EP1210513A1 - Fuel injection device for fuel internal combustion engines - Google Patents

Fuel injection device for fuel internal combustion engines

Info

Publication number
EP1210513A1
EP1210513A1 EP00958258A EP00958258A EP1210513A1 EP 1210513 A1 EP1210513 A1 EP 1210513A1 EP 00958258 A EP00958258 A EP 00958258A EP 00958258 A EP00958258 A EP 00958258A EP 1210513 A1 EP1210513 A1 EP 1210513A1
Authority
EP
European Patent Office
Prior art keywords
seat
valve
fuel injection
fuel
injection device
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP00958258A
Other languages
German (de)
French (fr)
Inventor
Patrick Mattes
Dietmar Schmieder
Wolfgang Stoecklein
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 EP1210513A1 publication Critical patent/EP1210513A1/en
Withdrawn legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • 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
    • F02M45/00—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship
    • F02M45/02—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts
    • F02M45/04—Fuel-injection apparatus characterised by having a cyclic delivery of specific time/pressure or time/quantity relationship with each cyclic delivery being separated into two or more parts with a small initial part, e.g. initial part for partial load and initial and main part for full load
    • 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
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • 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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
    • F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1, as is known from DE 196 24 001 AI.
  • the known device has a valve element which can be actuated by a piezo and which seals or opens the control chamber to a discharge channel in a fuel injection valve.
  • the sealing takes place either via a conical seat formed on the valve member or via a ball seat. Because of this design, when the valve member is lifted from its valve seat on the valve housing, the effect arises that the hydraulically effective seat diameter of the valve member is larger than its geometric seat diameter. The result of this is that an increased opening force has to be exerted by the piezo in order to lift the valve member from its valve seat. This increased opening force reduces the stroke of the piezo or limits the area of application of an upstream hydraulic force-displacement translator.
  • the effect of the hydraulically effective seat diameter of the valve member which is increased in relation to the geometric seat diameter in the case of the cone or ball seats mentioned, can be determined from flow or Explain throttling effects that arise when, when the valve member is lifted from its valve seat, a flow channel with a certain length is formed between the valve member and the valve seat, through which the fuel flows from the control chamber to the drain channel.
  • valve member has executed a certain minimum stroke, the effects described no longer occur.
  • valve member seals the relief chamber both to the relief line connected to the discharge chamber and to the control chamber.
  • the valve member forms, together with the valve housing, an upper and a lower sealing seat, which in the prior art are each designed as a ball or conical seat. Since the valve housing is divided horizontally in the area of the two sealing seats for manufacturing reasons and the valve member has a closing body mounted on the valve stem, a very complex and exact production is necessary so that no lateral forces are not caused on the valve member when changing from one sealing seat to the other aligned sealing seats occur, which in addition to increased wear and tear also results in increased noise.
  • the fuel injection device for internal combustion engines according to the invention with the characterizing feature of claim 1 has the advantage that the flat seat used when lifting the valve member from its valve seat whose hydraulically effective seat diameter is in practice only slightly larger than the geometric seat diameter of the valve member.
  • the hydraulically effective seat diameter corresponds more closely to the geometric seat diameter of the valve member, the smaller the difference in diameter between the opening closed by the valve member and the diameter of the valve member on the valve seat, since very short flow paths for the pressure medium at the valve seat are then created when the valve member is lifted, whereby the flow or throttling effects causing the differently effective seat diameters are reduced.
  • a flat seat can be realized particularly easily in terms of production technology, since the tolerance requirements with regard to the guidance of the valve member with respect to the valve seat are relatively low.
  • valve seat is designed as a flat seat, since the closing member then essentially only has to be aligned with a sealing seat.
  • valve member interacts with a peripheral, raised seat edge on the valve seat.
  • This circumferential seat edge can be realized relatively easily in terms of production technology by means of a bevel.
  • the hydraulically effective seat diameter of the valve member is almost the same as the geometric seat diameter, regardless of the size or diameter of the valve member at the level of the flat seat.
  • Figure 1 is a schematic representation of a fuel injection device according to the invention
  • FIG. 2 shows a fuel injection valve corresponding to section A of FIG. 1 in longitudinal section and FIGS. 3 and 4 modified compared to FIG. 2
  • Fuel injectors also in longitudinal section.
  • a so-called common rail system realizes a fuel injection device with which a large variation of the fuel injection is possible with high injection pressures and little effort, in particular with very precisely controllable injection times and injection quantities.
  • This provides a different type of high-pressure fuel source than is provided by the conventional high-pressure fuel injection pump.
  • the invention is in this so-called common rail system as well as in one Fuel injection pump can be used. However, preference is given to the common rail system.
  • a high-pressure fuel reservoir 1 is provided with respect to a common rail system as a high-pressure fuel source, which is supplied with fuel by a high-pressure fuel delivery pump 2 from a fuel reservoir 4.
  • the pressure in the high-pressure fuel accumulator 1 is controlled by a pressure control valve 5 in conjunction with a pressure sensor 6 via an electrical control device 8. This also controls a fuel injection valve 9.
  • the fuel injection valve 9 has a valve housing 11, which at one end, which is for installation on the
  • Fuel injection valve 9 is controlled by an injection valve member 14.
  • this is designed as an elongated valve needle which has a sealing surface 15 at one end, which cooperates with an internal valve seat.
  • the valve needle is located within a pressure chamber 16 connected to the high-pressure fuel reservoir 1 by a pressure line 17 within the valve housing 11.
  • a compression spring 19 is arranged, which is clamped axially between a valve plate 20 and the valve housing 11 and the injection valve member 14 acts in the closing direction.
  • a plunger 21 is provided coaxially to the compression spring 19, which rests on the one hand on the valve plate 20 and on the other hand dips into a guide bore 22 and there encloses a control chamber 25 with the closed end of the guide bore 22 with its end face 23, which forms a movable wall.
  • This control room 25 opens Inflow channel 26, in which an inlet throttle 27 is arranged, and which, starting from the pressure chamber 16, always delivers fuel under high pressure via the inlet throttle 27 into the control chamber 25.
  • Relief line 31 to a receivable drainage space 32 which can also be the fuel reservoir 4, for example.
