EP0911492B1 - Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne - Google Patents

Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne Download PDF

Info

Publication number
EP0911492B1
EP0911492B1 EP98890293A EP98890293A EP0911492B1 EP 0911492 B1 EP0911492 B1 EP 0911492B1 EP 98890293 A EP98890293 A EP 98890293A EP 98890293 A EP98890293 A EP 98890293A EP 0911492 B1 EP0911492 B1 EP 0911492B1
Authority
EP
European Patent Office
Prior art keywords
camshaft
driving member
housing
axis
pumping member
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 - Fee Related
Application number
EP98890293A
Other languages
German (de)
English (en)
Other versions
EP0911492A1 (fr
Inventor
Siegfried Heer
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.)
TCG Unitech AG
Original Assignee
TCG Unitech AG
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 TCG Unitech AG filed Critical TCG Unitech AG
Publication of EP0911492A1 publication Critical patent/EP0911492A1/fr
Application granted granted Critical
Publication of EP0911492B1 publication Critical patent/EP0911492B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related 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
    • 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
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/21—Elements
    • Y10T74/2101—Cams
    • Y10T74/2102—Adjustable

Definitions

  • the invention relates to a device for adjusting a camshaft Internal combustion engine according to the preamble of claim 1.
  • the camshaft one Internal combustion engine is usually driven by a sprocket connected to the crankshaft is connected via a drive chain, or one designed as a pulley Drive wheel connected to the crankshaft via a toothed belt stands, driven.
  • DE 41 10 088 C1 and DE 39 29 619 A1 are adjustment devices known in which between one connected to the camshaft Component and a component connected to the drive wheel an adjusting element is provided which has two helical teeth, which with corresponding toothing of the camshaft or the drive wheel in Stand by.
  • An axial displacement of this adjusting element can Rotation of the camshaft relative to the drive wheel can be caused.
  • a The possibility of axial displacement of the adjusting element is actuation by a hydraulic piston, which depends on the required adjustment is activated.
  • the disadvantage of this solution is that to achieve the necessary Forces a relatively large hydraulic piston is required, which is a represents great construction effort.
  • an electrical adjustment device is known from DE 41 01 676 A1, in which an electric motor is provided which has a thread play Adjustment element moves.
  • the adjustment element is essentially with camshaft speed, must be between the electric motor and the Adjustment element an axial thrust bearing can be provided, which the relative movement between the sales-resistant and the rotating component.
  • This Axial thrust bearing is practically throughout the known solution Engine operation is burdened by the acting between the drive wheel and camshaft Torsional moments always have an axial force on the Adjustment element is exercised.
  • This thrust bearing is therefore a critical one Component that limits the life of the engine.
  • EP 363 600 A shows an adjusting device for a camshaft has hydraulic transmission element with two vane wheels, of which one is arranged in a slider that is displaceable relative to the housing is. Such a device is due to a variety of sealing surfaces complex and prone to errors. There is also space due to the axial offset saving construction is difficult.
  • the object of the present invention is to avoid the disadvantages and a simple, reliable and compact device for adjusting the camshaft to accomplish.
  • the adjustment should be carried out with a minimal supply from external energy.
  • this object is characterized by the features of the partially solved by claim 1.
  • the relative rotation of the camshaft in Reference to the drive wheel is made by the drive part to the camshaft Work done, the driving part hydraulically by a pumping part pumped working fluid is driven.
  • the pump part is driven via the camshaft drive wheel.
  • a particularly simple control of the relative rotation of the camshaft with respect to the Driving wheel can be reached when controlling the flow rate and / or the pressure of the working fluid conveyed from the pump part to the driving part by moving the common housing is transverse to the direction of the camshaft axis.
  • By the shift of the housing are the displacement volumes in the pump section and in the drive section enlarged or reduced to each other, causing a phase shift between the Camshaft and the drive wheel is done.
  • the maximum phase shift is determined by limited a rotation stop between the drive wheel and the camshaft.
  • the hydraulic Adjusting element has a housing in which a pump part coaxial with the camshaft Vane impeller is arranged, which is also a vane impeller coaxial with the camshaft hydraulically drives as a driving part, the output side of the pump part with the input side of the driving part is connected to the flow, and the flow rate and / or the pressure of the working fluid delivered from the pump part to the driving part is controllable, and that the Control of the flow rate and / or the pressure of the pumped to the driving part Working fluids by rotating the common housing about one to the axis of the Camshaft parallel axis takes place.
  • the twisting can have an effect similar to that of the linear displacement can be achieved.
  • the housing is driven in the direction of rotation easier to display in some cases.
  • the housing Due to the eccentric rotation of the housing about a parallel to the camshaft axis, however, it is arranged at a distance from it that the housing extends along of a circular arc twisted. Depending on the design of the overflow openings, this can be done Be achieved that the torque transmitted from the drive wheel to the camshaft exerts a small moment on the housing to twist it in a certain direction. This effect can be used to increase any frictional forces and moments compensate, or to facilitate the camshaft adjustment in a certain direction and thereby accelerate. If necessary, this effect can be achieved by a spring element, which is designed as a torsion spring, reinforced or weakened.
  • the device according to the invention eliminates the need for adjusting devices acting in the axial direction required helical gearing, which increases the manufacturing costs reduced.
