WO2015043913A1 - Injecteur de carburant et procédé pour le fabriquer - Google Patents

Injecteur de carburant et procédé pour le fabriquer Download PDF

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Publication number
WO2015043913A1
WO2015043913A1 PCT/EP2014/068891 EP2014068891W WO2015043913A1 WO 2015043913 A1 WO2015043913 A1 WO 2015043913A1 EP 2014068891 W EP2014068891 W EP 2014068891W WO 2015043913 A1 WO2015043913 A1 WO 2015043913A1
Authority
WO
WIPO (PCT)
Prior art keywords
nozzle needle
throttle point
fuel injection
injection valve
rounding
Prior art date
Application number
PCT/EP2014/068891
Other languages
German (de)
English (en)
Inventor
Katja Grothe
Christian Berg
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 WO2015043913A1 publication Critical patent/WO2015043913A1/fr

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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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • F02M61/205—Means specially adapted for varying the spring tension or assisting the spring force to close the injection-valve, e.g. with 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
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/28—Details of throttles in fuel-injection apparatus
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/80—Fuel injection apparatus manufacture, repair or assembly
    • F02M2200/8069—Fuel injection apparatus manufacture, repair or assembly involving removal of material from the fuel apparatus, e.g. by punching, hydro-erosion or mechanical operation

