EP1344931A2 - Einspritzdüse - Google Patents

Einspritzdüse Download PDF

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Publication number
EP1344931A2
EP1344931A2 EP03251544A EP03251544A EP1344931A2 EP 1344931 A2 EP1344931 A2 EP 1344931A2 EP 03251544 A EP03251544 A EP 03251544A EP 03251544 A EP03251544 A EP 03251544A EP 1344931 A2 EP1344931 A2 EP 1344931A2
Authority
EP
European Patent Office
Prior art keywords
seating
injection nozzle
valve member
valve
valve needle
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
EP03251544A
Other languages
English (en)
French (fr)
Other versions
EP1344931A3 (de
EP1344931B1 (de
Inventor
Malcolm D. Lambert
Paul K. Hewitt
Steve R. Smith
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.)
Delphi Technologies Inc
Original Assignee
Delphi Technologies Inc
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 Delphi Technologies Inc filed Critical Delphi Technologies Inc
Publication of EP1344931A2 publication Critical patent/EP1344931A2/de
Publication of EP1344931A3 publication Critical patent/EP1344931A3/de
Application granted granted Critical
Publication of EP1344931B1 publication Critical patent/EP1344931B1/de
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
    • F02M61/1893—Details of valve member ends not covered by groups F02M61/1866 - F02M61/188

