EP0730090A2 - Kraftstoffeinspritzventil für Brennkraftmaschinen - Google Patents

Kraftstoffeinspritzventil für Brennkraftmaschinen Download PDF

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Publication number
EP0730090A2
EP0730090A2 EP95115298A EP95115298A EP0730090A2 EP 0730090 A2 EP0730090 A2 EP 0730090A2 EP 95115298 A EP95115298 A EP 95115298A EP 95115298 A EP95115298 A EP 95115298A EP 0730090 A2 EP0730090 A2 EP 0730090A2
Authority
EP
European Patent Office
Prior art keywords
valve
wall
injection
injection channel
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.)
Ceased
Application number
EP95115298A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0730090A3 (ja
Inventor
Erguen Dipl.-Ing. Filiz (Fh)
Friedrich Dipl.-Ing. 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 EP0730090A2 publication Critical patent/EP0730090A2/de
Publication of EP0730090A3 publication Critical patent/EP0730090A3/de
Ceased 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
    • F02M61/1806—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
    • F02M61/1846—Dimensional characteristics of discharge orifices

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a piston-shaped valve member is axially displaceably guided in a bore in a valve body, which on the combustion chamber side merges into a blind hole via a conical region.
  • the valve member has at its lower end facing the combustion chamber of the internal combustion engine to be supplied a conical sealing surface with which it interacts with a conical valve seat on the conical region of the bore.
  • at least one injection channel leads away from the blind hole or from the conical region of the bore in the valve body downstream of the valve seat.
  • a pressure chamber is provided between the stem of the valve member and the wall of the bore, said pressure chamber being adjacent to the valve seat surface via a pressure channel formed by an annular gap between the valve member and the bore.
  • the valve member also has, in a known manner, a pressure shoulder in the region of the pressure chamber, to which the high-pressure fuel flowing into the pressure chamber acts and thus lifts the valve member from its valve seat against the force of a return spring.
  • the inner end of the injection channel on the known injection valve is funnel-shaped by rounding the transition between the blind hole or conical region to the injection channel with a defined radius, the radius of which extends through the longitudinal axis of the injection channel in this way is that it merges tangentially into an injection jet constriction within the injection channel.
  • An edge remains between the rounded part and the cylindrical part of the injection channel, as well as between the rounded part and the wall of the blind hole or the conical area. This further promotes jet constriction, reduces the flow rate through the injection channel, and disadvantageously reduces the compactness of the emerging fuel jet.
  • the shape of the known injection opening has the disadvantage that it is not suitable for shaping an injection jet which extends far enough into the combustion chamber in order to safely reach distant combustion chamber areas.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage that eddies can be avoided by the edgeless rounding of the inlet areas of the injection channel, so that a uniform injection jet can be formed.
  • the strong rounding of the inlet areas in connection with the maintenance of a small spray hole diameter means that the strong jet impulse of the fuel to be injected from the fuel injection pump is not caused by a sharp deflection or swirling of the jet on sharp edges impaired, so that compared to the known solution, a longer, concentrated injection jet is generated, which allows a much deeper penetration into the combustion chamber of the internal combustion engine to be supplied. In this way, combustion chamber areas that are structurally far away from the injection point can also be safely reached with fuel, which considerably improves the quality of the combustion process.
  • the flow rate can be increased with the same spray hole cross section and the flow of the fuel flowing through can be shaped more uniformly, which also has a positive effect on the injection jet, since losses due to turbulence can be avoided.
  • the notch effect is reduced by the strong rounding of the spray hole inlet edges, which leads to an increase in the high pressure resistance in the top, blind hole and spray hole area to over 2000 bar.
  • Rounding can e.g. mechanically, hydraulically or electrochemically, this machining additionally leads to an increase in the crest strength, since this removes the edge oxidation in the hard part.
  • a particularly favorable course of the injection jet is achieved if the radius of the curve in the upper inlet area is 0.75 to 1.5 times and the radius of the curve in the lower inlet area is 0.2 to 1.0 times the spray hole diameter.
  • a further improvement in the injection jet shaping described above is achieved if the wall thickness of the valve body, which determines the length of the injection channel, is between 0.6 and 1.4 mm in the region of the injection channel.
  • the measure described for advantageously shaping the longest possible injection jet is possible both on injection valves of the blind-hole type and on injectors of the seat-hole type, the axis of the injection channel in blind-hole nozzles preferably in Direction valve member is tilted from a perpendicular to the wall of the blind hole.
  • FIG. 1 shows a section through the injection valve
  • FIG. 2 shows a first exemplary embodiment in an enlarged detail from FIG. 1, in which the injection valve is designed as a blind hole nozzle
  • FIG. 3 shows a second exemplary embodiment analogous to the illustration in FIG. 2, in which the injection valve is designed as a seat hole nozzle.
