EP1747370B1 - Fuel-injection valve for internal combustion engines - Google Patents

Fuel-injection valve for internal combustion engines Download PDF

Info

Publication number
EP1747370B1
EP1747370B1 EP05701547A EP05701547A EP1747370B1 EP 1747370 B1 EP1747370 B1 EP 1747370B1 EP 05701547 A EP05701547 A EP 05701547A EP 05701547 A EP05701547 A EP 05701547A EP 1747370 B1 EP1747370 B1 EP 1747370B1
Authority
EP
European Patent Office
Prior art keywords
valve
needle
outer needle
fuel
fuel injection
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Not-in-force
Application number
EP05701547A
Other languages
German (de)
French (fr)
Other versions
EP1747370A1 (en
Inventor
Dieter Junger
Joerg-Peter Fischer
Thilo Kreher
Jens-Peter Nagel
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 EP1747370A1 publication Critical patent/EP1747370A1/en
Application granted granted Critical
Publication of EP1747370B1 publication Critical patent/EP1747370B1/en
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

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
    • 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
    • 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
    • F02M45/08—Injectors peculiar thereto
    • F02M45/086—Having more than one injection-valve controlling discharge orifices
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/46—Valves, e.g. injectors, with concentric valve bodies
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
    • F02M2547/001—Control chambers formed by movable sleeves

Definitions

  • the invention is based on a fuel injection valve for internal combustion engines, as disclosed in the published patent application DE 102 05 970 A1 is known.
  • a valve outer needle and a valve inner needle are arranged, both of which are longitudinally displaceable, wherein the valve inner needle is arranged in the valve outer needle.
  • the valve needles cooperate with a correspondingly formed sealing surface with a valve seat and in this case in each case control the opening of at least one injection opening.
  • a pressure surface is formed, which exerts a directed away from the valve seat opening force on the respective valve needle upon application of fuel pressure.
  • a control chamber is formed in the housing, by the pressure of which an opening force opposing closing force is exerted on the valve outer needle and the valve inner needle.
  • the control chamber is in this case filled with fuel under pressure, wherein the pressure in the control chamber via a valve can be regulated.
  • valve outer needle In the known fuel injection valve, the valve outer needle is constantly acted upon by fuel, which is under injection pressure. With a pressure relief in the control chamber, the valve outer needle opens and releases the injection openings. Only then is the valve inner needle and its pressure surface acted upon by the fuel pressure, so that the valve inner needle opens after the valve outer needle.
  • the known fuel injection valve in this case has the disadvantage that the fuel pressure in the space between the valve outer needle and the valve inner needle periodically fluctuates, so that the valve outer needle is pressed more or less radially depending on the pressure difference radially inward. As a result, the sliding friction between the valve inner needle and the valve outer needle is changed, which can lead to increased wear or to a pinching of the valve outer needle on the valve inner needle. In addition, it is not possible to open the valve inner needle in front of the valve outer needle, which is advantageous in certain operating states of the internal combustion engine. Furthermore, the known fuel injection valve has the disadvantage that the valve needles close one after the other. Such successive closing of the valve needles causes low pressure fuel to enter the combustion chamber through the injection ports, resulting in an increase in hydrocarbon emissions there. This is especially the case when the valve outlet needle 1 closes in front of the valve inner needle.
  • the fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the valve inner needle can open in front of the valve outer needle, which allows a greater freedom of design in the Einspritzverlaufsformung.
  • the control room is possible with only one control room.
  • the valve inner needle and the valve outer needle are always acted upon by the fuel of the Zulaufraums, thereby resulting in a closing force opposing opening force on the valve needles. Since a different opening pressure of the valve outer needle and the valve inner needle can be achieved via a suitable design of the respective pressurized surfaces on the valve needles, the valve inner needle can open in front of the valve outer needle via the pressure control in the control room.
  • the intermediate space between the valve outer needle and the valve inner needle is always hydraulically connected to the inlet space.
  • the inner pressure surface is acted upon by the pressure of the intermediate space, so that the desired opening force results on the inner valve needle.
  • Due to the pressure connection of the intermediate space with the inlet space a deformation of the valve outer needle due to pressure differences on the outside and inside of the valve outer needle is avoided, so that the friction between the valve outer needle and valve inner needle always remains low and there is no jamming or excessive rubbing between the two Valve needles can come.
  • this connection is made via a connecting bore, which runs essentially radially in the valve outer needle and of which preferably several are distributed over the circumference of the valve outer needle.
  • a shoulder is formed on the inside of the valve outer needle, which is the inner pressure shoulder of the valve inner needle opposite.
  • the axial distance of the shoulder of the inner pressure shoulder is dimensioned so that when the inner valve needle and the valve outer needle on the valve seat, the inner pressure shoulder remains spaced from the paragraph.
  • valve outer needle is formed by the abutment of the shoulder on the inner pressure surface. This results in open valve needles to a Pressure drop in the space, which presses the valve outer needle by the pressure forces on the valve inner needle, so that a lead of the valve outer needle is prevented in the closing movement. Thus, a synchronous closing of the valve inner needle and valve outer needle is ensured.
  • the axial distance of the shoulder of the inner pressure surface is such that it is smaller with open valve needles than the opening stroke of the valve inner needle.
  • a valve sealing surface is formed with two sealing edges on the valve outer needle, wherein the outer sealing edge upstream and the inner sealing edge downstream of the outer injection port on the valve seat come to rest. This ensures that the outer injection opening are closed hydraulically even when the inner valve needle is open and no fuel can pass uncontrollably through this into the combustion chamber.
  • a control volume is formed between the valve outer needle and the valve inner needle, which serves as a hydraulic driver.
  • FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section.
  • the fuel injection valve 1 has a holding body 3, which is only partially shown, a throttle plate 5 and a valve body 7, which are pressed by a device, not shown, in this order.
  • an inlet chamber 12 is formed, which is formed substantially as a stepped bore, which is bounded at its combustion-chamber end by a substantially conical valve seat 20.
  • From the valve seat 20 go outside injection openings 22 and inner injection openings 24, which open into the installation position of the fuel injection valve in the combustion chamber of the internal combustion engine.
  • the outer injection openings 22 in this embodiment have a larger diameter than the inner injection openings 24.
  • a valve outer needle 15 is arranged, which is designed as a hollow needle and thus has an inner wall 31 and at its valve seat side end has a substantially conical outer valve sealing surface 18.
  • a collar 62 is formed in a central region, with which it is guided in a guide portion 60 of the inlet chamber 12, whereby the valve outer needle 15 in the inlet space 12 is longitudinally displaceable.
  • the valve outer needle 15 cooperates with its outer valve sealing surface 18 with the valve seat 20 in such a way that the outer injection openings 22 are thereby closed or released.
  • the outer valve sealing surface 18 has an outer sealing edge 25 and an inner sealing edge 27, so that the outer injection openings 22 are sealed both upstream and downstream when the valve outer needle 15 rests on the valve seat 20.
  • 62 bevels 64 are formed on the collar, whose cross-section and number is dimensioned so that a throttling-free flow of fuel to the injection openings 22, 24 is possible.
  • a piston-shaped valve inner needle 17 is arranged longitudinally displaceable, which is guided with a valve seat facing away from cylindrical projection 44 in the valve outer needle 15.
  • the valve inner needle 17 is guided in a direction to the valve seat 20 arranged second guide 45 in the valve outer needle 15, so that an exactly axial movement of Ventilinnennade1 17 is ensured.
  • On the guide 45 while passages are formed, for example in the form of polished sections, which allow a largely unthrottled fuel flow in the direction of the valve seat 20 in the space 50 formed between the valve inner needle 17 and the valve outer needle 15.
  • the valve inner needle 17 has at its valve seat side end an inner valve sealing surface 19, with which it cooperates with the valve seat 20 and in this case controls the opening of the inner injection openings 24 in the same way as the valve outer needle 15, the outer injection openings 22nd
  • a control chamber 28 which is filled with fuel and whose pressure is controllable.
  • the control chamber 28 is connected via a formed in the throttle plate 15 inlet throttle 34 with a Zulautkanal 9, via which the inlet chamber 12 can be filled with fuel at high pressure.
  • an outlet throttle 36 is formed, via which the control chamber 28 can be connected to a fuel tank 42, wherein the fuel tank 42 is always a low fuel pressure prevails.
  • a control valve 40 is arranged, which opens and closes the connection.
  • the control valve 40 is formed in the embodiment shown as a 2/2-way valve.
  • an inner closing spring 30 is arranged under pressure bias, which is supported on a spring paragraph 54 of the valve inner needle 17 and at the other end to the throttle plate 5.
  • an outer closing spring 32 is arranged in the inlet chamber 12, which is supported at one end to the sleeve 26 and at the other end to a ring 35 which rests on the valve outer needle 15. Due to the pressure bias of the outer closing spring 32 acts on the valve outer needle 15 a closing force in the direction of the valve seat 20.
  • the closing spring 32 is further dimensioned so that the closing force on the valve outer needle 15 is sufficient to seal in the closed position both sealing edges 25, 27 against the valve seat 20, even at a low pressure in the control chamber 28 and thus lower hydraulic closing force.
  • a small wall thickness to the inner wall 31 is provided in the region of the sealing edge 27.
  • a connecting bore 38 is formed, which connects the inlet chamber 12, in which there is always a high fuel pressure, with the intermediate space 50.
  • an inner pressure surface 48 of the valve inner needle 17 which is formed on the valve seat side to the connecting bore 38 on the valve inner needle 17, acted upon by the fuel pressure of the inlet chamber 12. This results in a hydraulic force that points away from the valve seat 20 and the force of the inner closing spring 30 is opposite.
  • a shoulder 47 is formed on the inside of the valve outer needle 15, which in the closed position of the valve outer needle 15 and the valve inner needle 17, that is, when they are in contact with the valve seat 20, axially spaced from the inner pressure surface 48. This distance is in FIG.
  • an outer pressure surface 49 is formed in the same way, which is acted upon by the fuel pressure in the inlet chamber 12, whereby the valve outer needle 15 undergoes a closing force of the outer closing spring 32 opposite opening force.
  • the bevels 64 on the collar 62 ensures that the outer pressure surface 49 is always acted upon by the full fuel pressure.
  • the operation of the fuel injection valve is as follows: At the beginning of the injection, the control valve 40 is closed, so that the connection of the control chamber 28 is interrupted with the fuel tank 42. As a result, the same pressure builds up on the inlet throttle 34 in the control chamber 28 as in the inlet chamber 12, which is always kept at a high fuel pressure due to its connection via the inlet channel 9. The pressure in the control chamber 28 results in a hydraulic force on the valve seat facing away from end 56 and the spring paragraph 54 of the valve inner needle 17 and the end face 58 of the valve outer needle 15.
  • valve outer needle 15 and the valve inner needle 17 are by the differential pressure from the hydraulic pressure in the control chamber 28 and in the Pressure chamber 12 on the one hand and the combustion chamber pressure on the other hand, which acts on the inner valve sealing surface 19 and the outer valve sealing surface 18 in part, held in addition to the force of the closing springs 30,32 in its closed position.
  • the surface of the end faces 56, 58, the valve sealing surfaces 19, 23 and the other acted upon by the fuel pressure in the pressure chamber 12 surfaces of the valve inner needle 17 and the valve outer needle 15 are designed accordingly.
  • the control valve 40 is opened, whereby fuel flows from the control chamber 28 via the outlet throttle 36 and the fuel pressure drops there.
  • the hydraulic force on the end face 56 of the valve inner needle 17 is lowered, so that the valve inner needle 17, driven by the hydraulic forces on the inner pressure surface 48 and on parts of the inner valve sealing surface 19, lifts off from the valve seat 20 until after passing through an opening stroke hi End 56 comes to rest on the throttle plate 5.
  • This position of the fuel injection valve is in FIG. 3 shown.
  • the fuel path from the inlet space 12 through the connecting bore 38 and the intermediate space 50 and between the inner valve sealing surface 19 and the valve seat 20 to the inner injection openings 24 is thereby controlled, so that a fuel injection takes place through the inner injection openings 24.
  • the formed on the outer valve sealing surface 18 sealing edges 25, 27 seal the outer injection openings 22, whereby they remain closed as before.
  • the opening pressure of the valve outer needle 15 is finally reached, ie the pressure at which the hydraulic closing force on the end face 58 and on the shoulder 47 and the force of the closing spring 32 are smaller than the sum
  • the valve opening needle 15 lifts off from the valve seat 20 and passes through an opening stroke h a , until it comes to rest with its end face 58 on the throttle plate 5 the hydraulic opening forces on the outer pressure surface 49 and the fuel.
  • This position of the Fuel injection valve is in FIG. 4 shown.
  • the opening stroke in the Ventilau strau strimade1 15 is in this case dimensioned so that in its open position, an axial distance between the shoulder 47 and the inner pressure surface 48 remains.
  • valve outer needle 15 again reach its closed position earlier, whereby less fuel enters the combustion chamber.
  • this open position flows to a fuel through the connecting bore 38 and the gap 50 and by polished on the second guide 45 through to the inner injection ports 24 and on the other hand fuel from the feed chamber 12 through the bevels 64 between the outer valve sealing surface 18 and the valve seat 20 therethrough to the outer injection openings 22, so that fuel is now injected through all the injection openings in the combustion chamber.
  • all injection ports 22, 24 are optimally supplied with fuel, so that at full pressure, a large amount of fuel can be introduced in a short time in the combustion chamber.
  • control valve 40 is closed so that the fuel pressure in the control chamber 28 increases again via the fuel flowing in through the inlet throttle 34.
  • the valve needles begin their closing movement after exceeding the respective closing pressure in the control chamber 28, wherein the closing pressure of the valve outer needle 15 is reached earlier than that of the valve inner needle 17. This is due to the fact that the force of the outer closing spring 32 is higher and the other in it in that the hydraulic pressure forces on the outer valve sealing face 18 are lower than the hydraulic pressure forces on the inner valve needle 17 due to the throttling of the fuel flow flowing from the inlet chamber 12 in the direction of the outer injection openings 22.
  • the pressure in the control chamber 28 remains during the closing movement of the Valve outer needle 15 at least approximately constant, since the fuel flow over the inlet throttle 34 and the enlargement of the control chamber 28 compensate.
  • the throttling on the outer valve sealing surface 18 increases, resulting in an accelerated closing valve outer needle 15 results.
  • FIG. 5 and FIG. 6 an alternative embodiment of the inner pressure surface 48 and the heel 47 is shown.
  • Both the shoulder 47 and the inner pressure surface 48 are preferably formed as conical surfaces, but not here, as in the Figures 2 . 3 and 4 shown, have the same opening angle, but in which the opening angle of the inner pressure surface 48 is greater than the opening angle of the shoulder 47.
  • the axial relationship between the inner pressure surface 48 and the shoulder 47 on the one hand and the end face 58 of the valve outer needle 15 on the other hand is designed so that between the end face 58 and the throttle plate 5 always a gap remains. This condition is in FIG. 6 shown.
  • valve outer needle 15 of the shoulder 47 rests on the inner pressure surface 48, there forms a sealing edge 51, whereby a lower pressure corresponding to the pressure conditions in the region of the valve seat 20 is established in the intermediate space 50. Due to the now lower pressure in the intermediate space 50, both with respect to the pressure in the inlet chamber 12 and with respect to the pressure in the control chamber 28, a greater closing force results on closing the valve inner needle 17.
  • the valve outer needle 15 acts a pressing force on the outer pressure surface 49, which is acted upon by the pressure of the inlet chamber 12, so that the closing movement of the valve outer needle 15 is delayed accordingly. This prevents that in the closing movement the valve outer needle 15 leads and the valve inner needle 17 closes later than this, which is otherwise favored by the ever greater seat throttling and the pressure reduction caused thereby on the outer valve sealing surface 18.
  • FIG. 7 and FIG. 8 is shown a further embodiment, which will be discussed below only the differences from the previous embodiments.
  • the inlet throttle 34 is arranged here in the throttle disk 5, that the valve inner needle 17, the inlet throttle 34 when it rests on the throttle plate 5 partially or completely closes.
  • the end face 56 of the valve inner needle 17 is formed as a surface parallel to the throttle plate 5 and provided with a biting edge 55, which ensures a sufficient seal at this point. Due to the partial or complete prohibition of the fuel flow through the inlet throttle 34 into the control chamber 28, the pressure in the control chamber 28 drops rapidly due to the outflow through the outlet throttle 36 until a control chamber pressure is reached at which the valve outer needle 15 also opens Valve outer needle 15 already shortly after the complete opening of the valve inner needle 17 to open.
  • a 3/2-way valve is provided here as a control valve 40 'such that in the first switching position the outlet throttle 36 connects to the fuel tank 42, while in the second switching position the outlet throttle is connected to the inlet channel 9.
  • the control valve 40 ' is brought into its second switching position, so that via the outlet throttle 36 fuel flows into the control chamber 28.
  • FIG. 9 is a further embodiment shown, in which the interaction of the valve inner needle 17 and valve outer needle 15 is hydraulically.
  • valve inner needle 17 and valve outer needle 15 By the control volume 53, a hydraulic damping of the relative movement between the valve inner needle 17 and valve outer needle 15 can be generated, which causes a reduced opening speed of the valve inner needle 17 due to the rapidly decreasing pressure in the control volume 53 and the lack of opening force on the inner pressure surface 48th Die Gottsbohrept 38 Sind between the other cylindrical projection 39 and the valve seat 20 to be arranged to ensure an unthrottled inlet to the gap 50.
  • the opening time of the valve outer needle 15 is to be set advantageously at a time after completion of the opening of the valve inner needle 17, which in combination with the in FIG. 7 and FIG. 8 illustrated embodiment can be ensured. As a result, the opening movement of the valve outer needle 15 is also damped without a sudden opening takes place.
  • valve outer needle 15 undergoes a partial stroke of the total stroke h a of the valve outer needle 15, whereby the opening duration of the valve outer needle 15 and the valve inner needle 17 is extended and the injection quantity increases proportionally.
  • control valve 40 'closed which is also designed here as a 3/2-way valve
  • the pressure in the control chamber 28 increases, causing the valve outer needle 15 first runs loose due to the larger seat throttling, but the valve inner needle 17 is due to the pressure reduction in the control volume 53, which is increased by the movement of the valve outer needle 15 and the resulting opening force on the inner pressure surface 48, taken in the direction of valve seat 20.
  • the closing order between the valve inner needle 17 and valve outer needle 15 is dependent on the drive time and the vote between the stroke of the valve inner needle 17 and the valve outer needle 15.
  • the stroke h a of the valve outer needle 15 is preferably so on the stroke h i of the valve inner needle 17 vote that at maximum injection quantity close the valve inner needle 17 and valve outer needle 15 at the same time and thus the shortest possible injection duration for the desired injection quantity is possible.
  • valve outer needle 15 does not come into abutment against a fixed stop at the maximum injection quantity.
  • the valve outer needle 15 throttles the fuel flow at the beginning of their ⁇ réelleshubiolo. If the valve outer needle 15 moves out of this throttle region, the fuel flow from the inlet chamber 12 to the injection openings 22, 24 is largely independent of the stroke of the valve outer needle 15. A stop can thus be dispensed with and the pressure in the control chamber 28 is increased in a timely manner, that the valve outer needle 15 remains in ballistic operation. This also leads to a reduction of the noise, since the stop of the valve outer needle 15 is omitted.
  • valve outer needle 15 Furthermore, a complex production of a targeted opening stroke of the valve outer needle 15 is not necessary. Also, a discontinuous movement due to a bounce at the stop can be avoided, which has a negative effect on the set characteristic curve.

