EP2009255A1 - Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique - Google Patents

Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique Download PDF

Info

Publication number
EP2009255A1
EP2009255A1 EP08156892A EP08156892A EP2009255A1 EP 2009255 A1 EP2009255 A1 EP 2009255A1 EP 08156892 A EP08156892 A EP 08156892A EP 08156892 A EP08156892 A EP 08156892A EP 2009255 A1 EP2009255 A1 EP 2009255A1
Authority
EP
European Patent Office
Prior art keywords
valve
chamber
section
throttle
throttle valve
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP08156892A
Other languages
German (de)
English (en)
Other versions
EP2009255B1 (fr
Inventor
Calin Petru Itoafa
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.)
IHO Holding GmbH and Co KG
Original Assignee
Schaeffler KG
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 Schaeffler KG filed Critical Schaeffler KG
Publication of EP2009255A1 publication Critical patent/EP2009255A1/fr
Application granted granted Critical
Publication of EP2009255B1 publication Critical patent/EP2009255B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/16—Silencing impact; Reducing wear
    • 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

Definitions

  • the invention relates to a throttle valve for an internal combustion engine with electro-hydraulic valve control for the variable actuation of a spring-loaded in the closing direction gas exchange valve.
  • the valve control has a gas exchange valve remote drive side with a hydraulic donor chamber and a gas exchange valve near the driven side with a hydraulic slave chamber which communicates via a main flow path and a secondary flow path hydraulically with the donor chamber.
  • the throttle valve has a liftable in the direction of flow valve body, which is arranged between a stationary in the secondary flow path receiving chamber side stop surface and a stationary extending in the secondary flow path geberhat technologyen stop surface and the system releases at the acceptor side abutment surface bounded by the geberhunt facultyen stop surface inflow cross section and the plant at the encoder chamber side stop surface closes the inflow cross section except for a throttle cross section.
  • While hydraulic valve brakes are known in various structural configurations in the prior art, serving as a hydraulic valve brake throttle valve of the type mentioned is considered from the considered generic US 5,577,468 out.
  • the throttle valve used there in the secondary flow path is the throttled emptying of the slave chamber in the final closing phase of the gas exchange valve by then both the main flow and the inflow cross section in the secondary flow path are closed except for a remaining throttle cross-section through which the hydraulic fluid can escape from the slave chamber.
  • the throttle valve allows in the initial opening phase of the gas exchange valve in favor of its high opening acceleration to a low-throttle and thus fast filling of the slave chamber by then the inflow cross-section is already open before opening the main flow path.
  • the central component of the proposed in the cited document throttle valve is designed as a plate valve body, wherein the throttle cross-section is formed either by a central bore through the plate or by a local bead on the surface thereof.
  • the indentation provided on the plate surface as an alternative to the bore has the disadvantage that the plate is always in the correct orientation, i. must be mounted with the indentation opposite to the encoder chamber-side stop surface, since the opposite surface of the plate with significantly larger indentations, which form the flow cross section to the slave chamber, is provided. Consequently, the hydraulic valve brake function would not be given in a faulty mounting of the plate also.
  • the present invention is therefore the object of a throttle valve of the type mentioned in such a way that the disadvantages mentioned are eliminated by simple means. Accordingly, on the one hand, the function of the throttle valve as a hydraulic valve brake within the usual life expectancy for internal combustion engine can be reliably maintained and on the other hand, the manufacture of the throttle valve under high volume conditions and be cost effective in terms of incorrect assembly of the valve body.
