EP2581597A1 - Fuel injection valve for internal combustion engines with directly actuated valve needle - Google Patents

Fuel injection valve for internal combustion engines with directly actuated valve needle Download PDF

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Publication number
EP2581597A1
EP2581597A1 EP12185618.1A EP12185618A EP2581597A1 EP 2581597 A1 EP2581597 A1 EP 2581597A1 EP 12185618 A EP12185618 A EP 12185618A EP 2581597 A1 EP2581597 A1 EP 2581597A1
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EP
European Patent Office
Prior art keywords
pressure
valve needle
valve
fuel injection
actuator
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.)
Granted
Application number
EP12185618.1A
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German (de)
French (fr)
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EP2581597B1 (en
Inventor
Henning Kreschel
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Robert Bosch GmbH
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Robert Bosch GmbH
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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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/701—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical
    • F02M2200/702—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger mechanical with actuator and actuated element moving in different directions, e.g. in opposite directions
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines, as it is used in particular for the injection of fuel in auto-igniting, high-speed internal combustion engines.
  • valves are known from the prior art with which fuel can be injected directly into the combustion chamber of self-igniting high-speed internal combustion engines.
  • the fuel is injected at pressures of up to 2500 bar, wherein the injection is controlled in the known injectors usually by means of a valve needle.
  • the valve needle acts together with a valve seat and is arranged in a pressure chamber in which fuel is kept under high pressure. Due to the high fuel pressure in the pressure chamber, very high hydraulic forces, which are used to move the valve needle in the longitudinal direction and to move it relative to the valve seat, act on the valve needle. Downstream of the valve seat one or more injection openings are arranged in the fuel injection valves, via which the fuel finally exits.
  • a direct control of the valve needle as is customary, for example, in spark-ignited internal combustion engines, eliminates due to the high hydraulic forces usually.
  • a fuel injection valve which has a piezoelectric actuator which moves a control piston via a hydraulic coupler.
  • the spool is hydraulic with the valve needle connected.
  • the control piston Upon actuation of the actuator, the control piston is moved away from the valve needle, whereby the fuel pressure in the control chamber of the valve needle is reduced and the valve needle lifts off from the valve seat, which ultimately releases the injection openings.
  • the valve needle can be controlled very precisely with the help of the piezoelectric actuator with this concept, however, the needle movement takes place here also with the aid of hydraulic forces on the valve needle.
  • fuel is removed from the control chamber each time it is opened, although it must be compressed by the high-pressure pump, but ultimately does not reach injection. This reduces the efficiency of the internal combustion engine.
  • a fuel injection valve which also works with a piezoelectric actuator.
  • the piezoelectric actuator acts via a lever, so a mechanical coupler, indirectly on the valve needle and can lift them controlled by the piezoelectric actuator from the valve seat.
  • the valve needle is in this case force balanced, that is, on the side facing away from the valve seat of the valve needle, a control chamber is formed, which is also flooded with fuel at high pressure, which largely lift the opening and closing hydraulic forces against each other.
  • the necessary forces must be applied by the piezoelectric actuator and the associated mechanical coupler. Which can be problematic depending on the injection pressure, in particular with regard to the wear of the mechanical coupler.
  • a fuel injection valve in which both a mechanical opening force is applied to the valve needle, as well as provide hydraulic forces for opening the valve needle.
  • a piezoelectric actuator is formed, which transmits the force to a control valve via a hydraulic coupler, on the one hand provides for the pressure relief in the control room, and on the other hand transmits via a mechanical coupler of an opening force on the valve needle.
  • this design is relatively expensive and does not cause the valve needle is ultimately balanced. There is still a lot of energy needed to move the valve needle and it will fall Fuel control amounts that reduce the efficiency of the internal combustion engine.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the valve needle is largely balanced in force both in its open and in its closed position. This allows on the one hand the movement of the valve needle with low energy consumption and avoids the other fuel control quantities, which otherwise have to be additionally compressed in servohydraulic valves of the high-pressure fuel pump.
  • the fuel injection valve can thereby be operated efficiently, with multiple injections being possible in one cycle due to the short switching times.
  • the valve needle on the opposite side of its valve sealing surface on a pin extension, which projects into a low pressure chamber and which is connected to a mechanical coupler, via which an opening force can be exerted on the valve needle. Since the valve needle is force-balanced in its closed position, the mechanical coupler only small forces on the pin extension and thus transferred in the longitudinal direction of the valve needle to move the valve needle in the opening direction.
  • an electrical actuator is at least indirectly connected to the mechanical coupler, so that the force of the actuator via the mechanical coupler is transferable to the valve needle.
  • the mechanical coupler preferably consists of a rocker arm having two ends, wherein the actuator acts at least indirectly on the first end and the second end is connected to the pin extension.
  • a hydraulic coupler is arranged between the actuator and the mechanical coupler, via which the force of the actuator is transmitted to the mechanical coupler.
  • changes of the actuator must be compensated, as resulting, for example, from thermal fluctuations.
  • the hydraulic coupler in this case comprises a primary piston, which is directly connected to the actuator, and a secondary piston separated from it by a hydraulic working space, which is connected to the mechanical coupler. The size of the hydraulic working space is variable, so that thereby a change in length of the actuator can be compensated.
  • An increase of the actuator movement can also be generated by the hydraulic coupler: If the primary piston has a larger diameter than the secondary piston, a larger amount of fuel in the hydraulic working space is displaced by the movement of the primary piston than by an equal movement of the secondary piston. If the primary piston thus moves along a certain distance, the displacement of the fuel in the hydraulic working space leads to a greater movement of the secondary piston. Together with the path reinforcement by the mechanical actuator can thus achieve a relatively large gain, so that even a small actuator is sufficient to achieve the necessary stroke for opening the valve needle.
  • the valve needle is hydraulically designed in its closed position so that a force equalization is achieved by the size of the sealing surface, with which the valve needle rests on the valve seat, and the size of the pin extension.
  • a gap choke is advantageously formed between the valve needle and the wall of the pressure chamber at which a pressure gradient between the region of the pressure chamber upstream of the gap throttle and the region downstream of the gap choke is formed with open valve needle. This results in a hydraulic closing force on the valve needle, which is compensated by the fact that now the part of the valve sealing surface, which is not acted upon by the fuel pressure in the pressure chamber in the closed valve needle, by lifting the Valve needle experiences a hydraulic force in the opening direction.
  • the gap choke can be achieved so even when the valve needle is open, a force balance of the valve needle.
  • the pressure difference before and after the gap throttle is about 10% of the upstream pressure, but at least 50 bar and at most 150 bar.
  • the mechanical coupler is arranged in the low-pressure space, wherein the low-pressure chamber is connected to a drain hole, which ensures a low pressure in the low pressure chamber always low.
  • the arrangement of the mechanical coupler and thus also the hydraulic coupler in the low-pressure space facilitates, in contrast to installation in a high-pressure region of the injector, the construction and thereby allows a simpler and more cost-effective production of the fuel injection valve.
  • the electrical actuator can be designed as a piezoelectric actuator, as a magnetic actuator or as a magnetostrictive actuator. Other types of actuators may also be considered, provided that they are suitable for use in a fuel injection valve.
  • Fig. 1 is a fuel injection valve according to the invention in longitudinal section dargterrorism.
  • the fuel injection valve has a holding body 1, an intermediate disc 2 and a valve body 3 which abut each other in this order.
  • the valve body 3 is clamped by a clamping nut 4 with the interposition of the washer 2 against the holding body 1.
  • a pressure chamber 5 is formed, which is designed as a blind hole and which emanates from the holding body 1 facing side of the valve body 3.
  • the pressure chamber is bounded at its base by a substantially conical valve seat 7.
  • the conical valve seat 7 is followed by a blind hole 11, from which one or more injection openings 10 emanate, via which the fuel is ultimately injected into the combustion chamber of the internal combustion engine.
  • the pressure chamber 5 is filled via a running in the washer 2 and the holding body 1 high-pressure bore 6 with fuel at high pressure.
  • the fuel is provided for example in a so-called rail available.
  • the rail is a high-pressure accumulator, which is filled via a high-pressure pump with fuel under high pressure, so that in the high-pressure bore 6 during operation of the internal combustion engine is always available fuel under injection pressure.
  • a kobenförmige valve needle 8 is arranged, which is guided longitudinally displaceable and at its the valve seat 7 facing the end of a valve sealing surface 9, which consists essentially of two conical surfaces.
  • a valve sealing surface 9 which consists essentially of two conical surfaces.
  • the area marked II is in Fig. 2 shown enlarged again.
  • a sealing edge 12 is formed, with which the valve needle 8 rests on the valve seat 7 and thereby separates the pressure chamber 5 from the blind hole 11 and thus from the injection openings 10.
  • the valve needle 8 has a diameter D and extends with this diameter, starting from the valve seat 7 to a guide portion 108.
  • the valve body 5 in FIG. 3 shown enlarged again.
  • the valve needle 8 is guided in the pressure chamber 5, wherein the fuel flow is ensured by a plurality of poles on the valve needle 8, which are formed in the guide portion 108.
  • the pressure chamber 5 expands, starting from the valve seat 7, to the holder body-side end of the valve body 3 to a spring chamber 105 into which the high-pressure bore 6 opens.
  • a closing spring 16 is arranged, which surrounds the valve needle 8 and which is supported at one end to a shoulder 208 of the valve needle 8. With its other end, the closing spring 16 bears against a sleeve 15, which is pressed by the force of the closing spring 16 against the washer 2.
  • the valve needle 8 is designed in this area as a pin extension 13, which has a diameter d, which is significantly smaller than the diameter D of the valve needle 8 at the valve seat side end.
  • the sleeve 15 is guided on the pin extension 13, wherein between the sleeve 15 and the pin extension 13 only a very small gap remains, as he is necessary for movement of the pin extension 13 in the sleeve 15.
  • the pin extension 13 protrudes through a guide bore 17 in the intermediate disc 2 through into a low-pressure space 18, which is formed in the holding body 1.
  • the sealing of the pressure chamber 5 with respect to the low pressure chamber 18 is done on the one hand by the seal of the guide sleeve 15 on the washer 2 and on the other hand by the sliding seal between the pin extension 13 and the sleeve 15th
  • a gap throttle 14 which is formed by a circumferential collar and which leaves only a very small gap between the valve needle 8 and the wall of the pressure chamber 5.
  • the fuel that flows through the high-pressure bore 6 via the spring chamber 105 in the valve seat side region of the pressure chamber 5 is throttled at this point in the gap throttle 14, which causes a pressure difference between the spring chamber 105 and the valve seat side region of the pressure chamber 5 with flowing fuel.
  • a mechanical coupler 20 is arranged, which comprises a rocker arm 22 rotatably mounted about a pivot point 24.
  • the rocker arm 22 has a first end 122 and a second end 222 which is connected to the pin extension 13. If the first end 122 of the rocker arm 22 is pressed in the direction of the intermediate disk 2, the rotation is reversed the pivot point 24, the second end 222 of the rocker arm 22 and lifts the valve needle 13 from the valve seat 7 from.
  • an electrical actuator 40 is formed, which is formed for example as a piezoelectric actuator.
  • the piezoelectric actuator 40 has at its end facing the valve body 3 an actuator head 42, which is connected to a hydraulic coupler 30, which is also arranged in the low-pressure chamber 18.
  • the hydraulic coupler 30 consists of a primary piston 32 which is connected to the actuator head 42, and a secondary piston 33, which is supported on the first end 122 of the rocker arm 22. Between the primary piston 22 and the secondary piston 33, which are both guided in a coupler sleeve 34, a hydraulic working space 35 is formed.
  • the hydraulic working space 35 allows a length compensation, as required by thermal changes in length of the actuator 40. Since these happen only comparatively slowly, the different filling of the hydraulic working space 35 can be easily compensated by the supply or discharge of fuel from or into the low-pressure space 18.
  • the stroke of the piezoelectric actuator is comparatively low and usually does not exceed 0.1 to 0.2% of its total length. If this is not sufficient for the stroke of the valve needle 8, both the hydraulic coupler 30, and the mechanical coupler 20 can be used to increase the maximum stroke.
  • the primary piston 32 has a larger diameter than the secondary piston 33. In its movement in the direction of the washer 2, the primary piston 32 thus displaces more fuel than the secondary piston 33 at the same stroke, so that the secondary piston 33 passes a greater distance than the Primary piston 32.
  • Further reinforcement may be achieved by the mechanical coupler 20 by having the effective lever from pivot 24 to first end 122 be smaller than the effective lever from pivot 24 to second end 222.
  • the path gain of the couplers may be up to 1, respectively. 5, d. H. that a change in length of the piezoelectric actuator of 100 microns leads to a movement of the mechanical coupler of 150 microns, which can be further enhanced in the mechanical coupler.
  • the piezoelectric actuator 40 is energized, whereby it expands in the longitudinal direction and moves the primary piston 32 in the direction of the washer 2 via the actuator head 42.
  • the fuel in the hydraulic working chamber 35 is compressed, and the increasing pressure in the hydraulic working chamber 35 pushes the secondary piston 33 also in the direction of the washer 2.
  • the valve needle 8 is pulled away from the valve seat 7. Due to the force compensation of the valve needle 8 in the longitudinal direction only a small force is necessary for the longitudinal movement, which can be applied via the piezoelectric actuator 40 without further notice.
  • the fuel flows from the pressure chamber 5 into the blind hole 11 and from there through the injection openings 10 into the combustion chamber of the internal combustion engine.
  • gap throttle 14 By suitable dimensioning of the gap throttle 14 can be achieved so that in turn results in a force balance due to the higher hydraulic pressure in the spring chamber 105 and the reduced fuel pressure on the valve sealing surface 9. Even in the open state of the valve needle 8, a force compensation in the longitudinal direction can be achieved, which requires only a small closing force on the valve needle 8, which can be easily reached via the mechanical coupler.
  • valve needle 8 In order to accelerate the closing of the valve needle 8, however, it may also be provided to generate a slight hydraulic closing force on the valve needle by means of suitable design parameters in the open state. A force through the mediation of the mechanical coupler 20 is then no longer required to close the valve needle 8, without pulling large hydraulic forces on the mechanical coupler 20, when it holds the valve needle 8 in its open position.
  • the sleeve 15 is omitted and the closing spring 16 on the one hand continues to be supported on the shoulder 208, but on the other hand directly to the washer 2.
  • the sealing of the pressure chamber 5 relative to the low-pressure chamber 18 then takes place exclusively through the gap choke, between the Pin extension 13 and the guide hole 17 in the washer 2 remains.
  • a washer 2 which has a greater thickness, so a sufficient seal is achieved.
  • the representation of the fuel injection valve in particular the representation of the hydraulic coupler 30, is only to be understood schematically.
  • the coupler sleeve 34 is firmly fixed in the actual embodiment in the holding body 1 so that it does not move during operation of the fuel injection valve.
  • the illustrated fuel injection valve according to the invention has the particular advantage that both the piezoelectric actuator 40, and the hydraulic coupler 30 and the mechanical coupler 20 are housed in low pressure.
  • both the piezoelectric actuator 40, and the hydraulic coupler 30 and the mechanical coupler 20 are housed in low pressure.
  • the high-pressure bore 6 in the entire holding body only low pressure, which significantly simplifies the design and construction of the coupler and the construction of the piezoelectric actuator and its encapsulation to seal against the fuel, which fills the entire low-pressure chamber 18, considerably simplified.
  • the fuel injection valve according to the invention operates without Abêtmenge, as inevitably obtained in servohydraulic control valves. This increases the efficiency of the injection system because the high pressure pump, which ultimately compresses the fuel and which is driven by the engine itself, need only insignificantly compress more fuel to the high injection pressure, as actually injected.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

