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EP0845077B1 - Fuel injection device for internal combustion engines - Google Patents

Fuel injection device for internal combustion engines Download PDF

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Publication number
EP0845077B1
EP0845077B1 EP97906987A EP97906987A EP0845077B1 EP 0845077 B1 EP0845077 B1 EP 0845077B1 EP 97906987 A EP97906987 A EP 97906987A EP 97906987 A EP97906987 A EP 97906987A EP 0845077 B1 EP0845077 B1 EP 0845077B1
Authority
EP
European Patent Office
Prior art keywords
valve
valve seat
fuel injection
valve member
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.)
Expired - Lifetime
Application number
EP97906987A
Other languages
German (de)
French (fr)
Other versions
EP0845077A1 (en
Inventor
Roger Potschin
Friedrich Boecking
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 EP0845077A1 publication Critical patent/EP0845077A1/en
Application granted granted Critical
Publication of EP0845077B1 publication Critical patent/EP0845077B1/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-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
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0035Poppet valves, i.e. having a mushroom-shaped valve member that moves perpendicularly to the plane of the valve seat
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02Fuel-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
    • F02M47/027Electrically actuated valves draining the chamber to release the closing pressure
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0014Valves characterised by the valve actuating means
    • F02M63/0015Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • FMECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02MSUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00Other 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
    • F02M63/0012Valves
    • F02M63/0031Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0033Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat
    • F02M63/0036Lift valves, i.e. having a valve member that moves perpendicularly to the plane of the valve seat with spherical or partly spherical shaped valve member ends

Definitions

  • the invention relates to a fuel injection device for internal combustion engines according to the preamble of the patent claim 1 off.
  • Fuel injection device of this type opens out from Control room coming drain channel into a collection room, the via a further relief line with a Relief room is connected.
  • the valve seat for the valve member is in this collecting space of the control valve provided.
  • This has a drive Piezo on and is as a valve member with a conical Sealing surface executed.
  • This valve fulfills the function of controlling the pressure in the control room, taking into account is that a piezo, in order to be able to work reliably, only pressurized.
  • EP 0 741 244 A (prior art according to Art. 54 (3) EPC) is a Fuel injector disclosed, wherein the closing force required for tight closing of the control valve is required, not from the piezo needs to be applied, but from the pressure in the control room is produced. A high positioning force to be applied by the piezo is only required for opening the valve, here again the piezo from the set pressure in the control room Pressure is applied. Once the valve has opened, becomes the actuating movement or the opening of the control valve counteracting force quickly dissipated, so that also in in this case the piezo does not experience any significant stress.
  • the invention provides according to claim 1 of that two valve seats in series with each other in the course of Outflow to relieve pressure in the control room via the Drain channel are provided.
  • the actuator moves Valve member in the direction of the control room is the one with the Valve member and the first valve seat formed valve opened and subsequently that of the valve member with the second valve seat formed valve closed. If that Valve element on the first valve seat with its sealing surface pressure is built up in the control room in the sense closing the fuel injector. Should that Sinspritzventil come in the open position, so lifts to one Actuation of the piezo towards the valve member from the first Valve seat from. It can according to claim 2 in one Intermediate position remain in the on both valve seats the flow cross-section is open.
  • valve seat on an elastically deformable intermediate part educated This has the advantage that the required working capacity of the piezo to drive the Valve member of the control valve can be kept even lower can.
  • the valve member of the control valve comes after the Open the cross-section at the first valve seat in the system the second valve seat is on the elastically deformable In between a differential pressure.
  • On the control room opposite side is a pressure relief to Relief room forward while closed Cross section on the second valve seat in the control room the high There is pressure.
  • FIG. 1 shows a schematic Representation of a fuel injection device with Supply from a high pressure accumulator and one from one Control valve controlled fuel injector known Type
  • Figure 2 is a partial section through a known Fuel injector accordingly the section A of Figure 1 showing the control room and one in a piezo not shown driven valve member of the control valve
  • Figure 3 shows a first Embodiment of the invention with a Control valve that has a first and a second valve seat has a modified form of leadership of the Drain channel
  • Figure 4 the injector stroke based on the Adjustment stroke of the control valve member
  • Figure 5 a second Embodiment modified from the embodiment according to Figure 3 with a second valve seat on a elastically deformable intermediate part is formed in one first position of the valve member of the control valve on the first Valve seat
  • Figure 6 is a representation of the control valve with in Close position on the second valve seat Valve member in a modified form, with according to Figure 5 provided
  • a fuel injector with the high Injection pressures and little effort a large variation fuel injection, especially with very precise controllable injection times and injection quantities possible is through a so-called common rail system realized.
  • the invention is both in this so-called Common rail system as well at one Fuel injection pump can be used.
  • the common rail system preference is to be given.
  • Figure 1 is related to a common rail pressure supply system as a high-pressure fuel source High-pressure fuel reservoir 1 provided by a High-pressure fuel delivery pump 2 from one Fuel tank 4 is supplied with fuel.
  • the pressure in the high-pressure fuel accumulator 1 is determined by a pressure control valve 5 in connection with a pressure sensor 6 controlled by an electrical control device 8. This also controls a fuel injection valve 9.
  • This is in the executed example as an elongated valve needle executed that at one end a sealing surface 15th owns that with an internal valve seat interacts.
  • the valve needle is inside a through a pressure line 17 with the High-pressure fuel accumulator 1 connected pressure chamber 16 inside the valve body.
  • a compression spring 19 arranged between a valve plate 20 and the Valve housing is clamped axially and that Injection valve member 14 is applied in the closing direction.
  • a plunger 21 is provided coaxially with the compression spring on the one hand rests on the valve plate 20 and on the other hand in a guide bore 22 dips and there with his End face 23, which forms a movable wall, a Control room 25 with the closed end of the guide bore includes.
  • An inflow channel 26 opens into this control chamber, in which a throttle 27 is arranged and that of the pressure chamber 16 always fuel under high pressure via the Throttle 27 in the control chamber 25 supplies.
  • the confluence of the drain channel 29 in the relief chamber 30 is in this known injection valve by a Valve member 34 of a control valve 36, which acts as a seat valve is formed, controlled, this valve member by a piezo 35 in the closed position or in the open position can be brought.
  • the known fuel injection device works here as follows:
  • FIG. 2 A section of FIG. 2 is shown a fuel injection valve that shown in Figure 1 shown basic type, wherein the figure 2 a Section A on this fuel injector corresponds.
  • the end face 23 is again there as a movable wall on the plunger 21 enclosing the control chamber 25 educated.
  • the control room opens on the side Circumferential wall of the guide bore 22 of the inflow channel 26 with the Throttle 27, such that the inflow through the plunger in each of his positions is not locked.
  • the guide bore 22 leads through a recess 38 in this end face 37 of the drain channel 129.
  • a valve member 44 acts here with the valve seat 39 opposite the valve member 34 of the control valve 36 from Figure 1 modified form together.
  • An introduction of the inflow channel 26 in one part of the Residual space-forming annular recess 28 offers the main advantage that the one shown in Figure 10 Inflow channel 726 introduced obliquely to the axis of the plunger 721 can be, starting from one of the pressure supply of the Pressure chamber 16 serving bore 59, which is parallel to the axis of the injection valve is guided. Will the injector body at the transition to relief chamber 30 (FIG. 1) separated, then the inflow channel 726, from the mouth 61 of the parallel bore 59 of this Partition plane 60 drilled obliquely to the residual space 738 become.
  • the drain channel can be used according to FIG 229 also lead away from the control room 25.
  • Figure 3 also shows the advantageous Embodiment of the invention, which is that here analogous to Figure 2 provided valve seat now a first Is valve seat 139, on which the space 40 in turn adjoins, of which the drain channel 229 then via a leads second throttle 142 to the relief chamber. additionally this first valve seat 139 is now a second one Valve seat 49 is provided, which is coaxial with the first valve seat 139 opposite to the side of the control room 25 is arranged.
  • the drain channel 229 has in one Intermediate area on a valve space 50, in which the for example spherical head 146 of the Valve member 144 can immerse.
  • the first is for a spherical head Sealing surface 147 to the side of the first valve seat 39 trained and this a second Sealing surface 152 realized in continuation of the spherical shape.
  • This second sealing surface is when the Valve member 144 for abutting the second valve seat 49 brought and in this position closes the valve member 144 after opening the drainage channel in the meantime 229 this again.
  • Relief of the control room 25 such that the Injector member can open briefly.
  • FIG. 4 shows the stroke profile of the injection valve member 14 and assigned to the Stroke course of the valve member 144 of the control valve over the Time.
  • Diagram shows that from the starting position with the stroke 0 the valve member 144 covers a stroke over which the Pre-injection takes place. At the stroke he is Pre-injection ended and also the largest displacement of the Valve member 144 reached.
  • valve member 144 After persistence over time SU in this end position, the Valve member 144 in an intermediate cell ZS, in which the Cross sections opened on both valve seats 139 and 49 are for performing the main injection HE and then the final return to the first Valve seat 139.
  • the valve seats are located 139 and 49 preferably coaxial one behind the other and coaxial to the valve lifter of valve member 144. On both Valve seats each become a seat valve in this way realized.
  • second valve seat as valve seat 349 on an elastic deformable intermediate part 55 is arranged.
  • This one has for example the shape of a disc, which is preferably made of There is metal and between two halves of the valve housing 11 is tightly clamped. It points coaxially to the plunger 21 or to the valve member 244 on a through hole 56 connects the valve chamber 150 to the control chamber 125.
  • the Entry of the through hole 56 in the valve chamber 150 is formed as a second valve seat 349 on which the second Sealing surface 352 of the valve member 344 in its maximum deflected position comes close to the system.
  • the head 346 of the valve member 344 carries a first sealing surface 347 Conical surface and as a second sealing surface 352 a spherical Surface, in a modification of the exemplary embodiment according to FIG. 3. But it could also be a configuration of the head 46 of Figure 2 apply here.
  • On the control room side 125 points out the elastically deformable intermediate part annular, concentric to the through hole 56 Recess 57 with which it is achieved that the elastic deformable intermediate part starting at this annular Recess 57; especially upwards to valve member 344 can be deflected more easily. This property leaves but also through different kinds of reductions in the strength of the Achieve intermediate.
  • one above the other lying diagram parts above is the lifting movement of the Injection valve member 14 reproduced, again with the Area of the pre-injection VE, the injection break SU and the Main injection HE.
  • curve M the movement of the elastic intermediate part played.
  • a starting position hm0 is referred to the travel of the valve member 444 the intermediate part with the second valve seat 349 brought into a position hm1. The begins at the end of the stroke of valve member 444 if the valve member starting from the initial position V0 in the Position hm0 comes into contact with the intermediate part.
  • the requirements for the The maximum stroke of the piezo is therefore less, since the actual closing force to the second valve seat 349 itself along with the deformation of the elastically deformable In between sets. This is essential advantageous because of the size of a piezo drive and the provided energy with the size of the required Stroke increases significantly. In the way shown here can the required stroke with the same power of the Control valve can be reduced.
  • Figure 8 shows another Variant with a head 546 of the valve member 544, which as first and second sealing surface each a conical Has sealing surface 547 and 552. They are accordingly Valve seats trained. Ultimately, it is also possible instead of a conical second sealing surface 552 also one Realize flat seat sealing surface with accordingly trained second valve seat.
  • valve member 644 of Figure 9 in two parts be carried out in such a way that it has a head 646, which carries the first sealing surface 647 and on which this Side facing away from the sealing surface has a guide surface 59 which is hydraulically coupled to the valve member 644 second valve member 60 is guided.
  • This is in the executed example realized as a ball with a spherical, but preferably with a conical second valve seat 649 cooperates.
  • the ball 60 by the pressure in the control room 625 in contact Valve member 644 held. When actuated, this comes out on the second valve seat 649 to the system.
  • one Ball can be used as a standard part with a tight fit achieve the valve seat.

