EP1983186A2 - Elément de commande à compensation de pression - Google Patents

Elément de commande à compensation de pression Download PDF

Info

Publication number
EP1983186A2
EP1983186A2 EP08103368A EP08103368A EP1983186A2 EP 1983186 A2 EP1983186 A2 EP 1983186A2 EP 08103368 A EP08103368 A EP 08103368A EP 08103368 A EP08103368 A EP 08103368A EP 1983186 A2 EP1983186 A2 EP 1983186A2
Authority
EP
European Patent Office
Prior art keywords
pressure
fuel
fuel injector
valve
injector according
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
EP08103368A
Other languages
German (de)
English (en)
Other versions
EP1983186A3 (fr
EP1983186B1 (fr
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/fr
Publication of EP1983186A3 publication Critical patent/EP1983186A3/fr
Application granted granted Critical
Publication of EP1983186B1 publication Critical patent/EP1983186B1/fr
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. In this projecting a closing piston of the fuel injector into a closing pressure chamber, so that a closing piston can be acted upon by fuel pressure to achieve a force acting in the closing direction on the closing piston force.
  • the closing pressure chamber and the rear space of the pressure booster device are formed by a common closing pressure-return chamber, wherein all portions of the closing pressure-return space 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. However, since the injection valve member requires a certain time t s until it has returned to its seat in the injector body of the fuel injector and closes the arranged below the seat injection ports, injects the fuel injector in the final phase of the injection process with an injection pressure below that in the high-pressure accumulator prevailing pressure.
  • the injection rate of such a fuel injector is characterized by a plateau, ie a dent. Due to the decreasing injection pressure in the final phase of the injection, however, the emission composition of an internal combustion engine operated in this way changes to the negative, ie the exhaust gas contains too many pollutants.
  • 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 takes place against the medium to be injected by a coating applied to the actuator in the form of a shrink tube or by consuming applied coatings.
  • An insulation applied in this way to a piezoactuator proves to be problematic, in particular at high system pressures, which can 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 and 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 , acts in the opening direction, a hydraulic force F ⁇ ff 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.
  • an additional sleeve 98 is pressed into the inner diameter of the spring element 28.
  • 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)
EP08103368A 2007-04-16 2008-04-04 Elément de commande à compensation de pression Not-in-force EP1983186B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007017729A DE102007017729A1 (de) 2007-04-16 2007-04-16 Druckausgeglichenes Stellelement

Publications (3)

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

Family

ID=39711849

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08103368A Not-in-force EP1983186B1 (fr) 2007-04-16 2008-04-04 Elément de commande à compensation de pression

Country Status (3)

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

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104797807A (zh) * 2012-12-20 2015-07-22 大陆汽车有限公司 压电喷射器
US10024285B2 (en) 2012-07-18 2018-07-17 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement
US10508635B2 (en) 2012-12-07 2019-12-17 Continental Automotive Gmbh Piezo injector

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102016220074B4 (de) * 2016-10-14 2023-02-02 Vitesco Technologies GmbH Piezo-Common-Rail-Injektor mit hydraulischem Spielausgleich über Bewegung des Ventilsitzes

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10218904A1 (de) 2001-05-17 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung

Family Cites Families (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10118053A1 (de) * 2001-04-11 2002-10-24 Bosch Gmbh Robert Ventil zum Steuern von Flüssigkeiten
DE102006055548A1 (de) * 2006-11-24 2008-05-29 Robert Bosch Gmbh Kraftstoffinjektor

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE10218904A1 (de) 2001-05-17 2002-12-05 Bosch Gmbh Robert Kraftstoffeinspritzeinrichtung

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10024285B2 (en) 2012-07-18 2018-07-17 Continental Automotive Gmbh Piezo injector with hydraulically coupled nozzle needle movement
US10508635B2 (en) 2012-12-07 2019-12-17 Continental Automotive Gmbh Piezo injector
CN104797807A (zh) * 2012-12-20 2015-07-22 大陆汽车有限公司 压电喷射器
US9689359B2 (en) 2012-12-20 2017-06-27 Continental Automotive Gmbh Piezo injector

Also Published As

Publication number Publication date
ATE529624T1 (de) 2011-11-15
EP1983186A3 (fr) 2009-01-07
DE102007017729A1 (de) 2008-10-23
EP1983186B1 (fr) 2011-10-19

Similar Documents

Publication Publication Date Title
EP1733139B1 (fr) Injecteur common rail
WO2007115853A1 (fr) Injecteur de carburant
WO2005075811A1 (fr) Injecteur de carburant avec obturateur d'injection a commande directe
DE102009000394A1 (de) Regelrückschlagventil und Kraftstoffeinspritzventil, das selbiges aufweist
EP2106500B1 (fr) Injecteur de carburant
EP1944500A2 (fr) Injecteur de carburant
EP1983186B1 (fr) Elément de commande à compensation de pression
WO2008049699A1 (fr) Injecteur de carburant
WO2005015002A1 (fr) Soupape de commande conçue pour un injecteur de carburant comprenant un dispositif multiplicateur de pression
WO2005068821A1 (fr) Injecteur de carburant dote d'un element de soupape d'injection a commande directe
EP1939441A2 (fr) Injecteur de carburant
EP1466086B1 (fr) Piece de commande destinee a des injecteurs a aiguille d'injecteur manoeuvrable
EP2011995A2 (fr) Injecteur doté d'un élément d'aération s'ouvrant vers l'extérieur
DE102007029969A1 (de) Schnellschaltender Kraftstoffinjektor für hohe Einspritzdrücke
DE102012220027A1 (de) Schaltventil für einen Kraftstoffinjektor
DE102008042227A1 (de) Kraftstoff-Injektor
EP1980742B1 (fr) Injecteur de carburant doté d'un amplificateur de pression intégré
DE102009046373A1 (de) Magnetventil sowie Kraftstoff-Injektor mit einem Magnetventil
DE102007040115A1 (de) Steuerventil für einen Kraftstoffinjektor
WO2008061842A1 (fr) Injecteur de carburant
DE102007018472A1 (de) Kraftstoffinjektor mit Magnetventil
DE102007038394A1 (de) Steuerventil für einen Kraftstoffinjektor
DE102006036779A1 (de) Kraftstoffinjektor mit direkter Nadelsteurung und Servoventil-Unterstützung
DE102007001365A1 (de) Injektor mit Steuer- und Schaltkammer
DE102006027484A1 (de) Kraftstoffinjektor mit kraftausgeglichenem Steuerventil

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