  • the adjustment energy is provided by the camshaft drive itself, whereby external energy sources, such as additional electric motors or hydraulic pumps, are eliminated.
  • the adjustment can be controlled mechanically using the simplest means, for example or electrically, with extremely small adjustment forces.
  • Another advantage is that the Adjustment device universally used for motors of different sizes and performance can be. This significantly reduces the manufacturing effort.
  • a camshaft 1 is partially shown schematically. About an oil supply 2, a bore 3 inside the camshaft 1 is supplied with lubricating oil.
  • a drive wheel 4 is fixed in the axial direction but rotatably on the camshaft 1, the drive wheel 4 has a toothing 5, for example driven by a chain drive, not shown to become.
  • a hydraulic adjustment element is generally designated 6.
  • the adjusting element 6 is made consisting of a pump part 7 and a drive part 8.
  • a vane wheel 9 arranged, which is firmly connected to the drive wheel 4.
  • a Analog vane wheel 10 is provided, which is firmly connected to the camshaft 1.
  • Pump part 7 and drive part 8 have a common housing 11, which is not rotatable, however is arranged movable back and forth transversely to the axis of rotation.
  • the housing 11 has a Partition wall 12, which separates the pump part 7 from the drive part 8.
  • Overflow openings 13a, 13b connect the pump part 7 to the drive part 8.
  • the oil supply for the adjusting element 6 takes place via a bore 14 which communicates with the longitudinal bore 3 of the camshaft stands.
  • a screw part 15 mechanically secures the adjusting element 6 on the camshaft 1.
  • a bore 16 of the housing 11 of the adjusting element 6 has a pin 17 inserted with it an operating rod 18 communicates with the housing 11 in the direction of the Double arrow 19 to move back and forth.
  • the adjustment is made by a not shown Adjustment element that can be operated electrically, pneumatically or hydraulically. The adjustment forces required are very low, since essentially only frictional forces must be overcome. The actual adjustment energy is derived from the Drive wheel 4 transmitted moment gained.
  • a driver 20 is provided on the pump part 7, which in a corresponding recess 21 engages on the driving part 8. Through the game between driver 20 and recess 21, the adjustment range of the camshaft 1 is defined.
  • Fig. 2 is a section through the driving part 8 is shown.
  • the housing 11 is eccentric a working space 22 is formed for the vane wheel 10 of the drive part 8.
  • Slider 23 of the Vane wheel 10 slide on the inner peripheral surface 22a of the working space 22. Zur To simplify the illustration, only two slides 23 are shown in FIG. 2. Indeed a plurality of sliders are formed on the impeller 10 at equal circumferential intervals.
  • the working space 22 has the shape of a circular cylinder, the axis 22m of the working space 22 relative to the axis 10m of the vane wheel 10, which is also the axis the camshaft 1 is at a distance.
  • the direction of rotation of the camshaft is through indicated the arrow 24.
  • the working space 22 becomes the vane wheel 10 through the opening 13a sucked oil, while through the opening 13b oil in the Working space 22 is pressed.
  • the vane wheel 9 of the pump part 7 is coaxial with the vane wheel 10 of the drive part 8 arranged and not visible in FIG. 2.
  • a working space 25 of the pump part 7 is with a broken line shown in FIG. 2.
  • the working space 25 is opposite the vane wheel 9 offset, its axis 25m in the neutral position of the housing 11 the same Has a distance from the axis 10m, like the axis 22m of the working space 22.
  • the direction of the transfer is opposite.
  • the housing 11 If the housing 11 is now moved downward from the neutral position, the increases Eccentricity of the pump part 7, so that the pumping effect is increased per revolution. At the same time, the oil absorption in the driving part 8 is reduced per revolution. This will causes a leading movement of the driving part 8 relative to the pump part 7, so that a Pre-adjustment of the camshaft 1 relative to the drive wheel 4 takes place. An ending the pre-adjustment is achieved in that the housing 11 is returned to the neutral position becomes. It is essential that the housing 11 essentially in the direction of adjustment no forces act, so that only minimal forces are required for the adjustment are.
  • the respective adjustment state of the camshaft 1 with respect to the drive wheel 4 can be seen in known to be detected by a Hall element, so that even when different Inaccuracies an exact adjustment of the adjustment angle is possible.
  • a drive wheel 4a is arranged coaxially but rotatably has a toothing 5.
  • the drive wheel 4a is with a screw 15a in the axial direction secured.
  • a vane 9, which with the drive wheel 4a is fixedly connected, and a vane wheel 10, which is fixedly connected to the camshaft 1a, arranged.
  • the vane wheels 9, 10 form the essential elements for the pump part 7 or the driving part 8.
  • the housing 11a is eccentric by a roller bearing 30 via holding elements 31 attached to the cylinder head of an internal combustion engine, which is only roughly indicated by 32 is.
  • the axis 30a of the roller bearing 30 is parallel to the axis 1b of the camshaft 1a offset a distance d.
  • the hydraulic Adjusting element 6a is moved out of the neutral position shown in FIG. 3 become.
  • a relative movement between the vane wheels 9 and 10 causes what results in an adjustment of the camshaft 1a.
  • the angle by which the housing 11a is rotated about the axis 30a can vary depending on the design variant and size of the eccentricity d are between 60 and 240 degrees.
  • the drive in the direction of rotation can be done by various means, preferably an electrical one Stepper motor or a hydraulic adjustment by an adjusting element that by the Pressure is driven by engine oil.
  • an electric drive it is particularly preferred when the housing 11a is firmly connected to the rotor of an electric motor, not shown is or is integrally formed with this. This is a particularly simple one and robust construction possible.
  • the particular advantage of the present invention is that the drive energy for Adjustment of the camshaft is provided by the camshaft drive itself.
  • the externally applied adjustment forces are therefore minimal, so that small and poorly performing Adjusting elements can be used that require little space and are inexpensive to manufacture.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve Device For Special Equipments (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Claims (10)

