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EP1321661B1 - Soupape d'injection de combustible pour moteurs à combustion interne - Google Patents

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

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Publication number
EP1321661B1
EP1321661B1 EP02017114A EP02017114A EP1321661B1 EP 1321661 B1 EP1321661 B1 EP 1321661B1 EP 02017114 A EP02017114 A EP 02017114A EP 02017114 A EP02017114 A EP 02017114A EP 1321661 B1 EP1321661 B1 EP 1321661B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve seat
annular groove
bore
conical
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
EP02017114A
Other languages
German (de)
English (en)
Other versions
EP1321661A2 (fr
EP1321661A3 (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 EP1321661A2 publication Critical patent/EP1321661A2/fr
Publication of EP1321661A3 publication Critical patent/EP1321661A3/fr
Application granted granted Critical
Publication of EP1321661B1 publication Critical patent/EP1321661B1/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
    • F02M61/1873—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
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known from the document DE 199 42 370 A1 is known.
  • a valve needle is arranged longitudinally displaceably in the bore of a valve body, wherein between the wall of the bore and the valve needle is formed with a fuel can be filled under high pressure pressure space.
  • a plurality of injection openings is formed in the valve body, through which the bore is connected to the combustion chamber of the internal combustion engine.
  • a conical valve seat is formed, on which the valve needle comes into abutment with a valve sealing surface in its closed position. In the closed position of the valve needle, the fuel from the pressure chamber can not flow to the injection openings.
  • the valve sealing surface has two conical surfaces, with the first conical surface located upstream of the second conical surface, and both conical surfaces directly adjacent one another.
  • the opening angle of the first conical surface is smaller than the opening angle of the valve seat, which in turn is smaller than the opening angle of the second conical surface.
  • the valve needle is moved in the bore by the hydraulic pressure acting on parts of the valve sealing surface against a closing force directed to the valve seat.
  • the pressure at which the valve needle just lifts off the valve seat is called the opening pressure.
  • This is dependent on the hydraulically effective seat diameter of the valve needle on the valve seat, which corresponds to the diameter of the sealing edge in the geometry described above. However, this only applies as long as no deformations of valve needle and valve seat occur. In operation, there is always an elastic and, in particular after prolonged operation, a plastic deformation of the valve sealing surface through the valve needle. Thus, the hydraulically effective seat diameter of the valve needle can change over time and thus also the opening pressure.
  • the DE 19 820 513 A1 discloses a fuel injection valve according to the preamble of claim 1.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that the hydraulically effective diameter of the valve needle is maintained at the valve seat over the entire life without the stiffness of the valve needle is reduced.
  • two mutually parallel annular grooves are formed in the valve seat, each extending in radial planes to the longitudinal axis of the bore. The valve needle rests against the valve seat between the two annular grooves. As a result, the area of the valve seat against which the valve needle rests is limited, and thus also the hydraulically effective seat diameter of the valve needle.
  • the difference angle between the first conical surface and the conical valve seat is greater than the difference angle between the second conical surface and the valve seat.
  • the first annular groove is configured as a flat depression of the bore. In this way, the first annular groove can be produced in a simple manner with high precision. It is particularly advantageous here that the first annular groove remains connected to the pressure chamber without further measures, so that the valve sealing surface is acted upon by the fuel pressure in the pressure chamber at any time.
  • FIG. 1 an embodiment of the fuel injection valve according to the invention is shown in longitudinal section.
  • a bore 3 is formed, which has a longitudinal axis 8 and in which a piston-shaped valve needle 5 is arranged longitudinally displaceable.
  • a conical valve seat 9 is arranged, in which at least one injection opening 11 is formed, which opens into the mounting position of the fuel injection valve in the combustion chamber of the internal combustion engine.
  • the valve needle 5 is sealingly guided in a guide section 23 of the bore 3 and tapers to the combustion chamber to form a pressure shoulder 13.