The valve has a valve sealing surface cooperating with a valve seat (7) for opening and closing an injection opening (10). A pressure chamber (5) is filled with fuel under injection pressure, and hydraulic forces are developed on a valve needle (8) and are raised with contact of the valve needle on the valve seat. A bolt extension (13) is formed at the valve needle and opposite to the valve seat surface. The bolt extension is projected into a low pressure chamber (18) and is connected with a mechanical coupler (20). Opening force is exerted on the valve needle by the coupler.

Description

Die Erfindung betrifft ein Kraftstoffeinspritzventil für Brennkraftmaschinen, wie es insbesondere zur Einspritzung von Kraftstoff in selbstzündende, schnelllaufende Brennkraftmaschinen Verwendung findet.The invention relates to a fuel injection valve for internal combustion engines, as it is used in particular for the injection of fuel in auto-igniting, high-speed internal combustion engines.

Stand der TechnikState of the art

Aus dem Stand der Technik sind verschiedene Kraftstoffeinspritzventile bekannt, mit denen Kraftstoff direkt in den Brennraum von selbstzündenden schnelllaufenden Brennkraftmaschinen eingespritzt werden kann. Der Kraftstoff wird dabei mit Drücken von bis zu 2500 bar eingespritzt, wobei die Einspritzung bei den bekannten Einspritzventilen in der Regel mittels einer Ventilnadel gesteuert wird. Die Ventilnadel wirkt dabei mit einem Ventilsitz zusammen und ist in einem Druckraum angeordnet, in dem Kraftstoff unter hohem Druck vorgehalten wird. Auf die Ventilnadel wirken dabei bedingt durch den hohen Kraftstoffdruck im Druckraum sehr hohe hydraulische Kräfte, die benutzt werden, um die Ventilnadel in Längsrichtung zu bewegen und relativ zum Ventilsitz zu bewegen. Dem Ventilsitz nachgeordnet sind in den Kraftstoffeinspritzventilen eine oder mehrere Einspritzöffnungen angeordnet, über die der Kraftstoff schließlich austritt. Eine direkte Ansteuerung der Ventilnadel, wie es beispielsweise bei fremdgezündeten Brennkraftmaschinen üblich ist, scheidet aufgrund der hohen hydraulischen Kräfte in aller Regel aus.Various fuel injection valves are known from the prior art with which fuel can be injected directly into the combustion chamber of self-igniting high-speed internal combustion engines. The fuel is injected at pressures of up to 2500 bar, wherein the injection is controlled in the known injectors usually by means of a valve needle. The valve needle acts together with a valve seat and is arranged in a pressure chamber in which fuel is kept under high pressure. Due to the high fuel pressure in the pressure chamber, very high hydraulic forces, which are used to move the valve needle in the longitudinal direction and to move it relative to the valve seat, act on the valve needle. Downstream of the valve seat one or more injection openings are arranged in the fuel injection valves, via which the fuel finally exits. A direct control of the valve needle, as is customary, for example, in spark-ignited internal combustion engines, eliminates due to the high hydraulic forces usually.

