EP0631056B1 - Dispositif d'entraînement pour une vanne de réglage - Google Patents

Dispositif d'entraînement pour une vanne de réglage Download PDF

Info

Publication number
EP0631056B1
EP0631056B1 EP94108751A EP94108751A EP0631056B1 EP 0631056 B1 EP0631056 B1 EP 0631056B1 EP 94108751 A EP94108751 A EP 94108751A EP 94108751 A EP94108751 A EP 94108751A EP 0631056 B1 EP0631056 B1 EP 0631056B1
Authority
EP
European Patent Office
Prior art keywords
valve
volume
oil
control valve
plate
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
EP94108751A
Other languages
German (de)
English (en)
Other versions
EP0631056B2 (fr
EP0631056A1 (fr
Inventor
Heinz Frey
Kamil Prochazka
Franz Suter
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 AG Germany
Original Assignee
ABB Management 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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6491077&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0631056(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by ABB Management AG filed Critical ABB Management AG
Publication of EP0631056A1 publication Critical patent/EP0631056A1/fr
Application granted granted Critical
Publication of EP0631056B1 publication Critical patent/EP0631056B1/fr
Publication of EP0631056B2 publication Critical patent/EP0631056B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
    • F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
    • F15B13/00—Details of servomotor systems ; Valves for servomotor systems
    • F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
    • F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
    • F15B13/0401—Valve members; Fluid interconnections therefor
    • F15B13/0405—Valve members; Fluid interconnections therefor for seat valves, i.e. poppet valves
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05B—INDEXING SCHEME RELATING TO WIND, SPRING, WEIGHT, INERTIA OR LIKE MOTORS, TO MACHINES OR ENGINES FOR LIQUIDS COVERED BY SUBCLASSES F03B, F03D AND F03G
    • F05B2220/00—Application
    • F05B2220/30—Application in turbines
    • F05B2220/301—Application in turbines in steam turbines
    • 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
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S91/00—Motors: expansible chamber type
    • Y10S91/03—Large area valve

