EP1983186B1 - Pressure-stabilised actuator - Google Patents

Pressure-stabilised actuator Download PDF

Info

Publication number
EP1983186B1
EP1983186B1 EP08103368A EP08103368A EP1983186B1 EP 1983186 B1 EP1983186 B1 EP 1983186B1 EP 08103368 A EP08103368 A EP 08103368A EP 08103368 A EP08103368 A EP 08103368A EP 1983186 B1 EP1983186 B1 EP 1983186B1
Authority
EP
European Patent Office
Prior art keywords
pressure
valve
fuel
fuel injector
valve body
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
EP08103368A
Other languages
German (de)
French (fr)
Other versions
EP1983186A2 (en
EP1983186A3 (en
Inventor
Michael Kurz
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 EP1983186A2 publication Critical patent/EP1983186A2/en
Publication of EP1983186A3 publication Critical patent/EP1983186A3/en
Application granted granted Critical
Publication of EP1983186B1 publication Critical patent/EP1983186B1/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
    • F02M63/00—Other fuel-injection apparatus having pertinent characteristics not provided for in groups F02M39/00 - F02M57/00 or F02M67/00; Details, component parts, or accessories of fuel-injection apparatus, not provided for in, or of interest apart from, the apparatus of groups F02M39/00 - F02M61/00 or F02M67/00; Combination of fuel pump with other devices, e.g. lubricating oil pump
    • F02M63/0012—Valves
    • F02M63/0014—Valves characterised by the valve actuating means
    • F02M63/0015—Valves characterised by the valve actuating means electrical, e.g. using solenoid
    • F02M63/0026—Valves characterised by the valve actuating means electrical, e.g. using solenoid using piezoelectric or magnetostrictive actuators
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • 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
    • F02M63/0031—Valves characterized by the type of valves, e.g. special valve member details, valve seat details, valve housing details
    • F02M63/0043—Two-way valves
    • 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
    • F02M63/0057—Means for avoiding fuel contact with valve actuator, e.g. isolating actuators by using bellows or diaphragms

