EP1563181A1 - Soupape d'injection de carburant pour moteurs combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs combustion interne

Info

Publication number
EP1563181A1
EP1563181A1 EP03795728A EP03795728A EP1563181A1 EP 1563181 A1 EP1563181 A1 EP 1563181A1 EP 03795728 A EP03795728 A EP 03795728A EP 03795728 A EP03795728 A EP 03795728A EP 1563181 A1 EP1563181 A1 EP 1563181A1
Authority
EP
European Patent Office
Prior art keywords
valve
sealing
fuel injection
conical surface
valve seat
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.)
Granted
Application number
EP03795728A
Other languages
German (de)
English (en)
Other versions
EP1563181B1 (fr
Inventor
Thomas Kuegler
Hasiman ÜSKÜDAR
Jochen Mertens
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
Priority claimed from DE10315820A external-priority patent/DE10315820A1/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP1563181A1 publication Critical patent/EP1563181A1/fr
Application granted granted Critical
Publication of EP1563181B1 publication Critical patent/EP1563181B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • 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
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as is known, for example, from the published patent application DE 100 58 153 AI. Such one
  • L5 fuel injection valve has a valve body in which a bore is formed which is delimited by a valve seat at its end on the combustion chamber side.
  • a piston-shaped hollow valve needle is arranged in the bore, the valve needle on its combustion chamber side, ie the valve seat
  • .0 End has a valve sealing surface with which it with the
  • Valve seat interacts. As a result, at least one injection opening is opened and closed, which starts from the valve seat and which opens into the combustion chamber of the internal combustion engine in the installed position of the fuel injection valve.
  • the fuel is usually kept in a pressure chamber which is formed between the valve needle and the wall of the bore.
  • a high pressure prevails in the pressure chamber, at least during the injection process, so that good atomization of the fuel is achieved, which is essential for an effective and low-pollution combustion process.
  • the injection openings must be sealed between the injections so that no fuel can get into the combustion chamber in an uncontrolled manner, which leads to increased pollutant emissions.
  • so-called back blowing in which from the Combustion chamber Combustion gases enter the injection valve through the injection openings and change the state there so that the subsequent injection process cannot run optimally. Too little fuel is then injected, for example, which is noticeable in a drop in performance.
  • the injection timing can be shifted, which results in uneven running and increased pollutant emissions from the internal combustion engine.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over the fact that the injection openings in the
  • the hollow valve needle has two sealing areas on its valve sealing surface, the first sealing area upstream and the second sealing area downstream of the at least one injection opening, a seal between the valve sealing surface and the valve
  • the first sealing area is designed as a conical surface. This results in a flat support on the valve seat, which reduces the surface pressure there and thus the mechanical stress.
  • the second sealing area can also be designed in this form. If the seal is also to withstand high pressures, the sealing areas can be formed by edges.
  • the first sealing area is formed at the transition from a first conical surface to a second conical surface, the conical surfaces forming part of the valve sealing surface.
  • the second sealing region can also be formed by an edge, preferably in that a third conical surface is provided on the valve sealing surface, and an annular groove is formed between the second and the conical surface.
  • Form L5 which are inclined so that this creates an annular groove-like recess that covers the injection openings.
  • Such a design is easier to manufacture than a rounded ring groove, since one and the same tool can be used for all cone surfaces.
  • the second sealing area which is arranged downstream of the first sealing area, touches the valve seat before the first sealing area during the closing movement of the valve needle.
