EP2927473B1 - Soupape d'injection de carburant pour moteurs à combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs à combustion interne Download PDF

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Publication number
EP2927473B1
EP2927473B1 EP14163463.4A EP14163463A EP2927473B1 EP 2927473 B1 EP2927473 B1 EP 2927473B1 EP 14163463 A EP14163463 A EP 14163463A EP 2927473 B1 EP2927473 B1 EP 2927473B1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
needle
fuel
section
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP14163463.4A
Other languages
German (de)
English (en)
Other versions
EP2927473A1 (fr
Inventor
Stefano Filippi
Mauro Grandi
Francesco Lenzi
Valerio Polidori
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.)
Continental Automotive GmbH
Original Assignee
Continental Automotive 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 Continental Automotive GmbH filed Critical Continental Automotive GmbH
Priority to EP14163463.4A priority Critical patent/EP2927473B1/fr
Publication of EP2927473A1 publication Critical patent/EP2927473A1/fr
Application granted granted Critical
Publication of EP2927473B1 publication Critical patent/EP2927473B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/08—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 the valves opening in direction of fuel flow
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0635—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding
    • F02M51/0642—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto
    • F02M51/0653—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a plate-shaped or undulated armature not entering the winding the armature having a valve attached thereto the valve being an elongated body, e.g. a needle valve