Definitions

  • An actuator for actuating a control valve with which, for example, the steam supply to a turbine of a power plant is regulated has a main piston of a piston-cylinder arrangement which is connected to the actuating rod of the control valve and which is acted upon on the one hand by spring force and on the other hand by oil under pressure.
  • the spring force securely closes the control valve, as a result of which the steam supply is interrupted. This ensures that the turbine does not get out of control if the pressure of the oil should drop.
  • the oil pressure in a drive volume, which acts on the main piston and actuates the control valve via it, is generated by an electro-hydraulic converter.
  • the invention seeks to remedy this.
  • the invention as characterized in the claims, solves the problem of creating an actuator for a control valve which can be improved in its dynamic behavior with comparatively simple means.
  • a connecting line is provided between the drive volume and the plate valve, which leads through a connecting piece into a spring chamber of the plate valve.
  • FIG. 1 shows an actuator 1, which actuates a control valve 2, which regulates the amount of hot steam flowing through a hot steam line 3 to a turbine (not shown).
  • the control valve 2 is connected by a valve spindle 4 to a main piston 6 sliding in a master cylinder 5.
  • a drive volume 7 pressurized with oil is arranged below the main piston 6. Instead of the oil, another hydraulic fluid or a gaseous medium can also be provided.
  • An oil-filled buffer volume 8 is provided above the main piston 6, in which a spring 9 is also arranged, which counteracts the oil pressure in the drive volume 7.
  • a line 52 leads from the buffer volume 8 to a drain device, not shown.
  • a rod 10 is provided on the spring side of the main piston 6, which connects the latter to a displacement measuring device 11.
  • connection 29 is connected on the one hand to a line 47, which in turn is connected to the bore 12, which in the Spring chamber 20 of the plate valve 17 leads, and on the other hand with a line 48, which leads to a normally closed, designed as a plate valve safety valve 49.
  • a line 50 leads into the intermediate volume 24 of the plate valve 17.
  • the last piece of the line 50 is shown in FIG. 1a as a bore penetrating the wall of the housing 22.
  • a line 51 branches off from the line 50 and establishes the connection with the connection 30 of the proportional directional valve 25.
  • the lines 50 and 51 are designed as bores in the housing 22, this is possible because both the proportional directional valve 25 and the safety valve 49 is also flanged directly and pressure-tight to the housing 22, so that a monolithic valve block is formed.
  • a drain port 24a leads from the intermediate volume 24 into a line leading to a drain device, not shown. From this drain device, the oil continues through the aforementioned pump back into line 45.
  • the safety valve 49 is designed as a plate valve with a cylinder 53, a volume 55 which is pressurized with oil under pressure from a safety oil circuit through a line 54 and which is delimited by a valve plate 56 and with a valve spring 57 which controls the oil pressure acting on the valve plate 56 counteracts. It cannot be seen from the schematic illustration of the safety valve 49 that the valve plate 56 is designed in such a way that it is impossible to jam it.
  • the line 54 normally leads through a directional control valve 58 and connects it to the volume 55.
  • the directional control valve 58 is actuated by an electromagnet 59.
  • An action line 60 indicates the path of the trigger command for the electromagnet 59.
  • the plate valve 17 can be used in all systems regardless of the design of the respective master cylinder 5.
  • the line 15 can generally be made comparatively short, so that the oil-filled line volume is correspondingly small, which advantageously increases the dynamics.
  • the actuator is therefore very versatile.
  • the interaction of the position controller 33 with the integrated power amplifier and the controller 36 as a common electronic control arrangement of a control circuit is particularly advantageous because the position controller 33 is specially adapted to the proportional directional control valve 25, so that no additional adjustments and adjustments are necessary.
  • this electronic control system it is entirely possible to assemble this electronic control system from other elements or to transfer its function to a higher-level system control system if, for example, the protection concept of the power plant would require this.
  • signals originating from the displacement measuring device 11 and from the stroke measurement 31 are processed continuously together with at least one setpoint value specified by the higher-level system control system according to a specified logic. In the event of deviations from this target value, this control arrangement generates correction signals which act on the actuating magnets 26, 27 of the proportional directional control valve 25 and cause the same to be reversed accordingly.
  • a breakthrough through the plate 18 has a cylindrical opening 66, which is followed by a conical extension.
  • a ball 67 is pressed into this conical extension by a spring 68, which is supported against a holder 69 connected to the plate 18, and closes the opening 66.
  • Oil 66 can pass through the opening 66 under pressure into the connecting piece 14 and through this and further flow through the connecting line 15 into the drive volume 7 as soon as a pressure difference occurs which is large enough to overcome the force of the spring 68 and the oil pressure acting on the ball 67.
  • FIG. 3 is similar to FIG. 2, except that in this case an opening with the opening 66 through the plate 18 is designed such that oil flows from the drive volume 7 through the connecting line 15 and through the connecting piece 14 into the spring chamber 20 can.
  • an opening with the opening 66 through the plate 18 is designed such that oil flows from the drive volume 7 through the connecting line 15 and through the connecting piece 14 into the spring chamber 20 can.
  • the cross section of the diaphragm 70 is designed to be significantly smaller than that of the opening 66.
  • FIG. 5 shows a plate 18 with two valve arrangements similar to that shown in FIG. 2, but which allow oil to pass through in opposite directions with a corresponding differential pressure.
  • the opening 66 which leads from the drive volume 7 into the spring chamber 20, has a substantially larger cross section than the second opening 66.
  • FIG. 1 is considered in more detail.
  • the control valve 2 must be comparatively in operation can be closed quickly.
  • the closing speed is normally around 1 m / sec, while the opening speed, on the other hand, only requires speeds around 0.02 m / sec.
  • These speed specifications are guide values; depending on the design of the power plant, there may also be significant deviations from these specifications.
  • the actuator 1 can be adapted to the respective operating conditions with comparatively little effort. If the control valve 2 is to be moved in the opening direction, the proportional directional control valve 25 is actuated by the position controller 33, and is actuated in such a way that it is to the left of the position shown standing scheme applies.
  • connection 28 and 29 are then connected through and oil under pressure flows from the line 45 through the proportional directional control valve 25.
  • No oil can flow through line 48 in normal operation, since the safety valve 49 closes this line 48.
  • the oil flows through the line 47, the bore 12 and the opening 13 into the spring chamber 20 of the plate valve 17 and from there through the opening of the plate 18, through the connector 14 and through the connecting line 15 into the drive volume 7.
  • the oil pressure in Drive volume 7 moves the main piston 6 upward and thus the control valve 2 in the opening direction via the valve spindle 4.
  • the position measuring device 11 monitors the stroke of the main piston 6 and continuously reports its position to the position controller 33, as indicated by the line of action 40.
  • the position controller 33 controls the proportional directional valve 25 so that the oil flow is interrupted.
  • the stroke measurement 31, the signals of which are processed in the position controller 33, monitors the operating behavior of the proportional directional valve 25.
  • the movement of the main piston 6 is ended at the same time as this control.
  • the spring 9 presses the main piston 6 down and thus the oil from the drive volume 7 until the end position of the control valve 2 is reached.
  • the oil flows out very quickly, since the cross section released by the plate valve 17 is comparatively large, so that the flow process is not negatively influenced by it.
  • the design of the plate 18 according to FIG. 5 also allows a small closing movement, for a larger stroke of the main piston 6 it is also necessary to open the plate valve 17 in this case.
  • the proportional directional control valve 25 is shown in the central position in FIG. 1. This position is assumed if, for example, the actuating magnets 26, 27 should not receive any voltage due to a power failure. Reaching this position is ensured by spring force of springs provided in the interior of the proportional directional valve 25 under all circumstances. In this position, the spring chamber 20 is relieved of pressure by the lines 47, 51 and 50, so that the plate valve 17 opens, which, as already described, leads to a quick closing of the control valve 2. In this way it is ensured that the control valve 2 is always definitely closed even in the event of a fault, so that under no circumstances can damage to the turbine being operated as a result of a defect in the actuator 1.
  • the directional control valve 58 is installed, which makes it possible as soon as it is switched electromagnetically to the right of the Shown position shown scheme that oil under pressure from line 45 through line 61 and through the directional control valve 58 can act on the volume 55, whereby the safety valve 49 is closed.
  • the command path for the directional control valve 58, as indicated by the line of action 60, must, however, be blocked as soon as it is switched over to normal operation, since otherwise the safety oil circuit may no longer be able to act on the safety valve 49, so that the protective function of this circuit is not more would be guaranteed.
  • the pressurized spring chamber 20 and the sealing points of the plate valve 17 are completely surrounded by volumes subjected to low pressure. If oil should escape from the spring chamber 20 under high pressure in the event of a defect, this escapes into the said volumes, so that secondary damage is avoided with great certainty.

