EP1507972B1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines Download PDF

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Publication number
EP1507972B1
EP1507972B1 EP03752691A EP03752691A EP1507972B1 EP 1507972 B1 EP1507972 B1 EP 1507972B1 EP 03752691 A EP03752691 A EP 03752691A EP 03752691 A EP03752691 A EP 03752691A EP 1507972 B1 EP1507972 B1 EP 1507972B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
space
control
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP03752691A
Other languages
German (de)
French (fr)
Other versions
EP1507972A1 (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
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Filing date
Publication date
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Publication of EP1507972A1 publication Critical patent/EP1507972A1/en
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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—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, the have two nested valve needles and otherwise the genus of claim 1 correspond.
  • fuel injection valves are for example from the published patent application DE 41 15 477 Al known.
  • the two valve pins control the opening with its combustion chamber end each of at least one injection port and let to control itself so that either only the outer valve needle opens up a part of the injection openings, or both Open valve pins and open all injection openings.
  • the injection cross section can be set optimally depending on the load of the internal combustion engine.
  • the longitudinal movement of the valve pins in the bore is done by the ratio of acting on the valve needles Opening force and one opposite each Closing force.
  • the opening force results from the hydraulic Pressure on corresponding pressure surfaces on the valve pins, while the closing force in the known fuel injection valves either by springs or likewise generated by hydraulic forces.
  • the known fuel injection valve has the disadvantage that not the opening of both needles in time and duration can be controlled arbitrarily.
  • the outer valve needle opens under pressure control against the force of a recoil spring while the inner valve needle - in addition to the closing force of a Closing spring - a force due to the hydraulic pressure in experiences a control room.
  • a solenoid valve can be However, so only control whether the inner valve needle at a Injection cycle opens or not.
  • the outer valve needle can not through the solenoid valve in its opening behavior to be influenced. This sets the control of the exact Injection timing and the exact injection amount one Border, which of course also the further optimization of the Combustion difficult.
  • the arranged in the housing of the fuel injection valve control valve a valve space in which a valve member is arranged is.
  • the valve member is between two end positions movable, wherein the valve member in the first end position causes both the control room, as well as the control pressure chamber filled with fuel under high pressure, so that both the outer valve needle and the inner valve needle remain in their closed position.
  • the valve member is moved by an actuator, the is preferably electrically operated.
  • the actuator as a piezo actuator, since this the Virtue, with almost any speed to be switchable.
  • the valve member moved by the actuator can be so with different speed of the drive first end position in the second end position, wherein itself by the switching speed of the injection cross section can be set.
  • FIG 1 is a longitudinal section through an inventive Fuel injection valve shown.
  • the fuel injector has a housing 1, which has a holding body 14, a control body 12, an intermediate disc 9, a Intermediate body 7 and a valve body 3 comprises, in abut each other in this order.
  • the individual components of the housing 1 are by a clamping nut 5 against each other pressed and fixed in their position to each other.
  • in the Valve body 3 is formed a bore 16 in which a outer valve needle 20 is arranged longitudinally displaceable.
  • the outer valve needle 20 is in a combustion chamber facing away portion guided in the bore 16 and tapers the Combustion chamber to form a pressure shoulder 27.
  • the outer Valve needle 20 extends to one on the combustion chamber side End of the bore 16 formed seat surface 24, in which a plurality of injection openings 30 are formed, the the seat 24 with the combustion chamber of the internal combustion engine connect.
  • an annular channel 28 is formed, of the Seat 24 extends to the height of the pressure shoulder 27.
  • the annular channel 28 widens a pressure chamber 26, in the one in the valve body 3, the intermediate body 7, the washer 9, the control body 12th and the valve holding body 14 extending inlet channel 10th empties.
  • the pressure chamber 26 and thus also in the annular channel 26 can fuel via the inlet channel 10 under high pressure be introduced.
  • the outer valve needle 20 has a Longitudinal bore 21, in which an inner valve needle 22nd is arranged longitudinally displaceable.
  • Figure 2 shows the designated II section of Figure 1 enlarged.
  • the seat surface 24 is conical and the injection ports 30 are grouped in two Injection opening rows, namely in an outer row of injection openings 130 and in an inner injection port row 230.
  • the outer valve needle 20 has at its combustion chamber side End of a conical outer valve sealing surface 32, so a sealing edge 34 is formed, with which the outer Valve needle 20 in its closed position on the seat surface 24th comes to the plant.
  • the outer injection port row 130 the consists of at least two injection ports 30, with respect to the longitudinal axis of the bore 16 in a radial plane lie, downstream of this sealing edge 34 are arranged.
  • the inner valve needle 22 has at its combustion chamber side End an inner valve sealing surface 36 and a conical surface 38, wherein at the transition, a sealing edge 37 is formed is, with the inner valve needle 22 on the seat 24 abuts in its Schrellowolf.
  • the inner injection port series 230 which also consists of at least two injection ports exists in a common radial plane are arranged to the longitudinal axis of the bore 16, open downstream of the sealing edge 37 of the inner valve needle 22 in the seat 24.
  • the interaction of the two valve pins 20, 22 for control the injection openings 30 is as follows: Should only by the outer injection port row 130 fuel in the Combustion chamber of the internal combustion engine are injected, which is particularly advantageous if the internal combustion engine to be operated in a partial load range, so raises for injection only the outer valve needle 20 of the Seat 24 from. This can cause fuel in the annular channel 28 is under high pressure, between the outer valve sealing surface 32 and the seat surface 24 to the outer injection opening row 130 flow and from there into the combustion chamber the internal combustion engine injected.
  • the inner valve needle 22 remains in its closed position, i. in Appendix on the seat 24, so that the inner row of injection openings 230 remains closed.
