EP1490593A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP1490593A1
EP1490593A1 EP03731607A EP03731607A EP1490593A1 EP 1490593 A1 EP1490593 A1 EP 1490593A1 EP 03731607 A EP03731607 A EP 03731607A EP 03731607 A EP03731607 A EP 03731607A EP 1490593 A1 EP1490593 A1 EP 1490593A1
Authority
EP
European Patent Office
Prior art keywords
fuel injection
injection valve
fuel
elastic sealing
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Withdrawn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
EP03731607A
Other languages
German (de)
French (fr)
Inventor
Detlef Nowak
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 EP1490593A1 publication Critical patent/EP1490593A1/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Withdrawn legal-status Critical Current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
    • F02M61/16—Details not provided for in, or of interest apart from, the apparatus of groups F02M61/02 - F02M61/14
    • 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
    • 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
    • F02M61/162—Means to impart a whirling motion to fuel upstream or near discharging orifices
    • 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
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/30—Fuel-injection apparatus having mechanical parts, the movement of which is damped
    • F02M2200/306—Fuel-injection apparatus having mechanical parts, the movement of which is damped using mechanical means
    • 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
    • F02M51/0685—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 and the valve being allowed to move relatively to each other or not being attached to each other
    • 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
    • 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
    • F02M61/166—Selection of particular materials

Definitions

  • the invention relates to a fuel injector according to the preamble of the main claim.
  • a fuel injector which has a guide body (referred to there as a guide element 35) for guiding the lower, downstream end of the valve needle.
  • the lower, downstream end of the ' valve needle is referred to as the valve closing body and, in cooperation with the guide body, serves in particular to seal the
  • the sealing effect is achieved through a relatively low guide clearance, low-wear materials and low manufacturing tolerances.
  • a disadvantage of the fuel injector known from the abovementioned publications is, in particular, that the inflow of non-swirled fuel into the combustion chamber is only inadequately achieved through the gap between the guide body and valve closing body.
  • the inflow of swirled fuel through the gap described is also referred to as a leakage flow.
  • the gap is kept small by using small manufacturing tolerances. On the one hand, manufacturing tolerances cannot be realized as small as desired, so they have limits, on the other hand they become disproportionately more expensive to manufacture the closer the manufacturing tolerances are to those limits.
  • the gap widens over the course of its service life due to frictional wear.
  • a so-called pre-jet emerges from the spray opening at the start of the injection.
  • This pre-jet is largely untwisted and always undesirable, since it does not correspond to the desired geometry of the injected fuel cloud and, in particular with direct fuel injection into the combustion chamber, causes deposits in the area of the spray opening, but at least does not counteract it.
  • the leakage flow significantly hinders the swirl preparation of the fuel and leads to a lengthened and enlarged pre-jet.
  • the leakage flow increases in the course of the service life in such a way that the flow values q ⁇ yn and -d Q stat are outside the permissible tolerance.
  • the needle stroke and valve opening times can be selected to be small and the number of swirl channels increased. This results in a slow and undisturbed swirl build-up. These measures result however at the same time to a lower valve dynamic.
  • the increased number of swirl channels increases the design effort and thus the costs.
  • the slower swirl build-up increases the sensitivity to dirt and thus the risk of deposits.
  • the fuel injector according to the invention with the characterizing features of the main claim has the advantage that the leakage flow of fuel passing through the gap between the guide body and the valve closing member is prevented.
  • the sealing device according to the invention makes it possible to dispense with cost-intensive measures for reducing the leakage flow, as are known from the prior art.
  • cost-intensive, low manufacturing tolerances for producing a minimized gap between the guide body and the valve closing body guided in it can be dispensed with.
  • the materials used for the guide body and the valve closing body can be optimized, in particular with regard to the guide function, since the task of leakage current sealing no longer falls within the scope of these components.
  • the swirl formation Since there is no leakage current, the swirl formation, especially at the beginning, is improved and the pre-jet is reduced. Since the sealing effect of the sealing device according to the invention is permanent, ie is not subject to wear and tear which causes the leakage flow to increase over the service life, the permissible limit values for the jet angle can be reliably maintained over the entire service life of the fuel injector, as can the required flow values q dyn and d Q stat without having to resort to measures that are detrimental to the valve dynamics.
  • the risk of deposits on the spray geometry of a fuel injector is increased in spray geometries that protrude directly into the combustion chamber or are in direct contact with it.
  • the swirl formation which develops early in the fuel injection valve according to the invention at the start of injection reduces the risk of deposits forming on the spray geometry.
  • the invention can be used particularly advantageously for fuel injection valves which have a so-called cardanic valve needle guide, since the problem of leakage flow sealing is particularly critical here.
  • the cardanic valve needle guide has a spherical valve closing body on the spray-side end of the valve needle, which is guided in a guide body.
  • the sealing effect to prevent the leakage flow is achieved here by the interaction of the inner surface of the guide body and the only short immediate area around the ball equator of the valve closing body. Due to the much shorter sealing length of the lower valve needle guide compared to fuel injectors with a cylindrical valve closing body, compliance with limit values is even more difficult to master. In particular, the wear and the dependence of the leakage flow on the wear is increased.
  • fuel injectors with cardanic valve needle guidance have other advantages.
  • they can be manufactured much more cost-effectively than designs with a cylindrical valve closing body.
  • the sealing device according to the invention allows cost savings in two respects.
  • the measure itself is less expensive than the measures of the prior art.
  • it allows the use of the inexpensive cardanic valve needle guide.
  • the measures listed in the subclaims allow advantageous further developments of the fuel injector specified in the main claim.
