[go: up one dir, main page]

WO2006003038A1 - Fuel injection valve - Google Patents

Fuel injection valve Download PDF

Info

Publication number
WO2006003038A1
WO2006003038A1 PCT/EP2005/051829 EP2005051829W WO2006003038A1 WO 2006003038 A1 WO2006003038 A1 WO 2006003038A1 EP 2005051829 W EP2005051829 W EP 2005051829W WO 2006003038 A1 WO2006003038 A1 WO 2006003038A1
Authority
WO
WIPO (PCT)
Prior art keywords
fuel injection
injection valve
spring sleeve
recesses
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.)
Ceased
Application number
PCT/EP2005/051829
Other languages
German (de)
French (fr)
Inventor
Dietmar Uhlmann
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 WO2006003038A1 publication Critical patent/WO2006003038A1/en
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices

Definitions

  • the invention is based on a fuel injection valve according to the preamble of patent claim 1.
  • Such a fuel injection valve has become known, for example, from DE 102 13382 A1.
  • the fuel injection valve known from DE 102 13 382 A1 has, as a spring element, a self-contained cylindrical spring sleeve, which has two recesses in a plurality of radial planes, so that the spring sleeve is elastically deformable in the axial direction.
  • the recesses are formed as waisted transverse slots with semicircular ends and all have the same shape or geometry.
  • the spring sleeve can be made by deep drawing in one piece, the recesses are formed after deep drawing, for example by means of a laser.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage that significantly lowered by this web and recess geometry, the voltage level at the same spring rate in the spring sleeve and thus the fatigue strength is significantly improved. As a result, a more uniform distribution of stress over the entire elliptical area on the inside of the spring sleeve adjusts itself at the end of the recess and forms the supporting components and the Stress distribution in the radial direction more uniform and homogeneous.
  • the high stress level not only concentrates locally on the inside of the spring sleeve, but the entire area over the wall thickness is used for carrying.
  • the elliptical contour at the recess end on the inside and outside is preferably the same. Especially with small outer diameters offers to make the spring sleeve of a thermoformed tube into which the slots are then introduced via saws.
  • Fig. 1 is a spring sleeve of the fuel injection valve according to the invention in a perspective view
  • FIG. 2 shows a detail view of the spring sleeve according to FIG. 1 in FIG. 1;
  • Fig. 3 is a cross-sectional view of the spring sleeve according to IH-III in Fig. 1;
  • Fig. 5 is a longitudinal section through a second inventive fuel injection valve with two spring sleeves.
  • the spring sleeve 1 shown in FIG. 1 has two recesses 2 in seven radial planes, which are each separated from one another by a web 3. Through the recesses 2, the spring sleeve 1 is elastically deformable in the axial direction.
  • the spring sleeve 1 is made for example of a deep-drawn tube, in which the recesses 2 are introduced by sawing.
  • the recesses 2 all have the same shape or geometry and are designed as extending in the circumferential direction of the spring sleeve 1 transverse slots with the same slot width d.
  • the recesses 2 of a radial plane are each arranged between two recesses 2 of the adjacent radial plane.
  • each recess 2 elliptical with two radii Ri, R 2 are formed.
  • This elliptical contour of the ends 4 is the same on the inside and outside of the spring sleeve 1.
  • the webs 3 are not ring segment-shaped in cross-section, but trapezoidal.
  • the webs 3 are symmetrical to their radial center plane 6, wherein the two side edges 7 of the webs 3 each run radially inwardly towards each other.
  • a more uniform stress distribution over the entire elliptical region on the inside of the spring sleeve 1 is established at the recess end 4, and the supporting components of the webs 3 and the stress distribution in the radial direction are more uniform and homogeneous.
  • the high stress level not only concentrates locally on the inside of the spring sleeve 1, but the entire area over the wall thickness is used for carrying. Overall, so the voltage level at the same spring rate in the spring sleeve 1 is significantly lowered, thus significantly improving the fatigue strength, which - compared to known spring sleeves with waisted transverse slots and semicircular slot ends - higher spring travel can be realized.
  • the spring sleeve 1 has a
  • the spring sleeve 1 makes sense to manufacture the spring sleeve 1 from a deep-drawn tube, in which the recesses 2 are introduced via saw cuts, which have the required contour.
  • the recesses 2 can also be cut into the tube by means of a laser.
  • the injection nozzle 10 of a fuel injection valve is shown, which projects into the combustion chamber of an internal combustion engine.
  • a valve needle 11 is slidably guided with a conical valve sealing surface 12, which hydraulically and by the spring sleeve 1 (schematically indicated as a helical spring) against a conical valve seat surface of
  • Injection nozzle 10 is pressed and closes the injection openings 13 provided there.
  • the valve needle 11 is limited with its side facing away from the combustion chamber a hydraulic control chamber 14 in which the spring sleeve 1 is arranged and supported on the housing side.
  • a feed line (not shown) opens into an annular gap 15 extending between guide bore and valve needle 21, which leads via an annular space 16 to the valve seat surface.
  • the valve needle 11 has in the annular space 16 a pressure shoulder 17 to which the pressure prevailing in the annular space 16 pressure on the valve needle 11 in the opening direction, while the prevailing in the control chamber 14 control pressure acts on the valve needle 11 in the closing direction.
  • valve needle 11 has on its side facing away from the combustion chamber a guide projection 18 on which the spring sleeve 1 is attached.
  • valve needle 11 is slidably guided in an additional valve sleeve 21.
  • the slidably guided in an axial guide bore valve sleeve 21 has a conical valve sealing surface 22 and is by a second spring sleeve 1 '(schematically indicated as a coil spring) pressed against a second conical valve seat surface of the injection nozzle 20, where it closes provided there second injection openings 23.
  • the other end of the spring sleeve 1 ' is supported on the housing side.
  • a supply line 24 opens into an annular gap 25 extending between the guide bore and the valve sleeve 21, which leads to the second valve seat surface.
  • the valve sleeve 21 has in the region of the feed line 24 a pressure shoulder 26, on which the fuel supplied via the feed line 24 acts in the opening direction on the valve sleeve 21. If the pressure acting on the pressure shoulder 36 is sufficient to control the valve sleeve 21 against the action of the spring sleeve V, the injection takes place with the pressure prevailing in the annular gap 25
  • Valve needle 11 and valve sleeve 21 are not coupled to each other, so that the injection can be done either with the pressure prevailing in the annular space 16 or in the annular gap 25 fuel pressure.

