EP1507972A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines

Info

Publication number
EP1507972A1
EP1507972A1 EP03752691A EP03752691A EP1507972A1 EP 1507972 A1 EP1507972 A1 EP 1507972A1 EP 03752691 A EP03752691 A EP 03752691A EP 03752691 A EP03752691 A EP 03752691A EP 1507972 A1 EP1507972 A1 EP 1507972A1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
pressure
control
connection
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
EP03752691A
Other languages
German (de)
French (fr)
Other versions
EP1507972B1 (en
Inventor
Detlev Potz
Thomas Kuegler
Andreas Koeninger
Predrag Nunic
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1507972A1 publication Critical patent/EP1507972A1/en
Application granted granted Critical
Publication of EP1507972B1 publication Critical patent/EP1507972B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/12—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship providing a continuous cyclic delivery with variable pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M59/00—Pumps specially adapted for fuel-injection and not provided for in groups F02M39/00 -F02M57/00, e.g. rotary cylinder-block type of pumps
    • F02M59/44—Details, components parts, or accessories not provided for in, or of interest apart from, the apparatus of groups F02M59/02 - F02M59/42; Pumps having transducers, e.g. to measure displacement of pump rack or piston
    • F02M59/46—Valves
    • F02M59/466—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means
    • F02M59/468—Electrically operated valves, e.g. using electromagnetic or piezoelectric operating means using piezoelectric 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators

Definitions

  • the invention is based on fuel injection valves which have two valve needles inserted into one another and otherwise correspond to the type of patent claim 1.
  • Such fuel injection valves are known, for example, from the published patent application DE 41 15 477 AI.
  • the two valve needles control the opening of at least one injection opening each and can be controlled in such a way that either only the outer valve needle opens part of the injection openings, or that both valve needles open and open all injection openings.
  • the injection cross section can be optimally adjusted depending on the load of the internal combustion engine.
  • the longitudinal movement of the valve needles in the bore takes place through the ratio of an opening force acting on the valve needles and in each case an opposing closing force.
  • the opening force results from the hydraulic pressure on corresponding pressure surfaces on the valve needles, while the closing force in the known fuel injection valves is generated either by springs or also by hydraulic forces.
  • the known fuel injection valve has the disadvantage that the opening and opening of both needles cannot be controlled at will and in time.
  • the outer valve needle opens under pressure control against the force of a closing spring, while the inner valve needle - in addition to the closing force of a closing spring - experiences a force due to the hydraulic pressure in a control room.
  • a solenoid valve can only control whether the inner valve needle opens or not during an injection cycle.
  • the opening behavior of the outer valve needle cannot be influenced by the solenoid valve. This places a limit on the control of the exact injection timing and the exact injection quantity, which of course also makes further optimization of the combustion difficult.
  • the fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the opening and opening times of both the outer and the inner valve needle can be controlled by a single control valve.
  • the control valve arranged in the housing of the fuel injection valve has a valve chamber in which a valve member is arranged.
  • the valve member is movable between two end positions, the valve member in the first end position causing both the control chamber and the control pressure chamber to be filled with fuel under high pressure, so that both the outer valve needle and the inner valve needle remain in their closed position. If the valve member moves quickly to its second end position, only the control chamber is relieved of pressure in the leakage chamber, while the control pressure chamber practically maintains its pressure.
  • valve needle As a result, only the outer valve needle opens, while the inner valve needle remains in its closed position. Should both valve needles, i.e. both the inner and the outer If the valve needle is opened, the valve member moves a little more slowly from its first to the second end position, as a result of which the pressure in the control pressure chamber also drops so far that, in addition to the outer valve needle, the inner valve needle also opens.
  • the switching time of the control valve can therefore be used to set whether the entire injection cross section or only part of the injection cross section is opened.
  • the coaxial varioduse can be controlled by means of only a single control valve.
  • the valve member is moved by an actuator, which is preferably operated electrically. It is particularly advantageous to design the actuator as a piezo actuator, since it has the advantage of being switchable at almost any speed.
  • the valve member moved by the actuator can thus be moved from the first end position to the second end position at different speeds, the injection cross section being able to be set by the switching speed.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention
  • FIG. 2 shows an enlargement of the section from FIG. 1 labeled II
  • FIG. 3 shows an enlargement of FIG. 1 in the section designated III
  • FIG. 4 shows the time course of pressure, needle stroke and valve limb stroke when opening only the outer valve needle
  • Figure 5 shows the time course of valve member stroke, pressure and needle stroke when opening both valve needles.
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention.
  • the fuel injection valve has a housing 1 which comprises a holding body 14, a control body 12, an intermediate disk 9, an intermediate body 7 and a valve body 3, which abut one another in this order.
  • the individual components of the housing 1 are pressed against one another by a clamping nut 5 and are fixed in their position relative to one another.
  • a bore 16 is formed in the valve body 3, in which an outer valve needle 20 is arranged so that it can be moved slowly.
  • the outer valve needle 20 is guided in a section facing away from the combustion chamber in the bore 16 and tapers towards the combustion chamber to form a pressure shoulder 27.
  • the outer valve needle 20 extends to a seat surface 24 formed at the end of the bore 16 on the combustion chamber side, in which several Injection openings 30 are formed, which connect the seat surface 24 to the combustion chamber of the internal combustion engine.
  • an annular channel 28 is formed, which extends from the seat surface 24 to the height of the pressure shoulder 27.
  • the annular channel 28 widens into a pressure chamber 26 into which an inlet channel 10 extends in the valve body 3, the intermediate body 7, the intermediate disk 9, the control body 12 and the valve holding body 14 tastes.
  • Fuel can be introduced under high pressure into the pressure chamber 26 and thus also into the annular channel 26 via the inlet channel 10.
  • the outer valve needle 20 has an elongated bore 21 in which an inner valve needle 22 is arranged so that it can be moved slowly.
  • FIG. 2 enlarged the section of FIG. 1 designated II.
  • the seat surface 24 is conical and the injection openings 30 are grouped into two injection opening rows, namely an outer injection opening row 130 and an inner injection opening row 230.
  • the outer valve needle 20 has a conical outer valve sealing surface 32 on its combustion chamber end, so that a sealing edge 34 is formed with which the outer valve needle 20 comes into contact with the seat surface 24 in its closed position.
  • the outer row of injection openings 130 which consists of at least two injection openings 30, which lie in a radial plane with respect to the longitudinal axis of the bore 16, are arranged downstream of this sealing edge 34.
  • the inner valve needle 22 has at its combustion chamber end an inner valve sealing surface 36 and a conical surface 38, at the transition of which a sealing edge 37 is formed, with which the inner valve needle 22 abuts the seat surface 24 in its closed position.
  • the inner row of injection openings 230 which likewise consists of at least two injection orifices, which are arranged in a common radial plane to the longitudinal axis of the bore 16, flow downstream of the sealing edge 37 of the inner valve needle 22 into the seat surface 24.
