EP1893866B1 - Valve for controlling an injection valve of an internal combustion engine - Google Patents

Valve for controlling an injection valve of an internal combustion engine Download PDF

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Publication number
EP1893866B1
EP1893866B1 EP06725667A EP06725667A EP1893866B1 EP 1893866 B1 EP1893866 B1 EP 1893866B1 EP 06725667 A EP06725667 A EP 06725667A EP 06725667 A EP06725667 A EP 06725667A EP 1893866 B1 EP1893866 B1 EP 1893866B1
Authority
EP
European Patent Office
Prior art keywords
valve
annular shoulder
sealing ring
bore
sealing
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.)
Not-in-force
Application number
EP06725667A
Other languages
German (de)
French (fr)
Other versions
EP1893866A1 (en
Inventor
Martin Boehm
Helmut Clauss
Arnad Beganovic
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 EP1893866A1 publication Critical patent/EP1893866A1/en
Application granted granted Critical
Publication of EP1893866B1 publication Critical patent/EP1893866B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—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
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/004—Joints; Sealings

Definitions

  • the invention relates to a valve for controlling an injection valve of an internal combustion engine according to the preamble of patent claim 1.
  • Such a valve is for example by the WO 2004/036033 A known.
  • a known control valve comprises a valve piece which is arranged in a stepped bore of the valve housing to form a high-pressure side annular space which is sealed relative to the valve housing by sealing contact of the valve member at a first annular shoulder of the bore and axially spaced therefrom by a sealing ring, with its one axial end face (sealing edge) bears against a second annular shoulder of the bore.
  • the other axial end face is axially spaced from an annular shoulder of the valve piece which is provided in the region of the first annular shoulder of the bore and axially delimits the high-pressure-side annular space.
  • valve according to the invention with the features of claim 1 has the advantage that the mounted under bias sealing ring seals the annulus immediately after installation.
  • the annular shoulder of the valve piece is chamfered and the annular shoulder of the bore conical, so that the pressure prevailing in the annulus high pressure presses the sealing ring to the two annular shoulders. The higher the high pressure, the greater the contact pressure and consequently the sealing of the annulus (self-sealing effect).
  • valve 1 serves to control an injection valve (injector) of an internal combustion engine and has an annular space 2 , which has a Fuel line 3 is connected to a high-pressure fuel storage (CommonRail), not shown.
  • CommonRail high-pressure fuel storage
  • the high-pressure side annular space 2 is formed in a stepped bore 4 of the valve housing 5 by a cylindrical, metallic valve piece 6 , which with a flange 7 on a first, in Fig.1 upper annular shoulder 8 of the bore 4 sealingly rests and - axially spaced therefrom - is sealed by a high-pressure sealing ring (O-ring) 9 relative to the valve housing 5.
  • a high-pressure sealing ring (O-ring) 9 relative to the valve housing 5.
  • the sealing ring 9 has a trapezoidal cross-section and is pressed between a tapered annular shoulder 10 of the valve member 6 and a lower, conical annular shoulder 11 of the bore 4, that is clamped with bias. Already due to this bias seals the sealing ring 9 in the clamped state, the annulus 2 immediately.
  • the sealing ring 9 is parallel with its two sealing flanks on the annular shoulders 10, 11 and has, in the embodiment shown, the tapered annular shoulder 10 and the conical annular shoulder 11 at the same angle ⁇ to the longitudinal axis, in cross-section the shape of a symmetrical trapezoid ,
  • the outer diameter d of the sealing ring 9 is smaller than the bore diameter D, so that the pressure prevailing in the annular space 2 high pressure (rail pressure) presses the sealing ring 9 radially inwardly of the annular shoulders 10, 11.
  • the higher the rail pressure the greater the contact pressure and consequently the sealing of the annulus 2 (self-sealing effect).
  • the contact force is generated, which presses the sealing ring 9 to the annular shoulder 10, 11 and ensures the sealing of the annulus2.
  • the upper end of a piston-shaped valve or actuator 12 of the injector is slidably guided in a guide bore 13 of the valve member 6 and limited in the valve piece 6 a control chamber 14.
  • the control chamber 14 is connected via an inlet throttle 15 with the annular space 2 and opens via an outlet throttle 16th in a valve seat opening of a conical valve seat 17, which is provided on the valve or actuator 12 facing away from the upper end side of the valve member 6 for cooperation with a valve closure member 18 .
  • valve closing member 18 In the closed valve position, not shown, in which the valve closing member 18 rests against the valve seat 17 and thus closes the valve seat opening, the control chamber 14 is acted upon by rail pressure and thereby the valve or actuator 12 of the injector moved to its lower position.
  • the valve closing member 18 In the open valve position shown, the valve closing member 18 is lifted from the valve seat 17 and the valve seat opening released, whereby the control chamber 14 is depressurized and the valve or actuator 12 is moved to its upper position.

