EP0508067A1 - Dispositif de réglage de la section d'écoulement dans une turbomachine - Google Patents

Dispositif de réglage de la section d'écoulement dans une turbomachine Download PDF

Info

Publication number
EP0508067A1
EP0508067A1 EP92102795A EP92102795A EP0508067A1 EP 0508067 A1 EP0508067 A1 EP 0508067A1 EP 92102795 A EP92102795 A EP 92102795A EP 92102795 A EP92102795 A EP 92102795A EP 0508067 A1 EP0508067 A1 EP 0508067A1
Authority
EP
European Patent Office
Prior art keywords
slide
control slide
turbine
channel
steam
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
EP92102795A
Other languages
German (de)
English (en)
Other versions
EP0508067B1 (fr
Inventor
Dieter Freuschle
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.)
ABB Asea Brown Boveri Ltd
ABB AB
Original Assignee
ABB Asea Brown Boveri Ltd
Asea Brown Boveri AB
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 ABB Asea Brown Boveri Ltd, Asea Brown Boveri AB filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0508067A1 publication Critical patent/EP0508067A1/fr
Application granted granted Critical
Publication of EP0508067B1 publication Critical patent/EP0508067B1/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
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/40—Movement of components
    • F05D2250/41—Movement of components with one degree of freedom
    • F05D2250/411—Movement of components with one degree of freedom in rotation