Definitions

  • Pressure-controlled fuel injectors with pressure booster, hydraulic nozzle opening pressure and control via only one control valve are for example out DE 102 18 904 A1 known.
  • the fuel injection device disclosed therein comprises a fuel injector, which can be supplied by a high-pressure fuel source, with a pressure booster device.
  • a closing piston of the Krartstoffinjektors in a closing pressure chamber, so that a closing piston with fuel pressure bcaufauflaglag to achieve a force acting in the closing direction on the closing piston force.
  • the closing pressure chamber and the rear space of the Druckschreib GmbHscinraum are formed by a common closing pressure-back space, wherein all portions of the closing pressure-Rückraumcs are permanently connected to each other for the exchange of fuel.
  • the effective area, on which a damper chamber pressure acts is the same size as the area on which the injection pressure acts. Due to this circumstance, the injection valve member only begins the closing process as soon as a pressure p TR in a nozzle chamber becomes smaller than a pressure p ST in a control chamber.
  • the injection valve member since the injection valve member requires a certain time t S until it has returned to its seat in the injector of the fuel injector and closes the arranged below the seat injection ports, injects the Kraflstoffinjektor in the final stages of the injection process with an injection pressure below that in the high-pressure accumulator prevailing pressure. Due to this, the injection rate of such a Krattstotffinjektors by a plateau, ie a dent, characterized. However, due to the decreasing in the final phase of the injection Eiuspritr horres the emission composition of such operated internal combustion engine changed to the negative, ie in the exhaust gas are too many pollutants.
  • a control valve for a fuel injector in which a movable control valve member is moved by the hydraulic pressure in two control chambers, thereby opening and closing a pressure relief line.
  • piezo actuators for driving mechanical or hydraulic control members or valves.
  • to drive and actuate injectors in fuel injectors in direct-injection internal combustion engines find piezo actuators increasingly use.
  • Direct-acting systems appear particularly advantageous since they react very quickly and allow multiple injections of fuel in short time intervals during a combustion cycle. Multiple injections prove to be very advantageous in terms of noise comfort and exhaust gas quality.
  • the medium to be injected i.e., the one to be injected, surrounds. as a rule, the fuel, the injector actuated actuator.
  • the term "wet" actuator is used.
  • the inserted piezoelectric actuator module is to be isolated from the medium to be injected.
  • this isolation of the actuator module against the medium to be injected takes place by a coating applied to the actuator coating in the form of a shrink tube or by elaborately applied coatings.
  • An insulation applied in this way to a piezoactuator proves to be problematic, in particular at high system pressures, which may be more than 1600 bar, on the one hand with regard to the costs and on the other hand with regard to the achievable durability.
  • the need to improve the exhaust gas quality direct injection internal combustion engines by further increasing the injection pressures exacerbated this problem.
  • inventively proposed fuel injector allows a realization of short consecutive multiple injections and a very good reproducibility in terms of the amount of fuel introduced, i. a particularly good stroke / stroke stability.
  • a fast-switching, tolerance-insensitive switching valve is installed, which switches easily even at higher system pressures, which are generated in the high-pressure accumulator body by means of a high pressure unit.
  • the switching valve is preferably formed pressure-balanced, so that lower switching forces are necessary. This in turn favors the pressurization of the inventively proposed fuel injector with higher system pressures, i. higher pressures generated in the high pressure accumulator. Due to the decoupling of the actuator, which is z. B.
  • the integration of the actuator module in the fuel injector is much easier and thus cheaper, since the actuator of the proposed solution according to the invention is now no longer shield against the fuel.
  • the significantly reduced number of components leads to a fuel injector, which can be produced cost-effectively in mass production, and which can be used in particular on high-pressure accumulator injection systems (common rail).
  • the actuator preferably designed as a piezoelectric actuator is housed in a fuel-free, in particular in a diesel fuel-free space in the holding body, which is separated by a trained example as O-ring seal and the other by a spring element from the low pressure path of the fuel injector is, so that the actuator module is not acted upon by the still under a residual pressure level fuel, in particular diesel fuel.
  • the pressure balanced trained switching valve comprises a guide pin, a valve pin and a compression spring which presses the valve pin in a rest position against a sealing seat.
  • a pressure prevailing in a control room pressure so that the guide pin is always pressed against a shim. Due to the relatively large pressure difference between the high pressure region and the low pressure region of the fuel injector, there is a continuous leakage through the radial guide between the guide pin, which is slidably received in the valve pin. This leakage is passed through the radial guide between the valve pin and valve bore via at least one transverse bore in a low pressure chamber and from there into a low pressure region of the fuel injector.
  • FIG. 1 shows an embodiment of the inventively proposed fuel injector comprising a holding body, a throttle plate, a nozzle module, which are joined together via a nozzle lock nut to a screw connection.
  • a fuel injector 10 designed according to the invention comprises a nozzle module 12, a throttle plate 14 and a holding body 18, which are joined together via a nozzle lock nut 16 and form a screw connection.
  • the introduced into the fuel injector 10 axial force with which the nozzle module 12, the throttle plate 14 and the holding body 18 are clamped together, is dependent from the tightening torque, which is applied to the nozzle lock nut 16 during assembly.
  • an actuator module 20 In the holding body 18 of the fuel injector 10 is an actuator module 20.
  • the actuator module 20 By means of the actuator module 20, a hydraulic 2/2-way switching valve 22 is driven.
  • the actuator module 20 is arranged in a fuel-free space 24 in the holding body 18.
  • the fuel-free space 24 is separated from the low-pressure path of the fuel injector 10 by a seal 26, which is formed in a simple and effective manner as an O-ring, and by a spring element 28.
  • the spring element 28 is on the one hand at an upper collar 32 with a coupler head 34 materially connected, so for example glued or welded, and holds the actuator of the actuator module 20 in each of its operating states under a defined bias.
  • the spring element 28 is formed on the lower collar 36 such that a radial clearance between the coupler head 34 and the spring element 28 allows a short-term pressure build-up within a coupler space 38.
  • the adjustment of the spring force generated by the spring element 28 takes place through the adjusting washer 40, which is inserted in the lower region of the holding body 18 above an upper plan side of the throttle plate 14.
  • the seal 26 is preferably formed as an O-ring.
  • Figure 1.1 shows an enlarged view of the low pressure side.
  • throttle check valve 100 In the low-pressure line, via which leakage from the leakage bore 64 is diverted into the low-pressure region of the fuel injector 10, a throttle check valve 100 is inserted to increase the low-pressure-side residual pressure.
  • throttle check valve 100 may be formed directly in the line a throttle point.
  • the 2/2-way valve 22 has a valve pin or valve piston 44 which has a through hole, in particular a through hole, in which a guide pin 42 is located.
  • the valve pin or valve piston 44 of the 2/2-way switching valve 22 is acted upon by a compression spring 46, which - as in FIG. 1 shown - on the underside of the inserted into the holding body 18 shim 40 is supported.
  • a compression spring 46 which - as in FIG. 1 shown - on the underside of the inserted into the holding body 18 shim 40 is supported.
  • the guide pin 42 is acted upon in a control chamber 86 prevailing system pressure.
  • the guide pin 42 is pressed with its opposite end face against the lower end face of the dial 40.
  • a nozzle chamber 68 is formed in the nozzle module 12 of the screw assembly of the fuel injector 10.
  • the nozzle chamber 68 is separated from the control chamber 86 by a control chamber sleeve 85.
  • the control chamber sleeve 85 is acted upon by a compression spring, which is supported on a collar of a preferably needle-shaped injection valve member 92.
  • the nozzle space 68 is supplied with fuel under respective system pressure via a high pressure pump 7 or other high pressure source such as a high pressure common rail of a fuel injection system.
  • the fuel under system pressure flows via supply holes 70 through the holding body 18 and the throttle plate 14 to the nozzle chamber 68.
  • the control chamber 86 is acted upon by a branch from the supply bore 70, in which an inlet throttle 96 is formed, with fuel under system pressure.
  • the pressure relief of the control chamber 86 by means of the pressure compensated trained 2/2-way switching valve 22 and a pressure-relieving the control chamber 86, the guide pin 42 in the valve pin or valve piston 44 flush mounted outlet throttle 88.
  • Reference numeral 90 denotes the diameter of the preferably needle-shaped Injector valve member 92 in the region of its seat above the at least one injection port 94 in the nozzle module 12 has.
  • the actuator module 20 accommodates an actuator 74 constructed in a layered fashion from a piezocrystal stack, which can be energized via an electrical contact 56.
  • Reference numeral 80 denotes an actuator foot
  • reference numeral 84 denotes a valve seat as shown in FIG FIG. 2 , on which a convex underside of the valve pin or valve piston 44 of the pressure-compensated 2/2-way switching valve 22 is seated.
  • the in FIG. 2 shown area provides an enlarged view of the in FIG. 1 already shown 2/2-way switching valve 22 is.
  • p K denotes the pressure in the coupler space 38
  • p N denotes a pressure which prevails in the low-pressure region of the fuel injector 10.
  • the actuator 74 is controlled via the electrical contact 76, which is guided via a low-pressure tight seal 78 on the actuator base 80 from the fuel injector 10, inversely.
  • the inverse activation of the actuator 74 means that in the rest position of the actuator 74 a positive voltage is applied thereto.
  • the actuator 74 thus has in its rest position its maximum length in the axial direction, ie in the direction of the center line of the piezocrystal stack - as in FIG. 1 indicated.
  • the piezoelectric actuator 74 If the piezoelectric actuator 74 is discharged, its length is shortened. Due to this, the coupler head 34 moves vertically upward. Due to the tight toleranced clearance between the coupler head 34 and the spring element 28 in the region of the lower collar 36, the pressure p K builds up within the coupler space 38. Via the connecting bore 82, the pressure also builds up in the valve chamber 54. Since the valve seat 84 on the valve piston 44 has the seat diameter d S , in the opening direction a hydraulic force F ⁇ ff acts on the surface ⁇ / 4 ⁇ (d v 2 -d S 2 ). The pressure in the return system is higher than 1 bar, due to a throttle arranged there 100 or a throttle check valve 100, see Figure 1.1 ,
  • the valve pin or the valve piston 44 moves only from its seating 48 when a force acting in the closing direction force F closing ⁇ F Publ is where F is closed from the spring force F F and the hydraulic force F Hyd that also at the area ⁇ / 4 ⁇ (d V 2 - d S 2 ) acts, is formed.
  • the valve pin or the valve piston 44 moves to the stop, which is formed by the lower edge of the dial 40. Since the low-pressure path is now released, the pressure in the control chamber 86 above the preferably needle-shaped injection valve member 92 builds up via the outlet throttle 88.
  • the preferably needle-shaped injection valve member 92 moves from its seat and allows injection of system under pressure fuel through the at least one arranged at the combustion chamber end of the nozzle module 12 injection port 94.
  • the opening speed or the closing speed of the needle-shaped injection valve member can be specified.
  • the piezoelectric actuator 74 of the actuator module 20 is again charged to its base voltage, so that, in contrast to the opening phase of the preferably needle-shaped injection valve member 92, the longest extent of the piezocrystal stack of the actuator 74 is set in the closing phase. Due to the elongation of the piezocrystal stack of the piezoelectric actuator 74 when subjected to its base voltage, the fuel volume contained in the coupler space 38 is compressed, so that the pressure p K in the coupler space increases.
  • the valve pin or the valve piston 44 again moves into the sealing seat 48 and decouples the connection between the control chamber 86 and the low-pressure-side region of the fuel injector 10
  • the pressure in the control chamber 86 is equalized by the inflow via the inlet throttle 96 back to the system pressure, which prevails in the high-pressure accumulator or is generated by a high pressure pumping unit.
  • the embodiment of the inventively proposed fuel injector 10 a filling of the fuel-free space 24 with an electrically insulating fluid is conceivable.
  • the electrically insulating fluid causes the temperature at the actuator 74, which arises during operation of the actuator 74, to be dissipated more rapidly than air due to the higher temperature conductivity of liquids.
  • FIG. 3 shows an alternative embodiment of the fuel injector 10, in which an additional sleeve 98 is pressed into the inner diameter of the spring element 28.
  • this embodiment can then be resorted to, if the radial guide between the coupler head 34 and the spring element 28 on the lower collar 36 for manufacturing reasons is not feasible.
  • throttle check valve in the low pressure region of the pressure is increased.
  • throttle check valve 100 in the low pressure line can be 100 in the low pressure line and the in Figure 1.1 shown throttle check valve 100 can be used, through which the low-pressure side pressure level is raised. The higher the low pressure level can be maintained, the easier it is to implement the function of the switching valve due to the small actuator stroke.

Landscapes

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

Abstract

The injector (10) has a nozzle module (12), a throttle plate (14), and a holding body (18). An actuator module such as piezo actuator, is accommodated in a fuel free space within the holding body. A control valve is pressure compensated, and includes a valve body, which contains a passage opening into which a guide pin is guided. The guide pin is supplied within a high pressure area with fuel, which stays under system pressure.

