EP0495793A1 - Electromagnetically operated fuel injection valve - Google Patents

Electromagnetically operated fuel injection valve

Info

Publication number
EP0495793A1
EP0495793A1 EP90913242A EP90913242A EP0495793A1 EP 0495793 A1 EP0495793 A1 EP 0495793A1 EP 90913242 A EP90913242 A EP 90913242A EP 90913242 A EP90913242 A EP 90913242A EP 0495793 A1 EP0495793 A1 EP 0495793A1
Authority
EP
European Patent Office
Prior art keywords
guide ring
valve
fuel injection
valve seat
injection valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP90913242A
Other languages
German (de)
French (fr)
Inventor
Ferdinand Reiter
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP0495793A1 publication Critical patent/EP0495793A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/10—Other injectors with elongated valve bodies, i.e. of needle-valve type
    • F02M61/12—Other injectors with elongated valve bodies, i.e. of needle-valve type characterised by the provision of guiding or centring means for valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M51/0682—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 body being hollow and its interior communicating with the fuel flow
    • 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
    • F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
    • F02B75/00—Other engines
    • F02B75/02—Engines characterised by their cycles, e.g. six-stroke
    • F02B2075/022—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle
    • F02B2075/027—Engines characterised by their cycles, e.g. six-stroke having less than six strokes per cycle four

Definitions

  • the invention relates to a fuel injection valve according to the preamble of claim 1.
  • a generic fuel injector is already known.
  • a part referred to as a nozzle and a separate stepped perforated disk are combined to form an assembly.
  • the stepped perforated disc with valve seat and with a hollow cylindrical guide track guides the valve closing body during its axial movement.
  • the nozzle is provided with an outlet opening for the fuel to be injected and receives the stepped perforated disk in a press fit.
  • Fuel injection valves are also known in which the nozzle and the valve seat are formed into a one-piece valve seat body - without a hollow cylindrical guideway.
  • the manufacturing effort for the stepped perforated disc is high due to the high accuracy requirements for the concentricity of the hollow cylindrical guide track to the valve seat.
  • the nozzle is in the Machining the area of the mounting of the stepped perforated disc very precisely. This increases the cost of the individual parts and the assembly effort when assembling them. If the dimensional tolerances of these individual parts are slightly exceeded, the valve seat is deformed when the fuel injector is installed. Such quality defects result in higher kinetic friction between the valve closing member, the guide tracks and the valve seat.
  • the fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the hollow cylindrical guideway of a separate guide ring guides the valve closing body in a particularly closely concentric manner, so that this position is secured when the valve closing body opens around the fuel.
  • a finer fit between the valve closing body and the hollow cylindrical guide track is possible within narrower tolerances with the cost-effective, separate guide ring because its position can be individually adjusted in relation to the valve seat.
  • the friction between the valve closing body and valve seat is high Reliability is reduced because the eccentricity of the valve closing body to the valve seat is reduced by the narrow guide.
  • the position of the guide ring with respect to the valve seat cannot be influenced by temperature fluctuations due to the radial distance of the opening surrounding it. Further advantageous refinements of the invention result from the subclaims.
  • the drawing shows the sectional view of the valve seat area of a fuel injection valve.
  • the fuel injection valve 1 shown in the drawing for a fuel injection system of mixture-compressing, spark-ignited internal combustion engines has a valve housing 3 which accommodates a valve seat body 5.
  • the valve seat body 5 is connected to a spacer ring 7 via a welded connection 6.
  • the spacer ring 7 sits with its free end face on a collar surface 9 of the valve housing 3 and thus determines the axial position of the valve seat body 5 relative to the valve housing 3.
  • An action 10 of a central longitudinal bore 11 in the valve seat body 5 narrows on the side facing away from the spacer ring 7 on a collar step 12, forms a valve seat 13 there and ends in an outlet opening 14 which forms the actual injection nozzle.
  • valve closing member 15 with radial openings 16 protrudes into the longitudinal bore 11.
  • valve closing member 15 On the side facing the valve seat 13, the valve closing member 15 carries a valve closing body 17 in the form of a hardened ball.
  • valve closing member 15 On the side facing away from the valve seat 13, the valve closing member 15 carries an armature 18 made of soft magnetic material.
  • a compression spring 19 acts on the valve closing member 15 in the area of the armature 18 in the closing direction.
  • a magnet coil 20 is arranged adjacent to the armature 18 in such a way that, as soon as it is excited, the armature 18 lifts against the closing direction of the valve closing member 15.
  • the guide ring 21 On the shoulder 12 sits a guide ring 21, the hollow cylindrical guide track 22 concentrically tightly enclosing the valve closing body 17.
  • the guide ring 21 is acted upon by a compression spring 25 supported on the spacer ring 7 in a normal manner to the collar step 12 and thereby secured in position.
  • the guide ring 21 is provided on its hollow cylindrical guide track 22 with swirl grooves 27.
  • the diameter of the longitudinal bore 11 is substantially larger than the outer diameter of the guide ring 21. There is therefore a radial distance between the wall 10 and and the guide ring 21. Due to the radial distance between the outer circumference of the guide ring 21 and the longitudinal bore 11, there is a floating arrangement of the guide ring 21 on the collar step 12. A floating displacement of the guide ring 21 is possible when external forces overcome the frictional forces on the spring-loaded guide ring 21. Such forces are to be applied, for example, when adjusting the guide ring 21 by means of a centering mandrel, which is inserted through the hollow cylindrical guide track 22 and is centered on the valve seat 13, or a special centering ball.
  • the forces necessary for the adjustment are greater than those which act on the guide ring 21 during normal operation of the fuel injection valve. If the guide ring 21 in the interior of the valve seat body 5 is adjusted without a welded-on spacer ring 7, the compression spring 25 can be tensioned less and act on the guide ring 21 with reduced force. The necessary adjustment forces are smaller than in the installation method described above. Here, after adjusting the valve seat body 5, the pressure spring 25 and the guide ring 21 must be inserted into the valve housing 3 and welded to the spacer ring 7.
  • an electrical circuit (not shown) of the magnet coil 20 is closed.
  • the magnetic forces then acting attract armature 18.
  • the valve closing body 17 of the valve closing member 15 is moved away from the valve seat 13, counter to the pressure spring 19 acting on it, so that the fuel passes through the valve closing member 15 and its radial openings 16 through the longitudinal bore 11 to the valve seat 13 and downstream thereof at least one ⁇ outlet opening 14 and can be hosed down.
  • valve seat body 5 When installing the valve seat body 5 in the valve housing 3, the valve seat body 5 is to be aligned axially with the already installed valve closing member 15. This position taking into account the intended stroke is secured by the welded-on spacer ring 7.
  • the swirl grooves 27 not only allow a fuel flow past the valve closing body 17, but they also cause the injected fuel to swirl and improve the fuel spray pattern.
  • the guide ring 21 can be produced in sheet metal stamping in a particularly cost-effective manner.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Electromagnetism (AREA)
  • Fuel-Injection Apparatus (AREA)