  • the throttle cross-section should be formed by one or more bead-like recesses in the encoder chamber side stop surface.
  • the invention is based on the idea not to arrange the throttle cross-section in the valve body itself, but on the encoder chamber side stop surface in the form of bead-like, ie recessed recesses.
  • a significant advantage over the well known in the cited prior art hole in the plate is the significantly lower sensitivity of the moldings with regard to clogging or clogging with dirt particles, since the indentations also in contact with the valve body at the acceptor chamber side stop surface, i. are freewheeled by the then entering into the slave chamber hydraulic fluid when released inflow cross-section. Consequently, dirt particles that may accumulate during the final closing phase of the gas exchange valve in the recesses, be flushed out of the recesses during the subsequent opening phase of the gas exchange valve.
  • the throttle cross-section formed in the encoder chamber-side abutment surface has over the known plate with throttle cross-section on the surface especially the advantage that the valve body can be formed symmetrically and in the case of a plate with identical surfaces and thus can be mounted with any orientation.
  • the geometry of the valve body is freely selectable within wide limits, so that instead of the known plate, for example, a ball or a conical valve body can be used.
  • the indentations have a substantially circular segment-shaped cross section with a depth of 0.03 mm to 0.09 mm and preferably from 0.05 mm to 0.07 mm.
  • this design of the indentations is particularly advantageous if the indentations are made without cutting by embossing.
  • the throttle valve should be formed as the valve body and a valve housing with the stop surfaces extending therein comprehensive unit.
  • the valve housing is formed in two parts with a valve carrier and a socket, wherein the socket is inserted in a receiving chamber-side hollow cylindrical recess of the valve carrier.
  • the encoder chamber-side abutment surface are formed by a bottom of the recess and the receiving chamber side abutment surface by a bottom facing annular end face of the socket.
  • the bush for axial positional fixation in the valve housing should be provided with a collar which bears against an end face of the valve carrier facing the slave chamber.
  • a sufficient flow cross-section for the inflowing into the receiving chamber hydraulic fluid can be produced particularly easily produced by the valve body is formed as a flat plate and only partially covered when applied to the annular end face of the bushing limited by the annular end face flow cross-section.
  • the plate as a simple stamped part and on the other hand, the annular end face of the socket be made completely flat, so that despite the sealing effect in the contact region of these two parts required for a quick filling of the slave chamber flow cross section remains.
  • a preferred form of the plate substantially corresponds to a rectangle with opposite thereto adjacent circle segments.
  • FIG. 1 is an essential for the understanding of the invention section of an electro-hydraulic valve control 1 for the variable actuation of a spring-loaded in the closing direction gas exchange valve 2 disclosed. Shown is a mounted in a cylinder head of an internal combustion engine actuator housing 3 with a receiving bore 4, in which a slave housing 5 is screwed.
  • the slave housing 5 serves for the longitudinally movable mounting of an elongate working piston 6 of an otherwise known hydraulic valve clearance compensation device 7, which contacts the shaft end of the gas exchange valve 2.
  • valve clearance compensation device 7 via a connected to the lubricant circuit of the engine supply bore 8 and a tap hole 9 in the actuator housing 3, an outer annular groove 10 and with this - not visible here - connected inner annular groove 11 in the slave housing 5 and a transverse bore 12 in the working piston 6.
  • a co-moving with the working piston 6 slave piston 13 is limited with its gas exchange valve 2 end face 14 a hydraulic slave chamber 15 whose volume in the closed position of the gas exchange valve 2 shown here only the interior of a - here not shown in section - throttle valve 16 corresponds.
