EP0809756A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines

Info

Publication number
EP0809756A1
EP0809756A1 EP96934344A EP96934344A EP0809756A1 EP 0809756 A1 EP0809756 A1 EP 0809756A1 EP 96934344 A EP96934344 A EP 96934344A EP 96934344 A EP96934344 A EP 96934344A EP 0809756 A1 EP0809756 A1 EP 0809756A1
Authority
EP
European Patent Office
Prior art keywords
valve
spring
fuel injection
internal combustion
injection valve
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.)
Granted
Application number
EP96934344A
Other languages
German (de)
French (fr)
Other versions
EP0809756B1 (en
Inventor
Karl Hofmann
Peter Kuegel
Ibrahim Oezyesilova
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 EP0809756A1 publication Critical patent/EP0809756A1/en
Application granted granted Critical
Publication of EP0809756B1 publication Critical patent/EP0809756B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • F02M61/168—Assembling; Disassembling; Manufacturing; Adjusting
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a valve member is guided axially displaceably in a valve body.
  • the valve member has one at one end on the combustion chamber side
  • Valve sealing surface with which it interacts for the purpose of controlling an injection cross section with a fixed valve seat on the valve body.
  • the valve member is acted upon at its other end remote from the combustion chamber by a valve spring, which the valve member abuts on
  • This valve spring is inserted into a spring chamber within the housing of the injection valve here in a holding body and is supported with its end facing away from the valve member on a stationary stop surface.
  • the valve spring is as
  • Coil spring formed the turns of a spring wire have a circular cross section.
  • the spring force of the valve spring determines the opening pressure at the injection valve, which is built up by the high fuel pressure acting on the valve member in the opening direction.
  • the performance or the spring force of the valve spring is therefore of great importance, this spring force being essentially dependent on the wire cross-sectional area at the windings. If the spring force is to be increased, it is customary with conventional round wire to increase the wire thickness, since its maximum area results from the given external and
  • the known fuel injection valve has the disadvantage that an increase in the wire thickness or an axial extension of the valve spring for one
  • valve spring which is designed as a helical spring, from stronger Spring wire is made with an enlarged basic cross-section on the windings and then ground on the outer diameter to such an extent that the valve spring can be inserted straight into the cylindrical spring chamber and only has as much play with the inner wall as with
  • the initially circular basic cross section of the spring windings then has bevels at its ends pointing radially outward to the spring axis, which are aligned parallel to the spring axis and to the wall of the spring chamber.
  • the tolerance on the outside diameter of the valve spring towards unprocessed springs can be reduced to a minimum.
  • the valve spring designed according to the invention has the advantage over alternative wire cross-sections such as rectangular, elliptical or other shaped wires that there is no additional outlay in wire production and the valve spring is therefore easier and cheaper to produce than these solutions.
  • the subsequent grinding of the outside diameter of the valve spring also enables a more precise outside diameter on the spring and thus a better use of space in the specified spring chamber.
  • possible material defects on the outside diameter of the valve spring are also removed in this way.
  • the use of this optimized spring is not limited to the use described in a fuel injection valve, but can be carried out wherever the spring force of a return spring should be increased despite a limited installation space, for example in injection pumps or gas exchange valves of internal combustion engines and the like.
  • Fuel injection valve for internal combustion engines is shown in the drawing and is explained in more detail in the following description.
  • Fuel injection valve and Figure 2 is an enlarged sectional view of the valve spring from Figure 1.
  • a piston-shaped valve member 1 is axially displaceably guided in a bore 3 in a valve body 5, which has a conical end at one end near the combustion chamber of the internal combustion engine
  • valve sealing surface 7, with which it interacts with a conical valve seat 9 on the inwardly projecting closed end of the bore 3.
  • the valve body 5 is with its end remote from the combustion chamber by means of a clamping nut 11 axially clamped against a valve holding body 13, an intermediate disk 15 with a central opening being clamped between the end faces of the valve body 5 and the valve holding body 13.
  • the valve body 5 is with its end remote from the combustion chamber by means of a clamping nut 11 axially clamped against a valve holding body 13, an intermediate disk 15 with a central opening being clamped between the end faces of the valve body 5 and the valve holding body 13.
  • Valve member 1 via a pressure piece 17 projecting through the intermediate disk 15 is acted upon by a valve spring 19 designed as a helical spring in the direction of the valve seat 9, which is inserted into a cylindrical spring chamber 21 in the valve holding body 13 and which on the other hand is fixed on a stationary wall formed by the upper axial wall of the spring chamber 21 Stop 23 supports.
  • a valve spring 19 designed as a helical spring in the direction of the valve seat 9, which is inserted into a cylindrical spring chamber 21 in the valve holding body 13 and which on the other hand is fixed on a stationary wall formed by the upper axial wall of the spring chamber 21 Stop 23 supports.
  • Injection opening 25 is provided in the wall of the valve body 5, which opens out from the bore 3 into the combustion chamber of the internal combustion engine to be supplied.
  • the high-pressure fuel supply to the sealing seat takes place in a known manner via an annular channel 27 formed between the shaft of the valve member 1 and the wall of the bore 3, which extends in the region of a ring shoulder 31 of the valve member 1 into a pressure chamber 29, one of which is not shown Injection pump discharging pressure line 33 opens.
  • valve spring 19 has, as shown in FIG cylindrical spring chamber 21 are aligned.
  • the valve spring 19 is first made from a round spring wire with such a large cross section y that the theoretical outer diameter of the unprocessed valve spring 19 is larger than the inner diameter of the spring chamber 21.
  • as much material is removed from the outer diameter of the valve spring, preferably ground that the valve spring 19 can be used with the necessary clearance in the spring chamber 21.
  • the remaining cross-sectional area z of the spring coils 41 is still significantly larger than the cross-sectional area of an unprocessed valve spring with an annular spring wire, the outside diameter of which is the same size, despite the cuts 43, so that the spring force of the valve spring 19 achieved can be increased considerably without additional installation space.
  • the ratio of y / z is preferably in a range from 1.05 to 1.3.

