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EP0484681A1 - Injection device for a fuel-gas mixture - Google Patents

Injection device for a fuel-gas mixture Download PDF

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Publication number
EP0484681A1
EP0484681A1 EP91117093A EP91117093A EP0484681A1 EP 0484681 A1 EP0484681 A1 EP 0484681A1 EP 91117093 A EP91117093 A EP 91117093A EP 91117093 A EP91117093 A EP 91117093A EP 0484681 A1 EP0484681 A1 EP 0484681A1
Authority
EP
European Patent Office
Prior art keywords
gas
fuel
valve
longitudinal
swirl element
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
EP91117093A
Other languages
German (de)
French (fr)
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EP0484681B1 (en
Inventor
Uwe Dipl.-Ing. Grytz
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Robert Bosch GmbH
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Robert Bosch GmbH
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Publication date
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Publication of EP0484681A1 publication Critical patent/EP0484681A1/en
Application granted granted Critical
Publication of EP0484681B1 publication Critical patent/EP0484681B1/en
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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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/04—Injectors peculiar thereto
    • F02M69/047—Injectors peculiar thereto injectors with air chambers, e.g. communicating with atmosphere for aerating the nozzles
    • 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
    • F02M67/00—Apparatus in which fuel-injection is effected by means of high-pressure gas, the gas carrying the fuel into working cylinders of the engine, e.g. air-injection type
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/08—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel characterised by the fuel being carried by compressed air into main stream of combustion-air
    • 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
    • F02M69/00—Low-pressure fuel-injection apparatus ; Apparatus with both continuous and intermittent injection; Apparatus injecting different types of fuel
    • F02M69/46—Details, component parts or accessories not provided for in, or of interest apart from, the apparatus covered by groups F02M69/02 - F02M69/44
    • F02M69/50—Arrangement of fuel distributors, e.g. with means for supplying equal portion of metered fuel to injectors

