EP1538331B1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

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Publication number
EP1538331B1
EP1538331B1 EP20040105050 EP04105050A EP1538331B1 EP 1538331 B1 EP1538331 B1 EP 1538331B1 EP 20040105050 EP20040105050 EP 20040105050 EP 04105050 A EP04105050 A EP 04105050A EP 1538331 B1 EP1538331 B1 EP 1538331B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
valve according
coupler
slave
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
EP20040105050
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German (de)
French (fr)
Other versions
EP1538331A1 (en
Inventor
Klaus Noller
Michael Huebel
Thomas Gerschwitz
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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Publication date
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Publication of EP1538331A1 publication Critical patent/EP1538331A1/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
    • 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
    • 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
    • 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
    • F02M61/166—Selection of particular materials
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/16—Sealing of fuel injection apparatus not otherwise provided for
    • 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
    • F02M2200/707—Linkage between actuator and actuated element, e.g. between piezoelectric actuator and needle valve or pump plunger hydraulic with means for avoiding fuel contact with actuators, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • the invention relates to a fuel injection valve according to the preamble of the main claim.
  • EP 0 477 400 A1 discloses an arrangement for an adaptive mechanical tolerance compensation acting in the stroke direction for a travel transformer of a piezoelectric actuator for a fuel injection valve.
  • 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.
  • 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 compress 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.
  • US 2002/0139863 A1 starts from a fuel injection valve with an actuator whose length changes, wherein the change in length of the actuator is coupled to a valve closing body, so that an extension of the actuator caused by an applied electrical voltage causes the valve closing body to be seated on the valve closing body brings the downstream end of the fuel injection valve in a sealing contact.
  • the fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the hydraulic medium of the coupler is permanently sealed and the space and the manufacturing cost is reduced.
  • the diameter feed engages or protrudes into a recess, wherein in a further development, the recess decreases in the case of an enlarging coupler volume.
  • the coupler can be made compact and the bias, with which the flexible portion acts on the hydraulic medium, be favorably influenced.
  • the throttle Due to the design of the throttle as a bore and the arrangement of the throttle in a throttle disk, the throttle can be very easily and inexpensively.
  • the hydraulic behavior of the coupler can be further advantageously adjusted.
  • the hydraulic behavior of the coupler can be further advantageously influenced.
  • FIGS. 1 and 2 Before the invention is described in more detail with reference to preferred embodiments, a fuel injection valve according to the prior art in its essential components in FIGS. 1 and 2 is briefly explained for better understanding. Matching components are provided in the figures with corresponding reference numerals.
  • the fuel injection valve 1 shown in FIG. 1 is 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 acts on the hydraulic coupler 7 with a bias, 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 coupler 7 constructed similarly to the coupler shown in FIG.
  • 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 a 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 between master piston 9 and Slave piston 10 formed coupler volume 23, which is connected to the expansion 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 bore 29, which may be closed, for example by means of a pressed-in ball 30.
  • a disadvantage of the described design of the fuel injector 1 and the hydraulic coupler 7 is in particular that the leakage losses at the arranged in the groove 27 sealing ring 28 are relatively high. This reduces the fatigue strength of the fuel injection valve 1, since the hydraulic medium on the sealing ring 28 leaks over time into the pressure storage space 32 and thus also reduces the prestress applied by the compression spring 11. Thus, the coupler 7 undesirably changes its behavior in the fuel injection valve 1 over the lifetime. Due to the complicated design, the production of the coupler 7 is very expensive and the size increased unfavorably. In addition, in particular by the shape of the flexible portion, a relatively large capacity of the hydraulic medium necessary. But this increases the temperature dependence by the temperature expansion.