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines and a, as it is used for fuel injection into the combustion chamber of an internal combustion engine.
  • a fuel injection valve for injecting fuel into the combustion chamber of an internal combustion engine comprising a nozzle body in which a high pressure bore or a pressure chamber is formed with a longitudinally displaceably arranged nozzle needle, which with a nozzle needle seat of Nozzle body cooperates. Due to the interaction of the nozzle needle with the nozzle needle seat, a fuel flow is opened or interrupted at least one injection port.
  • the known valve has a first gap throttle between the nozzle body and the nozzle needle and a second gap throttle between nozzle body and nozzle needle, the formation of at least one gap choke is dependent on the stroke of the nozzle needle.
  • the two gap throttles are used in the known fuel injection valve to allow a good injection characteristic both in the smallest quantity operation as well as in full load operation: fast needle closing in pre- and post-injection and maximum injection pressure in the full load range. That is, with small nozzle needle strokes, a reduction of the system pressure below the gap throttles and thus an increase of the hydraulically resulting closing force on the nozzle needle is desired, while in full load operation below the gap throttles the maximum injection pressure is to rest in order to achieve a very favorable combustion in the internal combustion engine. Furthermore, high pressure overshoots on the nozzle needle seat, such as may occur during nozzle needle closing, are minimized by the known fuel injector.
  • the object of the present invention is to achieve a good injection characteristic both in the smallest quantity operation and in full load operation with minimized high-pressure overshoots on the nozzle needle seat during the nozzle needle closing, and at the same time to reduce the production cost of the fuel injection valve, especially for the nozzle needle.
  • the stroke-dependent throttle point between the nozzle needle tip and nozzle body which arises when lifting the nozzle needle from the nozzle needle seat, to be used advantageously as a gap throttle or throttle point, so that upstream only between the nozzle body and nozzle needle, a further gap throttle or throttle must be located to achieve the above injection characteristics.
  • the production cost for the nozzle needle is reduced.
  • High pressure overshoot on the nozzle needle seat are minimized as well as the known fuel injector.
  • the fuel injection valve has a pressure chamber formed in a nozzle body, in which a nozzle needle is arranged to be longitudinally displaceable.
  • a nozzle needle tip formed on the nozzle needle cooperates with a nozzle needle seat formed on the nozzle body and thereby opens and closes at least one injection opening, wherein a first throttle point is formed when lifting the nozzle needle tip from the nozzle needle tip between the nozzle needle tip and the nozzle needle seat.
  • a central region formed on the nozzle needle forms, with a shaft region formed on the nozzle body, on its inner surface a second throttle point which has a constant flow cross-section over a first partial stroke of the nozzle needle.
  • the first throttle point is used as a stroke-dependent throttle and the second throttle point as at least until the first partial stroke of the nozzle needle hubuncol throttle.
  • the first partial stroke is less than 20% of a maximum stroke of the nozzle needle.
  • the first and the second throttle point are particularly effective for nozzle needle strokes up to the first partial stroke; In this area, above all, they determine the injection characteristics during the pilot injections or during the
  • the central region has at least one, but preferably three in the longitudinal direction of the nozzle needle Axial throttle thrust of depth h, which form the second throttle point with the inner surface.
  • the second throttle point is not formed over the entire circumference of the central region of the nozzle needle, but via the Drosselanschliffe.
  • the manufacturing tolerances between the middle region of the nozzle needle and the shaft region of the nozzle body need not be made too narrow; on the other hand, the throttling function of the second orifice during operation (eg at extreme temperatures or temperature differences) can be kept more robust.
  • the at least one throttling ground on a slot end face with the radius R is rounded to form a cylindrical outer surface of the central area.
  • a plurality of injection openings are present, and during the first part of the stroke, the flow cross section of the first throttle point is less than the summed flow area of all injection ports, preferably by more than 50% less.
  • the flow cross section of the second throttle point when reaching the first partial stroke of the nozzle needle is at least approximately as large as the flow cross section of the first throttle point.
  • either the first or the second throttle point can be used as an essential throttle function for the first partial stroke.
  • both throttle points advantageously have a smaller flow cross section than the summed flow cross section of all injection ports. This reduces the nozzle pressure in the system pressure in the pressure chamber between the first throttle point and the injection openings, so that the hydraulically resulting closing force increases on the nozzle needle and it comes to a faster closing of the nozzle needle and thus to a better injection characteristics with small injection quantities.
  • the second throttle point between the first partial stroke and a second partial stroke of the nozzle needle which is greater than the first partial stroke and smaller than the maximum stroke, a steadily expanding flow area on.
  • the flow cross section of the second throttle point is greater than the flow cross section of the first throttle point from the second partial stroke.
  • the middle region of the nozzle needle in the region of the second throttle point has a tapering towards the nozzle needle tip transition region, wherein the transition region is designed either as a chamfer, preferably at an angle ⁇ of 35 ° to 80 ° to the cylindrical lateral surface of the central region, or has at least one concave circular arc shape with radius R.
  • the flow cross section is increased by the second throttle point, when the tapered transition region of the nozzle needle forms the second throttle point with the shaft region of the nozzle body, so at nozzle needle strokes greater than the first partial stroke until reaching the second partial stroke.
