EP0558715A1 - Electromagnetically operable injection valve. - Google Patents

Electromagnetically operable injection valve.

Info

Publication number
EP0558715A1
EP0558715A1 EP92918897A EP92918897A EP0558715A1 EP 0558715 A1 EP0558715 A1 EP 0558715A1 EP 92918897 A EP92918897 A EP 92918897A EP 92918897 A EP92918897 A EP 92918897A EP 0558715 A1 EP0558715 A1 EP 0558715A1
Authority
EP
European Patent Office
Prior art keywords
valve
return spring
injector
injection valve
spring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP92918897A
Other languages
German (de)
French (fr)
Other versions
EP0558715B1 (en
Inventor
Ferdinand Reiter
Martin Maier
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 EP0558715A1 publication Critical patent/EP0558715A1/en
Application granted granted Critical
Publication of EP0558715B1 publication Critical patent/EP0558715B1/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
    • F02M51/00—Fuel-injection apparatus characterised by being operated electrically
    • F02M51/06—Injectors peculiar thereto with means directly operating the valve needle
    • 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
    • F02M61/20—Closing valves mechanically, e.g. arrangements of springs or weights or permanent magnets; Damping of valve lift
    • 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

Definitions

  • the invention is based on an electromagnetically actuated injection valve according to the preamble of the main claim.
  • the opening movement of a valve closing member interacting with a valve seat body is brought about by an armature lying in the magnetic field of a current-carrying winding via a needle sleeve connected to it, while the opposite closing movement by a valve sleeve via the needle sleeve to the valve firmly connected to it ⁇ closing member acting return spring is generated.
  • a return spring is already known (US Pat. No. 4,944,486), which is supported on a flat end face of an adjusting bush pressed into a flow bore in a core of the valve and acts on the valve closing member via the needle sleeve, a commercially available cylindrical helical spring being used is applied, at the two ends of which a turn is made and ground flat in order to achieve a uniform load on the contact surfaces.
  • the return spring is subjected to pressure and is just like the needle sleeve and that Valve closing member rotatably arranged in the flow bore relative to the core.
  • valve closing member By rotating the valve closing member with respect to the valve support body, the sealing surfaces have to constantly adapt to one another, which leads to a change in the valve stroke set first.
  • the change in the valve stroke has the result that the amount of fuel sprayed per stroke fluctuates accordingly, as a result of which the running behavior and consumption of the internal combustion engine deteriorate.
  • the electromagnetically actuated injection valve according to the invention with the characterizing features of the main claim has the advantage that it rotates the valve closing member relative to the valve seat body in a simple manner by means of a circumferentially positive connection of the return spring to the fixed adjusting sleeve on the one hand and the needle sleeve on the other hand is prevented.
  • valve seat body and the valve closing member lie at right angles to one another, so that the valve stroke remains unchanged after a one-off adjustment of the two sealing surfaces to one another.
  • the amount of fuel sprayed per stroke is essentially constant over the entire life of the valve.
  • a particularly advantageous embodiment is one in which the ends of the return spring are angled toward a valve longitudinal axis, so that the sharp-edged spring ends do not scrape along their surface when they are inserted into the flow bore. This eliminates the risk that chips produced in this way impair the functionality of the injection valve.
  • a complete U-shaped bending of the spring ends in the direction of the valve longitudinal axis prevents the return springs, e.g. in transport containers, chopping among each other and having to be separated before assembly.
  • FIG. 1 shows a fuel injection valve designed according to the invention
  • FIGS. 2 to 5 each show an exemplary embodiment of a return spring according to the invention.
  • the injection valve shown in FIG. 1 of the drawing for an electromagnetically actuated injection valve for fuel injection systems of, in particular, mixture-compressing externally ignited internal combustion engines has a core 2, which is surrounded by a magnet coil 1 and serves as a fuel inlet connector.
  • the magnet coil 1 with a coil body 3 is, for example provided with a plastic extrusion 5, at the same time an electrical connector 6 ' is also injected.
  • the coil body 3 of the magnetic coil 1, which is stepped in the radial direction, has a winding 7 which is stepped in the radial direction.
  • a tubular, metallic intermediate part 12 is tightly connected concentrically to a longitudinal valve axis 11, for example by welding, and in this case partially overlaps the core end 10 axially with an upper cylinder section 14.
  • the stepped bobbin 3 partially overlaps the core 2 and with a step 15 of larger internal diameter the upper cylinder section 14 of the intermediate part 12.
  • the intermediate part 12 is provided at its end facing away from the core 2 with a lower cylinder section 18 which overlaps a tubular nozzle carrier 19 and with this is tightly connected, for example by welding.
  • a cylindrical valve seat body 20 is tightly mounted by welding in a through bore 22 running concentrically to the valve longitudinal axis 11.
  • the valve seat body 20 has a fixed valve seat 21 facing the magnetic coil 1, downstream of which, for example, two spray openings 23 are formed in the valve seat body 20. Downstream of the spray openings 23, the valve seat body 20 has a processing bore 24 which widens in the shape of a truncated cone in the direction of flow.
  • a tubular adjusting bushing 27 is pressed into a stepped flow bore 25 of the core 2 that runs concentrically to the valve longitudinal axis 11.
  • the return spring 26, for example a helical spring, rests with one end on an end face 28 of the adjusting bushing 27 facing the valve seat body 20.
  • the press-in depth of the adjusting bush 27 into the flow bore 25 of the core 2 determines the spring force of the return spring 26 and thus also influences the dynamic fuel quantity emitted during the opening and closing stroke of the injection valve.
  • the return spring 26 With the end facing away from the adjusting bush 27, the return spring 26 is supported in the downstream direction against an end face 50 of a needle sleeve 51.
  • Two opposite spring ends 52, 53 of the return spring 26 are bent parallel to the longitudinal valve axis 11 relative to a spring winding 54 of the return spring 26 over a length that corresponds, for example, to a three-quarter turn, as FIG. 2 of the drawing shows more clearly.
  • the bent spring ends 52, 53 which extend in the continuation of the circumference of the return spring 26, can run such that they are aligned with one another or are rotated at an angle to one another.
  • a further angling prevents chips which are produced on the surface of the flow bore 25 by scraping the sharp-edged spring ends 52, 53 from affecting the functionality of the valve.
  • a transverse section 69 of the spring end 52, 53 extending transversely to the interior of the return spring 26 is formed on a longitudinal section 68 running parallel to the longitudinal valve axis 11.
  • the cross section 69 can, for example, have an almost straight shape as shown in FIG. 3 or may be bent towards the windings, as shown in FIG.
  • Winding of the return spring 26 ends has the further advantage that the spring ends 52, 53 of the return springs 26 no longer interlock.
  • the upstream spring end 52 engages in a corresponding recess 45 of the adjusting bushing 27, which is provided eccentrically, parallel to the longitudinal valve axis 11 and e.g. is formed as a slot extending over the entire length of a wall of the adjusting bush.
  • the downstream spring end 53 engages in the same way in a corresponding recess 46 of the needle sleeve 51, which is also eccentric, parallel to the valve axis 11 and e.g. is formed as a slot extending over the entire length of a wall of the needle sleeve 51.
  • the inventive design and arrangement of the return spring 26 enables the transmission of reaction forces which are directed opposite the hydraulic forces acting on the valve closing member 55 in the circumferential direction, so that a constant position in the circumferential direction of the valve seat body 20 to the valve closing member 55 is ensured. Due to the bent or U-shaped design of the spring ends 52, 53, the catch spring 26, e.g. prevented during transport, as well as a release of chips from the surface of the flow bore 25 during assembly.
  • a tube-shaped armature 49 is connected to the end of the needle sleeve 51 facing the return spring 26, for example by welding.
  • an axial gap 59 is formed, in which, by clamping, a residual air gap between an inlet-side end face 60 of the armature 49 and the End face 57 of the core 10, which forms the non-magnetic stop disk 62 and limits the stroke of the valve closing member 55 during the opening process of the valve.
  • the magnetic coil 1 is at least partially surrounded by at least one guide element 64, for example in the form of a bracket, which serves as a ferromagnetic element and has one end against the core 2 and the other end against the nozzle carrier 19 and with these e.g. is connected by welding or soldering.
  • guide element 64 for example in the form of a bracket, which serves as a ferromagnetic element and has one end against the core 2 and the other end against the nozzle carrier 19 and with these e.g. is connected by welding or soldering.
  • a part of the valve is enclosed by a plastic jacket 65, which extends from the core 2 in the axial direction over the magnet coil 1 with connector 6 and the at least one guide element 64.