Landscapes

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

Abstract

The inventive fuel injection valve for internal combustion engines comprises at least one valve member which controls a fuel supply to the combustion chamber of the engine by displacement thereof oppositely to elastic force of a cylindrical axially deformable spring sleeve (1), wherein said spring sleeve (1) comprises at least two recesses (2) which are arranged on each of several radial planes and are embodied in the form of transverse slots extending in the circumferential direction of said sleeve (1). The invention is characterised in that the width (d) of the recess (2) slots is constant and the ends (4) thereof are embodied in the ellipsoid form and the cross section of a web (3) disposed between two recesses (2) is not shaped in the form of an annular segment.

Description

Kraftstoffeinspritzventil Fuel injection valve

Stand der TechnikState of the art

Die Erfindung geht aus von einem Kraftstoffeinspritzventil nach der Gattung des Patentanspruchs 1.The invention is based on a fuel injection valve according to the preamble of patent claim 1.

Ein solches Kraftstoffeinspritzventil ist beispielsweise durch die DE 102 13382 A1 bekannt geworden.Such a fuel injection valve has become known, for example, from DE 102 13382 A1.

Das aus DE 102 13 382 A1 bekannte Kraftstoffeinspritzventil weist als Federelement eine in sich geschlossene zylindrische Federhülse auf, die in mehreren Radialebenen jeweils zwei Aussparungen aufweist, so dass die Federhülse in Axialrichtung elastisch verformbar ist. Die Aussparungen sind als taillierte Querschlitze mit halbkreisrunden Enden ausgebildet und haben alle die gleiche Form bzw. Geometrie. Die Federhülse kann durch Tiefziehen aus einem Stück hergestellt werden, wobei die Aussparungen nach dem Tiefziehen beispielsweise mittels eines Lasers ausgebildet werden.The fuel injection valve known from DE 102 13 382 A1 has, as a spring element, a self-contained cylindrical spring sleeve, which has two recesses in a plurality of radial planes, so that the spring sleeve is elastically deformable in the axial direction. The recesses are formed as waisted transverse slots with semicircular ends and all have the same shape or geometry. The spring sleeve can be made by deep drawing in one piece, the recesses are formed after deep drawing, for example by means of a laser.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil für Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, dass durch diese Steg- und Aussparungsgeometrie das Spannungsniveau bei gleicher Federrate in der Federhülse deutlich abgesenkt und damit die Dauerfestigkeit wesentlich verbessert wird. Dadurch stellt sich am Aussparungsende eine gleichförmigere Spannungsverteilung über den gesamten elliptischen Bereich an der Innenseite der Federhülse ein und gestalten sich die Traganteile und die Spannungsverteilung in radialer Richtung gleichförmiger und homogener. Das hohe Spannungsniveau konzentriert sich nicht nur lokal auf die Innenseite der Federhülse, sondern der gesamte Bereich über die Wanddicke wird zum Tragen herangezogen. Die elliptische Kontur am Aussparungsende auf der Innen- und Außenseite ist vorzugsweise gleich. Insbesondere bei kleinen Außendurchmessern bietet sich an, die Federhülse aus einem tiefgezogenen Rohr zu fertigen, in das die Schlitze dann über Sägen eingebracht werden.The fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage that significantly