Definitions

  • the invention relates to a device for injecting a fuel-gas mixture according to the preamble of the main claim.
  • a device for injecting a fuel-gas mixture is already known, in which the fuel injector protrudes with its valve end into a stepped longitudinal bore in a gas encasing part.
  • the gas comprises the sprayed fuel in its flow direction and leads to the formation of a fuel-gas mixture.
  • this device has the disadvantage that due to the uniform flow of the gas, which runs approximately in the direction of the sprayed-off fuel, only an unsatisfactory swirling of the fuel takes place, so that a relatively inhomogeneous fuel-gas mixture is formed with a relatively large fuel droplet size.
  • intensive swirling of the fuel and the associated fine droplets of fuel have a positive effect.
  • the device according to the invention with the characterizing features of the main claim has the advantage that the gas emerging from the at least one curved flow channel into the mixing opening of the swirl element strikes the sprayed fuel with swirl.
  • the fuel is particularly swirled and atomized so that a very homogeneous fuel-gas mixture is formed.
  • a homogeneous fuel-gas mixture ensures low exhaust emissions, good acceleration behavior and low fuel consumption of the internal combustion engine.
  • the device according to the invention has a simple structure and can therefore be manufactured in a simple and inexpensive manner.
  • the at least one flow channel of the swirl element is helically curved and its cross-sectional area tapers in the direction of the mixing opening.
  • the gas flowing into the mixing opening has a strong swirl and a high flow rate.
  • the at least one flow channel opens radially into the mixing opening.
  • the gas supply channel is tangentially connected to the longitudinal opening of the gas enclosing part, so that the supplied gas flows swirled into the longitudinal opening and into the flow channels of the swirl element.
  • a compression spring is arranged between a downstream holding shoulder of the longitudinal opening of the gas encasing part and an end face of the swirl element which is displaceable in the axial direction and faces away from the valve end of the fuel injection valve.
  • the compression spring enables axial compensation of the positional tolerances of the fuel injection valve and gas enclosing part or longitudinal opening with respect to one another, as well as a uniform pressing of the swirl element against the fuel injection valve.
  • the swirl element is secured against twisting with respect to the longitudinal bore of the gas enclosing part, so that the gas flowing through the swirl element cannot twist the swirl element, thereby ensuring the exact positioning of the gas outlet. This is particularly important when using two-jet fuel injection valves, for example for four-valve internal combustion engines.
  • a retaining lug is formed on the circumference of the swirl element, which cooperates with a recess formed in the wall of the longitudinal opening of the gas encasing part.
  • the gas encasing part which has a plurality of longitudinal bores, can be connected to a fuel distributor piece, which receives a number of fuel injectors corresponding to the number of longitudinal openings of the gas encasing part and arranged concentrically to these, and serves to supply fuel.
  • FIG. 1 shows the exemplary embodiment with a partially illustrated fuel injector and a partially illustrated fuel distributor piece
  • FIG. 2 shows a section along the line II-II in FIG. 1.
  • the device shown in FIG. 1, for example, for injecting a fuel-gas mixture into an intake pipe or directly into a combustion chamber of a mixture-compressing spark-ignition internal combustion engine has a fuel injector 1 with a valve end 3.
  • the fuel injector 1 is partially concentric to one in the axial direction Surround the longitudinal valve axis 4 stepped receiving opening 5 of a fuel distributor 7, which has, for example, a number of stepped receiving openings 5 corresponding to the number of cylinders of the internal combustion engine.
  • the fuel injection valve 1 protrudes with its valve end 3 into a stepped longitudinal opening 9 of a gas enclosing part 11, which is formed, for example, as a plastic injection part, concentrically with the valve longitudinal axis 4.
  • the gas enclosing part 11 has, for example, a number of longitudinal openings 9 corresponding to the number of cylinders of the internal combustion engine and is with the fuel distributor piece 7 connectable.
  • the stepped longitudinal openings 9 are arranged in the gas enclosing part 11 such that the longitudinal openings 9 run concentrically to the receiving openings 5 of the fuel distributor 7 when the fuel distributor 7 and gas enclosing part 11 are connected to one another, as shown in FIG.
  • a flat seal 12 is arranged between an end face 10 of the gas enclosing part 11 facing the fuel distributor piece 7 and an opposing contact surface 8 of the fuel distributor piece 7.
  • a gas supply channel 13 is formed, which is tangentially connected to the individual longitudinal openings 9 of the gas enclosing part 11. The gas supplied thus reaches the longitudinal openings 9 with swirl.
  • the fuel injection valve 1 has in its valve end 3 e.g. a valve closing part 17 which cooperates with a fixed valve seat 15 which tapers in the shape of a truncated cone in the direction of fuel flow.
  • the valve closing part 17 is connected at its end facing away from the fixed valve seat 15 to an armature 19 which cooperates with a magnet coil 21 partially surrounding the armature 19 in the axial direction and with a core 23 opposite the armature 19 in the direction facing away from the fixed valve seat 15.
  • a sealing section 25 of the valve closing part 17 which interacts with the fixed valve seat 15 is, for example, frustoconical.
  • a perforated plate 29 lies directly against an end face 27 of the valve end 3.
  • the perforated plate 29 has, for example, two spray openings 31 through which the fuel flowing past the fixed valve seat 15 when the valve closing part 17 is lifted off is released.
  • a pot-shaped protective cap 33 can be arranged, which rests with its base 35 on the perforated plate 29.
  • the bottom 35 has a through opening 36, through which the fuel flowing out of the spray openings 31 is injected.
  • the base 35 of the protective cap 33 is first adjoined by an axially extending parallel section 38 and by a radial section 40 pointing radially outward.
  • the protective cap 33 is connected to the circumference of the valve end 3 by means of a latching connection 42.
  • a holding ring 43 bears against the magnet coil 21.
  • a sealing ring 44 is arranged in the radial direction between the circumference of the valve end 3 and the wall of the receiving opening 5 of the fuel distributor piece 7. The axial displaceability of the sealing ring 44 on the circumference of the valve end 3 is limited by the radial section 40 of the protective cap 33 and by the retaining ring 43, so that a secure and reliable seal between the valve end 3 and the receiving opening 5 of the fuel distributor piece 7 is ensured.
  • the longitudinal opening 9 of the gas encasing part 11 has, at its end facing away from the fuel distributor 7, a radially inward-pointing holding shoulder 45 which, concentric to the longitudinal valve axis 4, has an outflow section 46 that widens away from the fuel injector 1, for example in the shape of a truncated cone.
  • the fuel distributor piece 7, with a centering part 48 facing the holding shoulder 45 of the gas enclosing part 11, projects with a slight radial play into a centering section 50 of the longitudinal opening 9 of the gas enclosing part 11, so that the receiving opening 5 of the fuel distributor piece 7 and the fuel injection valve 1 arranged therein opposite the longitudinal opening 9 of the gas enclosing part 11 are centered.
  • a swirl element 55 is arranged in the longitudinal opening 9 between the valve end 3 of the fuel injection valve 1 and the holding shoulder 45 of the gas enclosing part 11.
  • the swirl element 55 concentrically with the valve longitudinal axis 4 has a continuous mixing opening 57 which widens in the shape of a truncated cone in the direction of flow to the holding shoulder 45 and is displaceable in the axial direction in that between a holding surface 59 of the holding shoulder 45 facing the swirl element 55 and a holding surface 45 facing the holding shoulder 45 End face 61 of the swirl element 55, a compression spring 63, for example in the form of a plate spring, is arranged, which can be obtained inexpensively as a mass product.
  • the compression spring 63 lies with an outer radial section 65 in the axial direction on the holding surface 59 of the holding shoulder 45 and in the radial direction with its circumference formed by the outer edge 66 of the radial section 65 against a parallel section 67 of the longitudinal opening 9 of the gas encasing part 11.
  • An inclined section 69 of the compression spring 63 which is directed inward in the radial direction, rests with its end 70 facing the fuel injection valve 1 in the axial direction on the end face 61 of the swirl element 55.
  • the compression spring 63 is elastically deformed in the assembled device according to the invention in the axial direction, that is to say preloaded, so that the compression spring 63 has the swirl element 55, which is displaceable in the axial direction, with its end face 64 facing the protective cap 33 against the bottom 35 of the fuel injector at the valve end 3 1 attached protective cap 33 presses.
  • the compression spring 63 in this way enables the axial compensation of the position tolerances of the fuel injection valve 1 and the gas encasing part 11 or its longitudinal opening 9 with respect to one another. It is sufficient if the compression spring 63 has only a relatively low spring constant, so that the risk of damage to the swirl element 55, which is designed, for example, as a plastic injection-molded part, is avoided.
  • the swirl element 55 has on its periphery facing the compression spring 63 a first cylindrical section 72, the diameter of which is slightly smaller than the diameter of the parallel section 67 surrounding the swirl element 55 of the longitudinal opening 9, so that between the first cylindrical section 72 of the swirl element 55 and the Longitudinal opening 9 of the gas enclosing part 11 is formed a narrow radial gap.
  • a retaining lug 74 is formed on the circumference of the first cylindrical section 72 of the swirl element 55 and extends in the axial direction, for example over the entire axial length of the first cylindrical section 72.
  • a recess 76 is formed in the wall of the parallel section 67 of the longitudinal bore 9, which cooperates with the retaining lug 74 of the swirl element 55 in such a way that the retaining lug 74 projects into the recess 76 of the longitudinal bore 9 of the gas encasing part 11 and thus the swirl element 55 with respect to the longitudinal bore 9 is secured against twisting. This ensures a defined position of the gas outlet, as used for the use of multi-jet injection valves e.g. is important for four-valve internal combustion engines.
  • the first cylindrical section 72 is adjoined at its end facing the valve end 3 by a radially inward-pointing, flat radial section 78 of the swirl element 55, which extends up to a second cylindrical section 77.
  • a flow section 80 tapering in the direction of the valve longitudinal axis 4 of the protective cap 33 is formed in the axial direction between the second cylindrical section 77 and the end face 64 of the swirl element 55 abutting the protective cap 33.
  • the flow section 80 is, for example, concave on its circumference, ie curved away from the valve end 3.
  • At least one flow channel 82 is formed in the wall of the flow section 80 of the swirl element 55, but in the exemplary embodiment shown a plurality of flow channels 82 are formed, which have the shape of grooves 83, for example, extending into the second cylindrical section 77 and starting from the second cylindrical one Section 77 extends up to the end face 64 of the swirl element 55 in a helical curve and there, as shown in FIG. 2, which shows a section along the line II-II in FIG. 1, opens radially into the mixing opening 57 of the swirl element 55.
  • the flow channels 82 are designed such that the flow cross-sections taper continuously in the direction of the end face 64 towards the mixing opening 57 of the swirl element 55.
  • the flow channels 82 are laterally delimited by flow blades 85 which serve to guide the gas flowing in the direction of the mixing opening 57.
  • the gas is strongly accelerated due to the tapering flow cross-section and reaches its maximum speed when exiting the flow channels 82.
  • the flow channels 82 and the grooves 83 forming them, as shown in FIG. 1, have, for example, the same axial extent at their groove bases 84 as the second cylindrical section 77 of the swirl element 55.
  • the groove bases 84 run in the direction of the end face 64 of the swirl element 55 curved just as concavely as the circumference of the flow section 80.
  • the amount of gas fed into the mixing opening 57 of the swirl element 55 is determined by the size of the flow cross sections of the flow channels 82.
  • the swirling, radial supply of the gas at high speed into the mixing opening 57 to the fuel discharged from the spray openings 31 leads to the formation of a largely homogeneous fuel-gas mixture with particularly fine fuel droplets. This allows the Internal combustion engine to achieve significant improvements in terms of exhaust gas emission, acceleration behavior and fuel consumption.
  • Both fresh air and an inert gas and a mixture of the two can be used as the gas for forming the fuel-gas mixture.
  • the fresh air is branched off, for example, from the intake pipe in front of an arbitrarily adjustable throttle element and fed to the gas supply duct 13.
  • an inert gas e.g. use the exhaust gas of the internal combustion engine so that the pollutant emission of the internal combustion engine is reduced by this exhaust gas recirculation.
  • the gas can also be pumped using an additional pump.
  • the device according to the invention also has the advantage of having a simple structure and low manufacturing costs.
  • a system unit consisting of a fuel distributor 7, the fuel injection valves 1, the gas containment part 11 with the swirl elements 55 and a pressure regulator for the fuel can be easily and inexpensively mounted on the intake line of an internal combustion engine.

