersten Ventilsitz 62 anliegt, sind sowohl der Steuerraum 50 als auch der Steuerdruckraum 52 über die Zulaufdrossel 70 mit dem Hochdruckkanal 10 verbunden, so dass sowohl im Steuerraum 50 als auch im Steuerdruckraum 52 der hohe Kraftstoffdruck des Hochdruckkanals 10 herrscht, der dem Einspritzdruck entspricht. Die Stirnseite 51 des äußeren Druckkolbens 40 weist eine größere hydraulisch wirksame Fläche auf als die Druckschulter 27 der äußeren Ventilnadel 20, so dass die äußere Ventilnadel 20 in Schließstellung verbleibt. Die Kraft der Schließfeder 44 spielt hierbei nur eine untergeordnete Rolle; die Schließfeder 44 dient hauptsächlich dazu, die äußere Ventilnadel 20 in Schließstellung zu halten, wenn die Brennkraftmaschine nicht arbeitet. Auch im Ventilraum 68 herrscht durch die Verbindung über den Verbindungskanal 74 und auch über die Ablaufdrossel 72 der Druck im Hochdruckkanal 10. Im Leckölraum 78 herrscht dagegen ein niedriger Druck, der in der Regel etwa dem Atmosphärendruck entspricht. FIG. 3 shows an enlargement of FIG. 1 In the intermediate body 7, a piston bore 45 is formed, in which a pressure piston 40 is arranged, which abuts with its end facing the combustion chamber on the outer valve needle 20 in the designated III section, ie in the region of the intermediate body 7, intermediate disc 9 and control body. By a radial extension of the piston bore 45, a spring chamber 43 is formed, in which between a contact surface 41 of the spring chamber 43 and an annular surface 39 of the outer pressure piston 40 a closing spring 44 is arranged under pressure bias, which surrounds the outer pressure piston 40 on a part of its length. By the bias of the closing spring 44, the outer pressure piston 40 is pressed in the direction of the valve body 3 and thus also the outer valve needle 20 in the direction of the seat 24. In the outer pressure piston 40, a guide bore 47 is formed in the longitudinal direction, in which an inner pressure piston 42 is guided , which rests with its combustion chamber end on the inner valve needle 22. The inner pressure piston 42 is longitudinally displaceable in the outer pressure piston 40 and moves synchronously with the inner valve needle 22. By the piston bore 45, the brennraumabgewandte end 51 of the outer pressure piston 40 and the washer 9, a control chamber 50 is limited, via a in the outer pressure piston 40th formed connecting bore 55 is connected to a control pressure chamber 52 which is bounded by the guide bore 47 and the combustion chamber facing away from end face 53 of the inner pressure piston 42. The control chamber 50 is connected via an inlet throttle 70 to the high-pressure passage 10 and via an outlet throttle 72 with a formed in the control body 12 valve chamber 68. In the valve chamber 68, a valve member 60 is arranged, which is formed substantially hemispherical and forms a control valve 58. The flattened side faces the intermediate disk 9, while the hemispherical side of the valve member 60 is connected to a pressure piece 48, which is guided in a receiving body 13 arranged in the holding body 14. The pressure piece 48 is in this case longitudinally displaceable by an actuator 46 and thereby also moves the valve member 60 in the valve chamber 68, wherein the actuator is designed here as a piezoelectric actuator. The pressure member 48 is surrounded by a leakage oil chamber 78, which always has a low pressure because of its connection with a drain oil system, not shown in the drawing. The intermediate disc 9 faces away in the valve chamber 68 a first valve seat 62 is formed, on which the valve member 60 can come with its spherical valve sealing surface 66 to the plant. Opposite the first valve seat 62, a second valve seat 64 is formed in the valve space 68, on which the valve member 60 can come into abutment with the flattened side. By fitting the valve member 60 on the second valve seat 64, a connecting channel 74 is closed, which also opens into the valve chamber 68 and which is connected via a transverse channel 76 with the high pressure passage 10. FIG. 4 shows a cross section through FIG. 3 along the line IV-IV. The course of the transverse channel 76 as a semicircular groove on the abutment surface 7 of the intermediate disc 9 facing the intermediate body 7 becomes clear here. In the cross section illustrated there, the inlet throttle 70, the outlet throttle 72, the connecting channel 74 and the high-pressure passage 10 are also visible. The function of the fuel injection valve is as follows: At the beginning of the injection cycle, the fuel injection valve is in the closed position, ie both the outer valve needle 20 and the inner valve needle 22 are in contact with the seat surface 24 and close both the inner injection opening row 230 and the outer injection opening row 130. Since the valve member 60 rests against the first valve seat 62, both the control chamber 50 and the control pressure chamber 52 are connected via the inlet throttle 70 to the high pressure passage 10, so that both the control chamber 50 and the control pressure chamber 52, the high fuel pressure of the high pressure passage 10 prevails which corresponds to the injection pressure. The end face 51 of the outer pressure piston 40 has a larger hydraulically effective area than the pressure shoulder 27 of the outer valve needle 20, so that the outer valve needle 20 remains in the closed position. The force of the closing spring 44 plays only a minor role; the closing spring 44 is mainly used to hold the outer valve needle 20 in the closed position, when the internal combustion engine is not working. Also in the valve chamber 68 prevails through the connection via the connecting channel 74 and also via the outlet throttle 72, the pressure in the high-pressure passage 10. In the leakage oil chamber 78, however, there is a low pressure, which generally corresponds approximately to the atmospheric pressure.