  • the interaction of the two valve needles 20, 22 for controlling the injection openings 30 is as follows: If fuel is to be injected into the combustion chamber of the internal combustion engine only through the outer row of injection openings 130, which is particularly advantageous if the internal combustion engine If the machine is to be operated in a partial load range, only the outer valve needle 20 lifts off the seat surface 24 for injection. As a result, fuel which is present in the annular channel 28 under high pressure can flow between the outer valve sealing surface 32 and the seat surface 24 to the outer row of injection openings 130 and is injected from there into the combustion chamber of the internal combustion engine.
  • the inner valve needle 22 remains in its closed position, ie in contact with the seat surface 24, so that the inner row of injection openings L0 230 remains closed. If all of the injection openings 30 are to be used for injection, the inner valve needle 22 also lifts off the seat surface 24, as a result of which the inner row of injection openings 230 is also released.
  • a piston bore 45 is formed coaxially to the bore 16, which is stepped in diameter with the formation of a contact surface 41.
  • An outer pressure piston 40 is arranged in the receiving bore 35, which rests on the outer valve needle 20 and synchronously with it in longitudinal direction.
  • an annular surface 39 is arranged, between which and the contact surface 41 a closing spring 44 is arranged under pressure, which is designed as a helical compression spring and surrounds the outer pressure piston 40.
  • a control chamber 50 is limited, which is connected via an inlet throttle 70 to the inlet channel 10, which serves as a high pressure chamber in which fuel is always present under high pressure.
  • the outer pressure piston 40 has a guide bore 47 in which an inner pressure piston 42 is arranged so that it can be moved slowly.
  • the inner pressure piston 42 abuts the inner valve needle 22 and always moves synchronously with it.
  • a control pressure chamber 52 is delimited by the guide bore 47 and the end face 53 of the inner pressure piston 42, the pressure of which results in a hydraulic force on the pressure piston 42 and thus also on the inner valve needle 22 in the direction of the seat surface 24.
  • a receiving body 13 Arranged in the valve holding body 14 is a receiving body 13 in which there is an actuator 46 and a pressure piece 48 connected to it.
  • the actuator 46 which is preferably designed as a piezo actuator
  • the pressure piece 48 is moved in the longitudinal direction against or in the direction of the force of a spring 49 which is arranged between the pressure piece 48 and the receiving body 13.
  • the pressure piece 48 is connected to a valve member 60, which is arranged in a valve chamber 68 which is formed in the control body 12 and together with a first valve seat 62 and a second valve seat 64 opposite this
  • Control valve 58 forms.
  • the valve member 60 is essentially designed as a hemisphere, the hemispherical valve sealing surface 66 interacting with the first valve seat 62, while the flat side of the valve member 60 interacts with the second valve seat 64, which is designed as a flat seat.
  • the valve chamber 68 has a connection 59 to a leak oil chamber 78 formed in the valve holder body 14, the connection 59 being able to be opened and closed by the valve member 60 through its interaction with the first valve seat 62.
  • the tilraum 68 on an outlet throttle 72, which connects the valve chamber 68 with the control chamber 50.
  • the flow restrictor 72 always remains open, regardless of the position of the valve member 60.
  • connection channel 74 which forms a connection between the valve chamber 68 and the control pressure chamber 52.
  • the connecting channel 74 extends into the intermediate body 7 and merges laterally into the piston bore 45.
  • the connection to the control pressure chamber 52 is established via a transverse bore 55 in the outer pressure piston 40. This connection of the control pressure chamber 52 to the connecting channel 74 is maintained in every position of the outer pressure piston 40.
  • a throttle point 76 is provided in the connecting channel 74, which can limit the possible fuel flow through the connecting channel 74 and which can also be omitted if necessary.
  • control valve 58 The operation of the control valve 58 is as follows. At the beginning of the injection cycle, the valve member 60 is in contact with the first valve seat 62, so that the connection 59 of the valve chamber 68 to the leakage chamber 78 is closed. The connecting channel 74 and the outlet throttle 72 are open, so that the control pressure chamber 52 and the control chamber 50 are hydraulically connected to the valve chamber 68. Through the inlet throttle 70, the injection pressure P Q prevails in the control chamber 50, which also prevails in the high-pressure duct 10. The same pressure P Q is naturally also present in the control pressure chamber 52 due to the open connections.
  • the actuator 46 switches the valve member 60 very quickly from the first valve seat 62 into contact with the second valve seat 64 via the pressure piece 48. This opens the connection of the valve chamber 68 to the leakage chamber 78 and the Connection channel 74 closed. Since this switching process takes place very quickly, the pressure in the control pressure chamber 52 only drops considerably. Due to the now existing connection of the valve chamber 68 to the leak oil chamber 78, in which there is always a very low fuel pressure, the pressure in the pressure chamber 50 drops, since the inlet throttle 70 and the outlet throttle 72 are matched to one another in such a way that more fuel from the outlet throttle 72 Control chamber 50 flows out as can flow in from high-pressure duct 10 via inlet throttle 70.
  • FIG. 4 The time course of the valve member path V, the pressure p in the control pressure chamber 52 and the stroke h of the outer valve needle 20 and the inner valve needle 22 is shown in FIG. 4.
  • the upper diagram in FIG. 4 shows the movement of the valve member 60, which begins at a point in time tg and which comes into contact with the second valve seat 64 at the point in time t].
  • the middle diagram shows the pressure p in the control pressure chamber 52, and there is a pressure drop from the injection pressure pg to a pressure level which is above the pressure pj_, the pressure p ⁇ denoting the pressure at which the inner valve needle 22 is driven by the hydraulic force on the inner valve sealing surface 36, of the seat 24 lifts off.
  • the outer valve needle 20, the stroke h of which is shown in the lower diagram in FIG. 4 begins its movement shortly after the time tg and continues the movement until it has reached its maximum stroke. At time t2, the control valve 58 switches again and that
  • Valve member 60 again reaches its starting position at first valve seat 62 at time t3.
  • Control chamber 50 fills up with the injection pressure of high-pressure duct 10 via inlet throttle 70, and pressure pg builds up again in control pressure chamber 52 via connecting duct 74.
  • the control valve 58 switches more slowly than in the case of the injection just described through the outer row of injection openings 130.
  • the relatively slow movement of the valve member 60 remains for a certain time when the valve member 60 is between the first Valve seat 62 and the second valve seat 64 is located, both the connecting channel 74 and the connection to the leak oil chamber 78 open, so that the pressure in the control pressure chamber 52 drops below the opening pressure of the inner valve needle 22, the pressure p] _.
  • the outer pressure piston 40 and also the inner pressure piston 42 move in the manner described above, so that both the outer valve needle 20 and the inner valve needle 22 lift off the seat surface 24 and open all the injection openings 30.
  • FIG. 5 shows the time course of the decisive variables in the same way as in FIG.
  • the upper diagram in FIG. 5 shows the slower course of the movement of the valve member 60, the movement back into the starting position at the first valve seat 62 being able to take place at the same speed as with injection in the part-load range.
  • the pressure curve of the pressure p in the control pressure chamber 52 shows one Pressure drops below the pressure p] _, so that the inner valve needle 22 begins its lifting movement at the time t_. This is shown in the lower diagram in FIG. 5 by the dashed line.
  • the fuel injection valve is closed in the same way as for the partial load range
  • a piezo actuator which executes a stroke depending on the voltage applied, is preferably suitable as the actuator 46.
  • valve member 60 By means of a simple voltage regulation, almost any time course during the movement of the valve member 60 can be realized.
  • other actuators can also be considered, for example fast-switching magnetic actuators whose switching speed can be controlled as a function of the magnetic field strength.

