EP1327068A2 - Soupape d'injection de carburant - Google Patents

Soupape d'injection de carburant

Info

Publication number
EP1327068A2
EP1327068A2 EP01986331A EP01986331A EP1327068A2 EP 1327068 A2 EP1327068 A2 EP 1327068A2 EP 01986331 A EP01986331 A EP 01986331A EP 01986331 A EP01986331 A EP 01986331A EP 1327068 A2 EP1327068 A2 EP 1327068A2
Authority
EP
European Patent Office
Prior art keywords
fuel
fuel injection
injection valve
valve
channels
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.)
Withdrawn
Application number
EP01986331A
Other languages
German (de)
English (en)
Inventor
Guenter Dantes
Detlef Nowak
Joerg Heyse
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 EP1327068A2 publication Critical patent/EP1327068A2/fr
Withdrawn legal-status Critical Current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
    • F02M61/188—Spherical or partly spherical shaped valve member ends
    • 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
    • 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
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • 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
    • 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
    • F02M61/1806—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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/12—Other methods of operation
    • F02B2075/125—Direct injection in the combustion chamber for spark ignition engines, i.e. not in pre-combustion chamber
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/10—Internal combustion engine [ICE] based vehicles
    • Y02T10/12—Improving ICE efficiencies

Definitions

  • the invention relates to a fuel injector according to the type of the main claim.
  • a fuel injection valve which has a plurality of fuel channels in a flow path of the fuel from a fuel inlet to a spray opening, the cross section of which at a given fuel pressure determines the amount of fuel sprayed per unit of time.
  • at least some of the fuel channels are oriented in such a way that the fuel jets emerging from them are sprayed directly through the spray opening.
  • a disadvantage of the fuel injection valve known from the abovementioned publication is in particular that the fuel channels start in a plane perpendicular to the flow direction of the fuel, that is to say the openings are arranged on a circular line around a valve needle guide connected to the valve seat body.
  • the number of holes is not sufficient to produce a sufficiently homogeneous fuel cloud that meets the stoichiometric requirements for complete combustion. This is further reinforced by the large diameter of the fuel channels.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that a swirl flow caused by the fuel flowing through the fuel channels into the swirl chamber remains homogeneous without compensating measures in the circumferential direction, the volume of the swirl chamber being so small that the Swirl flow can also be obtained during the dead time of the fuel injector.
  • the fuel channels are formed in a hollow cylindrical valve needle guide, which is either formed in one piece with the valve seat body or connected to it, so that center offsets and tilting of the valve needle are prevented.
  • the design of the fuel channels in an annular insert, which can be inserted into the valve seat body, is particularly easy to manufacture and can be used for any type of fuel injector, since the valve seat body only has to have a cylindrical recess for receiving the insert.
  • the shape of the swirl chamber, which is designed as a recess on the spraying side of the insert, is also advantageous.
  • the volume can be selected by a corresponding turning or a similar processing and adapted to the requirements.
  • FIG. 1 shows a schematic section through an embodiment of a fuel injection valve according to the prior art
  • FIG. 2A shows a schematic section through a first
  • FIG. 2B is a schematic section through the first embodiment shown in FIG. 2A along the line IIB-IIB in FIG. 2A,
  • FIG. 3A shows a schematic section through a second exemplary embodiment of a fuel injector according to the invention in the area ITA in FIG. 1,
  • FIG. 3B is a schematic section through the second embodiment shown in FIG. 3A along the line IIB-IIB in FIG. 3A,
  • 3C is a schematic section along the line IIIC-IIIC in Fig. 3A,
  • Fig. 4A is a schematic section through a third embodiment of an inventive Fuel injector in the area IIA in Fig. 1, and
  • Fig. 4B is a plan view of the third embodiment of the invention shown in Fig. 4A
  • the fuel injection valve 1 is in the form of a fuel injection valve for fuel injection systems of mixture-compressing, spark-ignited
  • 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 a fuel injection valve 1 that opens inwards and has an injection opening 7.
  • the nozzle body 2 is sealed by a seal 8 against the outer pole 9 of a solenoid 10.
  • the magnet coil 10 is in a coil housing
  • 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 to 30c run, which conduct the fuel, which is supplied via a central fuel supply 16 and filtered by a filter element 25, to the spray opening 7.
  • the fuel injector 1 is sealed by a seal 28 against a fuel line, not shown.
  • the armature 20 In the idle state of the fuel fine 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 on the valve seat 6 in sealing contact.
  • Excitation of the magnetic coil 10 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 located 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.
  • the valve closing body 4, which is operatively connected to the valve needle 3, lifts off the valve seat surface 6 and the fuel led to the spray opening 7 via the fuel channels 30a to 30c is sprayed off.
  • the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the flange 21 which is operatively connected to the valve needle 3 moves counter to the stroke direction.
  • the valve needle 3 is thereby moved in the same direction, as a result of which the valve-closure member 4 is seated on the valve seat surface 6 and the fuel injection valve 1 is closed.
  • FIG. 2A shows an excerpted sectional view of a first embodiment of a fuel injector 1 according to the invention.
  • the section shown is designated IIA in FIG. 1.
  • the part of the fuel injector 1 on the spray side shown in FIG. 2A shows the nozzle body 2 with the valve seat body 5 inserted therein. At least one spray opening 7 is formed in the valve seat body 5.
  • the valve seat body 5 is connected to the nozzle body 2 via a weld 45.
  • the valve seat body 5 has a first annular recess 41, in which an annular insert 40 is inserted.
  • Fuel channels 35 are formed in the annular insert 40.
  • the fuel channels 35 are in two rows 34 which are arranged concentrically to one another Form rings, arranged.
  • Fuel channels 35 can be arranged radially one behind the other or circumferentially offset from one another.
  • a second annular recess 42 Downstream of the first annular recess 41, a second annular recess 42 is formed, which forms a swirl chamber 43.
  • Fuel channels 35 in annular insert 40 open into swirl chamber 43. They thus extend from an inlet-side end face of the valve seat body 5, in which the first annular recess 41 is formed, into the swirl chamber 43.