Description

Stand der TechnikState of the art

Druckgesteuerte Kraftstoffinjektoren mit Druckverstärker, hydraulischem Düsenöffnungsdruck und einer Steuerung über nur ein Steuerventil sind zum Beispiel aus DE 102 18 904 A1 bekannt. Die dort offenbarte Kraftstoffeinspritzeinrichtung umfasst einen von einer Kraftstoffhochdruckquelle versorgbaren Kraftstoffinjektor mit einer Druckübersetzungseinrichtung. Bei dieser ragt ein Schließkolben des Krartstoffinjektors in einen Schließdruckraum hinein, so dass ein Schließkolben mit Kraftstoffdruck bcaufischlagbar ist zur Erzielung einer in Schließrichtung auf den Schließkolben wirkenden Kraft. Der Schließdruckraum und der Rückraum der Druckübersetzungscinrichtung werden durch einen gemeinsamen Schließdruck-Rückraum gebildet, wobei sämtliche Teilbereiche des Schließdruck-Rückraumcs permanent zum Austausch von Kraftstoff miteinander verbunden sind. Damit lässt sich trotz einer relativ niedrigenDruckvcrstärkung durch die Druckübersetzungseinrichtung ein relativ niedriger Einspritzöffnungsdruck erreichen. Im geöffneten Zustand eines bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes ist die wirksame Fläche, auf die ein Dämpferraumdruck wirkt, genauso groß wie die Fläche, auf die der Einspritzdruck wirkt. Aufgrund dieses Umstandes beginnt das Einspritzventilglied erst dann mit dem Schließvorgang, sobald ein Druck pTR in einem Düsenraum kleiner als ein Druck pST in einem Steuerraum wird. Da das Einspritzventilglied jedoch eine bestimmte Zeit tS benötigt, bis es wieder in seinen Sitz im Injektorkörper des Kraftstoffinjektors angelangt ist und die unterhalb des Sitzes angeordneten Einspritzöffnungen verschließt, spritzt der Kraflstoffinjektor in der Schlussphase des Einspritzvorganges mit einem Einspritzdruck ein, der unterhalb des im Hochdruckspeicher herrschenden Druckes liegt. Aufgrunddessen ist die Einspritzrate eines derartigen Krattstotffinjektors durch ein Plateau, d.h. eine Eindellung, gekennzeichnet. Aufgrund des in der Schlussphase der Einspritzung abnehmenden Eiuspritrdruckes verändert sich jedoch die Emissionszusammensetzung einer derart betriebenen Verbrennungskraftmaschine zum Negativen, d.h. im Abgas sind zu viele Schadstoffe enthalten.Pressure-controlled fuel injectors with pressure booster, hydraulic nozzle opening pressure and control via only one control valve are for example out DE 102 18 904 A1 known. The fuel injection device disclosed therein comprises a fuel injector, which can be supplied by a high-pressure fuel source, with a pressure booster device. In this projecting a closing piston of the Krartstoffinjektors in a closing pressure chamber, so that a closing piston with fuel pressure bcaufauflaglag to achieve a force acting in the closing direction on the closing piston force. The closing pressure chamber and the rear space of the Druckübersetzungscinrichtung are formed by a common closing pressure-back space, wherein all portions of the closing pressure-Rückraumcs are permanently connected to each other for the exchange of fuel. Thus, despite a relatively low pressure increase by the pressure booster, a relatively low injection opening pressure can be achieved. In the open state of a preferably needle-shaped injection valve member, the effective area, on which a damper chamber pressure acts, is the same size as the area on which the injection pressure acts. Due to this circumstance, the injection valve member only begins the closing process as soon as a pressure p TR in a nozzle chamber becomes smaller than a pressure p ST in a control chamber. However, since the injection valve member requires a certain time t S until it has returned to its seat in the injector of the fuel injector and closes the arranged below the seat injection ports, injects the Kraflstoffinjektor in the final stages of the injection process with an injection pressure below that in the high-pressure accumulator prevailing pressure. Due to this, the injection rate of such a Krattstotffinjektors by a plateau, ie a dent, characterized. However, due to the decreasing in the final phase of the injection Eiuspritrdruckes the emission composition of such operated internal combustion engine changed to the negative, ie in the exhaust gas are too many pollutants.

Aus der WO 02/084106 Al ist darüber hinaus ein Steuerventil für einen Kraftstoffinjektor bekannt, bei dem ein bewegliches Steuerventilglied durch den hydraulisches Druck in zwei Steuerkammern bewegt wird und dadurch eine Druckentlastungsleitung öffnet und schließt.From the WO 02/084106 Al In addition, a control valve for a fuel injector is known in which a movable control valve member is moved by the hydraulic pressure in two control chambers, thereby opening and closing a pressure relief line.

Es ist bekannt, Piezoaktoren zum Antrieb mechanischer oder hydraulischer Steuerglieder oder Ventile einzusetzen. Insbesondere zum Antrieb und zur Betätigung von Einspritzventilen in Kraftstoffeinspritzeinrichtungen bei direkt einspritzenden Verbrennungskraftmaschinen finden Piezoaktoren zunehmend Verwendung. Besonders vorteilhaft erscheinen direktgesteuerte Systeme, da diese sehr schnell reagieren und das mehrfache Einspritzen von Kraftstoff in kurzen zeitlichen Abständen während eines Verbrennungstaktes erlauben. Mehrfacheinspritzungen erweisen sich in Bezug auf Geräuschkomfort und Abgasqualität als sehr vorteilhaft. Bei direktgesteuerten Kraftstoffeinspritzventilen umgibt das einzuspritzende Medium, d.h. im Regelfall der Kraftstoff, den das Einspritzventil betätigenden Aktor. In diesem Zusammenhang wird auch von einem "nassen" Aktor gesprochen.It is known to use piezo actuators for driving mechanical or hydraulic control members or valves. In particular, to drive and actuate injectors in fuel injectors in direct-injection internal combustion engines find piezo actuators increasingly use. Direct-acting systems appear particularly advantageous since they react very quickly and allow multiple injections of fuel in short time intervals during a combustion cycle. Multiple injections prove to be very advantageous in terms of noise comfort and exhaust gas quality. In direct injection fuel injection valves, the medium to be injected, i.e., the one to be injected, surrounds. as a rule, the fuel, the injector actuated actuator. In this context, the term "wet" actuator is used.

Da einzuspritzende Medien, wie zum Beispiel Dieselkraftstoff, teilweise elektrisch leitend sind und korrosive Eigenschaften haben können, ist das eingesetzte Piezoaktormodul gegenüber dem einzuspritzende Medium zu isolieren. Im Stand der Technik erfolgt diese Isolation des Aktormoduls gegen das einzuspritzende Medium durch einen auf den Aktor auf gebrachten Überzug in Gestalt eines Schrumpfschlauches oder durch aufwändig aufgebrachte Beschichtungen. Eine dergestalt auf einem Piezoaktor aufgebrachte Isolierung erweist sich insbesondere bei hohen Systemdrücken, die mehr als 1600 bar betragen können, als problematisch, einerseits bezüglich der Kosten und andererseits bezüglich der erzielbaren Dauerhaltbarkeit. Die Notwendigkeit zur Verbesserung der Abgasqualität direkt einspritzender Verbrennungskraftmaschinen durch eine weitere Anhebung der Einspritzdrücke verschärft diese Problematik zusätzlich.Since injected media, such as diesel fuel, are partially electrically conductive and may have corrosive properties, the inserted piezoelectric actuator module is to be isolated from the medium to be injected. In the prior art, this isolation of the actuator module against the medium to be injected takes place by a coating applied to the actuator coating in the form of a shrink tube or by elaborately applied coatings. An insulation applied in this way to a piezoactuator proves to be problematic, in particular at high system pressures, which may be more than 1600 bar, on the one hand with regard to the costs and on the other hand with regard to the achievable durability. The need to improve the exhaust gas quality direct injection internal combustion engines by further increasing the injection pressures exacerbated this problem.

Ein weiteres Problemfeld in Bezug auf die in Rede stehenden Kraftstoffinjektoren stellen hydraulische Druckschwingungen dar, die im einzuspritzenden Medium, in der Regel Kraftstoff, durch schnelles Öffnen und schnelles Schließen des Einspritzventilgliedes hervorgerufen werden. Damit diese auftretenden Druckschwingungen die einzuspritzende Kraftstoffmenge nicht unkontrolliert beeinflussen, was zur unerwünschten Abweichungen im Verbrennungsablauf und hinsichtlich der erzielbaren Abgasqualität führen kann, sind diese Druckschwingungen durch ausreichend große Flüssigkeitsvolumina innerhalb des Kraftstof finjektors zu bedämpfen.Another problem area with respect to the fuel injectors in question are hydraulic pressure oscillations which are caused in the medium to be injected, generally fuel, by rapid opening and closing of the injection valve member. In order for these occurring pressure oscillations not uncontrollably affect the fuel quantity to be injected, which can lead to undesirable deviations in the combustion process and in terms of the achievable exhaust quality, these pressure oscillations are damped by sufficiently large volumes of liquid within the fuel finjektors.

