EP1504189B1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

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

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Publication number
EP1504189B1
EP1504189B1 EP03729812A EP03729812A EP1504189B1 EP 1504189 B1 EP1504189 B1 EP 1504189B1 EP 03729812 A EP03729812 A EP 03729812A EP 03729812 A EP03729812 A EP 03729812A EP 1504189 B1 EP1504189 B1 EP 1504189B1
Authority
EP
European Patent Office
Prior art keywords
valve
region
bore
valve body
reinforced portion
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.)
Expired - Lifetime
Application number
EP03729812A
Other languages
German (de)
English (en)
Other versions
EP1504189A1 (fr
Inventor
Friedrich Boecking
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 EP1504189A1 publication Critical patent/EP1504189A1/fr
Application granted granted Critical
Publication of EP1504189B1 publication Critical patent/EP1504189B1/fr
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
    • F02M61/18—Injection nozzles, e.g. having valve seats; Details of valve member seated ends, not otherwise provided for
    • F02M61/1866—Valve seats or member ends having multiple cones
    • 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
    • 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
    • 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
    • F02M61/1833—Discharge orifices having changing cross sections, e.g. being divergent
    • 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

Definitions

  • the invention relates to a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • Such fuel injection valves have a valve body in which a bore is formed, which is delimited at its combustion-chamber end by a conical valve seat.
  • a piston-shaped valve needle is arranged longitudinally displaceable, which cooperates with a likewise conical valve sealing surface with the valve seat and thereby controls the opening of at least one injection channel, which starts from the valve seat and leads into the combustion chamber of the internal combustion engine.
  • fuel may or may not flow from a pressure space formed between the valve needle and the wall of the bore.
  • the conical valve seat in this case has an axis of symmetry which coincides with the longitudinal axis of the bore.
  • a fuel injection valve in which the valve body has a uniform wall thickness in the entire end region, even in the region in which the valve needle rests in its closed position and in the combustion chamber end region of the bore. This is the stability of the valve body is not always guaranteed, since high mechanical loads can occur in the end region of the valve body: On the one hand it comes through the placement of the valve needle when closing the injection channels to a deformation of the valve body, causing it to vibrate excited. On the other hand, the pressure in the pressure chamber during operation of the fuel injection valve varies considerably, since the high injection pressure - depending on the nature of the fuel injection valve - only in the pressure chamber abuts when an injection is to take place.
  • valve needle Due to these pressure fluctuations, there is a periodic widening of the valve body and thus mechanical stress.
  • the valve needle is slightly different on deformed valve body on the valve seat, as is the case in the pressureless state.
  • the known fuel injection valves therefore have the disadvantage that the deformations due to pressure oscillation and mechanical loading by the valve needle can lead to excessive wear between the valve needle and the valve seat.
  • an injection valve which has a conical valve seat and a valve needle cooperating with the valve seat for opening and closing a plurality of injection openings.
  • the injection openings start from the conical valve seat and open into countersinks which are formed on the outer surface of the injection valve.
  • the fuel injection valve according to the invention with the features of claim 1 has the advantage that the valve body in the region of the valve seat over the prior art is significantly enhanced, which reduces the expansion by the mechanical loads and thus less wear occurs in the valve seat.