  • the fuel channels 35 should have a very small diameter, for example less than 100 ⁇ m, in particular less than or equal to 70 ⁇ m.
  • Such small-bore holes can be produced, for example, by means of laser processing.
  • the fuel channels 35 are inclined at an angle in the spray direction relative to a plane which runs parallel to the inlet side end face 44 of the valve seat body 5.
  • the angle of inclination ⁇ can take place, for example, by correspondingly adapting the axial diameter of the annular insert 40.
  • the fuel channels 35 In order to impart a swirl to the fuel flowing through the fuel channels 35, the fuel channels 35 have a tangential component relative to the central axis 37 of the fuel injection valve 1. After flowing through the fuel channels 35, the fuel collects in the swirl chamber 43, causing a swirl flow in a circumferential direction.
  • the swirled fuel can pass through the spray opening 7 into the Combustion chamber, not shown, of an internal combustion engine are injected.
  • FIG. 2B shows a schematic section through the first exemplary embodiment of a fuel injector 1 according to the invention shown in FIG. 2A along the line IIB-IIB in FIG. 2A.
  • the fuel channels 35 are arranged in two rows 34, the fuel channels 35 being arranged offset in one circumference in the two rows 34.
  • the fuel channels 35 have a very small diameter, which is for example between 100 ⁇ m and 70 ⁇ m.
  • the number n of fuel channels 35 is only limited by the stability requirement. This means that a web must remain between two adjacent fuel channels 35 which is at least as wide as the diameter of the fuel channels.
  • at least 10 fuel channels 35 are advantageously provided, at least 50 fuel channels and even more advantageously at least 100 fuel channels.
  • FIG. 3A shows a schematic section through a second exemplary embodiment of a fuel injector 1 according to the invention, likewise in area IIA in FIG. 1.
  • the valve seat carrier 5 has a hollow cylindrical valve needle guide 31, which is either formed in one piece with the valve seat body 5 or is connected to it, for example by soldering, welding or similar methods.
  • the valve needle guide 31 has fuel channels 35 which extend from a radially outer side 36 of the valve needle guide 31 to a radially inner side of the valve needle guide 31.
  • the fuel channels 35 are arranged in several rows 34. In the present second exemplary embodiment, four rows 34 are provided.
  • the valve closing body 4 is in the valve needle guide 31 guided. It lies against an inner wall 38 of the valve needle guide 31 with at least one circumferential guide line 33, the valve closing body 4 being spherical in the present exemplary embodiment.
  • a swirl chamber 43 is formed between the valve closing body 4, the inner wall 38 of the valve needle guide 31 and the valve seat surface 6. This can be designed, for example, to reduce the volume of the swirl chamber 43 in the form of a spherical shell.
  • FIG. 3B shows a schematic section through the second exemplary embodiment of a fuel injector 1 according to the invention shown in FIG. 3A along the line IIB-IIB in FIG. 3A.
  • the sectional plane in FIG. 3A lies along a row 34 of fuel channels 35.
  • four fuel channels 35 in the first and in the third quadrant are shown as representative of all fuel channels 35, which are arranged in four rows 34 in the valve needle guide 31 .
  • the fuel channels 35 are again tangential Component provided relative to a central axis 37 of the fuel injector 1.
  • the fuel channels 35 open into the swirl chamber 43 on the radially inner side 39 of the valve needle guide 31. Due to the large number of fuel channels 35, a largely homogeneous swirl flow in the circumferential direction is also generated in the present second exemplary embodiment.
  • FIG. 3C shows a schematic section along the line IIIC-IIIC in FIG. 3A. Since the fuel channels 35, as already mentioned above, have a tangential component relative to the central axis 37 of the fuel injection valve 1 for generating a swirl, the cross section of the fuel channels 35 appears oval in FIG. 3C. The orientation of the tangential components of the fuel channels 35 is oriented in the same direction in each row 34 relative to the other rows 34.
  • Fig. 4A shows a schematic section through a third embodiment of an inventive
  • Fuel injector 1 also in area IIA in FIG. 1.
  • the essential components of the present exemplary embodiment correspond to the first exemplary embodiment shown in FIG. 2A.
  • the annular insert 40 in the first recess 41 which is formed in the inlet-side end face 44 of the valve seat body 5, has only one row 34 of fuel channels 35 arranged circumferentially. As in the first exemplary embodiment, these are inclined at an angle ⁇ with respect to a plane defined by the inlet side end face 44 of the valve seat body 5.
  • the fuel channels 35 open into the swirl chamber 43, which is formed by the second recess 42 in the valve seat body 5.
  • the fuel channels 35 have a larger diameter in order to take account of the reduced number of fuel channels 35. The amount of fuel flowing through is always the same, so that the product of cross-sectional area and number of fuel channels 35 is also the same.
  • FIG. 4B shows a top view of the third exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 4A.
  • Representative individual fuel channels 35 are again shown in the annular insert 40. They also have a tangential component relative to the central axis 37 of the fuel injector, around a swirl flow. to create. As indicated in FIG. 4B, the fuel channels 35 are inclined at an angle ⁇ relative to the plane defined by the inlet side end face 44 of the valve seat body 5.
  • the number n is at least 10, but is advantageously significantly larger and is, for example, 50 or 100 or more.
  • the large number n of fuel channels 35 has several advantages: Firstly, the large number n means that the diameters of the fuel channels 35 do not have to meet high requirements. Any inaccuracies in the manufacturing process are averaged out by the large number n, since statistically as many larger and smaller fuel channels 35 are available. It is sufficient if a statistical mean value comes close to the desired diameter.
  • the swirl flow becomes increasingly homogeneous, while local fuel accumulations, so-called strands, occur in a small number of fuel channels 35, which is avoided in particular when fuel is directly injected into the combustion chamber of a mixture-compressing, spark-ignited internal combustion engine should.
  • This is particularly favored by large volumes of the swirl chamber 43, since that in the swirl chamber 43 Existing fuel comes to a standstill during the dead time of the fuel injector 1 between two injection cycles and only has to be rotated again during the next injection cycle. At the beginning of the injection cycle, this leads to a fuel injection that is too high in quantity, while less or even too little fuel is subsequently injected. This is avoided by the small swirl chamber volumes according to the invention and the large number n of fuel channels 35.
  • the invention is not limited to the illustrated embodiments and z. B. can also be used for fuel injection valves 1 with piezoelectric or magnetostrictive actuators 10 and for any arrangement of fuel channels 35 in the rows 34.