Abstract

A fuel injection valve, having an outer valve needle cooperating with a valve seat for opening and closing at least one outer injection opening, an inner valve needle disposed in the outer valve needle and cooperating with the valve seat for opening and closing at least one inner injection opening. The fuel pressure in a control chamber that can be filled with fuel under pressure acts on the outer valve needle and the inner valve needle in such a way that a closing force in the direction of the valve seat is exerted on the inner valve needle and the outer valve needle. An inner pressure face disposed on the inner valve needle and a shoulder is disposed on the outer valve needle, which each, on being subjected to pressure, exert a hydraulic opening force, oriented counter to the closing force, on the inner valve needle and the outer valve needle. The outer valve needle is at least partly surrounded by an inflow chamber, in which fuel under pressure is always present, and the inner pressure face and the outer pressure face are always subjected to the fuel of the inflow chamber.

Description

Stand der TechnikState of the art

Die Erfindung geht von einem Kraftstoffeinspritzventil für Brennkraftmaschinen aus, wie es aus der Offenlegungsschrift DE 102 05 970 A1 bekannt ist. In dem Kraftstoffeinspritzventil ist eine Ventilaußennadel und eine Ventilinnennadel angeordnet, die beide längsverschiebbar sind, wobei die Ventilinnennadel in der Ventilaußennadel angeordnet ist. Die Ventilnadeln wirken mit einer entsprechend ausgebildeten Dichtfläche mit einem Ventilsitz zusammen und steuern hierbei jeweils die Öffnung wenigstens einer Einspritzöffnung. Sowohl an der Ventilaußennadel als auch an der Ventilinnennadel ist jeweils eine Druckfläche ausgebildet, die bei Beaufschlagung mit Kraftstoffdruck eine vom Ventilsitz weggerichtete Öffnungskraft auf die jeweilige Ventilnadel ausübt. Darüber hinaus ist im Gehäuse ein Steuerraum ausgebildet, durch dessen Druck eine der Öffnungskraft entgegengerichtete Schließkraft auf die Ventilaußennadel und die Ventilinnennadel ausgeübt wird. Der Steuerraum ist hierbei mit Kraftstoff unter Druck befüllbar, wobei der Druck im Steuerraum über ein Ventil regelbar ist.The invention is based on a fuel injection valve for internal combustion engines, as disclosed in the published patent application DE 102 05 970 A1 is known. In the fuel injection valve, a valve outer needle and a valve inner needle are arranged, both of which are longitudinally displaceable, wherein the valve inner needle is arranged in the valve outer needle. The valve needles cooperate with a correspondingly formed sealing surface with a valve seat and in this case in each case control the opening of at least one injection opening. Both on the valve outer needle and the valve inner needle in each case a pressure surface is formed, which exerts a directed away from the valve seat opening force on the respective valve needle upon application of fuel pressure. In addition, a control chamber is formed in the housing, by the pressure of which an opening force opposing closing force is exerted on the valve outer needle and the valve inner needle. The control chamber is in this case filled with fuel under pressure, wherein the pressure in the control chamber via a valve can be regulated.

Beim bekannten Kraftstoffeinspritzventil wird die Ventilaußennadel von Kraftstoff ständig beaufschlagt, der unter Einspritzdruck steht. Bei einer Druckentlastung im Steuerraum öffnet sich die Ventilaußennadel und gibt die Einspritzöffnungen frei. Erst danach wird die Ventilinnennadel und deren Druckfläche vom Kraftstoffdruck beaufschlagt, so dass die Ventilinnennadel nach der Ventilaußennadel öffnet.In the known fuel injection valve, the valve outer needle is constantly acted upon by fuel, which is under injection pressure. With a pressure relief in the control chamber, the valve outer needle opens and releases the injection openings. Only then is the valve inner needle and its pressure surface acted upon by the fuel pressure, so that the valve inner needle opens after the valve outer needle.