Bei zukünftig zu erwartenden Neuentwicklungen von Kraftstoffinjektoren für Hochdruckeinspritzsysteme wird der Schwerpunkt auf Robustheit und kostengünstiger Herstellbarkeit liegen. Des Weiteren haben künftige Injektorgenerationen die neuen nochmals verschärften Abgasnormen, so zum Beispiel die Norm EU5 und weitere zu erwartende Normen, zu erfüllen. Die Abgaswerte werden bei heutigen und zukünftigen Systemauslegungen mehrheitlich über eine Druckerhöhung, so zum Beispiel über eine Systemdruckerhöhung im Hochdruckspeicherraum (Common-Rail) sowie über intelligente Ansteuerstrategien, welche eine sehr eng gelagerte Mehrfacheinspritzung voraussetzen, zu reduzieren sein. Die heute eingesetzten, insbesondere bei Hochdruckspeichereinspritzsystemen (Common-Rail) eingesetzten Kraftstoffinjektoren sind hinsichtlich ihres Aufbaus sehr teuer, da sie eine Vielzahl von hochgenau zu bearbeitenden Komponenten aufweisen und für zukünftig zu erwartende Ansteuerstrategien nur bedingt tauglich sind.Future developments of fuel injectors for high-pressure injection systems will focus on robustness and cost-effective manufacturability. In addition, future generations of injectors will have to meet the new, even more stringent emissions standards, such as the EU5 standard and other standards to be expected. The exhaust gas values are in majority of today's and future system designs on a pressure increase, such as a system pressure increase in the high-pressure reservoir (Common Rail) as well as intelligent driving strategies, which require a very tight multi-injection, to be reduced. The fuel injectors used today, especially in high-pressure accumulator injection systems (common rail) used fuel injectors are very expensive in terms of their structure, since they have a variety of highly accurate components to be processed and are suitable only partially suitable for future expected driving strategies.

Offenbarung der ErfindungDisclosure of the invention

Der erfindungsgemäß vorgeschlagene Kraftstoffinjektor erlaubt eine Realisierung von kurz aufeinanderfolgenden Mehrfacheinspritzungen und eine sehr gute Reproduzierbarkeit hinsichtlich der eingebrachten Kraftstoffmenge, d.h. eine besonders gute Hub/Hub-Stabilität. Im erfindungsgemäß vorgeschlagenen Kraftstoffinjektor ist ein schnellschaltendes, toleranzunempfindliches Schaltventil eingebaut, welches auch bei höheren Systemdrücken, die im Hochdruckspeicherkörper mittels eines Hochdruckaggregates erzeugt werden, problemlos schaltet. Das Schaltventil wird bevorzugt druckausgeglichen ausgebildet, so dass geringere Schaltkräfte notwendig sind. Dies wiederum begünstigt die Beaufschlagung des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors mit höheren Systemdrücken, d.h. höheren im Hochdruckspeicher erzeugten Drücken. Durch die Entkopplung des Betätigungsorganes, bei dem es sich z. B. um einen Piezoaktor handelt, vom Kraftstoff, insbesondere vom Dieselkraftstoff, wird die Integration des Aktormoduls in den Kraftstoffinjektor wesentlich einfacher und damit kostengünstiger, da der Aktor der erfindungsgemäß vorgeschlagenen Lösung nunmehr nicht mehr gegen den Kraftstoff abzuschirmen ist. Die erheblich reduzierte Anzahl der Bauteile führt zu einem kostengünstig in Großserienproduktion herstellbaren Kraftstoffinjektor, der insbesondere an Hochdruckspeichereinspritzsystemen (Common-Rail) eingesetzt werden kann.The inventively proposed fuel injector allows a realization of short consecutive multiple injections and a very good reproducibility in terms of the amount of fuel introduced, i. a particularly good stroke / stroke stability. In inventively proposed fuel injector a fast-switching, tolerance-insensitive switching valve is installed, which switches easily even at higher system pressures, which are generated in the high-pressure accumulator body by means of a high pressure unit. The switching valve is preferably formed pressure-balanced, so that lower switching forces are necessary. This in turn favors the pressurization of the inventively proposed fuel injector with higher system pressures, i. higher pressures generated in the high pressure accumulator. Due to the decoupling of the actuator, which is z. B. is a piezoelectric actuator, fuel, in particular diesel fuel, the integration of the actuator module in the fuel injector is much easier and thus cheaper, since the actuator of the proposed solution according to the invention is now no longer shield against the fuel. The significantly reduced number of components leads to a fuel injector, which can be produced cost-effectively in mass production, and which can be used in particular on high-pressure accumulator injection systems (common rail).

Der erfindungsgemäß vorgeschlagenen Lösung folgend, wird das bevorzugt als Piezoaktor ausgebildete Betätigungsorgan in einem kraftstofffreien, insbesondere in einem dieselkraftstofffreien Raum im Haltekörper untergebracht, welcher zum einen durch eine zum Beispiel als O-Ring ausgebildete Abdichtung und zum anderen durch ein Federelement vom Niederdruckpfad des Kraftstoffinjektors getrennt ist, so dass das Aktormodul nicht durch den noch unter einem Restdruckniveau stehenden Kraftstoff, insbesondere Dieselkraftstoff, beaufschlagt ist.Following the solution proposed by the invention, the actuator preferably designed as a piezoelectric actuator is housed in a fuel-free, in particular in a diesel fuel-free space in the holding body, which is separated by a trained example as O-ring seal and the other by a spring element from the low pressure path of the fuel injector is, so that the actuator module is not acted upon by the still under a residual pressure level fuel, in particular diesel fuel.

Das druckausgeglichen ausgebildete Schaltventil umfasst einen Führungsstift, einen Ventilbolzen sowie eine Druckfeder, welche den Ventilbolzen in einer Ruhestellung gegen einen Dichtsitz drückt. An der den Einspritzöffnungen zugewandten Stirnfläche des Führungsstiftes steht ein in einem Steuerraum herrschender Druck an, so dass der Führungsstift stets gegen eine Einstellscheibe gedrückt wird. Bedingt durch den relativ großen Druckunterschied zwischen dem Hochdruckbereich und dem Niederdruckbereich des Kraftstoffinjektors, kommt es zu einer kontinuierlichen Leckage durch die Radialführung zwischen dem Führungsstift, der im Ventilbolzen verschieblich aufgenommen ist. Diese Leckage wird durch die Radialführung zwischen Ventilbolzen und Ventilbohrung über mindestens eine Querbohrung in einen Niederdruckraum und von dort in einen Niederdruckbereich des Kraftstoffinjektors geleitet.The pressure balanced trained switching valve comprises a guide pin, a valve pin and a compression spring which presses the valve pin in a rest position against a sealing seat. At the injection openings facing end face of the guide pin is a pressure prevailing in a control room pressure, so that the guide pin is always pressed against a shim. Due to the relatively large pressure difference between the high pressure region and the low pressure region of the fuel injector, there is a continuous leakage through the radial guide between the guide pin, which is slidably received in the valve pin. This leakage is passed through the radial guide between the valve pin and valve bore via at least one transverse bore in a low pressure chamber and from there into a low pressure region of the fuel injector.

Kurze Beschreibung der ZeichnungenBrief description of the drawings

Anhand der Zeichnung wird die Erfindung nachstehend eingehender beschrieben.With reference to the drawing, the invention will be described below in more detail.

Es zeigt:

Figur 1
einen Schnitt durch den erfindungsgemäß vorgeschlagenen Kraftstoffinjektor, einen Haltekörper einer Drosselplatte sowie ein Düsenmodul umfassend, die zusammen mit einer Düsenspannmutter einen Schraubverbund bilden,
Figur 1.1
ein niederdruckseitiges Drosselrückschlagventil,
Figur 2
eine vergrößerte Darstellung des druckausgeglichen ausgebildeten, als 2/2-Wege-Ventil ausgebildeten Schaltventiles,
Figur 3
eine alternative Ausgestaltung der Ankopplung eines hydraulischen Kopplers.
It shows:
FIG. 1
a section through the inventively proposed fuel injector comprising a holding body of a throttle plate and a nozzle module, which together with a nozzle retaining nut form a Schraubverbund,
Figure 1.1
a low-pressure side throttle check valve,
FIG. 2
an enlarged view of the pressure-compensated designed as a 2/2-way valve switching valve,
FIG. 3
an alternative embodiment of the coupling of a hydraulic coupler.

Ausführungsformenembodiments

Figur 1 zeigt eine Ausführungsform des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors, einen Haltekörper, eine Drosselplatte, ein Düsenmodul umfassend, die miteinander über eine Düsenspannmutter zu einem Schraubverbund gefügt sind. FIG. 1 shows an embodiment of the inventively proposed fuel injector comprising a holding body, a throttle plate, a nozzle module, which are joined together via a nozzle lock nut to a screw connection.

