EP0770176A1 - Fuel injection valve for internal combustion engines - Google Patents

Fuel injection valve for internal combustion engines

Info

Publication number
EP0770176A1
EP0770176A1 EP95937760A EP95937760A EP0770176A1 EP 0770176 A1 EP0770176 A1 EP 0770176A1 EP 95937760 A EP95937760 A EP 95937760A EP 95937760 A EP95937760 A EP 95937760A EP 0770176 A1 EP0770176 A1 EP 0770176A1
Authority
EP
European Patent Office
Prior art keywords
valve
fuel injection
membrane
combustion chamber
injection
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.)
Ceased
Application number
EP95937760A
Other languages
German (de)
French (fr)
Inventor
Karl Hofmann
Detlev Potz
Günter LEWENTZ
Uwe Gordon
Stefan Haug
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 EP0770176A1 publication Critical patent/EP0770176A1/en
Ceased legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M61/00—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00
    • F02M61/04—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series
    • F02M61/047—Fuel-injectors not provided for in groups F02M39/00 - F02M57/00 or F02M67/00 having valves, e.g. having a plurality of valves in series the valves being formed by deformable nozzle parts, e.g. flexible plates or discs with fuel discharge 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
    • 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

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • a fuel injection valve for internal combustion engines according to the preamble of claim 1.
  • the end face of a valve body on the combustion chamber side defines an annular pressure chamber into which an inlet line from the fuel injection pump opens.
  • the pressure chamber is delimited radially inwards by a pin projecting axially from the end face of the valve body, the cross section of which tapers conically at the end on the combustion chamber side to form a valve seat.
  • the pressure chamber is delimited by a disk-shaped valve membrane which is fastened to the valve body at its outer edge region with the interposition of a sleeve by means of a clamping nut and which has a central opening, the annular edge of which forms a sealing edge which interacts with the valve seat.
  • the valve membrane lies with its sealing surface in the closed state of the fuel injection valve under prestress against the valve seat, so that the pressure chamber is closed in the direction of the combustion chamber of the internal combustion engine to be supplied. If an injection is to take place, the pressure chamber acted upon by the supply line with high fuel pressure, which lifts the resilient valve membrane against the biasing force with its sealing surface from the valve seat.
  • the fuel injection takes place via the ring gap on the pin which is controlled in a manner analogous to known throttle pin nozzles.
  • the end of the injection process is controlled by stopping the high pressure supply in the pressure chamber.
  • the known fuel injection valve has the disadvantage that it is not suitable for use on direct-injection internal combustion engines, since only a single injection jet directed axially to the pin can be achieved with it.
  • the fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage that the diaphragm nozzles, which are simple in terms of their construction, can now also be used for fuel injection devices for direct-injection internal combustion engines. This is advantageously made possible by the free choice of the arrangement of the injection openings downstream of the sealing seat, it now being possible to provide a large number of injection openings which are oriented in such a way that the injection jets are at a certain angle to the axis of the shaft of the injection valve, so that optimal fuel preparation is possible even in direct injection internal combustion engines.
  • valve seat can also be provided on a ball fastened to the end face of the valve body, which once again reduces the manufacturing outlay for the injection valve.
  • the injection openings downstream of the sealing surface can be introduced directly into a spherical shape of the preferably disc-shaped valve membrane or are provided in a separate insert which also carries the sealing surface and is then inserted into the valve membrane.
  • This two-piece construction of the valve membrane has the advantage that different materials can be used, so that a material with good spring properties can be used for the membrane and a material with good properties with regard to strength and durability can be used for the membrane insert.
  • Another advantage is achieved by the protrusion of the pin and the valve membrane into the combustion chamber, since the injection openings can be guided into a central area of the combustion chamber in this way.
  • valve diaphragm is advantageously fastened to the valve body by means of a clamping nut, an adjusting disk or ring being arranged between the valve diaphragm and the valve body in order to adjust the opening pressure of the injection valve. It is particularly advantageous to make the setting, for example, by means of a nut that is accessible from the outside, since in this way the opening pressure of the injection valve can still be made from the outside even after assembly.
  • valve membrane If a later adjustment is not necessary, it is alternatively possible to weld the valve membrane to a ring connected to the valve body.
  • a cap-shaped clamping nut By gripping the end face of the valve membrane on the combustion chamber side by means of a cap-shaped clamping nut, it is also advantageously possible to limit the opening stroke movement of the valve membrane, in order to ensure a defined flow cross section between the valve seat and the sealing surface.
  • Another advantage is achieved by fixing the rotational position of the movable valve member (valve membrane) towards the pin, so that no tension affecting the tightness can occur when there is frictional engagement between the clamping nut and the valve membrane.
  • FIG. 1 shows a longitudinal section through a first exemplary embodiment of the fuel injection valve according to the invention
  • FIG. 2 shows an enlarged view of the valve membrane and the valve seat formed by a pin
  • FIG. 3 shows a second exemplary embodiment in which the valve seat is formed by a ball
  • FIG. 4 is a third exemplary embodiment, in which an insert in the form of a truncated cone that receives the sealing surface and injection openings is inserted into the valve membrane
  • FIGS. 5 and 5A show a fourth exemplary embodiment in which the membrane insert is designed as a spherical segment, FIGS.
  • FIGS. 6 and 6A show a fifth exemplary embodiment in which the membrane insert is designed as a sphere, the spherical surface of which forms a valve sealing surface with which it connects with an outer surface 7 and 7A, a sixth embodiment with a valve seat formed on a ball and a conical membrane insert interacting with it, FIGS. 8 and 8A, a seventh embodiment with a ball valve seat and a ball or. spherical shape of the otherwise disk-shaped valve membrane, FIGS. 9 and 10 show an eighth and ninth exemplary embodiment in which the clamping nut engages around the valve membrane in a cap-shaped manner, FIG.
  • FIG. 11 shows a tenth exemplary embodiment in which the pin supporting the valve seat and the membrane extend axially the valve body protrude into the combustion chamber of the internal combustion engine and
  • FIG. 12 shows an eleventh embodiment in which the valve membrane and sleeve are formed in one piece.
  • a rotationally symmetrical valve body 1 shown in FIG. 1 has at one end a connection 3 for an inlet line, not shown, from a fuel injection pump, from which an inlet channel 5, which extends longitudinally through the valve body 1, leads away from one of the combustion chambers the end face 7 of the valve body 1 facing the internal combustion engine opens.
  • This end face 7 borders on a space 9 which, in the first exemplary embodiment shown enlarged in FIG. 2, is delimited radially inwards by a central pin 11 projecting axially from the end face 7 and radially outward by a sleeve 13 .
  • the frustoconical forms Pin 11 with a part of its conical surface has a valve seat 15 against which a valve membrane 17, which delimits the chamber 9 on the combustion chamber side and is preferably made of resilient steel and is curved in the direction of the chamber 9, comes under pressure with a sealing surface 19.
  • the disc-shaped valve membrane 17, which forms a movable valve member has a frusto-conical shape 21 (depression) at the level of the pin 11, the end of which is formed spherical, the end of the combustion chamber on the combustion chamber side, the inner flanks of the shape 21 having the valve seat 15 form cooperating valve sealing surface 19.
  • a blind-hole-shaped space 23 is formed, which is connected downstream of the sealing cross section formed between the valve seat 15 and the sealing surface 19 in the injection direction and downstream of which at least one, upstream preferably discharge a plurality of injection openings 25 into the combustion chamber of the internal combustion engine.
  • valve membrane 17 On its outer edge, the valve membrane 17 is tightly clamped against the valve body 1 by means of a clamping nut 27 with the sleeve 13 interposed, for which purpose the clamping nut 27 has a collar 29 covering the outer edge of the valve membrane 17.
  • the outside diameter of the valve membrane 17 is made smaller than the inside diameter of the clamping nut 27, so that the valve membrane 17 optimally fits to the pin during assembly 11 can center.
  • the fuel injection valve according to the invention is injected by filling the space 9 with fuel under high pressure from the injection pump via the inlet channel 5.
  • the valve membrane 17 with its sealing surface 19 becomes counter to it
  • Preload force is lifted from the valve seat 15, so that the fuel reaches the blind-hole-shaped space 23 along the now open sealing cross-section and further via the injection openings 25 into the combustion chamber of the internal combustion engine to be supplied.
  • the injection is terminated by interrupting the high-pressure fuel supply in the space 9, as a result of which the pressure in the space 9 drops again under the force of the prestressing of the valve membrane 17, so that the valve sealing surface 19 springs back onto the valve seat 15 in a sealing manner.
  • valve seat 15 is constructed analogously to the first exemplary embodiment shown in FIGS. 1 and 2.
  • the valve seat 15 is formed there by a preferably welded ball 31 fastened in the middle of the end face 7 of the valve body 1, the surface of which forms the valve seat 15, which cooperates with the valve sealing face 19 of the valve membrane 17.
  • FIG. 4 shows a third exemplary embodiment in which the valve membrane 17 is constructed in two parts. Sealing surface 19 and injection openings 25 are arranged on a membrane insert 33, the shape of which corresponds to the shape 21 of FIG. 2 and which is inserted into a provided receiving bore 35 of valve membrane 17 and fastened in a sealing manner.
  • FIG. 5 and in an enlarged section 5A show a fourth embodiment of the fuel injection valve, in which the membrane insert 33 is formed as a hollow ball 37, on the side facing the space 9 an opening is provided, the walls of which are the valve sealing surface Form 19 and into which the pin 11 projects with its valve seat 15.
  • the valve seat 15 is formed by the opening of the inlet channel 5 in the end face 7 of the valve body 1.
  • the valve sealing surface 19 cooperating with this valve seat 15 is formed on a solid ball 39 which is connected to the valve membrane 17 and which is penetrated by intersecting bores 41 which form the injection openings 25 and which, starting from the space 9, enter the combustion chamber of the internal combustion engine flow out.
  • the space 9 which is permanently connected to the combustion chamber, takes over the function of the pocket-shaped space 23 during the operation of the fuel injection valve, the previous figures and the pressure in the inlet channel 5 flows directly against the valve sealing surface 19 of the valve membrane 17
  • the sleeve 13 is also inserted into this dead volume between the valve membrane 17 and the valve body 1, which is designed such that it controls the opening and closing movement of the valve membrane 17 not affected.
  • the sixth exemplary embodiment shown in FIGS. 7 and 7A is a combination of the valve seat 15 formed on the ball 31 and a valve sealing surface 19 according to FIGS. 3 and 7 arranged on the membrane insert 33.
  • the seventh exemplary embodiment shown in FIG. 8 and enlarged in FIG. 8A differs from the second exemplary embodiment shown in FIG. 3 only in the shape of the shape 21 on the valve membrane 17, which is now designed in the shape of a spherical cap, the intermediate spherical bottom and Valve seat ball 31 formed blind hole-shaped space 23, from which the injection openings 25 lead, is limited to reduce the volume of damage.
  • valve membrane 17 is approximately bell-shaped with an Sets formed
  • the clamping nut 27 presses the valve membrane 17 via an annular shoulder 43 directly against the end face 7 of the valve body 1.
  • the collar 29 of the clamping nut 27 projects radially inwards so far that it reaches the valve membrane 17 except for a small, adjustable gap dimension s, the size of the gap dimension s thus determining the maximum opening stroke of the valve membrane 17
  • the ninth exemplary embodiment shown differs from the eighth exemplary embodiment only in that an adjusting ring 45 is clamped between the end face 7 of the valve body 1 and the valve diaphragm 17, the strength or deformation of which adjusts the axial position of the valve diaphragm 17 to the valve body 1 and thus can set the biasing force of the system of valve sealing surface 19 on the valve seat 15 or the opening pressure of the fuel injector.
  • valve membrane 17 protrude from the overlap with the clamping nut 27 into the interior of the combustion chamber of the internal combustion engine, the valve membrane 17 during the pressurization of the space 9 in addition to an expansion the opening cross-section between valve seat 15 and valve sealing surface 19 also opens in the axial direction to valve body 1 by means of radial breathing.
  • valve membrane 17, which is otherwise designed analogously to FIG. 1, is made in one piece with the sleeve 13 from FIG.
  • there is no sealing joint which leads to less machining effort and, at the same time, a reduction in the risk of leaks.
  • a further advantage is the transition area that continuously merges into the sleeve, through which the stresses at the clamping point of the valve membrane can be reduced. It is thus possible with the fuel injection valve according to the invention to combine the advantages of a perforated nozzle with the advantages of a diaphragm nozzle in a structurally simple manner and thus to ensure high functional reliability when using fewer components.

