EP1342006A1 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant

Info

Publication number
EP1342006A1
EP1342006A1 EP01993761A EP01993761A EP1342006A1 EP 1342006 A1 EP1342006 A1 EP 1342006A1 EP 01993761 A EP01993761 A EP 01993761A EP 01993761 A EP01993761 A EP 01993761A EP 1342006 A1 EP1342006 A1 EP 1342006A1
Authority
EP
European Patent Office
Prior art keywords
swirl
valve
fuel injection
fuel
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
EP01993761A
Other languages
German (de)
English (en)
Other versions
EP1342006B1 (fr
Inventor
Hubert Stier
Norbert Keim
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 EP1342006A1 publication Critical patent/EP1342006A1/fr
Application granted granted Critical
Publication of EP1342006B1 publication Critical patent/EP1342006B1/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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging 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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • F02M51/061—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means
    • F02M51/0625—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures
    • F02M51/0664—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding
    • F02M51/0671—Injectors peculiar thereto with means directly operating the valve needle using electromagnetic operating means characterised by arrangement of mobile armatures having a cylindrically or partly cylindrically shaped armature, e.g. entering the winding; having a plate-shaped or undulated armature entering the winding the armature having an elongated valve body attached thereto

Definitions

  • the invention relates to a fuel injector according to the type of the main claim.
  • a fuel injection valve is known from US Pat. No. 5,058,549, which has a device for generating swirl as well as a main spray opening of large diameter and a secondary spray opening of smaller diameter.
  • the inclination of the spray orifices with respect to a longitudinal axis of the fuel injector is different, so that the fuel is sprayed through the secondary spray orifice with a high swirl and a large penetration length and with a small swirl and a large opening angle through the main spray orifice.
  • a disadvantage of the fuel injector known from US Pat. No. 5,058,549 is, in particular, the high production outlay both of the valve closing body and / or the valve needle, which have to be provided with swirl grooves, and of the valve seat body, in which the spray openings are formed.
  • the different inclination of the spray openings and the high demands on the accuracy of the diameter of the Spray openings require a ' complex manufacturing process.
  • a fuel injection valve which has a valve needle which is guided with its shaft in the bore of a valve guide part, when pressurized fuel is supplied via radial transverse bores arranged in the guide part and opening into the guide bore opens in the direction of flow of the fuel and rotates the fuel via grooves. Furthermore, the fuel injection valve has at least two spray openings on the downstream side of the valve needle.
  • a disadvantage of the fuel injector known from DE 1 601 988 is in particular the disturbance of the swirl of the fuel caused by the outward opening movement, which is primarily caused by the large dead volume of a swirl chamber formed between the valve closing body and the spray openings.
  • the swirl flow can no longer be kept homogeneous, and the cross section of the grooves is increased so much when the fuel injector is opened that the swirl flow comes to a standstill.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the advantages of a multi-hole fuel injector can be combined with those of a fuel injector with swirl processing with the most extensive use of standard components.
  • a swirl device for example a conventional swirl disk
  • a swirl chamber which communicates a swirl to the fuel, so that a homogeneous swirl flow is formed in the swirl chamber. Due to the homogeneous swirl flow, the fuel can flow through several Spray openings, which are formed, for example, in a valve seat body known from multi-hole nozzle technology, are sprayed simultaneously.
  • the swirl flow in the swirl chamber can be adjusted according to requirements by means of a tangential component relative to a longitudinal axis of the fuel injection valve.
  • the design of the swirl device as a swirl disk is advantageous because it is simple to manufacture and easy to assemble.
  • Another advantage is that any arrangement of spray openings can be realized in accordance with the requirements placed on the shape of the mixture cloud.
  • FIG. 1A shows a schematic section through a first exemplary embodiment of a fuel injector according to the invention
  • FIG. 1B is a schematic partial section through the first embodiment of a fuel injector according to the invention shown in FIG. 1 in the area IB in Fig. 1A, 1C shows a schematic section along the line labeled IC-IC in FIG. 1B,
  • FIG. 2 shows a schematic partial section through a second exemplary embodiment of a fuel injection valve according to the invention in the same area as FIG. 1B,
  • 3A-C are beam images of a conventional one
  • FIGS. 3A-3C shows a diagram of the static flow as a function of the stroke of the valve needle for the jet images of fuel injectors shown in FIGS. 3A-3C.
  • the first exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 1A is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, spark-ignition internal combustion engines.
  • the fuel injection valve 1 is particularly suitable for injecting fuel directly into a combustion chamber (not shown) of an internal combustion engine.
  • the fuel injector 1 consists of 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.
  • the fuel injection valve 1 is an inwardly opening fuel injection valve 1 which has a plurality of spray openings 7.
  • the nozzle body 2 is through a seal 8 sealed against the outer pole 9 of a solenoid 10.
  • the magnet coil 10 is encapsulated in a coil housing 11 and on one.
  • Coil carrier 12 is wound, 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.
  • valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disc 15 is used for stroke adjustment.
  • An armature 20 is located on the other side of the adjusting disc 15.
  • a restoring spring 23 is supported on the first flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24.
  • Fuel channels 30a and 30b run in the valve needle guide 14 and in the armature 20, which channels the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the spray-discharge openings 7.
  • inflow openings 34 are provided both for the fuel line and for the swirl preparation.
  • the fuel injector 1 is against by a seal 28 sealed a fuel feed 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 its stroke direction 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 predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20.
  • the armature 20 also carries the flange 21, which is welded to the valve needle 3, in the lifting direction.
  • valve closing body 4 which is operatively connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel which is led via the fuel channels 30a and 30b and the inflow openings 34 in the valve seat body 5 to the spray openings 7 is sprayed off.
  • the described first exemplary embodiment of a fuel injection valve 1 combines the advantages of swirl-conditioning measures with those of fuel injection valves 1 with a plurality of spray openings 7.
  • FIG. 1B shows an excerpted, schematic sectional view of the spray-side end of the fuel injector 1 according to the invention shown in FIG. 1A.