lowered by this web and recess geometry, the voltage level at the same spring rate in the spring sleeve and thus the fatigue strength is significantly improved. As a result, a more uniform distribution of stress over the entire elliptical area on the inside of the spring sleeve adjusts itself at the end of the recess and forms the supporting components and the Stress distribution in the radial direction more uniform and homogeneous. The high stress level not only concentrates locally on the inside of the spring sleeve, but the entire area over the wall thickness is used for carrying. The elliptical contour at the recess end on the inside and outside is preferably the same. Especially with small outer diameters offers to make the spring sleeve of a thermoformed tube into which the slots are then introduced via saws.

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

Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils sind in den Zeichnungen dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:Embodiments of the fuel injection valve according to the invention are illustrated in the drawings and explained in more detail in the following description. Show it:

Fig. 1 eine Federhülse des erfindungsgemäßen Kraftstoffeinspritzventils in perspektivischer Ansicht;Fig. 1 is a spring sleeve of the fuel injection valve according to the invention in a perspective view;

Fig. 2 eine Detailansicht der Federhülse gemäß Il in Fig. 1 ;FIG. 2 shows a detail view of the spring sleeve according to FIG. 1 in FIG. 1; FIG.

Fig. 3 eine Querschnittansicht der Federhülse gemäß IH-III in Fig. 1;Fig. 3 is a cross-sectional view of the spring sleeve according to IH-III in Fig. 1;

Fig.4 einen Längsschnitt durch ein erstes erfindungsgemäßes4 shows a longitudinal section through a first invention

Kraftstoffeinspritzventil mit einer Federhülse; undFuel injection valve with a spring sleeve; and

Fig. 5 einen Längsschnitt durch ein zweites erfindungsgemäßes Kraftstoffeinspritzventil mit zwei Federhülsen.Fig. 5 is a longitudinal section through a second inventive fuel injection valve with two spring sleeves.

Beschreibung der Ausführungsbeispiele Die in Fig. 1 gezeigte Federhülse 1 weist in sieben Radialebenen jeweils zwei Aussparungen 2 auf, die jeweils durch einen Steg 3 voneinander getrennt sind. Durch die Aussparungen 2 ist die Federhülse 1 in Axialrichtung elastisch verformbar. Die Federhülse 1 ist beispielsweise aus einem tiefgezogenen Rohr gefertigt, in das die Aussparungen 2 durch Sägen eingebracht sind. Die Aussparungen 2 haben alle die gleiche Form bzw. Geometrie und sind als in Umfangsrichtung der Federhülse 1 verlaufende Querschlitze mit gleich bleibender Schlitzbreite d ausgebildet. Die Aussparungen 2 der einen Radialebene sind jeweils zwischen zwei Aussparungen 2 der benachbarten Radialebene angeordnet.Description of the embodiments The spring sleeve 1 shown in FIG. 1 has two recesses 2 in seven radial planes, which are each separated from one another by a web 3. Through the recesses 2, the spring sleeve 1 is elastically deformable in the axial direction. The spring sleeve 1 is made for example of a deep-drawn tube, in which the recesses 2 are introduced by sawing. The recesses 2 all have the same shape or geometry and are designed as extending in the circumferential direction of the spring sleeve 1 transverse slots with the same slot width d. The recesses 2 of a radial plane are each arranged between two recesses 2 of the adjacent radial plane.

