EP1714026B1 - Fuel-injection valve - Google Patents

Fuel-injection valve Download PDF

Info

Publication number
EP1714026B1
EP1714026B1 EP04791347A EP04791347A EP1714026B1 EP 1714026 B1 EP1714026 B1 EP 1714026B1 EP 04791347 A EP04791347 A EP 04791347A EP 04791347 A EP04791347 A EP 04791347A EP 1714026 B1 EP1714026 B1 EP 1714026B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
coupler
spring element
valve according
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 - Fee Related
Application number
EP04791347A
Other languages
German (de)
French (fr)
Other versions
EP1714026A1 (en
Inventor
Klaus Noller
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 EP1714026A1 publication Critical patent/EP1714026A1/en
Application granted granted Critical
Publication of EP1714026B1 publication Critical patent/EP1714026B1/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • F02M61/167—Means for compensating clearance or thermal expansion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/0603—Injectors peculiar thereto with means directly operating the valve needle using piezoelectric or magnetostrictive operating means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/70—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger
    • F02M2200/703—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves opening in direction of fuel flow

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • a slave piston In the master cylinder, a slave piston is guided, which also closes the master cylinder and thereby forms the hydraulic chamber.
  • a spring In the hydraulic chamber, a spring is arranged, which presses apart the master cylinder and the slave piston.
  • this stroke movement is due to the pressure of a hydraulic fluid in the hydraulic chamber on the Transfer slave piston, since the hydraulic fluid in the hydraulic chamber can not be compressed and only a small proportion of the hydraulic fluid can escape through the annular gap during the short period of a stroke.
  • the slave piston In the resting phase, when the actuator exerts no pressure force on the master cylinder, the slave piston is pushed out of the cylinder by the spring and by the resulting negative pressure penetrates through the annular gap, the hydraulic fluid in the hydraulic chamber and fills it again.
  • the hydraulic coupler automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve.
  • the sealing of the hydraulic medium takes place via sealing rings.
  • fuel injectors are known from the prior art, which seal by flexible portions, for example in corrugated or bellows-like design, hydraulic medium and exert a bias on the hydraulic medium by an elastic design of the flexible portion.
  • a disadvantage of this known state of the art is that the bias exerted by the flexible portion unfavorably changes during the life of the fuel injector, the coupler constructed consuming and can be prepared by many items of the coupler only with high production costs.
  • the DE 197 08 304 A1 discloses an apparatus for transmitting motion from an actuator to an actuator having a pressure chamber at least partially filled with a transmission medium, and which is at least partially bounded by a first flexible element, with a compensation chamber, which is connected via a connection with the pressure chamber, wherein the connection and the transmission medium are designed such that short-term pressure differences between the pressure in the pressure chamber and the pressure in the compensation chamber hardly and temporally long-lasting pressure differences are completely compensated.
  • a transmission module is used in a common housing.
  • the pressure chamber and the compensation chamber are introduced in the transmission module and the compensation chamber is in operative connection with means which predetermine the pressure in the compensation chamber.
  • the fuel injection valve according to the invention with the characterizing features of the independent claims has the advantage that the internal pressures of the coupler are always reliably achieved at different load conditions of the coupler, the coupler simple and inexpensive to produce, less expensive and reliably reliable running.
  • the flexible section has an axial section running axially with respect to the axis of movement of the pistons and a radial section extending radially with respect to the axis of movement of the piston.
  • the flexible portion can be advantageously integrated into the coupler, so that the mechanical loads are minimized and the assembly is facilitated. This is also achieved by a sleeve-shaped and / or plate-shaped design of the flexible portion.
  • the flexible portion is elastic and consists for example of an elastomer. This allows the flexible section to be stretched while remaining tight against the commercial fuels.
  • the spring element is formed spirally.
  • the spring element can thereby be produced inexpensively and integrate in a particularly simple and space-saving manner in the coupler.
  • a first embodiment according to the invention shows that the spring element is supported on the master piston, in particular via a sleeve-shaped holder immovably connected to the master piston, and advantageously acts on the flexible section via an intermediate ring.
  • the coupler can be advantageously constructed simply and the pressure curve in the coupler are additionally influenced by the spring element is additionally stretched by an enlargement of the coupler volume by the relative movement of the two pistons.
  • the spring element acts via a sleeve ring, which has a plate-shaped radial course and outside has a sleeve-shaped axial course, on the flexible portion.
  • the coupler can be advantageously constructed simply and the pressure curve in the coupler are additionally influenced by the spring element is relaxed at an increase in the coupler volume by the relative movement of the two pistons.
  • a second embodiment of the invention provides an annular design of the spring element, whereby the size and the production cost can be further reduced.
  • the annular spring element can be constructed by open, overlapping ends. By rounding off the ends of the annular spring element, the flexible section is mechanically protected, in particular during assembly.
  • the throttle comprises a throttle ball, which is guided with a throttle gap in an opening
  • the throttle can be constructed in a particularly simple manner and, if the throttle ball is supported on a surface bounding the coupler volume of the master piston, be advantageously used for the function of the coupler.
  • fuel injection valve 1 is designed in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression, spark-ignition internal combustion engines.
  • the fuel injection valve 1 is suitable in particular for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel injection valve 1 comprises a housing 2, in which a provided with an Aktorumspritzung 3 piezoelectric or magnetostrictive actuator 4 is arranged.
  • the actuator 4 can be supplied by means of an electrical line 5, to which a protruding from the housing 2 electrical terminal 6, an electrical voltage can be supplied.
  • the actuator 4 is supported on the inflow side on a master piston 9 of a hydraulic coupler 7 and downstream of an actuator head 8.
  • the hydraulic coupler 7 further comprises a slave piston 10, a compression spring 11, which biases the hydraulic coupler 7, and a compensation chamber 12, which is filled with a hydraulic medium.
  • the fuel is fed centrally via an inlet 14.
  • an actuating body 15 Downstream of the actuator head 8, an actuating body 15 is arranged, which acts on a valve needle 16.
  • the valve needle 16 has at its downstream end a valve closing body 17. This acts together with a valve seat surface 18, which is formed on a nozzle body 19, to form a sealing seat.
  • a return spring 20 acts on the valve needle 16 so that the fuel injection valve 1 remains in the de-energized state of the actuator 4 in the closed state. Furthermore, it ensures the return of the valve needle 16 after the injection phase.
  • the nozzle body 19 is fixed by means of a weld 21 in an inner housing 22, which seals the actuator 4 against the fuel.
  • the fuel flows from the inlet 14 between the housing 2 and the inner housing 22 to the sealing seat.
  • Fig. 2 shows a similar to the one in Fig. 1 shown constructed coupler. 7
  • Hydraulic couplers 7 in fuel injection valves 1 are usually designed on the one hand for conversion or translation of the stroke of the actuator 4 on the valve needle 16 and / or on the other hand to compensate for temperature-induced changes in length of the actuator 4 and the housing 2.
  • the latter is realized, as shown in the exemplary embodiment, by means of the coupler 7 designed as a second medium coupler, which contains a hydraulic medium not coming into contact with the fuel.
  • the hydraulic medium fills the compensation chamber 12 and a coupler volume 23 formed between master piston 9 and slave piston 10, which is connected to the compensation chamber 12 via a throttle 24.
  • the compensation chamber 12 is disposed inside and outside the slave piston 10, wherein the two parts are connected by a transverse bore 31 and the outboard part of the compensation chamber 12 is sealed by means of a corrugated tube seal designed as flexible portion 13 relative to the fuel injector 1 flowing through the fuel.
  • hydraulic medium is exchanged between the coupler volume 23 via the throttle 24 with the compensation chamber 12.
  • the necessary filling pressure is applied via the pressure piston 11 arranged in the slave piston 10 in a pressure storage chamber 32.
  • This is arranged between a first closure body 25 and a second closure body 26, the former having a groove 27 with a sealing ring 28 arranged therein for sealing the coupler space 12.
  • the filling of the coupler 7, for example in the production, with hydraulic medium takes place through a channel 29, which may be closed, for example by means of a pressed-in closure ball 30.
  • Fig. 3 shows an embodiment, which is not part of the invention, a coupler 7 for a Fuel injector 1.
  • the slave piston 10 engages with a cup-shaped first slave portion 34 in the hollow-cylindrical master piston 9 closed on one side.
  • the slave piston 10 or the first slave section 34 is axially movably guided in the master piston 9 with a guide gap 38.
  • the guide gap 38 is relatively small, wherein the amount of hydraulic medium flowing through the guide gap 38 is very small. In other embodiments, the guide gap 38 may exert a throttle function.
  • the slave piston 10 of the first slave portion 34 and a second slave portion 35 defines with its closed end together with the bottom of the master piston 9, the coupler volume 23, wherein centered in the closed end of the first slave section 34, the throttle 24th is arranged.
  • the throttle 24 consists of an opening 36 centered in the bottom of the cup-shaped first slave section 24 and a throttle ball 39 guided therein with a throttle gap 37.
  • the open, the coupler volume 23 facing away from the end of the first slave section 34 is closed by the second slave section 35.
  • the second slave section 35 engages partially in the first slave section 34, tapers and is joined in the upper region of the first slave section 34, for example by pressing or welding with this movement.
  • the compression spring 11 is arranged with a bias in a arranged in the first slave section 34 spring chamber 45, the tapered portion of the second slave section 35 partially engages the helical compression spring 11 ,
  • the compression spring 11 presses on the throttle ball 39 with the interposition of a cup-shaped intermediate element 40, wherein the throttle ball 39 at the bottom of the master piston 9 in Coupler volume 23 is supported.
  • the intermediate element 40 may have holes, not shown, for the passage of fuel.
  • the upper, the coupler volume 23 facing away from the ends of the first slave section 34 and the master piston 9 are approximately at the same height.
  • the second slave section 35 has first a first flange 46 and then a second flange 47 and at the upper end a third flange 48.
  • All three flanges 46, 47 and 48 have approximately the same diameter.
  • the second slave section 35 is designed in two parts, wherein the first flange 46 at the lower and the second and third flange 47, 48 are arranged at the upper part. Both parts are immovable connected.
  • the first flange 46 rests on the upper end of the first slave section 34 with its lower side facing the first slave section 34.
  • the first flange 46 has approximately the diameter of the first slave section 34.
  • the compensation chamber 12 is limited by the flexible portion 13, the second slave portion 35 with its first flange 46 and the master piston 9, wherein the compensation chamber 12 via the transverse bore 31 and the spring chamber 45 communicates with the throttle 24.
  • the transverse bore 31 is arranged between the first flange 46 and the first slave section 34.
  • the channel 29 with the closure ball 30 is realized coaxially in the second slave section 35 through a bore which opens into the spring chamber 45.
  • the flexible portion 13 is elastic and is made of, for example, an elastomer or steel.
  • the flexible section 13 is divided into an axial section 51 extending axially relative to the direction of movement of the slave piston 10 and a radial section 52 extending radially with respect to the direction of movement of the slave piston 10.
  • the thereby plate and sleeve-shaped designed flexible portion 13 is thickened at its ends and arranged coaxially with the pistons 9, 10.
  • the flexible portion 13 is, for example frictionally joined by pressure, with the upper end or with the region of its inner periphery of the plate-shaped portion in a trough-shaped and annular first recess 42 which is formed between the first flange 46 and the second flange 47. With its lower end of the flexible portion 13 is located in a trough-shaped and annular groove-shaped second recess 43, which is arranged in the outer surface in the region of the upper end of the master piston 9.
  • the axial extent of the second recess 43 is in each case slightly larger than the axial extent of the lower thickened end of the flexible portion 13. As a result, in particular the assembly is facilitated.
  • a sleeve-shaped holder 41 includes an exact fit the upper half of the master piston 9 and part of the first slave section 34 beyond the upper part of the second slave section 35.
  • the holder 41 is immovably joined to the master piston 9, for example, material and / or non-positively by welding and / or pressing.
  • Above the flexible portion 13, the holder 41 tapers.
  • the axial portion 51 of the flexible portion 13 is axially outwardly supported on the holder 41 in this embodiment, so that the holder 41 limits the radial movement of the axial portion 51 to the outside.
  • a disposed between the second flange 47 and the third flange 48 spring element 33 is supported on the third flange 48 and exerts from the outside via a hole-and sleeve-shaped sleeve ring 50, which with its sleeve-shaped portion the second flange 47 comprises radially, a pressure on the flexible portion 13 and the axial portion 51 from.
  • the sleeve ring 50 is shaped similarly to the flexible portion 13 and its surfaces in contact with the flexible portion 13 are rounded.
  • the coupler volume 23 magnifying pressure is exerted on the hydraulic medium, so that in an externally unloaded coupler 7, the compression spring 11, the coupler volume 23 increases to a maximum value, which is limited, for example, characterized in that the intermediate element 40 the Throttle ball 39 presses down and touches on the bottom of the first slave section 34.
  • the spring element 33 is for example dimensioned so that at maximum coupler volume 23, the spring element 33 exerts no pressure on the flexible portion 13, so that the sleeve ring 50 rests only almost without pressure on the axial portion 51 and the spring element 33 is not tensioned.
  • the dynamic stiffness of the coupler 7 is determined in particular by the size and shape of the throttle gap 37 and possibly by the size and shape of the guide gap 38.
  • Fig. 4 shows a first embodiment of a fuel injection valve according to the invention in the region of the coupler 7, similar to the previous embodiment Fig. 3 , Deviating from the embodiment Fig. 3 the spring element 33 is supported on a retraction 49 fixedly mounted on the holder 41 and presses on the flexible section 13 via an intermediate ring 44.
  • the intermediate ring 44 presses, with rounded surfaces in this exemplary embodiment, on the transition between the axial section 51 and the radial section 52.
  • the holder 41 extends, without tapering, from the outer surface of the master piston 9 to the level of the upper end of the slave piston 10 and the second slave section 34 or the third flange 48, where it tapers as a retraction 49 in the radial direction.
  • the intermediate ring 44 is guided axially movable in the sleeve-shaped holder 41 approximately at the level of the second flange 47.
  • the second flange 47 has a diameter beyond the first and third flanges 46, 48 so that there is little play between the second flange 47 and the intermediate ring 44 radially.
  • the transverse bore 31 is not shown.
  • Fig. 5 shows an embodiment of an annular spring element 33, as in the second and third embodiments in Fig. 6 is used.
  • the spring element 33 is made of spring steel and is annular.
  • the ring shape has two ends, so it is not closed, with the areas of the ends overlap and run tangentially outward from the area where the ends intersect or overlap.
  • Fig. 6 shows a second and third embodiment of the coupler 7 of the fuel injection valve 1 according to the invention.
  • the third embodiment which is shown on the left, is similar to the first and second embodiments of the invention constructed.
  • the spring element 33 is, as in Fig. 5 shown, annular and extends around the axial portion 51 of the flexible portion 13.
  • the third embodiment shows the coupler 7 in the unloaded state. In the unloaded state of the coupler 7, the spring element 33 presses with a bias on the axial portion 51, so that the axial portion 51 in the region of the point at which the spring element 33 rests, is pressed slightly inward and thus reduces the compensation chamber 12.
  • the axial portion 51 may also be plastically preformed according to the shape just described, wherein the spring element 33 only almost depressurized rests in the plastically indented form and a voltage of the spring element 33 only when pressurized from the inside by the hydraulic medium at axial load of the coupler 7 sets.
  • the second flange 47 completely covers the upper side of the radial section 52 and the region of the transition from the radial section 52 to the axial section 51, thus continuing axially downward.
  • the holder 41 extends axially approximately from the center of the height of the master piston 9 to above the height of the thickened running end of the axial portion 51.
  • the transverse bore 31 is not shown.
  • the third embodiment of the invention shown on the right is constructed similarly to the second embodiment.
  • the flexible portion 13 is sleeve-shaped and thus has only the axial portion 51.
  • the flexible portion 13 with its thickened end between the second flange 47 and the first flange 46, which in this embodiment approximately assume the diameter of the master piston 9 and thereby form the trough-shaped and annular groove-shaped first recess 42, respectively.
  • the sleeve-shaped holder 41 is made in two parts, wherein the upper part of the upper, thickened end of the flexible portion 13 and the lower part comprises the lower thickened end of the flexible portion 13, so that both parts hermetically sealed and non-positively movement in the recesses 42, 43 are pressed.
  • the third flange 48 is not formed and the transverse bore 31 is not shown.
  • the invention is not limited to the illustrated embodiments and for any designs of fuel injection valves 1, in particular also for fuel injection valves 1 for self-igniting internal combustion engines and / or inwardly opening fuel injection valves suitable.
  • the features of the embodiments can be combined with each other.