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

Un injecteur à commande électromagnétique de la technique antérieure met en oeuvre un ressort de rappel hélicoïdal dont les extrémités sont comprimées et ont subi une rectification plane. Un organe de fermeture de soupape et un corps de siège de soupape peuvent tourner circonférentiellement l'un par rapport à l'autre, de sorte que le nouvel ajustement en continu des faces d'étanchéité l'une par rapport à l'autre se traduit par une course qui se modifie en cours de fonctionnement et s'accompagne, en conséquence, de variations de la quantité de carburant injecté par course. Le nouvel injecteur comporte un ressort de rappel (26) dont les extrémités (52, 53) sont recourbées, s'étendent axialement et parallèlement à un axe longitudinal (11) et s'engagent, de manière à ne pas tourner, dans des évidements (45) et (46) d'une douille de réglage fixe (27) d'une part et d'une douille à aiguilles (51) d'autre part. Grâce à la position angulaire conforme du corps de siège d'injecteur (21) par rapport à l'organe de fermeture d'injecteur (55) pendant toute la durée de vie de l'injecteur, le processus d'ajustement des deux pièces se limite à une phase de rodage unique. Le nouvel injecteur convient notamment pour des systèmes d'injection de carburant dans des moteurs à combustion interne à allumage par bougie et à compression du mélange.An electromagnetically controlled injector of the prior art uses a helical return spring, the ends of which are compressed and have undergone a plane grinding. A valve closure member and a valve seat body can rotate circumferentially with respect to each other, so that the new continuous adjustment of the sealing faces to each other results in by a stroke which changes during operation and is consequently accompanied by variations in the quantity of fuel injected per stroke. The new injector comprises a return spring (26) whose ends (52, 53) are curved, extend axially and parallel to a longitudinal axis (11) and engage, so as not to rotate, in recesses (45) and (46) of a fixed adjustment sleeve (27) on the one hand and of a needle sleeve (51) on the other hand. Thanks to the conforming angular position of the injector seat body (21) with respect to the injector closure member (55) during the entire life of the injector, the adjustment process of the two parts takes place. limited to a single running-in phase. The new injector is particularly suitable for fuel injection systems in internal combustion engines with spark plug ignition and compression of the mixture.