Wie Fig. 2 zeigt, sind die beiden Enden 4 jeder Aussparung 2 ellipsenförmig mit zwei Radien Ri, R2 ausgebildet. Diese ellipsenförmige Kontur der Enden 4 ist auf der Innen- und Außenseite der Federhülse 1 gleich.As shown in FIG. 2, the two ends 4 of each recess 2 elliptical with two radii Ri, R 2 are formed. This elliptical contour of the ends 4 is the same on the inside and outside of the spring sleeve 1.

Wie Fig. 3 zeigt, sind die Stege 3 im Querschnitt nicht ringsegmentförmig, sondern trapezähnlich ausgebildet. Die Stege 3 sind symmetrisch zu ihrer radialen Mittelebene 6, wobei die beiden Seitenflanken 7 der Stege 3 jeweils radial nach innen aufeinander zulaufen. Durch diese Steg- und Aussparungsgeometrie stellt sich am Aussparungsende 4 eine gleichförmigere Spannungsverteilung über den gesamten elliptischen Bereich an der Innenseite der Federhülse 1 ein und gestalten sich die Traganteile der Stege 3 und die Spannungsverteilung in radialer Richtung gleichförmiger und homogener. Das hohe Spannungsniveau konzentriert sich nicht nur lokal auf die Innenseite der Federhülse 1 , sondern der gesamte Bereich über die Wanddicke wird zum Tragen herangezogen. Insgesamt wird so das Spannungsniveau bei gleicher Federrate in der Federhülse 1 deutlich abgesenkt und damit die Dauerfestigkeit wesentlich verbessert, wodurch - im Vergleich zu bekannten Federhülsen mit taillierten Querschlitzen und halbkreisförmigen Schlitzenden - höhere Federwege realisiert werden können.As shown in FIG. 3, the webs 3 are not ring segment-shaped in cross-section, but trapezoidal. The webs 3 are symmetrical to their radial center plane 6, wherein the two side edges 7 of the webs 3 each run radially inwardly towards each other. As a result of this ridge and recess geometry, a more uniform stress distribution over the entire elliptical region on the inside of the spring sleeve 1 is established at the recess end 4, and the supporting components of the webs 3 and the stress distribution in the radial direction are more uniform and homogeneous. The high stress level not only concentrates locally on the inside of the spring sleeve 1, but the entire area over the wall thickness is used for carrying. Overall, so the voltage level at the same spring rate in the spring sleeve 1 is significantly lowered, thus significantly improving the fatigue strength, which - compared to known spring sleeves with waisted transverse slots and semicircular slot ends - higher spring travel can be realized.

Im gezeigten Ausführungsbeispiel hat die Federhülse 1 hat einenIn the illustrated embodiment, the spring sleeve 1 has a

Außendurchmesser von 1,9 mm, eine Wanddicke von 0,2 mm und eine Länge von 5,6 mm. Die Schlitzhöhe d beträgt 0,25 mm, die axiale Balkenhöhe zwischen den Aussparungen 2 0,14 mm und die minimale Stegbreite in Umfangsrichtung 0,144 mm. Die Radien Ri und R2 betragen 0,375 mm bzw. R2=0,08 mm. Die Steglänge in Umfangsrichtung ist auf Innen- und Außenseite unterschiedlich und beträgt auf der Innenseite 0,042 mm und auf der Außenseite 0,046 mm, so dass der durch die beiden Stegflanken 7 definierte Winkel ca. 101° beträgt.Outer diameter of 1.9 mm, a wall thickness of 0.2 mm and a length of 5.6 mm. The slot height d is 0.25 mm, the axial beam height between the recesses 2 0.14 mm and the minimum web width in the circumferential direction 0.144 mm. The radii Ri and R2 are 0.375 mm and R2 = 0.08 mm. The bridge length in The circumferential direction is different on the inside and outside and is 0.042 mm on the inside and 0.046 mm on the outside, so that the angle defined by the two web flanks 7 is approximately 101 °.