Landscapes

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

Abstract

A fuel injection valve for internal combustion engines with a valve body (1), at the combustion chamber end of which there is a chamber (9) connected to an inlet channel (5) bounded radially inwards by a spigot (11) projecting axially from the face (7) of the valve body (1) on the combustion chamber side and bearing a valve seat (15), and with a spring-loaded valve diaphragm (17) bounding the chamber (9) to the combustion chamber of the internal combustion engine to be fuelled and tensioned on the valve body (1) in its outer edge region, on which there is a valve sealing surface (19) tensioned against the valve seat (15), whereby the valve diaphragm (17) has injection apertures (25) arranged in the fuel injection flow direction behind the sealing surface (19) in the valve diaphragm (17).

Description

Kraftstoffeinspritzventil für BrennkraftmaschinenFuel injection valve for internal combustion engines
Stand der TechnikState of the art
Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einem derartigen aus dem DE-Gbm G 93 20 433.7 be¬ kannten Kraftstoffeinspritzventil begrenzt die brennraumsei- tige Stirnfläche eines Ventilkörpers einen ringförmigen Druckraum, in den eine Zulaufleitung von der Kraftstoffein¬ spritzpumpe münde . Der Druckraum ist radial einwärts von einem axial von der Stirnfläche des Ventilkörpers vorstehen¬ den Zapfen begrenzt, dessen Querschnitt sich am brennraum¬ seitigen Ende unter Bildung eines Ventilsitzes konisch ver¬ jüngt. An seinem brennraumseitigen Ende wird der Druckraum von einer scheibenförmigen Ventilmembran begrenzt, die an ihrem Außenrandbereich unter Zwischenschaltung einer Hülse mittels einer Spannmutter am Ventilkörper befestigt ist und die eine zentrale Öffnung aufweist, deren Ringkante eine mit dem Ventilsitz zusammenwirkende Dichtkante bildet. Dabei liegt die Ventilmembran mit ihrer Dichtfläche im geschlosse¬ nen Zustand des Kraftstoffeinspritzventils unter Vorspannung dichtend am Ventilsitz an, so daß der Druckraum in Richtung Brennraum der zu versorgenden Brennkraftmaschine verschlos¬ sen ist. Soll eine Einspritzung erfolgen, wird der Druckraum über die Zulaufleitung mit hohem Kraftstoffdruck beauf¬ schlagt, der dabei die federnde Ventilmembran entgegen der Vorspannkraft mit ihrer Dichtfläche vom Ventilsitz abhebt. Über den dabei aufgesteuerten Ringspalt am Zapfen erfolgt in Folge die Kraftstoffeinspritzung analog zu bekannten Dros¬ selzapfendüsen. Das Ende des Einspritzvorganges wird durch das Beenden der Hochdruckzufuhr in den Druckraum gesteuert . Dabei weist das bekannte Kraftstoffeinspritzventil jedoch den Nachteil auf, daß es zur Verwendung an direkt einsprit¬ zenden Brennkraftmaschinen nicht geeignet ist, da sich mit diesem nur ein einziger, axial zum Zapfen gerichteter Ein¬ spritzstrahl erreichen läßt.The invention is based on a fuel injection valve for internal combustion engines according to the preamble of claim 1. In such a fuel injection valve known from DE-Gbm G 93 20 433.7, the end face of a valve body on the combustion chamber side defines an annular pressure chamber into which an inlet line from the fuel injection pump opens. The pressure chamber is delimited radially inwards by a pin projecting axially from the end face of the valve body, the cross section of which tapers conically at the end on the combustion chamber side to form a valve seat. At its end on the combustion chamber side, the pressure chamber is delimited by a disk-shaped valve membrane which is fastened to the valve body at its outer edge region with the interposition of a sleeve by means of a clamping nut and which has a central opening, the annular edge of which forms a sealing edge which interacts with the valve seat. In this case, the valve membrane lies with its sealing surface in the closed state of the fuel injection valve under prestress against the valve seat, so that the pressure chamber is closed in the direction of the combustion chamber of the internal combustion engine to be supplied. If an injection is to take place, the pressure chamber acted upon by the supply line with high fuel pressure, which lifts the resilient valve membrane against the biasing force with its sealing surface from the valve seat. As a result, the fuel injection takes place via the ring gap on the pin which is controlled in a manner analogous to known throttle pin nozzles. The end of the injection process is controlled by stopping the high pressure supply in the pressure chamber. However, the known fuel injection valve has the disadvantage that it is not suitable for use on direct-injection internal combustion engines, since only a single injection jet directed axially to the pin can be achieved with it.
Vorteile der ErfindungAdvantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil für Brenn¬ kraftmaschinen mit den kennzeichnenden Merkmalen des Patent¬ anspruchs 1 hat demgegenüber den Vorteil, daß nunmehr die hinsichtlich ihres Aufbaus einfachen Membrandüsen auch für Kraftstoffeinspritzeinrichtungen für direkt einspritzende Brennkraf maschinen verwendet werden können. Dies wird dabei in vorteilhafter Weise durch die freie Wahl der Anordnung der, dem Dichtsitz nachgeschalteten Einspritz¬ öffnungen möglich, wobei nunmehr eine Vielzahl von Ein- spritzδffnungen vorgesehen werden kann, die so ausgerichtet sind, daß die Einspritzstrahlen in einem bestimmten Winkel zur Achse des Schafts des Einspritzventils verlaufen, so daß auch in direkt einspritzenden Brennkraftmaschinen eine opti¬ male Kraf stoffaufbereitung möglich ist.The fuel injection valve according to the invention for internal combustion engines with the characterizing features of claim 1 has the advantage that the diaphragm nozzles, which are simple in terms of their construction, can now also be used for fuel injection devices for direct-injection internal combustion engines. This is advantageously made possible by the free choice of the arrangement of the injection openings downstream of the sealing seat, it now being possible to provide a large number of injection openings which are oriented in such a way that the injection jets are at a certain angle to the axis of the shaft of the injection valve, so that optimal fuel preparation is possible even in direct injection internal combustion engines.