  • the sealing device can be attached to the valve needle via a flange such that the elastic part of the sealing device influences the closing or opening process of the fuel injector.
  • the movements of the valve needle can in particular be damped, slowed down or accelerated.
  • the shape of the elastic sealing body encompassed by the sealing device should be adaptable to the structural requirements.
  • a toroidal, elastic sealing body conceivable, which is only in its position, e.g. is held between a flange and the Fuhrungskorper, wherein it is constantly acted upon by a compressive force from the outside.
  • frictional forces or adhesive connections can hold the elastic sealing body in its position.
  • the elastic sealing body consists of an elastomer, since it is widely used
  • valve needle passes through the flange or the elastic sealing body and the flange and the elastic sealing element are disk-shaped, the forces that occur between these parts can be applied to the flange, elastic sealing body, valve needle and guide body evenly.
  • the sealing arrangement of the elastic sealing body between the flange and the guide body has the particular advantage that it is not necessary to connect the elastic sealing element directly to the valve needle. If the valve needle and the elastic sealing element were connected directly, the shear forces that occur would have an unfavorable effect on the service life of the connection. Further advantages arise, for example, in the case of an L-shaped profile of the flange, which can be produced cost-effectively without cutting and also has a higher strength due to the non-cutting production.
  • Figure 1 is a schematic section through an embodiment of a fuel injector designed according to the invention.
  • Fig. 2 is a schematic partial section of the spray-side end of the embodiment of the fuel injector according to it and
  • Fig. 3 is an enlarged detail of the section designated III of the schematic partial section shown in Fig. 2 in the region of the valve closing body and guide body.
  • FIG. 1 An exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 1 is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, semi-ignited internal combustion engines.
  • the fuel injector 1 is particularly suitable for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
  • the fuel fine injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged.
  • the valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat.
  • fuel injector 1 is a fuel injector 1 that opens inward and has a spray opening 7.
  • the nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10.
  • the magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12 which bears against an inner pole 13 of the magnet coil 10.
  • the inner pole 13 and the outer pole 9 are separated from one another by a constriction 26 and are connected to one another by a non-ferromagnetic connection component 29.
  • the magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17.
  • the plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
  • the valve needle 3 is guided in a valve needle guide 14, which is disc-shaped.
  • a paired adjusting disc 15 is used for stroke adjustment.
  • the armature 20 is located on the other side of the adjusting disc 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the valve needle by a weld seam 22. first flange 21 is connected.
  • a restoring spring 23 is supported on the first flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24.
  • Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and in the nozzle body 2. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25.
  • the fuel injector 1 is sealed by a seal 28 against a fuel rail, not shown, and by a seal 34 against a cylinder head, not shown.
  • An annular damping element 32 which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It rests on a second flange 31, which is non-positively connected to the valve needle 3 via a weld seam 33.
  • the armature 20 In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat surface 6.
  • the magnetic coil 10 When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20.
  • the armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction.
  • the valve closing body 4 connected to the valve needle 3 lifts off from the valve seat surface 6, and the fuel supplied via the swirl device 36 is sprayed through the spray opening 7.
  • a guide body 35, a swirl device 36 and the sealing device 40 according to the invention consisting of a flange 41 and an elastic sealing body 42, are provided, which are explained in more detail with reference to FIG. 2.
  • the end of the embodiment of the fuel injector 1 shown in FIG 1 comprises in particular a valve closing body 4, a guiding body 35, a swirl device 36 and the sealing device 40 according to the invention.
  • the swirl device 36 is located upstream of the valve seat surface 6, which is formed on the valve seat body 5.
  • the swirl device 36 consists of a swirl disk 38, the fuel channels (not shown) of which have a tangential component and open into a swirl chamber 37.
  • the fuel is conducted through the fuel channel 30c, past the flange 41, the elastic sealing body 42 and the guide body 35 to the swirl disk 38. After the fuel has passed the swirl disk 38, it enters the dali chamber 37 with a directional component that is tangential to the valve needle axis 43, is swirled and finally sprayed through the spray opening 7 into the combustion chamber (not shown).
  • the sealing device 40 which in this exemplary embodiment consists of the flange 41 and the elastic sealing body 42, prevents the entry of fuel from the fuel channel 30c through the gap 39 between the guide body 35 and the valve closing element 4 in FIG the swirl chamber 37.
  • the flange 41 is hydraulically sealed and non-positive, for example attached to the valve needle 3 by welding, soldering, gluing, pressing and / or shrinking.
  • the elastic sealing body 42 is always in hydraulic contact with the flange 41 as well as with the upstream side of the guide body 35.
  • the dimensions and the elasticity of the elastic sealing body 42 are dimensioned such that the sealing body 42 holds a hydraulically sealing connection between the guide body 35 and the flange 41 both when the fuel injector 1 is closed and when it is open.
  • All parts of the sealing device 40 and their connection points are temperature resistant and corrosion-resistant and further constructed and attached so that they do not significantly increase the force required to close the fuel injector 1 and thus do not significantly affect the valve dynamics.
  • the selection of materials and the shape of the parts of the sealing device 42 are optimized, inter alia, for low weight in order to keep inertial forces low.
  • the Fuhrungskorper 35 is used to guide the downstream part of the valve needle 3 over the spherical valve closing body 4.
  • the arrangement shown with spherical valve closing body 4, which takes over the downstream guidance of the valve needle 3 through the guide body 35, is also referred to as a cardan valve needle guide.
  • Fig. 3 shows a detail enlargement of the greatly exaggerated gap 39, which arises between the spherical valve closing body 4 and the guide body 35 through play.
  • the elastic sealing body 42 is attached upstream of the guide body 35.
  • the invention is not limited to the illustrated embodiments and z. B. also applicable for outward opening fuel injectors.

