EP1999363B1 - Fuel injection valves for internal combustion engines - Google Patents

Fuel injection valves for internal combustion engines Download PDF

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Publication number
EP1999363B1
EP1999363B1 EP07704166A EP07704166A EP1999363B1 EP 1999363 B1 EP1999363 B1 EP 1999363B1 EP 07704166 A EP07704166 A EP 07704166A EP 07704166 A EP07704166 A EP 07704166A EP 1999363 B1 EP1999363 B1 EP 1999363B1
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EP
European Patent Office
Prior art keywords
valve
fuel injection
pressure
bolt
needle
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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.)
Not-in-force
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EP07704166A
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German (de)
French (fr)
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EP1999363A1 (en
Inventor
Rolf-Juergen Giersch
Bernd Dittus
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication of EP1999363A1 publication Critical patent/EP1999363A1/en
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Publication of EP1999363B1 publication Critical patent/EP1999363B1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/042—The valves being provided with fuel passages
    • 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0078—Valve member details, e.g. special shape, hollow or fuel passages in the valve member
    • F02M63/008—Hollow valve members, e.g. members internally guided
    • 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
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/006—Springs assisting hydraulic closing force

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines, as it is preferably used for the direct injection of fuel into the combustion chamber of self-igniting internal combustion engines.
  • Injectors for the direct injection of fuel into the combustion chamber of internal combustion engines are known for a long time.
  • the injector includes a valve needle longitudinally movably disposed in a valve body which, by its longitudinal movement, controls the opening and closing of at least one injection port by cooperating with a valve seat.
  • the movement of the valve needle is controlled by a control valve, wherein the valve needle moving forces are generated hydraulically.
  • Disadvantage of these fuel injection valves is on the one hand the large moving mass, since the valve needle, which comprises the entire length of the injection nozzle, is relatively long and therefore heavy. The consequent inertia makes it very difficult to carry out successive injection operations very quickly.
  • valve needle On the other hand occurs with increasing injection pressures the problem that the valve needle must be moved with very large forces in order to achieve the fast opening and closing operations. As a result, the valve needle is hard on the valve seat, which there can lead to wear and premature failure of the injector, especially if in the course of further technical development ever higher injection pressures that are well above 2000 bar, are controlled.
  • valve needle includes a smaller valve needle which opens at least a part of the injection openings and closes.
  • this smaller valve needle which is preferably arranged in a longitudinal bore of the larger valve needle, at least certain operating states can be controlled quickly by the small valve needle.
  • a clean centering of the actual valve needle in the region of the valve seat is achieved via the smaller valve needle, so that a uniform injection is made possible through all injection ports.
  • the known fuel injection valve has the disadvantage that an independent control of the small valve needle is not possible. This complicates a fast control, as it is necessary for multiple injections, ie a subdivided into multiple injections fuel injection.
  • the known fuel injection valve has the disadvantage that at ever higher pressure surrounding the nozzle needle, significant elastic deformation of the valve body occur. This increases the leakage gap and results in more fuel being pumped into the fuel return, necessitating additional pumping of the high pressure pump, which compresses the fuel and provides it to the injector.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that rapid control of the injection can be carried out at low leakage, even at a pressure that is well above the achievable today 2000 bar.
  • a valve pin is arranged in the bore of the valve body, on which a valve needle is guided.
  • a first control chamber is located within the valve pin, the first control chamber being connected to a second control member through a connection formed in the valve pin.
  • the pressure in the second control chamber is adjustable, preferably via a control valve, so that the pressure in the first control chamber can be changed very quickly. Due to the low moving mass, the valve needle can very quickly open or close the injection openings, whereby very rapid successive injections are made possible. Since there are no leakage gaps in the high-pressure area, the result is also higher Injection pressures no impairment of the function of the fuel injection valve according to the invention.
  • the valve pin essentially has a hollow cylindrical shape, so that the connection between the two control chambers is formed by a longitudinal channel in the valve pin.
  • the valve pin is preferably supported on the valve needle via a closing spring, so that the valve needle is pressed against the valve seat by the spring force.
  • the valve pin can also advantageously be supported by a compression spring on a stationary stop, so that it is mounted between the closing spring on the one hand and the compression spring on the other. This facilitates easy assembly and disassembly of the fuel injection valve and allows to manufacture in the longitudinal direction with relatively large tolerances.
  • valve pin is supported at its valve seat side end with a contact surface on the valve seat, so that it is held stationary by the compression spring.
  • the valve pin in this case preferably has openings through which the fuel can flow from a pressure space surrounding the valve pin in the direction of the injection openings.
  • a further sleeve is provided, which is likewise arranged in the bore of the valve body and which surrounds the valve pin and the valve needle.
  • the sleeve is guided in this case in the bore and also ensures a guide of the valve pin and the valve needle, wherein the first control chamber between the valve pin and the valve needle is formed and is bounded radially outward by the sleeve.
  • the sleeve has valve seat near also openings through which fuel can flow to the injection openings.
  • the valve pin has a receptacle into which a pressure piston protrudes.
  • the plunger limits together with the recording the second control chamber, which is connected via a longitudinal channel within the valve pin with the first control chamber.
  • the pressure piston can be moved, for example via a piezoelectric actuator, so that the movement of the valve needle can be controlled directly above the piezoelectric actuator.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section.
  • the fuel injection valve comprises a valve body 1, which is braced in the installed position against a holding body, not shown in the drawing.
  • the valve body 1 has a bore 3 which is delimited at its combustion chamber end by a conical valve seat 4.
  • the conical valve seat 4 terminates in a blind hole 6, wherein at least one injection opening 10, 10 'either from the blind hole 6 or starting from the conical valve seat 4 and opens in installation position of the fuel injection valve in the combustion chamber of the internal combustion engine.
  • a valve pin 5 is arranged longitudinally displaceable, wherein between the wall of the bore 3 and the valve pin 5, a pressure chamber 8 is formed which can be filled with fuel under high pressure.
  • FIG. 1a shows a cross section through the in FIG FIG. 1 illustrated fuel injection valve along the line AA.
  • the valve pin 5 has in the middle guide portion 105 recesses 16 in the form of longitudinal grooves, so that here four guide surfaces 17 are formed on the outside of the valve pin 5, which bear against the wall of the bore 3. Through the recesses 16, a sufficiently large flow cross section is formed through which fuel in the direction of the injection openings 10 can flow unthrottled.
  • valve needle 7 At the valve seat side end of the valve pin 5 is in a guide section 14, which is reduced in diameter. On the guide portion 14, a valve needle 7 is guided, which has a corresponding receptacle 15 which receives the guide portion 14 of the valve pin 5.
  • the valve needle 7 has a substantially conical valve sealing surface 11, with which it rests on the valve seat 4 and thereby separates the pressure chamber 8 from the injection openings 10 when resting against the valve seat 4.
  • the valve needle 7 is clamped by a closing spring 12 against the valve pin 5, wherein the closing spring 12 surrounds the guide portion 14 of the valve pin 5.
  • a first control chamber 25 is limited, which is connected via a formed in the valve pin 5 longitudinal channel 22 with a second control chamber 27. This is delimited by the valve seat facing away from the end of the valve pin 5 and a pressure sleeve 18, wherein the pressure sleeve 18 surrounds the valve pin 5 at its valve seat facing away from the end.
  • the pressure sleeve 18 is supported via a compression spring 20, which is supported on a support ring 13 connected to the valve pin 5, against the in the FIG. 1 Holding body not shown pressed.
  • the valve pin 5 is also pressed in the direction of the valve seat 4, while it is simultaneously acted upon by the closing spring 12 in the opposite direction.