Ein ähnliches Kraftstoffeinspritzventil ist aus der US 5899389 auch bekannt.A similar fuel injection valve is out of the US 5899389 also known.

Das bekannte Kraftstoffeinspritzventil weist hierbei den Nachteil auf, dass der Kraftstoffdruck im Zwischenraum zwischen der Ventilaußennadel und der Ventilinnennadel periodisch schwankt, so dass die Ventilaußennadel je nach Druckdifferenz mehr oder weniger stark radial nach innen gepresst wird. Dadurch wird die Gleitreibung zwischen der Ventilinnennadel und der Ventilaußennadel verändert, was zu einem erhöhten Verschleiß oder zu einem Klemmen der Ventilaußennadel auf der Ventilinnennadel führen kann. Darüber hinaus ist es nicht möglich, die Ventilinnennadel vor der Ventilaußennadel zu öffnen, was bei bestimmten Betriebszuständen der Brennkraftmaschine vorteilhaft ist. Weiter weist das bekannte Kraftstoffeinspritzventil den Nachteil auf, dass die Ventilnadeln nacheinander schließen. Ein solch sukzessives Schließen der Ventilnadeln bewirkt, dass Kraftstoff mit niedrigem Druck durch die Einspritzöffnungen in den Brennraum gelangen kann, was dort zu einer Erhöhung der Kohlenwasserstoff-Emissionen führt. Dies ist insbesondere dann der Fall, wenn die Ventilaußennade1 vor der Ventilinnennadel schließt.The known fuel injection valve in this case has the disadvantage that the fuel pressure in the space between the valve outer needle and the valve inner needle periodically fluctuates, so that the valve outer needle is pressed more or less radially depending on the pressure difference radially inward. As a result, the sliding friction between the valve inner needle and the valve outer needle is changed, which can lead to increased wear or to a pinching of the valve outer needle on the valve inner needle. In addition, it is not possible to open the valve inner needle in front of the valve outer needle, which is advantageous in certain operating states of the internal combustion engine. Furthermore, the known fuel injection valve has the disadvantage that the valve needles close one after the other. Such successive closing of the valve needles causes low pressure fuel to enter the combustion chamber through the injection ports, resulting in an increase in hydrocarbon emissions there. This is especially the case when the valve outlet needle 1 closes in front of the valve inner needle.

Vorteile der ErfindungAdvantages of the invention

Das erfindungsgemäße Kraftstoffeinspritzventil mit den kennzeichnenden Merkmalen des Patentanspruchs 1 weist demgegenüber den Vorteil auf, dass die Ventilinnennadel vor der Ventilaußennadel öffnen kann, was eine größere Auslegungsfreiheit bei der Einspritzverlaufsformung erlaubt. Darüber hinaus ist die Steuerraum mit nur einem Steuerraum möglich. Hierzu werden die Ventilinnennadel und die Ventilaußennadel stets vom Kraftstoff des Zulaufraums so beaufschlagt, dass sich dadurch eine der Schließkraft entgegengerichtete Öffnungskraft auf die Ventilnadeln ergibt. Da über eine geeignete Auslegung der jeweils druckbeaufschlagten Flächen an den Ventilnadeln ein unterschiedlicher Öffnungsdruck der Ventilaußennadel und der Ventilinnennadel erreicht werden kann, kann über die Druckregelung im Steuerraum die Ventilinnennadel vor der Ventilaußennadel öffnen.The fuel injection valve according to the invention with the characterizing features of claim 1 has the advantage over that the valve inner needle can open in front of the valve outer needle, which allows a greater freedom of design in the Einspritzverlaufsformung. In addition, the control room is possible with only one control room. For this purpose, the valve inner needle and the valve outer needle are always acted upon by the fuel of the Zulaufraums, thereby resulting in a closing force opposing opening force on the valve needles. Since a different opening pressure of the valve outer needle and the valve inner needle can be achieved via a suitable design of the respective pressurized surfaces on the valve needles, the valve inner needle can open in front of the valve outer needle via the pressure control in the control room.

Durch die Unteransprüche sind vorteilhafte Weiterbildungen des Gegenstandes der Erfindung möglich. In einer ersten vorteilhaften Ausgestaltung ist der Zwischenraum zwischen der Ventilaußennadel und der Ventilinnennadel stets mit dem Zulaufraum hydraulisch verbunden. Hierbei wird die innere Druckfläche vom Druck des Zwischenraums beaufschlagt, so dass sich die gewünschte Öffnungskraft auf die Ventilinnennadel ergibt. Durch die Druckanbindung des Zwischenraums mit dem Zulaufraum wird darüber hinaus eine Verformung der Ventilaußennadel aufgrund von Druckunterschieden an der Außen- und Innenseite der Ventilaußennadel vermieden, so dass die Reibung zwischen Ventilaußennadel und Ventilinnennadel stets gering bleibt und es zu keinem Klemmen oder übermäßigem Reiben zwischen diesen beiden Ventilnadeln kommen kann. Vorteilhafterweise wird diese Verbindung über eine Verbindungsbohrung hergestellt, die im Wesentlichen radial in der Ventilaußennadel verläuft und von der vorzugsweise mehrere über den Umfang der Ventilaußennadel verteilt angeordnet sind.The subclaims advantageous developments of the subject invention are possible. In a first advantageous embodiment, the intermediate space between the valve outer needle and the valve inner needle is always hydraulically connected to the inlet space. In this case, the inner pressure surface is acted upon by the pressure of the intermediate space, so that the desired opening force results on the inner valve needle. Due to the pressure connection of the intermediate space with the inlet space, a deformation of the valve outer needle due to pressure differences on the outside and inside of the valve outer needle is avoided, so that the friction between the valve outer needle and valve inner needle always remains low and there is no jamming or excessive rubbing between the two Valve needles can come. Advantageously, this connection is made via a connecting bore, which runs essentially radially in the valve outer needle and of which preferably several are distributed over the circumference of the valve outer needle.

In einer weiteren vorteilhaften Ausgestaltung des Gegenstandes der Erfindung ist an der Innenseite der Ventilaußennadel ein Absatz ausgebildet, dem die innere Druckschulter der Ventilinnennadel gegenüber liegt. Hierbei ist der axiale Abstand des Absatzes von der inneren Druckschulter so bemessen, dass bei Anlage der Ventilinnennadel und der Ventilaußennadel auf dem Ventilsitz die innere Druckschulter von dem Absatz beabstandet bleibt. Hierdurch wird ein ungedrosselter Zufluss von Kraftstoff, der oberhalb des Absatzes in dem Zwischenraum eingeleitet wird, zu den inneren Einspritzöffnungen ermöglicht. Besonders vorteilhaft ist es, wenn der Öffnungshub der Ventilinnennadel und der Ventilaußennadel so aufeinander abgestimmt ist, dass die Ventilnadeln in Öffnungsstellung so zueinander positioniert sind, dass der Absatz der Ventilaußennadel weiterhin einen axialen Abstand von der inneren Druckschulter aufweist. Dadurch ist ein ungehinderter und ungedrosselter Zufluss von Kraftstoff zu sämtlichen Einspritzöffnungen sichergestellt Es kann alternativ auch vorgesehen sein, dass der Hubanschlag der Ventilaußennadel durch die Anlage des Absatzes an der inneren Druckfläche gebildet wird. Dadurch kommt es bei geöffneten Ventilnadeln zu einem Druckabfall im Zwischenraum, was die Ventilaußennadel durch die Druckkräfte auf die Ventilinnennadel drückt, so dass ein Voreilen der Ventilaußennadel bei der Schließbewegung verhindert wird. Somit ist ein synchrones Schließen von Ventilinnennadel und Ventilaußennadel sichergestellt.In a further advantageous embodiment of the object of the invention, a shoulder is formed on the inside of the valve outer needle, which is the inner pressure shoulder of the valve inner needle opposite. Here, the axial distance of the shoulder of the inner pressure shoulder is dimensioned so that when the inner valve needle and the valve outer needle on the valve seat, the inner pressure shoulder remains spaced from the paragraph. As a result, an unthrottled inflow of fuel, which is introduced above the shoulder in the intermediate space, made possible to the inner injection openings. It when the opening stroke of the valve inner needle and the valve outer needle is coordinated so that the valve needles are positioned in the open position to each other so that the shoulder of the valve outer needle further has an axial distance from the inner pressure shoulder is particularly advantageous. This ensures an unhindered and unthrottled inflow of fuel to all injection openings. It may alternatively also be provided that the stroke stop of the valve outer needle is formed by the abutment of the shoulder on the inner pressure surface. This results in open valve needles to a Pressure drop in the space, which presses the valve outer needle by the pressure forces on the valve inner needle, so that a lead of the valve outer needle is prevented in the closing movement. Thus, a synchronous closing of the valve inner needle and valve outer needle is ensured.

In einer weiteren vorteilhaften Ausgestaltung ist der axiale Abstand des Absatzes von der inneren Druckfläche so bemessen, dass dieser bei geöffneten Ventilnadeln kleiner ist als der Öffnungshub der Ventilinnennadel. Hierdurch nimmt die Ventilinnennadel bei ihrer Schließbewegung die Ventilaußennadel mit und zwingt diese somit in Richtung des Ventilsitzes. Bei Annäherung der Ventilaußennadel an den Ventilsitz kommt es zu einer starken Drosselung des Kraftstoffstroms zu den äußeren Einspritzöffnungen, so dass sich die hydraulische Öffnungskraft auf die Ventilaußennadel vermindert und diese beschleunigt zurück in ihre Schließstellung drückt. Dadurch setzt die Ventilaußennadel nur sehr kurze Zeit nach der Ventilinnennadel auf dem Ventilsitz aufIn a further advantageous embodiment, the axial distance of the shoulder of the inner pressure surface is such that it is smaller with open valve needles than the opening stroke of the valve inner needle. As a result, takes the valve inner needle with its closing movement with the valve outer needle and forces it thus in the direction of the valve seat. When approaching the valve outer needle to the valve seat, there is a strong throttling of the fuel flow to the outer injection ports, so that the hydraulic opening force is reduced to the valve outer needle and this accelerates back to its closed position. As a result, the valve outer needle sets only a very short time after the valve inner needle on the valve seat

In einer weiteren vorteilhaften Ausgestaltung ist an der Ventilaußennadel eine Ventildichtfläche mit zwei Dichtkanten ausgebildet, wobei die äußere Dichtkante stromaufwärts und die innere Dichtkante stromabwärts der äußeren Einspritzöffnung am Ventilsitz zur Anlage kommen. Dadurch ist sichergestellt, dass die äußeren Einspritzöffnung auch bei geöffneter Ventilinnennadel hydraulisch abgeschlossen werden und kein Kraftstoff durch diese unkontrolliert in den Brennraum gelangen kann.In a further advantageous embodiment, a valve sealing surface is formed with two sealing edges on the valve outer needle, wherein the outer sealing edge upstream and the inner sealing edge downstream of the outer injection port on the valve seat come to rest. This ensures that the outer injection opening are closed hydraulically even when the inner valve needle is open and no fuel can pass uncontrollably through this into the combustion chamber.