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

Abstract

In a fuel injection device for internal combustion engines, a fuel injection valve has a plunger (21) which actuates an injection valve member and which delimits a control chamber (25) which is constantly supplied with high pressure fuel through a choke (27) and which can be discharged through a control valve (36) and an outflow channel (129). The control valve (36) has for that purpose a valve member (44) actuated by a piezoelectric element (35) in such a way that the valve member is moved towards the control chamber (25) when the outflow channel (129) is opened. In the closed position, the valve member (44) is pushed in the closing direction by the pressure in the control chamber (25).

Description

Stand der TechnikState of the art

Die Erfindung geht von einer Kraftstoffeinspritzvorrichtung für Brennkraftmaschinen nach der Gattung des Patentanspruchs 1 aus. Bei einer durch die GB-PS 1 320 057 bekannten Kraftstoffeinspritzeinrichtung dieser Art mündet der vom Steuerraum kommende Abflußkanal in einen Sammelraum, der über eine weiterführende Entlastungsleitung mit einem Entlastungsraum verbunden ist. Am Eintritt des Abflußkanals in diesen Sammelraum ist der Ventilsitz für das Ventilglied des Steuerventils vorgesehen. Dieses weist als Antrieb einen Piezo auf und ist als Ventilglied mit kegelförmiger Dichtfläche ausgeführt. Dieses Ventil erfüllt die Funktion des Steuerns des Druckes im Steuerraum, wobei berücksichtigt ist, daß ein Piezo, um betriebssicher arbeiten zu können, nur auf Druck beaufschlagt werden darf. In diesem Sinne wirken auf den Piezo in Schließstellung die vom Ventilsitz übertragene Schließkraft und die resultierende Kraft, die aus der Druckbelastung über den Querschnitt des Abflußkanals auf das Ventilglied ausgeübt wird. Ein Teil des Arbeitsvermögens des Piezos geht dabei durch die Bereitstellung der Schließkraft verloren.The invention relates to a fuel injection device for internal combustion engines according to the preamble of the patent claim 1 off. In one known from GB-PS 1 320 057 Fuel injection device of this type opens out from Control room coming drain channel into a collection room, the via a further relief line with a Relief room is connected. At the entrance to the drainage channel the valve seat for the valve member is in this collecting space of the control valve provided. This has a drive Piezo on and is as a valve member with a conical Sealing surface executed. This valve fulfills the function of controlling the pressure in the control room, taking into account is that a piezo, in order to be able to work reliably, only pressurized. In this sense act on the piezo in the closed position from the valve seat transferred closing force and the resulting force that from the pressure load across the cross-section of the drainage channel is exerted on the valve member. Part of the Piezo's working capacity goes through the Deployment of the closing force lost.

In die EP 0 741 244 A (Stand der Technik gemäß Art. 54(3) EPU) ist eine Kraftstoffeinspritzvorrichtung offenbart, wobei die Schließkraft, die zum dichten Schließen des Steuerventils erforderlich ist, nicht vom Piezo aufgebracht werden braucht, sondern vom Druck im Steuerraum erzeugt wird. Eine vom Piezo aufzubringende hohe Stellkraft ist nur für das Öffnen des Ventils erforderlich, wobei hier wiederum der Piezo vom eingestellten Druck im Steuerraum auf Druck beaufschlagt wird. Sobald das Ventil geöffnet hat, wird die der Stellbewegung bzw. dem Öffnen des Steuerventils entgegenwirkende Kraft schnell abgebaut, so daß auch in diesem Falle der Piezo keine wesentliche Belastung erfährt. In EP 0 741 244 A (prior art according to Art. 54 (3) EPC) is a Fuel injector disclosed, wherein the closing force required for tight closing of the control valve is required, not from the piezo needs to be applied, but from the pressure in the control room is produced. A high positioning force to be applied by the piezo is only required for opening the valve, here again the piezo from the set pressure in the control room Pressure is applied. Once the valve has opened, becomes the actuating movement or the opening of the control valve counteracting force quickly dissipated, so that also in in this case the piezo does not experience any significant stress.