  • the downstream end of the hollow valve needle on the combustion chamber side has to deform elastically somewhat inward after the second sealing area has been placed on the valve sealing surface, which then enables the first sealing area to be placed on.
  • a groove can be provided downstream of the first sealing area on the valve hollow needle, through which a resilient sealing lip is formed.
  • the second sealing area which is in front of the first, is formed on the sealing lip Sealing area touches the valve seat.
  • the sealing lip is slightly elastically deformable, which on the one hand ensures a good seal and on the other hand does not lead to excessive deformation or tension of the hollow valve needle. 5
  • FIG. 1 shows a longitudinal section through a fuel injection valve according to the invention
  • FIG. 2 shows an enlargement of the section of FIG. 1, designated II,.
  • FIG. 3 shows an enlargement of the section of FIG. 2, designated III,
  • a fuel injector is shown in longitudinal section.
  • a bore 3 is formed in a valve body 1 and is delimited at its combustion chamber end by a conical valve seat 18. Go from valve seat 18
  • injection openings 20 and all inner injection openings 22 with respect to the longitudinal axis 7 of the bore 3 at the same height are arranged so that two rows of injection openings are formed.
  • the injection openings 20, 22 open into the combustion chamber of the internal combustion engine in the installed position of the fuel injection valve. 5
  • a hollow valve needle 8 is arranged to be longitudinally displaceable and is sealingly guided in a guide section of the bore 3 facing away from the combustion chamber. Starting from the guided section, the hollow valve needle 8 tapers
  • a pressure chamber 14 is formed, which is radially expanded in an area adjacent to the guide section.
  • An inlet channel 16 running in the valve body 1 opens into the radial expansion of the pressure chamber 14, via which the pressure chamber 14 is subjected to force.
  • '0 substance can be filled under high pressure.
  • the hollow valve needle 18 has a longitudinal bore 11 which is concentric with the longitudinal axis of the hollow valve needle 18 and extends over its entire length.
  • a valve needle 10 is arranged to be longitudinally displaceable and has a valve sealing surface 42 at its combustion chamber end, with which the valve needle 10 cooperates with the valve seat 18 for controlling the inner injection openings 22.
  • the valve needle 10 is in the longitudinal bore
  • FIG. 2 shows an enlargement of the section of FIG. 1 labeled II.
  • the hollow valve needle 8 interacts with the valve seat 18 in such a way that when the hollow valve needle 5 8 rests on the valve seat 18, the outer injection openings 20 are closed.
  • the valve needle 10 closes the inner injection openings 22 when it rests on the valve seat 18.
  • valve needle 10 initially remains in its closed position, in which the inner injection openings 22 are closed. Since only part of the injection openings 20, 22 has been opened up to now, the fuel is supplied with a
  • valve needle 10 After lifting the hollow valve needle 8 from the valve seat 18, the valve needle 10 is acted upon by the fuel pressure, so that there is also a hydraulic opening force on the valve needle 10, which the
  • valve needle 10 injection increased until the increasing fuel pressure by the hydraulic forces on the valve hollow needle 8 outweigh the closing force.
  • the valve needle 10 remains closed by a correspondingly large closing force and the valve hollow needle 8
  • L5 slides back to its closed position after opening.
  • Such an injection is required, for example, for a pre-injection or pilot injection that is separate from the main injection.
  • valve sealing surface 35 shows an enlarged section of valve hollow needle 8 in the area of valve sealing surface 35, this section being designated III in FIG. 2.
  • the valve sealing surface 35 has a first conical surface 30, a second conical surface 31 and a third conical surface 32
  • the first conical surface 30 borders directly on the second conical surface 31, so that an edge 34 is formed at the transition.
  • the opening angle a ⁇ of the first conical surface 30 is smaller than