Definitions

  • the invention relates to a device for the regulated loading of the diffuser of axially flow-through turbomachines, in particular of extraction steam turbines, with a control slide arranged at least two inlet windows for the working medium and arranged upstream of the diffuser.
  • the nozzle group control is particularly suitable for systems in which high partial load efficiencies are required.
  • the first turbine stage which is usually equipped with a constant pressure or Curtis blading, also called a control stage, has a plurality of admission sectors, the steam inflow from the steam generator to each of the admission sectors having one special control valve is set. It is customary here to open one control valve after the other as the steam turbine output increases. For a given load condition, therefore, a more or less large number of control valves is generally fully open and therefore does not cause throttling. Only one of the control valves will be partially open and cause an additional throttle loss. This loss can, however, be kept to a modest extent, because it only affects the partial mass flow flowing through the respective control valve.
  • Devices for regulating the cross-section through which a turbomachine flows are also used in steam extraction turbines. They allow a variable steam mass flow to be branched out of the turbine, for example for process purposes.
  • axially flow-through steam turbines such controlled withdrawals are known in which the entire mass flow after flowing through a turbine part led out of the turbine, regulated and then reintroduced into the subsequent sub-turbine.
  • overflow control valves For each internally regulated removal, several successively opening overflow control valves are flanged onto the turbine housing, with which the steam quantity flowing into the subsequent turbine part is controlled and the removal pressure is thereby kept constant.
  • devices with which the free cross-section through which flow is changed in the guide apparatus for regulating the steam mass flow are also known in the form of adjustable guide vanes.
  • the guide vanes can be rotated about their own longitudinal axis in order to reduce the cross section.
  • the fulcrum can be on the front edge of the blade, within the blade profile or on the rear edge of the blade.
  • the cross-section through which the flow passes can be completely blocked on the occasion of an adjustment.
  • the aerodynamically important blade geometry is also retained.
  • the inflow and outflow of the guide vanes are changed to a greater or lesser extent, which impairs the operation of at least the immediately following rotor blades.
  • the working medium here low-pressure steam
  • the working medium enters the guide blading directly via axial rotary valves with a large number of lockable entry windows.
  • the invention has for its object to provide a simple adjusting device for nozzle group control, while avoiding the above-mentioned number of control valves, with which the inflow conditions to the guide device and the outflow conditions from the guide device remain unchanged.
  • a channel element is arranged between the control slide and the guide apparatus, with a plurality of inflow channels which connect the inlet windows of the control slide to the nozzles of the guide apparatus, the control slide being rotatable in the circumferential direction by 180 ° to increase or open the inflow channels .
  • each individual nozzle of the diffuser is acted on via its own inflow channel.
  • the advantages of the invention can be seen in particular in the high efficiency that can be achieved.
  • a large number of lossless operating points can be driven, and on the other hand, there is an optimal inflow for the nozzles in question.
  • the extraction turbine shown in FIG. 1 is a single-shaft, two-part turbine with internally controlled extraction 1, for example for process steam. It consists of a high pressure turbine 3 in the back pressure type and a low pressure turbine 3 'in the condensation type. The latter is necessary to compensate for the fluctuations in the power requirement of the company if, for example, the frequency must also be maintained in addition to the regulated steam pressure in the extraction 1.
  • the rotor blades of the two partial turbines are arranged on a common rotor 4.
  • the blade carriers 6, 6 ' are suspended in the largely cylindrical turbine housing 5 so that they can be moved by heat.
  • the live steam flows into the diffuser 7 of the high-pressure turbine 3 via an inlet housing 2 connected to the turbine housing 5, from where it acts on the control stage blading of the control wheel 8.
  • This control stage blading usually works according to the constant pressure principle and is carried out in one stage in the case shown.
  • the steam then flows through the reaction blading of the high-pressure turbine 3, which is only shown symbolically, and reaches the high-pressure exhaust steam 9.
  • the steam to be expanded remains within the turbine housing 5.
  • the steam not removed in 1 flows through the low-pressure turbine 3 '. From their outlet, the steam reaches the exhaust steam housing, not shown, and from there into a condenser, on the cooled pipes of which the now relaxed steam is deposited.
  • the new regulating device can be used both on the high-pressure turbine 3 for fresh steam regulation and on the low-pressure turbine 3 'for regulating the extraction.
  • the guide device 7 on the high-pressure turbine consists of a nozzle box, which is integrated in a channel element 10 designed as a ring.
  • the individual nozzles in this case 42 in number, can either be inserted and caulked in the channel ring or welded into the channel ring.
  • the two-part channel ring which will generally be designed with a horizontal part plane, is on the one hand suspended in the inlet housing 2 and, on the other hand, surrounds the compensating piston 11 of the high-pressure turbine with its radially inner diameter. On its inner circumference, it is provided with a labyrinth 12 over its axial extent in order to form the piston seal.
  • the channel ring 10 is provided over its circumference with two symmetrically arranged sectors of inflow channels 13. These inflow channels, of which each sector has 20 pieces, each open into a nozzle of the guide apparatus (FIG. 5). This ensures optimal inflow to the nozzles. In the present case, only the inflow channel 13a which opens when the machine starts up extends over two nozzle divisions in order to keep the mechanical loads on the control wheel within limits. The dimensions of the inflow channels are unchanged.
  • the adaptation to the swallowing capacity of the blading is advantageously done via the geometry of the nozzles. For example, their width can be adjusted over the circumference and / or their radial height to the prevailing conditions.
  • the inflow channels 13 are led radially out of the channel ring.
  • the actual inlet openings of the channels of the upper sector and the lower sector are offset from one another in the axial direction (FIG. 1) and are therefore located in two different planes.
  • this two-part radial slide which is also formed with a horizontal partial plane, is a ring which surrounds the channel ring 10 with its inner diameter and seals against it.
  • the ring must be able to operate in the closed state, i.e. without the inflow of steam into the inflow channels, to be able to absorb the maximum pressure drop without great deformation. Since the permanently open entry windows are acted upon by the working medium even in the non-flowed state, the radial slide is equipped with sealing strips (not shown) for sealing purposes in its axial extent on both sides of the entry windows.
  • the aforementioned rotation of the radial slide by 180 ° can be done in a simple manner according to FIG. 3.
  • the slide On one of its end faces, the slide is provided over the circumference with a toothing 17 (only partially shown) into which a pinion inserted from the outside, which is inserted through the upper part of the inlet housing 2, engages.
  • the storage of the radial slide valve shown only schematically, takes place via four rolling pins 18, which are evenly distributed over the circumference.
  • valve points i.e. almost lossless operating points
  • the new solution thus corresponds to the effect of 20 of the control valves mentioned at the beginning.
  • the simultaneous loading of opposite inflow channels enables the subsequent turbine part to be warmed up evenly and avoids any additional bearing load.
  • FIG. 1 and FIG. 7 show an exemplary embodiment of the invention in the area of internally regulated steam extraction. Since there are significantly lower vapor pressures and thus pressure drops in this area, a simplified variant can be used. This has the additional advantage that the axial flow direction of the steam is not interrupted at the point of withdrawal. In addition, it is characterized by a short axial length.
  • the channel element here is a channel disk 19, in which the control device 20 of the control stage is integrated.
  • the two-part channel disk which will also generally be designed with a horizontal partial plane, is on the one hand suspended in the turbine housing 5 and, on the other hand, surrounds the low-pressure rotor 4 of the turbine with its radially inner diameter. On its inner circumference, it is provided with a labyrinth over its axial extent in order to form a seal.
  • the channel disk 19 is provided over its circumference with two symmetrically arranged sectors of inflow channels 21. These inflow channels, each sector having 20 pieces, each open into a nozzle of the control apparatus 20. Only the inflow channels 21a opening or closing last, in the present case, extend over two nozzle divisions in order to keep the mechanical stresses on the downstream control wheel within limits.
  • the inflow channels 21 are guided axially or obliquely axially out of the channel disk 19.
  • the actual inlet openings of the channels of the upper sector and the lower sector are offset from one another in the radial direction and are therefore located in two different radial planes.
  • the non-extracted steam passes through a control slide 23 provided with two inlet windows 22.
  • this two-part axial slide which is also formed with a horizontal partial plane, is a disk which rests against the end face of the channel disk, is guided there and seals against it.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP92102795A 1991-04-08 1992-02-20 Dispositif de réglage de la section d'écoulement dans une turbomachine Expired - Lifetime EP0508067B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH102291 1991-04-08
CH1022/91 1991-04-08

