EP0393328B1 - Fuel injection valve - Google Patents

Fuel injection valve 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
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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)
French (fr)
Other versions
EP0393328A1 (en
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/en
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Priority to EP90103656A priority Critical patent/EP0393328B1/en
Priority to AT90103656T priority patent/ATE97193T1/en
Publication of EP0393328A1 publication Critical patent/EP0393328A1/en
Application granted granted Critical
Publication of EP0393328B1 publication Critical patent/EP0393328B1/en
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.

Abstract

The fuel injection valve has a ferromagnetic valve housing containing a magnetic coil surrounding a core to which the valve armature is attached. The valve armature supports a valve needle (27) cooperating with an annular valve seat (48). The seal between the valve needle (27) and the valve seat (48) is provided by a rounded surface (90) defined by a toroid (94) with a circular or elliptical cross-section in the outer surface of the valve needle (27). Oref. the toroid (94) has an elliptical cross-section with its major axis parallel to the longitudinal axis of the valve needle (27).

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einem Kraftstoffeinspritzventil nach der Gattung des Patentanspruches 1.The invention relates to a fuel injection valve according to the preamble of claim 1.

Es ist ein gattungsmäßiges Kraftstoffeinspritzventil bekannt (DE-OS 33 01 501), bei dem sich zur Verbesserung des abgespritzten Brennstoffstrahles stromabwärts des Ventilsitzes eine Lochscheibe befindet. Durch in dieser Lochscheibe eingearbeitete Bohrungen wird der Kraftstoff auf die Innenwand einer Aufbereitungshülse gespritzt. Das eigentliche Abspritzende eines solchen Kraftstoffeinspritzventiles bildet ein Abschlußkragen der Aufbereitungshülse. Nachteilig ist bei diesem Kraftstoffeinspritzventil, daß die von der Lochscheibe erzeugten Kraftstoffstrahlen unter einem sehr steilen Winkel auf die Innenwand der Aufbereitungshülse treffen. Außerdem liegt der Auftreffpunkt weit oberhalb des Abspritzendes der Aufbereitungshülse. Der Kraftstoff "schraubt" sich entlang der Innenwand der Aufbereitungshülse zum Abspritzende, die Abspritzung erfolgt in Form eines Kegels. Die dabei abgespritzten Flüssigkeitströpfchen sind relativ groß, was die Bildung eines optimalen Kraftstoff-Luft-Gemisches erschwert.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.

Aus der DE-OS 33 01 501 ist auch ein Zapfen bekannt, welcher, einen Teil der Lochscheibe bildend, teilweise in den Ventilnadelkörper zu dessen Führung ragt und welcher zum Düsenkörper hin einen Ringkanal bildet. Dieser Ringkanal ist jedoch strömungstechnisch nicht vorteilhaft ausgebildet. Der Kraftstoff wird nicht, vom Ventilsitz kommend, zur Lochscheibe "geführt", sondern kann sich in verschiedenen Toträumen sammeln, insbesondere in der Sacklochbohrung des Ventilnadelkörpers, in die der Zapfen ragt. Dadurch verlängert sich die Zeitspanne zwischen dem Abheben des Ventilteils vom Ventilsitz und dem Abspritzen von Kraftstoff aus den Bohrungen, denn diese Toträume müssen zunächst aufgefüllt werden, das Ventil arbeitet mit Verzögerung. Nach dem Schließen des Kraftstoffeinspritzventiles besteht dann infolge dieser großen Toträume der Nachteil, daß aus diesen Toträumen in unerwünschter Weise Kraftstoff durch die Bohrungen der Lochscheibe abgesaugt wird, das Ventil also "nachdieselt".From DE-OS 33 01 501 a pin is also known 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. However, 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”.

Bekannt ist ebenfalls eine Einspritzdüse für Dieselmotoren (DE-B-10 46 950), bei der die Ventilnadel von einem Schließkegel sprunghaft in einen Drosselzapfen übergeht, der in eine stromabwärts des Ventilsitzes ausgebildete Düsenkörperöffnung unter Bildung eines Ringkanales übergeht und Bohrungen in einer Platte teilweise überdeckt, in deren Nähe er endet. Bei einer Öffnungsbewegung der Ventilnadel wird der Drosselzapfen nach einer drosselnden Zwischenstellung vollständig aus der Düsenkörperöffnung herausgezogen, so daß ein sehr großer Totraum gebildet und keinerlei strömungsleitende Funktion mehr wirksam wird.Also known is an injection nozzle for diesel engines (DE-B-10 46 950), in which the 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. When 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.