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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

In the case of known devices for the injection of a fuel-gas mixture with a fuel injection valve projecting into a stepped longitudinal bore of a gas enclosing section, the formation of an extremely homogeneous fuel-gas mixture and the fine atomisation of the fuel is not guaranteed if the gas encloses the sprayed fuel approximately in its direction of flow. <??>In the longitudinal opening (9) of the gas enclosing section (11) the novel device has a swirling element (55) with a mixing aperture (57) running concentrically to the valve longitudinal axis (4), into which aperture at least one curved, groove-shaped flow duct (82) formed in the wall of the swirling element (55) opens. In this way an especially fine atomisation of the fuel and the formation of an extremely homogeneous fuel-gas mixture is ensured. <??>The design of the device is particularly suitable for use on mixture-compressing spark ignition internal combustion engines. <IMAGE>

Description

Stand der TechnikState of the art

Die Erfindung geht aus von einer Vorrichtung zur Einspritzung eines Brennstoff-Gas-Gemisches nach der Gattung des Hauptanspruchs. Aus der DE 36 09 798 A1 ist schon eine Vorrichtung zur Einspritzung eines Brennstoff-Gas-Gemisches bekannt, bei der das Brennstoffeinspritzventil mit seinem Ventilende in eine abgestufte Längsbohrung eines Gasumfassungsteils ragt. Das Gas umfaßt den abgespritzten Brennstoff in seiner Strömungsrichtung und führt zur Bildung eines Brennstoff-Gas-Gemisches. Diese Vorrichtung hat aber den Nachteil, daß durch die gleichmäßige, in etwa in Richtung des abgespritzten Brennstoffes verlaufende Strömung des Gases nur eine unbefriedigende Verwirbelung des Brennstoffs stattfindet, so daß sich ein relativ inhomogenes Brennstoff-Gas-Gemisch mit einer verhältnismäßig großen Brennstofftröpfchengröße bildet. Hinsichtlich der Abgasemissionen sowie des Brennstoffverbrauchs wirken sich aber eine intensive Verwirbelung des Brennstoffs und damit verbundene feine Brennstofftröpfchen positiv aus.The invention relates to a device for injecting a fuel-gas mixture according to the preamble of the main claim. From DE 36 09 798 A1, a device for injecting a fuel-gas mixture is already known, in which the fuel injector protrudes with its valve end into a stepped longitudinal bore in a gas encasing part. The gas comprises the sprayed fuel in its flow direction and leads to the formation of a fuel-gas mixture. However, this device has the disadvantage that due to the uniform flow of the gas, which runs approximately in the direction of the sprayed-off fuel, only an unsatisfactory swirling of the fuel takes place, so that a relatively inhomogeneous fuel-gas mixture is formed with a relatively large fuel droplet size. With regard to exhaust gas emissions and fuel consumption, however, intensive swirling of the fuel and the associated fine droplets of fuel have a positive effect.

Vorteile der ErfindungAdvantages of the invention

Die erfindungsgemäße Vorrichtung mit den kennzeichnenden Merkmalen des Hauptanspruchs hat demgegenüber den Vorteil, daß das aus dem wenigstens einen gekrümmten Strömungskanal in die Mischöffnung des Drallelementes austretende Gas drallbehaftet auf den abgespritzten Brennstoff trifft. Hierdurch wird der Brennstoff besonders intensiv verwirbelt und fein zerstäubt, so daß sich ein sehr homogenes Brennstoff-Gas-Gemisch bildet. Ein homogenes Brennstoff-Gas-Gemisch gewährleistet niedrige Abgasemissionen, ein gutes Beschleunigungsverhalten sowie einen geringen Brennstoffverbrauch der Brennkraftmaschine.The device according to the invention with the characterizing features of the main claim has the advantage that the gas emerging from the at least one curved flow channel into the mixing opening of the swirl element strikes the sprayed fuel with swirl. As a result, the fuel is particularly swirled and atomized so that a very homogeneous fuel-gas mixture is formed. A homogeneous fuel-gas mixture ensures low exhaust emissions, good acceleration behavior and low fuel consumption of the internal combustion engine.

Zudem weist die erfindungsgemäße Vorrichtung einen einfachen Aufbau auf und ist dadurch auf einfache und kostengünstige Art und Weise herstellbar.In addition, the device according to the invention has a simple structure and can therefore be manufactured in a simple and inexpensive manner.

Durch die in den Unteransprüchen aufgeführten Maßnahmen sind vorteilhafte Weiterbildungen und Verbesserungen der im Hauptanspruch angegebenen Vorrichtung möglich.Advantageous further developments and improvements of the device specified in the main claim are possible through the measures listed in the subclaims.

Besonders vorteilhaft ist es, wenn der wenigstens eine Strömungskanal des Drallelementes schneckenförmig gekrümmt verläuft und sich seine Querschnittsfläche in Richtung zu der Mischöffnung hin verjüngt. So weist das in die Mischöffnung strömende Gas einen starken Drall und eine hohe Strömungsgeschwindigkeit auf.It is particularly advantageous if the at least one flow channel of the swirl element is helically curved and its cross-sectional area tapers in the direction of the mixing opening. The gas flowing into the mixing opening has a strong swirl and a high flow rate.

Damit das Gas beim Einströmen in die Mischöffnung unmittelbar auf den abgespritzten Brennstoff trifft, ist es von Vorteil, wenn der wenigstens eine Strömungskanal radial in die Mischöffnung mündet.So that the gas strikes the sprayed fuel as it flows into the mixing opening, it is advantageous if the at least one flow channel opens radially into the mixing opening.

Von Vorteil ist es, wenn der Gaszufuhrkanal tangential mit der Längsöffnung des Gasumfassungsteils in Verbindung steht, so daß das zugeführte Gas drallbehaftet in die Längsöffnung und in die Strömungskanäle des Drallelements einströmt.It is advantageous if the gas supply channel is tangentially connected to the longitudinal opening of the gas enclosing part, so that the supplied gas flows swirled into the longitudinal opening and into the flow channels of the swirl element.

Es ist vorteilhaft, wenn zwischen einem stromabwärtigen Halteabsatz der Längsöffnung des Gasumfassungsteils und einer dem Ventilende des Brennstoffeinspritzventils abgewandten Stirnseite des in axialer Richtung verschiebbaren Drallelementes eine Druckfeder angeordnet ist. Die Druckfeder ermöglicht den axialen Ausgleich der Lagetoleranzen von Brennstoffeinspritzventil und Gasumfassungsteil bzw. Längsöffnung zueinander sowie eine gleichmäßige Anpressung des Drallelementes an das Brennstoffeinspritzventil.It is advantageous if a compression spring is arranged between a downstream holding shoulder of the longitudinal opening of the gas encasing part and an end face of the swirl element which is displaceable in the axial direction and faces away from the valve end of the fuel injection valve. The compression spring enables axial compensation of the positional tolerances of the fuel injection valve and gas enclosing part or longitudinal opening with respect to one another, as well as a uniform pressing of the swirl element against the fuel injection valve.

Von Vorteil ist es, wenn das Drallelement gegenüber der Längsbohrung des Gasumfassungsteils gegen Verdrehen gesichert ist, so daß das das Drallelement durchströmende Gas das Drallelement nicht verdrehen kann und dadurch die exakte Positionierung des Gasaustrittes gewährleistet ist. Dies ist besonders wichtig bei der Verwendung von Zweistrahl-Brennstoffeinspritzventilen beispielsweise für Vier-Ventil-Brennkraftmaschinen.It is advantageous if the swirl element is secured against twisting with respect to the longitudinal bore of the gas enclosing part, so that the gas flowing through the swirl element cannot twist the swirl element, thereby ensuring the exact positioning of the gas outlet. This is particularly important when using two-jet fuel injection valves, for example for four-valve internal combustion engines.

