EP1502010B1 - Turbine a vapeur - Google Patents

Turbine a vapeur Download PDF

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Publication number
EP1502010B1
EP1502010B1 EP03730179A EP03730179A EP1502010B1 EP 1502010 B1 EP1502010 B1 EP 1502010B1 EP 03730179 A EP03730179 A EP 03730179A EP 03730179 A EP03730179 A EP 03730179A EP 1502010 B1 EP1502010 B1 EP 1502010B1
Authority
EP
European Patent Office
Prior art keywords
valve
control
steam
steam turbine
valves
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
EP03730179A
Other languages
German (de)
English (en)
Other versions
EP1502010A1 (fr
Inventor
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology AG
Publication of EP1502010A1 publication Critical patent/EP1502010A1/fr
Application granted granted Critical
Publication of EP1502010B1 publication Critical patent/EP1502010B1/fr
Anticipated expiration legal-status Critical
Expired - Fee Related legal-status Critical Current

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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
    • F01D17/145—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 by means of valves, e.g. for steam turbines
    • 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
    • F01D17/02—Arrangement of sensing elements
    • F01D17/08—Arrangement of sensing elements responsive to condition of working-fluid, e.g. pressure
    • 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
    • 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
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/165—Controlling means specially adapted therefor
    • 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
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/87917—Flow path with serial valves and/or closures