Der Ventilsitz kann dabei neben der Anordnung an einem axial vorstehenden Zapfen auch an einer an der Stirnfläche des Ventilkörpers befestigten Kugel vorgesehen werden, was den Fertigungsaufwand des Einspritzventils noch einmal verrin¬ gert. Die der Dichtfläche stromabwärts nachgeschalteten Einspritz- Öffnungen können dabei direkt in eine kugelförmige Ausfor¬ mung der vorzugsweise scheibenförmigen Ventilmembran einge¬ bracht werden oder sind in einem separaten, auch die Dicht- fläche tragenden Einsatz vorgesehen, der dann in die Ventil- membran eingesetzt wird. Diese Zweistückigkeit der Ventil- membran hat den Vorteil, daß verschiedene Werkstoffe verwen¬ det werden können, so daß für die Membran ein Werkstoff mit guten Federeigenschaften und den Membran-Einsatz ein Werk¬ stoff mit guten Eigenschaften hinsichtlich Festigkeit und Haltbarkeit verwendet werden kann. Zudem ermöglicht die Ver¬ wendung eines separaten, die Dichtfläche und die Einspritz¬ öffnungen aufnehmenden Teils, ein Baukasten-System, bei dem unter Verwendung eines Universal Ventilkörpers und einer ge¬ normten Ventilmembran die Anpassung an die jeweilige Brenn¬ kraftmaschine lediglich durch den Austausch des Membran-Ein¬ satzes erfolgen kann.In addition to being arranged on an axially projecting pin, the valve seat can also be provided on a ball fastened to the end face of the valve body, which once again reduces the manufacturing outlay for the injection valve. The injection openings downstream of the sealing surface can be introduced directly into a spherical shape of the preferably disc-shaped valve membrane or are provided in a separate insert which also carries the sealing surface and is then inserted into the valve membrane. This two-piece construction of the valve membrane has the advantage that different materials can be used, so that a material with good spring properties can be used for the membrane and a material with good properties with regard to strength and durability can be used for the membrane insert. In addition, the use of a separate part, which receives the sealing surface and the injection openings, enables a modular system in which, using a universal valve body and a standardized valve membrane, the adaptation to the respective internal combustion engine is only possible by replacing the Membrane insert can take place.
Alternativ ist es zudem möglich, die komplette Sitz- und Spritzloch-Geometrie mittels eines serienmäßig zu beziehen¬ den Kugeleinsatzes (z.B. Kugellagerkugel) in die Ventilmem¬ bran zu integrieren, der dann mit einem konstruktiv sehr einfachen, durch die Austrittsöffnung des Zulaufkanals in der Stirnfläche des Ventilkörpers gebildeten Ventilsitz zu¬ sammenwirkt.Alternatively, it is also possible to integrate the complete seat and spray hole geometry into the valve membrane by means of a ball insert (eg ball bearing ball), which can be obtained as standard, and which then has a very simple design through the outlet opening of the inlet channel in the end face of the valve body formed cooperates.
Ein weiterer Vorteil wird durch das Hineinragen von Zapfen und Ventilmembran in den Brennraum erreicht, da die Ein- spritzöffnungen auf diese Weise in einen zentralen Bereich des Brennraumes geführt werden können.Another advantage is achieved by the protrusion of the pin and the valve membrane into the combustion chamber, since the injection openings can be guided into a central area of the combustion chamber in this way.
Die Befestigung der Ventilmembran am Ventilkörper erfolgt vorteilhafterweise mittels einer Spannmutter, wobei zum Ein¬ stellen des Öffnungsdruckes des Einspritzventils eine Ein¬ stellscheibe bzw. -ring zwischen der Ventilmembran und dem Ventilkörper angeordnet ist. Besonders vorteilhaft ist es dabei, die Einstellung z.B. mittels einer von außen zugäng¬ lichen Mutter vorzunehmen, da auf diese Weise der Öffnungs- druck des Einspritzventils auch nach der Montage noch von außen vorgenommen werden kann.The valve diaphragm is advantageously fastened to the valve body by means of a clamping nut, an adjusting disk or ring being arranged between the valve diaphragm and the valve body in order to adjust the opening pressure of the injection valve. It is particularly advantageous to make the setting, for example, by means of a nut that is accessible from the outside, since in this way the opening pressure of the injection valve can still be made from the outside even after assembly.
Kann auf eine evtl. spätere Einstellung verzichtet werden, ist es alternativ auch möglich, die Ventilmembran an einem mit dem Ventilkörpers verbundenen Ring zu verschweißen. Durch ein Umgreifen der brennraumseitigen Stirnfläche der Ventilmembran durch eine kappenförmige Spannmutter ist es zudem in vorteilhafter Weise möglich, die Öffnungshubbewe¬ gung der Ventilmembran zu begrenzen, um so einen definierten Durchflußquerschnitt zwischen Ventilsitz und Dichtfläche zu gewährleisten.If a later adjustment is not necessary, it is alternatively possible to weld the valve membrane to a ring connected to the valve body. By gripping the end face of the valve membrane on the combustion chamber side by means of a cap-shaped clamping nut, it is also advantageously possible to limit the opening stroke movement of the valve membrane, in order to ensure a defined flow cross section between the valve seat and the sealing surface.
Ein weiterer Vorteil wird durch die Fixierung der Drehlage des beweglichen Ventilgliedes (Ventilmembran) zum Zapfen hin erreicht, wodurch bei Reibschluß zwischen der Spannmutter und der Ventilmembran keine die Dichtheit beeinflussende Verspannung auftreten kann.Another advantage is achieved by fixing the rotational position of the movable valve member (valve membrane) towards the pin, so that no tension affecting the tightness can occur when there is frictional engagement between the clamping nut and the valve membrane.
Weitere Vorteile und vorteilhafte Ausgestaltungen des Gegen¬ standes der Erfindung sind der Beschreibung, der Zeichnung und den Patentansprüchen entnehmbar.Further advantages and advantageous configurations of the subject of the invention can be gathered from the description, the drawing and the patent claims.
Zeichnungdrawing
Elf Ausführungsbeispiele des erfindungsgemäßen Kraftstoff¬ einspritzventils für Brennkraftmaschinen sind in der Zeich¬ nung dargestellt und werden in der nachfolgenden Beschrei¬ bung näher erläutert.Eleven exemplary embodiments of the fuel injection valve for internal combustion engines according to the invention are shown in the drawing and are explained in more detail in the following description.
Es zeigen die Figur 1 einen Längsschnitt durch ein erstes Ausführungsbeispiel des erfindungsgemäßen Kraftstoffein¬ spritzventils, die Figur 2 eine vergrößerte Darstellung der Ventilmembran und des durch einen Zapfen gebildeten Ventil¬ sitzes, die Figur 3 ein zweites Ausführungsbeispiel, bei dem der Ventilsitz durch eine Kugel gebildet ist, die Figur 4 ein drittes Ausführungsbeispie1, bei dem ein, die Dichtflä¬ che und Einspritzöffnungen aufnehmender Einsatz in Form ei¬ nes Kegelstumpfes in die Ventilmembran eingesetzt ist, die Figuren 5 und 5A ein viertes Ausführungsbeispiel, bei dem der Membraneinsatz als Kugelsegment ausgebildet ist, die Fi¬ guren 6 und 6A ein fünftes Ausführungsbeispiel, bei dem der Membraneinsatz als Kugel ausgebildet ist, deren Kugelfläche eine Ventildichtfläche bildet, mit der sie mit einer Aus¬ trittsöffnung eines Zulaufkanals in den Raum zusammenwirkt, die Figuren 7 und 7A ein sechstes Ausführungsbeispiel mit einem an einer Kugel gebildeten Ventilsitz und einem mit diesem zusammenwirkenden kegelförmigen Membraneinsatz, die Figuren 8 und 8A ein siebtes Ausführungsbeispiel mit einem Kugel-Ventilsitz und einer kugel-bzw. kalottenförmigen Aus- formung der ansonsten scheibenförmigen Ventilmembran, die Figuren 9 und 10 ein achtes und neuntes Ausführungsbeispiel, bei denen die Spannmutter die Ventilmembran kappenförmig um¬ greift, die Figur 11 ein zehntes Ausführungsbeispiel, bei dem der den Ventilsitz tragende