  • the opening angle a2 of the second cone surface 31 is equal to that of the second cone surface 31, and both cone surfaces 31, 32 lie on a common imaginary cone surface. Between the second cone surface 31 and the third cone surface 32, an annular groove 37 is formed, the upstream edge 45 and the downstream edge 46 when the valve sealing surface is in contact 35 lie on the valve seat 18 upstream or downstream of the outer injection openings 20.
  • the valve seat 18 is also conical and has an opening angle b which is equal to the opening angle a2 of the second cone surface 31 and the opening angle a3 of the third cone surface 32.
  • outer injection ports 20 only a small volume of fuel that can get into the combustion chamber when the fuel injector is closed.
  • Figure 4 shows the same view as Figure 3 of another
  • the second conical surface 31 has an opening angle a2 that is larger than the opening angle b of the conical valve seat 18.
  • the edge 34 which is arranged at the transition from the first conical surface 30 to the second conical surface 31, is a sealing edge
  • the third conical surface 32 is unchanged from the exemplary embodiment shown in FIG. 3.
  • the edge 34 and the third conical surface 32, that is to say the two sealing regions, are arranged in relation to the valve seat 18 in such a way that when new
  • the edge 34 abuts first on the valve seat 18, while the third conical surface 32 is still spaced from the valve seat 18, but only by a very thin gap, which results in an adequate but not complete seal. In operation, the edge 34 pounds
  • Sealing areas are aligned in such a way that the hollow valve needle 8 first touches the valve seat 18 with the second sealing area, ie the third conical surface 32.
  • the valve hollow needle 8 By interacting with the valve seat 18, the valve hollow needle
  • L0 is deformed somewhat elastically inward in the region of the third conical surface 32 to such an extent that the edge 34 is seated on the valve seat 18. This likewise results in a corresponding seal upstream and downstream of the outer injection openings 20.
  • FIG. 5 Another exemplary embodiment in the same representation as FIG. 3 shows FIG. 5.
  • both the opening angle a2 of the second cone surface 31 and the opening angle a3 of the third cone surface 32 are larger than the opening angle b
  • the downstream edge 46 of the annular groove 37 here forms the second sealing area, which is formed relative to the first sealing area, that is to say the edge 34, such that either the first or the second sealing area lies first on the valve seat 18. He comes
  • first sealing area i.e. the edge 34
  • the complete sealing at the second sealing area takes place only in operation, in which the edge 34 bends somewhat into the valve seat 18 until the downstream edge 46 of the annular groove 37 on the valve seat 18 rests.
  • FIG. 6 shows a further exemplary embodiment in the same representation as FIG. 5.
  • the opening angle a1 of the first conical surface 30 is smaller than the opening angle b of the conical valve seat 18, so that an upstream edge 45 is formed at the transition from the first 5 conical surface 30 to the annular groove 37 , which forms the first sealing area.
  • the downstream edge 46 of the annular groove 37 is designed as a second sealing region, which is followed by a convex end section 39.
  • L0 ger edge 45 and downstream edge 46 of the annular groove 37 is analogous to the exemplary embodiment in FIG. 5. It can therefore be provided that the upstream edge 45 rests against the valve seat 18 in front of the downstream edge 46 and vice versa.
  • valve needle 8 has an upper cone instead of an annular groove.
  • the first sealing area is designed in the form of an upstream edge 45 and, accordingly, at the transition from the lower cone surface 31b to the third cone surface 32
  • Sealing at both sealing areas by elastic deformation of the hollow valve needle 8 is also the principle in the embodiment shown in FIG. 8, in which the dental parts of the hollow valve needle are designated with the same reference numbers as in FIGS. 3, 4 and 5.
  • a groove 50 is provided here, through which a sealing lip 52 is formed.
  • a sealing edge 48 is provided on the sealing lip 52 and forms the second sealing area. Due to the 5 groove, the sealing lip 52 is made relatively thin, so that there is good elastic deformability.
  • the sealing principle is given by the fact that when the valve hollow needle 8 closes, the sealing edge 48 on the conical valve seat 18 first