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

Abstract

The invention relates to a fuel injection valve (1), especially for directly injecting fuel into the combustion chamber of an internal combustion engine. The inventive fuel injection valve comprises a valve needle (3) that is provided, on the injection end thereof, with a valve closing body (4) that interacts with a valve face (6), configured on a valve face body (5), to give a sealing seat and that is guided in a guide (35). A swirl device (36) generates a swirl of the fuel in a swirl chamber (37). In the valve seat body (5) an injection opening (7) is provided. An at least partially elastic sealing device (40) prevents the inflow of fuel through a gap (39) between the guide body (35) and the valve closing body (4) into the swirl chamber (37).

Description

Brennstoffeinspritzventil Fuel injector
Stand der TechnikState of the art
Die Erfindung geht aus von einem Brennstoffeinspritzventil nach der Gattung des Hauptanspruchs .The invention relates to a fuel injector according to the preamble of the main claim.
Aus der DE 197 36 682 AI ist ein Brennstoffeinspritzventil bekannt, welches einen Führungskörper (dort als Führungseiement 35 bezeichnet) zur Führung des unteren, stromab ärtigeri Endes der Ventilnadel aufweist. Das untere, stromabwärtige Ende der ' Ventilnadel wird als Ventilschließkörper bezeichnet und dient im Zusammenspiel mit dem Führungskörper insbesondere zur Abdichtung derFrom DE 197 36 682 AI a fuel injector is known which has a guide body (referred to there as a guide element 35) for guiding the lower, downstream end of the valve needle. The lower, downstream end of the ' valve needle is referred to as the valve closing body and, in cooperation with the guide body, serves in particular to seal the
Drallkammer gegen Eindringen von unverdrallte Brennstoff,Swirl chamber against the penetration of untwisted fuel
■ der sich stromaufwärtig des Führungskörpers befindet. ■ which is located upstream of the guide body.
Erreicht wird die abdichtende Wirkung durch ein relativ geringes Führungsspiel , verschleißarme Werkstoffe und geringe Fertigungstoleranzen.The sealing effect is achieved through a relatively low guide clearance, low-wear materials and low manufacturing tolerances.
Nachteilig bei dem aus den obengenannten Druckschriften bekannten Brennstoffeinspritzventil ist insbesondere, daß der Zustrom von unverdralltem Brennstoff in die Brennkammer, durch den zwischen Führungskörper und Ventilschließkörper befindlichen- Spalt, nur unzureichend erzielt wird. Der Zustrom von unverdralltem Brennstoff durch den beschriebenen Spalt wird auch als Leckagestrom bezeichnet. Um den Leckagestrom über die gesamte Lebensdauer des Brennstoffeinspritzventils möglichst gering zu halten, wird der Spalt durch den Einsatz geringer Fertigungstoleranzen klein gehalten. Fertigungstoleranzen sind zum einen, nicht beliebig klein realisierbar, haben also Grenzen, zum anderen verteuern sie sich in der Herstellung überproportional je näher die Fertigungstoleranzen zu jenen Grenzen hin gewählt werden. Zusätzlich weitet sich der Spalt im Verlauf der Lebensdauer durch Reibungsverschleiß. Um eine möglichst große Lebensdauer zu erreichen und um die Spaltweitung während dieser Dauer zu begrenzen, müssen teuere verschleißarme Werkstoffe eingesetzt werden, die zudem meist nur schwer und damit kostenintensiv zu bearbeiten sind. Schließlich muß eine gewisse Spaltwe.ite, aufgrund der extremen Temperaturbandbreite, dem das Brennstoffeinspritzventil im Betrieb ausgesetzt ist, eingehalten werden, da sonst ein zuverlässiger Betrieb auf Grund von Temperaturausdehnungen nicht gewährleistet werden kann.A disadvantage of the fuel injector known from the abovementioned publications is, in particular, that the inflow of non-swirled fuel into the combustion chamber is only inadequately achieved through the gap between the guide body and valve closing body. The inflow of swirled fuel through the gap described is also referred to as a leakage flow. To the To keep leakage flow as low as possible over the entire life of the fuel injector, the gap is kept small by using small manufacturing tolerances. On the one hand, manufacturing tolerances cannot be realized as small as desired, so they have limits, on the other hand they become disproportionately more expensive to manufacture the closer the manufacturing tolerances are to those limits. In addition, the gap widens over the course of its service life due to frictional wear. In order to achieve the longest possible service life and to limit the gap widening during this period, expensive, low-wear materials must be used, which are also usually difficult and therefore costly to machine. Finally, a certain gap width must be maintained due to the extreme temperature range to which the fuel injector is exposed during operation, since otherwise reliable operation cannot be guaranteed due to temperature expansions.
Prinzipbedingt tritt, verursacht durch das sog. Totraumvolumen, bei Beginn der Einspitzung zuerst ein sog. Vorstrahl aus der Abspritzöffnung. Dieser Vorstrahl ist weitgehend unverdrallt und stets unerwünscht, da er nicht der gewünschten Geometrie der eingespritzten Brennstoffwolke entspricht und insbesondere bei direkter Brennstoffeinspritzung in den Brennraum Ablagerungen im Bereich der Abspritzöffnung hervorruft, diesen aber zumindest nicht entgegenwirkt. Der Leckagestrom behindert maßgeblich die Drallaufbereitung des Brennstoffes und führt zu einem zeitlich verlängerten und vergrößerten Vorstrahl . Der Leckagestrom vergrößert sich im Laufe der Lebensdauer derart , daß sich die Durchflußwerte q^yn un-d Qstat außerhalb der zulässigen Toleranz bewegen.In principle, caused by the so-called dead space volume, a so-called pre-jet emerges from the spray opening at the start of the injection. This pre-jet is largely untwisted and always undesirable, since it does not correspond to the desired geometry of the injected fuel cloud and, in particular with direct fuel injection into the combustion chamber, causes deposits in the area of the spray opening, but at least does not counteract it. The leakage flow significantly hinders the swirl preparation of the fuel and leads to a lengthened and enlarged pre-jet. The leakage flow increases in the course of the service life in such a way that the flow values q ^ yn and -d Q stat are outside the permissible tolerance.