Description

Elektromagnetisch betäti bares EinspritzventilElectromagnetically actuated injection valve
Stand der TechnikState of the art
Die Erfindung geht aus von einem elektromagnetisch betätigbaren Ein¬ spritzventil nach der Gattung des Hauptanspruchs. Die Öffnungsbewe¬ gung eines mit einem Ventilsitzkörper zusammenwirkenden Ventil¬ schließgliedes wird durch einen im Magnetfeld einer stromdurchflos- sen Wicklung liegenden Anker über eine mit diesem verbundene Nadel¬ hülse bewirkt, während die entgegengesetzte Schließbewegung durch eine über die Nadelhülse auf das fest mit dieser verbundene Ventil¬ schließglied wirkende Rückstellfeder erzeugt wird.The invention is based on an electromagnetically actuated injection valve according to the preamble of the main claim. The opening movement of a valve closing member interacting with a valve seat body is brought about by an armature lying in the magnetic field of a current-carrying winding via a needle sleeve connected to it, while the opposite closing movement by a valve sleeve via the needle sleeve to the valve firmly connected to it ¬ closing member acting return spring is generated.
Es ist schon eine Rückstellfeder bekannt (US-PS 4.944.486), die sich an einer ebenen Stirnseite einer in eine Strömungsbohrung eines Kerns des Ventils eingepreßten Einstellbuchse abstützt und über die Nadelhülse auf das Ventilschließglied wirkt, wobei eine handelsübli¬ che, zylindrische Schraubenfeder verwendet wird, an deren beiden En¬ den je eine Windung angelegt und plan abgeschliffen ist um eine gleichmäßige Beanspruchung der Auflageflächen zu erreichen. Die Rückstellfeder wird auf Druck beansprucht und ist ebenso wie die Na- delhülse und das Ventilschließglied gegenüber dem Kern drehbar in der Stömungsbohrung angeordnet.A return spring is already known (US Pat. No. 4,944,486), which is supported on a flat end face of an adjusting bush pressed into a flow bore in a core of the valve and acts on the valve closing member via the needle sleeve, a commercially available cylindrical helical spring being used is applied, at the two ends of which a turn is made and ground flat in order to achieve a uniform load on the contact surfaces. The return spring is subjected to pressure and is just like the needle sleeve and that Valve closing member rotatably arranged in the flow bore relative to the core.
Die im Betrieb auf das Ventilschließglied wirkenden hydraulischen Kräfte in Umfangsrichtung bewirken ein Verdrehen gegenüber dem Ven¬ tilsitzkörper, das durch die an den jeweiligen Berührflächen zwi¬ schen der verdrehbaren Rückstellfeder und der -feststehenden Ein¬ stellbuchse einerseits sowie der Rückstellfeder und der Nadelhülse andererseits auftretenden Reibkräfte, die durch die Relativbewegung der betreffenden Bauteile zueinander entstehen, nur ungenügend ver¬ hindert wird.The hydraulic forces acting on the valve closing member in the circumferential direction during operation cause a rotation relative to the valve seat body, which is caused by the frictional forces occurring on the respective contact surfaces between the rotatable return spring and the fixed adjusting bush on the one hand and the return spring and the needle sleeve on the other hand which are caused by the relative movement of the relevant components relative to one another is insufficiently prevented.
Durch das Verdrehen des Ventilschließglieds gegenüber dem Ventil- sϊtzkörper müssen sich die Dichtflächen stetig neu aneinander anpas¬ sen, was zu einer Änderung des zuerst eingestellten Ventilhubs führt. Die Änderung des Ventilhubs hat zur Folge, daß die pro Hub abgespritzte Brennstoffmenge entspechend schwankt, wodurch sich Laufverhalten und Verbrauch der Brennkraftmaschine verschlechtem.By rotating the valve closing member with respect to the valve support body, the sealing surfaces have to constantly adapt to one another, which leads to a change in the valve stroke set first. The change in the valve stroke has the result that the amount of fuel sprayed per stroke fluctuates accordingly, as a result of which the running behavior and consumption of the internal combustion engine deteriorate.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße, elektromagnetisch betätigbare Einspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegen¬ über den Vorteil, daß bei ihm auf einfache Art und Weise ein Verdre¬ hen des Ventilschließgliedes gegenüber dem Ventilsitzkörper durch eine in Umfangsrichtung formschlüssige Verbindung der Rückstellfeder mit der feststehenden Einstellhülse einerseits und der Nadelhülse andererseits verhindert wird.In contrast, the electromagnetically actuated injection valve according to the invention with the characterizing features of the main claim has the advantage that it rotates the valve closing member relative to the valve seat body in a simple manner by means of a circumferentially positive connection of the return spring to the fixed adjusting sleeve on the one hand and the needle sleeve on the other hand is prevented.