Abstract

The invention relates to a fuel-injection valve comprising a piezoelectric or magnetostrictive actuator (4), which activates a valve closing body (17) that co-operates with a valve seat surface (18) to form a seal seat. A hydraulic coupler (7) comprises a master piston (9), a slave piston (10) and a coupler volume (23) that is configured between the two pistons. The master piston (9) and the slave piston (10) are axially displaceable in relation to one another. The coupler volume (23) is connected to a compensation chamber (12) via a throttle (24). A flexible section (13) at least partially delimits the compensation chamber (12) and the coupler volume (23), the throttle (24) and the compensation chamber (12) are filled with a hydraulic medium. The flexible section (13) is impinged by an external pressure under the action of a spring element (33) either directly or indirectly by means of fixed components.

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs.The invention relates to a fuel injection valve according to the preamble of the main claim.

Aus der EP 0 477 400 A1 ist eine Anordnung für einen in Hubrichtung wirkenden, adaptiven mechanischen Toleranzausgleich für einen Wegtransformator eines piezoelektrischen Aktors für ein Brennstoffeinspritzventil bekannt. Dabei wird der Hub des Aktors über eine Hydraulikkammer übertragen. Die Hydraulikkammer weist ein definiertes Leck mit einer definierten Leckrate auf. Der Hub des Aktors wird über einen Geberkolben in die Hydraulikkammer eingeleitet und über einen Nehmerkolben auf ein anzutreibendes Element übertragen. Dieses Element ist beispielsweise eine Ventilnadel eines Brennstoffeinspritzventils.From the EP 0 477 400 A1 an arrangement for an acting in the stroke direction, adaptive mechanical tolerance compensation for a path transformer of a piezoelectric actuator for a fuel injection valve is known. The stroke of the actuator is transmitted via a hydraulic chamber. The hydraulic chamber has a defined leak with a defined leak rate. The stroke of the actuator is introduced via a master piston in the hydraulic chamber and transmitted via a slave piston to a driven element. This element is for example a valve needle of a fuel injection valve.