Landscapes

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

Abstract

A fuel injection valve for internal combustion engines with a valve member axial movable in a valve body and having at one end a valve sealing surface by which it operates together with a fixed valve seat to control an injection cross-section and with at least one valve spring (19) forcing the valve member towards the valve seat which is supported at the other side on a fixed stop. To increase the spring pressure of the valve spring (19) for the same outside diameter, the turns (41) of the helical valve spring (19) have an enlarged circular basic cross-section (y) on which there is a ground portion (43) directed parallel to the spring axis (X) in a region pointing outwards radially to the spring axis (X).

Description

Kraftstoffeinspritzventil für Brennkraftmaschinen Fuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einem derartigen, aus der DE-PS 29 43 744 bekannten Kraftstoffeinspritzventil ist ein Ventilglied axial verschiebbar in einem Ventilkörper geführt. Das Ventilglied weist an seinem einen, brennraumseitigen Ende eineThe invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. In such a fuel injector known from DE-PS 29 43 744, a valve member is guided axially displaceably in a valve body. The valve member has one at one end on the combustion chamber side
Ventildichtfläche auf, mit der es zum Zweck der Steuerung eines Einspritzquerschnittes mit einem ortsfesten Ventilsitz am Ventilkörper zusammenwirkt. Daε Ventilglied wird dabei an seinem anderen, brennraumfernen Ende von einer Ventilfeder beaufschlagt, die das Ventilglied in Anlage an denValve sealing surface with which it interacts for the purpose of controlling an injection cross section with a fixed valve seat on the valve body. The valve member is acted upon at its other end remote from the combustion chamber by a valve spring, which the valve member abuts on
Ventilsitz preßt. Diese Ventilfeder ist in einen Federraum innerhalb des Gehäuses des Einspritzventils hier in einem Haltekörper eingesetzt und stützt sich mit ihrem dem Ventilglied abgewandten Ende an einer ortsfesten Anschlagfläche ab. Die Ventilfeder ist dabei alsValve seat presses. This valve spring is inserted into a spring chamber within the housing of the injection valve here in a holding body and is supported with its end facing away from the valve member on a stationary stop surface. The valve spring is as
Schraubenfeder ausgebildet, deren aus einem Federdraht bestehende Windungen einen kreisförmigen Querschnitt aufweisen. Dabei bestimmt die Federkraft der Ventilfeder den Öffnungsdruck am Einspritzventil, der vom in Öffnungsrichtung am Ventilglied angreifenden Kraftstoffhochdruck aufgebaut wird. Der Leistungsfähigkeit bzw. der Federkraft der Ventilfeder kommt somit eine hohe Bedeutung zu, wobei diese Federkraft wesentlich von der Drahtquerschnittsfläche an den Windungen abhängig ist. Soll die Federkraft erhöht werden ist es bei herkömmlichem runden Draht üblich, die Drahtstärke zu erhöhen, da sich dessen maximale Fläche aus dem vorgegebenen Außen- undCoil spring formed, the turns of a spring wire have a circular cross section. The spring force of the valve spring determines the opening pressure at the injection valve, which is built up by the high fuel pressure acting on the valve member in the opening direction. The performance or the spring force of the valve spring is therefore of great importance, this spring force being essentially dependent on the wire cross-sectional area at the windings. If the spring force is to be increased, it is customary with conventional round wire to increase the wire thickness, since its maximum area results from the given external and
Innendurchmesser des Windungsquerschnittes ergibt.Inside diameter of the winding cross section results.
Dabei weist das bekannte Kraftstoffeinspritzventil jedoch den Nachteil auf, daß einer Vergrößerung der Drahtstärke oder einer axialen Verlängerung der Ventilfeder für eineHowever, the known fuel injection valve has the disadvantage that an increase in the wire thickness or an axial extension of the valve spring for one
