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WO2002038944A2 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant Download PDF

Info

Publication number
WO2002038944A2
WO2002038944A2 PCT/DE2001/004187 DE0104187W WO0238944A2 WO 2002038944 A2 WO2002038944 A2 WO 2002038944A2 DE 0104187 W DE0104187 W DE 0104187W WO 0238944 A2 WO0238944 A2 WO 0238944A2
Authority
WO
WIPO (PCT)
Prior art keywords
valve
fuel injection
flow
fuel
swirl
Prior art date
Application number
PCT/DE2001/004187
Other languages
German (de)
English (en)
Other versions
WO2002038944A3 (fr
Inventor
Martin Maier
Guenther Hohl
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
Priority to JP2002541241A priority Critical patent/JP2004513294A/ja
Priority to EP01993759A priority patent/EP1336046A2/fr
Publication of WO2002038944A2 publication Critical patent/WO2002038944A2/fr
Publication of WO2002038944A3 publication Critical patent/WO2002038944A3/fr

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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices

Definitions

  • the invention relates to a fuel injector according to the type of the main claim.
  • Swirl-generating fuel injection valves are known from US Pat. No. 5,108,037, in which two flow paths are formed for the fuel.
  • the fuel flow is split into two components in the area of the valve closing body.
  • One part of the fuel flows through swirl channels arranged in a swirl disk.
  • the fuel flow is subjected to a peripheral speed that leads to the fuel being sprayed off on a conical jacket.
  • the swirl disk has a central bore which is used to guide the valve closing body.
  • the gap formed between the guide bore and the valve closing body is used in a targeted manner to enable a fuel leakage flow that flows through the guide bore in the axial direction without swirl. Upstream of the sealing seat, the swirled and axial fuel flows meet.
  • the mixing fuel flows are sprayed together.
  • a fuel injector in which two flow paths are also formed for generating a bi-flux flow. They are produced in a separate component that is inserted downstream of the sealing seat. The component is manufactured in a multi-layer process and inserted into a recess at the downstream end of the fuel injector. The fuel steel is sprayed directly from the swirl-generating component. The fuel flow is divided into an axial and a swirling flow component in the component. The axial portion of the flow is fed eccentrically back to the swirling fuel flow, as a result of which the cone on which the fuel is sprayed is inclined towards the central axis of the fuel injector.
  • Another disadvantage is the poorer guidance of the valve closing body. Fuel flows around the valve closing body during the spraying process. Due to the spherical geometry and the increased play between the valve closing body and the guide bore, the tendency to oscillate is increased. This can lead to the formation of an unsteady flow. The wear of the fuel injector increases. Furthermore, it is not possible to influence the relationship between the axial and swirling flow during the opening and closing process.
  • the setting is optimized for the case of the fully opened fuel injector and is accordingly a compromise during the opening and closing of the fuel injector, which leads to poorer combustion.
  • the fuel flow is split downstream of the sealing seat and reunited. A change in the axial proportion of the fuel flow can therefore not be made during opening and closing.
  • the multilayer swirl element also requires a complex manufacturing process and must be used in the fuel injection valve oriented due to the asymmetrical arrangement of the axial flow channel. This increases the manufacturing costs for the fuel injector.
  • the fuel injector according to the invention with the characterizing feature of the main claim has the advantage that no complex additional component is required to generate an axial flow component, but an unavoidable leakage flow is used in a targeted manner by simple measures becomes. The costs for this are low because hardly any additional manufacturing steps are required.
  • the setting of the leakage rate over the length of the flow-limiting gap is advantageous, since the guidance of the valve closing body is not adversely affected thereby.
  • the valve needle is guided over a surface and is therefore less influenced by fluctuations in the diameter of the valve needle than is the case when guided along a circumferential line.
  • the variation in the length of the flow-limiting axial channel over the valve lift makes it possible to change the axial flow component during the opening or closing process of the fuel injector.
  • the enrichment or leaning of the sprayed fuel jet that can be achieved in this way leads to improved combustion and thus ultimately reduces the harmful gas emissions.
  • FIG. 1 is a schematic partial section through a first embodiment of a fuel injector according to the invention.
  • FIG. 2 shows a schematic partial section in section II of FIG. 1 through the first exemplary embodiment of a fuel injector according to the invention;
  • FIG. 3 shows a schematic partial section in section II of FIG. 1 through a second exemplary embodiment of a fuel injector according to the invention
  • the fuel injection valve 1 is designed in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, spark-ignited internal combustion engines.
  • Fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
  • the fuel injection valve 1 comprises a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • fuel injector 1 is an electromagnetically actuated fuel injector 1, which has a spray opening 7.
  • the nozzle body 2 is against the outer pole of a magnet coil 10 by a seal 8 sealed.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12, which bears against an inner pole 13 of the magnet coil 10.
  • the inner pole 13 and the outer pole 9 are separated from one another by a gap 26 and are supported on a connecting component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • the valve needle 3 is guided in a disk-shaped valve needle guide 14. This is paired with a shim 15, which is used to adjust the valve needle stroke.