Aus der DE 10 2006 026 399 A1 ist ein Kraftstoffeinspritzventil bekannt, das einen piezoelektrischen Aktor aufweist, der über einen hydraulischen Koppler einen Steuerkolben bewegt. Der Steuerkolben ist hydraulisch mit der Ventilnadel verbunden. Bei einer Betätigung des Aktors wird der Steuerkolben von der Ventilnadel wegbewegt, wodurch sich der Kraftstoffdruck im Steuerraum der Ventilnadel reduziert und die Ventilnadel vom Ventilsitz abhebt, was letztendlich die Einspritzöffnungen freigibt. Die Ventilnadel kann mit diesem Konzept sehr präzise mit Hilfe des Piezoaktors gesteuert werden, jedoch erfolgt die Nadelbewegung auch hier mit Hilfe der hydraulischen Kräfte auf die Ventilnadel. Bei diesem Servoventil wird bei jedem Öffnen Kraftstoff aus dem Steuerraum abgesteuert, der zwar von der Hochdruckpumpe verdichtet werden muss, letztendlich aber nicht zur Einspritzung gelangt. Dies reduziert den Wirkungsgrad der Brennkraftmaschine.From the DE 10 2006 026 399 A1 For example, a fuel injection valve is known, which has a piezoelectric actuator which moves a control piston via a hydraulic coupler. The spool is hydraulic with the valve needle connected. Upon actuation of the actuator, the control piston is moved away from the valve needle, whereby the fuel pressure in the control chamber of the valve needle is reduced and the valve needle lifts off from the valve seat, which ultimately releases the injection openings. The valve needle can be controlled very precisely with the help of the piezoelectric actuator with this concept, however, the needle movement takes place here also with the aid of hydraulic forces on the valve needle. With this servo valve, fuel is removed from the control chamber each time it is opened, although it must be compressed by the high-pressure pump, but ultimately does not reach injection. This reduces the efficiency of the internal combustion engine.

Darüber hinaus ist aus der Offenlegungsschrift DE 102 20 498 A1 ein Kraftstoffeinspritzventil bekannt, das ebenfalls mit einem Piezoaktor arbeitet. Der Piezoaktor wirkt dabei über einen Hebel, also einem mechanischen Koppler, indirekt auf die Ventilnadel und kann diese gesteuert durch den Piezoaktor vom Ventilsitz abheben. Die Ventilnadel ist hierbei kraftausgeglichen, das heißt, dass auf der dem Ventilsitz abgewandten Seite der Ventilnadel ein Steuerraum ausgebildet ist, der ebenfalls mit Kraftstoff unter hohem Druck geflutet ist, wodurch sich die öffnenden und schließenden hydraulischen Kräfte gegeneinander weitgehend wegheben. Dies gilt jedoch nur dann, wenn die Ventilnadel in ihrer Schließstellung ist. Beim Öffnen der Ventilnadel müssen die notwendigen Kräfte vom Piezoaktor und dem damit verbundenen mechanischen Koppler aufgebracht werden. Was je nach Einspritzdruck problematisch sein kann, insbesondere im Hinblick auf den Verschleiß des mechanischen Kopplers.In addition, from the published patent application DE 102 20 498 A1 a fuel injection valve is known, which also works with a piezoelectric actuator. The piezoelectric actuator acts via a lever, so a mechanical coupler, indirectly on the valve needle and can lift them controlled by the piezoelectric actuator from the valve seat. The valve needle is in this case force balanced, that is, on the side facing away from the valve seat of the valve needle, a control chamber is formed, which is also flooded with fuel at high pressure, which largely lift the opening and closing hydraulic forces against each other. However, this only applies if the valve needle is in its closed position. When opening the valve needle, the necessary forces must be applied by the piezoelectric actuator and the associated mechanical coupler. Which can be problematic depending on the injection pressure, in particular with regard to the wear of the mechanical coupler.

Aus der DE 10 2008 042 136 A1 ist weiter ein Kraftstoffeinspritzventil bekannt, bei dem auf die Ventilnadel sowohl eine mechanische öffnende Kraft aufgebracht wird, als auch hydraulische Kräfte für das Öffnen der Ventilnadel sorgen. Hierzu ist ein Piezoaktor ausgebildet, der über einen hydraulischen Koppler die Kraft auf ein Steuerventil überträgt, das einerseits für die Druckentlastung im Steuerraum sorgt, und das andererseits über einen mechanischen Koppler einer Öffnungskraft auf die Ventilnadel überträgt. Diese Konstruktion ist jedoch relativ aufwendig und führt nicht dazu, dass die Ventilnadel letztendlich kraftausgeglichen ist. Es ist nach wie vor viel Energie für das Bewegen der Ventilnadel notwendig und es fallen Kraftstoff-Steuermengen an, die die Effizienz der Brennkraftmaschine herabsetzen.From the DE 10 2008 042 136 A1 Further, a fuel injection valve is known in which both a mechanical opening force is applied to the valve needle, as well as provide hydraulic forces for opening the valve needle. For this purpose, a piezoelectric actuator is formed, which transmits the force to a control valve via a hydraulic coupler, on the one hand provides for the pressure relief in the control room, and on the other hand transmits via a mechanical coupler of an opening force on the valve needle. However, this design is relatively expensive and does not cause the valve needle is ultimately balanced. There is still a lot of energy needed to move the valve needle and it will fall Fuel control amounts that reduce the efficiency of the internal combustion engine.

Offenbarung der ErfindungDisclosure of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass die Ventilnadel sowohl in ihrer geöffneten als auch in ihrer geschlossenen Stellung weitgehend kraftausgeglichen ist. Dies ermöglicht zum einen das Bewegen der Ventilnadel mit geringem Energieaufwand und Vermeidet zum anderen Kraftstoff-Steuermengen, die bei servohydraulischen Ventilen sonst von der Kraftstoffhochdruckpumpe zusätzlich verdichten werden müssen. Das Kraftstoffeinspritzventil kann dadurch effizient betrieben werden, wobei aufgrund der kurzen Schaltzeiten problemlos mehrere Einspritzungen in einem Zyklus möglich sind. Hierzu weist die Ventilnadel an der ihrer Ventildichtfläche entgegen gesetzten Seite einen Stiftfortsatz auf, der in einen Niederdruckraum ragt und der mit einem mechanischen Koppler verbunden ist, über den eine Öffnungskraft auf die Ventilnadel ausgeübt werden kann. Da die Ventilnadel in ihrer geschlossenen Stellung kraftausgeglichen ist, muss der mechanische Koppler nur geringe Kräfte auf den Stiftfortsatz und damit in Längsrichtung der Ventilnadel übertragen, um die Ventilnadel in Öffnungsrichtung zu bewegen.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the valve needle is largely balanced in force both in its open and in its closed position. This allows on the one hand the movement of the valve needle with low energy consumption and avoids the other fuel control quantities, which otherwise have to be additionally compressed in servohydraulic valves of the high-pressure fuel pump. The fuel injection valve can thereby be operated efficiently, with multiple injections being possible in one cycle due to the short switching times. For this purpose, the valve needle on the opposite side of its valve sealing surface on a pin extension, which projects into a low pressure chamber and which is connected to a mechanical coupler, via which an opening force can be exerted on the valve needle. Since the valve needle is force-balanced in its closed position, the mechanical coupler only small forces on the pin extension and thus transferred in the longitudinal direction of the valve needle to move the valve needle in the opening direction.