  • a remedy is provided by the embodiment described below of a designed as a second-medium coupler coupler 7, which is simple and inexpensive to manufacture, less expensive built, reliable continuous running and its behavior is less temperature-dependent.
  • FIG. 3 shows a non-inventive example of a coupler 7 for a fuel injection valve 1.
  • the slave piston 10 engages with a piston-shaped second slave section 35 into the essentially cylindrical master piston 9.
  • the slave piston 10 and the second slave section 35 are guided axially movably in the master piston 9 with a guide gap 38.
  • the guide gap 38 is relatively small, wherein the amount of hydraulic medium passing through the guide gap 38 during operation is negligibly small.
  • the guide gap 38 may exert a throttle function.
  • the slave piston 10 consists of a first slave section 34 and a second slave section 35, wherein in other embodiments, the slave piston 10 can also be made in one piece.
  • the first slave section 34 is cylindrical and tapers from a diameter which corresponds approximately to the diameter of the master piston 9, stepwise in the direction of the master piston 9, and the second slave section 35.
  • the first slave section 34 tapers at a step 40 and thus has a T-shaped cross-section.
  • the tapered part of the first slave portion 34 engages partially coaxially in the second slave portion 35 and is fixed there immovable, for example by pressing or welding.
  • the U-shaped diameter retraction 33 protrudes into the recess 39.
  • the flexible portion 13 In the region of the upper end of the flexible portion 13 on the circumference of the first slave portion 34, for example, cohesively, hermetically sealed. In the region of its lower end, the flexible portion 13 is circumferentially hermetically sealed to the master piston 9.
  • the slave piston 10 has a centered channel 29 which merges into a compensation channel 36 and is closed to the outside by a ball 30, which is introduced after filling the coupler 7 with hydraulic medium for closing the channel 29.
  • the compensation channel 36 which is formed in this embodiment as a stepped bore, ends at its the coupler volume 23 facing the end of a throttle plate 37, which has at least one designed as a relatively small bore, centered throttle 24.
  • the throttle 24 opens into the coupler volume 23.
  • the transverse bore 31 Approximately at the level of the transition of the channel 29 in the compensation channel 36 is the transverse bore 31, which can also be prepared by other molding methods than drilling.
  • the restrictor disk 37 is embedded in the surface of the second slave section 35 and, for example, joined to the second slave section 35 in a material-locking manner by welding.
  • the transverse bore 31 connects via the throttle 24, the coupler volume 23 with the expansion chamber 12th
  • FIG. 4 shows an exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the coupler 7, similar to the exemplary embodiment from FIG. 3.
  • the channel 29 is arranged in the master piston 9.
  • the channel 29 opens directly into the coupler volume 23.
  • the compensation channel 36 connects the coupler volume 23, the compensation chamber 12 and a chamber 41 with each other.
  • the chamber 41 is formed in the slave piston 10, wherein in this embodiment, the chamber 41 by a first recess 44 which is centered in a first slave portion 34 above and laterally comprehensive attachment 43 is disposed, and by a second recess 45 at the upper end of the first slave section 34 is formed centered, is formed.
  • the recesses 44, 45 lie with the interposition of a membrane 42 hydraulically outwardly close to each other and thereby form the chamber 41.
  • the membrane 42 consists for example of an elastomer and divides the chamber 41 hermetically sealed into the first recess 44 and the second recess 45th Die second recess 45 is connected via the compensation channel 36 with the coupler volume 23 in connection.
  • the first recess 44 is, for example, with a gas filled with pressure and thus exerts a pressure on the hydraulic medium.
  • the internal coupler pressure can be generated via an additionally arranged in the chamber 41 spring, so that the interior 41 is depressurized.
  • the membrane 42 is elastic and consists of an elastomer, for example of Viton.
  • the attachment part 43 belonging to the slave piston 10 is connected, for example, by pressing and / or welding to the first slave section 34.
  • the flexible portion 13 is hermetically sealed at its upper end to the radially outer surface of the attachment 43.
  • the invention is also suitable for fuel injection valves 1 for self-igniting internal combustion engines and / or inwardly opening fuel injection valves.