Die Erfindung sieht gemäß Anspruch 1 von, daß zwei in Reihe zueinander liegende Ventilsitze im Verlauf des Abflusses zur Druckentlastung des Steuerraumes über den Abflußkanal vorgesehen sind. Bei einer Stellbewegung des Ventilgliedes in Richtung Steuerraum wird dabei das mit dem Ventilglied und dem ersten Ventilsitz gebildete Ventil geöffnet und in der Folge das vom Ventilglied mit dem zweiten Ventilsitz gebildete Ventil geschlossen. Wenn das Ventilglied auf dem ersten Ventilsitz mit seiner Dichtfläche anliegt wird der Druck im Steuerraum aufgebaut im Sinne eines Schließens des Kraftstoffeinspritzventils. Soll das Sinspritzventil in Öffnungsstellung kommen, so hebt auf eine Betätigung des Piezos hin das Ventilglied vom ersten Ventilsitz ab. Dabei kann es gemäß Patentanspruch 2 in einer Zwischenstellung verharren, in der an beiden Ventilsitzen der Durchströmquerschnitt geöffnet ist. In dieser Position kann das Einspritzventilglied des Kraftstoffeinspritzventils in Öffnungsstellung gehen, so daß eine durch die Dauer dieser Beharrungslage des Ventilgliedes des Steuerventils bestimmte Kraftstoffeinspritzung erfolgt. Wird dagegen der Piezo so angesteuert, daß er seinen vollen Betätigungshub ausführen kann, so kommt das Ventilglied des Steuerventils nach dem Öffnen des Querschnitts am ersten Ventilsitz in Anlage an den zweiten Ventilsitz, so daß in dieser Position der Steuerraum wiederum zur Entlastungsseite versperrt ist. Über die Dauer der Bewegung vom ersten Ventilsitz zum zweiten Ventilsitz erfolgt jedoch eine kurzzeitige Entlastung des Steuerraums, während der ein kurzzeitiger Einspritzvorgang ermöglicht wird. Dieser Einspritzvorgang wird zu einer Voreinspritzung genutzt. Für die nachfolgend erforderliche Haupteinspritzung kann dann das Ventilglied in die Zwischenstellung zwischen den beiden Ventilsitzen gebracht werden und zur Beendigung der Haupteinspritzung wieder an den ersten Ventilsitz unter Mitwirkung des sich im Steuerraum aufbauenden Hochdrucks zurückgeführt werden. Mit dieser Ausgestaltung ergibt sich eine besonders vorteilhafte Möglichkeit mit geringstem Aufwand kleinste Voreinspritzmengen zu steuern.The invention provides according to claim 1 of that two valve seats in series with each other in the course of Outflow to relieve pressure in the control room via the Drain channel are provided. When the actuator moves Valve member in the direction of the control room is the one with the Valve member and the first valve seat formed valve opened and subsequently that of the valve member with the second valve seat formed valve closed. If that Valve element on the first valve seat with its sealing surface pressure is built up in the control room in the sense closing the fuel injector. Should that Sinspritzventil come in the open position, so lifts to one Actuation of the piezo towards the valve member from the first Valve seat from. It can according to claim 2 in one Intermediate position remain in the on both valve seats the flow cross-section is open. In this position can the fuel injector valve member go into the open position so that one by the duration this steady state of the valve member of the control valve certain fuel injection occurs. However, if the Piezo controlled so that it reaches its full actuation stroke can perform, so the valve member of the control valve comes after opening the cross section at the first valve seat in Attachment to the second valve seat so that in this position the control room is in turn blocked on the discharge side. Over the duration of the movement from the first valve seat to second valve seat takes place for a short time Relief of the control room, during a short-term Injection process is made possible. This injection process is used for a pre-injection. For the following required main injection can then in the valve member the intermediate position between the two valve seats be brought and to end the main injection back to the first valve seat with the participation of the Control room building high pressure can be returned. With this configuration results in a special one advantageous option with the least effort to control the smallest pre-injection quantities.

Die Patentansprüche 3 bis 5 beziehen sich auf vorteilhafte Ausgestaltungen dieser Lösung. In weiterhin vorteilhafter Weiterbildung wird gemäß Patentanspruch 6 der zweite Ventilsitz an einem elastisch verformbaren Zwischenteil ausgebildet. Dies hat den Vorteil, daß hiermit das erforderliche Arbeitsvermögen des Piezos als Antrieb des Ventilglieds des Steuerventils noch geringer gehalten werden kann. Kommt das Ventilglied des Steuerventils nach dem Öffnen des Querschnitts am ersten Ventilsitz in Anlage an den zweiten Ventilsitz, steht an dem elastisch verformbaren Zwischenteil ein Differenzdruck an. Auf der dem Steuerraum abgewandten Seite liegt eine Druckentlastung zum Entlastungsraum hin vor, während bei geschlossenem Querschnitt am zweiten Ventilsitz im Steuerraum der hohe Druck herrscht. Infolge dieses Kräfteverhältnisses kann sich nun das Zwischenteil verformen und in Richtung Antriebsseite des Ventilglieds des Steuerventils bewegen. Das reduziert den Hub, den der Piezo für das Öffnen des Querschnitts am zweiten Ventilsitz ausüben muß, um in der Folge den Steuerraum zur Bereitstellung der Haupteinspritzung zu entlasten. Hebt das Ventilglied zu diesem Zweck von dem zweiten Ventilsitz ab, so erfolgt aufgrund der Wiederaufhebung der einseitigen Kräftebelastung am verformbaren Zwischenteil ein Wiederzurückgehen dieses Zwischenteil in seine Normallage und damit ein schnelles Öffnen des Entlastungsquerschnitts. Claims 3 to 5 relate to advantageous Refinements of this solution. In more advantageous Training is the second according to claim 6 Valve seat on an elastically deformable intermediate part educated. This has the advantage that the required working capacity of the piezo to drive the Valve member of the control valve can be kept even lower can. The valve member of the control valve comes after the Open the cross-section at the first valve seat in the system the second valve seat is on the elastically deformable In between a differential pressure. On the the control room opposite side is a pressure relief to Relief room forward while closed Cross section on the second valve seat in the control room the high There is pressure. As a result of this balance of power now deform the intermediate part and towards the drive side of the valve member of the control valve. That reduces the stroke that the piezo opens to open the cross section second valve seat must exert in order to the Control room to provide the main injection too relieve. For this purpose, lift the valve member from the second valve seat, so it is due to the Recovery of the unilateral load on deformable intermediate part a return this Intermediate part in its normal position and thus a quick one Opening the relief cross section.

Weitere vorteilhafte Ausgestaltungen sind den übrigen Patentansprüchen zu entnehmen. Dabei sind insbesondere vorteilhafte Ausbildungen der Dichtflächen an dem Ventilglied des Steuerventils dargestellt.Further advantageous configurations are the others Claims to be found. Here are particular advantageous designs of the sealing surfaces on the Valve element of the control valve shown.

Zeichnungdrawing

In der Zeichnung sind 6 Ausführungsbeispiele der Erfindung dargestellt und werden in der nachfolgenden Beschreibung näher erläutert. Es zeigen Figur 1 eine schematische Darstellung einer Kraftstoffeinspritzvorrichtung mit Versorgung aus einem Hochdruckspeicher und einem von einem Steuerventil gesteuerten Kraftstoffeinspritzventil bekanntes Bauart, Figur 2 einen Teilschnitt durch ein bekanntes Kraftstoffeinspritzventil entsprechend dem Ausschnitt A von Figur 1 mit Darstellung des Steuerraums und eines in einem nicht weiter gezeigten Piezo angetriebenen Ventilglieds des Steuerventils, Figur 3 ein erstes Ausführungsbeispiel der Erfindung mit einem Steuerventil, das einen ersten und einen zweiten Ventilsitz aufweist mit einer abgewandelten Form der Führung des Abflußkanals, Figur 4 den Einspritzventilhub bezogen auf den Stellhub des Steuerventilgliedes, Figur 5 ein Zweites Ausführungsbeispiel in Abwandlung zum Ausführungsbeispiel nach Figur 3 mit einem zweiten Ventilsitz, der an einem elastisch verformbaren Zwischenteil ausgebildet ist in einer ersten Stellung des Ventilglieds des Steuerventils am ersten Ventilsitz, Figur 6 ein Darstellung des Steuerventils mit in Schließstellung am zweiten Ventilsitz befindlichen Ventilglied in einer abgewandelten Form, mit gemäß Figur 5 vorgesehenen elastisch verformbaren Zwischenteil und einer übertrieben dargestellten Auslenkung dieses Zwischenteils aufgrund des an ihm herrschenden Differenzdruckes, Figur 7 eine Darstellung der Bewegungsverläufe des Ventilsitzes am Zwischenteil und des Stellhubes des Ventilglieds, zugeordnet zum Bewegungsverlauf des Einspritzventilglieds, Figur 8 ein viertes Ausführungsbeispiel der Erfindung mit einer abgewandelten Ausführung des zweiten Ventilsitzes und der mit diesem zusammenwirkenden zweiten Dichtfläche am Ventilglied, Figur 9 ein fünftes Ausführungsbeispiel der Erfindung mit einem mehrteilig ausgebildeten Ventilglied und Figur 10 ein sechstes Ausführungsbeispiel mit einer vorteilhaften Ausbildung des Ventilgehäuses und Anordnung des Zuflußkanals zum Steuerraum.In the drawing there are 6 exemplary embodiments of the invention are shown and are described in the following description explained in more detail. 1 shows a schematic Representation of a fuel injection device with Supply from a high pressure accumulator and one from one Control valve controlled fuel injector known Type, Figure 2 is a partial section through a known Fuel injector accordingly the section A of Figure 1 showing the control room and one in a piezo not shown driven valve member of the control valve, Figure 3 shows a first Embodiment of the invention with a Control valve that has a first and a second valve seat has a modified form of leadership of the Drain channel, Figure 4 the injector stroke based on the Adjustment stroke of the control valve member, Figure 5 a second Embodiment modified from the embodiment according to Figure 3 with a second valve seat on a elastically deformable intermediate part is formed in one first position of the valve member of the control valve on the first Valve seat, Figure 6 is a representation of the control valve with in Close position on the second valve seat Valve member in a modified form, with according to Figure 5 provided elastically deformable intermediate part and one exaggerated displacement of this intermediate part due to the differential pressure prevailing on it, Figure 7 a representation of the movements of the valve seat on Intermediate part and the stroke of the valve member assigned 8 shows a fourth for the course of movement of the injection valve member Embodiment of the invention with a modified version of the second valve seat and with this cooperating second sealing surface on Valve element, Figure 9 shows a fifth embodiment of the Invention with a multi-part valve member and Figure 10 shows a sixth embodiment with a advantageous design of the valve housing and arrangement of the inflow channel to the control room.