Zu diesem Zweck ist es vorteilhaft, wenn an dem Umfang des Drallelementes eine Haltnase ausgebildet ist, die mit einer in der Wandung der Längsöffnung des Gasumfassungsteils ausgeformten Ausnehmung zusammenwirkt.For this purpose, it is advantageous if a retaining lug is formed on the circumference of the swirl element, which cooperates with a recess formed in the wall of the longitudinal opening of the gas encasing part.

Es ist besonders vorteilhaft, wenn in dem Gasumfassungsteil mehrere abgestufte, jeweils ein Drallelement aufweisende Längsöffnungen ausgebildet sind, die mit einem gemeinsamen Gaszufuhrkanal verbunden sind, so daß sich eine kompakte und kostengünstig herstellbare Einheit ergibt.It is particularly advantageous if a plurality of stepped longitudinal openings, each having a swirl element, are formed in the gas encasing part and are connected to a common gas supply duct, so that a compact and inexpensive unit can be produced.

Aus dem gleichen Grund ist es dabei von Vorteil, wenn das mehrere Längsbohrungen aufweisende Gasumfassungsteil mit einem Brennstoffverteilerstück verbindbar ist, das eine der Zahl der Längsöffnungen des Gasumfassungsteils entsprechende und konzentrisch zu diesen angeordnete Anzahl von Brennstoffeinspritzventilen aufnimmt und der Zufuhr von Brennstoff dient.For the same reason, it is advantageous if the gas encasing part, which has a plurality of longitudinal bores, can be connected to a fuel distributor piece, which receives a number of fuel injectors corresponding to the number of longitudinal openings of the gas encasing part and arranged concentrically to these, and serves to supply fuel.

Zeichnungdrawing

Ein Ausführungsbeispiel der Erfindung ist in der Zeichnung vereinfacht dargestellt und in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 das Ausführungsbeispiel mit einem teilweise dargestellten Brennstoffeinspritzventil und einem teilweise dargestellten Brennstoffverteilerstück und Figur 2 einen Schnitt entlang der Linie II-II in Figur 1.An embodiment of the invention is shown in simplified form in the drawing and explained in more detail in the following description. FIG. 1 shows the exemplary embodiment with a partially illustrated fuel injector and a partially illustrated fuel distributor piece, and FIG. 2 shows a section along the line II-II in FIG. 1.

Beschreibung des AusführungsbeispielsDescription of the embodiment

Die in der Figur 1 beispielsweise dargestellte Vorrichtung zur Einspritzung eines Brennstoff-Gas-Gemisches in ein Ansaugrohr oder unmittelbar in einen Brennraum einer gemischverdichtenden fremdgezündeten Brennkraftmaschine besitzt ein Brennstoffeinspritzventil 1 mit einem Ventilende 3. Das Brennstoffeinspritzventil 1 ist in axialer Richtung teilweise von einer konzentrisch zu einer Ventillängsachse 4 verlaufenden abgestuften Aufnahmeöffnung 5 eines Brennstoffverteilerstücks 7 umgeben, das beispielsweise eine der Zylinderzahl der Brennkraftmaschine entsprechende Anzahl von abgestuften Aufnahmeöffnungen 5 hat. Das Brennstoffeinspritzventil 1 ragt mit seinem Ventilende 3 in eine konzentrisch zu der Ventillängsachse 4 verlaufende abgestufte Längsöffnung 9 eines beispielsweise als Kunststoffspritzteil ausgeformten Gasumfassungsteils 11. Das Gasumfassungsteil 11 weist z.B. eine der Zylinderzahl der Brennkraftmaschine entsprechende Anzahl von Längsöffnungen 9 auf und ist mit dem Brennstoffverteilerstück 7 verbindbar. Die abgestuften Längsöffnungen 9 sind in dem Gasumfassungsteil 11 derart angeordnet, daß die Längsöffnungen 9 konzentrisch zu den Aufnahmeöffnungen 5 des Brennstoffverteilerstücks 7 verlaufen, wenn Brennstoffverteilerstück 7 und Gasumfassungsteil 11, wie in der Figur 1 dargestellt, miteinander verbunden sind.The device shown in FIG. 1, for example, for injecting a fuel-gas mixture into an intake pipe or directly into a combustion chamber of a mixture-compressing spark-ignition internal combustion engine has a fuel injector 1 with a valve end 3. The fuel injector 1 is partially concentric to one in the axial direction Surround the longitudinal valve axis 4 stepped receiving opening 5 of a fuel distributor 7, which has, for example, a number of stepped receiving openings 5 corresponding to the number of cylinders of the internal combustion engine. The fuel injection valve 1 protrudes with its valve end 3 into a stepped longitudinal opening 9 of a gas enclosing part 11, which is formed, for example, as a plastic injection part, concentrically with the valve longitudinal axis 4. The gas enclosing part 11 has, for example, a number of longitudinal openings 9 corresponding to the number of cylinders of the internal combustion engine and is with the fuel distributor piece 7 connectable. The stepped longitudinal openings 9 are arranged in the gas enclosing part 11 such that the longitudinal openings 9 run concentrically to the receiving openings 5 of the fuel distributor 7 when the fuel distributor 7 and gas enclosing part 11 are connected to one another, as shown in FIG.

Zwischen einer dem Brennstoffverteilerstück 7 zugewandten Stirnseite 10 des Gasumfassungsteils 11 und einer gegenüberliegenden Anlagefläche 8 des Brennstoffverteilerstücks 7 ist eine Flachdichtung 12 angeordnet. In dem Gasumfassungsteil 11 ist z.B. ein Gaszufuhrkanal 13 ausgeformt, der tangential mit den einzelnen Längsöffnungen 9 des Gasumfassungsteils 11 in Verbindung steht. So gelangt das zugeführte Gas drallbehaftet in die Längsöffnungen 9.A flat seal 12 is arranged between an end face 10 of the gas enclosing part 11 facing the fuel distributor piece 7 and an opposing contact surface 8 of the fuel distributor piece 7. In the gas containment part 11, e.g. a gas supply channel 13 is formed, which is tangentially connected to the individual longitudinal openings 9 of the gas enclosing part 11. The gas supplied thus reaches the longitudinal openings 9 with swirl.