Weiterhin ist eine Einspritzdüse für Dieselmtoren bekannt (DE-B-12 12 352), deren Ventilnadel gerundet in einem Zapfen ausläuft, der mit einem Düsenkörperaustrittskanal einen Ringraum bildet, von dem Einspritzbohrungen ausgehen.Furthermore, 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.

Aus der GB-A-2 029 508 ist ein Kraftstoffeinspritzventil bekannt, bei dem die Ventilnadel stromaufwärts des Zapfens (Figur 3) einen kegeligen Abschnitt aufweist und der Übergang zwischen dem kegeligen Abschnitt und dem Zapfen gerundet ist und bei dem die Ventilsitzfläche stromabwärts in eine den Zapfen umgebende Düsenöffnung übergeht und der Übergang zwischen Ventilsitzfläche und Düsenkörperöffnung gerundet ist.From GB-A-2 029 508 a fuel injection valve is known 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.

Aus der GB-A-2 097 470 ist ein Kraftstoffeinspritzventil bekannt, bei dem die gedachten Mittelachsen der Bohrungen des Plättchens die Mantelfläche der Aufbereitungsbohrung knapp stromaufwärts der Kante der Aufbereitungsbohrung schneiden.From GB-A-2 097 470 a fuel injection valve is known, in which the imaginary central axes of the holes in the plate cut the lateral surface of the processing hole just upstream of the edge of the processing hole.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruches 1 hat demgegenüber den Vorteil einen guten Strömungsverlauf zu gewährleisten. Außerdem bewirkt die glatte Oberflächenkontur von Ventilnadel und Ventilsitzfläche eine sehr gute Korrelation zwischen dem Hub der Ventilnadel und der abströmenden Kraftstoffmenge.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. In addition, 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.

Vorteilhaft ist es insbesondere, auch die stromab des Dichtsitzes angeordneten Übergänge zu runden, um einen gleichmäßigen Kraftstofffluß vom Dichtsitz weg zu erreichen.It is particularly advantageous to also round the transitions arranged downstream of the sealing seat in order to achieve a uniform fuel flow away from the sealing seat.

Eine besonders gute Zerstäubung des Kraftstoffes wird ermöglicht, wenn dieser über mehrere Bohrungen in einem dünnen, zwischen Düsenkörper und einer Aufbereitungshülse eingespannten Plättchen abgespritzt wird. Dieses Plättchen ist leicht und preiswert herzustellen, es läßt sich außerdem durch Tiefziehen in eine Form bringen, welche eine zuverlässige Zentrierung ermöglicht.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.

Von Vorteil ist es, an der Ventilnadel einen bis knapp an das Plättchen reichenden Zapfen vorzusehen. Durch den zwischen Zapfen und Düsenkörper gebildeten Ringraum wird die Kraftstoffströmung beruhigt und ohne störende Toträume bis zu den Bohrungen geführt. Eine Strömungsoptimierung ist außerdem durch entsprechende Bearbeitung der Ventilnadel im Bereich zwischen Ventilsitz und Zapfen möglich, etwa durch Verwendung von Radien anstelle kantiger Übergänge. Dies führt in der Praxis zu einer verringerten Ansprechzeit des Kraftstoffeinspritzventils zwischen dem Abheben der Ventilnadel vom Ventilsitz und dem Abspritzen von Kraftstoff aus den Bohrungen. Den Zapfen als Teil der Ventilnadel auszuführen und nicht als Teil des Plättchens bietet fertigungstechnische Vorteile, führt zur Vermeidung unerwünschter Toträume und ermöglicht zur Strömungsberuhigung allmähliche, gerundete Übergänge.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.

Durch die in den weiteren Patentansprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen des in dem Patentanspruch 1 angegebenen Kraftstoffeinspritzventiles möglich.The measures listed in the further claims allow advantageous developments and improvements of the fuel injector specified in claim 1.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Figur 1 zeigt eine vorteilhafte Ausführungsform des erfindungsgemäßen Kraftstoffeinspritzventiles, Figur 2 einen Ausschnitt aus Figur 1 in vergrößertem Maßstab.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. 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.