Zapfen und die Membran axial aus dem Ventilkörper vorstehend in den Brennraum der Brenn¬ kraftmaschine ragen und die Figur 12 ein elftes Ausführungs- beispiel, bei dem Ventilmembran und Hülse einstückig ausge¬ bildet sind.FIG. 1 shows a longitudinal section through a first exemplary embodiment of the fuel injection valve according to the invention, FIG. 2 shows an enlarged view of the valve membrane and the valve seat formed by a pin, and FIG. 3 shows a second exemplary embodiment in which the valve seat is formed by a ball FIG. 4 is a third exemplary embodiment, in which an insert in the form of a truncated cone that receives the sealing surface and injection openings is inserted into the valve membrane FIGS. 5 and 5A show a fourth exemplary embodiment in which the membrane insert is designed as a spherical segment, FIGS. 6 and 6A show a fifth exemplary embodiment in which the membrane insert is designed as a sphere, the spherical surface of which forms a valve sealing surface with which it connects with an outer surface 7 and 7A, a sixth embodiment with a valve seat formed on a ball and a conical membrane insert interacting with it, FIGS. 8 and 8A, a seventh embodiment with a ball valve seat and a ball or. spherical shape of the otherwise disk-shaped valve membrane, FIGS. 9 and 10 show an eighth and ninth exemplary embodiment in which the clamping nut engages around the valve membrane in a cap-shaped manner, FIG. 11 shows a tenth exemplary embodiment in which the pin supporting the valve seat and the membrane extend axially the valve body protrude into the combustion chamber of the internal combustion engine and FIG. 12 shows an eleventh embodiment in which the valve membrane and sleeve are formed in one piece.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Ein in der Figur 1 dargestellter rotationssymmetrischer Ven¬ tilkörper 1 weist an seinem einen Ende einen Anschluß 3 für eine nicht dargestellte Zulaufleitung von einer Kraftstoff¬ einspritzpumpe auf, von dem ein, den Ventilkörper 1 längs¬ durchsetzender Zulaufkanal 5 abführt, der an einer dem Brennraum der zu versorgenden Brennkraftmschine zugewandten Stirnfläche 7 des Ventilkörpers 1 mündet. Diese Stirnfläche 7 grenzt dabei an einen Raum 9, der im in der Figur 2 ver¬ größert dargestellten ersten Ausführungsbeispiel radial ein¬ wärts gerichtet von einem zentralen, axial von der Stirnflä¬ che 7 vorstehenden Zapfen 11 und radial auswärts von einer Hülse 13 begrenzt ist. Dabei bildet der kegelstumpfförmige Zapfen 11 mit einem Teil seiner Kegelfläche einen Ventilsitz 15, an dem eine den Raum 9 brennraumseitig begrenzende, vor¬ zugsweise aus einem federnden Stahl ausgebildete, in Rich¬ tung Raum 9 gewölbte Ventilmembran 17 mit einer Dichtfläche 19 unter Vorspannung zur Anlage kommt. Die, ein bewegliches Ventilglied bildende scheibenförmige Ventilmembran 17 weist dazu in Höhe des Zapfens 11 eine kegelstumpfförmige, in Richtung Brennraum ragende Ausformung 21 (Vertiefung) auf, deren brennraumseitiges Ende kugelförmig ausgebildet ist, wobei die Innenflanken der Ausformung 21 die mit dem Ventil¬ sitz 15 zusammenwirkende Ventildichtfläche 19 bilden. Zwi¬ schen dem brennraumseitigen Ende des Zapfens 11 und dem Bo¬ den der Ausformung 21 ist dabei ein sacklochförmiger Raum 23 gebildet, der dem zwischen Ventilsitz 15 und Dichtfläche 19 gebildeten Dichtquerschnitt in Einspritzrichtung stromab¬ wärts nachgeschaltet ist und von dem wenigstens eine, vor¬ zugsweise eine Vielzahl von Einspritzöffnungen 25 in den Brennraum der Brennkraftmaschine abführen.A rotationally symmetrical valve body 1 shown in FIG. 1 has at one end a connection 3 for an inlet line, not shown, from a fuel injection pump, from which an inlet channel 5, which extends longitudinally through the valve body 1, leads away from one of the combustion chambers the end face 7 of the valve body 1 facing the internal combustion engine opens. This end face 7 borders on a space 9 which, in the first exemplary embodiment shown enlarged in FIG. 2, is delimited radially inwards by a central pin 11 projecting axially from the end face 7 and radially outward by a sleeve 13 . The frustoconical forms Pin 11 with a part of its conical surface has a valve seat 15 against which a valve membrane 17, which delimits the chamber 9 on the combustion chamber side and is preferably made of resilient steel and is curved in the direction of the chamber 9, comes under pressure with a sealing surface 19. For this purpose, the disc-shaped valve membrane 17, which forms a movable valve member, has a frusto-conical shape 21 (depression) at the level of the pin 11, the end of which is formed spherical, the end of the combustion chamber on the combustion chamber side, the inner flanks of the shape 21 having the valve seat 15 form cooperating valve sealing surface 19. Between the end of the pin 11 on the combustion chamber side and the bottom of the formation 21, a blind-hole-shaped space 23 is formed, which is connected downstream of the sealing cross section formed between the valve seat 15 and the sealing surface 19 in the injection direction and downstream of which at least one, upstream preferably discharge a plurality of injection openings 25 into the combustion chamber of the internal combustion engine.
An ihrem Außenrand ist die Ventilmembran 17 unter Zwischen¬ schaltung der Hülse 13 mittels einer Spannmutter 27 dichtend gegen den Ventilkörper 1 verspannt, wozu die Spannmutter 27 einen den Außenrand der Ventilmembran 17 überdeckenden Kra¬ gen 29 aufweist.On its outer edge, the valve membrane 17 is tightly clamped against the valve body 1 by means of a clamping nut 27 with the sleeve 13 interposed, for which purpose the clamping nut 27 has a collar 29 covering the outer edge of the valve membrane 17.
Um eine für die Dichtheit des Ventilsitzes ausreichende Fi¬ xierung zwischen dem Zapfen 11 und der Ventilmembran 17 zu gewährleisten, ist der Außendurchmesser der Ventilmembran 17 kleiner ausgeführt, als der Innendurchmesser der Spannmutter 27, so daß sich bei der Montage die Ventilmembran 17 optimal zum Zapfen 11 zentrieren kann.In order to ensure a sufficient fixation between the pin 11 and the valve membrane 17 for the tightness of the valve seat, the outside diameter of the valve membrane 17 is made smaller than the inside diameter of the clamping nut 27, so that the valve membrane 17 optimally fits to the pin during assembly 11 can center.