  • the valve needle 5 is in a valve sealing surface 7, which abuts the valve seat 9 in the closed position of the valve needle 5.
  • a pressure chamber 19 is formed which is radially expanded at the level of the pressure shoulder 13.
  • the pressure in the space 19 constantly or temporarily high fuel pressure builds.
  • the valve needle 5 is acted upon by a device, not shown in the drawing, with a closing force acting on the valve needle 5 in the direction of the valve seat 9. Characterized the valve needle 5 is pressed with the valve sealing surface 7 against the valve seat 9, so that no fuel from the pressure chamber 19 can reach the injection openings 11.
  • the pressure in the pressure chamber 19 is increased until, when an opening pressure is reached, the hydraulic force on the pressure shoulder 13 and on parts of the valve sealing surface 7 exceeds the closing force.
  • the valve needle 5 then lifts off with its valve sealing surface 7 from the valve seat 9, and fuel flows from the pressure chamber 19 between the valve sealing surface 7 and the valve seat 9 through the injection openings 11 and is injected from there into the combustion chamber.
  • the injection is terminated either by an increase in the closing force or by an interruption of the fuel supply into the pressure chamber 19.
  • the valve needle 5 slides, driven by the closing force, back into contact with the valve seat 9 in its closed position and thus interrupts the fuel supply to the injection openings eleventh
  • FIG. 2 shows an enlargement of the FIG. 1 in the region of the valve seat 9.
  • the valve sealing surface 7 is divided into a first conical surface 30 and a second conical surface 32, wherein an annular edge 34 is formed at the transition of the two surfaces.
  • the opening angle of the first conical surface 30 is in this case smaller than the opening angle of the conical valve seat 9, which in turn is smaller than the opening angle of the second conical surface 32 in the valve seat 9, a first annular groove 36 is formed and a second annular groove 38 parallel thereto, wherein both annular grooves 36,38 with respect to the longitudinal axis 8 of the bore 3 lie in a radial plane.
  • the first annular groove 36 is used as a countersink of the bore 3 carried out, thereby forming an annular shoulder 37 is formed.
  • the edge 40 formed at the transition of the annular shoulder 37 to the valve sealing surface 9 and the second annular groove 38 bound the part of the valve seat 9, which serves as a contact surface 10 for the valve needle 5.
  • the annular edge 34 is arranged in the closed position of the valve needle 5 either within this portion of the valve seat 9 or at the level of the second annular groove 38.
  • valve needle 9 and the valve body 1 were ideally rigid, then the valve needle 5 and the valve seat 9 would contact the second annular groove 38 only at the annular edge 34 or at the transition of the valve seat 9. Due to the occurring elastic deformations, the valve needle 5 is located on the entire contact surface 10 or at least on the largest part thereof, so that reduce the surface pressures occurring accordingly.
  • the two annular grooves 36,38 is ensured in any case that the contact surface 10 can not grow beyond the limited by the annular grooves 36,38 area.
  • the applied by the fuel pressure in the pressure chamber 19 partial surface of the first conical surface 30 is determined and thus the opening pressure of the valve needle 5, since this is in addition to the surface of the pressure shoulder 13 and the corresponding part surface of the valve sealing surface 7 determinative.
  • the difference angle d 1 between the first conical surface 30 and the valve seat 9 is smaller than the difference angle d 2 between the second conical surface 32 and the valve seat 9, which corresponds to the so-called inverse seat angle difference. This additionally prevents that by hamming the annular edge 34 in the valve seat 9, the hydraulically acted upon by the fuel in the pressure chamber 19 surface is changed and thereby causes a change in the opening pressure.
  • FIG. 3 a further embodiment is shown, wherein the same section as in FIG. 2 is shown.
  • the valve seat 9 extends to the wall of the bore 3.
  • the first annular groove 36 is formed in the same way as the second annular groove 38, but it has a greater depth and comprises a larger area of the valve seat 9.
  • the contact surface 10 is again through the both annular grooves 36,38 limited, being ensured by the relatively large first annular groove 36, that this always remains hydraulically connected to the pressure chamber 19.
  • the opening angle of the valve seat 9 is about 55 ° to 65 °, preferably about 60 °.
  • the corresponding difference angles d 1 and d 2 to the conical surfaces 30, 32 of the valve sealing surface 7 are a few degrees, preferably 0.5 ° to 3 °.