Im Geberzylinder ist ein Nehmerkolben geführt, der den Geberzylinder ebenfalls abschließt und hierdurch die Hydraulikkammer bildet. In der Hydraulikkammer ist eine Feder angeordnet, die den Geberzylinder und den Nehmerkolben auseinanderdrückt. Wenn der Aktor auf den Geberzylinder eine Hubbewegung überträgt, wird diese Hubbewegung durch den Druck eines Hydraulikfluids in der Hydraulikkammer auf den Nehmerkolben übertragen, da das Hydraulikfluid in der Hydraulikkammer sich nicht zusammenpressen lässt und nur ein geringer Anteil des Hydraulikfluids durch den Ringspalt während des kurzen Zeitraumes eines Hubes entweichen kann. In der Ruhephase, wenn der Aktor keine Druckkraft auf den Geberzylinder ausübt, wird durch die Feder der Nehmerkolben aus dem Zylinder herausgedrückt und durch den entstehenden Unterdruck dringt über den Ringspalt das Hydraulikfluid in den Hydraulikraum ein und füllt diesen wieder auf. Dadurch stellt sich der hydraulische Koppler automatisch auf Längenausdehnungen und druckbedingte Dehnungen eines Brennstoffeinspritzventils ein. Die Abdichtung des Hydraulikmediums erfolgt über Dichtringe.In the master cylinder, a slave piston is guided, which also closes the master cylinder and thereby forms the hydraulic chamber. In the hydraulic chamber, a spring is arranged, which presses apart the master cylinder and the slave piston. When the actuator transmits to the master cylinder a lifting movement, this stroke movement is due to the pressure of a hydraulic fluid in the hydraulic chamber on the Transfer slave piston, since the hydraulic fluid in the hydraulic chamber can not be compressed and only a small proportion of the hydraulic fluid can escape through the annular gap during the short period of a stroke. In the resting phase, when the actuator exerts no pressure force on the master cylinder, the slave piston is pushed out of the cylinder by the spring and by the resulting negative pressure penetrates through the annular gap, the hydraulic fluid in the hydraulic chamber and fills it again. As a result, the hydraulic coupler automatically adjusts to length expansions and pressure-related expansions of a fuel injection valve. The sealing of the hydraulic medium takes place via sealing rings.

Aus dem Stand der Technik sind außerdem Brennstoffeinspritzventile bekannt, die durch flexible Abschnitte, beispielsweise in wellrohr- bzw. wellbalgförmiger Ausführung, Hydraulikmedium abdichten und durch eine elastische Ausführung des flexiblen Abschnitts eine Vorspannung auf das Hydraulikmedium ausüben.In addition, fuel injectors are known from the prior art, which seal by flexible portions, for example in corrugated or bellows-like design, hydraulic medium and exert a bias on the hydraulic medium by an elastic design of the flexible portion.

Nachteilig an diesem bekannten Stand der Technik ist, dass sich die durch den flexiblen Abschnitt ausgeübte Vorspannung während der Lebensdauer des Brennstoffeinspritzventils unvorteilhaft ändert, der Koppler aufwendig aufgebaut und durch viele Einzelteile der Koppler nur mit hohen Herstellungskosten hergestellt werden kann.A disadvantage of this known state of the art is that the bias exerted by the flexible portion unfavorably changes during the life of the fuel injector, the coupler constructed consuming and can be prepared by many items of the coupler only with high production costs.

Die DE 197 08 304 A1 offenbart eine Vorrichtung zur Übertragung einer Bewegung von einem Aktor auf ein Stellglied mit einer Druckkammer, die mit einem Übertragungsmedium mindestens teilweise gefüllt ist, und die mindestens teilweise von einem ersten flexiblen Element begrenzt ist, mit einer Ausgleichskammer, die über eine Verbindung mit der Druckkammer verbunden ist, wobei die Verbindung und das Übertragungsmedium derart ausgebildet sind, dass kurzzeitige Druckunterschiede zwischen dem Druck in der Druckkammer und dem Druck in der Ausgleichskammer kaum und zeitlich lang anhaltende Druckunterschiede vollständig ausgeglichen werden. Zwischen den Aktor und das Stellglied ist ein Übertragungsmodul in ein gemeinsames Gehäuse einsetzbar. Die Druckkammer und die Ausgleichskammer sind in dem Übertragungsmodul eingebracht und die Ausgleichskammer steht mit Mitteln in Wirkverbindung, die den Druck in der Ausgleichskammer vorgeben.The DE 197 08 304 A1 discloses an apparatus for transmitting motion from an actuator to an actuator having a pressure chamber at least partially filled with a transmission medium, and which is at least partially bounded by a first flexible element, with a compensation chamber, which is connected via a connection with the pressure chamber, wherein the connection and the transmission medium are designed such that short-term pressure differences between the pressure in the pressure chamber and the pressure in the compensation chamber hardly and temporally long-lasting pressure differences are completely compensated. Between the actuator and the actuator, a transmission module is used in a common housing. The pressure chamber and the compensation chamber are introduced in the transmission module and the compensation chamber is in operative connection with means which predetermine the pressure in the compensation chamber.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen der unabhängigen Ansprüche hat demgegenüber den Vorteil, dass die Innendrücke des Kopplers bei verschiedenen Belastungszuständen des Kopplers jeweils dauerhaft zuverlässig erreicht werden, der Koppler einfach und kostengünstig herstellbar, weniger aufwendig gebaut und zuverlässig dauerlauffest ist.The fuel injection valve according to the invention with the characterizing features of the independent claims has the advantage that the internal pressures of the coupler are always reliably achieved at different load conditions of the coupler, the coupler simple and inexpensive to produce, less expensive and reliably reliable running.

Durch die in den abhängigen Ansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des in den unabhängigen Ansprüchen angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in the independent claims are possible.

In einer ersten Weiterbildung weist der flexible Abschnitt einen axial zur Bewegungsachse der Kolben verlaufenden Axialabschnitt und einen zur Bewegungsachse der Kolben radial verlaufenden Radialabschnitt auf. Der flexible Abschnitt kann dadurch vorteilhaft in den Koppler integriert werden, so daß die mechanischen Belastungen minimiert und die Montage erleichtert wird. Dies wird auch durch eine hülsenförmige und/oder tellerförmige Ausbildung des flexiblen Abschnitts erreicht.In a first development, the flexible section has an axial section running axially with respect to the axis of movement of the pistons and a radial section extending radially with respect to the axis of movement of the piston. The flexible portion can be advantageously integrated into the coupler, so that the mechanical loads are minimized and the assembly is facilitated. This is also achieved by a sleeve-shaped and / or plate-shaped design of the flexible portion.

Vorteilhafterweise ist der flexible Abschnitt elastisch und besteht beispielsweise aus einem Elastomer. Dadurch kann der flexible Abschnitt gedehnt werden und bleibt dabei gegenüber den handelsüblichen Brennstoffen dicht.Advantageously, the flexible portion is elastic and consists for example of an elastomer. This allows the flexible section to be stretched while remaining tight against the commercial fuels.

Vorteilhaft ist es zudem, wenn das Federelement spiralförmig ausgebildet ist. Das Federelement läßt sich dadurch kostengünstig herstellen und besonders einfach und raumsparend in den Koppler integrieren.It is also advantageous if the spring element is formed spirally. The spring element can thereby be produced inexpensively and integrate in a particularly simple and space-saving manner in the coupler.

Eine erste erfindungsgemässe Ausführung zeigt, dass sich das Federelement insbesondere über einen mit dem Geberkolben bewegungsfest verbundenen hülsenförmigen Halter am Geberkolben abstützt, und vorteilhafterweise über einen Zwischenring auf den flexiblen Abschnitt wirkt. Der Koppler kann dadurch vorteilhaft einfach aufgebaut werden und der Druckverlauf im Koppler zusätzlich beeinflußt werden, indem das Federelement bei einer Vergrößerung des Kopplervolumens zusätzlich durch die relative Bewegung der beiden Kolben gespannt wird.A first embodiment according to the invention shows that the spring element is supported on the master piston, in particular via a sleeve-shaped holder immovably connected to the master piston, and advantageously acts on the flexible section via an intermediate ring. The coupler can be advantageously constructed simply and the pressure curve in the coupler are additionally influenced by the spring element is additionally stretched by an enlargement of the coupler volume by the relative movement of the two pistons.

In weiteren Weiterbildungen das Federelement wirkt über einen Hülsenring, welcher einen tellerförmigen radialen Verlauf aufweist und außen einen hülsenförmigen axialen Verlauf hat, auf den flexiblen Abschnitt. Der Koppler kann dadurch vorteilhaft einfach aufgebaut werden und der Druckverlauf im Koppler zusätzlich beeinflußt werden, indem das Federelement bei einer Vergrößerung des Kopplervolumens durch die relative Bewegung der beiden Kolben entspannt wird.In further developments, the spring element acts via a sleeve ring, which has a plate-shaped radial course and outside has a sleeve-shaped axial course, on the flexible portion. The coupler can be advantageously constructed simply and the pressure curve in the coupler are additionally influenced by the spring element is relaxed at an increase in the coupler volume by the relative movement of the two pistons.