Beschreibung des AusführungsbeispielesDescription of the embodiment

Das in der Zeichnung beispielsweise dargestellte Kraftstoffeinspritzventil für eine Kraftstoffeinspritzanlage einer gemischverdichtenden, fremdgezündeten Brennkraftmaschine hat ein Ventilgehäuse 1 aus ferromagnetischem Material, in dem auf einem Spulenträger 2 eine Magnetspule 3 angeordnet ist. Die Magnetspule 3 hat eine Stromzuführung über einen Steckanschluß 4, der in einem das Ventilgehäuse 1 teilweise umgreifenden Kunststoffring 5 eingebettet ist.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.

Der Spulenträger 2 der Magnetspule 3 sitzt in einem Spulenraum 6 des Ventilgehäuses 1 auf einem den Kraftstoff, beispielsweise Benzin, zuführenden Anschlußstutzen 7, der teilweise in das Ventilgehäuse 1 ragt. Das Ventilgehäuse 1 umschließt dem Kraftstoffstutzen 7 abgewandt teilweise einen Düsenkörper 9.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.

Zwischen einer Stirnfläche 11 des Anschlußstutzens 7 und einer zum genauen Einstellen des Ventils eine bestimmte Dicke aufweisenden Anschlagplatte 12, die auf eine Innenschulter 13 des Ventilgehäuses 1 aufgesetzt ist, befindet sich ein zylindrischer Anker 14. Der Anker 14 besteht aus einem nicht korrosionsanfälligen, magnetischen Material und befindet sich mit geringem radialen Abstand zu einem magnetisch leitfähigen Absatz des Ventilgehäuses 1, auf diese Weise zwischen Anker 14 und Absatz einen ringförmigen Magnetspalt bildend, koaxial im Ventilgehäuse 1. Von seinen beiden Stirnflächen aus ist der zylindrische Anker 14 mit einer ersten 15 und einer zweiten 16 koaxialen Sackbohrung versehen, wobei die zweite Sackbohrung 16 sich zum Düsenkörper 9 hin öffnet. Erste 15 und zweite 16 Sackbohrung sind miteinander durch eine koaxiale Öffnung 17 verbunden. Der Durchmesser der Öffnung 17 ist kleiner als der Durchmesser der zweiten Sackbohrung 16. Der dem Düsenkörper 9 zugewandte Endabschnitt des Ankers 14 ist als Verformungsbereich 18 ausgeführt. Dieser Verformungsbereich 18 hat die Aufgabe, durch Umgreifen eines, einen Teil einer Ventilnadel 27 bildenden und die zweite Sackbohrung 16 aussfüllenden Haltekörpers 28 den Anker 14 mit der Ventilnadel 27 formschlüssig zu verbinden. Das Umgreifen des Haltekörpers 28 durch den Verformungsbereich 18 des Ankers 14 wird durch Einpressen von Material des Verformungsbereichs 18 in am Haltekörper 28 befindliche Rillen 29 erreicht.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.

Am Boden der ersten koaxialen Sackbohrung 15 liegt eine Druckfeder 30 mit ihrem einen Ende an, welche andererseits an einem im Anschlußstutzen 7 durch Verschrauben oder Verstemmen befestigten Rohreinsatz 31 anliegt und welche bestrebt ist, Anker 14 und Ventilnadel 27 mit einer vom Anschlußstutzen 7 abgewandten Kraft zu beaufschlagen.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.

Die Ventilnadel 27 durchdringt mit radialem Abstand eine Durchgangsbohrung 34 in der Anschlagplatte 12 und wird in einer Führungsbohrung 35 des Düsenkörpers 9 geführt. In der Anschlagplatte 12 ist eine von der Durchgangsbohrung 34 zum Umfang der Anschlagplatte 12 führende Aussparung 37 vorgesehen, deren Lichte Weite größer ist als der Durchmesser der Ventilnadel 27 in ihrem von der Anschlagplatte 12 umgebenen Bereich.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. 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.

Die Ventilnadel 27 hat zwei Führungsabschnitte 39 und 40, die der Ventilnadel 27 in der Führungsbohrung 35 Führung geben sowie einen Axialdurchgang für den Kraftstoff freilassen und beispielsweise als Vierkante ausgebildet sind.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.

