EP1485585B1 - Dispositif de commande de soupapes de transfert de gaz - Google Patents

Dispositif de commande de soupapes de transfert de gaz Download PDF

Info

Publication number
EP1485585B1
EP1485585B1 EP03704223A EP03704223A EP1485585B1 EP 1485585 B1 EP1485585 B1 EP 1485585B1 EP 03704223 A EP03704223 A EP 03704223A EP 03704223 A EP03704223 A EP 03704223A EP 1485585 B1 EP1485585 B1 EP 1485585B1
Authority
EP
European Patent Office
Prior art keywords
valve
pressure
gas exchange
lower pressure
pressure space
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.)
Expired - Lifetime
Application number
EP03704223A
Other languages
German (de)
English (en)
Other versions
EP1485585A1 (fr
Inventor
Thomas Ludwig
Udo Diehl
Bernd Rosenau
Simon Kieser
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 EP1485585A1 publication Critical patent/EP1485585A1/fr
Application granted granted Critical
Publication of EP1485585B1 publication Critical patent/EP1485585B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L9/00—Valve-gear or valve arrangements actuated non-mechanically
    • F01L9/10—Valve-gear or valve arrangements actuated non-mechanically by fluid means, e.g. hydraulic
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
    • F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
    • F01L1/3442—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear using hydraulic chambers with variable volume to transmit the rotating force
    • F01L2001/34423—Details relating to the hydraulic feeding circuit
    • F01L2001/34446—Fluid accumulators for the feeding circuit