  • the relief chamber 30 has an upper region 33 and a lower region 34 facing the control chamber 25.
  • the relief line 31 branches off from the upper area 33, which is smaller in diameter in relation to the lower area 34, on the side opposite the inlet channel 26.
  • a circumferential elevation or a web 35 projects into the lower region 34, the inner wall 36 of which is designed as an extension of the bore wall 37 of the upper region 33.
  • the web 35 On the side facing away from the inner wall 36, the web 35 has a slope 39, so that the web 35 is triangular in the longitudinal section shown in FIG.
  • the end face of the web 35 facing the drain channel 29 forms a peripheral seat edge 40 which, when it interacts with a valve member 42, forms a first sealing seat 41.
  • the valve member 42 is part of a control valve 43, the valve member 42 being able to be brought into the closed or open position by a piezo 45.
  • the valve member 42 has a valve stem 46 and a closing element 47 which adjoins one end of the valve stem 46 and cooperates with the seat edge 40.
  • the valve stem 46 is arranged in the upper region 33 of the relief chamber 30 with radial play.
  • Closing element 47 is hemispherical or spherical section-shaped, with a flat seat surface 48 facing the seat edge 40, to which the valve stem 46 is also connected.
  • the first sealing seat 41 is thus formed as a flat seat by the seat surface 48 and the seat edge 40, the seat surface 48 of the closing element 47 projecting beyond the seat edge 40 in diameter.
  • the fuel injection device described above works as follows:
  • the fuel high-pressure feed pump 2 which is preferably driven synchronously with the internal combustion engine, transfers fuel from the fuel tank 4 into the fuel tank 4
  • High-pressure fuel accumulator 1 is conveyed, the pressure of which is set to a preferably constant value via the pressure control valve 5 in conjunction with the pressure sensor 6. This value can also be changed if necessary.
  • valve member 42 of the control valve 43 is in the closed position shown, is due to the Pressure line 17 supplied fuel also maintained a relatively high pressure in the control chamber 25, which acts on the injection valve member 14 in addition to the compression spring 19 with a closing force via the movable wall 23, so that the injection valve member 14 is brought into the closed position and remains in this position.
  • the control valve 43 is opened, the control chamber 25 can be relieved via the drain channel 29, the relief chamber 30 and the relief line 31 to the drain chamber 32.
  • the first sealing seat 41 As a flat seat when the closing element 47 is lifted from the seat edge 40, only a very short flow path for the fuel from the lower region 34 into the upper region 33 of the relief chamber 30 is created. Thus, there are only very small flow effects which increase the opening force of the piezo 45.
  • the special design of the seat edge 40 on the raised web 35 additionally reduces the effect of the diameter differences between the closing element 47 in the region of the seat surface 48 and the upper region 33, which has an additional positive effect on the required opening force of the piezo 45.
  • valve member 42 If the valve member 42 is now moved again in the direction of the first sealing seat 41, a second injection process, called the main injection, is triggered. This triggering takes place in analogy to the first
  • Injection process by lowering the pressure in the control chamber 25 as a result of fuel flowing out into the drain chamber 32.
  • the main injection is ended as soon as the valve member 42 rests on the seat edge 40 with its seat 48, forming the first sealing seat 41.
  • the closing element 47 shuts off the upper region 33 to the lower region 34 in the relief chamber 30, so that the high fuel pressure is generated again in the control chamber 25, which then brings the injection valve member 14 back into the closed position.
  • FIG. 3 shows the multi-part construction of the valve housing with a lower valve housing part 111 and an upper valve housing part
  • valve stem 461 and the closing element 471 are designed as separate, interconnected components which together form the valve member 421. Furthermore, the web 35 is dispensed with, so that the contact surface on the first sealing seat 411 is enlarged.
  • the conical seat offers advantages in terms of wear resistance and leakage losses.

Abstract

Disclosed is a fuel-injection device for internal combustion engines, whereby a fuel-injection valve (9) has a push rod (21) actuated by an injection valve member (14). Said push rod delimits a control space (25) which is constantly supplied with high-pressure fuel and which can be discharged via a control valve (43) and a discharge canal (29) into a discharge chamber (32). The control valve (43) has a valve member (42, 421, 422) which is actuated by a piezo system (45) whereby the valve member (42, 421, 422) together with the edge of a seat (40) forms a first sealing seat (41, 411, 522) with a flat seat.

Description

Kraftstoffeinspritzvorrichtung für BrennkraftmaschinenFuel injection device for internal combustion engines
Stand der TechnikState of the art
Die Erfindung betrifft eine Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen nach dem Oberbegriff des Anspruchs 1, wie sie aus der DE 196 24 001 AI bekannt ist. Die bekannte Vorrichtung weist ein von einem Piezo betätigbares Ventilglied auf, das in einem Kraftstoffeinspritzventil den Steuerraum zu einem Abflußkanal hin abdichtet oder öffnet.The invention relates to a fuel injection device for internal combustion engines according to the preamble of claim 1, as is known from DE 196 24 001 AI. The known device has a valve element which can be actuated by a piezo and which seals or opens the control chamber to a discharge channel in a fuel injection valve.