Eine zweite erfindungsgemässe Ausführung sieht eine ringförmige Gestaltung des Federelements vor, wodurch die Baugröße und der Herstellungsaufwand weiter verringert werden kann. Besonders einfach und montagefreundlich kann das ringförmige Federelement durch offene, sich überlappende Enden aufgebaut werden. Durch eine Abrundung der Enden des ringförmigen Federelements wird der flexible Abschnitt insbesondere bei der Montage mechanisch geschont.A second embodiment of the invention provides an annular design of the spring element, whereby the size and the production cost can be further reduced. Particularly simple and easy to install, the annular spring element can be constructed by open, overlapping ends. By rounding off the ends of the annular spring element, the flexible section is mechanically protected, in particular during assembly.

Übt das Federelement in unbelastetem Zustand des Kopplers keinen Druck auf den flexiblen Abschnitt aus, so kann der flexible Abschnitt ebenfalls geschont werden.Does the spring element in the unloaded state of the coupler no pressure on the flexible portion, so the flexible portion can also be spared.

Umfaßt die Drossel eine Drosselkugel, die mit einem Drosselspalt in einer Öffnung geführt ist, kann die Drossel besonders einfach aufgebaut werden und, wenn sich die Drosselkugel an einer das Kopplervolumen begrenzenden Fläche des Geberkolbens abstützt, für die Funktion des Kopplers vorteilhaft genutzt werden.If the throttle comprises a throttle ball, which is guided with a throttle gap in an opening, the throttle can be constructed in a particularly simple manner and, if the throttle ball is supported on a surface bounding the coupler volume of the master piston, be advantageously used for the function of the coupler.

Zeichnungdrawing

Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:

Fig. 1
einen schematischen Schnitt durch ein Brennstoffeinspritzventil gemäß dem Stand der Technik,
Fig. 2
einen schematischen Ausschnitt eines Brennstoffeinspritzventils im Bereich des Kopplers gemäß dem Stand der Technik, ähnlich dem in Fig. 1 dargestellten Brennstoffeinspritzventil,
Fig. 3
ein Ausführungsbeispiel eines Brennstoffeinspritzventils im Bereich des Kopplers, welches nicht Teil die Erfindung ausmacht.
Fig. 4
ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich des Kopplers,
Fig. 5
ein Ausführungsbeispiel des ringförmigen Federelements und
Fig. 6
ein zweites und drittes Ausführungsbeispiel des Kopplers des erfindungsgemäßen Brennstoffeinspritzventils.
Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1
a schematic section through a fuel injection valve according to the prior art,
Fig. 2
a schematic section of a fuel injection valve in the region of the coupler according to the prior art, similar to that in Fig. 1 illustrated fuel injector,
Fig. 3
an embodiment of a fuel injection valve in the region of the coupler, which does not form part of the invention.
Fig. 4
A first embodiment of a fuel injection valve according to the invention in the region of the coupler,
Fig. 5
an embodiment of the annular spring element and
Fig. 6
A second and third embodiment of the coupler of the fuel injection valve according to the invention.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Nachfolgend werden Ausführungsbeispiele der Erfindung beispielhaft beschrieben.Hereinafter, embodiments of the invention will be described by way of example.

Bevor die Erfindung anhand bevorzugter Ausführungsformen näher beschrieben wird, wird zum besseren Verständnis ein Brennstoffeinspritzventil gemäß dem Stand der Technik in seinen wesentlichen Bauteilen in Fig. 1 und Fig. 2 kurz erläutert. Übereinstimmende Bauteile sind dabei in den Figuren mit übereinstimmenden Bezugszeichen versehen.Before the invention with reference to preferred embodiments will be described in more detail, for better understanding, a fuel injection valve according to the prior art in its essential components in Fig. 1 and Fig. 2 briefly explained. Matching components are provided in the figures with corresponding reference numerals.

Das in Fig. 1 dargestellte Brennstoffeinspritzventil 1 ist in der Form eines Brennstoffeinspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden, fremdgezündeten Brennkraftmaschinen ausgeführt. Das Brennstoffeinspritzventil 1 eignet sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraftmaschine.This in Fig. 1 shown fuel injection valve 1 is designed in the form of a fuel injection valve 1 for fuel injection systems of mixture-compression, spark-ignition internal combustion engines. The fuel injection valve 1 is suitable in particular for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.

Das Brennstoffeinspritzventil 1 umfaßt ein Gehäuse 2, in welchem ein mit einer Aktorumspritzung 3 versehener piezoelektrischer oder magnetostriktiver Aktor 4 angeordnet ist. Dem Aktor 4 kann mittels einer elektrischen Leitung 5, an welcher ein aus dem Gehäuse 2 ragender elektrischer Anschluß 6 ausgebildet sein kann, eine elektrische Spannung zugeführt werden. Der Aktor 4 stützt sich zuströmseitig an einem Geberkolben 9 eines hydraulischen Kopplers 7 und abströmseitig an einem Aktorkopf 8 ab. Der hydraulische Koppler 7 umfaßt weiterhin einen Nehmerkolben 10, eine Druckfeder 11, welche den hydraulischen Koppler 7 mit einer Vorspannung beaufschlagt, und einen Ausgleichsraum 12, welcher mit einem Hydraulikmedium gefüllt ist. Der Brennstoff wird über einen Zulauf 14 zentral zugeführt.The fuel injection valve 1 comprises a housing 2, in which a provided with an Aktorumspritzung 3 piezoelectric or magnetostrictive actuator 4 is arranged. The actuator 4 can be supplied by means of an electrical line 5, to which a protruding from the housing 2 electrical terminal 6, an electrical voltage can be supplied. The actuator 4 is supported on the inflow side on a master piston 9 of a hydraulic coupler 7 and downstream of an actuator head 8. The hydraulic coupler 7 further comprises a slave piston 10, a compression spring 11, which biases the hydraulic coupler 7, and a compensation chamber 12, which is filled with a hydraulic medium. The fuel is fed centrally via an inlet 14.

Eine detaillierte Beschreibung des Kopplers 7 sowie seiner Funktion ist der Beschreibung zu Fig. 2 zu entnehmen.A detailed description of the coupler 7 and its function is the description of Fig. 2 refer to.

Abströmseitig des Aktorkopfes 8 ist ein Betätigungskörper 15 angeordnet, welcher auf eine Ventilnadel 16 einwirkt. Die Ventilnadel 16 weist an ihrem abströmseitigen Ende einen Ventilschließkörper 17 auf. Dieser wirkt mit einer Ventilsitzfläche 18, welche an einem Düsenkörper 19 ausgebildet ist, zu einem Dichtsitz zusammen. Eine Rückstellfeder 20 beaufschlagt die Ventilnadel 16 so, daß das Brennstoffeinspritzventil 1 im unbestromten Zustand des Aktors 4 in geschlossenem Zustand verbleibt. Weiterhin sorgt sie nach der Einspritzphase für die Rückstellung der Ventilnadel 16.Downstream of the actuator head 8, an actuating body 15 is arranged, which acts on a valve needle 16. The valve needle 16 has at its downstream end a valve closing body 17. This acts together with a valve seat surface 18, which is formed on a nozzle body 19, to form a sealing seat. A return spring 20 acts on the valve needle 16 so that the fuel injection valve 1 remains in the de-energized state of the actuator 4 in the closed state. Furthermore, it ensures the return of the valve needle 16 after the injection phase.

Der Düsenkörper 19 ist mittels einer Schweißnaht 21 in einem Innengehäuse 22 fixiert, welches den Aktor 4 gegen den Brennstoff abdichtet. Der Brennstoff strömt vom Zulauf 14 zwischen dem Gehäuse 2 und dem Innengehäuse 22 zum Dichtsitz.The nozzle body 19 is fixed by means of a weld 21 in an inner housing 22, which seals the actuator 4 against the fuel. The fuel flows from the inlet 14 between the housing 2 and the inner housing 22 to the sealing seat.

Fig. 2 zeigt einen ähnlich dem in Fig. 1 dargestellten aufgebauten Koppler 7. Fig. 2 shows a similar to the one in Fig. 1 shown constructed coupler. 7

Hydraulische Koppler 7 in Brennstoffeinspritzventilen 1 sind gewöhnlich einerseits zur Um- oder Übersetzung des Hubs des Aktors 4 auf die Ventilnadel 16 und/oder andererseits zum Ausgleich temperaturbedingter Längenänderungen des Aktors 4 und des Gehäuses 2 konzipiert. Letzteres wird, wie im Ausführungsbeispiel gezeigt, mittels des als Zweitmediumkoppler ausgeführten Kopplers 7 realisiert, welcher ein nicht mit dem Brennstoff in Berührung kommendes Hydraulikmedium enthält.Hydraulic couplers 7 in fuel injection valves 1 are usually designed on the one hand for conversion or translation of the stroke of the actuator 4 on the valve needle 16 and / or on the other hand to compensate for temperature-induced changes in length of the actuator 4 and the housing 2. The latter is realized, as shown in the exemplary embodiment, by means of the coupler 7 designed as a second medium coupler, which contains a hydraulic medium not coming into contact with the fuel.