Claims (3)

  1. Servomoteur (1) pour une soupape de réglage (2) avec un circuit de régulation, qui règle le servomoteur (1) conformément à une valeur de consigne prédéterminée par une technique prioritaire de conduite de l'installation, avec un piston principal (6) coulissant dans un cylindre principal (5), avec un volume de commande (7) pouvant être soumis de façon commandée à de l'huile sous pression d'un côté du piston principal (6) et avec une soupape à plateau (17) placée avant le volume de commande (7), caractérisé en ce que
    - la soupape à plateau (17) est pourvue d'un volume d'accumulation séparé (volume 21, volume intermédiaire 24) relié à un dispositif d'évacuation pour l'huile sortant hors de la soupape à plateau (17).
  2. Servomoteur suivant la revendication 1, caractérisé en ce que
    - il est prévu entre le volume de commande (7) et la soupape à plateau (17) une conduite de raccordement (15), qui débouche par une pièce de raccordement (14) dans une chambre de ressort (20) de la soupape à plateau (17).
  3. Servomoteur suivant la revendication 2, caractérisé en ce que
    - le volume d'accumulation séparé (volume 21, volume intermédiaire 24) est disposé concentriquement autour de la chambre de ressort (20).
EP94108751A 1993-06-24 1994-06-08 Dispositif d'entraínement pour une vanne de réglage Expired - Lifetime EP0631056B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4320937A DE4320937A1 (de) 1993-06-24 1993-06-24 Stellantrieb für ein Regelventil
DE4320937 1993-06-24

