EP1963661B1 - Anordnung zum dämpfen der druckschwingungen eines kraftstoffzufuhrsystems eines kolbenmotors - Google Patents

Anordnung zum dämpfen der druckschwingungen eines kraftstoffzufuhrsystems eines kolbenmotors Download PDF

Info

Publication number
EP1963661B1
EP1963661B1 EP06808043A EP06808043A EP1963661B1 EP 1963661 B1 EP1963661 B1 EP 1963661B1 EP 06808043 A EP06808043 A EP 06808043A EP 06808043 A EP06808043 A EP 06808043A EP 1963661 B1 EP1963661 B1 EP 1963661B1
Authority
EP
European Patent Office
Prior art keywords
space
fuel
pressure
gas
feed system
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.)
Active
Application number
EP06808043A
Other languages
English (en)
French (fr)
Other versions
EP1963661A4 (de
EP1963661A1 (de
Inventor
Kai Lehtonen
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.)
Wartsila Finland Oy
Original Assignee
Wartsila Finland Oy
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 Wartsila Finland Oy filed Critical Wartsila Finland Oy
Publication of EP1963661A1 publication Critical patent/EP1963661A1/de
Publication of EP1963661A4 publication Critical patent/EP1963661A4/de
Application granted granted Critical
Publication of EP1963661B1 publication Critical patent/EP1963661B1/de
Active 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
    • 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
    • F02M55/00—Fuel-injection apparatus characterised by their fuel conduits or their venting means; Arrangements of conduits between fuel tank and pump F02M37/00
    • F02M55/02—Conduits between injection pumps and injectors, e.g. conduits between pump and common-rail or conduits between common-rail and injectors
    • F02M55/025—Common rails
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02M—SUPPLYING COMBUSTION ENGINES IN GENERAL WITH COMBUSTIBLE MIXTURES OR CONSTITUENTS THEREOF
    • F02M2200/00—Details of fuel-injection apparatus, not otherwise provided for
    • F02M2200/31—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements
    • F02M2200/315—Fuel-injection apparatus having hydraulic pressure fluctuations damping elements for damping fuel pressure fluctuations