Insbesondere bei so kleinen Außendurchmessers bietet es sich an, die Federhülse 1 aus einem tiefgezogenen Rohr zu fertigen, bei dem die Aussparungen 2 über Sägeschnitte eingebracht werden, welche die geforderte Kontur aufweisen. Alternativ können die Aussparungen 2 auch mittels eines Lasers in das Rohr geschnitten werden.Especially with such small outer diameter, it makes sense to manufacture the spring sleeve 1 from a deep-drawn tube, in which the recesses 2 are introduced via saw cuts, which have the required contour. Alternatively, the recesses 2 can also be cut into the tube by means of a laser.

In Fig.4 ist die Einspritzdüse 10 eines Kraftstoffeinspritzventils gezeigt, die in den Brennraum einer Brennkraftmaschine ragt. In einer axialen Führungsbohrung der Einspritzdüse 10 ist eine Ventilnadel 11 mit einer konischen Ventildichtfläche 12 verschiebbar geführt, welche hydraulisch und durch die Federhülse 1 (schematisch als Schraubenfeder angedeutet) gegen eine konische Ventilsitzfläche der4, the injection nozzle 10 of a fuel injection valve is shown, which projects into the combustion chamber of an internal combustion engine. In an axial guide bore of the injection nozzle 10, a valve needle 11 is slidably guided with a conical valve sealing surface 12, which hydraulically and by the spring sleeve 1 (schematically indicated as a helical spring) against a conical valve seat surface of

Einspritzdüse 10 gedrückt wird und die dort vorgesehenen Einspritzöffnungen 13 verschließt. Die Ventilnadel 11 begrenzt mit ihrer dem Brennraum abgewandten Stirnseite einen hydraulischen Steuerraum 14, in dem die Federhülse 1 angeordnet und gehäuseseitig abgestützt ist. Eine Zulaufleitung (nicht gezeigt) mündet in einen zwischen Führungsbohrung und Ventilnadel 21 verlaufenden Ringspalt 15, der über einen Ringraum 16 bis zur Ventilsitzfläche führt. Die Ventilnadel 11 hat im Ringraum 16 eine Druckschulter 17, an welcher der im Ringraum 16 herrschende Druck an der Ventilnadel 11 im Öffnungssinn angreift, während der im Steuerraum 14 herrschende Steuerdruck an der Ventilnadel 11 in Schließrichtung angreift. Wenn der im Ringraum 16 herrschende Druck ausreicht, die Ventilnadel 11 gegen die Wirkung der Federhülse 1 und des im Steuerraum 14 herrschenden Steuerdrucks aufzusteuern, erfolgt die Einspritzung mit dem im Ringraum 16 herrschenden Kraftstoffdruck. Die Ventilnadel 11 hat auf ihrer dem Brennraum abgewandten Stirnseite einen Führungsansatz 18, auf den die Federhülse 1 aufgesteckt ist.Injection nozzle 10 is pressed and closes the injection openings 13 provided there. The valve needle 11 is limited with its side facing away from the combustion chamber a hydraulic control chamber 14 in which the spring sleeve 1 is arranged and supported on the housing side. A feed line (not shown) opens into an annular gap 15 extending between guide bore and valve needle 21, which leads via an annular space 16 to the valve seat surface. The valve needle 11 has in the annular space 16 a pressure shoulder 17 to which the pressure prevailing in the annular space 16 pressure on the valve needle 11 in the opening direction, while the prevailing in the control chamber 14 control pressure acts on the valve needle 11 in the closing direction. If the pressure prevailing in the annular space 16 sufficient pressure to aufzusteuern the valve needle 11 against the action of the spring sleeve 1 and the ruling in the control chamber 14 control pressure, the injection takes place with the ruling in the annular space 16 fuel pressure. The valve needle 11 has on its side facing away from the combustion chamber a guide projection 18 on which the spring sleeve 1 is attached.