Das Hydraulikmedium füllt dabei den Ausgleichsraum 12 und ein zwischen Geberkolben 9 und Nehmerkolben 10 ausgebildetes Kopplervolumen 23, welches mit dem Ausgleichsraum 12 über eine Drossel 24 verbunden ist. Der Ausgleichsraum 12 ist innerhalb und außerhalb des Nehmerkolben 10 angeordnet, wobei die beiden Teile durch eine Querbohrung 31 miteinander verbunden sind und der außerhalb liegende Teil des Ausgleichsraums 12 mittels eines als Wellrohrdichtung ausgeführten flexiblen Abschnitts 13 gegenüber dem das Brennstoffeinspritzventil 1 durchströmenden Brennstoff abgedichtet ist.The hydraulic medium fills the compensation chamber 12 and a coupler volume 23 formed between master piston 9 and slave piston 10, which is connected to the compensation chamber 12 via a throttle 24. The compensation chamber 12 is disposed inside and outside the slave piston 10, wherein the two parts are connected by a transverse bore 31 and the outboard part of the compensation chamber 12 is sealed by means of a corrugated tube seal designed as flexible portion 13 relative to the fuel injector 1 flowing through the fuel.

Bei Temperaturänderungen wird Hydraulikmedium zwischen dem Kopplervolumen 23 über die Drossel 24 mit dem Ausgleichsraum 12 ausgetauscht. Der notwendige Befülldruck wird dabei über die im Nehmerkolben 10 in einem Druckspeicherraum 32 angeordnete Druckfeder 11 aufgebracht. Diese ist zwischen einem ersten Verschlußkörper 25 und einem zweiten Verschlußkörper 26 angeordnet, wobei ersterer eine Nut 27 mit einem darin angeordneten Dichtring 28 zur Abdichtung des Kopplerraumes 12 aufweist.In the event of temperature changes, hydraulic medium is exchanged between the coupler volume 23 via the throttle 24 with the compensation chamber 12. The necessary filling pressure is applied via the pressure piston 11 arranged in the slave piston 10 in a pressure storage chamber 32. This is arranged between a first closure body 25 and a second closure body 26, the former having a groove 27 with a sealing ring 28 arranged therein for sealing the coupler space 12.

Die Befüllung des Kopplers 7, beispielsweise bei der Herstellung, mit Hydraulikmedium erfolgt durch einen Kanal 29, welcher beispielsweise mittels einer eingepreßten Verschlußkugel 30 verschlossen sein kann.The filling of the coupler 7, for example in the production, with hydraulic medium takes place through a channel 29, which may be closed, for example by means of a pressed-in closure ball 30.

Fig. 3 zeigt ein Ausführungsbeispiel, welches nicht Teil der Erfindung ist, eines Kopplers 7 für ein Brennstoffeinspritzventil 1. Der Nehmerkolben 10 greift mit einem becherförmigen ersten Nehmerabschnitt 34 in den einseitig geschlossenen hohlzylinderförmigen Geberkolben 9 ein. Der Nehmerkolben 10 bzw. der erste Nehmerabschnitt 34 ist im Geberkolben 9 axial beweglich mit einem Führungsspalt 38 geführt. Der Führungsspalt 38 ist relativ klein, wobei die durch den Führungsspalt 38 strömende Menge an Hydraulikmedium sehr klein ist. In anderen Ausführungsbeispielen kann der Führungsspalt 38 eine Drosselfunktion ausüben. Fig. 3 shows an embodiment, which is not part of the invention, a coupler 7 for a Fuel injector 1. The slave piston 10 engages with a cup-shaped first slave portion 34 in the hollow-cylindrical master piston 9 closed on one side. The slave piston 10 or the first slave section 34 is axially movably guided in the master piston 9 with a guide gap 38. The guide gap 38 is relatively small, wherein the amount of hydraulic medium flowing through the guide gap 38 is very small. In other embodiments, the guide gap 38 may exert a throttle function.

In diesem Ausführungsbeispiel besteht der Nehmerkolben 10 aus dem ersten Nehmerabschnitt 34 und einem zweiten Nehmerabschnitt 35. Der erste Nehmerabschnitt 34 begrenzt mit seinem geschlossenen Ende zusammen mit dem Grund des Geberkolbens 9 das Kopplervolumen 23, wobei im geschlossenen Ende des ersten Nehmerabschnitts 34 zentriert die Drossel 24 angeordnet ist. Die Drossel 24 besteht aus einer zentriert im Boden des becherförmigen ersten Nehmerabschnitts 24 angeordneten Öffnung 36 und einer darin mit einem Drosselspalt 37 geführten Drosselkugel 39.In this embodiment, the slave piston 10 of the first slave portion 34 and a second slave portion 35. The first slave section 34 defines with its closed end together with the bottom of the master piston 9, the coupler volume 23, wherein centered in the closed end of the first slave section 34, the throttle 24th is arranged. The throttle 24 consists of an opening 36 centered in the bottom of the cup-shaped first slave section 24 and a throttle ball 39 guided therein with a throttle gap 37.

Das offene, dem Kopplervolumen 23 abgewandte Ende des ersten Nehmerabschnitts 34 ist durch den zweiten Nehmerabschnitt 35 verschlossen. Der zweite Nehmerabschnitt 35 greift dabei teilweise in den ersten Nehmerabschnitt 34 ein, verjüngt sich dabei und ist im oberen Bereich des ersten Nehmerabschnitts 34 beispielsweise durch Pressen oder Schweißen mit diesem bewegungsfest gefügt. Zwischen dem in den ersten Nehmerabschnitt 34 eingreifenden Ende des zweiten Nehmerabschnitts 35 und der Drosselkugel 39 ist die Druckfeder 11 mit einer Vorspannung in einem im ersten Nehmerabschnitt 34 angeordneten Federraum 45 angeordnet, wobei der verjüngte Teil des zweiten Nehmerabschnitts 35 teilweise in die spiralförmige Druckfeder 11 eingreift.The open, the coupler volume 23 facing away from the end of the first slave section 34 is closed by the second slave section 35. The second slave section 35 engages partially in the first slave section 34, tapers and is joined in the upper region of the first slave section 34, for example by pressing or welding with this movement. Between the engaging in the first slave section 34 end of the second slave section 35 and the throttle ball 39, the compression spring 11 is arranged with a bias in a arranged in the first slave section 34 spring chamber 45, the tapered portion of the second slave section 35 partially engages the helical compression spring 11 ,

Die Druckfeder 11 drückt auf die Drosselkugel 39 unter Zwischenlage eines becherförmigen Zwischenelements 40, wobei sich die Drosselkugel 39 am Boden des Geberkolbens 9 im Kopplervolumen 23 abstützt. Das Zwischenelement 40 kann nicht dargestellte Bohrungen zur Durchleitung von Brennstoff aufweisen. Die oberen, dem Kopplervolumen 23 abgewandten Enden des ersten Nehmerabschnitts 34 und des Geberkolbens 9 liegen etwa auf gleicher Höhe. Im axialen Verlauf des zweiten Nehmerabschnitts 35 vom Kopplervolumen 23 weggerichtet, also nach oben, weist der zweite Nehmerabschnitt 35 zuerst einen ersten Flansch 46 und dann einen zweiten Flansch 47 und am oberen Ende einen dritten Flansch 48 auf.The compression spring 11 presses on the throttle ball 39 with the interposition of a cup-shaped intermediate element 40, wherein the throttle ball 39 at the bottom of the master piston 9 in Coupler volume 23 is supported. The intermediate element 40 may have holes, not shown, for the passage of fuel. The upper, the coupler volume 23 facing away from the ends of the first slave section 34 and the master piston 9 are approximately at the same height. In the axial course of the second slave section 35 away from the coupler volume 23, ie upwards, the second slave section 35 has first a first flange 46 and then a second flange 47 and at the upper end a third flange 48.

Alle drei Flansche 46, 47 und 48 weisen in etwa den gleichen Durchmesser auf. Der zweite Nehmerabschnitt 35 ist zweiteilig ausgeführt, wobei der erste Flansch 46 am unteren und der zweite und dritte Flansch 47, 48 am oberen Teil angeordnet sind. Beide Teile sind bewegungsfest miteinander verbunden. Der erste Flansch 46 liegt in diesem Ausführungsbeispiel mit seiner unteren, dem ersten Nehmerabschnitt 34 zugewandten Seite auf dem oberen Ende des ersten Nehmerabschnitts 34 auf. Der erste Flansch 46 hat etwa den Durchmesser des ersten Nehmerabschnitts 34.All three flanges 46, 47 and 48 have approximately the same diameter. The second slave section 35 is designed in two parts, wherein the first flange 46 at the lower and the second and third flange 47, 48 are arranged at the upper part. Both parts are immovable connected. In this exemplary embodiment, the first flange 46 rests on the upper end of the first slave section 34 with its lower side facing the first slave section 34. The first flange 46 has approximately the diameter of the first slave section 34.

Der Ausgleichsraum 12 wird durch den flexiblen Abschnitt 13, den zweiten Nehmerabschnitt 35 mit seinem ersten Flansch 46 und den Geberkolben 9 begrenzt, wobei der Ausgleichsraum 12 über die Querbohrung 31 und den Federraum 45 mit der Drossel 24 in Verbindung steht. Die Querbohrung 31 ist zwischen erstem Flansch 46 und erstem Nehmerabschnitt 34 angeordnet. Der Kanal 29 mit der Verschlußkugel 30 ist koaxial im zweiten Nehmerabschnitt 35 durch eine Bohrung realisiert, die in den Federraum 45 mündet.The compensation chamber 12 is limited by the flexible portion 13, the second slave portion 35 with its first flange 46 and the master piston 9, wherein the compensation chamber 12 via the transverse bore 31 and the spring chamber 45 communicates with the throttle 24. The transverse bore 31 is arranged between the first flange 46 and the first slave section 34. The channel 29 with the closure ball 30 is realized coaxially in the second slave section 35 through a bore which opens into the spring chamber 45.