  • the known to be located on the gas exchange valve near output side of the valve control 1 slave chamber 15 is connected via a main flow path 17 in the form of holes 18 in the slave housing 5 and a Maustrompfad 19 in the form of the throttle valve 16 and a recess 4 for receiving bore 4 in the actuator housing 3 to a on the Gas monventilfernen drive side of the valve control 1 extending donor chamber 21 connected.
  • This is visible here only in the form of an inlet bore 22 in the actuator housing 3 and an annular chamber 23 between the actuator housing 3 and the slave housing 5.
  • the fixed throttle valve 16 in the secondary flow path serves as a hydraulic valve brake by the gas exchange valve 2 in its final closing phase, i. decelerates shortly before reaching its closed position to a set according to acoustic and mechanical criteria Aufsetz ancient.
  • the final closing phase begins at the time when the bores 18 in the slave housing 5 are being closed by the returning slave piston 13 and consequently the hydraulic fluid can only escape from the slave chamber 15 via the throttle valve 16.
  • the throttle valve 16 is formed as a structural unit and comprises a two-part valve housing 24 with a valve carrier 25 and a bushing 26 which is inserted in a slave chamber side hollow cylindrical recess 27 of the valve carrier 25, and a valve body 28 formed here as a flat plate, in the flow direction of the hydraulic fluid between a receiving chamber-side stop surface 29 and a geberhunt principleen stop surface 30 is arranged to be movable.
  • the encoder chamber side abutment surface 30 are formed by a bottom 31 of the recess 27 and the receiving chamber side abutment surface 29 by a bottom 31 facing annular end face 32 of the bushing 26.
  • the sleeve 26 is provided with a collar 33 which rests against one of the slave chamber 15 facing end face 34 of the valve carrier 25.
  • the valve carrier 25 also has a radially outwardly directed collar 35, so that the Throttle valve 16, as in FIG. 1 recognizable, between the gas exchange valve remote end face 36 of the slave housing 5 and a shoulder 37 of the receiving bore 4 can be clamped.
  • FIG. 2 illustrated abutment position of the plate 28, in which this abuts the receiving chamber-side abutment surface 29, a limited by the encoder chamber-side stop surface 30 inlet cross-section 38 is released.
  • the hydraulic fluid in this position of the plate 28 largely unthrottled to flow into the slave chamber 15 by the plate 28 only partially obscured by the annular end face 32 of the sleeve 26 flow cross-section 39.
  • the plate 28 has a shape corresponding to a rectangle with opposite thereto adjoining and flush with the annular end face 32 flush circle segments.
  • FIG. 3 illustrated bottom view of the valve carrier 25 is formed by the bottom 31 of the recess 27 formed geberhunt worne stop surface 30 with two diametrically opposite bead-like indentations 40.
  • FIG. 4 As can be seen, in the case of the voltage applied to the encoder chamber side abutment surface 30 plate 28 of the inflow cross section 38 is closed in the valve carrier 25 to a throttle cross section formed by the indentations 40. This state occurs at closing gas exchange valve 2, wherein the hydraulic means located in the slave chamber 15 is initially mainly displaced via the bores 18 in the slave housing 5 and then, when the holes 18 are closed by the slave piston 13, only by the indentations 40 in the Donor chamber 21 can escape with a corresponding delay of the gas exchange valve 2.
  • the indentations 40 produced without cutting by embossing the valve carrier 25 have a substantially circular segment-shaped cross section with a depth of only in view of a long service life of the embossing tool 0.05mm to 0.07mm.
  • corresponding throttle cross section may be formed differently from the embodiment of the throttle valve 16 shown here by only one or more than two indentations 40, which may also have a non-circular segmental cross-section and / or one of have significantly different depths in the specified range.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Check Valves (AREA)
EP08156892A 2007-06-29 2008-05-26 Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique Not-in-force EP2009255B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007030215A DE102007030215A1 (de) 2007-06-29 2007-06-29 Drosselventil für eine Brennkraftmaschine mit elektrohydraulischer Ventilsteuerung