Abstract

L'invention a pour tâche d'améliorer la précision d'ajustage et le fonctionnement d'injecteurs de carburant selon le terme générique et de diminuer le coût de fabrication. L'invention crée pour un injecteur de carburant à commande électromagnétique (1) destiné aux moteurs à explosion une disposition très précise entre l'orifice de sortie (14), le siège de soupape (13) et la voie de guidage (22), en améliorant ainsi la précision de fonctionnement et le comportement à l'usure de l'injecteur de carburant par le fait qu'une bague de guidage (21) particulière sollicitée par ressort est maintenue flottante dans le trou longitudinal (11) à une distance radiale par rapport à la paroi (10), les forces de maintien étant plus élevées que les forces d'attaque exercées sur la bague de guidage (21) lors du fonctionnement de l'injecteur de carburant. L'invention est prévue en particulier pour injecteurs de carburant de moteurs d'automobiles.The task of the invention is to improve the adjustment precision and the operation of fuel injectors according to the generic term and to reduce the manufacturing cost. The invention creates, for an electromagnetically controlled fuel injector (1) intended for internal combustion engines, a very precise arrangement between the outlet orifice (14), the valve seat (13) and the guide track (22), thereby improving the operating precision and the wear behavior of the fuel injector by the fact that a particular guide ring (21) biased by spring is kept floating in the longitudinal hole (11) at a radial distance relative to the wall (10), the holding forces being higher than the driving forces exerted on the guide ring (21) during the operation of the fuel injector. The invention is intended in particular for fuel injectors for automobile engines.