Somit liegen der Ventilsitzkörper und das Ventilschließglied winkel¬ treu zueinander, so daß der Ventilhub nach einer einmaligen Anpas¬ sung der beiden Dichtflächen aneinander unverändert bleibt. Die pro Hub abgespritzt Brennstoffmenge ist über der gesamte Lebensdauer des Ventils im wesentlichen konstant. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vor¬ teilhafte Weiterbildungen und Verbesserungen des im Hauptanspruch angegebenen Einspritzventils möglich.Thus, the valve seat body and the valve closing member lie at right angles to one another, so that the valve stroke remains unchanged after a one-off adjustment of the two sealing surfaces to one another. The amount of fuel sprayed per stroke is essentially constant over the entire life of the valve. Advantageous further developments and improvements of the injection valve specified in the main claim are possible through the measures listed in the subclaims.
Besonders vorteilhaft ist eine Ausführung, bei der die Enden der Rückstellfeder zu einer Ventillängsachse hin abgewinkelt sind, so daß die scharfkantigen Federenden beim Einführen in die Strömungs¬ bohrung nicht an deren Oberfläche entlangschaben. Somit ist die Ge¬ fahr ausgeschlossen, daß hierbei entstehende Späne die Funktions¬ fähigkeit des Einspritzventils beinträchtigen. Ein vollständiges U-förmiges Umbiegen der Federenden in Richtung der Ventillängsachse verhindert, daß sich die Rückstellfedern, z.B. in Transportbehäl¬ tern, untereinander verhacken und vor der Montage erst aufwendig ge¬ trennt werden müssen.A particularly advantageous embodiment is one in which the ends of the return spring are angled toward a valve longitudinal axis, so that the sharp-edged spring ends do not scrape along their surface when they are inserted into the flow bore. This eliminates the risk that chips produced in this way impair the functionality of the injection valve. A complete U-shaped bending of the spring ends in the direction of the valve longitudinal axis prevents the return springs, e.g. in transport containers, chopping among each other and having to be separated before assembly.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 ein erfindungsgemäße ausgebildetes Brennstoffein¬ spritzventil, Figur 2 bis 5 je ein Ausführungsbeispiel einer erfin¬ dungsgemäßen Rückstellfeder.Embodiments of the invention are shown in simplified form in the drawing and explained in more detail in the following description. FIG. 1 shows a fuel injection valve designed according to the invention, FIGS. 2 to 5 each show an exemplary embodiment of a return spring according to the invention.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Das in Figur 1 der Zeichnung beispielhaft für ein elektromagnetisch betätigbares Einspritzventil dargestellte Einspritzventil für Brenn- stoffeinspritzanlagen von insbesondere gemischverdichtenden fremdge¬ zündeten Brennkraftmaschinen hat einen von einer Magnetspule 1 umge¬ benen, als Brennstoffeinlaßstutzen dienenden Kern 2. Die Magnetspule 1 mit einem Spulenkörper 3 ist z.B. mit einer Kunststoffumspritzung 5 versehen, wobei zugleich ein elektrischer Anschlußstecker 6' mitangespritzt ist. Der in radialer Richtung gestufte Spulenkörper 3 der Magnetspule 1 weist eine in radialer Richtung gestufte Bewick¬ lung 7 auf. Mit einem unteren Kernende 10 des Kerns 2 ist konzen¬ trisch zu einer Ventillängsachse 11 dicht ein rohrförmiges, metalle¬ nes Zwischenteil 12 beispielsweise durch Schweißen verbunden und übergreift dabei mit einem oberen Zylinderabschnitt 14 das Kernende 10 teilweise axial. Der gestufte Spulenkörper 3 übergreift teilweise den Kern 2 und mit einer Stufe 15 größeren Innendurchmessers den oberen Zylinderabschnitt 14 des Zwischenteils 12. Das Zwischenteil 12 ist an seinem dem Kern 2 abgewandten Ende mit einem unteren Zylinderabschitt 18 versehen, der einen rohrförmigen Düsenträger 19 übergreift und mit diesem beispielsweise durch Schweißen dicht ver¬ bunden ist. In das stromabwärts liegende Ende des Düsenträgers 19 ist in einer konzentrisch zu der Ventillängsachse 11 verlaufenden Durchgangsbohrung 22 ein zylinderförmiger Ventilsitzkörper 20 durch Schweißen dicht montiert. Der Ventilsitzkörper 20 weist der Magnet¬ spule 1 zugewandt einen festen Ventilsitz 21 auf, stromabwärts des¬ sen im Ventilsitzkörper 20 z.B. zwei Abspritzöffnungen 23 ausgebil¬ det sind. Stromabwärts der Abspritzöffnungen 23 weist der Ventil¬ sitzkörper 20 eine sich in Strömungsrichtung kegelstumpfförmig erweiternde Auf ereitungsbohrung 24 auf.The injection valve shown in FIG. 1 of the drawing for an electromagnetically actuated injection valve for fuel injection systems of, in particular, mixture-compressing externally ignited internal combustion engines has a core 2, which is surrounded by a magnet coil 1 and serves as a fuel inlet connector. The magnet coil 1 with a coil body 3 is, for example provided with a plastic extrusion 5, at the same time an electrical connector 6 ' is also injected. The coil body 3 of the magnetic coil 1, which is stepped in the radial direction, has a winding 7 which is stepped in the radial direction. With a lower core end 10 of the core 2, a tubular, metallic intermediate part 12 is tightly connected concentrically to a longitudinal valve axis 11, for example by welding, and in this case partially overlaps the core end 10 axially with an upper cylinder section 14. The stepped bobbin 3 partially overlaps the core 2 and with a step 15 of larger internal diameter the upper cylinder section 14 of the intermediate part 12. The intermediate part 12 is provided at its end facing away from the core 2 with a lower cylinder section 18 which overlaps a tubular nozzle carrier 19 and with this is tightly connected, for example by welding. In the downstream end of the nozzle carrier 19, a cylindrical valve seat body 20 is tightly mounted by welding in a through bore 22 running concentrically to the valve longitudinal axis 11. The valve seat body 20 has a fixed valve seat 21 facing the magnetic coil 1, downstream of which, for example, two spray openings 23 are formed in the valve seat body 20. Downstream of the spray openings 23, the valve seat body 20 has a processing bore 24 which widens in the shape of a truncated cone in the direction of flow.