Beschreibung der AusführungsbeispieleDescription of the embodiments

Eine Kraftstoffeinspritzeinrichtung, 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 der Vorzug zu geben.A fuel injector with the high Injection pressures and little effort a large variation fuel injection, especially with very precise controllable injection times and injection quantities possible is through a so-called common rail system realized. This represents a different kind of High pressure fuel source available than it is through the Usual high pressure fuel injection pump is given. there However, the invention is both in this so-called Common rail system as well at one Fuel injection pump can be used. The common rail system preference is to be given.

In der Figur 1 ist bezüglich eines Common-Rail-Druckversorgungssystems 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 ein elektrische Steuereinrichtung 8 gesteuert. Diese steuert auch ein Kraftstoffeinspritzventil 9.In Figure 1 is related to a common rail pressure supply system as a high-pressure fuel source High-pressure fuel reservoir 1 provided by a High-pressure fuel delivery pump 2 from one Fuel tank 4 is supplied with fuel. The pressure in the high-pressure fuel accumulator 1 is determined by a pressure control valve 5 in connection with a pressure sensor 6 controlled by an electrical control device 8. This also controls a fuel injection valve 9.

In einer bekannten Ausgestaltung weist das Kraftstoffeinspritzventil 9 ein Ventilgehäuse 11 auf, das an seinem einen Ende, das zum Einbau an der Brennkraftmaschine bestimmt ist, Einspritzöffnungen 12 besitzt, deren Austritt aus dem Innern des Kraftstoffeinspritzventils durch ein Einspritzventilglied 14 gesteuert wird. Dieses ist im ausgeführten Beispiel als langgestreckte Ventilnadel ausgeführt, die an ihrem einem 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. In einem im Durchmesser vergrößerten Teil dieses Druckraumes ist eine Druckfeder 19 angeordnet, die zwischen einem Ventilteller 20 und dem Ventilgehäuse axial eingespannt ist und das Einspritzventilglied 14 in Schließrichtung beaufschlagt. Koaxial zur Druckfeder ist ein Stößel 21 vorgesehen, der einerseits am Ventilteller 20 anliegt und andererseits in eine Führungsborhung 22 eintaucht und dort mit seiner Stirnseite 23, die eine bewegliche Wand bildet, einen Steuerraum 25 mit dem geschlossenen Ende der Führungsbohrung einschließt. In diesen Steuerraum mündet ein Zuflußkanal 26, in dem eine Drossel 27 angeordnet ist und der vom Druckraum 16 ausgehend immer Kraftstoff unter Hochdruck über die Drossel 27 in den Steuerraum 25 liefert. In a known embodiment, the Fuel injection valve 9 on a valve housing 11, the one end that is for installation on the internal combustion engine is determined, has injection openings 12, the outlet from inside the fuel injector by a Injection valve member 14 is controlled. This is in the executed example as an elongated valve needle executed that at one end a sealing surface 15th owns that with an internal valve seat interacts. The valve needle is inside a through a pressure line 17 with the High-pressure fuel accumulator 1 connected pressure chamber 16 inside the valve body. In one in diameter enlarged part of this pressure chamber is a compression spring 19 arranged between a valve plate 20 and the Valve housing is clamped axially and that Injection valve member 14 is applied in the closing direction. A plunger 21 is provided coaxially with the compression spring on the one hand rests on the valve plate 20 and on the other hand in a guide bore 22 dips and there with his End face 23, which forms a movable wall, a Control room 25 with the closed end of the guide bore includes. An inflow channel 26 opens into this control chamber, in which a throttle 27 is arranged and that of the pressure chamber 16 always fuel under high pressure via the Throttle 27 in the control chamber 25 supplies.

Vom Steuerraum 25 führt koaxial zum Stößel 21 von der diesem gegenüberliegenden Stirnseite ein Abflußkanal 29 ab, der in einen Entlastungsraum 30 innerhalb des Ventilgehäuses 11 mündet, wobei dieser Entlastungsraum über eine weiterführende Entlastungsleitung 31 zu einem aufnahmefähigen Entlastungsraum 32 führt, der z. B. der Kraftstoffvorratsbehälter 4 sein kann.From the control room 25 leads coaxially to the plunger 21 of the latter opposite end of a drain channel 29, which in a relief space 30 within the valve housing 11 opens, this relief space over a further relief line 31 to a Recordable relief space 32 leads z. B. the Fuel tank 4 can be.

Die Einmündung des Abflußkanals 29 in den Entlastungsraum 30 wird bei diesem bekannten Einspritzventil durch ein Ventilglied 34 eines Steuerventils 36, das als Sitzventil ausgebildet ist, gesteuert, wobei dieses Ventilglied durch einen Piezo 35 in schließstellung bzw. in Öffnungsstellung gebracht werden kann.The confluence of the drain channel 29 in the relief chamber 30 is in this known injection valve by a Valve member 34 of a control valve 36, which acts as a seat valve is formed, controlled, this valve member by a piezo 35 in the closed position or in the open position can be brought.

Die bekannte Kraftstoffeinspritzvorrichtung arbeitet dabei folgendermaßen:The known fuel injection device works here as follows:

Durch die vorzugsweise synchron zur Brennkraftmaschine angetriebene Kraftstoffhochdruckpumpe 2 wird Kraftstoff aus dem Kraftstoffvorratsbehälter 4 in den Hochdruckspeicher 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 diesem Kraftstoffhochdruckspeicher zur Verfügung stehende Kraftstoff versorgt mehrere Kraftstoffeinspritzventile der beschriebenen Bauart. Solange das Ventilglied 34 des Steuerventils 36 in der gezeigten Schließstellung ist, wird aufgrund des über die Druckleitung 17 zugeführten Kraftstoffhochdruck auch im Steuerram 25 dieser hohe Druck eingehalten, der nun über die bewegliche Wand 23 das Ventilglied 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 36 jedoch geöffnet, kann der Steuerraum 25 über den Abflußkanal 29 entlastet werden. Aufgrund des im Steuerraum sinkenden Druckes reicht die Schließkraft der Druckfeder 19 nicht mehr aus, das Einspritzventilglied 14 gegen den an einer Druckfläche 41 des Ventilglieds angreifenden Kraftstoffhochdruckes in Schließstellung zu halten, so daß dieses in Offenstellung geht. Schließt das Ventilglied 34 des Steuerventils 36 dagegen wieder in Abflußkanal 29, entsteht sofort wieder im Steuerrahmen 25 der hohe Kraftstoffdruck, der dann das Einspritzventilglied 14 wieder in Schließstellung bringt und so die Kraftstoffeinspritzung beendigt wird.By preferably synchronous to the internal combustion engine driven fuel high pressure pump 2, fuel is out the fuel reservoir 4 in the high-pressure accumulator 1 promoted, the pressure on the pressure control valve 5 in Connection with the pressure sensor 6 on a preferably constant value is set. This value can be at Needs to be changed too. The one from this High-pressure fuel storage available Fuel powers multiple fuel injectors described type. As long as the valve member 34 of the Control valve 36 is in the closed position shown due to the supplied via the pressure line 17 High fuel pressure also in the control frame 25 this high pressure complied with, which is now on the movable wall 23 Valve member 14 in addition to the compression spring 19 with a Closing force applied, so that the injection valve member 14 is brought into the closed position and in this position remains. However, if the control valve 36 is opened, the Control chamber 25 are relieved via the drain channel 29. Due to the falling pressure in the control room, that is enough Closing force of the compression spring 19 no longer from that Injection valve member 14 against that on a pressure surface 41 of the valve member attacking high fuel pressure in To keep the closed position so that this is in the open position goes. Closes the valve member 34 of the control valve 36 on the other hand, again in drain channel 29, immediately arises again in Control frame 25 the high fuel pressure, which is then the Brings injection valve member 14 back into the closed position and so the fuel injection is stopped.