Description

Elektromagnetisch betätigbares Kraftstoffeinspritzventil Electromagnetically actuated fuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Kraftstoffeinspritzventil nach der Gattung des Anspruchs 1.The invention relates to a fuel injection valve according to the preamble of claim 1.
Durch die DE-PS 31 02 642 bzw. die US-PS 44 03 741 ist schon ein gattungsgemäßes Kraftstoffeinspritzventil bekannt. Bei diesem sind ein als Düse bezeichnetes Teil und eine gesonderte Stufenlochscheibe zu einer Baugruppe zusammengefügt. Die Stufenlochscheibe mit Ventil¬ sitz und mit hohlzylindrischer Führungsbahn führt den Ventilschlie߬ körper bei seiner axialen Bewegung. Die Düse ist mit einer Aus¬ trittsöffnung für den einzuspritzenden Kraftstoff versehen und nimmt die Stufenlochscheibe in einem Preßsitz auf.From DE-PS 31 02 642 and US-PS 44 03 741 a generic fuel injector is already known. In this, a part referred to as a nozzle and a separate stepped perforated disk are combined to form an assembly. The stepped perforated disc with valve seat and with a hollow cylindrical guide track guides the valve closing body during its axial movement. The nozzle is provided with an outlet opening for the fuel to be injected and receives the stepped perforated disk in a press fit.
Es sind auch Krafstoffeinspritzventile bekannt, bei denen die Düse und der Ventilsitz zu einem einteiligen Ventilsitzkörper - ohne hohlzylindrische Führungsbahn - ausgebildet sind.Fuel injection valves are also known in which the nozzle and the valve seat are formed into a one-piece valve seat body - without a hollow cylindrical guideway.
Der Fertigungsaufwand für die Stufenlochscheibe ist aufgrund der ho¬ hen Genauigkeitsforderungen für die Konzentrizität der hohlzylindri- schen Führungsbahn zum Ventilsitz hoch. Außerdem ist die Düse im Bereich der Aufnahme der Stufenlochscheibe sehr genau zu bearbeiten. Dies verteuert die Einzelteile und den Montageaufwand bei deren Zu¬ sammenbau. Geringe Überschreitungen der Maßtoleranzen dieser Einzel¬ teile führen bei der Montage des Kraftstoffeinspritzventils zu einer Deformierung des Ventilsitzes. Derartige Qualitätsmängel haben eine höhere Bewegungsreibung zwischen Ventilschließglied, den Führungs¬ bahnen und dem Ventilsitz zur Folge.The manufacturing effort for the stepped perforated disc is high due to the high accuracy requirements for the concentricity of the hollow cylindrical guide track to the valve seat. In addition, the nozzle is in the Machining the area of the mounting of the stepped perforated disc very precisely. This increases the cost of the individual parts and the assembly effort when assembling them. If the dimensional tolerances of these individual parts are slightly exceeded, the valve seat is deformed when the fuel injector is installed. Such quality defects result in higher kinetic friction between the valve closing member, the guide tracks and the valve seat.
Diese Bewegungsreibung führt zu Hysteresefehlern bei der Ansteuerung des Kraftstoffeinspritzventils, zu Verschleiß und außerdem zu einem zunehmend ungleichmäßigen Kraftstoffstrahlbild. Dadurch wird der Kraftstoff schlechter aufbereitet und die einzelnen Zylinder von Brennkraftmaschinen werden unterschiedlich mit Kraftstoff versorgt. Bei den bisherigen, gröber tolerierten Passungen zwischen Ventil¬ schließkörper und Führungsbahnen stört bei geöffnetem Kraftstoffein¬ spritzventil ein exzentrisches Aufliegen des Ventilschließkörpers am Ventilsitz oder an der Führung mit den bereits genannten Folgen.This kinetic friction leads to hysteresis errors in the control of the fuel injection valve, to wear and also to an increasingly uneven fuel jet pattern. As a result, the fuel is processed poorly and the individual cylinders of internal combustion engines are supplied with fuel differently. In the previous, more coarsely tolerated fits between valve closing body and guideways, an eccentric bearing of the valve closing body on the valve seat or on the guide interferes with the consequences already mentioned when the fuel injection valve is open.