EP2156047A1 - Fuel injector having low wear - Google Patents
Fuel injector having low wearInfo
- Publication number
- EP2156047A1 EP2156047A1 EP08759582A EP08759582A EP2156047A1 EP 2156047 A1 EP2156047 A1 EP 2156047A1 EP 08759582 A EP08759582 A EP 08759582A EP 08759582 A EP08759582 A EP 08759582A EP 2156047 A1 EP2156047 A1 EP 2156047A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- pressure
- fuel injector
- injector
- damping
- bore
- 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
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
- F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
- F02M55/04—Means for damping vibrations or pressure fluctuations in injection pump inlets or outlets
-
- 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
- F02M2547/00—Special features for fuel-injection valves actuated by fluid pressure
- F02M2547/003—Valve inserts containing control chamber and valve piston
-
- 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
- F02M63/02—Fuel-injection apparatus having several injectors fed by a common pumping element, or having several pumping elements feeding a common injector; Fuel-injection apparatus having provisions for cutting-out pumps, pumping elements, or injectors; Fuel-injection apparatus having provisions for variably interconnecting pumping elements and injectors alternatively
- F02M63/0225—Fuel-injection apparatus having a common rail feeding several injectors ; Means for varying pressure in common rails; Pumps feeding common rails
Definitions
- the invention is based on known fuel injectors for injecting fuel into a combustion chamber of an internal combustion engine.
- These fuel injectors may in particular be fuel injectors for high-pressure accumulator injection systems, which are also referred to as common rail injectors.
- fuel from a high-pressure accumulator (rail) is supplied to the fuel injectors via a high-pressure inlet, and the injection of the fuel, i. the opening of the fuel injector, is usually controlled by an actuator, such as a magnetic or piezoelectric actuator.
- One advantage of the common-rail injectors is that the injection behavior can be controlled very precisely via the actuator, so that even complex, for combustion particularly favorable injection curves can be realized. This makes it possible to realize internal combustion engines with extremely low pollutant emission.
- pressure oscillations in the common rail system can have undesirable or damaging effects on the operating behavior of the overall system and of the internal combustion engine. In addition, these can also reduce the durability of the entire system and individual injectors. For example, pressure oscillations in the high-pressure range with an amplitude of approx. 300 bar are in many cases an everyday occurrence.
- a high-pressure line between huiien an injector and a common rail proposed, which degrades the pressure waves resulting from actuation of the injector in whole or in part.
- the high-pressure line has a first section and a second section, which are connected in parallel with one another.
- DE 103 07 871 A1 contributes to the improvement of the vibration behavior and to the elimination of pressure oscillations. Nevertheless, DE 103 07 871 A1 leaves room for further improvements, in particular since the proposed high-pressure line is structurally comparatively complex and as a rule only dampens pressure oscillations within a narrow frequency range due to the fixedly predetermined aspect ratios.
- the invention is essentially based on the idea of providing at least one further, separate vibration damping bore in addition to a high-pressure bore which is usually present in common-rail injectors and extends essentially parallel to the injector axis.
- This vibration damping bore comprises a damping channel extending essentially parallel to the injector axis in the injector housing.
- the vibration damping behavior according to the invention is not based, as in DE 103 07 871 Al, on a superposition of back and forth waves. As a result, an attenuation within a wide frequency range can be realized.
- the damping behavior is based on known systems rather on a "parallel circuit" of a damping channel, with a corresponding resistance to pressure waves and a corresponding volume of liquid.
- the vibration damping bore is located between a high-pressure region, in particular a high-pressure chamber, which is adjacent to the control chamber (for example, a high-pressure annulus, which surrounds the control chamber).
- a high-pressure chamber which is adjacent to the control chamber (for example, a high-pressure annulus, which surrounds the control chamber).
- the vibration damping bore can be substantially the same length and extend substantially parallel to a high-pressure bore, which conveys fuel under high pressure into the nozzle chamber so that it can be injected from there through injection openings in the combustion chamber.
- the vibration damping bore comprises at least one throttle element, wherein two or more throttle elements are preferred.
- the throttle element may comprise a first throttle element connecting the damping channel and the high-pressure chamber (in particular the high-pressure annular space).
- the throttle element may comprise a second throttle element connecting the damping channel and the nozzle chamber.
- the throttle elements have a cross section with a diameter between 0.1 and 0.8 mm, in particular between 0.2 and 0.5 and particularly preferably at 0.3 mm.