Definitions

  • the invention relates to a device for controlling a gas exchange valve in internal combustion engines according to the preamble of claim 1.
  • the upper Working chamber is additionally connected via a likewise designed as a 2/2-way solenoid valve with spring return second control valve to a receding in a fluid reservoir return line.
  • a likewise designed as a 2/2-way solenoid valve with spring return second control valve to a receding in a fluid reservoir return line.
  • the second control valve is closed and the first control valve is opened.
  • the speed of the valve lift depends on the level of fluid or hydraulic pressure delivered by the pressure supply unit.
  • To close the gas exchange valve both control valves are switched so that the upper working chamber is closed off on the one hand by the pressure supply device and on the other hand connected to the return line.
  • the actuator piston is displaced upwards by the pressure prevailing in the lower working chamber and closes the gas exchange valve.
  • a Notschegafeder is provided, which is used as a compression spring in the lower working space and on the Actuator piston supported.
  • the Notschegafeder is dimensioned so that it overcomes the friction moments in the gas exchange valve and the valve actuator under all conditions and the actuator piston from each of his Move displacement positions out into the closed position is able to move.
  • the device according to the invention for controlling a gas exchange valve with the features of claim 1 has the advantage that with similar functionality, the device per gas exchange valve requires only a single electrical control valve. With the saving of one control valve per gas exchange valve not only reduces the number of control valves by half, but also halves the number of output stages required in the control unit for controlling the control valves. This results in a considerable savings potential in the production costs, which is e.g. in a four-cylinder engine with sixteen valves, eight control valves and eight output stages makes. In addition, the electrical energy requirement and the electrical wiring costs are reduced. The smaller number of control valves reduces the installation volume and reduces the probability of failure of the device. Overall, the device is less complex than the known one.
  • the control valve is designed as an electrically operated directional control valve.
  • the directional control valve is a 2/2-way solenoid valve.
  • a variable stroke of the gas exchange valve can be achieved only by short opening times by aborting the valve lift.
  • only the opening time and the closing time of the gas exchange valve can be specified.
  • the 2/2-way solenoid valve is clocked switched according to a preferred embodiment of the invention, wherein preferably the clock frequency is selected in response to the desired valve lift so that at a desired valve travel adjustment of the Control piston on the one hand and on the other hand via the 2/2-way solenoid valve on the other hand flowing fluid flows are the same size.
  • the proportional valve is controlled so that at a desired valve lift corresponding adjustment of the actuating piston via the throttle on the one hand and the proportional valve on the other hand flowing fluid flows are equal and thus sets a balance of power between the upper pressure chamber and the lower pressure chamber.
  • the device shown in block diagram in Fig. 1 is used to control gas exchange valves 10 in internal combustion engines.
  • the internal combustion engine or the internal combustion engine for a motor vehicle usually has four or more combustion cylinders, of which in Fig. 1 a detail of a cylinder head 11 of a combustion cylinder is shown.
  • combustion chamber 12 In the combustion cylinder a closed by the cylinder head 11 combustion chamber 12 is formed, which has at least one inlet cross section and an outlet cross section, which are each controlled by a gas exchange valve 10.
  • Each gas exchange valve 10 has, in a known manner, a valve member 13 with an axially displaceable on one guided valve stem 131 seated valve closing body 132, which cooperates with a inlet or outlet cross-section in the cylinder head 11 enclosing the valve seat 14.
  • the valve closing body 132 lifts off from the valve seat 14 or settles sealingly thereon.
  • each gas exchange valve 10 is assigned a hydraulic valve actuator 16, also called an actuator.
  • the hydraulic valve actuator 16 and a hydraulic output 162 having a hydraulic valve actuator 16 comprises a double-acting cylinder 17, a throttle 18 and a control valve 19.
  • the cylinder 17 has in a known manner a cylinder housing 20 and an axially displaceable guided therein and with the valve stem 131 of the associated gas exchange valve 10 coupled actuating piston 21, which divides the interior of the cylinder housing 20 in an upper pressure chamber 22 and a lower pressure chamber 23.
  • the upper pressure chamber 22 is connected directly and the lower pressure chamber 23 via the throttle 18 to the hydraulic input 161.
  • the control valve which is formed in FIG. 1 as a 2/2-way solenoid valve 24, is connected on the one hand to the lower pressure chamber 23 and on the other hand to the hydraulic output 162.
  • a relief line is connected, which is designed here as a fluid return line 25.
  • All valve actuators 16 are provided by a pressure supply device 25 with high-pressure fluid, preferably hydraulic oil, for which the hydraulic input 161 of each valve actuator 16 is connected to a fluid outlet 251 of the pressure supply device 25.
  • the pressure supply device 25 comprises a fluid reservoir 26, in which the fluid return line 27 opens, a high-pressure pump 28, the fluid from the fluid reservoir 26 sucks and promotes high pressure to the fluid outlet 251 of the pressure supply means 25, and connected to the fluid outlet 251 high-pressure accumulator 29, as Energy storage and pulsation damper is used. Between the output of the high-pressure pump 28 and the fluid outlet 251 of the pressure supply device 25 is still a check valve 30 is arranged with the pump outlet facing blocking direction.
  • valve control device The operation of the valve control device is as follows:
  • the pressure supply device 25 supplies the double-acting cylinder 17 with pressurized fluid.
  • the pressure in the upper pressure chamber 22 and in the lower pressure chamber 23 is equal. Since the coupling of the valve stem 131 the upper pressure chamber 22 limiting Druckbeaufschlagungs- or effective area of the actuating piston 21 is greater than the lower pressure chamber 23 limiting Druckbeaufschlagungs- or effective area, in the lower pressure chamber 23 acting as a return spring compression spring 31 is arranged, on the one hand on the cylinder housing 20 and on the other hand on the actuating piston 21 is supported.
  • the compression spring 31 is dimensioned so that it holds the adjusting piston 21 in its in Fig.
  • the pressure spring 31 also fulfills the requirement for resetting the gas exchange valve 10 in its closed state during prolonged standstill of the internal combustion engine or in the event of failure of the pressure supply device 25 as an emergency closing spring.
  • the 2/2-way solenoid valve 24 is switched from its switching position shown in FIG. 1, so that the lower pressure chamber 23 is relieved by its connection to the fluid return line 27.
  • the control piston 21 moves down and opens the gas exchange valve 10.
  • the 2/2-way solenoid valve 24 is reset and thus the lower pressure chamber 23 separated from the fluid return line 27. Via the throttle 18 high-pressure fluid flows into the lower pressure chamber 23, and the actuating piston 21 is returned with support by the compression spring 31 in its the gas exchange valve 10 closing top dead center.
  • the solenoid valve 24 is controlled clocked.
  • the clock frequency is selected as a function of the desired valve lift, in such a way that at a desired valve travel adjustment of the actuating piston 21 via the throttle 18 on the one hand and the 2/2-way solenoid valve 24 on the other flowing fluid flows are the same size and thus adjusts an equilibrium of forces on the actuating piston 21 between the upper pressure chamber 22 and the lower pressure chamber 23.
  • the double-acting working cylinder 17 'shown schematically in FIG. 2 can be inserted into the valve control device 15 instead of the working cylinder 17 shown in FIG.
  • the working cylinder 17 ' is modified insofar as the compression spring 31 is omitted and the actuating piston 21 is formed as a stepped piston 32 with the upper pressure chamber 22 limiting active surface 321 and the lower pressure chamber 23 limiting effective surface 322.
  • With equal pressure in the upper pressure chamber 22 and the lower pressure chamber 23 of the stepped piston 32 is due to the lower pressure chamber 23 limiting larger effective area 322 safely moved to its top dead center and reliable in this held, so that the gas exchange valve 10 is reliably held in its closed position.
  • a same compression spring as the compression spring 31 can be provided in Fig. 1, but which can be dimensioned much weaker and only the holding of the stepped piston 32 must ensure in its top dead center.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)