Definitions

  • the present invention relates to an arrangement for dampening the pressure vibration of the fuel feed system of a piston engine.
  • injection pumps are used for introducing pressurized fuel into the cylinders via injector nozzles.
  • the injection pump comprises a cylinder element having a reciprocating piston arranged in a pressure chamber thereof. The movement of the piston causes the increase of the pressure of the fuel.
  • the cylinder element usually includes one or two inlet channels through which fuel is introduced from the low pressure side of the fuel feed system into a pressure plenum as the piston is in its bottom dead center. The piston moving upwards in the pressure plenum covers the fuel inlet channels and pressurized fuel flows from the pressure plenum to the high pressure pipe leading to the injector nozzle.
  • the fuel flow to the injector nozzle stops as a screw-like cut in the piston moves to the inlet channel and uncovers the inlet channel, whereby fuel in high pressure is discharged via the inlet channel to the low pressure side of the fuel feed system. This, in turn, causes a pressure pulse on the low pressure side of the fuel feed system.
  • injection pumps are in flow connection with the main fuel pipe of the low pressure side, whereby the pressure in the pipe will continuously vibrate as the engine is running.
  • dampeners such as gas dampeners and mechanical dampeners
  • a gas dampener comprises a gas space separated from the fuel feed system by means of a membrane. As the fuel pressure is changed, the membrane moves and the volume of the fuel space is changed, whereby the pressure vibration in the fuel feed system is dampened. The service life of such a dampener is limited, as the membrane can easily be broken, whereby the dampener is unusable.
  • a mechanical dampener comprises a piston or other intermediate piece arranged inside a space in the dampener.
  • the space is in flow connection with the fuel feed system, whereby the piston moves and thus the volume of the fuel feed system is changed as the pressure fluctuates.
  • the piston is supported by the dampener by means of at least one spring dampening the movement of the piston. The service life of this kind of mechanical dampener is limited by the durability of the springs.
  • a pressure pulse damper comprising the features of preamble of claim 1 is known from document DE 4031239 A1 .
  • Document DE 19621897 C1 discloses an arrangement for dampening pressure vibrations in a hydraulic system having a damper housing which contains a counterbalancing chamber enclosed by a counterbalancing piston working between stops in a cylindrical portion of the chamber.
  • the piston is pot-shaped with a seal on the inside and outside, the inside seal acting against a pipe end protruding into the housing.
  • the pipe is connected to a pressure source with regulator valve so as to vary the pressure exerted on the piston at the side furthest from the counterbalancing chamber.
  • the object of the invention is to produce an improved arrangement for dampening the pressure vibration of the fuel feed system of a piston engine.
  • the arrangement according to the invention for dampening the pressure vibration of the fuel feed system of a piston engine comprises a vibration dampener having a body part inside which is a space containing a movably arranged intermediate piece.
  • the body part has a first opening arranged to open to the first side of the intermediate piece for connecting the space with the fuel feed system and a second opening arranged to open into the space on the other side of the intermediate piece, the opening being in flow connection with the source of pressurized gas.
  • a gas pipe is arranged between the second opening and the gas source.
  • the gas pipe is provided with a one-way valve allowing flow therethough from the gas source to the space, but preventing flow from the space to the gas source.
  • the gas pipe is provided with a pressure regulation valve for maintaining a desired gas pressure in the part of the gas pipe between the pressure source and the one-way valve.
  • dampener used in a dampening arrangement according to the invention there is no membrane separating air and fuel from each other and no mechanical spring, whereby the dampener can be produced to be reliable and durable.
  • the dampening properties of the dampener can easily be adjusted by changing the gas pressure acting on the intermediate piece.
  • the intermediate piece comprises a first surface limiting the space in the part on the side of the first opening and a second surface limiting the space in the part on the side of the second opening. Further, the area of the first surface is larger than that of the second surface.
  • the pressure of the gas applying a force on the intermediate piece can be smaller than the pressure of the fuel for maintaining an equilibrium of the intermediate piece. Due to the low pressure the load on the gas system is low, whereby the design of the system can be simple.
  • FIG. 1 is a schematic view of a part of a fuel feed system 1 of an internal combustion engine.
  • the internal combustion engine is, for example, a large multicylinder diesel engine used in ships or power plants. For example, crude oil can be used as fuel.
  • Fuel is fed from the fuel tank 2 with a fuel pump 3 in a relatively low pressure via the low pressure piping 4 to each injection pump 5.