An den stromabwärts liegenden zweiten Führungsabschnitt 40 schließt sich ein zylindrischer Abschnitt 43 geringeren Durchmessers an. An den zylindrischen Abschnitt 43 wiederum fügt sich ein zulaufender, kegeliger Abschnitt 44, welcher in einem koaxialen, bevorzugt zylindrischen Zapfen 45 ausläuft.A cylindrical section 43 of smaller diameter adjoins the downstream second guide section 40. In turn, a tapered, conical section 44 joins the cylindrical section 43, which ends in a coaxial, preferably cylindrical pin 45.

In der einen Ausschnitt aus Figur 1 darstellenden Figur 2 ist zu erkennen, daß der Übergang zwischen dem zylindrischen Abschnitt 43 und dem kegeligen Abschnitt 44 gerundet ist - etwa in Form eines Radius - und einen Dichtsitz 47 bildet, welcher im Zusammenwirken mit einer am Düsenkörper 9 eingearbeiteten kegeligen Ventilsitzfläche 48 ein Öffnen bzw. Schließen des Kraftstoffeinspritzventiles bewirkt. Die kegelige Ventilsitzfläche 48 des Düsenkörpers 9 setzt sich in der dem Anker 14 abgewandten Richtung in einer zylindrischen Düsenkörperöffnung 49 fort, welche auf ungefähr gleicher Länge wie die Länge des Zapfens 45 verläuft, so daß zwischen der zylindrischen Düsenkörperöffnung 49 und dem zylindrischen Zapfen 45 ein Ringspalt konstanten Querschnitts verbleibt. Die Übergänge zwischen der kegeligen Ventilsitzfläche 48 einerseits und der zylindrischen Düsenkörperöffnung 49 andererseits sowie dem kegeligen Abschnitt 44 der Ventilnadel 27 einerseits und dem Zapfen 45 andererseits sind gerundet, um einen guten Strömungsverlauf zu gewährleisten. Den Abschluß des Düsenkörpers 9 in der dem Anker 14 abgewandten Richtung bildet eine Flachseite 51, welche durch die Mündung der Düsenkörperöffnung 49 unterbrochen ist.In 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.

Die Länge des Zapfens 45 ist so bemessen, daß bei geschlossenem Kraftstoffeinspritzventil der Zapfen 45 gerade nicht aus der Düsenkörperöffnung 49 hinausragt, d.h. der Zapfen 45 endet unmittelbar vor der durch die Flachseite 51 des Düsenkörpers 9 definierten Ebene.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.

Während die Flachseite 51 des Düsenkörpers 9 innen durch die Düsenkörperöffnung 49 begrenzt ist, kann sie außen durch einen konischen Bereich 52 begrenzt sein, welcher sich in der dem Anker 14 zugewandten Richtung erweitert.While 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.

An der Flachseite 51 des Düsenkörpers 9 liegt ein Plättchen 55 an, welches einen hochgezogenen Rand 56 aufweist, der in etwa der Kontur des konischen Bereiches 52 des Düsenkörpers 9 folgt. Die Herstellung des Randes 56 am Plättchen 55 kann etwa durch Tiefziehen des Plättchens 55 bewerkstelligt werden. Die Befestigung des Plättchens 55 an der Flachseite 51 wird durch eine Aufbereitungshülse 58 gewährleistet. Das Plättchen 55 wird gegen die Flachseite 51 gedrückt, indem ein Boden 60 einer koaxialen Sackbohrung 61 der Aufbereitungshülse 58 das Plättchen 55 in seinem äußeren Bereich umfaßt. Das Plättchen 55 ist also zwischen dem Boden 60 der Sackbohrung 61 der Aufbereitungshülse 58 und der Flachseite 51 des Düsenkörpers 9 eingespannt. Die Zentrierung des Plattchens 55 wird dabei erreicht, indem sich der Rand 56 des Plättchens 55 an den konischen Bereich 52 des Düsenkörpers 9 anlegt, das Plättchen 55 somit kein radiales Spiel mehr aufweist. Eine besonders gute Zentrierung des Plättchens 55 ist erreichbar, wenn sich der Rand 56 des Plättchens 55 beim Aufschieben auf den konischen Bereich 52 aufweitet, also eine radiale Einspannung vorgenommen wird.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.