- cross-sections of at least 1.0 mm, in particular at least 1.5 mm and particularly preferably of approximately 2.0 mm have proved to be advantageous.
- the latter value represents a compromise that can be realized in practice between the highest possible volume of fluid for the damping (inertial mass) and the space requirement of the damping channel in the injector body.
- the damping channel In order to be able to provide the highest possible damping volume as an "inertial mass,” it is preferable for the damping channel to have a length of at least 40 mm, in particular of at least 60 mm and particularly preferably of 90 mm Fuel injectors can be implemented without their outer dimensions would have to be changed.
- the fuel injector in one of the embodiments described above allows vibration damping of pressure oscillations within a wide frequency range.
- the wear of the fuel injector can be significantly reduced, and the life of the common rail systems can be significantly improved.
- FIG. 2 shows a system response in the frequency space of a common rail system to its own injection and a neighboring injection
- Figure 3 shows cumulative wear for a single injector system and an entire common rail system with multiple active injectors
- Figure 4 shows an embodiment of a common rail injector according to the present invention
- Figure 5 shows a transmission behavior of a common rail injector according to the prior
- Figure 6 simulated wear of common rail injectors with different wear reducing measures.
- FIG. 1 shows a characteristic operating behavior of a commercially available common rail injector as a time characteristic.
- the upper curve (reference numeral 110) shows the pressure curve in bar, and the lower curve (reference symbol 112) the force, the nozzle needle or the injection valve member (hereinafter referred to as needle force), plotted in Newtons. Shown is the time course over a full injection cycle of a six-cylinder engine.
- the operating behavior of the injection system can be divided into two areas: on the one hand into the area (denoted by reference numeral 114 in FIG. 1), in which the response to the own injection dominates, and into a second area (in FIG 1 with reference numeral 116), in which the influence of the neighboring injec- Li ⁇ nen uweei weighs.
- the boundary between the two areas is approximately 0.027 sec.
- the oscillation behavior for example the oscillation of the needle force 112
- the vibration behavior is dominated by the injection of the considered fuel injector.
- the vibration behavior is triggered by neighboring injections, that is to say by injections of adjacent fuel injectors of the internal combustion engine. This area of unfamiliarized vibrations is commonly referred to as the "telephony" area or “telephony” area.
- Fig. 2 a possible cause of the effects described above is shown.
- the gradients of the system responses that is to say the derivatives I of the needle force (see curve 112 in Fig. 1), are plotted in the frequency domain in arbitrary units. While curve 118 represents the system response to its own injection, curve 120 shows the system response to neighbor injections.
- the system response 120 of the neighboring injections shows a multiplicity of further excitation frequencies. This means that the nozzle needle or the injection valve member of a Kraftstoff ⁇ njektors reacts very sensitive to suggestions by neighboring injections and has a much more pronounced vibration behavior.
- Fig. 3 the result of such a wear model is graphically illustrated.
- the Y-axis 122 shows the accumulated wear
- the X-axis 124 symbolizes the time.
- the time is plotted over a complete injection cycle of a six-cylinder engine.
- the injections of the individual injectors are designated by the reference numeral 126.
- a curve 128, in which only the own injection is taken into account and a wear curve 130 in which also adjacent injections are taken into account, which thus symbolize a fully activated system of an internal combustion engine.
- one significant approach of the present invention is to reduce the sensitivities of a fuel injector to higher frequencies through geometric changes in the high pressure fluid system. Accordingly, a measure is proposed which is able to minimize the transmission behavior of the input pressure on the needle force in terms of its gain with respect to the natural frequencies.
- the fuel injector 132 has an injector housing 134, which is modularly composed of a plurality of modules held together by a union nut 136. iii an injection valve element 140 is accommodated, which is mounted movably parallel to the injector axis 142.
- the injection valve member 140 is surrounded by a nozzle chamber 144 and closes at its lower end injection openings 146.
- the nozzle chamber 144 communicates with a high-pressure bore 148 in connection, which extends substantially parallel to the injector 142, ie with an angular deviation of about 4 °.
- the high-pressure bore 148 communicates with a high-pressure inlet 150 and can be acted upon by this from a high-pressure accumulator (common rail), which is not shown in Fig. 4, with high-pressure fuel.
