EP2932087A1 - Fuel injection valve - Google Patents

Fuel injection valve

Info

Publication number
EP2932087A1
EP2932087A1 EP13779192.7A EP13779192A EP2932087A1 EP 2932087 A1 EP2932087 A1 EP 2932087A1 EP 13779192 A EP13779192 A EP 13779192A EP 2932087 A1 EP2932087 A1 EP 2932087A1
Authority
EP
European Patent Office
Prior art keywords
control valve
valve seat
fuel injection
abiaufbohrung
fuel
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP13779192.7A
Other languages
German (de)
French (fr)
Other versions
EP2932087B1 (en
Inventor
Lars Olems
Stefan Schuerg
Robert Barunovic
Ronny Leonhardt
Wolfgang Stoecklein
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Robert Bosch GmbH
Original Assignee
Robert Bosch GmbH
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Robert Bosch GmbH filed Critical Robert Bosch GmbH
Publication of EP2932087A1 publication Critical patent/EP2932087A1/en
Application granted granted Critical
Publication of EP2932087B1 publication Critical patent/EP2932087B1/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M47/00—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure
    • F02M47/02—Fuel-injection apparatus operated cyclically with fuel-injection valves actuated by fluid pressure of accumulator-injector type, i.e. having fuel pressure of accumulator tending to open, and fuel pressure in other chamber tending to close, injection valves and having means for periodically releasing that closing pressure
    • F02M47/027—Electrically actuated valves draining the chamber to release the closing pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/007—Details not provided for in, or of interest apart from, the apparatus of the groups F02M63/0014 - F02M63/0059
    • F02M63/0077—Valve seat details
    • 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
    • F02M2200/28—Details of throttles in fuel-injection apparatus

Definitions

  • the invention relates to a fuel injection valve, as it is preferably used for injection of fuel in combustion chambers of internal combustion engines.
  • Fuel injection valves as they are preferably used to inject fuel under high pressure into combustion chambers of internal combustion engines, are known from the prior art, for example from the published patent application DE 198 27 267 AI.
  • the fuel injection valves comprise a nozzle needle which cooperates with a nozzle seat for opening and closing at least one injection opening.
  • the nozzle needle is thereby moved directly or indirectly by the pressure in a control chamber in the longitudinal direction and thus opens and closes the injection openings, wherein the control chamber via a control valve with a low pressure space is connectable.
  • the control valve comprises an electrically controllable actuator which actuates a control valve member which opens and closes a beideboh- tion connecting the control chamber with the low-pressure chamber.
  • the prior art fuel injector has a control valve member that includes a sealing ball that cooperates with a control valve seat to open and close the drainage bore.
  • the sealing ball acts together with a conical control valve seat, so that between the control valve seat and the sealing ball a flow cross-section is opened, through which the fuel flows from the Abiaufbohrung in the low pressure chamber.
  • it is essential that the injection is very precise, ie at a precisely defined time and with the exact duration.
  • the injection is often divided into two or more partial injections, which is achieved by correspondingly fast opening and closing of the control valve.
  • the control valve To relieve the control room as quickly as possible and refill with fuel under high pressure after closing the control valve, the control valve must release the Abiaufbohrung as soon as possible and close again, which is possible the faster, the smaller the stroke, the Pass control valve member, since the length of the stroke is received directly in the switching time.
  • the forces necessary for moving the control valve member should be kept as low as possible, since the construction of, for example, a strong magnetic force requires high currents, which can be switched only relatively slowly.
  • the sealing ball has the largest possible diameter
  • the sealing line on which the control valve member, so here the sealing ball rests on the control valve seat has the largest possible diameter.
  • control valve member loading spring must be provided, which in turn must be suppressed by a very strong electromagnet or piezoelectric actuator, which requires high currents and thus high energy and has a negative effect on the switching time of the control valve.
  • the sealing line on which the control valve member is seated on the valve seat and which limits the pressurized surface of the control valve member to the outside, thus can not be chosen too large, so that an acceleration of the switching time are set narrow limits.
  • the fuel injection valve according to the invention has the advantage that the switching time compared to the known control valves is significantly reduced, without the required forces for movement of the control valve member are increased.
  • the fuel injection valve has a control valve which controls the fuel flow through a Abiaufbohrung connecting the control chamber with a low-pressure chamber, wherein the control valve comprises a movable sealing element which cooperates with a control valve seat and closes or opens a Abiaufbohrung, the seal happens along a boundary length.
  • the boundary length encloses a cross-sectional area, and the relationship is that the quotient of the square of the boundary length and the cross-sectional area is greater than 4 ⁇ ⁇ . This ratio is always met at an outlet opening of a Abiaufbohrung when the outlet is not circular. The larger the boundary length in the
  • the quotient of the sum of the squares of the boundary lengths of the respective outlet openings and the sum of the cross-sectional areas of the individual drainage boreholes must be greater than 4 ⁇ ⁇ .
  • the effect here is the same as in the provision of a non-circular outlet opening of the Abiaufbohrung, namely, that the controlled flow area is greater than when the same flow area is formed by a single circular drain opening.
  • the Control valve seat formed flat, which is easy to manufacture, even if several Abiaufbohritch are provided.
  • the sealing element which cooperates with its sealing surface with the control valve seat, is also formed flat in an advantageous manner.
  • the boundary lengths of the individual drain holes or the outlet openings are identical in this case with the outlet openings in the control valve seat and can be produced easily and inexpensively.
  • a plurality of drainage bores are provided, and their outlet openings in the control valve seat are arranged in a circle around a center.
  • the outflow of fuel from the Abiaufbohronne can be done in this case both inward and outward, so that a particularly large flow area is achieved.
  • the Abiaufbohrung or the Abiaufbohrept are advantageously designed so that they have a throttle function, which are necessary for the operation of the respective fuel injection valve.
  • a throttle function which are necessary for the operation of the respective fuel injection valve.
  • FIG. 1 shows a longitudinal section through a fuel injection valve in a schematic
  • Figure 2 is an enlargement in the region of the control valve seat of the known
  • Figure 3 shows the valve piece with associated sealing element of a first embodiment of the fuel injection valve according to the invention
  • Figure 3a shows a plan view of the valve piece
  • FIG. 3b shows a further cross section through the valve piece in the region of the control valve seat in a representation rotated by 90 degrees with respect to FIG. 3
  • FIG. 4 shows a cross section through the valve piece of a further fuel injection valve according to the invention
  • Figure 4a is a plan view of this valve piece
  • Figure 5 in the same representation as Figure 4 shows a further embodiment of the invention.
  • FIG. 1 a known from the prior art fuel injection valve is shown schematically in longitudinal section.
  • the fuel injection valve has a housing 1, which comprises a holding body 2 and a nozzle body 3, which are clamped liquid-tight against each other by a tensioning device, not shown in the drawing.
  • a pressure chamber 5 is formed, which is connected via a high-pressure line 12 to a high-pressure accumulator 13 and is always filled with fuel under high pressure during operation of the fuel injection valve.
  • the high pressure accumulator 13 is in turn supplied via a high pressure pump 14 with compressed fuel, which sucks the high pressure pump 14 from a tank 15 via a line 16.
  • a piston-shaped nozzle needle 6 is arranged longitudinally displaceable, which is guided in a guide portion 106 in the nozzle body 3.
  • the fuel flow through the pressure chamber 5 in the region of the guide section 106 is ensured by a plurality of polished sections 18 on the nozzle needle 6.
  • the nozzle needle 6 has at its combustion chamber end, a sealing surface 19, with which it cooperates with a nozzle seat 20 which has a conical shape in this embodiment and in which a plurality of injection openings 22 are formed, which are closed by the nozzle needle 8, if in Attachment to the nozzle seat 20 is. Facing away from the nozzle seat 20, the nozzle needle 6 is guided in the bore 8 of a valve piece 7, which closes the pressure chamber 5 away from the valve seat.
  • the valve member 7 is in turn fixed by an intermediate body 9 by a closing plate 4 which is screwed into the holding body 3, fixed within the housing 1.
  • the valve member 7 also separates the pressure chamber 5 from a low pressure chamber 29, in which a control valve 10 is arranged and which is connected via a drain line 37 to the fuel tank 15 and thereby always maintained at low pressure.
  • a control chamber 25 is limited, which is connected via an inlet bore 27 which is formed in the valve member 7 with the pressure chamber 5.
  • a drain bore 28 is also provided, which connects the control chamber 25 with the low-pressure chamber 29.
  • the Abiaufbohrung 28 in this case has an outlet throttle 128 which is formed within the Abiaufbohrung 28, so that the fuel flow is only throttled by the Abiillerbohrung.
  • the Abiaufbohrung 28 opens into a control valve seat 33 which is formed on the valve piece 7 and has a conical shape, and there forms an outlet opening 228, as shown in more detail in Figure 2.
  • the control valve 29 which includes a magnet armature 30 to which a sealing ball 32 is fixed, which cooperates with the conical control valve seat 33.
  • the armature 30 is acted upon by a spring 35 in the direction of the control valve seat 33 with a closing force and can be moved by means of an electromagnet 31 against the force of the spring 35, so that the sealing ball 32, the outlet opening 228 of Abiillerbohrung 28 releases. Since the Abiaufbohrung 28 is rotationally symmetrical, the outlet opening 228 forms a circle on which the sealing ball 32 sealingly abuts when it is in the closed position in contact with the control valve seat 33.
  • the control valve 10 is closed, so that in the control chamber 25, the same high fuel pressure prevails as in the pressure chamber 5, which presses the nozzle needle 6 against the nozzle seat 20 and thus closes the injection openings 22. If an injection takes place, then the electromagnet 31 is energized and attracts the armature 30 against the force of the spring 35. The sealing ball 32 thereby lifts off from the control valve seat 33 and releases the outlet opening 228 of the drainage bore 28.
  • the outflowing fuel from the control chamber 25 can drop the fuel pressure in the control chamber 25, although constantly fuel flows through the inlet bore 27, but this inflow is less than that
  • FIG. 3 shows the valve piece 7 of a fuel injection valve according to the invention, in which only the valve piece 7 and the sealing element 40 cooperating with the control valve seat 33 formed thereon have been changed with respect to the fuel injection valve shown in FIG.
  • the valve piece 7 is here constructed in two parts and, in addition to the actual valve piece 7, which receives the nozzle needle 6, still a valve section 7 ', in which the outlet throttle 128 is formed here.
  • the control valve seat 33 is formed in contrast to the embodiment shown in Figure 1 as a flat seat in which the outlet opening 228 of the Abiaufbohrung 28 is arranged centrally.
  • a sealing element is provided here for cooperation with the control valve seat 33, which has a hemispherical shape, wherein the flat side of the hemisphere faces the control valve seat 33.
  • the outlet opening 228 of the drainage bore 28 is rectangular in this embodiment, as shown in Figure 3a in a plan view of the valve section 7 '.
  • the rectangular outlet opening 228 has a length a and a width b, because the rectangular outlet opening 228 is completely covered by the sealing element 40 in the closed position of the control valve and thereby sealed. Since both the control valve seat 33 and the sealing element 40 are formed flat, the outlet opening 228 is sealed exactly along the contour of this rectangle, so that the boundary length U of the outlet opening 228 twice (a
  • the portion of the Abiaufbohrung 28 is shown in cross-section, which is formed in the valve section 7 ', wherein the representation is rotated relative to that in Figure 3 by 90 degrees.
  • the Abiaufbohrung shows in this illustration a funnel shape, which forms the transition from the cylindrical Abiaufbohrung 28 within the valve piece 7 to the rectangular outlet opening 228 on the control valve seat 33.
  • the valve piece 7 is divided depends on the shape of the Abiaufbohrung 28 and the available manufacturing process. It can also be provided that the valve member 7 shown here and the valve section 7 'are integrally formed.
  • the outflow of the fuel within the Abiaufbohrung 28 is turbulent in a fuel injection valve, that is, the influence of the surface of Abiaufbohrung 28 for a given cross-sectional area is of minor importance.
  • the fuel flows through the Abiaufbohrung 28 thus about the same resistance that a circular Abiaufbohrung with the same
  • FIG. 4 shows a further embodiment of the fuel injection valve according to the invention is shown, in which case only the valve section 7 'is shown in cross section. Instead of a single Abiaufbohrung here a plurality of Abiaufbohrept 28 'is provided, which open into the control valve seat 33.
  • Figure 4a shows in a plan view of the valve section 7 ', the Abiaufbohrept 28' and the outlet openings 228 'are arranged in a circle around the center of the valve section 7'.
  • Each of these outlet openings 228 'analogous to the embodiment of Figure 3 has a boundary length U and a
  • the Abiaufbohritch 28 'of the embodiment of Figure 4 can also be designed so that they take over the necessary function of the fuel injector throttle function, that is, a separate outlet throttle, as shown for example in Figure 3, can be omitted.
  • FIG. 5 shows a further exemplary embodiment, wherein this exemplary embodiment differs from that in FIG. 3 only in that an annular groove 44 is provided in the control valve seat 33.
  • This annular groove 44 limits the effective control valve seat on which the sealing element 40 is seated, which improves the sealing function.
  • the outflowing fuel which is indicated by arrows, can be set in turbulence and thereby braked, so that a throttling function is provided by the annular groove 44, which can replace the function of the outlet throttle, so that a separate outlet throttle within the Abiaufbohrung 28 is not necessary ,
  • the annular groove 44 can also be fluidically connected to the low-pressure side, that is, to the low-pressure space 29, for example, by a radial direction This prevents the control valve seat 33 is undermined by the inevitable wear with pressure and the acted upon by high pressure from the Abiaufbohrung 28 surface of the sealing element 40 too strong elevated.
  • the hydraulic opening force on the sealing element 40 or the armature 30 can thus always be kept below a limit, for example, below the spring force with which the magnet armature 30 is pressed by the spring 35 against the control valve seat 33. This ensures the tightness of the control valve 29 over the entire life.
  • control valve seat 33 is not flat, but for example, has a slight conical shape, which cooperates with a corresponding conical sealing element. This allows a centering function of the sealing element with respect to the control valve seat 33, so that a part of the guide function for the armature 30 is thereby adopted.