Eine Einspritzung am erfindungsgemäßen Kraftstoffeinspritz- ventil erfolgt durch das Befüllen des Raumes 9 mit unter ho¬ hem Druck stehenden Kraftstoff von der Einspritzpumpe über den Zulaufkanal 5. In Folge dieses Druckaufbaus wird die Ventilmembran 17 mit ihrer Dichtfläche 19 entgegen ihrer Vorspannkraft vom Ventilsitz 15 abgehoben, so daß der Kraft¬ stoff entlang dem nunmehr geöffneten Dichtquerschnitt in den sacklochförmigen Raum 23 und weiter über die Einspritzöff¬ nungen 25 in den Brennraum der zu versorgenden Brennkraftma¬ schine gelangt. Die Einspritzung wird durch die Unterbre¬ chung der Kraftstoffhochdruckzufuhr in den Raum 9 beendet, in deren Folge der Druck im Raum 9 erneut unter die Kraft der Vorspannung der Ventilmembran 17 absinkt, so daß die Ventildichtfläche 19 dichtend auf den Ventilsitz 15 zurück¬ federt.The fuel injection valve according to the invention is injected by filling the space 9 with fuel under high pressure from the injection pump via the inlet channel 5. As a result of this pressure build-up, the valve membrane 17 with its sealing surface 19 becomes counter to it Preload force is lifted from the valve seat 15, so that the fuel reaches the blind-hole-shaped space 23 along the now open sealing cross-section and further via the injection openings 25 into the combustion chamber of the internal combustion engine to be supplied. The injection is terminated by interrupting the high-pressure fuel supply in the space 9, as a result of which the pressure in the space 9 drops again under the force of the prestressing of the valve membrane 17, so that the valve sealing surface 19 springs back onto the valve seat 15 in a sealing manner.
Das in der Figur 3 gezeigte zweite Ausführungsbeispiel ist bis auf die Ausgestaltung des Ventilsitzes 15 analog zum er¬ sten in den Figuren 1 und 2 dargestellten Ausführungsbei- spiel aufgebaut. Dabei wird der Ventilsitz 15 dort durch ei¬ ne in der Mitte der Stirnfläche 7 des Ventilkörpers 1 befe¬ stigte, vorzugsweise geschweißte Kugel 31 gebildet, deren Oberfläche den Ventilsitz 15 bildet, der mit der Ventil¬ dichtfläche 19 der Ventilmembran 17 zusammenwirkt.Except for the configuration of the valve seat 15, the second exemplary embodiment shown in FIG. 3 is constructed analogously to the first exemplary embodiment shown in FIGS. 1 and 2. The valve seat 15 is formed there by a preferably welded ball 31 fastened in the middle of the end face 7 of the valve body 1, the surface of which forms the valve seat 15, which cooperates with the valve sealing face 19 of the valve membrane 17.
Die Figur 4 zeigt ein drittes Ausführungsbeispiel, bei dem die Ventilmembran 17 zweiteilig ausgebildet ist. Dabei sind Dichtfläche 19 und Einspritzöffnungen 25 an einem Membran¬ einsatz 33 angeordnet, dessen Form der Ausformung 21 der Fi¬ gur 2 entspricht und der in eine vorgesehene Aufnahmebohrung 35 der Ventilmembran 17 eingesetzt und dichtend befestigt wird.FIG. 4 shows a third exemplary embodiment in which the valve membrane 17 is constructed in two parts. Sealing surface 19 and injection openings 25 are arranged on a membrane insert 33, the shape of which corresponds to the shape 21 of FIG. 2 and which is inserted into a provided receiving bore 35 of valve membrane 17 and fastened in a sealing manner.
Die Figuren 5 und in einem vergrößerten Ausschnitt 5A zeigen ein viertes Ausführungsbeispiel des Kraf stoffeinspritzven¬ tils, bei dem der Membraneinsatz 33 als Hohlkugel 37 ausge¬ bildet ist, an deren dem Raum 9 zugewandter Seite eine Öff¬ nung vorgesehen ist, deren Wände die Ventildichtfläche 19 bilden und in die der Zapfen 11 mit seinem Ventilsitz 15 hineinragt. Bei dem in der Figur 6 und vergrößert in Figur 6A darge¬ stellten fünften Ausführungsbeispiel ist der Ventilsitz 15 durch die Mündung des Zulaufkanals 5 in der Stirnfläche 7 des Ventilkörpers 1 gebildet. Die mit diesem Ventilsitz 15 zusammenwirkende Ventildichtfläche 19 ist dabei an einer Vollkugel 39 gebildet, die mit der Ventilmembran 17 verbun¬ den ist und die von sich kreuzenden, die Einspritzöffnungen 25 bildenden Bohrungen 41 durchdrungen ist, die vom Raum 9 ausgehend in den Brennraum der Brennkraftmaschine münden. Dabei übernimmt hier der ständig mit dem Brennraum verbunde¬ ne Raum 9 während des Betriebs des Kraftstoffeinspritzven- tils die Funktion des sacklochförmigen Raumes 23, der vorhe¬ rigen Figuren und der Druck im Zulaufkanal 5 strömt direkt gegen die Ventildichtfläche 19 der Ventilmembran 17. Um das mit dem Brennraum in Verbindung stehende schädliche Volumen innerhalb des Einspritzventils zu minimieren, ist zudem die Hülse 13 in dieses Totvolumen zwischen Ventilmem¬ bran 17 und Ventilkörper 1 eingesetzt, die dabei so ausge¬ bildet ist, daß sie die Öffnungs- und Schließbewegung der Ventilmembran 17 nicht beeinträchtigt.Figures 5 and in an enlarged section 5A show a fourth embodiment of the fuel injection valve, in which the membrane insert 33 is formed as a hollow ball 37, on the side facing the space 9 an opening is provided, the walls of which are the valve sealing surface Form 19 and into which the pin 11 projects with its valve seat 15. In the fifth exemplary embodiment shown in FIG. 6 and enlarged in FIG. 6A, the valve seat 15 is formed by the opening of the inlet channel 5 in the end face 7 of the valve body 1. The valve sealing surface 19 cooperating with this valve seat 15 is formed on a solid ball 39 which is connected to the valve membrane 17 and which is penetrated by intersecting bores 41 which form the injection openings 25 and which, starting from the space 9, enter the combustion chamber of the internal combustion engine flow out. Here, the space 9, which is permanently connected to the combustion chamber, takes over the function of the pocket-shaped space 23 during the operation of the fuel injection valve, the previous figures and the pressure in the inlet channel 5 flows directly against the valve sealing surface 19 of the valve membrane 17 To minimize harmful volume within the injection valve in connection with the combustion chamber, the sleeve 13 is also inserted into this dead volume between the valve membrane 17 and the valve body 1, which is designed such that it controls the opening and closing movement of the valve membrane 17 not affected.
Das in den Figuren 7 und 7A dargestellte sechste Ausfüh¬ rungsbeispiel ist eine Kombination des an der Kugel 31 ge¬ bildeten Ventilsitzes 15 und einer am Membraneinsatz 33 an¬ geordneten Ventildichtfläche 19 nach den Figuren 3 und . Das in der Figur 8 und vergrößert in Figur 8A dargestellte siebte Ausführungsbeispiel unterscheidet sich zum in der Fi¬ gur 3 dargestellten zweiten Ausführungsbeispiel lediglich in der Form der Ausformung 21 an der Ventilmembran 17, die jetzt kugelkalottenförτnig ausgebildet ist, wobei der zwi¬ schen Kugelboden und Ventilsitzkugel 31 gebildete sackloch- förmige Raum 23, von dem die Einspritzöffnungen 25 abführen, zur Verringerung des Schadvolumens begrenzt ist . Bei dem in der Figur 9 dargestellten achten Ausführungsbei- spiel ist die Ventilmembran 17 in etwa glockenförmig mit Ab- Sätzen ausgebildet, wobei die Spannmutter 27 die Ventilmem¬ bran 17 über eine Ringschulter 43 direkt gegen die Stirnflä¬ che 7 des Ventilkörpers 1 preßt. Zudem ragt der Kragen 29 der Spannmutter 27 radial derart weit einwärts, daß er bis auf ein geringes, einstellbares Spaltmaß s an die Ventilmem¬ bran 17 heranreicht, wobei die Größe des Spaltmaßes s somit den maximalen Öffnungshub der Ventilmembran 17 bestimmt Das in der Figur 10 gezeigte neunte Ausführungsbeispiel un¬ terscheidet sich zum achten Ausführungsbeispiel nur dadurch, daß zwischen der Stirnfläche 7 des Ventilkörpers 1 und der Ventilmembran 17 ein Einstellring 45 eingespannt ist, über dessen Stärke oder Verformung sich die axiale Lage der Ven¬ tilmembran 17 zum Ventilkörper 1 und somit die Vorspannkraf der Anlage von Ventildichtfläche 19 am Ventilsitz 15 bzw. der Öffnungsdruck des Kraftstoffeinspritzventils einstellen läßt.The sixth