  • the gap width of the second throttle point thereby increases while at the same time being easier to manufacture.
  • the execution of the transition region as a chamfer or as a concave circular arc shape may be more advantageous.
  • the concave arc shape of the angle between lateral surface and imaginary tangential extension of the circular arc shape and depending on the chamfer length or circular arc length so the injection characteristics of the fuels insp - valve in the partial load range can be designed depending on the application.
  • the entire region of the nozzle needle is designated from the transition region in the direction of the combustion chamber of the internal combustion engine. This will be a sufficient fuel flow between the first and second throttle point achieved by the longitudinal grinding with good management of the nozzle needle tip in the shaft region of the nozzle body.
  • the leadership of the nozzle needle tip in the shaft region takes place on the surfaces of the nozzle needle tip on which no longitudinal cuts are formed.
  • the longitudinal sections to the transition region are each rounded with the radius R.
  • the fillets of the longitudinal cuts simultaneously represent the transition region of the nozzle needle, and the second throttle point can be manufactured on the nozzle needle side with the same tool as the longitudinal cuts.
  • the summed flow cross section of all injection openings is less than the flow cross section of the first throttle point and less than the flow cross section of the second throttle point at the maximum stroke of the nozzle needle.
  • a manufacturing method of the fuel injection valve according to the invention having the following features: formed in a nozzle body pressure chamber in which a nozzle needle is arranged longitudinally displaceable, wherein a formed on the nozzle needle nozzle needle cooperates with a formed on the nozzle body nozzle needle seat and thereby at least one injection opening opens and closes, wherein the Lifting the nozzle needle tip from the nozzle needle seat between the nozzle needle tip and the nozzle needle seat, a first throttle point is formed, wherein a formed on the nozzle needle central region form on its outer surface with a formed on the nozzle body shaft portion on the inner surface of a second throttle point, wherein on the nozzle needle, a central region is formed and the nozzle needle tip between the central region and nozzle needle seat has longitudinal sections which extend in the direction of the nozzle needle axis, wherein the longitudinal sections are rounded to the central region in a concave transition region having a first rounding and a second rounding, wherein the second throttle point over a first partial stroke of the nozzle
  • steps 1) and 2) are carried out together in one production step.
  • the first rounding at a first angle ⁇ and the second rounding be ground at a second angle ß to the cylindrical surface, where ⁇ ⁇ ß, and the first rounding and the second rounding have the same radius R, where the second fillet is ground in a tangential manner to the longitudinal cuts and the grinding tool has a corresponding negative mold. Due to the angular relationship ⁇ ⁇ , the flow cross-section through the second throttle point from the second partial stroke is increased more than between the first and the second partial stroke. Since the first and second fillets have the same radius R, the same radius of the grinding tool can be used for the grinding processes. Due to the tangential discharge from the second rounding to the longitudinal cuts, a sharp edge or burr formation is avoided at the transition of the longitudinal cuts to the transition region; subsequent deburring production steps can be omitted at this transition.
  • Fig.l shows a longitudinal section through a fuel injection valve according to the invention in a schematic representation, wherein only the essential areas are shown.
  • FIG. 2 shows a longitudinal section of a further embodiment of the fuel injection valve according to the invention in a schematic representation, wherein only the essential areas are shown.
  • FIG. 3 shows the designated III section of Fig.2
  • FIG. 4 shows the detail of FIG. 3 designated IV
  • Fig.5 shows a step of a manufacturing process of the embodiment of Fig.2.
  • Fig.l schematically shows a detail of a fuel injection valve 100 according to the invention in longitudinal section.
  • the fuel insp scrib valve 100 has a formed in a nozzle body 10 pressure chamber 20 in which a nozzle needle 30 is arranged longitudinally displaceable. Due to the longitudinal movement of the nozzle needle 30, a nozzle needle 30 acts on the nozzle needle 30. formed nozzle needle tip 31 with a formed on the nozzle body 10 nozzle needle seat 11 and thereby opens and closes at least one formed in the nozzle body 10 injection port 19 for injection of fuel under high pressure in a combustion chamber 110 of an internal combustion engine.
  • a transition region 37 and a central region 34 adjoin one another as further components of the nozzle needle 30 away from the combustion chamber.
  • the central region 34 has a cylindrical lateral surface 35 with a diameter d 35
  • the transition region 37 is conical in the illustrated embodiment with an angle ⁇ to the cylindrical lateral surface 35.
  • the nozzle body 10 has a shank region 14 with a cylindrical inner surface 15 of diameter d i5 and, facing away from the combustion chamber, thereupon a nozzle body shoulder 17, the inner diameter of which widens in the direction away from the combustion chamber.
  • a second throttle gap 50 with the width (di 5 -d 35 ) / 2 and with formed the length Si, wherein the length Si corresponds to a first partial stroke Si.
  • the second throttle gap 50 divides the pressure chamber 20 into a upper pressure chamber 21 facing away from the combustion chamber and a lower pressure chamber 22 facing the combustion chamber.
  • a second partial stroke s 2 is defined by the sum of the first partial stroke Si and the axial length IÜ of the transitional region 37.
  • Drosselanschliffe 40 are arranged with the depth h in the longitudinal direction of the nozzle needle 30, which lead into the transition region 37 of the nozzle needle 30.
  • the depth h is 25 ⁇ to 40 ⁇ .
  • the illustrated embodiment has three Drosselanschliffe 40, which are arranged uniformly distributed over the circumference. Further embodiments with two or four throttle slits 40 are also possible.