Um dem entgegenzuwirken können Nadelhub und Ventilöffungzeiten klein gewählt, sowie die Anzahl der Drallkanäle erhöht werden. Dadurch wird ein langsamer und ungestörter Drallaufbau erreicht. Diese Maßnahmen führen jedoch gleichzeitig zu einer geringeren Ventildyna ik. Die erhöhte Anzahl von Drallkanälen erhöht den konstruktiven Aufwand und damit die Kosten. Der langsamere Drallaufbau erhöht die Schmutsempfindlichkeit und damit die Gefahr von Ablagerungen.To counteract this, the needle stroke and valve opening times can be selected to be small and the number of swirl channels increased. This results in a slow and undisturbed swirl build-up. These measures result however at the same time to a lower valve dynamic. The increased number of swirl channels increases the design effort and thus the costs. The slower swirl build-up increases the sensitivity to dirt and thus the risk of deposits.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Brennstoffeinspritzventil mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß der durch den Spalt zwischen Führungskörper und Ventilschließkorper hindurchtretende Leckagestrom von Brennstoff unterbunden ist. Durch die erfindungsgemäße Dichtvorrichtung kann gleichzeitig auf kostenintensive Maßnahmen zur Reduzierung des Leckagestroms, wie sie aus dem Stand der Technik bekannt sind, verzichtet werden. Insbesondere kann auf kostenintensive geringe Fertigungstoleranzen zur Herstellung eines minimierten Spaltes zwischen dem Führungskörper und dem in ihm geführten Ventilschließkorper verzichtet werden. Im weiteren können die für den Führungskörper und den Ventilschließkorper eingesetzten Materialien, insbesondere hinsichtlich Führungsfunktion, optimiert werden, da die Aufgabe der LeckageStromabdichtung nicht mehr in den Aufgabenbereich dieser Bauteile fällt .The fuel injector according to the invention with the characterizing features of the main claim has the advantage that the leakage flow of fuel passing through the gap between the guide body and the valve closing member is prevented. At the same time, the sealing device according to the invention makes it possible to dispense with cost-intensive measures for reducing the leakage flow, as are known from the prior art. In particular, cost-intensive, low manufacturing tolerances for producing a minimized gap between the guide body and the valve closing body guided in it can be dispensed with. Furthermore, the materials used for the guide body and the valve closing body can be optimized, in particular with regard to the guide function, since the task of leakage current sealing no longer falls within the scope of these components.
Da kein Leckagestrom stattfindet, ist die Drallausbildung, insbesondere zu ihrem Beginn, verbessert und der Vorstrahl ist vermindert. Da die abdichtende Wirkung der erfindungsgemäßen Dichtvorrichtung dauerhaft ist, d.h. keinem Verschleiß unterliegt, der über die Lebensdauer eine Erhöhung des Leckagestroms bewirkt, können die zulässigen Grenzwerte der Strahlwinkel über die gesamte Lebensdauer des Brennstoffeinspritzventils sicher eingehalten werden, ebenso die geforderten Druchflußwerte qdyn und Qstat, ohne auf Maßnahmen zurückgreifen zu müssen, die der Ventildynamik abträglich sind. Die Gefahr einer Ablagerung an der Abspritzgeometrie eines Brennstoffeinspritzventils ist bei Abspritzgeometrien, die unmittelbar in den Brennraum ragen oder mit diesem unmittelbar in Kontakt stehen, vergrößert. Die sich beim erfindungsgemäßen Brennstoffeinspritzventil zu Einspritzbeginn frühzeitig entwickelnde Drallausbildung reduziert die Gefahr einer Bildung von Ablagerungen an der Abspritzgeometrie .Since there is no leakage current, the swirl formation, especially at the beginning, is improved and the pre-jet is reduced. Since the sealing effect of the sealing device according to the invention is permanent, ie is not subject to wear and tear which causes the leakage flow to increase over the service life, the permissible limit values for the jet angle can be reliably maintained over the entire service life of the fuel injector, as can the required flow values q dyn and d Q stat without having to resort to measures that are detrimental to the valve dynamics. The risk of deposits on the spray geometry of a fuel injector is increased in spray geometries that protrude directly into the combustion chamber or are in direct contact with it. The swirl formation which develops early in the fuel injection valve according to the invention at the start of injection reduces the risk of deposits forming on the spray geometry.
Besonders vorteilhaft kann die Erfindung bei Brennstoffeinspritzventilen angewandt werden, die eine sog. kardanische Ventilnadelführung aufweisen, da hier die Problematik der Leckagestromabdichtung besonders kritisch ist. Die kardanische Ventilnadelführung weist am abspritzseitigen Ende der Ventilnadel einen kugelförmigen Ventilschließkorper auf, der in einem Führungskörper geführt wird. Die dichtende Wirkung zur Verhinderung des Leckagestroms, wird hier durch das Zusammenspiel von Innenfläche des Führungskörpers und dem nur kurzen unmittelbaren Bereich um den Kugeläquator des Ventilschließkörpers erreicht. Aufgrund der im Vergleich zu Brennstoffeinspritzventilen mit zylinderförmigem Ventilschließkorper stark verkürzten Dichtlänge der unteren Ventilnadelführung, ist die Einhaltung von Grenzwerten noch schwerer zu beherrschen. Insbesondere ist der Verschleiß sowie die Abhängigkeit des Leckagestromes vom Verschleiß erhöht. Trotzdem weisen Brennstoffeinspritzventile mit kardanischer Ventilnadelführung andere Vorteile auf. Insbesondere lassen sie sich wesentlich kostengünstiger herstellen als Ausführungen mit zylinderförmigem Ventilschließkorper. Die erfindungsgemäße Dichtvorrichtung erlaubt Kosteneinsparungen in doppelter Hinsicht. Zum einen ist die Maßnahme selbst, im Vergleich zu den Maßnahmen des Standes der Technik, kostengünstiger. Zum anderen erlaubt sie den Einsatz der kostengünstigen kardanischen Ventilnadelführung. Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterentwicklungen des im Hauptanspruch angegebenen Brennstoffeinspritzventils möglich.The invention can be used particularly advantageously for fuel injection valves which have a so-called cardanic valve needle guide, since the problem of leakage flow sealing is particularly critical here. The cardanic valve needle guide has a spherical valve closing body on the spray-side end of the valve needle, which is guided in a guide body. The sealing effect to prevent the leakage flow is achieved here by the interaction of the inner surface of the guide body and the only short immediate area around the ball equator of the valve closing body. Due to the much shorter sealing length of the lower valve needle guide compared to fuel injectors with a cylindrical valve closing body, compliance with limit values is even more difficult to master. In particular, the wear and the dependence of the leakage flow on the wear is increased. Nevertheless, fuel injectors with cardanic valve needle guidance have other advantages. In particular, they can be manufactured much more cost-effectively than designs with a cylindrical valve closing body. The sealing device according to the invention allows cost savings in two respects. On the one hand, the measure itself is less expensive than the measures of the prior art. On the other hand, it allows the use of the inexpensive cardanic valve needle guide. The measures listed in the subclaims allow advantageous further developments of the fuel injector specified in the main claim.