Von der Einspritzdüse 10 unterscheidet sich die in Fig. 5 gezeigte Kraftstoffeinspritzdüse 20 darin, dass die Ventilnadel 11 in einer zusätzlichen Ventilhülse 21 verschiebbar geführt ist. Die in einer axialen Führungsbohrung verschiebbar geführte Ventilhülse 21 hat eine konische Ventildichtfläche 22 und ist durch eine zweite Federhülse 1' (schematisch als Schraubenfeder angedeutet) gegen eine zweite konische Ventilsitzfläche der Einspritzdüse 20 gedrückt, wo sie dort vorgesehene zweite Einspritzöffnungen 23 verschließt. Das andere Ende der Federhülse 1' ist gehäuseseitig abgestützt. Eine Zulaufleitung 24 mündet in einen zwischen Führungsbohrung und Ventilhülse 21 verlaufenden Ringspalt 25, der bis zur zweiten Ventilsitzfläche führt. Die Ventilhülse 21 hat im Bereich der Zulaufleitung 24 eine Druckschulter 26, an welcher der über die Zuleitung 24 zugeführte Kraftstoff im Öffnungssinn an der Ventilhülse 21 angreift. Wenn der an der Druckschulter 36 angreifende Druck ausreicht, die Ventilhülse 21 gegen die Wirkung der Federhülse V aufzusteuern, erfolgt die Einspritzung mit dem im Ringspalt 25 herrschendenFrom the injection nozzle 10, the fuel injection nozzle 20 shown in Fig. 5 differs in that the valve needle 11 is slidably guided in an additional valve sleeve 21. The slidably guided in an axial guide bore valve sleeve 21 has a conical valve sealing surface 22 and is by a second spring sleeve 1 '(schematically indicated as a coil spring) pressed against a second conical valve seat surface of the injection nozzle 20, where it closes provided there second injection openings 23. The other end of the spring sleeve 1 'is supported on the housing side. A supply line 24 opens into an annular gap 25 extending between the guide bore and the valve sleeve 21, which leads to the second valve seat surface. The valve sleeve 21 has in the region of the feed line 24 a pressure shoulder 26, on which the fuel supplied via the feed line 24 acts in the opening direction on the valve sleeve 21. If the pressure acting on the pressure shoulder 36 is sufficient to control the valve sleeve 21 against the action of the spring sleeve V, the injection takes place with the pressure prevailing in the annular gap 25

Kraftstoffdruck. Ventilnadel 11 und Ventilhülse 21 sind miteinander nicht gekoppelt, so dass die Einspritzung wahlweise mit dem im Ringraum 16 oder im Ringspalt 25 herrschenden Kraftstoffdruck erfolgen kann. Fuel pressure. Valve needle 11 and valve sleeve 21 are not coupled to each other, so that the injection can be done either with the pressure prevailing in the annular space 16 or in the annular gap 25 fuel pressure.