Die Einspannung des Plättchens 55 zwischen Düsenkörper 9 und Aufbereitungshülse 58 wird realisiert, indem die Aufbereitungshülse 58 mit einem Innengewinde 64 auf ein am Umfang des Düsenkörpers 9 eingearbeitetes Außengewinde 65 geschraubt wird. Um die Lage der Aufbereitungshülse 58 relativ zum Düsenkörper 9 nach erfolgter Verschraubung zu sichern, kann die Aufbereitungshülse 58 mittels einer Stemmnase 66 in einer Außennut 68 des Düsenkörpers 9 verstemmt werden. Als Stemmnase 66 findet der dem Anker 14 zugewandte Rand der Aufbereitungshülse 58 Verwendung. Zur Verstemmung wird dieser nach innen in die Außennut 68 des Düsenkörpers 9 gebogen. Zwischen dem die Stemmnase 66 bildenden Rand und dem Boden 60 der Aufbereitungshülse 58 erstreckt sich die Mantelfläche der Sackbohrung 61, welche fast auf ihrer gesamten Längen durch das Innengewinde 64 gebildet wird. Innengewinde 64 und Außengewinde 65 werden vorzugsweise als Feingewinde ausgeführt. Die Aufbereitungshülse 58 kann gleichzeitig dazu dienen, einen den Düsenkörper 9 radial umfassenden Dichtring 69 axial zu sichern, wie in Figur 1 dargestellt ist.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. In order to secure the position of the processing sleeve 58 relative to the nozzle body 9 after screwing, 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.

Koaxial im Boden 60 der Aufbereitungshülse 58 mündet eine Aufbereitungsbohrung 70 von vorzugsweise zylindrischem Querschnitt, welche andererseits in einer scharfen Aufbereitungskante 71 mündet. Die Aufbereitungskante 71 ist von einer Ringnut 73 umgeben. Der Querschnitt der Ringnut 73 ist bei dem gezeigten Ausführungsbeispiel in etwa trapezförmig, d.h. sowohl eine innere Wand 74 der Ringnut 73 als auch eine äußere Wand 75 der Ringnut 73 sind schräg. Die Aufbereitungskante 71 wird durch den spitzen Winkel zwischen der schrägen inneren Wand 74 der Ringnut 73 und der Aufbereitungsbohrung 70 gebildet. Dieser Winkel sollte zwischen 10 und 20° betragen. Die äußere Wand 75 der Ringnut 73 bildet gleichzeitig die innere Fläche eines Kragens 77. Der Kragen 77 stellt das in der dem Anker 14 abgewandten Richtung am weitesten vorstehende Teil des Kraftstoffeinspritzventiles dar. Der Kragen 77 umschließt die Aufbereitungskante 71 und ragt gleichzeitig über diese hinaus. Aufgabe des Kragens 77 ist es, die zurückversetzte Aufbereitungskante 71 vor Beschädigungen zu sichern, etwa während der Montage des Kraftstoffeinspritzventils an eine Brennkraftmaschine.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.

In dem Plättchen 55 befinden sich mehrere Bohrungen 80, welche von stromauf nach stromab des Plättchens 55 führen. Stromaufwärts des Plättchens 55 münden die Bohrungen 80 in dem zwischen Düsenkörperöffnung 49 und Zapfen 45 gebildeten Ringraum. Die Bohrungen 80 sind mit ihrer Mittelachse 81 unmittelbar auf die Aufbereitungskante 71 oder aber knapp stromauf derselben gerichtet. Bezüglich der Längsachse des Kraftstoffeinspritzventils weist die Mittelachse 81 der Bohrungen 80 sowohl eine radiale als auch eine tangentiale Komponente auf. Entscheidend ist, daß der zwischen den Mittelachsen 81 der Bohrungen 80 und der Mantelfläche der Aufbereitungsbohrung 70 gebildete Winkel sehr flach verläuft, die aus den Bohrungen 80 austretenden Kraftstoffstrahlen also sehr flach auf die Aufbereitungsbohrung 70 treffen. Dieser Auftreffwinkel sollte weniger als 10° betragen.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 °.

Die Form der Ventilnadel 27 im Bereich des Dichtsitzes 47 ist als Rundung ausgebildet. Über den zusammen mit der kegeligen Ventilsitzfläche 48 das Öffnen und Schließen des Einspritzventiles bewirkenden Dichtsitz 47 der Ventilnadel 27 geht der zylindrische Abschnitt 43 der Ventilnadel 27 stetig in den kegeligen Abschnitt 44 übergeht. Sowohl der Übergang vom zylindrischen Abschnitt 43 auf die Rundung als auch der Übergang von der Rundung auf den kegeligen Abschnitt 44 erfolgt dabei, in Richtung der Strömung betrachtet, vorzugsweise tangential.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.

