EP1967730B1 - Einspritzdüse - Google Patents

Einspritzdüse Download PDF

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Publication number
EP1967730B1
EP1967730B1 EP08157000A EP08157000A EP1967730B1 EP 1967730 B1 EP1967730 B1 EP 1967730B1 EP 08157000 A EP08157000 A EP 08157000A EP 08157000 A EP08157000 A EP 08157000A EP 1967730 B1 EP1967730 B1 EP 1967730B1
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EP
European Patent Office
Prior art keywords
region
seat
cone angle
angle
seating
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Application number
EP08157000A
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English (en)
French (fr)
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EP1967730A1 (de
Inventor
Malcolm Lambert
John Stevens
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Delphi Technologies Inc
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Delphi Technologies Inc
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Priority to EP08157000A priority Critical patent/EP1967730B1/de
Publication of EP1967730A1 publication Critical patent/EP1967730A1/de
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Publication of EP1967730B1 publication Critical patent/EP1967730B1/de
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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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1873—Valve seats or member ends having circumferential grooves or ridges, e.g. toroidal
    • 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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1806—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for characterised by the arrangement of discharge orifices, e.g. orientation or size

Definitions

  • the invention relates to an injection nozzle for use in a fuel injection system for an internal combustion engine.
  • the invention relates to an injection nozzle for use in a compression ignition internal combustion engine, in which a valve needle is engageable with a seating surface to control the injection of fuel to an associated combustion space through a nozzle outlet.
  • a valve needle 10 has a seating surface 12, or seating "line", which engages with a seat defined by an internal surface of a nozzle body bore 14 within which the needle 10 moves.
  • injection nozzle outlets 16 are opened to enable high pressure fuel to be injected to the associated engine cylinder.
  • the outlets 16 are closed and injection is terminated.
  • valve needle 10 Immediately downstream of its seating line 12 the valve needle 10 includes a downstream region 18 of frusto-conical form defining a first cone angle, ⁇ A, which typically is around 60 degrees.
  • the nozzle body bore 14 is also of conical form, and defines a second cone angle, ⁇ B. The difference between the first and second cone angles is typically about 1 degree.
  • the valve needle 10 Immediately upstream of its seating line 12, the valve needle 10 includes an upstream region 20 of frusto-conical form.
  • the upstream region 20 defines a third cone angle, ⁇ C, that typically is around 45 degrees.
  • the difference between the third cone angle, ⁇ C, and the second cone angle, ⁇ B is typically about 15 degrees.
  • the differential angle between the cone angle, ⁇ D, of the valve tip region 19 and the cone angle, ⁇ B, of the nozzle body bore 14 is typically just a few minutes.
  • the valve tip region 19 terminates in a chamfered tip 22.
  • the effective diameter of the seating line varies with wear during nozzle service life.
  • the effective seat diameter influences fuel delivery pressure, or nozzle opening pressure (i.e. that pressure at which the valve needle is caused to lift from the bore seat), and this affects the quantity of fuel that is delivered during injection (i.e. when the valve needle is lifted).
  • US 5 890 660 describes an injection nozzle in which a circumferential groove is provided downstream of the valve needle seating line to prevent drift of the effective seat diameter in a downstream direction. This also has the benefit that variations in nozzle opening pressure throughout nozzle service life are reduced.
  • an injection nozzle for an internal combustion engine comprising:
  • the seat region and the second region define a first intersection therebetween, said regions being shaped such that a radial clearance between the first intersection and the seating surface is in the range 0.5 to 10 ⁇ m in order for the seat region to provide a load bearing surface for the needle, thereby to limit migration of the seating line in the downstream direction due to wear.
  • the second differential angle is up to 20 degrees greater than the first differential angle More Preferably, the second differential angle is between 5 and 15 degrees greater than the first differential angle.