Publications (2)

Publication Number Publication Date
EP0508067A1 true EP0508067A1 (fr) 1992-10-14
EP0508067B1 EP0508067B1 (fr) 1995-07-12

Family

ID=4200625

Family Applications (1)

Application Number Title Priority Date Filing Date
EP92102795A Expired - Lifetime EP0508067B1 (fr) 1991-04-08 1992-02-20 Dispositif de réglage de la section d'écoulement dans une turbomachine

Country Status (3)

Country Link
US (1) US5269648A (fr)
EP (1) EP0508067B1 (fr)
DE (1) DE59202840D1 (fr)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0568909A1 (fr) * 1992-05-04 1993-11-10 ABBPATENT GmbH Obturateur à disque rotatif pour turbine à gaz
EP0568905A1 (fr) * 1992-05-04 1993-11-10 ABBPATENT GmbH Obturateur à disque rotatif pour turbine à vapeur
WO2007104647A3 (fr) * 2006-03-15 2008-01-10 Siemens Ag Turbine à gaz pour centrale thermique,, et procédé permettant de faire fonctionner une telle turbine à gaz
CZ301591B6 (cs) * 2004-05-27 2010-04-28 Siemens Aktiengesellschaft Zarízení pro regulaci tlaku v odberu turbíny
DE102009010608A1 (de) * 2009-02-25 2010-08-26 Siemens Aktiengesellschaft Gestaltung der Einströmkammer mit radialer Zuströmung und Aufteilung des Frischdampfstroms in 2 Abschnitten
WO2012130879A1 (fr) * 2011-04-01 2012-10-04 Siemens Aktiengesellschaft Augmentation du rendement d'un étage régulateur d'une turbine à action
DE102017005641A1 (de) * 2017-06-17 2018-12-20 EXCELLENCE Gesellschaft zur Obhutsverwaltung erlesener Liegenschaften und Vermögensanlagen mbH Verfahren für dezentrale mit Biomasse betriebene Blockheizkraftwerke im kleineren Leistungsbereich