Erhöhung der Federkraft konstruktive Grenzen gesetzt sind, da der vorgegebene Bauraum des Federraumes begrenzt ist und sich nicht ohne umfangreiche Änderungen am Einspritzventil vergrößern läßt, so daß eine Erhöhung der Federkraft der Ventilfeder nicht ohne aufwendige Veränderungen am Einspritzventil möglich ist.Increasing the spring force are constructive limits, since the given space of the spring chamber is limited and cannot be increased without extensive changes to the injection valve, so that an increase in the spring force of the valve spring is not possible without complex changes to the injection valve.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil fürThe fuel injector according to the invention for
Brennkraftmaschinen mit den kennzeichnenden Merkmalen des Patentanspruchs 1 hat demgegenüber den Vorteil, daß die Federkraft der Ventilfeder vergrößert werden kann, ohne dabei den benötigten Einbauraum der Ventilfeder im Gehäuse des Einspritzventils zu vergrößern, wobei dieser Vorteil besonders an Federn mit sehr kleinem Innendurchmesser und somit kleinem Wickelverhältnis (Dm/y bis zu 2,5) auftritt.Internal combustion engines with the characterizing features of claim 1 have the advantage that the spring force of the valve spring can be increased without increasing the required installation space of the valve spring in the housing of the injection valve, this advantage especially on springs with a very small inner diameter and thus a small winding ratio (Dm / y up to 2.5) occurs.
Dies wird in vorteilhafter Weise möglich, indem die als Schraubenfeder ausgebildete Ventilfeder aus stärkerem Federdraht mit einem vergrößerten Grundquerschnitt an den Windungen gefertigt wird und dann am Außendurchmesser soweit abgeschliffen wird, daß die Ventilfeder gerade in den zylindrischen Federraum einsetzbar ist und dort zur Innenwand lediglich so viel Spiel aufweist, wie beimThis is advantageously possible by making the valve spring, which is designed as a helical spring, from stronger Spring wire is made with an enlarged basic cross-section on the windings and then ground on the outer diameter to such an extent that the valve spring can be inserted straight into the cylindrical spring chamber and only has as much play with the inner wall as with
Zusammendrücken der Ventilfeder benötigt wird. Der zunächst kreisförmige Grundquerschnitt der Federwindungen weist dann an seinen zur Federachse radial auswärts weisenden Enden Anschliffe auf, die parallel zur Federachse und zur Wand des Federraumes ausgerichtet sind.Compression of the valve spring is required. The initially circular basic cross section of the spring windings then has bevels at its ends pointing radially outward to the spring axis, which are aligned parallel to the spring axis and to the wall of the spring chamber.
Auf diese Weise lassen sich bei gleichbleibendem Bauraum der Ventilfeder größere Öffnungsdrücke und bei der Verwendung von zwei hintereinander wirksam werdenden Ventilfedern an sogenannten 2-Feder-Haltern größere Öffnungsdruckdifferenzen realisieren.In this way, larger opening pressures can be achieved while the installation space of the valve spring remains the same and larger opening pressure differences when using two valve springs which act in succession on so-called 2-spring holders.
Zudem kann die Toleranz am Außendurchmesser der Ventilfeder gegenüber unbearbeiteten Federn auf ein Minimalmaß reduziert werden.In addition, the tolerance on the outside diameter of the valve spring towards unprocessed springs can be reduced to a minimum.