  • Target through all injection openings Be injected so also raises the inner Valve needle 22 from the seat 24 from, which also the inner injection port row 230 is released.
  • the intermediate body 7 is coaxial with the bore 16 , a piston bore 45 is formed, the diameter in the formation of a contact surface 41st is designed graduated.
  • a receiving bore 35 is a outer pressure piston 40 disposed on the outer valve needle 20 rests and synchronously with this in the longitudinal direction can move.
  • an annular surface 39 is arranged between the and the contact surface 41 a closing spring 44 under compressive bias is arranged, which formed as a helical compression spring is and surrounds the outer pressure piston 40.
  • the outer pressure piston 40 has a guide bore 47, in which an inner pressure piston 42 is arranged longitudinally displaceable is.
  • the inner pressure piston 42 is located on the inner valve needle 22 and always moves in sync with this.
  • a control pressure chamber 52 Through the guide bore 47 and the end face 53 of the inner Pressure piston 42 is a control pressure chamber 52 limited by the pressure of a hydraulic Kraftrauf the Pressure piston 42 and thus also on the inner valve needle 22nd in the direction of the seat 24 results.
  • a receiving body 13 is arranged, in which an actuator 46 and an associated with this Pressure piece 48 is located.
  • the actuator 46 preferably is designed as a piezo actuator, the pressure piece 48 in the longitudinal direction or in the direction of Force of a spring 49 moves between the pressure piece 48th and the receiving body 13 is arranged.
  • the pressure piece 48 is connected to a valve member 60 which is in a valve chamber 68 is arranged, which formed in the control body 12 is and together with a first valve seat 62 and a this opposite second valve seat 64 a Control valve 58 forms.
  • the valve member 60 is substantially formed as a hemisphere, the hemispherical Valve sealing surface 66 cooperates with the first valve seat 62, while the flat side of the valve member 60 with the second valve seat 64 cooperates, which formed as a flat seat is.
  • the valve space 68 has a connection 59 a leakage oil space 78 formed in the valve holding body 14 on, wherein the connection 59 through the valve member 60 through its interaction with the first valve seat 62 is opened and can be closed.
  • the valve chamber points 68, an outlet throttle 72, the valve space 68th connects to the control room 50.
  • the outlet throttle 72 remains always open, regardless of the position of the valve member 60.
  • connection channel 74 By the interaction of the valve member 60 with the second valve seat 64 is controlled a connection channel 74, the connection between the valve chamber 68 and forms the control pressure chamber 52.
  • the connection channel 74 This extends into the intermediate body 7 and opens laterally in the piston bore 45.
  • the connection to the control pressure chamber 52 is via a transverse bore 55 in the outer pressure piston 40 produced.
  • This connection of the control pressure chamber 52 to the connection channel 74 remains at each position of the outer Pressure piston 40 received.
  • a throttle point 76 is provided which the possible fuel flow can limit through the connecting channel 74 and which can 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 is closed to the leakage oil chamber 78. The connecting channel 74 and the outlet throttle 72 are opened, so that the control pressure chamber 52 and the control chamber 50 are hydraulically connected to the valve chamber 68. By the inlet throttle 70 prevails in the control chamber 50 of the injection pressure P 0 , which also prevails in the high-pressure passage 10. Of course, the same pressure P 0 is also present in the control pressure chamber 52 due to the open connections.
  • 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 Figure 4.
  • the upper diagram of Figure 4 shows the movement of the valve member 60, which begins at a time t 0 and which comes at time t 1 at the second valve seat 64 for conditioning.
  • the middle graph shows the pressure p in the control pressure chamber 52 again, and there is a pressure drop from the injection pressure p 0 to a pressure level that is above the pressure p 1 , wherein the pressure p 1 denotes the pressure at which the inner valve needle 22nd driven by the hydraulic force on the inner valve sealing surface 36 lifts off from the seat surface 24.
  • the outer valve needle 20, the stroke h is shown in the lower diagram of Figure 4, begins their movement shortly after the time t 0 and continues the movement until it has reached its maximum stroke.
  • the control valve 58 switches again and the valve member 60 reaches its original position at the first valve seat 62 at time t 3.
  • the control chamber 50 fills via the inlet throttle 70 with the injection pressure of the high-pressure passage 10 and via the connecting channel 74 also builds up in the Control pressure chamber 52 back to the pressure p 0 . Due to the increasing pressure in the control chamber 50, the outer valve needle 20 is pushed back into its closed position.
  • the control valve 58 switches more slowly than in the just described injection through the outer injection opening 130.
  • the relatively slow movement of the valve member 60 remains for a certain time when the valve member 60 between the first valve seat 62 and the second valve seat 64 is open, both the connecting channel 74 and the connection to the leakage oil chamber 78, so that the pressure in the control pressure chamber 52 below the opening pressure of the inner valve needle 22, the pressure p 1 , drops.
  • the outer pressure piston 40 and also the inner pressure piston 42 so that both the outer valve needle 20 and the inner valve needle 22 lift off from the seat surface 24 and release all the injection ports 30.
  • FIG. 5 the time course of the governing quantities is shown in the same manner as in FIG.
  • the upper diagram of FIG. 5 shows the slower course of the movement of the valve member 60, wherein the movement back to the starting position on the first valve seat 62 can take place at the same speed as in the partial load injection.
  • the pressure curve of the pressure p in the control pressure chamber 52 shows a drop in pressure below the pressure p 1 , so that the inner valve needle 22 begins its stroke movement at the time t 1 . This is shown in the lower diagram of Figure 5 by the dashed line.
  • the closing of the fuel injection valve is analogous to the partial load range by the reconstruction of the pressure in the control chamber 50 and the control pressure chamber 52nd
  • actuator 46 is preferably a piezoelectric actuator, the performs a stroke depending on the applied voltage. With a simple voltage regulation it is almost possible each time course in the movement of the valve member 60th realize.
  • other actuators come for example, fast-switching magnetic actuators, their switching speed depends on the magnetic field strength can be controlled.