Abstract

The invention relates to a fuel injection valve comprising a control valve (10) for controlling a fuel flow through a drain bore (28), through which drain bore (28) fuel is directed from a control space (10) into a low-pressure space (29) and which drain bore (28) opens into a control valve seat (33) and forms an outlet opening (228) at said control valve seat. The control valve (10) comprises a movable sealing element (40) that interacts with the control valve seat (33; 33') and that closes the outlet opening (228) of the drain bore (28) when abutting at the control valve seat (33; 33'), wherein the sealing element (40) in the closed state of the control valve (10) closes the drain bore (28) along a boundary line (U) against the low pressure space (29) and the boundary line (U) encompasses a cross-section surface (A), wherein the quotient of the square of the boundary line (U2) and the cross-section surface (A) is higher than 4π. Alternatively, several drain bores can be provided, wherein the quotient of the sum of the squares of the boundary lines (U2) and the sum of the cross-section surfaces (A) of the individual drain bores (28') is higher than 4π.

Description

Beschreibung  description
Titel title
Kraftstoffe i ns p r itz ve nti I  Fuels i ns p r itz ve nti I
Die Erfindung betrifft ein Kraftstoffeinspritzventil, wie es vorzugsweise zur Einspritzung von Kraftstoff in Brennräumen von Brennkraftmaschinen verwendet wird. The invention relates to a fuel injection valve, as it is preferably used for injection of fuel in combustion chambers of internal combustion engines.
Stand der Technik State of the art
Kraftstoffeinspritzventile, wie sie vorzugsweise benutzt werden, um Kraftstoff unter hohem Druck in Brennräume von Brennkraftmaschinen einzuspritzen, sind aus dem Stand der Technik bekannt, beispielweise aus der Offenlegungsschrift DE 198 27 267 AI. Die Kraftstoffeinspritzventile umfassen dabei eine Düsennadel, die mit einem Düsensitz zum Öffnen und Schließen wenigstens einer Einspritzöffnung zusammenwirkt. Die Düsennadel wird dabei direkt oder indirekt durch den Druck in einem Steuerraum in Längsrichtung bewegt und öffnet und schließt so die Einspritzöffnungen, wobei der Steuerraum über ein Steuerventil mit einem Niederdruckraum verbindbar ist. Das Steuerventil umfasst einen elektrisch ansteuerbaren Aktor, der ein Steuerventilglied betätigt, das eine Ablaufboh- rung öffnet und schließt, die den Steuerraum mit dem Niederdruckraum verbindet. Das aus dem Stand der Technik bekannte Kraftstoffeinspritzventil weist ein Steuerventilglied auf, das eine Dichtkugel umfasst, die mit einem Steuerventilsitz zum Öffnen und Schließen der Abiaufbohrung zusammenwirkt. Die Dichtkugel wirkt dabei mit einem konischen Steuerventilsitz zusammen, so dass zwischen dem Steuerventilsitz und der Dichtkugel ein Ablaufquerschnitt aufgesteuert wird, durch den der Kraftstoff aus der Abiaufbohrung in den Niederdruckraum abströmt. Insbesondere bei der Verwendung des Kraftstoffeinspritzventils bei einer schnelllaufenden, selbstzündenden Brennkraftmaschine ist es essentiell, dass die Einspritzung sehr präzise geschieht, d. h. zu einem genau festgelegten Zeitpunkt und mit der exakten Dauer. Für eine ruhige und schadstoffarme Verbrennung wird darüber hinaus die Einspritzung häufig in zwei oder mehr Teileinspritzungen aufgeteilt, was durch entsprechend schnelles Öffnen und Schließen des Steuerventils erreicht wird. Um den Steuerraum möglichst rasch zu entlasten und nach dem Schließen des Steuerventils wieder mit Kraftstoff unter hohem Druck zu befüllen, muss das Steuerventil die Abiaufbohrung dazu möglichst rasch freigeben und wieder verschließen, was um so schneller möglich ist, je kleiner der Hub ist, den das Steuerventilglied durchfahren muss, da die Länge des Hubes direkt in die Schaltzeit eingeht. Darüber hinaus sollten die Kräfte, die zur Bewegung des Steuerventilglieds notwendig sind, so gering wie möglich gehalten werden, da der Aufbau z.B. einer starken Magnetkraft hohe Ströme erfordert, die nur relativ langsam geschalten werden können. Fuel injection valves, as they are preferably used to inject fuel under high pressure into combustion chambers of internal combustion engines, are known from the prior art, for example from the published patent application DE 198 27 267 AI. The fuel injection valves comprise a nozzle needle which cooperates with a nozzle seat for opening and closing at least one injection opening. The nozzle needle is thereby moved directly or indirectly by the pressure in a control chamber in the longitudinal direction and thus opens and closes the injection openings, wherein the control chamber via a control valve with a low pressure space is connectable. The control valve comprises an electrically controllable actuator which actuates a control valve member which opens and closes a Ablaufboh- tion connecting the control chamber with the low-pressure chamber. The prior art fuel injector has a control valve member that includes a sealing ball that cooperates with a control valve seat to open and close the drainage bore. The sealing ball acts together with a conical control valve seat, so that between the control valve seat and the sealing ball a flow cross-section is opened, through which the fuel flows from the Abiaufbohrung in the low pressure chamber. In particular, when using the fuel injection valve in a high-speed, self-igniting internal combustion engine, it is essential that the injection is very precise, ie at a precisely defined time and with the exact duration. For a quiet and low-emission combustion, moreover, the injection is often divided into two or more partial injections, which is achieved by correspondingly fast opening and closing of the control valve. To relieve the control room as quickly as possible and refill with fuel under high pressure after closing the control valve, the control valve must release the Abiaufbohrung as soon as possible and close again, which is possible the faster, the smaller the stroke, the Pass control valve member, since the length of the stroke is received directly in the switching time. In addition, the forces necessary for moving the control valve member should be kept as low as possible, since the construction of, for example, a strong magnetic force requires high currents, which can be switched only relatively slowly.
Um einen möglichst großen Querschnitt mit möglichst geringem Hub To have the largest possible cross section with the smallest possible stroke
aufzusteuern, ist es somit vorteilhaft, wenn die Dichtkugel einen möglichst großen Durchmesser aufweist, und die Dichtlinie, an der das Steuerventilglied, also hier die Dichtkugel, auf dem Steuerventilsitz aufliegt, einen möglichst großen Durchmesser aufweist. Bei der Bewegung des Steuerventilglieds vom Steuerventilglied weg wird so bereits bei geringem Hub ein großer Durchflussquerschnitt aufgesteuert. Wird der Durchmesser jedoch groß gewählt, so ist das Steuerventilglied durch den hohen Kraftstoffdruck von Seiten des Steuerraums einer hohen öffnenden Kraft ausgesetzt, die das Steuerventilglied vom Steuerventilsitz wegdrückt. Um diese Kraft zu kompensieren, muss eine entsprechend starke, das Steuerventilglied belastende Feder vorgesehen sein, die wiederum durch einen sehr starken Elektromagneten oder Piezoaktor überdrückt werden muss, was hohe Ströme und damit hohe Energie erfordert und sich negativ auf die Schaltzeit des Steuerventils auswirkt. Die Dichtlinie, an der das Steuerventilglied auf dem Ventilsitz aufsitzt und die die druckbeaufschlagte Fläche des Steuerventilglieds nach außen begrenzt, kann somit nicht allzu groß gewählt werden, so dass einer Beschleunigung der Schaltzeit enge Grenzen gesetzt sind. Vorteile der Erfindung aufzusteuern, it is thus advantageous if the sealing ball has the largest possible diameter, and the sealing line on which the control valve member, so here the sealing ball rests on the control valve seat, has the largest possible diameter. During the movement of the control valve member away from the control valve member, a large flow cross-section is already opened at low lift. However, if the diameter is made large, the control valve member will be exposed to a high opening force by the high fuel pressure from the side of the control space which pushes the control valve member away from the control valve seat. To compensate for this force, a correspondingly strong, the control valve member loading spring must be provided, which in turn must be suppressed by a very strong electromagnet or piezoelectric actuator, which requires high currents and thus high energy and has a negative effect on the switching time of the control valve. The sealing line on which the control valve member is seated on the valve seat and which limits the pressurized surface of the control valve member to the outside, thus can not be chosen too large, so that an acceleration of the switching time are set narrow limits. Advantages of the invention