  • a throttle grind 40 consists of a usually planar groove base 41, which terminates in the transition region 37 and a Nutstirnseite 42, which is designed as a rounding with the radius R to the lateral surface 35 of the central region 34.
  • the second throttle restriction 50 is essentially formed between the throttle snares 40 and the cylindrical inner surface 15 of the shaft region 14 of the nozzle body 10.
  • the diameter d 35 of the lateral surface 35 of the central region 34 is in this embodiment only slightly smaller than the diameter d i5 of the inner surface 15 of the shaft portion 14, so that outside the Drosselanschliffe 40 between the central region 34 and shaft portion 14 no throttle gap is formed; In these areas, the nozzle needle 30 to the nozzle body 10 is almost dense.
  • the downstream of the second throttle body 50 form a substantial part of the flow cross-section between the nozzle needle tip 31 and shaft portion 14.
  • the longitudinal cuts 38 are made almost over the entire length of the nozzle needle tip 31, ie from the transition region 37 to near the first throttle point 12, and have largely a planar base.
  • the longitudinal cuts 38 are rounded, viewed in cross section, first with the second rounding 37b, which preferably terminates tangentially into the planar base of the longitudinal cut 38, and subsequently with the first fillet 37a, both fillets 37a, 37b the same Radius R have.
  • transition region 37 may be instead of two
  • three longitudinal slits 38 are uniformly distributed over the circumference of the nozzle needle tip 31 and are arranged so that the longitudinal slices 38 in the transition region 37 each lead into a throttle slit 40.
  • Demzufol- ge changed in other embodiments, the number of longitudinal grinding 38 analogous to the number of Drosselanschliffe 40 to two or four longitudinal cuts 38th
  • the nozzle needle tip 31 In the region of the nozzle needle tip 31 lying in the shaft region 14, which is not provided with longitudinal cuts 38, the nozzle needle tip 31 has a cylindrical shape with the same diameter d 35 as the jacket surface 35 of the middle region 34; As a result, the nozzle needle tip 31 can be guided well in the nozzle body 10 during strokes of the nozzle needle 30.
  • FIG. 3 shows for better illustration the detail III of FIG. 2 in the area of the second throttle point 50 with the nozzle needle 30 closed.
  • the second orifice 50 is formed between the inner surface 15 of the shank portion 14 of diameter d i5 and the throttle bevels 40 of the central portion 34 over the length Si.
  • the concave transition region 37 of the nozzle needle 30 between the central region 34 and nozzle needle tip 31 is divided into a first rounding 37 a, which adjoins the central region 34, and a second rounding 37 b, which adjoins the nozzle needle tip 31.
  • the first rounding 37a extends at an angle ⁇ to the lateral surface 35 or to the groove bottom 41 and connects directly to this.
  • the second fillet 37b is formed between the first fillet 37a and the nozzle needle tip 31; Their imaginary tangential outlet runs at an angle ⁇ to the lateral surface 35 or to the groove base 41.
  • the cylindrical lateral surface 35 is arranged coaxially to a nozzle needle axis 39 of the nozzle needle 30.
  • Both fillets 37a, 37b have the same radius R, with which the Nutstirnseite 42 is rounded. However, the arc length of the first fillet 37a is smaller than the arc length of the second fillet 37b.
  • the first partial stroke Si, the second partial stroke s 2 and the maximum stroke v of the nozzle needle 30 are outlined.
  • an axial reference 16 along the nozzle needle axis 39 to the edge between the nozzle body shoulder 17 and the inner surface 15 of the shaft portion 14 of the nozzle body 10 is used, extending from the combustion chamber in the direction away from the diameter of the bore of the nozzle body 10 and thus the volume of the pressure chamber 20 increases :
  • the first partial stroke Si describes the axial distance along the nozzle needle axis 39 from the reference 16 to the transition from the throttle pin 40 to the first rounding 37a.
  • the second partial stroke s 2 describes the axial distance along the nozzle needle axis 39 from the reference 16 to the transition from the first rounding 37 a to the second rounding 37 b.
  • the maximum stroke v can have a height which leads from the cover 16 either to the second rounding 37b or into the nozzle needle tip 31.
  • FIG. 4 shows the detail IV of Figure 3. Shown are the first angle ⁇ of the first rounding 37a and the second angle ß of the second rounding 37b to the groove bottom 41 of the Drosselanschliffs 40, which is formed in the central region 34 of the nozzle needle 30.
  • the dashed lines each show the tangential outlet of the two fillets as a reference for the two angles. Ideally, 0 ° ⁇ ⁇ ⁇ 90 °.
  • the groove base 41 runs parallel to the longitudinal axis of the nozzle needle 30, and thus also parallel to the lateral surface 35 of the central region 34, within the scope of manufacturing accuracy.
  • FIG. 5 shows a production step for manufacturing the nozzle needle 30 from the embodiment of FIGS. 2-4: a first rounding 37a is ground.
  • a grinding tool 200 having a convex radius R is brought into abutment with the first rounding 37a of a longitudinal cut 38.
  • the grinding tool 200 likewise has a planar surface which, however, is arranged at a distance from the planar surface of the longitudinal cut 38 in the illustrated production step.
  • the throttle section 40 belonging to the longitudinal section 38 can be manufactured by machining the planar surface of the grinding tool 200 the groove base 41 and the convex radius R the groove end side 42.
  • the operation of the fuel injection valve 100 according to the invention is as follows:
  • the nozzle needle tip 31 is in contact with the nozzle needle seat 11, so that the injection openings 19 from the pressure chamber 20 and the lower pressure chamber 22 are separated and therefore no fuel is injected into the combustion chamber 110.
  • the second throttle body 50 is formed between the inner surface 15 of the shaft portion 14 with diameter d i5 and the lateral surface 35 of the central region 34 with diameter d 35 and the throttle grindings 40 over the length Si corresponding to the first partial stroke Si.
  • the nozzle needle 30 via a control device, for example, lowering a pressure on a combustion chamber 110 opposite end face of the nozzle needle 30, lifted from the nozzle needle seat 31, so that the hydraulic connection between the pressure chamber 20 and lower pressure chamber 22 and injection ports 19 is opened and the first throttle 12 is formed.