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

Description

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 Kraftstoffeinspritzventile sind beispielsweise aus der Offenlegungsschrift DE 41 15 477 Al bekannt. Die beiden Ventilnadeln steuern mit ihrem brennraumseitigen Ende die Öffnung von jeweils wenigstens einer Einspritzöffnung und lassen sich so ansteuern, dass entweder nur die äußere Ventilnadel einen Teil der Einspritzöffnungen aufsteuert, oder dass beide Ventilnadeln öffnen und sämtliche Einspritzöffnungen aufsteuern. Auf diese Weise lässt sich der Einspritzquerschnitt abhängig von der Last der Brennkraftmaschine optimal einstellen. Die Längsbewegung der Ventilnadeln in der Bohrung erfolgt durch das Verhältnis einer auf die Ventilnadeln wirkenden Öffnungskraft und jeweils einer entgegengerichteten Schließkraft. Die Öffnungskraft ergibt sich durch den hydraulischen Druck auf entsprechende Druckflächen an den Ventilnadeln, während die Schließkraft bei den bekannten Kraftstoffeinspritzventilen entweder durch Federn oder ebenfalls durch hydraulische Kräfte erzeugt wird. Das bekannte Kraftstoffeinspritzventil weist hierbei den Nachteil auf, dass sich nicht die Öffnung beider Nadeln in Zeitpunkt und Dauer beliebig steuern lässt. Die äußere Ventilnadel öffnet druckgesteuert gegen die Kraft einer Schließfeder, während die innere Ventilnadel - zusätzlich zur Schließkraft einer Schließfeder - eine Kraft durch den hydraulischen Druck in einem Steuerraum erfährt. Durch ein Magnetventil lässt sich so jedoch nur steuern, ob die innere Ventilnadel bei einem Einspritzzyklus öffnet oder nicht. Die äußere Ventilnadel kann durch das Magnetventil in ihrem Öffnungsverhalten nicht beeinflusst werden. Dies setzt der Steuerung des exakten Einspritzzeitpunkts und der genauen Einspritzmenge eine Grenze, was natürlich auch die weitere Optimierung der Verbrennung erschwert.The invention is based on fuel injection valves, the have two nested valve needles and otherwise the genus of claim 1 correspond. Such fuel injection valves are for example from the published patent application DE 41 15 477 Al known. The two valve pins control the opening with its combustion chamber end each of at least one injection port and let to control itself so that either only the outer valve needle opens up a part of the injection openings, or both Open valve pins and open all injection openings. In this way, the injection cross section can be set optimally depending on the load of the internal combustion engine. The longitudinal movement of the valve pins in the bore is done by the ratio of acting on the valve needles Opening force and one opposite each Closing force. The opening force results from the hydraulic Pressure on corresponding pressure surfaces on the valve pins, while the closing force in the known fuel injection valves either by springs or likewise generated by hydraulic forces. The known fuel injection valve has the disadvantage that not the opening of both needles in time and duration can be controlled arbitrarily. The outer valve needle opens under pressure control against the force of a recoil spring while the inner valve needle - in addition to the closing force of a Closing spring - a force due to the hydraulic pressure in experiences a control room. By a solenoid valve can be However, so only control whether the inner valve needle at a Injection cycle opens or not. The outer valve needle can not through the solenoid valve in its opening behavior to be influenced. This sets the control of the exact Injection timing and the exact injection amount one Border, which of course also the further optimization of the Combustion difficult.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass durch ein einziges Steuerventil Öffnungszeitpunkt und Öffnungsdauer 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 befüllt sind, so dass sowohl die äußere Ventilnadel als auch die innere Ventilnadel in ihrer Schließstellung verharren. Fährt das Ventilglied schnell in seine zweite Endposition, so wird nur der Steuerraum in den Leckölraum druckentlastet, während der Steuerdruckraum seinen Druck praktisch beibehält. Hierdurch öffnet nur die äußere Ventilnadel, während die innere Ventilnadel in ihrer Schließstellung verharrt. Sollen beide Ventilnadeln, also sowohl die innere als auch die äußere Ventilnadel aufgesteuert werden, so fährt das Ventilglied etwas langsamer von seiner ersten in die zweite Endposition, wodurch jetzt auch der Druck im Steuerdruckraum so weit absinkt, dass zusätzlich zur äußeren Ventilnadel auch die innere Ventilnadel öffnet. Über die Schaltzeit des Steuerventils lässt sich also einstellen, ob der gesamte Einspritzquerschnitt oder nur ein Teil des Einspritzquerschnitts aufgesteuert wird. Es ist eine Steuerung der Koaxial-Variodüse mittels nur eines einzigen Steuerventils möglich.The fuel injection valve according to the invention with the characterizing Features of claim 1, in contrast the advantage of having a single control valve Opening time and opening duration of both the outer and also the inner valve needle is controllable. For this purpose, the arranged in the housing of the fuel injection valve control valve a valve space in which a valve member is arranged is. The valve member is between two end positions movable, wherein the valve member in the first end position causes both the control room, as well as the control pressure chamber filled with fuel under high pressure, so that both the outer valve needle and the inner valve needle remain in their closed position. Moves the valve member fast in its second end position, so only the control chamber is relieved of pressure in the leakage oil chamber while the Control pressure chamber practically maintains its pressure. hereby only opens the outer valve needle, while the inner valve needle remains in its closed position. Both should Valve needles, so both the inner and the outer Valve needle are turned on, so the valve member moves slightly slower from its first to the second end position, which now also reduces the pressure in the control pressure chamber so far that in addition to the outer valve needle and the inner Valve needle opens. About the switching time of the control valve So it can be adjusted whether the entire injection cross section or only a part of the injection cross section opened becomes. It is a control of the coaxial Vario nozzle possible 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 lässt sich so mit unterschiedlicher Geschwindigkeit von der ersten Endposition in die zweite Endposition fahren, wobei sich durch die Schaltgeschwindigkeit der Einspritzquerschnitt einstellen lässt.In an advantageous embodiment of the subject of the Invention, the valve member is moved by an actuator, the is preferably electrically operated. Especially advantageous is the training of the actuator as a piezo actuator, since this the Virtue, with almost any speed to be switchable. The valve member moved by the actuator can be so with different speed of the drive first end position in the second end position, wherein itself by the switching speed of the injection cross section can be set.