Landscapes

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

Abstract

The invention relates to a fuel injection valve for internal combustion engines, comprising a housing (1) provided with a borehole (16) containing a longitudinally displaceable outer valve needle (20) and an inner valve needle (22) which can be longitudinally displaced in the outer valve needle, said valve needles each controlling at least one injection opening (30) with the combustion chamber end thereof. The pressure in a control chamber (50) exerts a closing force at least indirectly on the outer valve needle (20), and the pressure in a control pressure chamber (52) exerts a closing force at least indirectly on the inner valve needle (22). The housing (1) contains a control valve (58) comprising a valve chamber (68) which has a valve member (60), said valve chamber (68) being provided with a connection (59) to the leakage chamber (78), a continuously open connection to the control chamber (50), and a connection to the control pressure chamber (52). The valve member (60) in the valve chamber (68) can be displaced between two end positions. In the first end position, said valve member (60) closes the connection (59) to the leakage chamber (78) and opens the connection (74) to the control pressure chamber (52), and in the second end position, closes the connection (74) to the control pressure chamber (78) and opens the connection to the leakage chamber (78).

Description

Kraftstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von Kraftstoffeinspritzventilen aus, die zwei ineinander geführte Ventilnadeln aufweisen und sonst der Gattung des Patentanspruchs 1 entsprechen. Solche Kraft- stoffeinspritzventile sind beispielsweise aus der Offenle- gungsschrift DE 41 15 477 AI bekannt. Die beiden Ventilna- dein steuern mit ihrem brennraumseitigen Ende die Öffnung von jeweils wenigstens einer Einspritzoffnung und lassen sich so ansteuern, dass entweder nur die äußere Ventilnadel einen Teil der Einspritzoffnungen aufsteuert, oder dass beide Ventilnadeln offnen und samtliche Einspritzoffnungen auf- steuern. Auf diese Weise lasst sich der Einspritzquerschnitt abhangig von der Last der Brennkraftmaschine optimal einstellen. Die Langsbewegung der Ventilnadeln in der Bohrung erfolgt durch das Verhältnis einer auf die Ventilnadeln wirkenden Offnungskraft und jeweils einer entgegengerichteten Schließkraft. Die Offnungskraft ergibt sich durch den hydraulischen Druck auf entsprechende Druckflachen an den Ventilnadeln, wahrend die Schließkraft bei den bekannten Kraft- stoffeinspritzventilen entweder durch Federn oder ebenfalls durch hydraulische Kräfte erzeugt wird. Das bekannte Kraft- stoffeinspritzventil weist hierbei den Nachteil auf, dass sich nicht die Öffnung beider Nadeln in Zeitpunkt und Dauer beliebig steuern lasst. Die äußere Ventilnadel öffnet druckgesteuert gegen die Kraft einer Schließfeder, wahrend die innere Ventilnadel - zusatzlich zur Schließkraft einer Schließfeder - eine Kraft durch den hydraulischen Druck in einem Steuerraum erfahrt. Durch ein Magnetventil lasst sich so jedoch nur steuern, ob die innere Ventilnadel bei einem Einspritzzyklus öffnet oder nicht. Die äußere Ventilnadel kann durch das Magnetventil in ihrem Offnungsverhalten nicht beeinflusst werden. Dies setzt der Steuerung des exakten Einspritzzeitpunkts und der genauen Einspritzmenge eine Grenze, was naturlich auch die weitere Optimierung der Verbrennung erschwert.The invention is based on fuel injection valves which have two valve needles inserted into one another and otherwise correspond to the type of patent claim 1. Such fuel injection valves are known, for example, from the published patent application DE 41 15 477 AI. With their end on the combustion chamber side, the two valve needles control the opening of at least one injection opening each and can be controlled in such a way that either only the outer valve needle opens part of the injection openings, or that both valve needles open and open all injection openings. In this way, the injection cross section can be optimally adjusted depending on the load of the internal combustion engine. The longitudinal movement of the valve needles in the bore takes place through the ratio of an opening force acting on the valve needles and in each case an opposing closing force. The opening force results from the hydraulic pressure on corresponding pressure surfaces on the valve needles, while the closing force in the known fuel injection valves is generated either by springs or also by hydraulic forces. The known fuel injection valve has the disadvantage that the opening and opening of both needles cannot be controlled at will and in time. The outer valve needle opens under pressure control against the force of a closing spring, while the inner valve needle - in addition to the closing force of a closing spring - experiences a force due to the hydraulic pressure in a control room. However, a solenoid valve can only control whether the inner valve needle opens or not during an injection cycle. The opening behavior of the outer valve needle cannot be influenced by the solenoid valve. This places a limit on the control of the exact injection timing and the exact injection quantity, which of course also makes further optimization of the combustion difficult.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemaße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass durch ein einziges Steuerventil Offnungszeitpunkt und Offnungsdauer sowohl der äußeren als auch der inneren Ventilnadel steuerbar ist. Hierzu weist das im Gehäuse des Kraftstoffeinspritzventils angeordnete Steuerventil einen Ventilraum auf, in dem ein Ventilglied angeordnet ist. Das Ventilglied ist zwischen zwei Endpositionen beweglich, wobei das Ventilglied in der ersten Endposition bewirkt, dass sowohl der Steuerraum, als auch der Steuerdruckraum mit Kraftstoff unter hohem Druck befullt sind, so dass sowohl die äußere Ventilnadel als auch die innere Ventilnadel in ihrer Schließstellung verharren. Fahrt das Ven- tilglied schnell in seine zweite Endposition, so wird nur der Steuerraum in den Leckolraum druckentlastet, wahrend der Steuerdruckraum seinen Druck praktisch beibehalt. Hierdurch öffnet nur die äußere Ventilnadel, wahrend die innere Ventilnadel in ihrer Schließstellung verharrt. Sollen beide Ventilnadeln, also sowohl die innere als auch die äußere Ventilnadel aufgesteuert werden, so fahrt das Ventilglied etwas langsamer von seiner ersten in die zweite Endposition, wodurch ]etzt auch der Druck im Steuerdruckraum so weit absinkt, dass zusatzlich zur äußeren Ventilnadel auch die innere Ventilnadel öffnet. Über die Schaltzeit des Steuerventils lasst sich also einstellen, ob der gesamte Einspritzquerschnitt oder nur ein Teil des Einspritzquerschnitts aufgesteuert wird. Es ist eine Steuerung der Koaxial-Varioduse mittels nur eines einzigen Steuerventils möglich.The fuel injection valve according to the invention with the characterizing features of patent claim 1 has the advantage that the opening and opening times of both the outer and the inner valve needle can be controlled by a single control valve. For this purpose, the control valve arranged in the housing of the fuel injection valve has a valve chamber in which a valve member is arranged. The valve member is movable between two end positions, the valve member in the first end position causing both the control chamber and the control pressure chamber to be filled with fuel under high pressure, so that both the outer valve needle and the inner valve needle remain in their closed position. If the valve member moves quickly to its second end position, only the control chamber is relieved of pressure in the leakage chamber, while the control pressure chamber practically maintains its pressure. As a result, only the outer valve needle opens, while the inner valve needle remains in its closed position. Should both valve needles, i.e. both the inner and the outer If the valve needle is opened, the valve member moves a little more slowly from its first to the second end position, as a result of which the pressure in the control pressure chamber also drops so far that, in addition to the outer valve needle, the inner valve needle also opens. The switching time of the control valve can therefore be used to set whether the entire injection cross section or only part of the injection cross section is opened. The coaxial varioduse can be controlled by means of only a single control valve.