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

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.EP 0 477 400 A1 discloses an arrangement for an adaptive mechanical tolerance compensation acting in the stroke direction for a travel transformer of a piezoelectric actuator for a fuel injection valve. 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 compress 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.

Die Druckschrift US 2002/0139863 A1 geht aus von einem Brennstoffeinspritzventil mit einem Aktor, dessen Länge sich ändert, wobei die Längenänderung des Aktors mit einem Ventilschließkörper gekoppelt ist, so dass eine durch eine angelegte elektrische Spannung hervorgerufene Ausdehnung des Aktors den Ventilschließkörper mit einem Dichtsitz am stromabwärtigen Ende des Brennstoffeinspritzventils in eine dichtende Anlage bringt.US 2002/0139863 A1 starts from a fuel injection valve with an actuator whose length changes, wherein the change in length of the actuator is coupled to a valve closing body, so that an extension of the actuator caused by an applied electrical voltage causes the valve closing body to be seated on the valve closing body brings the downstream end of the fuel injection valve in a sealing contact.

Aus dem Stand der Technik sind außerdem Brennstoffeinspritzventile bekannt, die mit wellrohr- bzw. wellbalgförmigen Dichtungen Hydraulikmedium abdichten.In addition, fuel injection valves are known from the prior art, which seal hydraulic medium with Wellrohr- or bellows-shaped seals.

Nachteilig an diesem bekannten Stand der Technik ist, daß eine Leckage durch Dichtringe nicht vollständig vermieden werden kann und die Brennstoffeinspritzventile dadurch eine geringere Lebensdauer haben. Die Abdichtung durch Wellrohrdichtungen erhöht die Menge an Hydraulikmedium stark und damit das temperaturabhängige Verhalten des Kopplers. Außerdem ist die Baugröße und der Herstellungsaufwand erhöht.A disadvantage of this known prior art that leakage through sealing rings can not be completely avoided and the fuel injectors thereby have a shorter life. Sealing with corrugated pipe seals increases the amount of hydraulic medium and thus the temperature-dependent behavior of the coupler. In addition, the size and the production cost is increased.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß das Hydraulikmedium des Kopplers dauerhaft abgedichtet wird und der Bauraum sowie der Herstellungsaufwand vermindert sind.The fuel injection valve according to the invention with the characterizing features of the main claim has the advantage that the hydraulic medium of the coupler is permanently sealed and the space and the manufacturing cost is reduced.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The measures listed in the dependent claims advantageous developments of the fuel injection valve specified in the main claim are possible.

In einer ersten Weiterbildung greift bzw. ragt der Durchmessereinzug in eine Ausnehmung ein, wobei sich in einer weiteren Weiterbildung die Ausnehmung bei einem sich vergrößernden Kopplervolumen verkleinert. Dadurch kann der Koppler kompakt gebaut werden und die Vorspannung, mit der der flexible Abschnitt auf das Hydraulikmedium wirkt, vorteilhaft beeinflußt werden.In a first development, the diameter feed engages or protrudes into a recess, wherein in a further development, the recess decreases in the case of an enlarging coupler volume. As a result, the coupler can be made compact and the bias, with which the flexible portion acts on the hydraulic medium, be favorably influenced.

Durch die Ausführung der Drossel als Bohrung und die Anordnung der Drossel in einer Drosselscheibe läßt sich die Drossel sehr einfach und kostengünstig herstellen.Due to the design of the throttle as a bore and the arrangement of the throttle in a throttle disk, the throttle can be very easily and inexpensively.

Durch die Verbindung des Ausgleichsraum mit einer Kammer, die durch eine elastische Membran eine Vorspannung auf das Hydraulikmedium ausübt, kann das hydraulische Verhalten des Kopplers weiter vorteilhaft eingestellt werden.By the connection of the compensation chamber with a chamber which exerts a bias on the hydraulic medium by an elastic membrane, the hydraulic behavior of the coupler can be further advantageously adjusted.

Durch die druckbehaftete Gasfüllung der durch die Membran vom Ausgleichsraum getrennten Aussparung der Kammer, kann das hydraulische Verhalten des Kopplers weiter vorteilhaft beeinflußt werden.Due to the pressurized gas filling of the membrane separated from the compensation chamber recess of the chamber, the hydraulic behavior of the coupler can be further advantageously influenced.

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 nicht erfindungsgemäßes Beispiel eines Brennstoffeinspritzventils im Bereich des Kopplers und
Fig. 4
ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils im Bereich des Kopplers.
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
FIG. 2 shows a schematic section of a fuel injection valve in the region of the coupler according to the prior art, similar to the fuel injection valve illustrated in FIG. 1, FIG.
Fig. 3
a not inventive example of a fuel injection valve in the region of the coupler and
Fig. 4
An embodiment of a fuel injection valve according to the invention in the region of the coupler.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Nachfolgend werden Ausführungsbeispiele beispielhaft beschrieben.Hereinafter, embodiments 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 den Fig. 1 und 2 kurz erläutert. Übereinstimmende Bauteile sind dabei in den Figuren mit übereinstimmenden Bezugszeichen versehen.Before the invention is described in more detail with reference to preferred embodiments, a fuel injection valve according to the prior art in its essential components in FIGS. 1 and 2 is briefly explained for better understanding. 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.The fuel injection valve 1 shown in FIG. 1 is 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 acts on the hydraulic coupler 7 with a bias, 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 can be seen.