  1. Dispositif pour déplacer un arbre à cames (1) d'un moteur à combustion interne par rapport à la roue d'entraínement (4) qui l'entraíne, avec un élément hydraulique de déplacement (6) qui est solidaire, d'une part, avec un élément structurel supportant l'arbre à cames (4) et, d'autre part, avec un élément structurel solidaire de l'arbre à cames (1), où l'élément hydraulique de déplacement (6) comporte une partie pompe (7) entraínée par la roue d'entraínement et une partie motrice (8) entraínée hydrauliquement par la partie pompe (7) et solidaire de l'arbre à cames (1), lesquelles parties sont réalisées comme des roues à cellules, où le côté sortie de la partie pompe (7) est en communication fluide avec le côté entrée de la partie motrice (8), où on peut contrôler le débit et / ou la pression du fluide de travail fourni par la partie pompe (7) à la partie motrice (8), caractérisé en ce qu'aussi bien la partie pompe (7) que la partie motrice (8) sont disposées coaxialement par rapport à l'axe de l'arbre à cames et dans un logement commun (11, 11a).
  2. Dispositif selon la revendication 1, caractérisé en ce que le contrôle du débit et / ou de la pression du fluide de travail fourni par la partie pompe (7) à la partie motrice (8) se fait par un déplacement linéaire du logement commun (11) perpendiculairement à l'axe (10m) de l'arbre à cames (1).
  3. Dispositif selon la revendication 1, caractérisé en ce que le contrôle du débit et/ou de la pression du fluide de travail fourni par la partie pompe (7) à la partie motrice se fait par une rotation du logement commun (11a) autour d'un axe (30a) parallèle à l'axe (1b) de l'arbre à cames (1a).
  4. Dispositif selon la revendication 3, caractérisé en ce qu'un élément de ressort est prévu, qui sollicite le logement (11a) dans la direction de rotation.
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que la communication fluide entre la partie pompe (7) et la partie motrice (8) communique, par une soupape de surpression, avec une conduite de fuite pour l'huile.
  6. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce que dans le logement (11), il est prévu une chambre de travail (25) pour la partie pompe (7) et une chambre de travail (22) pour la partie motrice (8), où les chambres de travail (25, 22) sont disposées de manière à être décalées dans des directions opposées par rapport à l'axe (10m) de l'arbre à cames.
  7. Dispositif selon l'une des revendications 1 à 6, caractérisé en ce que la communication fluide entre la partie de pompe (7) et la partie motrice (8) se fait par des ouvertures (13a, 13b) dans une paroi de séparation (12) entre la pompe (7) et la partie motrice (8).
  8. Dispositif selon l'une dès revendications 1 à 7, caractérisé en ce que la commande du déplacement ou de la rotation du logement commun (11a) est électrique, assurée, de préférence, par un moteur pas-à-pas.
  9. Dispositif selon la revendication 8, caractérisé en ce que le logement (11a) est solidaire du rotor d'un moteur électrique.
  10. Dispositif selon l'une des revendications 1 à 7, caractérisé en ce que la commande du déplacement ou la rotation du logement commun (11a) est hydraulique, assurée, de préférence, par l'huile du moteur.
EP98890293A 1997-10-21 1998-10-13 Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne Expired - Fee Related EP0911492B1 (fr)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
AT177897 1997-10-21
AT177897 1997-10-21
AT1778/97 1997-10-21
AT1422/98 1998-08-20
AT142298 1998-08-20
AT142298 1998-08-20