Das Brennstoffeinspritzventil 1 weist in seinem Ventilende 3 z.B. ein mit einem festen, sich in Brennstoffströmungsrichtung kegelstumpfförmig verjüngenden Ventilsitz 15 zusammenwirkendes Ventilschließteil 17 auf. Das Ventilschließteil 17 ist an seinem dem festen Ventilsitz 15 abgewandten Ende mit einem Anker 19 verbunden, der mit einer den Anker 19 in axialer Richtung teilweise umgebenden Magnetspule 21 und einem dem Anker 19 in dem festen Ventilsitz 15 abgewandter Richtung gegenüberliegenden Kern 23 zusammenwirkt. Ein mit dem festen Ventilsitz 15 zusammenwirkender Dichtabschnitt 25 des Ventilschließteils 17 ist beispielsweise kegelstumpfförmig ausgebildet. An dem mit dem Anker 19 verbundenen Ende des Ventilschließteils 17 liegt eine Rückstellfeder 26 an, die bestrebt ist, das Ventilschließteil 17 in Richtung des festen Ventilsitzes 15 zu bewegen.The fuel injection valve 1 has in its valve end 3 e.g. a valve closing part 17 which cooperates with a fixed valve seat 15 which tapers in the shape of a truncated cone in the direction of fuel flow. The valve closing part 17 is connected at its end facing away from the fixed valve seat 15 to an armature 19 which cooperates with a magnet coil 21 partially surrounding the armature 19 in the axial direction and with a core 23 opposite the armature 19 in the direction facing away from the fixed valve seat 15. A sealing section 25 of the valve closing part 17 which interacts with the fixed valve seat 15 is, for example, frustoconical. At the end of the valve closing part 17 connected to the armature 19 there is a return spring 26 which tends to move the valve closing part 17 in the direction of the fixed valve seat 15.

Unmittelbar an einer Stirnfläche 27 des Ventilendes 3 liegt ein Lochplättchen 29 an. Das Lochplättchen 29 weist beispielsweise zwei Abspritzöffnungen 31 auf, durch die der bei abgehobenem Ventilschließteil 17 an dem festen Ventilsitz 15 vorbeiströmende Brennstoff abgegeben wird.A perforated plate 29 lies directly against an end face 27 of the valve end 3. The perforated plate 29 has, for example, two spray openings 31 through which the fuel flowing past the fixed valve seat 15 when the valve closing part 17 is lifted off is released.

An dem Ventilende 3 des Brennstoffeinspritzventils 1 kann eine topfförmige Schutzkappe 33 angeordnet sein, die mit ihrem Boden 35 an dem Lochplättchen 29 anliegt. Der Boden 35 hat eine Durchgangsöffnung 36, durch die der aus den Abspritzöffnungen 31 strömende Brennstoff gespritzt wird. In der Magnetspule 21 zugewandter Richtung schließt sich an den Boden 35 der Schutzkappe 33 zunächst ein axial verlaufender Parallelabschnitt 38 und daran ein radial nach außen weisender Radialabschnitt 40 an. Die Schutzkappe 33 ist mittels einer Rastverbindung 42 mit dem Umfang des Ventilendes 3 verbunden.At the valve end 3 of the fuel injection valve 1, a pot-shaped protective cap 33 can be arranged, which rests with its base 35 on the perforated plate 29. The bottom 35 has a through opening 36, through which the fuel flowing out of the spray openings 31 is injected. In the direction facing the magnet coil 21, the base 35 of the protective cap 33 is first adjoined by an axially extending parallel section 38 and by a radial section 40 pointing radially outward. The protective cap 33 is connected to the circumference of the valve end 3 by means of a latching connection 42.

An dem Umfang des Ventilendes 3 des Brennstoffeinspritzventils 1 liegt der Magnetspule 21 zugewandt ein Haltering 43 an. In radialer Richtung ist zwischen dem Umfang des Ventilendes 3 und der Wandung der Aufnahmeöffnung 5 des Brennstoffverteilerstücks 7 ein Dichtring 44 angeordnet. Die axiale Verschiebbarkeit des Dichtringes 44 auf dem Umfang des Ventilendes 3 wird durch den Radialabschnitt 40 der Schutzkappe 33 sowie durch den Haltering 43 begrenzt, so daß eine sichere und zuverlässige Abdichtung zwischen dem Ventilende 3 und der Aufnahmeöffnung 5 des Brennstoffverteilerstücks 7 gewährleistet ist.On the circumference of the valve end 3 of the fuel injection valve 1, a holding ring 43 bears against the magnet coil 21. A sealing ring 44 is arranged in the radial direction between the circumference of the valve end 3 and the wall of the receiving opening 5 of the fuel distributor piece 7. The axial displaceability of the sealing ring 44 on the circumference of the valve end 3 is limited by the radial section 40 of the protective cap 33 and by the retaining ring 43, so that a secure and reliable seal between the valve end 3 and the receiving opening 5 of the fuel distributor piece 7 is ensured.

Die Längsöffnung 9 des Gasumfassungsteils 11 weist an ihrem dem Brennstoffverteilerstück 7 abgewandten Ende einen radial nach innen weisenden Halteabsatz 45 auf, der konzentrisch zu der Ventillängsachse 4 einen sich dem Brennstoffeinspritzventil 1 abgewandt beispielsweise kegelstumpfförmig erweiternden Abströmabschnitt 46 hat. Das Brennstoffverteilerstück 7 ragt mit einem dem Halteabsatz 45 des Gasumfassungsteils 11 zugewandten Zentrierteil 48 mit geringem radialen Spiel in einen Zentrierabschnitt 50 der Langsöffnung 9 des Gasumfassungsteils 11, so daß die Aufnahmeöffnung 5 des Brennstoffverteilerstücks 7 und das darin angeordnete Brennstoffeinspritzventil 1 gegenüber der Längsöffnung 9 des Gasumfassungsteils 11 zentriert sind.The longitudinal opening 9 of the gas encasing part 11 has, at its end facing away from the fuel distributor 7, a radially inward-pointing holding shoulder 45 which, concentric to the longitudinal valve axis 4, has an outflow section 46 that widens away from the fuel injector 1, for example in the shape of a truncated cone. The fuel distributor piece 7, with a centering part 48 facing the holding shoulder 45 of the gas enclosing part 11, projects with a slight radial play into a centering section 50 of the longitudinal opening 9 of the gas enclosing part 11, so that the receiving opening 5 of the fuel distributor piece 7 and the fuel injection valve 1 arranged therein opposite the longitudinal opening 9 of the gas enclosing part 11 are centered.