  • the low pressure piping 4 extends from the high pressure side of the fuel pump 3 to each injection pump 5.
  • the low pressure piping 4 comprises a main line 6 from which a branch line 7 extends to each injection pump 5.
  • Each injection pump 5 is connected to the injector nozzle 9 via high-pressure pipes 10.
  • the injection pump 5 carries out the injection of fuel together with the injector nozzles 9.
  • the injector pump increases the fuel pressure to such a level that a sufficient injection pressure is achieved at injector nozzles 9.
  • the fuel feed system also includes low-pressure return channels 8 returning from each injection pump 5 back to the fuel tank 2. Fuel is directed from the injection pumps 5 back to the fuel tank 2 through return channels 8.
  • One or more pressure vibration dampener(s) 11 is arranged in the fuel feed system.
  • the vibration dampener By means of the vibration dampener the fuel pressure fluctuations occurring in the fuel feed system 1 are dampened. Pressure fluctuations are caused, for example, as the high-pressure fuel in the injection pumps 5 is discharged into the low-pressure piping 4 when the injection stops. Because a number of injection pumps 5 are in flow connection with the same main line 6, the pressure in the main line 6 vibrates rapidly.
  • the vibration dampener 11 is arranged in connection with the low-pressure piping 4, for example. In the embodiment of figure 1 there are two dampeners 11 and they are arranged in the main line 6, preferably near the openings of the branch lines 7 leading to the injection pumps 5. Alternatively or additionally pressure vibration dampeners 11 can be installed in other places of the low pressure piping 4 or other places of the fuel system, such as in connection with the injection pump 5.
  • FIG 2 illustrates in more detail the vibration dampener 11 shown in figure 1 .
  • the dampener comprises a body part 12 delimiting a space 13 inside it.
  • the body part 12 includes a first opening 14, by means of which the space 13 is in flow connection with the fuel pipes of the fuel feed system 1, such as the main line 6.
  • the body part 12 additionally includes a second opening 15 by means of which the space 13 is in flow connection with the gas pipe 20 containing pressurized gas, such as air.
  • the pressure of the gas in gas pipe 20 is higher than the ambient pressure.
  • the cross-sectional area of the space 13 on the side of the first opening 14 is smaller than on the side of the second opening 15.
  • the space 13 includes an intermediate piece arranged to reciprocate, such as a piston 16.
  • the first opening 14 opens on the first side of the piston 16 and the second opening 15 to the second side of the piston 16.
  • the second side is on the opposite side of the piston 16 in relation to the first side.
  • the piston 16 moves in the space 13 when the pressure difference between the first opening 14 and the second opening 15 changes.
  • the piston 16 comprises a first surface 17 limiting the space 13 on the side of the first opening 14 and a second surface 18 limiting the space 13 on the side of the second opening 15.
  • the first surface 17 and the second surface 18 limit the space 13 in the direction of the movement of the piston 16. Further, the area of the first surface 17 is smaller than that of the second surface 18.
  • Annular seals 19, 19' are arranged around the piston 16 for sealing the gap between the piston 16 and the body part 12.
  • the first seal 19 is arranged near the first surface 17 of the piston 16 and the second seal 19' is arranged near the second surface 18 of the piston 16.
  • the body part 12 further includes a drain opening 24 with a drain pipe 25 attached thereto, through which fuel and/or gas leaked past the seals 19, 19' to between the piston 16 and the body part 12 is drained from the space 13.
  • fuel is not transmitted past the piston 16 from the first side to the second side and gas is not transmitted past the piston 16 from the second side to the first side.
  • Pressurized gas is introduced into the gas pipe 20 from a gas source 22, such as a tank filled with pressurized gas.
  • the gas pipe 20 is provided with a non-return valve 21 allowing flow therethrough into the space 13 but preventing flow from the space 13.
  • the non-return valve 21 opens when the pressure on its inlet side, i.e. on the side of the gas source 22 is higher than on the outlet side, i.e. on the side of the space 13.
  • the gas pipe 20 includes a pressure regulation valve 23 that opens and allows flow therethough when the force caused by the pressure on the inlet side, i.e. in the gas pipe 20 is higher than the closing force of the pressure regulation valve 23.
  • the outlet side of the pressure regulation valve 23 is in lower pressure than the inlet side, such as in ambient pressure.
  • the pressure in the gas pipe 20 can be maintained at the desired level by means of the pressure regulation valve 23.
  • the pressure regulation valve 23 is a spring loaded valve, i.e. the closing force of the valve is formed by means of
  • the gas pressure on the second side of the piston 16 can be lower than the fuel pressure on the first side of the piston 16 for maintaining an equilibrium position of the piston 16.
  • the dampening properties of the dampener 11 can be changed by changing the pressure of the gas in the gas pipe 20.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Fuel-Injection Apparatus (AREA)
  • High-Pressure Fuel Injection Pump Control (AREA)