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnen¬ den Merkmalen des Anspruchs 1 hat demgegenüber den Vorteil, daß die hohlzylindrische Führungsbahn eines gesonderten Führungsringes den Ventilschließkörper besonders eng konzentrisch umfassend führt, so daß diese Lage bei öffnendem, kraftstoffumströmtem Ventilschließkör¬ per gesichert ist.The fuel injector according to the invention with the characterizing features of claim 1 has the advantage that the hollow cylindrical guideway of a separate guide ring guides the valve closing body in a particularly closely concentric manner, so that this position is secured when the valve closing body opens around the fuel.
Eine feinere Passung zwischen Ventilschließkörper und der hohlzylin¬ drischen Führungsbahn ist innerhalb engerer Toleranzen mit dem ko¬ stengünstigen, gesonderten Führungsring deshalb möglich, weil dessen Lage jeweils individuell zum Ventilsitz einstellbar ist. Dadurch ist die Reibung zwischen Ventilschließkörper und Ventilsitz mit hoher Zuverlässigkeit verringert, weil die Exzentrizität des Ventil¬ schließkörpers zum Ventilsitz durch die enge Führung verringert wird. Damit wird ein präziseres Ansprechen des Kraftstoffeinspritz¬ ventils bei exakterer Dosierung des Kraftstoffs und verbessertem Kraftstoffstrahlbild erreicht. Die Lage des Führungsringes bezüglich des Ventilsitzes ist aufgrund des radialen Abstandes der ihn umge¬ benden Öffnung nicht durch Temperaturschwankungen beeinflußbar. Wei¬ tere vorteilhafte Ausgestaltungen der Erfindung ergeben sich aus den Unteransprüchen.A finer fit between the valve closing body and the hollow cylindrical guide track is possible within narrower tolerances with the cost-effective, separate guide ring because its position can be individually adjusted in relation to the valve seat. As a result, the friction between the valve closing body and valve seat is high Reliability is reduced because the eccentricity of the valve closing body to the valve seat is reduced by the narrow guide. This achieves a more precise response of the fuel injection valve with more precise metering of the fuel and an improved fuel spray pattern. The position of the guide ring with respect to the valve seat cannot be influenced by temperature fluctuations due to the radial distance of the opening surrounding it. Further advantageous refinements of the invention result from the subclaims.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der nachfolgenden Be¬ schreibung anhand der zugehörigen Zeichnung näher erläutert. Die Zeichnung zeigt die Schnittdarstellung des Ventilsitzbereichs eines Kraftstoffeinspritzventils.An embodiment of the invention is explained in more detail in the following description with reference to the accompanying drawing. The drawing shows the sectional view of the valve seat area of a fuel injection valve.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Das in der Zeichnung gezeigte Kraftstoffeinspritzventil 1 für eine Kraftstoffeinspritzanlage von gemischverdichtenden, fremdgezündeten Brennkraftmaschinen hat ein Ventilgehäuse 3, das einen Ventilsitz¬ körper 5 aufnimmt. Der Ventilsitzkörper 5 ist über eine Schweißver¬ bindung 6 mit einem Distanzring 7 verbunden. Der Distanzring 7 sitzt mit seiner freien Stirnfläche an einer Bundfläche 9 des Ventilgehäu¬ ses 3 und bestimmt somit die Axiallage des Ventilsitzkörpers 5 zum Ventilgehäuse 3. Eine Handung 10 einer zentralen Längsbohrung 11 im Ventilsitzkörper 5 verengt sich auf der dem Distanzring 7 abgewand¬ ten Seite an einer Bundstufe 12, bildet dort einen Ventilsitz 13 und endet in einer die eigentliche Einspritzdüse bildenden Austritts¬ öffnung 14.The fuel injection valve 1 shown in the drawing for a fuel injection system of mixture-compressing, spark-ignited internal combustion engines has a valve housing 3 which accommodates a valve seat body 5. The valve seat body 5 is connected to a spacer ring 7 via a welded connection 6. The spacer ring 7 sits with its free end face on a collar surface 9 of the valve housing 3 and thus determines the axial position of the valve seat body 5 relative to the valve housing 3. An action 10 of a central longitudinal bore 11 in the valve seat body 5 narrows on the side facing away from the spacer ring 7 on a collar step 12, forms a valve seat 13 there and ends in an outlet opening 14 which forms the actual injection nozzle.