Die Abdichtung erfolgt entsprechend der Ausführungsbeispiele entweder über einen am Ventilglied ausgebildeten Kegel- oder über einen Kugelsitz. Aufgrund dieser Bauart entsteht beim Abheben des Ventilgliedes von seinem Ventilsitz am Ventilgehäuse der Effekt, daß der hydraulisch wirksame Sitzdurchmesser des Ventilgliedes größer ist als dessen geometrischer Sitzdurchmesser. Dadurch resultiert, daß zum Abheben des Ventilgliedes von seinem Ventilsitz eine erhöhte Öffnungskraft von dem Piezo aufzubringen ist. Diese erhöhte Öffnungskraft verringert den Hub des Piezos bzw. begrenzt den Einsatzbereich eines vorgeschalteten hydraulischen Kraft-Weg-Übersetzers . Der Effekt des im Verhältnis zum geometrischen Sitzdurchmesser erhöhten hydraulisch wirksamen Sitzdurchmesser des Ventilgliedes bei den angesprochenen Kegel- oder Kugelsitzen läßt sich aus Strömungs- bzw. Drosseleffekten erklären, die entstehen, wenn sich beim Abheben des Ventilgliedes von seinem Ventilsitz zwischen dem Ventilglied und dem Ventilsitz ein Strömungskanal mit einer gewissen Länge ausgebildet, durch den der Kraftstoff vom Steuerraum zum Abflußkanal hindurchströmt. Sobald dasAccording to the exemplary embodiments, the sealing takes place either via a conical seat formed on the valve member or via a ball seat. Because of this design, when the valve member is lifted from its valve seat on the valve housing, the effect arises that the hydraulically effective seat diameter of the valve member is larger than its geometric seat diameter. The result of this is that an increased opening force has to be exerted by the piezo in order to lift the valve member from its valve seat. This increased opening force reduces the stroke of the piezo or limits the area of application of an upstream hydraulic force-displacement translator. The effect of the hydraulically effective seat diameter of the valve member, which is increased in relation to the geometric seat diameter in the case of the cone or ball seats mentioned, can be determined from flow or Explain throttling effects that arise when, when the valve member is lifted from its valve seat, a flow channel with a certain length is formed between the valve member and the valve seat, through which the fuel flows from the control chamber to the drain channel. As soon as that
Ventilglied jedoch einen bestimmten Mindesthub ausgeführt hat, treten die beschriebenen Effekte nicht mehr auf.However, the valve member has executed a certain minimum stroke, the effects described no longer occur.
Eine weitere Problematik betrifft die konstruktive Auslegung des Kraftstoffeinspritzventils, bei der das Ventilglied den Entlastungsraum sowohl zu der mit dem Abflußraum verbundenen Entlastungsleitung, als auch zum Steuerraum abdichtet. Das Ventilglied bildet in diesem Fall, je nach Stellung, zusammen mit dem Ventilgehäuse einen oberen und einen unteren Dichtsitz aus, die beim Stand der Technik jeweils als Kugel- bzw. Kegelsitz ausgebildet sind. Da das Ventilgehäuse aus fertigungstechnischen Gründen im Bereich der beiden Dichtsitze horizontal geteilt ist und das Ventilglied einen auf dem Ventilschaft montierten Schließkörper aufweist, ist eine sehr aufwendige und genaue Herstellung erforderlich, damit auf das Ventilglied beim Wechsel vom einen auf den anderen Dichtsitz keine Querkräfte infolge nicht fluchtender Dichtsitze auftreten, was neben einem erhöhten Verschleiß auch eine erhöhte Geräuschbildung zur Folge hat.Another problem relates to the structural design of the fuel injection valve, in which the valve member seals the relief chamber both to the relief line connected to the discharge chamber and to the control chamber. In this case, depending on the position, the valve member forms, together with the valve housing, an upper and a lower sealing seat, which in the prior art are each designed as a ball or conical seat. Since the valve housing is divided horizontally in the area of the two sealing seats for manufacturing reasons and the valve member has a closing body mounted on the valve stem, a very complex and exact production is necessary so that no lateral forces are not caused on the valve member when changing from one sealing seat to the other aligned sealing seats occur, which in addition to increased wear and tear also results in increased noise.
Vorteile der ErfindungAdvantages of the invention
Die erfindungsgemäße Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit dem kennzeichnenden Merkmal des Anpruchs 1 hat demgegenüber den Vorteil, daß durch den verwendeten Flachsitz beim Abheben des Ventilgliedes von seinem Ventilsitz dessen hydraulisch wirksamer Sitzdurchmesser in der Praxis nur geringfügig größer als der geometrische Sitzdurchmesser des Ventilgliedes ist. Dabei entspricht der hydraulisch wirksame Sitzdurchmesser desto eher dem geometrischen Sitzdurchmesser des Ventilgliedes , desto geringer der Durchmesserunterschied zwischen der von dem Ventilglied verschlossenen Öffnung und dem Durchmesser des Ventilgliedes am Ventilsitz ist, da dann beim Abheben des Ventilgliedes sehr kurze Strömungwege für das Druckmittel am Ventilsitz geschaffen werden, wodurch sich die die unterschiedlich wirksamen Sitzdurchmesser verursachenden Stömungs- bzw. Drosseleffekte verringern. Weiterhin läßt sich ein Flachsitz besonders einfach fertigungstechnisch realisieren, da die Toleranzanforderungen bezüglich der Führung des Ventilgliedes in Bezug auf den Ventilsitz relativ gering sind.The fuel injection device for internal combustion engines according to the invention with the characterizing feature of claim 1 has the advantage that the flat seat used when lifting the valve member from its valve seat whose hydraulically effective seat diameter is in practice only slightly larger than the geometric seat diameter of the valve member. there the hydraulically effective seat diameter corresponds more closely to the geometric seat diameter of the valve member, the smaller the difference in diameter between the opening closed by the valve member and the diameter of the valve member on the valve seat, since very short flow paths for the pressure medium at the valve seat are then created when the valve member is lifted, whereby the flow or throttling effects causing the differently effective seat diameters are reduced. Furthermore, a flat seat can be realized particularly easily in terms of production technology, since the tolerance requirements with regard to the guidance of the valve member with respect to the valve seat are relatively low.
Auch die bereits angesprochene Fertigungsproblematik mit dem geteilten Ventilgehäuse und der auf das Ventilglied einwirkenden Querkräfte wird bei der Ausbildung des Ventilsitzes als Flachsitz vermieden, da dann das Schließglied im wesentlichen nur noch mit einem Dichtsitz ausgerichtet werden muß.The already mentioned manufacturing problems with the divided valve housing and the transverse forces acting on the valve member are avoided when the valve seat is designed as a flat seat, since the closing member then essentially only has to be aligned with a sealing seat.
Weitere vorteilhafte Ausgestaltungen der erfindungsgemäßen KrafStoffeinspritzvorrichtung für Brennkraftmaschinen sind in den Unteransprüchen angegeben.Further advantageous refinements of the fuel injection device according to the invention for internal combustion engines are specified in the subclaims.