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 in 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 Koppler aufgebauten Koppler 7.FIG. 2 shows a coupler 7 constructed similarly to the coupler shown in FIG.

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 eines als Zweitmediumkoppler ausgeführten Kopplers 7 realisiert, welcher ein nicht mit dem Brennstoff in Berührung kommendes Hydraulikmedium enthält. 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.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 a 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 between master piston 9 and Slave piston 10 formed coupler volume 23, which is connected to the expansion chamber 12 via a throttle 24.

Der Ausgleichsraum 12 ist innerhalb und außerhalb des Nehmerkolbens 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. 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.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. 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 eine Bohrung 29, welche beispielsweise mittels einer eingepreßten Kugel 30 verschlossen sein kann.The filling of the coupler 7, for example in the production, with hydraulic medium takes place through a bore 29, which may be closed, for example by means of a pressed-in ball 30.

Nachteilig an der beschriebenen Bauform des Brennstoffeinspritzventils 1 bzw. des hydraulischen Kopplers 7 ist dabei insbesondere, daß die Leckageverluste an dem in der Nut 27 angeordneten Dichtring 28 relativ hoch sind. Dies setzt die Dauerlauffestigkeit des Brennstoffeinspritzventils 1 herab, da das Hydraulikmedium am Dichtring 28 mit der Zeit in den Druckspeicherraum 32 leckt und damit auch die durch die Druckfeder 11 aufgebrachte Vorspannung nachläßt. Damit verändert der Koppler 7 unerwünscht sein Verhalten im Brennstoffeinspritzventil 1 über die Lebensdauer. Aufgrund der komplizierten Bauweise ist die Herstellung des Kopplers 7 sehr aufwendig und die Baugröße unvorteilhaft gesteigert. Außerdem ist insbesondere durch die Form des flexiblen Abschnitts eine relativ große Füllmenge des Hydraulikmediums notwendig. Dies aber erhöht die Temperaturabhängigkeit durch die Temperaturausdehnung.A disadvantage of the described design of the fuel injector 1 and the hydraulic coupler 7 is in particular that the leakage losses at the arranged in the groove 27 sealing ring 28 are relatively high. This reduces the fatigue strength of the fuel injection valve 1, since the hydraulic medium on the sealing ring 28 leaks over time into the pressure storage space 32 and thus also reduces the prestress applied by the compression spring 11. Thus, the coupler 7 undesirably changes its behavior in the fuel injection valve 1 over the lifetime. Due to the complicated design, the production of the coupler 7 is very expensive and the size increased unfavorably. In addition, in particular by the shape of the flexible portion, a relatively large capacity of the hydraulic medium necessary. But this increases the temperature dependence by the temperature expansion.

Abhilfe wird durch das im Folgenden beschriebene Ausführungsbeispiel eines als Zweitmediums-Koppler ausgeführten Kopplers 7 geschaffen, welcher einfach und kostengünstig herstellbar, weniger aufwendig gebaut, zuverlässig dauerlauffest ist und dessen Verhalten weniger temperaturabhängig ist.A remedy is provided by the embodiment described below of a designed as a second-medium coupler coupler 7, which is simple and inexpensive to manufacture, less expensive built, reliable continuous running and its behavior is less temperature-dependent.