  • the injection nozzle according to the first aspect of the present invention may be one of (i) VCO-type or (ii) sac-type.
  • an injection nozzle for an internal combustion engine includes a valve member having a major needle axis and being engageable with a seating surface, defining a seat cone angle, so as to control fuel delivery through a nozzle outlet, the valve member including a downstream seat region of part-conical form, which defines a first cone angle, and, at its uppermost edge, a seating line for engagement with the seating surface, a first circumferential groove, arranged immediately downstream of the downstream seat region, an upper region arranged so that a lower edge thereof defines, at its intersection with the downstream seat region, the seating line, and a lower region arranged immediately downstream of the first circumerferential groove.
  • a lower edge of the first circumferential groove and the lower region together define a line of intersection which itself defines, together with the seating surface, a radial clearance that is sufficiently small so that the downstream seat region defines a load bearing surface for the valve needle, and wherein the first circumferential groove serves to prevent the seating line migrating beyond a pre-determined amount, with wear of the needle.
  • This combination of features is particularly beneficial as wear of the seating line, which occurs in a downstream direction, is not only confined to the seat region, but is also limited due to the provision of the groove.
  • the lower region may be an end region, arranged immediately downstream of the first circumferential groove, which defines a lower cone angle, and wherein the lower cone angle is less than the first cone angle.
  • the upper region of the nozzle forms an upstream seat region of part-conical form, said upstream seat region defining an upper cone angle, wherein a first differential angle between the first cone angle and the seat cone angle is substantially the same as a second differential angle between the upper cone angle and the seat cone angle, thereby to ensure wear of the seating line, in use, maintains the seating line at approximately the same axial position along the valve member.
  • the upper region that is immediately upstream of the upstream seat region may alternatively be of cylindrical form.
  • the injection nozzle may include a second circumferential groove located downstream of the first circumferential groove and positioned axially along the valve member so that, when the seating line is engaged with the seating surface the second groove approximately aligns with the outlet.
  • the first and second grooves may be spaced apart by an intermediate region of part-conical form which defines a further cone angle selected so that the intermediate region provides an additional load bearing surface for the valve member.
  • the provision of the intermediate region further limits the extent of wear of the needle seat region (i.e. the combined upper and lower portions).
  • FIG. 1 a generally known type of injection nozzle is shown in Figure 1 , in which a valve member in the form of a needle 10 is engageable with a seating to control fuel injection through a plurality of outlet openings 16 (two of which are shown) into an associated engine cylinder or other combustion space.
  • FIG 2 shows an injection nozzle of an embodiment of the invention, which provides improved seat wear characteristics over the nozzle shown in Figure 1 .
  • the nozzle includes a valve needle 30 that is slideable within a bore provided in a nozzle body 34 and engageable with a seating surface 32 defined by the bore.
  • the valve needle 30 is typically movable by means of an injection control valve arrangement (not shown), typically of the type actuated by means of a piezoelectric actuator, as would be familiar to a person skilled in the art.
  • the valve needle 30 may be movable by electromagnetic means, or simply by means of hydraulic forces causing the valve needle 30 to lift from its seating 32.
  • the nozzle body 34 is provided with a set of at least first and second outlets 36 which provide a flow path for fuel into the combustion chamber from an injection nozzle delivery chamber 38.
  • the delivery chamber 38 is together defined by the seating surface 32 and an outer surface of the valve needle 30 in a region downstream of a valve needle seating surface, or seating line, 40 of annular form.
  • the seating line 40 is engageable with the seating surface 32 to control fuel flow into the delivery chamber 38 from an upstream supply chamber 42.
  • the upstream supply chamber 42 is supplied with high pressure fuel for injection.
  • the valve needle 30 is actuated or otherwise caused to lift so as to move the seating line 40 away from its seating surface 32.
  • the valve needle 30 includes at least three distinct regions, and in this example four distinct regions.