In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist ein elektrischer Aktor zumindest mittelbar mit dem mechanischen Koppler verbunden, so dass die Kraft des Aktors über den mechanischen Koppler auf die Ventilnadel übertragbar ist. Der mechanische Koppler besteht hierbei vorzugsweise aus einem Kipphebel, der zwei Enden aufweist, wobei der Aktor zumindest mittelbar auf das erste Ende einwirkt und das zweite Ende mit dem Stiftfortsatz verbunden ist. Durch diese Konstruktion lässt sich in vorteilhafter Weise auch eine Wegverstärkung der Aktorbewegung erreichen, indem der Kipphebel einen Drehpunkt aufweist und der wirksame Hebel vom Drehpunkt zum ersten Ende des Kipphebels kleiner ist als der wirksame Hebel zum zweiten Ende des Kipphebels.In an advantageous embodiment of the object of the invention, an electrical actuator is at least indirectly connected to the mechanical coupler, so that the force of the actuator via the mechanical coupler is transferable to the valve needle. The mechanical coupler preferably consists of a rocker arm having two ends, wherein the actuator acts at least indirectly on the first end and the second end is connected to the pin extension. By this construction can be achieved in an advantageous manner, a Wegverstärkung the actuator movement by the rocker arm having a pivot point and the effective lever from the pivot point to the first end of the rocker arm is smaller than the effective lever to the second end of the rocker arm.

In einer weiteren vorteilhaften Ausgestaltung ist zwischen dem Aktor und dem mechanischen Koppler ein hydraulischer Koppler angeordnet, über den die Kraft des Aktors auf den mechanischen Koppler übertragen wird. Insbesondere bei Verwendung eines Piezoaktors oder eines magnetostriktiven Aktors müssen Längenänderungen des Aktors ausgeglichen werden, wie sie beispielsweise aus thermischen Schwankungen resultieren. Dies kann in vorteilhafter Weise mit einem hydraulischen Koppler geschehen. Der hydraulische Koppler umfasst hierbei einen Primärkolben, der direkt mit dem Aktor verbunden ist, und einen durch einen hydraulischen Arbeitsraum davon getrennten Sekundärkolben, der mit dem mechanischen Koppler verbunden ist. Die Größe des hydraulischen Arbeitsraums ist variabel, so dass dadurch eine Längenänderung des Aktors ausgeglichen werden kann.In a further advantageous embodiment, a hydraulic coupler is arranged between the actuator and the mechanical coupler, via which the force of the actuator is transmitted to the mechanical coupler. In particular, when using a piezoelectric actuator or a magnetostrictive actuator length changes of the actuator must be compensated, as resulting, for example, from thermal fluctuations. This can be done advantageously with a hydraulic coupler. The hydraulic coupler in this case comprises a primary piston, which is directly connected to the actuator, and a secondary piston separated from it by a hydraulic working space, which is connected to the mechanical coupler. The size of the hydraulic working space is variable, so that thereby a change in length of the actuator can be compensated.

Auch durch den hydraulischen Koppler lässt sich eine Verstärkung der Aktorbewegung erzeugen: Weist der Primärkolben einen größeren Durchmesser auf als der Sekundärkolben, so wird durch die Bewegung des Primärkolbens eine größere Kraftstoffmenge im hydraulischen Arbeitsraum verdrängt als durch eine gleich große Bewegung des Sekundärkolbens. Bewegt sich der Primärkolben damit eine bestimmte Wegstrecke, so führt die Verdrängung des Kraftstoffs im hydraulischen Arbeitsraum zu einer größeren Bewegung des Sekundärkolbens. Zusammen mit der Wegverstärkung durch den mechanischen Aktor lässt sich so eine relativ große Verstärkung erreichen, so dass bereits ein kleiner Aktor ausreicht, um den notwendigen Hub für das Öffnen der Ventilnadel zu erreichen.An increase of the actuator movement can also be generated by the hydraulic coupler: If the primary piston has a larger diameter than the secondary piston, a larger amount of fuel in the hydraulic working space is displaced by the movement of the primary piston than by an equal movement of the secondary piston. If the primary piston thus moves along a certain distance, the displacement of the fuel in the hydraulic working space leads to a greater movement of the secondary piston. Together with the path reinforcement by the mechanical actuator can thus achieve a relatively large gain, so that even a small actuator is sufficient to achieve the necessary stroke for opening the valve needle.

Die Ventilnadel ist in ihrer geschlossenen Stellung hydraulisch so ausgelegt, dass durch die Größe der Dichtfläche, mit der die Ventilnadel auf dem Ventilsitz aufliegt, und die Größe des Stiftfortsatzes ein Kraftausgleich erreicht wird. Um einen Kraftausgleich auch bei geöffneter Ventilnadel zu erreichen, ist in vorteilhafterweise zwischen der Ventilnadel und der Wand des Druckraums eine Spaltdrossel ausgebildet, an der sich bei geöffneter Ventilnadel ein Druckgefälle zwischen dem Bereich des Druckraums stromaufwärts der Spaltdrossel und dem Bereich stromabwärts der Spaltdrossel bildet. Dadurch ergibt sich eine hydraulische Schließkraft auf die Ventilnadel, die jedoch dadurch ausgeglichen wird, dass jetzt der Teil der Ventildichtfläche, der bei geschlossener Ventilnadel nicht vom Kraftstoffdruck im Druckraum beaufschlagt wird, durch das Abheben der Ventilnadel eine hydraulische Kraft in Öffnungsrichtung erfährt. Bei entsprechender Auslegung der Spaltdrossel lässt sich so auch bei geöffneter Ventilnadel ein Kraftausgleich der Ventilnadel erreichen. In vorteilhafter Weise beträgt dabei die Druckdifferenz vor und hinter der Spaltdrossel etwa 10 % des stromaufwärtigen Drucks, mindestens aber 50 bar und höchstens 150 bar.The valve needle is hydraulically designed in its closed position so that a force equalization is achieved by the size of the sealing surface, with which the valve needle rests on the valve seat, and the size of the pin extension. In order to achieve a force balance even when the valve needle is open, a gap choke is advantageously formed between the valve needle and the wall of the pressure chamber at which a pressure gradient between the region of the pressure chamber upstream of the gap throttle and the region downstream of the gap choke is formed with open valve needle. This results in a hydraulic closing force on the valve needle, which is compensated by the fact that now the part of the valve sealing surface, which is not acted upon by the fuel pressure in the pressure chamber in the closed valve needle, by lifting the Valve needle experiences a hydraulic force in the opening direction. With appropriate design of the gap choke can be achieved so even when the valve needle is open, a force balance of the valve needle. Advantageously, the pressure difference before and after the gap throttle is about 10% of the upstream pressure, but at least 50 bar and at most 150 bar.

In einer weiteren vorteilhaften Ausgestaltung ist der mechanische Koppler im Niederdruckraum anordnet, wobei der Niederdruckraum mit einer Ablaufbohrung verbunden ist, die für einen stets niedrigen Druck im Niederdruckraum sorgt. Die Anordnung des mechanischen Kopplers und damit auch des hydraulischen Kopplers im Niederdruckraum erleichtert, im Gegensatz zum Einbau in einem Hochdruckbereich des Injektors, die Konstruktion und erlaubt dadurch eine einfachere und kostengünstigere Fertigung des Kraftstoffeinspritzventils.In a further advantageous embodiment, the mechanical coupler is arranged in the low-pressure space, wherein the low-pressure chamber is connected to a drain hole, which ensures a low pressure in the low pressure chamber always low. The arrangement of the mechanical coupler and thus also the hydraulic coupler in the low-pressure space facilitates, in contrast to installation in a high-pressure region of the injector, the construction and thereby allows a simpler and more cost-effective production of the fuel injection valve.

Der elektrische Aktor kann als Piezoaktor, als Magnetaktor oder als magnetostriktiver Aktor ausgebildet sein. Auch weitere Aktortypen können in Frage kommen, sofern diese für die Anwendung in einem Kraftstoffeinspritzventil geeignet sind.The electrical actuator can be designed as a piezoelectric actuator, as a magnetic actuator or as a magnetostrictive actuator. Other types of actuators may also be considered, provided that they are suitable for use in a fuel injection valve.

Zeichnungdrawing

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

Figur 1
eine Gesamtansicht des Kraftstoffeinspritzventils im Längsschnitt,
Figur 2
eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1,
Figur 3
eine vergrößerte Darstellung des Ventilkörpers des Kraftstoffeinspritzventils und
Figur 4
eine vergrößerte Darstellung des hydraulischen und mechanischen Kopplers.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
an overall view of the fuel injection valve in longitudinal section,
FIG. 2
a magnification of the designated II section of FIG. 1 .
FIG. 3
an enlarged view of the valve body of the fuel injection valve and
FIG. 4
an enlarged view of the hydraulic and mechanical coupler.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Fig. 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargstellt. Das Kraftstoffeinspritzventil weist einen Haltekörper 1, eine Zwischenscheibe 2 und einen Ventilkörper 3 auf, die in dieser Reihenfolge aneinander anliegen. Der Ventilkörper 3 wird dabei durch eine Spannmutter 4 unter Zwischenlage der Zwischenscheibe 2 gegen den Haltekörper 1 verspannt. Im Ventilkörper 3, der in Fig. 3 nochmals vergrößert dargestellt ist, ist ein Druckraum 5 ausgebildet, der als Sackbohrung ausgeführt ist und der von der dem Haltekörper 1 zugewandten Seite des Ventilkörpers 3 ausgeht. Der Druckraum wird an seinem Grund von einem im Wesentlichen konischen Ventilsitz 7 begrenzt. An den konischen Ventilsitz 7 schließt sich ein Sackloch 11 an, von dem eine oder mehrere Einspritzöffnungen 10 ausgehen, über die der Kraftstoff letztendlich in den Brennraum der Brennkraftmaschine eingespritzt wird.In Fig. 1 is a fuel injection valve according to the invention in longitudinal section dargstellt. The fuel injection valve has a holding body 1, an intermediate disc 2 and a valve body 3 which abut each other in this order. The valve body 3 is clamped by a clamping nut 4 with the interposition of the washer 2 against the holding body 1. In the valve body 3, the in Fig. 3 shown enlarged again, a pressure chamber 5 is formed, which is designed as a blind hole and which emanates from the holding body 1 facing side of the valve body 3. The pressure chamber is bounded at its base by a substantially conical valve seat 7. The conical valve seat 7 is followed by a blind hole 11, from which one or more injection openings 10 emanate, via which the fuel is ultimately injected into the combustion chamber of the internal combustion engine.