In die Längsbohrung 11 ragt ein rohrförmiges Ventilschließglied 15 mit radialen Öffnungen 16. Auf der dem Ventilsitz 13 zugewandten Seite trägt das Ventilschließglied 15 einen Ventilschließkörper 17 in Form einer gehärteten Kugel. Auf der dem Ventilsitz 13 abgewand¬ ten Seite trägt das Ventilschließglied 15 einen Anker 18 aus weich¬ magnetischem Material.A tubular valve closing member 15 with radial openings 16 protrudes into the longitudinal bore 11. On the side facing the valve seat 13, the valve closing member 15 carries a valve closing body 17 in the form of a hardened ball. On the side facing away from the valve seat 13, the valve closing member 15 carries an armature 18 made of soft magnetic material.
Eine Druckfeder 19 beaufschlagt das Ventilschließglied 15 im Bereich des Ankers 18 in Schließrichtung. Eine Magnetspule 20 ist zum Anker 18 benachbart so angeordnet, daß sie, sobald sie erregt wird, den Anker 18 entgegen der Schließrichtung des Ventilschließgliedes 15 anhebt.A compression spring 19 acts on the valve closing member 15 in the area of the armature 18 in the closing direction. A magnet coil 20 is arranged adjacent to the armature 18 in such a way that, as soon as it is excited, the armature 18 lifts against the closing direction of the valve closing member 15.
Auf der Bundstufe 12 sitzt ein Führungsring 21, dessen hohlzylindri- sche Führungsbahn 22 den Ventilschließkörper 17 konzentrisch eng um¬ schließt. Der Führungsring 21 ist über eine am Distanzring 7 abge¬ stützte Druckfeder 25 normal zur Bundstufe 12 beaufschlagt und da¬ durch lagegesichert. Der Führungsring 21 ist an seiner hohlzylindri- schen Führungsbahn 22 mit Drallnuten 27 versehen.On the shoulder 12 sits a guide ring 21, the hollow cylindrical guide track 22 concentrically tightly enclosing the valve closing body 17. The guide ring 21 is acted upon by a compression spring 25 supported on the spacer ring 7 in a normal manner to the collar step 12 and thereby secured in position. The guide ring 21 is provided on its hollow cylindrical guide track 22 with swirl grooves 27.
Der Durchmesser der Längsbohrung 11 ist wesentlich größer als der Außendurchmesser des Führungsringes 21. Zwischen der Wandung 10 und und dem Führungsring 21 besteht daher ein radialer Abstand. Aufgrund des radialen AbStandes zwischen dem Außenumfang des Führungsringes 21 und der Längsbohrung 11 liegt eine schwimmende Anordnung des Füh¬ rungsringes 21 auf der Bundstufe 12 vor. Ein schwimmendes Verschie¬ ben des Führungsringes 21 ist dann möglich, wenn äußere Kräfte die Reibkräfte am federbeaufschlagten Führungsring 21 überwinden. Derar¬ tige Kräfte sind beispielsweise beim Justieren des Führungsringes 21 mittels eines durch die hohlzylindrische Führungsbahn 22 gesteckten, auf dem Ventilsitz 13 zentrisch sitzenden Zentrierdornes oder einer speziellen Zentrierkugel aufzubringen. Wenn der von der Druckfeder 25 beaufschlagte Führungsring 21 im Inneren des mit dem Distanzring 7 verschweißten Ventilsitzkörpers 5 justiert wird, sind die für die Justierung notwendigen Kräfte größer, als jene, die im Normalbetrieb des Kraftstoffeinspritzventils am Führungsring 21 angreifen. Wenn der Führungsring 21 im Inneren des Ventilsitzkörpers 5 ohne ange¬ schweißten Distanzring 7 justiert wird, kann die Druckfeder 25 ge¬ ringer gespannt sein und den Führungsring 21 mit verminderter Kraft beaufschlagen. Die notwendigen Justierkräfte sind dabei