Von besonderem Vorteil bei dem beschriebenen Kraftstoffeinspritzventil ist die durch die Rundung des Dichtsitzes 47 bedingte sehr gute Korrelation zwischen Ventilnadelhub und abströmender Kraftstoffmenge. Durch den vergleichsweise geringen Radius bzw. Halbmesser der Rundung, welcher zu einer ausgeprägt linienförmigen Berührung zwischen Ventilnadel 27 und kegeliger Ventilsitzfläche 48 führt, ist die Neigung der Ventilnadel 27 zum hydraulischen "Kleben" an der Ventilsitzfläche 48 weit geringer als etwa bei solchen Einspritzventilen, welche über kugelförmige Verschlußteile mit ihrem eher flächigen Dichtsitz verfügen.Of particular advantage in the fuel injection valve described is the very good correlation between the valve needle stroke and the outflowing fuel quantity due to the rounding of the sealing seat 47. Due to the comparatively small radius or radius of the Rounding, which leads to a pronounced linear contact between the valve needle 27 and the conical valve seat surface 48, the tendency of the valve needle 27 to hydraulically "stick" to the valve seat surface 48 is far less than, for example, in the case of those injection valves which have spherical closure parts with their rather flat sealing seat .

Die Funktion des Kraftstoffeinspritzventiles ist wie folgt:The function of the fuel injector is as follows:

Bei von Strom durchflossener Magnetspule 3 wird der Anker 14 in Richtung auf den Anschlußstutzen 7 gezogen. Die mit dem Anker 14 fest verbundene Ventilnadel 27 hebt mit ihrem Dichtsitz 47 von der kegeligen Ventilsitzfläche 48 ab, zwischen Dichtsitz 47 und kegeliger Ventilsitzfläche 48 wird ein Strömungsquerschnitt freigegeben, der Kraftstoff kann durch den zwischen Düsenkörperöffnung 49 und Zapfen 45 gelegenen Ringraum zu den Bohrungen 80 gelangen. Die Bohrungen 80 werden vom Kraftstoff unter hohem Druckabfall durchströmt, da diese den engsten Strömungsquerschnitt innerhalb des Kraftstoffeinspritzventiles bilden. Die Größe der Bohrungen 80 entscheidet also über den Mengenstrom des abgespritzten Kraftstoffes, der Fachmann spricht hierbei von "Zumessung". Der aus den Bohrungen 80 austretende Kraftstoffstrahl ist so auf die Aufbereitungsbohrung 70 gerichtet, daß er knapp stromaufwärts oder unmittelbar auf der Aufbereitungskante 71 auftrifft. Die Auftreffgeschwindigkeit ist dabei so groß, daß man von einem "Prallen" sprechen kann. Durch die hohe kinetische Energie beim Auftreffen auf die Aufbereitungsbohrung 70 werden die einzelnen Kraftstofftröpfchen aufgerissen und zerstäubt. Die Folge davon ist, daß stromabwärts der Aufbereitungskante 71 ein Kraftstoffnebel das Kraftstoffeinspritzventil verläßt. Dieser Kraftstoffnebel gestattet eine gute Vermischung mit der Ansaugluft der Brennkraftmaschine.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". Due to the high kinetic energy when it hits the processing bore 70, the individual fuel droplets are torn open and atomized. 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.

Die die Aufbereitungskante 71 umgebende Ringnut 73 bietet den Vorteil, daß eventuell an der inneren Wand 74 der Ringnut 73 angelagerte Kraftstoffpartikel durch einen Sekundärwirbel innerhalb der Ringnut 73 zur Aufbereitungskante 71 hin mitgerissen werden und dort ebenfalls zur Abspritzung gelangen. Kraftstoffeinspritzventile, welche über die erfindungsgemäß gestaltete Ringnut 73 verfügen, neigen weit weniger zum Tropfen als Kraftstoffeinspritzventile ohne die Ringnut 73. Die für diesen Effekt maßgebenden Ursachen sind noch weitgehend ungeklärt.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.