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstandes der Erfindung sind der Beschreibung und der Zeichnung entnehmbar.Further advantages and advantageous embodiments of the subject The invention are the description and the Drawing removable.

Zeichnungdrawing

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

Figur 1
einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil,
Figur 2
eine Vergrößerung des mit II bezeichneten Ausschnitts von Figur 1,
Figur 3
eine Vergrößerung von Figur 1 im mit III bezeichneten Ausschnitt,
Figur 4
den Zeitverlauf von Druck, Nadelhub und Ventilgliedhub beim Aufsteuern nur der äußeren Ventilnadel und
Figur 5
den zeitlichen Verlauf von Ventilgliedhub, Druck und Nadelhub beim Aufsteuern beider Ventilnadeln.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a longitudinal section through a fuel injection valve according to the invention,
FIG. 2
an enlargement of the section of FIG. 1 denoted by II,
FIG. 3
an enlargement of FIG. 1 in the detail marked III,
FIG. 4
the time course of pressure, needle lift and Ventilgliedhub when controlling only the outer valve needle and
FIG. 5
the time course of Ventilgliedhub, pressure and needle stroke when controlling both valve pins.

Beschreibung des AusführungsbeispielsDescription of the embodiment

In Figur 1 ist ein Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das einen Haltekörper 14, einen Steuerkörper 12, eine Zwischenscheibe 9, einen Zwischenkörper 7 und einen Ventilkörper 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 Ventilkörper 3 ist eine Bohrung 16 ausgebildet, in der eine äußere Ventilnadel 20 längsverschiebbar angeordnet ist. Die äußere Ventilnadel 20 wird in einem brennraumabgewandten Abschnitt in der Bohrung 16 geführt und verjüngt sich dem Brennraum zu unter Bildung einer Druckschulter 27. Die äußere Ventilnadel 20 erstreckt sich bis zu einer am brennraumseitigen Ende der Bohrung 16 ausgebildeten Sitzfläche 24, in welcher mehrere Einspritzöffnungen 30 ausgebildet sind, die die Sitzfläche 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 Sitzfläche 24 bis zur Höhe der Druckschulter 27 reicht. Auf Höhe der Druckschulter 27 erweitert sich der Ringkanal 28 zu einem Druckraum 26, in den ein im Ventilkörper 3, dem Zwischenkörper 7, der Zwischenscheibe 9, dem Steuerkörper 12 und dem Ventilhaltekörper 14 verlaufender Zulaufkanal 10 mündet. 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 Längsbohrung 21 auf, in der eine innere Ventilnadel 22 längsverschiebbar angeordnet ist. Zur Verdeutlichung der Steuerung der Einspritzöffnungen 30 durch die Ventilnadeln 20, 22 zeigt Figur 2 den mit II bezeichneten Ausschnitt von Figur 1 vergrößert. Die Sitzfläche 24 ist konisch ausgebildet und die Einspritzöffnungen 30 gruppieren sich in zwei Einspritzöffnungsreihen, nämlich in eine äußere Einspritzöffnungsreihe 130 und in eine innere Einspritzöffnungsreihe 230. Die äußere Ventilnadel 20 weist an ihrem brennraumseitigen Ende eine konische äußere Ventildichtfläche 32 auf, so dass eine Dichtkante 34 gebildet wird, mit der die äußere Ventilnadel 20 in ihrer Schließstellung an der Sitzfläche 24 zur Anlage kommt. Die äußere Einspritzöffnungsreihe 130, die aus wenigstens zwei Einspritzöffnungen 30 besteht, die bezüglich der Längsachse der Bohrung 16 in einer Radialebene liegen, sind stromabwärts dieser Dichtkante 34 angeordnet. Die innere Ventilnadel 22 weist an ihrem brennraumseitigen Ende eine innere Ventildichtfläche 36 und eine Konusfläche 38 auf, wobei an deren Übergang eine Dichtkante 37 ausgebildet ist, mit der die innere Ventilnadel 22 an der Sitzfläche 24 in ihrer Schrießstellung anliegt. Die innere Einspritzöffnungsreihe 230, die ebenfalls aus wenigstens zwei Einspritzöffnungen besteht, die in einer gemeinsamen Radialebene zur Längsachse der Bohrung 16 angeordnet sind, münden stromabwärts der Dichtkante 37 der inneren Ventilnadel 22 in die Sitzfläche 24.In Figure 1 is a longitudinal section through an inventive Fuel injection valve shown. The fuel injector has a housing 1, which has a holding body 14, a control body 12, an intermediate disc 9, a Intermediate body 7 and a valve body 3 comprises, in abut each other in this order. The individual components of the housing 1 are by a clamping nut 5 against each other pressed and fixed in their position to each other. in the Valve body 3 is formed a bore 16 in which a outer valve needle 20 is arranged longitudinally displaceable. The outer valve needle 20 is in a combustion chamber facing away portion guided in the bore 16 and tapers the Combustion chamber to form a pressure shoulder 27. The outer Valve needle 20 extends to one on the combustion chamber side End of the bore 16 formed seat surface 24, in which a plurality of injection openings 30 are formed, the the seat 24 with the combustion chamber of the internal combustion engine connect. Between the outer valve needle 20 and the wall the bore 16 is an annular channel 28 is formed, of the Seat 24 extends to the height of the pressure shoulder 27. On Height of the pressure shoulder 27, the annular channel 28 widens a pressure chamber 26, in the one in the valve body 3, the intermediate body 7, the washer 9, the control body 12th and the valve holding body 14 extending inlet channel 10th empties. In the pressure chamber 26 and thus also in the annular channel 26 can fuel via the inlet channel 10 under high pressure be introduced. The outer valve needle 20 has a Longitudinal bore 21, in which an inner valve needle 22nd is arranged longitudinally displaceable. To clarify the Control of the injection openings 30 through the valve pins 20, 22, Figure 2 shows the designated II section of Figure 1 enlarged. The seat surface 24 is conical and the injection ports 30 are grouped in two Injection opening rows, namely in an outer row of injection openings 130 and in an inner injection port row 230. The outer valve needle 20 has at its combustion chamber side End of a conical outer valve sealing surface 32, so a sealing edge 34 is formed, with which the outer Valve needle 20 in its closed position on the seat surface 24th comes to the plant. The outer injection port row 130, the consists of at least two injection ports 30, with respect to the longitudinal axis of the bore 16 in a radial plane lie, downstream of this sealing edge 34 are arranged. The inner valve needle 22 has at its combustion chamber side End an inner valve sealing surface 36 and a conical surface 38, wherein at the transition, a sealing edge 37 is formed is, with the inner valve needle 22 on the seat 24 abuts in its Schrießstellung. The inner injection port series 230, which also consists of at least two injection ports exists in a common radial plane are arranged to the longitudinal axis of the bore 16, open downstream of the sealing edge 37 of the inner valve needle 22 in the seat 24.