  • the volume of the two control chambers 25, 27 and the volume of the longitudinal channel 22 should be as small as possible. Since the diameter of the longitudinal channel 22 due to production must have a certain minimum cross-section, it can be provided that a filling pin 31 is arranged in the longitudinal channel 22. Over the thickness and the length of the filler pin 31 so the volume can be optimally adjusted.
  • the operation of the fuel injection valve is as follows: In the pressure chamber 8, a predetermined high fuel pressure is maintained, which is provided for example in a so-called common rail. By a separate connection or by leakage gaps, such as between the valve pin 5 and the pressure sleeve 18, prevails in the second control chamber 27 and via the longitudinal channel 22 in the first control chamber 25, the same high fuel pressure as in the pressure chamber 8. If an injection takes place, then the over a control device, for example a control valve, which is accommodated in the holding body, not shown in the drawing, set a lower pressure in the second control chamber 27. Due to the pressure drop in the second control chamber 27, the pressure in the first control chamber 25 drops virtually instantaneously since both control chambers 25, 27 are hydraulically connected to one another via the longitudinal channel 22.
  • valve needle 7 This causes a drop in the hydraulic force to the valve needle 7, which experiences a closing force in the direction of the valve seat 4 by the pressure in the first control chamber 25.
  • the valve needle 7 By pressurizing a portion of the valve sealing surface 11, the valve needle 7 now lifts off the valve seat 4, so that fuel from the pressure chamber 8 between the valve sealing surface 11 and the valve seat 4 flows through to the injection openings 10 and is injected from there into the combustion chamber.
  • the pressure in the first control chamber 25 also rises again, and the valve needle 7 slides back into its closed position, ie. in contact with the valve seat 4.
  • FIG. 2 a second embodiment of the fuel injection valve according to the invention is shown.
  • the valve needle 7 is here, apart from the conical valve sealing surface 11, designed as a compact cylinder and thus not guided on the valve pin 5.
  • the first control chamber 25 is formed between the valve needle 7 and the valve seat facing end face of the valve pin 5.
  • a sleeve 30 is additionally arranged in this embodiment, which surrounds both the valve pin 5 and the pressure sleeve 18 and the valve needle 7 and rests with a contact surface 37 on the valve seat 4.
  • the sleeve 30 is fixedly disposed in the bore 3 and has recesses 16 through which - also in the embodiment according to FIG. 1 - Guide surfaces 17 are formed, with which the sleeve 30 on the wall of the bore.
  • FIG. 2a shows a cross section along the line AA of the FIG. 2 by which the arrangement of the pressure sleeve 18 in the sleeve 30 is clear.
  • the operation of this fuel injection valve is identical to the operation of the in FIG. 1 shown injector, so that it can be omitted here a functional description.
  • FIG. 2b shows an alternative embodiment of the valve seat facing away from the end of the injector FIG. 2
  • a pressure piece 34 is provided here, which has a longitudinal bore 36.
  • a gap 29 is formed in which the compression spring 20 is arranged, which presses the pressure piece 34 against the holding body, not shown, and at the same time the valve pin 5 in the direction of the valve needle 7.
  • a series circuit the second control chamber 27, the intermediate space 29 and the first control chamber 25, which are connected to each other via a longitudinal bore 36 and a longitudinal channel 22 in the valve pin 5 and in the pressure piece 34.
  • FIG. 3 is a further embodiment shown in longitudinal section.
  • the valve pin 5 is here, as well as in the FIG. 1 illustrated embodiment, guided by guide surfaces 17 in the bore 3. Between the pressure sleeve 18 and the valve pin 5, a compression spring is arranged here, which presses the valve pin 5 with a contact surface 19 against the valve seat 4.
  • the valve needle 7, facing away from the valve sealing surface 11, has a piston-shaped end 21, with which it is guided in a receptacle 24 in the valve pin 5.
  • the closing spring 12 is arranged, which presses the valve needle 7 against the valve seat 4.
  • the first control chamber 25 is formed by the end face of the piston-shaped end 21 and by the base of the receptacle 24th limited and is also connected here by the longitudinal channel 22 with the second control chamber 27.
  • a further pressure surface 35 is formed by the annular collar 33 on the valve needle 7, which causes an additional hydraulic force to the valve needle 7 in the opening direction.
  • the valve pin 5 does not move here and remains stationary during the entire injection.
  • FIG. 4 a further embodiment is shown, wherein here the same representation as in FIG. 3 was chosen.
  • the two embodiments differ only in that the valve needle 7 terminates here in a pin 23 which is arranged in the receptacle 24 and through which a valve needle 7, a shoulder is formed on which the closing spring 12 is applied.
  • the valve needle 7 is guided in the receptacle 24, wherein a hydraulic opening force only results from the fact that a part of the sealing surface 11 is acted upon by the fuel pressure of the pressure chamber 8.
  • the valve pin 5 has no guide surfaces 17, but a cylindrical outer shape and an outer diameter which is significantly smaller than the inner diameter of the bore 3.
  • a guide plate 38 is provided, which rests against a shoulder 41 on the pressure pin 5.
  • the compression spring 20 is arranged, which presses against the shoulder 41 against the shoulder 41.
  • a plurality of passages 39 are provided, so that the fuel can flow unthrottled through the pressure chamber 8 in the direction of the injection openings.
  • FIG. 6 another embodiment is shown, in which in addition to the valve body 1 nor a drive device, shown here in the form of a piezoelectric actuator 40, which is usually arranged in the holding body.
  • the valve pin 5 has a receptacle 24, in which the valve needle 7 - as in previous embodiments - is guided.
  • the valve pin 5 on its opposite side on a further receptacle 26 in which a pressure piston 42 is guided, wherein the second control chamber 27 through the pressure piston 42 and through the wall of the second receptacle 26 is limited.
  • the compression spring 20 is arranged, which pushes the pressure piston 42 away from the valve pin 5.
  • the pressure piston 42 is connected directly to the piezoelectric actuator 40, so that by a corresponding energization of the piezoelectric actuator 40, a longitudinal movement of the pressure piston 42 takes place, through which the volume of the second control chamber 27 is variable, so that either fuel from the second control chamber 27 displaced or via leakage gaps between the wall of the second receptacle 26 and the pressure piston 42 in the second control chamber 27 is required.
  • the piezoelectric actuator 40 is shortened.
  • the second control chamber 27 is as well as the first control chamber 25 and the longitudinal channel 22 via leakage gaps, the z. B. are formed between the pressure piston 42 and the second receptacle 26, connected to the pressure chamber 8 and thus filled with fuel under pressure.
  • the piezoelectric actuator 40 is in its maximum deflection position, so that the volume of the second control chamber 27 and the first control chamber 25 is as small as possible. If an injection takes place, then the piezoactuator 40 is shortened so that the pressure piston 42 retracts. This increases the volume of the second control chamber 27, as a result of which the pressure in the first control chamber 25 drops rapidly, wherein a throttle 28 can be provided to avoid pressure oscillations and to control the pressure drop in the longitudinal channel 22 over time. Due to the pressure drop in the first control chamber 25 and the concomitant decrease in the hydraulic closing force on the valve needle 7, this is the fuel pressure in the pressure chamber 8 in its open position, d. H. pushed away from the valve seat 4, so that the injection openings 10 are released.
  • valve body 1 By arranging the components according to FIG. 6 can be laid in the valve body 1, the entire control of the valve needle 7 and thus the injection, which must be provided in the holding body, only the piezoelectric actuator 40 with its electrical connections and the connection of the pressure chamber 8 with the high-pressure fuel source.
  • valve needle 7 is made very small, so that the manufacturing costs can be reduced. This is particularly interesting if, to further increase the precision of relatively expensive Materials for the production of the valve needle 7 find use, such as stainless steels.

Abstract

Fuel injection valve having a valve body (1) in which a bore (3) with a valve needle (7) arranged therein is formed. The valve needle (7) interacts with a valve seat (4), formed in the valve body (1), in such a way that at least one injection opening (10; 10') can be opened or closed as a result. Arranged in the bore (3) is a valve pin (5) which defines together with the valve needle (7) a first control space (25) which can be filled with fuel, wherein the fuel pressure in the first control space (25) acts on the valve needle (7) in such a way that the latter is pressed against the valve seat (4). Formed in the valve pin (5) is a longitudinal passage (22) leading to a second control space (27) in which a variable pressure can be set.

Description

Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen, wie es vorzugsweise für die direkte Einspritzung von Kraftstoff in den Brennraum von selbstzündenden Brennkraftmaschinen verwendet wird.The invention relates to a fuel injection valve for internal combustion engines, as it is preferably used for the direct injection of fuel into the combustion chamber of self-igniting internal combustion engines.