  • the section shown in FIG. 1B is designated IB in FIG. 1A.
  • Matching components are provided with matching reference numerals.
  • the injection-side end of the fuel injector 1 according to the invention shown in FIG is formed in one piece or is connected to the valve seat body 5 by means of welding, soldering or similar methods.
  • the valve needle 3 with the valve closing body 4 formed thereon is guided through the guide extension 35 to avoid center offsets in order to ensure the fault-free operation of the fuel injection valve 1.
  • At least two spray openings 7 are formed in the valve seat body 5.
  • the two spray openings 7 shown in FIG. 1B can for example be part of an annular arrangement of spray openings 7 which consists of one or more preferably concentric rings.
  • a preferably spherical swirl chamber 36 is formed, the volume of which is preferably dimensioned such that the dead volume is minimal and a circumferentially directed swirl flow can form when fuel flows into the swirl chamber 36.
  • FIG. 1C shows an excerpt, schematic sectional illustration of a section through the exemplary embodiment of the fuel injector 1 according to the invention shown in FIG.
  • two lines A and B are introduced, which represent the eccentricity of the inflow opening 34.
  • Due to a tangential component of the inflow opening 34 relative to a longitudinal axis 44 of the fuel injection valve 1, fuel does not directly enter radially into the swirl chamber 36 formed between the valve seat body 5 and the valve closing body 4, so that a swirl flow directed in the circumferential direction can form.
  • the . Swirl flow transports the fuel evenly to all spray openings 7, so that a homogeneous and symmetrical fuel cloud can be generated.
  • inflow opening 34 For reasons of clarity, only one inflow opening 34 is shown in FIG. IC. For reasons of clarity, however, there should be at least two, more advantageously, but four or more inflow openings 34, on the one hand to symmetrize the forces acting through the fuel flowing through and on the other hand to adapt the injected fuel cloud as well as possible to the stoichiometric requirements.
  • FIG. 2 shows a second exemplary embodiment of a fuel injector 1 designed according to the invention in the same area as in FIG. IB.
  • the outflow-side part of the fuel injection valve 1 is composed of three components which are manufactured individually and then assembled.
  • a swirl disk 39 is arranged on the inlet side of the valve seat body 5 and has at least one, advantageously more than two swirl channels 40.
  • the guidance of the valve needle 3 or the valve closing body 4 without offset is ensured in the present exemplary embodiment by a guide element 38.
  • the guide element 38 and the swirl disk 39 each have a recess 41, 42 through which the valve needle 3 passes.
  • the Guide element 38 and the swirl disk 39 can be connected to one another and to the valve seat body 5, for example by soldering, welding, gluing or other connecting methods.
  • a swirl chamber 36 is formed, which ensures the homogenization of the swirl flow, which is caused by the fuel flowing through the swirl disk 39 in the swirl chamber 36.
  • FIG. 3A to 3C show schematic jet images of various fuel injection valves 1 with and without swirl processing and with one or more spray orifices 7.
  • FIG. 4 is to be considered in each case, in which the stroke throttling coefficients of the differently configured fuel injection valves 1 in Dependence on the stroke of the valve needle are shown.
  • the stroke throttling coefficient dQ stat / dh defines the change in the static flow Q stat with the stroke h of the valve needle 3.
  • FIG. 3A shows the spray pattern of a fuel injection valve 1 with conventional swirl processing, for example with a swirl disk 39, and only one spray opening 7.
  • the swirl processing shows a relatively homogeneous mixture cloud 43, which, however due to the shape of the spray opening 7, opens relatively wide and so that no deep penetration of the combustion chamber is achieved. Modifications in the shape of the spray opening 7 are not satisfactory in the representation of the mixture cloud 43, since throttling effects and turbulence are noticeably noticeable, which is why the penetration of the combustion chamber is limited by a spray opening 7 which cannot be reduced further.
  • the curve A belonging to FIG. 3A in FIG. 4 is marked with diamonds.
  • the stroke throttling coefficient for the fuel injector 1 equipped with conventional swirl preparation and only one spray opening 7 is constant over the stroke of the valve needle 3 approximately 0.01% / ⁇ m. This means that the static fuel flow through the fuel injection valve 1 depends only very slightly on changes in stroke.
  • 3B shows, in comparison, the spray pattern of a fuel injection valve 1 without swirl preparation, which, however, is provided with several spray openings 7 according to known multi-hole concepts.
  • the penetration of the combustion chamber is significantly greater here, the mixture cloud 43 penetrates almost three times further into the combustion chamber than the mixture cloud 43 shown in FIG. 3A.
  • the reason for this is in particular the large number of very small spray openings 7, which avoid throttling effects and generate sharp injection jets , which overlap to form a stoichiometric mixture cloud 43.
  • a disadvantage of multi-hole fuel injection valves 1 without swirl preparation is in particular the strong dependence of the static fuel flow on the stroke of the valve needle 3.
  • curve B belonging to FIG. 3B is identified by triangles.
  • the stroke throttling coefficient for a fuel injection valve 1 equipped with a plurality of spray openings 7 according to known multi-hole concepts is approximately 0.1% / ⁇ m, which corresponds to approximately ten times the value of the fuel injection valve 1 with swirl preparation shown in FIG. 3A.
  • the static fuel flow through the fuel injection valve 1 depends heavily on the stroke of the valve needle 3, as a result of which large variations in the injection quantities can occur.
  • 3C shows the spray pattern of a fuel injector 1 designed according to the invention
  • the spray pattern of the fuel injection valve 1 according to the invention shows only insignificant differences, i. H. the penetration depth of the mixture cloud 43 in the combustion chamber continues to reach satisfactory values, while the tolerance of the fuel flow to stroke changes approaches the value of the fuel injection valve 1 with swirl conditioning, which is shown in FIG. 3A.
  • the curve C in FIG. 4 corresponds to the beam distribution shown in FIG. 3C.
  • the stroke throttling coefficient marked with squares in FIG. 4 of the fuel injector 1 designed according to the invention at least reaches a value of approximately 0.02% / ⁇ m, which is only slightly above the value of the fuel injector 1 with swirl preparation shown in FIG. 3A.
  • the fuel injection valve 1 designed according to the invention thus has a high penetration depth of the mixture cloud 43 in the combustion chamber and only a slight dependence of the static flow on the stroke of the valve needle 3 and accordingly only a slight scatter of the static flow.
  • the invention is not limited to the illustrated embodiments and z. B. can also be used for fuel injection valves 1 with other arrangements of swirl processing devices, with more or fewer inflow openings 34 or swirl disks with more or less swirl channels 40 and for any designs of fuel injection valves 1.