  • the valve body in the end region to a gain with a wall thickness which is at least a factor of 1.2 greater than the wall thickness at the adjacent wall portion. Due to the relatively small wall thickness at the piercing point of the longitudinal axis a certain flexibility of the valve body is maintained, which is essential to a mechanical failure of the valve body by the Avoid opening the valve needle when closing the fuel injection valve.
  • the reinforcement is formed in the region of the valve seat.
  • the injection channels which emanate from the valve seat, open into a recess which is formed on the outside of the valve body.
  • the effective length of the injection channels is shortened, without the stability of the valve body is significantly impaired.
  • a not too long length of the injection channels is required so that the throttling of the fuel flow in the injection channels is not too large.
  • the recess is designed as an annular groove, into which all injection channels open. It does not need to be made for each injection channel a separate recess, which is generally associated with more effort.
  • the reinforcement is formed on the combustion chamber-side end portion of the bore on the inner wall and thereby adjoins the valve seat.
  • a widening of the bore which also leads to a deformation of the valve seat, significantly reduced.
  • the annular gap between the valve needle and the wall of the bore is formed, in the region of the reinforcement at least approximately the same as in the adjacent region of the bore, so as not to hinder the fuel flow to the injection openings.
  • a fuel injection valve is shown in longitudinal section, with only the left half is fully drawn.
  • the fuel injection valve comprises a valve body 1, which is rotationally symmetrical with respect to a longitudinal axis 4 and has a bore 5 whose axis coincides with the longitudinal axis 4.
  • a first reinforcement 22 By a first reinforcement 22, the bore 5 is narrowed at its combustion chamber end, so that on the inner wall of the bore 5, a conical surface 26 and a reduced diameter cylinder portion 24 is formed.
  • the first reinforcement 22 of the valve body 1 is in the figure 1 through a dashed line illustrates.
  • a conical valve seat 8 connects, which forms the combustion chamber end of the bore 5.
  • valve needle 3 From the valve seat 8 is at least one injection channel 18 from which penetrates the valve body 1 and opens directly into the combustion chamber of the internal combustion engine.
  • a piston-shaped valve needle 3 is arranged longitudinally displaceable, wherein between the valve needle 3 and the wall of the bore 5, a pressure chamber 7 is formed, which is filled via a supply channel, not shown in the drawing with fuel at high pressure.
  • the valve needle 3 has at the level of the conical surface 26 on a pressure shoulder 6 and then passes into a tapered portion 103, to which a conical valve sealing surface 10 is connected.
  • the combustion chamber-side tip of the valve needle 3 is formed by a conical surface 14, which is separated from the valve sealing surface 10 by an annular groove 12.
  • valve needle tip and the conical valve seat 8 By appropriate opening angle of the conical surfaces of the valve needle tip and the conical valve seat 8 can be achieved that the edge acts at the transition of the annular groove 12 to the valve sealing surface 10 as a sealing edge, which rests against the valve seat 8 at this first plant on the valve needle.
  • the valve needle 3 By elastic deformation of the valve needle 3 and the valve body 1 in the region of the valve seat 8, the valve needle 3 is finally in its closed position with a large part of the valve sealing surface 10 on the valve seat 8.
  • the valve needle 3 cooperates with the valve seat 8 for controlling the injection channels 18.
  • the valve needle 3 is acted upon by a device, not shown in the drawing, with a closing force, for example by a prestressed spring, in the direction of the valve seat 8, so that it rests with the valve sealing surface 10 on the valve seat 8.
  • a closing force for example by a prestressed spring
  • the hydraulic force on the valve needle 3 results in a force that is opposite to the closing force.
