EP0310607A1 - Soupape d'injection de carburant. - Google Patents

Soupape d'injection de carburant.

Info

Publication number
EP0310607A1
EP0310607A1 EP87903254A EP87903254A EP0310607A1 EP 0310607 A1 EP0310607 A1 EP 0310607A1 EP 87903254 A EP87903254 A EP 87903254A EP 87903254 A EP87903254 A EP 87903254A EP 0310607 A1 EP0310607 A1 EP 0310607A1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
valve
nozzle body
section
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
EP87903254A
Other languages
German (de)
English (en)
Other versions
EP0310607B1 (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 AT87903254T priority Critical patent/ATE62323T1/de
Publication of EP0310607A1 publication Critical patent/EP0310607A1/fr
Application granted granted Critical
Publication of EP0310607B1 publication Critical patent/EP0310607B1/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
    • 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 is based on a fuel injection valve according to the preamble of claims 1 or 6.
  • Known fuel injectors working with a valve needle as a closure part have a conical sealing seat at the tip of the valve needle, which in cooperation with a likewise conical valve seat surface releases a flow opening for the fuel or closes.
  • Such a fuel injector for example described in DE-OS 35 02 410, has the disadvantage that burrs can arise when grinding the sealing surfaces of the valve needle, which deteriorates the sealing effect and the quality of the flow. If these burrs are removed afterwards, shape errors and edge damage to the sealing seat can occur.
  • a 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 treatment sleeve.
  • the disadvantage of this fuel injection valve is that the fuel jets generated by the perforated disc hit the inner wall of the processing sleeve at a very steep angle. In addition, the point of impact is far above the end of the processing sleeve.
  • the fuel "screws" along the inner wall of the preparation sleeve at the end of the spray, the spray takes place in the form of a cone.
  • the liquid droplets sprayed off 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 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” from the valve seat to the perforated disc, but can collect in different dead spaces. This increases the time between lifting the valve part from the valve seat and spraying fuel from the bores, the valve works with a delay.
  • the fuel injection valve according to the invention with the characterizing features of claims 1 or 6, in contrast, has the advantage of easy and precise manufacture, burrs and other impurities which impair the flow are avoided.
  • 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. Since hydraulic sticking of the valve needle to the valve seat surface is largely avoided, the fuel injection valve operates with a short opening time.
  • 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 treatment 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. Due to the annular space formed between the pin and the nozzle body, the fuel flow is calmed and led to the bores without annoying dead spaces. Flow optimization is also possible by machining the valve needle in the area between the valve seat and the pin, for example by using radii instead of angular transitions. In practice, this leads to a reduced response time of the fuel injection valve between the lifting of the valve needle from the valve seat and spraying fuel out of the holes. Executing the pin as part of the valve needle and not as part of the plate offers manufacturing advantages.
  • 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
  • Figure 3 in the form of two half-cuts two different embodiments of the valve needle in the area of the sealing seat.
  • 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 magnet coil 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 slight 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.
  • the cylindrical armature 14 is provided 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 with 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 bore tion 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 larger 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 a 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 is approximately 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 project 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 by a bottom 60 of a coaxial blind bore 61 of the processing sleeve 58 encompassing 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 lies 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 plate 55 is clamped between the nozzle body 9 and the treatment sleeve 58 by screwing the treatment sleeve 58 with an internal thread 64 onto an external thread 65 incorporated 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 outer 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 processing sleeve 58 can at the same time serve to axially secure a sealing ring 69 radially surrounding 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 processing edge 71 is formed by the acute angle between the inclined inner wall 74 of the annular groove 73 and the processing 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 the furthest in the direction facing away from the armature 14.
  • the collar 77 surrounds the preparation edge 71 and at the same time projects 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 °.
  • valve needle 27 in the area of the sealing seat 47 is shown in FIG. 3.
  • the part of the valve needle 27 which causes the opening and closing of the injection valve together with the conical valve seat surface 48 is designed as a curve 90, via which 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 curve 90 and also the transition from the curve 90 to the conical section 44 take place, viewed in the direction of the flow, preferably tangentially.
  • the contour of the curve 90 can, as shown in the left half section of FIG. 3, be formed by a radius R. If one imagines the radius R describing the rounding 90 expanded to form a circle 93 (shown in broken lines), then all the circles 93 forming the sealing seat 47 together represent a torus 94.
  • the right half section of FIG. 3 shows a second exemplary embodiment.
  • the curve 90 follows the contour of an imaginary ellipse 96.
  • the arrangement of the ellipse 96 is selected such that the longer two ellipse radius a, b extends in the axial direction of the injection valve.
  • the curve 90 can also follow any other contour which cannot be described by a radius R or by a radius a, b, but which overall forms a torus.
  • the rounding 90 is preferably produced by appropriate grinding of the valve needle 27 rotating about its longitudinal axis.
  • the grinding of the entire tip of the valve needle 27 from the cylindrical section 43 to the pin 45 can be carried out in a single machining step.
  • 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 individual droplets of fuel are torn open and atomized by the high kinetic energy when they strike the processing bore 70. The result of this is that a fuel mist leaves the fuel injection valve downstream of the processing edge 71. This fuel mist allows good mixing with the intake air of the internal combustion engine.
  • the annular groove 73 surrounding the preparation edge 71 has 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, have a much lower tendency 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 thickness of the plate 55 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.
  • Fuel injection valve which serves for injeeting fuel into the admission passage of a mixture-compressing, externally-ignited infernal combustion engine.
  • the fuel injection valve is provided with a valve needle (27) which, by means of an armature linked therewith, is drawn against a core when a magnetic coil is excited, the valve needle (27) rising, together with a sealing seating (47) formed thereon, from a valve seating surface (48) formed on a nozzle body (9).
  • the sealing seating (47) is designed with a rounded profile (90), the contour of which follows the external envelope of an imaginary torus (94).
  • the cross-section of the torus (94) can for example, be circular (93) or elliptical (96).
  • valve needle (27) In view of the comparatively small radius of the rounded profile (90), which leads to a distinctly line-like contact between the valve needle (27) and the valve seating surface (48), the tendency of the valve needle (27) to "ad- here" hydraulically to the valve seating surface (48) is much smaller than in conventional fuel injection valves.
  • Fuel injection valve which is used to inject fuel into the intake tract of a mixture-compression-ignition internal combustion engine.
  • the fuel injection valve has a valve needle (27) which is pulled against a core by an armature connected to it when a magnetic coil is excited, the Ven needle (27) having a sealing seat (47) formed thereon from one to a nozzle body (9 ) trained valve seat surface (48).
  • the sealing seat (47) is designed as a curve (90), the contour of which follows the outer lateral surface of a roofed torus (94).
  • the torus (94) can have, for example, the cross section of a circle (93) or the cross section of an ellipse (96).
  • valve needle (27) Due to the comparatively small radius of the rounding (90), which leads to a pronounced lini-shaped contact between the valve needle (27) and valve seat surface (48), the tendency of the valve needle (27) to drastically “stick” to the valve seat surface (48) is wide less than with conventional fuel injection valves.