In einer vorteilhaften Ausgestaltung des Gegenstandes der Erfindung wird das Ventilglied durch einen Aktor bewegt, der vorzugsweise elektrisch betrieben ist. Besonders vorteilhaft ist die Ausbildung des Aktors als Piezo-Aktor, da dieser den Vorzug aufweist, mit nahezu beliebiger Geschwindigkeit schaltbar zu sein. Das durch den Aktor bewegte Ventilglied lasst sich so mit unterschiedlicher Geschwindigkeit von der ersten Endposition in die zweite Endposition fahren, wobei sich durch die Schaltgeschwindigkeit der Einspritzquer- schnitt einstellen lasst.In an advantageous embodiment of the subject of the invention, the valve member is moved by an actuator, which is preferably operated electrically. It is particularly advantageous to design the actuator as a piezo actuator, since it has the advantage of being switchable at almost any speed. The valve member moved by the actuator can thus be moved from the first end position to the second end position at different speeds, the injection cross section being able to be set by the switching speed.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be found in the description and the drawing.
Zeichnungdrawing
In der Zeichnung ist ein Ausfuhrungsbeispiel des erfindungs- gemaßen Kraftstoffeinspritzventils dargestellt. Es zeigtIn the drawing, an exemplary embodiment of the fuel injection valve according to the invention is shown. It shows
Figur 1 einen Längsschnitt durch ein erfindungsgemaßes Kraftstoffeinspritzventil,FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention,
Figur 2 eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1, Figur 3 eine Vergrößerung von Figur 1 im mit III bezeichneten Ausschnitt,FIG. 2 shows an enlargement of the section from FIG. 1 labeled II, FIG. 3 shows an enlargement of FIG. 1 in the section designated III,
Figur 4 den Zeitverlauf von Druck, Nadelhub und Ventil- gliedhub beim Aufsteuern nur der äußeren Ventil- nadel undFIG. 4 shows the time course of pressure, needle stroke and valve limb stroke when opening only the outer valve needle and
Figur 5 den zeitlichen Verlauf von Ventilgliedhub, Druck und Nadelhub beim Aufsteuern beider Ventilnadeln.Figure 5 shows the time course of valve member stroke, pressure and needle stroke when opening both valve needles.
Beschreibung des AusfuhrungsbeispielsDescription of the exemplary embodiment
In Figur 1 ist ein Längsschnitt durch ein erfindungsgemaßes Kraftstoffeinspritzventil dargestellt. Das Kraftstoffein- spritzventil weist ein Gehäuse 1 auf, das einen Haltekorper 14, einen Steuerkorper 12, eine Zwischenscheibe 9, einen Zwischenkorper 7 und einen Ventilkorper 3 umfasst, die in dieser Reihenfolge aneinander anliegen. Die einzelnen Bauteile des Gehäuses 1 werden durch eine Spannmutter 5 gegeneinander gepresst und in ihrer Lage zueinander fixiert. Im Ventilkorper 3 ist eine Bohrung 16 ausgebildet, in der eine äußere Ventilnadel 20 langsverschiebbar angeordnet ist. Die äußere Ventilnadel 20 wird in einem brennraumabgewandten Abschnitt in der Bohrung 16 gefuhrt und verjungt sich dem Brennraum zu unter Bildung einer Druckschulter 27. Die auße- re Ventilnadel 20 erstreckt sich bis zu einer am brennraumseitigen Ende der Bohrung 16 ausgebildeten Sitzflache 24, in welcher mehrere Einspritzoffnungen 30 ausgebildet sind, die die Sitzflache 24 mit dem Brennraum der Brennkraftmaschine verbinden. Zwischen der äußeren Ventilnadel 20 und der Wand der Bohrung 16 ist ein Ringkanal 28 ausgebildet, der von der Sitzflache 24 bis zur Hohe der Druckschulter 27 reicht. Auf Hohe der Druckschulter 27 erweitert sich der Ringkanal 28 zu einem Druckraum 26, in den ein im Ventilkorper 3, dem Zwischenkorper 7, der Zwischenscheibe 9, dem Steuerkorper 12 und dem Ventilhaltekorper 14 verlaufender Zulaufkanal 10 mundet. In den Druckraum 26 und damit auch in den Ringkanal 26 kann über den Zulaufkanal 10 Kraftstoff unter hohem Druck eingebracht werden. Die äußere Ventilnadel 20 weist eine Langsbohrung 21 auf, in der eine innere Ventilnadel 22 langsverschiebbar angeordnet ist. Zur Verdeutlichung derFIG. 1 shows a longitudinal section through a fuel injection valve according to the invention. The fuel injection valve has a housing 1 which comprises a holding body 14, a control body 12, an intermediate disk 9, an intermediate body 7 and a valve body 3, which abut one another in this order. The individual components of the housing 1 are pressed against one another by a clamping nut 5 and are fixed in their position relative to one another. A bore 16 is formed in the valve body 3, in which an outer valve needle 20 is arranged so that it can be moved slowly. The outer valve needle 20 is guided in a section facing away from the combustion chamber in the bore 16 and tapers towards the combustion chamber to form a pressure shoulder 27. The outer valve needle 20 extends to a seat surface 24 formed at the end of the bore 16 on the combustion chamber side, in which several Injection openings 30 are formed, which connect the seat surface 24 to the combustion chamber of the internal combustion engine. Between the outer valve needle 20 and the wall of the bore 16, an annular channel 28 is formed, which extends from the seat surface 24 to the height of the pressure shoulder 27. At the level of the pressure shoulder 27, the annular channel 28 widens into a pressure chamber 26 into which an inlet channel 10 extends in the valve body 3, the intermediate body 7, the intermediate disk 9, the control body 12 and the valve holding body 14 tastes. Fuel can be introduced under high pressure into the pressure chamber 26 and thus also into the annular channel 26 via the inlet channel 10. The outer valve needle 20 has an elongated bore 21 in which an inner valve needle 22 is arranged so that it can be moved slowly. To illustrate the
Steuerung der Einspritzoffnungen 30 durch die Ventilnadeln 20, 22 zeigt Figur 2 den mit II bezeichneten Ausschnitt von Figur 1 vergrößert. Die Sitzflache 24 ist konisch ausgebildet und die Einspritzoffnungen 30 gruppieren sich in zwei Einspritzoffnungsreihen, nämlich in eine äußere Einspritzoffnungsreihe 130 und in eine innere Einspritzoffnungsreihe 230. Die äußere Ventilnadel 20 weist an ihrem brennraumseitigen Ende eine konische äußere Ventildichtflache 32 auf, so dass eine Dichtkante 34 gebildet wird, mit der die äußere Ventilnadel 20 in ihrer Schließstellung an der Sitzflache 24 zur Anlage kommt. Die äußere Einspritzoffnungsreihe 130, die aus wenigstens zwei Einspritzoffnungen 30 besteht, die bezuglich der Langsachse der Bohrung 16 in einer Radialebene liegen, sind stromabwärts dieser Dichtkante 34 angeordnet. Die innere Ventilnadel 22 weist an ihrem brennraumseitigen Ende eine innere Ventildichtflache 36 und eine Konusflache 38 auf, wobei an deren Übergang eine Dichtkante 37 ausgebildet ist, mit der die innere Ventilnadel 22 an der Sitzflache 24 in ihrer Schließstellung anliegt. Die innere Einspritz- offnungsreihe 230, die ebenfalls aus wenigstens zwei Einspritzoffnungen besteht, die in einer gemeinsamen Radialebene zur Langsachse der Bohrung 16 angeordnet sind, munden stromabwärts der Dichtkante 37 der inneren Ventilnadel 22 in die Sitzflache 24.Control of the injection openings 30 by the valve needles 20, 22 shows FIG. 2 enlarged the section of FIG. 1 designated II. The seat surface 24 is conical and the injection openings 30 are grouped into two injection opening rows, namely an outer injection opening row 130 and an inner injection opening row 230. The outer valve needle 20 has a conical outer valve sealing surface 32 on its combustion chamber end, so that a sealing edge 34 is formed with which the outer valve needle 20 comes into contact with the seat surface 24 in its closed position. The outer row of injection openings 130, which consists of at least two injection openings 30, which lie in a radial plane with respect to the longitudinal axis of the bore 16, are arranged downstream of this sealing edge 34. The inner valve needle 22 has at its combustion chamber end an inner valve sealing surface 36 and a conical surface 38, at the transition of which a sealing edge 37 is formed, with which the inner valve needle 22 abuts the seat surface 24 in its closed position. The inner row of injection openings 230, which likewise consists of at least two injection orifices, which are arranged in a common radial plane to the longitudinal axis of the bore 16, flow downstream of the sealing edge 37 of the inner valve needle 22 into the seat surface 24.