Publications (2)

Publication Number Publication Date
EP2009255A1 true EP2009255A1 (fr) 2008-12-31
EP2009255B1 EP2009255B1 (fr) 2010-09-15

Family

ID=39758780

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08156892A Not-in-force EP2009255B1 (fr) 2007-06-29 2008-05-26 Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique

Country Status (3)

Country Link
EP (1) EP2009255B1 (fr)
CN (1) CN201326424Y (fr)
DE (2) DE102007030215A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012110120A1 (fr) * 2011-02-18 2012-08-23 Schaeffler Technologies AG & Co. KG Mécanisme de distribution hydraulique d'un moteur à combustion interne
WO2015117603A1 (fr) * 2014-02-04 2015-08-13 Schaeffler Technologies AG & Co. KG Actionneur d'une commande de soupape d'échange de gaz électrohydraulique d'un moteur à combustion interne

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010048135A1 (de) 2010-10-11 2012-04-12 Schaeffler Technologies Gmbh & Co. Kg Aktuator eines elektrohydraulischen Gaswechselventiltriebs einer Brennkraftmaschine
DE102019104459B4 (de) * 2019-02-21 2023-01-05 Schaeffler Technologies AG & Co. KG Aktuator eines hydraulischen Ventiltriebs einer Brennkraftmaschine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5577468A (en) 1991-11-29 1996-11-26 Caterpillar Inc. Engine valve seating velocity hydraulic snubber
US6192841B1 (en) * 1997-11-21 2001-02-27 Diesel Engine Retarders, Inc. Device to limit valve seating velocities in limited lost motion tappets
US6302370B1 (en) * 1998-08-26 2001-10-16 Diesel Engine Retarders, Inc. Valve seating control device with variable area orifice
US6769385B1 (en) * 2003-03-12 2004-08-03 Caterpillar Inc System for controlling engine valve seating velocity
US20050034691A1 (en) * 2003-08-15 2005-02-17 Chang David Yu-Zhang Engine valve actuation system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5577468A (en) 1991-11-29 1996-11-26 Caterpillar Inc. Engine valve seating velocity hydraulic snubber
US6192841B1 (en) * 1997-11-21 2001-02-27 Diesel Engine Retarders, Inc. Device to limit valve seating velocities in limited lost motion tappets
US6302370B1 (en) * 1998-08-26 2001-10-16 Diesel Engine Retarders, Inc. Valve seating control device with variable area orifice
US6769385B1 (en) * 2003-03-12 2004-08-03 Caterpillar Inc System for controlling engine valve seating velocity
US20050034691A1 (en) * 2003-08-15 2005-02-17 Chang David Yu-Zhang Engine valve actuation system

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2012110120A1 (fr) * 2011-02-18 2012-08-23 Schaeffler Technologies AG & Co. KG Mécanisme de distribution hydraulique d'un moteur à combustion interne
US9267397B2 (en) 2011-02-18 2016-02-23 Schaeffler Technologies AG & Co. KG Hydraulic valve train of an internal combustion engine
WO2015117603A1 (fr) * 2014-02-04 2015-08-13 Schaeffler Technologies AG & Co. KG Actionneur d'une commande de soupape d'échange de gaz électrohydraulique d'un moteur à combustion interne
KR20160117465A (ko) * 2014-02-04 2016-10-10 섀플러 테크놀로지스 아게 운트 코. 카게 내연 기관의 전기 유압식 가스 교환 밸브 트레인용 액추에이터
US9920664B2 (en) 2014-02-04 2018-03-20 Schaeffler Technologies AG & Co. KG Actuator for an electrohydraulic gas-exchange valve train of a combustion engine

Also Published As

Publication number Publication date
CN201326424Y (zh) 2009-10-14
EP2009255B1 (fr) 2010-09-15
DE102007030215A1 (de) 2009-01-08
DE502008001290D1 (de) 2010-10-28