In der Figur 2 ist ein Ausschnitt aus einem Kraftstoffeinspritzventil der in Figur 1 gezeigten grundsätzlichen Art dargestellt, wobei die Figur 2 einem Ausschnitt A an diesem Kraftstoffeinspritzventil entspricht. Auch dort ist wiederum die Stirnseite 23 als bewegliche Wand an dem den Steuerraum 25 einschließenden Stößel 21 ausgebildet. In den Steuerraum mündet seitlich an der Umfangswand der Führungbohrung 22 der Zuflußkanal 26 mit der Drossel 27 ein, derart, daß der Zufluß durch den Stößel in jeder seiner Stellungen nicht verschlossen wird. Auf der der Stirnseite 23 des Stößels gegenüberliegenden Stirnseite 37 der Führungsbohrung 22 führt über eine Ausnehmung 38 in dieser Stirnseite 37 der Abflußkanal 129 ab. Der Übergang von der kreis zylindrisch ausgebildten Ausnehmung 38 zum Abflußkanal erfolgt über einen kegelförmigen Ventilsitz 39, an dem sich zunächst ein zylindrischer, zum Stößel 21 koaxialer Zwischenraum 40 anschließt von dem aus der Entlastungskanal dann seitlich abführt, wobei in dem Abflußkanal 129 zusätzlich noch eine zweite Drossel 42 angeordnet ist. Zusammen mit der ersten Drossel 27 bestimmt diese das zeitliche Verhalten der Druckentlastung des Steuerraumes.A section of FIG. 2 is shown a fuel injection valve that shown in Figure 1 shown basic type, wherein the figure 2 a Section A on this fuel injector corresponds. The end face 23 is again there as a movable wall on the plunger 21 enclosing the control chamber 25 educated. In the control room opens on the side Circumferential wall of the guide bore 22 of the inflow channel 26 with the Throttle 27, such that the inflow through the plunger in each of his positions is not locked. On the the End face 23 of the plunger opposite end face 37 the guide bore 22 leads through a recess 38 in this end face 37 of the drain channel 129. The transition from the circular cylindrical recess 38 to Drain channel takes place via a conical valve seat 39, which is initially a cylindrical, to the plunger 21st coaxial space 40 connects from which the Relief channel then discharges laterally, in which Drain channel 129 additionally a second throttle 42nd is arranged. Determined together with the first throttle 27 this the temporal behavior of the pressure relief of the Control space.

Mit dem Ventilsitz 39 wirkt hier ein Ventilglied 44 in gegenüber dem Ventilglied 34 des Steuerventils 36 von Figur 1 abgewandelter Form zusammen. Dieses weist einen Ventilstößel 45 auf, der in einer Bohrung 43 des Ventilgehäuses 11 geführt ist und an seinem hier nicht gezeigten anderseitigen Ende mit dem Piezo 35 gekoppelt ist. An seinem in die Ausnehmung 38 ragenden Ende trägt dieser Ventilstößel einen Kopf 46, an dem eine zum Ventilsitz 39 weisende kegelförmige Dichtfläche 47 angebracht ist. In der gezeigten Schließstellung des Steuerventils 36 liegt diese Dichtfläche 47 am Ventilsitz 39 an, so daß über der durch den Zuflußkanal 26 zuströmende Kraftstoff im Steuerraum 25 einen hohen Druck aufbaut, der das Einspritzventilglied 14 in Schließstellung hält. In dieser Stellung ist der Kopf 46 vom im Steuerraum 25 herrschenden Druck beaufschlagt, der das Ventilglied auch ohne Betätigung durch den Piezo in Schließstellung hält. Zum Öffnen des Steuerventils wird der Piezo betätigt derart, daß der Kopf 46 weiter in die Ausnehmung 38 eintaucht und den Durchströmquerschnitt am Ventilsitz freigibt. Dies erfolgt in der Initialisierung zunächst gegen den Hochdruck im Steuerraum. Sobald das Ventilglied ein bißchen vom Ventilsitz 39 abgehoben hat, erfolgt ein Druckausgleich am Ventilglied, so daß für den weiteren Öffnungshub relativ wenig Öffnungsarbeit am Piezo aufgewendet werden muß. Der Steuerraum wird entlastet und das Einspritzventilglied 14 öffnet. Dabei bewegt sich der Stößel 21 in der gezeigten Darstellung nach oben zur Stirnseite 37 hin. Aufgrund einer Anfasung 24 auf der Stirnseite 23 des Stößels 21 und einer dieser gegenüberliegenden ringförmigen Ausnehmung 28 in der Stirnseite 37 wird ein Restraum gebildet, der als hydraulischer Anschlag wirkt. Im Bereich dieses Restraumes bleibt dabei immer eine Restfläche des Stößels 21 dem über den Zuflußkanal 26 zugeführten Kraftstoffhochdruck unmittelbar ausgesetzt. Zwischen Stirnfläche 23 und der Stirnfläche 37 im Bereich zwischen diesem Restraum und der Ausnehmung 38 verbleibt ein Drosselspalt, der die entlastete Ausnehmung 38 vom Restraum abkoppelt und der dem Druckaufbau auch in der Ausnehmung 38 nach Schließen des am Ventilsitzes 39 und Ventilglied 44 realisierten Ventils dient.A valve member 44 acts here with the valve seat 39 opposite the valve member 34 of the control valve 36 from Figure 1 modified form together. This shows one Valve tappet 45, which in a bore 43 of the Valve housing 11 is guided and not at his here shown opposite end is coupled to the piezo 35. At its end protruding into the recess 38, this carries Valve tappet a head 46 on which one to the valve seat 39 facing conical sealing surface 47 is attached. In the shown closed position of the control valve 36 is this Sealing surface 47 on the valve seat 39 so that the through the fuel flowing into the inflow channel 26 in the control chamber 25 builds up a high pressure that the injection valve member 14 holds in the closed position. In this position the head is 46 acted upon by the pressure prevailing in the control chamber 25, the the valve member even without actuation by the piezo Closed position holds. To open the control valve, the Piezo actuates such that the head 46 continues into the Recess 38 dips and the flow cross section on Valve seat releases. This is done in the initialization first against the high pressure in the control room. As soon as that Valve member has lifted a little from valve seat 39, there is a pressure compensation on the valve member, so that for the further opening stroke relatively little opening work on the piezo must be used. The control room is relieved and the injection valve member 14 opens. The moves Tappet 21 in the illustration shown to the top End face 37 back. Due to a chamfer 24 on the Face 23 of the plunger 21 and one of these opposite annular recess 28 in the An end space 37 is formed, which as hydraulic stop works. In the area of this residual space there always remains a residual surface of the plunger 21 above the inflow channel 26 supplied high fuel pressure immediately exposed. Between face 23 and the End face 37 in the area between this residual space and the Recess 38 remains a throttle gap, which relieved the Decoupling recess 38 from the residual space and the pressure build-up also in the recess 38 after closing the valve seat 39 and valve member 44 realized valve is used.

Eine Einführung des Zuflußkanals 26 in den einen Teil des Restraumes bildenden ringförmigem Ausnehmung 28 bietet dabei den wesentlichen Vorteil, daß der in Figur 10 gezeigte Zuflußkanal 726 schräg zur Achse des Stößels 721 eingebracht werden kann, ausgehend von einer der Druckversorgung des Druckraumes 16 dienenden Bohrung 59, die parallel zur Achse des Einspritzventils geführt wird. Wird das Einspritzventilgehäuse am Übergang zum Entlastungsraum 30 (Figur 1) getrennt, so kann dann vorteilhaft der Zuflußkanal 726, von der Mündung 61 der parallelen Bohrung 59 von dieser Trennebene 60 aus schräg zum Restraum 738 hin gebohrt werden. Dies hat den wesentlichen Vorteil, daß um den Steuerraum 725 herum das massive Einspritzventilgehäuse erhalten bleibt und keine durch den im Hochdruckzulauf anstehenden Hochdruck verursachte Wandverformungen das Passungsspiel zwischen Führungsbohrung 722 und Stößel 721 nachteilig beeinflussen können. Insbesondere ist kein von einem separaten Einsatz gebildeter Ringraum erforderlich, von dem der Zuflußkanal Hochdruckkraftstoff zum Steuerraum führen muß, wie es in der EP A1- 0 661 442 gezeigt ist. Dort ist die Führung des Stößels innerhalb eines Einsatzes vorgesehen, der von einem dem Hochdruck ausgesetzen Ringraum umgeben ist, und so mit geringer Wandstärke den Steuerraum vom Ringraum trennt. An introduction of the inflow channel 26 in one part of the Residual space-forming annular recess 28 offers the main advantage that the one shown in Figure 10 Inflow channel 726 introduced obliquely to the axis of the plunger 721 can be, starting from one of the pressure supply of the Pressure chamber 16 serving bore 59, which is parallel to the axis of the injection valve is guided. Will the injector body at the transition to relief chamber 30 (FIG. 1) separated, then the inflow channel 726, from the mouth 61 of the parallel bore 59 of this Partition plane 60 drilled obliquely to the residual space 738 become. This has the main advantage that the Control room 725 around the massive injector housing remains and none due to the high pressure inlet upcoming high pressure caused wall deformations Fit between guide bore 722 and plunger 721 can adversely affect. In particular, none of a separate insert requires an annular space, from which the inflow channel high pressure fuel to the control room must lead, as shown in EP A1-0 661 442. There is the guidance of the ram within an insert provided that of an annulus exposed to high pressure is surrounded, and so with a small wall thickness the control room separates from the annulus.

Mit dieser Ausgestaltung kann bereits mit relativ wenig Aufwand bzgl. des das Steuerventil betätigenden Piezos 35 eine sichere und schnelle Steuerung der Einspritzvorgänge vorgenommen werden. Dadurch, daß das Ventilglied nur im Moment des Öffnens dem Piezo einen hohen Widerstand entgegensetzt, danach aber wegen der Druckentlastung im Steuerraum 25 diese Widerstände praktisch 0 werden, braucht der Piezo nur für diese spezielle Belastung ausgelegt zu werden.With this configuration, relatively little can be done Effort relating to the piezo 35 actuating the control valve safe and fast control of the injection processes be made. The fact that the valve member only in Moment of opening the piezo a high resistance opposed, but then because of the pressure relief in the Control room 25 these resistors need to be practically 0 the piezo is only designed for this special load become.