In axialer Richtung ist zwischen dem Ventilende 3 des Brennstoffeinspritzventils 1 und dem Halteabsatz 45 des Gasumfassungsteils 11 in der Längsöffnung 9 ein Drallelement 55 angeordnet. Das Drallelement 55 weist konzentrisch zu der Ventillängsachse 4 eine durchgehende, sich in Strömungsrichtung zum Halteabsatz 45 hin kegelstumpfförmig erweiternde Mischöffnung 57 auf und ist in axialer Richtung dadurch verschiebbar, daß zwischen einer dem Drallelement 55 zugewandten Haltefläche 59 des Halteabsatzes 45 und einer dem Halteabsatz 45 zugewandten Stirnseite 61 des Drallelementes 55 eine Druckfeder 63, beispielsweise in Form einer Tellerfeder, angeordnet ist, die preiswert als Massenprodukt bezogen werden kann. Die Druckfeder 63 liegt mit einem äußeren Radialabschnitt 65 in axialer Richtung an der Haltefläche 59 des Halteabsatzes 45 und in radialer Richtung mit ihrem durch den äußeren Rand 66 des Radialabschnittes 65 gebildeten Umfang an einem Parallelabschnitt 67 der Längsöffnung 9 des Gasumfassungsteils 11 an. Ein in radialer Richtung nach innen gerichteter Schrägabschnitt 69 der Druckfeder 63 liegt mit seinem in axialer Richtung dem Brennstoffeinspritzventil 1 zugewandten Ende 70 an der Stirnseite 61 des Drallelementes 55 an. Die Druckfeder 63 ist in der montierten erfindungsgemäßen Vorrichtung in axialer Richtung elastisch verformt, d.h. also vorgespannt, so daß die Druckfeder 63 das in axialer Richtung verschiebbare Drallelement 55 mit seiner der Schutzkappe 33 zugewandten Stirnseite 64 gegen den Boden 35 der an dem Ventilende 3 des Brennstoffeinspritzventils 1 befestigten Schutzkappe 33 preßt. Die Druckfeder 63 ermöglicht auf diese Art und Weise den axialen Ausgleich der Lagetoleranzen von Brennstoffeinspritzventil 1 und Gasumfassungsteil 11 bzw. dessen Längsöffnung 9 zueinander. Es ist ausreichend, wenn die Druckfeder 63 nur eine relativ niedrige Federkonstante aufweist, so daß die Gefahr einer Beschädigung des beispielsweise als Kunststoffspritzteil ausgebildeten Drallelementes 55 vermieden wird.In the axial direction, a swirl element 55 is arranged in the longitudinal opening 9 between the valve end 3 of the fuel injection valve 1 and the holding shoulder 45 of the gas enclosing part 11. The swirl element 55 concentrically with the valve longitudinal axis 4 has a continuous mixing opening 57 which widens in the shape of a truncated cone in the direction of flow to the holding shoulder 45 and is displaceable in the axial direction in that between a holding surface 59 of the holding shoulder 45 facing the swirl element 55 and a holding surface 45 facing the holding shoulder 45 End face 61 of the swirl element 55, a compression spring 63, for example in the form of a plate spring, is arranged, which can be obtained inexpensively as a mass product. The compression spring 63 lies with an outer radial section 65 in the axial direction on the holding surface 59 of the holding shoulder 45 and in the radial direction with its circumference formed by the outer edge 66 of the radial section 65 against a parallel section 67 of the longitudinal opening 9 of the gas encasing part 11. An inclined section 69 of the compression spring 63, which is directed inward in the radial direction, rests with its end 70 facing the fuel injection valve 1 in the axial direction on the end face 61 of the swirl element 55. The compression spring 63 is elastically deformed in the assembled device according to the invention in the axial direction, that is to say preloaded, so that the compression spring 63 has the swirl element 55, which is displaceable in the axial direction, with its end face 64 facing the protective cap 33 against the bottom 35 of the fuel injector at the valve end 3 1 attached protective cap 33 presses. The compression spring 63 in this way enables the axial compensation of the position tolerances of the fuel injection valve 1 and the gas encasing part 11 or its longitudinal opening 9 with respect to one another. It is sufficient if the compression spring 63 has only a relatively low spring constant, so that the risk of damage to the swirl element 55, which is designed, for example, as a plastic injection-molded part, is avoided.

Das Drallelement 55 weist an seinem Umfang der Druckfeder 63 zugewandt einen ersten zylindrischen Abschnitt 72 auf, dessen Durchmesser gegenüber dem Durchmesser des das Drallelement 55 umgebenden Parallelabschnittes 67 der Längsöffnung 9 geringfügig kleiner ist, so daß zwischen dem ersten zylindrischen Abschnitt 72 des Drallelementes 55 und der Längsöffnung 9 des Gasumfassungsteils 11 ein enger radialer Spalt gebildet ist. Hierdurch und durch das Anliegen der Druckfeder 63 in axialer Richtung an der Stirnseite 61 des Drallelementes 55 und an der Haltefläche 59 des Halteabsatzes 45 sowie in radialer Richtung an dem Parallelabschnitt 67 der Längsöffnung 9 wird ein Vorbeiströmen des Gases an dem Umfang des Drallelementes 55 hin zu dem Abströmabschnitt 46 des Halteabsatzes 45 verhindert. An dem Umfang des ersten zylindrischen Abschnittes 72 des Drallelementes 55 ist eine Haltenase 74 angeformt, die sich in axialer Richtung beispielsweise über die gesamte axiale Länge des ersten zylindrischen Abschnittes 72 erstreckt. In der Wandung des Parallelabschnittes 67 der Längsbohrung 9 ist eine Ausnehmung 76 ausgeformt, die mit der Haltenase 74 des Drallelementes 55 derart zusammenwirkt, daß die Haltenase 74 in die Ausnehmung 76 der Längsbohrung 9 des Gasumfassungsteils 11 ragt und so das Drallelement 55 gegenüber der Längsbohrung 9 gegen Verdrehen gesichert ist. Dies gewährleistet eine definierte Lage des Gasaustritts, wie sie für die Verwendung von Mehrstrahleinspritzventilen z.B. für Vier-Ventil-Brennkraftmaschinen wichtig ist.The swirl element 55 has on its periphery facing the compression spring 63 a first cylindrical section 72, the diameter of which is slightly smaller than the diameter of the parallel section 67 surrounding the swirl element 55 of the longitudinal opening 9, so that between the first cylindrical section 72 of the swirl element 55 and the Longitudinal opening 9 of the gas enclosing part 11 is formed a narrow radial gap. As a result of this and due to the abutment of the compression spring 63 in the axial direction on the end face 61 of the swirl element 55 and on the holding surface 59 of the holding shoulder 45 and in the radial direction on the parallel section 67 of the longitudinal opening 9, the gas flows past the circumference of the swirl element 55 the outflow section 46 of the holding paragraph 45 prevented. A retaining lug 74 is formed on the circumference of the first cylindrical section 72 of the swirl element 55 and extends in the axial direction, for example over the entire axial length of the first cylindrical section 72. A recess 76 is formed in the wall of the parallel section 67 of the longitudinal bore 9, which cooperates with the retaining lug 74 of the swirl element 55 in such a way that the retaining lug 74 projects into the recess 76 of the longitudinal bore 9 of the gas encasing part 11 and thus the swirl element 55 with respect to the longitudinal bore 9 is secured against twisting. This ensures a defined position of the gas outlet, as used for the use of multi-jet injection valves e.g. is important for four-valve internal combustion engines.

