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EP0774069A1 - Soupape d'injection de carburant pour moteurs a combustion interne - Google Patents

Soupape d'injection de carburant pour moteurs a combustion interne

Info

Publication number
EP0774069A1
EP0774069A1 EP96900279A EP96900279A EP0774069A1 EP 0774069 A1 EP0774069 A1 EP 0774069A1 EP 96900279 A EP96900279 A EP 96900279A EP 96900279 A EP96900279 A EP 96900279A EP 0774069 A1 EP0774069 A1 EP 0774069A1
Authority
EP
European Patent Office
Prior art keywords
valve seat
seat body
fuel injection
shoulder
spray
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
EP96900279A
Other languages
German (de)
English (en)
Other versions
EP0774069B1 (fr
Inventor
Clemens Willke
Klaus Franzke
Hartmut Albrodt
Norbert Belzner
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 EP0774069A1 publication Critical patent/EP0774069A1/fr
Application granted granted Critical
Publication of EP0774069B1 publication Critical patent/EP0774069B1/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
    • F02M61/18—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
    • F02M61/1853—Orifice plates
    • 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
    • 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
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S239/00—Fluid sprinkling, spraying, and diffusing
    • Y10S239/90—Electromagnetically actuated fuel injector having ball and seat type valve

Definitions

  • the invention is based on a fuel injection valve according to the preamble of claim 1.
  • a fuel injection valve is already known (DE 42 21 185 AI), in which at very high engine and fuel temperatures
  • the fuel injector according to the invention with the characterizing features of claim 1 the advantage that the risk of a reduction (leaning) of the injected fuel quantity is reduced or avoided in a simple manner, especially at very high engine or fuel temperatures, so that the running behavior of the hot internal combustion engine is improved, especially when it is started hot or idling.
  • the at least one transition element between the valve seat body and the spray orifice plate reduces the heat transfer from the valve seat body to the spray orifice plate, and thus decouples them from one another, so that the heat of vaporization required to evaporate the fuel sprayed off at the spray orifice holes, which is withdrawn from the spray orifice plate, leads to cooling of the spray orifice plate , while a flow of heat from the valve seat body to the spray orifice plate is reduced or almost completely prevented by the transition element.
  • the at least one transition element is advantageous to design the at least one transition element as a raised body shoulder on the valve seat body, in order to reduce the contact area between the valve seat body and the spray orifice plate and thereby create a throttle point for the heat transfer. It is also advantageous to design the at least one transition element as a raised disk shoulder on the spray hole disk, which likewise reduces the contact area between the valve seat body and the spray hole disk and thus reduces the heat transfer. It is furthermore advantageous to form the disc shoulder by means of a recessed step or an arching in the spray-perforated disc. Another advantageous embodiment is such that at least one transition element as a raised body shoulder on the
  • Valve seat body and at least one transition element is designed as a raised disc shoulder on the spray orifice plate in order to throttle the heat transfer between the valve seat body and spray orifice plate. It is also advantageous to form the body shoulder or the disk shoulder in a circular shape.
  • Another advantageous embodiment is to design the at least one transition element as a separate, thermally insulating insulating body and between
  • valve seat body and spray hole plate Arrange valve seat body and spray hole plate to reduce the amount of heat transferred from the valve seat body to the spray hole plate. It is advantageous to design the insulating body from plastic, in particular as a plastic injection molded body.
  • FIG. 1 shows a first exemplary embodiment of the invention on the basis of a fuel injector shown schematically in partial representation
  • FIG. 2 to FIG. 8 shows a second to an eighth exemplary embodiment of the invention with a partial representation of a fuel injector.
  • FIG. 1 partially shows an example of an otherwise already known fuel injection valve for fuel injection systems of mixture-compressing spark-ignition internal combustion engines, which is designed as a first exemplary embodiment according to the invention.
  • the fuel injector has a tubular valve housing 1, in which a longitudinal opening 3 is formed concentrically with a valve longitudinal axis 2. In the longitudinal opening 3 is a z.
  • the fuel injector is actuated in a known manner, for example electromagnetically.