Zur Verbesserung der Arbeitsweise dieser bekannten Kraftstoffeinspritzvorrichtung ist nun erfindungsgemäß das Steuerventil verbessert worden. Die Einzelheiten, in denen sich die Erfindung realisiert, sind den nachfolgenden Figuren 3-10 zu entnehmen.To improve the operation of this known Fuel injection device is now the invention Control valve has been improved. The details in which realized the invention are the following Figures 3-10.

In Abwandlung zu Figur 2 kann gemäß Figur 3 der Abflußkanal 229 auch seitlich vom Steuerraum 25 abführen. Die Figur 3 zeigt darüberhinaus noch die vorteilhafte Ausgestaltung der Erfindung, die darin besteht, daß der hier analog zur Figur 2 vorgesehene Ventilsitz nun ein erster Ventilsitz 139 ist, an dem der Zwischenraum 40 wiederum angrenzt, von welchem dann der Abflußkanal 229 über eine zweite Drossel 142 zum Entlastungsraum abführt. Zusätzlich zu diesem ersten Ventilsitz 139 ist nun ein zweiter Ventilsitz 49 vorgesehen, der koaxial zum ersten Ventilsitz 139 diesen zur Seite des Steuerraumes 25 gegenüberliegend angeordnet ist. Der Abflußkanal 229 weist dazu in einem Zwischenbereich einen Ventilraum 50 auf, in den der beispielweise kugelförmig ausgebildete Kopf 146 des Ventilgliedes 144 eintauchen kann. Statt dieser kugelförmigen Form wäre durchaus auch eine Form, wie sie in Figur 2 gezeigt ist, möglich, mit einer der kegelförmigen Dichtfläche 47 als erste Dichtfläche und einer dieser gegenüberliegenden zweiten, ebenfalls kegelförmigen Dichtfläche 52, die in der Figur 2 als mögliche Alternative für eine Anwendung bei Figur 3 mit einer gestrichelten Bezugslinie bezeichnet ist. As a modification to FIG. 2, the drain channel can be used according to FIG 229 also lead away from the control room 25. Figure 3 also shows the advantageous Embodiment of the invention, which is that here analogous to Figure 2 provided valve seat now a first Is valve seat 139, on which the space 40 in turn adjoins, of which the drain channel 229 then via a leads second throttle 142 to the relief chamber. additionally this first valve seat 139 is now a second one Valve seat 49 is provided, which is coaxial with the first valve seat 139 opposite to the side of the control room 25 is arranged. The drain channel 229 has in one Intermediate area on a valve space 50, in which the for example spherical head 146 of the Valve member 144 can immerse. Instead of this spherical shape would definitely be a shape as in Figure 2 is shown possible with one of the conical Sealing surface 47 as the first sealing surface and one of these opposite second, also conical Sealing surface 52, which in Figure 2 as a possible alternative for an application in FIG. 3 with a dashed line Reference line is designated.

Bei der Figur 3 ist bei einem kugelförmigen Kopf die erste Dichtfläche 147 zur Seite des ersten Ventilsitzes 39 hin ausgebildet und dieser gegenüberliegen eine zweite Dichtfläche 152 in Fortsetzung der Kugelform verwirklicht. Diese zweite Dichtfläche wird bei Betätigung des Ventilglieds 144 zur Anlage an dem zweiten Ventilsitz 49 gebracht und in dieser Position verschließt das Ventilglied 144 nach einem zwischenzeitlichen Öffnen des Abflußkanals 229 diesen wieder. Über die Dauer des Hubes des Ventilglieds 144 von seiner in der Figur 3 gezeigten Stellung am ersten Ventilsitz 139 zum zweiten Ventilsitz 49 erfolgt eine Entlastung des Steuerraumes 25 derart, daß das Einspritzventilglied kurzzeitig öffnen kann. Liegt das Ventilglied mit seiner zweiten Dichtfläche 152 am zweiten Ventilsitz 49 wieder an, so baut sich sehr schnell der Druck im Steuerraum 25 wieder auf und das Kraftstoffeinspritzventil schließt. Diese Ausgestaltung hat den sehr wesentlichen Vorteil, daß in einer einzigen Bewegungsabfolge und -richtung bei Betätigung des Ventilglieds 144 durch den Piezo 35 ein Öffnen und Wiederschließen der Entlastungsleitung mit Zwischenentlastung des Steuerraumes durchgeführt werden kann, was es ermöglicht, daß sehr kurze Entlastungszeiten zu verwirklichen sind. Dies ist ganz im Sinne der Einspritzunterbrechung zwischen einer Voreinspritzung und einer nachfolgenden Haupteinspritzung. Während bei allen bekannten Ausgestaltungen für diesen Vorgang eine erste Hinund Herbewegung des Ventilglieds zur Erzeugung einer Voreinspritzung erforderlich war und eine zweite Hin- und Herbewegung des Ventilglieds zur Bestimmung der Haupteinspritzung erforderlich war, kann nun durch eine einzige Hin- und Herbewegung des Ventilglieds sowohl die Voreinspritzung als auch die Haupteinspritzung mit Spritzunterbrechung gesteuert werden. In the case of FIG. 3, the first is for a spherical head Sealing surface 147 to the side of the first valve seat 39 trained and this a second Sealing surface 152 realized in continuation of the spherical shape. This second sealing surface is when the Valve member 144 for abutting the second valve seat 49 brought and in this position closes the valve member 144 after opening the drainage channel in the meantime 229 this again. Over the duration of the stroke of the valve member 144 from its position shown in FIG. 3 on the first Valve seat 139 to the second valve seat 49 takes place Relief of the control room 25 such that the Injector member can open briefly. Is that Valve member with its second sealing surface 152 on the second Valve seat 49 on again, so the pressure builds up very quickly in control room 25 again and that Fuel injector closes. This configuration has the very essential advantage that in a single Sequence and direction of movement when the Valve member 144 through the piezo 35 opening and Re-close the relief line with Intermediate relief of the control room can be carried out can, which allows very short relief times are realized. This is entirely in the spirit of Injection interruption between a pre-injection and a subsequent main injection. While everyone known configurations for this process a first Hinund Movement of the valve member to generate a Pre-injection was required and a second round trip Movement of the valve member to determine the Main injection was required, can now be done through a only reciprocation of the valve member both the Pre-injection as well as the main injection Spray interruption can be controlled.

Der Figur 4 ist dazu oben der Hubverlauf des Einspritzventilglieds 14 zu entnehmen und diesem zugeordnet der Hubverlauf des Ventilglieds 144 des Steuerventils über der Zeit. Man erkennt im oben liegenden Teil des Diagramms die kurzzeitige Öffnung des Einspritzventils zur Durchführung der Voreinspritzung VE, dann eine Spritzunterbrechung SU und dann folgt die Öffnung des Einspritzventils für die Haupteinspritzung HE. Im darunterliegenden Teil des Diagramms erkennt man, daß aus der Ausgangslage mit dem Hub 0 das Ventilglied 144 einen Hub zurücklegt, über den die Voreinspritzung erfolgt. Beim Hub he ist diese Voreinspritzung beendet und auch die größte Auslenkung des Ventilglieds 144 erreicht. Nach Verharrung über die Zeit SU in dieser Endlage folgt das Wiederzurücklaufen des Ventilglieds 144 in eine Zwischenscellung ZS, in der die Querschnitte an beiden Ventilsitzen 139 und 49 geöffnet sind für die Durchführung der Haupteinspritzung HE und anschließenden der endgültige Zurücklauf zum ersten Ventilsitz 139. In dieser Ausführung liegen die Ventilsitze 139 und 49 vorzugsweise koaxial hintereinander und koaxial zum Ventilstößel des Ventilglieds 144. An beiden Ventilsitzen wird jeweils ein Sitzventil auf diese Weise realisiert.For this purpose, FIG. 4 shows the stroke profile of the injection valve member 14 and assigned to the Stroke course of the valve member 144 of the control valve over the Time. You can see that in the part of the diagram above brief opening of the injection valve for execution the pre-injection VE, then a spray interruption SU and then the injection valve opens for the Main injection HE. In the part below Diagram shows that from the starting position with the stroke 0 the valve member 144 covers a stroke over which the Pre-injection takes place. At the stroke he is Pre-injection ended and also the largest displacement of the Valve member 144 reached. After persistence over time SU in this end position, the Valve member 144 in an intermediate cell ZS, in which the Cross sections opened on both valve seats 139 and 49 are for performing the main injection HE and then the final return to the first Valve seat 139. In this version, the valve seats are located 139 and 49 preferably coaxial one behind the other and coaxial to the valve lifter of valve member 144. On both Valve seats each become a seat valve in this way realized.