  • the flow cross-section increases through the first throttle point 12, which is thus dependent on the stroke.
  • the first partial stroke Si is less than 20% of the maximum stroke v of the nozzle needle 30, in the case of fuel injection valves for passenger car engines, for example, less than 80 ⁇ . Furthermore, until the first partial stroke Si, the flow cross section through the first throttle 12 is less than the flow cross section through the injection port 19, or in the case of multiple injection ports 19 less than the summed flow cross section through all injection ports 19, preferably more than 50% lower.
  • the flow cross-section of the first throttle point 12 is at least approximately as large as the flow cross section of the second throttle point 50.
  • the injection characteristic of the fuel injection valve 100 up to the first partial stroke Si therefore primarily determines the first throttle point 12 and the second throttle point 50.
  • the flow cross-section of the second throttle point 50 which thus becomes stroke-dependent, also expands.
  • this can be achieved, for example, by means of a transition region 37 designed as a chamfer at the angle ⁇ over the entire circumference of the nozzle needle 30, as shown in FIG.
  • the nozzle needle 30 tapers in the transition region 37 - either over the entire circumference or in the region of the longitudinal grind 38 - and thereby increases the width of the second throttle body 50 as soon as the transition region forms the second throttle body 50, ie as soon as the transition region 37 during the stroke movement of the nozzle needle 30th the axial reference 16 passes through.
  • the flow cross section of the first throttle point 12 is at least approximately as large as the flow cross section of the second throttle point 50.
  • the flow cross section of the first Throttle 12 is at least approximately as large as the flow area of the second throttle body 50.
  • the flow cross-section of the second throttle body 50 increases more than between the first partial stroke Si and the second partial stroke s 2 .
  • this can be implemented, for example, via a vertical shoulder on the nozzle needle 30 -as shown in FIG. 1 -or a second rounding 37b in the transition region 37 -as shown in FIGS. 2-5-depending on the embodiment, again over the entire circumference the nozzle needle 30 or only in the region of longitudinal cuts 38:
  • the second rounding 37b of the exemplary embodiments of FIGS. 2-5 leads to a greater increase in the flow cross section of the second throttle point 50 than in the previous stroke phase between the first partial stroke Si and the second partial stroke s 2 , but not to a sudden increase.
  • the second rounding 37b has a tangential angle ⁇ to the lateral surface 35 or to the groove bottom 41, which is greater than the tangential angle ⁇ the first rounding 37a to the lateral surface 35 and the groove bottom 41 but less than or equal to 90 °.
  • both fillets 37a and 37b are made with the same radius R, but the second fillet 37b has a longer arc length.
  • the nozzle needle 30 is lifted from the nozzle needle seat 11 so far that in the region of the second throttle body 50 the edge of the nozzle body shoulder 17 faces the inner surface 15 of the nozzle body 10 at the level of the axial reference 16, a region of the nozzle needle 30 is opposite, which has a correspondingly smaller cross-section than the diameter determined by the diameter d 35 , so that a comparatively large gap between the nozzle body 10 and the nozzle needle 30 is formed:
  • this region is the nozzle needle tip 31 that is tapered due to the vertical shoulder relative to the transition region 37.
  • this may likewise be the nozzle needle tip 31, or else a region in the transition region 37 which is at the level of the second
  • the cylindrical lateral surface 35 of the central region 34 and the nozzle needle tip 31 are made cylindrical to the diameter d 35 .
  • a less high manufacturing accuracy is required to achieve a defined flow cross-section through the second throttle point 50 to the first partial stroke Si, as if the second throttle body 50 would be formed over the entire circumference of the nozzle needle 30, since then still the Drosselanschliffe 40 are made.
  • This manufacturing step can be performed with the grinding tool 200; however, it is advantageously carried out by a turning operation in an upstream production step.
  • the planar surface of a longitudinal grinding 38 on the nozzle needle tip is first ground with the grinding tool 200.
  • the second rounding 37b is ground at the outlet of the longitudinal cut 38.
  • the grinding tool 200 has a convex radius R which corresponds to the concave radius R of the second rounding 37b, ie forms a negative mold of the second rounding 37b.
  • the first rounding 37a is ground by the radius R of the grinding tool 200, while the grinding tool 200 is lifted off the planar surface of the longitudinal cut 38, as can be seen in FIG. Not all of the radius R of the grinding tool 200 is engaged with the nozzle needle 30, so that the arc length of the first fillet 37a is made shorter than the arc length of the second fillet 37b.
  • a throttle pin 40 is ground.
  • the planar groove base 41 is ground with the planar surface of the grinding tool 200 and the Nutstirnseite 42 with the convex radius R of the grinding tool 200, wherein only a small portion of the grinding tool 200 is in engagement with the nozzle needle 30.
  • the preceding manufacturing steps 1 to 3b are then repeated for the remaining longitudinal cuts 38 and throttle grindings 40.
  • a total of three longitudinal slits 38 and three throttle slits 40 are made, which are arranged uniformly distributed over the circumference of the nozzle needle tip 31, wherein a respective Drosselanschliff 40 terminates in a first rounding 37a of a longitudinal section 38.
  • steps 1) and 2) are performed together in one manufacturing step, since the grinding tool 200 has the corresponding negative mold of planar surface of the longitudinal cut 38 and second fillet 37b.
  • the cylindrical surface 35 and the cylindrical portion of the nozzle needle tip 31 can be made only at the end of the production chain to the diameter d 35 , the manufacturing order would then l-2-3-3b -4-0.
  • Drosselanschliffe 40, longitudinal grinding 38, fillets 37 and outer surface 35 are made from the outside in, in the order 0-3b-3-2-l-4.