Stand der TechnikState of the art

Einspritzdüsen zur direkten Einspritzung von Kraftstoff in den Brennraum von Brennkraftmaschinen sind seit langer Zeit bekannt. So zeigt die Offenlegungsschrift DE 100 24 703 A1 ein solches Einspritzventil, wie es bei so genannten Common-Rail-Einspritzsystemen verwendet wird. Die Einspritzdüse beinhaltet eine Ventilnadel, die längsbeweglich in einem Ventilkörper angeordnet ist und die durch ihre Längsbewegung das Öffnen und Schließen wenigstens einer Einspritzöffnung steuert, indem sie mit einem Ventilsitz zusammenwirkt. Die Bewegung der Ventilnadel wird hierbei durch ein Steuerventil geregelt, wobei die die Ventilnadel bewegenden Kräfte hydraulisch erzeugt werden. Nachteil dieser Kraftstoffeinspritzventile ist zum einen die große bewegte Masse, da die Ventilnadel, die die gesamte Länge der Einspritzdüse umfasst, relativ lang und damit schwer ist. Die dadurch bedingte Trägheit macht sehr schnell aufeinander folgende Einspritzvorgänge nur schwer durchführbar. Zum anderen tritt bei immer höheren Einspritzdrücken das Problem auf, dass die Ventilnadel mit sehr großen Kräften bewegt werden muss, um die schnellen Öffnungs- und Schließvorgänge zu erreichen. Dadurch setzt die Ventilnadel hart auf dem Ventilsitz auf, was dort zu Verschleiß und vorzeitigem Ausfall des Einspritzventils führen kann, insbesondere wenn im Zuge der weiteren technischen Entwicklung immer höhere Einspritzdrücke, die deutlich über 2000 bar liegen, angesteuert werden.Injectors for the direct injection of fuel into the combustion chamber of internal combustion engines are known for a long time. Thus, the published patent application DE 100 24 703 A1 Such an injection valve, as used in so-called common rail injection systems. The injector includes a valve needle longitudinally movably disposed in a valve body which, by its longitudinal movement, controls the opening and closing of at least one injection port by cooperating with a valve seat. The movement of the valve needle is controlled by a control valve, wherein the valve needle moving forces are generated hydraulically. Disadvantage of these fuel injection valves is on the one hand the large moving mass, since the valve needle, which comprises the entire length of the injection nozzle, is relatively long and therefore heavy. The consequent inertia makes it very difficult to carry out successive injection operations very quickly. On the other hand occurs with increasing injection pressures the problem that the valve needle must be moved with very large forces in order to achieve the fast opening and closing operations. As a result, the valve needle is hard on the valve seat, which there can lead to wear and premature failure of the injector, especially if in the course of further technical development ever higher injection pressures that are well above 2000 bar, are controlled.

Aus der europäischen Patentanmeldung EP 967 382 A2 ist ein Einspritzventil bekannt, bei dem die Ventilnadel eine kleinere Ventilnadel beinhaltet, die zumindest einen Teil der Einspritzöffnungen öffner und schließt. Durch diese kleinere Ventilnadel, die vorzugsweise in einer Längsbohrung der größeren Ventilnadel angeordnet ist, lassen sich zumindest bestimmte Betriebszustände schnell durch die kleine Ventilnadel steuern. Darüber hinaus wird über die kleinere Ventilnadel eine saubere Zentrierung der eigentlichen Ventilnadel im Bereich des Ventilsitzes erreicht, sodass eine gleichmäßige Einspritzung durch sämtliche Einspritzöffnungen ermöglicht wird.From the European patent application EP 967 382 A2 an injection valve is known in which the valve needle includes a smaller valve needle which opens at least a part of the injection openings and closes. By means of this smaller valve needle, which is preferably arranged in a longitudinal bore of the larger valve needle, at least certain operating states can be controlled quickly by the small valve needle. In addition, a clean centering of the actual valve needle in the region of the valve seat is achieved via the smaller valve needle, so that a uniform injection is made possible through all injection ports.

Eine andere Lösung ist aus dem WO 02/084110 bekannt. Das bekannte Kraftstoffeinspritzventil weist hierbei jedoch den Nachteil auf, dass eine unabhängige Steuerung der kleinen Ventilnadel nicht möglich ist. Dies erschwert eine schnelle Ansteuerung, wie sie für Mehrfach-Einspritzungen, d. h. eine in mehrere Teileinspritzungen unterteilte Kraftstoffeinspritzung notwendig ist. Darüber hinaus weist das bekannte Kraftstoffeinspritzventil den Nachteil auf, dass bei immer höherem Druck, der die Düsennadel umgibt, erhebliche elastische Verformungen des Ventilkörpers auftreten. Dies vergrößert die Leckagespalte und führt dazu, dass Kraftstoff vermehrt in den Kraftstoffrücklauf gefördert wird, was zusätzliche Pumpenleistung der Hochdruckpumpe notwendig macht, die den Kraftstoff verdichtet und der Einspritzdüse zur Verfügung stellt.Another solution is from the WO 02/084110 known. However, the known fuel injection valve has the disadvantage that an independent control of the small valve needle is not possible. This complicates a fast control, as it is necessary for multiple injections, ie a subdivided into multiple injections fuel injection. In addition, the known fuel injection valve has the disadvantage that at ever higher pressure surrounding the nozzle needle, significant elastic deformation of the valve body occur. This increases the leakage gap and results in more fuel being pumped into the fuel return, necessitating additional pumping of the high pressure pump, which compresses the fuel and provides it to the injector.

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

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass eine schnelle Steuerung der Einspritzung bei niedriger Leckage erfolgen kann, auch bei einem Druck, der deutlich über den heute erreichbaren 2000 bar liegt. Dazu ist in der Bohrung des Ventilkörpers ein Ventilbolzen angeordnet, auf dem eine Ventilnadel geführt ist. Ein erster Steuerraum befindet sich innerhalb des Ventilbolzens, wobei der erste Steuerraum mit einem zweiten Steuen-aum durch eine im Ventilbolzen ausgebildete Verbindung verbunden ist. Der Druck im zweiten Steuerraum ist einstellbar, vorzugsweise über ein Steuerventil, sodass sich auch der Druck im ersten Steuerraum sehr rasch ändern lässt. Durch die geringe bewegte Masse kann die Ventilnadel sehr schnell die Einspritzöffnungen öffnen oder verschließen, wodurch sehr rasch aufeinander folgende Einspritzungen ermöglicht werden. Da im Hochdruckbereich keine Leckagespalten vorhanden sind, ergibt sich auch bei höheren Einspritzdrücken keine Beeinträchtigung der Funktion des erfindungsgemäßen Kraftstoffeinspritzventils.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that rapid control of the injection can be carried out at low leakage, even at a pressure that is well above the achievable today 2000 bar. For this purpose, a valve pin is arranged in the bore of the valve body, on which a valve needle is guided. A first control chamber is located within the valve pin, the first control chamber being connected to a second control member through a connection formed in the valve pin. The pressure in the second control chamber is adjustable, preferably via a control valve, so that the pressure in the first control chamber can be changed very quickly. Due to the low moving mass, the valve needle can very quickly open or close the injection openings, whereby very rapid successive injections are made possible. Since there are no leakage gaps in the high-pressure area, the result is also higher Injection pressures no impairment of the function of the fuel injection valve according to the invention.

Durch die abhängigen Ansprüche sind vorteilhafte Weiterbildungen des Gegenstandes der Erfindung möglich. In einer ersten vorteilhaften Ausgestaltung weist der Ventilbolzen im wesentlichen eine Hohlzylinderform auf, sodass die Verbindung zwischen den beiden Steuerräumen durch einen Längskanal im Ventilbolzen gebildet wird. Der Ventilbolzen stützt sich hierbei vorzugsweise über eine Schließfeder an der Ventilnadel ab, sodass die Ventilnadel durch die Federkraft gegen den Ventilsitz gedrückt wird. Dadurch bleiben die Einspritzöffnungen auch dann verschlossen, wenn das Kraftstoffeinspritzventil nicht betrieben wird. Der Ventilbolzen kann sich darüber hinaus vorteilhafterweise über eine Druckfeder an einem ortfesten Anschlag abstützen, sodass er zwischen der Schließfeder einerseits und der Druckfeder andererseits gelagert ist. Dies erleichtert eine leichte Montage und Demontage des Kraftstoffeinspritzventils und erlaubt es, in Längsrichtung mit relativ großen Toleranzen zu fertigen.By the dependent claims advantageous developments of the subject invention are possible. In a first advantageous embodiment, the valve pin essentially has a hollow cylindrical shape, so that the connection between the two control chambers is formed by a longitudinal channel in the valve pin. The valve pin is preferably supported on the valve needle via a closing spring, so that the valve needle is pressed against the valve seat by the spring force. As a result, the injection openings remain closed even when the fuel injection valve is not operated. The valve pin can also advantageously be supported by a compression spring on a stationary stop, so that it is mounted between the closing spring on the one hand and the compression spring on the other. This facilitates easy assembly and disassembly of the fuel injection valve and allows to manufacture in the longitudinal direction with relatively large tolerances.