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

L'invention concerne une soupape d'injection de carburant (1), notamment pour l'injection directe de carburant dans la chambre de combustion d'un moteur à combustion interne. Cette soupape d'injection de carburant comporte un actionneur (10) servant à actionner un pointeau de soupape (3). Ledit pointeau de soupape (3) présente à une extrémité côté injection, un corps de fermeture de soupape (4) qui forme un siège d'étanchéité, conjointement avec une surface de siège de soupape (6) formée sur un corps de siège de soupape (5). Dans un guide de pointeau de soupape (31) lié au corps de siège de soupape (5) ou formé monobloc, il est prévu des canaux pour carburant (35) qui débouchent dans une chambre de tourbillonnement (43). Le nombre de canaux pour carburant (35) est calculé de manière qu'un écoulement en tourbillonnement produit dans la chambre de tourbillonnement (43) soit homogène dans le sens périphérique.
EP01986331A 2000-10-06 2001-10-06 Soupape d'injection de carburant Withdrawn EP1327068A2 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10049518A DE10049518B4 (de) 2000-10-06 2000-10-06 Brennstoffeinspritzventil
DE10049518 2000-10-06
PCT/DE2001/003838 WO2002029242A2 (fr) 2000-10-06 2001-10-06 Soupape d'injection de carburant

Publications (1)

Publication Number Publication Date
EP1327068A2 true EP1327068A2 (fr) 2003-07-16

Family

ID=7658890

Family Applications (1)

Application Number Title Priority Date Filing Date
EP01986331A Withdrawn EP1327068A2 (fr) 2000-10-06 2001-10-06 Soupape d'injection de carburant

Country Status (5)

Country Link
US (1) US6739525B2 (fr)
EP (1) EP1327068A2 (fr)
JP (1) JP2004510913A (fr)
DE (1) DE10049518B4 (fr)
WO (1) WO2002029242A2 (fr)

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EP1811166B1 (fr) * 2006-01-24 2008-11-05 Continental Automotive GmbH Ensemble à vanne pour une soupape d'injection et soupape d'injection
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Also Published As

Publication number Publication date
DE10049518B4 (de) 2005-11-24
WO2002029242A2 (fr) 2002-04-11
US20030106946A1 (en) 2003-06-12
JP2004510913A (ja) 2004-04-08
US6739525B2 (en) 2004-05-25
WO2002029242A3 (fr) 2002-06-27
DE10049518A1 (de) 2002-04-18

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