EP0393328B1 - Soupape d'injection de combustible - Google Patents

Soupape d'injection de combustible Download PDF

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Publication number
EP0393328B1
EP0393328B1 EP90103656A EP90103656A EP0393328B1 EP 0393328 B1 EP0393328 B1 EP 0393328B1 EP 90103656 A EP90103656 A EP 90103656A EP 90103656 A EP90103656 A EP 90103656A EP 0393328 B1 EP0393328 B1 EP 0393328B1
Authority
EP
European Patent Office
Prior art keywords
nozzle body
fuel injection
valve
injection valve
pintle
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.)
Expired - Lifetime
Application number
EP90103656A
Other languages
German (de)
English (en)
Other versions
EP0393328A1 (fr
Inventor
Waldemar Hans
Wilhelm Kind
Manfred Kirchner
Siegfried Werner
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
Priority claimed from DE3710467A external-priority patent/DE3710467C2/de
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP90103656A priority Critical patent/EP0393328B1/fr
Priority to AT90103656T priority patent/ATE97193T1/de
Publication of EP0393328A1 publication Critical patent/EP0393328A1/fr
Application granted granted Critical
Publication of EP0393328B1 publication Critical patent/EP0393328B1/fr
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
    • F02M61/188—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
    • F02M51/0675—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 the valve body having cylindrical guiding or metering portions, e.g. with fuel passages
    • F02M51/0678—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 the valve body having cylindrical guiding or metering portions, e.g. with fuel passages all portions having fuel passages, e.g. flats, grooves, diameter reductions
    • 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
    • F02M51/08—Injectors peculiar thereto with means directly operating the valve needle specially for low-pressure fuel-injection
    • 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
    • F02M61/06—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 the valves being furnished at seated ends with pintle or plug shaped extensions
    • 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
    • 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 relates to a fuel injection valve according to the preamble of claim 1.
  • a generic fuel injection valve is known (DE-OS 33 01 501), in which a perforated disk is located downstream of the valve seat to improve the sprayed fuel jet. The holes are injected into this perforated disc and the fuel is sprayed onto the inner wall of a processing sleeve. The actual injection end of such a fuel injection valve forms an end collar of the processing sleeve.
  • a disadvantage of this fuel injection valve is that the fuel jets generated by the perforated disk hit the inner wall of the processing sleeve at a very steep angle. In addition, the point of impact is far above the spray end of the processing sleeve. The fuel “screws" along the inner wall of the processing sleeve towards the end of the spray, and the spray takes the form of a cone. The sprayed liquid droplets are relatively large, which makes it difficult to form an optimal fuel-air mixture.
  • a pin which, forming part of the perforated disk, partially projects into the valve needle body for guiding it and which forms an annular channel towards the nozzle body.
  • this ring channel is not advantageously designed in terms of flow.
  • the fuel is not “led” to the perforated disc coming from the valve seat, but can collect in various dead spaces, especially in the blind hole of the valve needle body, into which the pin protrudes. This increases the time between lifting the valve part from the valve seat and spraying fuel out of the holes, because these dead spaces have to be filled up first, the valve works with a delay. After the fuel injection valve has been closed, there is the disadvantage due to these large dead spaces that fuel is sucked out of these dead spaces through the holes in the perforated disk in an undesirable manner, that is to say the valve “diesels”.
  • valve needle jumps from a closing cone into a throttle pin, which merges into a nozzle body opening formed downstream of the valve seat to form an annular channel and partially covers holes in a plate near which it ends.
  • the valve needle opens, the throttle pin is completely pulled out of the nozzle body opening after a throttling intermediate position, so that a very large dead space is formed and no flow-guiding function is effective anymore.
  • an injection nozzle for diesel gates is known (DE-B-12 12 352), the valve needle of which ends in a rounded cone, which forms an annular space with a nozzle body outlet channel, from which injection bores originate.
  • a fuel injection valve in which the valve needle has a conical section upstream of the pin ( Figure 3) and the transition between the conical section and the pin is rounded and in which the valve seat surface is downstream into one Nozzle surrounding the nozzle passes over and the transition between the valve seat surface and the nozzle body opening is rounded.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over the other hand of ensuring a good flow pattern.
  • the smooth surface contour of the valve needle and valve seat surface results in a very good correlation between the stroke of the valve needle and the outflowing amount of fuel.
  • a particularly good atomization of the fuel is made possible if it is sprayed through several holes in a thin plate clamped between the nozzle body and a processing sleeve.
  • This plate is easy and inexpensive to manufacture, it can also be deep-drawn into a shape that enables reliable centering.
  • valve needle It is advantageous to provide on the valve needle a pin that extends almost to the plate.
  • the fuel flow is calmed by the annular space formed between the pin and the nozzle body and is guided to the bores without annoying dead spaces.