Claims

Patentansprüche claims 1. Kraftstoffeinspritzventil für Brennkraftmaschinen, mit mindestens einem Ventilglied (11; 21), das durch seine Bewegung entgegen der elastischen Kraft einer in Axialrichtung verformbaren zylindrischen Federhülse (1 ; 1 ') die1. A fuel injection valve for internal combustion engines, comprising at least one valve member (11, 21), which by its movement against the elastic force of an axially deformable cylindrical spring sleeve (1, 1 ') the Kraftstoffzufuhr zum Brennraum der Brennkraftmaschine steuert, wobei die Federhülse (1; 1') in mehreren Radialebenen jeweils mindestens zwei Aussparungen (2) aufweist und die Aussparungen (2) als in Umfaπgsrichtung der Federhülse (1 ; 1') verlaufende Querschlitze ausgebildet sind, dadurch gekennzeichnet, dass die Aussparungen (2) eine gleich bleibende Schlitzbreite (d) und etwa ellipsenförmig ausgebildete Enden (14) aufweisen und dass der Querschnitt eines zwischen zwei Aussparungen (2) befindlichen Steges (3) nicht ringsegmentförmig ist.Fuel supply to the combustion chamber of the internal combustion engine controls, wherein the spring sleeve (1, 1 ') in each case at least two recesses (2) in several radial planes and the recesses (2) in the Umfaπgsrichtung the spring sleeve (1, 1') extending transverse slots are formed, characterized characterized in that the recesses (2) have a constant slot width (d) and approximately elliptical-shaped ends (14) and that the cross section of a between two recesses (2) located web (3) is not ring segment-shaped. 2. Kraftstoffeinspritzventil nach Anspruch 1 , dadurch gekennzeichnet, dass das ellipsenförmig ausgebildete Ende (4) einer Aussparung (2) durch mindestens zwei Radien (Ri, R2) definiert ist.2. Fuel injection valve according to claim 1, characterized in that the elliptically shaped end (4) of a recess (2) by at least two radii (Ri, R2) is defined. 3. Kraftstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die ellipsenförmige Kontur des Endes (4) auf der Innen- und Außenseite der Federhülse (1; 1') gleich ist.3. Fuel injection valve according to claim 1 or 2, characterized in that the elliptical contour of the end (4) on the inside and outside of the spring sleeve (1, 1 ') is equal. 4. Kraftstoffeinspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass der Querschnitt der Stege (3) trapezähnlich ist.4. Fuel injection valve according to one of the preceding claims, characterized in that the cross section of the webs (3) is trapezoidal. 5. Kraftstoffeinspritzventil nach Anspruch 4, dadurch gekennzeichnet, dass die beiden Seitenflanken (7) des im Querschnitt trapezähnlichen Steges (3) radial nach innen zulaufen. 5. Fuel injection valve according to claim 4, characterized in that the two side edges (7) of the cross-sectionally trapezoidal web (3) run radially inwardly. 6. Kraftstoffeinspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass alle Aussparungen (2) eine identische Form und jeweils symmetrisch zu ihrer axialen Mittelebene (6) sind und dass alle Stege (3) eine identische Form und jeweils symmetrisch zu ihrer axialen Mittelebene (6) sind.6. Fuel injection valve according to one of the preceding claims, characterized in that all the recesses (2) are of identical shape and in each case symmetrical to its axial center plane (6) and that all the webs (3) have an identical shape and in each case symmetrical to its axial center plane ( 6). 7. Kraftstoffeinspritzventil nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die Federhülse (1 ) einen Außendurchmesser von kleiner als ca. 5 mm, vorzugsweise gleich oder kleiner als ca. 2 mm, und eine Wanddicke von kleiner als ca. 0,5, vorzugsweise von ca. 0,2 mm, hat.7. Fuel injection valve according to one of the preceding claims, characterized in that the spring sleeve (1) has an outer diameter of less than about 5 mm, preferably equal to or less than about 2 mm, and a wall thickness of less than about 0.5, preferably of about 0.2 mm. 8. Verfahren zum Herstellen der Federhülse (1 ; 1') eines Kraftstoffeinspritzventils nach einem der vorhergehenden Ansprüche, wobei die Aussparungen (2) mittels einer Säge oder eines Lasers in ein Rohr geschnitten werden.8. A method of manufacturing the spring sleeve (1, 1 ') of a fuel injection valve according to one of the preceding claims, wherein the recesses (2) are cut into a tube by means of a saw or a laser. 9. Verfahren nach Anspruch 8, dadurch gekennzeichnet, dass das Sägeblatt der Säge eine etwa ellipsenförmige Kontur aufweist. 9. The method according to claim 8, characterized in that the saw blade of the saw has an approximately elliptical contour.
PCT/EP2005/051829 2004-06-30 2005-04-25 Fuel injection valve Ceased WO2006003038A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004031597A DE102004031597A1 (en) 2004-06-30 2004-06-30 Fuel injection valve
DE102004031597.3 2004-06-30

Publications (1)

Publication Number Publication Date
WO2006003038A1 true WO2006003038A1 (en) 2006-01-12

Family

ID=34966580

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/EP2005/051829 Ceased WO2006003038A1 (en) 2004-06-30 2005-04-25 Fuel injection valve

Country Status (2)

Country Link
DE (1) DE102004031597A1 (en)
WO (1) WO2006003038A1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102006035038A1 (en) 2006-07-28 2008-01-31 Epcos Ag Spring element for pre-loading of piezo actuator, comprises tube shape body of recesses, where recesses is formed in form of polygon with round corner
US8100346B2 (en) 2007-11-30 2012-01-24 Caterpillar Inc. Piezoelectric actuator with multi-function spring and device using same

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0283987A (en) * 1988-09-21 1990-03-26 Toyota Motor Corp Piezoelectric actuator
DE4335329A1 (en) * 1993-10-18 1995-04-20 Fichtel & Sachs Ag Rolled bush, in particular for a vibration damper
WO2000008353A1 (en) * 1998-08-06 2000-02-17 Siemens Aktiengesellschaft Piezoelectric actuator unit
US20030034594A1 (en) * 2001-08-16 2003-02-20 Robert Bosch Gmbh Spring bushing and method for producing a spring bushing
WO2003033933A1 (en) * 2001-10-09 2003-04-24 Siemens Aktiengesellschaft Method for producing a tubular spring and an actuator unit comprising one such tubular spring
DE10213382A1 (en) 2002-03-26 2003-10-16 Bosch Gmbh Robert Fuel injection valve