Landscapes

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

Abstract

Soupape d'injection de carburant pour moteurs à combustion interne, qui comporte un corps (1) de soupape dans lequel est formé un trou (3) délimité au niveau de son extrémité se trouvant du côté de la chambre de combustion par un siège (18) de soupape conique à partir duquel est ménagé un orifice d'injection. Une aiguille (8) creuse de soupape est placée de manière à se déplacer longitudinalement dans le trou (3), ladite aiguille comportant une surface d'étanchéité (35) sur son extrémité orientée vers le siège (18) de soupape. La surface d'étanchéité (35) de la soupape comporte une première zone d'étanchéité (31; 34) et une seconde zone d'étanchéité (32; 46; 48), et lors de l'appui de l'aiguille (8) creuse de soupape sur le siège (18) de soupape, la première zone d'étanchéité (31; 34) produit une étanchéité en amont de l'orifice d'injection (20) et la seconde zone d'étanchéité (32; 46; 48) produit une étanchéité en aval dudit orifice (20).
EP03795728A 2002-11-11 2003-10-27 Soupape d'injection de carburant pour moteurs combustion interne Expired - Lifetime EP1563181B1 (fr)

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE10252660 2002-11-11
DE10252660 2002-11-11
DE10315820A DE10315820A1 (de) 2002-11-11 2003-04-07 Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10315820 2003-04-07
PCT/DE2003/003561 WO2004044414A1 (fr) 2002-11-11 2003-10-27 Soupape d'injection de carburant pour moteurs à combustion interne

Publications (2)

Publication Number Publication Date
EP1563181A1 true EP1563181A1 (fr) 2005-08-17
EP1563181B1 EP1563181B1 (fr) 2006-10-04

Family

ID=32313556

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03795728A Expired - Lifetime EP1563181B1 (fr) 2002-11-11 2003-10-27 Soupape d'injection de carburant pour moteurs combustion interne

Country Status (5)

Country Link
US (1) US7331537B2 (fr)
EP (1) EP1563181B1 (fr)
JP (1) JP2006505745A (fr)
DE (1) DE50305296D1 (fr)
WO (1) WO2004044414A1 (fr)

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Publication number Priority date Publication date Assignee Title
DE10245573A1 (de) * 2002-09-27 2004-04-08 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
ATE474071T1 (de) * 2003-08-11 2010-07-15 Honeywell Int Inc Target/trägerplatte-konstruktionen und herstellungsverfahren dafür
DE102005025135A1 (de) * 2005-06-01 2006-12-07 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
DE602005005981T2 (de) 2005-07-13 2009-05-20 Delphi Technologies, Inc., Troy Einspritzdüse
JP5044556B2 (ja) * 2005-08-25 2012-10-10 キャタピラー インコーポレイテッド 溝付逆止部材を備えた燃料噴射器
DE102005042200A1 (de) * 2005-09-06 2007-03-08 Robert Bosch Gmbh Kraftstoffinjektoren oder Einspritzdüsen für selbstzündende Verbrennungskraftmaschinen
DE102006052817A1 (de) * 2006-11-09 2008-05-15 Robert Bosch Gmbh Brennstoffeinspritzventil
DE102007062701A1 (de) * 2007-12-27 2009-07-02 Robert Bosch Gmbh Kraftstoffeinspritzdüse
JP2010053796A (ja) * 2008-08-29 2010-03-11 Hitachi Ltd 燃料噴射弁
DE102009042155A1 (de) * 2009-09-21 2011-04-07 Continental Automotive Gmbh Kraftstoff-Einspritzventil für eine Brennkraftmaschine
US20140175192A1 (en) * 2012-12-21 2014-06-26 Quantlogic Corporation Mixed-mode fuel injector with a variable orifice
US20170175693A1 (en) * 2014-03-28 2017-06-22 Quantlogic Corporation A fuel injector flexible for single and dual fuel injection
CN103994004A (zh) * 2014-05-16 2014-08-20 江苏大学 可移动压力室式喷油嘴
JP6354519B2 (ja) * 2014-10-23 2018-07-11 株式会社デンソー 燃料噴射弁
US11815055B1 (en) * 2022-12-01 2023-11-14 Caterpillar Inc. Multi-fuel injector and method

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Also Published As

Publication number Publication date
US7331537B2 (en) 2008-02-19
JP2006505745A (ja) 2006-02-16
US20060011749A1 (en) 2006-01-19
WO2004044414A1 (fr) 2004-05-27
EP1563181B1 (fr) 2006-10-04
DE50305296D1 (de) 2006-11-16

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