  • a flow optimization is also possible by appropriate processing of the valve needle in the area between the valve seat and pin, for example by using radii instead of angular transitions. This leads to in practice to a reduced response time of the fuel injector between the lifting of the valve needle from the valve seat and the spraying of fuel from the bores. Executing the spigot as part of the valve needle and not as part of the plate offers manufacturing advantages, leads to the avoidance of undesired dead spaces and enables gradual, rounded transitions to calm the flow.
  • Figure 1 shows an advantageous embodiment of the fuel injection valve according to the invention
  • Figure 2 shows a detail of Figure 1 on an enlarged scale.
  • the fuel injection valve shown in the drawing for example, for a fuel injection system of a mixture-compressing, spark-ignition internal combustion engine has a valve housing 1 made of ferromagnetic material, in which a magnet coil 3 is arranged on a coil carrier 2.
  • the solenoid 3 has a power supply via a plug connection 4 which is embedded in a plastic ring 5 which partially encompasses the valve housing 1.
  • the coil carrier 2 of the magnet coil 3 is seated in a coil space 6 of the valve housing 1 on a connecting piece 7 which supplies the fuel, for example gasoline, and which projects partially into the valve housing 1.
  • the valve housing 1 partially encloses a nozzle body 9 facing away from the fuel nozzle 7.
  • a cylindrical armature 14 is located between an end face 11 of the connection piece 7 and a stop plate 12, which has a certain thickness and which is placed on an inner shoulder 13 of the valve housing 1, for precise adjustment of the valve.
  • the armature 14 is made of a non-corrosion-sensitive, magnetic material and is located at a small radial distance from a magnetically conductive shoulder of the valve housing 1, thus forming an annular magnetic gap between the armature 14 and shoulder, coaxially in the valve housing 1. From its two end faces is the cylindrical armature 14 with a first 15 and one second 16 coaxial blind bore, the second blind bore 16 opening towards the nozzle body 9. First 15 and second 16 blind holes are connected to one another by a coaxial opening 17.
  • the diameter of the opening 17 is smaller than the diameter of the second blind bore 16.
  • the end section of the armature 14 facing the nozzle body 9 is designed as a deformation region 18.
  • This deformation region 18 has the task of positively connecting the armature 14 to the valve needle 27 by gripping around a holding body 28 which forms part of a valve needle 27 and fills the second blind bore 16.
  • the gripping of the holding body 28 by the deformation area 18 of the armature 14 is achieved by pressing material of the deformation area 18 into grooves 29 located on the holding body 28.
  • a compression spring 30 At the bottom of the first coaxial blind bore 15 is a compression spring 30 at one end, which on the other hand rests against a pipe insert 31 fastened in the connecting piece 7 by screwing or caulking and which tends to anchor 14 and valve needle 27 with a force facing away from the connecting piece 7 act upon.
  • the valve needle 27 penetrates a through hole 34 in the stop plate 12 at a radial distance and is in a guide hole 35 of the nozzle body 9 out.
  • a recess 37 Provided in the stop plate 12 is a recess 37 leading from the through hole 34 to the circumference of the stop plate 12, the clear width of which is greater than the diameter of the valve needle 27 in its area surrounded by the stop plate 12.
  • the valve needle 27 has two guide sections 39 and 40, which give guidance to the valve needle 27 in the guide bore 35 and also leave an axial passage for the fuel and are designed, for example, as a square.
  • a cylindrical section 43 of smaller diameter adjoins the downstream second guide section 40.
  • a tapered, conical section 44 joins the cylindrical section 43, which ends in a coaxial, preferably cylindrical pin 45.
  • FIG. 2 which shows a detail from FIG. 1, it can be seen that the transition between the cylindrical section 43 and the conical section 44 is rounded - for example in the form of a radius - and forms a sealing seat 47 which, in cooperation with one on the nozzle body 9 incorporated conical valve seat surface 48 causes an opening or closing of the fuel injector.
  • the tapered valve seat surface 48 of the nozzle body 9 continues in the direction facing away from the armature 14 in a cylindrical nozzle body opening 49, which extends approximately at the same length as the length of the pin 45, so that an annular gap between the cylindrical nozzle body opening 49 and the cylindrical pin 45 constant cross section remains.
  • the transitions between the conical valve seat surface 48 on the one hand and the cylindrical nozzle body opening 49 on the other hand and the conical section 44 of the valve needle 27 on the one hand and the pin 45 on the other hand are rounded in order to ensure a good flow pattern.
  • the completion of the Nozzle body 9 in the direction facing away from armature 14 forms a flat side 51 which is interrupted by the mouth of nozzle body opening 49.
  • the length of the pin 45 is dimensioned such that when the fuel injection valve is closed, the pin 45 does not protrude from the nozzle body opening 49, i.e. the pin 45 ends immediately in front of the plane defined by the flat side 51 of the nozzle body 9.
  • the flat side 51 of the nozzle body 9 is delimited on the inside by the nozzle body opening 49, it can be delimited on the outside by a conical region 52 which widens in the direction facing the armature 14.
  • a plate 55 On the flat side 51 of the nozzle body 9 there is a plate 55 which has a raised edge 56 which roughly follows the contour of the conical area 52 of the nozzle body 9.
  • the edge 56 on the plate 55 can be produced, for example, by deep drawing the plate 55.
  • the attachment of the plate 55 on the flat side 51 is ensured by a processing sleeve 58.