Das Zusammenspiel der beiden Ventilnadeln 20, 22 zur Steuerung der Einspritzöffnungen 30 ist wie folgt: Soll nur durch die äußere Einspritzöffnungsreihe 130 Kraftstoff in den Brennraum der Brennkraftmaschine eingespritzt werden, was insbesondere dann von Vorteil ist, wenn die Brennkraftmaschine in einem Teillastbereich betrieben werden soll, so hebt zur Einspritzung nur die äußere Ventilnadel 20 von der Sitzfläche 24 ab. Dadurch kann Kraftstoff, der im Ringkanal 28 unter hohem Druck anliegt, zwischen der äußeren Ventildichtfläche 32 und der Sitzfläche 24 zur äußeren Einspritzöffnungsreihe 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 Sitzfläche 24, so dass die innere Einspritzöffnungsreihe 230 verschlossen bleibt. Soll durch sämtliche Einspritzöffnungen 30 eingespritzt werden, so hebt auch die innere Ventilnadel 22 von der Sitzfläche 24 ab, wodurch auch die innere Einspritzöffnungsreihe 230 freigegeben wird.The interaction of the two valve pins 20, 22 for control the injection openings 30 is as follows: Should only by the outer injection port row 130 fuel in the Combustion chamber of the internal combustion engine are injected, which is particularly advantageous if the internal combustion engine to be operated in a partial load range, so raises for injection only the outer valve needle 20 of the Seat 24 from. This can cause fuel in the annular channel 28 is under high pressure, between the outer valve sealing surface 32 and the seat surface 24 to the outer injection opening row 130 flow and from there into the combustion chamber the internal combustion engine injected. The inner valve needle 22 remains in its closed position, i. in Appendix on the seat 24, so that the inner row of injection openings 230 remains closed. Target through all injection openings Be injected, so also raises the inner Valve needle 22 from the seat 24 from, which also the inner injection port row 230 is released.

Zur Steuerung der beiden Ventilnadeln 20, 22 dienen die Vorrichtungen, die im Zwischenkörper 7, der Zwischenscheibe 9, dem Steuerkörper 12 und auch im Ventilhaltekörper 14 angeordnet sind. Dieser in Figur 1 mit III bezeichnete Ausschnitt ist in Figur 3 näher dargestellt. Im Zwischenkörper 7 ist koaxial zur Bohrung 16 eine Kolbenbohrung 45 ausgebildet, die im Durchmesser unter Bildung einer Anlagefläche 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 Längsrichtung bewegen kann. An der Außenseite des äußeren Druckkolbens 40 ist eine Ringfläche 39 angeordnet, zwischen der und der Anlagefläche 41 eine Schließfeder 44 unter Druckvorspannung angeordnet ist, die als Schraubendruckfeder ausgebildet ist und den äußeren Druckkolben 40 umgibt. Durch die Stirnfläche 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. Neben der Kraft der Schließfeder 44 wirkt also auf den äußeren 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.For controlling the two valve needles 20, 22 serve the devices, in the intermediate body 7, the intermediate disc 9, the control body 12 and also arranged in the valve holding body 14 are. This designated in Figure 1 with III section is shown in more detail in FIG. In the intermediate body 7 is coaxial with the bore 16, a piston bore 45 is formed, the diameter in the formation of a contact surface 41st is designed graduated. In the receiving bore 35 is a outer pressure piston 40 disposed on the outer valve needle 20 rests and synchronously with this in the longitudinal direction can move. On the outside of the outer pressure piston 40, an annular surface 39 is arranged between the and the contact surface 41 a closing spring 44 under compressive bias is arranged, which formed as a helical compression spring is and surrounds the outer pressure piston 40. By the End face 51 of the outer pressure piston 40, the intermediate disc 9 and the wall of the piston bore 45 becomes a control room 50 limits, via an inlet throttle 70 with the inlet channel 10 connected here as a high pressure room serves, in which always fuel under high pressure. In addition to the force of the closing spring 44 thus acts on the outer Pressure piston 40 and thus on the outer valve needle 20th the hydraulic force on the end face 51 through the Pressure in the control chamber 50 results is applied.