Soll eine Einspritzung stattfinden, so wird der Aktor 46 betätigt, und das Ventilglied 60 bewegt sich zusammen mit dem Druckstück 48 vom ersten Ventilsitz 62 weg zum zweiten Ventilsitz 64. Hierdurch wird der Ventilraum 68 mit dem Leckölraum 78 verbunden, so dass der Ventilraum 68 und auch der Steuerraum 50 über die Ablaufdrossel 72 druckentlastet werden. Durch die Anlage des Ventilglieds 60 am zweiten Ventilsitz 64 wird der Verbindungskanal 74 verschlossen, so dass in den Ventilraum 68 kein Kraftstoff mehr über den Querkanal 76 zufließen kann. Die Zulaufdrossel 70 und die Ablaufdrossel 72 sind dabei so dimensioniert, dass der Druck im Steuerraum 50 zwar abfällt, aber nicht auf das Niveau des Leckölraums 78. Durch den abfallenden Druck im Steuerraum 50 erniedrigt sich die hydraulische Kraft auf die Stirnseite 51 des äußeren Druckkolbens 40, so dass jetzt die hydraulische Kraft auf die Druckschulter 27 überwiegt. Die äußere Ventilnadel 20 hebt daraufhin von der Sitzfläche 24 ab, und Kraftstoff strömt aus dem Ringraum 28 zur äußeren Einspritzöffnungsreihe 130 und wird von dort in den Brennraum der Brennkraftmaschine eingespritzt. Durch das Abheben der äußeren Ventilnadel 20 wird jetzt auch die Druckfläche 36 der inneren Ventilnadel 22 vom Kraftstoff beaufschlagt, jedoch reicht diese Kraft nicht aus, die hydraulische Kraft auf die Stirnseite 53 des inneren Druckkolbens 42 zu überwinden, da der Druck im Steuerraum 50 hierfür noch zu hoch ist. Die äußere Ventilnadel 20 bzw. der äußere Druckkolben 40 bewegen sich solange vom Brennraum weg, bis die Stirnseite 51 des äußeren Druckkolbens 40 an der Zwischenscheibe 9 zur Anlage kommt.If an injection takes place, the actuator 46 is actuated, and the valve member 60 moves together with the pressure piece 48 from the first valve seat 62 away to the second valve seat 64. In this way, the valve chamber 68 is connected to the leakage oil chamber 78, so that the valve chamber 68 and also the control chamber 50 are relieved of pressure via the outlet throttle 72. By the installation of the valve member 60 on the second valve seat 64, the connecting channel 74 is closed, so that no more fuel can flow into the valve chamber 68 via the transverse channel 76. The inlet throttle 70 and the outlet throttle 72 are dimensioned such that the pressure in the control chamber 50 drops, but not to the level of the leakage oil chamber 78. Due to the falling pressure in the control chamber 50, the hydraulic force decreases to the end face 51 of the outer pressure piston 40th , so that now the hydraulic force on the pressure shoulder 27 outweighs. The outer valve needle 20 then lifts off from the seat surface 24, and fuel flows from the annular space 28 to the outer injection port row 130 and is injected from there into the combustion chamber of the internal combustion engine. By lifting the outer valve needle 20, the pressure surface 36 of the inner valve needle 22 is now acted upon by the fuel, but this force is not sufficient to overcome the hydraulic force on the end face 53 of the inner pressure piston 42, since the pressure in the control chamber 50 for this still is too high. The outer valve needle 20 and the outer pressure piston 40 move away from the combustion chamber until the end face 51 of the outer pressure piston 40 comes to rest on the intermediate disk 9.