In eine konzentrisch zu der Ventillängsachse 11 verlaufende, abge¬ stufte Strömungsbohrung 25 des Kerns 2 ist zur Einstellung der Fe¬ derkraft einer Rückstellfeder 26 eine rohrförmige Einstellbuchse 27 eingepreßt. Die Rückstellfeder 26, z.B. eine Schraubenfeder, liegt mit einem Ende an einer dem Ventilsitzkörper 20 zugewandten Stirn¬ seite 28 der Einstellbuchse 27 an. Die Einpreßtiefe der Einstell¬ buchse 27 in die Strömungsbohrung 25 des Kerns 2 bestimmt die Feder¬ kraft der Rückstellfeder 26 und beeinflußt damit auch die dynami¬ sche, während des Offnungs- und des Schließhubs des Einspritzventils abgegebene Brennstoffmenge. Mit dem der Einstellbuchse 27 abgewandten Ende stützt sich die Rück¬ stellfeder 26 in stromabwärtiger Richtung gegen eine Stirnseite 50 einer Nadelhülse 51 ab.In order to adjust the spring force of a return spring 26, a tubular adjusting bushing 27 is pressed into a stepped flow bore 25 of the core 2 that runs concentrically to the valve longitudinal axis 11. The return spring 26, for example a helical spring, rests with one end on an end face 28 of the adjusting bushing 27 facing the valve seat body 20. The press-in depth of the adjusting bush 27 into the flow bore 25 of the core 2 determines the spring force of the return spring 26 and thus also influences the dynamic fuel quantity emitted during the opening and closing stroke of the injection valve. With the end facing away from the adjusting bush 27, the return spring 26 is supported in the downstream direction against an end face 50 of a needle sleeve 51.
Zwei gegenüberliegende Federenden 52, 53 der Rückstellfeder 26 sind gegenüber einer Federwicklung 54 der Rückstellfeder 26 auf einer Länge, die beispielsweise einer dreiviertel Windung entspricht, parallel zur Ventillängsachse 11 abgebogen, wie Figur 2 der Zeich¬ nung deutlicher zeigt. Dabei können die abgebogenen Federenden 52, 53, die sich in der Fortsetzung des Umfangs der Rückstellfeder 26 erstrecken, so verlaufen, daß sie zueinander fluchten oder um einen Winkel gegeneinander verdreht sind.Two opposite spring ends 52, 53 of the return spring 26 are bent parallel to the longitudinal valve axis 11 relative to a spring winding 54 of the return spring 26 over a length that corresponds, for example, to a three-quarter turn, as FIG. 2 of the drawing shows more clearly. The bent spring ends 52, 53, which extend in the continuation of the circumference of the return spring 26, can run such that they are aligned with one another or are rotated at an angle to one another.
Durch eine weitere Abwinklung, wie in Figur 3 und 4 der Zeichnung dargestellt, wird verhindert, daß bei der Montage durch Schaben der scharfkantigen Federenden 52, 53 auf der Oberfläche der Strömungs¬ bohrung 25 entstehende Späne die Funktionsfähigkeit des Ventils be¬ einträchtigen. Hierfür ist bei der Ausführung nach Figur 3 an einem parallel zur Ventillangsachse 11 verlaufenden Längsabschnitt 68 ein sich quer dazu ins Innere der Rückstellfeder 26 erstreckender Quer¬ abschnitt 69 des Federendes 52, 53 ausgebildet. Der Querabschnitt 69 kann z.B. eine in Figur 3 gezeigte nahezu gerade Form haben oder zu den Windungen hin gebogen sein, wie es Figur 4 zeigt. Eine, wie in Figur 5 der Zeichnung dargestellt, U-förmige Ausbildung der Federen¬ den 52, 52 derart, daß sich jeweils einem parallel zur Ventillängs¬ achse 11 am Umfang der Rückstellfeder 26 erstreckenden Längsab¬ schnitt 68 ein zur Ventillängsachse 11 gewandter bogenförmiger Quer¬ abschnitt 69 anschließt, der beispielsweise einen Durchmesser auf¬ weist, der dem Radius der Federwicklung 54 entspricht und in einem wiederum zur Ventillängsachse 11 parallelen Längsabschnitt 70 aus¬ läuft, der kurz vor der dem Abschnitt 70 nächstliegenden - 6 -A further angling, as shown in FIGS. 3 and 4 of the drawing, prevents chips which are produced on the surface of the flow bore 25 by scraping the sharp-edged spring ends 52, 53 from affecting the functionality of the valve. For this purpose, in the embodiment according to FIG. 3, a transverse section 69 of the spring end 52, 53 extending transversely to the interior of the return spring 26 is formed on a longitudinal section 68 running parallel to the longitudinal valve axis 11. The cross section 69 can, for example, have an almost straight shape as shown in FIG. 3 or may be bent towards the windings, as shown in FIG. A, as shown in Figure 5 of the drawing, U-shaped design of the spring ends 52, 52 such that a longitudinal section 68 extending parallel to the longitudinal valve axis 11 on the circumference of the return spring 26 extends an arcuate cross facing the longitudinal valve axis 11 ¬ section 69 connects, for example, has a diameter that corresponds to the radius of the spring winding 54 and ends in a longitudinal section 70, again parallel to the valve longitudinal axis 11, which is just before the section 70 closest - 6 -