kleiner als bei der vorbeschriebenen Montageweise. Hier ist nach dem Justieren der Ventilsitzkörper 5 gemeinsam mit der Druckfeder 25 und dem Füh¬ rungsring 21 in das Ventilgehäuse 3 einzusetzen und mit dem Distanz¬ ring 7 zu verschweißen.The diameter of the longitudinal bore 11 is substantially larger than the outer diameter of the guide ring 21. There is therefore a radial distance between the wall 10 and and the guide ring 21. Due to the radial distance between the outer circumference of the guide ring 21 and the longitudinal bore 11, there is a floating arrangement of the guide ring 21 on the collar step 12. A floating displacement of the guide ring 21 is possible when external forces overcome the frictional forces on the spring-loaded guide ring 21. Such forces are to be applied, for example, when adjusting the guide ring 21 by means of a centering mandrel, which is inserted through the hollow cylindrical guide track 22 and is centered on the valve seat 13, or a special centering ball. If the guide ring 21 acted upon by the compression spring 25 is adjusted inside the valve seat body 5 welded to the spacer ring 7, the forces necessary for the adjustment are greater than those which act on the guide ring 21 during normal operation of the fuel injection valve. If the guide ring 21 in the interior of the valve seat body 5 is adjusted without a welded-on spacer ring 7, the compression spring 25 can be tensioned less and act on the guide ring 21 with reduced force. The necessary adjustment forces are smaller than in the installation method described above. Here, after adjusting the valve seat body 5, the pressure spring 25 and the guide ring 21 must be inserted into the valve housing 3 and welded to the spacer ring 7.
Um das Kraftstoffeinspritzventil 1 zu öffnen, wird ein nicht darge¬ stellter elektrischer Stromkreis der Magnetspule 20 geschlossen. Die daraufhin wirksamen magnetischen Kräfte ziehen den Anker 18 an. Mit diesem gemeinsam wird der Ventilschließkörper 17 des Ventilschlie߬ gliedes 15 vom Ventilsitz 13, entgegen der beaufschlagenden Druckfe¬ der 19 wegbewegt, so daß der Kraftstoff durch das Ventilschließglied 15 und dessen radiale Öffnungen 16 hindurch über die Längsbohrung 11 zum Ventilsitz 13 und stromabwärts zu dessen mindestens einer λus- trittsöffnung 14 gelangen und abgespritzt werden kann.To open the fuel injection valve 1, an electrical circuit (not shown) of the magnet coil 20 is closed. The magnetic forces then acting attract armature 18. Together with this, the valve closing body 17 of the valve closing member 15 is moved away from the valve seat 13, counter to the pressure spring 19 acting on it, so that the fuel passes through the valve closing member 15 and its radial openings 16 through the longitudinal bore 11 to the valve seat 13 and downstream thereof at least one λ outlet opening 14 and can be hosed down.
Beim Einbau des Ventilsitzkörpers 5 in das Ventilgehäuse 3 ist der Ventilsitzkörper 5 axial zum bereits montierten Ventilschließglied 15 auszurichten. Diese den vorgesehenen Hub berücksichtigende Lage ist durch den angeschweißten Distanzring 7 gesichert.When installing the valve seat body 5 in the valve housing 3, the valve seat body 5 is to be aligned axially with the already installed valve closing member 15. This position taking into account the intended stroke is secured by the welded-on spacer ring 7.
Die Drallnuten 27 erlauben nicht nur eine Kraftstoffströmung am Ven¬ tilschließkörper 17 vorbei, sondern sie bewirken auch eine Verwirbe- lung des eingespritzten Kraftstoffes und verbessern das Kraftstoff¬ strahlbild.The swirl grooves 27 not only allow a fuel flow past the valve closing body 17, but they also cause the injected fuel to swirl and improve the fuel spray pattern.
Besonders kostengünstig ist der Führungsring 21 in Blechprägeaus¬ führung herstellbar. The guide ring 21 can be produced in sheet metal stamping in a particularly cost-effective manner.