Abstract

The valve (1) according to the invention for controlling an injection valve of an internal combustion engine comprises a valve element (6) which is arranged in a stepped bore (4) of the valve housing (5) with the formation of a high-pressure-side annular space (2) which is sealed with respect to the valve housing (5) by sealing contact of the valve element (6) with a first annular shoulder (8) of the bore (4) and, axially spaced apart therefrom, by a sealing ring (9), the sealing ring (9) being arranged between an annular shoulder (10) of the valve element (6) and a second annular shoulder (12) of the bore (4), in particular being clamped in with prestress.

Description

Stand der TechnikState of the art

Die Erfindung betrifft ein Ventil zur Steuerung eines Einspritzventils einer Brennkraftmaschine nach der Gattung des Patentanspruchs 1.The invention relates to a valve for controlling an injection valve of an internal combustion engine according to the preamble of patent claim 1.

Ein derartiges Ventil ist beispielsweise durch die WO 2004/036033 A bekannt geworden.Such a valve is for example by the WO 2004/036033 A known.

Bei bekannten Magnetventilen von Einspritzsystemen (Common Rail Injektoren) ist zwischen Ventilgehäuse (Injektorkörper) und einem Ventilstück ein hochdruckseitiger Ringraum gebildet, der über zwei axial beabstandete Dichtstellen, nämlich über die dichtende Anlage des Ventilstücks am Ventilgehäuse einerseits und andererseits über einen meist noch mit einem Stützring abgestützten Dichtring, abgedichtet ist.In known solenoid valves of injection systems (common rail injectors) between the valve housing (injector) and a valve piece, a high-pressure side annular space formed over two axially spaced sealing points, namely on the sealing contact of the valve piece on the valve housing on the one hand and on the other hand usually with a support ring supported sealing ring, is sealed.

Das aus WO 2004/036033 A bekannte Steuerventil umfasst ein Ventilstück, das in einer gestuften Bohrung des Ventilgehäuses unter Ausbildung eines hochdruckseitigen Ringraums angeordnet ist, welcher gegenüber dem Ventilgehäuse durch dichtende Anlage des Ventilstücks an einem ersten Ringabsatz der Bohrung und davon axial beabstandet durch einen Dichtring abgedichtet ist, der mit seiner einen axialen Stirnseite (Dichtflanke) an einem zweiten Ringabsatz der Bohrung anliegt. Die andere axiale Stirnseite ist von einem Ringabsatz des Ventilstücks, der im Bereich des ersten Ringabsatzes der Bohrung vorgesehen ist und den hochdruckseitigen Ringraum axial begrenzt, axial beabstandet.The end WO 2004/036033 A known control valve comprises a valve piece which is arranged in a stepped bore of the valve housing to form a high-pressure side annular space which is sealed relative to the valve housing by sealing contact of the valve member at a first annular shoulder of the bore and axially spaced therefrom by a sealing ring, with its one axial end face (sealing edge) bears against a second annular shoulder of the bore. The other axial end face is axially spaced from an annular shoulder of the valve piece which is provided in the region of the first annular shoulder of the bore and axially delimits the high-pressure-side annular space.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Ventil mit den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, dass der unter Vorspannung montierte Dichtring den Ringraum sofort nach der Montage abdichtet. Bevorzugt ist der Ringabsatz des Ventilstücks angeschrägt und der Ringabsatz der Bohrung konisch, so dass der im Ringraum herrschende Hochdruck den Dichtring an die beiden Ringabsätze presst. Je höher der Hochdruck, desto größer ist die Anpresskraft und folglich die Abdichtung des Ringraums (selbstdichtender Effekt).The valve according to the invention with the features of claim 1 has the advantage that the mounted under bias sealing ring seals the annulus immediately after installation. Preferably, the annular shoulder of the valve piece is chamfered and the annular shoulder of the bore conical, so that the pressure prevailing in the annulus high pressure presses the sealing ring to the two annular shoulders. The higher the high pressure, the greater the contact pressure and consequently the sealing of the annulus (self-sealing effect).

Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegenstands der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject invention are the description, the drawings and claims removed.