  • the fuel injection valve for internal combustion engines shown in FIG. 1 with its components essential to the invention has a cylindrical valve body 1, which projects with its diameter-reduced end into the combustion chamber of an internal combustion engine, not shown.
  • An axial bore 3 is arranged in the valve body 1 and merges into a blind hole 21 in the valve body 1 via a conical region on the combustion chamber side.
  • a piston-shaped valve member 5 is guided axially displaceably in this bore 3 and has a conical sealing surface 7 at its lower end on the combustion chamber side, with which it cooperates with a conical valve seat surface 9 of the valve body 1 formed on part of the conical region.
  • the Valve member 5 has on its shaft a cross-sectional widening forming a pressure shoulder 11, which is followed in the direction facing away from valve sealing surface 7 by an enlarged valve member part, which is sealingly guided on the wall of bore 3.
  • the smaller in diameter part of the valve member shaft extends from the pressure shoulder 11 to the sealing surface 7, an annular gap forming a pressure channel 13 remaining between the wall of the bore 3 and the valve member 5.
  • This pressure channel 13 extends from a pressure space 15 formed by a cross-sectional expansion of the bore 3 in the area of the pressure shoulder 11 to the valve seat 9, a pressure line 17 which can be connected to a high-pressure fuel pump (not shown) opening into the pressure space 15.
  • a return spring 19 is also provided, which acts on the end of the valve member 5 facing away from the combustion chamber and thus keeps the valve sealing surface 7 pressed against the valve seat surface 9.
  • the fuel injection valve is designed as a so-called blind hole nozzle.
  • the closed end of the bore 3 forms the blind hole 21, which adjoins the valve seat surface 9 on the combustion chamber side and whose end on the combustion chamber side is preferably dome-shaped.
  • the wall thickness of the valve body 1, which essentially determines the axial extent of the injection channel 23, in the region of the injection channel 23 is between 0.6 mm and 1.4 mm.
  • the inlet areas of the injection channel 23 leading away from the inner wall of the blind hole 21 are rounded off, the radius RA of the rounding of the inlet area near the valve seat being larger than the radius RB of the rounding of the inlet area facing away from the valve seat 9 .
  • the upper radius RA is 0.75 to 1.5 times and the lower radius RB 0.2 to 1.0 times the diameter D of the injection channel 23. This, both the inner wall of the blind hole 21 and the walls Radii tangent to the injection channel 23 enable the fuel under high pressure to flow optimally into the injection channel 23 while avoiding turbulence that affects jet formation.
  • the fuel injection valve according to the invention works in the following way.
  • the return spring 19 holds the valve member 5, against the standing pressure of the fuel-filled pressure chamber 15, with its sealing surface 7 in contact with the valve seat 9.
  • the pressure chamber 15 For injection at the injection valve, its pressure chamber 15 is pressurized with high fuel pressure via the pressure line 17, the pressure force now acting on the pressure shoulder 11 exceeding the force of the return spring 19 and lifting the valve member 5 from the valve seat 9.
  • the fuel under high pressure passes through the pressure chamber 15 and the pressure channel 13 to the valve seat 9 and, when the valve member 5 is lifted off, flows along this into the blind hole 21.
  • the fuel flows via the rounded inlets into the injection channel 23 and thus passes for injection into the combustion chamber of the internal combustion engine to be supplied.
  • the inlet areas provided with a radius RA, RB in the injection channel 23 produce a uniform and directed injection jet. Since the largest part of the injection quantity, or the part having the greatest flow velocity, flows over the upper curve close to the valve seat 9, its radius RA is larger than the lower radius RB.
  • valve member 5 is moved back from the return spring 19 to the valve seat 9 in a known manner with the pressure chamber 15 relieved of high pressure.
  • the second exemplary embodiment shown in FIG. 3 differs from the first exemplary embodiment only in the type of the injection valve, which is designed there as a so-called hole nozzle.
  • the closed end (blind hole 21) of the bore 3 on the combustion chamber side is of hollow-conical design, the conical flanks forming the valve seat surface 9, against which the valve member 5 with its conical sealing surface 7 comes into sealing contact.
  • the injection channel 23 leads away from the valve seat surface 9, so that it is covered by the sealing surface 7 of the valve member 5 in the closed state of the injection valve and is therefore closed.
  • the injection channel 23 is arranged perpendicular to the valve seat surface 9 forming part of the blind hole 21 and, analogously to the first exemplary embodiment shown in FIG.
  • the wall thickness of the valve body 1 in the region of the injection channel 23 is between 0.6 mm and 1.4 mm, analogous to the first.
  • the injection channel 23 of the fuel injection valve according to the invention it is thus possible, compared to known injection valves, to generate a directed injection jet which is not or only slightly swirled when it enters the injection channel, the rounded inlet areas not reducing the effective spray hole length.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
EP95115298A 1995-03-02 1995-09-28 Kraftstoffeinspritzventil für Brennkraftmaschinen Ceased EP0730090A2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE19507171 1995-03-02
DE19507171A DE19507171C1 (de) 1995-03-02 1995-03-02 Kraftstoffeinspritzventil für Brennkraftmaschinen