In einer weiteren vorteilhaften Ausgestaltung ist zwischen der Ventilaußennadel und der Ventilinnennadel ein Steuervolumen ausgebildet, das als hydraulischer Mitnehmer dient. Hierdurch kann die Bewegung der Ventilaußennadel durch die Ventilinnennadel beeinflusst werden, ohne dass es zu einem mechanischen Kontakt zwischen den Ventilnadeln kommt, was in der Regel mit einer erhöhten Geräuschemission und mit Verschleißproblemen einhergehtIn a further advantageous embodiment, a control volume is formed between the valve outer needle and the valve inner needle, which serves as a hydraulic driver. As a result, the movement of the valve outer needle can be influenced by the valve inner needle, without causing mechanical contact between the valve needles, which is usually accompanied by an increased noise emission and wear problems

Zeichnungdrawing

In der Zeichnung ist ein Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt

Figur 1
einen Längsschnitt durch ein erfindungsgemäßes Kraftstoffeinspritzventil mit schematisch dargestellten peripheren Bauteilen,
Figur 2
eine vergrößerte Darstellung des Kraftstoffeinspritzventils, wobei aufgrund der Symmetrie nur die rechte Hälfte gezeichnet ist,
Figur 3, Figur 4 und Figur 5
verschiedene Öffnungsstellungen der Ventilnadeln, wobei die Darstellung mit der in Figur 2 identisch ist,
Figur 6
in identischer Darstellung wie Figur 4 eine alternativ ausgebildete Ventilaußennadel,
Figur 7 und Figur 8
ein weiteres Ausführungsbeispiel und
Figur 9
ein weiteres Ausführungsbeispiel des Kraftstoffeinspritzventils.
In the drawing, an embodiment of the fuel injection valve according to the invention is shown. It shows
FIG. 1
a longitudinal section through a fuel injection valve according to the invention with schematically represented peripheral components,
FIG. 2
an enlarged view of the fuel injection valve, wherein due to the symmetry only the right half is drawn,
FIG. 3, FIG. 4 and FIG. 5
different opening positions of the valve needles, the representation with the in FIG. 2 is identical,
FIG. 6
in an identical representation as FIG. 4 an alternatively formed valve outer needle,
FIG. 7 and FIG. 8
another embodiment and
FIG. 9
a further embodiment of the fuel injection valve.

Beschreibung der AusführungsbeispieleDescription of the embodiments

In Figur 1 ist ein erfindungsgemäßes Kraftstoffeinspritzventil im Längsschnitt dargestellt. Das Kraftstoffeinspritzventil 1 weist einen Haltekörper 3, der nur teilweise dargestellt ist, eine Drosselplatte 5 und einen Ventilkörper 7 auf, die durch eine nicht dargestellte Vorrichtung in dieser Reihenfolge aneinandergepresst werden. Im Ventilkörper 7 ist ein Zulaufraum 12 ausgebildet, der im wesentlichen als eine gestufte Bohrung ausgebildet ist, die an ihrem brennraumseitigen Ende von einem im wesentlichen konischen Ventilsitz 20 begrenzt wird. Vom Ventilsitz 20 gehen äußere Einspritzöffnungen 22 und innere Einspritzöffnungen 24 aus, die in Einbaulage des Kraftstoffeinspritzventils in den Brennraum der Brennkraftmaschine münden. Die äußeren Einspritzöffnungen 22 weisen in diesem Ausführungsbeispiel einen größeren Durchmesser auf als die inneren Einspritzöffnungen 24. Im Zulaufraum 12 ist eine Ventilaußennadel 15 angeordnet, die als Hohlnadel ausgebildet ist und damit eine Innenwand 31 aufweist und die an ihrem ventilsitzseitigen Ende eine im wesentlichen konische äußere Ventildichtfläche 18 aufweist. An der Ventilaußennadel 15 ist in einem mittleren Bereich einen Bund 62 ausgebildet, mit der sie in einem Führungsabschnitt 60 des Zulaufraums 12 geführt ist, wodurch die Ventilaußennadel 15 im Zulaufraum 12 längsverschiebbar ist. Durch die Längsbewegung wirkt die Ventilaußennadel 15 mit ihrer äußeren Ventildichtfläche 18 mit dem Ventilsitz 20 so zusammen, dass dadurch die äußeren Einspritzöffnungen 22 verschlossen oder freigegeben werden. Wie in Figur 2 dargestellt weist die äußere Ventildichtfläche 18 dabei eine äußere Dichtkante 25 und eine innere Dichtkante 27 auf, so dass die äußeren Einspritzöffnungen 22 bei Anlage der Ventilaußennadel 15 auf dem Ventilsitz 20 sowohl stromaufwärts als auch stromabwärts abgedichtet werden. Um den Kraftstoffdurchtritt in Richtung der Einspritzöffnungen 22, 24 zu ermöglichen, sind am Bund 62 Anschliffe 64 ausgebildet, deren Querschnitt und Anzahl so bemessen ist, dass ein drosselungsfreier Zustrom von Kraftstoff zu den Einspritzöffnungen 22, 24 möglich ist.In FIG. 1 a fuel injection valve according to the invention is shown in longitudinal section. The fuel injection valve 1 has a holding body 3, which is only partially shown, a throttle plate 5 and a valve body 7, which are pressed by a device, not shown, in this order. In the valve body 7, an inlet chamber 12 is formed, which is formed substantially as a stepped bore, which is bounded at its combustion-chamber end by a substantially conical valve seat 20. From the valve seat 20 go outside injection openings 22 and inner injection openings 24, which open into the installation position of the fuel injection valve in the combustion chamber of the internal combustion engine. The outer injection openings 22 in this embodiment have a larger diameter than the inner injection openings 24. In the inlet chamber 12, a valve outer needle 15 is arranged, which is designed as a hollow needle and thus has an inner wall 31 and at its valve seat side end has a substantially conical outer valve sealing surface 18. At the valve outer needle 15, a collar 62 is formed in a central region, with which it is guided in a guide portion 60 of the inlet chamber 12, whereby the valve outer needle 15 in the inlet space 12 is longitudinally displaceable. As a result of the longitudinal movement, the valve outer needle 15 cooperates with its outer valve sealing surface 18 with the valve seat 20 in such a way that the outer injection openings 22 are thereby closed or released. As in FIG. 2 In this case, the outer valve sealing surface 18 has an outer sealing edge 25 and an inner sealing edge 27, so that the outer injection openings 22 are sealed both upstream and downstream when the valve outer needle 15 rests on the valve seat 20. In order to enable the passage of fuel in the direction of the injection openings 22, 24, 62 bevels 64 are formed on the collar, whose cross-section and number is dimensioned so that a throttling-free flow of fuel to the injection openings 22, 24 is possible.

In der Ventilaußennadel 15 ist eine kolbenförmige Ventilinnennadel 17 längsverschiebbar angeordnet, die mit einem ventilsitzabgewandten zylindrischen Ansatz 44 in der Ventilaußennadel 15 geführt ist. Darüber hinaus ist die Ventilinnennadel 17 in einer zum Ventilsitz 20 hin angeordneten zweiten Führung 45 in der Ventilaußennadel 15 geführt, so dass eine exakt axiale Bewegung der Ventilinnennade1 17 gewährleistet ist. An der Führung 45 sind dabei Durchlässe, etwa in Form von Anschliffen ausgebildet, die einen weitgehend ungedrosselten Kraftstoffstrom in Richtung des Ventilsitzes 20 in dem zwischen der Ventilinnennadel 17 und der Ventilaußennadel 15 ausgebildeten Zwischenraum 50 erlauben. Die Ventilinnennadel 17 weist an ihrem ventilsitzseitigem Ende eine innere Ventildichtfläche 19 auf, mit der sie mit dem Ventilsitz 20 zusammenwirkt und hierbei die Öffnung der inneren Einspritzöffnungen 24 in gleicher Weise steuert wie die Ventilaußennadel 15 die äußeren Einspritzöffnungen 22.In the valve outer needle 15, a piston-shaped valve inner needle 17 is arranged longitudinally displaceable, which is guided with a valve seat facing away from cylindrical projection 44 in the valve outer needle 15. In addition, the valve inner needle 17 is guided in a direction to the valve seat 20 arranged second guide 45 in the valve outer needle 15, so that an exactly axial movement of Ventilinnennade1 17 is ensured. On the guide 45 while passages are formed, for example in the form of polished sections, which allow a largely unthrottled fuel flow in the direction of the valve seat 20 in the space 50 formed between the valve inner needle 17 and the valve outer needle 15. The valve inner needle 17 has at its valve seat side end an inner valve sealing surface 19, with which it cooperates with the valve seat 20 and in this case controls the opening of the inner injection openings 24 in the same way as the valve outer needle 15, the outer injection openings 22nd

Durch die Stirnseite 56 der Ventilinnennadel 17, die ringscheibenförmige Stirnseite 58 und der Ventilaußennadel 15, die Drosselplatte 5 sowie einer Hülse 26, die am ventilsitzabgewandten Ende der Ventilaußennadel 15 angeordnet ist und diese umgibt, wird ein Steuerraum 28 begrenzt, der mit Kraftstoff befüllt ist und dessen Druck regelbar ist. Der Steuerraum 28 ist über eine in der Drosselplatte 15 ausgebildete Zulaufdrossel 34 mit einem Zulautkanal 9 verbunden, über den der Zulaufraum 12 mit Kraftstoff unter hohem Druck befüllbar ist. Darüber hinaus ist in der Drosselplatte 5 eine Ablaufdrossel 36 ausgebildet, über die der Steuerraum 28 mit einem Kraftstoffbehälter 42 verbindbar ist, wobei im Kraftstoffbehälter 42 stets ein niedriger Kraftstoffdruck herrscht. In der Verbindungsleitung vom Steuerraum 28 zum Kraftstoffbehälter 42 ist ein Steuerventil 40 angeordnet, das die Verbindung öffnet und schließt. Das Steuerventil 40 ist in dem gezeigten Ausführungsbeispiel als 2/2-Wege-Ventil ausgebildet.By the end face 56 of the valve inner needle 17, the annular disk-shaped end face 58 and the valve outer needle 15, the throttle plate 5 and a sleeve 26 which is disposed at the valve seat facing away from the end of the valve outer needle 15 and surrounds a control chamber 28 is limited, which is filled with fuel and whose pressure is controllable. The control chamber 28 is connected via a formed in the throttle plate 15 inlet throttle 34 with a Zulautkanal 9, via which the inlet chamber 12 can be filled with fuel at high pressure. In addition, in the throttle plate 5, an outlet throttle 36 is formed, via which the control chamber 28 can be connected to a fuel tank 42, wherein the fuel tank 42 is always a low fuel pressure prevails. In the connecting line from the control chamber 28 to the fuel tank 42, a control valve 40 is arranged, which opens and closes the connection. The control valve 40 is formed in the embodiment shown as a 2/2-way valve.