Abstract

Dispositif de commande de soupapes de transfert de gaz, qui comporte au moins un actionneur (16) de soupape associé à une soupape de transfert de gaz (10) et un dispositif d'alimentation en pression (25) qui alimente l'actionneur (16) de soupape en fluide sous haute pression. L'actionneur (16) de soupape comporte un cylindre de travail (17) pourvu d'un piston de commande (21) couplé à la soupape de transfert de gaz (10) et définissant une chambre supérieure (22) à fluide sous pression pour la fermeture de la soupape et une chambre inférieure (23) à fluide sous pression pour l'ouverture de la soupape, ainsi qu'une soupape pilote (19) destinée à réguler la pression hydraulique dans les chambres (22, 23) à fluide sous pression. Selon la présente invention, pour réduire les coûts de fabrication et la consommation en énergie électrique du dispositif, la chambre supérieure (22) à fluide sous pression est reliée directement, et la chambre inférieure (23) à fluide sous pression par l'intermédiaire d'un étranglement (18), au dispositif d'alimentation en pression (25), et la soupape pilote (19) est reliée à la chambre inférieure (23) à fluide sous pression et à une conduite de décharge (27). Selon sa position de commutation, la soupape pilote (19) relie en outre la chambre inférieure (23) à fluide sous pression à la conduite de décharge (27) ou l'isole de ladite conduite.

Claims (11)

  1. Dispositif de commande des soupapes d'échange de gaz dans un moteur à combustion interne comprenant au moins un actionneur de soupape (16) associé à une soupape d'échange de gaz (10), cet actionneur comprenant un vérin hydraulique (17) à double effet couplé à la soupape d'échange de gaz (10), un piston d'actionnement (21) délimitant une chambre de pression supérieure (22) pour actionner la soupape d'échange de gaz (10) dans le sens de l'ouverture et une chambre de pression inférieure (23) pour actionner la soupape d'échange de gaz (10) dans le sens de la fermeture ainsi qu'une vanne de commande (19) pour commander la pression hydraulique dans les chambres de pression (22, 23) et
    une installation d'alimentation en pression (25) qui fournit du fluide à haute pression aux chambres de pression (22, 23) du cylindre de travail (17),
    caractérisé en ce que
    la chambre de pression supérieure (22) est reliée directement à l'installation d'alimentation en pression (25) alors que la chambre de pression inférieure (23) est reliée à celle-ci par un organe d'étranglement (18) et
    la vanne de commande (19) est reliée d'un côté à la chambre de pression inférieure (23) et de l'autre à une conduite de décharge (27) et suivant la position de commutation, elle ouvre ou ferme la liaison entre la chambre de pression inférieure (23) et la conduite de décharge (27).
  2. Dispositif selon la revendication 1,
    caractérisé en ce que
    la vanne de commande (19) est un distributeur à tiroir à commande électrique.
  3. Dispositif selon la revendication 1,
    caractérisé en ce que
    le distributeur à tiroir est une électrovanne à tiroir à 2/2 voies (24).
  4. Dispositif selon la revendication 3,
    caractérisé en ce que
    l'électrovanne à 2/2 voies (24) est commutée de manière cadencée pour réaliser une course de vanne variable.
  5. Dispositif selon la revendication 4,
    caractérisé en ce que
    la fréquence est réglée en fonction de la course souhaitée pour la soupape et pour une course de réglage correspondant à une course de soupape souhaitée du piston d'actionnement (21), les débits de fluide sont identiques d'une part à travers l'organe d'étranglement (18) et d'autre part à travers la vanne à tiroir à 2/2 voies (24).
  6. Dispositif selon la revendication 2,
    caractérisé en ce que
    le distributeur à tiroir à commande électrique est une vanne proportionnelle commandée pour réaliser une course de vanne variable, de façon que pour la course de réglage du piston d'actionnement (21), correspondant à la course de vanne souhaitée, les débits de fluide d'une part dans l'organe d'étranglement (18) et d'autre part dans la vanne proportionnelle sont identiques.
  7. Dispositif selon l'une des revendications 1 à 6,
    caractérisé en ce que
    le vérin (17) comporte un ressort de rappel (31) sollicitant le piston d'actionnement (21) contre la pression régnant dans la chambre de pression supérieure (22).
  8. Dispositif selon la revendication 7,
    caractérisé en ce que
    le ressort de rappel est un ressort de compression (31) logé dans la chambre de pression inférieure (23), ce ressort s'appuyant par une extrémité dans la chambre de pression inférieure (23) et par l'autre, contre le piston d'actionnement (21).
  9. Dispositif selon l'une des revendications 1 à 8,
    caractérisé en ce que
    le piston d'actionnement (21) a une surface exposée à la pression (321) délimitant la chambre de pression supérieure (22) et une surface d'application de pression (322) délimitant la chambre de pression inférieure (23) et
    la surface inférieure d'application de pression (322) est plus grande que la surface supérieure d'application de pression (321).
  10. Dispositif selon la revendication 9,
    caractérisé en ce que
    le piston d'actionnement (21) est un piston étagé (32).
  11. Dispositif selon l'une des revendications 1 à 10,
    caractérisé en ce que
    la conduite de décharge est une conduite de retour de fluide (27) débouchant dans le réservoir de liquide (26) de l'installation d'alimentation en pression (25).
EP03704223A 2002-03-08 2003-01-17 Dispositif de commande de soupapes de transfert de gaz Expired - Lifetime EP1485585B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10210334 2002-03-08
DE10210334A DE10210334A1 (de) 2002-03-08 2002-03-08 Vorrichtung zur Steuerung eines Gaswechselventils
PCT/DE2003/000121 WO2003076772A1 (fr) 2002-03-08 2003-01-17 Dispositif de commande de soupapes de transfert de gaz