Der flexible Abschnitt 13 ist elastisch und besteht beispielsweise aus einem Elastomer oder aus Stahl. In diesem Ausführungsbeispiel teilt sich der flexible Abschnitt 13 in einen zur Bewegungsrichtung des Nehmerkolbens 10 axial verlaufenden Axialabschnitt 51 und einen radial zur Bewegungsrichtung des Nehmerkolbens 10 verlaufenden Radialabschnitt 52 auf. Der dadurch teller- und hülsenförmig gestaltete flexible Abschnitt 13 ist an seinen Enden verdickt und koaxial zu den Kolben 9, 10 angeordnet.The flexible portion 13 is elastic and is made of, for example, an elastomer or steel. In this exemplary embodiment, the flexible section 13 is divided into an axial section 51 extending axially relative to the direction of movement of the slave piston 10 and a radial section 52 extending radially with respect to the direction of movement of the slave piston 10. The thereby plate and sleeve-shaped designed flexible portion 13 is thickened at its ends and arranged coaxially with the pistons 9, 10.

Der flexible Abschnitt 13 liegt, bei spielsweise kraftschlüssig durch Druck gefügt, mit dem oberen Ende bzw. mit dem Bereich seines Innenumfangs des tellerförmigen Bereichs in einer muldenförmigen und ringnutförmigen ersten Ausnehmung 42, welche zwischen dem ersten Flansch 46 und dem zweiten Flansch 47 ausgebildet ist. Mit seinem unteren Ende liegt der flexible Abschnitt 13 in einer muldenförmigen und ringnutförmigen zweiten Ausnehmung 43, welche in der Außenfläche im Bereich des oberen Endes des Geberkolbens 9 angeordnet ist. Die axiale Ausdehnung der zweiten Ausnehmung 43 ist dabei jeweils etwas größer als die axiale Ausdehnung des unteren verdickten Endes des flexiblen Abschnitts 13. Dadurch ist insbesondere die Montage erleichtert.The flexible portion 13 is, for example frictionally joined by pressure, with the upper end or with the region of its inner periphery of the plate-shaped portion in a trough-shaped and annular first recess 42 which is formed between the first flange 46 and the second flange 47. With its lower end of the flexible portion 13 is located in a trough-shaped and annular groove-shaped second recess 43, which is arranged in the outer surface in the region of the upper end of the master piston 9. The axial extent of the second recess 43 is in each case slightly larger than the axial extent of the lower thickened end of the flexible portion 13. As a result, in particular the assembly is facilitated.

Ein hülsenförmiger Halter 41 umfaßt passgenau die obere Hälfte des Geberkolbens 9 und einen Teil des über den ersten Nehmerabschnitt 34 hinaus stehenden oberen Teils des zweiten Nehmerabschnitts 35. Der Halter 41 ist bewegungsfest mit dem Geberkolben 9 gefügt, beispielsweise stoff- und/oder kraftschlüssig durch Schweißen und/oder Pressen. Oberhalb des flexiblen Abschnitts 13 verjüngt sich der Halter 41. Der Axialabschnitt 51 des flexiblen Abschnitts 13 stützt sich in diesem Ausführungsbeispiel am Halter 41 axial nach außen ab, so daß der Halter 41 die radiale Bewegung des Axialabschnitts 51 nach außen begrenzt.A sleeve-shaped holder 41 includes an exact fit the upper half of the master piston 9 and part of the first slave section 34 beyond the upper part of the second slave section 35. The holder 41 is immovably joined to the master piston 9, for example, material and / or non-positively by welding and / or pressing. Above the flexible portion 13, the holder 41 tapers. The axial portion 51 of the flexible portion 13 is axially outwardly supported on the holder 41 in this embodiment, so that the holder 41 limits the radial movement of the axial portion 51 to the outside.

Ein zwischen dem zweiten Flansch 47 und dem dritten Flansch 48 angeordnetes Federelement 33 stützt sich am dritten Flansch 48 ab und übt von außen über einen lochscheiben- und hülsenförmigen Hülsenring 50, welcher mit seinem hülsenförmigen Abschnitt den zweiten Flansch 47 radial umfaßt, einen Druck auf den flexiblen Abschnitt 13 bzw. den Axialabschnitt 51 aus. Der Hülsenring 50 ist ähnlich dem flexiblen Abschnitt 13 geformt und seine mit dem flexiblen Abschnitt 13 in Kontakt stehenden Flächen sind abgerundet.A disposed between the second flange 47 and the third flange 48 spring element 33 is supported on the third flange 48 and exerts from the outside via a hole-and sleeve-shaped sleeve ring 50, which with its sleeve-shaped portion the second flange 47 comprises radially, a pressure on the flexible portion 13 and the axial portion 51 from. The sleeve ring 50 is shaped similarly to the flexible portion 13 and its surfaces in contact with the flexible portion 13 are rounded.

Über lange Zeiträume auf den Koppler 7 axial wirkende Kräfte, wie sie beispielsweise bei einer temperaturbedingten Ausdehnung des Aktors 4 auftreten, bewirken eine Verkleinerung des Kopplervolumens 23 durch Abfließen von Hydraulikmedium vom Kopplervolumen 23 durch die Drossel 24 über den Federraum 45 und die Querbohrung 31 in den Ausgleichsraum 12, der durch den elastischen und membranartigen flexiblen Abschnitt 13 teilweise begrenzt ist.Over long periods on the coupler 7 axially acting forces, such as occur in a temperature-induced expansion of the actuator 4, cause a reduction in the Kopplervolumens 23 by flow of hydraulic fluid from the coupler volume 23 through the throttle 24 via the spring chamber 45 and the transverse bore 31 in the Compensation space 12, which is partially limited by the elastic and membrane-like flexible portion 13.

Durch eine Vorspannung der Druckfeder 11 wird ein das Kopplervolumen 23 vergrößernder Druck auf das Hydraulikmedium ausgeübt, so daß bei einem von außen unbelastetem Koppler 7 die Druckfeder 11 das Kopplervolumen 23 zu einem maximalen Wert vergrößert, der beispielsweise dadurch begrenzt wird, daß das Zwischenelement 40 die Drosselkugel 39 nach unter drückt und auf dem Boden des ersten Nehmerabschnitts 34 aufsetzt. Das Federelement 33 ist beispielsweise so dimensioniert, das bei maximalem Kopplervolumen 23 das Federelement 33 keinen Druck auf den flexiblen Abschnitt 13 ausübt, so daß der Hülsenring 50 nur nahezu drucklos auf dem Axialabschnitt 51 aufliegt und das Federelement 33 nicht gespannt ist.By a bias of the compression spring 11, the coupler volume 23 magnifying pressure is exerted on the hydraulic medium, so that in an externally unloaded coupler 7, the compression spring 11, the coupler volume 23 increases to a maximum value, which is limited, for example, characterized in that the intermediate element 40 the Throttle ball 39 presses down and touches on the bottom of the first slave section 34. The spring element 33 is for example dimensioned so that at maximum coupler volume 23, the spring element 33 exerts no pressure on the flexible portion 13, so that the sleeve ring 50 rests only almost without pressure on the axial portion 51 and the spring element 33 is not tensioned.

Die dynamische Steifigkeit des Kopplers 7 wird insbesondere durch die Größe und Form des Drosselspalts 37 und ggf. durch die Größe und Form des Führungsspalts 38 bestimmt.The dynamic stiffness of the coupler 7 is determined in particular by the size and shape of the throttle gap 37 and possibly by the size and shape of the guide gap 38.

Fig. 4 zeigt ein erstes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich des Kopplers 7, ähnlich dem vorhergehenden Ausführungsbeispiel aus Fig. 3. Abweichend vom Ausführungsbeispiel aus Fig. 3 stützt sich das Federelement 33 an einem am Halter 41 bewegungsfest angeordneten Einzug 49 ab und drückt andererseits über einen Zwischenring 44 auf den flexiblen Abschnitt 13. Der Zwischenring 44 drückt, mit abgerundeten Flächen in diesem Ausführungsbeispiel auf den Übergang zwischen Axialabschnitt 51 und Radialabschnitt 52. Fig. 4 shows a first embodiment of a fuel injection valve according to the invention in the region of the coupler 7, similar to the previous embodiment Fig. 3 , Deviating from the embodiment Fig. 3 the spring element 33 is supported on a retraction 49 fixedly mounted on the holder 41 and presses on the flexible section 13 via an intermediate ring 44. The intermediate ring 44 presses, with rounded surfaces in this exemplary embodiment, on the transition between the axial section 51 and the radial section 52.