In einer weiteren vorteilhaften Ausgestaltung der Erfindung stützt sich der Ventilbolzen an seinem ventilsitzseitigen Ende mit einer Anlagefläche am Ventilsitz ab, sodass er durch die Druckfeder ortsfest gehalten wird. Der Ventilbolzen weist in diesem Fall vorzugsweise Öffnungen auf, durch die der Kraftstoff aus einem Druckraum, der den Ventilbolzen umgibt, in Richtung der Einspritzöffnungen fließen kann.In a further advantageous embodiment of the invention, the valve pin is supported at its valve seat side end with a contact surface on the valve seat, so that it is held stationary by the compression spring. The valve pin in this case preferably has openings through which the fuel can flow from a pressure space surrounding the valve pin in the direction of the injection openings.

In einer weiteren vorteilhaften Ausgestaltung ist es ebenso möglich, dass eine weitere Hülse vorgesehen ist, die ebenfalls in der Bohrung des Ventilkörpers angeordnet ist und die den Ventilbolzen und die Ventilnadel umgibt. Die Hülse wird hierbei in der Bohrung geführt und sorgt ebenso für eine Führung des Ventilbolzens und der Ventilnadel, wobei der erste Steuerraum zwischen dem Ventilbolzen und der Ventilnadel ausgebildet ist und von der Hülse radial nach außen begrenzt wird. Die Hülse weist ventilsitznah ebenfalls Öffnungen auf, durch die Kraftstoff zu den Einspritzöffnungen fließen kann. Durch die Hülse werden sowohl der Ventilbolzen als auch die Ventilnadel sehr exakt bezüglich der Längsachse des Ventilkörpers geführt, sodass auch die Einspritzung entsprechend symmetrisch stattfindet.In a further advantageous embodiment, it is also possible that a further sleeve is provided, which is likewise arranged in the bore of the valve body and which surrounds the valve pin and the valve needle. The sleeve is guided in this case in the bore and also ensures a guide of the valve pin and the valve needle, wherein the first control chamber between the valve pin and the valve needle is formed and is bounded radially outward by the sleeve. The sleeve has valve seat near also openings through which fuel can flow to the injection openings. Through the sleeve, both the valve pin and the valve needle are guided very exactly with respect to the longitudinal axis of the valve body, so that the injection takes place correspondingly symmetrical.

In einer weiteren vorteilhaften Ausgestaltung weist der Ventilbolzen eine Aufnahme auf, in die ein Druckkolben hineinragt. Der Druckkolben begrenzt zusammen mit der Aufnahme den zweiten Steuerraum, der über einen Längskanal innerhalb des Ventilbolzens mit dem ersten Steuerraum verbunden ist. Der Druckkolben lässt sich beispielsweise über ein Piezoaktor bewegen, sodass die Bewegung der Ventilnadel direkt über dem Piezoaktor gesteuert werden kann. Durch diese Bauform, bei der die Steuerung der Ventilnadel in den Ventilkörper verlegt wird, lassen sich sehr kompakte Einspritzventile konstruieren, die dem steten Bedarfnach Bauteilverkleinerung Rechnung tragen.In a further advantageous embodiment, the valve pin has a receptacle into which a pressure piston protrudes. The plunger limits together with the recording the second control chamber, which is connected via a longitudinal channel within the valve pin with the first control chamber. The pressure piston can be moved, for example via a piezoelectric actuator, so that the movement of the valve needle can be controlled directly above the piezoelectric actuator. This design, in which the control of the valve needle is laid in the valve body, can be very compact injectors construct that take into account the constant need for component reduction.

Zeichnungdrawing

In der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt:

Figur 1
einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
Figur 1a
einen Querschnitt durch das in Figur 1 gezeigte Kraftstoffeinspritzventil entlang der Linie A-A,
Figur 2
ein weiteres Ausführungsbeispiel eines erfindungsgemäßen Kraftstoffeinspritzventils im Längsschnitt,
Figur 2a
einen Querschnitt entlang der Linie A-A und
Figur 2b
eine alternative Konstruktion des in Figur 2 gezeigten Einspritzventils, wobei nur der ventilsitzabgewandte Bereich dargestellt ist,
Figur 3, Figur 4
und
Figur 5
zeigen weitere Ausführungsbeispiele, die jeweils im Längsschnitt dargestellt sind und
Figur 6
ein letztes Ausführungsbeispiel, bei dem zusätzlich ein Piezoaktor dargestellt ist, der Teil des gesamten Einspritzventils ist.
In the drawing, various embodiments of the fuel injection valve according to the invention are shown. It shows:
FIG. 1
a longitudinal section through a fuel injection valve according to the invention,
FIG. 1a
a cross section through the in FIG. 1 shown fuel injector along the line AA,
FIG. 2
a further embodiment of a fuel injection valve according to the invention in longitudinal section,
FIG. 2a
a cross section along the line AA and
FIG. 2b
an alternative construction of the in FIG. 2 shown injector, wherein only the valve seat facing away region is shown,
FIG. 3, FIG. 4
and
FIG. 5
show further embodiments, which are each shown in longitudinal section and
FIG. 6
a final embodiment, in which in addition a piezoelectric actuator is shown, which is part of the entire injection valve.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt. Das Kraftstoffeinspritzventil umfasst einen Ventilkörper 1, der in Einbaulage gegen einen in der Zeichnung nicht dargestellten Haltekörper verspannt ist. Der Ventilkörper 1 weist eine Bohrung 3 auf, die an ihrem brennraumseitigen Ende von einem konischen Ventilsitz 4 begrenzt wird. Der konische Ventilsitz 4 läuft in eine Sacklochbohrung 6 aus, wobei wenigstens eine Einspritzöffnung 10, 10' entweder von der Sacklochbohrung 6 oder vom konischen Ventilsitz 4 ausgeht und in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraftmaschine mündet. In der Bohrung 3 ist ein Ventilbolzen 5 längsverschiebbar angeordnet, wobei zwischen der Wand der Bohrung 3 und dem Ventilbolzen 5 ein Druckraum 8 ausgebildet, der mit Kraftstoff unter hohem Druck befüllbar ist. Der Ventilbolzen 5 ist in einem mittleren Abschnitt 105 in der Bohrung 3 geführt: Figur 1a zeigt hierzu einen Querschnitt durch das in Figur 1 dargestellte Kraftstoffeinspritzventil entlang der Linie A-A. Der Ventilbolzen 5 weist im mittleren Führungsabschnitt 105 Ausnehmungen 16 in Form von Längsnuten auf, sodass hier vier Führungsflächen 17 an der Außenseite des Ventilbolzens 5 gebildet werden, die an der Wand der Bohrung 3 anliegen. Durch die Ausnehmungen 16 ist ein ausreichend großer Durchflussquerschnitt gebildet, durch den Kraftstoff in Richtung der Einspritzöffnungen 10 ungedrosselt fließen kann.In FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section. The fuel injection valve comprises a valve body 1, which is braced in the installed position against a holding body, not shown in the drawing. The valve body 1 has a bore 3 which is delimited at its combustion chamber end by a conical valve seat 4. The conical valve seat 4 terminates in a blind hole 6, wherein at least one injection opening 10, 10 'either from the blind hole 6 or starting from the conical valve seat 4 and opens in installation position of the fuel injection valve in the combustion chamber of the internal combustion engine. In the bore 3, a valve pin 5 is arranged longitudinally displaceable, wherein between the wall of the bore 3 and the valve pin 5, a pressure chamber 8 is formed which can be filled with fuel under high pressure. The valve pin 5 is guided in a middle portion 105 in the bore 3: FIG. 1a shows a cross section through the in FIG FIG. 1 illustrated fuel injection valve along the line AA. The valve pin 5 has in the middle guide portion 105 recesses 16 in the form of longitudinal grooves, so that here four guide surfaces 17 are formed on the outside of the valve pin 5, which bear against the wall of the bore 3. Through the recesses 16, a sufficiently large flow cross section is formed through which fuel in the direction of the injection openings 10 can flow unthrottled.