Eine vorteilhafte Ausgestaltung ergibt sich, wenn das Ventilglied mit einer umlaufenden, erhöhten Sitzkante am Ventilsitz zusammenwirkt. Diese umlaufende Sitzkante läßt sich fertigungstechnisch relativ einfach mittels einer Schräge realisieren. In der besonders vorteilhaften Ausgestaltung ist der hydraulisch wirksame Sitzdurchmesser des Ventilgliedes nahezu gleich dem geometrischen Sitzdurchmesser, und zwar unabhängig von der Größe bzw. dem Durchmesser des Ventilgliedes in Höhe des Flachsitzes. Weiterhin ist es besonders vorteilhaft, den Flachsitz auf der dem Steuerraum zugewandten Seite des Schließelements auszubilden, da der obere Sitz länger und stärker belastet ist und ein Kegelsitz gegenüber einem Flachsitz dichter und verschleißfester ist.An advantageous embodiment results when the valve member interacts with a peripheral, raised seat edge on the valve seat. This circumferential seat edge can be realized relatively easily in terms of production technology by means of a bevel. In the particularly advantageous embodiment, the hydraulically effective seat diameter of the valve member is almost the same as the geometric seat diameter, regardless of the size or diameter of the valve member at the level of the flat seat. Furthermore, it is particularly advantageous to design the flat seat on the side of the closing element facing the control chamber, since the upper seat is loaded longer and more and a conical seat is denser and more wear-resistant than a flat seat.
Zeichnungdrawing
Ausführungsbeispiele der Erfindung sind in der Zeichnung dargestellt und werden nachfolgend näher erläutert . Es zeigen:Embodiments of the invention are shown in the drawing and are explained in more detail below. Show it:
Figur 1 eine schematische Darstellung einer erfindungsgemäßen Kraftstoffeinspritzvorrichtung mitFigure 1 is a schematic representation of a fuel injection device according to the invention
Versorgung aus einem Hochdruckspeicher und einem von einem Steuerventil gesteuertem Kraftstoffeinspritzventil , Figur 2 ein Kraftstoffeinspritzventil entsprechend dem Ausschnitt A der Figur 1 im Längsschnitt und die Figuren 3 und 4 gegenüber der Figur 2 abgewandelteSupply from a high pressure accumulator and a fuel injection valve controlled by a control valve, FIG. 2 shows a fuel injection valve corresponding to section A of FIG. 1 in longitudinal section and FIGS. 3 and 4 modified compared to FIG. 2
Kraftstoffeinspritzventile ebenfalls im Längsschnitt.Fuel injectors also in longitudinal section.
Beschreibung der AusführungsbeispieleDescription of the embodiments
Eine Kraftstoffeinspritzvorrichtung, mit der mit hohen Einspritzdrücken und geringem Aufwand eine große Variation der Kraftstoffeinspritzung, insbesondere mit sehr exakt steuerbaren Einspritzzeitpunkten und Einspritzmengen möglich ist, wird durch ein sogenanntes Common-Rail-System verwirklicht. Dieses stellt eine andere Art von Kraftstoffhochdruckquelle zur Verfügung, als es durch die übliche Kraftstoffhochdruckeinspritzpumpe gegeben ist. Dabei ist jedoch die Erfindung sowohl bei diesem sogenannten Common-Rail -System, als auch bei einer Kraftstoffeinspritzpumpe verwendbar. Dem Common-Rail -System ist dabei jedoch der Vorzug zu geben.A so-called common rail system realizes a fuel injection device with which a large variation of the fuel injection is possible with high injection pressures and little effort, in particular with very precisely controllable injection times and injection quantities. This provides a different type of high-pressure fuel source than is provided by the conventional high-pressure fuel injection pump. However, the invention is in this so-called common rail system as well as in one Fuel injection pump can be used. However, preference is given to the common rail system.
In der Figur 1 ist bezüglich eines Common-Rail -Systems als Kraftstoffhochdruckquelle ein Kraftstoffhochdruckspeicher 1 vorgesehen, der von einer Kraftstoffhochdruckförderpumpe 2 aus einem Kraftstoffvorratsbehälter 4 mit Kraftstoff versorgt wird. Der Druck in dem Kraftstoffhochdruckspeicher 1 wird durch ein Drucksteuerventil 5 in Verbindung mit einem Drucksensor 6 über eine elektrische Steuereinrichtung 8 gesteuert. Diese steuert auch ein Kraftstoffeinspritzventil 9.In FIG. 1, a high-pressure fuel reservoir 1 is provided with respect to a common rail system as a high-pressure fuel source, which is supplied with fuel by a high-pressure fuel delivery pump 2 from a fuel reservoir 4. The pressure in the high-pressure fuel accumulator 1 is controlled by a pressure control valve 5 in conjunction with a pressure sensor 6 via an electrical control device 8. This also controls a fuel injection valve 9.
Das Kraftstoffeinspritzventil 9 weist ein Ventilgehäuse 11 auf, das an seinem einen Ende, das zum Einbau an derThe fuel injection valve 9 has a valve housing 11, which at one end, which is for installation on the
Brennkraftmaschine bestimmt ist, Einspritzöffnungen 12 besitzt, deren Austritt aus dem Inneren desInternal combustion engine is determined, has injection openings 12, the outlet of which from the inside of the
Kraftstoffeinspritzventils 9 durch ein Einspritzventilglied 14 gesteuert wird. Dieses ist im ausgeführten Beispiel als langgestreckte Ventilnadel ausgeführt, die an ihrem einen Ende eine Dichtfläche 15 besitzt, die mit einem innenliegenden Ventilsitz zusammenwirkt. Die Ventilnadel befindet sich innerhalb eines durch eine Druckleitung 17 mit dem Kraftstoffhochdruckspeicher 1 verbundenen Druckraumes 16 innerhalb des Ventilgehäuses 11. In einem im Durchmesser vergrößerten Teils des Druckraumes 16 ist eine Druckfeder 19 angeordnet, die zwischen einem Ventilteller 20 und dem Ventilgehäuse 11 axial eingespannt ist und das Einspritzventilglied 14 in Schließrichtung beaufschlagt. Koaxial zur Druckfeder 19 ist ein Stößel 21 vorgesehen, der einerseits am Ventilteller 20 anliegt und andererseits in eine Führungbohrung 22 eintaucht und dort mit seiner Stirnseite 23, die eine bewegliche Wand bildet, einen Steuerraum 25 mit dem geschlossenen Ende der Führungsbohrung 22 einschließt. In diesen Steuerraum 25 mündet ein Zuflußkanal 26, in dem eine Zulaufdrossel 27 angeordnet ist, und der vom Druckraum 16 ausgehend immer Kraftstoff unter Hochdruck über die Zulaufdrossel 27 in den Steuerraum 25 liefert .Fuel injection valve 9 is controlled by an injection valve member 14. In the example shown, this is designed as an elongated valve needle which has a sealing surface 15 at one end, which cooperates with an internal valve seat. The valve needle is located within a pressure chamber 16 connected to the high-pressure fuel reservoir 1 by a pressure line 17 within the valve housing 11. In a part of the pressure chamber 16 which is enlarged in diameter, a compression spring 19 is arranged, which is clamped axially between a valve plate 20 and the valve housing 11 and the injection valve member 14 acts in the closing direction. A plunger 21 is provided coaxially to the compression spring 19, which rests on the one hand on the valve plate 20 and on the other hand dips into a guide bore 22 and there encloses a control chamber 25 with the closed end of the guide bore 22 with its end face 23, which forms a movable wall. In this control room 25 opens Inflow channel 26, in which an inlet throttle 27 is arranged, and which, starting from the pressure chamber 16, always delivers fuel under high pressure via the inlet throttle 27 into the control chamber 25.