Fig. 3 zeigt ein nicht erfindungsgemäßes Beispiel eines Kopplers 7 für ein Brennstoffeinspritzventil 1. Der Nehmerkolben 10 greift mit einem kolbenförmigen zweiten Nehmerabschnitt 35 in den im wesentlichen zylinderförmigen Geberkolben 9 ein. Der Nehmerkolben 10 bzw. der zweite Nehmerabschnitt 35 sind im Geberkolben 9 axial beweglich mit einem Führungsspalt 38 geführt. Der Führungsspalt 38 ist relativ klein, wobei die durch den Führungsspalt 38 im Betrieb durchtretende Menge an Hydraulikmedium vernachlässigbar klein ist. In anderen Ausführungsbeispielen kann der Führungsspalt 38 eine Drosselfunktion ausüben.FIG. 3 shows a non-inventive example of a coupler 7 for a fuel injection valve 1. The slave piston 10 engages with a piston-shaped second slave section 35 into the essentially cylindrical master piston 9. The slave piston 10 and the second slave section 35 are guided axially movably in the master piston 9 with a guide gap 38. The guide gap 38 is relatively small, wherein the amount of hydraulic medium passing through the guide gap 38 during operation is negligibly small. In other embodiments, the guide gap 38 may exert a throttle function.

In diesem Ausführungsbeispiel besteht der Nehmerkolben 10 aus einem ersten Nehmerabschnitt 34 und einem zweiten Nehmerabschnitt 35, wobei in anderen Ausführungsbeispielen der Nehmerkolben 10 auch einteilig ausgeführt werden kann. Der erste Nehmerabschnitt 34 ist zylinderförmig und verjüngt sich von einem Durchmesser, der etwa dem Durchmesser des Geberkolbens 9 entspricht, stufenförmig in Richtung des Geberkolbens 9, bzw. des zweiten Nehmerabschnitts 35. In diesem Ausführungsbeispiel verjüngt sich der erste Nehmerabschnitt 34 an einer Stufe 40 und weist dadurch einen T-förmigen Querschnitt auf. Der verjüngte Teil des ersten Nehmerabschnitts 34 greift teilweise koaxial in den zweiten Nehmerabschnitt 35 ein und ist dort bewegungsfest fixiert, beispielsweise durch Pressen oder Schweißen.In this embodiment, the slave piston 10 consists of a first slave section 34 and a second slave section 35, wherein in other embodiments, the slave piston 10 can also be made in one piece. The first slave section 34 is cylindrical and tapers from a diameter which corresponds approximately to the diameter of the master piston 9, stepwise in the direction of the master piston 9, and the second slave section 35. In this embodiment, the first slave section 34 tapers at a step 40 and thus has a T-shaped cross-section. The tapered part of the first slave portion 34 engages partially coaxially in the second slave portion 35 and is fixed there immovable, for example by pressing or welding.

Zwischen der Stufe 40 und dem dem ersten Nehmerabschnitt 34 zugewandten oberen Rand des Geberkolbens 9 verbleibt so eine in diesem Ausführungsbeispiel ringnutförmige Ausnehmung 39. Die Größe der Ausnehmung 39, d.h. der Abstand zwischen der Stufe 40 und dem oberen Rand des Geberkolbens 9, nimmt ab, wenn das Kopplervolumen 23 zunimmt.Between the step 40 and the first slave section 34 facing upper edge of the master piston 9 remains so a ringnutförmige in this embodiment recess 39. The size of the recess 39, i. the distance between the step 40 and the upper edge of the master piston 9, decreases as the coupler volume 23 increases.

Ein flexibler Abschnitt 13, der rohrförmig und elastisch ist und einen U-förmigen Durchmessereinzug 33 aufweist, ist umfänglich, im Bereich der Ausnehmung 39 angeordnet. Der U-förmige Durchmessereinzug 33 ragt dabei in die Ausnehmung 39. Im Bereich des oberen Endes ist der flexible Abschnitt 13 am Umfang des ersten Nehmerabschnitts 34 beispielsweise stoffschlüssig, hermetisch dicht gefügt. Im Bereich seines unteren Endes ist der flexible Abschnitt 13 umfänglich des Geberkolbens 9 hermetisch dicht gefügt.A flexible portion 13, which is tubular and elastic and has a U-shaped diameter retraction 33, is circumferentially disposed in the region of the recess 39. The U-shaped diameter retraction 33 protrudes into the recess 39. In the region of the upper end of the flexible portion 13 on the circumference of the first slave portion 34, for example, cohesively, hermetically sealed. In the region of its lower end, the flexible portion 13 is circumferentially hermetically sealed to the master piston 9.