exemplary embodiment shown in FIGS. 7 and 7A is a combination of the valve seat 15 formed on the ball 31 and a valve sealing surface 19 according to FIGS. 3 and 7 arranged on the membrane insert 33. The seventh exemplary embodiment shown in FIG. 8 and enlarged in FIG. 8A differs from the second exemplary embodiment shown in FIG. 3 only in the shape of the shape 21 on the valve membrane 17, which is now designed in the shape of a spherical cap, the intermediate spherical bottom and Valve seat ball 31 formed blind hole-shaped space 23, from which the injection openings 25 lead, is limited to reduce the volume of damage. In the eighth exemplary embodiment shown in FIG. 9, the valve membrane 17 is approximately bell-shaped with an Sets formed, the clamping nut 27 presses the valve membrane 17 via an annular shoulder 43 directly against the end face 7 of the valve body 1. In addition, the collar 29 of the clamping nut 27 projects radially inwards so far that it reaches the valve membrane 17 except for a small, adjustable gap dimension s, the size of the gap dimension s thus determining the maximum opening stroke of the valve membrane 17 The ninth exemplary embodiment shown differs from the eighth exemplary embodiment only in that an adjusting ring 45 is clamped between the end face 7 of the valve body 1 and the valve diaphragm 17, the strength or deformation of which adjusts the axial position of the valve diaphragm 17 to the valve body 1 and thus can set the biasing force of the system of valve sealing surface 19 on the valve seat 15 or the opening pressure of the fuel injector.
Bei dem in der Figur 11 gezeigten zehnten Ausführungsbei- spiel ragen Zapfen 11 und Ventilmembran 17 aus der Über¬ deckung mit der Spannmutter 27 in das Innere des Brennraumes der Brennkraftmaschine, wobei die Ventimembran 17 während der Druckbeaufschlagung des Raumes 9 dabei neben einer Aus¬ dehnung in Achsrichtung zum Ventilkörper 1 auch mittels ei¬ nes radialen Atmens den Öffnungsquerschnitt zwischen Ventil¬ sitz 15 und Ventildichtfläche 19 aufsteuert.In the tenth exemplary embodiment shown in FIG. 11, the pin 11 and the valve membrane 17 protrude from the overlap with the clamping nut 27 into the interior of the combustion chamber of the internal combustion engine, the valve membrane 17 during the pressurization of the space 9 in addition to an expansion the opening cross-section between valve seat 15 and valve sealing surface 19 also opens in the axial direction to valve body 1 by means of radial breathing.
Bei dem in der Figur 12 gezeigten elften Ausführungsbeispiel ist die ansonsten analog zur Figur 1 ausgebildete Ventilmem¬ bran 17 einstückig mit der Hülse 13 aus der Figur 1 ausge¬ führt. Neben dem Vorteil einer weiteren Bauteilreduzierung entfällt hierbei eine Dichtfuge, was zu weniger Bearbei¬ tungsaufwand bei gleichzeitiger Verringerung des Dichtheits¬ risikos führt. Ein weiterer Vorteil stellt der stetig in die Hülse übergehende Übergangsbereich dar, durch den die Span¬ nungen an der Einspannstelle der Ventilmembran verringert werden können. Es ist somit mit dem erfindungsgemäßen Kraftstoffeinspritz¬ ventil möglich, die Vorteile einer Lochdüse in konstruktiv einfacher Weise mit den Vorteilen einer Membrandüse zu ver¬ binden und so bei Verwendung weniger Bauteile eine hohe Funktionssicherheit zu gewährleisten. In the eleventh embodiment shown in FIG. 12, the valve membrane 17, which is otherwise designed analogously to FIG. 1, is made in one piece with the sleeve 13 from FIG. In addition to the advantage of a further reduction in the number of components, there is no sealing joint, which leads to less machining effort and, at the same time, a reduction in the risk of leaks. A further advantage is the transition area that continuously merges into the sleeve, through which the stresses at the clamping point of the valve membrane can be reduced. It is thus possible with the fuel injection valve according to the invention to combine the advantages of a perforated nozzle with the advantages of a diaphragm nozzle in a structurally simple manner and thus to ensure high functional reliability when using fewer components.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzventil für Brennkraftmaschinen mit ei¬ nem Ventilkörper (1) mit einem ortsfesten Ventilsitz (15) und einem beweglichen Ventilglied (17) , das eine federnd verstellbare Wand aufweist, deren Rand am Ventilkörper (1) festgelegt ist und die zusammen mit der Stirnfläche (7) des Ventilkörpers (1) einen Raum (9) einschließt und von dem an¬ dererseits an die verstellbare Wand angrenzenden Brennraum der zu versorgenden Brennkraftmaschine trennt, mit einem von einer Kraftstoffhochdruckquelle versorgten Zulaufkanal (5) , der in den Raum (9) mündet und mit einer Ventildichtfläche (19) am beweglichen Ventilglied (17) , die unter Einwirkung des stromaufwärts des ortsfesten Ventilsitzes (15) anstehen¬ den Kraftstoffhochdruckes vom ortsfesten Ventilsitz (15) ab¬ hebbar ist und dabei wenigstens eine stromabwärts der Ven¬ tildichtfläche (19) liegende Einspritzöffnung (25) mit dem Zulaufkanal (5) verbindet, dadurch gekennzeichnet, daß als Einspritzöffnung (25) wenigstens ein geometrisch festgeleg¬ tes Einspritzloch vorgesehen ist, das stromabwärts der Ven¬ tildichtfläche (19) durch das bewegliche Ventilglied (17) hindurchführt.1. Fuel injection valve for internal combustion engines with a valve body (1) with a fixed valve seat (15) and a movable valve member (17) which has a resiliently adjustable wall, the edge of which is fixed to the valve body (1) and which together with the end face (7) of the valve body (1) encloses a space (9) and separates it from the combustion chamber of the internal combustion engine to be supplied, which combustion chamber is adjacent to the adjustable wall, with an inlet channel (5) supplied by a high-pressure fuel source which leads into the space (9) opens and with a valve sealing surface (19) on the movable valve member (17), which can be lifted off under the action of the upstream of the fixed valve seat (15) high fuel pressure from the fixed valve seat (15) and at least one downstream of the valve sealing surface ( 19) connecting the injection opening (25) to the inlet channel (5), characterized in that whom as the injection opening (25) At least one geometrically defined injection hole is provided, which leads downstream of the valve sealing surface (19) through the movable valve member (17).
2. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge¬ kennzeichnet, daß der Ventilsitz (15) an einem koaxial zur Achse des Ventilkörpers (1) von der brennraumseitigen Stirn¬ fläche (7) des Ventilkörpers (1) vorstehenden Zapfen (11) gebildet ist, dessen Querschnitt sich in Richtung des als Ventilmembran ausgebildeten beweglichen Ventilglieds (17) verringert und daß das bewegliche Ventilglied (17) eine sich an die Ventildichtfläche (19) anschließende Vertiefung (21) aufweist, von der die Einspritzlöcher ausgehen.2. Fuel injection valve according to claim 1, characterized in that the valve seat (15) on a coaxial to the axis of the valve body (1) from the combustion chamber end face (7) of the valve body (1) projecting pin (11) is formed, the cross section of which is reduced in the direction of the movable valve member (17) in the form of a valve membrane, and in that the movable valve member (17) has a depression (21) adjoining the valve sealing surface (19), from which the injection holes originate.
3. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge¬ kennzeichnet, daß der Ventilsitz (15) durch eine an der brennraumseitigen Stirnfläche (7) des Ventilkörpers (1) be¬ festigte Kugel (31) gebildet ist.3. A fuel injection valve according to claim 1, characterized in that the valve seat (15) is formed by a ball (31) fastened on the end face (7) of the valve body (1) on the combustion chamber side.
4. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge¬ kennzeichnet, daß die Einspritzöffnungen (25) in einer, in Richtung Brennraum von der Stirnfläche des vorzugsweise als scheibenförmige Ventilmembran (17) ausgebildeten beweglichen Ventilgliedes vorstehenden Ausformung (21) angeordnet sind, die mit einem Teil ihrer dem Raum 9 zugewandten Wand die Dichtfläche (19) bildet, wobei zwischen Dichtfläche (19) und Einspritzöffnungen (25) ein sacklochförmiger Raum (23) ver¬ bleibt.4. Fuel injection valve according to claim 1, characterized ge indicates that the injection openings (25) in a, in the direction of the combustion chamber from the end face of the preferably formed as a disc-shaped valve membrane (17) movable valve member protruding formation (21) are arranged with a part its wall facing the space 9 forms the sealing surface (19), a blind hole-shaped space (23) remaining between the sealing surface (19) and the injection openings (25).
5. Kraftstoffeinspritzventil nach Anspruch 4, dadurch ge¬ kennzeichnet, daß die die Einspritzöffnungen (25) aufnehmen¬ de Ausformung (21) der Ventilmembran (17) an ihrem brenn¬ raumseitigen Ende kugelsegmentförmig ausgebildet ist, wobei die Einspritzöffnungen (25) vorzugsweise zur Symmetrieachse versetzt angeordnet sind.5. Fuel injection valve according to claim 4, characterized ge indicates that the injection openings (25) receiving de formation (21) of the valve membrane (17) is spherical segment-shaped at its combustion chamber end, the injection openings (25) preferably to the axis of symmetry are staggered.
6. Kraftstoffeinspritzventil nach Anspruch 4, dadurch ge¬ kennzeichnet, daß die die Einspritzöffnungen (25) aufnehmen¬ de Ausformung (21) der Ventilmembran (17) mit dieser ein¬ stückig ist.6. The fuel injector according to claim 4, characterized in that the injection openings (25) receiving the formation (21) of the valve membrane (17) are integral therewith.
7. Kraf stoffeinspritzventil nach Anspruch 4, dadurch ge¬ kennzeichnet, daß die die Einspritzöffnungen aufnehmende Ausformung durch einen druckdicht mit der Ventilmembran (17) verbundenen Membraneinsatz (33) gebildet ist.7. Kraf fuel injection valve according to claim 4, characterized ge indicates that the receiving the injection openings Forming is formed by a pressure-tight membrane insert (33) connected to the valve membrane (17).
8. Kraftstoffeinspritzventil nach Anspruch 7 ,dadurch ge¬ kennzeichnet, daß der Membraneinsatz (33) als hohlzylindri- ger Kegelstumpf mit einer kugelförmigen Kuppe ausgebildet ist.8. Fuel injection valve according to claim 7, characterized ge indicates that the membrane insert (33) is designed as a hollow cylindrical truncated cone with a spherical cap.
9. Kraftstoffeinspritzventil nach Anspruch 7 »dadurch ge¬ kennzeichnet, daß der Membraneinsatz (33) als hohlzylindri- ges Kugelsegment ausgebildet ist.9. Fuel injection valve according to claim 7 » characterized in that the membrane insert (33) is designed as a hollow cylindrical spherical segment.
10. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge¬ kennzeichnet, daß der Ventilsitz (15) durch die dem Raum (9) zugewandte Austrittsöffnung des Zulaufkanals (5) an der brennraumseitigen Stirnfläche (7) des Ventilkörpers (1) ge¬ bildet ist und daß an der beweglichen Wand eine Kugel (39) befestigt ist, die mit einem Teil ihrer Wandfläche die mit dem Ventilsitz (15) zusammenwirkende Ventildichtfläche (19) bildet und die eine Vielzahl von Einspritzkanälen (41) auf¬ weist, deren eines Ende jeweils ständig mit dem Raum (9) und deren anderes Ende ständig mit dem Brennraum verbunden sind.10. Fuel injection valve according to claim 1, characterized ge indicates that the valve seat (15) through the space (9) facing outlet opening of the inlet channel (5) on the combustion chamber end face (7) of the valve body (1) is ge and that a ball (39) is fastened to the movable wall, which forms part of its wall surface with the valve sealing surface (19) which cooperates with the valve seat (15) and which has a multiplicity of injection channels (41), one end of which always coexists the room (9) and the other end of which are permanently connected to the combustion chamber.
11. Kraftstoffeinspritzventil nach Anspruch 1, dadurch ge¬ kennzeichnet, daß das bewegliche Ventilglied (17) mittels einer Spannmutter (27) am Ventilkörper (1) befestigt ist.11. The fuel injection valve according to claim 1, characterized in that the movable valve member (17) is fastened to the valve body (1) by means of a clamping nut (27).
12. Kraftstoffeinspritzventil nach Anspruch 11, dadurch ge¬ kennzeichnet, daß zwischen dem beweglichen Ventilglied (17) und dem Ventilkörper (1) eine Hülse (13) oder ein Einstell- ring (45) vorgesehen ist.12. Fuel injection valve according to claim 11, characterized in that between the movable valve member (17) and the valve body (1) a sleeve (13) or an adjusting ring (45) is provided.
13. Kraftstoffeinspritzventil nach Anspruch 2, dadurch ge¬ kennzeichnet, daß der den Ventilsitz (15) tragende Zapfen13. Fuel injection valve according to claim 2, characterized in that the valve seat (15) bearing pin
(11) in den Brennraum der Brennkraftmaschine hineinragt, wo- zu ein Teil der Ventilmembran (17) ebenfalls hohlzylinder- förmig ausgebildet ist.(11) protrudes into the combustion chamber of the internal combustion engine, where part of the valve membrane (17) is also designed as a hollow cylinder.
14. Kraftstoffeinspritzventil nach Anspruch l, dadurch ge¬ kennzeichnet, daß das bewegliche Ventilglied (17) mit dem Ventilkörper (1) verschweißt ist.14. Fuel injection valve according to claim 1, characterized in that the movable valve member (17) is welded to the valve body (1).
15. Kraftstoffeinspritzventil nach Anspruch l, dadurch ge¬ kennzeichnet, daß das bewegliche Ventilglied (17) einstückig mit einer zwischen Ventilmembran (17) und Ventilkörper (1) einsetzbaren Hülse (13) ausgeführt ist. 15. Fuel injection valve according to claim l, characterized ge indicates that the movable valve member (17) is made in one piece with a between the valve membrane (17) and valve body (1) insertable sleeve (13).
EP95937760A 1994-12-20 1995-11-15 Fuel injection valve for internal combustion engines Ceased EP0770176A1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4445585 1994-12-20
DE4445585A DE4445585A1 (en) 1994-12-20 1994-12-20 Fuel injection valve for internal combustion engines
PCT/DE1995/001580 WO1996019660A1 (en) 1994-12-20 1995-11-15 Fuel injection valve for internal combustion engines