Wenn beabsichtigt ist, beispielsweise für eine Piloteinspritzung, nur durch die äußere Einspritzöffnungsreihe 130 Kraftstoff in den Brennraum der Brennkraftmaschine einzuspritzen, so muss zu diesem Zeitpunkt durch die Betätigung des Aktors 46 das Ventilglied 60 erneut bewegt werden, so dass die Verbindung des Ventilraums 68 zum Leckölraum 78 unterbrochen wird. Hierdurch wird die Verbindung des Hochdruckkanals 10 über den Verbindungskanal 74 zum Ventilraum 68 wieder hergestellt, so dass Kraftstoff mit Einspritzdruck aus dem Hochdruckkanal 10 über die Ablaufdrossel 72 und über die Zulaufdrossel 70 in den Steuerraum 50 strömt. Dort baut sich erneut ein hohes Kraftstoffdruckniveau auf, das den äußeren Druckkolben 40 und damit auch die äußere Ventilnadel 20 wieder zurück in die Schließstellung drückt.If it is intended, for example for a pilot injection, to inject fuel into the combustion chamber of the internal combustion engine only through the outer injection opening row 130, then, by actuating the actuator 46, the valve member 60 must be moved again so that the connection of the valve space 68 to the leakage oil space 78 is interrupted. As a result, the connection of the high-pressure passage 10 via the connecting channel 74 to the valve chamber 68 is restored, so that fuel flows with injection pressure from the high-pressure passage 10 via the outlet throttle 72 and via the inlet throttle 70 into the control chamber 50. There again, a high fuel pressure level builds up, which presses the outer pressure piston 40 and thus also the outer valve needle 20 back into the closed position.

Ist hingegen vorgesehen, durch den gesamten Einspritzquerschnitt, d.h. durch sämtliche Einspritzöffnungen 30 einzuspritzen, so verbleibt das Ventilglied 60 in Anlage am zweiten Ventilsitz 64. Durch die Anlage der Stirnseite 51 des äußeren Druckkolbens 40 an der Zwischenscheibe 9 wird die Zulaufdrossel 70 verschlossen. Der Druck im Steuerdruckraum 52 kann somit über die Ablaufdrossel 72 und die Verbindung des Ventilraums 68 zum Leckölraum 78 weiter abfallen, bis die hydraulische Kraft auf die Druckfläche 36 der inneren Ventilnadel 22 größer ist als die hydraulische Kraft auf die Stirnseite 53 des inneren Druckkolbens 42. Die innere Ventilnadel 22 hebt jetzt mit der Dichtkante 37 von der Sitzfläche 24 ab, und Kraftstoff wird zusätzlich durch die innere Einspritzöffnungsreihe 230 eingespritzt. Die Einspritzung wird auch hier dadurch beendet, dass der Aktor 46 betätigt wird, so dass das Ventilglied 60 wieder zurück in Anlage an den ersten Ventilsitz 62 fährt. In der bereits oben beschriebenen Weise wird nun wieder Kraftstoffhochdruck in den Steuerraum 50 und über die Verbindungsbohrung 55 auch in den Steuerdruckraum 52 geleitet. Hierdurch schließen sowohl die innere Ventilnadel 22 als auch die äußere Ventilnadel 20 die Einspritzöffnungen 30 wieder gegen den Ringkanal 28.If, on the other hand, it is provided to inject through the entire injection cross section, ie through all the injection openings 30, then the valve member 60 remains in abutment with the second valve seat 64. The feed throttle 70 is closed by abutment of the end face 51 of the outer pressure piston 40 on the intermediate disk 9. The pressure in the control pressure chamber 52 can thus further drop via the outlet throttle 72 and the connection of the valve chamber 68 to the leakage oil chamber 78 until the hydraulic force on the pressure surface 36 of the inner valve needle 22 is greater than the hydraulic force on the end face 53 of the inner pressure piston 42nd The inner valve needle 22 now lifts with the sealing edge 37 from the seat surface 24, and fuel is additionally injected through the inner injection port row 230. The injection is also terminated here by actuation of the actuator 46 so that the valve member 60 moves back into abutment against the first valve seat 62. In the manner already described above, high-pressure fuel is again conducted into the control chamber 50 and via the connecting bore 55 into the control pressure chamber 52. This will close both the inner valve needle 22 and the outer valve needle 20, the injection openings 30 again against the annular channel 28th