Der Nehmerkolben 10 weist einen zentriert angeordneten Kanal 29 auf, der im Verlauf in einen Ausgleichskanal 36 übergeht und nach außen durch eine Kugel 30, welche nach dem Befüllen des Kopplers 7 mit Hydraulikmedium zum Verschließen des Kanals 29 eingebracht ist, verschlossen ist. Der Ausgleichskanal 36, welcher in diesem Ausführungsbeispiel als Stufenbohrung ausgebildet ist, endet an seinem dem Kopplervolumen 23 zugewandten Ende an einer Drosselscheibe 37, die zumindest eine als relativ kleine Bohrung ausgeführte, zentriert angeordnete Drossel 24 aufweist. Die Drossel 24 mündet in das Kopplervolumen 23.The slave piston 10 has a centered channel 29 which merges into a compensation channel 36 and is closed to the outside by a ball 30, which is introduced after filling the coupler 7 with hydraulic medium for closing the channel 29. The compensation channel 36, which is formed in this embodiment as a stepped bore, ends at its the coupler volume 23 facing the end of a throttle plate 37, which has at least one designed as a relatively small bore, centered throttle 24. The throttle 24 opens into the coupler volume 23.

Etwa auf Höhe des Übergangs des Kanals 29 in den Ausgleichskanals 36 befindet sich die Querbohrung 31, welche auch durch andere Formgebungsverfahren als Bohren hergestellt werden kann. Die Drosselscheibe 37 ist in die Oberfläche des zweiten Nehmerabschnitts 35 eingelassen und beispielsweise durch Schweißen stoffschlüssig an den zweiten Nehmerabschnitt 35 gefügt. Die Querbohrung 31 verbindet über die Drossel 24 das Kopplervolumen 23 mit dem Ausgleichsraum 12.Approximately at the level of the transition of the channel 29 in the compensation channel 36 is the transverse bore 31, which can also be prepared by other molding methods than drilling. The restrictor disk 37 is embedded in the surface of the second slave section 35 and, for example, joined to the second slave section 35 in a material-locking manner by welding. The transverse bore 31 connects via the throttle 24, the coupler volume 23 with the expansion chamber 12th

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 Ausgleichskanal 36 und die Querbohrung 31 in den Ausgleichsraum 12, der durch den elastischen und membranartigen flexiblen Abschnitt 13 teilweise begrenzt ist. Der flexible Abschnitt 13 übt durch eine Vorspannung einen Druck auf das Hydraulikmedium aus, wobei der flexible Abschnitt 13 so angeordnet bzw. ausgeführt sein kann, daß sich die Vorspannung durch die Verkleinerung der Ausnehmung 39 verstärken kann. Der flexible Abschnitt 13 übernimmt sowohl die Dichtfunktion als auch den Druckausgleich.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 equalization channel 36 and the transverse bore 31 in the Compensation space 12, which is partially limited by the elastic and membrane-like flexible portion 13. The flexible portion 13 exerts by a bias pressure from the hydraulic medium, wherein the flexible portion 13 may be arranged or carried out so that the bias can increase by the reduction of the recess 39. The flexible section 13 assumes both the sealing function and the pressure equalization.

Fig. 4 zeigt ein Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 im Bereich des Kopplers 7, ähnlich dem Ausführungsbeispiel aus Fig. 3. Im Unterschied zum Ausführungsbeispiel aus Fig. 3 ist der Kanal 29 im Geberkolben 9 angeordnet. Der Kanal 29 mündet direkt in das Kopplervolumen 23. Der Ausgleichskanal 36 verbindet das Kopplervolumen 23, den Ausgleichsraum 12 und eine Kammer 41 miteinander. Die Kammer 41 ist im Nehmerkolben 10 ausgebildet, wobei in diesem Ausführungsbeispiel die Kammer 41 durch eine erste Aussparung 44, die zentriert in einem den ersten Nehmerabschnitt 34 oben und seitlich umfassenden Anbauteil 43 angeordnet ist, und durch eine zweite Aussparung 45, die am oberen Ende des ersten Nehmerabschnitts 34 zentriert ausgebildet ist, gebildet wird.4 shows an exemplary embodiment of a fuel injection valve 1 according to the invention in the region of the coupler 7, similar to the exemplary embodiment from FIG. 3. In contrast to the exemplary embodiment from FIG. 3, the channel 29 is arranged in the master piston 9. The channel 29 opens directly into the coupler volume 23. The compensation channel 36 connects the coupler volume 23, the compensation chamber 12 and a chamber 41 with each other. The chamber 41 is formed in the slave piston 10, wherein in this embodiment, the chamber 41 by a first recess 44 which is centered in a first slave portion 34 above and laterally comprehensive attachment 43 is disposed, and by a second recess 45 at the upper end of the first slave section 34 is formed centered, is formed.