Das erfindungsgemäße Kraftstoffeinspritzventil weist demgegenüber den Vorteil auf, dass die Schaltzeit gegenüber den bekannten Steuerventilen deutlich redu- ziert ist, ohne dass die erforderlichen Kräfte zur Bewegung des Steuerventilglieds erhöht sind. Zu diesem Zweck weist das Kraftstoffeinspritzventil ein Steuerventil auf, das den Kraftstofffluss durch eine Abiaufbohrung steuert, die den Steuerraum mit einem Niederdruckraum verbindet, wobei das Steuerventil ein bewegliches Dichtelement umfasst, das mit einem Steuerventilsitz zusammenwirkt und die eine Abiaufbohrung verschließt oder öffnet, wobei die Abdichtung entlang einer Berandungslänge geschieht. Die Berandungslänge umschließt dabei eine Querschnittsfläche, und es gilt die Beziehung, dass der Quotient aus dem Quadrat der Berandungslänge und der Querschnittsfläche größer als 4·π ist. Dieses Verhältnis ist bei einer Austrittsöffnung einer Abiaufbohrung immer dann erfüllt, wenn die Austrittsöffnung nicht kreisförmig ist. Je größer die Berandungslänge imIn contrast, the fuel injection valve according to the invention has the advantage that the switching time compared to the known control valves is significantly reduced, without the required forces for movement of the control valve member are increased. For this purpose, the fuel injection valve has a control valve which controls the fuel flow through a Abiaufbohrung connecting the control chamber with a low-pressure chamber, wherein the control valve comprises a movable sealing element which cooperates with a control valve seat and closes or opens a Abiaufbohrung, the seal happens along a boundary length. The boundary length encloses a cross-sectional area, and the relationship is that the quotient of the square of the boundary length and the cross-sectional area is greater than 4 · π. This ratio is always met at an outlet opening of a Abiaufbohrung when the outlet is not circular. The larger the boundary length in the
Verhältnis zur umschlossenen Querschnittsfläche, desto größer ist der aufgesteuerte Durchflussquerschnitt, durch den der Kraftstoff aus der Ablaufboh- rung in den Niederdruckraum strömen kann. Somit genügt ein kleiner Hub des Steuerventilglieds, um einen ausreichenden Ablaufquerschnitt aufzusteuern und den Kraftstoffabfluss aus dem Steuerraum zu ermöglichen, was die Schaltzeit des Steuerventils verringert. Relative to the enclosed cross-sectional area, the greater is the controlled flow cross-section through which the fuel can flow from the drain hole into the low-pressure space. Thus, a small stroke of the control valve member is sufficient to control a sufficient flow area and to allow the fuel drain from the control chamber, which reduces the switching time of the control valve.
Alternativ kann auch vorgesehen sein, dass statt einer Abiaufbohrung mit einer entsprechenden Austrittsöffnung mehrere Abiaufbohrungen vorgesehen sind, die alle in den Niederdruckraum münden und die alle durch das Steuerventilglied beiAlternatively it can also be provided that instead of a Abiaufbohrung with a corresponding outlet opening several Abiaufbohrungen are provided, all of which open into the low-pressure chamber and all by the control valve member at
Anlage am Steuerventilsitz verschlossen werden. Hierbei muss der Quotient aus der Summe der Quadrate der Berandungslängen der jeweiligen Austrittsöffnungen und der Summe der Querschnittsflächen der einzelnen Abiaufbohrungen größer als 4·π sein. Der Effekt ist hier der gleiche wie bei dem Vorsehen einer nicht kreisförmigen Austrittsöffnung der Abiaufbohrung, nämlich, dass der aufgesteuerte Ablaufquerschnitt größer ist als wenn der gleiche Ablaufquerschnitt durch eine einzelne kreisrunde Ablauföffnung gebildet wird. System be closed at the control valve seat. Here, the quotient of the sum of the squares of the boundary lengths of the respective outlet openings and the sum of the cross-sectional areas of the individual drainage boreholes must be greater than 4 · π. The effect here is the same as in the provision of a non-circular outlet opening of the Abiaufbohrung, namely, that the controlled flow area is greater than when the same flow area is formed by a single circular drain opening.
In einer ersten vorteilhaften Ausgestaltung, gleich ob eine einzelne Ablaufboh- rung vorgesehen ist oder mehrere Abiaufbohrungen vorgesehen sind, ist der Steuerventilsitz flach ausgebildet, was einfach zu fertigen ist, gerade, wenn mehrere Abiaufbohrungen vorgesehen sind. Das Dichtelement, das mit seiner Dichtfläche mit dem Steuerventilsitz zusammenwirkt, ist dabei in vorteilhafter Weise ebenfalls flach ausgebildet. Die Berandungslängen der einzelnen Ablaufbohrun- gen bzw. der Austrittsöffnungen sind in diesem Fall identisch mit den Austrittsöffnungen im Steuerventilsitz und lassen sich einfach und kostengünstig herstellen. In a first advantageous embodiment, whether a single drainage hole is provided or a plurality of drainage holes are provided, the Control valve seat formed flat, which is easy to manufacture, even if several Abiaufbohrungen are provided. The sealing element, which cooperates with its sealing surface with the control valve seat, is also formed flat in an advantageous manner. The boundary lengths of the individual drain holes or the outlet openings are identical in this case with the outlet openings in the control valve seat and can be produced easily and inexpensively.
In einer weiteren vorteilhaften Ausgestaltung sind mehrere Abiaufbohrungen vorgesehen, und deren Austrittsöffnungen im Steuerventilsitz sind kreisförmig um eine Mitte angeordnet. Das Abströmen des Kraftstoffs aus den Abiaufbohrungen kann in diesem Fall sowohl nach innen als auch nach außen geschehen, sodass ein besonders großer Abflussquerschnitt erreicht wird. In a further advantageous embodiment, a plurality of drainage bores are provided, and their outlet openings in the control valve seat are arranged in a circle around a center. The outflow of fuel from the Abiaufbohrungen can be done in this case both inward and outward, so that a particularly large flow area is achieved.
Die Abiaufbohrung bzw. die Abiaufbohrungen sind in vorteilhafter Weise so ausgebildet, dass sie eine Drosselfunktion aufweisen, die für den Betrieb des jeweiligen Kraftstoffeinspritzventils notwendig sind. Durch diese entsprechende Ausgestaltung kann erreicht werden, dass die Abiaufbohrung keine separate Drossel mehr aufweisen muss, wie bei sonstigen Kraftstoffeinspritzventilen, was die Fertigung erleichtert. The Abiaufbohrung or the Abiaufbohrungen are advantageously designed so that they have a throttle function, which are necessary for the operation of the respective fuel injection valve. By this appropriate configuration can be achieved that the Abiaufbohrung no longer need to have a separate throttle, as with other fuel injection valves, which facilitates the production.
Zeichnung drawing
In der Zeichnung sind verschiedene Ausführungsbeispiele des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt. Es zeigt In the drawing, various embodiments of the fuel injection valve according to the invention are shown. It shows
Figur 1 einen Längsschnitt durch ein Kraftstoffeinspritzventil in schematischer  1 shows a longitudinal section through a fuel injection valve in a schematic
Darstellung, wie es aus dem Stand der Technik bekannt ist, Representation, as is known from the prior art,