Der äußere Druckkolben 40 weist eine Führungsbohrung 47 auf, in der ein innerer Druckkolben 42 längsverschiebbar angeordnet ist. Der innere Druckkolben 42 liegt an der inneren Ventilnadel 22 an und bewegt sich stets synchron mit dieser. Durch die Führungsbohrung 47 und die Stirnfläche 53 des inneren Druckkolbens 42 ist ein Steuerdruckraum 52 begrenzt, durch dessen Druck sich eine hydraulische Kraftrauf den Druckkolben 42 und damit auch auf die innere Ventilnadel 22 in Richtung der Sitzfläche 24 ergibt.The outer pressure piston 40 has a guide bore 47, in which an inner pressure piston 42 is arranged longitudinally displaceable is. The inner pressure piston 42 is located on the inner valve needle 22 and always moves in sync with this. Through the guide bore 47 and the end face 53 of the inner Pressure piston 42 is a control pressure chamber 52 limited by the pressure of a hydraulic Kraftrauf the Pressure piston 42 and thus also on the inner valve needle 22nd in the direction of the seat 24 results.

Im Ventilhaltekörper 14 ist ein Aufnahmekörper 13 angeordnet, in welchem sich ein Aktor 46 und ein mit diesem verbundenes Druckstück 48 befindet. Durch den Aktor 46, der vorzugsweise als Piezo-Aktor ausgeführt ist, wird das Druckstück 48 in Längsrichtung entgegen oder in Richtung der Kraft einer Feder 49 bewegt, die zwischen dem Druckstück 48 und dem Aufnahmekörper 13 angeordnet ist. Das Druckstück 48 ist mit einem Ventilglied 60 verbunden, das in einem Ventilraum 68 angeordnet ist, welcher im Steuerkörper 12 ausgebildet ist und zusammen mit einem ersten Ventilsitz 62 und einem diesem gegenüberliegenden zweiten Ventilsitz 64 ein Steuerventil 58 bildet. Das Ventilglied 60 ist im wesentlichen als Halbkugel ausgebildet, wobei die halbkugelförmige Ventildichtfläche 66 mit dem ersten Ventilsitz 62 zusammenwirkt, während 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 Ventilhaltekörper 14 ausgebildeten Leckölraum 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 Ventilraum 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 Verbindungskanal 74 gesteuert, der eine Verbindung zwischen dem Ventilraum 68 und dem Steuerdruckraum 52 bildet. Der Verbindungskanal 74 reicht hierbei bis in den Zwischenkörper 7 und mündet seitlich in die Kolbenbohrung 45. Die Verbindung zum Steuerdruckraum 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 Kraftstoffstrom durch den Verbindungskanal 74 begrenzen kann und die bei Bedarf auch entfallen kann.In the valve holding body 14, a receiving body 13 is arranged, in which an actuator 46 and an associated with this Pressure piece 48 is located. By the actuator 46, preferably is designed as a piezo actuator, the pressure piece 48 in the longitudinal direction or in the direction of Force of a spring 49 moves between the pressure piece 48th and the receiving body 13 is arranged. The pressure piece 48 is connected to a valve member 60 which is in a valve chamber 68 is arranged, which formed in the control body 12 is and together with a first valve seat 62 and a this opposite second valve seat 64 a Control valve 58 forms. The valve member 60 is substantially formed as a hemisphere, the hemispherical Valve sealing surface 66 cooperates with the first valve seat 62, while the flat side of the valve member 60 with the second valve seat 64 cooperates, which formed as a flat seat is. The valve space 68 has a connection 59 a leakage oil space 78 formed in the valve holding body 14 on, wherein the connection 59 through the valve member 60 through its interaction with the first valve seat 62 is opened and can be closed. In addition, the valve chamber points 68, an outlet throttle 72, the valve space 68th connects to the control room 50. The outlet throttle 72 remains always open, regardless of the position of the valve member 60. By the interaction of the valve member 60 with the second valve seat 64 is controlled a connection channel 74, the connection between the valve chamber 68 and forms the control pressure chamber 52. The connection channel 74 This extends into the intermediate body 7 and opens laterally in the piston bore 45. The connection to the control pressure chamber 52 is via a transverse bore 55 in the outer pressure piston 40 produced. This connection of the control pressure chamber 52 to the connection channel 74 remains at each position of the outer Pressure piston 40 received. In the connection channel 74 is a throttle point 76 is provided which the possible fuel flow can limit through the connecting channel 74 and which can 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 Leckölraum 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 Zulaufdrossel 70 herrscht im Steuerraum 50 der Einspritzdruck P0, der auch im Hochdruckkanal 10 herrscht. Derselbe Druck P0 ist aufgrund der offenen Verbindungen natürlich auch im Steuerdruckraum 52 vorhanden. Soll nur durch die äußere Einspritzöffnungsreihe 130 Kraftstoff eingespritzt werden, so schaltet der Aktor 46 über das Druckstück 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 Leckölraum 78 geöffnet und der Verbindungskanal 74 verschlossen. Da dieser Schaltvorgang sehr schnell geschieht, fällt der Druck im Steuerdruckraum 52 nur unwesentlich ab. Durch die jetzt vorhandene Verbindung des Ventilraums 68 zum Leckölraum 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 über die Zulaufdrossel 70 aus dem Hochdruckkanal 10 nachfließen kann. Hierdurch erniedrigt sich die hydraulische Kraft auf die Stirnfläche 51 des äußeren Druckkolbens 40, so dass die auf die Druckschulter 27 wirkenden hydraulischen Kräfte im Druckraum 26 die äußere Ventilnadel 20 von der Sitzfläche 24 abhebt, so dass die äußere Einspritzöffnungsreihe 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 bezüglich des inneren Ventilkolbens 42, der ortsfest bleibt, vergrößert sich zwar das Volumen des Steuerdruckraums 52 geringfügig, jedoch fällt 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 is closed to the leakage oil chamber 78. The connecting channel 74 and the outlet throttle 72 are opened, so that the control pressure chamber 52 and the control chamber 50 are hydraulically connected to the valve chamber 68. By the inlet throttle 70 prevails in the control chamber 50 of the injection pressure P 0 , which also prevails in the high-pressure passage 10. Of course, the same pressure P 0 is 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 via the pressure member 48, the valve member 60 very quickly from the first valve seat 62 in abutment against the second valve seat 64. Thus, the connection of the valve chamber 68 is opened to the leakage oil chamber 78 and the Connecting channel 74 closed. Since this switching process happens very quickly, the pressure in the control pressure chamber 52 drops only insignificantly. Due to the now existing connection of the valve chamber 68 to the leakage oil chamber 78, in which there is always a very low fuel pressure, the pressure in the pressure chamber 50 decreases, since the inlet throttle 70 and the outlet throttle 72 are coordinated so that more fuel from the. Through the outlet throttle 72 Control chamber 50 drains as can flow on the inlet throttle 70 from the high-pressure passage 10. As a result, the hydraulic force on the end face 51 of the outer pressure piston 40 is lowered, so that acting on the pressure shoulder 27 hydraulic forces in the pressure chamber 26, the outer valve needle 20 lifts from the seat surface 24, so that the outer injection opening row 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 to rest on the washer 9. Although the volume of the control pressure chamber 52 increases slightly due to the movement of the outer valve piston with respect to the inner valve piston 42, which remains stationary, the pressure in the control pressure chamber does not substantially decrease due to the large volume of control pressure chamber 52 and connection channel 74.