Der Darstellung gemäß Figur 1 ist entnehmbar, dass ein erfindungsgemäß ausgebildeter Kraftstoffinjektor 10 ein Düsenmodul 12, eine Drosselplatte 14 sowie einen Haltekörper 18 umfasst, die über eine Düsenspannmutter 16 miteinander gefügt sind und einen Schraubverbund bilden. Die in den Kraftstoffinjektor 10 eingebrachte Axialkraft, mit der das Düsenmodul 12, die Drosselplatte 14 sowie der Haltekörper 18 miteinander verspannt sind, ist abhängig von dem Anzugsdrehmoment, mit dem die Düsenspannmutter 16 bei der Montage beaufschlagt wird.The representation according to FIG. 1 can be taken that a fuel injector 10 designed according to the invention comprises a nozzle module 12, a throttle plate 14 and a holding body 18, which are joined together via a nozzle lock nut 16 and form a screw connection. The introduced into the fuel injector 10 axial force with which the nozzle module 12, the throttle plate 14 and the holding body 18 are clamped together, is dependent from the tightening torque, which is applied to the nozzle lock nut 16 during assembly.

Im Haltekörper 18 des Kraftstoffinjektors 10 befindet sich ein Aktormodul 20. Mittels des Aktormoduls 20 wird ein hydraulisches 2/2-Wege-Schaltventil 22 angesteuert. Der erfindungsgemäß vorgeschlagenen Lösung folgend, ist das Aktormodul 20 in einem kraftstoff freien Raum 24 im Haltekörper 18 angeordnet. Der kraftstofffreie Raum 24 ist durch eine Abdichtung 26, die in einfacher und wirksamer Weise als O-Ring ausgebildet ist, und zum anderen durch ein Federelement 28 vom Niederdruckpfad des Kraftstoffinjektors 10 getrennt. Das Federelement 28 ist einerseits an einem oberen Bund 32 mit einem Kopplerkopf 34 stoffschlüssig verbunden, so zum Beispiel verklebt oder verschweißt, und hält den Aktor des Aktormoduls 20 in jedem seiner Betriebszustände unter einer definierten Vorspannung. Des Weiteren ist das Federelement 28 am unteren Bund 36 derart ausgebildet, dass ein Radialspiel zwischen dem Kopplerkopf 34 und dem Federelement 28 einen kurzzeitigen Druckaufbau innerhalb eines Kopplerraumes 38 zulässt. Die Einstellung der durch das Federelement 28 erzeugten Federkraft erfolgt durch die Einstellscheibe 40, die im unteren Bereich des Haltekörpers 18 oberhalb einer oberen Planseite der Drosselplatte 14 eingelegt ist. Zwischen der Einstellscheibe 40, dem Haltekörper 18 und dem unteren Bund 36 befindet sich die Abdichtung 26, die in bevorzugter Weise als O-Ring ausgebildet ist.In the holding body 18 of the fuel injector 10 is an actuator module 20. By means of the actuator module 20, a hydraulic 2/2-way switching valve 22 is driven. Following the solution proposed according to the invention, the actuator module 20 is arranged in a fuel-free space 24 in the holding body 18. The fuel-free space 24 is separated from the low-pressure path of the fuel injector 10 by a seal 26, which is formed in a simple and effective manner as an O-ring, and by a spring element 28. The spring element 28 is on the one hand at an upper collar 32 with a coupler head 34 materially connected, so for example glued or welded, and holds the actuator of the actuator module 20 in each of its operating states under a defined bias. Furthermore, the spring element 28 is formed on the lower collar 36 such that a radial clearance between the coupler head 34 and the spring element 28 allows a short-term pressure build-up within a coupler space 38. The adjustment of the spring force generated by the spring element 28 takes place through the adjusting washer 40, which is inserted in the lower region of the holding body 18 above an upper plan side of the throttle plate 14. Between the dial 40, the holding body 18 and the lower collar 36 is the seal 26, which is preferably formed as an O-ring.

Unterhalb der Einstellscheibe 40, die unter Zwischenschaltung der Abdichtung 26 in den Haltekörper 18 des Kraftstoffinjektors 10 eingelassen ist, befindet sich das druckausgeglichen ausgebildete 2/2-Wege-Schaltventil 22.Below the shim 40, which is inserted with the interposition of the seal 26 in the holding body 18 of the fuel injector 10, there is the pressure-balanced trained 2/2-way switching valve 22nd

Figur 1.1 zeigt eine vergrößerte Darstellung der Niederdruckseite. Figure 1.1 shows an enlarged view of the low pressure side.

In der Niederdruckleitung, über welche Leckage aus der Leckagebohrung 64 in den Niederdruckbereich des Kraftstoffinjektors 10 abgesteuert wird, ist zur Erhöhung des niederdruckseitigen Restdruckes ein Drosselrückschlagventil 100 eingelassen. Anstelle des in Figur 1.1 in vergrößerter Darstellung wiedergegebenen Drosselrückschlagventiles 100 kann auch in der Leitung unmittelbar eine Drosselstelle ausgebildet sein.In the low-pressure line, via which leakage from the leakage bore 64 is diverted into the low-pressure region of the fuel injector 10, a throttle check valve 100 is inserted to increase the low-pressure-side residual pressure. Instead of in Figure 1.1 represented in an enlarged scale throttle check valve 100 may be formed directly in the line a throttle point.

Der Darstellung gemäß Figur 2 ist entnehmbar, dass das 2/2-Wege-Ventil 22 einen Ventilbolzen oder Ventilkolben 44 aufweist, der eine Durchgangsöffnung, insbesondere eine Durchgangsbohrung, aufweist, in der sich ein Führungsstift 42 befindet. Der Ventilbolzen oder Ventilkolben 44 des 2/2-Wege-Schaltventiles 22 wird über eine Druckfeder 46 beaufschlagt, die sich - wie in Figur 1 dargestellt - an der Unterseite der in den Haltekörper 18 eingelegten Einstellscheibe 40 abstützt. An der dem Düsenmodul 12 zuweisenden Stirnseite ist der Führungsstift 42 mit in einem Steuerraum 86 herrschenden Systemdruck beaufschlagt. Dadurch wird der Führungsstift 42 mit seiner gegenüberliegenden Stirnseite gegen die untere Stirnseite der Einstellscheibe 40 gedrückt. Bedingt durch den großen Druckunterschied zwischen einem Hochdruckbereich 52, d.h. einem Bereich, in dem Systemdruck vom Steuerraum 86 aus anliegend, herrscht, und einem Ventilraum 54 oberhalb des Ventilbolzens oder Ventilkolbens 44, kommt es zu einer kontinuierlichen Leckage entlang einer Radialführung 56, in der der Führungsstift 42 im Ventilbolzen oder Ventilkolben 44 des druckausgeglichen ausgebildeten 2/2-Wege-Ventils 22 geführt ist. Diese kontinuierlich über die Radialführung 56 abströmende Leckagemenge wird wiederum durch die Radialführung zwischen dem Ventilbolzen beziehungsweise Ventilkolben 44 und einer Ventilbohrung 58 über mindestens eine Querbohrung 60, eine Leckagebohrung 64 und einen Niederdruckraum 62 in den Niederdruckbereich 66 des Kraftstoffinjektors abgesteuert.The representation according to FIG. 2 can be removed that the 2/2-way valve 22 has a valve pin or valve piston 44 which has a through hole, in particular a through hole, in which a guide pin 42 is located. The valve pin or valve piston 44 of the 2/2-way switching valve 22 is acted upon by a compression spring 46, which - as in FIG. 1 shown - on the underside of the inserted into the holding body 18 shim 40 is supported. At the nozzle module 12 assigning end face the guide pin 42 is acted upon in a control chamber 86 prevailing system pressure. As a result, the guide pin 42 is pressed with its opposite end face against the lower end face of the dial 40. Due to the large pressure difference between a high-pressure region 52, ie an area in the system pressure from the control chamber 86 fitting out prevails, and a valve chamber 54 above the valve pin or valve piston 44, there is a continuous leakage along a radial guide 56, in which Guide pin 42 in the valve pin or valve piston 44 of the pressure balanced trained 2/2-way valve 22 is guided. This leakage quantity flowing continuously via the radial guide 56 is in turn diverted into the low-pressure region 66 of the fuel injector by the radial guide between the valve pin or valve piston 44 and a valve bore 58 via at least one transverse bore 60, a leakage bore 64 and a low-pressure space 62.