  • a first region 44 at the uppermost end in the view shown in Figure 2 , is of substantially cylindrical form.
  • a second region 46 of frusto-conical or part conical form is arranged immediately downstream of the first region 44 and defines, or includes, at its uppermost edge, the seating line 40.
  • a third region 48 of substantially frusto-conical form is arranged immediately downstream of the second region 46 and a fourth, or end region, 50 of substantially conical form is arranged immediately downstream of the third region 48.
  • the fourth region 50 includes, and terminates in, a chamfered tip 52 which extends into a sac volume or chamber 53 defined at the blind end of the nozzle body bore 32.
  • the valve needle 30 is shaped such that when the valve needle 30 is seated, the fourth region 50 is positioned in the vicinity of, and so substantially occludes, the outlets 36.
  • the second, third and fourth regions 46, 48, 50 of the valve needle 30 define first, second and third cone angles ⁇ 1, ⁇ 2, ⁇ 3 respectively and each is of uniform cone angle along its respective lengths.
  • the seating surface 32 defines a seat cone angle, ⁇ s, (also referred to as the nozzle body cone angle), which is different again from the first and second cone angles, ⁇ 1, ⁇ 2.
  • the difference in cone angle between ⁇ 1 and ⁇ s is typically between 0.1 and 3 degrees and the second region 46 of the valve needle has a length, d, (along its outer surface) of between about 0.05 to 0.4 millimetres.
  • the third region 48 of the valve needle 30 is shaped such that the differential angle between its cone angle, ⁇ 2, and the seat cone angle, ⁇ s, is typically between 1 and 20 degrees greater than the further upstream differential angle, defined by the cone angle, ⁇ 1, of the second region 46 and the seat cone angle ⁇ s.
  • the fourth region 50 is shaped to define a differential angle with the seat cone angle ⁇ s of, typically, between 0 degrees (i.e. the cone angles are the same) and 2 degrees.
  • the cone angle, ⁇ 3, of the fourth region 50 is typically less than the second cone angle, ⁇ 2.
  • the third and fourth regions 48, 50 of the valve needle 30 are shaped so as to define, at their line of intersection (identified at 55), a radial clearance or gap between the seating surface 32, of between approximately 5 and 15 ⁇ m.
  • the effective diameter of the seating line 40 will tend to decrease as the second region 46 of the valve needle 30 becomes worn.
  • the relatively large radial clearance between the line of intersection 55 and the seating surface 32 is particularly beneficial as it ensures wear of the valve needle 30 is substantially restricted to the second and third regions 46, 48.
  • the finite length, d, of the second region 46, as defined by the location of the third region 48, serves to limit the extent of wear of the seating line 40, and thus limits the extent to which the effective seating diameter is reduced.
  • the limit of reduction in effective seating diameter is defined by the diameter of a line of intersection 54 between the seat region 46 and the third region 48 of the needle 30.
  • an additional valve needle region in the form of the second region 46, is provided to define the seating line 40.
  • This additional region may be considered to provide a downstream seat region 46 for the needle, as opposed to just a seating line 40.
  • the valve needle 'beds in' over this seat region 46 as the needle wears and the seating line 40 is caused to migrate to lower values (i.e. axially down the needle), with the effective diameter being limited by the effective diameter of the intersection 54 between the second and third regions 46, 48.
  • the cone angles and lengths of the second and third regions 46, 48 are shaped so that a very small radial clearance, typically between 0.5 and 10 ⁇ m, is defined between the valve needle surface at the intersection 54 and the seating surface 32, so that the seat region 46 provides an effective load bearing surface for the needle during closure.
  • the length, d, of the seat region 46 is selected to be between about 0.05 to 0.4 millimetres, and by incorporating this seat region 46 of relatively long length, loading of the needle is distributed over a large surface area, with the effect that contact pressure, and hence wear, is reduced.
  • any increase in fuel delivery quantity over the service life of the nozzle can be disadvantageous, even if the increase is limited (as for the embodiment described previously).
  • other parts of the system also suffer from effects of wear which tend to have a similar effect of increasing fuel delivery quantity.
  • seat wear within the nozzle has the effect of decreasing fuel delivery quantity as a means of compensation.
  • the seat region 46 of the valve needle is arranged immediately upstream of the seating line 40, adjacent to the first region 44.