  • the plate 55 is pressed against the flat side 51 in that a bottom 60 of a coaxial blind bore 61 of the processing sleeve 58 surrounds the plate 55 in its outer region. The plate 55 is thus clamped between the bottom 60 of the blind bore 61 of the processing sleeve 58 and the flat side 51 of the nozzle body 9.
  • the centering of the plate 55 is achieved in that the edge 56 of the plate 55 bears against the conical region 52 of the nozzle body 9, the plate 55 thus no longer having any radial play.
  • a particularly good centering of the plate 55 can be achieved if the edge 56 of the plate 55 widens when pushed onto the conical area 52, that is to say a radial clamping is carried out.
  • the clamping of the plate 55 between the nozzle body 9 and the processing sleeve 58 is realized by screwing the processing sleeve 58 with an internal thread 64 onto an external thread 65 machined on the circumference of the nozzle body 9.
  • the processing sleeve 58 can be caulked in an outer groove 68 of the nozzle body 9 by means of a caulking lug 66.
  • the edge of the processing sleeve 58 facing the anchor 14 is used as the caulking nose 66. For caulking, this is bent inwards into the outer groove 68 of the nozzle body 9.
  • the lateral surface of the blind bore 61 extends between the edge forming the caulking lug 66 and the bottom 60 of the processing sleeve 58, which is formed by the internal thread 64 over almost its entire length.
  • Internal thread 64 and external thread 65 are preferably designed as fine threads.
  • the preparation sleeve 58 can at the same time serve to axially secure a sealing ring 69 which radially surrounds the nozzle body 9, as shown in FIG. 1.
  • a reprocessing bore 70 of preferably cylindrical cross section opens coaxially in the bottom 60 of the reprocessing sleeve 58, which on the other hand ends in a sharp reprocessing edge 71.
  • the preparation edge 71 is surrounded by an annular groove 73.
  • the cross section of the annular groove 73 is approximately trapezoidal in the exemplary embodiment shown, ie both an inner wall 74 of the annular groove 73 and an outer wall 75 of the annular groove 73 are oblique.
  • the preparation edge 71 is formed by the acute angle between the inclined inner wall 74 of the annular groove 73 and the preparation bore 70. This angle should be between 10 and 20 °.
  • the outer wall 75 of the annular groove 73 simultaneously forms the inner surface of a collar 77.
  • the collar 77 represents the part of the fuel injector which protrudes furthest in the direction facing away from the armature 14.
  • the collar 77 surrounds the preparation edge 71 and at the same time protrudes beyond it. Checking the collar 77 is to secure the set-back conditioning edge 71 against damage, for example during assembly of the fuel injection valve on an internal combustion engine.
  • the bores 80 There are several bores 80 in the plate 55, which lead from upstream to downstream of the plate 55. Upstream of the plate 55, the bores 80 open into the annular space formed between the nozzle body opening 49 and the pin 45.
  • the bores 80 are directed with their central axis 81 directly onto the preparation edge 71 or just upstream thereof. With respect to the longitudinal axis of the fuel injection valve, the central axis 81 of the bores 80 has both a radial and a tangential component. It is crucial that the angle formed between the central axes 81 of the bores 80 and the lateral surface of the processing bore 70 runs very flat, that is to say the fuel jets emerging from the bores 80 hit the processing bore 70 very flat. This impact angle should be less than 10 °.
  • the shape of the valve needle 27 in the area of the sealing seat 47 is designed as a curve. Via the sealing seat 47 of the valve needle 27 which causes the opening and closing of the injection valve together with the conical valve seat surface 48, the cylindrical section 43 of the valve needle 27 continuously merges into the conical section 44. Both the transition from the cylindrical section 43 to the rounding and the transition from the rounding to the conical section 44 are preferably tangential when viewed in the direction of the flow.
  • the function of the fuel injector is as follows:
  • the armature 14 When current flows through the magnet coil 3, the armature 14 is pulled in the direction of the connecting piece 7.
  • the valve needle 27, which is fixedly connected to the armature 14, lifts with its sealing seat 47 from the conical valve seat surface 48; a flow cross section is released between the sealing seat 47 and the conical valve seat surface 48, and the fuel can pass through the annular space between the nozzle body opening 49 and the pin 45 to the bores 80 reach.
  • the bores 80 are flowed through by the fuel under a high pressure drop, since these form the narrowest flow cross section within the fuel injection valve. The size of the bores 80 thus decides on the mass flow of the sprayed-off fuel.
  • the fuel jet emerging from the bores 80 is directed onto the processing bore 70 in such a way that it strikes the processing edge 71 just upstream or directly.
  • the impact speed is so great that one can speak of a "bounce”.
  • the annular groove 73 surrounding the preparation edge 71 offers the advantage that fuel particles which may have accumulated on the inner wall 74 of the annular groove 73 are entrained by a secondary vortex within the annular groove 73 to the preparation edge 71 and are also sprayed there.
  • Fuel injection valves, which have the annular groove 73 designed according to the invention, are far less likely to drip than fuel injection valves without the annular groove 73. The causes which are decisive for this effect are still largely unclear.
  • a very good fuel preparation is achieved with the fuel injection valve according to the invention.
  • the best results are achieved with a plate 55 thickness of 0.3 mm if the diameter of the processing bore 70 is 2.2 mm and the length 5 mm.
  • the diameter of the bores 80 depends on the respective application, it is in the range between 0.15 and 0.35 mm.