Vom Steuerraum 25 führt koaxial zum Stößel 21 von der diesem gegenüberliegenden Stirnseite ein Abflußkanal 29 mit einer darin angeordneten Abflußdrossel 28 ab, der in einen Entlastungsraum 30 innerhalb des Ventilgehäuses 11 mündet. Der Entlastungsraum 30 führt über eine weiterführendeFrom the control chamber 25 leads coaxially to the plunger 21 from the end face opposite this, a discharge channel 29 with a discharge throttle 28 arranged therein, which opens into a relief chamber 30 within the valve housing 11. The relief space 30 leads over a further
Entlastungsleitung 31 zu einem aufnahmefähigen Abflußraum 32, der zum Beispiel auch der Kraftstoffvorratsbehälter 4 sein kann.Relief line 31 to a receivable drainage space 32, which can also be the fuel reservoir 4, for example.
Wie am besten aus der Figur 2 ersichtlich ist, weist der Entlastungsraum 30 einen oberen Bereich 33 und einen dem Steuerraum 25 zugewandten unteren Bereich 34 auf. Von dem im Verhältnis zum unteren Bereich 34 im Durchmesser kleineren oberen Bereich 33 zweigt seitlich, auf der dem Zulaufkanal 26 gegenüberliegenden Seite, die Entlastungsleitung 31 ab.As can best be seen from FIG. 2, the relief chamber 30 has an upper region 33 and a lower region 34 facing the control chamber 25. The relief line 31 branches off from the upper area 33, which is smaller in diameter in relation to the lower area 34, on the side opposite the inlet channel 26.
In den unteren Bereich 34 ragt eine umlaufende Erhebung bzw. ein Steg 35 hinein, dessen Innenwand 36 als Verlängerung der Bohrungswand 37 des oberen Bereichs 33 ausgebildet ist. Auf der der Innenwand 36 abgewandten Seite weist der Steg 35 eine Schräge 39 auf, so daß der Steg 35 in dem in der Figur 2 dargestellten Längsschnitt dreiecksförmig ausgebildet ist.A circumferential elevation or a web 35 projects into the lower region 34, the inner wall 36 of which is designed as an extension of the bore wall 37 of the upper region 33. On the side facing away from the inner wall 36, the web 35 has a slope 39, so that the web 35 is triangular in the longitudinal section shown in FIG.
Die dem Abflußkanal 29 zugewandte Stirnseite des Steges 35 bildet eine umlaufende Sitzkante 40 aus, die, wenn sie mit einem Ventilglied 42 zusammenwirkt, einen ersten Dichtsitz 41 bildet. Das Ventilglied 42 ist Bestandteil eines Steuerventils 43, wobei das Ventilglied 42 durch einen Piezo 45 in Schließstellung bzw. Öffnungsstellung gebracht werden kann. Das Ventilglied 42 hat einen Ventilschaft 46 und ein sich an das eine Ende des Ventilschaftes 46 anschließendes, mit der Sitzkante 40 zusammenwirkendes Schließelement 47. Der Ventilschaft 46 ist im oberen Bereich 33 des Entlastungsraums 30 mit radialem Spiel angeordnet. DasThe end face of the web 35 facing the drain channel 29 forms a peripheral seat edge 40 which, when it interacts with a valve member 42, forms a first sealing seat 41. The valve member 42 is part of a control valve 43, the valve member 42 being able to be brought into the closed or open position by a piezo 45. The valve member 42 has a valve stem 46 and a closing element 47 which adjoins one end of the valve stem 46 and cooperates with the seat edge 40. The valve stem 46 is arranged in the upper region 33 of the relief chamber 30 with radial play. The
Schließelement 47 ist halbkugel- bzw. kugelabschnittsförmig ausgebildet, mit einer der Sitzkante 40 zugewandten ebenen Sitzfläche 48, an die sich auch der Ventilschaft 46 anschließt. Der erste Dichtsitz 41 ist somit von der Sitzfläche 48 und der Sitzkante 40 als Flachsitz ausgebildet, wobei die Sitzfläche 48 des Schließelements 47 die Sitzkante 40 im Durchmesser überragt.Closing element 47 is hemispherical or spherical section-shaped, with a flat seat surface 48 facing the seat edge 40, to which the valve stem 46 is also connected. The first sealing seat 41 is thus formed as a flat seat by the seat surface 48 and the seat edge 40, the seat surface 48 of the closing element 47 projecting beyond the seat edge 40 in diameter.
Die gewölbte, der Sitzfläche 48 abgewandte Fläche 49 des Schließelements 47 bildet zusammen mit einer der Fläche 49 zumindest teilweise formschlüssig angepaßten Sitzfläche 51 im Mündungsbereich des Abflußkanals 29 in dem unteren Bereich 34 des Entlastungsraums 30 einen Kugelsitz als zweiten Dichtsitz 52 aus.The curved surface 49 of the closing element 47 facing away from the seat surface 48, together with a seat surface 51 which is at least partially form-fittingly adapted to the surface 49, forms a spherical seat as a second sealing seat 52 in the lower region 34 of the relief chamber 30 in the mouth region of the discharge channel 30.