  • the seat region 46 defines a cone angle ⁇ 1 and, together with the seat cone angle ⁇ s, defines a relatively small differential angle of just a few degrees, typically between 0.5 and 5 degrees.
  • the third region 48 of the needle 30 downstream of the seating line 40 defines a cone angle ⁇ 2 which, together with the seat cone angle ⁇ s, defines a differential angle that is greater than that defined by ⁇ 1 and ⁇ s.
  • the third region 48 in Figure 3 is shaped to define a differential angle with the seat cone angle of between about 1 and 20 degrees.
  • the end region 50 of the valve needle 30 has a uniform cone angle along its entire length (with the exception of the slight chamfering of its tip) and aligns in the vicinity of the nozzle outlet when the valve needle is seated. Put another way, the valve needle 30 is received in the nozzle bore so that the end region 50 locates within that region of the bore in which the outlets 36 are provided.
  • a seat region 46 immediately upstream of the seating line 40, to define a relatively small differential angle may be referred to as an "inverted” or “negative” seat region; that is a seat region which wears in a direction upstream of the seating line 40. This is in contrast with the embodiment of Figure 2 , where a "noninverted” or “positive” seat region is included downstream of the seating line 40.
  • valve needle 30 is therefore shaped to provide a means for compensating for the effects of wear in the fuel injection system, this being provided by the seat region 46 upstream of the seating line 40 having a relatively small differential angle (with the seat cone angle) compared to the differential angle defined by the third region 48 (with the seat cone angle) downstream of the seating line 40.
  • Figure 3 shows the first region 44 of the valve needle 30 upstream of the seat region 46, as being of cylindrical form, but it will be appreciated that the aforementioned advantages are also achieved if the first region 44 is of conical form, either defining the same differential angle with the seat cone angle, in which case it forms a continuous region with the upstream seat region 46, or defining a greater differential angle to that defined by the upstream seat region 46 (with the seat cone angle).
  • the latter configuration provides the benefit that migration of the seating line 40 is limited, as determined by the finite length of the seat region 46.
  • shaping the upstream seat region 46 and the seating surface 32 to together define a differential angle of less than 3 degrees provides a hydraulically self-centralising force to the end region 50 the needle 30. If at least two outlets 36 are provided, this has the advantage of achieving good "hole-to-hole" flow balance. For small values of needle lift, and if fuel sprays are relatively wide, improved hole-to-hole flow balance is particularly important and the selection of the upstream differential angle within this range provides a particular benefit in such circumstances.
  • a possible disadvantage of the nozzle shown in Figure 3 compared to that in Figure 2 may occur in some applications for which very small fuel delivery quantities are required, for example where it is required to deliver a low volume, pilot injection of fuel prior to a main injection of fuel. If the effective seat diameter tends to increase with wear, thus tending to decrease fuel delivery quantities, it is possible that the pilot injection of fuel may disappear altogether.
  • Figure 4 shows a further embodiment which ensures the effective seating diameter tends to decrease with wear (i.e. as in the Figure 2 embodiment).
  • the first region 44 of the valve needle 30 is of cylindrical form, and the seat region 46 is shaped to define a cone angle, ⁇ 1.
  • the differential angle defined by the cone angle ⁇ 1 of the seat region 46 and the seat cone angle ⁇ s is typically between about 0 degrees 10 minutes and 3 degrees (i.e. relatively small).
  • the seating line 40 wears it tends to migrate downstream along the seat region 46 and, thus, the effective diameter tends to decrease. Any variation in fuel delivery quantity due to this wear is therefore in the form of an increased fuel delivery quantity.
  • the valve needle 30 also includes a circumferential groove 58 immediately downstream of the seat region 46.
  • the provision of the groove 58 serves to limit the extent to which the seat region 46 can wear, in use, so that there is a limit on the variation (increase) in fuel delivery quantity, and nozzle opening pressure, with such seat wear.
  • the groove 58 provides a similar function to the third region 48 in the Figure 2 embodiment.
  • the lower end region 50 of the valve member 30 defines a cone angle, ⁇ 3, which is greater than the first cone angle, ⁇ 1, of the seat region 46.