Figur 2 eine Vergrößerung im Bereich des Steuerventilsitzes des bekannten Figure 2 is an enlargement in the region of the control valve seat of the known
Kraftstoffeinspritzventils,  Fuel injector,
Figur 3 das Ventilstück mit zugehörigem Dichtelement einer ersten Ausführungsform des erfindungsgemäßen Kraftstoffeinspritzventils, die Figure 3 shows the valve piece with associated sealing element of a first embodiment of the fuel injection valve according to the invention, the
Figur 3a zeigt eine Draufsicht auf das Ventilstück und Figure 3a shows a plan view of the valve piece and
Figur 3b einen weiteren Querschnitt durch das Ventilstück im Bereich des Steuerventilsitzes in einer gegenüber der Figur 3 um 90 Grad gedrehten Darstellung, Figur 4 einen Querschnitt durch das Ventilstück eines weiteren erfindungsge- mäßen Kraftstoffeinspritzventils und FIG. 3b shows a further cross section through the valve piece in the region of the control valve seat in a representation rotated by 90 degrees with respect to FIG. 3, FIG. 4 shows a cross section through the valve piece of a further fuel injection valve according to the invention and FIG
Figur 4a eine Draufsicht auf dieses Ventilstück, und Figure 4a is a plan view of this valve piece, and
Figur 5 in derselben Darstellung wie Figur 4 ein weiteres Ausführungsbeispiel der Erfindung.  Figure 5 in the same representation as Figure 4 shows a further embodiment of the invention.
Beschreibung der Ausführungsbeisp DESCRIPTION OF EMBODIMENT
In Figur 1 ist ein aus dem Stand der Technik bekanntes Kraftstoffeinspritzventil im Längsschnitt schematisch dargestellt. Das Kraftstoffeinspritzventil weist ein Gehäuse 1 auf, das einen Haltekörper 2 und einen Düsenkörper 3 umfasst, die durch eine in der Zeichnung nicht dargestellte Spannvorrichtung flüssigkeitsdicht gegeneinander verspannt sind. Im Gehäuse 1 ist ein Druckraum 5 ausgebildet, der über eine Hochdruckleitung 12 mit einem Hochdruckspeicher 13 verbunden ist und so beim Betrieb des Kraftstoffeinspritzventils stets mit Kraftstoff unter hohem Druck befüllt ist. Der Hochdruckspeicher 13 wird seinerseits über eine Hochdruckpumpe 14 mit verdichtetem Kraftstoff versorgt, den die Hochdruckpumpe 14 aus einem Tank 15 über eine Leitung 16 ansaugt. In Figure 1, a known from the prior art fuel injection valve is shown schematically in longitudinal section. The fuel injection valve has a housing 1, which comprises a holding body 2 and a nozzle body 3, which are clamped liquid-tight against each other by a tensioning device, not shown in the drawing. In the housing 1, a pressure chamber 5 is formed, which is connected via a high-pressure line 12 to a high-pressure accumulator 13 and is always filled with fuel under high pressure during operation of the fuel injection valve. The high pressure accumulator 13 is in turn supplied via a high pressure pump 14 with compressed fuel, which sucks the high pressure pump 14 from a tank 15 via a line 16.
Im Druckraum 5 ist eine kolbenförmige Düsennadel 6 längsverschiebbar angeordnet, die in einem Führungsabschnitt 106 im Düsenkörper 3 geführt ist. Der Kraftstofffluss durch den Druckraum 5 im Bereich des Führungsabschnitts 106 wird dabei durch mehrere Anschliffe 18 an der Düsennadel 6 sichergestellt. Die Düsennadel 6 weist an ihrem brennraumseitigen Ende eine Dichtfläche 19 auf, mit der sie mit einem Düsensitz 20 zusammenwirkt, der in diesem Ausführungsbeispiel eine konische Form hat und in dem mehrere Einspritzöffnungen 22 ausgebildet sind, die durch die Düsennadel 8 verschlossen werden, wenn diese in Anlage am Düsensitz 20 ist. Dem Düsensitz 20 abgewandt wird die Düsennadel 6 in der Bohrung 8 eines Ventilstücks 7 geführt, das den Druckraum 5 ventilsitz- abgewandt verschließt. Das Ventilstück 7 wird seinerseits über einen Zwischenkörper 9 durch eine Schlussplatte 4, die in den Haltekörper 3 eingeschraubt ist, innerhalb des Gehäuses 1 ortsfest fixiert. Das Ventilstück 7 trennt dabei auch den Druckraum 5 von einem Niederdruckraum 29, in dem ein Steuerventil 10 angeordnet ist und der über eine Ablaufleitung 37 mit dem Kraftstofftank 15 verbunden ist und dadurch stets auf niedrigem Druck gehalten wird. Durch die Düsennadel 6 und die Bohrung 8 im Ventilstück 7 wird ein Steuerraum 25 begrenzt, der über eine Zulaufbohrung 27, die im Ventilstück 7 ausgebildet ist, mit dem Druckraum 5 verbunden ist. Im Ventilstück 7 ist darüber hinaus eine Ab- laufbohrung 28 vorgesehen, die den Steuerraum 25 mit dem Niederdruckraum 29 verbindet. Die Abiaufbohrung 28 weist dabei eine Ablaufdrossel 128 auf, die innerhalb der Abiaufbohrung 28 ausgebildet ist, sodass der Kraftstofffluss durch die Abiaufbohrung nur gedrosselt geschieht. Die Abiaufbohrung 28 mündet in einen Steuerventilsitz 33, der am Ventilstück 7 ausgebildet ist und eine konische Form hat, und bildet dort eine Austrittsöffnung 228, wie dies näher in Figur 2 dargestellt ist. In the pressure chamber 5, a piston-shaped nozzle needle 6 is arranged longitudinally displaceable, which is guided in a guide portion 106 in the nozzle body 3. The fuel flow through the pressure chamber 5 in the region of the guide section 106 is ensured by a plurality of polished sections 18 on the nozzle needle 6. The nozzle needle 6 has at its combustion chamber end, a sealing surface 19, with which it cooperates with a nozzle seat 20 which has a conical shape in this embodiment and in which a plurality of injection openings 22 are formed, which are closed by the nozzle needle 8, if in Attachment to the nozzle seat 20 is. Facing away from the nozzle seat 20, the nozzle needle 6 is guided in the bore 8 of a valve piece 7, which closes the pressure chamber 5 away from the valve seat. The valve member 7 is in turn fixed by an intermediate body 9 by a closing plate 4 which is screwed into the holding body 3, fixed within the housing 1. The valve member 7 also separates the pressure chamber 5 from a low pressure chamber 29, in which a control valve 10 is arranged and which is connected via a drain line 37 to the fuel tank 15 and thereby always maintained at low pressure. Through the nozzle needle 6 and the bore 8 in the valve piece 7, a control chamber 25 is limited, which is connected via an inlet bore 27 which is formed in the valve member 7 with the pressure chamber 5. In the valve piece 7, a drain bore 28 is also provided, which connects the control chamber 25 with the low-pressure chamber 29. The Abiaufbohrung 28 in this case has an outlet throttle 128 which is formed within the Abiaufbohrung 28, so that the fuel flow is only throttled by the Abiaufbohrung. The Abiaufbohrung 28 opens into a control valve seat 33 which is formed on the valve piece 7 and has a conical shape, and there forms an outlet opening 228, as shown in more detail in Figure 2.
Zum Öffnen und Schließen der Abiaufbohrung 28 dient das Steuerventil 29, das einen Magnetanker 30 umfasst, an dem eine Dichtkugel 32 befestigt ist, die mit dem konischen Steuerventilsitz 33 zusammenwirkt. Der Magnetanker 30 wird von einer Feder 35 in Richtung des Steuerventilsitzes 33 mit einer Schließkraft beaufschlagt und kann mit Hilfe eines Elektromagneten 31 entgegen der Kraft der Feder 35 bewegt werden, sodass die Dichtkugel 32 die Austrittsöffnung 228 der Abiaufbohrung 28 freigibt. Da die Abiaufbohrung 28 rotationssymmetrisch ausgebildet ist, bildet die Austrittsöffnung 228 einen Kreis, an dem die Dichtkugel 32 dichtend anliegt, wenn sie in Schließstellung in Anlage am Steuerventilsitz 33 ist. To open and close the Abiaufbohrung 28 serves the control valve 29, which includes a magnet armature 30 to which a sealing ball 32 is fixed, which cooperates with the conical control valve seat 33. The armature 30 is acted upon by a spring 35 in the direction of the control valve seat 33 with a closing force and can be moved by means of an electromagnet 31 against the force of the spring 35, so that the sealing ball 32, the outlet opening 228 of Abiaufbohrung 28 releases. Since the Abiaufbohrung 28 is rotationally symmetrical, the outlet opening 228 forms a circle on which the sealing ball 32 sealingly abuts when it is in the closed position in contact with the control valve seat 33.