Am ventilsitzseitigen Ende geht der Ventilbolzen 5 in einen Führungsabschnitt 14 über, der im Durchmesser verringert ist. Auf dem Führungsabschnitt 14 ist eine Ventilnadel 7 geführt, die eine entsprechende Aufnahme 15 aufweist, die den Führungsabschnitt 14 des Ventilbolzens 5 aufnimmt. Die Ventilnadel 7 weist eine im wesentlichen konische Ventildichtfläche 11 auf, mit der sie auf dem Ventilsitz 4 aufliegt und dabei bei Anlage am Ventilsitz 4 den Druckraum 8 von den Einspritzöffnungen 10 trennt. Die Ventilnadel 7 ist über eine Schließfeder 12 gegen den Ventilbolzen 5 verspannt, wobei die Schließfeder 12 den Führungsabschnitt 14 des Ventilbolzens 5 umgibt.At the valve seat side end of the valve pin 5 is in a guide section 14, which is reduced in diameter. On the guide portion 14, a valve needle 7 is guided, which has a corresponding receptacle 15 which receives the guide portion 14 of the valve pin 5. The valve needle 7 has a substantially conical valve sealing surface 11, with which it rests on the valve seat 4 and thereby separates the pressure chamber 8 from the injection openings 10 when resting against the valve seat 4. The valve needle 7 is clamped by a closing spring 12 against the valve pin 5, wherein the closing spring 12 surrounds the guide portion 14 of the valve pin 5.

Durch die Aufnahme 15 der Ventilnadel 7 und den Führungsabschnitt 14 des Ventilbolzens 5 wird ein erster Steuerraum 25 begrenzt, der über einen im Ventilbolzen 5 ausgebildeten Längskanal 22 mit einem zweiten Steuerraum 27 verbunden ist. Dieser wird durch das ventilsitzabgewandte Ende des Ventilbolzens 5 und eine Druckhülse 18 begrenzt, wobei die Druckhülse 18 den Ventilbolzen 5 an seinem ventilsitzabgewandten Ende umgibt. Die Druckhülse 18 wird über eine Druckfeder 20, die sich an einem mit dem Ventilbolzen 5 verbundenen Stützring 13 abstützt, gegen den in der Figur 1 nicht dargestellten Haltekörper gedrückt. Dadurch wird auch der Ventilbolzen 5 in Richtung des Ventilsitzes 4 gedrückt, während er gleichzeitig von der Schließfeder 12 in die entgegengesetzte Richtung beaufschlagt wird.By receiving 15 of the valve needle 7 and the guide portion 14 of the valve pin 5, a first control chamber 25 is limited, which is connected via a formed in the valve pin 5 longitudinal channel 22 with a second control chamber 27. This is delimited by the valve seat facing away from the end of the valve pin 5 and a pressure sleeve 18, wherein the pressure sleeve 18 surrounds the valve pin 5 at its valve seat facing away from the end. The pressure sleeve 18 is supported via a compression spring 20, which is supported on a support ring 13 connected to the valve pin 5, against the in the FIG. 1 Holding body not shown pressed. As a result, the valve pin 5 is also pressed in the direction of the valve seat 4, while it is simultaneously acted upon by the closing spring 12 in the opposite direction.

Damit sich der Druck möglichst rasch von zweiten Steuerraum 27 in den ersten Steuerraum 25 fortsetzt, muss das Volumen der beiden Steuerräume 25, 27 und das Volumen des Längskanals 22 möglichst klein sein. Da der Durchmesser des Längskanals 22 fertigungsbedingt einen gewissen Mindestquerschnitt aufweisen muss, kann es vorgesehen sein, dass im Längskanal 22 ein Füllstift 31 angeordnet ist. Über die Dicke und die Länge des Füllstiftes 31 kann so das Volumen optimal angepasst werden.So that the pressure continues as quickly as possible from the second control chamber 27 into the first control chamber 25, the volume of the two control chambers 25, 27 and the volume of the longitudinal channel 22 should be as small as possible. Since the diameter of the longitudinal channel 22 due to production must have a certain minimum cross-section, it can be provided that a filling pin 31 is arranged in the longitudinal channel 22. Over the thickness and the length of the filler pin 31 so the volume can be optimally adjusted.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Im Druckraum 8 wird ein vorgegebener Kraftstoffhochdruck aufrechterhalten, der beispielsweise in einem sogenannten Common-Rail zur Verfügung gestellt wird. Durch eine gesonderte Verbindung oder durch Leckagespalte, etwa zwischen dem Ventilbolzen 5 und der Druckhülse 18, herrscht im zweiten Steuerraum 27 und über den Längskanal 22 auch im ersten Steuerraum 25 derselbe hohe Kraftstoffdruck wie im Druckraum 8. Soll eine Einspritzung erfolgen, so wird die über eine Steuervorrichtung, beispielsweise ein Steuerventil, das in dem in der Zeichnung nicht dargestellten Haltekörper untergebracht ist, ein niedrigerer Druck im zweiten Steuerraum 27 eingestellt. Durch den Druckabfall im zweiten Steuerraum 27 sinkt praktisch instantan auch der Druck im ersten Steuerraum 25, da beide Steuerräume 25, 27 über den Längskanal 22 hydraulisch miteinander verbunden sind. Dies bewirkt ein Absinken der hydraulischen Kraft auf die Ventilnadel 7, die durch den Druck im ersten Steuerraum 25 eine Schließkraft in Richtung des Ventilsitzes 4 erfährt. Durch Druckbeaufschlagung eines Teils der Ventildichtfläche 11 hebt die Ventilnadel 7 nunmehr vom Ventilsitz 4 ab, sodass Kraftstoff aus dem Druckraum 8 zwischen der Ventildichtfläche 11 und dem Ventilsitz 4 hindurch zu den Einspritzöffnungen 10 strömt und von dort in den Brennraum eingespritzt wird. Durch anschließende Druckerhöhung im zweiten Steuerraum 27 steigt auch der Druck im ersten Steuerraum 25 wieder an, und die Ventilnadel 7 gleitet zurück in ihre Schließstellung, d.h. in Anlage an den Ventilsitz 4.The operation of the fuel injection valve is as follows: In the pressure chamber 8, a predetermined high fuel pressure is maintained, which is provided for example in a so-called common rail. By a separate connection or by leakage gaps, such as between the valve pin 5 and the pressure sleeve 18, prevails in the second control chamber 27 and via the longitudinal channel 22 in the first control chamber 25, the same high fuel pressure as in the pressure chamber 8. If an injection takes place, then the over a control device, for example a control valve, which is accommodated in the holding body, not shown in the drawing, set a lower pressure in the second control chamber 27. Due to the pressure drop in the second control chamber 27, the pressure in the first control chamber 25 drops virtually instantaneously since both control chambers 25, 27 are hydraulically connected to one another via the longitudinal channel 22. This causes a drop in the hydraulic force to the valve needle 7, which experiences a closing force in the direction of the valve seat 4 by the pressure in the first control chamber 25. By pressurizing a portion of the valve sealing surface 11, the valve needle 7 now lifts off the valve seat 4, so that fuel from the pressure chamber 8 between the valve sealing surface 11 and the valve seat 4 flows through to the injection openings 10 and is injected from there into the combustion chamber. As a result of subsequent pressure increase in the second control chamber 27, the pressure in the first control chamber 25 also rises again, and the valve needle 7 slides back into its closed position, ie. in contact with the valve seat 4.