Publications (2)

Publication Number Publication Date
EP1485585A1 EP1485585A1 (fr) 2004-12-15
EP1485585B1 true EP1485585B1 (fr) 2008-01-30

Family

ID=27762810

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03704223A Expired - Lifetime EP1485585B1 (fr) 2002-03-08 2003-01-17 Dispositif de commande de soupapes de transfert de gaz

Country Status (5)

Country Link
US (1) US6857618B2 (fr)
EP (1) EP1485585B1 (fr)
JP (1) JP4290563B2 (fr)
DE (2) DE10210334A1 (fr)
WO (1) WO2003076772A1 (fr)

Families Citing this family (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8597849B2 (en) * 2005-08-30 2013-12-03 GM Global Technology Operations LLC Pressure activated shut-off valve
CN101509404B (zh) * 2008-02-15 2011-05-18 蔡学功 可变气门系统
DE102010024723B4 (de) * 2010-06-23 2014-02-13 Samson Aktiengesellschaft Pneumatischer Stellantrieb und Verfahren zum Betreiben des pneumatischen Stellantriebs
JP5768186B2 (ja) * 2012-05-31 2015-08-26 株式会社フジキン ビルドダウン方式流量モニタ付流量制御装置及びこれを用いたモニタ付流量制御方法。
US10202968B2 (en) * 2012-08-30 2019-02-12 Illinois Tool Works Inc. Proportional air flow delivery control for a compressor
JP6187434B2 (ja) 2014-11-14 2017-08-30 トヨタ自動車株式会社 燃料電池システム、移動体及び制御方法
EP3406866A1 (fr) * 2017-05-22 2018-11-28 EMPA Eidgenössische Materialprüfungs- und Forschungsanstalt Entraînement hydraulique destiné à accélérer ou ralentir dynamiquement des composants en mouvement
TWI684719B (zh) * 2019-02-27 2020-02-11 陳文彬 流體控制裝置