Landscapes

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

Abstract

La présente invention concerne une soupape d'injection de carburant (1), servant notamment à l'injection directe de carburant dans une chambre de combustion d'un moteur à combustion interne. Cette soupape d'injection de carburant comprend une aiguille de soupape (3), qui présente un corps de fermeture de soupape (4) à son extrémité côté injection. Ce corps de fermeture de soupape coopère avec une surface de siège de soupape (6), qui est formée sur un corps de siège de soupape (5), afin de former un siège d'étanchéité. Ladite soupape d'injection de carburant comprend également au moins un canal de turbulence (37, 40), une chambre de turbulence (36), pourvue sur le corps de siège de soupape (5), ainsi que plusieurs ouvertures d'injection (7), provenant de la chambre de turbulence (36), qui permettent d'injecter simultanément le carburant imprimé d'une certaine turbulence. Ledit canal de turbulence (37, 40) est pourvu dans le corps de siège de soupape (5) ou dans un disque de turbulence (39) voisin du corps de siège de soupape (5).
EP01993761A 2000-11-09 2001-11-09 Soupape d'injection de carburant Expired - Lifetime EP1342006B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10055513 2000-11-09
DE10055513A DE10055513B4 (de) 2000-11-09 2000-11-09 Brennstoffeinspritzventil
PCT/DE2001/004188 WO2002038946A1 (fr) 2000-11-09 2001-11-09 Soupape d'injection de carburant