In Figur 2 ist ein zweites Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Die Ventilnadel 7 ist hier, abgesehen von der konischen Ventildichtfläche 11, als kompakter Zylinder ausgeführt und somit nicht auf dem Ventilbolzen 5 geführt. Der erste Steuerraum 25 ist zwischen der Ventilnadel 7 und der ventilsitzzugewandten Stirnfläche des Ventilbolzens 5 ausgebildet. In der Bohrung 3 ist in diesem Ausführungsbeispiel zusätzlich eine Hülse 30 angeordnet, die sowohl den Ventilbolzen 5 als auch die Druckhülse 18 und die Ventilnadel 7 umgibt und die mit einer Anlagefläche 37 am Ventilsitz 4 aufliegt. Die Hülse 30 ist ortsfest in der Bohrung 3 angeordnet und weist Ausnehmungen 16 auf, durch die - ebenso bei dem Ausführungsbeispiel nach Figur 1 - Führungsflächen 17 gebildet werden, mit denen die Hülse 30 an der Wand der Bohrung 3 anliegt. Ventilsitzzugewandt wird die Hülse 30 vom Druckraum 8 umgeben, der ebenfalls mit Kraftstoff unter hohem Druck befüllt ist. Um den Zustrom von Kraftstoff zu den Einspritzöffnungen 10 zu ermöglichen, sind an der Hülse 30 mehrere Öffnungen 32 angeordnet, die schlitzförmig ausgeführt sind und einen ausreichenden Strömungsquerschnitt zur Verfügung stellen. Figur 2a zeigt hierzu einen Querschnitt entlang der Linie A-A der Figur 2, durch die die Anordnung der Druckhülse 18 in der Hülse 30 deutlich wird. Die Funktionsweise dieses Kraftstoffeinspritzventils ist identisch mit der Funktionsweise des in Figur 1 gezeigten Einspritzventils, sodass auf eine Funktionsbeschreibung hier verzichtet werden kann.In FIG. 2 a second embodiment of the fuel injection valve according to the invention is shown. The valve needle 7 is here, apart from the conical valve sealing surface 11, designed as a compact cylinder and thus not guided on the valve pin 5. The first control chamber 25 is formed between the valve needle 7 and the valve seat facing end face of the valve pin 5. In the bore 3, a sleeve 30 is additionally arranged in this embodiment, which surrounds both the valve pin 5 and the pressure sleeve 18 and the valve needle 7 and rests with a contact surface 37 on the valve seat 4. The sleeve 30 is fixedly disposed in the bore 3 and has recesses 16 through which - also in the embodiment according to FIG. 1 - Guide surfaces 17 are formed, with which the sleeve 30 on the wall of the bore. 3 is applied. Facing the valve seat, the sleeve 30 is surrounded by the pressure chamber 8, which is also filled with fuel under high pressure. In order to allow the flow of fuel to the injection openings 10, a plurality of openings 32 are arranged on the sleeve 30, which are designed slot-shaped and provide a sufficient flow cross-section available. FIG. 2a shows a cross section along the line AA of the FIG. 2 by which the arrangement of the pressure sleeve 18 in the sleeve 30 is clear. The operation of this fuel injection valve is identical to the operation of the in FIG. 1 shown injector, so that it can be omitted here a functional description.

Figur 2b zeigt eine alternative Ausgestaltung des ventilsitzabgewandten Endes des Einspritzventils nach Figur 2, wobei hier nur die wesentlichen Komponenten gezeigt sind. Statt der Druckhülse 18 ist hier ein Druckstück 34 vorgesehen, das eine Längsbohrung 36 aufweist. Zwischen dem Druckstück 34 und dem Ventilbolzen 5 ist ein Zwischenraum 29 ausgebildet, in dem die Druckfeder 20 angeordnet ist, die das Druckstück 34 gegen den nicht gezeigten Haltekörper drückt und gleichzeitig den Ventilbolzen 5 in Richtung der Ventilnadel 7. Somit ergibt sich eine Hintereinander-Schaltung des zweiten Steuerraums 27, des Zwischenraums 29 und des ersten Steuerraums 25, die jeweils über eine Längsbohrung 36 bzw. einen Längskanal 22 im Ventilbolzen 5 und im Druckstück 34 miteinander verbunden sind. Durch diese Ausgestaltung ergeben sich andere Dämpfüngseigenschaften, insbesondere, wenn der Ventilbolzen 5 bei der Öffnungshubbewegung der Ventilnadel 7 eine leichte Bewegung ausführt. FIG. 2b shows an alternative embodiment of the valve seat facing away from the end of the injector FIG. 2 Here, only the essential components are shown. Instead of the pressure sleeve 18, a pressure piece 34 is provided here, which has a longitudinal bore 36. Between the pressure piece 34 and the valve pin 5, a gap 29 is formed in which the compression spring 20 is arranged, which presses the pressure piece 34 against the holding body, not shown, and at the same time the valve pin 5 in the direction of the valve needle 7. Thus, a series circuit the second control chamber 27, the intermediate space 29 and the first control chamber 25, which are connected to each other via a longitudinal bore 36 and a longitudinal channel 22 in the valve pin 5 and in the pressure piece 34. By this configuration, other Dämpfüngseigenschaften arise, in particular, when the valve pin 5 performs a slight movement in the opening stroke of the valve needle 7.

In Figur 3 ist ein weiteres Ausführungsbeispiel im Längsschnitt dargestellt. Der Ventilbolzen 5 ist hier, ebenso wie bei dem in Figur 1 dargestellten Ausführungsbeispiel, durch Führungsflächen 17 in der Bohrung 3 geführt. Zwischen der Druckhülse 18 und dem Ventilbolzen 5 ist hier eine Druckfeder angeordnet, die den Ventilbolzen 5 mit einer Anlagefläche 19 gegen den Ventilsitz 4 drückt. Um den Kraftstofffluss zu den Einspritzöffnungen 10 zu ermöglichen, sind hier Öffnungen 32' vorgesehen, die ähnlich wie die Öffnungen 32 in der Hülse 30 des Ausführungsbeispiels nach Figur 2 ausgeführt sind. Die Ventilnadel 7 weist der Ventildichtfläche 11 abgewandt ein kolbenförmiges Ende 21 auf, mit der sie in einer Aufnahme 24 im Ventilbolzen 5 geführt ist. Zwischen einem Ringbund 33 und einem Absatz in der Aufnahme 24 ist die Schließfeder 12 angeordnet, die die Ventilnadel 7 gegen den Ventilsitz 4 drückt. Der erste Steuerraum 25 wird durch die Stirnfläche des kolbenförmigen Endes 21 und durch die Grundfläche der Aufnahme 24 begrenzt und ist auch hier durch den Längskanal 22 mit dem zweiten Steuerraum 27 verbunden. Die Funktionsweise ist auch hier identisch mit dem der vorangegangenen Ausführungsbeispiele, wobei hier an der Ventilnadel 7 eine weitere Druckfläche 35 durch den Ringbund 33 gebildet wird, der eine zusätzliche hydraulische Kraft auf die Ventilnadel 7 in Öffnungsrichtung bewirkt. Anders als bei den vorangegangenen Ausführungsbeispielen bewegt sich der Ventilbolzen 5 hier nicht und bleibt während der gesamten Einspritzung ortsfest.In FIG. 3 is a further embodiment shown in longitudinal section. The valve pin 5 is here, as well as in the FIG. 1 illustrated embodiment, guided by guide surfaces 17 in the bore 3. Between the pressure sleeve 18 and the valve pin 5, a compression spring is arranged here, which presses the valve pin 5 with a contact surface 19 against the valve seat 4. In order to allow the fuel flow to the injection openings 10, openings 32 'are here provided, which similar to the openings 32 in the sleeve 30 of the embodiment according to FIG. 2 are executed. The valve needle 7, facing away from the valve sealing surface 11, has a piston-shaped end 21, with which it is guided in a receptacle 24 in the valve pin 5. Between a collar 33 and a shoulder in the receptacle 24, the closing spring 12 is arranged, which presses the valve needle 7 against the valve seat 4. The first control chamber 25 is formed by the end face of the piston-shaped end 21 and by the base of the receptacle 24th limited and is also connected here by the longitudinal channel 22 with the second control chamber 27. The operation is also identical to that of the preceding embodiments, in which case a further pressure surface 35 is formed by the annular collar 33 on the valve needle 7, which causes an additional hydraulic force to the valve needle 7 in the opening direction. Unlike the previous embodiments, the valve pin 5 does not move here and remains stationary during the entire injection.