Zurückkommend auf die Darstellung gemäß Figur 1, ist im Düsenmodul 12 des Schraubverbundes des Kraftstoffinjektors 10 ein Düsenraum 68 ausgebildet. Der Düsenraum 68 ist durch eine Steuerraumhülse 85 vom Steuerraum 86 getrennt. Die Steuerraumhülse 85 ist durch eine Druckfeder beaufschlagt, die sich an einem Bund eines bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 92 abstützt. Der Düsenraum 68 wird über eine Hochdruckpumpe 7 oder eine andere Hochdruckquelle, wie zum Beispiel einen Hochdrucksammelraum (Common-Rail) eines Kraftstoffeinspritzsystems mit unter jeweiligem Systemdruck stehenden Kraftstoff versorgt. Der unter Systemdruck stehende Kraftstoff strömt über Versorgungsbohrungen 70 durch den Haltekörper 18 und die Drosselplatte 14 dem Düsenraum 68 zu. Der Steuerraum 86 wird über einen Abzweig von der Versorgungsbohrung 70, in der eine Zulaufdrossel 96 ausgebildet ist, mit unter Systemdruck stehendem Kraftstoff beaufschlagt. Die Druckentlastung des Steuerraumes 86 erfolgt mittels des druckausgeglichen ausgebildeten 2/2-Wege-Schaltventiles 22 und über eine den Steuerraum 86 druckentlastende, zum Führungsstift 42 im Ventilbolzen oder Ventilkolben 44 fluchtend angebrachte Ablaufdrossel 88. Bezugszeichen 90 bezeichnet den Durchmesser, den das bevorzugt nadelförmig ausgebildete Einspritzventilglied 92 im Bereich seines Sitzes oberhalb der mindestens einen Einspritzöffnung 94 im Düsenmodul 12 aufweist. Der Darstellung gemäß Figur 1 kann überdies entnommen werden, dass das Aktormodul 20 einen aus einem Piezokristallstapel geschichtet aufgebauten Aktor 74 aufnimmt, der über eine elektrische Kontaktierung 56 bestrombar ist. Mit Bezugszeichen 80 ist ein Aktorfuß bezeichnet, Bezugszeichen 84 bezeichnet einen Ventilsitz gemäß der Darstellung in Figur 2, auf dem eine auch ballig ausbildbare Unterseite des Ventilbolzens oder Ventilkolbens 44 des druckausgeglichen ausgebildeten 2/2-Wege-Schaltventils 22 aufsitzt. Der in Figur 2 dargestellte Bereich stellt eine vergrößerte Darstellung des in Figur 1 bereits dargestellten 2/2-Wege-Schaltventils 22 dar. Im Zusammenhang mit der Darstellung gemäß Figur 2 ist noch zu erwähnen, dass mit pK der Druck im Kopplerraum 38 bezeichnet ist und pN einen Druck bezeichnet, der im Niederdruckbereich des Kraftstoffinjektors 10 herrscht.Coming back to the presentation according to FIG. 1 , In the nozzle module 12 of the screw assembly of the fuel injector 10, a nozzle chamber 68 is formed. The nozzle chamber 68 is separated from the control chamber 86 by a control chamber sleeve 85. The control chamber sleeve 85 is acted upon by a compression spring, which is supported on a collar of a preferably needle-shaped injection valve member 92. The nozzle space 68 is supplied with fuel under respective system pressure via a high pressure pump 7 or other high pressure source such as a high pressure common rail of a fuel injection system. The fuel under system pressure flows via supply holes 70 through the holding body 18 and the throttle plate 14 to the nozzle chamber 68. The control chamber 86 is acted upon by a branch from the supply bore 70, in which an inlet throttle 96 is formed, with fuel under system pressure. The pressure relief of the control chamber 86 by means of the pressure compensated trained 2/2-way switching valve 22 and a pressure-relieving the control chamber 86, the guide pin 42 in the valve pin or valve piston 44 flush mounted outlet throttle 88. Reference numeral 90 denotes the diameter of the preferably needle-shaped Injector valve member 92 in the region of its seat above the at least one injection port 94 in the nozzle module 12 has. The representation according to FIG. 1 In addition, it can be seen that the actuator module 20 accommodates an actuator 74 constructed in a layered fashion from a piezocrystal stack, which can be energized via an electrical contact 56. Reference numeral 80 denotes an actuator foot, reference numeral 84 denotes a valve seat as shown in FIG FIG. 2 , on which a convex underside of the valve pin or valve piston 44 of the pressure-compensated 2/2-way switching valve 22 is seated. The in FIG. 2 shown area provides an enlarged view of the in FIG. 1 already shown 2/2-way switching valve 22 is. In connection with the presentation according to FIG. 2 It should also be mentioned that p K denotes the pressure in the coupler space 38 and p N denotes a pressure which prevails in the low-pressure region of the fuel injector 10.

Die Funktionsweise des erfindungsgemäß vorgeschlagenen, in den Figuren 1 und 2 dargestellten Kraftstoffinjektors stellt sich folgendermaßen dar:The operation of the invention proposed in the FIGS. 1 and 2 illustrated fuel injector is shown as follows:

Während der Öffnungsphase des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 92 wird der Aktor 74 über die elektrische Kontaktierung 76, die über eine niederdruckfeste Abdichtung 78 am Aktorfuß 80 aus dem Kraftstoffinjektor 10 geführt wird, invers angesteuert. Das inverse Ansteuern des Aktors 74 bedeutet, dass in der Ruhestellung des Aktors 74 eine positive Spannung an diesem anliegt. Der Aktor 74 hat somit in seiner Ruhestellung seine maximale Länge in axiale Richtung, d.h. in Richtung der Mittellinie des Piezokristallstapels - wie in Figur 1 angedeutet.During the opening phase of the preferably needle-shaped injection valve member 92, the actuator 74 is controlled via the electrical contact 76, which is guided via a low-pressure tight seal 78 on the actuator base 80 from the fuel injector 10, inversely. The inverse activation of the actuator 74 means that in the rest position of the actuator 74 a positive voltage is applied thereto. The actuator 74 thus has in its rest position its maximum length in the axial direction, ie in the direction of the center line of the piezocrystal stack - as in FIG. 1 indicated.

Wird der Piezoaktor 74 entladen, verkürzt sich seine Länge. Aufgrunddessen bewegt sich der Kopplerkopf 34 in vertikale Richtung nach oben. Bedingt durch das eng tolerierte Spiel zwischen dem Kopplerkopf 34 und dem Federelement 28 im Bereich des unteren Bundes 36 baut sich der Druck pK innerhalb des Kopplerraumes 38 ab. Über die Verbindungsbohrung 82 baut sich im Ventilraum 54 der Druck ebenfalls ab. Da der Ventilsitz 84 am Ventilkolben 44 den Sitzdurchmesser dS aufweist, wirkt in Öffnungsrichtung eine hydraulische Kraft FÖff an der Fläche π/4 · (dv 2 - dS 2). Der Druck im Rücklaufsystem liegt höher als 1 bar, bedingt durch eine dort angeordnete Drossel 100 oder ein Drosselrückschlagventil 100, vergleiche Figur 1.1.If the piezoelectric actuator 74 is discharged, its length is shortened. Due to this, the coupler head 34 moves vertically upward. Due to the tight toleranced clearance between the coupler head 34 and the spring element 28 in the region of the lower collar 36, the pressure p K builds up within the coupler space 38. Via the connecting bore 82, the pressure also builds up in the valve chamber 54. Since the valve seat 84 on the valve piston 44 has the seat diameter d S , in the opening direction a hydraulic force F Öff acts on the surface π / 4 · (d v 2 -d S 2 ). The pressure in the return system is higher than 1 bar, due to a throttle arranged there 100 or a throttle check valve 100, see Figure 1.1 ,