- the injection valve member 140 is acted upon by a nozzle spring 152 with a closing force. Furthermore, the injection valve member 140 is in communication with a control piston 154, above which a control chamber 156 is located.
- the control chamber 156 is surrounded by a high pressure annulus 158, which in turn communicates with the high pressure bore 148.
- the high-pressure annulus 158 is connected to the control chamber 156 via a control chamber throttle element 160.
- the pressure in the control chamber 156 is controlled in this embodiment by a solenoid valve 162, via which a relief hole 164, which is also equipped with a throttle element, can be closed or released. Thereby, the relief hole 164 and thus the control chamber 156 is disconnected from a low pressure drain 166 and connected thereto.
- the solenoid valve 162 If the solenoid valve 162 is opened, the pressure in the control chamber 156 drops, and the control piston 154 and thus the injection valve member 140 move upwards and release the injection opening 146. This starts the injection process. If the solenoid valve 162 is closed, high pressure prevails in the control chamber 156, so that the injection valve member 140 is pressed into its valve seat, the injection openings 146 being closed.
- a damping measure according to the invention is implemented in order to dampen these pressure fluctuations.
- a vibration damping hole 168 is provided, wel- a uampfungskanal 170 has.
- This damping channel 170 extends essentially the same length to the high-pressure bore 148 through the injector body 134 and likewise runs essentially parallel to the injector axis 142. The angle deviations from the parallelism substantially correspond to the angular deviations of the high-pressure bores 148.
- the vibration damping bore 168 connects the high-pressure annulus 158 to the nozzle chamber 144.
- the damping passage 170 in this exemplary embodiment is connected via an annular space throttle 172 and to the nozzle space 144 via a nozzle space throttle 174.
- the fluidic oscillation behavior of the fuel injector 132 can be modified in a simple manner (that is, only by additional implementation of the damping channel 170 and the throttles 172, 174) in a targeted manner.
- the natural frequencies of the vibration system can be detuned and the sensitivity of the system to external stimulation can be significantly reduced.
- a length of the damping channel 170 of 90 mm and a diameter of approximately 2 mm have proven to be suitable.
- Throttles 172, 174 each have a diameter of 0.3 mm in this exemplary embodiment.
- the vibration damping bore 168 thus represents a total of a second fluidic
- High pressure system which is arranged parallel to the high pressure bore 148.
- Vibration damping is essentially caused by the combination of the inert fluidic mass within the damping channel 170 and the throttles 172, 174, which is similarly describable as electrical damping in an RC resonant circuit.
- the damping measure shown in FIG. 4 changes the transmission behavior of the fuel injector 132 in a positive sense. 5
- a transfer function for a standard injector (trace 176) is compared with a transfer function 178 of an injector having a vibration damping bore 168.
- the transmission function ⁇ is plotted in dB, which is the quotient of the derivative of the needle force and the derivative of the rail pressure. The application takes place in the frequency domain.
- the two curves 176, 178 correspond to a fuel injector 132 according to FIG. 4, wherein curve 176 represents a fuel injector without the vibration damping bore 168 (ie without damping channel 170, without annular space throttle 172 and without nozzle space throttle 174), while curve 178 represents a fuel injector 132 according to FIG. 4 with the above elements, ie with a vibration damping hole 168.
- the peaks in the transfer functions are also significantly minimized, so that overall a broadband attenuation in the entire frequency range is recorded.
- the sensitivity of the fuel injector 132 against pressure fluctuations is significantly minimized.
- the amplitude responses due to the vibration damping bore 168 have been significantly reduced.
- vibration damping bore 168 According to the exemplary embodiment in FIG. 4, clear advantages over known vibration damping measures result, such as the measure described in DE 103 07 871 A1. There is overall a vibration damping recorded in the entire frequency range, so that the vibration measure, for example, is not specifically set to a specific operating point of the entire injector system or the internal combustion engine. This is a considerable advantage, as this, for example, the flexibility and applicability of the vibration damping system is extended not only with respect to different Injektortypen or types of machines, but also with respect to the efficiency of the individual operating points of the internal combustion engine.
- the vibration damping bore 168 is integrated directly in the injector housing 134, which saves additional measures outside of the fuel injector. The absorption damping is thus additional components or components within the fuel injector 132 itself.
- the bar 182 designates a fuel injector 132 with a so-called “Rail Injector Throttle” (RIT) with a diameter of 1.1 mm.