Neben der Zeitsteuerung für das Öffnen nur der äußeren Einspritzöffnungsreihe kann ein selektives Öffnen auch durch eine Mittelstellung des Steuerventils 58 erreicht werden. Das Ventilglied 60 wird mittels des Piezo-Aktors 48 in eine Mittelstellung zwischen dem ersten Ventilsitz 62 und dem zweiten Ventilsitz 64 gefahren, so dass sämtliche Verbindungen zum Ventilraum 68 geöffnet sind. Hierdurch fließt einerseits Kraftstoff aus dem Ventilraum 68 in den Leckölraum 78, andererseits über den Verbindungskanal 74 ständig in den Ventilraum 68, so dass sich nur ein gewisser Druckabfall im Ventilraum 68 einstellt, der noch deutlich über dem Druck des Leckölraums 78 liegt. Dieser Druck reicht aus, um die innere Ventilnadel 22 in ihrer Schließstellung zu halten, die Schließkraft auf die äußere Ventilnadel 20 ist jedoch soweit reduziert, dass diese öffnet. Die Einspritzung wird auch hier wieder in der bereits oben beschriebenen Art und Weise durch Schalten des Steuerventils 58 beendet.In addition to the timing for the opening of only the outer injection opening row, a selective opening can also be achieved by means of a middle position of the control valve 58. The valve member 60 is moved by means of the piezo-actuator 48 in a middle position between the first valve seat 62 and the second valve seat 64, so that all connections to the valve chamber 68 are opened. As a result, on the one hand fuel flows from the valve chamber 68 into the leakage oil chamber 78, on the other hand via the connecting channel 74 constantly in the valve chamber 68, so that only a certain pressure drop in the valve chamber 68 sets, which is still significantly above the pressure of the leakage oil chamber 78. This pressure is sufficient to hold the inner valve needle 22 in its closed position, but the closing force on the outer valve needle 20 is reduced to the extent that it opens. The injection is also terminated here again in the manner already described above by switching the control valve 58.

Der Aktor 46 ist in diesem Ausführungsbeispiel ein Piezo-Aktor. Das Ventilglied 60 im Ventilraum 68 benötigt für seine Funktion nur einen geringen Hub, wie er in der Regel von einem Piezo-Aktor aufgebracht werden kann. Notfalls kann ein hydraulischer Übersetzer vorgesehen werden, mit dem größere Hübe realisiert werden können und der aus dem Stand der Technik hinlänglich bekannt ist. Darüber hinaus bieten Piezo-Aktoren den Vorteil, dass sie äußerst schnell schalten können. Es ist so ohne Probleme in der oben beschriebenen Art und Weise möglich ist, eine präzise Voreinspritzung nur durch die äußere Einspritzöffnungsreihe 130 durchzuführen.The actuator 46 is a piezoelectric actuator in this embodiment. The valve member 60 in the valve chamber 68 requires only a small stroke for its function, as it can usually be applied by a piezoelectric actuator. If necessary, a hydraulic translator can be provided with which larger strokes can be realized and which is well known from the prior art. In addition, piezo actuators have the advantage that they can switch extremely fast. It is thus possible without any problems in the manner described above to carry out a precise pre-injection only through the outer injection opening row 130.

Claims (8)