In Figur 4 ist ein weiteres Ausführungsbeispiel dargestellt, wobei hier dieselbe Darstellung wie in Figur 3 gewählt wurde. Die beiden Ausführungsbeispiele unterscheiden sich nur dadurch, dass die Ventilnadel 7 hier in einen Zapfen 23 ausläuft, der in der Aufnahme 24 angeordnet ist und durch den eine Ventilnadel 7 eine Schulter gebildet wird, an der die Schließfeder 12 anliegt. Die Ventilnadel 7 wird in der Aufnahme 24 geführt, wobei sich eine hydraulische Öffnungskraft nur dadurch ergibt, dass ein Teil der Dichtfläche 11 vom Kraftstoffdruck des Druckraums 8 beaufschlagt wird.In FIG. 4 a further embodiment is shown, wherein here the same representation as in FIG. 3 was chosen. The two embodiments differ only in that the valve needle 7 terminates here in a pin 23 which is arranged in the receptacle 24 and through which a valve needle 7, a shoulder is formed on which the closing spring 12 is applied. The valve needle 7 is guided in the receptacle 24, wherein a hydraulic opening force only results from the fact that a part of the sealing surface 11 is acted upon by the fuel pressure of the pressure chamber 8.

Bei dem in Figur 5 dargestellten Ausführungsbeispiel, das ebenfalls im Längsschnitt dargestellt ist, weist der Ventilbolzen 5 keine Führungsflächen 17 auf, sondern eine zylindrische Außenform und einen Außendurchmesser, der deutlich kleiner ist als der Innendurchmesser der Bohrung 3. Um den Druckbolzen 5 in der Bohrung 3 zu zentrieren, ist eine Führungsscheibe 38 vorgesehen, die an einem Absatz 41 am Druckbolzen 5 anliegt. Zwischen der Führungsscheibe 38 und der Druckhülse 18 ist die Druckfeder 20 angeordnet, die an die Führungsscheibe 38 gegen den Absatz 41 drückt. In der Führungsscheibe 38 sind mehrere Durchlässe 39 vorgesehen, sodass der Kraftstoff durch den Druckraum 8 in Richtung der Einspritzöffnungen ungedrosselt fließen kann. Bei der Öffnungshubbewegung der Ventilnadel 7 wird nur die Ventilnadel 7 bewegt, während der Druckbolzen 5 ortsfest in der Bohrung 3 verbleibt.At the in FIG. 5 illustrated embodiment, which is also shown in longitudinal section, the valve pin 5 has no guide surfaces 17, but a cylindrical outer shape and an outer diameter which is significantly smaller than the inner diameter of the bore 3. To center the pressure pin 5 in the bore 3 is a guide plate 38 is provided, which rests against a shoulder 41 on the pressure pin 5. Between the guide plate 38 and the pressure sleeve 18, the compression spring 20 is arranged, which presses against the shoulder 41 against the shoulder 41. In the guide plate 38 a plurality of passages 39 are provided, so that the fuel can flow unthrottled through the pressure chamber 8 in the direction of the injection openings. During the opening stroke of the valve needle 7, only the valve needle 7 is moved, while the pressure pin 5 remains stationary in the bore 3.

In Figur 6 ist ein weiteres Ausführungsbeispiel dargestellt, bei dem neben dem Ventilkörper 1 noch eine Antriebsvorrichtung, hier in Form eines Piezoaktors 40 dargestellt, der in der Regel im Haltekörper angeordnet ist. Der Ventilbolzen 5 weist eine Aufnahme 24 auf, in der die Ventilnadel 7 - wie bereits in vorhergehenden Ausführungsbeispielen - geführt ist. Darüber hinaus weist der Ventilbolzen 5 an seiner gegenüberliegenden Seite eine weitere Aufnahme 26 auf, in der ein Druckkolben 42 geführt ist, wobei der zweite Steuerraum 27 durch den Druckkolben 42 und durch die Wandung der zweiten Aufnahme 26 begrenzt wird. Zwischen dem Druckkolben 42 und dem Ventilbolzen 5 ist die Druckfeder 20 angeordnet, die den Druckkolben 42 vom Ventilbolzen 5 wegdrückt.In FIG. 6 another embodiment is shown, in which in addition to the valve body 1 nor a drive device, shown here in the form of a piezoelectric actuator 40, which is usually arranged in the holding body. The valve pin 5 has a receptacle 24, in which the valve needle 7 - as in previous embodiments - is guided. In addition, the valve pin 5 on its opposite side on a further receptacle 26 in which a pressure piston 42 is guided, wherein the second control chamber 27 through the pressure piston 42 and through the wall of the second receptacle 26 is limited. Between the pressure piston 42 and the valve pin 5, the compression spring 20 is arranged, which pushes the pressure piston 42 away from the valve pin 5.

Der Druckkolben 42 ist direkt mit dem Piezoaktor 40 verbunden, sodass durch eine entsprechende Bestromung des Piezoaktors 40 eine Längsbewegung des Druckkolbens 42 erfolgt, durch die das Volumen des zweiten Steuerraums 27 veränderbar ist, so dass entweder Kraftstoff aus dem zweiten Steuerraum 27 verdrängt oder über Leckagespalte zwischen der Wand der zweiten Aufnahme 26 und dem Druckkolben 42 in den zweiten Steuerraum 27 gefordert wird. Zu Beginn der Einspritzung ist der Piezoaktor 40 verkürzt. Der zweite Steuerraum 27 ist ebenso wie der erste Steuerraum 25 und der Längskanal 22 über Leckagespalte, die z. B. zwischen dem Druckkolben 42 und der zweiten Aufnahme 26 ausgebildet sind, mit dem Druckraum 8 verbunden und damit mit Kraftstoff unter Druck befüllt. Der Piezoaktor 40 befindet sich in seiner maximalen Auslenkungslage, sodass das Volumen des zweiten Steuerraums 27 und des ersten Steuerraum 25 möglichst klein ist. Soll eine Einspritzung erfolgen, so wird der Piezoaktor 40 verkürzt, sodass sich der Druckkolben 42 zurückzieht. Hierdurch erhöht sich das Volumen des zweiten Steuerraums 27, wodurch der Druck auch im ersten Steuerraum 25 rasch absinkt, wobei zur Vermeidung von Druckschwingungen und zur zeitlichen Steuerung des Druckabfalls im Längskanal 22 eine Drossel 28 vorgesehen sein kann. Durch den Druckabfall im ersten Steuerraum 25 und die damit einhergehende Abnahme der hydraulischen Schließkraft auf die Ventilnadel 7 wird diese vom Kraftstoffdruck im Druckraum 8 in ihre Öffnungsstellung, d. h. vom Ventilsitz 4 weggedrückt, so dass die Einspritzöffnungen 10 freigegeben werden. Zur Beendigung der Einspritzung wird der Piezoaktor 40 wieder verlängert, sodass sich der Druck in den Steuerräumen 25, 27 erneut aufbaut und die Ventilnadel 7 zurück in ihre Schließstellung drückt. Über die Leckagespalte findet anschließend ein Druckausgleich zwischen dem Druckraum 8 und den Steuerräumen 25, 27 statt.The pressure piston 42 is connected directly to the piezoelectric actuator 40, so that by a corresponding energization of the piezoelectric actuator 40, a longitudinal movement of the pressure piston 42 takes place, through which the volume of the second control chamber 27 is variable, so that either fuel from the second control chamber 27 displaced or via leakage gaps between the wall of the second receptacle 26 and the pressure piston 42 in the second control chamber 27 is required. At the beginning of the injection, the piezoelectric actuator 40 is shortened. The second control chamber 27 is as well as the first control chamber 25 and the longitudinal channel 22 via leakage gaps, the z. B. are formed between the pressure piston 42 and the second receptacle 26, connected to the pressure chamber 8 and thus filled with fuel under pressure. The piezoelectric actuator 40 is in its maximum deflection position, so that the volume of the second control chamber 27 and the first control chamber 25 is as small as possible. If an injection takes place, then the piezoactuator 40 is shortened so that the pressure piston 42 retracts. This increases the volume of the second control chamber 27, as a result of which the pressure in the first control chamber 25 drops rapidly, wherein a throttle 28 can be provided to avoid pressure oscillations and to control the pressure drop in the longitudinal channel 22 over time. Due to the pressure drop in the first control chamber 25 and the concomitant decrease in the hydraulic closing force on the valve needle 7, this is the fuel pressure in the pressure chamber 8 in its open position, d. H. pushed away from the valve seat 4, so that the injection openings 10 are released. To complete the injection of the piezoelectric actuator 40 is extended again, so that the pressure in the control chambers 25, 27 builds up again and pushes the valve needle 7 back into its closed position. About the leakage column is then a pressure equalization between the pressure chamber 8 and the control chambers 25, 27 instead.