Publications (1)

Publication Number Publication Date
EP0770176A1 true EP0770176A1 (en) 1997-05-02

Family

ID=6536448

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95937760A Ceased EP0770176A1 (en) 1994-12-20 1995-11-15 Fuel injection valve for internal combustion engines

Country Status (7)

Country Link
EP (1) EP0770176A1 (en)
JP (1) JPH09509717A (en)
KR (1) KR970701310A (en)
CN (1) CN1141664A (en)
CZ (1) CZ241596A3 (en)
DE (1) DE4445585A1 (en)
WO (1) WO1996019660A1 (en)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19536330A1 (en) * 1995-09-29 1997-04-03 Bosch Gmbh Robert Fuel injection valve for IC engines
DE10064802A1 (en) * 2000-12-22 2002-06-27 Bosch Gmbh Robert Fuel injection valve for combustion engine has valve sealing surface on radially outer edge of valve element biased in center section by holding element with respect to contact with valve seat
EP1559905A1 (en) * 2004-01-29 2005-08-03 Siemens VDO Automotive S.p.A. Fluid injector with a deformable valve needle
DE102008007203A1 (en) * 2008-02-01 2009-08-06 Robert Bosch Gmbh Compact injection device with pressure-controlled nozzle
TWI470149B (en) * 2009-02-12 2015-01-21 Bosch Gmbh Robert Kompakte einspritzvorrichtung mit druckgesteuerter duese
CN101592112B (en) * 2009-04-24 2012-06-27 靳北彪 Valve sheet deformation fuel injector for engine
CN101592106B (en) * 2009-04-24 2013-10-30 靳北彪 Apertured valve sheet deformation fuel injector for engine
CN101598096B (en) * 2009-05-12 2012-04-25 靳北彪 Global fuel injection device for engine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE363572C (en) * 1922-11-10 Oskar Robert Groenkwist Device for atomizing liquids, in particular liquid fuel for internal combustion engines
DE497439C (en) * 1926-03-28 1930-05-09 Super Diesel Tractor Corp Method and device for the airless introduction of liquid fuel in a gaseous state into the working space of an internal combustion engine
US2805891A (en) * 1954-04-05 1957-09-10 Mcculloch Motors Corp Fluid spray nozzle
GB760852A (en) * 1954-06-11 1956-11-07 Dewandre Co Ltd C Improvements relating to fuel injection nozzles for internal combustion engines including gas turbines
FR1218966A (en) * 1958-03-25 1960-05-13 Motorpal Jihlava Np Injection nozzle for internal combustion engine injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9619660A1 *

Also Published As

Publication number Publication date
CZ241596A3 (en) 1997-02-12
CN1141664A (en) 1997-01-29
JPH09509717A (en) 1997-09-30
DE4445585A1 (en) 1996-06-27
KR970701310A (en) 1997-03-17
WO1996019660A1 (en) 1996-06-27

Similar Documents

Publication Publication Date Title
DE19547423B4 (en) Fuel injection valve for internal combustion engines
CH700396A1 (en) Fuel injection valve for internal combustion engines.
WO2008083881A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
DE19523243B4 (en) Fuel injection valve for internal combustion engines with a clamping nut with a conically formed annular shoulder
EP1552135B1 (en) Fuel injection device for an internal combustion engine
EP0783626B1 (en) Fuel injection valve arrangement for internal combustion engines
DE4214646A1 (en) FUEL INJECTION NOZZLE FOR PRIME AND MAIN INJECTION
DE102008001597A1 (en) Fuel injector
EP2329133B1 (en) Fuel injection valve
EP1373711B1 (en) Fuel injection valve
EP0770176A1 (en) Fuel injection valve for internal combustion engines
WO2000019088A1 (en) Fuel injection valve for an internal combustion engine
EP0900334A1 (en) Pressure valve
WO2010009932A1 (en) Fuel injector
DE19829553A1 (en) Pressure valve
DE19536330A1 (en) Fuel injection valve for IC engines
DE19507188C1 (en) Fuel injection valve for internal combustion engines
EP1309788A1 (en) Fuel injection valve
WO2008049668A1 (en) Injector for injecting fuel into combustion chambers of internal combustion engines
EP1526274B1 (en) Fuel injection device, especially for a direct injection internal combustion engine
EP0811119B1 (en) Fuel injection valve for internal combustion engines
WO2000014400A1 (en) Fuel injector for internal combustion engines
WO2003031803A1 (en) Fuel injection device, especially an injector for direct-injection internal combustion engines, fuel system and internal combustion engine
EP0920583A1 (en) Valve for controlling liquids
DE19623759A1 (en) Fuel injection valve for internal combustion engines

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 19961227

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): DE FR GB IT

17Q First examination report despatched

Effective date: 19970410

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

Free format text: STATUS: THE APPLICATION HAS BEEN REFUSED

18R Application refused

Effective date: 19990402