Zeichnungendrawings

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

Fig. 1
einen Längsschnitt durch ein erstes Ausführungsbeispiel des erfindungsgemäßen Ventils;
Fig. 2
eine vergrößerte Detailansicht gemäß II in Fig. 1;
Fig. 3
ein zweites Ausführungsbeispiel des erfindungsgemäßen Ventils in einer Darstellung analog zu Fig. 2; und
Fig. 4
ein drittes Ausführungsbeispiel des erfindungsgemäßen Ventils in einer Darstellung analog zu Fig. 2.
Various embodiments of the invention are illustrated in the drawings and explained in more detail in the following description. Show it:
Fig. 1
a longitudinal section through a first embodiment of the valve according to the invention;
Fig. 2
an enlarged detail view according to II in Fig. 1 ;
Fig. 3
A second embodiment of the valve according to the invention in a representation analogous to Fig. 2 ; and
Fig. 4
a third embodiment of the valve according to the invention in a representation analogous to Fig. 2 ,

Beschreibung des AusführungsbeispielsDescription of the embodiment

Das in Fig. 1 gezeigte Ventil 1 dient zur Steuerung eines Einspritzventils (Injektor) einer Brennkraftmaschine und weist einen Ringraum 2 auf, der über eine Kraftstoffleitung 3 an einen nicht gezeigten Kraftstoff-Hochdruckspeicher (CommonRail) angeschlossen ist.This in Fig. 1 shown valve 1 serves to control an injection valve (injector) of an internal combustion engine and has an annular space 2 , which has a Fuel line 3 is connected to a high-pressure fuel storage (CommonRail), not shown.

Der hochdruckseitige Ringraum 2 ist in einer gestuften Bohrung 4 des Ventilgehäuses 5 durch ein zylindrisches, metallisches Ventilstück 6 gebildet, welches mit einem Flansch 7 auf einem ersten, in Fig.1 oberen Ringabsatz 8 der Bohrung 4 dichtend aufliegt und - davon nach unten axial beabstandet - durch einen Hochdruck-Dichtring (O-Ring) 9 gegenüber dem Ventilgehäuse 5 abgedichtet ist. Durch eine Ventilspannschraube (nicht gezeigt) ist der Flansch 7 gegen den oberen Ringabsatz 8 gedrückt. Der Dichtring 9 hat einen trapezförmigen Querschnitt und ist zwischen einem angeschrägten Ringabsatz 10 des Ventilstücks 6 und einem unteren, konischen Ringabsatz 11 der Bohrung 4 eingepresst, d.h. mit Vorspannung eingespannt. Schon aufgrund dieser Vorspannung dichtet der Dichtring 9 im eingespannten Zustand den Ringraum 2 sofort ab.The high-pressure side annular space 2 is formed in a stepped bore 4 of the valve housing 5 by a cylindrical, metallic valve piece 6 , which with a flange 7 on a first, in Fig.1 upper annular shoulder 8 of the bore 4 sealingly rests and - axially spaced therefrom - is sealed by a high-pressure sealing ring (O-ring) 9 relative to the valve housing 5. By a valve clamping screw (not shown), the flange 7 is pressed against the upper annular shoulder 8. The sealing ring 9 has a trapezoidal cross-section and is pressed between a tapered annular shoulder 10 of the valve member 6 and a lower, conical annular shoulder 11 of the bore 4, that is clamped with bias. Already due to this bias seals the sealing ring 9 in the clamped state, the annulus 2 immediately.

Wie in Fig. 2 gezeigt, liegt der Dichtring 9 mit seinen beiden Dichtflanken an den Ringabsätzen 10, 11 parallel an und hat, da im gezeigten Ausführungsbeispiel der angeschrägte Ringabsatz 10 und der konische Ringabsatzes 11 unter dem gleichen Winkel α zur Längsachse verlaufen, im Querschnitt die Form eines symmetrischen Trapezes. Der Außendurchmesser d des Dichtrings 9 ist kleiner als der Bohrungsdurchmesser D, so dass der im Ringraum 2 herrschende Hochdruck (Raildruck) den Dichtring 9 radial nach innen an die Ringabsätze 10, 11 presst. Je höher der Raildruck, desto größer ist die Anpresskraft und folglich die Abdichtung des Ringraums 2 (selbstdichtender Effekt). Mit anderen Worten wird durch den im Ringraum 2 herrschenden Betriebsdruck die Anpresskraft erzeugt, die den Dichtring 9 an die Ringabsatz 10, 11 presst und für die Abdichtung des Ringraum2 sorgt.As in Fig. 2 shown, the sealing ring 9 is parallel with its two sealing flanks on the annular shoulders 10, 11 and has, in the embodiment shown, the tapered annular shoulder 10 and the conical annular shoulder 11 at the same angle α to the longitudinal axis, in cross-section the shape of a symmetrical trapezoid , The outer diameter d of the sealing ring 9 is smaller than the bore diameter D, so that the pressure prevailing in the annular space 2 high pressure (rail pressure) presses the sealing ring 9 radially inwardly of the annular shoulders 10, 11. The higher the rail pressure, the greater the contact pressure and consequently the sealing of the annulus 2 (self-sealing effect). In other words, by the pressure prevailing in the annular space 2 operating pressure, the contact force is generated, which presses the sealing ring 9 to the annular shoulder 10, 11 and ensures the sealing of the annulus2.