Der Druckraum 5 wird über eine in der Zwischenscheibe 2 und im Haltekörper 1 verlaufende Hochdruckbohrung 6 mit Kraftstoff unter hohem Druck befüllt. Der Kraftstoff wird dabei beispielsweise in einem sogenannten Rail zur Verfügung gestellt. Das Rail ist ein Hochdruckspeicher, der über eine Hochdruckpumpe mit Kraftstoff unter hohem Druck befüllt wird, so dass in der Hochdruckbohrung 6 bei Betrieb der Brennkraftmaschine stets Kraftstoff unter Einspritzdruck zur Verfügung steht.The pressure chamber 5 is filled via a running in the washer 2 and the holding body 1 high-pressure bore 6 with fuel at high pressure. The fuel is provided for example in a so-called rail available. The rail is a high-pressure accumulator, which is filled via a high-pressure pump with fuel under high pressure, so that in the high-pressure bore 6 during operation of the internal combustion engine is always available fuel under injection pressure.

Im Druckraum 5 ist eine kobenförmige Ventilnadel 8 angeordnet, die längsverschiebbar geführt ist und die an ihrem dem Ventilsitz 7 zugewandten Ende eine Ventildichtfläche 9 aufweist, die im Wesentlichen aus zwei Konusflächen besteht. Dieser, in Fig. 1 mit II gekennzeichnete Bereich, ist in Fig. 2 nochmals vergrößert dargestellt. Zwischen den beiden Konusflächen ist eine Dichtkante 12 ausgebildet, mit der die Ventilnadel 8 am Ventilsitz 7 aufliegt und dadurch den Druckraum 5 vom Sackloch 11 und damit von den Einspritzöffnungen 10 trennt. Die Ventilnadel 8 weist einen Durchmesser D auf und erstreckt sich mit diesem Durchmesser ausgehend vom Ventilsitz 7 bis zu einem Führungsabschnitt 108. Hierzu ist der Ventilkörper 5 in Figur 3 nochmals vergrößert dargestellt. Im Führungsbereich 108 wird die Ventilnadel 8 im Druckraum 5 geführt, wobei der Kraftstofffluss durch mehrere Anschliffe an der Ventilnadel 8 sichergestellt wird, die im Führungsabschnitt 108 ausgebildet sind.In the pressure chamber 5, a kobenförmige valve needle 8 is arranged, which is guided longitudinally displaceable and at its the valve seat 7 facing the end of a valve sealing surface 9, which consists essentially of two conical surfaces. This, in Fig. 1 The area marked II is in Fig. 2 shown enlarged again. Between the two conical surfaces, a sealing edge 12 is formed, with which the valve needle 8 rests on the valve seat 7 and thereby separates the pressure chamber 5 from the blind hole 11 and thus from the injection openings 10. The valve needle 8 has a diameter D and extends with this diameter, starting from the valve seat 7 to a guide portion 108. For this purpose, the valve body 5 in FIG. 3 shown enlarged again. In the guide region 108, the valve needle 8 is guided in the pressure chamber 5, wherein the fuel flow is ensured by a plurality of poles on the valve needle 8, which are formed in the guide portion 108.

Der Druckraum 5 erweitert sich, ausgehend vom Ventilsitz 7, zum haltekörperseitigen Ende des Ventilkörpers 3 zu einem Federraum 105, in den auch die Hochdruckbohrung 6 mündet. Im Federraum 105 ist eine Schließfeder 16 angeordnet, die die Ventilnadel 8 umgibt und die sich mit einem Ende an einem Absatz 208 der Ventilnadel 8 abstützt. Mit ihrem anderen Ende liegt die Schließfeder 16 an einer Hülse 15 an, die durch die Kraft der Schließfeder 16 gegen die Zwischenscheibe 2 gedrückt wird. Die Ventilnadel 8 ist in diesem Bereich als Stiftfortsatz 13 ausgeführt, der einen Durchmesser d aufweist, welcher deutlich kleiner ist als der Durchmesser D der Ventilnadel 8 am ventilsitzseitigen Ende. Die Hülse 15 ist auf dem Stiftfortsatz 13 geführt, wobei zwischen der Hülse 15 und dem Stiftfortsatz 13 nur ein sehr kleiner Spalt verbleibt, wie er zur Bewegung des Stiftfortsatzes 13 in der Hülse 15 notwendig ist. Der Stiftfortsatz 13 ragt durch eine Führungsbohrung 17 in der Zwischenscheibe 2 hindurch bis in einen Niederdruckraum 18, der im Haltekörper 1 ausgebildet ist. Die Abdichtung des Druckraums 5 gegenüber dem Niederdruckraum 18 geschieht einerseits durch die Dichtung der Führungshülse 15 an der Zwischenscheibe 2 und andererseits durch die Gleitdichtung zwischen dem Stiftfortsatz 13 und der Hülse 15.The pressure chamber 5 expands, starting from the valve seat 7, to the holder body-side end of the valve body 3 to a spring chamber 105 into which the high-pressure bore 6 opens. In the spring chamber 105, a closing spring 16 is arranged, which surrounds the valve needle 8 and which is supported at one end to a shoulder 208 of the valve needle 8. With its other end, the closing spring 16 bears against a sleeve 15, which is pressed by the force of the closing spring 16 against the washer 2. The valve needle 8 is designed in this area as a pin extension 13, which has a diameter d, which is significantly smaller than the diameter D of the valve needle 8 at the valve seat side end. The sleeve 15 is guided on the pin extension 13, wherein between the sleeve 15 and the pin extension 13 only a very small gap remains, as he is necessary for movement of the pin extension 13 in the sleeve 15. The pin extension 13 protrudes through a guide bore 17 in the intermediate disc 2 through into a low-pressure space 18, which is formed in the holding body 1. The sealing of the pressure chamber 5 with respect to the low pressure chamber 18 is done on the one hand by the seal of the guide sleeve 15 on the washer 2 and on the other hand by the sliding seal between the pin extension 13 and the sleeve 15th

Im Bereich des Führungsabschnitts 108 der Ventilnadel 8 befindet sich darüber hinaus eine Spaltdrossel 14, die durch einen umlaufenden Bund gebildet ist und die nur einen sehr geringen Spalt zwischen der Ventilnadel 8 und der Wand des Druckraums 5 belässt. Der Kraftstoff, der durch die Hochdruckbohrung 6 über den Federraum 105 in den ventilsitzseitigen Bereich des Druckraums 5 strömt, wird an dieser Stelle in der Spaltdrossel 14 gedrosselt, was bei fließendem Kraftstoff eine Druckdifferenz zwischen dem Federraum 105 und dem ventilsitzseitigen Bereich des Druckraums 5 bewirkt.In the area of the guide section 108 of the valve needle 8 there is, moreover, a gap throttle 14, which is formed by a circumferential collar and which leaves only a very small gap between the valve needle 8 and the wall of the pressure chamber 5. The fuel that flows through the high-pressure bore 6 via the spring chamber 105 in the valve seat side region of the pressure chamber 5 is throttled at this point in the gap throttle 14, which causes a pressure difference between the spring chamber 105 and the valve seat side region of the pressure chamber 5 with flowing fuel.

Im Niederdruckraum 18 ist ein mechanischer Koppler 20 angeordnet, der einen um einen Drehpunkt 24 drehend gelagert Kipphebel 22 umfasst. Der Kipphebel 22 weist dabei ein erstes Ende 122 und ein zweites Ende 222 auf, das mit dem Stiftfortsatz 13 verbunden ist. Wird das erste Ende 122 des Kipphebels 22 in Richtung der Zwischenscheibe 2 gedrückt, so hebt sich durch die Drehung um den Drehpunkt 24 das zweite Ende 222 des Kipphebels 22 und hebt die Ventilnadel 13 vom Ventilsitz 7 ab.In the low-pressure space 18, a mechanical coupler 20 is arranged, which comprises a rocker arm 22 rotatably mounted about a pivot point 24. The rocker arm 22 has a first end 122 and a second end 222 which is connected to the pin extension 13. If the first end 122 of the rocker arm 22 is pressed in the direction of the intermediate disk 2, the rotation is reversed the pivot point 24, the second end 222 of the rocker arm 22 and lifts the valve needle 13 from the valve seat 7 from.