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 (6)

  1. Soupape d'injection de carburant pour moteurs à combustion interne comprenant un corps de soupape (1), dans lequel est disposée, dans un alésage (3), une aiguille de soupape (5) en forme de piston déplaçable longitudinalement, un espace de pression (19) pouvant être rempli de carburant étant disposé entre l'aiguille de soupape (5) et la paroi de l'alésage (3), du carburant pouvant affluer hors de cet espace de pression au moins dans une ouverture d'injection (11) réalisée à une extrémité de l'alésage (3) du côté de la chambre de combustion, et comprenant un siège de soupape (9) conique, réalisé à l'extrémité de l'alésage (3) du côté de la chambre de combustion, avec lequel l'aiguille de soupape (5) coopère avec une surface d'étanchéité de soupape (7) réalisée à son extrémité du côté de la chambre de combustion en vue de commander l'au moins une ouverture d'injection (11), une première surface conique (30) et une deuxième surface conique (32) étant réalisées sur la surface d'étanchéité de soupape, la première surface conique (30) présentant un angle d'ouverture qui est inférieur à l'angle d'ouverture du siège de soupape (9), qui est à son tour inférieur à l'angle d'ouverture de la deuxième surface conique (32), et entre les deux surfaces coniques (30 ; 32) étant réalisée une arête annulaire (34), une première rainure annulaire (36) s'étendant dans un plan radial de l'alésage (3) étant réalisée dans le siège de soupape (9) ainsi qu'une deuxième rainure annulaire (38) disposée en aval de la première rainure annulaire (36) et parallèlement à celle-ci, caractérisée en ce que la première rainure annulaire (36) est réalisée sous forme de renfoncement de surface de l'alésage (3), une arête (40) étant formée au niveau de la transition de la première rainure annulaire (36) au siège de soupape (9), de sorte que la partie du siège de soupape (9) limitée par l'arête (40) et la deuxième rainure annulaire (38) serve de surface d'appui (10) pour l'aiguille de soupape (5), l'aiguille de soupape (5) reposant, dans sa position de fermeture, sur la totalité de la surface d'appui (10) ou au moins sur la plus grande partie de celle-ci.
  2. Soupape d'injection de carburant selon la revendication 1, caractérisée en ce que l'arête annulaire (34) se situe dans la position de fermeture de l'aiguille de soupape (5) à l'intérieur de la deuxième rainure annulaire (38).
  3. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que l'angle différentiel (d2) de la deuxième surface conique (32) avec le siège de soupape conique (9) est supérieur à l'angle différentiel (d2) entre la première surface conique (30) et le siège de soupape (9).
  4. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que l'angle d'ouverture du siège de soupape conique (9) vaut au moins approximativement 60°.
  5. Soupape d'injection de combustible selon la revendication 1, caractérisée en ce que les ouvertures d'injection (11) débouchent dans le siège de soupape (9) en aval de la deuxième rainure annulaire (38).
  6. Soupape d'injection de combustible selon l'une quelconque des revendications précédentes, caractérisée en ce que la première rainure annulaire (36) est toujours connectée hydrauliquement à l'espace de pression (19).
EP02017114A 2001-12-22 2002-07-30 Soupape d'injection de combustible pour moteurs à combustion interne Expired - Lifetime EP1321661B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10163908A DE10163908A1 (de) 2001-12-22 2001-12-22 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10163908 2001-12-22

Publications (3)