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

Soupape d'injection de carburant servant à injecter du carburant dans le passage d'admission d'un moteur à combustion interne à compression de mélange et à allumage externe. La soupape d'injection de carburant comporte un pointeau (27) qui, au moyen d'un induit auquel il est relié, est attiré contre un noyau lorsqu'une bobine magnétique est excitée, le pointeau (27) se soulevant, conjointement avec un siège d'étanchéité (47) formé sur lui, depuis une surface (48) de siège de soupape formée sur un corps (9) de gicleur. Le siège d'étanchéité (47) se présente sous la forme d'un arrondi (90) dont le contour épouse la surface de l'enveloppe externe d'un tore imaginaire (94). La section du tore (94) peut par exemple être circulaire ou elliptique (96). Grâce au rayon comparativement faible de l'arrondi (90), ce qui se traduit par un contact en forme de ligne très marqué entre le pointeau (27) et la surface (48) de siège de soupape, la tendance du pointeau (27) à ''adhérer'' hydrauliquement à la surface (48) de siège de soupape est bien moindre que dans les soupapes d'injection de carburant classiques.
EP19870903254 1986-05-31 1987-05-27 Soupape d'injection de carburant Expired - Lifetime EP0310607B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT87903254T ATE62323T1 (de) 1986-05-31 1987-05-27 Kraftstoffeinspritzventil.

Applications Claiming Priority (4)

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

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP90103656.6 Division-Into 1990-02-26

Publications (2)

Publication Number Publication Date
EP0310607A1 true EP0310607A1 (fr) 1989-04-12
EP0310607B1 EP0310607B1 (fr) 1991-04-03

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 Before (1)

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

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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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
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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
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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
EP0393328B1 (fr) 1993-11-10
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
BR8707711A (pt) 1989-10-31

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