Definitions

  • the present invention relates to an injection nozzle for use in controlling fluid flow through an outlet and particularly, but not exclusively, to an injection nozzle for use in a fuel injector for delivering fuel to an internal combustion engine.
  • Such injection nozzles generally comprise a valve member which is slidable within a blind bore provided in a nozzle body. A region of the valve member proximal to the blind end of the bore is engageable with an annular valve seating, defined by a portion of the bore. The valve member is biased into engagement with the valve seating and is selectively movable away from the valve seating, thereby to control fuel delivery through a set of outlet openings provided in the nozzle body.
  • fuel within a delivery chamber defined by the bore and the outer surface of the valve member is able to flow past the valve seating and out through the outlet openings into an associated engine cylinder or other combustion space.
  • the valve member is provided with a circumferential groove, one edge of the groove forming with the downstream edge of the first conical surface a so-called “seating line" along which, in the closed position of the valve member, the valve member engages with the seating.
  • the other edge of the groove corresponds to the upstream edge of the second conical surface.
  • Injection nozzles of this design provide a number of advantages. Over a period of time, deformation of the seating line will take place so that the seating line effectively becomes a zone or area. However, the presence of the groove prevents the effective seating line moving in the downstream direction so that the pressure which is required to lift the valve member from its seating (known in the art as the "nozzle opening pressure") is substantially unaffected. This enables the differential angle between the second conical surface and the seating to be made as small as possible, in the order of 2.5° or less. The junction of the two conical surfaces would lie on the seat line but because of the provision of the groove, there is no actual junction and the manufacturing difficulties of providing an accurate junction are avoided. In practice, the zone contact which develops means that the effective seating line moves in the upstream direction to provide compensation for spring relaxation.
  • valve member geometry described in US 5,890,660 also provides a much improved spray symmetry and hole-to-hole spray form variation.
  • the first differential angle i.e. the angle between the first conical surface and the valve seating
  • the groove combine to have an hydraulic centralising effect on the valve member. As a result, a more even flow to and within the outlet openings is achieved, resulting in an improved spray symmetry.
  • an injection nozzle for use in delivering fuel to a combustion space, the injection nozzle comprising:
  • the invention provides the advantage that, for relatively small amounts of valve needle lift away from the seating, an asymmetric flow regime is achieved, resulting in some of the sprays through the outlets having a more "bushy” effect than others. Sprays exhibiting a more "bushy” effect reach ignition conditions in the combustion space earlier than narrower sprays with less fuel having been injected by this time. The ignition process is therefore more gradual and less combustion noise is generated. As the valve member lifts further through its range of travel, the effect of the eccentricity has a less significant effect on the symmetry of the flow regime, such that the spray form becomes substantially symmetric. Smoke reduction associated with the improved fuel/air mixing characteristics of the nozzle can therefore be maintained.
  • the eccentricity of the second surface relative to the first surface is in the range 1 to 50 microns and is preferably greater than 5 microns. More preferably, the eccentricity of the second surface relative to the first surface is in the range of 5 to 25 microns, and still more preferably between 5 and 10 microns.
  • the injection nozzle is provided with means for biasing the valve member into engagement with the seating.
  • the seating may be defined by the bore.
  • the valve member in a closed position of the valve member, there is a radial clearance between the second surface and the seating which radial clearance varies around the circumference of the second surface.
  • the difference in the maximum radial clearance between the second surface and the seating and the minimum radial clearance is in the range of 5 to 10 microns.
  • a first edge of the groove defines a lower edge of the first surface and a second edge of the groove defines an upper edge of the second surface.
  • the first edge of the groove or the lower edge of the first surface defines a seating line along which, in a closed position of the valve member, the valve member engages with the seating.
  • the seating is machined to frusto-conical form having a substantially constant cone angle.
  • the first surface may have a cone angle which is less than that of the seating.
  • the second surface may have a cone angle which is greater than that of the seating.
  • the included angle between the first surface and the seating and the included angle between the second surface and the seating are each in the range 0.1 to 5° and, more preferably, are each approximately 0.75°.
  • a known fuel injection nozzle comprises a nozzle body 10 of stepped cylindrical form having a blind bore 11 extending generally axially therein.
  • a valve seating surface 12A in the form of a generally frusto-conical restriction or narrowing, which is shown more clearly in Figure 2, is formed at the blind end of the bore and an enlargement 12, which communicates with a fuel inlet passage 13, is formed intermediate the ends of the bore.
  • the fuel inlet passage 13 extends through an end portion 14 of the nozzle body 10 and through a wall portion of a nozzle holder 15 to a fuel inlet (not shown) which in use is connected to the outlet of a fuel injection pump.
  • the nozzle body 10 is secured to the nozzle holder 15 by means of a cap nut 17 and, in use, a narrower portion of the nozzle body 10 extends through a bore into a combustion space of an associated combustion engine.
  • a valve member in the form of a valve needle 18 is slidably mounted within the bore 11 and, along a portion of its length corresponding substantially to the region of the nozzle body 5 intermediate the enlarged portion 12 and the seating 12A, has a diameter which is less than that of the bore 11 thereby to define an annular space 19 through which fuel from the fuel inlet passage 13 can flow.
  • the valve needle 18 is provided with an extension 20 which extends with clearance through an aperture in the end portion 14 of the nozzle body 10.
  • the free end of the extension 20 is engaged by a spring abutment 21 located at one end of a coiled compression spring 22, the other end of which bears against an abutment 23 of the nozzle holder 15.
  • the spring 22 acts to maintain the valve needle 18 in the closed position and the chamber in which the spring is located is connected to a drain (not shown) through a passage 16.
  • the seating 12A is of frusto-conical form and at its narrower end opens into a small recess or sac region 24, the purpose of which is to permit accurate grinding of the valve seating surface 12A.