Der Halter 41 erstreckt sich, ohne sich zu verjüngen, von der Außenfläche des Geberkolbens 9 bis auf Höhe des oberen Endes des Nehmerkolbens 10 bzw. des zweiten Nehmerabschnitts 34 oder des dritten Flansches 48, wo er sich als Einzug 49 in radialer Richtung verjüngt. Der Zwischenring 44 ist im hülsenförmigen Halter 41 etwa auf Höhe des zweiten Flansches 47 axial beweglich geführt. Der zweite Flansch 47 weist einen über den ersten und dritte Flansch 46, 48 hinaus stehenden Durchmesser auf, so daß radial zwischen dem zweiten Flansch 47 und dem Zwischenring 44 nur geringes Spiel besteht. Die Querbohrung 31 ist nicht dargestellt.The holder 41 extends, without tapering, from the outer surface of the master piston 9 to the level of the upper end of the slave piston 10 and the second slave section 34 or the third flange 48, where it tapers as a retraction 49 in the radial direction. The intermediate ring 44 is guided axially movable in the sleeve-shaped holder 41 approximately at the level of the second flange 47. The second flange 47 has a diameter beyond the first and third flanges 46, 48 so that there is little play between the second flange 47 and the intermediate ring 44 radially. The transverse bore 31 is not shown.

Fig. 5 zeigt ein Ausführungsbeispiel eines ringförmigen Federelements 33, wie es im zweiten und dritten Ausführungsbeispiel in Fig. 6 verwendet wird. Das Federelement 33 besteht aus Federstahl und ist ringförmig. Die Ringform weist zwei Enden auf, ist also nicht geschlossen, wobei sich die Bereiche der Enden überlappen und ab dem Bereich an dem sich die Enden kreuzen bzw. überlappen tangential nach außen laufen. Fig. 5 shows an embodiment of an annular spring element 33, as in the second and third embodiments in Fig. 6 is used. The spring element 33 is made of spring steel and is annular. The ring shape has two ends, so it is not closed, with the areas of the ends overlap and run tangentially outward from the area where the ends intersect or overlap.

Fig. 6 zeigt ein zweites und drittes Ausführungsbeispiel des Kopplers 7 des erfindungsgemäßen Brennstoffeinspritzventils 1. Das dritte Ausführungsbeispiel, welches links dargestellt ist, ist ähnlich dem ersten und zweiten erfindungsgemäßen Ausführungsbeispiel aufgebaut. Das Federelement 33 ist jedoch, wie in Fig. 5 dargestellt, ringförmig und verläuft um den Axialabschnitt 51 des flexiblen Abschnitts 13. Das dritte Ausführungsbeispiel zeigt den Koppler 7 in unbelastetem Zustand. In unbelastetem Zustand des Kopplers 7 drückt das Federelement 33 mit einer Vorspannung auf den Axialabschnitt 51, so daß der Axialabschnitt 51 im Bereich der Stelle, an dem das Federelement 33 aufliegt, leicht nach innen eingedrückt ist und so den Ausgleichsraum 12 verkleinert. Fig. 6 shows a second and third embodiment of the coupler 7 of the fuel injection valve 1 according to the invention. The third embodiment, which is shown on the left, is similar to the first and second embodiments of the invention constructed. However, the spring element 33 is, as in Fig. 5 shown, annular and extends around the axial portion 51 of the flexible portion 13. The third embodiment shows the coupler 7 in the unloaded state. In the unloaded state of the coupler 7, the spring element 33 presses with a bias on the axial portion 51, so that the axial portion 51 in the region of the point at which the spring element 33 rests, is pressed slightly inward and thus reduces the compensation chamber 12.

In anderen Ausführungsbeispielen kann der Axialabschnitt 51 entsprechend der gerade beschriebenen Form auch plastisch vorgeformt sein, wobei das Federelement 33 nur nahezu drucklos in der plastisch eingedrückten Form aufliegt und sich eine Spannung des Federelements 33 erst bei Druckbeaufschlagung von innen durch das Hydraulikmedium bei axialer Belastung des Kopplers 7 einstellt. Durch eine Beschichtung des Federelements 33 und/oder des flexiblen Abschnitts 13 bzw. des Axialabschnitts 51 kann die Reibung zwischen Federelement 33 und flexiblem Abschnitt 13 reduziert werden.In other embodiments, the axial portion 51 may also be plastically preformed according to the shape just described, wherein the spring element 33 only almost depressurized rests in the plastically indented form and a voltage of the spring element 33 only when pressurized from the inside by the hydraulic medium at axial load of the coupler 7 sets. By coating the spring element 33 and / or the flexible section 13 or the axial section 51, the friction between the spring element 33 and the flexible section 13 can be reduced.

Der zweite Flansch 47 überdeckt im Unterschied zum ersten und zweiten Ausführungsbeispiel die obere Seite des Radialabschnitts 52 und des Bereichs des Übergangs vom Radialabschnitt 52 zum Axialabschnitt 51 vollständig, setzt sich also axial nach unten fort. Der Halter 41 erstreckt sich axial etwa von der Mitte der Höhe des Geberkolbens 9 bis über die Höhe des verdickt ausgeführten Endes des Axialabschnitts 51. Die Querbohrung 31 ist nicht dargestellt.In contrast to the first and second embodiments, the second flange 47 completely covers the upper side of the radial section 52 and the region of the transition from the radial section 52 to the axial section 51, thus continuing axially downward. The holder 41 extends axially approximately from the center of the height of the master piston 9 to above the height of the thickened running end of the axial portion 51. The transverse bore 31 is not shown.

Das dritte erfindungsgemäße Ausführungsbeispiel, welches rechts dargestellt ist, ist ähnlich dem zweiten Ausführungsbeispiel aufgebaut. Der flexible Abschnitt 13 ist hülsenförmig ausgebildet und weist somit nur den Axialabschnitt 51 auf. Im oberen Bereich ist der flexible Abschnitt 13 mit seinem verdickten Ende zwischen dem zweiten Flansch 47 und dem ersten Flansch 46, welche in diesem Ausführungsbeispiel in etwa den Durchmesser des Geberkolbens 9 annehmen und dabei die muldenförmige und ringnutförmige erste Ausnehmung 42 bilden, angeordnet. Der hülsenförmige Halter 41 ist zweiteilig ausgeführt, wobei der obere Teil das obere, verdickte Ende des flexiblen Abschnitts 13 umfaßt und der untere Teil das untere verdickte Ende des flexiblen Abschnitts 13 umfaßt, so daß beide Teile hermetisch dicht und kraftschlüssig bewegungsfest in die Ausnehmungen 42, 43 gedrückt werden. Der dritte Flansch 48 ist nicht ausgebildet und die Querbohrung 31 nicht dargestellt.The third embodiment of the invention shown on the right is constructed similarly to the second embodiment. The flexible portion 13 is sleeve-shaped and thus has only the axial portion 51. In the upper region, the flexible portion 13 with its thickened end between the second flange 47 and the first flange 46, which in this embodiment approximately assume the diameter of the master piston 9 and thereby form the trough-shaped and annular groove-shaped first recess 42, respectively. The sleeve-shaped holder 41 is made in two parts, wherein the upper part of the upper, thickened end of the flexible portion 13 and the lower part comprises the lower thickened end of the flexible portion 13, so that both parts hermetically sealed and non-positively movement in the recesses 42, 43 are pressed. The third flange 48 is not formed and the transverse bore 31 is not shown.

Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und für beliebige Bauformen von Brennstoffeinspritzventilen 1, insbesondere auch für Brennstoffeinspritzventile 1 für selbstzündende Brennkraftmaschinen und/oder nach innen öffnende Brennstoffeinspritzventile, geeignet. Die Merkmale der Ausführungsbeispiele sind beliebig miteinander kombinierbar.The invention is not limited to the illustrated embodiments and for any designs of fuel injection valves 1, in particular also for fuel injection valves 1 for self-igniting internal combustion engines and / or inwardly opening fuel injection valves suitable. The features of the embodiments can be combined with each other.

Claims (13)