  • Figure 4 is similar to the injection nozzle described in US 5 890 660 .
  • the effective seating diameter tends to migrate to higher values (i.e. as defined by the upstream region of the valve needle) due to the inverted differential angle upstream of the seating line 40.
  • Figure 4 provides an injection nozzle for which the effective seating diameter tends to migrate to lower values, due to the differential angle defined by the seat region 46 (with the surface 32), so that any problems associated with reduced fuel delivery quantities which may arise in the nozzle in US 5 890 660 are overcome.
  • a line of intersection 55 is defined between the circumferential groove 58 and the lower end region 50.
  • the radial clearance between the line of intersection 55 and the seating surface 32 is very small, typically between 0.5 and 10 ⁇ m (and preferably between 0.5 and 5 ⁇ m), to ensure that the seat region 46 provides an effective load bearing surface for the needle 30 as it seats, in use.
  • FIG. 5 An alternative embodiment to that shown in Figure 4 is shown in Figure 5 , in which the needle is provided with both an upstream seat region 46a (i.e. that region immediately upstream of the seating line 40) and a downstream seat region 46b (i.e. that region immediately downstream of the seating line 40).
  • the cone angles of the upstream and downstream seat regions 46a, 46b are both selected to define relatively small differential angles with the seat cone angle, ⁇ s.
  • the upstream and downstream seat regions 46a, 46b are shaped so that each defines a differential angle with the nozzle body cone angle, ⁇ s, of between about 0 degrees 10 minutes and 5 degrees.
  • the differential angles defined by the seat regions 46a, 46b are substantially the same, but alternatively they may be slightly different, providing always that they are relatively small.
  • the embodiment in Figure 5 also includes a circumferential groove 58, which serves to limit the extent of wear of the downstream seat region 46 of the valve needle 30.
  • the effective seating diameter is defined by the surface or line of intersection 40 between the upstream seat region 46a and the downstream seat region 46b.
  • contact pressure between the valve needle 30 and the surface 32 tends to distribute approximately equally over both seat regions 46a, 46b, although the primary line of contact remains at approximately the same axial position (i.e. that of the original seating line 40).
  • the effective seating diameter changes very little with wear, and hence the fuel delivery quantity and nozzle opening pressure also varies only a little.
  • FIG. 6 A further alternative embodiment to that shown in Figures 4 and 5 is shown in Figure 6 , in which the valve needle is provided with a first circumferential groove 58 located immediately downstream of the downstream seat region 46b (as in Figure 5 ), with a second circumferential groove 60 being provided further downstream so as to approximately align with the outlets 36 when the valve needle 30 is seated.
  • the first and second circumferential grooves 58, 60 are separated by an intermediate region 62 of the valve needle 30.
  • the intermediate region 62 defines a differential cone angle with the seat cone angle ⁇ s which, typically, is between about 10 minutes and 3 degrees. This region 62 provides a load bearing surface upon needle closure, which serves to reduce the loading on, and hence wear of, the upper and lower seat regions 46a, 46b.
  • One benefit of providing the second groove 60, approximately at the same axial position along the major axis of the valve needle 30 as the outlets 36, is that it permits fuel pressure to homogenise within that region of the delivery chamber adjacent to the inlet ends (i.e. inner ends) of the outlets 36. This has the effect of equalising fuel delivery quantity through each of the outlets 36, and helps to ensure equal spray formations are achieved through each outlet also.
  • an additional circumferential groove may be provided to align with this second set, as described above for the first set.
  • a further circumferential groove may be provided in the same manner.
  • All of the injection nozzles described hereinbefore are of VCO (valve covered orifice) type, in which the valve needle 30 covers or occludes the inlet end of the or each nozzle outlet 36 when it is seated (i.e. when no injection takes place).
  • VCO valve covered orifice
  • the present invention is equally applicable, however, to sac-type injection nozzles in which the or each nozzle outlet is not covered by the valve needle when it is seated, but the inlet end of each outlet is in constant communication with the sac chamber at the blind end of the nozzle body bore. In sac-type nozzles it is unseating and seating of the valve needle that again controls whether or not injection occurs through the outlets, as in VCO-type nozzles.