Vorteilhafterweise kann die Dichtvorrichtung über einen Flansch an der Ventilnadel so angebracht sein, daß der elastische Teil der Dichtvorrichtung den Schließvorgang bzw. Öffnungsvorgang des Brennstoffeinspritzventils beeinflußt. Die Bewegungen der Ventilnadel können dabei insbesondere gedämpft, verlangsamt oder beschleunigt werden.Advantageously, the sealing device can be attached to the valve needle via a flange such that the elastic part of the sealing device influences the closing or opening process of the fuel injector. The movements of the valve needle can in particular be damped, slowed down or accelerated.
Die Form des von der Dichtvorrichtung umfaßten elastischen Dichtkörpers soll den konstruktiven Erfordernissen anpaßbar sein. So ist z.B. ein torusför iger , elastischer Dichtkörper vorstellbar, der nur durch seine äußere Form in seiner Position, z.B. zwischen einem Flansch und dem Fuhrungskorper, gehalten wird, wobei er ständig von einer Druckkraft von außen beaufschlagt ist. Zusätzlich können Reibungskräfte oder Klebeverbindungen den elastischen Dichtkörper in seiner Position halten.The shape of the elastic sealing body encompassed by the sealing device should be adaptable to the structural requirements. For example, a toroidal, elastic sealing body conceivable, which is only in its position, e.g. is held between a flange and the Fuhrungskorper, wherein it is constantly acted upon by a compressive force from the outside. In addition, frictional forces or adhesive connections can hold the elastic sealing body in its position.
Von Vorteil ist außerdem, daß der elastische Dichtkδrper aus einem Elastomer besteht, da diese über weiteIt is also advantageous that the elastic sealing body consists of an elastomer, since it is widely used
Temperaturbereiche ihre elastischen Eigenschaften beibehalten.Temperature ranges maintain their elastic properties.
Wenn die Ventilnadel den Flansch bzw. den elastischen Dichtkörper durchgreift und der Flansch sowie das elastische Dichtelement scheibenförmig sind, können Flansch, elastischer Dichtkörper, Ventilnadel und Führungskörper mit den zwischen diesen Teilen auftretenden Kräften flächenmäßig gleichmäßig 'beaufschlagt werden. Die dichtende Anordnung von elastischem Dichtkörper zwischen Flansch und Fuhrungskorper hat insbesondere den Vorteil, das elastische Dichtelement nicht unmittelbar mit der Ventilnadel verbinden zu müssen. Bei einer unmittelbaren Verbindung von Ventilnadel und elastischem Dichtelement würden sich die auftretenden Scherkräfte ungünstig auf die Lebensdauer der Verbindung auswirken . Weitere Vorteile ergeben sich beispielsweise bei einem L- förmigen Profil- des Flansches, das sich kostengünstig spanlos herstellen läßt und durch die spanlose Herstellung außerdem eine höhere Festigkeit aufweist.If the valve needle passes through the flange or the elastic sealing body and the flange and the elastic sealing element are disk-shaped, the forces that occur between these parts can be applied to the flange, elastic sealing body, valve needle and guide body evenly. The sealing arrangement of the elastic sealing body between the flange and the guide body has the particular advantage that it is not necessary to connect the elastic sealing element directly to the valve needle. If the valve needle and the elastic sealing element were connected directly, the shear forces that occur would have an unfavorable effect on the service life of the connection. Further advantages arise, for example, in the case of an L-shaped profile of the flange, which can be produced cost-effectively without cutting and also has a higher strength due to the non-cutting production.
Zeichnungdrawing
Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen:An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. Show it:
Fig. 1 einen schematischen Schnitt durch ein Ausführungsbeispiel eines erfindungsgemäß ausgestalteten Brennstoffeinspritzventils ;Figure 1 is a schematic section through an embodiment of a fuel injector designed according to the invention.
Fig. 2 einen schematischen Teilschnitt des abspritzseitigen Endes des Ausführungsbeispiels des er indungsgemäßen Brennstoffeinspritzventils undFig. 2 is a schematic partial section of the spray-side end of the embodiment of the fuel injector according to it and
Fig. 3 eine Detailvergrößerung des mit III bezeichneten Ausschnitts des in Fig. 2 dargestellten schematischen Teilausschnitts im Bereich von Ventilschließkorper und Führungskörper.Fig. 3 is an enlarged detail of the section designated III of the schematic partial section shown in Fig. 2 in the region of the valve closing body and guide body.
Beschreibung des AusführungsbeispielsDescription of the embodiment
Ein in Fig. 1 dargestelltes Ausführungsbeispiel eines erfindungsgemäßen Brennstoffeinspritzventils 1 ist in der Form eines Brennstoffeinspritzventils 1 für Brennstoffeinspritzanlagen von gemischverdichtenden, remdgezündeten Brennkraftmaschinen ausgeführt. Das Brennstoffeinspritzventil 1 eignet sich insbesondere zum direkten Einspritzen von Brennstoff in einen nicht dargestellten Brennraum einer Brennkraf maschine .An exemplary embodiment of a fuel injection valve 1 according to the invention shown in FIG. 1 is in the form of a fuel injection valve 1 for fuel injection systems of mixture-compressing, semi-ignited internal combustion engines. The fuel injector 1 is particularly suitable for the direct injection of fuel into a combustion chamber, not shown, of an internal combustion engine.