Windung der Rückstellfeder 26 endet, bringt den weiteren Vorteil mit sich, daß sich die Federenden 52, 53 der Rückstellfedern 26 nicht mehr untereinander verhaken.Winding of the return spring 26 ends, has the further advantage that the spring ends 52, 53 of the return springs 26 no longer interlock.
Das stromaufwärts gerichtete Federende 52 greift verdrehsicher in eine entsprechende Ausnehmung 45 der Einstellbuchse 27, die exzen¬ trisch, parallel zur Ventillängsachse 11 vorgesehen und z.B. als sich über die gesamte Länge einer Wandung der Einstellbuchse er¬ streckender Schlitz ausgebildet ist. Das stromabwärts gerichtete Fe¬ derende 53 greift in gleicher Art und Weise in eine entsprechende Ausnehmung 46 der Nadelhülse 51, die ebenso exzentrisch, parallel zur Ventilachse 11 vorgesehen und z.B. als sich über die gesamte Länge einer Wandung der Nadelhülse 51 erstreckender Schlitz ausge- bildetet ist.The upstream spring end 52 engages in a corresponding recess 45 of the adjusting bushing 27, which is provided eccentrically, parallel to the longitudinal valve axis 11 and e.g. is formed as a slot extending over the entire length of a wall of the adjusting bush. The downstream spring end 53 engages in the same way in a corresponding recess 46 of the needle sleeve 51, which is also eccentric, parallel to the valve axis 11 and e.g. is formed as a slot extending over the entire length of a wall of the needle sleeve 51.
Die erfindungsgemäße Ausbildung und Anordnung der Rückstellfeder 26 ermöglicht die Übertragung von Reaktionskräften, die entgegengesetzt den am Ventilschließglied 55 angreifenden hydraulischen Kräften in Umfangsrichtung gerichtet sind, so daß eine in Umfangsrichtung gleichbleibende Lage des Ventilsitzkörpers 20 zum Ventilschließglied 55 gewährleistet ist. Durch die abgebogene bzw. U-förmige Ausbildung der Federenden 52, 53 wird ein Verhaken der Rüchstellfeder 26, z.B. während des Transportes, sowie ein Auslösen von Spänen aus der Ober¬ fläche der Strömungsbohrung 25 bei der Montage verhindert.The inventive design and arrangement of the return spring 26 enables the transmission of reaction forces which are directed opposite the hydraulic forces acting on the valve closing member 55 in the circumferential direction, so that a constant position in the circumferential direction of the valve seat body 20 to the valve closing member 55 is ensured. Due to the bent or U-shaped design of the spring ends 52, 53, the catch spring 26, e.g. prevented during transport, as well as a release of chips from the surface of the flow bore 25 during assembly.
Die an der Oberfläche des Ventilsitzes 21 und des Ventilschließ- glieds 55 vorhandenen Oberflächenrauheiten glätten sich während der ersten Betriebszeit, wodurch sich der Ventilhub geringfügig ändert. Dieser Anpassungsprozeß wird bei dem erfindungsgemäßen Einspritzven¬ til auf eine einmalige Einlaufphase reduziert. Mit dem der Rückstellfeder 26 zugewandten Ende der Nadelhülse 51 ist beispielsweise durch Schweißen ein rohrför iger Anker 49 verbunden. Zwischen einer Stirnseite 57 des dem Anker 49 zugewandten Kernendes 10 und einer zum oberen Zylinderabschnitt 14 führenden Schulter 58 des Zwischenteiles 12 ist ein axialer Spalt 59 gebildet, in dem durch Einklemmen eine, einen Restluftspalt zwischen einer zulaufsei- tigen Stirnseite 60 des Ankers 49 und der Stirnseite 57 des Kernen¬ des 10 bildende, den Hub des Ventilschließglieds 55 beim Öffnungs¬ vorgang des Ventils begrenzende, nichtmagnetische Anschlagscheibe 62 angeordnet ist.The surface roughness present on the surface of the valve seat 21 and the valve closing member 55 smoothen during the first operating time, as a result of which the valve lift changes slightly. In the injection valve according to the invention, this adaptation process is reduced to a one-time running-in phase. A tube-shaped armature 49 is connected to the end of the needle sleeve 51 facing the return spring 26, for example by welding. Between an end face 57 of the core end 10 facing the armature 49 and a shoulder 58 of the intermediate part 12 leading to the upper cylinder section 14, an axial gap 59 is formed, in which, by clamping, a residual air gap between an inlet-side end face 60 of the armature 49 and the End face 57 of the core 10, which forms the non-magnetic stop disk 62 and limits the stroke of the valve closing member 55 during the opening process of the valve.
Die Magnetspule 1 ist von wenigstens einem, beispielsweise als Bügel ausgebildeten, als ferromagnetisches Element dienenden Leitelement 64 wenigstens teilweise umgeben, das mit seinem einen Ende an dem Kern 2 und mit seinem anderen Ende an dem Düsenträger 19 anliegt und mit diesen z.B. durch Schweißen oder Löten verbunden ist.The magnetic coil 1 is at least partially surrounded by at least one guide element 64, for example in the form of a bracket, which serves as a ferromagnetic element and has one end against the core 2 and the other end against the nozzle carrier 19 and with these e.g. is connected by welding or soldering.
Ein Teil des Ventils ist von einer Kunststoffummantelung 65 um¬ schlossen, die sich vom Kern 2 ausgehend in axialer Richtung über die Magnetspule 1 mit Anschlußstecker 6 und das wenigstens eine Leitelement 64 erstreckt. A part of the valve is enclosed by a plastic jacket 65, which extends from the core 2 in the axial direction over the magnet coil 1 with connector 6 and the at least one guide element 64.