  • An armature 20 is located on the upstream side of the adjusting disk 15. This armature is non-positively connected to the valve needle 3 via a flange 21, which is connected to the flange 21 by a weld seam 22.
  • a restoring spring 23 is supported on the flange 21 and, in the present design of the fuel injector 1, is preloaded by a sleeve 24 pressed into the inner pole 13.
  • Fuel channels 30a, 30b run in the valve needle guide 14 and in the armature 20.
  • a filter element 25 is arranged in a central fuel feed 16.
  • the fuel injection valve 1 is sealed by a seal 28 against a fuel line, not shown.
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against the stroke direction via the flange 21 on the valve needle 3 in such a way that the valve closing body 4 is held in sealing contact with the valve seat surface 6.
  • the magnetic coil 10 When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being achieved by a position between the inner pole 13 and the Anchor 20 located working gap 27 is predetermined.
  • the armature 20 takes the flange 21, which is welded to the valve needle 2, and thus also the valve needle 3 in the lifting direction.
  • the valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6, and the fuel reaching the spray opening 7 via swirl channels 32 and an axial channel 35 is sprayed off.
  • a swirl disk 31 is arranged upstream of the valve seat body 5, in which a guide recess 34 for guiding the valve needle 3 and swirl channels 32 for producing a swirl in the fuel flow are introduced.
  • the valve needle 3 is cylindrical in the region of the guide recess 34 and has a change in its radial extent.
  • the swirl disk 31 arranged upstream of the valve seat body 5 has swirl channels 32 for generating swirl. These are introduced, for example, as grooves in the downward surface of the valve seat body 5 and have a tangential component with respect to the longitudinal axis 38 of the fuel injector 1. You will be through the upstream surface of the valve seat body 5 supplemented to closed channels. Furthermore, the swirl disk 31 has a guide recess 34, on the downstream side of which a swirl chamber 33 is arranged, which is designed as a radial extension of the guide recess 34.
  • the swirl channels 32 preferably open tangentially into the swirl chamber 33.
  • the volume pressurized with fuel upstream of the swirl disk 31 is connected to the swirl channels 32 by fuel channels 30c, which are introduced into the swirl disk 31 parallel to the longitudinal axis 38 of the fuel injection valve 1.
  • valve needle 3 penetrates the guide recess 34 and the swirl chamber 33 of the swirl disk 31 and forms the axial channel 35 together with the guide recess 34
  • valve needles 3 and 4 Annular gap in the form of a hollow cylinder.
  • valve needles 3 and 4 Annular gap in the form of a hollow cylinder.
  • Valve closing body 4 made in one piece. However, an embodiment with two components, which are welded together, for example, is also possible.
  • the axial channel 35 has a change in cross section, which is formed by a change in the radial extension of the valve needle 3.
  • the axial channel 35 is divided into two areas.
  • the flow restricting portion 36 of the axial channel 35 is a thin-walled annular gap area which is obtained by a clearance for guiding the valve needle 3 in the swirl disk 31 , The fit is chosen so that it forms a strong throttle point for the axial flow.
  • the resulting leakage depends on the length of the flow-restricting part 36, the maximum can be equal to the length of the guide recess 34.
  • an enlarged part 37 follows, which opens out in the swirl chamber 33.
  • the length of the stroke of the valve needle 3 is smaller than the length of the flow-restricting part 36 of the axial channel 35 in the idle state of the fuel injector 1.
  • Two design variants are conceivable. If the length of the flow-limiting part 36 of the axial channel 35 is only slightly longer than the stroke length of the valve needle 3, this leads to a significant change in the leakage during the valve stroke.
  • the shortening of the length of the flow-limiting part 36 of the axial channel 35 relevant for the formation of a flow resistance increases the leakage flow. This leads to an increase in the axial flow component in the fuel to be sprayed off.
  • the spray pattern of the sprayed fuel is less fanned out.
  • the proportion of the fuel sprayed on the longitudinal axis 38 of the fuel injection valve 1 increases with the opening of the fuel injection valve 1.
  • Fig. 3 shows a second embodiment, in which during the opening process of the
  • Fuel injector 1 the proportion of the axial fuel flow decreases.
  • the axial channel 35 formed as an annular gap in the form of a hollow cylinder through which the fuel flow receives an axial component when the fuel injector 1 is open.
  • the axial channel 35 is in turn divided into a flow-restricting part 36 and an enlarged part 37.
  • the flow restricting part 36 is arranged on the downstream side of the guide recess 34.
  • the valve needle 3 Upstream, the valve needle 3 has a radial taper, which forms the enlarged part 37 of the axial channel 35 with the guide recess 34.
  • the length of the part of the valve needle 3 which forms the flow-restricting part 36 is at least so long that it projects into the guide recess 34 upstream of the swirl chamber 33 in the idle state.
  • the length of the flow-restricting part 36 of the axial channel 35 is increased.
  • the flow resistance along this ring-shaped or hollow-cylindrical, flow-limiting part 36 of the axial channel 35 increases as a result and the axial proportion of the fuel flow is reduced.
  • the spray pattern of the fuel is further fanned out.
  • the flow-limiting part 36 of the axial channel 35 can be long compared to the stroke of the valve needle 3, as in the first embodiment. As a result, the independence of the leakage flow from the valve needle stroke can also be set when the flow restriction is arranged on the downstream side of the guide recess.
  • the gap between the valve needle 3 and the guide recess 34 is used in both exemplary embodiments to set the leakage.
  • a concentrated or fanned-out spray pattern is achieved.