  • Two outlet openings 25 are disposed in the nozzle body 10 to allow fuel in and adjacent to the sac region 24 to flow out of the bore and into a combustion chamber of an associated engine. It will be appreciated however, that the number and position of the outlet openings 25 may be varied in dependence on the application for which the fuel injection nozzle is intended.
  • the lower end of the valve needle 18, adjacent or proximal to the blind end of the bore 11, includes a first, upper annular surface or region 27 of substantially frusto-conical form and a second, lower annular surface or region 29 of generally conical form.
  • the second region 29 defines the end or tip of the needle valve 18 and thus occupies a lower axial position along the axis of the valve member than the first region 27, the second region 29 therefore being disposed downstream of the first region 27.
  • the first region 27 has an outer surface defining a seating surface which is engageable with the valve seating surface 12A.
  • the included angle between the valve seating surface 12A defined by the bore 11 and the seating surface defined by the first region 27 of the valve needle 18 (hereafter referred to as the first differential angle) is approximately 0.75° such that the cone angle of the seating surface is slightly less than that of the valve seating surface 12A.
  • the differential angle is around 0.75° although satisfactory results may be obtained by the use of a differential angle of between approximately 0.1 and 5°
  • the included angle between the valve seating surface 12A defined by the bore and the surface of the second region 29 of the valve needle 18 (hereafter referred to as the second differential angle) is also 0.75° such that the cone angle of the latter is slightly greater than that of the valve seating surface.
  • the needle valve 18 is provided with a circumferential groove 26 intermediate the first region 27 and the second region 29.
  • An first, upper (or upstream) edge of the groove 26, is defined by a lower (or downstream) edge of the first region 27 while a second, lower (or downstream) edge of the groove 26 is defined by an upper (or upstream) edge of the second region 29.
  • the upstream edge of the groove 26 forms with the first region 27 a so-called “seating line” 28 and, in use, in the closed position of the valve needle 18, the latter engages with the valve seating surface 12A along the seating line 28.
  • FIG 3 this illustrates part of a preferred form of injection nozzle according to the invention in a view comparable to that of Figure 2.
  • the geometry of the valve needle 18 of Figure 3 is substantially identical to that of Figure 2.
  • the valve needle 18 includes first and second regions 27, 29 and an intermediate groove 26.
  • the first and second differential angles are in the range of 0.1 to 5°, and are preferably both 0.75°.
  • the second region 29 of the needle valve 18 is disposed eccentrically (i.e. axially offset) relative to the first region 27 such that, in the closed position of the valve needle, a radial clearance 30 is provided between the surface of the second region 29 and the outlet openings 25A, 25B which varies around the circumference of the second region 29.
  • the second region has a larger clearance with some outlet openings (e.g. opening 25A in the drawing) than with others (e.g. opening 25B).
  • the eccentricity of the second region 29 relative to the first region 27 i.e. the difference in the maximum radial clearance between the second region 29 and the outlet openings and the minimum radial clearance
  • valve needle 18 moves to the open position, as described above with reference to Figure 2. Fuel is then able to flow past the valve seating surface 12A and through the outlet openings 25A, 25B. During the initial lifting movement of the valve needle 18, the first region 29 and the groove 26 act to keep the first region 29 concentric with the nozzle body 10.
  • the eccentricity of the second region 29 relative to the first region 27 has a significant effect on the symmetry of the fuel flow in the tip 30, 24 of the injection nozzle.
  • An asymmetric flow regime is therefore provided, with more fuel flowing through outlet opening 25A than through outlet opening 25B. In practice, this asymmetric flow regime results in some of the sprays having a more "bushy" effect than others.
  • the eccentricity of the second region 29 relative to the first region 27 is small, the asymmetric fuel flow is a highly controlled effect.
  • the effect of the eccentricity between the second region 29 and the first region 27 has a less significant effect on the symmetry of the flow regime set up in the tip of the injection nozzle (i.e. through the clearance 30 and within the sac region 24) such that the spray form becomes substantially symmetric.
  • the smoke reduction associated with the improved fuel/air mixing characteristics exhibited by the nozzle of Figure 2 can be maintained.
  • the present invention provides a simple and effective improvement over existing nozzles and provides a particular advantage where improved noise reduction is required in addition to improved smoke reduction.
  • the differential angle values and the eccentricity values disclosed above are not intended to be limiting and may take different values to those described. More particularly, the first and second differential angles need not be identical and may take any suitable range, although the preferred range is between 0.1 and 5°, and more preferably between 0.5 and 1°.
  • the eccentricity of the second region 29 relative to the first region 27 i.e. the perpendicular offset of the central axis of the second region 29 relative to that of the first region 27
  • the eccentricity is arranged such that the effect for a relatively small extent of valve needle lift is substantially less than the effect for a relatively large extent of lift.
  • the injection nozzle of the present invention may be incorporated in a unit/pump injector or in a fuel injector arranged to be supplied with fuel from a common rail fuel system. It will be appreciated that movement of the valve needle 18 within the blind bore 11 to open and close the outlet openings 25A, 25B may be controlled in any appropriate manner, for example by means of a piezoelectric or electromagnetic actuator arrangement, and that the fuel injector may be of the single or multi-stage lift type, the nozzle body 10 of the injector injection nozzle being provided with an appropriate number of outlet openings for fuel accordingly.
  • valve needle movement may be effected, for example, by providing an actuation force directly to the valve needle 18, or through a hydraulic amplifier arrangement or though a needle control valve for controlling fuel pressure acting on the back end of the valve needle 18 remote from the outlet openings 25A, 25B.
  • injection nozzle of the present invention may be used in controlling the delivery of any fluid, and is not limited to use in injecting fuel.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • Percussion Or Vibration Massage (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
EP03251544A 2002-03-14 2003-03-13 Einspritzdüse Expired - Lifetime EP1344931B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
GBGB0205966.5A GB0205966D0 (en) 2002-03-14 2002-03-14 Injection nozzle
GB0205966 2002-03-14