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

Claims (5)

  1. Einspritzdüse für eine Brennkraftmaschine, wobei die Düse Folgendes umfasst:
    ein mit einer Sitzfläche (32) in Eingriff bringbares Ventilelement (30), das einen Sitzkegelwinkel (s) definiert, um die Kraftstoffabgabe durch einen Düsenauslass (36) zu steuern,
    wobei das Ventilelement (30) eine zylindrische obere Region (44), eine abströmseitig unmittelbar nach der oberen Region (33) angeordnete Sitzregion (46), die einen ersten Kegelwinkel (ϑ1) definiert, wobei die obere Region (44) und die Sitzregion (46) an ihrem Schnittpunkt eine Sitzlinie (40) für den Eingriff mit der Sitzfläche (32) definieren, eine abströmseitig unmittelbar nach der Sitzregion (46) angeordnete zweite Region (48), die einen zweiten Kegelwinkel (ϑ2) definiert, und eine abströmseitig unmittelbar nach der zweiten Region (48) angeordnete Kegelendregion (50) hat,
    wobei ein erster Differenzwinkel zwischen dem ersten Kegelwinkel (ϑ1) und dem Sitzkegelwinkel (ϑs) kleiner als ein zweiter Differenzwinkel zwischen dem zweiten Kegelwinkel (ϑ2) und dem Sitzkegelwinkel (ϑs) ist, wobei der genannte erste Differenzwinkel so gewählt ist, dass sichergestellt wird, dass die Sitzlinie (40) im Gebrauch in Abströmrichtung entlang der Sitzregion (46) wandert, wenn das Ventilelement (30) abgenutzt zu werden beginnt, und der zweite Differenzwinkel so gewählt ist, dass die genannte Wanderung der Sitzlinie (40) über einen vorbestimmten Betrag hinaus verhindert wird,
    wobei die genannte zweite Region (48) und die Endregion (50) zwischen sich einen zweiten Schnittpunkt (55) definieren, dadurch gekennzeichnet, dass die genannte zweite Region (48) und die genannte Endregion (50) so gestaltet sind, dass ein Radialspalt zwischen der zweiten Schnittstelle und der Sitzfläche (32) im Bereich von 5 bis 15 µm liegt, um die Abnutzung der Ventilnadel auf die Sitz- und die zweite Region (46, 48) zu beschränken,
    wobei die Endregion (50) einen kleineren Kegelwinkel (ϑ3) definiert und wobei ein dritter Differenzwinkel zwischen dem kleineren Kegelwinkel (ϑ3) und dem Sitzkegelwinkel (ϑs) etwa der gleiche wie der erste Differenzwinkel ist.
  2. Einspritzdüse nach Anspruch 1, bei der die Sitzregion (46) und die zweite Region (48) zwischen sich einen ersten Schnittpunkt (54) definieren, wobei die genannten Regionen (46, 48) so gestaltet sind, dass ein Radialspalt zwischen der ersten Schnittstelle (54) und der Sitzfläche (32) im Bereich von 0,5 bis 10 µm liegt, damit die Sitzregion (46) eine tragende Oberfläche für die Nadel (30) bereitstellt, um dadurch die abnutzungsbedingte Wanderung der Sitzlinie (40) in Abströmrichtung zu begrenzen.
  3. Einspritzdüse nach Anspruch 1 oder Anspruch 2, bei der der zweite Differenzwinkel bis zu 20 Grad größer als der erste Differenzwinkel ist.
  4. Einspritzdüse nach Anspruch 3, bei der der zweite Differenzwinkel zwischen 5 und 15 Grad größer als der erste Differenzwinkel ist.
  5. Einspritzdüse nach einem der Ansprüche 1 bis 4, die (i) vom Sitzlochdüsentyp (VCO-Typ) oder (ii) vom Sacklochtyp ist.
EP08157000A 2003-07-15 2004-07-15 Einspritzdüse Active EP1967730B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08157000A EP1967730B1 (de) 2003-07-15 2004-07-15 Einspritzdüse