An den ersten zylindrischen Abschnitt 72 schließt sich an seinem dem Ventilende 3 zugewandten Ende ein radial nach innen weisender, sich bis zu einem zweiten zylindrischen Abschnitt 77 erstreckender ebener Radialabschnitt 78 des Drallelementes 55 an. In axialer Richtung ist zwischen dem zweiten zylindrischen Abschnitt 77 und der an der Schutzkappe 33 anliegenden Stirnseite 64 des Drallelementes 55 ein sich in Richtung der Ventillängsachse 4 der Schutzkappe 33 verjüngender Strömungsabschnitt 80 ausgebildet. Der Strömungsabschnitt 80 ist an seinem Umfang beispielsweise konkav, also vom Ventilende 3 weg gewölbt ausgeformt. In der Wandung des Strömungsabschnittes 80 des Drallelementes 55 ist wenigstens ein Strömungskanal 82, in dem dargestellten Ausführungsbeispiel aber eine Mehrzahl von Strömungskanälen 82 ausgebildet, die die Form von sich beispielsweise bis in den zweiten zylindrischen Abschnitt 77 erstreckenden Nuten 83 haben und ausgehend von dem zweiten zylindrischen Abschnitt 77 bis zu der Stirnseite 64 des Drallelementes 55 schneckenförmig gekrümmt verlaufen und dort, wie in der einen Schnitt entlang der Linie II-II in Figur 1 zeigenden Figur 2 dargestellt, radial in die Mischöffnung 57 des Drallelementes 55 münden. Dabei sind die Strömungskanäle 82 so ausgebildet, daß sich die Strömungsquerschnitte in Richtung der Stirnseite 64 zu der Mischöffnung 57 des Drallelementes 55 hin kontinuierlich verjüngen. Die Strömungskanäle 82 werden seitlich durch Strömungsschaufeln 85 begrenzt, die zur Führung des in Richtung der Mischöffnung 57 strömenden Gases dienen. Das Gas wird aufgrund des sich verjüngenden Strömungsquerschnittes stark beschleunigt und erreicht beim Austritt aus den Strömungskanälen 82 seine maximale Geschwindigkeit. Die Strömungskanäle 82 bzw. die diese bildenden Nuten 83 weisen, wie in der Figur 1 gezeigt, an ihren Nutgründen 84 z.B. die gleiche axiale Erstreckung auf wie der zweite zylindrische Abschnitt 77 des Drallelementes 55. Die Nutgründe 84 verlaufen in Richtung der Stirnseite 64 des Drallelementes 55 ebenso konkav gekrümmt wie der Umfang des Strömungsabschnittes 80.The first cylindrical section 72 is adjoined at its end facing the valve end 3 by a radially inward-pointing, flat radial section 78 of the swirl element 55, which extends up to a second cylindrical section 77. A flow section 80 tapering in the direction of the valve longitudinal axis 4 of the protective cap 33 is formed in the axial direction between the second cylindrical section 77 and the end face 64 of the swirl element 55 abutting the protective cap 33. The flow section 80 is, for example, concave on its circumference, ie curved away from the valve end 3. At least one flow channel 82 is formed in the wall of the flow section 80 of the swirl element 55, but in the exemplary embodiment shown a plurality of flow channels 82 are formed, which have the shape of grooves 83, for example, extending into the second cylindrical section 77 and starting from the second cylindrical one Section 77 extends up to the end face 64 of the swirl element 55 in a helical curve and there, as shown in FIG. 2, which shows a section along the line II-II in FIG. 1, opens radially into the mixing opening 57 of the swirl element 55. The flow channels 82 are designed such that the flow cross-sections taper continuously in the direction of the end face 64 towards the mixing opening 57 of the swirl element 55. The flow channels 82 are laterally delimited by flow blades 85 which serve to guide the gas flowing in the direction of the mixing opening 57. The gas is strongly accelerated due to the tapering flow cross-section and reaches its maximum speed when exiting the flow channels 82. The flow channels 82 and the grooves 83 forming them, as shown in FIG. 1, have, for example, the same axial extent at their groove bases 84 as the second cylindrical section 77 of the swirl element 55. The groove bases 84 run in the direction of the end face 64 of the swirl element 55 curved just as concavely as the circumference of the flow section 80.

Die Menge des in die Mischöffnung 57 des Drallelementes 55 zugeführten Gases wird durch die Größe der Strömungsquerschnitte der Stromungskanäle 82 bestimmt. Die drallbehaftete, radiale Zufuhr des Gases mit hoher Geschwindigkeit in die Mischöffnung 57 zu dem aus den Abspritzöffnungen 31 abgegebenen Brennstoff führt zu der Bildung eines weitestgehend homogenen Brennstoff-Gas-Gemisches mit besonders feinen Brennstofftröpfchen. Hierdurch lassen sich im Betrieb der Brennkraftmaschine wesentliche Verbesserungen hinsichtlich der Abgasemission, des Beschleunigungsverhaltens sowie des Brennstoffverbrauchs erzielen.The amount of gas fed into the mixing opening 57 of the swirl element 55 is determined by the size of the flow cross sections of the flow channels 82. The swirling, radial supply of the gas at high speed into the mixing opening 57 to the fuel discharged from the spray openings 31 leads to the formation of a largely homogeneous fuel-gas mixture with particularly fine fuel droplets. This allows the Internal combustion engine to achieve significant improvements in terms of exhaust gas emission, acceleration behavior and fuel consumption.

Als Gas zur Bildung des Brennstoff-Gas-Gemisches kann sowohl Frischluft als auch ein Inertgas sowie eine Mischung aus beiden verwendet werden. Die Frischluft wird beispielsweise aus dem Ansaugrohr vor einem willkürlich verstellbaren Drosselorgan abgezweigt und dem Gaszufuhrkanal 13 zugeführt. Als Inertgas läßt sich z.B. das Abgas der Brennkraftmaschine verwenden, so daß durch diese Abgasrückführung die Schadstoffemission der Brennkraftmaschine reduziert wird. Das Gas kann aber auch mittels einer Zusatzpumpe gefördert werden.Both fresh air and an inert gas and a mixture of the two can be used as the gas for forming the fuel-gas mixture. The fresh air is branched off, for example, from the intake pipe in front of an arbitrarily adjustable throttle element and fed to the gas supply duct 13. As an inert gas, e.g. use the exhaust gas of the internal combustion engine so that the pollutant emission of the internal combustion engine is reduced by this exhaust gas recirculation. The gas can also be pumped using an additional pump.

Die erfindungsgemäße Vorrichtung hat außerdem den Vorteil, einen einfachen Aufbau und geringe Herstellkosten aufzuweisen. Eine aus Brennstoffverteilerstück 7, den Brennstoffeinspritzventilen 1, dem Gasumfassungsteil 11 mit den Drallelementen 55 und einem Druckregler für den Brennstoff bestehende Systemeinheit läßt sich auf einfache Art und Weise und dadurch kostengünstig an die Ansaugleitung einer Brennkraftmaschine montieren.The device according to the invention also has the advantage of having a simple structure and low manufacturing costs. A system unit consisting of a fuel distributor 7, the fuel injection valves 1, the gas containment part 11 with the swirl elements 55 and a pressure regulator for the fuel can be easily and inexpensively mounted on the intake line of an internal combustion engine.

Claims (11)