Im Steuerraum 28 ist eine innere Schließfeder 30 unter Druckvorspannung angeordnet, die sich an einem Federabsatz 54 der Ventilinnennadel 17 abstützt und am anderen Ende an der Drosselscheibe 5. Durch die innere Schließfeder 30 wird eine Kraft in Richtung des Ventilsitzes 20 auf die Ventilinnennadel 17 ausgeübt. Entsprechend gleichwirkend wie die innere Schließfeder 30 ist im Zulaufraum 12 eine äußere Schließfeder 32 angeordnet, die sich mit einem Ende an der Hülse 26 abstützt und am anderen Ende an einem Ring 35, der auf der Ventilaußennadel 15 aufliegt. Aufgrund der Druckvorspannung der äußeren Schließfeder 32 wirkt auf die Ventilaußennadel 15 eine Schließkraft in Richtung des Ventilsitzes 20. Durch die innere Schließfeder 30 und die äußere Schließfeder 32 ist damit sichergestellt, dass die Ventilaußennadel 15 und die Ventilinnennadel 17 in ihrer Schließstellung verbleiben, falls keine weiteren Kräfte wirken, also insbesondere bei abgeschalteter Brennkraftmaschine. Die Schließfeder 32 ist weiterhin so bemessen, dass die Schließkraft auf die Ventilaußennadel 15 ausreicht, in Schließstellung beide Dichtkanten 25, 27 gegenüber dem Ventilsitz 20 abzudichten, auch bei einem niedrigen Druck im Steuerraum 28 und damit niedriger hydraulischer Schließkraft. Um die dafür erforderliche Kraft niedrig zu halten, ist im Bereich der Dichtkante 27 eine geringe Wandstärke zur Innenwand 31 vorgesehen.In the control chamber 28, an inner closing spring 30 is arranged under pressure bias, which is supported on a spring paragraph 54 of the valve inner needle 17 and at the other end to the throttle plate 5. By the inner closing spring 30, a force in the direction of the valve seat 20 is exerted on the valve inner needle 17. According to the same effect as the inner closing spring 30, an outer closing spring 32 is arranged in the inlet chamber 12, which is supported at one end to the sleeve 26 and at the other end to a ring 35 which rests on the valve outer needle 15. Due to the pressure bias of the outer closing spring 32 acts on the valve outer needle 15 a closing force in the direction of the valve seat 20. By the inner closing spring 30 and the outer closing spring 32 is thus ensured that the valve outer needle 15 and the valve inner needle 17 remain in its closed position, if no further Forces act, so in particular when the internal combustion engine. The closing spring 32 is further dimensioned so that the closing force on the valve outer needle 15 is sufficient to seal in the closed position both sealing edges 25, 27 against the valve seat 20, even at a low pressure in the control chamber 28 and thus lower hydraulic closing force. In order to keep the required force low, a small wall thickness to the inner wall 31 is provided in the region of the sealing edge 27.

In der Ventilaußennadel 15 ist eine Verbindungsbohrung 38 ausgebildet, die den Zulaufraum 12, in dem stets ein hoher Kraftstoffdruck herrscht, mit dem Zwischenraum 50 verbindet. Durch die Verbindungsbohrung 38 wird eine innere Druckfläche 48 der Ventilinnennadel 17, die ventilsitzseitig zur Verbindungsbohrung 38 an der Ventilinnennadel 17 ausgebildet ist, vom Kraftstoffdruck des Zulaufraums 12 beaufschlagt. Hierdurch ergibt sich eine hydraulische Kraft, die vom Ventilsitz 20 wegweist und der Kraft der inneren Schließfeder 30 entgegengerichtet ist. Der inneren Druckfläche 48 gegenüberliegend ist an der Innenseite der Ventilaußennadel 15 ein Absatz 47 ausgebildet, der in Schließstellung der Ventilaußennadel 15 und der Ventilinnennadel 17, das heißt, wenn diese in Anlage am Ventilsitz 20 sind, von der inneren Druckfläche 48 axial beabstandet ist. Dieser Abstand ist in Figur 2 mit hm bezeichnet. An der Ventilaußennadel 15 ist in gleicher Weise eine äußere Druckfläche 49 ausgebildet, die vom Kraftstoffdruck im Zulaufraum 12 beaufschlagt wird, wodurch die Ventilaußennadel 15 eine der Schließkraft der äußeren Schließfeder 32 entgegengerichtete Öffnungskraft erfährt. Durch die Anschliffe 64 am Bund 62 ist sichergestellt, dass die äußere Druckfläche 49 stets vom vollen Kraftstoffdruck beaufschlagt ist.In the valve outer needle 15, a connecting bore 38 is formed, which connects the inlet chamber 12, in which there is always a high fuel pressure, with the intermediate space 50. Through the connecting bore 38, an inner pressure surface 48 of the valve inner needle 17, which is formed on the valve seat side to the connecting bore 38 on the valve inner needle 17, acted upon by the fuel pressure of the inlet chamber 12. This results in a hydraulic force that points away from the valve seat 20 and the force of the inner closing spring 30 is opposite. Opposite the inner pressure surface 48, a shoulder 47 is formed on the inside of the valve outer needle 15, which in the closed position of the valve outer needle 15 and the valve inner needle 17, that is, when they are in contact with the valve seat 20, axially spaced from the inner pressure surface 48. This distance is in FIG. 2 denoted by h m . At the valve outer needle 15, an outer pressure surface 49 is formed in the same way, which is acted upon by the fuel pressure in the inlet chamber 12, whereby the valve outer needle 15 undergoes a closing force of the outer closing spring 32 opposite opening force. By the bevels 64 on the collar 62 ensures that the outer pressure surface 49 is always acted upon by the full fuel pressure.

Die Funktionsweise des Kraftstoffeinspritzventils ist wie folgt: Zu Beginn der Einspritzung ist das Steuerventil 40 geschlossen, so dass die Verbindung des Steuerraums 28 mit dem Kraftstoffbehälter 42 unterbrochen ist. Hierdurch baut sich über die Zulaufdrossel 34 im Steuerraum 28 der gleiche Druck auf wie im Zulaufraum 12, der aufgrund seiner Verbindung über den Zulaufkanal 9 stets auf einem hohen Kraftstoffdruck gehalten wird. Durch den Druck im Steuerraum 28 ergibt sich eine hydraulische Kraft auf die ventilsitzabgewandte Stirnseite 56 und den Federabsatz 54 der Ventilinnennadel 17 und die Stirnseite 58 der Ventilaußennadel 15. Die Ventilaußennadel 15 und die Ventilinnennadel 17 werden durch den Differenzdruck aus dem hydraulischen Druck im Steuerraum 28 und im Druckraum 12 einerseits und dem Brennraumdruck andererseits, der die innere Ventildichtfläche 19 und die äußere Ventildichtfläche 18 zum Teil beaufschlagt, zusätzlich zur Kraft der Schließfedern 30,32 in ihrer Schließposition gehalten. Dazu werden die Fläche der Stirnseiten 56, 58, die Ventildichtflächen 19, 23 und die sonstigen vom Kraftstoffdruck im Druckraum 12 beaufschlagten Flächen der Ventilinnennadel 17 und der Ventilaußennadel 15 entsprechend ausgelegt.The operation of the fuel injection valve is as follows: At the beginning of the injection, the control valve 40 is closed, so that the connection of the control chamber 28 is interrupted with the fuel tank 42. As a result, the same pressure builds up on the inlet throttle 34 in the control chamber 28 as in the inlet chamber 12, which is always kept at a high fuel pressure due to its connection via the inlet channel 9. The pressure in the control chamber 28 results in a hydraulic force on the valve seat facing away from end 56 and the spring paragraph 54 of the valve inner needle 17 and the end face 58 of the valve outer needle 15. The valve outer needle 15 and the valve inner needle 17 are by the differential pressure from the hydraulic pressure in the control chamber 28 and in the Pressure chamber 12 on the one hand and the combustion chamber pressure on the other hand, which acts on the inner valve sealing surface 19 and the outer valve sealing surface 18 in part, held in addition to the force of the closing springs 30,32 in its closed position. For this purpose, the surface of the end faces 56, 58, the valve sealing surfaces 19, 23 and the other acted upon by the fuel pressure in the pressure chamber 12 surfaces of the valve inner needle 17 and the valve outer needle 15 are designed accordingly.

Soll eine Einspritzung erfolgen, so wird das Steuerventil 40 geöffnet, wodurch über die Ablaufdrossel 36 Kraftstoff aus dem Steuerraum 28 abfließt und der Kraftstoffdruck dort abfällt. Hierdurch erniedrigt sich die hydraulische Kraft auf die Stirnseite 56 der Ventilinnennadel 17, so dass die Ventilinnennadel 17, angetrieben durch die hydraulischen Kräfte auf die innere Druckfläche 48 und auf Teile der inneren Ventildichtfläche 19, vom Ventilsitz 20 abhebt, bis nach Durchfahren eines Öffnungshubs hi die Stirnseite 56 an der Drosselscheibe 5 zur Anlage kommt. Diese Stellung des Kraftstoffeinspritzventils ist in Figur 3 dargestellt. Der Kraftstoffweg vom Zulaufraum 12 durch die Verbindungsbohrung 38 und den Zwischenraum 50 und zwischen der inneren Ventildichtfläche 19 und dem Ventilsitz 20 hindurch zu den inneren Einspritzöffnungen 24 wird dadurch aufgesteuert, so dass eine Kraftstoff-Einspritzung durch die inneren Einspritzöffnungen 24 stattfindet. Die an der äußeren Ventildichtfläche 18 ausgebildeten Dichtkanten 25, 27 dichten die äußeren Einspritzöffnungen 22 ab, wodurch diese nach wie vor geschlossen bleiben.If an injection takes place, the control valve 40 is opened, whereby fuel flows from the control chamber 28 via the outlet throttle 36 and the fuel pressure drops there. As a result, the hydraulic force on the end face 56 of the valve inner needle 17 is lowered, so that the valve inner needle 17, driven by the hydraulic forces on the inner pressure surface 48 and on parts of the inner valve sealing surface 19, lifts off from the valve seat 20 until after passing through an opening stroke hi End 56 comes to rest on the throttle plate 5. This position of the fuel injection valve is in FIG. 3 shown. The fuel path from the inlet space 12 through the connecting bore 38 and the intermediate space 50 and between the inner valve sealing surface 19 and the valve seat 20 to the inner injection openings 24 is thereby controlled, so that a fuel injection takes place through the inner injection openings 24. The formed on the outer valve sealing surface 18 sealing edges 25, 27 seal the outer injection openings 22, whereby they remain closed as before.

Fällt der Kraftstoffdruck im Steuerraum 28 weiter ab, so wird schließlich der Öffnungsdruck der Ventilaußennadel 15 erreicht, also der Druck, bei dem die hydraulische Schließkraft auf die Stirnseite 58 und auf den Absatz 47 sowie die Kraft der Schließfeder 32 in Summe kleiner sind als die Summe der hydraulischen Öffnungskräfte auf die äußere Druckfläche 49 und auf die vom Kraftstoffbeaufschlagte Teilfläche der äußeren Ventildichtfläche 18. Die Ventilaußennadel 15 hebt vom Ventilsitz 20 ab und durchfährt einen Öffnungshub ha, bis sie mit ihrer Stirnseite 58 an der Drosselscheibe 5 zur Anlage kommt. Diese Stellung des Kraftstoffeinspritzventils ist in Figur 4 dargestellt. Der Öffnungshub in der Ventilaußennade1 15 ist hierbei so bemessen, dass in ihrer Öffnungsstellung ein axialer Abstand zwischen den Absatz 47 und der inneren Druckfläche 48 verbleibt. Auch kann durch ein Schließen des Steuerventils 40 die Ventilaußennadel 15 ihre Schließstellung wieder früher erreichen, wodurch weniger Kraftstoff in den Brennraum gelangt. In dieser Öffnungsstellung fließt zum einen Kraftstoff durch die Verbindungsbohrung 38 und den Zwischenraum 50 und durch Anschliffe an der zweiten Führung 45 hindurch zu den inneren Einspritzöffnungen 24 und andererseits Kraftstoff aus dem Zulaufraum 12 durch die Anschliffe 64 zwischen der äußeren Ventildichtfläche 18 und den Ventilsitz 20 hindurch zu den äußeren Einspritzöffnungen 22, so dass nunmehr durch sämtliche Einspritzöffnungen Kraftstoff in den Brennraum eingespritzt wird. Durch die Einströmung von Kraftstoff sowohl über den Zulaufraum 12 als auch über den Zwischenraum 50 werden sämtliche Einspritzöffnungen 22, 24 optimal mit Kraftstoff versorgt, so dass mit vollem Druck eine große Menge Kraftstoff in kurzer Zeit in den Brennraum eingebracht werden kann.If the fuel pressure in the control chamber 28 continues to decrease, the opening pressure of the valve outer needle 15 is finally reached, ie the pressure at which the hydraulic closing force on the end face 58 and on the shoulder 47 and the force of the closing spring 32 are smaller than the sum The valve opening needle 15 lifts off from the valve seat 20 and passes through an opening stroke h a , until it comes to rest with its end face 58 on the throttle plate 5 the hydraulic opening forces on the outer pressure surface 49 and the fuel. This position of the Fuel injection valve is in FIG. 4 shown. The opening stroke in the Ventilaußennade1 15 is in this case dimensioned so that in its open position, an axial distance between the shoulder 47 and the inner pressure surface 48 remains. Also, by closing the control valve 40, the valve outer needle 15 again reach its closed position earlier, whereby less fuel enters the combustion chamber. In this open position flows to a fuel through the connecting bore 38 and the gap 50 and by polished on the second guide 45 through to the inner injection ports 24 and on the other hand fuel from the feed chamber 12 through the bevels 64 between the outer valve sealing surface 18 and the valve seat 20 therethrough to the outer injection openings 22, so that fuel is now injected through all the injection openings in the combustion chamber. By the inflow of fuel through both the inlet chamber 12 and the gap 50 all injection ports 22, 24 are optimally supplied with fuel, so that at full pressure, a large amount of fuel can be introduced in a short time in the combustion chamber.