Dabei hat die erfindungsgemäß ausgebildete Ventilfeder gegenüber alternativen Drahtquerschnitten wie rechteckigen, elliptischen oder sonstigen Formdrähten den Vorteil, daß kein Mehraufwand bei der Drahtherstellung anfällt und die Ventilfeder somit gegenüber diesen Lösungen leichter und kostengünstiger herstellbar ist. Durch das nachträgliche Abschleifen des Außendurchmessers der Ventilfeder lassen sich zudem genauere Außendurchmesser an der Feder und somit eine bessere Raumausnutzung im vorgegebenen Federraum erreichen. Zudem werden auf diese Weise mögliche Werkstoff- Fehler am Außendurchmesser der Ventilfeder gleichzeitig mitentfernt. Die Verwendung dieser optimierten Feder ist dabei nicht auf den beschriebenen Einsatz in einem Kraftstoffeinspritzventil beschränkt, sondern kann überall dort erfolgen, wo trotz eines beschränkten Einbauraumes die Federkraft einer Rückstellfeder erhöht werden soll, z.B. bei Einspritzpumpen oder Gaswechselventilen von Brennkraftmaschinen und ähnlichem.The valve spring designed according to the invention has the advantage over alternative wire cross-sections such as rectangular, elliptical or other shaped wires that there is no additional outlay in wire production and the valve spring is therefore easier and cheaper to produce than these solutions. The subsequent grinding of the outside diameter of the valve spring also enables a more precise outside diameter on the spring and thus a better use of space in the specified spring chamber. In addition, possible material defects on the outside diameter of the valve spring are also removed in this way. The use of this optimized spring is not limited to the use described in a fuel injection valve, but can be carried out wherever the spring force of a return spring should be increased despite a limited installation space, for example in injection pumps or gas exchange valves of internal combustion engines and the like.
Weitere Vorteile und vorteilhafte Ausgestaltungen deε Gegenstandes der Erfindung sind der Beschreibung, der Zeichnung und den Ansprüchen entnehmbar.Further advantages and advantageous embodiments of the subject matter of the invention can be found in the description, the drawing and the claims.
Zeichnungdrawing
Ein Ausführungsbeispiel des erfindungsgemaßenAn embodiment of the invention
Kraftstoffeinspritzventils für Brennkraftmaschinen ist in der Zeichnung dargestellt und wird in der folgenden Beschreibung näher erläutert.Fuel injection valve for internal combustion engines is shown in the drawing and is explained in more detail in the following description.
Es zeigen die Figur 1 einen Längsschnitt durch das1 shows a longitudinal section through the
Kraftstoffeinspritzventil und die Figur 2 eine vergrößerte Einzelschnittdarstellung der Ventilfeder aus der Figur 1.Fuel injection valve and Figure 2 is an enlarged sectional view of the valve spring from Figure 1.
BesehreibungDescription
Bei dem in der Figur 1 dargestellten Ausführungsbeispiel deε erfindungsgemäßen Kraftstoffeinspritzventils für Brennkraftmaschinen ist ein kolbenförmiges Ventilglied 1 axial verschiebbar in einer Bohrung 3 eines Ventilkörpers 5 geführt, das an seinem einen, dem Brennraum der Brennkraftmaschine nahen Ende eine konischeIn the embodiment of the fuel injection valve according to the invention for internal combustion engines shown in FIG. 1, a piston-shaped valve member 1 is axially displaceably guided in a bore 3 in a valve body 5, which has a conical end at one end near the combustion chamber of the internal combustion engine
Ventildichtfläche 7 aufweist, mit der es mit einem konischen Ventilsitz 9 am nach innen kragenden geschlossenen Ende der Bohrung 3 zusammenwirkt. Der Ventilkörper 5 ist dabei mit seinem brennraumfernen Ende mittels einer Spannmutter 11 axial gegen einen Ventilhaltekörper 13 verspannt, wobei zwischen den Stirnflächen des Ventilkörpers 5 und des Ventilhaltekörpers 13 eine Zwischenscheibe 15 mit einer zentralen Öffnung eingespannt ist. An seinem dem Ventilsitz 9 abgewandten Ende wird dasHas valve sealing surface 7, with which it interacts with a conical valve seat 9 on the inwardly projecting closed end of the bore 3. The valve body 5 is with its end remote from the combustion chamber by means of a clamping nut 11 axially clamped against a valve holding body 13, an intermediate disk 15 with a central opening being clamped between the end faces of the valve body 5 and the valve holding body 13. At its end facing away from the valve seat 9, the