Vorrichtung zur Einspritzung eines Brennstoff-Gas-Gemisches mit einem Brennstoffeinspritzventil, das an einem Ventilende wenigstens eine Abspritzöffnung aufweist, mit einem Gasumfassungsteil, das konzentrisch zu einer Ventillängsachse verlaufend eine abgestufte Längsöffnung hat, in die das Brennstoffeinspritzventil mit seinem Ventilende ragt, und mit einem Gaszufuhrkanal, der mit der Längsöffnung des Gasumfassungsteils in Verbindung steht, dadurch gekennzeichnet, daß stromabwärts des Ventilendes (3) des Brennstoffeinspritzventils (1) in der Längsöffnung (9) des Gasumfassungsteils (11) ein Drallelement (55) angeordnet ist, das eine konzentrisch zu der Ventillängsachse (4) verlaufende Mischöffnung (57) hat und in dem zum Umfang hin offen in radialer Richtung wenigstens ein gekrümmter nutförmiger Strömungskanal (82) ausgebildet ist, der mit dem Gaszufuhrkanal (13) verbunden ist und in die Mischöffnung (57) des Drallelementes (55) mündet.Device for injecting a fuel-gas mixture with a fuel injection valve, which has at least one spray opening at one valve end, with a gas encasing part, which has a stepped longitudinal opening that extends concentrically to a longitudinal valve axis, into which the fuel injection valve projects with its valve end, and with a gas supply channel , which is connected to the longitudinal opening of the gas encasing part, characterized in that downstream of the valve end (3) of the fuel injection valve (1) in the longitudinal opening (9) of the gas encasing part (11) a swirl element (55) is arranged, which is concentric to the Has valve longitudinal axis (4) extending mixing opening (57) and in the open to the circumference in the radial direction at least one curved groove-shaped flow channel (82) is formed, which is connected to the gas supply channel (13) and into the mixing opening (57) of the swirl element ( 55) ends. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der wenigstens eine Strömungskanal (82) des Drallelementes (55) radial nach innen schneckenförmig gekrümmt verlauft und sich seine Strömungsquerschnittsfläche in Richtung zu der Mischöffnung (57) hin kontinuierlich verjüngt.Apparatus according to claim 1, characterized in that the at least one flow channel (82) of the swirl element (55) is curved in a helical manner radially inwards and its flow cross-sectional area tapers continuously in the direction of the mixing opening (57). Vorrichtung nach Anspruch 1 oder 2, dadurch gekennzeichnet, daß der wenigstens eine Strömungskanal (82) radial in die Mischöffnung (57) des Drallelementes (55) mündet.Apparatus according to claim 1 or 2, characterized in that the at least one flow channel (82) opens radially into the mixing opening (57) of the swirl element (55). Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß der Gaszufuhrkanal (13) tangential mit der Längsöffnung (9) des Gasumfassungsteils (11) in Verbindung steht.Device according to one of the preceding claims, characterized in that the gas supply channel (13) is tangentially connected to the longitudinal opening (9) of the gas enclosing part (11). Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, daß zwischen einem stromabwärtigen Halteabsatz (45) der Längsöffnung (9) des Gasumfassungsteils (11) und einer dem Ventilende (3) des Brennstoffeinspritzventils (1) abgewandten Stirnseite (61) des Drallelementes (55) eine Druckfeder (63) angeordnet ist.Device according to one of the preceding claims, characterized in that between a downstream holding shoulder (45) of the longitudinal opening (9) of the gas enclosing part (11) and an end face (61) of the swirl element (55) facing away from the valve end (3) of the fuel injection valve (1). a compression spring (63) is arranged. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, daß die Druckfeder (63) tellerfederförmig ausgebildet ist.Apparatus according to claim 5, characterized in that the compression spring (63) is in the form of a plate spring. Vorrichtung nach einem der vorhergehenden Ansprüche dadurch gekennzeichnet, daß das Drallelement (55) gegenüber der Längsöffnung (9) des Gasumfassungsteils (11) gegen Verdrehen gesichert ist.Device according to one of the preceding claims, characterized in that the swirl element (55) is secured against rotation with respect to the longitudinal opening (9) of the gas enclosing part (11). Vorrichtung nach Anspruch 7, dadurch gekennzeichnet, daß an dem Umfang des Drallelementes (55) eine Haltenase (74) ausgebildet ist, die mit einer in der Wandung der Längsöffnung (9) des Gasumfassungsteils (11) ausgeformten Ausnehmung (76) zusammenwirkt.Apparatus according to claim 7, characterized in that a retaining lug (74) is formed on the circumference of the swirl element (55) and cooperates with a recess (76) formed in the wall of the longitudinal opening (9) of the gas encasing part (11). Vorrichtung nach einem der vorhergehenden Ansprüche dadurch gekennzeichnet, daß in dem Gasumfassungsteil (11) mehrere abgestufte, jeweils ein Drallelement (55) aufweisende Längsöffnungen (9) ausgebildet und mit einem gemeinsamen Gaszufuhrkanal (13) verbunden sind.Device according to one of the preceding claims, characterized in that a plurality of stepped longitudinal openings (9), each having a swirl element (55), are formed in the gas enclosing part (11) and are connected to a common gas supply channel (13). Vorrichtung nach Anspruch 9, dadurch gekennzeichnet, daß das Gasumfassungsteil (11) mit einem Brennstoffverteilerstück (7) verbindbar ist, das eine der Zahl der Längsöffnungen (9) des Gasumfassungsteils (11) entsprechende und konzentrisch zu diesen angeordnete Anzahl von Brennstoffeinspritzventilen (1) aufnimmt und der Zufuhr von Brennstoff dient.Apparatus according to claim 9, characterized in that the gas containment part (11) can be connected to a fuel distributor piece (7) which receives a number of fuel injection valves (1) corresponding to the number of longitudinal openings (9) of the gas containment part (11) and arranged concentrically to them and serves to supply fuel. Vorrichtung nach einem der Ansprüche 9 oder 10, dadurch gekennzeichnet, daß ein aus dem Brennstoffverteilerstück (7), den Brennstoffeinspritzventilen (1), dem Gasumfassungsteil (11) mit den darin angeordneten Drallelementen (55) sowie einem Druckregler bestehendes Brennstoff-Gas-Einspritzsystem als gemeinsame Einheit an die Ansaugleitung der Brennkraftmaschine montierbar ist.Device according to one of claims 9 or 10, characterized in that a fuel-gas injection system consisting of the fuel distributor piece (7), the fuel injection valves (1), the gas containment part (11) with the swirl elements (55) arranged therein, and a pressure regulator common unit can be mounted on the intake pipe of the internal combustion engine.
EP91117093A 1990-11-07 1991-10-08 Injection device for a fuel-gas mixture Expired - Lifetime EP0484681B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4035312 1990-11-07
DE4035312A DE4035312A1 (en) 1990-11-07 1990-11-07 DEVICE FOR INJECTING A FUEL-GAS MIXTURE

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EP0484681A1 true EP0484681A1 (en) 1992-05-13
EP0484681B1 EP0484681B1 (en) 1994-03-02

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EP91117093A Expired - Lifetime EP0484681B1 (en) 1990-11-07 1991-10-08 Injection device for a fuel-gas mixture

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EP (1) EP0484681B1 (en)
JP (1) JPH04265468A (en)
DE (2) DE4035312A1 (en)

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WO1993017237A1 (en) * 1992-02-25 1993-09-02 Robert Bosch Gmbh Gas distributor for fuel injection systems
EP0681104A1 (en) * 1994-05-06 1995-11-08 Robert Bosch Gmbh Fuel injection valve
WO1996012886A1 (en) * 1994-10-19 1996-05-02 Dejoux, André Device for injecting a fuel gas mixture into a combustion engine
WO1997001706A3 (en) * 1995-06-27 1997-02-27 Siemens Automotive Corp Lp Air assist fuel injector
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WO1993009344A1 (en) * 1991-11-01 1993-05-13 Siemens Automotive L.P. Air assist atomizer for fuel injector
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EP0681104A1 (en) * 1994-05-06 1995-11-08 Robert Bosch Gmbh Fuel injection valve
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US20120241032A1 (en) * 2011-03-25 2012-09-27 Tokyo Electron Limited Lid opening and closing device
US9082807B2 (en) * 2011-03-25 2015-07-14 Tokyo Electron Limited Lid opening and closing device

Also Published As

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US5232163A (en) 1993-08-03
JPH04265468A (en) 1992-09-21
EP0484681B1 (en) 1994-03-02
DE59101093D1 (en) 1994-04-07
DE4035312A1 (en) 1992-05-14

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