Das Brennsto feinspritzventil 1 besteht aus einem Düsenkörper 2, in welchem eine Ventilnadel 3 angeordnet ist. Die Ventilnadel 3 steht mit einem Ventilschließkorper 4 in Wirkverbindung, der mit einer auf einem Ventilsitzkörper 5 angeordneten Ventilsitzfläche 6 zu einem Dichtsitz zusammenwirkt. Bei dem Brennstoffeinspritzventil 1 handelt es sich im Ausführungsbeispiel um ein nach innen öffnendes Brennstoffeinspritzventil 1, welches über eine Abspritzöffnung 7 verfügt. Der Düsenkörper 2 ist durch eine Dichtung 8 gegen einen Außenpol 9 einer Magnetspule 10 abgedichtet . Die Magnetspule 10 ist in einem Spulengehäuse 11 gekapselt und auf einen Spulenträger 12 gewickelt, welcher an einem Innenpol 13 der Magnetspule 10 anliegt. Der Innenpol 13 und der Außenpol 9 sind durch eine Verengung 26 voneinander getrennt und miteinander durch ein nicht ferromagnetiscb.es Verbindungsbauteil 29 verbunden. Die Magnetspule 10 wird über eine Leitung 19 von einem über einen elektrischen Steckkontakt 17 zuführbaren elektrischen Strom erregt . Der Steckkontakt 17 ist von einer Kunststoffummantelung 18 umgeben, die am Innenpol 13 angespritzt sein kann.The fuel fine injection valve 1 consists of a nozzle body 2, in which a valve needle 3 is arranged. The valve needle 3 is operatively connected to a valve closing body 4, which cooperates with a valve seat surface 6 arranged on a valve seat body 5 to form a sealing seat. In the exemplary embodiment, fuel injector 1 is a fuel injector 1 that opens inward and has a spray opening 7. The nozzle body 2 is sealed by a seal 8 against an outer pole 9 of a solenoid 10. The magnet coil 10 is encapsulated in a coil housing 11 and wound on a coil carrier 12 which bears against an inner pole 13 of the magnet coil 10. The inner pole 13 and the outer pole 9 are separated from one another by a constriction 26 and are connected to one another by a non-ferromagnetic connection component 29. The magnet coil 10 is excited via a line 19 by an electrical current that can be supplied via an electrical plug contact 17. The plug contact 17 is surrounded by a plastic sheath 18, which can be molded onto the inner pole 13.
Die Ventilnadel 3 ist in einer Ventilnadelführung 14 geführt, welche scheibenförmig ausgeführt ist. Zur Hubeinstellung dient eine zugepaarte Einstellscheibe 15. An der anderen Seite der Einstellscheibe 15 befindet sich der Anker 20. Dieser steht über einen ersten Flansch 21 kraftschlüssig mit der Ventilnadel 3 in Verbindung, welche durch eine Schweißnaht 22 mit dem. ersten Flansch 21 verbunden ist. Auf dem ersten Flansch 21 stützt sich eine Rückstellfeder 23 ab, welche in der vorliegenden Bauform des Brennstoffeinspritzventils 1 durch eine Hülse 24 auf Vorspannung gebracht wird. In der Ventilnadelführung 14, im Anker 20 und im Düsenkörper 2 verlaufen Brennstof kanäle 30a bis 30c. Der Brennstoff wird über eine zentrale Brennstoffzufuhr 16 zugeführt und durch ein Filterelement 25 gefiltert. Das Brennstoffeinspritzventil 1 ist durch eine Dichtung 28 gegen eine nicht weiter dargestellte Brennstoffverteilerleitung und durch eine Dichtung 34 gegen einen nicht dargestellten Zylinderkopf abgedichtet . An der abspritzseitigen Seite des Ankers 20 ist .ein ringförmiges Dämpfungselement 32, welches aus einem Elastomerwerkstoff besteht, angeordnet. Es liegt auf einem zweiten Flansch 31 auf, welcher über eine Schweißnaht 33 kraftschlüssig mit der Ventilnadel 3 verbunden ist.The valve needle 3 is guided in a valve needle guide 14, which is disc-shaped. A paired adjusting disc 15 is used for stroke adjustment. The armature 20 is located on the other side of the adjusting disc 15. This armature is non-positively connected to the valve needle 3 via a first flange 21, which is connected to the valve needle by a weld seam 22. first flange 21 is connected. A restoring spring 23 is supported on the first flange 21, which in the present design of the fuel injector 1 is preloaded by a sleeve 24. Fuel channels 30a to 30c run in the valve needle guide 14, in the armature 20 and in the nozzle body 2. The fuel is supplied via a central fuel supply 16 and filtered by a filter element 25. The fuel injector 1 is sealed by a seal 28 against a fuel rail, not shown, and by a seal 34 against a cylinder head, not shown. An annular damping element 32, which consists of an elastomer material, is arranged on the spray-side side of the armature 20. It rests on a second flange 31, which is non-positively connected to the valve needle 3 via a weld seam 33.
Im Ruhezustand des Brennstoffeinspritzventils 1 wird der Anker 20 von der Rückstellfeder 23 entgegen seiner Hubrichtung so beaufschlagt, daß der Ventilschließkorper 4 an der Ventilsitzfläche 6 in dichtender Anlage gehalten wird. Bei Erregung der Magnetspule 10 baut diese ein Magnetfeld auf, welches den Anker 20 entgegen der Federkraft der Rückstellfeder 23 in Hubrichtung bewegt, wobei der Hub durch einen in der Ruhestellung zwischen dem Innenpol 12 und dem Anker 20 befindlichen Arbeitsspalt 27 vorgegeben ist. Der Anker 20 nimmt den ersten Flansch 21, welcher mit der Ventilnadel 3 verschweißt ist, ebenfalls in Hubrichtung mit. Der mit der Ventilnadel 3 in Verbindung stehende Ventilschließkorper 4 hebt von der Ventilsitzfläche 6 ab, und der über die Dralleinrichtung 36 zugeführte Brennstoff wird durch die Abspritzöf nung 7 abgespritzt.In the idle state of the fuel injection valve 1, the armature 20 is acted upon by the return spring 23 against its stroke direction in such a way that the valve closing body 4 is held in sealing contact with the valve seat surface 6. When the magnetic coil 10 is excited, it builds up a magnetic field which moves the armature 20 against the spring force of the return spring 23 in the stroke direction, the stroke being predetermined by a working gap 27 which is in the rest position between the inner pole 12 and the armature 20. The armature 20 also takes the first flange 21, which is welded to the valve needle 3, in the lifting direction. The valve closing body 4 connected to the valve needle 3 lifts off from the valve seat surface 6, and the fuel supplied via the swirl device 36 is sprayed through the spray opening 7.
Wird der Spulenstrom abgeschaltet, fällt der Anker 20 nach genügendem Abbau des Magnetfeldes durch den Druck der Rückstellfeder 23 vom Innenpol 13 ab, wodurch sich der mit der Ventilnadel 3 in Verbindung stehende erste Flansch 21 entgegen der Hubrichtung bewegt. Die Ventilnadel 3 wird dadurch in die gleiche Richtung bewegt, wodurch der Ventilschließkorper 4 auf der Ventilsitzflache 6 aufsetzt und das . Brennstoffeinspritzventil 1 geschlossen wird.If the coil current is switched off, the armature 20 drops from the inner pole 13 after the magnetic field has been sufficiently reduced by the pressure of the return spring 23, as a result of which the first flange 21, which is connected to the valve needle 3, moves counter to the stroke direction. The valve needle 3 is thereby moved in the same direction, as a result of which the valve closing body 4 rests on the valve seat surface 6 and that. Fuel injector 1 is closed.