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0283987A (en) * 1988-09-21 1990-03-26 Toyota Motor Corp Piezoelectric actuator
DE4335329A1 (en) * 1993-10-18 1995-04-20 Fichtel & Sachs Ag Rolled bush, in particular for a vibration damper
WO2000008353A1 (en) * 1998-08-06 2000-02-17 Siemens Aktiengesellschaft Piezoelectric actuator unit
US20030034594A1 (en) * 2001-08-16 2003-02-20 Robert Bosch Gmbh Spring bushing and method for producing a spring bushing
WO2003033933A1 (en) * 2001-10-09 2003-04-24 Siemens Aktiengesellschaft Method for producing a tubular spring and an actuator unit comprising one such tubular spring
DE10213382A1 (en) 2002-03-26 2003-10-16 Bosch Gmbh Robert Fuel injection valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 014, no. 268 (E - 0939) 11 June 1990 (1990-06-11) *

Also Published As

Publication number Publication date
DE102004031597A1 (en) 2006-02-09

Similar Documents

Publication Publication Date Title
DE112005002698T5 (en) Fuel pump with a guided plunger assembly and method of guidance and assembly
WO2017207156A1 (en) High-pressure accumulator and method for producing a high-pressure accumulator
DE3914486A1 (en) METHOD FOR PRODUCING A VALVE NEEDLE AND VALVE NEEDLE
DE102016217117A1 (en) Frequency-selective damping valve arrangement
EP2297447B1 (en) High-pressure pump
DE69915946T2 (en) poetry
EP2824311A1 (en) Piston element assembly, and fuel injector with a piston element assembly
DE10232050A1 (en) Fuel injection valve, for an IC motor, has micro-recesses in the valve needle sealing surface and/or the valve seat to improve the drift behavior of the injected fuel volume and increase the working life
DE10152261A1 (en) High pressure accumulators like high pressure fuel accumulators
EP1519072B1 (en) Tubular spring for actuators
DE102004011284A1 (en) High-pressure pump, in particular for a fuel injection device of an internal combustion engine
EP1356203B1 (en) Device for supplying high pressure fuel to an internal combustion engine
DE19943402A1 (en) Self-tensioner creates measured tension in engine synchronous belt in order to reduce noise and prolong useful life, is of free piston type with body in which piston is moved
WO2006003038A1 (en) Fuel injection valve
DE102004027825A1 (en) High-pressure pump, especially for fuel injection device for internal combustion engine, has smallest throughflow cross-section region downstream of sealing surface when valve element in open position
EP1605159B1 (en) Fuel injector
EP1423601B1 (en) High pressure fuel accumulator for an accumulator injection system
WO2005078273A1 (en) High pressure pump, in particular for a fuel injection device in an internal combustion engine
DE10346075B4 (en) Method for producing a fuel injection valve and fuel injection valve produced by this method
EP1076771B1 (en) Fuel injection valve for internal combustion engines
EP3054149A1 (en) Device for fixing at least one fuel injection nozzle
DE19942983B4 (en) Hydraulic clearance compensation element
DE10132756B4 (en) Actuator for switching elements of fuel injectors
EP1076770B1 (en) Fuel injection valve for internal combustion engines
EP1846655A1 (en) Method for producing an injector body and corresponding injector body

Legal Events

Date Code Title Description
AK Designated states

Kind code of ref document: A1

Designated state(s): AE AG AL AM AT AU AZ BA BB BG BR BW BY BZ CA CH CN CO CR CU CZ DK DM DZ EC EE EG ES FI GB GD GE GH GM HR HU ID IL IN IS JP KE KG KM KP KR KZ LC LK LR LS LT LU LV MA MD MG MK MN MW MX MZ NA NI NO NZ OM PG PH PL PT RO RU SC SD SE SG SK SL SM SY TJ TM TN TR TT TZ UA UG US UZ VC VN YU ZA ZM ZW

AL Designated countries for regional patents

Kind code of ref document: A1

Designated state(s): BW GH GM KE LS MW MZ NA SD SL SZ TZ UG ZM ZW AM AZ BY KG KZ MD RU TJ TM AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LT LU MC NL PL PT RO SE SI SK TR BF BJ CF CG CI CM GA GN GQ GW ML MR NE SN TD TG

122 Ep: pct application non-entry in european phase