Similar Documents

Publication Publication Date Title
EP1579137B1 (fr) Soupape pour la regulation d'un fluide
EP2193282B1 (fr) Elément hydraulique
EP2246601B1 (fr) Soupape hydraulique électromagnétique
DE102005014100B4 (de) Elektromagnetventil, insbesondere für schlupfgeregelte Kraftfahrzeugbremsanlagen
DE10321413B4 (de) Elektromagnetisch betätigbares Ventil
DE102011076784B4 (de) Einlassventil für eine Fluidpumpe und Montageverfahren für ein Einlassventil für eine Fluidpumpe
EP3551512B1 (fr) Arrangement de maître-cylindre avec un capteur de position et arrangement d'étanchéité
DE102015111175A1 (de) Hydraulikventil und Pleuel mit einem Hydraulikventil
WO2008086963A1 (fr) Dispositif de fermeture pour récipient sous pression de générateur de gaz basse température, pouvant être rempli de gaz sous pression
EP3161280A1 (fr) Élément de support
EP2009255B1 (fr) Valve d'étranglement pour un moteur à combustion interne doté d'une commande de soupape hydroélectrique
EP1087109B1 (fr) Actionneur de soupape de moteur à combustion interne
DE102016107986A1 (de) Hydraulikventil und Pleuel mit einem Hydraulikventil
EP1595764B1 (fr) Vanne de réduction de pression
DE102017110380A1 (de) Ablassventil für hohe Drücke
DE102009049246A1 (de) Kupplungspedalkraftunterstützungseinrichtung
DE102004048071A1 (de) Ventiltrieb für ein nockenbetätigtes Hubventil
EP2108081B1 (fr) Fixation de douille élastique
WO2020114560A1 (fr) Soupape et dispositif de régulation de la pression d'un fluide dans une transmission de véhicule muni d'une soupape
EP1468171A1 (fr) Dispositif pour commander une section d'ouverture d'un cylindre de combustion d'un moteur a combustion interne
EP1837567B1 (fr) Obturateur de sécurité automatique pour conduites de gaz
DE102016219722A1 (de) Steuerbares Saugventil für eine Hochdruckpumpe, Hochdruckpumpe
WO2008116703A1 (fr) Mécanisme de distribution d'un moteur à combustion interne
EP1706301B1 (fr) Soupape commandant des fluides avec possibilite de compensation de pression integree
DE102016208973A1 (de) Elektromagnetisch betätigbares Saugventil und Kraftstoff-Hochdruckpumpe

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: 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

17P Request for examination filed

Effective date: 20090630

17Q First examination report despatched

Effective date: 20090731

AKX Designation fees paid

Designated state(s): DE FR GB IT SE

GRAP Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOSNIGR1

GRAS Grant fee paid

Free format text: ORIGINAL CODE: EPIDOSNIGR3

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): DE FR GB IT SE

REG Reference to a national code

Ref country code: GB

Ref legal event code: FG4D

Free format text: NOT ENGLISH

REF Corresponds to:

Ref document number: 502008001290

Country of ref document: DE

Date of ref document: 20101028

Kind code of ref document: P

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: 20100915

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: 20110616

REG Reference to a national code

Ref country code: DE

Ref legal event code: R097

Ref document number: 502008001290

Country of ref document: DE

Effective date: 20110616

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502008001290

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

Ref country code: DE

Ref legal event code: R081

Ref document number: 502008001290

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20120828

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502008001290

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

Ref country code: DE

Ref legal event code: R081

Ref document number: 502008001290

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES AG & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20140218

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

Ref country code: GB

Payment date: 20140530

Year of fee payment: 7

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

Ref country code: IT

Payment date: 20140527

Year of fee payment: 7

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

Ref country code: DE

Payment date: 20140731

Year of fee payment: 7

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

Ref country code: FR

Payment date: 20140528

Year of fee payment: 7

REG Reference to a national code

Ref country code: DE

Ref legal event code: R081

Ref document number: 502008001290

Country of ref document: DE

Owner name: SCHAEFFLER TECHNOLOGIES AG & CO. KG, DE

Free format text: FORMER OWNER: SCHAEFFLER TECHNOLOGIES GMBH & CO. KG, 91074 HERZOGENAURACH, DE

Effective date: 20150223

REG Reference to a national code

Ref country code: DE

Ref legal event code: R119

Ref document number: 502008001290

Country of ref document: DE

GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20150526

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

Ref country code: IT

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

Effective date: 20150526

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20160129

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: 20151201

Ref country code: GB

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

Effective date: 20150526

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: 20150601

P01 Opt-out of the competence of the unified patent court (upc) registered

Effective date: 20230522