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  • 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)

Claims (7)

  1. Injecteur pour des installations d'injection de carburant de moteurs thermiques comportant un corps de valve (1) en matière ferromagnétique et une bobine (7) entourant d'un enroulement d'électroaimant (3) ainsi qu'un induit (14) coopérant avec l'enroulement (7) (noyau), cet induit étant solidaire d'une aiguille d'injecteur (27) qui en coopérant avec une surface de siège de soupape (48) réalisée dans le corps (9) de l'injecteur commande l'ouverture et la fermeture de l'injecteur ainsi qu'une ouverture (49) dans le corps d'un injecteur en aval de la surface formant le siège de soupape (48) et une plaquette (55) munie de perçages (80) placée entre le corps d'injecteur (9) et un manchon de préparation (58) du mélange, cette plaquette étant disposée en travers de l'ouverture (49) du corps d'injecteur, le manchon de préparation (58) ayant un perçage de préparation (70) central se terminant par une arête (71), injecteur caractérisé en ce que l'aiguille (27) se termine par un téton (45) cylindrique qui, pendant le mouvement d'ouverture de l'aiguille (27), forme avec l'ouverture (49) du corps d'injecteur un volume annulaire de section constante, et en aval, dans son prolongement axial, se trouvent les perçages (80) de la plaquette (55) occupant toute la section et la transition vers le téton (45) est arrondie.
  2. Injecteur selon la revendication 1, caractérisé en ce que le téton (45) se termine au voisinage immédiat de la plaquette (55) lorsque l'injecteur est fermé.
  3. Injecteur selon la revendication 1, caractérisé en ce qu'en amont du téton (45) l'aiguille (27) comporte un segment conique (44) et la transition entre le segment conique (44) et le téton (45) est arrondie.
  4. Injecteur selon la revendication 3, caractérisé en ce que la surface formant siège (48) se poursuit en aval par une ouverture de corps de buse (49) entourant le téton (45) et la transition entre la surface de siège (48) et l'ouverture de corps d'injecteur (49) est arrondie.
  5. Injecteur selon la revendication 1, caractérisé en ce que les lignes centrales imaginaires (81) des perçages (80) de la plaquette (55) coupent la surface-enveloppe du perçage de préparation (70) du mélange sur l'arête (71) de ce perçage de préparation (70) ou légèrement en amont.
  6. Injecteur selon la revendication 1, caractérisé en ce que la plaquette (55) comporte un bord (56) qui s'appuie contre une zone conique (52) du corps d'injecteur (9).
  7. Injecteur selon la revendication 6, caractérisé en ce que le manchon de préparation (58) du mélange est vissé sur le corps (9) de l'injecteur et une partie du manchon (58) est matée contre le corps d'injecteur (9).
EP90103656A 1986-05-31 1987-05-27 Soupape d'injection de combustible Expired - Lifetime EP0393328B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP90103656A EP0393328B1 (fr) 1986-05-31 1987-05-27 Soupape d'injection de combustible
AT90103656T ATE97193T1 (de) 1986-05-31 1990-02-26 Kraftstoffeinspritzventil.