Die Funktionsweise des Kraftstoffeinspritzventils wie folgt: Zu Beginn der Einspritzung ist das Steuerventil 10 geschlossen, so dass im Steuerraum 25 der gleiche hohe Kraftstoffdruck wie im Druckraum 5 herrscht, der die Düsennadel 6 gegen den Düsensitz 20 drückt und so die Einspritzöffnungen 22 verschließt. Soll eine Einspritzung erfolgen, so wird der Elektromagnet 31 bestromt und zieht den Magnetanker 30 entgegen der Kraft der Feder 35 an. Die Dichtkugel 32 hebt dadurch vom Steuerventilsitz 33 ab und gibt die Austrittsöffnung 228 der Ablaufboh- rung 28 frei. Der abströmende Kraftstoff aus dem Steuerraum 25 lässt den Kraftstoffdruck im Steuerraum 25 absinken, wobei zwar ständig Kraftstoff über die Zulaufbohrung 27 nachströmt, diese Zuströmung jedoch geringer als die The operation of the fuel injection valve as follows: At the beginning of the injection, the control valve 10 is closed, so that in the control chamber 25, the same high fuel pressure prevails as in the pressure chamber 5, which presses the nozzle needle 6 against the nozzle seat 20 and thus closes the injection openings 22. If an injection takes place, then the electromagnet 31 is energized and attracts the armature 30 against the force of the spring 35. The sealing ball 32 thereby lifts off from the control valve seat 33 and releases the outlet opening 228 of the drainage bore 28. The outflowing fuel from the control chamber 25 can drop the fuel pressure in the control chamber 25, although constantly fuel flows through the inlet bore 27, but this inflow is less than that
Abströmung durch die Abiaufbohrung 28 ist. Die somit verringerte hydraulische Kraft auf die düsensitzabgewandte Stirnseite der Düsennadel 6 bewirkt, dass die Düsennadel 6 durch den Kraftstoff druck im Druckraum 5 vom Düsensitz 20 weggedrückt wird, sodass die Einspritzöffnungen 22 mit dem Druckraum 5 verbunden werden und Kraftstoff aus den Einspritzöffnungen 22 austritt. Zur Beendigung der Einspritzung wird die Bestromung des Elektromagneten 31 beendet, worauf die Feder 35 den Magnetanker 30 und damit auch die Dichtkugel 32 wieder zurück in ihre Schließstellung drückt. Über den Zustrom von Kraftstoff durch die Zulaufbohrung 27 baut sich sehr rasch wieder ein hoher Kraftstoffdruck im Steuerraum 25 auf, der die Düsennadel 6 zurück in ihre Schließstellung in Anlage an den Düsensitz 20 drückt. Outflow through the Abiaufbohrung 28 is. The thus reduced hydraulic force on the nozzle seat facing away from the end of the nozzle needle 6 causes the Nozzle needle 6 is pushed away from the nozzle seat 20 by the fuel pressure in the pressure chamber 5, so that the injection openings 22 are connected to the pressure chamber 5 and fuel exits from the injection openings 22. To end the injection, the energization of the electromagnet 31 is stopped, whereupon the spring 35 presses the armature 30 and thus also the sealing ball 32 back into its closed position. About the influx of fuel through the inlet bore 27 is again very quickly a high fuel pressure in the control chamber 25, which presses the nozzle needle 6 back into its closed position in contact with the nozzle seat 20.
Figur 3 zeigt das Ventilstück 7 eines erfindungsgemäßen Kraftstoffeinspritzventils, bei dem gegenüber dem in Figur 1 gezeigten Kraftstoffeinspritzventil nur das Ventilstück 7 und das mit dem daran ausgebildeten Steuerventilsitz 33 zusammenwirkende Dichtelement 40 geändert wurden. Das Ventilstück 7 ist hier zwei- teilig aufgebaut und umfasst neben dem eigentlichen Ventilstück 7, das die Düsennadel 6 aufnimmt, noch ein Ventilteilstück 7', in dem hier die Ablaufdrossel 128 ausgebildet ist. Der Steuerventilsitz 33 ist im Gegensatz zu dem in Figur 1 gezeigten Ausführungsbeispiel als Flachsitz ausgebildet, in dem die Austrittsöffnung 228 der Abiaufbohrung 28 mittig angeordnet ist. Am Magnetanker 30 ist hier zum Zusammenwirken mit dem Steuerventilsitz 33 ein Dichtelement vorgesehen, das eine Halbkugelform aufweist, wobei die flache Seite der Halbkugel dem Steuerventilsitz 33 zugewandt ist. Die Austrittsöffnung 228 der Ablaufboh- rung 28 ist in diesem Ausführungsbeispiel rechteckförmig ausgebildet, wie dies in Figur 3a in einer Draufsicht auf das Ventilteilstück 7' gezeigt ist. Die rechteckför- mige Austrittsöffnung 228 weist eine Länge a und eine Breite b auf, weil die rechteckförmige Austrittsöffnung 228 durch das Dichtelement 40 in Schließstellung des Steuerventils vollständig überdeckt und dadurch abgedichtet wird. Da sowohl der Steuerventilsitz 33 als auch das Dichtelement 40 flach ausgebildet sind, wird die Austrittsöffnung 228 genau entlang der Kontur dieses Rechtecks abgedichtet, sodass die Berandungslänge U der Austrittsöffnung 228 zweimal (aFIG. 3 shows the valve piece 7 of a fuel injection valve according to the invention, in which only the valve piece 7 and the sealing element 40 cooperating with the control valve seat 33 formed thereon have been changed with respect to the fuel injection valve shown in FIG. The valve piece 7 is here constructed in two parts and, in addition to the actual valve piece 7, which receives the nozzle needle 6, still a valve section 7 ', in which the outlet throttle 128 is formed here. The control valve seat 33 is formed in contrast to the embodiment shown in Figure 1 as a flat seat in which the outlet opening 228 of the Abiaufbohrung 28 is arranged centrally. At the magnet armature 30, a sealing element is provided here for cooperation with the control valve seat 33, which has a hemispherical shape, wherein the flat side of the hemisphere faces the control valve seat 33. The outlet opening 228 of the drainage bore 28 is rectangular in this embodiment, as shown in Figure 3a in a plan view of the valve section 7 '. The rectangular outlet opening 228 has a length a and a width b, because the rectangular outlet opening 228 is completely covered by the sealing element 40 in the closed position of the control valve and thereby sealed. Since both the control valve seat 33 and the sealing element 40 are formed flat, the outlet opening 228 is sealed exactly along the contour of this rectangle, so that the boundary length U of the outlet opening 228 twice (a
+ b) ist: + b) is:
U = 2 ■ (a + b) U = 2 ■ (a + b)
Die von der Berandungslänge U umschlossene Querschnittsfläche A ist damit a -b: A = a-b The cross-sectional area A enclosed by the boundary length U is thus a -b: A = down
Es lässt sich leicht zeigen, dass für alle Werte a, b der Quotient aus dem Quadrat der Berandungslänge U2 und der Querschnittsfläche A größer als 4·π ist: It can easily be shown that for all values a, b the quotient of the square of the boundary length U 2 and the cross-sectional area A is greater than 4 · π:
U2 U 2
— > 4π.  -> 4π.
A  A
Je länger die Austrittsöffnung 228 in diesem Ausführungsbeispiel ist, d. h. je kleiner b im Verhältnis zu a ist, desto größer ist der aufgesteuerte Abflussquerschnitt des Steuerventils bei gegebener Querschnittsfläche A der Austrittsöffnung 228. The longer the exit opening 228 in this embodiment, d. H. the smaller b in relation to a, the larger the opened out flow cross-section of the control valve for a given cross-sectional area A of the outlet opening 228.
In Figur 3b ist der Abschnitt der Abiaufbohrung 28 im Querschnitt dargestellt, der im Ventilteilstück 7' ausgebildet ist, wobei die Darstellung gegenüber der in Figur 3 um 90 Grad gedreht ist. Die Abiaufbohrung zeigt in dieser Darstellung eine Trichterform, die den Übergang von der zylindrischen Abiaufbohrung 28 innerhalb des Ventilstücks 7 zur rechteckförmigen Austrittsöffnung 228 am Steuerventilsitz 33 bildet. In wie viele Teile das Ventilstück 7 unterteilt ist, hängt von der Form der Abiaufbohrung 28 und der zur Verfügung stehenden Herstellungsverfahren ab. Es kann auch vorgesehen sein, dass das hier gezeigte Ventilstück 7 und das Ventilteilstück 7' einstückig ausgebildet sind. In Figure 3b, the portion of the Abiaufbohrung 28 is shown in cross-section, which is formed in the valve section 7 ', wherein the representation is rotated relative to that in Figure 3 by 90 degrees. The Abiaufbohrung shows in this illustration a funnel shape, which forms the transition from the cylindrical Abiaufbohrung 28 within the valve piece 7 to the rectangular outlet opening 228 on the control valve seat 33. In how many parts the valve piece 7 is divided depends on the shape of the Abiaufbohrung 28 and the available manufacturing process. It can also be provided that the valve member 7 shown here and the valve section 7 'are integrally formed.