Definitions

  • Fuel injection valves which operate electromagnetically are well known. With the aid of a magnetic coil which is chargeable by electricity to generate a magnetic field, a magnetisable armature which may be combined with a valve needle, will be stimulated for movement. Normally, the movement is an axial movement along a valve needle axis of the valve needle.
  • Fuel injection valves may have different nozzle orifices producing different injection sprays.
  • the pattern of the injection spray depends on the nozzle orifice.
  • the most well known injection spray is a conical spray pattern which may be generated for example by an inward opening injector.
  • Inward opening injectors such as the injector disclosed by US 2002/0079386 A1 , have a valve needle which moves in upstream direction with respect to the fuel stream for opening the nozzle orifice so that the valve needle has to be opened against a fuel force produced by the fuel.
  • Another pattern of an injection spray is a holed cone spray pattern which may be realized e.g. by an outward opening injector.
  • WO 03/072929 A1 discloses such an injector.
  • the valve needle of an outward opening injector moves in the direction of the fuel stream for opening the nozzle orifice.
  • a needle tip of the valve needle may project beyond a housing of the fuel injection valve.
  • the needle tip may be shaped analogously to that of a charge-cycle valve of the combustion engine. This needle tip shape is particularly well suited for producing a holed cone spray distribution.
  • the guide means is designed to support the mechanism of movement in a stable condition, i.e. few microns of tolerance exists between the housing and the valve needle in the guided area. On the other side, the guide means has to guarantee that a sufficient amount of fuel may pass the guide means; therefore, a fluid channel has to be created.
  • valve needle When the valve needle starts to move for a few microns of lift, a pressure drop distribution of the fuel is mainly responsible for the spray formation. Because of the channels and stays of the guide means, a degradation of the axial-symmetrical spray momentum can occur so that the spray cone deviates from a desired balanced and rotationally invariant shape.
  • a fuel injection valve for an internal combustion engine is specified.
  • the fuel injection valve may be provided for a fuel injection device of the internal combustion engine.
  • the fuel injection valve comprises a housing and a valve needle.
  • the housing has a first housing portion with a recess having an inner surface.
  • a nozzle orifice is provided in first housing portion being positioned at a downstream end of the recess.
  • the valve needle has a needle axis and is movably positioned in the recess.
  • the valve needle comprises a shaft and a needle tip which is positioned at a first end of the shaft.
  • the needle tip of the valve needle is in the shape of a truncated double cone with the base areas of the two truncated cone sections facing towards each other and in particular coinciding.
  • the nozzle orifice and the needle tip together form an injection nozzle of the fuel injection valve.
  • the needle tip is operable to prevent fuel from passing through the nozzle orifice in a closing position and is movable in downstream direction to allow a stream of fuel passing the nozzle orifice in an opening position of the valve needle.
  • a first guide portion of the valve needle has a plurality of protrusions for guiding the valve needle.
  • a fluid channel - through which fuel can pass the first guide portion in axial direction - is formed between in each case two protrusions which directly follow one another in angular direction around the needle axis.
  • This may be realized by a guide means with stays - representing the protrusions - and flats, the stays and flats alternating in angular direction around the needle axis so that channels between the inner surface and each of the flats are realized and at the same time the stays enable the guiding of the valve needle in the housing.
  • the valve needle comprises a resistance portion between the first guide portion and the needle tip for orientating the fuel stream.
  • the resistance portion in particular protrudes radially from the shaft of the valve needle.
  • the resistance portion is in particular operable to effect a flow resistance for fuel flowing along the needle shaft from the first guide portion towards the needle tip by means of protruding radially from the shaft.
  • the flow resistance may also be denoted as flow resistivity or as drag.
  • a first radial gap between the inner surface and the protrusions is formed.
  • the protrusions are radially spaced apart from the inner surface of the recess by a first distance.
  • the first distance is in particular the smallest distance between any one of the protrusions and the inner surface when the valve needle is centered in the recess.
  • the resistance portion has a rotationally invariant shape with respect to rotation around the needle axis.
  • the third gap is annularly shaped, i.e. it is in particular rotationally invariant with respect to the needle axis. Such shapes may be particularly advantageous for achieving a rotationally symmetric spray distribution.
  • the resistance portion comprises a first section and a second section. They are both in the shape of truncated cones wherein the base of the first section corresponds to the base of the second section.
  • the - imaginary - bases are congruent and flush.