Das Zusammenspiel der beiden Ventilnadeln 20, 22 zur Steuerung der Einspritzoffnungen 30 ist wie folgt: Soll nur durch die äußere Einspritzoffnungsreihe 130 Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt werden, was insbesondere dann von Vorteil ist, wenn die Brennkraftma- schine in einem Teillastbereich betrieben werden soll, so hebt zur Einspritzung nur die äußere Ventilnadel 20 von der Sitzflache 24 ab. Dadurch kann Kraftstoff, der im Ringkanal 28 unter hohem Druck anliegt, zwischen der äußeren Ventil- 5 dichtflache 32 und der Sitzflache 24 zur äußeren Einspritzoffnungsreihe 130 strömen und wird von dort in den Brennraum der Brennkraftmaschine eingespritzt. Die innere Ventilnadel 22 bleibt hierbei in ihrer Schließstellung, d.h. in Anlage an der Sitzflache 24, so dass die innere Einspritzoffnungs- L0 reihe 230 verschlossen bleibt. Soll durch samtliche Einspritzoffnungen 30 eingespritzt werden, so hebt auch die innere Ventilnadel 22 von der Sitzflache 24 ab, wodurch auch die innere Einspritzoffnungsreihe 230 freigegeben wird.The interaction of the two valve needles 20, 22 for controlling the injection openings 30 is as follows: If fuel is to be injected into the combustion chamber of the internal combustion engine only through the outer row of injection openings 130, which is particularly advantageous if the internal combustion engine If the machine is to be operated in a partial load range, only the outer valve needle 20 lifts off the seat surface 24 for injection. As a result, fuel which is present in the annular channel 28 under high pressure can flow between the outer valve sealing surface 32 and the seat surface 24 to the outer row of injection openings 130 and is injected from there into the combustion chamber of the internal combustion engine. The inner valve needle 22 remains in its closed position, ie in contact with the seat surface 24, so that the inner row of injection openings L0 230 remains closed. If all of the injection openings 30 are to be used for injection, the inner valve needle 22 also lifts off the seat surface 24, as a result of which the inner row of injection openings 230 is also released.
L5 Zur Steuerung der beiden Ventilnadeln 20, 22 dienen die Vorrichtungen, die im Zwischenkorper 7, der Zwischenscheibe 9, dem Steuerkorper 12 und auch im Ventilhaltekorper 14 angeordnet sind. Dieser in Figur 1 mit III bezeichnete Ausschnitt ist in Figur 3 naher dargestellt. Im ZwischenkorperL5 The devices which are arranged in the intermediate body 7, the intermediate disk 9, the control body 12 and also in the valve holding body 14 serve to control the two valve needles 20, 22. This section, designated III in FIG. 1, is shown in more detail in FIG. In the intermediate body
20 7 ist koaxial zur Bohrung 16 eine Kolbenbohrung 45 ausgebildet, die im Durchmesser unter Bildung einer Anlageflache 41 gestuft ausgebildet ist. In der Aufnahmebohrung 35 ist ein äußerer Druckkolben 40 angeordnet, der an der äußeren Ventilnadel 20 anliegt und sich synchron mit dieser in Langs-20 7, a piston bore 45 is formed coaxially to the bore 16, which is stepped in diameter with the formation of a contact surface 41. An outer pressure piston 40 is arranged in the receiving bore 35, which rests on the outer valve needle 20 and synchronously with it in longitudinal direction.
25 richtung bewegen kann. An der Außenseite des äußeren Druckkolbens 40 ist eine Ringflache 39 angeordnet, zwischen der und der Anlageflache 41 eine Schließfeder 44 unter Druckvorspannung angeordnet ist, die als Schraubendruckfeder ausgebildet ist und den äußeren Druckkolben 40 umgibt. Durch die25 direction can move. On the outside of the outer pressure piston 40, an annular surface 39 is arranged, between which and the contact surface 41 a closing spring 44 is arranged under pressure, which is designed as a helical compression spring and surrounds the outer pressure piston 40. Through the
30 Stirnflache 51 des äußeren Druckkolbens 40, die Zwischenscheibe 9 und die Wand der Kolbenbohrung 45 wird ein Steuerraum 50 begrenzt, der über eine Zulaufdrossel 70 mit dem Zulaufkanal 10 verbunden ist, der hier als Hochdruckraum dient, in dem stets Kraftstoff unter hohem Druck anliegt.30 face 51 of the outer pressure piston 40, the washer 9 and the wall of the piston bore 45, a control chamber 50 is limited, which is connected via an inlet throttle 70 to the inlet channel 10, which serves as a high pressure chamber in which fuel is always present under high pressure.
35 Neben der Kraft der Schließfeder 44 wirkt also auf den auße- ren Druckkolben 40 und damit auf die äußere Ventilnadel 20 die hydraulische Kraft auf die Stirnfläche 51, die durch den Druck im Steuerraum 50 ergibt beaufschlagt wird.35 In addition to the force of the closing spring 44, Ren pressure piston 40 and thus on the outer valve needle 20, the hydraulic force on the end face 51, which results from the pressure in the control chamber 50 is applied.
Der äußere Druckkolben 40 weist eine Fuhrungsbohrung 47 auf, in der ein innerer Druckkolben 42 langsverschiebbar angeordnet ist. Der innere Druckkolben 42 liegt an der inneren Ventilnadel 22 an und bewegt sich stets synchron mit dieser. Durch die Fuhrungsbohrung 47 und die Stirnflache 53 des m- neren Druckkolbens 42 ist ein Steuerdruckraum 52 begrenzt, durch dessen Druck sich eine hydraulische Kraft auf den Druckkolben 42 und damit auch auf die innere Ventilnadel 22 in Richtung der Sitzflache 24 ergibt.The outer pressure piston 40 has a guide bore 47 in which an inner pressure piston 42 is arranged so that it can be moved slowly. The inner pressure piston 42 abuts the inner valve needle 22 and always moves synchronously with it. A control pressure chamber 52 is delimited by the guide bore 47 and the end face 53 of the inner pressure piston 42, the pressure of which results in a hydraulic force on the pressure piston 42 and thus also on the inner valve needle 22 in the direction of the seat surface 24.
Im Ventilhaltekorper 14 ist ein Aufnahmekorper 13 angeordnet, in welchem sich ein Aktor 46 und ein mit diesem verbundenes Druckstuck 48 befindet. Durch den Aktor 46, der vorzugsweise als Piezo-Aktor ausgeführt ist, wird das Druckstuck 48 in Längsrichtung entgegen oder in Richtung der Kraft einer Feder 49 bewegt, die zwischen dem Druckstuck 48 und dem Aufnahmekorper 13 angeordnet ist. Das Druckstuck 48 ist mit einem Ventilglied 60 verbunden, das in einem Ventilraum 68 angeordnet ist, welcher im Steuerkorper 12 ausgebildet ist und zusammen mit einem ersten Ventilsitz 62 und ei- nem diesem gegenüberliegenden zweiten Ventilsitz 64 einArranged in the valve holding body 14 is a receiving body 13 in which there is an actuator 46 and a pressure piece 48 connected to it. By means of the actuator 46, which is preferably designed as a piezo actuator, the pressure piece 48 is moved in the longitudinal direction against or in the direction of the force of a spring 49 which is arranged between the pressure piece 48 and the receiving body 13. The pressure piece 48 is connected to a valve member 60, which is arranged in a valve chamber 68 which is formed in the control body 12 and together with a first valve seat 62 and a second valve seat 64 opposite this
Steuerventil 58 bildet. Das Ventilglied 60 ist im wesentlichen als Halbkugel ausgebildet, wobei die halbkugelformige Ventildichtflache 66 mit dem ersten Ventilsitz 62 zusammenwirkt, wahrend die flache Seite des Ventilglieds 60 mit dem zweiten Ventilsitz 64 zusammenwirkt, der als Flachsitz ausgebildet ist. Der Ventilraum 68 weist eine Verbindung 59 zu einem im Ventilhaltekorper 14 ausgebildeten Leckolraum 78 auf, wobei die Verbindung 59 durch das Ventilglied 60 durch sein Zusammenwirken mit dem ersten Ventilsitz 62 geöffnet und geschlossen werden kann. Darüber hinaus weist der Ven- tilraum 68 eine Ablaufdrossel 72 auf, die den Ventilraum 68 mit dem Steuerraum 50 verbindet. Die Ablaufdrossel 72 bleibt hierbei stets offen, unabhängig von der Stellung des Ventilglieds 60. Durch das Zusammenspiel des Ventilglieds 60 mit dem zweiten Ventilsitz 64 wird ein Verbmdungskanal 74 gesteuert, der eine Verbindung zwischen dem Ventilraum 68 und dem Steuerdruckraum 52 bildet. Der Verbindungskanal 74 reicht hierbei bis in den Zwischenkorper 7 und mundet seitlich in die Kolbenbohrung 45. Die Verbindung zum Steuer- druckraum 52 wird über eine Querbohrung 55 im äußeren Druckkolben 40 hergestellt. Diese Verbindung des Steuerdruckraums 52 zum Verbindungskanal 74 bleibt bei jeder Stellung des äußeren Druckkolbens 40 erhalten. Im Verbindungskanal 74 ist eine Drosselstelle 76 vorgesehen, die den möglichen Kraft- Stoffstrom durch den Verbindungskanal 74 begrenzen kann und die bei Bedarf auch entfallen kann.Control valve 58 forms. The valve member 60 is essentially designed as a hemisphere, the hemispherical valve sealing surface 66 interacting with the first valve seat 62, while the flat side of the valve member 60 interacts with the second valve seat 64, which is designed as a flat seat. The valve chamber 68 has a connection 59 to a leak oil chamber 78 formed in the valve holder body 14, the connection 59 being able to be opened and closed by the valve member 60 through its interaction with the first valve seat 62. In addition, the tilraum 68 on an outlet throttle 72, which connects the valve chamber 68 with the control chamber 50. The flow restrictor 72 always remains open, regardless of the position of the valve member 60. The interaction of the valve member 60 with the second valve seat 64 controls a connection channel 74, which forms a connection between the valve chamber 68 and the control pressure chamber 52. The connecting channel 74 extends into the intermediate body 7 and merges laterally into the piston bore 45. The connection to the control pressure chamber 52 is established via a transverse bore 55 in the outer pressure piston 40. This connection of the control pressure chamber 52 to the connecting channel 74 is maintained in every position of the outer pressure piston 40. A throttle point 76 is provided in the connecting channel 74, which can limit the possible fuel flow through the connecting channel 74 and which can also be omitted if necessary.