Der Ventilbolzen beziehungsweise der Ventilkolben 44 verfährt erst aus seinem Dichtsitz 48, wenn eine in Schließrichtung wirkende Kraft FSchließ ≤ FÖff beträgt, wobei FSchließ aus der Federkraft FF und der hydraulischen Kraft FHyd, die ebenfalls an der Fläche π/4 · (dV 2 - dS 2) wirkt, gebildet wird. Der Ventilbolzen beziehungsweise der Ventilkolben 44 verfährt bis zum Anschlag, der durch die Unterkante der Einstellscheibe 40 gebildet wird. Da nun der Niederdruckpfad freigegeben wird, baut sich der Druck im Steuerraum 86 oberhalb des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 92 über die Ablaufdrossel 88 ab. Bedingt durch die Ausbildung einer Druckstufe oberhalb des Nadelsitzdurchmessers 90 bewegt sich das bevorzugt nadelförmig ausgebildete Einspritzventilglied 92 aus seinem Sitz und ermöglicht eine Einspritzung von unter Systemdruck stehendem Kraftstoff über die mindestens eine am brennraumseitigen Ende des Düsenmoduls 12 angeordnete Einspritzöffnung 94. Über die Dimensionierung der Ablaufdrossel 88 sowie die Dimensionierung der Zulaufdrossel 96 kann die Öffnungsgeschwindigkeit beziehungsweise die Schließgeschwindigkeit des nadelförmig ausgebildeten Einspritzventilgliedes vorgegeben werden.The valve pin or the valve piston 44 moves only from its seating 48 when a force acting in the closing direction force F closing ≤ F Publ is where F is closed from the spring force F F and the hydraulic force F Hyd that also at the area π / 4 · (d V 2 - d S 2 ) acts, is formed. The valve pin or the valve piston 44 moves to the stop, which is formed by the lower edge of the dial 40. Since the low-pressure path is now released, the pressure in the control chamber 86 above the preferably needle-shaped injection valve member 92 builds up via the outlet throttle 88. Due to the formation of a pressure level above the needle seat diameter 90, the preferably needle-shaped injection valve member 92 moves from its seat and allows injection of system under pressure fuel through the at least one arranged at the combustion chamber end of the nozzle module 12 injection port 94. About the dimensioning of the outlet throttle 88th as well as the sizing of the Inlet throttle 96, the opening speed or the closing speed of the needle-shaped injection valve member can be specified.

Zur Beendigung der Einspritzung wird der Piezoaktor 74 des Aktormoduls 20 wieder auf seine Basisspannung geladen, so dass sich, im Gegensatz zur Öffnungsphase des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 92, in der Schließphase die längste Ausdehnung des Piezokristallstapels des Aktors 74 einstellt. Aufgrund der Längung des Piezokristallstapels des Piezoaktors 74 bei Beaufschlagung mit seiner Basisspannung wird das im Kopplerraum 38 enthaltene Kraftstoffvolumen komprimiert, so dass der Druck pK im Kopplerraum ansteigt. Da nun der Druck pK im Kopplerraum den im Niederdruckbereich herrschenden Druck pN unterhalb der Ventilsitzfläche 84 übersteigt, verfährt der Ventilbolzen beziehungsweise der Ventilkolben 44 wieder in den Dichtsitz 48 und entkoppelt die Verbindung zwischen dem Steuerraum 86 und dem niederdruckseitigen Bereich des Kraftstoffinjektors 10. Daraufhin gleicht sich der Druck im Steuerraum 86 durch den Zufluss über die Zulaufdrossel 96 wieder dem Systemdruck an, der im Hochdrucksammelraum herrscht oder durch ein Hochdruckförderaggregat erzeugt wird.To end the injection, the piezoelectric actuator 74 of the actuator module 20 is again charged to its base voltage, so that, in contrast to the opening phase of the preferably needle-shaped injection valve member 92, the longest extent of the piezocrystal stack of the actuator 74 is set in the closing phase. Due to the elongation of the piezocrystal stack of the piezoelectric actuator 74 when subjected to its base voltage, the fuel volume contained in the coupler space 38 is compressed, so that the pressure p K in the coupler space increases. Since the pressure p K in the coupler chamber exceeds the pressure p N prevailing in the low-pressure region below the valve seat surface 84, the valve pin or the valve piston 44 again moves into the sealing seat 48 and decouples the connection between the control chamber 86 and the low-pressure-side region of the fuel injector 10 The pressure in the control chamber 86 is equalized by the inflow via the inlet throttle 96 back to the system pressure, which prevails in the high-pressure accumulator or is generated by a high pressure pumping unit.

Da am brennraumseitigen Ende des bevorzugt nadelförmig ausgebildeten Einspritzventilgliedes 92 ein geringerer Druck herrscht als an der dem Brennraum abgewandten Stirnfläche des Einspritzventilgliedes 92 innerhalb des Steuerraumes 86, verfährt das bevorzugt nadelförmig ausgebildete Einspritzventilglied 92 wieder in seinen Düsensitz, so dass die Einspritzung beendet ist.Since the combustion chamber end of the preferably needle-shaped injection valve member 92, a lower pressure prevails than at the combustion chamber facing away from the end face of the injection valve member 92 within the control chamber 86, moves the preferably needle-shaped injection valve member 92 back into its nozzle seat, so that the injection is completed.

Alternativ zur in den Figuren 1 und 2 vorstehend beschriebenen Ausführungsform des erfindungsgemäß vorgeschlagenen Kraftstoffinjektors 10, ist eine Befüllung des kraftstofffreien Raumes 24 mit einem elektrisch isolierenden Fluid denkbar. Durch das elektrisch isolierende Fluid wird bewirkt, dass die Temperatur am Aktor 74, welche im Betrieb des Aktors 74 entsteht, aufgrund des höheren Temperaturleitwertes von Flüssigkeiten gegenüber Luft schneller abgeführt werden kann.Alternatively to in the FIGS. 1 and 2 As described above, the embodiment of the inventively proposed fuel injector 10, a filling of the fuel-free space 24 with an electrically insulating fluid is conceivable. The electrically insulating fluid causes the temperature at the actuator 74, which arises during operation of the actuator 74, to be dissipated more rapidly than air due to the higher temperature conductivity of liquids.

Figur 3 zeigt eine alternative Ausführungsvariante des Kraftstoffinjektors 10, bei der eine zusätzliche Hülse 98 in den Innendurchmesser des Federelementes 28 eingepresst ist. Zu dieser Ausführungsvariante kann dann gegriffen werden, falls die Radialführung zwischen dem Kopplerkopf 34 und dem Federelement 28 am unteren Bund 36 aus fertigungstechnischen Gründen nicht umsetzbar ist. FIG. 3 shows an alternative embodiment of the fuel injector 10, in which an additional sleeve 98 is pressed into the inner diameter of the spring element 28. For this embodiment can then be resorted to, if the radial guide between the coupler head 34 and the spring element 28 on the lower collar 36 for manufacturing reasons is not feasible.

Durch die Drossel 100 beziehungsweise das in der Niederdruckleitung angeordnete Drosselrückschlagventil im Niederdruckbereich wird der Druck angehoben. Anstelle der in Figur 1 dargestellten Drosselstelle 100 kann in der Niederdruckleitung auch das in Figur 1.1 dargestellte Drosselrückschlagventil 100 eingesetzt werden, durch das das niederdruckseitige Druckniveau angehoben wird. Je höher das Niederdruckniveau gehalten werden kann, umso leichter lässt sich die Funktion des Schaltventiles aufgrund des geringen Aktorhubes umsetzen. By the throttle 100 and arranged in the low pressure line throttle check valve in the low pressure region of the pressure is increased. Instead of in FIG. 1 can be 100 in the low pressure line and the in Figure 1.1 shown throttle check valve 100 can be used, through which the low-pressure side pressure level is raised. The higher the low pressure level can be maintained, the easier it is to implement the function of the switching valve due to the small actuator stroke.