Publications (2)

Publication Number Publication Date
EP0911492A1 EP0911492A1 (fr) 1999-04-28
EP0911492B1 true EP0911492B1 (fr) 2002-03-06

Family

ID=25595811

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98890293A Expired - Fee Related EP0911492B1 (fr) 1997-10-21 1998-10-13 Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne

Country Status (4)

Country Link
US (1) US6138623A (fr)
EP (1) EP0911492B1 (fr)
AT (1) ATE214125T1 (fr)
DE (1) DE59803257D1 (fr)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1078148B1 (fr) * 1998-05-12 2003-05-14 Trochocentric International AG Dispositif pour le reglage de la position de phase d'un arbre
US6302073B1 (en) * 1999-03-23 2001-10-16 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6257186B1 (en) * 1999-03-23 2001-07-10 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6328006B1 (en) * 1999-03-23 2001-12-11 Tcg Unitech Aktiengesellschaft Device for adjusting the phase angle of a camshaft of an internal combustion engine
US6277045B1 (en) * 1999-12-08 2001-08-21 Daimlerchrysler Corporation Thin profile cam sprocket with integrated timing target

Family Cites Families (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3103209A (en) 1961-03-10 1963-09-10 Gen Motors Corp Phase adjusting servo mechanism for internal combustion engine and the like
US4091776A (en) 1974-04-04 1978-05-30 Rockwell International Corporation Fluid actuated timing mechanism
DE3415861A1 (de) * 1984-04-28 1985-10-31 Pierburg Gmbh & Co Kg, 4040 Neuss Vorrichtung zur steuerung einer kopplungseinrichtung
EP0363600B1 (fr) * 1988-10-13 1992-07-29 Bayerische Motoren Werke Aktiengesellschaft, Patentabteilung AJ-3 Dispositif de décalage angulaire d'un arbre à cames
DE3929619A1 (de) 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Kuppelstange fuer eine vorrichtung zur drehwinkelverstellung einer welle relativ zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
DE3929621A1 (de) * 1989-09-06 1991-03-07 Bayerische Motoren Werke Ag Vorrichtung zur relativen drehwinkelverstellung einer welle zu einem antriebsrad, insbesondere nockenwelle einer brennkraftmaschine
DE4101676A1 (de) 1991-01-22 1992-07-23 Schaeffler Waelzlager Kg Verstellvorrichtung fuer eine nockenwelle
DE4110088C1 (en) 1991-03-27 1992-07-09 Bayerische Motoren Werke Ag, 8000 Muenchen, De Relative shaft bearing position changing mechanism - has annular coupler with inner and outer toothing linked to axially displaceable piston
JPH04132414U (ja) * 1991-05-29 1992-12-08 株式会社アツギユニシア 内燃機関のバルブタイミング制御装置
US5293845A (en) * 1991-09-02 1994-03-15 Toyota Jidosha Kabushiki Kaisha Control mechanism for engine valve timing
DE4135380A1 (de) * 1991-10-26 1993-04-29 Bosch Gmbh Robert Hydraulische steuereinrichtung
DE4237193A1 (de) * 1992-11-04 1994-05-05 Bosch Gmbh Robert Verfahren zur Ansteuerung einer Einrichtung zum relativen Verdrehen einer Welle und Einrichtung zum relativen Verdrehen der Welle einer Brennkraftmaschine
DE69606613T2 (de) 1995-11-30 2000-07-13 Aisin Seiki Ventilzeitsteuerungsvorrichtung