Zur Reduzierung der Anforderungen an den Piezo zur Durchführung der Stellbewegung des Ventilglieds ist in Weiterbildung zum Ausführungsbeispiel nach Figur 3 in Figur 5 der zweite Ventilsitz als Ventilsitz 349 an einem elastisch verformbaren Zwischenteil 55 angeordnet. Dieses hat beispielsweise die Form einer Scheibe, die vorzugsweise aus Metall besteht und zwischen zwei Hälften des Ventilgehäuses 11 dicht eingespannt ist. Sie weist koaxial zum Stößel 21 bzw. zum Ventilglied 244 eine Durchgangsbohrung 56 auf, die den Ventilraum 150 mit dem Steuerraum 125 verbindet. Der Eintritt der Durchgangsbohrung 56 in den Ventilraum 150 ist als zweiter Ventilsitz 349 ausgebildet, an dem die zweite Dichtfläche 352 des Ventilglieds 344 in seiner maximal ausgelenkten Position dicht zur Anlage kommt. Der Kopf 346 des Ventilglieds 344 trägt als erste Dichtfläche 347 eine Kegelfläche und als zweite Dichtfläche 352 eine kugelförmige Fläche, in Abwandlung zum Ausführungsbeispiel nach Figur 3. Es könnte aber auch eine Konfiguration des Kopfes 46 von Figur 2 hier Anwendung finden. Auf der Seite zum Steuerraum 125 hin weist das elastisch verformbare Zwischenteil eine konzentrisch zur Durchgangsbohrung 56 liegende, ringförmige Ausnehmung 57 auf, mit der erreicht wird, daß das elastisch verformbare Zwischenteil beginnend an dieser ringförmigen Ausnehmung 57; insbesondere nach oben zum Ventilglied 344 hin, leichter ausgelenkt werden kann. Diese Eigenschaft läßt sich aber auch durch andersartige Minderungen der Stärke des Zwischteils erzielen. In Figur 6 ist diese Situation der Auslenkung des Zwischenteils dargestellt, dort jedoch anhand eines Ventils mit einem Kopf 446 des Ventilgliedes 444, der gemäß Figur 3 kugelförmig ist. Gelangt der Kopf 446 mit seiner zweiten Dichtfläche in Anlage an den zweiten Ventilsitz 349 kann sich im Steuerraum 25 der im Kraftstoffhochdruckspeicher herrschende hohe Druck aufbauen. War in der Position des Ventilglieds 344 von Figur 5 der Ventilraum 150 dem selben Druck ausgesetzt wie der Steuerraum 125, so herrschen bei der Position gemäß Figur 6 nun unterschiedliche Drücke derart, daß das elastisch verformbare Zwischenteil 55 nun zum Ventilglied 444 hin verformt wird. In der Figur 7 ist dieser Vorgang dargestellt. In einander zugeordneten, übereinander liegenden Diagrammteilen ist oben die Hubbewegung des Einspritzventilglieds 14 wiedergegeben, wiederum mit dem Bereich der Voreinspritzung VE, der Spritzpause SU und der Haupteinspritzung HE. In dem unteren Teil des Diagramms ist mit der Kurve M die Bewegung des elastischen Zwischenteils wiedergegeben. Bei einer Ausgangslage hm0 wird bezogen auf den Stellweg des Ventilglieds 444 das Zwischenteil mit dem zweiten Ventilsitz 349 in eine Position hm1 gebracht. Das beginnt mit Ende der Hubbewegung des Ventilglieds 444, wenn das Ventilglied ausgehend von der Ausgangsstellung V0 in die Position hm0 in Anlage an das Zwischentiel gelangt. Ist diese Position erreicht wird das Ventilglied zusammen mit dem zweiten Ventilsitz 349 des Zwischenteils unter Einwirkung des nun entstehenden Differenzdruckes in die Position hm1 gebracht und verharrt dort, solange das Ventilglied 444 am zweiten Ventilsitz 349 anliegt. Danach geht nach dem Wiederabheben des Ventilglieds 444 vom zweiten Ventilsitz 349 dieser wieder in seine Ausgangslage hm0 zurück und das Ventilglied 444 wie bei dem Diagramm nach Figur 4 in eine Zwischenstellung ZS, bei der der Steuerraum 125 entlastet ist und die Haupteinspritzung vollzogen wird. Anschließend geht das Ventilglied in seine Endlage V0 zurück. In dem Bereich, in dem die Membran in Richtung Hub hm1 ausweicht kann auch das Ventilglied rückgehend ausgelenkt werden, so daß sich sein Hub von der ursprünglichen Endlage hm0 in eine gemeinsame Endlage hm1 zurückbewegt. Der danach zum vollständigen Öffnen vom Ventilglied 444 durchzuführende Hub ist somit verringert gegenüber der gestrichelt eingezeigten Version der Kurve V1, die sich ohne elastisches Ausweichen des Zwischenteils einstellen würde. Dadurch, daß unmittelbar nach dem Abheben vom zweiten Ventilsitz 349 beide Teile, das Ventilglied 444 und das elastisch verformbare Zwischenteil 55, einen Hub im Öffnungssinne durchführen, ergibt sich hier ein sehr schnelles Entlasten des steuerraumes 125 für die Durchführung der Haupteinspritzung. Die Anforderungen an den Maximalhub des Piezos sind somit geringer, da die eigentliche Schließkraft zum zweiten Ventilsitz 349 sich zusammen mit der Verformung des elastisch verformbaren Zwischenteils einstellt. Dies ist ganz wesentlich vorteilhaft, da die Größe eines Piezoantriebs und der dazu bereitgestellten Energie mit der Größe des erforderlichen Stellhubes wesentlich zunimmt. Auf hier dargestellten Weise kann der erforderliche Hub bei gleicher Leistung des Steuerventils reduziert werden.To reduce the demands on the piezo Execution of the actuating movement of the valve member is in Further development of the embodiment of Figure 3 in Figure 5 second valve seat as valve seat 349 on an elastic deformable intermediate part 55 is arranged. This one has for example the shape of a disc, which is preferably made of There is metal and between two halves of the valve housing 11 is tightly clamped. It points coaxially to the plunger 21 or to the valve member 244 on a through hole 56 connects the valve chamber 150 to the control chamber 125. The Entry of the through hole 56 in the valve chamber 150 is formed as a second valve seat 349 on which the second Sealing surface 352 of the valve member 344 in its maximum deflected position comes close to the system. The head 346 of the valve member 344 carries a first sealing surface 347 Conical surface and as a second sealing surface 352 a spherical Surface, in a modification of the exemplary embodiment according to FIG. 3. But it could also be a configuration of the head 46 of Figure 2 apply here. On the control room side 125 points out the elastically deformable intermediate part annular, concentric to the through hole 56 Recess 57 with which it is achieved that the elastic deformable intermediate part starting at this annular Recess 57; especially upwards to valve member 344 can be deflected more easily. This property leaves but also through different kinds of reductions in the strength of the Achieve intermediate. This situation is shown in FIG Deflection of the intermediate part shown, but based there a valve with a head 446 of the valve member 444, the 3 is spherical. If the head 446 comes along its second sealing surface in contact with the second Valve seat 349 can be located in the control chamber 25 Build up high pressure fuel pressure prevailing high pressure. Was in the position of the valve member 344 of Figure 5 the Valve chamber 150 exposed to the same pressure as that Control room 125, so prevail in the position according to FIG. 6 now different pressures such that the elastic deformable intermediate part 55 now towards the valve member 444 is deformed. This process is shown in FIG shown. In one another, one above the other lying diagram parts above is the lifting movement of the Injection valve member 14 reproduced, again with the Area of the pre-injection VE, the injection break SU and the Main injection HE. In the lower part of the diagram is with curve M the movement of the elastic intermediate part played. With a starting position hm0 is referred to the travel of the valve member 444 the intermediate part with the second valve seat 349 brought into a position hm1. The begins at the end of the stroke of valve member 444 if the valve member starting from the initial position V0 in the Position hm0 comes into contact with the intermediate part. is this position is reached together with the second valve seat 349 of the intermediate part below Effect of the differential pressure now arising in the Position hm1 brought and remains there as long as that Valve member 444 abuts the second valve seat 349. After that goes from the second one after the valve member 444 is lifted off Valve seat 349 this in its original position hm0 back and valve member 444 as in the diagram below Figure 4 in an intermediate position ZS, in which the control room 125 is relieved and the main injection is carried out. The valve member then moves to its end position V0 back. In the area where the diaphragm is in the direction of the stroke hm1 evades can also decrease the valve member be deflected so that its stroke is different from that original end position hm0 into a common end position hm1 moved back. The one after that to fully open from The valve member 444 stroke to be performed is thus reduced compared to the dashed version of curve V1, which is without elastic deflection of the intermediate part would set. Because immediately after taking off from the second valve seat 349 both parts, the valve member 444 and the elastically deformable intermediate part 55, a stroke in Performing an opening sense results in a very great deal here quick relief of the control room 125 for the Execution of the main injection. The requirements for the The maximum stroke of the piezo is therefore less, since the actual closing force to the second valve seat 349 itself along with the deformation of the elastically deformable In between sets. This is essential advantageous because of the size of a piezo drive and the provided energy with the size of the required Stroke increases significantly. In the way shown here can the required stroke with the same power of the Control valve can be reduced.