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 t0 einsetzt und die zum Zeitpunkt t1 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 p0 bis zu einem Druckniveau, das oberhalb des Drucks p1 liegt, wobei der Druck p1 den Druck bezeichnet, bei dem die innere Ventilnadel 22, angetrieben durch die hydraulische Kraft auf die innere Ventildichtfläche 36, von der Sitzfläche 24 abhebt. Die äußere Ventilnadel 20, deren Hub h im unteren Diagramm der Figur 4 dargestellt ist, beginnt ihre Bewegung kurz nach dem Zeitpunkt t0 und setzt die Bewegung fort, bis sie ihren Maximalhub erreicht hat. Zum Zeitpunkt t2 schaltet das Steuerventil 58 erneut und das Ventilglied 60 erreicht zum Zeitpunkt t3 wieder seine Ausgangsposition am ersten Ventilsitz 62. Der Steuerraum 50 befüllt 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 p0 auf. Durch den ansteigenden Druck im Steuerraum 50 wird die äußere Ventilnadel 20 zurück in ihre Schließstellung gedrückt.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 Figure 4. The upper diagram of Figure 4 shows the movement of the valve member 60, which begins at a time t 0 and which comes at time t 1 at the second valve seat 64 for conditioning. The middle graph shows the pressure p in the control pressure chamber 52 again, and there is a pressure drop from the injection pressure p 0 to a pressure level that is above the pressure p 1 , wherein the pressure p 1 denotes the pressure at which the inner valve needle 22nd driven by the hydraulic force on the inner valve sealing surface 36 lifts off from the seat surface 24. The outer valve needle 20, the stroke h is shown in the lower diagram of Figure 4, begins their movement shortly after the time t 0 and continues the movement until it has reached its maximum stroke. At time t 2 , the control valve 58 switches again and the valve member 60 reaches its original position at the first valve seat 62 at time t 3. The control chamber 50 fills via the inlet throttle 70 with the injection pressure of the high-pressure passage 10 and via the connecting channel 74 also builds up in the Control pressure chamber 52 back to the pressure p 0 . Due to the increasing pressure in the control chamber 50, the outer valve needle 20 is pushed back into its closed position.