Die Abströmung des Kraftstoffs innerhalb der Abiaufbohrung 28 ist bei einem Kraftstoffeinspritzventil turbulent, das heißt, dass der Einfluss der Oberfläche der Abiaufbohrung 28 bei gegebener Querschnittsfläche von untergeordneter Bedeutung ist. Der Kraftstoff strömt über die Abiaufbohrung 28 somit etwa mit dem gleichen Widerstand, den eine kreisrunde Abiaufbohrung mit derselben The outflow of the fuel within the Abiaufbohrung 28 is turbulent in a fuel injection valve, that is, the influence of the surface of Abiaufbohrung 28 for a given cross-sectional area is of minor importance. The fuel flows through the Abiaufbohrung 28 thus about the same resistance that a circular Abiaufbohrung with the same
Querschnittsfläche. Somit ist es nicht notwendig, den Einfluss der größeren Oberfläche der Abiaufbohrung 28 gegenüber den bekannten rotationssymmetrischen Abiaufbohrungen durch eine angepasste Querschnittsfläche zu kompensieren. Cross sectional area. Thus, it is not necessary to compensate for the influence of the larger surface of the Abiaufbohrung 28 over the known rotationally symmetrical Abiaufbohrungen by an adapted cross-sectional area.
In Figur 4 ist ein weiteres Ausführungsbeispiel des erfindungsgemäßen Kraftstoffeinspritzventils dargestellt, wobei hier nur das Ventilteilstück 7' im Querschnitt dargestellt ist. Statt einer einzelnen Abiaufbohrung ist hier eine Vielzahl von Abiaufbohrungen 28' vorgesehen, die in den Steuerventilsitz 33 münden. Wie Figur 4a in einer Draufsicht des Ventilteilstücks 7' zeigt, sind die Abiaufbohrungen 28' bzw. deren Austrittsöffnungen 228' kreisförmig um die Mitte des Ventilteilstücks 7' angeordnet. Jede dieser Austrittsöffnungen 228' weist analog zu dem Ausführungsbeispiel der Figur 3 eine Berandungslänge U und eine 4 shows a further embodiment of the fuel injection valve according to the invention is shown, in which case only the valve section 7 'is shown in cross section. Instead of a single Abiaufbohrung here a plurality of Abiaufbohrungen 28 'is provided, which open into the control valve seat 33. As Figure 4a shows in a plan view of the valve section 7 ', the Abiaufbohrungen 28' and the outlet openings 228 'are arranged in a circle around the center of the valve section 7'. Each of these outlet openings 228 'analogous to the embodiment of Figure 3 has a boundary length U and a
Querschnittsfläche A-, auf. Entsprechend gilt hier die Beziehung, dass der Quotient aus der Summe der Quadrate der Berandungslängen U und der Summe der Querschnittsflächen A-, der einzelnen Abiaufbohrungen 28' größer als 4·π ist: Cross-sectional area A-, on. Accordingly, the relationship applies here that the quotient of the sum of the squares of the boundary lengths U and the sum of the cross-sectional areas A-, of the individual drill bores 28 'is greater than 4 · π:
Die Abströmung des Kraftstoffs aus den Austrittsöffnungen 228' erfolgt nach allen möglichen Richtungen praktisch über die gesamte Berandungslänge U-„ so dass auch bei nur geringem Hub des Dichtelements 40 ein hoher The outflow of fuel from the outlet openings 228 'takes place in all possible directions virtually over the entire boundary length U- "so that even with only a small stroke of the sealing element 40, a high
Abströmquerschnitt aufgesteuert wird. Im Gegensatz zu dem in Figur 3 gezeigten Ausführungsbeispiel kann das Dichtelement 40' hier eine ringscheibenförmige Fläche aufweisen, da so die Auftrittsfläche auf dem Steuerventilsitz 33 vermindert wird, was Flächenpressung erhöht und damit die Dichtfunktion verbessert. Outflow cross section is opened. In contrast to the embodiment shown in Figure 3, the sealing element 40 'here have an annular disk-shaped surface, since so the tread surface on the control valve seat 33 is reduced, which increases surface pressure and thus improves the sealing function.
Die Abiaufbohrungen 28' des Ausführungsbeispiels der Figur 4 können auch so ausgestaltet sein, dass sie die für die Funktion des Kraftstoffeinspritzventils notwendige Drosselfunktion übernehmen, das heißt, dass eine separate Ablaufdrossel, wie sie beispielsweise in Figur 3 dargestellt ist, entfallen kann. The Abiaufbohrungen 28 'of the embodiment of Figure 4 can also be designed so that they take over the necessary function of the fuel injector throttle function, that is, a separate outlet throttle, as shown for example in Figure 3, can be omitted.
In Figur 5 ist ein weiteres Ausführungsbeispiel dargestellt, wobei sich dieses Ausführungsbeispiel von dem in der Figur 3 nur dadurch unterscheidet, dass eine Ringnut 44 im Steuerventilsitz 33 vorgesehen ist. Diese Ringnut 44 begrenzt den wirksamen Steuerventilsitz, auf dem das Dichtelement 40 aufsitzt, was die Dichtfunktion verbessert. Darüber hinaus kann der abströmende Kraftstoff, der durch Pfeile angedeutet ist, in Turbulenz versetzt und dadurch abgebremst werden, sodass durch die Ringnut 44 eine Drosselfunktion gegeben ist, die die Funktion der Ablaufdrossel ersetzen kann, sodass eine gesonderte Ablaufdrossel innerhalb der Abiaufbohrung 28 nicht notwendig ist. FIG. 5 shows a further exemplary embodiment, wherein this exemplary embodiment differs from that in FIG. 3 only in that an annular groove 44 is provided in the control valve seat 33. This annular groove 44 limits the effective control valve seat on which the sealing element 40 is seated, which improves the sealing function. In addition, the outflowing fuel, which is indicated by arrows, can be set in turbulence and thereby braked, so that a throttling function is provided by the annular groove 44, which can replace the function of the outlet throttle, so that a separate outlet throttle within the Abiaufbohrung 28 is not necessary ,
Die Ringnut 44 kann auch fluidisch mit der Niederdruckseite, also mit dem Niederdruckraum 29, verbunden sein, beispielsweise durch eine in radialer Richtung von der Abiaufbohrung 28 ausgehende Nut oder durch eine leichte Anschrägung des Steuerventilsites 33 außerhalb der Ringnut 44. Dies verhindert, dass der Steuerventilsitz 33 durch den unvermeidlichen Verschleiß mit Druck unterwandert wird und sich die mit Hochdruck aus der Abiaufbohrung 28 beaufschlagte Fläche des Dichtelements 40 zu stark erhöht. Die hydraulische Öffnungskraft auf das Dichtelement 40 bzw. den Magnetanker 30 kann so immer unter einem Grenzwert gehalten werden, beispielsweise unterhalb der Federkraft, mit der der Magnetanker 30 durch die Feder 35 gegen den Steuerventilsitz 33 gedrückt wird. Dies sichert die Dichtheit des Steuerventils 29 über die gesamte Lebensdauer. The annular groove 44 can also be fluidically connected to the low-pressure side, that is, to the low-pressure space 29, for example, by a radial direction This prevents the control valve seat 33 is undermined by the inevitable wear with pressure and the acted upon by high pressure from the Abiaufbohrung 28 surface of the sealing element 40 too strong elevated. The hydraulic opening force on the sealing element 40 or the armature 30 can thus always be kept below a limit, for example, below the spring force with which the magnet armature 30 is pressed by the spring 35 against the control valve seat 33. This ensures the tightness of the control valve 29 over the entire life.
Im Gegensatz zu den zuvor gezeigten Ausführungsbeispielen kann es auch vorgesehen sein, dass der Steuerventilsitz 33 nicht flach ausgebildet ist, sondern beispielsweise eine leichte Konusform aufweist, die mit einem entsprechend konischen Dichtelement zusammenwirkt. Dies ermöglicht eine zentrierende Funktion des Dichtelements in Bezug auf den Steuerventilsitz 33, sodass dadurch ein Teil der Führungsfunktion für den Magnetankers 30 übernommen wird. In contrast to the embodiments previously shown, it can also be provided that the control valve seat 33 is not flat, but for example, has a slight conical shape, which cooperates with a corresponding conical sealing element. This allows a centering function of the sealing element with respect to the control valve seat 33, so that a part of the guide function for the armature 30 is thereby adopted.