Die Funktionsweise des Steuerventils 58 ist wie folgt. Zu Beginn des Einspritzzyklus ist das Ventilglied 60 in Anlage am ersten Ventilsitz 62, so dass die Verbindung 59 des Ventilraums 68 zum Leckolraum 78 verschlossen ist. Der Verbindungskanal 74 und die Ablaufdrossel 72 sind geöffnet, so dass der Steuerdruckraum 52 und der Steuerraum 50 hydraulisch mit dem Ventilraum 68 verbunden sind. Durch die Zu- laufdrossel 70 herrscht im Steuerraum 50 der Einspritzdruck PQ, der auch im Hochdruckkanal 10 herrscht. Derselbe Druck PQ ist aufgrund der offenen Verbindungen naturlich auch im Steuerdruckraum 52 vorhanden. Soll nur durch die äußere Einspritzoffnungsreihe 130 Kraftstoff eingespritzt werden, so schaltet der Aktor 46 über das Druckstuck 48 das Ventilglied 60 sehr rasch vom ersten Ventilsitz 62 in Anlage an den zweiten Ventilsitz 64. Dadurch wird die Verbindung des Ventilraums 68 zum Leckolraum 78 geöffnet und der Verbindungskanal 74 verschlossen. Da dieser Schaltvorgang sehr schnell geschieht, fallt der Druck im Steuerdruckraum 52 nur unwe- sentlich ab. Durch die jetzt vorhandene Verbindung des Ventilraums 68 zum Leckolraum 78, in welchem stets ein sehr niedriger Kraftstoffdruck herrscht, sinkt der Druck im Druckraum 50, da die Zulaufdrossel 70 und die Ablaufdrossel 72 so aufeinander abgestimmt sind, dass über die Ablaufdrossel 72 mehr Kraftstoff aus dem Steuerraum 50 abfließt als u- ber die Zulaufdrossel 70 aus dem Hochdruckkanal 10 nachfließen kann. Hierdurch erniedrigt sich die hydraulische Kraft auf die Stirnflache 51 des äußeren Druckkolbens 40, so dass die auf die Druckschulter 27 wirkenden hydraulischen Kräfte im Druckraum 26 die äußere Ventilnadel 20 von der Sitzflache 24 abhebt, so dass die äußere Einspritzoffnungsreihe 130 freigegeben wird. Die Bewegung der äußeren Ventilnadel 20 und des äußeren Ventilkolbens 40 wird so lange fortgesetzt, bis die Stirnseite 51 des äußeren Ventilkolbens 40 an der Zwischenscheibe 9 zur Anlage kommt. Durch die Bewegung des äußeren Ventilkolbens bezuglich des inneren Ventilkolbens 42, der ortsfest bleibt, vergrößert sich zwar das Volumen des Steuerdruckraums 52 geringfügig, jedoch fallt aufgrund des großen Volumens von Steuerdruckraum 52 und Verbindungskanal 74 auch hierdurch der Druck im Steuerdruckraum nicht wesentlich ab.The operation of the control valve 58 is as follows. At the beginning of the injection cycle, the valve member 60 is in contact with the first valve seat 62, so that the connection 59 of the valve chamber 68 to the leakage chamber 78 is closed. The connecting channel 74 and the outlet throttle 72 are open, so that the control pressure chamber 52 and the control chamber 50 are hydraulically connected to the valve chamber 68. Through the inlet throttle 70, the injection pressure P Q prevails in the control chamber 50, which also prevails in the high-pressure duct 10. The same pressure P Q is naturally also present in the control pressure chamber 52 due to the open connections. If fuel is to be injected only through the outer row of injection openings 130, the actuator 46 switches the valve member 60 very quickly from the first valve seat 62 into contact with the second valve seat 64 via the pressure piece 48. This opens the connection of the valve chamber 68 to the leakage chamber 78 and the Connection channel 74 closed. Since this switching process takes place very quickly, the pressure in the control pressure chamber 52 only drops considerably. Due to the now existing connection of the valve chamber 68 to the leak oil chamber 78, in which there is always a very low fuel pressure, the pressure in the pressure chamber 50 drops, since the inlet throttle 70 and the outlet throttle 72 are matched to one another in such a way that more fuel from the outlet throttle 72 Control chamber 50 flows out as can flow in from high-pressure duct 10 via inlet throttle 70. As a result, the hydraulic force on the end face 51 of the outer pressure piston 40 is reduced, so that the hydraulic forces acting on the pressure shoulder 27 in the pressure chamber 26 lifts the outer valve needle 20 from the seat face 24, so that the outer row of injection openings 130 is released. The movement of the outer valve needle 20 and the outer valve piston 40 is continued until the end face 51 of the outer valve piston 40 comes into contact with the intermediate disk 9. Due to the movement of the outer valve piston with respect to the inner valve piston 42, which remains stationary, the volume of the control pressure chamber 52 increases slightly, but due to the large volume of the control pressure chamber 52 and the connecting channel 74, the pressure in the control pressure chamber does not decrease significantly as a result.
Der zeitliche Verlauf des Ventilgliedweges V, des Drucks p im Steuerdruckraum 52 und des Hubs h der äußeren Ventilnadel 20 und der inneren Ventilnadel 22 ist in Figur 4 dargestellt. Das obere Diagramm der Figur 4 zeigt die Bewegung des Ventilglieds 60, die zu einem Zeitpunkt tg einsetzt und die zum Zeitpunkt t]_ am zweiten Ventilsitz 64 zur Anlage kommt. Das mittlere Diagramm gibt den Druck p im Steuerdruckraum 52 wieder, und es zeigt sich ein Druckabfall vom Einspritzdruck pg bis zu einem Druckniveau, das oberhalb des Drucks pj_ liegt, wobei der Druck p^ den Druck bezeichnet, bei dem die innere Ventilnadel 22, angetrieben durch die hydraulische Kraft auf die innere Ventildichtflache 36, von der Sitzflache 24 abhebt. Die äußere Ventilnadel 20, deren Hub h im unteren Diagramm der Figur 4 dargestellt ist, beginnt ihre Bewegung kurz nach dem Zeitpunkt tg und setzt die Bewegung fort, bis sie ihren Maximalhub erreicht hat. Zum Zeitpunkt t2 schaltet das Steuerventil 58 erneut und dasThe time course of the valve member path V, the pressure p in the control pressure chamber 52 and the stroke h of the outer valve needle 20 and the inner valve needle 22 is shown in FIG. 4. The upper diagram in FIG. 4 shows the movement of the valve member 60, which begins at a point in time tg and which comes into contact with the second valve seat 64 at the point in time t]. The middle diagram shows the pressure p in the control pressure chamber 52, and there is a pressure drop from the injection pressure pg to a pressure level which is above the pressure pj_, the pressure p ^ denoting the pressure at which the inner valve needle 22 is driven by the hydraulic force on the inner valve sealing surface 36, of the seat 24 lifts off. The outer valve needle 20, the stroke h of which is shown in the lower diagram in FIG. 4, begins its movement shortly after the time tg and continues the movement until it has reached its maximum stroke. At time t2, the control valve 58 switches again and that
Ventilglied 60 erreicht zum Zeitpunkt t3 wieder seine Ausgangsposition am ersten Ventilsitz 62. Der Steuerraum 50 be- fullt sich über die Zulaufdrossel 70 mit dem Einspritzdruck des Hochdruckkanals 10 und über den Verbindungskanal 74 baut sich auch im Steuerdruckraum 52 wieder der Druck pg auf.Valve member 60 again reaches its starting position at first valve seat 62 at time t3. Control chamber 50 fills up with the injection pressure of high-pressure duct 10 via inlet throttle 70, and pressure pg builds up again in control pressure chamber 52 via connecting duct 74.
Durch den ansteigenden Druck im Steuerraum 50 wird die äußere Ventilnadel 20 zurück in ihre Schließstellung gedruckt.Due to the increasing pressure in the control chamber 50, the outer valve needle 20 is pressed back into its closed position.