  • valve needle 3 lifts off from the valve seat 8, so that fuel can flow from the pressure chamber 7 between the valve sealing surface 10 and the valve seat 8 to the injection channels 18. With a reduction of the fuel supply in the pressure chamber 7, the fuel pressure decreases there again. Finally, the closing force on the valve needle 3 again predominates and this slides back into its closed position.
  • valve needle 3 Due to the increasing pressure in the pressure chamber 7 results in a slight widening of the valve body 1 in the region of the valve seat 8 and the cylinder portion 24.
  • the valve needle 3 remains virtually unchanged in shape, since it is solid. It thus changes the shape of the valve body 1 in the region of the valve seat 8 slightly, so that there is a slight movement of the valve seat 8 relative to the valve sealing surface 10, which leads over time to wear in this area. Also, by the impact of the valve needle 3 on the valve seat 8 results in vibrations of the valve body 1, which lead to a relative movement of valve sealing surface 10 and valve seat 8.
  • the valve body 1 is thickened in the region of the valve seat 8 by a second reinforcement 23, so that a greater stability results and thus a reduced expansion. This is also the effect of the first reinforcement 22, which reduces a widening of the valve body 1 in the region of the combustion chamber-side end of the bore 5. It can also be provided here that either only the first reinforcement 22 or only the second reinforcement 23 is formed.
  • the wall thickness of the valve body 1 in the region of the valve seat 8 is at the point at which the piercing point 30 of the longitudinal axis 4 is equal to a thickness h 0 .
  • the valve body 1 is thickened by the second reinforcement 23, so that perpendicular to the valve sealing surface 8 a wall thickness h 1 results which exceeds at least a factor of 1.2 the wall thickness h 0 is.
  • a fixed upper limit for the ratio of the wall thicknesses h 0 and h 1 does not exist, but should be at a ratio h 1 / h 0 of about 2.0 a meaningful upper limit.
  • the wall thickness H 1 in the region of the first reinforcement 22 is greater than the wall thickness H 0 of the adjacent wall region by at least a factor of 1.2, ie a ratio of H 1 / H 0 ⁇ 1.2.
  • FIG. 2 shows a fuel injection valve.
  • the valve body 1 is again shown in longitudinal section, with only one half of the rotationally symmetrical valve body 1 is drawn. Instead of an annular groove and a conical surface, the valve needle 3 has only a single conical valve sealing surface 10, which is pressed into the conical valve seat 8 by the contact pressure of the closing force.
  • the valve seat 8 is thickened by a second reinforcement 23, whose share on the valve body 1 is illustrated by a dashed line.
  • the wall thickness h 1 in the region of the injection channels 18 is also greater here by at least a factor of 1.2 than the wall thickness h 0 am Piercing point 30 of the longitudinal axis 4.
  • h 1 With increasing wall thickness h 1 correspondingly extends the length of the injection channels 18, but this is only possible to a limited extent: If the injection channel 18 is too long, the fuel flow during the injection is throttled too much and reduces the effective effective injection pressure yourself.
  • recesses 20 are formed from the outside, which are designed as a countersink and in each of which an injection channel 18 opens. The effective length of the injection channels 18 is thus smaller, since the opening angle of the countersink 20 is so large that the exiting injection jet does not touch the wall of the countersink 20.
  • a countersink 20 with a strictly conical outer wall and other shapes are conceivable, for example, cylindrical recesses, which have a sufficiently large diameter.
  • the formation of the countersink 20 can be done for example by drilling or electroerodating.
  • FIG. 3 shows an external view of the combustion-chamber-side tip of the valve body 1 of an injection valve according to the invention.
  • various recesses 20 instead of various recesses 20 only a single recess in the form of an annular groove 32 is formed here, which surrounds the valve body 1 over its entire circumference and open into the all injection channels 18.
  • the cross section of the annular groove 32 is dimensioned so that the injection jets do not touch the wall of the annular groove 32 here as well.