Die oben beschriebene Kraftstoffeinspritzvorrichtung arbeitet wie folgt: Durch die vorzugsweise synchron zur Brennkraftmaschine angetriebene Kraftstoffhochdruckförderpumpe 2 wird Kraftstoff aus dem Kraftstoffvorratsbehälter 4 in denThe fuel injection device described above works as follows: The fuel high-pressure feed pump 2, which is preferably driven synchronously with the internal combustion engine, transfers fuel from the fuel tank 4 into the fuel tank 4
Kraftstoffhochdruckspeicher 1 gefördert, dessen Druck über das Drucksteuerventil 5 in Verbindung mit dem Drucksensor 6 auf einen vorzugsweise konstanten Wert eingestellt wird. Dieser Wert kann bei Bedarf auch geändert werden. Der aus dem Kraftstoffhochdruckspeicher 1 zur Verfügung stehendeHigh-pressure fuel accumulator 1 is conveyed, the pressure of which is set to a preferably constant value via the pressure control valve 5 in conjunction with the pressure sensor 6. This value can also be changed if necessary. The one available from the high-pressure fuel reservoir 1
Kraftstoff versorgt mehrere Kraftstoffeinspritzventile 9 der beschriebenen Bauart .Fuel supplies several fuel injection valves 9 of the type described.
So lange das Ventilglied 42 des Steuerventils 43 in der gezeigten Schließstellung ist, wird aufgrund des über die Druckleitung 17 zugeführten Kraftstoffs auch im Steuerraum 25 ein relativ hoher Druck eingehalten, der über die bewegliche Wand 23 das Einspritzventilglied 14 zusätzlich zur Druckfeder 19 mit einer Schließkraft beaufschlagt, so daß das Einspritzventilglied 14 in Schließstellung gebracht wird und in dieser Stellung bleibt. Wird das Steuerventil 43 jedoch geöffnet, kann der Steuerraum 25 über den Abflußkanal 29, den Entlastungsraum 30 und die Entlastungsleitung 31 zum Abflußraum 32 hin entlastet werden.As long as the valve member 42 of the control valve 43 is in the closed position shown, is due to the Pressure line 17 supplied fuel also maintained a relatively high pressure in the control chamber 25, which acts on the injection valve member 14 in addition to the compression spring 19 with a closing force via the movable wall 23, so that the injection valve member 14 is brought into the closed position and remains in this position. However, if the control valve 43 is opened, the control chamber 25 can be relieved via the drain channel 29, the relief chamber 30 and the relief line 31 to the drain chamber 32.
Wesentlich dabei ist, daß aufgrund der Ausbildung des ersten Dichtsitzes 41 als Flachsitz beim Abheben des Schließelements 47 von der Sitzkante 40 nur ein sehr kurzer Strömungsweg für den Kraftstoff von dem unteren Bereich 34 in den oberen Bereich 33 des Entlastungsraums 30 entsteht. Somit treten nur sehr geringe, die Öffnungskraft des Piezos 45 erhöhende Strömungseffekte auf. Durch die besondere Ausbildung der Sitzkante 40 an dem erhöhten Steg 35 wird zusätzlich der Effekt der Durchmesserunterschiede zwischen dem Schließelement 47 im Bereich der Sitzfläche 48 und dem oberen Bereich 33 reduziert, was auf die erforderliche Öffnungskraft des Piezos 45 einen zusätzlichen positiven Effekt bewirkt .It is essential that due to the design of the first sealing seat 41 as a flat seat when the closing element 47 is lifted from the seat edge 40, only a very short flow path for the fuel from the lower region 34 into the upper region 33 of the relief chamber 30 is created. Thus, there are only very small flow effects which increase the opening force of the piezo 45. The special design of the seat edge 40 on the raised web 35 additionally reduces the effect of the diameter differences between the closing element 47 in the region of the seat surface 48 and the upper region 33, which has an additional positive effect on the required opening force of the piezo 45.
Aufgrund des im Steuerraum 25 sinkenden Druckes reicht die Schließkraft der Druckfeder 19 beim Abheben des Schließelements 47 von der Sitzkante 40 nicht mehr aus, das Einspritzventilglied 14 gegen den an einer Druckfläche 53 des Ventilgliedes 42 angreifenden Kraftstoffhochdruck in Schließstellung zu halten, so daß das Einspritzventilglied 14 in Offenstellung geht. Dies bewirkt im beschriebenen Ausführungsbeispiel, bei dem das Ventilglied 42 einen zweiten Dichtsitz 52 ausbildet, einen ersten Einspritzvorgang, Voreinspritzung genannt. Wenn das Ventilglied 42 seinen vollen Hubweg durchlaufen hat, bildet die Fläche 49 des Schließelements 47 mit der Sitzfläche 51 den zweiten Dichtsitz 52 aus, womit die Voreinspritzung dadurch beendet wird, daß im Steuerraum 25 wieder der ursprüngliche, hohe Kraftstoffdruck herrscht, da kein Kraftstoff zum Ablaufräum 32 hin abströmen kann.Due to the falling pressure in the control chamber 25, the closing force of the compression spring 19 when the closing element 47 is lifted from the seat edge 40 is no longer sufficient to hold the injection valve member 14 in the closed position against the high fuel pressure acting on a pressure surface 53 of the valve member 42, so that the injection valve member 14 goes into open position. In the exemplary embodiment described, in which the valve member 42 forms a second sealing seat 52, this causes a first injection process, referred to as pre-injection. When the valve member 42 has passed its full stroke, forms the surface 49 of the closing element 47 with the seat surface 51 from the second sealing seat 52, with which the pre-injection is ended in that the original high fuel pressure prevails again in the control chamber 25, since no fuel can flow out to the outlet chamber 32.