  • An indicated electromagnetic circuit with a magnet coil 10, an armature 11 and a core 12 is used for the axial movement of the valve needle 5 and thus for opening against the spring force of a return spring (not shown) or closing the fuel injector.
  • the armature 11 is facing away from the valve closing body 7 End of the valve needle 5 by z. B. a weld seam connected by a laser and aligned with the core 12.
  • a guide opening 15 of a valve seat body 16 serves to guide the valve closing body 7 during the axial movement Downstream end of the valve housing 1 facing away from the core 11, the cylindrical valve seat body 16 is inserted into the longitudinal opening 3 which is concentric with the longitudinal axis 2 of the valve.
  • the circumference of the valve seat body 16 has a slightly smaller diameter than the longitudinal opening 3 of the valve housing 1.
  • the valve seat body 16 On its one lower end face 17 facing away from the valve closing body 7, the valve seat body 16 is provided with a raised body shoulder 18 on which a bottom part 20 of a z.
  • B. pot-shaped spray plate 21 rests with its upper end face 19 and is concentrically and firmly connected to it.
  • Spray hole disk 21 has at least one, for example four, spray holes 25 formed by eroding or stamping.
  • valve seat part consisting of valve seat body 16 and cup-shaped spray orifice plate 21 into the longitudinal opening 3 determines the presetting of the stroke of the valve needle 5, since the one end position of the valve needle 5 when the solenoid 10 is not excited due to the contact of the
  • Valve closing body 7 is fixed to a valve seat surface 29 of the valve seat body 16.
  • the other end position of the valve needle 5 is determined when the solenoid 10 is excited, for example by the armature 11 resting on the core 12.
  • the Path between these two end positions of the valve needle 5 thus represents the stroke.
  • the holding edge 26 of the spray plate 21 is tightly and firmly connected to the wall of the longitudinal opening 3.
  • a circumferential weld seam 30 is provided between the end 27 of the holding edge 26 and the wall of the longitudinal opening 3. Outside the central area 24, the bottom part 20 is sealed with the body shoulder 18 on the end face 17 of the valve seat body with a further circumferential weld seam 31
  • valve seat body 16 A tight connection of the valve seat body 16 and the spray orifice plate 21 and of the spray orifice plate 21 and the valve housing 1 is required so that the fuel does not pass between the longitudinal opening 3 of the valve housing 1 and the circumference of the valve seat body 16 to the spraying holes 25 or between the longitudinal opening 3 of the valve seat carrier 1 and can flow directly through the holding edge 26 of the pot-shaped spray perforated disk 21 into an air intake line of the internal combustion engine.
  • the spherical valve closing body 7 interacts with the valve seat surface 29 of the valve seat body 16 tapering in the shape of a truncated cone, which in the axial direction between the guide opening 15 and an outflow opening 32 in the lower end face 17 of the
  • Valve seat body 16 is formed.
  • the valve seat body 16 has a valve seat body opening 34 facing the solenoid 10, which has a larger diameter than the diameter of the guide opening 15 of the valve seat body 16.
  • the diameter of the guide opening 15 is designed such that the spherical valve closing body 7 projects through the guide opening 15 outside of its flattened portions 8 with a small radial distance.
  • the central region 24 of the base part 20 of the spray perforated disk 21 is bent out of the plane of the base part 20, for example in the downstream direction, ie in the direction pointing away from the valve closing body 7, so that a bulge 36 results in the central region.
  • a collecting space 37 is formed, into which, when the valve closing body 7 is lifted from the valve seat surface 29, the fuel first reaches it before it passes through the Spray holes 25 are metered and sprayed into the air intake line of the internal combustion engine.
  • the at least one body shoulder 18 on the lower end face 17 of the valve seat body 16 forms a transition element from the valve seat body 16 to the spray hole disk 21 and throttles the heat transfer between the valve seat body and the spray hole disk.
  • the body shoulder 18 is preferably annular, in particular concentric to the longitudinal axis 2 of the valve, and reduces the contact area between the bottom part 20 of the spray hole disk 21 and the valve seat body 16.
  • the body shoulder 18 in Axial direction parallel to the longitudinal axis 2 of the valve has a height of a few hundredths of a millimeter, for example five hundredths of a millimeter.
  • the width of the body shoulder 18 in the radial direction, that is to say transversely to the valve longitudinal axis 2, is approximately one millimeter, for example 0.8 mm.