  • they are parallel to one another and preferably perpendicular to the needle axis. In one development, they are positioned in a common plane. The advantage of this design is the particularly small risk for a stall of the fluid stream, in particular when the first portion has an axial extension which is larger than the axial extension of the second portion.
  • a segue between the first portion and the second portion is formed having a third axial extension and in particular a maximum diameter, wherein the third gap is defined by the segue and the inner surface.
  • the resistance portion has its largest cross-sectional dimension -represented by the maximum diameter - in the region of the segue.
  • the minimum spacing defining the third diameter is, thus, located between the segue of resistance portion and the inner surface. Because of the third axial extension of the third gap the fuel stream distribution becomes more stabilized.
  • the valve needle 3 is movably arranged in a first housing portion 5 of the housing 2, in particular it is received in a recess 6 of the first housing portion 5.
  • the valve needle 3 is operable to open and close a nozzle orifice 7 of the recess 6, the nozzle orifice 7 being positioned at a downstream end of the recess 6.
  • the needle tip 8 has a first truncated cone shaped section 24 and a second truncated cone shaped section 25.
  • the first truncated cone 24 and the second truncated cone 25 are positioned in such way that a base area 26 of the first truncated cone 24 coincides with a base area 27 of the second truncated cone 26.
  • the seconf cone shaped section 25 is positioned subsequent to the first cone shaped section 24 in axial direction away from the shaft 16.
  • the first truncated cone shaped section 24 interacts with the valve seat 23 for sealing of the nozzle orifice 7.
  • the second housing portion 9 comprises a valve spring 10.
  • This valve spring 10 is circumferentially surrounding a portion of the valve needle 3.
  • the valve spring 10 is preloaded to press the needle tip 8 against the valve seat 23.
  • Figure 2 represents a longitudinal sectional view of a cut-out of the fuel injection valve 1 as seen in figure 1 .
  • the needle tip 8 is designed like a typically cylinder valve of an inlet or an outlet valve of an internal combustion engine. With exception of the nozzle orifice 7 and an upstream portion of the recess 6 where the valve spring 10 is positioned, an inner diameter di of the recess 6 may be constant. Also, with exception of the guide portions 17, 18 a first diameter dv of the shaft 16 is constant, so that an annular passage 28 with a constant flow cross-section 29 having a second gap 30 is created.
  • Figure 3 shows a longitudinal sectional view of a cut-out of an exemplary embodiment of fuel injection valve.
  • the fuel injection valve of the present exemplary embodiment is, in general, of the same construction as the fuel injection valve discussed in connection with figures 1 and 2 above.
  • the valve needle 3 has a resistance portion 32.
  • the resistance portion 32 is arranged between the first guide portion 17 and the needle tip 8, upstream of the first truncated cone 25.
  • the resistance portion 32 is a rotationally symmetric protrusion of the shaft 16.
  • An annular third gap 31 between the valve needle 3 and the inner surface 21 is shaped by the resistance portion 32 of the valve needle 3.
  • the third gap 31 is bigger than the first gap 22 but smaller than the second gap 30.
  • the resistance portion 32 due to the resistance portion 32 protruding radially outward from the shaft 16 and reducing the hydraulic diameter, the resistance portion 32 generates a constriction of in the fuel path through the recess 6 in this or any other embodiment of the invention.
  • the fuel path has in particular a rotationally invariant shape with respect to rotation around the needle axis.
  • the resistance portion 32 effects a flow resistance for the fuel flowing through the fluid channels of the first guide portion 17 and further along the shaft 16 which smoothes angular differences in fuel flow and improves the homogeneity of the angular flow distribution.
  • a ratio between the smallest flow cross section of the first guide portion 17 and the smallest flow cross section of the resistance portion 32 has a value of 10 or more, in particular of 20 or more.
  • the hydraulic diameter of the recess 6 in the region of the first guide portion 17 is at least 10 times larger, in particular at least 20 times larger, than in the region of the resistance portion 32.
  • the hydraulic diameter is in particular defined by the cross-sectional area of the fluid channels shaped by the stays 20 and flats 19. The value is set in dependence on a stabilization pressure level which is desired for an application of the combustion engine.
  • the resistance portion 32 has a first section 33 and a second section 34 both formed as a truncated cone.
  • the truncated cones are orientated to each other in this way that their base areas correspond.
  • the second section 34 is positioned between the first section 33 and the first truncated cone 24 of the needle tip 8.
  • the second axial extension L2 of the second section 34 is smaller than a first axial extension L1 of the first section 33. This relates to a preferred flow cross section upstream of the third gap 31.
  • a segue 35 between the first section 33 and the second section 34 is designed, see Figure 4 .
  • the segue 35 has a constant maximum diameter dmax over a third axial extension L3, so that the third gap 31 is realized between the segue 35 and the inner surface 21.
  • the resistance portion 32 and the needle tip 6 together have a shape 38 formed like a "S”, respectively a curved shape 38.