Applications Claiming Priority (5)

Application Number Priority Date Filing Date Title
DE3618413 1986-05-31
DE3618413 1986-05-31
DE3710467 1987-03-30
DE3710467A DE3710467C2 (de) 1986-05-31 1987-03-30 Kraftstoffeinspritzventil
EP90103656A EP0393328B1 (fr) 1986-05-31 1987-05-27 Soupape d'injection de combustible

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP87903254.8 Division 1987-05-27

Publications (2)

Publication Number Publication Date
EP0393328A1 EP0393328A1 (fr) 1990-10-24
EP0393328B1 true EP0393328B1 (fr) 1993-11-10

Family

ID=25844272

Family Applications (2)

Application Number Title Priority Date Filing Date
EP90103656A Expired - Lifetime EP0393328B1 (fr) 1986-05-31 1987-05-27 Soupape d'injection de combustible
EP19870903254 Expired - Lifetime EP0310607B1 (fr) 1986-05-31 1987-05-27 Soupape d'injection de carburant

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP19870903254 Expired - Lifetime EP0310607B1 (fr) 1986-05-31 1987-05-27 Soupape d'injection de carburant

Country Status (8)

Country Link
US (2) US4934605A (fr)
EP (2) EP0393328B1 (fr)
JP (1) JP2553120B2 (fr)
AT (1) ATE97193T1 (fr)
AU (2) AU593914B2 (fr)
BR (1) BR8707711A (fr)
ES (1) ES2006151A6 (fr)
WO (1) WO1987007334A2 (fr)

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DE58902133D1 (de) * 1988-06-28 1992-10-01 Siemens Ag Elektromagnetisches kraftstoffeinspritzventil.
IT223984Z2 (it) * 1990-01-17 1995-10-05 Weber Srl Valvola di un dispositivo di alimentazione di un motore a combustione interna
IT1250845B (it) * 1991-10-11 1995-04-21 Weber Srl Valvola dosatrice e polverizzatrice di carburante ad azionamento elettromagnetico per un dispositivo di alimentazione di un motore endotermico
DE4141930B4 (de) * 1991-12-19 2007-02-08 Robert Bosch Gmbh Elektromagnetisch betätigbares Einspritzventil
EP0636210B1 (fr) * 1992-04-01 1996-12-11 Siemens Automotive Corporation Siege de soupape d'injection a piege de remise en circulation
JP3085008B2 (ja) * 1993-03-12 2000-09-04 株式会社デンソー 流体噴射弁
US5651501A (en) * 1993-12-23 1997-07-29 Caterpillar Inc. Fluid damping of a valve assembly
JP2660388B2 (ja) * 1993-12-29 1997-10-08 株式会社ケーヒン 電磁式燃料噴射弁
JP3440534B2 (ja) * 1994-03-03 2003-08-25 株式会社デンソー 流体噴射ノズル
CN1168712A (zh) * 1994-10-17 1997-12-24 美国西门子汽车公司 减少油流，特别是偏离轴线油流弥散的燃油喷射器
JP3183156B2 (ja) * 1995-04-27 2001-07-03 株式会社デンソー 流体噴射ノズル
JP3156554B2 (ja) * 1995-07-24 2001-04-16 トヨタ自動車株式会社 燃料噴射弁
DE19545333A1 (de) * 1995-12-05 1997-06-12 Bosch Gmbh Robert Ventilschließkörper und Verfahren und Vorrichtung zur Herstellung von Dichtsitzen an Ventilschließkörpern
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US4934605A (en) 1990-06-19
AU607871B2 (en) 1991-03-14
AU7435987A (en) 1987-12-22
WO1987007334A3 (fr) 1987-12-30
JPH01502766A (ja) 1989-09-21
WO1987007334A2 (fr) 1987-12-03
AU4548889A (en) 1990-03-08
JP2553120B2 (ja) 1996-11-13
US5016821A (en) 1991-05-21
ATE97193T1 (de) 1993-11-15
ES2006151A6 (es) 1989-04-16
EP0310607B1 (fr) 1991-04-03
EP0393328A1 (fr) 1990-10-24
AU593914B2 (en) 1990-02-22
EP0310607A1 (fr) 1989-04-12
BR8707711A (pt) 1989-10-31

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