Publication Number Publication Date
EP1321661A2 EP1321661A2 (fr) 2003-06-25
EP1321661A3 EP1321661A3 (fr) 2005-07-13
EP1321661B1 true EP1321661B1 (fr) 2009-09-16

Family

ID=7710830

Family Applications (1)

Application Number Title Priority Date Filing Date
EP02017114A Expired - Lifetime EP1321661B1 (fr) 2001-12-22 2002-07-30 Soupape d'injection de combustible pour moteurs à combustion interne

Country Status (4)

Country Link
US (1) US6789783B2 (fr)
EP (1) EP1321661B1 (fr)
JP (1) JP2003201938A (fr)
DE (2) DE10163908A1 (fr)

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DE10359302A1 (de) * 2003-12-17 2005-07-21 Robert Bosch Gmbh Ventilkörper mit Mehrfachkegelgeometrie am Ventilstitz
JP4197506B2 (ja) * 2004-08-31 2008-12-17 株式会社パイオラックス カットバルブ
US7578450B2 (en) * 2005-08-25 2009-08-25 Caterpillar Inc. Fuel injector with grooved check member
US7360722B2 (en) * 2005-08-25 2008-04-22 Caterpillar Inc. Fuel injector with grooved check member
US20070200011A1 (en) 2006-02-28 2007-08-30 Caterpillar Inc. Fuel injector having nozzle member with annular groove
DE202006007883U1 (de) * 2006-05-17 2006-10-19 Robert Bosch Gmbh Kraftstoffinjektor mit doppelter Nadelführung
US8006715B2 (en) 2007-09-20 2011-08-30 Caterpillar Inc. Valve with thin-film coating
DE102008039920A1 (de) * 2008-08-27 2010-03-04 Continental Automotive Gmbh Düsenkörper, Düsenbaugruppe und Kraftstoffinjektor, sowie Verfahren zum Herstellen eines Düsenkörpers
JP2012007529A (ja) * 2010-06-24 2012-01-12 Toyota Motor Corp 燃料噴射弁
DE102013107390B4 (de) * 2013-07-12 2023-06-07 Svm Schultz Verwaltungs-Gmbh & Co. Kg Druckregelventil mit Regelelement
US9126223B2 (en) 2013-10-31 2015-09-08 Nordson Corporation Dispensing module and method for dispensing an adhesive
US9108214B2 (en) 2013-10-31 2015-08-18 Nordson Corporation Dispensing module having a sealing zone and method for dispensing an adhesive
CN105298706B (zh) * 2014-07-09 2017-09-29 江苏大学 燃油喷射装置的针阀组件
JP6355765B2 (ja) * 2015-01-30 2018-07-11 日立オートモティブシステムズ株式会社 燃料噴射弁
EP3156641A1 (fr) * 2015-10-14 2017-04-19 Continental Automotive GmbH Injecteur pour injection de fluides
DE102016203028A1 (de) * 2016-02-26 2017-08-31 Bayerische Motoren Werke Aktiengesellschaft Kraftstoffinjektor
DE102016215637A1 (de) * 2016-08-19 2018-02-22 Robert Bosch Gmbh Kraftstoffeinspritzdüse
KR102155850B1 (ko) * 2017-01-31 2020-09-15 가부시키가이샤 후지킨 분류 밸브
CN108286626A (zh) * 2018-03-07 2018-07-17 烟台杰瑞石油装备技术有限公司 一种带有环形槽的阀座密封结构
CN113883758A (zh) * 2021-09-19 2022-01-04 青岛海尔空调器有限总公司 单向阀、换热器、制冷循环系统、空调器

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Also Published As

Publication number Publication date
DE50213847D1 (de) 2009-10-29
US20030132413A1 (en) 2003-07-17
JP2003201938A (ja) 2003-07-18
EP1321661A2 (fr) 2003-06-25
DE10163908A1 (de) 2003-07-03
EP1321661A3 (fr) 2005-07-13
US6789783B2 (en) 2004-09-14

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