Das obere Ende eines kolbenförmigen Ventil- oder Stellglieds 12 des Einspritzventils ist in einer Führungsbohrung 13 des Ventilstückes 6 verschiebbar geführt und begrenzt im Ventilstück 6 einen Steuerraum 14. Der Steuerraum 14 ist über eine Zulaufdrossel 15 mit dem Ringraum 2 verbunden und mündet über eine Ablaufdrossel 16 in eine Ventilsitzöffnung eines konischen Ventilsitzes 17, der auf der dem Ventil- oder Stellglied 12 abgewandten oberen Stirnseite des Ventilstücks 6 zum Zusammenwirken mit einem Ventilschließglied 18 vorgesehen ist.The upper end of a piston-shaped valve or actuator 12 of the injector is slidably guided in a guide bore 13 of the valve member 6 and limited in the valve piece 6 a control chamber 14. The control chamber 14 is connected via an inlet throttle 15 with the annular space 2 and opens via an outlet throttle 16th in a valve seat opening of a conical valve seat 17, which is provided on the valve or actuator 12 facing away from the upper end side of the valve member 6 for cooperation with a valve closure member 18 .

In der nicht gezeigten geschlossenen Ventilstellung, in der das Ventilschließglied 18 am Ventilsitz 17 anliegt und somit die Ventilsitzöffnung verschließt, ist der Steuerraum 14 mit Raildruck beaufschlagt und dadurch das Ventil- oder Stellglied 12 des Einspritzventils in seine untere Stellung verschoben. In der gezeigten geöffneten Ventilstellung ist das Ventilschließglied 18 vom Ventilsitz 17 abgehoben und die Ventilsitzöffnung freigegeben, wodurch der Steuerraum 14 druckentlastet wird und das Ventil- oder Stellglied 12 in seine obere Stellung verschoben ist.In the closed valve position, not shown, in which the valve closing member 18 rests against the valve seat 17 and thus closes the valve seat opening, the control chamber 14 is acted upon by rail pressure and thereby the valve or actuator 12 of the injector moved to its lower position. In the open valve position shown, the valve closing member 18 is lifted from the valve seat 17 and the valve seat opening released, whereby the control chamber 14 is depressurized and the valve or actuator 12 is moved to its upper position.

Von Fig. 2 unterscheidet sich das in Fig. 3 gezeigte Ausführungsbeispiel allein dadurch, dass die beiden Dichtflanken des trapezförmigen Dichtrings 9' nicht parallel zu den unter dem Winkel α zur Längsachse verlaufenden Ringabsätzen 10, 11, sondern unter einem steileren Winkel β zur Längsachse verlaufen.From Fig. 2 this is different in Fig. 3 shown embodiment only in that the two sealing flanks of the trapezoidal sealing ring 9 ' not parallel to the α at the angle to the longitudinal axis extending annular shoulders 10, 11, but at a steeper angle β to the longitudinal axis.

Von Fig. 2 unterscheidet sich das in Fig. 4 gezeigte Ausführungsbeispiel allein dadurch, dass der Dichtring 9" im Wesentlichen rechteckförmig ausgebildet ist und mit zwei Dichtkanten an den Ringabsätzen 10, 11 anliegt.From Fig. 2 this is different in Fig. 4 shown embodiment only in that the sealing ring 9 " is substantially rectangular in shape and rests with two sealing edges on the annular shoulders 10, 11.