Landscapes

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

Claims (9)

  1. Soupape d'injection de carburant pour moteur à combustion interne, comprenant :
    - un boîtier (2) ayant une première partie (5) de boîtier comportant un évidement (6) avec une surface intérieure (21),
    - un orifice (7) de gicleur de la première partie (5) de boîtier étant placé à l'extrémité aval de l'évidement (6),
    - un pointeau (3) de soupape ayant un axe (4) de pointeau et étant placé mobile dans l'évidement (6), comprenant une tige (16) et une pointe (8) de pointeau placée à une première extrémité de la tige (16), constituant avec l'orifice (7) de gicleur l'injecteur de carburant de la soupape (1) d'injection de carburant et empêchant le carburant de traverser l'orifice (7) de gicleur dans la position fermée de la soupape (1) d'injection de carburant et étant mobile en direction aval pour permettre à un jet de carburant de passer par l'orifice (7) de gicleur dans une position d'ouverture du pointeau (3) de soupape,
    - une première partie (17) de guide du pointeau (3) de soupape ayant une pluralité de protubérances radiales (39) pour guider le pointeau (3) de soupape,
    - un premier interstice radial (22) entre la surface intérieure (21) et les protubérances (39),
    - un deuxième interstice radial (30) entre la surface intérieure (21) et la tige (16),
    dans laquelle le pointeau (3) de soupape comprend une partie (32) de résistance pour orienter le jet de carburant entre la première partie (17) de guide et la pointe (8) de pointeau,
    dans laquelle est constitué un troisième interstice radial (31) entre la surface intérieure (21) et la partie (32) de résistance, qui est plus grand que le premier interstice (22) et plus petit que le deuxième interstice (30).
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que la partie (32) de résistance dépasse radialement de la tige (16) de telle façon que le troisième interstice radial (31) est en forme d'anneau.
  3. Soupape d'injection de carburant selon la revendication 1 ou 2, caractérisée en ce que la partie (32) de résistance comprend une première section (33) et une seconde section (34), les deux en forme de tronc de cône, dans laquelle la base de la première section (33) correspond à la base de la seconde section (34).
  4. Soupape d'injection de carburant selon la revendication 3, caractérisée en ce que la première extension axiale (L1) de la première partie est supérieure à la seconde extension axiale (L2) de la seconde partie.
  5. Soupape d'injection de carburant selon la revendication 3 ou 4, caractérisée en ce que la partie (32) de résistance comporte une transition (35) entre la première section (33) et la seconde section (34), la transition (35) ayant une troisième extension axiale (L3) et un diamètre maximal (dmax), dans laquelle le troisième interstice radial (31) est constitué entre la transition (35) et la surface intérieure (21).
  6. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce que la partie (32) de résistance a une forme (38) courbe.
  7. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce que le diamètre hydraulique de l'évidement (6) dans la zone de la première partie (17) de guide est au moins dix fois plus grand que dans la zone de la partie (32) de résistance.
  8. Soupape d'injection de carburant selon l'une quelconque des revendications précédentes, caractérisée en ce que le pointeau (3) de soupape comprend une seconde partie (18) de guide en amont de la première partie (17) de guide.
  9. Soupape d'injection de carburant selon la revendication 8, caractérisée en ce que la seconde partie (18) de guide comprend au moins une protubérance radiale (39).
EP14163463.4A 2014-04-03 2014-04-03 Soupape d'injection de carburant pour moteurs à combustion interne Not-in-force EP2927473B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP14163463.4A EP2927473B1 (fr) 2014-04-03 2014-04-03 Soupape d'injection de carburant pour moteurs à combustion interne

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP14163463.4A EP2927473B1 (fr) 2014-04-03 2014-04-03 Soupape d'injection de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP2927473A1 EP2927473A1 (fr) 2015-10-07
EP2927473B1 true EP2927473B1 (fr) 2017-09-20

Family

ID=50424130

Family Applications (1)

Application Number Title Priority Date Filing Date
EP14163463.4A Not-in-force EP2927473B1 (fr) 2014-04-03 2014-04-03 Soupape d'injection de carburant pour moteurs à combustion interne

Country Status (1)

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EP (1) EP2927473B1 (fr)

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2861553B2 (ja) * 1991-12-12 1999-02-24 日産自動車株式会社 燃料噴射弁
DE19623713B4 (de) * 1996-06-14 2008-06-19 Robert Bosch Gmbh Einspritzventil, insbesondere zum direkten Einspritzen von Kraftstoff in einen Brennraum eines Verbrennungsmotors
DE10055651A1 (de) * 2000-11-10 2002-05-23 Bosch Gmbh Robert Druckgesteuerter Injektor mit optimierten Einspritzverlauf über den Hubweg
DE10208222A1 (de) * 2002-02-26 2003-10-30 Bosch Gmbh Robert Brennstoffeinspritzventil
DE102011077464A1 (de) * 2011-06-14 2012-12-20 Robert Bosch Gmbh Kraftstoffinjektor für eine Brennkraftmaschine
EP2698527A1 (fr) * 2012-08-16 2014-02-19 Continental Automotive GmbH Ensemble de soupape pour soupape dýinjection et soupape dýinjection

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
None *

Also Published As

Publication number Publication date
EP2927473A1 (fr) 2015-10-07

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