- RIT Rotary Injector Throttle
- This throttling element RIT which is likewise known from the prior art, is arranged in the high-pressure inlet 150. in the rail exit in front of the high-pressure line leading to the injector, and already causes a certain damping of pressure oscillations in the rail, thus already reducing the wear of the fuel injector by approx.
- the beam 184 illustrates a vibration damping measure according to the invention, for example the vibration damping bore 168 shown in FIG. 4 or its effect. It can be clearly seen that the vibration damping bore 168 reduces the overall wear from 100% to approx. 66%.
- the invention thus provides a way to efficiently reduce wear on fuel injectors 132 by simple additional damping measures.
- the damping measures can be implemented, in particular, in fuel injectors 132, in which the distance between the control chamber 150 and the nozzle chamber 144 is high, so that a sufficient volume of fluid and a sufficient discharge path through the damping channel 170 can be provided here.
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Fuel-Injection Apparatus (AREA)
Abstract
Description
Claims
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE200710025617 DE102007025617A1 (en) | 2007-06-01 | 2007-06-01 | Fuel injector with low wear |
PCT/EP2008/055899 WO2008145515A1 (en) | 2007-06-01 | 2008-05-14 | Fuel injector having low wear |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2156047A1 true EP2156047A1 (en) | 2010-02-24 |
EP2156047B1 EP2156047B1 (en) | 2014-07-16 |
Family
ID=39865567
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP08759582.3A Not-in-force EP2156047B1 (en) | 2007-06-01 | 2008-05-14 | Fuel injector having low wear |
Country Status (3)
Country | Link |
---|---|
EP (1) | EP2156047B1 (en) |
DE (1) | DE102007025617A1 (en) |
WO (1) | WO2008145515A1 (en) |
Families Citing this family (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US9644590B2 (en) * | 2014-01-31 | 2017-05-09 | Cummins Inc. | Fuel injection pressure pulsation dampening system |
DE102016209546A1 (en) | 2016-06-01 | 2017-12-07 | Robert Bosch Gmbh | Fuel injection valve |
DE102017126642A1 (en) | 2017-11-13 | 2019-05-16 | Volkswagen Aktiengesellschaft | Device for reducing pressure wave oscillations in an injection device |
Family Cites Families (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE19842067A1 (en) * | 1998-09-15 | 2000-03-16 | Daimler Chrysler Ag | Fuel injection system for diesel internal combustion engine has accumulator associated directly with each injector to eliminate fuel pressure fluctuations |
DE10060812A1 (en) * | 2000-12-07 | 2002-06-13 | Bosch Gmbh Robert | Fuel injection system for internal combustion engines |
DE10060811A1 (en) * | 2000-12-07 | 2002-06-13 | Bosch Gmbh Robert | Fuel injection system for internal combustion engines |
DE10121891A1 (en) * | 2001-05-05 | 2002-11-07 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
DE10121892A1 (en) * | 2001-05-05 | 2002-11-07 | Bosch Gmbh Robert | Fuel injection valve for internal combustion engines |
DE10307871A1 (en) | 2003-02-25 | 2004-09-02 | Robert Bosch Gmbh | High pressure line for a fuel injection system |
DE102004007342A1 (en) * | 2004-02-14 | 2005-09-01 | Robert Bosch Gmbh | Hydraulic system for an internal combustion engine's fuel injection system has a source for a fluid under high pressure linked to a valve with control and nozzle devices |
ATE413527T1 (en) * | 2004-06-30 | 2008-11-15 | Fiat Ricerche | FUEL INJECTION DEVICE FOR AN INTERNAL COMBUSTION ENGINE |
-
2007
- 2007-06-01 DE DE200710025617 patent/DE102007025617A1/en not_active Withdrawn
-
2008
- 2008-05-14 WO PCT/EP2008/055899 patent/WO2008145515A1/en active Application Filing
- 2008-05-14 EP EP08759582.3A patent/EP2156047B1/en not_active Not-in-force
Non-Patent Citations (1)
Title |
---|
See references of WO2008145515A1 * |
Also Published As
Publication number | Publication date |
---|---|
DE102007025617A1 (en) | 2008-12-04 |
WO2008145515A1 (en) | 2008-12-04 |
EP2156047B1 (en) | 2014-07-16 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
EP2635794B1 (en) | Device for injecting fuel into the combustion chamber of an internal combustion engine | |
DE4340305C2 (en) | Fuel injection nozzle for an internal combustion engine | |
DE102007000080B4 (en) | Fuel injector and fuel injector | |
AT503660B1 (en) | DEVICE FOR INJECTING FUEL IN THE COMBUSTION ENGINE OF AN INTERNAL COMBUSTION ENGINE | |
EP2049787A1 (en) | Injector for a fuel injection system | |
EP2516839A1 (en) | Fuel injector apparatus | |
EP1342005B1 (en) | Fuel injection system for internal combustion engines | |
DE112006002281T5 (en) | Injection device for a single fluid with rate forming capability | |
EP1252437A2 (en) | Injection device and method for injecting a fluid | |
EP2387661A1 (en) | Fuel injector for internal combustion engines | |
EP2156047B1 (en) | Fuel injector having low wear | |
EP1117921B1 (en) | Fuel injector for a common rail fuel system | |
DE19938169A1 (en) | Fuel injector | |
AT9288U1 (en) | HYDRAULIC DEVICE WITH AT LEAST ONE PRESSURE MEMORY | |
DE10132246A1 (en) | Fuel injector with high pressure resistant inlet | |
EP2807367B1 (en) | Device for injecting fuel into the combustion chamber of an internal combustion engine | |
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 | |
WO2003027485A1 (en) | Fuel injection system with injector hydraulically decoupled from the supply | |
DE102008044743A1 (en) | Injection valve and fluid delivery system with injection valve | |