Claims

Ansprüche Expectations
1. Elektromagnetisch betätigbares Kraftstoffeinspritzventil (1) mit einem Ventilgehäuse (3), einem mindestens teilweise im Ventilgehäuse (3) angeordneten Ventilsitzkörper (5) mit einer Längsbohrung (11), in die sich ein einem Ventilsitz (13) mit einer λustrittsöffnung (14) zugeordnetes Ventilschließglied (17) erstreckt, das in einer hohlzylindrischen Führungsbahn (22) eines Führungsringes (22) ge¬ führt ist, dadurch gekennzeichnet, daß der Führungsring (21) in axialer Richtung federbeaufschlagt in der Längsbohrung (11) mit ei¬ nem radialen Abstand zur Wandung (10) gehalten ist, wobei die Halte¬ kräfte größer als die beim Betrieb des Kraftstoffeinspritzventils (1) am Führungsring (21) angreifenden Kräfte sind.1. Electromagnetically actuated fuel injection valve (1) with a valve housing (3), an at least partially in the valve housing (3) arranged valve seat body (5) with a longitudinal bore (11) into which a valve seat (13) with an λ outlet opening (14) The associated valve closing member (17) extends in a hollow cylindrical guide track (22) of a guide ring (22), characterized in that the guide ring (21) is spring-loaded in the axial direction in the longitudinal bore (11) with a radial distance to the wall (10), the holding forces being greater than the forces acting on the guide ring (21) during operation of the fuel injection valve (1).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeich¬ net, daß der Führungsring (21) aus Blech gefertigt ist.2. Fuel injection valve according to claim 1, characterized gekennzeich¬ net that the guide ring (21) is made of sheet metal.
3. Kraftstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der Führungsring (21) mit zur Führungsbahn (22) hin offenen Drallnuten (27) versehen ist. 3. Fuel injection valve according to claim 1 or 2, characterized in that the guide ring (21) with the guide track (22) open swirl grooves (27) is provided.
EP90913242A 1989-10-21 1990-09-13 Electromagnetically operated fuel injection valve Withdrawn EP0495793A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3935148A DE3935148A1 (en) 1989-10-21 1989-10-21 ELECTROMAGNETICALLY ACTUABLE FUEL INJECTION VALVE
DE3935148 1989-10-21

Publications (1)

Publication Number Publication Date
EP0495793A1 true EP0495793A1 (en) 1992-07-29

Family

ID=6391949

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90913242A Withdrawn EP0495793A1 (en) 1989-10-21 1990-09-13 Electromagnetically operated fuel injection valve

Country Status (8)

Country Link
US (1) US5209408A (en)
EP (1) EP0495793A1 (en)
JP (1) JPH05501139A (en)
KR (1) KR920704000A (en)
BR (1) BR9007768A (en)
CS (1) CS504290A3 (en)
DE (1) DE3935148A1 (en)
WO (1) WO1991005951A1 (en)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4137994C2 (en) * 1991-11-19 1999-06-02 Bosch Gmbh Robert Electromagnetically actuated injection valve with a nozzle holder and method for producing a nozzle holder of an injection valve
JPH0874699A (en) * 1994-09-09 1996-03-19 Zexel Corp Fuel injection valve
DE19736684A1 (en) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Fuel injector for internal combustion engine
US5915591A (en) * 1997-09-10 1999-06-29 Illinois Tool Works Inc. Electric solenoid valve for hot melt adhesive and method therefor
US6508418B1 (en) * 1998-05-27 2003-01-21 Siemens Automotive Corporation Contaminant tolerant compressed natural gas injector and method of directing gaseous fuel therethrough
US6431474B2 (en) 1999-05-26 2002-08-13 Siemens Automotive Corporation Compressed natural gas fuel injector having magnetic pole face flux director
DE19927899A1 (en) * 1999-06-18 2000-12-21 Bosch Gmbh Robert Fuel injection valve for fuel injection device for IC engine has guide disc infront of valve seat provided with opening having alternating guide regions for valve closure element and fuel flow regions
US6405947B2 (en) 1999-08-10 2002-06-18 Siemens Automotive Corporation Gaseous fuel injector having low restriction seat for valve needle
DE19937961A1 (en) * 1999-08-11 2001-02-15 Bosch Gmbh Robert Fuel injection valve and method for producing outlet openings on valves
US6105884A (en) * 1999-09-15 2000-08-22 Delphi Technologies, Inc. Fuel injector with molded plastic valve guides
US6409145B1 (en) * 2000-02-28 2002-06-25 Delphi Technologies, Inc. Plunger assembly having a preset spring force pre-load
US6799733B1 (en) * 2000-06-28 2004-10-05 Siemens Automotive Corporation Fuel injector having a modified seat for enhanced compressed natural gas jet mixing
US6360440B1 (en) * 2000-09-13 2002-03-26 Delphi Technologies, Inc. Method for locating injector ball valve guide
DE10202722A1 (en) * 2002-01-24 2003-11-27 Siemens Ag Nozzle clamping nut for injector and method for manufacturing the nozzle clamping nut
DE10215980B4 (en) 2002-04-11 2008-03-27 Siemens Ag Leakage connection for a fuel injector
CN102252124B (en) * 2010-05-21 2013-07-24 北京亚新科天纬油泵油嘴股份有限公司 Electromagnetic valve applied to common rail fuel injector
JP5838014B2 (en) * 2012-11-09 2015-12-24 株式会社ノリタケカンパニーリミテド Fluid mixing device
FR3059052B1 (en) * 2016-11-23 2019-06-21 Delphi Technologies Ip Limited FUEL INJECTOR