Im Haltekörper 1 ist ein elektrischer Aktor 40 ausgebildet, der beispielsweise als Piezoaktor ausgebildet ist. Der Piezoaktor 40 weist an seinem dem Ventilkörper 3 zugewandten Ende einen Aktorkopf 42 auf, der mit einem hydraulischen Koppler 30 verbunden ist, der ebenfalls im Niederdruckraum 18 angeordnet ist. Der hydraulische Koppler 30 besteht dabei aus einem Primärkolben 32, der mit dem Aktorkopf 42 verbunden ist, und einem Sekundärkolben 33, der sich am ersten Ende 122 des Kipphebels 22 abstützt. Zwischen dem Primärkolben 22 und dem Sekundärkolben 33, die beide in einer Kopplerhülse 34 geführt sind, ist ein hydraulischer Arbeitsraum 35 ausgebildet. Der hydraulische Arbeitsraum 35 erlaubt einen Längenausgleich, wie er durch thermische Längenänderungen des Aktors 40 notwendig ist. Da diese nur vergleichsweise langsam geschehen, kann die unterschiedliche Befüllung des hydraulischen Arbeitsraums 35 durch zu- oder abströmen von Kraftstoff aus bzw. in den Niederdruckraum 18 problemlos ausgeglichen werden.In the holding body 1, an electrical actuator 40 is formed, which is formed for example as a piezoelectric actuator. The piezoelectric actuator 40 has at its end facing the valve body 3 an actuator head 42, which is connected to a hydraulic coupler 30, which is also arranged in the low-pressure chamber 18. The hydraulic coupler 30 consists of a primary piston 32 which is connected to the actuator head 42, and a secondary piston 33, which is supported on the first end 122 of the rocker arm 22. Between the primary piston 22 and the secondary piston 33, which are both guided in a coupler sleeve 34, a hydraulic working space 35 is formed. The hydraulic working space 35 allows a length compensation, as required by thermal changes in length of the actuator 40. Since these happen only comparatively slowly, the different filling of the hydraulic working space 35 can be easily compensated by the supply or discharge of fuel from or into the low-pressure space 18.

Der Hub des Piezoaktors ist vergleichsweise gering und übersteigt in der Regel nicht 0,1 bis 0,2 % seiner Gesamtlänge. Wenn dies für den Hub der Ventilnadel 8 nicht ausreicht, kann sowohl der hydraulische Koppler 30, als auch der mechanische Koppler 20 zur Verstärkung des maximalen Hubs eingesetzt werden. Hierzu weist der Primärkolben 32 einen größeren Durchmesser auf als der Sekundärkolben 33. Bei seiner Bewegung in Richtung auf die Zwischenscheibe 2 verdrängt der Primärkolben 32 damit mehr Kraftstoff als der Sekundärkolben 33 bei einem gleichen Hub, so dass der Sekundärkolben 33 eine größere Wegstrecke durchfährt als der Primärkolben 32. Eine weitere Verstärkung kann durch den mechanischen Koppler 20 erreicht werden, indem der wirksame Hebel vom Drehpunkt 24 zum ersten Ende 122 kleiner ist als der wirksame Hebel vom Drehpunkt 24 zum zweiten Ende 222. Die Wegverstärkung der Koppler kann jeweils bis zu 1,5 betragen, d. h. dass eine Längenänderung des Piezoaktors von 100 µm zu einer Bewegung des mechanischen Kopplers von 150 µm führt, was im mechanischen Koppler nochmals verstärkt werden kann.The stroke of the piezoelectric actuator is comparatively low and usually does not exceed 0.1 to 0.2% of its total length. If this is not sufficient for the stroke of the valve needle 8, both the hydraulic coupler 30, and the mechanical coupler 20 can be used to increase the maximum stroke. For this purpose, the primary piston 32 has a larger diameter than the secondary piston 33. In its movement in the direction of the washer 2, the primary piston 32 thus displaces more fuel than the secondary piston 33 at the same stroke, so that the secondary piston 33 passes a greater distance than the Primary piston 32. Further reinforcement may be achieved by the mechanical coupler 20 by having the effective lever from pivot 24 to first end 122 be smaller than the effective lever from pivot 24 to second end 222. The path gain of the couplers may be up to 1, respectively. 5, d. H. that a change in length of the piezoelectric actuator of 100 microns leads to a movement of the mechanical coupler of 150 microns, which can be further enhanced in the mechanical coupler.

Die Arbeitsweise des Kraftstoffeinspritzventils ist wie folgt:

  • Zu Beginn der Einspritzung befindet sich die Ventilnadel 8 in Anlage am Ventilsitz 7, so dass im gesamten Druckraum 5 der gleiche hohe Druck herrscht, wie er über die Hochdruckbohrung 6 zugeführt wird. Hierbei wirken große hydraulische Kräfte auf die Ventilnadel 8, die sich in radialer Richtung gesehen jedoch gegenseitig aufheben. Um auch in Längsrichtung zumindest näherungsweise einen Kraftausgleich zu erreichen, muss der Durchmesser d des Stiftfortsatzes 13 zumindest näherungsweise dem Durchmesser der kreisförmigen Dichtkante 12 an der Ventildichtfläche 9 entsprechen. Es kann jedoch auch vorgesehen sein, durch entsprechende Wahl der Durchmesser eine geringe hydraulische Schließkraft in Richtung des Ventilsitzes 7 zu erzeugen, da die Ventilnadel 8 sonst nur durch die Schließfeder 16 in Anlage am Ventilsitz 7 gehalten wird. Im Niederdruckraum 18, der über einen Ablaufkanal 25 stets mit einem Niederdruckrücklauf verbunden ist, herrscht niedriger Kraftstoffdruck, der erheblich niedriger ist als der Kraftstoffdruck im Druckraum 5 und nicht mehr als einige bar beträgt.
The operation of the fuel injection valve is as follows:
  • At the beginning of the injection, the valve needle 8 is in contact with the valve seat 7, so that in the entire pressure chamber 5, the same high pressure prevails, as it is supplied via the high-pressure bore 6. In this case, large hydraulic forces act on the valve needle 8, but seen in the radial direction cancel each other out. In order to achieve at least approximately a force compensation in the longitudinal direction, the diameter d of the pin extension 13 must correspond at least approximately to the diameter of the circular sealing edge 12 on the valve sealing surface 9. However, it may also be provided to produce a low hydraulic closing force in the direction of the valve seat 7 by appropriate choice of the diameter, since the valve needle 8 is otherwise held only by the closing spring 16 in contact with the valve seat 7. In the low pressure chamber 18, which is always connected via a discharge channel 25 with a low pressure return, there is a lower fuel pressure, which is considerably lower than the fuel pressure in the pressure chamber 5 and not more than a few bar.

Soll eine Einspritzung erfolgen, so wird der Piezoaktor 40 bestromt, wodurch er sich in Längsrichtung ausdehnt und über den Aktorkopf 42 den Primärkolben 32 in Richtung der Zwischenscheibe 2 bewegt. Dabei wird der Kraftstoff im hydraulischen Arbeitsraum 35 komprimiert, und der steigenden Druck im hydraulischen Arbeitsraum 35 drückt den Sekundärkolben 33 ebenfalls in Richtung der Zwischenscheibe 2. Durch die Verbindung des Sekundärkolbens 33 mit dem ersten Ende 122 des Kipphebels 22 dreht sich damit der Kipphebel 22 um seinen Drehpunkt 24 und hebt den Stiftfortsatz 13 der Ventilnadel 8 an. Dabei wird die Ventilnadel 8 vom Ventilsitz 7 weggezogen. Durch den Kraftausgleich der Ventilnadel 8 in Längsrichtung ist für die Längsbewegung nur eine geringe Kraft notwendig, die ohne Weiteres über den Piezoaktor 40 aufgebracht werden kann. Sobald die Ventilnadel 8 vom Ventilsitz 7 abgehoben hat, strömt der Kraftstoff aus dem Druckraum 5 in das Sackloch 11 und von dort durch die Einspritzöffnungen 10 in den Brennraum der Brennkraftmaschine.If an injection takes place, then the piezoelectric actuator 40 is energized, whereby it expands in the longitudinal direction and moves the primary piston 32 in the direction of the washer 2 via the actuator head 42. In this case, the fuel in the hydraulic working chamber 35 is compressed, and the increasing pressure in the hydraulic working chamber 35 pushes the secondary piston 33 also in the direction of the washer 2. By connecting the secondary piston 33 with the first end 122 of the rocker arm 22 so that the rocker arm 22 rotates its pivot point 24 and raises the pin extension 13 of the valve needle 8 at. The valve needle 8 is pulled away from the valve seat 7. Due to the force compensation of the valve needle 8 in the longitudinal direction only a small force is necessary for the longitudinal movement, which can be applied via the piezoelectric actuator 40 without further notice. As soon as the valve needle 8 has lifted off the valve seat 7, the fuel flows from the pressure chamber 5 into the blind hole 11 and from there through the injection openings 10 into the combustion chamber of the internal combustion engine.