Die Aussparungen 44, 45 liegen unter Zwischenlage einer Membran 42 hydraulisch nach außen dicht aufeinander und bilden dabei die Kammer 41. Die Membran 42 besteht beispielsweise aus einem Elastomer und teilt die Kammer 41 hermetisch dicht in die erste Aussparung 44 und die zweite Aussparung 45. Die zweite Aussparung 45 steht über den Ausgleichskanal 36 mit dem Kopplervolumen 23 in Verbindung. Die erste Aussparung 44 ist beispielsweise mit einem Gas druckbehaftet gefüllt und übt so auf das Hydraulikmedium einen Druck aus. Alternativ hierzu kann der Kopplerinnendruck über eine zusätzlich in der Kammer 41 angeordneten Feder erzeugt werden, so daß der Innenraum 41 drucklos ist. Die Membran 42 ist elastisch und besteht aus einem Elastomer, beispielsweise aus Viton. Das zum Nehmerkolben 10 gehörende Anbauteil 43 ist beispielsweise durch Pressen und/oder Schweißen mit dem ersten Nehmerabschnitt 34 verbunden. Der flexible Abschnitt 13 ist mit seinem oberen Ende an der radial liegenden Außenfläche des Anbauteils 43 hermetisch dicht gefügt.The recesses 44, 45 lie with the interposition of a membrane 42 hydraulically outwardly close to each other and thereby form the chamber 41. The membrane 42 consists for example of an elastomer and divides the chamber 41 hermetically sealed into the first recess 44 and the second recess 45th Die second recess 45 is connected via the compensation channel 36 with the coupler volume 23 in connection. The first recess 44 is, for example, with a gas filled with pressure and thus exerts a pressure on the hydraulic medium. Alternatively, the internal coupler pressure can be generated via an additionally arranged in the chamber 41 spring, so that the interior 41 is depressurized. The membrane 42 is elastic and consists of an elastomer, for example of Viton. The attachment part 43 belonging to the slave piston 10 is connected, for example, by pressing and / or welding to the first slave section 34. The flexible portion 13 is hermetically sealed at its upper end to the radially outer surface of the attachment 43.

Die Erfindung ist auch für Brennstoffeinspritzventile 1 für selbstzündende Brennkraftmaschinen und/oder nach innen öffnende Brennstoffeinspritzventile, geeignet.The invention is also suitable for fuel injection valves 1 for self-igniting internal combustion engines and / or inwardly opening fuel injection valves.

Claims (17)