  1. Fuel injection valve having a piezoelectric or magnetostrictive actuator (4) which actuates a valve closing body (17) which interacts with a valve seat face (18) to form a sealing seat, and having a hydraulic coupler (7) which comprises a master piston (9), a slave piston (10) and a coupler volume (23) which is formed between them, the master piston (9) and the slave piston (10) being movable axially with respect to one another, the coupler volume (23) being connected via a restrictor (24) to a compensation space (12), a flexible section (13) delimiting the compensation space (12) at least partially, and the coupler volume (23), the restrictor (24) and the compensation space (12) being filled with a hydraulic medium, the actuator (4) being supported on the inflow side on the master piston (9) and on the outflow side on an actuator head (8), on which on the outflow side an actuating body (15) is arranged which acts on a valve needle (16), the flexible section (13) being loaded with a pressure by at least one spring element (33) directly or indirectly via fixed components from outside the coupler volume (23), characterized in that the spring element (33) is supported on the master piston (9) via a sleeve-shaped holder (41) which is fixed on the master piston (9) in a stationary manner.
  2. Fuel injection valve according to Claim 1, characterized in that the flexible section (13) has an axial section (51) which extends axially with respect to the movement direction of the pistons (9, 10) and a radial section (47) which extends radially with respect to the movement direction of the pistons (9, 10).
  3. Fuel injection valve according to Claim 1 or 2, characterized in that the flexible section (13) is in the shape of a perforated disc and/or a sleeve.
  4. Fuel injection valve according to one of the preceding claims, characterized in that the flexible section (13) is elastic and is composed, in particular, of an elastomer.
  5. Fuel injection valve according to one of the preceding claims, characterized in that the at least one spring element (33) is spiral.
  6. Fuel injection valve according to one of the preceding claims, characterized in that the spring element (33) acts on the flexible section (13) via an intermediate ring (44).
  7. Fuel injection valve according to one of the preceding claims, characterized in that the spring element (33) acts via a sleeve ring (50) which is shaped like a plate in the radial profile and like a sleeve on the outside in the axial profile.
  8. Fuel injection valve having a piezoelectric or magnetostrictive actuator (4) which actuates a valve closing body (17) which interacts with a valve seat face (18) to form a sealing seat, and having a hydraulic coupler (7) which comprises a master piston (9), a slave piston (10) and a coupler volume (23) which is formed between them, the master piston (9) and the slave piston (10) being movable axially with respect to one another, the coupler volume (23) being connected via a restrictor (24) to a compensation space (12), a flexible section (13) delimiting the compensation space (12) at least partially, and the coupler volume (23), the restrictor (24) and the compensation space (12) being filled with a hydraulic medium, the flexible section (13) being loaded with a pressure by at least one spring element (33) directly or indirectly via fixed components from outside the coupler volume (23), characterized in that the spring element (33) is annular, and in that the spring element (33) extends radially around the flexible section (13).
  9. Fuel injection valve according to Claim 8, characterized in that the spring element (33) is open, the ends overlap and the ends are rounded.
  10. Fuel injection valve according to one of the preceding claims, characterized in that the spring element (33) is composed of steel, in particular spring steel.
  11. Fuel injection valve according to one of the preceding claims, characterized in that the spring element (33) exerts no pressure on the flexible section (13) in the unloaded state of the coupler (7).
  12. Fuel injection valve according to one of the preceding claims, characterized in that the restrictor (24) comprises a throttle ball (39) which is guided with a throttle gap (37) in an opening (36).
  13. Fuel injection valve according to Claim 12, characterized in that the throttle ball (39) is supported on a face of the master piston (9), which face delimits the coupler volume (23).
EP04791347A 2003-12-08 2004-10-29 Fuel-injection valve Expired - Fee Related EP1714026B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10357189A DE10357189A1 (en) 2003-12-08 2003-12-08 Fuel injector
PCT/EP2004/052727 WO2005054662A1 (en) 2003-12-08 2004-10-29 Fuel-injection valve

Publications (2)

Publication Number Publication Date
EP1714026A1 EP1714026A1 (en) 2006-10-25
EP1714026B1 true EP1714026B1 (en) 2009-05-20

Family

ID=34638469

Family Applications (1)

Application Number Title Priority Date Filing Date
EP04791347A Expired - Fee Related EP1714026B1 (en) 2003-12-08 2004-10-29 Fuel-injection valve

Country Status (5)

Country Link
US (1) US7422006B2 (en)
EP (1) EP1714026B1 (en)
JP (1) JP4314276B2 (en)
DE (2) DE10357189A1 (en)
WO (1) WO2005054662A1 (en)

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10357189A1 (en) * 2003-12-08 2005-07-07 Robert Bosch Gmbh Fuel injector
DE602004003928T2 (en) * 2004-06-30 2007-10-18 C.R.F. S.C.P.A. Injection valve for internal combustion engine
DE102006013958B4 (en) * 2006-03-27 2016-11-10 Robert Bosch Gmbh Fuel injector
DE102007012920A1 (en) 2007-03-19 2008-09-25 Robert Bosch Gmbh Hydraulic coupler
JP4998835B2 (en) * 2008-10-02 2012-08-15 株式会社デンソー Fuel injection device
US10006429B2 (en) * 2016-03-31 2018-06-26 GM Global Technology Operations LLC Variable-area poppet nozzle actuator

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0656162B2 (en) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 Variable stroke device
ATE192263T1 (en) * 1990-09-25 2000-05-15 Siemens Ag ARRANGEMENT FOR AN ADAPTIVE, MECHANICAL TOLERANCE COMPENSATION FOR THE DISTANCE TRANSFORMER OF A PIEZOELECTRIC ACTUATOR, ACTING IN THE STROKE DIRECTION
DE19708304C2 (en) 1997-02-28 1999-09-30 Siemens Ag Movement transmission device and injection valve with a movement transmission device
DE19962177A1 (en) * 1999-12-22 2001-07-12 Siemens Ag Hydraulic device for transmitting an actuator movement
DE10148594A1 (en) * 2001-10-02 2003-04-10 Bosch Gmbh Robert Fuel injection valve has corrugated tube around guide sleeve with sealed connections to pistons that seals storage chamber for hydraulic fluid with respect to enclosing fuel chamber
DE10159749A1 (en) * 2001-12-05 2003-06-12 Bosch Gmbh Robert Fuel injection valve for an internal combustion engine comprises a pressure space which contains a hydraulic fluid and, by means of sealing units, is separated from the actuator and fuel spaces
DE10162045B4 (en) * 2001-12-17 2005-06-23 Siemens Ag Device for translating a deflection of an actuator, in particular for an injection valve
DE10204655A1 (en) * 2002-02-05 2003-08-28 Bosch Gmbh Robert Fuel injector
US7500648B2 (en) * 2003-02-27 2009-03-10 Robert Bosch Gmbh Fuel-injection valve
DE10360449A1 (en) * 2003-02-27 2004-09-09 Robert Bosch Gmbh Fuel injector
DE10310499A1 (en) * 2003-03-11 2004-09-23 Robert Bosch Gmbh Fuel injection valve for IC engine fuel injection system, has hydraulic coupler provided with piston having internal hollow space acting as pressure equalization chamber
DE10310790A1 (en) * 2003-03-12 2004-09-23 Robert Bosch Gmbh Fuel injection valve for IC engine fuel injection system, has hydraulic coupler between actuator and valve group incorporating valve closure and valve seat surface
DE10357189A1 (en) * 2003-12-08 2005-07-07 Robert Bosch Gmbh Fuel injector
DE102004021920A1 (en) * 2004-05-04 2005-12-01 Robert Bosch Gmbh Fuel injector

Also Published As

Publication number Publication date
WO2005054662A1 (en) 2005-06-16
DE502004009511D1 (en) 2009-07-02
EP1714026A1 (en) 2006-10-25
JP4314276B2 (en) 2009-08-12
US20070246017A1 (en) 2007-10-25
JP2007513293A (en) 2007-05-24
US7422006B2 (en) 2008-09-09
DE10357189A1 (en) 2005-07-07

Similar Documents

Publication Publication Date Title
EP1115970B1 (en) Fuel injection valve
EP2394049B1 (en) Fuel injection valve for internal combustion engines
EP1423600B1 (en) Fuel injection valve
EP2108080A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
EP1714026B1 (en) Fuel-injection valve
EP1601868B1 (en) Fuel-injection valve
EP1381774A1 (en) Fuel injection device with two coaxial valve elements and fuel system for internal combustion engines, as well as internal combustion engine
DE10217594A1 (en) Fuel injection valve for IC engines has throttle gap formed by Laser/erosion drilling, and positioned separate from guide gaps, for cheaper fabrication of gaps
EP1538331B1 (en) Fuel injection valve
EP1452727B1 (en) Fuel injector
EP1373710A1 (en) Fuel-injection valve for internal combustion engines
DE4301521A1 (en) Pressure valve
DE10353641B4 (en) Fuel injector
EP1620645B1 (en) Fuel injection valve free of loss
DE102012211233A1 (en) Fuel injection valve for fuel injection system of internal combustion engine, has actuator that affects mechanical translator over hydraulic temperature equalizing device when translating stroke of actuator into stroke of nozzle needle
WO2006079425A1 (en) Fuel injection device
EP1406006B1 (en) Fuel injection valve
DE10132450A1 (en) Fuel injection valve for internal combustion engines
DE19756669A1 (en) Valve for controlling liquids
DE19963934A1 (en) Control valve for an injector for a fuel injection system with an actuator guided by a tappet
EP3035520B1 (en) Hydraulic coupler unit for controlling a valve
DE102013220875A1 (en) Valve for metering fluid
WO2005003550A1 (en) Fuel injection valve for combustion engines
EP1526275A1 (en) Fuel injection valve
WO2003081019A1 (en) Fuel injection valve for internal combustion engines

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: 20060710

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 20070131

DAX Request for extension of the european patent (deleted)
RBV Designated contracting states (corrected)

Designated state(s): DE FR GB IT

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAJ Information related to disapproval of communication of intention to grant by the applicant or resumption of examination proceedings by the epo deleted

Free format text: ORIGINAL CODE: EPIDOSDIGR1

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

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 GB IT

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502004009511

Country of ref document: DE

Date of ref document: 20090702

Kind code of ref document: P

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: 20100223

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 12

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 13

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 14

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 15

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

Ref country code: DE

Payment date: 20181206

Year of fee payment: 15

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

Ref country code: FR

Payment date: 20191022

Year of fee payment: 16

Ref country code: IT

Payment date: 20191021

Year of fee payment: 16

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

Ref country code: GB

Payment date: 20191023

Year of fee payment: 16

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502004009511

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: 20200501

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20201029

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: 20201031

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

Ref country code: GB

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

Effective date: 20201029

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

Ref country code: IT

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

Effective date: 20201029