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP03254661 2003-07-15
EP08157000A EP1967730B1 (de) 2003-07-15 2004-07-15 Einspritzdüse
EP04254231A EP1498602B1 (de) 2003-07-15 2004-07-15 Einspritzventil

Related Parent Applications (1)

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EP04254231A Division EP1498602B1 (de) 2003-07-15 2004-07-15 Einspritzventil

Publications (2)

Publication Number Publication Date
EP1967730A1 EP1967730A1 (de) 2008-09-10
EP1967730B1 true EP1967730B1 (de) 2009-12-23

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EP04254231A Active EP1498602B1 (de) 2003-07-15 2004-07-15 Einspritzventil
EP08157000A Active EP1967730B1 (de) 2003-07-15 2004-07-15 Einspritzdüse

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EP (2) EP1498602B1 (de)
AT (2) ATE400736T1 (de)
DE (2) DE602004014854D1 (de)

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Publication number Priority date Publication date Assignee Title
KR970029982A (ko) * 1995-11-07 1997-06-26 윤종용 칼라 음극선관용 블랙 매트릭스, 형광막 및 그의 제조방법
CN114483403B (zh) * 2022-01-24 2023-02-24 宁波兴马油嘴油泵有限公司 一种油嘴检测方法、系统、存储介质及智能终端

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EP0283154A1 (de) * 1987-03-14 1988-09-21 LUCAS INDUSTRIES public limited company Brennstoffeinspritzdüse
US5033679A (en) * 1987-10-30 1991-07-23 Golev Vladislav I Injector nozzle for a diesel engine
GB9425652D0 (en) * 1994-12-20 1995-02-22 Lucas Ind Plc Fuel injection nozzle
DE19844638A1 (de) * 1998-09-29 2000-03-30 Siemens Ag Kraftstoffeinspritzventil für eine Brennkraftmaschine
DE19942370A1 (de) * 1999-09-04 2001-03-22 Bosch Gmbh Robert Einspritzdüse für Brennkraftmaschinen mit einer Ringnut in der Düsennadel
JP2001107826A (ja) * 1999-10-12 2001-04-17 Toyota Motor Corp 筒内噴射式内燃機関の燃料噴射ノズル
JP2001221135A (ja) * 2000-02-09 2001-08-17 Yanmar Diesel Engine Co Ltd 燃料噴射ノズル
DE10031264A1 (de) * 2000-06-27 2002-01-17 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
GB0017542D0 (en) 2000-07-18 2000-09-06 Delphi Tech Inc Valve member
DE10054183A1 (de) * 2000-11-02 2002-05-29 Siemens Ag Einspritznadel mit elastischer Nadelspitze

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Publication number Publication date
EP1967730A1 (de) 2008-09-10
ATE453048T1 (de) 2010-01-15
DE602004014854D1 (de) 2008-08-21
DE602004024835D1 (de) 2010-02-04
ATE400736T1 (de) 2008-07-15
EP1498602A2 (de) 2005-01-19
EP1498602A3 (de) 2005-05-04
EP1498602B1 (de) 2008-07-09

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