Weiterhin sind ein Führungskörper 35, eine Dralleinrichtung 36 und die erfindungsgemäße Dichtvorrichtung 40, bestehend aus einem Flansch 41 und einem elastischen Dichtkδrper 42, vorgesehen, die anhand von Fig. 2 näher erläutert werden.Furthermore, a guide body 35, a swirl device 36 and the sealing device 40 according to the invention, consisting of a flange 41 and an elastic sealing body 42, are provided, which are explained in more detail with reference to FIG. 2.
Das in Fig. 2 ausschnittsweise vergrößert dargestellte abspritzseitige Ende des erfindungsgemäßen Ausführungsbeispiels des Brennstoffeinspritzventils 1 aus Fig. 1 umfaßt insbesondere einen Ventilschließkorper 4, einen Fuhrungskorper 35, eine Dralleinrichtung 36 und die erfindungsgemäße Dichtvorrichtung 40. Die Dralleinrichtung 36 liegt stromaufwärtig der Ventilsitzfläche 6, die an dem Ventilsitzkörper 5 ausgebildet ist. In dem dargestellten Ausführungsbeispiel besteht die Dralleinrichtung 36 aus einer Drallscheibe 38, deren nicht dargestellten Brennstoffkanäle eine Tangentialkomponente haben und in eine Drallkammer 37 ausmünden. Der Brennstoff wird dabei durch den Brennstoffkanal 30c, vorbei an Flansch 41, elastischem Dichtkörper 42 und Führungskörper 35 zur Drallscheibe 38 geleitet. Nachdem der Brennstoff die Drallscheibe 38 passiert hat, tritt er mit einem zur Ventilnadelachse 43 tangential verlaufenden Richtungsanteil in die Dalikammer 37 ein, wird verwirbelt und schließlich durch die Abspritzöffnung 7 in den nicht dargestellten Brennraum abgespritzt .The end of the embodiment of the fuel injector 1 shown in FIG 1 comprises in particular a valve closing body 4, a guiding body 35, a swirl device 36 and the sealing device 40 according to the invention. The swirl device 36 is located upstream of the valve seat surface 6, which is formed on the valve seat body 5. In the exemplary embodiment shown, the swirl device 36 consists of a swirl disk 38, the fuel channels (not shown) of which have a tangential component and open into a swirl chamber 37. The fuel is conducted through the fuel channel 30c, past the flange 41, the elastic sealing body 42 and the guide body 35 to the swirl disk 38. After the fuel has passed the swirl disk 38, it enters the dali chamber 37 with a directional component that is tangential to the valve needle axis 43, is swirled and finally sprayed through the spray opening 7 into the combustion chamber (not shown).
Die erfindungsgemäße Dichtvorrichtung 40, die in diesem Ausführungsbeispiel aus dem Flansch 41 und dem elastischen Dichtkörper 42 besteht, verhindert dabei in jedem Betriebszustand einen Eintrag von Brennstoff von Brennstoffkanal 30c durch den in Fig. 3 stark übertrieben dargestellten Spalt 39 zwischen Führungskörper 35 und Ventilschließkorper 4 in die Drallkammer 37. Der Flansch 41 ist dabei hydraulisch dichtend und kraftschlüssig, z.B. durch Schweißen, Löten, Kleben, Pressen und/oder Schrumpfen an der Ventilnadel 3 angebracht. Der elastische Dichtkörper 42 steht stets sowohl mit dem Flansch 41 wie auch mit der stromaufwärtigen Seite des Führungskörpers 35 in hydraulisch dichtendem Kontakt . Dazu sind die Abmessungen und die Elastizität des elastischen Dichtkörpers 42 so bemessen, daß der Dichtkörper 42 sowohl bei geschlossenem als auch bei geöffnetem Brennstoffeinspritzventil 1 eine hydraulisch dichtende Verbindung zwischen Führungskörper 35 und Flansch 41 hält.The sealing device 40 according to the invention, which in this exemplary embodiment consists of the flange 41 and the elastic sealing body 42, prevents the entry of fuel from the fuel channel 30c through the gap 39 between the guide body 35 and the valve closing element 4 in FIG the swirl chamber 37. The flange 41 is hydraulically sealed and non-positive, for example attached to the valve needle 3 by welding, soldering, gluing, pressing and / or shrinking. The elastic sealing body 42 is always in hydraulic contact with the flange 41 as well as with the upstream side of the guide body 35. For this purpose, the dimensions and the elasticity of the elastic sealing body 42 are dimensioned such that the sealing body 42 holds a hydraulically sealing connection between the guide body 35 and the flange 41 both when the fuel injector 1 is closed and when it is open.
Alle Teile der Dichtvorrichtung 40 sowie ihrer Verbindungsstellen sind temperaturbeständig und korrosionsfest ausgeführt und des weiteren so konstruiert und angebracht, daß sie die benötigte Kraft zur Schließung des Brennstoffeinspritzventils 1 nicht wesentlich erhöhen und somit die Ventildynamik nicht wesentlich beeinflussen. Materialauswahl und Formgebung der- Teile der Dichtvorrichtung 42 sind u.a. auf geringes Gewicht hin optimiert, um Trägheitskräfte gering zu halten. Der Fuhrungskorper 35 dient der Führung des stromabwärtigen Teils der Ventilnadel 3 über den kugelförmigen Ventilschließkorper 4. Die abgebildete Anordnung mit kugelförmigem Ventilschließkorper 4, der durch den Führungskörper 35 die stromabwärtige Führung der Ventilnadel 3 übernimmt, wird auch als kardanische Ventilnadelführung bezeichnet .All parts of the sealing device 40 and their connection points are temperature resistant and corrosion-resistant and further constructed and attached so that they do not significantly increase the force required to close the fuel injector 1 and thus do not significantly affect the valve dynamics. The selection of materials and the shape of the parts of the sealing device 42 are optimized, inter alia, for low weight in order to keep inertial forces low. The Fuhrungskorper 35 is used to guide the downstream part of the valve needle 3 over the spherical valve closing body 4. The arrangement shown with spherical valve closing body 4, which takes over the downstream guidance of the valve needle 3 through the guide body 35, is also referred to as a cardan valve needle guide.
Fig. 3 zeigt eine Detail ergrößerung des stark übertrieben dargestellten Spalts 39, der zwischen kugelförmigem Ventilschließkorper 4 und Fuhrungskorper 35 durch Spiel entsteht. Stromaufwärtig des Führungskörpers 35 ist der elastische Dichtkörper 42 angebracht.Fig. 3 shows a detail enlargement of the greatly exaggerated gap 39, which arises between the spherical valve closing body 4 and the guide body 35 through play. The elastic sealing body 42 is attached upstream of the guide body 35.
Die Erfindung ist nicht auf die dargestellten Ausführungsbeispiele beschränkt und z. B. auch für nach außen öffnende Brennstoffeinspritzventile anwendbar. The invention is not limited to the illustrated embodiments and z. B. also applicable for outward opening fuel injectors.