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

La présente invention concerne une soupape d'injection de carburant (1) pour installations d'injection de carburant de moteurs à combustion interne. Cette soupape d'injection de carburant comprend une aiguille de soupape (3) et un corps de fermeture de soupape (4) qui se trouve en liaison active avec cette aiguille de soupape et qui coopère avec une surface de siège de soupape (6) se trouvant dans un corps de siège de soupape (5), afin de former un siège d'étanchéité. Au moins un canal de turbulence (32) est pourvu en amont du siège d'étanchéité. Ce canal de turbulence présente une composante tangentielle par rapport à l'axe longitudinal (38) de la soupape d'injection de carburant (1). Un canal axial (35) est également pourvu entre le corps de fermeture de soupape (4) et l'évidement de guidage (34) du disque de turbulence (31). Ce canal axial présente une composante axiale par rapport à l'axe longitudinal (38) de la soupape d'injection de carburant (1). Ledit canal axial (35) est conçu sous forme d'espace annulaire et présente une partie qui limite l'écoulement (36) et une partie élargie (37).
PCT/DE2001/004187 2000-11-09 2001-11-09 Soupape d'injection de carburant WO2002038944A2 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
JP2002541241A JP2004513294A (ja) 2000-11-09 2001-11-09 燃料噴射弁
EP01993759A EP1336046A2 (fr) 2000-11-09 2001-11-09 Soupape d'injection de carburant

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE10055484.9 2000-11-09
DE2000155484 DE10055484B4 (de) 2000-11-09 2000-11-09 Brennstoffeinspritzventil

Publications (2)

Publication Number Publication Date
WO2002038944A2 true WO2002038944A2 (fr) 2002-05-16
WO2002038944A3 WO2002038944A3 (fr) 2003-01-09

Family

ID=7662663

Family Applications (1)

Application Number Title Priority Date Filing Date
PCT/DE2001/004187 WO2002038944A2 (fr) 2000-11-09 2001-11-09 Soupape d'injection de carburant

Country Status (4)

Country Link
EP (1) EP1336046A2 (fr)
JP (1) JP2004513294A (fr)
DE (1) DE10055484B4 (fr)
WO (1) WO2002038944A2 (fr)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5108037A (en) 1989-03-10 1992-04-28 Hitachi Ltd. Fuel injection valve

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS6056165A (ja) * 1983-09-05 1985-04-01 Toyota Central Res & Dev Lab Inc 間欠式渦巻噴射弁
JP3473884B2 (ja) * 1996-07-29 2003-12-08 三菱電機株式会社 燃料噴射弁
DE19815795A1 (de) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Zerstäuberscheibe und Brennstoffeinspritzventil mit Zerstäuberscheibe
JP2000291512A (ja) * 1999-04-07 2000-10-17 Mitsubishi Electric Corp 筒内噴射用燃料噴射弁

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5108037A (en) 1989-03-10 1992-04-28 Hitachi Ltd. Fuel injection valve

Also Published As

Publication number Publication date
WO2002038944A3 (fr) 2003-01-09
EP1336046A2 (fr) 2003-08-20
DE10055484B4 (de) 2005-10-27
DE10055484A1 (de) 2002-05-23
JP2004513294A (ja) 2004-04-30

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