Publications (3)

Publication Number Publication Date
EP0631056A1 EP0631056A1 (fr) 1994-12-28
EP0631056B1 true EP0631056B1 (fr) 1996-05-01
EP0631056B2 EP0631056B2 (fr) 1999-05-12

Family

ID=6491077

Family Applications (1)

Application Number Title Priority Date Filing Date
EP94108751A Expired - Lifetime EP0631056B2 (fr) 1993-06-24 1994-06-08 Dispositif d'entraínement pour une vanne de réglage

Country Status (5)

Country Link
US (1) US5467683A (fr)
EP (1) EP0631056B2 (fr)
JP (1) JPH07139307A (fr)
CN (1) CN1102233A (fr)
DE (2) DE4320937A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009009852A1 (de) 2009-02-20 2010-08-26 Alstom Technology Ltd. Plattenablaufventil, insbesondere zum Beeinflussen des Ansteuerdrucks eines Regelventils

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE59909685D1 (de) 1999-01-14 2004-07-15 Alstom Technology Ltd Baden Plattenventil
DE10058560A1 (de) * 2000-11-24 2002-06-13 Voith Turbo Kg Elektrohydraulischer Stellantrieb
US7137407B2 (en) * 2005-02-22 2006-11-21 Emerson Process Management Power & Water Solutions, Inc. Trip manifold
CN100393985C (zh) * 2006-10-13 2008-06-11 成都发动机（集团）有限公司 精确调节顶压和紧急全关静叶的调节机构
CN102615264A (zh) * 2012-03-28 2012-08-01 蚌埠市华艺压铸机制造有限责任公司 压铸机升降阀板增压截止阀
CN107842642B (zh) * 2017-12-12 2024-04-02 大连亨利测控仪表工程有限公司 高效能切断型单作用气动执行机构

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2204270A (en) * 1938-04-29 1940-06-11 Watson Stillman Co Surge valve for hydraulic presses
CA1038260A (fr) * 1974-05-14 1978-09-12 Westinghouse Electric Corporation Systeme de fermeture positive pour robinets a opercule flottant
EP0127027B1 (fr) * 1983-05-30 1988-03-09 BBC Brown Boveri AG Servomoteur électrohydraulique pour soupapes de turbines
CH666132A5 (de) * 1984-07-20 1988-06-30 Bbc Brown Boveri & Cie Einrichtung zur ueberwachung von physikalischen groessen an anlagen.
DD263801A1 (de) † 1987-06-09 1989-01-11 Goerlitzer Maschinenbau Veb Hydraulische schaltung fuer entnahme- oder anzapf-schnellschlussventile von dampfturbinen
US5137253A (en) * 1989-12-01 1992-08-11 Asea Brown Boveri Ltd. Actuator

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009009852A1 (de) 2009-02-20 2010-08-26 Alstom Technology Ltd. Plattenablaufventil, insbesondere zum Beeinflussen des Ansteuerdrucks eines Regelventils

Also Published As

Publication number Publication date
EP0631056B2 (fr) 1999-05-12
CN1102233A (zh) 1995-05-03
JPH07139307A (ja) 1995-05-30
EP0631056A1 (fr) 1994-12-28
DE4320937A1 (de) 1995-01-05
US5467683A (en) 1995-11-21
DE59400247D1 (de) 1996-06-05