Definitions

  • the invention relates to a steam turbine and in particular a valve arrangement for the live steam supply to the steam turbine.
  • Steam turbines are known in which the fresh steam supply is regulated by nozzle control by means of a control stage, also called a first turbine stage.
  • a control stage has, for example, differently sized admission sectors, to which the live steam is supplied in each case via a live steam inlet with a plurality of control valves.
  • the control valves are preceded by a quick-closing valve.
  • These steam turbines are typically operated at a live steam pressure, which is set by the operating parameters of the steam generator for all operating loads of the steam turbine. Through various settings of the three or four control valves, the steam turbine can be operated at a plurality of partial load points and also within these partial load points associated load ranges.
  • the sequentially operable control valves are either closed or fully or regulated opened.
  • Other known steam turbines are operated without control stage. These typically have one or two live steam inlets, each with a quick-action valve and a downstream control valve. Such steam turbines are described, for example, in the sales documentation of ABB Power Generation, Description. HTGD 666 159 and a valve arrangement arranged therein for the regulation of the live steam supply in the same sales documentation, GMDT N06 014.
  • the live steam pressure may be variable in these steam turbines, such as in steam turbine plants for sliding pressure operation or in steam turbine plants whose cycle is combined with a gas turbine plant. However, in newer steam turbine plants, the live steam pressure can also be set at a single pressure level for all operating loads.
  • valves in the steam turbine plants mentioned are preferably designed so that valve vibrations due to an increased load are kept within limits and the longest possible damage-free service life of the valve is granted.
  • valves In the steam turbines without control stage and in particular those that are operated at fixed live steam pressure, the valves must be in always throttled operation to allow safe partial load operation of the steam turbine. As a result, the valves are exposed to an increased load compared to the steam turbine with control stage.
  • the pressure is reduced exclusively via the valves, while in steam turbines with control stage, the pressure is reduced via the valve and the upstream nozzles.
  • the quick-acting valves ensure safety for the live steam supply, but can not assume a throttling function.
  • Operating a steam turbine at fixed pressure may result in increased loads and critical pressure ratios in the control valves, causing correspondingly increased valve vibration and increased damage risk. This is particularly the case with steam turbines without control stage and throttle operation in partial load operation of the case.
  • JP 61126302 discloses two series-connected butterfly valves (English: butterfly valves) with a vapor sieve arranged between them.
  • a housing for the steam strainer is assembled with separate housings for the two flaps.
  • the disclosed flaps are typically suitable for the control of steam flows in the low pressure range, ie not for the live steam supply.
  • FR 2206438 discloses a method of controlling the operation of a steam turbine by means of a series of steam inlet valves, including throttle inlet valves (TV1-TV4) and regulator valves (GV1-GV8).
  • TV1-TV4 throttle inlet valves
  • GV1-GV8 regulator valves
  • EP 0 361 835 discloses a system for monitoring the operating state of a throttle valve connected in series with a regulator valve.
  • a steam turbine has a valve arrangement for regulating the live steam supply, which consists of two control valves which are connected in series.
  • the two control valves are each designed as unloaded single-seat valves with a pre-stroke or unloaded single-seat valves without a pre-stroke of the type of a tubular valve.
  • the two control valves (6, 7) are arranged in a single housing.
  • This embodiment is particularly suitable for controlling the steam supply, ie steam in higher pressure ranges, and also has a reduced risk of damage when reducing the high pressures.
  • the inventive valve arrangement allows for partial load operation, a gradual reduction of the pressure loss across the two individual control valves, that is, the converted energy during throttle operation is distributed to the two or more control valves.
  • the load of a single control valve is thereby greatly reduced in comparison to a valve arrangement with quick-closing valve and only one control valve.
  • the risk of valve vibration and consequent possible valve damage is thereby reduced.
  • the safety function of a quick-acting valve can be taken over by the first control valve in the arrangement according to the invention, so that the safety afforded by this valve arrangement is not reduced in comparison to the prior art.
  • valve arrangement according to the invention can be applied to steam turbines both with and without control stage. In steam turbines without control stage, it reduces in particular the relatively high loads of the control valves there. Furthermore, it is suitable for steam turbines in fixed pressure operation as well as in operation with variable live steam pressure. Again, the valve arrangement according to the invention is particularly effective for steam turbines without a control stage and especially for those in the fixed pressure mode, the reduction of load-related valve vibrations.
  • the valve arrangement has the advantage that the problem of potential valve vibrations is achieved in particular in steam turbines without control stage and at fixed pressure operation by a simple arrangement of a single valve type and without loss of security.
  • control valves and actuators can be used.
  • control or control valves preferably the same drive are used.