Mit dem erfindungsgemäßen Kraftstoffeinspritzventil wird eine sehr gute Kraftstoffaufbereitung erzielt. Die besten Ergebnisse werden bei einer Stärke des Plättchens 55 von 0,3 mm dann erreicht, wenn der Durchmesser der Aufbereitungsbohrung 70 2,2 mm beträgt und die Länge 5 mm. Der Durchmesser der Bohrungen 80 ist vom jeweiligen Anwendungsfall abhängig, er liegt im Bereich zwischen 0,15 und 0,35 mm.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.

Claims (7)

  1. Fuel injection valve for fuel injection systems of internal combustion engines, having a valve housing (1) in ferromagnetic material and a core (7) surrounded by a magnet coil (3), having an armature (14) interacting with the core (7), which armature is firmly connected to a valve needle (27) which, controls, in interaction with a valve seating surface (48) configured on a nozzle body (9), an opening and closing of the fuel injection valve, having a nozzle body opening (49) located downstream of the valve seating surface (48) and having a platelet (55), which is provided with holes (80) and is mounted transverse to the nozzle body opening (49) between the nozzle body (9) and a preparation sleeve (58), the preparation sleeve (58) having a central preparation hole (70) running out into an edge (71), characterised in that the valve needle (27) runs out into a cylindrical pintle (45) which, together with the nozzle body opening (49) forms an annular space of constant cross-section during the opening motion of the valve needle (27), downstream of the axial extension of which annular space the holes (80) of the platelet (55) emerge with their total cross-section, and the transition to the pintle (45) is rounded.
  2. Fuel injection valve according to Claim 1, characterised in that, when the fuel injection valve is closed, the pintle (45) ends in the immediate vicinity of the platelet (55).
  3. Fuel injection valve according to Claim 1, characterised in that the valve needle (27) has a conical section (44) upstream of the pintle (45) and the transition between the conical section (44) and the pintle (45) is rounded.
  4. Fuel injection valve according to Claim 3, characterised in that the valve seating surface (48) merges downstream into a nozzle body opening (49) surrounding the pintle (45) and the transition between the valve seating surface (48) and the nozzle body opening (49) is rounded.
  5. Fuel injection valve according to Claim 1, characterised in that the hypothetical centre lines (81) of the holes (80) of the platelet (55) intersect the generated surface of the preparation hole (70) on or just upstream of the edge (71) of the preparation hole (70).
  6. Fuel injection valve according to Claim 1, characterised in that the platelet (55) has a rim (56), which is in contact with a conical region (52) of the nozzle body (9).
  7. Fuel injection valve according to Claim 6, characterised in that the preparation sleeve (58) is screwed onto the nozzle body (9) and a part of the preparation sleeve (58) is caulked against the nozzle body (9).
EP90103656A 1986-05-31 1987-05-27 Fuel injection valve Expired - Lifetime EP0393328B1 (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP90103656A EP0393328B1 (en) 1986-05-31 1987-05-27 Fuel injection valve
AT90103656T ATE97193T1 (en) 1986-05-31 1990-02-26 FUEL INJECTION VALVE.

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 (en) 1986-05-31 1987-03-30 Fuel injector
EP90103656A EP0393328B1 (en) 1986-05-31 1987-05-27 Fuel injection valve

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 (en) 1990-10-24
EP0393328B1 true EP0393328B1 (en) 1993-11-10

Family

ID=25844272

Family Applications (2)

Application Number Title Priority Date Filing Date
EP90103656A Expired - Lifetime EP0393328B1 (en) 1986-05-31 1987-05-27 Fuel injection valve
EP19870903254 Expired - Lifetime EP0310607B1 (en) 1986-05-31 1987-05-27 Fuel injection valve

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP19870903254 Expired - Lifetime EP0310607B1 (en) 1986-05-31 1987-05-27 Fuel injection valve

Country Status (8)

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

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Also Published As

Publication number Publication date
WO1987007334A3 (en) 1987-12-30
BR8707711A (en) 1989-10-31
AU4548889A (en) 1990-03-08
AU7435987A (en) 1987-12-22
JPH01502766A (en) 1989-09-21
AU607871B2 (en) 1991-03-14
US4934605A (en) 1990-06-19
AU593914B2 (en) 1990-02-22
WO1987007334A2 (en) 1987-12-03
EP0310607B1 (en) 1991-04-03
EP0310607A1 (en) 1989-04-12
ES2006151A6 (en) 1989-04-16
JP2553120B2 (en) 1996-11-13
US5016821A (en) 1991-05-21
ATE97193T1 (en) 1993-11-15
EP0393328A1 (en) 1990-10-24

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