Families Citing this family (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH06312158A (ja) * 1993-04-30 1994-11-08 Matsui Mfg Co 空気振動波発生方法及びその装置
US5494405A (en) * 1995-03-20 1996-02-27 Westinghouse Electric Corporation Method of modifying a steam turbine
SE509390C2 (sv) * 1996-05-15 1999-01-18 Abb Stal Ab Ångturbin
DE102007056889A1 (de) * 2007-11-26 2009-05-28 Bosch Mahle Turbo Systems Gmbh & Co. Kg Abgasturbolader mit mindestens einer Turbine variabler Turbinengeometrie
JP5615150B2 (ja) 2010-12-06 2014-10-29 三菱重工業株式会社 原子力発電プラントおよび原子力発電プラントの運転方法
US20130064665A1 (en) * 2011-09-13 2013-03-14 General Electric Company Low pressure steam turbine including pivotable nozzle
KR101831837B1 (ko) * 2016-12-15 2018-02-23 한국에너지기술연구원 상시 부분분사운전 효율 향상을 위한 부분분사운전 터빈장치 및 이를 이용한 터빈장치 작동방법
CN111005771B (zh) * 2020-01-03 2021-05-14 清华大学 旋转式可变喷嘴部分进气轴流式涡轮
CN111156052B (zh) * 2020-01-03 2021-07-09 清华大学 旋转式可变喷嘴部分进气径流式涡轮
CN111535876B (zh) * 2020-04-07 2022-05-10 东方电气集团东方汽轮机有限公司 给水泵汽轮机调节阀与喷嘴组一体式结构
US12497903B2 (en) * 2024-04-17 2025-12-16 Rtx Corporation Multi-stage partial admission axial turbine

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE630147C (de) * 1936-05-20 Siemens Schuckertwerke Akt Ges Turbine mit einer durch Zu- und Abschalten von Duesen oder Duesengruppen veraenderbaren Beaufschlagung
CH428775A (de) * 1965-09-24 1967-01-31 Escher Wyss Ag Dampf- oder Gasturbine
GB2076065A (en) * 1980-05-20 1981-11-25 Forster Terence Owen Turbine
EP0419871A1 (fr) * 1989-09-29 1991-04-03 React Energy Ltd. Turbine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US707727A (en) * 1901-05-10 1902-08-26 Richard Schulz Steam-turbine.
US746388A (en) * 1903-05-23 1903-12-08 Frederick A Scheffler Steam-turbine.
US884719A (en) * 1908-01-22 1908-04-14 Richard Cramp Turbine.
US958430A (en) * 1908-12-12 1910-05-17 Charles Algernon Parsons Turbine.
US3209537A (en) * 1960-05-02 1965-10-05 Bendix Corp Motive fluid control for a re-expansion gas turbine engine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE630147C (de) * 1936-05-20 Siemens Schuckertwerke Akt Ges Turbine mit einer durch Zu- und Abschalten von Duesen oder Duesengruppen veraenderbaren Beaufschlagung
CH428775A (de) * 1965-09-24 1967-01-31 Escher Wyss Ag Dampf- oder Gasturbine
GB2076065A (en) * 1980-05-20 1981-11-25 Forster Terence Owen Turbine
EP0419871A1 (fr) * 1989-09-29 1991-04-03 React Energy Ltd. Turbine

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0568909A1 (fr) * 1992-05-04 1993-11-10 ABBPATENT GmbH Obturateur à disque rotatif pour turbine à gaz
EP0568905A1 (fr) * 1992-05-04 1993-11-10 ABBPATENT GmbH Obturateur à disque rotatif pour turbine à vapeur
US5383763A (en) * 1992-05-04 1995-01-24 Abb Patent Gmbh Steam turbine with a rotary slide for controlling steam throughput
US5409351A (en) * 1992-05-04 1995-04-25 Abb Patent Gmbh Steam turbine with a rotary slide
CZ301591B6 (cs) * 2004-05-27 2010-04-28 Siemens Aktiengesellschaft Zarízení pro regulaci tlaku v odberu turbíny
WO2007104647A3 (fr) * 2006-03-15 2008-01-10 Siemens Ag Turbine à gaz pour centrale thermique,, et procédé permettant de faire fonctionner une telle turbine à gaz
US8635876B2 (en) 2006-03-15 2014-01-28 Siemens Aktiengesellschaft Gas turbine for a thermal power plant, and method for operating such a gas turbine
DE102009010608A1 (de) * 2009-02-25 2010-08-26 Siemens Aktiengesellschaft Gestaltung der Einströmkammer mit radialer Zuströmung und Aufteilung des Frischdampfstroms in 2 Abschnitten
DE102009010608B4 (de) * 2009-02-25 2011-06-16 Siemens Aktiengesellschaft Gestaltung der Einströmkammer mit radialer Zuströmung und Aufteilung des Frischdampfstroms in 2 Abschnitten
WO2012130879A1 (fr) * 2011-04-01 2012-10-04 Siemens Aktiengesellschaft Augmentation du rendement d'un étage régulateur d'une turbine à action
DE102017005641A1 (de) * 2017-06-17 2018-12-20 EXCELLENCE Gesellschaft zur Obhutsverwaltung erlesener Liegenschaften und Vermögensanlagen mbH Verfahren für dezentrale mit Biomasse betriebene Blockheizkraftwerke im kleineren Leistungsbereich
WO2018228627A1 (fr) 2017-06-17 2018-12-20 EXCELLENCE Gesellschaft zur Obhutsverwaltung erlesener Liegenschaften und Vermögensanlagen mbH Procédé destiné à des centrales thermiques en montage-bloc exploitées d'une manière décentralisée avec une biomasse, pour une petite gamme de puissance