  • FIG. 1 shows schematically a steam turbine plant with a steam generator 1, which is connected via a live steam supply line 2 to a steam turbine 3.
  • the steam turbine 3 is coupled to a generator G.
  • the steam which has been expanded in the turbine is supplied to a condenser 4, condensate accumulating there being fed back to the water-steam circuit of the system.
  • the supply line 2 has a valve arrangement 5 for regulating the live steam pressure according to a predetermined operating load.
  • the valve arrangement has here in the flow direction a first control valve 6 and a second control valve 7, which are connected to each other in series.
  • the control valves 6 and 7 each have an actuator 6a and 7a, which are connected to a control or regulating device 8.
  • the two control valves can be placed in a full closed position, a full open position or any partial open position.
  • the first control valve 6 can also take over the function of a quick-acting valve.
  • the live steam generated in the steam generator 1 has on entry into the valve assembly 5 a live steam pressure P D1 , which is there gradually reduced via the intermediate pressure P Z to a vapor pressure P D2 , which corresponds to a full operating load or a predetermined partial load.
  • the actuators 6a and 7a may be formed, for example, as a hydraulic drive with electro-hydraulic converter. Incoming electrical control signals are then converted into corresponding hydraulic currents, the corresponding Setting movements on the throttle bodies or shut-off valves of the control valves 6 and 7 generate.
  • FIG. 2 shows a first possible embodiment of the inventive valve assembly, in which the control valves are designed as pipe valves.
  • the two control valves 6 and 7 can be combined in a common housing to form an assembly 20, whereby the installation effort in the installation of the live steam supply line 2 is simplified.
  • the two control valves 6 and 7 may expediently be configured identically with identical or similar components. In this way, on the one hand reduces the variety of parts and on the other hand can be reduced by higher quantities of the item price.
  • the valve seats or diffusers 22 may be the same or different, whereby the flow cross sections of the two valves are either the same or different.
  • each control valve 6 includes a valve body 21 which cooperates in its closed position with a valve seat 22.
  • FIG. 2 one valve body half in the closed position of the valve body 21 and the other valve body half in the maximally open open position of the valve body 21 are shown for each valve body 21 with respect to a symmetry plane 23 perpendicular to the plane of the drawing.
  • FIG. 3 shows a further embodiment of the valve arrangement according to the invention.
  • the two control valves 6 and 7 are rotated by 90 ° to each other.
  • each control valve 6 includes a valve body 24 which cooperates in its closed position with a valve seat 25.
  • For each valve body 24 on the plane of the plane of symmetry plane 26 which is a valve body half in the closed position of the valve body 24 and the other valve body half in the maximum open open position of the valve body 24 is shown.
  • valve arrangement according to the invention is operated as follows:
  • the first control valve 6 On the input side of the first control valve 6 is set by the steam generator fresh steam pressure P D1 .
  • This pressure can be either a fixed predetermined pressure or a variable by predetermined measures in the boiler system predetermined pressure.
  • the steam turbine 3 receives a working pressure P D2 , which varies with the operating state of the steam turbine 3.
  • the live steam pressure P D1 present on the input side is throttled to the actual working pressure P D2 .
  • this takes place in two stages, with the invention for the first stage comprising two different methods:
  • the first control valve 6 throttles the live steam pressure P D1 to an intermediate pressure P Z , wherein this throttling is controlled.
  • control valve 6 is set to a valve lift.
  • the resulting intermediate pressure is then variable depending on the live steam pressure P D1 .
  • this intermediate pressure P Z is always slightly higher than the maximum required by the steam turbine 3 working pressure P D2 .
  • variable live steam pressure P D2 is regulated by means of the control valve 6 to a load-dependent intermediate pressure P Z.
  • the actuation of the first control valve 6 is realized, for example, by a control circuit whose command variable is expediently formed by the load-dependent intermediate pressure P Z.
  • control deviations are determined by a desired-actual comparison of the values of the intermediate pressure P Z and compensated by suitable control commands.
  • the second control valve 7 now throttles from the intermediate pressure P Z to the working pressure P D2 , whereby this throttling takes place only regulated.
  • a control loop for the actuation of the second control valve 7 contains as guide variables, for example, the power of the steam turbine or the rotational speed of the rotor of the machine.
  • the working pressure P D2 adjusts according to these reference variables. This means that control deviations, which are compensated for by a nominal / actual comparison of the values of the working pressure P D2 or the reference values, according to which the working pressure adjusts, are compensated by suitable control commands.
  • the valve assembly 5 comes in the invention with two simple control circuits.
  • the effort for the control and / or control of the valve assembly 5 is reduced.
  • the two-stage throttling has the consequence that the maximum of the control valves 6 and 7 individually applied pressure differences are significantly smaller than the pressure difference between live steam pressure P D1 and working pressure P D2 , which causes the reduced stress on the control valves 6 and 7.
  • vibrations, vibration excitations and noise developments can be reduced or avoided altogether.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Control Of Turbines (AREA)