  • the position of the body shoulder 18 on the lower end face 17 of the valve seat body 16 can be selected in a suitable manner between a position in the vicinity of the outflow opening 32 and a position in the vicinity of the diameter of the valve seat body 16, that is to say in the vicinity of the longitudinal opening 3.
  • the transition element is designed as a raised disc shoulder 39, which projects beyond the upper end face 19 of the base part 20 in the direction of the valve seat body 16 and bears against the lower end face 17 and by means of the circumferential one Weld 31 is connected to this.
  • the at least one disc heel 39 on the z. B. 0.15 mm thick bottom portion 20 of the spray plate 21 is preferably annular and has about the same dimensions as the body heel 18 in the first embodiment.
  • a thermal decoupling is also used again by means of the disk shoulder 39 Valve seat body and spray orifice plate and thus throttling the heat transfer achieved.
  • the position of the disc shoulder 39 can be selected in a suitable manner between a position in the vicinity of the outflow opening 32 of the valve seat body 16 and a position in the vicinity of the diameter of the spray orifice plate.
  • Valve seat body 16 and also a disk shoulder 39 on the bottom part 20 of the spray hole disk 21 is used, the disk shoulder 39 abutting the body shoulder 18 and being tightly connected to it by means of the circumferential weld seam 31.
  • the lower end face 17 of the valve seat body 16 is of flat design, and no elevation is provided on the upper end face 19 of the spray orifice plate 21 either.
  • At least one transition element designed as a separate, thermally insulating insulating body 41 is arranged between the valve seat body 16 and the spray hole disk 21, which reduces the heat transfer between the valve seat body and the spray hole disk, as a result of which vapor bubbles form in the collecting space 37 or on the spray holes 25 is reduced or avoided entirely.
  • Valve seat body 16 can either be pressed into the longitudinal opening 3 of the valve housing 1 with a press fit, as shown in FIG. 5, or the valve seat body 16 is adjusted on the lower end face 17 by means of a weld 43 shown in FIGS. 4 and 6 fixed between valve seat body 16 and valve housing 1.
  • Plastic, rubber, glass, ceramic or another insulating material can serve as the material for the insulating body 41.
  • the insulating body 41 has a flat disk shape with a through hole 45 connecting the outflow opening 32 to the central region 24 of the base part 20.
  • a groove 47 is formed in the region of the lower end face 17 of the valve seat body 16 in the valve housing 1, which in this embodiment extends in the axial direction parallel to the valve longitudinal axis 2 only to the extent that it does not extend to the end 27 of the Retaining edge 26 of the spray perforated disk 21 is sufficient so that the end 27 abuts the wall of the longitudinal opening 3 and can be welded to it by means of the weld seam 30.
  • the pot-shaped insulating body 41 engages in the groove 47 with one
  • the insulating body 41 according to FIG. 5 can be made of plastic, for example, and can be produced by direct injection molding in the longitudinal opening 3. Subsequently, the spray orifice plate 21 is inserted into the longitudinal opening 3 and welded by means of the weld seam 30.
  • the insulating body 41 is also cup-shaped, and the groove 47 and the cylinder edge 49 extend from the valve seat body 16 in the axial direction over the end 27 of the spray plate 21 so that the
  • Splash plate 21 is completely surrounded by the insulating body 41, except in its central region 24 on its outer surface.
  • the end 27 of the spray plate 21st claws when inserting the spray perforated disk into the cylinder edge 49 of the insulating body 41.
  • the insulating body 41 according to the exemplary embodiment according to FIG. 6 can also be produced by plastic injection molding.
  • a recessed step 52 is worked into the upper end face 19 of the base part 20, for example embossed, which surrounds the central area 24 with the at least one spray hole 25 with a larger diameter, so that starting from step 52 to to the periphery of the bottom part 20 of the disc shoulder 39 is formed, which rests on the lower end face 17 of the valve seat body 16.
  • a deep indentation 53 is worked into the upper end face 19 of the base part 20, for example embossed, which surrounds the central region 24 with the at least one injection hole 25 with a larger diameter, so that the indentation 53 extends from to to the extent of
  • the heat flow to the central area 24 is reduced by the formation of the body portion 18 or the disk shoulder 39 and the cross section of the spray disk 21, for example, which is only 0.15 mm thick and thus the risk of vapor bubble formation is reduced.
  • Spray-hole disks are suitable, but they also apply to spray-jet disks that are only very flat.