Abstract

L'invention concerne un injecteur de carburant (100), destiné à des moteurs à combustion interne pour injecter du carburant sous haute pression dans une chambre de pression (20), qui est réalisé sous la forme d'un corps de gicleur (10) et dans lequel une aiguille de gicleur (30) est disposée de façon déplaçable longitudinalement. Au niveau de l'aiguille de gicleur (30) est formée une pointe d'aiguille de gicleur (31) qui coopère avec un siège d'aiguille de gicleur (11) configuré au niveau du corps de gicleur (10) et qui ouvre et ferme ainsi au moins un orifice d'injection (19). Lorsque la pointe d'aiguille de gicleur (31) se soulève du siège d'aiguille de gicleur (11), un premier point d'étranglement (12) est formé entre la pointe d'aiguille de gicleur (31) et le siège d'aiguille de gicleur (11). Une zone médiane (34), réalisée au niveau de l'aiguille de gicleur (30), forme conjointement avec une zone de tige (14), réalisée au niveau du corps de gicleur (10), sur la surface intérieure (15) de celle-ci, un second point d'étranglement (50). Le second point d'étranglement (50) a une section transversale d'écoulement constante sur une première course partielle (s1) de l'aiguille de gicleur (30). L'invention concerne en outre un procédé de fabrication de l'injecteur de carburant (100) de l'invention.
PCT/EP2014/068891 2013-09-27 2014-09-05 Injecteur de carburant et procédé pour le fabriquer WO2015043913A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102013219568.0 2013-09-27
DE201310219568 DE102013219568A1 (de) 2013-09-27 2013-09-27 Kraftstoffeinspritzventil und ein Verfahren zu dessen Herstellung

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WO2015043913A1 true WO2015043913A1 (fr) 2015-04-02

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Application Number Title Priority Date Filing Date
PCT/EP2014/068891 WO2015043913A1 (fr) 2013-09-27 2014-09-05 Injecteur de carburant et procédé pour le fabriquer

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DE (1) DE102013219568A1 (fr)
WO (1) WO2015043913A1 (fr)

Citations (8)

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DE10055651A1 (de) * 2000-11-10 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor mit optimierten Einspritzverlauf über den Hubweg
US20060186227A1 (en) * 2005-02-22 2006-08-24 Siemens Vdo Automotive Corporation Common rail injector with active needle closing device
DE102007032741A1 (de) * 2007-07-13 2009-01-15 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
EP2280160A2 (fr) * 2009-07-29 2011-02-02 Robert Bosch GmbH Soupape d'injection de carburant dotée d'une capacité à petites quantités augmentée
DE102009046452A1 (de) * 2009-11-06 2011-05-12 Robert Bosch Gmbh Einspritzdüse für einen lecklosen Kraftstoffinjektor
DE102010044088A1 (de) * 2010-11-18 2012-05-24 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor
DE102011078390A1 (de) * 2011-06-30 2013-01-03 Robert Bosch Gmbh Düsenbaugruppe für einen Kraftstoffinjektor sowie Kraftstoffinjektor

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