Zur Beendigung der Einspritzung wird das Steuerventil 40 geschlossen, so dass über den durch die Zulaufdrossel 34 nachströmenden Kraftstoff der Kraftstoffdruck in Steuerraum 28 wieder ansteigt. Die Ventilnadeln beginnen ihre Schließbewegung nach Überschreitung des jeweiligen Schließdrucks im Steuerraum 28, wobei der Schließdruck der Ventilaußennadel 15 früher erreicht wird als der der Ventilinnennadel 17. Dies hat seinen Grund zum einen darin, dass die Kraft der äußeren Schließfeder 32 höher ist und zum anderen darin, dass die hydraulischen Druckkräfte an der äußeren Ventildichtfläche 18 aufgrund der Drosselung des Kraftstoffstroms, der aus dem Zulaufraum 12 in Richtung der äußeren Einspritzöffnungen 22 fließt, niedriger sind als die hydraulischen Druckkräfte auf die Ventilinnennadel 17. Der Druck im Steuerraum 28 bleibt während der Schließbewegung der Ventilaußennadel 15 zumindest annähernd konstant, da sich der Kraftstoffzustrom über die Zulaufdrossel 34 und die Vergrößerung des Steuerraum 28 ausgleichen. Mit zunehmender Annäherung der Ventilaußennadel 15 an den Ventilsitz 20 verstärkt sich die Drosselung an der äußeren Ventildichtfläche 18, woraus ein beschleunigtes Schließen Ventilaußennadel 15 resultiert. Die Stellung der Ventilaußennadel 15 und der Ventilinnennadel 17 zueinander, bei der die Ventilaußennadel 15 bereits auf dem Ventilsitz 20 aufgesetzt hat, aber die Ventilinnennadel 17 noch einen Abstand zum Ventilsitz 20 aufweist, entspricht wiederum der Darstellung in Figur 3.To end the injection, the control valve 40 is closed so that the fuel pressure in the control chamber 28 increases again via the fuel flowing in through the inlet throttle 34. The valve needles begin their closing movement after exceeding the respective closing pressure in the control chamber 28, wherein the closing pressure of the valve outer needle 15 is reached earlier than that of the valve inner needle 17. This is due to the fact that the force of the outer closing spring 32 is higher and the other in it in that the hydraulic pressure forces on the outer valve sealing face 18 are lower than the hydraulic pressure forces on the inner valve needle 17 due to the throttling of the fuel flow flowing from the inlet chamber 12 in the direction of the outer injection openings 22. The pressure in the control chamber 28 remains during the closing movement of the Valve outer needle 15 at least approximately constant, since the fuel flow over the inlet throttle 34 and the enlargement of the control chamber 28 compensate. With increasing approach of the valve outer needle 15 to the valve seat 20, the throttling on the outer valve sealing surface 18 increases, resulting in an accelerated closing valve outer needle 15 results. The position of the valve outer needle 15 and the valve inner needle 17 to each other, in which the valve outer needle 15 has already placed on the valve seat 20, but the valve inner needle 17 still has a distance from the valve seat 20, in turn corresponds to the illustration in FIG FIG. 3 ,

In Figur 5 und Figur 6 ist eine alternative Ausbildung der inneren Druckfläche 48 und des Absatzes 47 dargestellt. Sowohl der Absatz 47 als auch die innere Druckfläche 48 sind vorzugsweise als konische Flächen ausgebildet, die hier jedoch nicht, wie in den Figuren 2, 3 und 4 dargestellt, denselben Öffnungswinkel aufweisen, sondern bei denen der Öffnungswinkel der inneren Druckfläche 48 größer ist als der Öffnungswinkel des Absatzes 47. Die axiale Zuordnung zwischen dem der inneren Druckfläche 48 und dem Absatz 47 einerseits und der Stirnseite 58 der Ventilaußennadel 15 andererseits ist so ausgelegt, dass zwischen der Stirnseite 58 und der Drosselplatte 5 stets ein Spalt verbleibt. Dieser Zustand ist in Figur 6 dargestellt. Wenn bei der Öffnungsbewegung der Ventilaußennadel 15 der Absatz 47 auf der inneren Druckfläche 48 aufliegt, bildet sich dort eine Dichtkante 51, wodurch sich im Zwischenraum 50 ein niedrigerer Druck entsprechend den Druckverhältnissen im Bereich des Ventilsitzes 20 einstellt. Durch den jetzt niedrigeren Druck im Zwischenraum 50, sowohl gegenüber dem Druck im Zulaufraum 12 als auch gegenüber dem Druck im Steuerraum 28, ergibt sich beim Schließvorgang auf die Ventilinnennadel 17 eine größere Schließkraft. Auf die Ventilaußennadel 15 wirkt hingegen eine der Schließbewegung entgegengerichtete Druckkraft auf die äußere Druckfläche 49, welche mit dem Druck des Zulaufraums 12 beaufschlagt ist, so dass sich die Schließbewegung der Ventilaußennadel 15 entsprechend verzögert. Hierdurch wird verhindert, dass bei der Schließbewegung die Ventilaußennadel 15 vorauseilt und die Ventilinnennadel 17 später als diese schließt, was sonst durch die stets größere Sitzdrosselung und die dadurch verursachte Druckerniedrigung an der äußeren Ventildichtfläche 18 begünstigt wird.In FIG. 5 and FIG. 6 an alternative embodiment of the inner pressure surface 48 and the heel 47 is shown. Both the shoulder 47 and the inner pressure surface 48 are preferably formed as conical surfaces, but not here, as in the Figures 2 . 3 and 4 shown, have the same opening angle, but in which the opening angle of the inner pressure surface 48 is greater than the opening angle of the shoulder 47. The axial relationship between the inner pressure surface 48 and the shoulder 47 on the one hand and the end face 58 of the valve outer needle 15 on the other hand is designed so that between the end face 58 and the throttle plate 5 always a gap remains. This condition is in FIG. 6 shown. If during the opening movement of the valve outer needle 15 of the shoulder 47 rests on the inner pressure surface 48, there forms a sealing edge 51, whereby a lower pressure corresponding to the pressure conditions in the region of the valve seat 20 is established in the intermediate space 50. Due to the now lower pressure in the intermediate space 50, both with respect to the pressure in the inlet chamber 12 and with respect to the pressure in the control chamber 28, a greater closing force results on closing the valve inner needle 17. On the other hand, the valve outer needle 15 acts a pressing force on the outer pressure surface 49, which is acted upon by the pressure of the inlet chamber 12, so that the closing movement of the valve outer needle 15 is delayed accordingly. This prevents that in the closing movement the valve outer needle 15 leads and the valve inner needle 17 closes later than this, which is otherwise favored by the ever greater seat throttling and the pressure reduction caused thereby on the outer valve sealing surface 18.

In Figur 7 und Figur 8 ist ein weiteres Ausführungsbeispiel dargestellt, wobei im folgenden nur auf die Unterschiede zu den vorangegangenen Ausführungsbeispielen eingegangen wird. Die Zulaufdrossel 34 ist hier so in der Drosselscheibe 5 angeordnet, dass die Ventilinnennadel 17 die Zulaufdrossel 34 bei Anlage an der Drosselplatte 5 teilweise bzw. vollständig verschließt. Die Stirnseite 56 der Ventilinnennadel 17 ist als zur Drosselplatte 5 parallele Fläche ausgebildet und mit einer Beißkante 55 versehen, die für eine ausreichende Abdichtung an dieser Stelle sorgt. Durch das teilweise oder vollständige Unterbinden des Kraftstoffzuflusses durch die Zulaufdrossel 34 in den Steuerraum 28 sinkt der Druck im Steuerraum 28 durch das Abfließen durch die Ablaufdrossel 36 sehr schnell bis zum Erreichen eines Steuerraumsdruck, bei dem auch die Ventilaußennadel 15 öffnet Dadurch ist es möglich, die Ventilaußennadel 15 bereits kurz nach dem vollständigen Öffnen der Ventilinnennadel 17 zu öffnen. Weiterhin kann der Unterschied zwischen den Öffnungsdrücken der Ventilinnennadel 17 und der Ventilaußennadel 15 vergrößert werden, ohne dass dies zu einem großen Zeitverzug zwischen dem Öffnungszeitpunkt der Ventilinnennadel 17 und der Ventilaußennadel 15 führt. Um den Schließvorgang zu steuern ist hier als Steuerventil 40' ein 3/2-Wegeventil vorgesehen, dass in der ersten Schaltstellung die Ablaufdrossel 36 mit dem Kraftstoffbehälter 42 verbindet, während in der zweiten Schaltstellung die Ablaufdrossel mit dem Zulaufkanal 9 verbunden wird. Beim Schließvorgang wird das Steuerventil 40' in seine zweite Schaltstellung gebracht, so dass über die Ablaufdrossel 36 Kraftstoff in den Steuerraum 28 strömt. Durch diesen Zufluss kann der Steuerraumdruck rasch erhöht werden, auch wenn die Zulaufdrossel 34 vollständig durch die Ventilinnennadel 17 abgedichtet ist. Sofort nach dem Abheben der Ventilinnennadel 17 von der Drosselscheibe 5 strömt sowohl durch die Zulaufdrossel 34 als auch durch die Ablaufdrossel 36 Kraftstoff in den Steuerraum 28, so dass der Schließvorgang mit verringerter Drosselung und damit höherer Geschwindigkeit erfolgt.In FIG. 7 and FIG. 8 is shown a further embodiment, which will be discussed below only the differences from the previous embodiments. The inlet throttle 34 is arranged here in the throttle disk 5, that the valve inner needle 17, the inlet throttle 34 when it rests on the throttle plate 5 partially or completely closes. The end face 56 of the valve inner needle 17 is formed as a surface parallel to the throttle plate 5 and provided with a biting edge 55, which ensures a sufficient seal at this point. Due to the partial or complete prohibition of the fuel flow through the inlet throttle 34 into the control chamber 28, the pressure in the control chamber 28 drops rapidly due to the outflow through the outlet throttle 36 until a control chamber pressure is reached at which the valve outer needle 15 also opens Valve outer needle 15 already shortly after the complete opening of the valve inner needle 17 to open. Furthermore, the difference between the opening pressures of the valve inner needle 17 and the valve outer needle 15 can be increased without resulting in a large time delay between the opening timing of the valve inner needle 17 and the valve outer needle 15. In order to control the closing operation, a 3/2-way valve is provided here as a control valve 40 'such that in the first switching position the outlet throttle 36 connects to the fuel tank 42, while in the second switching position the outlet throttle is connected to the inlet channel 9. During the closing operation, the control valve 40 'is brought into its second switching position, so that via the outlet throttle 36 fuel flows into the control chamber 28. By this inflow of the control chamber pressure can be increased rapidly, even if the inlet throttle 34 is completely sealed by the valve inner needle 17. Immediately after lifting the valve inner needle 17 from the throttle disk 5 flows through both the inlet throttle 34 and through the outlet throttle 36 fuel into the control chamber 28, so that the closing process with reduced throttling and thus higher speed.