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59170414A (ja) * 1983-03-18 1984-09-26 Nissan Motor Co Ltd 油圧式弁駆動装置
JPS6040711A (ja) 1983-08-12 1985-03-04 Yanmar Diesel Engine Co Ltd 動弁装置
JPS63176610A (ja) * 1987-01-19 1988-07-20 Honda Motor Co Ltd 吸・排気弁の制御装置
JPH086571B2 (ja) * 1989-09-08 1996-01-24 本田技研工業株式会社 内燃機関の動弁装置
US5255641A (en) * 1991-06-24 1993-10-26 Ford Motor Company Variable engine valve control system
US5572961A (en) * 1995-04-05 1996-11-12 Ford Motor Company Balancing valve motion in an electrohydraulic camless valvetrain
DE19826047A1 (de) * 1998-06-12 1999-12-16 Bosch Gmbh Robert Vorrichtung zur Steuerung eines Gaswechselventils für Brennkraftmaschinen
GR1003820B (el) 2001-05-18 2002-02-21 Συστημα ηλεκτρουδραυλικης κινησης βαλβιδων
DE10127205A1 (de) * 2001-06-05 2002-09-05 Bosch Gmbh Robert Nockenwellenlose Steuerung eines Gaswechselventils einer Brennkraftmaschine

Also Published As

Publication number Publication date
US20040089829A1 (en) 2004-05-13
DE10210334A1 (de) 2003-09-18
DE50309104D1 (de) 2008-03-20
JP4290563B2 (ja) 2009-07-08
US6857618B2 (en) 2005-02-22
EP1485585A1 (fr) 2004-12-15
WO2003076772A1 (fr) 2003-09-18
JP2005519225A (ja) 2005-06-30

Similar Documents

Publication Publication Date Title
DE19853355C1 (de) Hydraulisch steuerbares Hubventil
DE69506219T2 (de) Hydraulisch betätigte ventilanordnung
EP1029158B1 (fr) Dispositif de commande d'une valve d'echange gazeux destine a des moteurs a combustion interne
DE19621719C1 (de) Hydraulische Ventilsteuervorrichtung
EP1001143A2 (fr) Commande de soupape pour soupapes d'admission et d'échappement de moteur à combustion interne
DE102013112751A1 (de) Kraftstoffinjektor
AT513603B1 (de) Hubkolbenkompressor mit Kapazitätsregelung
WO2001029395A2 (fr) Dispositif de commande hydraulique, en particulier pour un injecteur
DE10155669A1 (de) Vorrichtung zur Steuerung mindestens eines Gaswechselventils
EP1485585B1 (fr) Dispositif de commande de soupapes de transfert de gaz
EP0845398B1 (fr) Régulateur de pression pour installations de production d'air comprimé dans des véhicules
EP2501968B1 (fr) Ensemble soupape piloté à commutation à plusieurs étages
EP1029156A1 (fr) Procede de commande d'une valve d'echange gazeux de moteurs a combustion interne
DE19710814C1 (de) Druckluftaufbereitungseinrichtung für Druckluftbeschaffungsanlagen auf Kraftfahrzeugen
DE102004022447A1 (de) Hydraulischer Steller und Verfahren zum Betreiben eines hydraulischen Stellers
EP1481148B1 (fr) Dispositif de commande de soupape de changement des gaz
EP0975856A1 (fr) Dispositif de commande hydraulique pour au moins une soupape de cylindre
DE102013112752A1 (de) Kraftstoffinjektor
DE3239119A1 (de) Ventileinrichtung zur steuerung von druckmittel
EP1521902B1 (fr) Dispositif pour commander des soupapes de changement des gaz
EP1440224B1 (fr) Dispositif de commande de soupapes de changement des gaz
DE4232573A1 (de) In richtung auf einen brennraum schliessendes ladungswechselventil fuer eine brennkraftmaschine
WO2003027449A1 (fr) Dispositif de commande d'une section d'ouverture dans un cylindre de combustion d'un moteur a combustion interne
DE10140528A1 (de) Vorrichtung zur Steuerung von Gaswechselventilen
DE102006036660B4 (de) Hubkolbenbrennkraftmaschine mit Motorbremsung durch Öffnen der Auslassventile

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: 20041008

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 IT LI LU MC NL PT SE SI SK TR

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

RBV Designated contracting states (corrected)

Designated state(s): DE FR IT

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): DE FR IT

REF Corresponds to:

Ref document number: 50309104

Country of ref document: DE

Date of ref document: 20080320

Kind code of ref document: P

EN Fr: translation not filed
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: 20081031

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

Effective date: 20081121

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: 20080130

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

Ref country code: DE

Payment date: 20090327

Year of fee payment: 7

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: 20100803