Publications (2)

Publication Number Publication Date
EP0730090A2 true EP0730090A2 (de) 1996-09-04
EP0730090A3 EP0730090A3 (ja) 1996-10-16

Family

ID=7755373

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95115298A Ceased EP0730090A2 (de) 1995-03-02 1995-09-28 Kraftstoffeinspritzventil für Brennkraftmaschinen

Country Status (4)

Country Link
US (1) US5875973A (ja)
EP (1) EP0730090A2 (ja)
JP (1) JPH08247001A (ja)
DE (1) DE19507171C1 (ja)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10050704A1 (de) * 2000-10-13 2003-02-20 Siemens Ag Einspritzventil für die Einspritzung von Kraftstoff in eine Verbrennungskraftmaschine

Families Citing this family (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19814858A1 (de) * 1998-04-02 1999-10-14 Siemens Ag Kraftstoffeinspritzdüse mit optimierter Spritzlochkanalgeometrie sowie Verfahren zur Herstellung einer solchen Spritzlochkanalgeometrie
DE19841158A1 (de) * 1998-09-09 2000-03-16 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE19843895B4 (de) * 1998-09-24 2005-08-11 Siemens Ag Kraftstoffeinspritzdüse mit optimierter Spritzlochkanalgeometrie
JP4055315B2 (ja) * 1999-03-17 2008-03-05 株式会社日立製作所 燃料噴射弁およびこれを搭載した内燃機関
DE19914719C2 (de) * 1999-03-31 2001-05-03 Siemens Ag Vorrichtung zum hydroerosiven Runden von Einlaufkanten der Spritzlochkanäle in einem Düsenkörper
DE19931890A1 (de) * 1999-07-08 2001-01-18 Siemens Ag Düsenkörper für eine Kraftstoffeinspritzdüse mit optimierter Spritzlochkanalgeometrie
DE10163908A1 (de) * 2001-12-22 2003-07-03 Bosch Gmbh Robert Kraftstoffeinspritzventil für Brennkraftmaschinen
DE10330256A1 (de) † 2003-07-04 2005-01-20 Robert Bosch Gmbh Kraftstoffeinspritzventil für Brennkraftmaschinen
JP2008068360A (ja) * 2006-09-14 2008-03-27 Mitsubishi Heavy Ind Ltd ノズルボディの噴孔加工方法、噴孔加工装置、及びそれらを用いて作製された燃料噴射ノズル
DE102006062008A1 (de) * 2006-12-29 2008-07-03 Robert Bosch Gmbh Vorrichtung für Hochdruckanwendungen
GB0712403D0 (en) * 2007-06-26 2007-08-01 Delphi Tech Inc A Spray Hole Profile
DE102009002480A1 (de) * 2009-04-20 2010-10-21 Robert Bosch Gmbh Kraftstoffeinspritzvorrichtung
JP5959892B2 (ja) 2012-03-26 2016-08-02 日立オートモティブシステムズ株式会社 火花点火式燃料噴射弁