Claims

Ansprüche claims
1. Kraftstoffeinspritzventil mit einem Steuerventil (10) zur Steuerung eines 1. Fuel injection valve with a control valve (10) for controlling a
Kraftstoffflusses durch eine Abiaufbohrung (28), durch welche Abiaufbohrung (28) Kraftstoff aus einem Steuerraum (10) in einen Niederdruckraum (29) abgesteuert wird und welche Abiaufbohrung (28) in einen Steuerventilsitz (33) mündet und dort eine Austrittsöffnung (228) bildet, wobei das Steuerventil (10) ein bewegliches Dichtelement (40) umfasst, das mit dem Steuerventilsitz (33; 33') zusammenwirkt und das bei Anlage am Steuerventilsitz (33; 33') die Austrittsöffnung (228) der Abiaufbohrung (28) verschließt, dadurch gekennzeichnet, dass das Dichtelement (40) im geschlossenen Zustand des Steuerventils (10) die Abiaufbohrung (28) entlang einer Berandungslänge (U) gegen den Niederdruckraum (29) abschließt und die Berandungslänge (U) eine  Fuel flow through a Abiaufbohrung (28), through which Abiaufbohrung (28) fuel from a control chamber (10) is controlled in a low-pressure chamber (29) and which Abiaufbohrung (28) in a control valve seat (33) opens and there forms an outlet opening (228) wherein the control valve (10) comprises a movable sealing element (40) which cooperates with the control valve seat (33; 33 ') and closes the outlet opening (228) of the drainage bore (28) when resting against the control valve seat (33; 33'); characterized in that the sealing element (40) in the closed state of the control valve (10) the Abiaufbohrung (28) along a boundary length (U) against the low-pressure space (29) terminates and the boundary length (U) a
Querschnittsfläche (A) umschließt, wobei der Quotient aus dem Quadrat der Berandungslänge (U2) und der Querschnittsfläche (A) größer als 4·π ist. Cross-section area (A) encloses, wherein the quotient of the square of the boundary length (U 2 ) and the cross-sectional area (A) is greater than 4 · π.
2. Kraftstoffeinspritzventil mit einem Steuerventil (10) zur Steuerung eines 2. Fuel injection valve with a control valve (10) for controlling a
Kraftstoffflusses durch mehrere Abiaufbohrungen (28'), durch welche Abiaufbohrungen (28') Kraftstoff aus einem Steuerraum (10) in einen Niederdruckraum (29) abgesteuert wird und welche Abiaufbohrungen (28') in einen Steuerventilsitz (33) münden und dort Austrittsöffnungen (228') bilden, wobei das Steuerventil (10) ein bewegliches Dichtelement (40) umfasst, das mit dem Steuerventilsitz (33; 33') zusammenwirkt und das bei Anlage am Steuerventilsitz (33; 33') die Austrittsöffnungen (228') der Abiaufbohrungen (28') verschließt, dadurch gekennzeichnet, dass das Dichtelement (40) die Austrittsöffnungen (228') der mehreren Ab- laufbohrungen (28') jeweils entlang einer Berandungslänge (U,) gegen den Niederdruckraum (29) abschließt und jede Berandungslänge (U,) jeweils eine Querschnittsfläche (A) umschließt, wobei der Quotient aus dem Quadrat der Summe der einzelnen Berandungslängen (U,2) und der Summe der einzelnen Querschnittsflächen (A) größer als 4·π ist. Fuel flow through a plurality of Abiaufbohrungen (28 '), through which Abiaufbohrungen (28') fuel from a control chamber (10) is controlled in a low pressure chamber (29) and which Abiaufbohrungen (28 ') into a control valve seat (33) open and there outlet openings (228 '), wherein the control valve (10) comprises a movable sealing element (40) which cooperates with the control valve seat (33; 33') and the outlet openings (228 ') of the Abiaufbohrungen (338) when applied to the control valve seat (33; 28 ') closes, characterized in that the sealing element (40) the outlet openings (228') of the several Ab- running bores (28 ') in each case along a boundary length (U,) against the low-pressure space (29) and encloses each boundary length (U,) each have a cross-sectional area (A), wherein the quotient of the square of the sum of the individual boundary lengths (U, 2 ) and the sum of the individual cross-sectional areas (A) is greater than 4 · π.
Kraftstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass der Steuerventilsitz (33) flach ausgebildet ist. Fuel injection valve according to claim 1 or 2, characterized in that the control valve seat (33) is formed flat.
Kraftstoffeinspritzventil nach Anspruch 3, dadurch gekennzeichnet, dass das Dichtelement (40) eine flache Dichtfläche (41) aufweist, mit der es mit dem Steuerventilsitz (33) zusammenwirkt. Fuel injection valve according to claim 3, characterized in that the sealing element (40) has a flat sealing surface (41), with which it cooperates with the control valve seat (33).
Kraftstoffeinspritzventil nach Anspruch 2, dadurch gekennzeichnet, dass die Austrittsöffnungen (228') der Abiaufbohrungen (28') im Steuerventilsitz (33) kreisförmig angeordnet sind. Fuel injection valve according to claim 2, characterized in that the outlet openings (228 ') of the Abiaufbohrungen (28') in the control valve seat (33) are arranged in a circle.
Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Abiaufbohrung (28) eine rechteckförmige Austrittsöffnung (228) aufweist. Fuel injection valve according to claim 1, characterized in that the Abiaufbohrung (28) has a rectangular outlet opening (228).
Kraftstoffeinspritzventil nach Anspruch 1, dadurch gekennzeichnet, dass die Abiaufbohrung (28) eine ovale Austrittsöffnung (228) aufweist. Fuel injection valve according to claim 1, characterized in that the Abiaufbohrung (28) has an oval outlet opening (228).
Kraftstoffeinspritzventil nach Anspruch 1 oder 2, dadurch gekennzeichnet, dass die Abiaufbohrung (28) oder die Abiaufbohrungen (28') so ausgebildet sind, dass sie eine Drosselfunktion aufweisen, die für den Betrieb des jeweilige Kraftstoffeinspritzventils notwendig sind. Fuel injection valve according to claim 1 or 2, characterized in that the Abiaufbohrung (28) or the Abiaufbohrungen (28 ') are formed so that they have a throttle function, which are necessary for the operation of the respective fuel injection valve.
EP13779192.7A 2012-12-14 2013-10-15 Fuel injection valve Active EP2932087B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201210223259 DE102012223259A1 (en) 2012-12-14 2012-12-14 Fuel injection valve
PCT/EP2013/071492 WO2014090444A1 (en) 2012-12-14 2013-10-15 Fuel injection valve