Wird das Ventilglied 42 nunmehr wieder in Richtung des ersten Dichtsitzes 41 bewegt, wird ein zweiter Einspritzvorgang, Haupteinspritzung genannt, ausgelöst. Diese Auslösung erfolgt in Analogie zum erstenIf the valve member 42 is now moved again in the direction of the first sealing seat 41, a second injection process, called the main injection, is triggered. This triggering takes place in analogy to the first
Einspritzvorgang durch Druckabsenkung im Steuerraum 25 infolge Abströmens von Kraftstoff in den Abflußraum 32. Die Haupteinspritzung wird beendet, sobald das Ventilglied 42 mit seiner Sitzfläche 48 unter Bildung des ersten Dichtsitzes 41 wieder auf der Sitzkante 40 aufliegt. In diesem Moment sperrt des Schließelement 47 den oberen Bereich 33 zum unteren Bereich 34 im Entlastungsraum 30 hin ab, so daß im Steuerraum 25 sofort wieder der hohe Kraftstoffdruck entsteht, der dann das Einspritzventilglied 14 wieder in Schließstellung bringt.Injection process by lowering the pressure in the control chamber 25 as a result of fuel flowing out into the drain chamber 32. The main injection is ended as soon as the valve member 42 rests on the seat edge 40 with its seat 48, forming the first sealing seat 41. At this moment, the closing element 47 shuts off the upper region 33 to the lower region 34 in the relief chamber 30, so that the high fuel pressure is generated again in the control chamber 25, which then brings the injection valve member 14 back into the closed position.
Das Ausführungsbeispiel gemäß der Figur 3 zeigt den in der Praxis aus Fertiguungsgründen realisierten mehrteiligen Aufbau des Ventilgehäuses mit einem unteren Ventilgehäuseteil 111 und einem oberen VentilgehäuseteilThe embodiment according to FIG. 3 shows the multi-part construction of the valve housing with a lower valve housing part 111 and an upper valve housing part
112. Ferner sind der Ventilschaft 461 und das Schließelement 471 als separate, miteinander verbundenen Bauteile ausgebildet, die zusammen das Ventilglied 421 bilden. Weiterhin wird auf den Steg 35 verzichtet, so daß die Auflagefläche am ersten Dichtsitz 411 vergrößert ist.112. Furthermore, the valve stem 461 and the closing element 471 are designed as separate, interconnected components which together form the valve member 421. Furthermore, the web 35 is dispensed with, so that the contact surface on the first sealing seat 411 is enlarged.
In der Figur 4 ist das Schließelement 472 des Ventilgliedes 422 gegenüber der Figur 3 um 180 Grad verdreht. Dadurch wird am oberen, ersten Dichtsitz 412 ein Kegelsitz ausgebildet und am unteren, zweiten Dichtsitz 522 der Flachsitz. Da der obere Dichtsitz 412 im Betrieb desIn FIG. 4, the closing element 472 of the valve member 422 is rotated by 180 degrees with respect to FIG. 3. As a result, a conical seat is formed on the upper, first sealing seat 412 and the flat seat on the lower, second sealing seat 522. Since the upper sealing seat 412 in the operation of the
Kraftstoffeinspritzventils länger und stärker belastet wird als der untere Dichtsitz 522 ergeben sich mit dem Kegelsitz Vorteile bezüglich der Verschleißfestigkeit und der Leckverluste.If the fuel injection valve is loaded longer and more heavily than the lower sealing seat 522, the conical seat offers advantages in terms of wear resistance and leakage losses.
Ergänzend wird erwähnt, daß die Erfindung selbstverständlich nicht auf die beschriebenen Ausführungsbeispiele begrenzt sein soll, sondern daß vielmehr auch Elemente aus den einzelnen Ausführungsbeispielen miteinander vertauscht werden können. In addition, it is mentioned that the invention should of course not be limited to the exemplary embodiments described, but rather that elements from the individual exemplary embodiments can also be interchanged.

Claims

Ansprüche Expectations
1. Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen mit einer Kraftstoffhochdruckquelle (1), aus der ein1. Fuel injection device for internal combustion engines with a high-pressure fuel source (1) from which a
Kraftstoffeinspritzventil (9) mit Kraftstoff versorgt wird, das ein Einspritzventilglied (14) zur Steuerung von wenigstens einer Einspritzöffnung (12) und einen Steuerraum (25) aufweist, der von einer beweglichen Wand (23), die mit dem Einspritzventilglied (14) wenigstens mittelbar verbunden ist, begrenzt wird, und der einen mittels einer ersten Drossel (27) dimensionierten, von einer Hochdruckquelle, vorzugsweise von der Kraftstoffhochdruckquelle (1) kommenden Zuflußkanal (26) und einen Abflußkanal (29) mit definiertem maximalem Abflußquerschnitt zu einem Entlastungsraum (30) aufweist, wobei der Abfluß von Kraftstoff aus dem Steuerraum (25) in einen Abflußbehälter (32) mittels eines einen Ventilsitz (41, 411, 522) aufweisenden Ventilgliedes (42, 421, 422), das Bestandteil eines von einem Piezo (45) betätigbaren Steuerventils (43) ist, sperrbar ist, dadurch gekennzeichnet, daß der Ventilsitz (41, 411, 522) als Flachsitz ausgebildet ist.Fuel injection valve (9) is supplied with fuel, which has an injection valve member (14) for controlling at least one injection opening (12) and a control chamber (25) which is at least indirectly connected to a movable wall (23) which is connected to the injection valve member (14) is connected, is limited, and the one by means of a first throttle (27), coming from a high-pressure source, preferably from the high-pressure fuel source (1), inflow channel (26) and an outflow channel (29) with a defined maximum outflow cross-section to a relief chamber (30) The outflow of fuel from the control chamber (25) into an outflow tank (32) by means of a valve member (42, 421, 522) having a valve member (42, 421, 422) which is part of a piezo (45) actuable Control valve (43) is lockable, characterized in that the valve seat (41, 411, 522) is designed as a flat seat.
2. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß der Flachsitz gebildet ist von einer ebenen Fläche (48) des Ventilgliedes (42, 421, 422) und einer Wand im Übergangsbereich zwischen einem dem Steuerraum (25) zugewandten ersten Bereich (34) des Entlastungsraums (30) und einem dem Steuerraum (25) abgewandten zweiten Bereich (33) des Entlastungsraums (30) .2. Fuel injection device according to claim 1, characterized in that the flat seat is formed by a flat surface (48) of the valve member (42, 421, 422) and a wall in the transition area between a control area (25) facing the first area (34) of relief chamber (30) and a second region (33) of the relief chamber (30) facing away from the control chamber (25).