In Figur 9 ist ein weiteres Ausführungsbeispiel dargestellt, bei dem das Zusammenwirken von Ventilinnennadel 17 und Ventilaußennadel 15 hydraulisch erfolgt. Der Absatz 47 und die innere Druckfläche 48 schließen zusammen mit dem zylindrischen Ansatz 44 und einem weiteren, an der Ventilinnennadel 17 ausgebildeten weiteren zylindrischen Ansatz 39 ein Steuervolumen 53 ein, welches durch eine in der Ventilaußennadel 15 ausgebildete Drosselbohrung 37 mit dem Zulaufraum 12 verbunden ist und als hydraulischer Mitnehmer dient. Sowohl der zylindrische Ansatz 44 als auch der weitere zylindrische Ansatz 39 dichten das Steuervolumen 53 hierbei ausreichend ab. Durch das Steuervolumen 53 kann eine hydraulische Dämpfung der Relativbewegung zwischen Ventilinnennadel 17 und Ventilaußennadel 15 erzeugt werden, was eine reduzierte Öffnungsgeschwindigkeit der Ventilinnennadel 17 bewirkt aufgrund des rasch abfallenden Drucks im Steuervolumen 53 und der damit fehlenden Öffnungskraft auf die innere Druckfläche 48. Die Verbindungsbohrungen 38 sind zwischen dem weiteren zylindrischen Ansatz 39 und dem Ventilsitz 20 anzuordnen, um einen ungedrosselten Zulauf zum Zwischenraum 50 zu gewährleisten. Der Öffnungszeitpunkt der Ventilaußennadel 15 ist in vorteilhafter Weise auf einen Zeitpunkt nach Beendigung des Öffnens der Ventilinnennadel 17 zu legen, was in Kombination mit dem in Figur 7 und Figur 8 dargestellten Ausführungsbeispiel sichergestellt werden kann. Dadurch ist die Öffnungsbewegung der Ventilaußennadel 15 ebenfalls gedämpft, ohne dass ein sprungartiges Öffnen stattfindet.In FIG. 9 is a further embodiment shown, in which the interaction of the valve inner needle 17 and valve outer needle 15 is hydraulically. The shoulder 47 and the inner pressure surface 48, together with the cylindrical projection 44 and another, formed on the valve inner needle 17 further cylindrical projection 39, a control volume 53, which is connected by a formed in the valve outer needle 15 throttle bore 37 with the inlet chamber 12 and serves as a hydraulic driver. Both the cylindrical projection 44 and the further cylindrical projection 39 seal the control volume 53 in this case sufficiently. By the control volume 53, a hydraulic damping of the relative movement between the valve inner needle 17 and valve outer needle 15 can be generated, which causes a reduced opening speed of the valve inner needle 17 due to the rapidly decreasing pressure in the control volume 53 and the lack of opening force on the inner pressure surface 48th Die Verbindungsbohrungen 38 sind between the other cylindrical projection 39 and the valve seat 20 to be arranged to ensure an unthrottled inlet to the gap 50. The opening time of the valve outer needle 15 is to be set advantageously at a time after completion of the opening of the valve inner needle 17, which in combination with the in FIG. 7 and FIG. 8 illustrated embodiment can be ensured. As a result, the opening movement of the valve outer needle 15 is also damped without a sudden opening takes place.

In Abhängigkeit von der Öffnungsdauer des Steuerventils 40' durchläuft die Ventilaußennadel 15 einen Teilhub des Gesamthubs ha der Ventilaußennadel 15, wodurch die Öffnungsdauer der Ventilaußennadel 15 und der Ventilinnennadel 17 verlängert wird und die Einspritzmenge anteilig zunimmt. Wird das Steuerventil 40' geschlossen, das hier ebenfalls als 3/2-Wegeventil ausgebildet ist, erhöht sich der Druck im Steuerraum 28, wodurch die Ventilaußennadel 15 aufgrund der größeren Sitzdrosselung zuerst losläuft, jedoch wird die Ventilinnennadel 17 durch die Druckerniedrigung im Steuervolumen 53, das sich durch die Bewegung der Ventilaußennadel 15 vergrößert und die damit wegfallende Öffnungskraft auf die innere Druckfläche 48, in Richtung Ventilsitzes 20 mitgenommen. Die Schließreihenfolge zwischen Ventilinnennadel 17 und Ventilaußennadel 15 ist abhängig von der Ansteuerdauer und der Abstimmung zwischen dem Hub der Ventilinnennadel 17 und dem der Ventilaußennadel 15. Der Hub ha der Ventilaußennadel 15 ist vorzugsweise so auf den Hub hi der Ventilinnennadel 17 abzustimmen, dass bei maximaler Einspritzmenge die Ventilinnennadel 17 und Ventilaußennadel 15 zeitgleich schließen und somit die für die gewünschte Einspritzmenge kürzeste Einspritzdauer möglich wird.Depending on the opening duration of the control valve 40 ', the valve outer needle 15 undergoes a partial stroke of the total stroke h a of the valve outer needle 15, whereby the opening duration of the valve outer needle 15 and the valve inner needle 17 is extended and the injection quantity increases proportionally. If the control valve 40 'closed, which is also designed here as a 3/2-way valve, the pressure in the control chamber 28 increases, causing the valve outer needle 15 first runs loose due to the larger seat throttling, but the valve inner needle 17 is due to the pressure reduction in the control volume 53, which is increased by the movement of the valve outer needle 15 and the resulting opening force on the inner pressure surface 48, taken in the direction of valve seat 20. The closing order between the valve inner needle 17 and valve outer needle 15 is dependent on the drive time and the vote between the stroke of the valve inner needle 17 and the valve outer needle 15. The stroke h a of the valve outer needle 15 is preferably so on the stroke h i of the valve inner needle 17 vote that at maximum injection quantity close the valve inner needle 17 and valve outer needle 15 at the same time and thus the shortest possible injection duration for the desired injection quantity is possible.

Bei der Auslegung des Steuervolumens 53 ist es vorteilhaft, wenn die Ventilaußennadel 15 bei der maximalen Einspritzmenge nicht an einem ortsfesten Anschlag zur Anlage kommt. Die Ventilaußennadel 15 drosselt den Kraftstoffstrom zur zu Beginn ihrer Öffnungshubbewegung. Bewegt sich die Ventilaußennadel 15 aus diesem Drosselbereich heraus, ist der Kraftstoffstrom aus dem Zulaufraum 12 zu den Einspritzöffnungen 22, 24 weitgehend unabhängig vom Hub der Ventilaußennadel 15. Auf einen Anschlag kann damit verzichtet werden und der Druck im Steuerraum 28 wird so rechtzeitig wieder erhöht, dass die Ventilaußennadel 15 im ballistischen Betrieb bleibt. Dies führt auch zu einer Minderung des Geräusches, da der Anschlag der Ventilaußennadel 15 entfällt.In the design of the control volume 53, it is advantageous if the valve outer needle 15 does not come into abutment against a fixed stop at the maximum injection quantity. The valve outer needle 15 throttles the fuel flow at the beginning of their Öffnungshubbewegung. If the valve outer needle 15 moves out of this throttle region, the fuel flow from the inlet chamber 12 to the injection openings 22, 24 is largely independent of the stroke of the valve outer needle 15. A stop can thus be dispensed with and the pressure in the control chamber 28 is increased in a timely manner, that the valve outer needle 15 remains in ballistic operation. This also leads to a reduction of the noise, since the stop of the valve outer needle 15 is omitted.

Weiterhin ist eine aufwendige Herstellung eines gezielten Öffnungshubs der Ventilaußennadel 15 nicht notwendig. Auch kann eine unstetige Bewegung infolge eines Prellens am Anschlag vermieden werden, welche sich negativ auf den Mengenkennlinienverlauf auswirkt.Furthermore, a complex production of a targeted opening stroke of the valve outer needle 15 is not necessary. Also, a discontinuous movement due to a bounce at the stop can be avoided, which has a negative effect on the set characteristic curve.

Claims (15)