Claims (10)

  1. Valve (1) for controlling an injection valve of an internal combustion engine, with a valve piece (6) which is arranged in a stepped bore (4) of the valve housing (5) so as to form a high-pressure-side annular space (2) which is sealed off with respect to the valve housing (5) by the valve piece (6) coming to bear sealingly against a first annular shoulder (8) of the bore (4) and, spaced apart axially from this, by means of a sealing ring (9; 9'; 9") which bears with its one axial sealing flank or sealing edge against a second annular shoulder (11) of the bore (4), characterized in that the sealing ring (9; 9'; 9") bears with its other axial sealing flank or sealing edge against an annular shoulder (10) of the valve piece (6).
  2. Valve according to Claim 1, characterized in that the sealing ring (9; 9'; 9") is tension-mounted with prestress between the annular shoulder (10) of the valve piece (6) and the second annular shoulder (11) of the bore (4).
  3. Valve according to Claim 1 or 2, characterized in that the annular shoulder (10) of the valve piece (6) is bevelled and the second annular shoulder (11) of the bore (4) is conical.
  4. Valve according to one of the preceding claims, characterized in that the sealing ring (9; 9') has a trapezoidal cross section.
  5. Valve according to Claim 4, characterized in that the two axial sealing flanks of the sealing ring (9) run in each case approximately parallel to the bevelled annular shoulder (10) and to the conical annular shoulder (11).
  6. Valve according to Claim 4, in combination with Claim 3, characterized in that the two axial sealing flanks of the sealing ring (9') run at a steeper angle (β) to the axial longitudinal axis of the valve housing (5) or of the valve piece (6) than the annular shoulders (10, 11).
  7. Valve according to one of Claims 1 to 3, characterized in that the sealing ring (9") has an approximately rectangular cross section.
  8. Valve according to one of Claims 3 to 7, Claims 4 and 7 referring back in each case to Claim 3, characterized in that the bevelled annular shoulder (10) and the conical annular shoulder (11) run at about the same angle (α) to the axial longitudinal axis of the valve housing (5) or of the valve piece (6).
  9. Valve according to one of the preceding claims, characterized in that the outside diameter (d) of the sealing ring (9; 9'; 9")is smaller than the bore diameter (D) of the annular space (2).
  10. Valve according to one of the preceding claims, characterized in that a control space (14) in a guide bore (13) of the valve piece (6) is delimited by a valve member or actuating member (12) of the injection valve, the said valve member or actuating member being guided displaceably in the said guide bore, the control space (14) being connected to the high-pressure-side annular space (2) via an inflow throttle (15) and issuing via an outflow throttle (16) into a valve-seat orifice of a valve seat (17) which is provided, on that end face of the valve piece (6) which faces away from the valve member or actuating member (12), for cooperating with a movable valve-closing member (18).
EP06725667A 2005-06-09 2006-04-10 Valve for controlling an injection valve of an internal combustion engine Not-in-force EP1893866B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102005026513A DE102005026513A1 (en) 2005-06-09 2005-06-09 Valve for controlling an injection valve of an internal combustion engine
PCT/EP2006/061466 WO2006131411A1 (en) 2005-06-09 2006-04-10 Valve for controlling an injection valve of an internal combustion engine

Publications (2)

Publication Number Publication Date
EP1893866A1 EP1893866A1 (en) 2008-03-05
EP1893866B1 true EP1893866B1 (en) 2009-08-19

Family

ID=36600206

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06725667A Not-in-force EP1893866B1 (en) 2005-06-09 2006-04-10 Valve for controlling an injection valve of an internal combustion engine

Country Status (5)

Country Link
EP (1) EP1893866B1 (en)
CN (1) CN101194098B (en)
AT (1) ATE440215T1 (en)
DE (2) DE102005026513A1 (en)
WO (1) WO2006131411A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007008262A1 (en) * 2007-02-20 2008-08-21 Robert Bosch Gmbh Fuel injection valve for fuel injection in internal combustion engines

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ATE24594T1 (en) * 1982-05-13 1987-01-15 Hydrotechnik Gmbh VALVE COUPLING FOR FLUIDIC SYSTEMS.
DE19802244A1 (en) * 1998-01-22 1999-07-29 Bosch Gmbh Robert Fuel injection valve for IC engines
JP3486383B2 (en) * 1999-12-17 2004-01-13 株式会社日立ユニシアオートモティブ Gas injection valve
US6845756B2 (en) * 2001-05-21 2005-01-25 Robert Bosch Gmbh High-pressure sealing element to four injectors
JP2004137915A (en) * 2002-10-15 2004-05-13 Bosch Automotive Systems Corp Sealing construction of fuel injection valve

Also Published As

Publication number Publication date
WO2006131411A1 (en) 2006-12-14
ATE440215T1 (en) 2009-09-15
CN101194098A (en) 2008-06-04
DE502006004601D1 (en) 2009-10-01
CN101194098B (en) 2011-01-05
EP1893866A1 (en) 2008-03-05
DE102005026513A1 (en) 2006-12-14

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