  1. Fuel injection valve (1) having a piezoelectric or magnetostrictive actuator (4) which activates 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) formed between them, the coupler volume (23) being connected via a throttle (24) to an equalization space (12), a flexible section (13) at least partially bounding the equalization space (12), and the coupler volume (23), the throttle (24) and the equalization space (12) being filled with a hydraulic medium, the flexible section (13) being elastic and having an essentially U-shaped diameter indent (33), the flexible section (13) applying, by virtue of its elastic behaviour, a pressure to the hydraulic medium and the equalization space (12) being connected to a chamber (41), characterized in that the chamber (41) is divided in a hydraulically sealed fashion into a first recess (44) and a second recess (45) by an elastic diaphragm (42).
  2. Fuel injection valve according to Claim 1, characterized in that the diameter indent (33) engages in a cut-out (39) or projects into the cut-out (39).
  3. Fuel injection valve according to Claim 2, characterized in that the cut-out (39) becomes axially smaller as the coupler volume (23) increases.
  4. Fuel injection valve according to Claim 3, characterized in that the decrease in size of the cut-out (39) increases the prestress of the flexible section (13) or of the diameter indent (33) upon the hydraulic medium.
  5. Fuel injection valve according to one of Claims 2 to 4, characterized in that the cut-out (33) is formed by a step (40) which is formed on the slave piston (10) and an upper edge of the master piston (9) which is directed towards the step (40).
  6. Fuel injection valve according to one of Claims 2 to 5, characterized in that the cut-out (33) is in the form of an annular groove.
  7. Fuel injection valve according to one of the preceding claims, characterized in that the equalization space (12) is bounded by the flexible section (12), the slave piston (10) and the master piston (9).
  8. Fuel injection valve according to one of the preceding claims, characterized in that the throttle (24) is embodied as a bore.
  9. Fuel injection valve according to one of the preceding claims, characterized in that the coupler volume (23) is connected to the equalization space (12) via an equalization duct (36) and a transverse bore (31) which is arranged in the slave piston (10).
  10. Fuel injection valve according to one of the preceding claims, characterized in that the throttle (24) is arranged in a throttle disc (37).
  11. Fuel injection valve according to one of the preceding claims, characterized in that the hydraulic medium is an oil-like fluid.
  12. Fuel injection valve according to Claim 1, characterized in that one of the two recesses (45) can exchange hydraulic medium with the equalization space (12).
  13. Fuel injection valve according to Claim 12, characterized in that the other recess (44) is filled with a gas under pressure.
  14. Fuel injection valve according to Claim 12, characterized in that a spring which generates an internal pressure in the coupler is arranged in the chamber (41).
  15. Fuel injection valve according to one of Claims 12 to 14, characterized in that the diaphragm (42) is composed of an elastomer, in particular of Viton.
  16. Fuel injection valve according to one of Claims 12 to 15, characterized in that the chamber (41) is arranged between a first slave section (34) of the slave piston (10) and an attachment part (43) which is connected to the first slave section (34).
  17. Fuel injection valve according to Claim 16, characterized in that the diaphragm (42) is clamped between the first slave section (34) and the attachment part (43).
EP20040105050 2003-12-03 2004-10-14 Fuel injection valve Expired - Lifetime EP1538331B1 (en)

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EP1591656B1 (en) * 2004-04-26 2008-03-12 Isuzu Motors Limited Differential expansion absorption mechanism and fuel injection valve comprising same
EP1780405B1 (en) * 2005-10-26 2008-09-17 Siemens Aktiengesellschaft Injector, compensation device for the injector and pressure transferring device for the compensation device
EP1813805A1 (en) * 2006-01-27 2007-08-01 Siemens VDO Automotive S.p.A. Compensation assembly for an injector
EP1918571B1 (en) * 2006-11-02 2010-08-18 Continental Automotive GmbH Injector for dosing fluid
EP2235251B1 (en) 2007-12-21 2018-03-07 BSH Hausgeräte GmbH Ironing device
EP2078846B1 (en) * 2008-01-14 2014-12-03 Continental Automotive GmbH Actuator arrangement and injection valve
DE102012202909A1 (en) * 2012-02-27 2013-08-29 Robert Bosch Gmbh Valve for metering fluid

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JPH0656162B2 (en) * 1987-03-03 1994-07-27 トヨタ自動車株式会社 Variable stroke device
EP0477400B1 (en) * 1990-09-25 2000-04-26 Siemens Aktiengesellschaft Device for compensating the tolerance in the lift direction of the displacement transformer of a piezoelectric actuator
WO1993006625A1 (en) * 1991-09-27 1993-04-01 Siemens Aktiengesellschaft Hydraulic displacement transformer for the piezoelectric actuator of an inlet valve
DE19962177A1 (en) * 1999-12-22 2001-07-12 Siemens Ag Hydraulic device for transmitting an actuator movement
US6676030B2 (en) * 2000-10-11 2004-01-13 Siemens Automotive Corporation Compensator assembly having a flexible diaphragm for a fuel injector and method
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
DE10149914A1 (en) * 2001-10-10 2003-04-24 Bosch Gmbh Robert Fuel injection valve consists of an actuator located in a housing connected on the side of a valve needle to a valve body
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
DE502004002718D1 (en) * 2003-02-27 2007-03-15 Bosch Gmbh Robert Fuel injector

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