  1. Fuel injection valve for internal combustion engines, having a housing (1) in which an outer valve needle (20) and an inner valve needle (22) which is guided in said outer valve needle (20) are arranged in a bore (16), with the outer valve needle (20) coming to bear, in a closed position, against a valve seat (24) which is arranged at the combustion-chamber-side end of the housing (1) and with said outer valve needle (20), by means of a longitudinal movement in an opening direction, opening up an outer row of injection openings (130), and with the inner valve needle (22) likewise bearing, in a closed position, against the valve seat (24) and, by means of a longitudinal movement in an opening direction, opening up an inner row of injection openings (230), to which rows of injection openings (130; 230) pressurized fuel from a pressure chamber (26) which is formed in the housing (1) flows when the valve needles (20; 22) are in the opened-up state, and said fuel is injected from there into the combustion chamber of the internal combustion engine, and having a pressure shoulder (27) which is formed on the outer valve needle (20) and which is acted on by the fuel pressure in the pressure chamber (26) such that, in this way, a force which acts in the opening direction is exerted on the outer valve needle (20), and having a pressure surface (36) on the inner valve needle (22), which pressure surface (36), after the outer valve needle (20) has been lifted from the valve seat (24), is acted on by the fuel pressure in the opening direction, and having a high-pressure duct (10) which runs in the housing (1) and which opens out into the pressure chamber (26) and in which highly pressurized fuel is present at all times, and having a fuel-filled control pressure chamber (52), the pressure of which can be controlled and by means of the pressure of which a closing force is exerted at least indirectly on the inner valve needle (22), with a fuel-filled control chamber (50) being formed in the housing (1), by means of the pressure of which a closing force is exerted at least indirectly on the outer valve needle (20), and having an inflow throttle (70) by means of which the control chamber (50) is connected to the high-pressure duct (10), and having an outflow throttle (72) by means of which the control chamber (50) can be connected to an unpressurized leakage oil chamber (78), with it being possible for the outflow throttle (72) to be closed off by means of a control valve (58) and with the outflow throttle (72) and the inflow throttle (70) being dimensioned such that, when the outflow throttle (72) is open, more fuel flows out of the control chamber (50) than flows in through the inflow throttle (70), and having a connection (55) between the control chamber (50) and the control pressure chamber (52), with the control pressure chamber (52) being closed off with the exception of the connection (55) and with the connection (55) being dimensioned such that, when the outflow throttle (72) is opened by means of the control valve (58), the pressure in the control chamber (50) falls first and the pressure in the control pressure chamber (52) also falls only after a time delay, with the control valve (58) having a valve chamber (68) which is connected to the control chamber (50) and having a valve element (60) which can be controlled by means of an electrical piezoelectric actuator (46).
  2. Fuel injection valve according to Claim 1, characterized in that the valve element (60) interacts in a first switching position with a first valve seat (62) and in a second switching position with a second valve seat (64), with the valve chamber (68) being sealed off with respect to the leakage oil chamber (78) in the first switching position and being connected to the leakage oil chamber (78) in the second switching position.
  3. Fuel injection valve according to Claim 2, characterized in that the valve chamber (68) can be connected by means of a connecting duct (74; 76) to the high-pressure duct (10), with the valve element (60), when in contact with the second valve seat (64), closing off the connecting duct (74).
  4. Fuel injection valve according to Claim 2, characterized in that the valve element (60) can be placed into a central position such that the valve element (60) bears neither against the first valve seat (62) nor against the second valve seat (64).
  5. Fuel injection valve according to Claim 1, characterized in that an outer pressure piston (40) is arranged in the housing (1), which outer pressure piston (40) is connected to the outer valve needle (20) and the end surface (51) of which outer pressure piston (40) delimits the control chamber (50), such that a closing force is exerted on the outer valve needle (20) by the hydraulic force on said end surface (51).
  6. Fuel injection valve according to Claim 5, characterized in that, during the opening movement of the outer valve needle (20), the outer pressure piston (40) comes to bear against a wall of the control chamber (50) and thereby blocks the inflow throttle (70) which connects the control chamber (50) to the high-pressure duct (10).
  7. Fuel injection valve according to Claim 5, characterized in that the control pressure chamber (52) is formed in the outer pressure piston (40), and in that the connection to the control chamber (50) is formed as a connecting bore (55) in the outer pressure piston (40).
  8. Fuel injection valve according to Claim 1, characterized in that a pressure which is considerably lower than the injection pressure, preferably atmospheric pressure, prevails in the leakage oil chamber (78) at all times.
EP03704252A 2002-02-14 2003-01-27 Fuel injection valve for internal combustion engines Expired - Lifetime EP1478840B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10205970A DE10205970A1 (en) 2002-02-14 2002-02-14 Fuel injection valve for internal combustion engines
DE10205970 2002-02-14
PCT/DE2003/000210 WO2003069151A1 (en) 2002-02-14 2003-01-27 Fuel injection valve for internal combustion engines

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EP1478840A1 EP1478840A1 (en) 2004-11-24
EP1478840B1 true EP1478840B1 (en) 2009-12-30

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EP03704252A Expired - Lifetime EP1478840B1 (en) 2002-02-14 2003-01-27 Fuel injection valve for internal combustion engines

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US (1) US7051958B2 (en)
EP (1) EP1478840B1 (en)
JP (1) JP2005517858A (en)
KR (1) KR20040091522A (en)
CN (1) CN100366889C (en)
AT (1) ATE453798T1 (en)
DE (2) DE10205970A1 (en)
PL (1) PL201040B1 (en)
WO (1) WO2003069151A1 (en)

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US7051958B2 (en) 2006-05-30
WO2003069151A1 (en) 2003-08-21
PL363037A1 (en) 2004-11-15
CN100366889C (en) 2008-02-06
PL201040B1 (en) 2009-02-27
EP1478840A1 (en) 2004-11-24
CN1533474A (en) 2004-09-29
ATE453798T1 (en) 2010-01-15
KR20040091522A (en) 2004-10-28
US20040129804A1 (en) 2004-07-08
DE10205970A1 (en) 2003-09-04
DE50312286D1 (en) 2010-02-11
JP2005517858A (en) 2005-06-16

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