Soll durch sämtliche Einspritzöffnungen 30 eingespritzt werden, so schaltet das Steuerventil 58 langsamer als bei der eben geschilderten Einspritzung durch die äußere Einspritzöffnungsreihe 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 Leckölraum 78 geöffnet, so dass der Druck im Steuerdruckraum 52 unter den Öffnungsdruck der inneren Ventilnadel 22, den Druck p1, abfällt. Dadurch bewegt sich in der oben beschriebenen Art und Weise der äußere Druckkolben 40 und auch der innere Druckkolben 42, so dass sowohl die äußere Ventilnadel 20 als auch die innere Ventilnadel 22 von der Sitzfläche 24 abheben und sämtliche Einspritzöffnungen 30 freigeben. In Figur 5 ist in der selben Art und Weise wie in Figur 4 der zeitliche Verlauf der maßgebenden Größen 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 p1, so dass die innere Ventilnadel 22 ihre Hubbewegung zum Zeitpunkt t1 beginnt. Dies ist im unteren Diagramm der Figur 5 durch die gestrichelte Linie dargestellt. Das Schließen des Kraftstoffeinspritzventil erfolgt analog zum Teillastbereich durch den Wiederaufbau des Drucks im Steuerraum 50 und im Steuerdruckraum 52.To be injected through all the injection ports 30, the control valve 58 switches more slowly than in the just described injection through the outer injection opening 130. The relatively slow movement of the valve member 60 remains for a certain time when the valve member 60 between the first valve seat 62 and the second valve seat 64 is open, both the connecting channel 74 and the connection to the leakage oil chamber 78, so that the pressure in the control pressure chamber 52 below the opening pressure of the inner valve needle 22, the pressure p 1 , drops. Thereby moves in the manner described above, the outer pressure piston 40 and also the inner pressure piston 42, so that both the outer valve needle 20 and the inner valve needle 22 lift off from the seat surface 24 and release all the injection ports 30. In FIG. 5, the time course of the governing quantities is shown in the same manner as in FIG. The upper diagram of FIG. 5 shows the slower course of the movement of the valve member 60, wherein the movement back to the starting position on the first valve seat 62 can take place at the same speed as in the partial load injection. The pressure curve of the pressure p in the control pressure chamber 52 shows a drop in pressure below the pressure p 1 , so that the inner valve needle 22 begins its stroke movement at the time t 1 . This is shown in the lower diagram of Figure 5 by the dashed line. The closing of the fuel injection valve is analogous to the partial load range by the reconstruction of the pressure in the control chamber 50 and the control pressure chamber 52nd

Als Aktor 46 eignet sich vorzugsweise ein Piezo-Aktor, der einen Hub abhängig von der angelegten Spannung ausführt. Durch eine einfache Spannungsregelung lässt 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 Magnetaktoren, deren Schaltgeschwindigkeit abhängig von der Magnetfeldstärke gesteuert werden kann.As actuator 46 is preferably a piezoelectric actuator, the performs a stroke depending on the applied voltage. With a simple voltage regulation it is almost possible each time course in the movement of the valve member 60th realize. In addition to a piezo actuator also other actuators come for example, fast-switching magnetic actuators, their switching speed depends on the magnetic field strength can be controlled.

Claims (7)

  1. Fuel injection valve for internal combustion engines having a housing (1), in which a longitudinally displaceable outer valve needle (20) and an inner valve needle (22) which can be longitudinally displaced in the latter are arranged in a bore (16), which needles each control at least one injection opening (30) with their combustion space end, and having a control space (50) which is connected via an inflow throttle (70) to a high-pressure space (10) and by means of whose pressure a closing force is exerted at least indirectly on the outer valve needle (20), and having a control-pressure space (52) by means of whose pressure a closing force is exerted at least indirectly on the inner valve needle (22), and having a leakage oil space (78) in which there always prevails a low fuel pressure, characterized in that a control valve (58) which has a valve space (68) and a valve member (60) arranged therein is arranged in the housing (1), the valve space (68) having a connection (59) to the leakage oil space (78), a continuously open connection (72) to the control space (50) and a connection (74) to the control-pressure space (52), the valve member (60) being able to move in the valve space (68) between two end positions and, in the first end position, closing the connection (59) to the leakage oil space (78) and opening the connection (74) to the control-pressure space (52) and, in the second end position, closing the connection (74) to the control-pressure space (52) and opening the connection (59) to the leakage oil space (78).
  2. Fuel injection valve according to Claim 1, characterized in that less fuel flows into the control space (50) via the inflow throttle (70) than flows out of the control space (50) into the leakage oil space (78) via an outflow throttle (72) for a corresponding position of the control valve (58).
  3. Fuel injection valve according to Claim 1, characterized in that the valve member (60) is moved by an actuator (46).
  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 into the second end position.
  5. Fuel injection valve according to Claim 3 or 4, characterized in that the actuator (46) is a piezo actuator.
  6. Fuel injection valve according to Claim 1, characterized in that all the connections (59; 74; 72) to the valve space (68) are open when the valve member (60) is situated between the first end position and the second end position.
  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 at such a speed that the pressure in the control-pressure space (52) decreases only insignificantly in the process.
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 EP1507972A1 (en) 2005-02-23
EP1507972B1 true EP1507972B1 (en) 2005-12-28

Family

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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
ATE493577T1 (en) * 2004-12-03 2011-01-15 Ganser Hydromag FUEL INJECTION VALVE WITH PRESSURE BOOST
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
DE102007011611B4 (en) * 2007-01-22 2010-12-09 Airbus Deutschland Gmbh Fixing arrangement for lashing strap in a cargo hold floor 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
EP2674608B1 (en) * 2012-06-13 2015-08-12 Delphi International Operations Luxembourg S.à r.l. 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
US11970977B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of a secondary circuit of a fuel injector
US11913382B1 (en) 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Variable restriction of a fuel circuit of a fuel nozzle
US11970976B2 (en) 2022-08-26 2024-04-30 Hamilton Sundstrand Corporation Variable restriction of fuel nozzle with an auxiliary circuit
US11913381B1 (en) * 2022-08-26 2024-02-27 Hamilton Sundstrand Corporation Force modification of passive spool for control of secondary nozzle circuits

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003069151A1 (en) * 2002-02-14 2003-08-21 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Family Cites Families (8)

* 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

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003069151A1 (en) * 2002-02-14 2003-08-21 Robert Bosch Gmbh Fuel injection valve for internal combustion engines

Also Published As

Publication number Publication date
DE50302074D1 (en) 2006-02-02
EP1507972A1 (en) 2005-02-23
US20050224598A1 (en) 2005-10-13
JP2005526211A (en) 2005-09-02
WO2003098028A1 (en) 2003-11-27
US7021567B2 (en) 2006-04-04
DE10222196A1 (en) 2003-11-27

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