Also Published As

Publication number Publication date
US5269648A (en) 1993-12-14
DE59202840D1 (de) 1995-08-17
EP0508067B1 (fr) 1995-07-12

Similar Documents

Publication Publication Date Title
EP0508067B1 (fr) Dispositif de réglage de la section d'écoulement dans une turbomachine
DE69933601T2 (de) Gasturbine
EP0568909B1 (fr) Obturateur à disque rotatif pour turbine à gaz
DE2913548C2 (de) Wellenkühlung für ein Gasturbinentriebwerk
EP0906494B1 (fr) Arbre de turbine et procede de refroidissement d'un arbre de turbine
EP2123860B1 (fr) Redresseur de tourbillons combiné
EP1611315B1 (fr) Turbomachine
DE3226052A1 (de) Deckbandaufbau fuer ein gasturbinentriebwerk
DE69018338T2 (de) Gasturbine.
DE3206209A1 (de) "luftsteuervorrichtung fuer ein gasturbinentriebwerk
EP1111189B1 (fr) Chemin d'air de refroidissement pour le rotor d'une turbine à gaz
DE19620828C1 (de) Turbinenwelle sowie Verfahren zur Kühlung einer Turbinenwelle
DE2654525C1 (de) Stroemungsmaschine mit einer Regeleinrichtung zur Konstanthaltung des Radialspielraums zwischen den Rotorschaufelspitzen und der Statorkonstruktion
DE2836864A1 (de) Reibungsturbine
EP2532898A1 (fr) Turbocompresseur axial
EP1000224A1 (fr) Repartition de l'air de refroidissement dans l'etage de turbine d'une turbine a gaz
EP0491134A1 (fr) Enveloppe d'admission pour turbine à gaz
EP0992656B1 (fr) Turbomachine pour comprimer ou détendre un fluide comprimable
DE3424138A1 (de) Luftspeichergasturbine
DE3248439A1 (de) Gasturbinentriebwerk mit gekuehlten schaufelspitzen
DE2503493A1 (de) Thermische turbomaschine, insbesondere niederdruck-dampfturbine
DE3424141A1 (de) Luftspeicher-gasturbine
DE1942346A1 (de) Vorrichtung zur Abdichtung des Rotors gegenueber dem Stator bei einer zu einem Gasturbinentriebwerk gehoerigen Turbine
EP0568905B1 (fr) Obturateur à disque rotatif pour turbine à vapeur
DE3242713A1 (de) Einlassgehaeuse fuer dampfturbine

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): CH DE FR IT LI

17P Request for examination filed

Effective date: 19930326

17Q First examination report despatched

Effective date: 19940216

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR IT LI

REF Corresponds to:

Ref document number: 59202840

Country of ref document: DE

Date of ref document: 19950817

ET Fr: translation filed
ITF It: translation for a ep patent 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
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 19970114

Year of fee payment: 6

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

Ref country code: CH

Payment date: 19970305

Year of fee payment: 6

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

Ref country code: LI

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

Effective date: 19980228

Ref country code: FR

Free format text: THE PATENT HAS BEEN ANNULLED BY A DECISION OF A NATIONAL AUTHORITY

Effective date: 19980228

Ref country code: CH

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

Effective date: 19980228

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

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

Ref country code: DE

Payment date: 20000122

Year of fee payment: 9

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: 20011201

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;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.

Effective date: 20050220