Bei geöffneter Ventilnadel 8 ergeben sich folgende hydraulische Verhältnisse: Der Kraftstoff strömt aus der Hochdruckbohrung 6 in den Druckraum 5, am Führungsabschnitt 108 vorbei und von dort zwischen den Raum, der zwischen der Ventilnadel 8 und der Wand des Druckraums 5 verbleibt, zum Sackloch 11. Hierbei muss der Kraftstoff jedoch die Spaltdrossel 14 passieren, was ein Druckgefälle zwischen dem Bereich vor und hinter der Spaltdrossel 14 bewirkt, so dass der Druck im Federraum 105 höher ist als im stromabwärtigen Teil des Druckraums 5. Die Druckverminderung beträgt dabei in etwa 50 bis 150 bar, je nach den hydraulischen Verhältnissen. Durch den geringeren Druck im stromabwärtigen Teil des Druckraums 5 ergibt sich stromabwärts der Spaltdrossel 14 eine geringere hydraulische Kraft auf die Ventildichtfläche 9, was die hydraulische Öffnungskraft auf die Ventilnadel 8 vermindert. Durch geeignete Dimensionierung der Spaltdrossel 14 lässt sich so erreichen, dass durch den höheren hydraulischen Druck im Federraum 105 und den verminderten Kraftstoffdruck auf die Ventildichtfläche 9 wiederum ein Kraftausgleich entsteht. Auch im geöffneten Zustand der Ventilnadel 8 kann so ein Kraftausgleich in Längsrichtung erreicht werden, was nur eine geringe Schließkraft auf die Ventilnadel 8 erfordert, die ohne Weiteres über den mechanischen Koppler erreichbar ist.When the valve needle 8 is open, the following hydraulic conditions result: The fuel flows from the high-pressure bore 6 into the pressure chamber 5, past the guide section 108 and from there to the blind hole 11 between the space remaining between the valve needle 8 and the wall of the pressure chamber 5. in this connection However, the fuel must pass through the gap throttle 14, causing a pressure gradient between the area before and after the gap throttle 14, so that the pressure in the spring chamber 105 is higher than in the downstream part of the pressure chamber 5. The pressure reduction is approximately 50 to 150 bar , depending on the hydraulic conditions. Due to the lower pressure in the downstream part of the pressure chamber 5 downstream of the gap throttle 14 results in a lower hydraulic force on the valve sealing surface 9, which reduces the hydraulic opening force on the valve needle 8. By suitable dimensioning of the gap throttle 14 can be achieved so that in turn results in a force balance due to the higher hydraulic pressure in the spring chamber 105 and the reduced fuel pressure on the valve sealing surface 9. Even in the open state of the valve needle 8, a force compensation in the longitudinal direction can be achieved, which requires only a small closing force on the valve needle 8, which can be easily reached via the mechanical coupler.

Um das Schließen der Ventilnadel 8 zu beschleunigen kann es jedoch auch vorgesehen sein, durch geeignete Auslegung Parameter in geöffneten Zustand eine leichte hydraulische Schließkraft auf die Ventilnadel zu erzeugen. Eine Kraft durch die Vermittlung des mechanischen Kopplers 20 ist dann zum Schließen der Ventilnadel 8 nicht mehr erforderlich, ohne dass große hydraulische Kräfte am mechanischen Koppler 20 ziehen, wenn dieser die Ventilnadel 8 in ihrer Öffnungsstellung hält.In order to accelerate the closing of the valve needle 8, however, it may also be provided to generate a slight hydraulic closing force on the valve needle by means of suitable design parameters in the open state. A force through the mediation of the mechanical coupler 20 is then no longer required to close the valve needle 8, without pulling large hydraulic forces on the mechanical coupler 20, when it holds the valve needle 8 in its open position.

Es kann weiter vorgesehen sein, dass die Hülse 15 entfällt und sich die Schließfeder 16 einerseits weiterhin am Absatz 208 abstützt, andererseits aber direkt an der Zwischenscheibe 2. Die Abdichtung des Druckraums 5 gegenüber dem Niederdruckraum 18 erfolgt dann ausschließlich durch die Spaltdrossel, die zwischen dem Stiftfortsatz 13 und der Führungsbohrung 17 in der Zwischenscheibe 2 verbleibt. Insbesondere bei einer Zwischenscheibe 2, die eine größere Dicke aufweist, wird so eine ausreichende Abdichtung erreicht.It can further be provided that the sleeve 15 is omitted and the closing spring 16 on the one hand continues to be supported on the shoulder 208, but on the other hand directly to the washer 2. The sealing of the pressure chamber 5 relative to the low-pressure chamber 18 then takes place exclusively through the gap choke, between the Pin extension 13 and the guide hole 17 in the washer 2 remains. In particular, with a washer 2, which has a greater thickness, so a sufficient seal is achieved.

Die Darstellung des Kraftstoffeinspritzventils, insbesondere die Darstellung des hydraulischen Kopplers 30, ist nur schematisch zu verstehen. Die Kopplerhülse 34 ist bei der tatsächlichen Ausführungsform fest im Haltekörper 1 fixiert, so dass sie sich beim Betrieb des Kraftstoffeinspritzventils nicht bewegt.The representation of the fuel injection valve, in particular the representation of the hydraulic coupler 30, is only to be understood schematically. The coupler sleeve 34 is firmly fixed in the actual embodiment in the holding body 1 so that it does not move during operation of the fuel injection valve.

Das dargestellte erfindungsgemäße Kraftstoffeinspritzventil weist insbesondere den Vorteil auf, dass sowohl der Piezoaktor 40, als auch der hydraulische Koppler 30 und der mechanische Koppler 20, im Niederdruck untergebracht sind. Damit herrscht mit Ausnahme der Hochdruckbohrung 6 im gesamten Haltekörper nur Niederdruck, was die Konstruktion und Bauweise der Koppler erheblich vereinfacht und auch die Konstruktion des Piezoaktors und seine Kapselung zur Abdichtung gegenüber dem Kraftstoff, der den gesamten Niederdruckraum 18 ausfüllt, erheblich vereinfacht.The illustrated fuel injection valve according to the invention has the particular advantage that both the piezoelectric actuator 40, and the hydraulic coupler 30 and the mechanical coupler 20 are housed in low pressure. Thus, with the exception of the high-pressure bore 6 in the entire holding body only low pressure, which significantly simplifies the design and construction of the coupler and the construction of the piezoelectric actuator and its encapsulation to seal against the fuel, which fills the entire low-pressure chamber 18, considerably simplified.

Außer der unvermeidlichen Leckagemenge, die zwischen der Hülse 15 und dem Stiftfortsatz 13 einerseits und zwischen der Führungsbohrung 17 und dem Stiftfortsatz 13 andererseits in den Niederdruckraum 18 fließt, arbeitet das erfindungsgemäße Kraftstoffeinspritzventil ohne Absteuermenge, wie sie bei servohydraulischen Steuerventilen zwangsläufig anfällt. Dies erhöht die Effizienz des Einspritzsystems, da die Hochdruckpumpe, die den Kraftstoff letztendlich komprimiert und die durch den Motor selbst angetrieben wird, nur unwesentlich mehr Kraftstoff auf den hohen Einspritzdruck komprimieren muss, wie tatsächlich eingespritzt wird.Except the unavoidable amount of leakage flowing between the sleeve 15 and the pin extension 13 on the one hand and between the guide bore 17 and the pin extension 13 on the other hand in the low-pressure chamber 18, the fuel injection valve according to the invention operates without Absteuermenge, as inevitably obtained in servohydraulic control valves. This increases the efficiency of the injection system because the high pressure pump, which ultimately compresses the fuel and which is driven by the engine itself, need only insignificantly compress more fuel to the high injection pressure, as actually injected.