Also Published As

Publication number Publication date
DE59803257D1 (de) 2002-04-11
EP0911492A1 (fr) 1999-04-28
ATE214125T1 (de) 2002-03-15
US6138623A (en) 2000-10-31

Similar Documents

Publication Publication Date Title
DE68910532T2 (de) Phasenvariatoranordnung für nockenwelle.
WO2015082722A2 (fr) Bielle de longueur variable d'un moteur à combustion interne
EP0335083B1 (fr) Dispositif de déplacement angulaire relatif entre deux arbres en liaison d'entraînement
DE69907989T2 (de) Variable Ventilzeitsteuervorrichtung
DE19903594C2 (de) Verstellbare Ventilsteuervorrichtung
DE3619956C2 (fr)
WO1994023209A1 (fr) Pompe a engrenages pour le refoulement d'un liquide
WO2008089714A1 (fr) Pompe à réfrigérant réglable
EP0560201B1 (fr) Pompe à huile pour une scie à chaîne
DE19821228A1 (de) Ventilsteuervorrichtung für einen Verbrennungsmotor
EP0911492B1 (fr) Dispositif pour modifier la phase angulaire d'un arbre à cames de moteur à combustion interne
DE102012203114B4 (de) Einlegeteil für Nockenwellenversteller mit Mittenverriegelung, sowie Steuertrieb und Verbrennungskraftmaschine damit
DE10315151A1 (de) Vorrichtung zur relativen Winkelverstellung einer Nockenwelle gegenüber dem antreibenden Antriebsrad
EP0846861B1 (fr) Pompe annulaire à engrenages continuellement variable
DE10207350C2 (de) Volumenstromvariable Rotorpumpe
DE1751979C3 (de) Hydraulische Steuereinrichtung
DE19850947A1 (de) Vorrichtung zur Steuerung der Öffnungs- und Schließzeiten von Gaswechselventilen einer Brennkraftmaschine
DE19954639C2 (de) Hydraulische Kolbenpumpe, insb. für Common Rail-Einspritzsysteme
EP0940622B1 (fr) Pompe à huile
EP2584221B1 (fr) Dispositif de transmission destiné à transmettre un couple et dispositif de production ou de conversion d'un couple
DE4116196A1 (de) Nockenwelle-verstellvorrichtung fuer verbrennungsmotoren
EP1783331B1 (fr) Système comprenant un arbre à cames d'admission, un arbre à cames d'échappement et un variateur de phase, et utilisation de ce système
DE713778C (de) Mittels einer rotierenden Taumelscheibe angetriebener Einspritzpumpensatz fuer Brennkraftmaschinen
EP0090796B1 (fr) Dispositif de réglage du début de refoulement d'une pompe d'injection de combustible
WO2001088344A1 (fr) Dispositif de reglage pour ajuster la position angulaire d'un arbre

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 DE ES FR GB IT

AX Request for extension of the european patent

Free format text: AL;LT;LV;MK;RO;SI

17P Request for examination filed

Effective date: 19990706

AKX Designation fees paid

Free format text: AT DE ES FR GB IT

17Q First examination report despatched

Effective date: 20000602

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAG Despatch of communication of intention to grant

Free format text: ORIGINAL CODE: EPIDOS AGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): AT DE ES FR GB IT

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 PRE;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.SCRIBED TIME-LIMIT

Effective date: 20020306

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: 20020306

REF Corresponds to:

Ref document number: 214125

Country of ref document: AT

Date of ref document: 20020315

Kind code of ref document: T

REF Corresponds to:

Ref document number: 59803257

Country of ref document: DE

Date of ref document: 20020411

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 20020509

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

Ref country code: ES

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

Effective date: 20020925

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: 20021013

Ref country code: AT

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

Effective date: 20021013

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: 20021209

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: 20030501

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

Effective date: 20021013