Publications (3)

Publication Number Publication Date
EP1344931A2 true EP1344931A2 (de) 2003-09-17
EP1344931A3 EP1344931A3 (de) 2004-04-28
EP1344931B1 EP1344931B1 (de) 2008-06-11

Family

ID=9932916

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03251544A Expired - Lifetime EP1344931B1 (de) 2002-03-14 2003-03-13 Einspritzdüse

Country Status (4)

Country Link
EP (1) EP1344931B1 (de)
AT (1) ATE398237T1 (de)
DE (1) DE60321500D1 (de)
GB (1) GB0205966D0 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005059353A1 (de) * 2003-12-17 2005-06-30 Robert Bosch Gmbh Ventilkörper mit mehrfachkegelgeometrie am ventilsitz

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5890660A (en) 1994-12-20 1999-04-06 Lucas Industries Public Limited Company Fuel injection nozzle

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2636659A1 (de) * 1976-08-14 1978-02-16 Daimler Benz Ag Betriebsverfahren fuer eine luftansaugende, fremdgezuendete brennkraftmaschine, entsprechende brennkraftmaschine sowie geeignetes einspritzventil
DE2841967A1 (de) * 1978-09-27 1980-04-10 Daimler Benz Ag Mehrloch-einspritzduese fuer luftverdichtende brennkraftmaschinen
JPS59153969A (ja) * 1983-02-19 1984-09-01 Daihatsu Motor Co Ltd 燃料噴射ノズル
JPS6248958A (ja) * 1985-08-28 1987-03-03 Hino Motors Ltd 燃料噴射ノズル
JPH0953543A (ja) * 1995-08-10 1997-02-25 Nippon Soken Inc 燃料噴射弁
JP4221898B2 (ja) * 2000-02-29 2009-02-12 株式会社デンソー 燃料噴射ノズル

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5890660A (en) 1994-12-20 1999-04-06 Lucas Industries Public Limited Company Fuel injection nozzle

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2005059353A1 (de) * 2003-12-17 2005-06-30 Robert Bosch Gmbh Ventilkörper mit mehrfachkegelgeometrie am ventilsitz
CN1894500B (zh) * 2003-12-17 2010-12-08 罗伯特·博世有限公司 在阀座上具有多锥几何结构的阀体

Also Published As

Publication number Publication date
DE60321500D1 (de) 2008-07-24
GB0205966D0 (en) 2002-04-24
ATE398237T1 (de) 2008-07-15
EP1344931A3 (de) 2004-04-28
EP1344931B1 (de) 2008-06-11

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