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DE1212352B (de) * 1960-02-20 1966-03-10 Orange G M B H L Brennstoff-Einspritzventil mit brennstoff-gesteuerter Ventilnadel
DE2557772A1 (de) * 1975-12-20 1977-06-23 Kloeckner Humboldt Deutz Ag Brennstoffeinspritzventil
DE2610927C2 (de) * 1976-03-16 1983-01-27 Institut für Motorenbau Prof. Huber e.V., 8000 München Einspritzdüse zur Kraftstoffeinspritzung in den Brennraum einer Brennkraftmaschine
CH612733A5 (en) * 1976-05-26 1979-08-15 Sulzer Ag Nozzle of a fuel injection valve of a piston internal combustion engine
US4275844A (en) * 1979-11-30 1981-06-30 Caterpillar Tractor Co. Fuel injection nozzle
DE3234829A1 (de) * 1982-09-21 1984-03-22 Deutsche Forschungs- und Versuchsanstalt für Luft- und Raumfahrt e.V., 5000 Köln Einspritzvorrichtung fuer einen dieselmotor
US4578164A (en) * 1983-08-24 1986-03-25 Nissan Motor Co., Ltd. Method of electrolytically finishing spray-hole of fuel injection nozzle
EP0219591B1 (de) * 1985-10-22 1988-12-28 VOEST-ALPINE AUTOMOTIVE Gesellschaft m.b.H. Verfahren zum Herstellen eines Einspritzdüsenkörpers
JPS63302173A (ja) * 1987-05-30 1988-12-09 Niigata Eng Co Ltd 内燃機関の燃料弁ノズル
GB8817774D0 (en) * 1988-07-26 1988-09-01 Lucas Ind Plc Fuel injectors for i c engines
DE68905502T2 (de) * 1988-02-05 1993-09-23 Lucas Ind Plc Brennstoffeinspritzventil.
GB8827107D0 (en) * 1988-11-19 1988-12-21 Lucas Ind Plc Fuel injection nozzle
US5026462A (en) * 1990-03-06 1991-06-25 Ail Corporation Method and apparatus for electrochemical machining of spray holes in fuel injection nozzles
JPH05231267A (ja) * 1992-02-19 1993-09-07 Isuzu Motors Ltd 燃料噴射ノズル及びその製造方法
JPH05231272A (ja) * 1992-02-19 1993-09-07 Isuzu Motors Ltd 燃料噴射ノズル及びその製造方法
JP3114334B2 (ja) * 1992-02-19 2000-12-04 いすゞ自動車株式会社 燃料噴射ノズル及びその製造方法
JPH05240129A (ja) * 1992-02-26 1993-09-17 Isuzu Motors Ltd 燃料噴射ノズル
US5467924A (en) * 1994-09-20 1995-11-21 Alfred J. Buescher Unit injector optimized for reduced exhaust emissions

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Title
None

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10050704A1 (de) * 2000-10-13 2003-02-20 Siemens Ag Einspritzventil für die Einspritzung von Kraftstoff in eine Verbrennungskraftmaschine

Also Published As

Publication number Publication date
US5875973A (en) 1999-03-02
DE19507171C1 (de) 1996-08-14
EP0730090A3 (ja) 1996-10-16
JPH08247001A (ja) 1996-09-24

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