Claims (12)

Kraftstoffeinspritzventil für Brennkraftmaschinen mit einer Ventilnadel (8), die in einem Druckraum (5) längsverschiebbar angeordnet ist, und mit einer an der Ventilnadel (8) ausgebildeten Ventildichtfläche (9), die mit einem Ventilsitz (7) zum Öffnen und Schließen wenigstens einer Einspritzöffnung (10) zusammenwirkt, wobei der Druckraum (5) mit Kraftstoff unter Einspritzdruck befüllbar ist, wobei sich die hydraulischen Kräfte auf die Ventilnadel (8), die durch den Druck im Druckraum (5) entstehen, bei Anlage der Ventilnadel (8) auf dem Ventilsitz (7) zumindest im Wesentlichen aufheben, dadurch gekennzeichnet, dass der Ventildichtfläche (9) entgegengesetzt an der Ventilnadel (8) ein Stiftfortsatz (13) ausgebildet ist, der in einen Niederdruckraum (18) ragt und der mit einem mechanischen Koppler (20) verbunden ist, über den eine Öffnungskraft auf die Ventilnadel (8) ausgeübt werden kann.Fuel injection valve for internal combustion engines with a valve needle (8) which is arranged longitudinally displaceable in a pressure chamber (5) and with a valve needle (8) formed on the valve sealing surface (9) with a valve seat (7) for opening and closing at least one injection port (10) cooperates, wherein the pressure chamber (5) can be filled with fuel under injection pressure, wherein the hydraulic forces on the valve needle (8) caused by the pressure in the pressure chamber (5), when the valve needle (8) on the Valve seat (7) at least substantially cancel, characterized in that the valve sealing surface (9) opposite to the valve needle (8) a pin extension (13) is formed, which projects into a low-pressure space (18) and with a mechanical coupler (20) is connected, via which an opening force on the valve needle (8) can be exercised. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass ein elektrischer Aktor (40) zumindest mittelbar mit dem mechanischen Koppler (20) verbunden ist, so dass die Kraft des Aktors (40) über den mechanischen Koppler (20) auf die Ventilnadel (8) übertragbar ist.Fuel injection valve according to claim 1, characterized in that an electrical actuator (40) is at least indirectly connected to the mechanical coupler (20), so that the force of the actuator (40) via the mechanical coupler (20) on the valve needle (8) transferable is. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass der mechanische Koppler (20) einen Kipphebel (22) umfasst, der zwei Enden (122; 222) aufweist, wobei der Aktor (40) zumindest mittelbar auf das erste Ende (122) einwirkt und das zweite Ende (222) mit dem Stiftfortsatz (13) verbunden ist.Fuel injection valve according to claim 2, characterized in that the mechanical coupler (20) comprises a rocker arm (22) having two ends (122; 222), the actuator (40) acting at least indirectly on the first end (122) and the second end (222) is connected to the pin extension (13). Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, dass der Kipphebel (22) einen Drehpunkt (24) aufweist, um den sich der Kipphebel (22) bei der Öffnungsbewegung der Ventilnadel (8) drehend bewegt, wobei der wirksame Hebel vom Drehpunkt (24) zum ersten Ende (122) kleiner ist als der wirksame Hebel zum zweiten Ende (222), so dass die Bewegung des Aktors (40) durch den Kipphebel (22) verstärkt wird.Fuel injection valve according to Claim 3, characterized in that the rocker arm (22) has a pivot point (24) about which the rocker arm (22) rotates during the opening movement of the valve needle (8) the effective lever from the fulcrum (24) to the first end (122) is smaller than the effective lever to the second end (222) so that movement of the actuator (40) is enhanced by the rocker arm (22). Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass zwischen dem Aktor (40) und dem mechanischen Koppler (20) ein hydraulischer Koppler (30) angeordnet ist, über den die Kraft des Aktors (40) auf den mechanischen Koppler (20) übertragen wird.Fuel injection valve according to claim 2, characterized in that between the actuator (40) and the mechanical coupler (20) a hydraulic coupler (30) is arranged, via which the force of the actuator (40) is transmitted to the mechanical coupler (20). Kraftstoffeinspritzventil nach Anspruch 5, dadurch gekennzeichnet, dass der hydraulische Koppler (30) einen mit dem Aktor wirkverbundenen Primärkolben (32) und einen durch einen hydraulischen Arbeitsraum (34) davon getrennten Sekundärkolben (33) aufweistFuel injection valve according to claim 5, characterized in that the hydraulic coupler (30) has a primary piston (32) operatively connected to the actuator and a secondary piston (33) separated therefrom by a hydraulic working chamber (34) Kraftstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, dass der Primärkolben (32) einen größeren Durchmesser aufweist als der Sekundärkolben (33), so dass die Bewegung des Aktors (40) durch den hydraulischen Koppler (30) verstärkt wird.Fuel injection valve according to claim 6, characterized in that the primary piston (32) has a larger diameter than the secondary piston (33), so that the movement of the actuator (40) by the hydraulic coupler (30) is amplified. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass zwischen der Ventilnadel (8) und der Wand des Druckraums (5) eine Spaltdrossel (14) ausgebildet ist, so dass bei geöffneter Ventilnadel (8) ein Druckgefälle zwischen dem Bereich des Druckraums (5) stromaufwärts der Spaltdrossel (14) und dem Bereich stromabwärts der Spaltdrossel (14) herrscht.Fuel injection valve according to claim 1, characterized in that between the valve needle (8) and the wall of the pressure chamber (5) a gap throttle (14) is formed, so that when the valve needle (8) open a pressure gradient between the region of the pressure chamber (5) upstream the gap throttle (14) and the region downstream of the gap throttle (14) prevails. Kraftstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, dass die Druckdifferenz etwa 10 % des stromaufwärtigen Drucks beträgt, mindestens aber 50 bar und höchstens 150 bar.Fuel injection valve according to claim 8, characterized in that the pressure difference is about 10% of the upstream pressure, but at least 50 bar and at most 150 bar. Kraftstoffeinspritzventil nach Anspruch 8, dadurch gekennzeichnet, dass die Ventilnadel (8) im geöffneten Zustand durch den Druck im Druckraum (5) eine in Richtung des Ventilsitzes (7) gerichtete hydraulische Schließkraft erfährt.Fuel injection valve according to claim 8, characterized in that the valve needle (8) in the open state by the pressure in the pressure chamber (5) in the direction of the valve seat (7) directed hydraulic closing force undergoes. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass der mechanische Koppler (20) im Niederdruckraum (18) angeordnet ist und der Niederdruckraum (18) mit einer Ablaufbohrung (25) verbunden ist, so dass im Niederdruckraum (18) stets ein niedriger Druck herrscht.Fuel injection valve according to claim 1, characterized in that the mechanical coupler (20) is arranged in the low-pressure space (18) and the low-pressure space (18) is connected to a drainage bore (25), so that there is always a low pressure in the low-pressure space (18). Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass der Aktor ein Piezoaktor (40), ein Magnetaktor oder ein magnetostriktiver Aktor ist.Fuel injection valve according to claim 2, characterized in that the actuator is a piezoelectric actuator (40), a magnetic actuator or a magnetostrictive actuator.
EP20120185618 2011-10-12 2012-09-24 Fuel injection valve for internal combustion engines with directly actuated valve needle Not-in-force EP2581597B1 (en)

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DE201110084342 DE102011084342A1 (en) 2011-10-12 2011-10-12 Fuel injection valve for internal combustion engines with directly controlled valve needle

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Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10220498A1 (en) 2001-05-08 2002-11-28 Cummins Engine Co Inc Proportional needle control injector
DE102006026399A1 (en) 2006-06-07 2007-12-13 Robert Bosch Gmbh Fuel injector with servo support e.g. for injecting fuel into combustion chamber of internal combustion engine, uses actuator and operated with fuel inlet and connected via system under pressure
DE102006031567A1 (en) * 2006-07-07 2008-01-10 Siemens Ag Injection system and method for manufacturing an injection system
DE102007032741A1 (en) * 2007-07-13 2009-01-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102008042136A1 (en) 2008-09-16 2010-03-18 Robert Bosch Gmbh Fuel injector for high-pressure accumulator injection system i.e. common rail, has servo-valve operatively generating hydraulic force in opening direction during opening process of injection-valve member
DE102008043085A1 (en) * 2008-10-22 2010-04-29 Robert Bosch Gmbh Fuel injector, particularly for injecting fuel from high pressure reservoir in combustion chamber of internal combustion engine, has actuator and injection valve element which is axially moved in injector body
WO2010142753A1 (en) * 2009-06-10 2010-12-16 Continental Automotive Gmbh Injection valve comprising a transmission unit

Patent Citations (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10220498A1 (en) 2001-05-08 2002-11-28 Cummins Engine Co Inc Proportional needle control injector
DE102006026399A1 (en) 2006-06-07 2007-12-13 Robert Bosch Gmbh Fuel injector with servo support e.g. for injecting fuel into combustion chamber of internal combustion engine, uses actuator and operated with fuel inlet and connected via system under pressure
DE102006031567A1 (en) * 2006-07-07 2008-01-10 Siemens Ag Injection system and method for manufacturing an injection system
DE102007032741A1 (en) * 2007-07-13 2009-01-15 Robert Bosch Gmbh Fuel injection valve for internal combustion engines
DE102008042136A1 (en) 2008-09-16 2010-03-18 Robert Bosch Gmbh Fuel injector for high-pressure accumulator injection system i.e. common rail, has servo-valve operatively generating hydraulic force in opening direction during opening process of injection-valve member
DE102008043085A1 (en) * 2008-10-22 2010-04-29 Robert Bosch Gmbh Fuel injector, particularly for injecting fuel from high pressure reservoir in combustion chamber of internal combustion engine, has actuator and injection valve element which is axially moved in injector body
WO2010142753A1 (en) * 2009-06-10 2010-12-16 Continental Automotive Gmbh Injection valve comprising a transmission unit

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DE102011084342A1 (en) 2013-04-18

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