Im vorstehenden waren verschiedene Ausführungsformen des Vencilgliedes wiedergegeben. Dazu zeigt Figur 8 noch eine Variante mit einem Kopf 546 des Ventilgliedes 544, der als erste und zweite Dichtfläche jeweils eine kegelförmige Dichtfläche 547 un 552 hat. Entsprechend sind die Ventilsitze ausgebildet. Letztendlich ist es auch möglich, statt einer kegelförmigen zweiten Dichtfläche 552 auch eine Flachsitzdichtfläche zu verwirklichen, mit entsprechend ausgebildeten zweiten Ventilsitz.Various embodiments of the Vencillied reproduced. Figure 8 shows another Variant with a head 546 of the valve member 544, which as first and second sealing surface each a conical Has sealing surface 547 and 552. They are accordingly Valve seats trained. Ultimately, it is also possible instead of a conical second sealing surface 552 also one Realize flat seat sealing surface with accordingly trained second valve seat.

In einer Weiterbildung gemäß einem fünften Ausführungsbeispiel kann das Ventilglied 644 von Figur 9 zweiteilig ausgeführt werden, derart, daß es einen Kopf 646 aufweist, der die erste Dichtfläche 647 trägt und auf der dieser Dichtfläche abgewandten Seite eine Führungsfläche 59 hat, an der ein mit dem Ventilglied 644 hydraulisch gekoppeltes zweites Ventilglied 60 geführt wird. Dieses ist im ausgeführten Beispiel als Kugel verwirklicht, die mit einem kugelförmigen, vorzugsweise aber mit einem kegelförmigen zweiten Ventilsitz 649 zusammenwirkt. In der gezeigten Position des Ventilglieds 644 am ersten Ventilsitz 639 wird die Kugel 60 durch den Druck im Steuerraum 625 in Anlage am Ventilglied 644 gehalten. Bei Betätigung kommt diese geführt auf den zweiten Ventilsitz 649 zur Anlage. Mit einer solchen Kugel läßt sich günstig als Normteil eine dichte Passung mit dem Ventilsitz erzielen.In a further development according to a fifth embodiment can the valve member 644 of Figure 9 in two parts be carried out in such a way that it has a head 646, which carries the first sealing surface 647 and on which this Side facing away from the sealing surface has a guide surface 59 which is hydraulically coupled to the valve member 644 second valve member 60 is guided. This is in the executed example realized as a ball with a spherical, but preferably with a conical second valve seat 649 cooperates. In the shown Position of the valve member 644 on the first valve seat 639 the ball 60 by the pressure in the control room 625 in contact Valve member 644 held. When actuated, this comes out on the second valve seat 649 to the system. With one Ball can be used as a standard part with a tight fit achieve the valve seat.

Claims (16)

  1. Fuel injection device for internal combustion engines, having a high-pressure fuel source (1), from which fuel is supplied to a fuel injection valve (9) which has an injection valve member for controlling injection openings (12) and a control space (25), which is delimited by a movable wall (23), which is at least indirectly connected to the injection valve member (14), and which has an inlet passage (26), which is dimensioned by means of a throttle and originates from a high-pressure source, preferably from the high-pressure fuel source (1), and an outlet passage (29) with a defined maximum outlet cross section to a relief space (30), at which outlet passage a valve seat (39) is formed, which valve seat is controlled by a sealing surface (47) of a valve member (44, 46) of a control valve (36) which is actuated by a piezo (35), the valve seat (39) being arranged at the outlet passage (129) so as to face towards the control space (25), and the piezo (35) lifting the valve member (44, 46) off the valve seat (39), counter to the pressure prevailing in the control space (25), in order to open the outlet passage (129) towards the control space (25), and the valve member (44, 46) being acted on in the closing direction by the pressure in the control space (25), characterized in that the valve seat at the outlet passage is a first valve seat (139), and on the control space side of this first valve seat there is a second valve seat (49), which delimits the outlet cross section of the outlet passage (229) and is closed off by an additional, second sealing surface (152), which is moved by the valve member (144, 146) under the influence of the actuation by the piezo after the valve member (144, 146) has lifted off the first valve seat (139).
  2. Fuel injection device according to Claim 1, characterized in that the distance between the first valve seat (139) and the second valve seat (49) is such that, in an intermediate position of the valve member (144, 146), the outlet cross sections at both valve seats are open.
  3. Fuel injection device according to Claim 2, characterized in that the valve seats (139, 49) are arranged coaxially with respect to one another.
  4. Fuel injection device according to Claim 3, characterized in that the valve member (44, 144, 344, 444, 544, 644) has a head (46, 146, 346, 446, 546, 646) which bears at least one of the sealing surfaces (47, 52, 152, 147, 347, 352, 547, 552, 647) and is arranged at the end of a rod (45) which projects through the cross section of the outlet passage which is delimited by the first valve seat (39, 139) and, between itself and the first valve seat, defines the largest outlet cross section.
  5. Fuel injection device according to Claim 4, characterized in that the second sealing surface (152) and the second valve seat (49) together form a seat valve, and the valve member (144, 146), when the seat valve is closed, is acted on in the opening direction by the pressure in the control space (25).
  6. Fuel injection device according to Claim 1, characterized in that the second valve seat (349), together with a connecting cross section which leads onwards to the control space (25), are formed on an intermediate part (55), which is elastically deformable in the region of the second valve seat (349) and at its edges is clamped fixedly between parts of the housing (11) of the fuel injection valve.
  7. Fuel injection device according to Claim 6, characterized in that the intermediate part (55) is formed as a diaphragm.
  8. Fuel injection device according to Claim 7, characterized in that the diaphragm is a metal diaphragm, the deformability of which is increased by regions of reduced diaphragm thickness, in particular by annular recesses (57) which lie concentrically with respect to the second valve seat.
  9. Fuel injection device according to one of the preceding claims, characterized in that the maximum outlet cross section is formed by a throttle (42).
  10. Fuel injection device according to one of Claims 1 to 9, characterized in that the first valve seat is designed as a conical valve seat (39, 139).
  11. Fuel injection device according to Claim 10, characterized in that the second valve seat is formed as a ball seat.
  12. Fuel injection device according to Claim 10, characterized in that the second valve seat (552, 649) is formed as a conical seat.
  13. Fuel injection device according to Claim 10, characterized in that the second valve seat is formed as a flat seat.
  14. Fuel injection device according to Claim 10, characterized in that the second sealing surface is formed on a part (60) which is actuated by the valve member and, under the pressure in the control space (25), comes to bear against the valve member (644, 646).
  15. Fuel injection device according to Claim 14, characterized in that the second sealing surface is formed on a ball (60) which is guided on a guide surface (59) of the valve member (644, 646).
  16. Fuel injection device according to one of Claims 4 to 15, characterized in that the rod (45) is guided in a bore (43), which runs coaxially with respect to the valve seats and between which and the first valve seat there is delimited a space (40) via which the outlet passage (129) leads to the relief space (30, 32, 4).
EP97906987A 1996-06-15 1997-01-09 Fuel injection device for internal combustion engines Expired - Lifetime EP0845077B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19624001A DE19624001A1 (en) 1996-06-15 1996-06-15 Fuel injection device for internal combustion engines
DE19624001 1996-06-15
PCT/DE1997/000019 WO1997048900A1 (en) 1996-06-15 1997-01-09 Fuel injection device for internal combustion engines

Publications (2)

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EP0845077A1 EP0845077A1 (en) 1998-06-03
EP0845077B1 true EP0845077B1 (en) 2003-01-22

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US (1) US5975428A (en)
EP (1) EP0845077B1 (en)
JP (1) JP3916670B2 (en)
KR (1) KR100482901B1 (en)
CN (2) CN1184416C (en)
BR (1) BR9702305A (en)
DE (2) DE19624001A1 (en)
ES (1) ES2191169T3 (en)
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WO (1) WO1997048900A1 (en)

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WO1997048900A1 (en) 1997-12-24
JPH11510879A (en) 1999-09-21
KR100482901B1 (en) 2005-08-04
JP3916670B2 (en) 2007-05-16
CN1358934A (en) 2002-07-17
CN1189877A (en) 1998-08-05
BR9702305A (en) 1999-03-02
US5975428A (en) 1999-11-02
CN1080825C (en) 2002-03-13
KR19990036336A (en) 1999-05-25
RU2170846C2 (en) 2001-07-20
DE59709189D1 (en) 2003-02-27
ES2191169T3 (en) 2003-09-01
EP0845077A1 (en) 1998-06-03
CN1184416C (en) 2005-01-12
DE19624001A1 (en) 1997-12-18

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