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

Dans les soupapes d'injection connues, le carburant s'évapore en amont du disque perforé d'injection et au niveau des orifices d'injection lorsque le moteur à combustion interne est chaud, notamment au démarrage ou en marche à vide à chaud, ce qui affecte de manière indésirable la marche du moteur, car celui-ci n'est pas suffisamment alimenté en carburant. L'objet de l'invention est d'améliorer la marche du moteur à combustion interne en évitant la formation de bulles de vapeur. En façonnant un épaulement (18) sur le corps (16) du siège de soupape, on obtient un élément de transition qui réduit le transfert de chaleur entre le corps (16) du siège de soupape et le disque perforé d'injection (21). Le disque perforé d'injection se refroidit ainsi, étant donné que la chaleur d'évaporation du carburant injectée est soutirée, ce qui réduit le risque de formation de bulles de vapeur au niveau ou en amont des orifices d'injection (25). Cette soupape d'injection de carburant est particulièrement utile dans des systèmes d'injection de carburant de moteurs à combustion interne à compression du mélange et à allumage à étincelles.
EP96900279A 1995-02-02 1996-01-17 Soupape d'injection de carburant pour moteurs a combustion interne Expired - Lifetime EP0774069B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19503269 1995-02-02
DE19503269A DE19503269A1 (de) 1995-02-02 1995-02-02 Brennstoffeinspritzventil für Brennkraftmaschinen
PCT/DE1996/000053 WO1996023968A1 (fr) 1995-02-02 1996-01-17 Soupape d'injection de carburant pour moteurs a combustion interne

Publications (2)

Publication Number Publication Date
EP0774069A1 true EP0774069A1 (fr) 1997-05-21
EP0774069B1 EP0774069B1 (fr) 2001-09-26

Family

ID=7752928

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96900279A Expired - Lifetime EP0774069B1 (fr) 1995-02-02 1996-01-17 Soupape d'injection de carburant pour moteurs a combustion interne

Country Status (10)

Country Link
US (1) US5862991A (fr)
EP (1) EP0774069B1 (fr)
JP (1) JP3625838B2 (fr)
KR (1) KR100441813B1 (fr)
CN (1) CN1062335C (fr)
BR (1) BR9605297A (fr)
DE (2) DE19503269A1 (fr)
ES (1) ES2164862T3 (fr)
RU (1) RU2151905C1 (fr)
WO (1) WO1996023968A1 (fr)

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Also Published As

Publication number Publication date
BR9605297A (pt) 1997-09-16
CN1062335C (zh) 2001-02-21
US5862991A (en) 1999-01-26
RU2151905C1 (ru) 2000-06-27
DE19503269A1 (de) 1996-08-08
CN1145655A (zh) 1997-03-19
EP0774069B1 (fr) 2001-09-26
KR970702431A (ko) 1997-05-13
WO1996023968A1 (fr) 1996-08-08
JPH09511308A (ja) 1997-11-11
ES2164862T3 (es) 2002-03-01
JP3625838B2 (ja) 2005-03-02
KR100441813B1 (ko) 2004-11-08
DE59607762D1 (de) 2001-10-31

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