  1. Fuel injection valve for internal combustion engines, having a valve outer needle (15) which interacts, by means of a longitudinal movement, with a valve seat (20) so as to open and close at least one outer injection opening (22), and having a valve inner needle (17) which is arranged in the valve outer needle (20) and which, by means of its longitudinal movement, interacts with a valve seat (20) so as to open and close at least one inner injection opening (24), and having a control chamber (28) which can be filled with pressurized fuel, with the fuel pressure acting on the valve outer needle (15) and the valve inner needle (17) in such a way that a closing force in the direction of the valve seat (20) is thereby exerted on the valve inner needle (17) and on the valve outer needle (15), and having an inflow chamber (12) which at least partially surrounds the valve outer needle (15) and which can be filled with pressurized fuel, with the fuel pressure in the inflow chamber (12) exerting an opening force, which is directed counter to the closing force, both on the valve inner needle (17) and also on the valve outer needle (15), and with a shoulder (47) being formed on the inner side of the valve outer needle (15), which shoulder (47) is situated opposite an inner pressure surface (48) of the valve inner needle (17) and which shoulder (47) is spaced apart axially from the inner pressure surface (48) when the valve inner needle (17) and the valve outer needle (15) are in contact against the valve seat (20), characterized in that the valve inner needle (17), during its closing movement towards the valve seat (20), moves the open valve outer needle (15) in the closing direction by coming into contact against the shoulder (47).
  2. Fuel injection valve according to Claim 1,
    characterized in that an intermediate chamber (50) is formed between the valve outer needle (15) and the valve inner needle (17), which intermediate chamber (50) is permanently hydraulically connected to the inflow chamber (12).
  3. Fuel injection valve according to Claim 2,
    characterized in that the valve inner needle (17) has formed on it the inner pressure surface (48), which is acted on by the pressure in the intermediate chamber (50).
  4. Fuel injection valve according to Claim 2,
    characterized in that the connection of the intermediate chamber (50) to the inflow chamber (12) is produced by means of at least one connecting bore (38) which is formed in the valve outer needle (15).
  5. Fuel injection valve according to Claim 1,
    characterized in that the valve inner needle (17), after rising up from the valve seat (20) and after travelling through an opening stroke (hi), comes into contact with its end side (56) against a positionally fixed stop, and likewise, the valve outer needle (15), after travelling through an opening stroke (ha), comes into contact with its end side (58) against a positionally fixed stop, with the opening strokes being dimensioned relative to one another in such a way that the shoulder (47) of the valve outer needle (15) remains spaced apart from the inner pressure surface (48) when the valve outer needle (15) and the valve inner needle (17) are in their open position.
  6. Fuel injection valve according to Claim 1,
    characterized in that the valve inner needle (17), after rising up from the valve seat (20) and after travelling through an opening stroke (hi), moves into an open position, with the valve inner needle (17) coming into contact with its end side against a positionally fixed stop and with the valve outer needle (15), during its opening stroke (ha), coming into contact with the shoulder (47) against the inner pressure surface (48).
  7. Fuel injection valve according to Claim 1,
    characterized in that the inner pressure surface (48) and the shoulder (47) are of conical design, with the cone surfaces having a different opening angle such that the shoulder (47) can come into contact with a sealing edge (51) against the inner pressure surface (48) in such a way that the connection of the inflow chamber (12) to the intermediate chamber (50) via the connecting bore (38) is separated.
  8. Fuel injection valve according to Claim 1,
    characterized in that the valve seat (20) is of substantially conical design and at least one outer injection opening (22) and one inner injection opening (24) extend from the valve seat (20), with the valve outer needle (15) controlling the outer injection openings (22) and the valve inner needle (17) controlling the inner injection openings (24).
  9. Fuel injection valve according to Claim 8,
    characterized in that the outer valve sealing surface (18) on the valve outer needle (15) is shaped such that, when the valve outer needle (15) is in contact against the valve seat (20), the outer injection openings (22) are sealed off both upstream and also downstream.
  10. Fuel injection valve according to Claim 9,
    characterized in that the outer valve sealing surface (18) on the valve outer needle (15) has an outer sealing edge (25) and an inner sealing edge (27), of which the outer sealing edge (25) comes into contact against the valve seat (20) upstream of the outer injection openings (22) and the inner sealing edge (27) comes into contact against the valve seat (20) downstream of the outer injection openings (22), and said outer valve sealing surface (18) hereby seals off the outer injection openings (22) in both flow directions.
  11. Fuel injection valve according to Claim 1,
    characterized in that the control chamber (28) is connected via an inflow throttle (34) to an inflow duct (9) and via an outflow duct (36) to a fuel tank (42), with the outflow duct (36) having arranged in it a control valve (40) which opens or closes off the outflow duct (36) (2/2-way valve).
  12. Fuel injection valve according to Claim 1,
    characterized in that the control chamber (28) can be connected via an outflow duct (36) to a fuel tank (42), with the outflow duct (36), the fuel tank (42) and the inflow duct (9) being connected to a control valve (40') in such a way that, in a first switching position of the control valve (40'), the outflow duct (36) is connected to the fuel tank (42), and in a second switching position, the outflow duct (36) is connected to the inflow duct (9) (3/2-way valve).
  13. Fuel injection valve according to Claim 1,
    characterized in that a cylindrical collar (44) and a further cylindrical collar (39) are formed on the valve inner needle (17), which cylindrical collars are spaced apart from one another axially and are designed such that, at the cylindrical collars (39; 44), hydraulic sealing takes place between the valve inner needle (17) and the valve outer needle (15), with the hydraulic collars (39; 42) delimiting a control volume (53) which is connected via a throttle bore (37) to the inflow chamber (12).
  14. Fuel injection valve according to Claim 13,
    characterized in that the control volume (53) and the throttle bore (37) are designed such that the valve outer needle (15) does not come into contact against a positionally fixed stop at the maximum injection quantity of the fuel injection valve in a ballistic operating mode.
  15. Fuel injection valve according to Claim 14,
    characterized in that the closing speeds of the valve outer needle (15) and of the valve inner needle (17) are coordinated with one another in such a way that, at the maximum injection quantity of the fuel injection valve, said valve outer needle (15) and valve inner needle (17) come into contact against the valve seat (20) at the same time during their closing movement.
EP05701547A 2004-03-30 2005-01-19 Fuel-injection valve for internal combustion engines Not-in-force EP1747370B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102004015360A DE102004015360A1 (en) 2004-03-30 2004-03-30 Fuel injection valve for internal combustion engines
PCT/EP2005/050201 WO2005095785A1 (en) 2004-03-30 2005-01-19 Fuel-injection valve for internal combustion engines

Publications (2)

Publication Number Publication Date
EP1747370A1 EP1747370A1 (en) 2007-01-31
EP1747370B1 true EP1747370B1 (en) 2010-03-17

Family

ID=34959829

Family Applications (1)

Application Number Title Priority Date Filing Date
EP05701547A Not-in-force EP1747370B1 (en) 2004-03-30 2005-01-19 Fuel-injection valve for internal combustion engines

Country Status (7)

Country Link
US (1) US20070290075A1 (en)
EP (1) EP1747370B1 (en)
JP (1) JP2007530862A (en)
CN (1) CN1938513A (en)
AT (1) ATE461362T1 (en)
DE (2) DE102004015360A1 (en)
WO (1) WO2005095785A1 (en)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102005046665A1 (en) * 2005-09-29 2007-04-05 Robert Bosch Gmbh Fuel injection valve for e.g. self-ignition internal combustion engine, has inclined groove formed at valve seat near guide section of inner needle, such that tangential force is exerted on needle during flow of fuel
JP4226011B2 (en) * 2006-02-16 2009-02-18 株式会社デンソー Fuel injection device
JP4331225B2 (en) * 2007-04-10 2009-09-16 トヨタ自動車株式会社 Fuel injection control device for internal combustion engine
JP2009008032A (en) * 2007-06-29 2009-01-15 Toyota Motor Corp Fuel injection control device for internal combustion engine
DE102008031271B4 (en) * 2008-07-02 2011-07-28 Continental Automotive GmbH, 30165 Nozzle assembly for an injection valve
JP2011185264A (en) * 2010-02-11 2011-09-22 Denso Corp Injector
KR101116504B1 (en) * 2010-04-21 2012-02-28 현대중공업 주식회사 Two solenoid valve of relay hybrid with two-phase fuel injection valve for Diesel engine
DE102011086339A1 (en) 2011-11-15 2013-05-16 Robert Bosch Gmbh Fuel injector, in particular common rail injector
WO2013138805A1 (en) * 2012-03-16 2013-09-19 International Engine Intellectual Property Company, Llc Fuel injector needle sleeve
GB201309122D0 (en) * 2013-05-21 2013-07-03 Delphi Tech Holding Sarl Fuel Injector
CN104481765B (en) * 2014-12-03 2016-08-24 中国第一汽车股份有限公司无锡油泵油嘴研究所 Fuelinjection nozzle
DE102015208767A1 (en) * 2015-05-12 2016-11-17 Robert Bosch Gmbh Gas injector with improved sealing
CN106014739B (en) * 2016-05-25 2018-05-18 中国第一汽车股份有限公司无锡油泵油嘴研究所 A kind of atomizer
EP3642520B1 (en) 2017-06-23 2023-11-22 Graco Minnesota Inc. Variable flow poppet valve
CN111075626B (en) * 2019-12-19 2020-12-18 武汉科技大学 Oil sprayer with variable spray holes
CN111075624B (en) * 2019-12-20 2021-04-09 一汽解放汽车有限公司 Oil injection device

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5899389A (en) * 1997-06-02 1999-05-04 Cummins Engine Company, Inc. Two stage fuel injector nozzle assembly
GB9916464D0 (en) * 1999-07-14 1999-09-15 Lucas Ind Plc Fuel injector
DE10010863A1 (en) * 2000-03-06 2001-09-27 Bosch Gmbh Robert Fuel injection nozzle; has nozzle body with two groups of nozzle holes opened and closed by two nozzle needles, which are independently operated and are arranged next to each other
DE10122241A1 (en) * 2001-05-08 2002-12-05 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
US6705543B2 (en) * 2001-08-22 2004-03-16 Cummins Inc. Variable pressure fuel injection system with dual flow rate injector
DE10141679A1 (en) * 2001-08-25 2003-03-06 Bosch Gmbh Robert Fuel injection device for an internal combustion engine
DE10205970A1 (en) * 2002-02-14 2003-09-04 Bosch Gmbh Robert Fuel injection valve for internal combustion engines
DE10222196A1 (en) * 2002-05-18 2003-11-27 Bosch Gmbh Robert Fuel injection valve for combustion engine, has control valve with valve chamber and valve member that is moveable between two end positions for opening or closing connections to certain chambers

Also Published As

Publication number Publication date
WO2005095785A1 (en) 2005-10-13
DE102004015360A1 (en) 2005-10-20
US20070290075A1 (en) 2007-12-20
DE502005009231D1 (en) 2010-04-29
EP1747370A1 (en) 2007-01-31
CN1938513A (en) 2007-03-28
JP2007530862A (en) 2007-11-01
ATE461362T1 (en) 2010-04-15

Similar Documents

Publication Publication Date Title
EP1747370B1 (en) Fuel-injection valve for internal combustion engines
DE19612738C2 (en) Accumulator injection system for internal combustion engines
EP1656498B1 (en) Fuel injection valve controlled by a pilot valve
DE102006036843B4 (en) Fuel injector
EP2183476B1 (en) Fuel injection valve with improved tightness on the sealing seat of a pressure-compensated control valve
EP1654456B1 (en) Fuel injection device for an internal combustion engine
EP1387939B1 (en) Fuel injection valve for internal combustion engines
EP1476652B1 (en) Fuel injection valve for internal combustion engines
DE10315821A1 (en) Motor vehicle internal combustion engine injection valve has housing with bore and pressure space defining throttled connection with valve shoulder on needle
CH689282A5 (en) Injection valve for a particular intended as a diesel engine internal combustion engine.
DE102007000095B4 (en) Fuel injection element
WO2007141094A1 (en) Fuel injection device for an internal combustion engine
EP1719904A1 (en) Fuel injector
EP1650427B1 (en) Fuel injection valve for internal combustion engines
EP2458194B1 (en) Fuel injector valve for combustion engines
EP1952012B1 (en) Injector
WO2001079688A1 (en) Fuel injection valve for internal combustion engines
WO2005045233A1 (en) Fuel injection valve for internal combustion engines
EP1608866A1 (en) Fuel-injection valve for internal combustion engines
WO2005052352A1 (en) Injection nozzle
EP2740927B1 (en) Fuel injector valve for combustion engines
EP1576283A1 (en) Fuel injection valve for internal combustion engines
EP1546546A1 (en) Fuel injection valve for internal combustion engines
DE102005005713A1 (en) Jet construction group with injection valve for internal combustion engine has two recesses in jet needle
DE3410476A1 (en) Fuel injection nozzle for internal combustion engines

Legal Events

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

Free format text: ORIGINAL CODE: 0009012

17P Request for examination filed

Effective date: 20061030

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

DAX Request for extension of the european patent (deleted)
17Q First examination report despatched

Effective date: 20081209

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IS IT LI LT LU MC NL PL PT RO SE SI SK TR

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

REF Corresponds to:

Ref document number: 502005009231

Country of ref document: DE

Date of ref document: 20100429

Kind code of ref document: P

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20100317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20100317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: PL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: SI

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

REG Reference to a national code

Ref country code: IE

Ref legal event code: FD4D

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: RO

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: ES

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100628

Ref country code: NL

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: GR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100618

Ref country code: EE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: CY

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: SE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: IS

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100717

Ref country code: CZ

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: BG

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100617

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: PT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100719

Ref country code: DK

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

Ref country code: IE

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

26N No opposition filed

Effective date: 20101220

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

BERE Be: lapsed

Owner name: ROBERT BOSCH G.M.B.H.

Effective date: 20110131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: MC

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110131

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20110119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110131

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110131

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: BE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110131

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110119

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 461362

Country of ref document: AT

Kind code of ref document: T

Effective date: 20110119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: AT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110119

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20130207

Year of fee payment: 9

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LU

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20110119

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: TR

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: HU

Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20100317

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20140325

Year of fee payment: 10

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20140930

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20140131

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502005009231

Country of ref document: DE

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20150801