Ventilglied 1 über ein die Zwischenscheibe 15 durchragendes Druckstück 17 von einer als Schraubenfeder ausgebildeten Ventilfeder 19 in Richtung Ventilsitz 9 beaufschlagt, die in einen zylindrischen Federraum 21 im Ventilhaltekörper 13 eingesetzt ist und die sich andererseits an einem durch die obere axiale Wand des Federraumes 21 gebildeten ortsfesten Anschlag 23 abstützt.Valve member 1 via a pressure piece 17 projecting through the intermediate disk 15 is acted upon by a valve spring 19 designed as a helical spring in the direction of the valve seat 9, which is inserted into a cylindrical spring chamber 21 in the valve holding body 13 and which on the other hand is fixed on a stationary wall formed by the upper axial wall of the spring chamber 21 Stop 23 supports.
Desweiteren ist stromabwärts des Dichtsitzes zwischen der Ventildichtfläche 7 und dem Ventilsitz 9 eineFurthermore, there is a downstream of the sealing seat between the valve sealing surface 7 and the valve seat 9
Einspritzöffnung 25 in der Wand des Ventilkörpers 5 vorgesehen, die von der Bohrung 3 ausgehend in den Brennraum der zu versorgenden Brennkraftmaschine mündet.Injection opening 25 is provided in the wall of the valve body 5, which opens out from the bore 3 into the combustion chamber of the internal combustion engine to be supplied.
Die Kraftstoffhochdruckzufuhr an den Dichtsitz erfolgt in bekannter Weise über einen zwischen dem Schaft des Ventilgliedes 1 und der Wand der Bohrung 3 gebildeten Ringkanal 27, der sich im Bereich eines Ringabsatzes 31 des Ventilgliedes 1 in einen Druckraum 29 erweitert, in den eine von einer nicht gezeigten Einspritzpumpe abführende Druckleitung 33 mündet.The high-pressure fuel supply to the sealing seat takes place in a known manner via an annular channel 27 formed between the shaft of the valve member 1 and the wall of the bore 3, which extends in the region of a ring shoulder 31 of the valve member 1 into a pressure chamber 29, one of which is not shown Injection pump discharging pressure line 33 opens.
Für eine Erhöhung der Federkraft bei gleichbleibenden Außenabmessungen weist die Ventilfeder 19 wie in der Figur 2 vergrößert dargestellt, an den zur Federachse X radial auswärts weisenden Enden des kreisringförmigen Grundquerschnittes y ihrer Federwindungen 41 Anschliffe 43 auf, die parallel zur Federachse X und zu der Innenwand des zylindrischen Federraumes 21 ausgerichtet sind. Dabei wird die Ventilfeder 19 zunächst aus einem runden Federdraht mit derart großem Querschnitt y gefertigt, daß der theoretische Außendurchmesser der unbearbeiteten Ventilfeder 19 größer ist als der Innendurchmesser des Federraumes 21. In einem anschließenden Arbeitsgang wird am Außendurchmesser der Ventilfeder so viel Material abgetragen, vorzugsweise abgeschliffen, daß die Ventilfeder 19 mit dem notwendigen Spiel gerade in den Federraum 21 einsetzbar ist.In order to increase the spring force with the outer dimensions remaining the same, the valve spring 19 has, as shown in FIG cylindrical spring chamber 21 are aligned. The valve spring 19 is first made from a round spring wire with such a large cross section y that the theoretical outer diameter of the unprocessed valve spring 19 is larger than the inner diameter of the spring chamber 21. In a subsequent operation, as much material is removed from the outer diameter of the valve spring, preferably ground that the valve spring 19 can be used with the necessary clearance in the spring chamber 21.
Dabei ist die verbleibende Querschnittsfläche z der Federwindungen 41 trotz der Anschliffe 43 immer noch bedeutend größer als die Querschnittsfläche einer unbearbeiteten Ventilfeder mit ringförmigem Federdraht, deren Außendurchmesεer gleich groß ist, εo daß die erzielte Federkraft der Ventilfeder 19 ohne zusätzlichen Bauraum erheblich vergrößert werden kann.The remaining cross-sectional area z of the spring coils 41 is still significantly larger than the cross-sectional area of an unprocessed valve spring with an annular spring wire, the outside diameter of which is the same size, despite the cuts 43, so that the spring force of the valve spring 19 achieved can be increased considerably without additional installation space.