Claims

- aAnsprüche - claims
1. Elektromagnetisch betätigbares Einspritzventil für Brennstoffein- spritzanlagen von Brennkraftmaschinen, mit einem sich entlang einer Ventillängsachse erstreckenden metallenen Kern, mit einer Magnetspu¬ le und einem Anker, durch den ein mit einem festen Ventilsitz zusam¬ menwirkendes Ventilschließglied betätigbar ist, und einer in eine konzentrisch zu der Ventill ngsachse ausgebildeten Strömungsbohrung des Kerns eingepreßten zylindrischen Einstellbuchse, an der sich ei¬ ne Rückstellfeder abstützt, die andererseits an einer Nadelhülse an¬ greift, die mit dem Ventilschließglied verbunden ist, dadurch ge¬ kennzeichnet, daß die Rückstellfeder (26) an ihren beiden Enden ab¬ gebogen ist, wobei das der Einstellbuchse (27) zugewandte Federende (52) in eine Ausnehmung (45) der Einstellbuchse (27) und das der Na¬ delhülse (51) zugewandte Federende (53) in eine Ausnehmung (46) der Nadelhülse (51) in Umfangsrichtung formschlüssig eingreift.1. Electromagnetically actuated injection valve for fuel injection systems of internal combustion engines, with a metal core which extends along a longitudinal axis of the valve, with a magnet coil and an armature, by means of which a valve closing member cooperating with a fixed valve seat can be actuated, and one in a concentric manner cylindrical adjusting bush pressed into the flow axis of the core, on which a return spring is supported, which, on the other hand, engages a needle sleeve which is connected to the valve closing member, characterized in that the return spring (26) rests on it is bent at both ends, the spring end (52) facing the adjusting bush (27) into a recess (45) of the adjusting bush (27) and the spring end (53) facing the needle sleeve (51) into a recess (46) the needle sleeve (51) engages positively in the circumferential direction.
2. Einspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die beiden Federenden (52, 53) der Rückstellfeder (26) je einen parallel zur Ventillängsachse (11) verlaufenden, geradlinigen Längsabschnitt (68) aufweisen.2. Injection valve according to claim 1, characterized in that the two spring ends (52, 53) of the return spring (26) each have a straight longitudinal section (68) extending parallel to the valve longitudinal axis (11).
3. Einspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß sich dem Längsabschnitt (68) ein ins Innere der Rückstellfeder (26) ge¬ richteter Querabschnitt (69) anschließt.3. Injection valve according to claim 2, characterized in that the longitudinal section (68) in the interior of the return spring (26) ge-directed cross section (69) connects.
4. Einspritzventil nach Anspruch 3, dadurch gekennzeichnet, daß der Querabschnitt (69) bogenförmig ausgebildet ist.4. Injection valve according to claim 3, characterized in that the transverse section (69) is arcuate.
5. Einspritzventil nach Anspruch 4, dadurch gekennzeichnet, daß sich dem Längsabschnitt (69) ein zur Ventillängsachse (11) paralleler, geradliniger Längsabschnitt (70) anschließt. 5. Injection valve according to claim 4, characterized in that the longitudinal section (69) adjoins a straight longitudinal section (70) parallel to the valve longitudinal axis (11).
6. Einspritzventil nach Anspruch 1 bis 5, dadurch gekennzeichnet, daß die Federenden (52, 53) in beliebiger Weise zueinander fluchtend oder zueinander versetzt angeordnet sind. 6. Injection valve according to claim 1 to 5, characterized in that the spring ends (52, 53) are arranged in any manner in alignment or offset from one another.
EP92918897A 1991-09-21 1992-09-02 Electromagnetically operable injection valve Expired - Lifetime EP0558715B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4131500A DE4131500A1 (en) 1991-09-21 1991-09-21 ELECTROMAGNETICALLY OPERATED INJECTION VALVE
DE4131500 1991-09-21
PCT/DE1992/000727 WO1993006360A1 (en) 1991-09-21 1992-09-02 Electromagnetically operable injection valve