Claims (5)

  1. Anordnung zum Dämpfen der Druckschwingungen eines Kraftstoffzufuhrsystems (1) eines Kolbenmotors, wobei die Anordnung einen Schwingungsdämpfer (11) umfasst, der einen Körperteil (12), in dem sich ein Raum (13) befindet, der ein beweglich angeordnetes Zwischenstück (16) umfasst, eine erste Öffnung (14), die eingerichtet ist, um sich an der ersten Seite des Zwischenstücks (16) in den Raum (13) zu öffnen, um den Raum (13) mit dem Kraftstoffzufuhrsystem (1) zu verbinden, eine zweite Öffnung (15), die eingerichtet ist, um sich an der zweiten Seite des Zwischenstücks (16) in den Raum (13) zu öffnen, wobei die zweite Öffnung (15) in einer Fließverbindung mit einer Druckgas umfassenden Gasquelle (22) steht, und ein Gasrohr (20), das zwischen der zweiten Öffnung (15) und der Gasquelle (22) eingerichtet ist, wobei das Gasrohr (20) mit einem Einwegventil (21) versehen ist, das einen Fluss von der Gasquelle (22) zu dem Raum (13) gestattet, aber einen Fluss von dem Raum (13) zu der Gasquelle (22) verhindert, aufweist, dadurch gekennzeichnet, dass das Gasrohr (20) mit einem Druckregelventil (23) versehen ist, um in dem Teil des Gasrohrs (20) zwischen der Druckquelle (22) und dem Einwegventil (21) einen gewünschten Gasdruck aufrechtzuerhalten.
  2. Anordnung nach Anspruch 1, dadurch gekennzeichnet, dass das Zwischenstück (16) eine erste Fläche (17), die den Raum (13) auf Seiten der ersten Öffnung (14) begrenzt, und eine zweite Fläche (18), die den Raum (13) auf Seiten der zweiten Öffnung (15) begrenzt, umfasst, und dass der Flächeninhalt der ersten Fläche (17) kleiner als jener der zweiten Fläche (18) ist.
  3. Anordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass in dem Körperteil (12) eine Abflussöffnung (24) eingerichtet ist, um Kraftstoff und/oder Gas, das zwischen den Körperteil (12) und das Zwischenstück (16) ausgelaufen ist, aus dem Raum (13) zu entfernen.
  4. Anordnung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass an dem Umfang des Zwischenstücks (16) eine Dichtungsanordnung (19, 19') eingerichtet ist, um einen Transport von Kraftstoff und/oder Gas zwischen das Zwischenstück (16) und den Körperteil (12) zu verhindern.
  5. Kraftstoffzufuhrsystem (1) für einen Verbrennungsmotor, wobei das Kraftstoffzufuhrsystem Einspritzpumpen (5) zur Zufuhr von Kraftstoff zu den Einspritzdüsen (9), eine Hauptleitung (6) zum Richten von Kraftstoff in das Zufuhrsystem (1) und Abzweigleitungen (7), die zwischen der Hauptleitung (6) und den Einspritzpumpen (5) eingerichtet sind, um Kraftstoff von der Hauptleitung (6) zu den Einspritzpumpen (5) zu richten, umfasst, dadurch gekennzeichnet, dass das Kraftstoffzufuhrsystem eine Anordnung nach einem der vorhergehenden Ansprüche umfasst, wobei der Schwingungsdämpfer (11) der Anordnung in Verbindung mit der Hauptleitung (6) und/oder der Einspritzpumpe (5) eingerichtet ist.
EP06808043A 2005-12-22 2006-11-20 Anordnung zum dämpfen der druckschwingungen eines kraftstoffzufuhrsystems eines kolbenmotors Active EP1963661B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FI20055688A FI120214B (fi) 2005-12-22 2005-12-22 Järjestely mäntämoottorin polttoaineen syöttöjärjestelmän paineen värähtelyn vaimentamiseksi
PCT/FI2006/050502 WO2007071817A1 (en) 2005-12-22 2006-11-20 Arrangement for dampening the pressure vibration of a fuel feed system of a piston engine

Publications (3)

Publication Number Publication Date
EP1963661A1 EP1963661A1 (de) 2008-09-03
EP1963661A4 EP1963661A4 (de) 2010-12-22
EP1963661B1 true EP1963661B1 (de) 2012-03-14

Family

ID=35510766

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06808043A Active EP1963661B1 (de) 2005-12-22 2006-11-20 Anordnung zum dämpfen der druckschwingungen eines kraftstoffzufuhrsystems eines kolbenmotors

Country Status (4)

Country Link
EP (1) EP1963661B1 (de)
AT (1) ATE549507T1 (de)
FI (1) FI120214B (de)
WO (1) WO2007071817A1 (de)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010064185A1 (de) * 2010-12-27 2012-06-28 Robert Bosch Gmbh Kraftstoffeinspritzsystem für eine Brennkraftmaschine
DE102013206905A1 (de) * 2013-04-17 2014-10-23 Robert Bosch Gmbh Einrichtung zur Pulsationsdämpfung für eine Hochdruckpumpe

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4031239A1 (de) * 1990-10-04 1992-04-09 Kaltenberg Hans Georg Regelbarer druckstossdaempfer fuer fluessigkeitspumpen
DE19621897C1 (de) * 1996-05-31 1997-08-28 Man B & W Diesel Gmbh Einrichtung zum Ausbalancieren von Druckextremen in hydraulischen Systemen
DE10350941A1 (de) * 2003-10-31 2005-06-02 Hydac Technology Gmbh Vorrichtung zum Dämpfen von Druckstößen