Soll durch samtliche Einspritzoffnungen 30 eingespritzt wer- den, so schaltet das Steuerventil 58 langsamer als bei der eben geschilderten Einspritzung durch die äußere Einspritzoffnungsreihe 130. Durch die relativ langsame Bewegung des Ventilglieds 60 bleibt für eine gewisse Zeit, wenn sich das Ventilglied 60 zwischen dem ersten Ventilsitz 62 und dem zweiten Ventilsitz 64 befindet, sowohl der Verbindungskanal 74 als auch die Verbindung zum Leckolraum 78 geöffnet, so dass der Druck im Steuerdruckraum 52 unter den Offnungsdruck der inneren Ventilnadel 22, den Druck p]_, abfallt. Dadurch bewegt sich in der oben beschriebenen Art und Weise der au- ßere Druckkolben 40 und auch der innere Druckkolben 42, so dass sowohl die äußere Ventilnadel 20 als auch die innere Ventilnadel 22 von der Sitzflache 24 abheben und samtliche Einspritzoffnungen 30 freigeben. In Figur 5 ist in der selben Art und Weise wie in Figur 4 der zeitliche Verlauf der maßgebenden Großen dargestellt. Es zeigt das obere Diagramm der Figur 5 den langsameren Verlauf der Bewegung des Ventilglieds 60, wobei die Bewegung zurück in die Ausgangsposition am ersten Ventilsitz 62 mit der gleichen Geschwindigkeit wie bei Einspritzung im Teillastbereich erfolgen kann. Der Druckverlauf des Drucks p im Steuerdruckraum 52 zeigt einen Abfall des Drucks unter den Druck p]_, so dass die innere Ventilnadel 22 ihre Hubbewegung zum Zeitpunkt t_ beginnt. Dies ist im unteren Diagramm der Figur 5 durch die gestrichelte Linie dargestellt. Das Schließen des Kraftstoffein- spritzventil erfolgt analog zum Teillastbereich durch denIf all of the injection openings 30 are to be used for injection, the control valve 58 switches more slowly than in the case of the injection just described through the outer row of injection openings 130. The relatively slow movement of the valve member 60 remains for a certain time when the valve member 60 is between the first Valve seat 62 and the second valve seat 64 is located, both the connecting channel 74 and the connection to the leak oil chamber 78 open, so that the pressure in the control pressure chamber 52 drops below the opening pressure of the inner valve needle 22, the pressure p] _. As a result, the outer pressure piston 40 and also the inner pressure piston 42 move in the manner described above, so that both the outer valve needle 20 and the inner valve needle 22 lift off the seat surface 24 and open all the injection openings 30. FIG. 5 shows the time course of the decisive variables in the same way as in FIG. The upper diagram in FIG. 5 shows the slower course of the movement of the valve member 60, the movement back into the starting position at the first valve seat 62 being able to take place at the same speed as with injection in the part-load range. The pressure curve of the pressure p in the control pressure chamber 52 shows one Pressure drops below the pressure p] _, so that the inner valve needle 22 begins its lifting movement at the time t_. This is shown in the lower diagram in FIG. 5 by the dashed line. The fuel injection valve is closed in the same way as for the partial load range
Wiederaufbau des Drucks im Steuerraum 50 und im Steuerdruckraum 52.Reconstruction of the pressure in the control room 50 and in the control pressure room 52.
Als Aktor 46 eignet sich vorzugsweise ein Piezo-Aktor, der einen Hub abhangig von der angelegten Spannung ausfuhrt.A piezo actuator, which executes a stroke depending on the voltage applied, is preferably suitable as the actuator 46.
Durch eine einfache Spannungsregelung lasst sich so nahezu jeder zeitliche Verlauf bei der Bewegung des Ventilglieds 60 realisieren. Neben einem Piezo-Aktor kommen auch andere Aktoren in Betracht, beispielsweise schnell schaltende Magnet- aktoren, deren Schaltgeschwindigkeit abhangig von der Magnetfeldstarke gesteuert werden kann. By means of a simple voltage regulation, almost any time course during the movement of the valve member 60 can be realized. In addition to a piezo actuator, other actuators can also be considered, for example fast-switching magnetic actuators whose switching speed can be controlled as a function of the magnetic field strength.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem Gehäuse (1), in dem in einer Bohrung (16) eine langsverschiebbare äußere Ventilnadel (20) und eine in dieser langsverschiebbare innere Ventilnadel (22) angeordnet sind, die mit ihrem brennraumseitigen Ende je wenigstens eine Einspritzoffnung (30) steuern, und mit einem Steuerraum (50) , der über eine Zulaufdrossel (70) mit einem Hochdruckraum (10) verbunden ist und durch dessen Druck wenigstens mittelbar eine Schließkraft auf die äußere Ventilnadel (20) ausgeübt wird, und mit einem Steuerdruckraum (52), durch dessen Druck zumindest mittelbar eine Schließkraft auf die innere Ventilnadel (22) ausgeübt wird, und mit einem Leckolraum (78), in dem stets ein niedriger Kraftstoffdruck herrscht, dadurch gekennzeich- net, dass im Gehäuse (1) ein Steuerventil (58) angeordnet ist, das einen Ventilraum (68) und ein darin angeordnetes Ventilglied (60) aufweist, wobei der Ventilraum (68) eine Verbindung (59) zum Leckolraum (78), eine stets offene Verbindung (72) zum Steuerraum (50) und eine Verbindung (74) zum Steuerdruckraum (52) aufweist, wobei das Ventilglied (60) im Ventilraum (68) zwischen zwei Endpositionen beweglich ist und in der ersten Endposition die Verbindung (59) zum Leckolraum (78) verschließt und die Verbindung (74) zum Steuerdruckraum (52) öffnet und in der zweiten Endposition die Verbindung (74) zum Steuerdruck- räum (52) schließt und die Verbindung (59) zum Leckolraum (78) öffnet.1.Fuel injection valve for internal combustion engines with a housing (1), in which a slowly displaceable outer valve needle (20) and a slowly displaceable inner valve needle (22) are arranged in a bore (16), each of which has at least one injection opening with its combustion chamber end ( 30), and with a control chamber (50), which is connected via an inlet throttle (70) to a high-pressure chamber (10) and at least indirectly exerts a closing force on the outer valve needle (20) by its pressure, and with a control pressure chamber ( 52), the pressure of which exerts a closing force on the inner valve needle (22) at least indirectly, and with a leakage space (78) in which there is always a low fuel pressure, characterized in that a control valve () 58) which has a valve chamber (68) and a valve member (60) arranged therein, the valve chamber (68) connecting (59) to the leak oil chamber (7 8), always has an open connection (72) to the control chamber (50) and a connection (74) to the control pressure chamber (52), the valve member (60) in the valve chamber (68) being movable between two end positions and in the first end position Closes the connection (59) to the leak oil chamber (78) and opens the connection (74) to the control pressure chamber (52) and in the second end position the connection (74) to the control pressure Room (52) closes and the connection (59) to the leakage chamber (78) opens.
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass über die Zulaufdrossel (70) weniger2. Fuel injection valve according to claim 1, characterized in that via the inlet throttle (70) less
5 Kraftstoff in den Steuerraum (50) einfließt, als bei entsprechender Stellung des Steuerventils (58) über die Ablaufdrossel (72) in den Leckolraum (78) abfließt.5 Fuel flows into the control chamber (50) than, when the control valve (58) is in the appropriate position, flows into the leakage chamber (78) via the outlet throttle (72).
3. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass das Ventilglied (60) durch einen Aktor3. Fuel injection valve according to claim 1, characterized in that the valve member (60) by an actuator
10 (46) bewegt wird.10 (46) is moved.
4. Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, dass der Aktor (46) das Ventilglied (60) mit unterschiedlicher Geschwindigkeit von der ersten Endposition in die zweite Endposition bewegen kann.4. Fuel injection valve according to claim 3, characterized in that the actuator (46) can move the valve member (60) at different speeds from the first end position to the second end position.
L5 5. Kraftstoffeinspritzventil nach Anspruch 3 oder 4, dadurch gekennzeichnet, dass der Aktor (46) ein Piezo-Aktor ist.L5 5. Fuel injection valve according to claim 3 or 4, characterized in that the actuator (46) is a piezo actuator.
6. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass sämtliche Verbindungen (59; 74; 72) zum Ventilraum (68) geöffnet sind, wenn sich das Ventil-6. Fuel injection valve according to claim 1, characterized in that all connections (59; 74; 72) to the valve chamber (68) are open when the valve
20 glied (60) zwischen der ersten Endposition und der zweiten Endposition befindet.20 link (60) between the first end position and the second end position.
7. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass sich das Ventilglied (60) so schnell von der ersten Endposition in die zweite Endposition be- 5 wegen lasst, dass der Druck im Steuerdruckraum (52) dabei nur unwesentlich abnimmt. 7. Fuel injection valve according to claim 1, characterized in that the valve member (60) can be moved from the first end position into the second end position so quickly that the pressure in the control pressure chamber (52) decreases only insignificantly.
EP03752691A 2002-05-18 2003-03-25 Fuel injection valve for internal combustion engines Expired - Lifetime EP1507972B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10222196 2002-05-18
DE10222196A DE10222196A1 (en) 2002-05-18 2002-05-18 Fuel injection valve for combustion engine, has control valve with valve chamber and valve member that is moveable between two end positions for opening or closing connections to certain chambers
PCT/DE2003/000973 WO2003098028A1 (en) 2002-05-18 2003-03-25 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1507972A1 true EP1507972A1 (en) 2005-02-23
EP1507972B1 EP1507972B1 (en) 2005-12-28