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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)

Abstract

L'invention concerne une soupape d'injection de carburant pour moteurs à combustion interne, qui comprend un corps de soupape (1), dans lequel un pointeau de soupape en forme de piston (3) est installé de manière à pouvoir effectuer un déplacement longitudinal dans un alésage (5) présentant un axe longitudinal (4), lequel pointeau de soupape coopère avec un siège de soupape conique (8), formé sur l'extrémité côté chambre de combustion dudit alésage (5), par le biais d'une surface d'étanchéité (10) de ladite soupape. Au moins un canal d'injection (18) s'étend du siège de soupape (8) pour déboucher dans la chambre de combustion du moteur à combustion interne. L'épaisseur de paroi (h1) du corps de soupape (1) dans la zone du siège de soupape (8) est, au moins dans une zone partielle, au moins 1,3 fois supérieure à l'épaisseur de paroi (h0) du corps de soupape (1) au point de percée (30) de l'axe longitudinal (4).

Claims (4)

  1. Injecteur de carburant pour un moteur à combustion interne, dans lequel :
    - un corps de soupape (1) dans lequel un alésage (5) a son extrémité située du côté de la chambre de combustion, délimitée par un siège de soupape essentiellement conique,
    - une aiguille de soupape (3) en forme de piston peut coulisser dans l'alésage (15) et coopère par une portée d'étanchéité de soupape (10) avec le siège de soupape (8),
    - au moins un canal d'injection (18) part du siège de soupape (8) et débouche dans la chambre de combustion du moteur,
    - le corps de soupape (1) à sa zone d'extrémité située du côté de la chambre de combustion, présente un renforcement (22 ; 23) dont l'épaisseur de paroi (h1) est au moins 1,2 fois plus grande que l'épaisseur de paroi (h0) dans la zone de paroi en limite du renforcement (22), et
    - le renforcement (22) se trouve au moins dans une zone partielle proche du siège de soupape (8),
    caractérisé en ce que
    la face externe du corps de soupape (1) présente un évidement (20) en forme de rainure annulaire (32) s'étendant sur toute la périphérie du corps de soupape (1) et dans laquelle débouchent les canaux d'injection (18).
  2. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    la longueur du canal d'injection (18) correspond au moins approximativement à l'épaisseur de paroi (h0) du corps de soupape (1) dans la zone du point de traversée (30) de l'axe longitudinal (4).
  3. Injecteur de carburant selon la revendication 1,
    caractérisé en ce que
    le renforcement (22) sur la partie d'extrémité de l'alésage (5) située du côté de la chambre de combustion, est réalisé sur la paroi interne, ce renforcement (22) étant en limite du siège de soupape (8).
  4. Injecteur de carburant selon la revendication 3,
    caractérisé en ce que
    l'aiguille de soupape (3) est amincie dans la zone de renforcement (22), de sorte que la largeur de la fente annulaire entre la paroi interne de l'alésage (5) et l'aiguille de soupape (3) est, dans la zone du renforcement, au moins à peu près égale à ce qu'elle est dans la zone de l'alésage (5) délimitant le renforcement (22) dans la direction opposée à la chambre de combustion.
EP03729812A 2002-05-02 2003-03-21 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP1504189B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE2002119608 DE10219608A1 (de) 2002-05-02 2002-05-02 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10219608 2002-05-02
PCT/DE2003/000936 WO2003093669A1 (fr) 2002-05-02 2003-03-21 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP1504189A1 EP1504189A1 (fr) 2005-02-09
EP1504189B1 true EP1504189B1 (fr) 2007-07-04

Family

ID=29264993

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03729812A Expired - Lifetime EP1504189B1 (fr) 2002-05-02 2003-03-21 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (3)

Country Link
EP (1) EP1504189B1 (fr)
DE (2) DE10219608A1 (fr)
WO (1) WO2003093669A1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102007051408A1 (de) 2007-10-25 2009-05-28 Prelatec Gmbh Verfahren zum Bohren von Löchern definierter Geometrien mittels Laserstrahlung
WO2010121767A1 (fr) * 2009-04-20 2010-10-28 Prelatec Gmbh Buse présentant au moins un trou d'injection pour la pulvérisation de fluides
DE102011077268A1 (de) * 2011-06-09 2012-12-13 Robert Bosch Gmbh Einspritzventil für Brennkraftmaschinen
DE102012211459A1 (de) * 2012-07-03 2014-01-09 Robert Bosch Gmbh Kraftstoffeinspritzventil mit verbessertem Spritzloch
DE102013220917A1 (de) * 2013-10-15 2015-04-16 Continental Automotive Gmbh Einspritzdüse

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3306078A1 (de) * 1983-02-22 1984-08-23 Robert Bosch Gmbh, 7000 Stuttgart Kraftstoffeinspritzduese fuer brennkraftmaschinen
JP2819702B2 (ja) * 1989-12-12 1998-11-05 株式会社デンソー 燃料噴射弁
DE4025542A1 (de) * 1990-08-11 1992-02-13 Kloeckner Humboldt Deutz Ag Verfahren zum betreiben einer selbstzuendenden brennkraftmaschine
DE4200709A1 (de) * 1992-01-14 1993-07-15 Bosch Gmbh Robert Kraftstoffeinspritzduese fuer brennkraftmaschinen
JPH07224739A (ja) * 1994-02-15 1995-08-22 Nissan Motor Co Ltd 燃料噴射ノズル
JPH09177640A (ja) * 1995-12-15 1997-07-11 Caterpillar Inc 高サック容積を有する燃料噴射器による燃焼排気ガス清浄化システムとその方法
DE19729827A1 (de) * 1997-07-11 1999-01-14 Bosch Gmbh Robert Kraftstoffeinspritzventil
DE10000501A1 (de) 2000-01-08 2001-07-19 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen

Non-Patent Citations (1)

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

Also Published As

Publication number Publication date
EP1504189A1 (fr) 2005-02-09
DE10219608A1 (de) 2003-11-20
DE50307613D1 (de) 2007-08-16
WO2003093669A1 (fr) 2003-11-13

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