Publications (2)

Publication Number Publication Date
EP1342006A1 true EP1342006A1 (fr) 2003-09-10
EP1342006B1 EP1342006B1 (fr) 2005-02-23

Family

ID=7662679

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01993761A Expired - Lifetime EP1342006B1 (fr) 2000-11-09 2001-11-09 Soupape d'injection de carburant

Country Status (5)

Country Link
US (1) US6966504B2 (fr)
EP (1) EP1342006B1 (fr)
JP (1) JP2004513295A (fr)
DE (2) DE10055513B4 (fr)
WO (1) WO2002038946A1 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ITBO20040560A1 (it) 2004-09-10 2004-12-10 Magneti Marelli Powertrain Spa Iniettore di carburante con valvola di iniezione provvista di alimentazione laterale
JPWO2007013165A1 (ja) * 2005-07-29 2009-02-05 三菱電機株式会社 燃料噴射弁
CN101371033B (zh) 2007-03-27 2010-10-27 三菱电机株式会社 燃料喷射阀
EP2700808A1 (fr) * 2012-08-23 2014-02-26 Continental Automotive GmbH Plaque de siège et ensemble de soupape pour soupape d'injection
WO2017099714A1 (fr) * 2015-12-07 2017-06-15 Cummins Inc. Sac sphérique à l'intérieur d'une buse d'injecteur de carburant
DE102018218678A1 (de) 2018-10-31 2020-04-30 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids, insbesondere Brennstoffeinspritzventil
DE102018221086A1 (de) 2018-12-06 2020-06-10 Robert Bosch Gmbh Ventil zum Zumessen eines Fluids, insbesondere Brennstoffeinspritzventil

Family Cites Families (18)

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Publication number Priority date Publication date Assignee Title
DE1601988C3 (de) * 1968-03-07 1974-01-10 Clayton Dewandre Holdings Ltd., London Kraftstoffeinspritzventil für Brennkraftmaschinen
DE3602956A1 (de) * 1986-01-31 1987-08-06 Vdo Schindling Elektromagnetisch betaetigbares kraftstoffeinspritzventil
US5058549A (en) * 1988-02-26 1991-10-22 Toyota Jidosha Kabushiki Kaisha Fuel swirl generation type fuel injection valve and direct fuel injection type spark ignition internal combustion engine
DE3943005A1 (de) * 1988-12-28 1990-07-05 Hitachi Ltd Elektromagnetische einspritzventilvorrichtung
JP2628742B2 (ja) * 1989-03-10 1997-07-09 株式会社日立製作所 電磁式燃料噴射弁
US4971254A (en) * 1989-11-28 1990-11-20 Siemens-Bendix Automotive Electronics L.P. Thin orifice swirl injector nozzle
DE3940585A1 (de) 1989-12-08 1991-06-13 Bosch Gmbh Robert Elektromagnetisch betaetigbares kraftstoffeinspritzventil
JP2819702B2 (ja) 1989-12-12 1998-11-05 株式会社デンソー 燃料噴射弁
DE4018256A1 (de) * 1990-06-07 1991-12-12 Bosch Gmbh Robert Elektromagnetisch betaetigbares brennstoffeinspritzventil
DE4445358A1 (de) * 1994-12-20 1996-06-27 Bosch Gmbh Robert Ventil und Verfahren zur Herstellung eines Ventiles
US6125818A (en) * 1997-03-19 2000-10-03 Hiatchi, Ltd. Fuel injector and internal combustion engine having the same
JPH10281039A (ja) * 1997-04-02 1998-10-20 Hitachi Ltd 燃料噴射装置とその制御方法
DE19726991A1 (de) * 1997-06-25 1999-01-07 Bosch Gmbh Robert Ventil und Verfahren zur Herstellung eines Ventilsitzes für ein Ventil
DE19736682A1 (de) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Brennstoffeinspritzventil
BR9906683A (pt) 1998-08-27 2000-10-17 Bosch Gmbh Robert Válvula de injeção de combustìvel
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JP2001082283A (ja) * 1999-09-20 2001-03-27 Hitachi Ltd 電磁式燃料噴射弁
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Also Published As

Publication number Publication date
EP1342006B1 (fr) 2005-02-23
JP2004513295A (ja) 2004-04-30
WO2002038946A1 (fr) 2002-05-16
DE10055513B4 (de) 2006-03-09
DE10055513A1 (de) 2002-05-23
US6966504B2 (en) 2005-11-22
DE50105435D1 (de) 2005-03-31
US20040055566A1 (en) 2004-03-25

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