Similar Documents

Publication Publication Date Title
EP0496021B1 (fr) Soupape d'arrêt pour système hydraulique de sécurité
EP1598560B1 (fr) Dispositif de soupape hydraulique
DE102010053811A1 (de) Störungssicheres Betätigungssystem
EP0540963B1 (fr) Système d'alimentation pour système hydraulique divisé
EP0433791B1 (fr) Actuateur pour une valve d'alimentation
EP0430089B1 (fr) Actuateur
EP0631056B1 (fr) Dispositif d'entraînement pour une vanne de réglage
EP0054602A1 (fr) Soupape d'arrêt contrôlée par son propre fluide
EP0451543B1 (fr) Système d'actionnement pour une vanne de régulation de vapeur
EP1082560B1 (fr) Unite de commande pour une soupape de surete
DE4036564A1 (de) Hydraulische einrichtung zur steuerung eines arbeitszylinders einer presse
DE102012016838B4 (de) Hydraulische Steuerschaltung für eine hydraulisch betätigte Gießeinheit
DE102014226623A1 (de) Druckbegrenzungsventil und damit ausgestattete hydraulische Maschine
EP0604805B1 (fr) Dispositif de commande pour vérin hydraulique avec signal de réglage proportionnel
EP2452078B1 (fr) Dispositif constituant une restriction variable pour un écoulement fluidique
EP3353385B1 (fr) Turbine munie de soupapes à fermeture rapide et de soupapes de régulation
DE3225132A1 (de) Hydraulisches sicherheitsbremsventil
EP3037678B1 (fr) Module de levage
EP1203161B1 (fr) Soupape de securite de presse
DE1945951A1 (de) Entsperrbares Rueckschlagventil
WO2005093263A1 (fr) Systeme de commande hydraulique
DE102014007475B4 (de) Ventilanordnung zur gesteuerten Druckentlastung fluidgefüllter Leitungen unter erhöhten Sicherheitsanforderungen
EP0419946B1 (fr) Moteur pour une vanne
DE4418881A1 (de) Hubwerkregelsystem mit Regelventil
DE3532591A1 (de) Hydraulische vorrichtung, insbesondere 2-wege-proportionaldrosselventil

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): DE FR GB IT

17P Request for examination filed

Effective date: 19950513

17Q First examination report despatched

Effective date: 19951004

GRAH Despatch of communication of intention to grant a patent

Free format text: ORIGINAL CODE: EPIDOS IGRA

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

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: 19960501

REF Corresponds to:

Ref document number: 59400247

Country of ref document: DE

Date of ref document: 19960605

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

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

Effective date: 19960708

ET Fr: translation filed
PLAV Examination of admissibility of opposition

Free format text: ORIGINAL CODE: EPIDOS OPEX

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

PLBQ Unpublished change to opponent data

Free format text: ORIGINAL CODE: EPIDOS OPPO

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

26 Opposition filed

Opponent name: SIEMENS AG ZENTRALABTEILUNG TECHNIK ABTLG. ZT PA 3

Effective date: 19970127

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

Ref country code: FR

Payment date: 19970513

Year of fee payment: 4

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

PLBF Reply of patent proprietor to notice(s) of opposition

Free format text: ORIGINAL CODE: EPIDOS OBSO

RAP2 Party data changed (patent owner data changed or rights of a patent transferred)

Owner name: ASEA BROWN BOVERI AG

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

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

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

27A Patent maintained in amended form

Effective date: 19990512

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): DE FR GB IT

ITF It: translation for a ep patent filed

Owner name: DE DOMINICIS & MAYER S.R.L.

EN Fr: translation not filed
REG Reference to a national code

Ref country code: GB

Ref legal event code: 732E

GBTA Gb: translation of amended ep patent filed (gb section 77(6)(b)/1977)
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20000512

Year of fee payment: 7

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: 20010608

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

Effective date: 20010608

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

Ref country code: IT

Payment date: 20070626

Year of fee payment: 14

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: 20080608

REG Reference to a national code

Ref country code: DE

Ref legal event code: R082

Ref document number: 59400247

Country of ref document: DE

Representative=s name: ROESLER, UWE, DIPL.-PHYS.UNIV., DE

Effective date: 20120621

Ref country code: DE

Ref legal event code: R081

Ref document number: 59400247

Country of ref document: DE

Owner name: ALSTOM TECHNOLOGY LTD., CH

Free format text: FORMER OWNER: ALSTOM, PARIS, FR

Effective date: 20120621

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

Ref country code: DE

Payment date: 20130628

Year of fee payment: 20

REG Reference to a national code

Ref country code: DE

Ref legal event code: R071

Ref document number: 59400247

Country of ref document: DE

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 EXPIRATION OF PROTECTION

Effective date: 20140611