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2807052A1 (en) * 1978-02-18 1979-08-23 Bosch Gmbh Robert ELECTROMAGNETIC FUEL INJECTION VALVE FOR COMBUSTION MACHINES
JPS5510016A (en) * 1978-07-06 1980-01-24 Nissan Motor Co Ltd Fuel injection valve
US4286623A (en) * 1978-11-10 1981-09-01 Moschoula Spanides Faucet control device
EP0042799A3 (en) * 1980-06-23 1982-01-13 The Bendix Corporation Electromagnetic fuel injector
DE3120160A1 (en) * 1981-05-21 1982-12-09 Robert Bosch Gmbh, 7000 Stuttgart ELECTROMAGNETICALLY ACTUABLE VALVE, ESPECIALLY FUEL INJECTION VALVE FOR FUEL INJECTION SYSTEMS
US4423841A (en) * 1982-01-28 1984-01-03 General Motors Corporation Electromagnetic fuel injector with pivotable armature stop
DE3427526A1 (en) * 1984-07-26 1986-02-06 Robert Bosch Gmbh, 7000 Stuttgart ELECTROMAGNETICALLY ACTUABLE VALVE
DE3878599T2 (en) * 1987-06-26 1993-09-23 Hitachi Ltd ELECTROMAGNETIC FUEL INJECTION VALVE.
DE3843862A1 (en) * 1988-12-24 1990-06-28 Bosch Gmbh Robert ELECTROMAGNETICALLY ACTUABLE VALVE

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9105951A1 *

Also Published As

Publication number Publication date
BR9007768A (en) 1992-08-11
DE3935148A1 (en) 1991-05-02
CS504290A3 (en) 1992-03-18
KR920704000A (en) 1992-12-18
US5209408A (en) 1993-05-11
WO1991005951A1 (en) 1991-05-02
JPH05501139A (en) 1993-03-04

Similar Documents

Publication Publication Date Title
EP0495793A1 (en) Electromagnetically operated fuel injection valve
EP0865574A1 (en) Fuel injection valve and method of producing the same
EP0796393B1 (en) Electromagnetically operable valve, especially fuel injection valve
WO2002068816A1 (en) Fuel injection valve with a filter bush
EP1062421B1 (en) Fuel injector
EP0812389A1 (en) Fuel injection valve
DE10122353B4 (en) Fuel injector
EP1651860A1 (en) Fuel injection valve and method for the assembly thereof
WO2004042225A1 (en) Fuel metering unit for the fuel injection system of a combustion engine
DE3328467A1 (en) ELECTROMAGNETICALLY ACTUABLE VALVE
DE3207918A1 (en) ELECTROMAGNETICALLY ACTUABLE VALVE
EP1088182A1 (en) Electromagnetic valve
EP1062422B1 (en) Method for mounting a valve module of a fuel injector
EP1042610B1 (en) Fuel injection valve
DE10116186A1 (en) Fuel injector
WO2000032926A1 (en) Fuel injection valve
EP0455758A1 (en) Electromagnetically operated fuel-injection valve.
EP0504147A1 (en) Electromagnetically operable fuel injection valve.
EP1706634A1 (en) Method for production of a fuel injection valve and fuel injection valve
DE102019205301A1 (en) Valve for metering a fluid
DE10118161A1 (en) Fuel injection valve has needle valve, valve seating surface forming seal-seating, armature, damping element, elastomeric damping segment and support disc
WO2003027489A1 (en) Fuel injection valve
DE102018219054A1 (en) Valve for metering a fluid
EP0890732A2 (en) Electromagnetically actuatable valve
WO2004101986A1 (en) Fuel injection valve

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19920317

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: THE APPLICATION HAS BEEN WITHDRAWN

18W Application withdrawn

Withdrawal date: 19930407