Durch die Anordnung der Komponenten nach Figur 6 kann die komplette Steuerung der Ventilnadel 7 und damit der Einspritzung in den Ventilkörper 1 verlegt werden, was im Haltekörper lediglich der Piezoaktor 40 mit seinen elektrischen Anschlüssen vorgesehen sein muss und die Verbindung des Druckraums 8 mit der Kraftstoffhochdruckquelle.By arranging the components according to FIG. 6 can be laid in the valve body 1, the entire control of the valve needle 7 and thus the injection, which must be provided in the holding body, only the piezoelectric actuator 40 with its electrical connections and the connection of the pressure chamber 8 with the high-pressure fuel source.

Die gezeigten Ausführungsbeispiele weisen drüber hinaus den Vorteil auf, dass die Ventilnadel 7 sehr klein ausgeführt ist, sodass sich die Herstellungskosten senken lassen. Dies ist insbesondere dann interessant, wenn zur weiteren Erhöhung der Präzision relativ teure Materialien zur Herstellung der Ventilnadel 7 Verwendung finden, beispielsweise Edelstähle. The exemplary embodiments shown moreover have the advantage that the valve needle 7 is made very small, so that the manufacturing costs can be reduced. This is particularly interesting if, to further increase the precision of relatively expensive Materials for the production of the valve needle 7 find use, such as stainless steels.

Claims (17)

  1. Fuel injection valve for internal combustion engines, having a valve body (1) in which is formed a bore (3) with a valve needle (7) arranged therein, the valve needle (7) interacting with a valve seat (4), which is formed in the valve body (1), in such a way that at least one injection opening (10; 10') can thereby be opened or closed, and having a valve bolt (5) which is likewise arranged in the bore (3) and which, together with the valve needle (7), delimits a first control chamber (25) which can be filled with fuel, the fuel pressure in the first control chamber (25) acting on the valve needle (7) in such a way that the latter is pressed against the valve seat (4), characterized in that a longitudinal duct (22) is formed in the valve bolt (5) to a second control chamber (27) in which a variable pressure can be set.
  2. Fuel injection valve according to Claim 1,
    characterized in that the valve bolt (5) has substantially the shape of a hollow cylinder.
  3. Fuel injection valve according to Claim 2,
    characterized in that the valve bolt (5) is supported on the valve needle (7) via a closing spring (12), such that the valve needle (7) is pressed against the valve seat (4) by the spring force.
  4. Fuel injection valve according to Claim 3,
    characterized in that the valve bolt (5) is positionally fixedly supported, at its end facing away from the valve needle (7), by means of a pressure spring (20).
  5. Fuel injection valve according to Claim 4,
    characterized in that the valve bolt (5) is supported by means of the pressure spring (20) on a pressure sleeve (18) which delimits the second control chamber (27).
  6. Fuel injection valve according to Claim 2 or 3, characterized in that the valve needle (7) has a receptacle (15) into which the valve bolt (5) protrudes with a guide section (14), such that the valve needle (7), during its movement for opening and closing the at least one injection opening (10; 10'), is guided on the guide section (14).
  7. Fuel injection valve according to Claim 2 or 3, characterized in that the valve bolt (5) has a receptacle (24) at its end facing towards the valve needle (7), into which receptacle (24) the valve needle (7) projects, and here, said valve needle (7), during its movement for opening and closing the at least one injection opening (10; 10'), is guided in the receptacle (24).
  8. Fuel injection valve according to Claim 1 or 2, characterized in that the valve bolt (5) is positionally fixedly supported, at its end facing away from the valve needle (7), by means of a pressure spring (20), and is thereby pressed with a contact surface (19) against the valve seat (4).
  9. Fuel injection valve according to Claim 8,
    characterized in that openings (32') are formed in the valve bolt (5), via which openings (32') fuel can flow to the at least one injection opening (10; 10') when the valve needle (7) opens up the at least one injection opening (10; 10').
  10. Fuel injection valve according to Claim 9,
    characterized in that a pressure surface (35) is formed on the valve needle (7), which pressure surface (35) is acted on by the fuel which acts through the openings (32') of the valve bolt (5), such that, as a result of the hydraulic force on the pressure surface (35), a force which is directed away from the valve seat (4) acts on the valve needle (7).
  11. Fuel injection valve according to Claim 1,
    characterized in that the valve bolt (5) is surrounded by a sleeve (30) which rests with a contact surface (37) on the valve seat (4) and which delimits the first control chamber (25) radially to the outside.
  12. Fuel injection valve according to Claim 1,
    characterized in that the valve bolt (5) has, facing away from the valve seat, a second receptacle (26) for a pressure piston (42), such that the second control chamber (27) is delimited by the wall (26) of the second receptacle and by the pressure piston (42).
  13. Fuel injection valve according to Claim 12,
    characterized in that the pressure bolt (5) can be moved longitudinally by a drive device (40), in such a way that the volume of the second control chamber (27) can be varied by means of the longitudinal movement of said pressure bolt (5).
  14. Fuel injection valve according to Claim 13,
    characterized in that the drive device is a piezoelectric actuator (40).
  15. Fuel injection valve according to Claim 12 or 13, characterized in that a throttle point (28) is provided in the longitudinal duct (22).
  16. Fuel injection valve according to one of the preceding claims, characterized in that the valve bolt (5) is centred in the bore (3) of the valve body (1) by guide surfaces (17) which bear against the wall of the bore (3).
  17. Fuel injection valve according to Claim 16,
    characterized in that recesses (16) are formed on the valve bolt (5), which recesses (16) enable a flow of fuel to the at least one injection opening (10; 10').
EP07704166A 2006-03-21 2007-01-26 Fuel injection valves for internal combustion engines Not-in-force EP1999363B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102006012842A DE102006012842A1 (en) 2006-03-21 2006-03-21 Fuel injection valves for internal combustion engines
PCT/EP2007/050775 WO2007107397A1 (en) 2006-03-21 2007-01-26 Fuel injection valves for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1999363A1 EP1999363A1 (en) 2008-12-10
EP1999363B1 true EP1999363B1 (en) 2010-05-12

Family

ID=38169609

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07704166A Not-in-force EP1999363B1 (en) 2006-03-21 2007-01-26 Fuel injection valves for internal combustion engines

Country Status (4)

Country Link
EP (1) EP1999363B1 (en)
AT (1) ATE467756T1 (en)
DE (2) DE102006012842A1 (en)
WO (1) WO2007107397A1 (en)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007035752A1 (en) * 2007-07-31 2009-02-05 Robert Bosch Gmbh Fuel injector with a seated on the cone valve seat of a nozzle needle centering as a guide for the nozzle needle
DE102013212269A1 (en) 2013-06-26 2014-12-31 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
CH709403A1 (en) * 2014-03-25 2015-09-30 Liebherr Machines Bulle Sa Injector and internal combustion engine with a corresponding injector.

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0967382B1 (en) * 1998-06-24 2004-11-24 Delphi Technologies, Inc. Fuel injector
DE10118699A1 (en) * 2001-04-17 2002-10-31 Bosch Gmbh Robert Fuel injection device and fuel system for internal combustion engines, and internal combustion engine
DE10326044A1 (en) * 2003-06-10 2004-12-30 Robert Bosch Gmbh Injection nozzle for internal combustion engines
EP1566538B1 (en) * 2004-02-20 2006-08-09 Delphi Technologies, Inc. Injection nozzle
EP1693561B1 (en) * 2005-01-19 2008-03-05 Delphi Technologies, Inc. Fuel injector

Also Published As

Publication number Publication date
DE102006012842A1 (en) 2007-09-27
EP1999363A1 (en) 2008-12-10
WO2007107397A1 (en) 2007-09-27
ATE467756T1 (en) 2010-05-15
DE502007003735D1 (en) 2010-06-24

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