Das Verhältnis von y/z liegt dabei vorzugsweise in einem Bereich von 1,05 bis 1,3. The ratio of y / z is preferably in a range from 1.05 to 1.3.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit einem in einem Ventilkörper (5) axial verschiebbaren Ventilglied (1) , das an seinem einen Ende eine Ventildichtfläche (7) aufweist, mit der es zur Steuerung eines Einspritzquerschnittes mit einem ortsfesten Ventilsitz (9) zusammenwirkt und mit wenigstens einer das Ventilglied (1) in Richtung Ventilsitz (9) beaufschlagenden Ventilfeder (19) , die sich andererseits an einem ortsfesten Anschlag (23) abstützt, dadurch gekennzeichnet, daß die Windungen (41) der als Schraubenfeder ausgebildeten Ventilfeder (19) einen kreisförmigen Grundquerschnitt (y) aufweisen, der in einem zur Achse (X) der Ventilfeder (19) radial auswärts weisenden Bereich einen parallel zur Federachse (X) ausgerichteten Anschliff (43) aufweist.1.Fuel injection valve for internal combustion engines with a valve member (5) axially displaceable valve member (1), which has at one end a valve sealing surface (7) with which it interacts with a fixed valve seat (9) to control an injection cross section and with at least a valve spring (19) acting on the valve member (1) in the direction of the valve seat (9), which on the other hand is supported on a fixed stop (23), characterized in that the windings (41) of the valve spring (19) designed as a helical spring have a circular basic cross section (y), which has a bevel (43) aligned parallel to the spring axis (X) in a region pointing radially outward to the axis (X) of the valve spring (19).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Ventilfeder (1) in einen zylindrischen Federraum (21) eingesetzt ist, dessen Innendurchmesser kleiner ausgebildet ist, als der Außendurchmesser der unbearbeiteten Ventilfeder (19) ohne Anschliffe (43) . 2. Fuel injection valve according to claim 1, characterized in that the valve spring (1) is inserted into a cylindrical spring chamber (21), the inside diameter of which is made smaller than the outside diameter of the unprocessed valve spring (19) without bevels (43).
3. Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der mittels der Anschliffe (43) verkleinerte Außendurchmesser (da) der Ventilfeder (19) ein geringes Spiel zum Innendurchmesser des Federraumes (21) aufweist .3. Fuel injection valve according to claim 2, characterized in that the outer diameter (da) of the valve spring (19) reduced by means of the bevels (43) has a slight clearance to the inner diameter of the spring chamber (21).
4. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß daε Verhältnis y/z der Ventilfeder (19) vorzugsweise im Bereich von 1,05 bis 1,3 liegt. 4. Fuel injection valve according to claim 1, characterized in that daε ratio y / z of the valve spring (19) is preferably in the range of 1.05 to 1.3.
EP96934344A 1995-12-16 1996-08-08 Fuel injection valve for internal combustion engines Expired - Lifetime EP0809756B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19547102 1995-12-16
DE19547102A DE19547102A1 (en) 1995-12-16 1995-12-16 Fuel injection valve for internal combustion engines
PCT/DE1996/001480 WO1997022801A1 (en) 1995-12-16 1996-08-08 Fuel injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP0809756A1 true EP0809756A1 (en) 1997-12-03
EP0809756B1 EP0809756B1 (en) 2001-12-12

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP96934344A Expired - Lifetime EP0809756B1 (en) 1995-12-16 1996-08-08 Fuel injection valve for internal combustion engines

Country Status (5)

Country Link
US (1) US5934572A (en)
EP (1) EP0809756B1 (en)
JP (1) JP3737124B2 (en)
DE (2) DE19547102A1 (en)
WO (1) WO1997022801A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19719295A1 (en) 1997-05-07 1998-11-12 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
JP4016370B2 (en) * 1999-03-29 2007-12-05 株式会社デンソー solenoid valve
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Publication number Publication date
JPH11501102A (en) 1999-01-26
JP3737124B2 (en) 2006-01-18
WO1997022801A1 (en) 1997-06-26
DE19547102A1 (en) 1997-06-19
US5934572A (en) 1999-08-10
DE59608445D1 (en) 2002-01-24
EP0809756B1 (en) 2001-12-12

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