Also Published As

Publication number Publication date
FI20055688A (fi) 2007-06-23
FI120214B (fi) 2009-07-31
FI20055688A0 (fi) 2005-12-22
WO2007071817A1 (en) 2007-06-28
EP1963661A4 (de) 2010-12-22
EP1963661A1 (de) 2008-09-03
ATE549507T1 (de) 2012-03-15

Similar Documents

Publication Publication Date Title
EP1342911B1 (de) Brennstoffversorgungssystem
US8556602B2 (en) Fuel pump with reduced seal wear for a direct injection system
EP1365142B1 (de) Hochdruckkraftstoffpumpe
CN101094988B (zh) 活塞泵、尤其是用于内燃机的燃料高压泵
EP0911512B1 (de) Hochdruck-Kraftstoffeinspritzpumpe mit Kraftstoffeinspritzung in den Motorzylinder
US6948479B1 (en) Inline pulsation damper system
JP2003035239A (ja) 高圧燃料供給ポンプ
EP1963661B1 (de) Anordnung zum dämpfen der druckschwingungen eines kraftstoffzufuhrsystems eines kolbenmotors
US6360722B1 (en) Fuel supply apparatus
JP2010007521A (ja) 燃料噴射ポンプ
US11035356B2 (en) High pressure pump and method for compressing a fluid
EP2110543B1 (de) Sicherheitsventil
KR102179627B1 (ko) 고압 연료 펌프
CN108779766B (zh) 具有流体阻尼器的高压泵
KR102139713B1 (ko) 펌프
AU7316898A (en) Cylinder injection high-pressure fuel pump
EP1805411B1 (de) Druckschwingungsdämpfer für das kraftstoffeinspritzsystem eines verbrennungsmotors
CN111512039B (zh) 高压燃料泵
CN111650974A (zh) 压力控制装置
JP6684174B2 (ja) 燃料供給装置
EP3283755B1 (de) Kraftstoffeinspritzsystem für einen kolbenmotor und verfahren zur dämpfung von druckfluktuationen
GB2544974B (en) An accumulator for use in a fuel line to attenuate pressure peaks
JP5338587B2 (ja) レギュレート弁
JPH11257189A (ja) 高圧燃料ポンプのフィード圧脈動低減装置

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: 20080609

AK Designated contracting states

Kind code of ref document: A1

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

A4 Supplementary search report drawn up and despatched

Effective date: 20101122

17Q First examination report despatched

Effective date: 20101206

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

DAX Request for extension of the european patent (deleted)
GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

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

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

REG Reference to a national code

Ref country code: CH

Ref legal event code: EP

Ref country code: AT

Ref legal event code: REF

Ref document number: 549507

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120315

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: 602006028220

Country of ref document: DE

Effective date: 20120510

REG Reference to a national code

Ref country code: NL

Ref legal event code: VDEP

Effective date: 20120314

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

Ref country code: LT

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

Effective date: 20120314

LTIE Lt: invalidation of european patent or patent extension

Effective date: 20120314

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: 20120314

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: 20120615

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: 20120314

REG Reference to a national code

Ref country code: AT

Ref legal event code: MK05

Ref document number: 549507

Country of ref document: AT

Kind code of ref document: T

Effective date: 20120314

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: 20120314

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

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: 20120314

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: 20120314

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: 20120714

Ref country code: BE

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: 20120314

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: 20120314

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: 20120314

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: 20120314

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: 20120314

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

Ref country code: PT

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

Effective date: 20120716

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: 20120314

PLBE No opposition filed within time limit

Free format text: ORIGINAL CODE: 0009261

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

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

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

Ref country code: DK

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

Effective date: 20120314

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: 20120314

Ref country code: AT

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: 20120314

26N No opposition filed

Effective date: 20121217

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

Ref country code: IT

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

Effective date: 20120314

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 602006028220

Country of ref document: DE

Effective date: 20121217

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

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: 20121130

Ref country code: LI

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

Effective date: 20121130

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: 20120614

REG Reference to a national code

Ref country code: IE

Ref legal event code: MM4A

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20130731

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

Ref country code: IE

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

Effective date: 20121120

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: 20120625

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: 20121130

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: 20121130

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: 20120314

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: 20121120

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: 20061120

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

Ref country code: GB

Payment date: 20231123

Year of fee payment: 18

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

Ref country code: DE

Payment date: 20231121

Year of fee payment: 18