Publications (2)

Publication Number Publication Date
EP2932087A1 true EP2932087A1 (en) 2015-10-21
EP2932087B1 EP2932087B1 (en) 2017-03-01

Family

ID=49385247

Family Applications (1)

Application Number Title Priority Date Filing Date
EP13779192.7A Active EP2932087B1 (en) 2012-12-14 2013-10-15 Fuel injection valve

Country Status (3)

Country Link
EP (1) EP2932087B1 (en)
DE (1) DE102012223259A1 (en)
WO (1) WO2014090444A1 (en)

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP6677194B2 (en) * 2017-03-03 2020-04-08 株式会社デンソー Fuel injection valve

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19827267A1 (en) 1998-06-18 1999-12-23 Bosch Gmbh Robert Fuel injection valve for high pressure injection with improved control of the fuel supply
DE102007034318A1 (en) * 2007-07-24 2009-01-29 Robert Bosch Gmbh injector
DE102007038138A1 (en) * 2007-08-13 2009-02-19 Robert Bosch Gmbh Control valve for a fuel injector

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO2014090444A1 *

Also Published As

Publication number Publication date
WO2014090444A1 (en) 2014-06-19
EP2932087B1 (en) 2017-03-01
DE102012223259A1 (en) 2014-06-18

Similar Documents

Publication Publication Date Title
EP1991773B1 (en) Fuel injection valve for internal combustion engines
WO1999015783A1 (en) Fuel injection device for internal combustion engines
DE102005057526A1 (en) Control valve for fuel injection valve of internal combustion engine, has valve materials which selectively connect either of two ports to control channel
EP2867517B1 (en) Fuel injection valve for internal combustion engines
EP2102486B1 (en) Injector with an axial pressure-compensating control valve
DE112012004633T5 (en) Fuel injection device with a needle control system with F, A, Z and E orifices
DE112006002281T5 (en) Injection device for a single fluid with rate forming capability
DE60125304T2 (en) ADJUSTABLE LIFTING DEVICE FOR A FUEL INJECTION VALVE
EP1944500A2 (en) Fuel injector
WO2007003458A1 (en) Fuel injection valves in combustion engines
DE102006026400A1 (en) Fuel injector with servo assistance
EP2743493B1 (en) Fuel injector
WO2008049671A1 (en) Fuel injector
DE102005010453A1 (en) Fuel injection valve for internal combustion engines
EP1939441A2 (en) Fuel injector
EP3055551B1 (en) Control valve
EP2932087B1 (en) Fuel injection valve
EP3380715A1 (en) Fuel injector
EP2798192B1 (en) Fuel injector for combustion engine
WO2008061842A1 (en) Fuel injector
EP1328726B1 (en) Fuel injection system for internal combustion engines
WO2009138279A1 (en) Solenoid valve having an armature slot configuration
DE10132248A1 (en) Fuel injector with 2-way valve control
WO2017202540A1 (en) Control valve for a fuel injection valve
WO2009146974A1 (en) Fuel injector with perforated seat nozzle

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: 20150714

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM TR

AX Request for extension of the european patent

Extension state: BA ME

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

Effective date: 20160607

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

INTG Intention to grant announced

Effective date: 20161117

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): AL AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HR HU IE IS IT LI LT LU LV MC MK MT NL NO PL PT RO RS SE SI SK SM 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

Ref country code: AT

Ref legal event code: REF

Ref document number: 871685

Country of ref document: AT

Kind code of ref document: T

Effective date: 20170315

REG Reference to a national code

Ref country code: IE

Ref legal event code: FG4D

Free format text: LANGUAGE OF EP DOCUMENT: GERMAN

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502013006547

Country of ref document: DE

REG Reference to a national code

Ref country code: NL

Ref legal event code: MP

Effective date: 20170301

REG Reference to a national code

Ref country code: LT

Ref legal event code: MG4D

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

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: 20170602

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: 20170301

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: 20170301

Ref country code: NO

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: 20170601

Ref country code: HR

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: 20170301

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

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: 20170601

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: 20170301

Ref country code: RS

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: 20170301

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: 20170301

Ref country code: LV

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: 20170301

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

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: 20170301

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 5

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: 20170301

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: 20170301

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: 20170301

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: 20170301

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: 20170703

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: 20170301

Ref country code: SM

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: 20170301

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: 20170701

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502013006547

Country of ref document: DE

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: 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: 20170301

26N No opposition filed

Effective date: 20171204

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

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: 20170301

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 FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT

Effective date: 20170301

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: 20171015

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

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

Ref country code: CH

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

Effective date: 20171031

Ref country code: LU

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

Effective date: 20171015

Ref country code: LI

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

Effective date: 20171031

Ref country code: GB

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

Effective date: 20171015

REG Reference to a national code

Ref country code: BE

Ref legal event code: MM

Effective date: 20171031

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: 20171031

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

Ref country code: MT

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: 20170301

REG Reference to a national code

Ref country code: FR

Ref legal event code: PLFP

Year of fee payment: 6

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

Ref country code: IE

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

Effective date: 20171015

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; INVALID AB INITIO

Effective date: 20131015

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

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: 20170301

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

Ref country code: MK

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: 20170301

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 871685

Country of ref document: AT

Kind code of ref document: T

Effective date: 20181015

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: 20181015

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: 20170301

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

Ref country code: AL

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: 20170301

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

Ref country code: DE

Payment date: 20211214

Year of fee payment: 9

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

Ref country code: FR

Payment date: 20221020

Year of fee payment: 10

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

Ref country code: IT

Payment date: 20221031

Year of fee payment: 10

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502013006547

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: 20230503