DE102008041561A1 (en) | Fuel injector, particularly common rail injector for injecting fuel into combustion chamber of internal combustion engine, comprises two injector valve element units that are coupled together over hydraulic coupler | |
DE102004016508A1 (en) | Common rail automotive fuel injection assembly has throttle prior to jet causing lower back-pressure to pump than to jet | |
DE10358861A1 (en) | injection | |
DE102019220172A1 (en) | Fuel injector for an internal combustion engine | |
DE102007005574A1 (en) | Injector for injecting fuel into combustion chambers of fuel engines | |
DE10326506A1 (en) | Device for injecting fuel with a stroke-stabilized injection valve member |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
17P | Request for examination filed |
Effective date: 20100104 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR 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 |
|
DAX | Request for extension of the european patent (deleted) | ||
17Q | First examination report despatched |
Effective date: 20130708 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R079 Ref document number: 502008012017 Country of ref document: DE Free format text: PREVIOUS MAIN CLASS: F02M0047020000 Ipc: F02M0063020000 |
|
RIC1 | Information provided on ipc code assigned before grant |
Ipc: F02M 63/02 20060101AFI20131219BHEP Ipc: F02M 47/02 20060101ALI20131219BHEP Ipc: F02M 55/04 20060101ALI20131219BHEP |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
INTG | Intention to grant announced |
Effective date: 20140220 |
|
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 Free format text: LANGUAGE OF EP DOCUMENT: GERMAN |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: REF Ref document number: 677823 Country of ref document: AT Kind code of ref document: T Effective date: 20140815 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R096 Ref document number: 502008012017 Country of ref document: DE Effective date: 20140828 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: VDEP Effective date: 20140716 |
|
REG | Reference to a national code |
Ref country code: LT Ref legal event code: MG4D |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: 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: 20140716 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: 20141117 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: 20141016 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: 20140716 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: 20141017 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: 20140716 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: 20140716 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: 20141016 |
|
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: 20140716 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: 20140716 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: 20140716 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: 20141116 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: 20140716 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R097 Ref document number: 502008012017 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20140716 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: 20140716 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: 20140716 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: 20140716 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: 20140716 Ref country code: IT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140716 |
|
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 |
|
26N | No opposition filed |
Effective date: 20150417 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140716 |
|
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: 20150514 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150531 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150531 Ref country code: LU 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: 20150514 Ref country code: MC Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20140716 |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: MM4A |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150514 Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150514 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 9 |
|
REG | Reference to a national code |
Ref country code: AT Ref legal event code: MM01 Ref document number: 677823 Country of ref document: AT Kind code of ref document: T Effective date: 20150514 |
|
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: 20150514 |
|
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: 20140716 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 10 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT; INVALID AB INITIO Effective date: 20080514 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
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: 20140716 Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20150531 |
|
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: 20140716 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: PLFP Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20200519 Year of fee payment: 13 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20200728 Year of fee payment: 13 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 502008012017 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20211201 |
|
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: 20210531 |