Family

ID=29285567

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03752691A Expired - Lifetime EP1507972B1 (en) 2002-05-18 2003-03-25 Fuel injection valve for internal combustion engines

Country Status (5)

Country Link
US (1) US7021567B2 (en)
EP (1) EP1507972B1 (en)
JP (1) JP2005526211A (en)
DE (2) DE10222196A1 (en)
WO (1) WO2003098028A1 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10304605A1 (en) * 2003-02-05 2004-08-19 Robert Bosch Gmbh Fuel injector with two coaxial valve needles
DE10357769B4 (en) * 2003-12-10 2007-06-21 Siemens Ag Fuel injection valve
WO2005075810A1 (en) * 2004-02-05 2005-08-18 Siemens Aktiengesellschaft Injection valve
DE102004015360A1 (en) * 2004-03-30 2005-10-20 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE102004020550A1 (en) * 2004-04-27 2005-11-24 Robert Bosch Gmbh injection
DE102004032700B3 (en) * 2004-07-06 2005-10-06 Siemens Ag Fuel injector for internal combustion engine, has inner and outer valve bodies with inner and outer valve seats to seal inner and outer control rooms from fuel, where inner seat is spherically thickened with radius
DE502005010779D1 (en) * 2004-12-03 2011-02-10 Ganser Hydromag FUEL INJECTION VALVE WITH PRESSURE REINFORCEMENT
DE102004061800A1 (en) * 2004-12-22 2006-07-06 Robert Bosch Gmbh Injector of a fuel injection system of an internal combustion engine
DE102004062073B4 (en) * 2004-12-23 2015-08-13 Continental Automotive Gmbh Method and device for compensation of bounce effects in a piezo-controlled injection system of an internal combustion engine
FR2894631A1 (en) * 2005-12-13 2007-06-15 Renault Sas Fuel injector, especially for diesel engines, comprises a needle valve moving inside a cylinder at a speed which can be varied by an electromagnet and a switch whatever its position in the cylinder
DE102006040645A1 (en) * 2006-08-30 2008-03-13 Robert Bosch Gmbh Injector for internal combustion engines
DE102007011613B4 (en) * 2007-01-22 2011-07-28 Airbus Operations GmbH, 21129 Fitting for the introduction of high forces in a fuselage cell of an aircraft
DE102007009165A1 (en) * 2007-02-26 2008-08-28 Robert Bosch Gmbh Fuel injector for injecting fuel into combustion chamber of internal-combustion engine, has output choke arranged in area of passage from riser bore into ring chamber, where amount of fuel guided by riser bore flows through choke
JP4772016B2 (en) * 2007-09-07 2011-09-14 トヨタ自動車株式会社 Fuel injection control device for internal combustion engine
DE102010039051A1 (en) * 2010-08-09 2012-02-09 Robert Bosch Gmbh Injector
US8690075B2 (en) * 2011-11-07 2014-04-08 Caterpillar Inc. Fuel injector with needle control system that includes F, A, Z and E orifices
HUE027556T2 (en) * 2012-06-13 2016-10-28 Delphi Int Operations Luxembourg Sarl Fuel injector
JP6384366B2 (en) * 2015-03-09 2018-09-05 株式会社デンソー Fuel injection device
US11591995B2 (en) * 2020-09-15 2023-02-28 Caterpillar Inc. Fuel injector having valve seat orifice plate with valve seat and drain and re-pressurization orifices
US11970976B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of fuel nozzle with an auxiliary circuit
US11970977B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of a secondary circuit of a fuel injector
US11913381B1 (en) * 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Force modification of passive spool for control of secondary nozzle circuits
US11913382B1 (en) 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Variable restriction of a fuel circuit of a fuel nozzle

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4115477C2 (en) * 1990-05-17 2003-02-06 Avl Verbrennungskraft Messtech Injection nozzle for an internal combustion engine
GB9709678D0 (en) * 1997-05-14 1997-07-02 Lucas Ind Plc Fuel injector
GB9813476D0 (en) * 1998-06-24 1998-08-19 Lucas Ind Plc Fuel injector
GB9916464D0 (en) * 1999-07-14 1999-09-15 Lucas Ind Plc Fuel injector
AT3763U3 (en) * 1999-08-05 2000-12-27 Avl List Gmbh CAM-ACTUATED INJECTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE
GB9922408D0 (en) * 1999-09-23 1999-11-24 Lucas Ind Plc Fuel injector
DE10115215A1 (en) * 2001-03-28 2002-10-10 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
US6705543B2 (en) * 2001-08-22 2004-03-16 Cummins Inc. Variable pressure fuel injection system with dual flow rate injector
DE10205970A1 (en) * 2002-02-14 2003-09-04 Bosch Gmbh Robert Fuel injection valve for internal combustion engines

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO03098028A1 *

Also Published As

Publication number Publication date
US7021567B2 (en) 2006-04-04
WO2003098028A1 (en) 2003-11-27
DE10222196A1 (en) 2003-11-27
DE50302074D1 (en) 2006-02-02
US20050224598A1 (en) 2005-10-13
EP1507972B1 (en) 2005-12-28
JP2005526211A (en) 2005-09-02

Similar Documents

Publication Publication Date Title
EP1507972A1 (en) Fuel injection valve for internal combustion engines
EP1478840B1 (en) Fuel injection valve for internal combustion engines
DE4115477C2 (en) Injection nozzle for an internal combustion engine
DE19732802A1 (en) Fuel injection device for internal combustion engines
DE4311627A1 (en) Fuel injection device for internal combustion engines
DE10103164A1 (en) Pilot operated spool valve assembly and fuel injector using the same
DE19946906A1 (en) Fuel injection valve for internal combustion engines
DE102009039647A1 (en) Fuel injector, particularly common rail fuel injector, for injecting fuel into combustion chamber of internal combustion engine, has servo valve that is controlled by piezoelectric actuator
DE10060836C1 (en) Pressure-controlled CR injector with stepped opening and closing behavior
EP1344929B1 (en) Fuel injector for internal combustion engines
WO2001014718A1 (en) Injector
WO2005015000A1 (en) Control valve with pressure compensation for a fuel injector comprising a pressure intensifier
DE10031574B4 (en) Pressure-controlled double-acting high-pressure injector
DE10031580A1 (en) Pressure-controlled control part for common rail injectors
DE10357769B4 (en) Fuel injection valve
DE19623211A1 (en) Fuel injection valve for internal combustion engines
DE10155412A1 (en) Fuel injection device for an internal combustion engine
WO2009146974A1 (en) Fuel injector with perforated seat nozzle
EP1415082A1 (en) Fuel injector having two-way valve control
DE19623759A1 (en) Fuel injection valve for internal combustion engines
DE19947196A1 (en) Fuel injection device for diesel engine has control valve for regulating fuel feed from high pressure space to injection valve
EP1527270A1 (en) Fuel injection valve for internal combustion engines
WO2006079425A1 (en) Fuel injection device
DE102007030794A1 (en) Fuel injector for internal combustion engine, comprises nozzle body with nozzle needle, which is guided movably into it, which controls injection of fuel from nozzle area of nozzle body
DE10100512A1 (en) Injector

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20041220

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RBV Designated contracting states (corrected)

Designated state(s): DE FR

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR

REF Corresponds to:

Ref document number: 50302074

Country of ref document: DE

Date of ref document: 20060202

Kind code of ref document: P

ET Fr: translation filed
PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

26N No opposition filed

Effective date: 20060929

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20090318

Year of fee payment: 7

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20101130

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20100331

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20180517

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 50302074

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20191001