Claims (4)

  1. Fuel injector (10) having a nozzle module (12), having a throttle plate (14) and having a retaining body (18), wherein an actuator module (20, 74) is accommodated in the retaining body (18), which actuator module comprises a 2/2-way switching valve (22) for the pressurization of or release of pressure from a control chamber (86) by means of which a preferably needle-shaped injection valve member (92) is actuated, wherein the 2/2-way switching valve (22) is pressure-balanced and has a valve body (44) which comprises a passage opening in which is guided a guide pin (42) which, within a high-pressure region (52), is acted on with fuel at system pressure, characterized in that the valve body (44) has a valve seat surface (84) which is acted on by the low pressure of a leakage bore (64) in the fuel injector and which thereby exerts a hydraulic force (Fopen) on the valve body (44), wherein a throttling check valve (100) or a throttle (100) is positioned in the leakage bore (64) in order to increase the low-pressure-side residual pressure, and the valve body (44) moves out of its sealing seat (48) as a result of the hydraulic force (Fopen) only when said force (Fopen) is greater than a force (Fclose) acting on the valve body (44) in the closing direction, wherein said force (Fclose) which acts in the closing direction is formed by a spring force (FF) and a hydraulic force (FHyd), and the hydraulic force (FHyd) is generated by the pressure in a valve chamber (54), and the pressure in the valve chamber (54) can be dissipated by the movement of a coupler head (34).
  2. Fuel injector according to Claim 1, characterized in that the valve body (44) of the 2/2-way switching valve (22) is acted on by a compression spring (46) which is supported on a setting disc (40) on the retaining body (18).
  3. Fuel injector according to Claim 1, characterized in that the passage opening in the valve body (44) is aligned with a duct for the release of pressure from the control chamber (86), in which duct an outflow throttle (88) is formed.
  4. Fuel injector according to Claim 1, characterized in that leakage flowing out via a radial guide (56) of the guide pin (42) in the valve body (44) is discharged via the leakage bore (64) into the low-pressure region (66) of the fuel injection system.
EP08103368A 2007-04-16 2008-04-04 Pressure-stabilised actuator Not-in-force EP1983186B1 (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007017729A DE102007017729A1 (en) 2007-04-16 2007-04-16 Pressure compensated actuator

Publications (3)

Publication Number Publication Date
EP1983186A2 EP1983186A2 (en) 2008-10-22
EP1983186A3 EP1983186A3 (en) 2009-01-07
EP1983186B1 true EP1983186B1 (en) 2011-10-19

Family

ID=39711849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08103368A Not-in-force EP1983186B1 (en) 2007-04-16 2008-04-04 Pressure-stabilised actuator

Country Status (3)

Country Link
EP (1) EP1983186B1 (en)
AT (1) ATE529624T1 (en)
DE (1) DE102007017729A1 (en)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102012212614A1 (en) 2012-07-18 2014-01-23 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement
DE102012222509A1 (en) 2012-12-07 2014-06-12 Continental Automotive Gmbh piezoinjector
DE102012223934B4 (en) 2012-12-20 2015-10-15 Continental Automotive Gmbh piezoinjector
DE102016220074B4 (en) * 2016-10-14 2023-02-02 Vitesco Technologies GmbH Piezo common rail injector with hydraulic play compensation by moving the valve seat

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10118053A1 (en) * 2001-04-11 2002-10-24 Bosch Gmbh Robert Valve for controlling liquids e.g. for vehicle fuel injection system, has hydraulic chamber that transfers control piston movement to actuating piston, which is in hydraulic force equilibrium with valve element closed
DE10218904A1 (en) 2001-05-17 2002-12-05 Bosch Gmbh Robert Fuel injection system
DE102006055548A1 (en) * 2006-11-24 2008-05-29 Robert Bosch Gmbh fuel injector

Also Published As

Publication number Publication date
EP1983186A2 (en) 2008-10-22
ATE529624T1 (en) 2011-11-15
EP1983186A3 (en) 2009-01-07
DE102007017729A1 (en) 2008-10-23

Similar Documents

Publication Publication Date Title
EP1733139B1 (en) Common rail injector
WO2007115853A1 (en) Fuel injector
EP2106500B1 (en) Fuel injector
EP1944500A2 (en) Fuel injector
EP1983186B1 (en) Pressure-stabilised actuator
WO2005015002A1 (en) Control valve for a fuel injector comprising a pressure exchanger
EP2084392A1 (en) Fuel injector
WO2005068821A1 (en) Fuel injector comprising a directly triggered injection valve member
EP1939441A2 (en) Fuel injector
EP1466086B1 (en) Control element for injectors with switched injector pin
EP2011995A2 (en) Injector with a valve element which opens to the outside
DE102007029969A1 (en) Fast-acting fuel injector for high injection pressures
DE102012220027A1 (en) Switching valve for common-rail fuel injector for injecting diesel into combustion chamber of internal combustion engine, has control space filled with fuel via hole, and closing element closing hole in position for pressure relief of space
EP1421272B1 (en) Fuel-injection device for internal combustion engines
EP1980742B1 (en) Fuel injector with integrated pressure intensifier
DE10307002A1 (en) Fuel injection nozzle has outer nozzle needle and control element in form of inner nozzle needle with first and second lower and higher fuel outlet cross-section positions
DE102009046373A1 (en) Magnetic valve e.g. pressure-balanced valve for use in common rail-injector for injecting diesel into combustion chamber of diesel internal combustion engine, has damping chamber connected with low-pressure area by connection
DE102007040115A1 (en) Control valve for actuating control chamber of fuel injector, has valve piston, which is guided in valve body in axially movable manner and is operated by actuator
WO2008061842A1 (en) Fuel injector
EP1887213B1 (en) Fuel injector with direct pin control and servo-valve support
DE102007018472A1 (en) Fuel injector with solenoid valve
DE102007001365A1 (en) Common rail injector, for injecting e.g. petrol, into combustion chamber of internal combustion engine, has switching chamber connected with low pressure area by connecting channel that is closed and opened by control valve
DE102007038394A1 (en) Control valve for a fuel injector
DE102008000596A1 (en) Common rail injector for injecting fuel into combustion chamber of internal combustion engine, has nozzle needle comprising nozzle-sided part with extension, which is axially, displaceably guided into recess or hole on nozzle body
DE102009045560A1 (en) Fuel injector, particularly common-rail-fuel injector, has actuator module which is arranged in holding body that is clamped with nozzle body by insertion of throttle plate, where nozzle needle is longitudinally guided to nozzle body

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

AK Designated contracting states

Kind code of ref document: A2

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

AX Request for extension of the european patent

Extension state: AL BA MK RS

PUAL Search report despatched

Free format text: ORIGINAL CODE: 0009013

AK Designated contracting states

Kind code of ref document: A3

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

AX Request for extension of the european patent

Extension state: AL BA MK RS

17P Request for examination filed

Effective date: 20090707

17Q First examination report despatched

Effective date: 20090731

AKX Designation fees paid

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

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 HR HU IE IS IT LI LT LU LV MC MT NL NO 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

REG Reference to a national code

Ref country code: DE

Ref legal event code: R096

Ref document number: 502008005231

Country of ref document: DE

Effective date: 20111215

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20111019

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20111019

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

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: 20120219

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: 20111019

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: 20120119

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: 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: 20111019

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: 20120220

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: 20111019

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: 20120120

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20111019

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: 20120119

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: 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: 20111019

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: 20111019

26N No opposition filed

Effective date: 20120720

BERE Be: lapsed

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

Effective date: 20120430

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008005231

Country of ref document: DE

Effective date: 20120720

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: 20120430

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: 20120404

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: 20120430

Ref country code: LI

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

Effective date: 20120430

Ref country code: GB

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

Effective date: 20120404

Ref country code: CH

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

Effective date: 20120430

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

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: 20120130

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: 20111019

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: 20111019

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: 20111019

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: 20120404

REG Reference to a national code

Ref country code: AT

Ref legal event code: MM01

Ref document number: 529624

Country of ref document: AT

Kind code of ref document: T

Effective date: 20130404

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: 20080404

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: 20130404

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

Ref country code: IT

Payment date: 20140429

Year of fee payment: 7

Ref country code: FR

Payment date: 20140416

Year of fee payment: 7

Ref country code: DE

Payment date: 20140626

Year of fee payment: 7

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008005231

Country of ref document: DE

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 NON-PAYMENT OF DUE FEES

Effective date: 20150404

Ref country code: DE

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

Effective date: 20151103

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20151231

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: 20150430