3. Kraftstoffeinspritzvorrichtung nach Anspruch 2, dadurch gekennzeichnet, daß die Wand als eine in den ersten Bereich3. Fuel injection device according to claim 2, characterized in that the wall as one in the first area
(34) des Entlastungsraums (30) hineinragende, umlaufende Sitzkante (40) ausgebildet ist.(34) of the relief space (30) protruding, circumferential seat edge (40) is formed.
4. Kraftstoffeinspritzvorrichtung nach Anspruch 3, dadurch gekennzeichnet, daß die Sitzkante (40) an einem Steg (35) ausgebildet ist.4. Fuel injection device according to claim 3, characterized in that the seat edge (40) is formed on a web (35).
5. Kraftstoffeinspritzvorrichtung nach Anspruch 4, dadurch gekennzeichnet, daß der Steg (35) eine Schräge (39) aufweist.5. Fuel injection device according to claim 4, characterized in that the web (35) has a slope (39).
6. Kraftstoffeinspritzvorrichtung nach einem der Ansprüche 1 bis 5, dadurch gekennzeichnet, daß das Ventilglied (42, 421, 422) ein halbkugel- oder kugelabschnittstörmiges Schließglied (47, 471, 472) aufweist.6. Fuel injection device according to one of claims 1 to 5, characterized in that the valve member (42, 421, 422) has a hemispherical or spherical segment-shaped closing member (47, 471, 472).
7. Kraftstoffeinspritzvorrichtung nach Anspruch 6, dadurch gekennzeichnet, daß die dem Ventilsitz (41, 411) abgewandte Fläche (49) des Schließgliedes (47, 471) im Übergangsbereich zwischen dem Abflußkanal (29) und dem Entlastungsraum (30) einen zusätzlichen Ventilsitz (52) ausbildet.7. Fuel injection device according to claim 6, characterized in that the valve seat (41, 411) facing away from the surface (49) of the closing member (47, 471) in the transition region between the drain channel (29) and the relief chamber (30) an additional valve seat (52 ) trains.
8. Kraftstoffeinspritzvorrichtung nach Anspruch 1, dadurch gekennzeichnet, daß das Ventilglied (422) ein halbkugel- oder kugelabschnittsförmiges Schließglied (472) aufweist, daß der als Flachsitz ausgebildete Ventilsitz (522) im Übergangsbereich zwischen dem Abflußkanal (29) und dem Entlastungsraum (30) angeordnet ist und daß die dem Ventilsitz (522) abgewandte Fläche des Schließgliedes (472) im Übergangsbereich von einem ersten Bereich (34) zu einem zweiten Bereich (33) des Entlastungsraumes (30), welcher mit dem Abflußbehälter (32) gekoppelt ist, einen zusätzlichen Ventilsitz (412) ausbildet.8. Fuel injection device according to claim 1, characterized in that the valve member (422) has a hemispherical or spherical segment-shaped closing member (472) that the valve seat (522) designed as a flat seat in the transition region between the drain channel (29) and the relief chamber (30) is arranged and that the surface of the closing member (472) facing away from the valve seat (522) in the transition region from a first region (34) to one second region (33) of the relief chamber (30), which is coupled to the drain tank (32), forms an additional valve seat (412).
9. Kraftstoffeinspritzvorrichtung nach Anspruch 8, dadurch gekennzeichnet, daß der zusätzliche Ventilsitz (412) ein Kegelsitz ist.9. Fuel injection device according to claim 8, characterized in that the additional valve seat (412) is a conical seat.
10. Kraftstoffeinspritzvorrichtung nach einem der Ansprüche 6 bis 9, dadurch gekennzeichnet, daß das Ventilglied (421, 422) aus einem Ventilschaft (461) und dem mit dem Ventilschaft (461) verbundenen Schließglied (471, 472) besteht . 10. Fuel injection device according to one of claims 6 to 9, characterized in that the valve member (421, 422) consists of a valve stem (461) and the closing member (471, 472) connected to the valve stem (461).
EP00958258A 1999-08-20 2000-08-17 Fuel injection device for fuel internal combustion engines Withdrawn EP1210513A1 (en)

Applications Claiming Priority (3)

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DE19939450A DE19939450A1 (en) 1999-08-20 1999-08-20 Fuel injection device for internal combustion engines
DE19939450 1999-08-20
PCT/DE2000/002782 WO2001014721A1 (en) 1999-08-20 2000-08-17 Fuel injection device for fuel internal combustion engines

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DE10122245A1 (en) * 2001-05-08 2002-12-12 Bosch Gmbh Robert Leakage-reduced pressure-controlled fuel injector
DE102004021652A1 (en) 2004-05-03 2005-12-01 Siemens Ag Method for producing an injector
EP1836385B1 (en) * 2004-12-03 2010-12-29 Ganser-Hydromag AG Fuel injection valve with pressure gain
KR101314991B1 (en) 2012-01-25 2013-10-04 홍종한 Piezo injector for vehicle

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IT220660Z2 (en) * 1990-10-31 1993-10-08 Elasis Sistema Ricerca Fiat IMPROVEMENTS IN THE HIGH PRESSURE SHUTTER SYSTEM IN A PILOT VALVE OF AN ELECTROMAGNETIC INJECTOR FOR FUEL INJECTION SYSTEMS OF INTERNAL COMBUSTION ENGINES
DE4406901C2 (en) * 1994-03-03 1998-03-19 Daimler Benz Ag Solenoid valve controlled injector for an internal combustion engine
DE19624001A1 (en) * 1996-06-15 1997-12-18 Bosch Gmbh Robert Fuel injection device for internal combustion engines
JP3719468B2 (en) * 1996-09-02 2005-11-24 株式会社デンソー Accumulated fuel injection system
DE29723706U1 (en) * 1997-04-26 1999-06-10 Dualon International S A Hydraulic servo control
EP0976924B1 (en) * 1998-07-31 2003-09-17 Siemens Aktiengesellschaft Injector with a servo valve

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Title
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