Publications (2)

Publication Number Publication Date
EP0558715A1 true EP0558715A1 (en) 1993-09-08
EP0558715B1 EP0558715B1 (en) 1995-06-28

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Country Status (6)

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US (1) US5360197A (en)
EP (1) EP0558715B1 (en)
JP (1) JPH06502903A (en)
KR (1) KR930702607A (en)
DE (2) DE4131500A1 (en)
WO (1) WO1993006360A1 (en)

Families Citing this family (23)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5842502A (en) * 1992-10-23 1998-12-01 Palmer; David W. System for controlling flow through a process region
US5494223A (en) * 1994-08-18 1996-02-27 Siemens Automotive L.P. Fuel injector having improved parallelism of impacting armature surface to impacted stop surface
JP3245035B2 (en) * 1996-01-19 2002-01-07 三菱電機株式会社 Air control valve
US5918818A (en) * 1996-05-22 1999-07-06 Denso Corporation Electromagnetically actuated injection valve
US5848780A (en) * 1997-06-05 1998-12-15 Liberty Controls, Inc. Straight fluid flow solenoid valve
DE19730202A1 (en) * 1997-07-15 1999-01-21 Bosch Gmbh Robert Electromagnetically actuated valve
DE19739850A1 (en) * 1997-09-11 1999-03-18 Bosch Gmbh Robert Electromagnetically actuated valve
DE10048597A1 (en) * 2000-09-30 2002-04-11 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10109411A1 (en) 2001-02-28 2002-09-05 Bosch Gmbh Robert Fuel injector
DE10142302A1 (en) * 2001-08-29 2003-03-20 Bosch Gmbh Robert Fuel injection valve, for the direct fuel injection at an IC motor, has a guide sleeve for the armature return spring, within an axial recess at the valve needle to give a force fit bond with the armature and a firm seating for the spring
US6644568B1 (en) 2002-10-24 2003-11-11 Visteon Global Technologies, Inc. Fuel injector with spiral-wound spring adjustment tube
DE102004025079A1 (en) * 2004-05-21 2005-12-08 Robert Bosch Gmbh Fuel injector
DE102004028523A1 (en) * 2004-06-11 2005-12-29 Robert Bosch Gmbh Fuel injector with clamping sleeve as stop for valve needle
DE102006002664A1 (en) * 2006-01-19 2007-08-02 Robert Bosch Gmbh magnetic valve
CN201169816Y (en) * 2007-12-27 2008-12-24 上海科勒电子科技有限公司 Flushing control valve core
DE102008040068B4 (en) * 2008-07-02 2019-07-18 Robert Bosch Gmbh Concave air gap limitation with solenoid valve
US8286896B2 (en) * 2010-03-26 2012-10-16 Delphi Technologies, Inc. Valve seat and shroud for gaseous fuel injector
KR101869119B1 (en) * 2010-12-14 2018-06-19 베에스하 하우스게랫테 게엠베하 Gas valve unit comprising an actuation mechanism for a solenoid valve
FR2982327B1 (en) * 2011-11-07 2013-11-29 Delphi Tech Holding Sarl CAP ASSEMBLY FOR HIGH PRESSURE VALVE
GB2519171B (en) * 2013-10-14 2016-02-17 Redd & Whyte Ltd Micro-Valve
JP6400372B2 (en) * 2014-07-31 2018-10-03 Ntn株式会社 Spool valve
JP6187563B2 (en) * 2015-09-28 2017-08-30 株式会社デンソー Fuel injection valve
JP7116609B2 (en) * 2018-07-05 2022-08-10 株式会社Soken fuel injector

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US189153A (en) * 1877-04-03 Improvement in attachments for automatically closing cocks and faucets
DE3825134A1 (en) * 1988-07-23 1990-01-25 Bosch Gmbh Robert ELECTROMAGNETICALLY ACTUABLE VALVE AND METHOD FOR THE PRODUCTION THEREOF
JPH0318662A (en) * 1989-05-29 1991-01-28 Aisan Ind Co Ltd Nozzle structure of electromagnetic fuel injection valve
DE4003227C1 (en) * 1990-02-03 1991-01-03 Robert Bosch Gmbh, 7000 Stuttgart, De EM fuel injection valve for IC engine - has two overlapping parts welded together as narrowed section of one part
DE4003228A1 (en) * 1990-02-03 1991-08-22 Bosch Gmbh Robert ELECTROMAGNETICALLY ACTUABLE VALVE
US5301874A (en) * 1990-05-26 1994-04-12 Robert Bosch Gmbh Adjusting sleeve for an electromagnetically actuatable valve

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9306360A1 *

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Publication number Publication date
DE4131500A1 (en) 1993-03-25
JPH06502903A (en) 1994-03-31
KR930702607A (en) 1993-09-09
US5360197A (en) 1994-11-01
DE59202731D1 (en) 1995-08-03
EP0558715B1 (en) 1995-06-28
WO1993006360A1 (en) 1993-04-01

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