Claims

Ansprüche Expectations
1. Brennstoffeinspritzventil (1), insbesondere zum direkten Einspritzen von Brennstoff in einen Brennraum einer Brennkraftmaschine, mit einer Ventilnadel (3), die an einem abspritzseitigen Ende einen Ventilschließkorper (4) aufweist, der mit einer Ventilsitzfläche (6), die an einem Ventilsitzkörper (5) ausgebildet ist, zu einem Dichtsitz zusammenwirkt, und in einem Führungskörper (35) geführt ist, einer Dralleinrichtung (36) zur Erzeugung eines Dralls des Brennstoffs in einer Drallkammer (37) und einer stromabwärts der Ventilsitzfläche (6) vorgesehenen Abspritzöffnung (7), dadurch gekennzeichnet, daß durch eine wenigstens teilweise elastische Dichtvorrichtung (40) ein Zustrom von Brennstoff durch einen Spalt (39) zwischen Führungskörper (35) und Ventilschließkorper (4) in die Drallkammer (37) verhindert ist.1. Fuel injection valve (1), in particular for the direct injection of fuel into a combustion chamber of an internal combustion engine, with a valve needle (3) which has a valve closing body (4) on an injection-side end, which has a valve seat surface (6) on a valve seat body (5), cooperates to form a sealing seat, and is guided in a guide body (35), a swirl device (36) for generating a swirl of the fuel in a swirl chamber (37) and a spray opening (7) provided downstream of the valve seat surface (6) ), characterized in that an at least partially elastic sealing device (40) prevents the inflow of fuel through a gap (39) between the guide body (35) and valve closing body (4) into the swirl chamber (37).
2. Brennstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, daß die Dichtvorrichtung (40) einen elastischen Dichtkörper (42) umfaßt, der entlang der Bewegungsrichtungen der Ventilnadel (3) Zug- oder Druckkräfte mittelbar oder unmittelbar auf die Ventilnadel (3) ausübt.2. Fuel injection valve according to claim 1, characterized in that the sealing device (40) comprises an elastic sealing body (42) which exerts tensile or compressive forces indirectly or directly on the valve needle (3) along the directions of movement of the valve needle (3).
3. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) eine Torusform oder3. Fuel injection valve according to claim 2, characterized in that the elastic sealing body (42) has a toroidal shape or
Hohlzylinderform aufweist.Has hollow cylindrical shape.
4. Brennstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, daß der elastische Dichtkorper (42) scheibenförmig ist.4. Fuel injection valve according to claim 2, characterized in that the elastic sealing body (42) is disc-shaped.
5. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 4, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) von der Ventilnadel (3) durchgriffen ist.5. Fuel injection valve according to one of claims 2 to 4, characterized in that the elastic sealing body (42) is penetrated by the valve needle (3).
6. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis6. Fuel injection valve according to one of claims 2 to
5, dadurch gekennzeichnet, daß ein Flansch (41) mit der Ventilnadel (3) fest verbunden ist und der elastische Dichtkörper (42) zwischen dem Flansch (41) und dem Führungskörper (35) eingespannt ist.5, characterized in that a flange (41) is firmly connected to the valve needle (3) and the elastic sealing body (42) is clamped between the flange (41) and the guide body (35).
7. Brennstoffeinspritzventil nach Anspruch 6, dadurch gekennzeichnet, daß der Flansch (41) von der Ventilnadel (3) durchgriffen ist.7. Fuel injection valve according to claim 6, characterized in that the flange (41) is penetrated by the valve needle (3).
8. Brennstoffeinspritzventil nach Anspruch 6 oder 7, dadurch gekennzeichnet, daß der Flansch (41) ein L-förmiges Querschnitts-Profil aufweist.8. Fuel injection valve according to claim 6 or 7, characterized in that the flange (41) has an L-shaped cross-sectional profile.
9. Brennstoffeinspritzventil nach einem der Ansprüche 6 bis 8, dadurch gekennzeichnet, daß der Flansch (41) kraftschlüssig durch ein Fügeverfahren an der Ventilnadel (3) angebracht ist, insbesondere durch Schweißen, Löten, Kleben, Pressen und/oder Schrumpfen. 9. Fuel injection valve according to one of claims 6 to 8, characterized in that the flange (41) is non-positively attached by a joining process to the valve needle (3), in particular by welding, soldering, gluing, pressing and / or shrinking.
10. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 9, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) aus einem Elastomer besteht.10. Fuel injection valve according to one of claims 2 to 9, characterized in that the elastic sealing body (42) consists of an elastomer.
11. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) durch äußere Reibung in seiner Position gehalten ist.11. Fuel injection valve according to one of claims 2 to 10, characterized in that the elastic sealing body (42) is held in position by external friction.
12. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) durch Formschluß in seiner Position gehalten ist.12. Fuel injection valve according to one of claims 2 to 10, characterized in that the elastic sealing body (42) is held in its position by positive locking.
13. Brennstoffeinspritzventil nach einem der Ansprüche 2 bis 10, dadurch gekennzeichnet, daß der elastische Dichtkörper (42) durch eine13. Fuel injection valve according to one of claims 2 to 10, characterized in that the elastic sealing body (42) by a
Klebeverbindung in seiner Position gehalten ist. Adhesive connection is held in position.
EP03731607A 2002-03-27 2003-01-09 Fuel injection valve Withdrawn EP1490593A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10213857 2002-03-27
DE10213857A DE10213857A1 (en) 2002-03-27 2002-03-27 Fuel injector
PCT/DE2003/000040 WO2003081022A1 (en) 2002-03-27 2003-01-09 Fuel injection valve

Publications (1)

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EP1490593A1 true EP1490593A1 (en) 2004-12-29

Family

ID=27816011

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EP03731607A Withdrawn EP1490593A1 (en) 2002-03-27 2003-01-09 Fuel injection valve

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EP (1) EP1490593A1 (en)
JP (1) JP2005520980A (en)
KR (1) KR20040093188A (en)
DE (1) DE10213857A1 (en)
WO (1) WO2003081022A1 (en)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1811166A1 (en) * 2006-01-24 2007-07-25 Siemens Aktiengesellschaft Valve assembly for an injection valve and injection valve
EP2110541A1 (en) * 2008-04-18 2009-10-21 MAGNETI MARELLI POWERTRAIN S.p.A. Fuel injector with direct shutter actuation for internal combustion engines

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Publication number Priority date Publication date Assignee Title
JP2007162678A (en) * 2005-11-16 2007-06-28 Toyota Motor Corp Fuel injection valve
CN114440038B (en) * 2021-12-21 2024-03-22 河南中泽新材料股份有限公司 Pipeline joint sealing assembly and same-layer drainage cyclone combined structure

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US5642862A (en) * 1995-07-28 1997-07-01 Siemens Automotive Corporation Fuel injection valve having a guide diaphragm and method for assembling
DE19736682A1 (en) * 1997-08-22 1999-02-25 Bosch Gmbh Robert Fuel injector for internal combustion engine
DE19815780A1 (en) * 1998-04-08 1999-10-14 Bosch Gmbh Robert Fuel injector and method for assembling a fuel injector
DE19907859A1 (en) * 1998-08-27 2000-03-02 Bosch Gmbh Robert Fuel injection valve for direct injection into combustion chamber of internal combustion engine has activatable operating component with valve closure body movable axially along valve longitudinal axis
US6065692A (en) * 1999-06-09 2000-05-23 Siemens Automotive Corporation Valve seat subassembly for fuel injector
DE19956830C2 (en) * 1999-11-25 2002-07-18 Siemens Ag execution

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Title
See references of WO03081022A1 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1811166A1 (en) * 2006-01-24 2007-07-25 Siemens Aktiengesellschaft Valve assembly for an injection valve and injection valve
EP2110541A1 (en) * 2008-04-18 2009-10-21 MAGNETI MARELLI POWERTRAIN S.p.A. Fuel injector with direct shutter actuation for internal combustion engines

Also Published As

Publication number Publication date
KR20040093188A (en) 2004-11-04
JP2005520980A (en) 2005-07-14
DE10213857A1 (en) 2003-10-09
WO2003081022A1 (en) 2003-10-02

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