Claims (5)

  1. Turbine à vapeur (3) avec un agencement de soupape (5) pour la régulation de l'apport de vapeur vive dans la turbine à vapeur (3), l'agencement de soupape (5) présentant deux soupapes de réglage (6, 7) dans la direction de l'écoulement de la vapeur vive qui sont montées en série,
    caractérisée en ce que
    les deux soupapes de réglage (6, 7) sont configurées chacune sous la forme de soupapes à un siège déchargées avec une pré-levée ou sous la forme de soupapes à un siège déchargées sans pré-levée, du type d'une soupape tubulaire et les deux soupapes de réglage (6, 7) sont disposées dans un seul boîtier.
  2. Turbine à vapeur selon la revendication 1,
    caractérisée en ce que
    la turbine à vapeur (3) est configurée avec ou sans étage de réglage et la pression (PD1) de la vapeur vie est ajustée fixement ou de manière variable avant l'agencement de soupape (5) pour toutes les charges de fonctionnement de la turbine à vapeur (3).
  3. Turbine à vapeur (3) selon l'une quelconque des revendications précédentes,
    caractérisée en ce que
    les deux soupapes de réglage (6, 7) présentent chacune un mécanism de commande (6a, 7a) qui est connecté à un dispositif de réglage (8) pour la commande ou la réglage des mécanisms de commande (6a, 7a).
  4. Turbine à vapeur selon l'une quelconque des revendications précédentes 1 à 3,
    caractérisée en ce que
    les sections transversales d'écoulement des deux soupapes de réglage (6, 7) sont identiques.
  5. Turbine à vapeur selon l'une quelconque des revendications précédentes 1 à 3,
    caractérisée en ce que
    les sections transversales d'écoulement des deux soupapes de réglage (6, 7) sont différentes.
EP03730179A 2002-05-03 2003-04-10 Turbine a vapeur Expired - Fee Related EP1502010B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE2002119948 DE10219948A1 (de) 2002-05-03 2002-05-03 Dampfturbine
DE10219948 2002-05-03
PCT/EP2003/050099 WO2003093653A1 (fr) 2002-05-03 2003-04-10 Turbine a vapeur

Publications (2)

Publication Number Publication Date
EP1502010A1 EP1502010A1 (fr) 2005-02-02
EP1502010B1 true EP1502010B1 (fr) 2007-02-14

Family

ID=29225029

Family Applications (1)

Application Number Title Priority Date Filing Date
EP03730179A Expired - Fee Related EP1502010B1 (fr) 2002-05-03 2003-04-10 Turbine a vapeur

Country Status (5)

Country Link
US (1) US7223065B2 (fr)
EP (1) EP1502010B1 (fr)
AU (1) AU2003240766A1 (fr)
DE (2) DE10219948A1 (fr)
WO (1) WO2003093653A1 (fr)

Families Citing this family (19)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2004040099A1 (fr) 2002-10-29 2004-05-13 Kabushiki Kaisha Toshiba Soupape de vapeur
EP1637783B1 (fr) 2004-09-20 2012-08-01 Siemens Aktiengesellschaft Combinaison de soupape pour turbine à vapeur avec une soupape à fermeture rapide et une soupape de régulation
CH699864A1 (de) 2008-10-31 2010-05-14 Alstom Technology Ltd Dampfturbine.
US8881526B2 (en) 2009-03-10 2014-11-11 Bastian Family Holdings, Inc. Laser for steam turbine system
US8978380B2 (en) 2010-08-10 2015-03-17 Dresser-Rand Company Adiabatic compressed air energy storage process
ITMI20110830A1 (it) * 2011-05-12 2012-11-13 Alstom Technology Ltd Valvola per una turbina a vapore 700 c
EP2703699A1 (fr) * 2012-09-04 2014-03-05 Siemens Aktiengesellschaft Combinaison de soupapes pour une turbomachine
US9938895B2 (en) 2012-11-20 2018-04-10 Dresser-Rand Company Dual reheat topping cycle for improved energy efficiency for compressed air energy storage plants with high air storage pressure
US9279344B2 (en) * 2014-02-24 2016-03-08 General Electric Company Valve poppet element defining balance chamber
DE102014225608A1 (de) * 2014-12-11 2016-06-16 Siemens Aktiengesellschaft Vorrichtung und Verfahren zur Regelung eines Dampfmassenstroms bei einer Dampfturbine
EP3249183A1 (fr) * 2016-05-23 2017-11-29 Siemens Aktiengesellschaft Procédé destiné au chauffage d'une soupape
US10626749B2 (en) 2016-08-31 2020-04-21 General Electric Technology Gmbh Spindle vibration evaluation module for a valve and actuator monitoring system
US10151216B2 (en) 2016-08-31 2018-12-11 General Electric Technology Gmbh Insulation quality indicator module for a valve and actuator monitoring system
US10544700B2 (en) 2016-08-31 2020-01-28 General Electric Technology Gmbh Advanced startup counter module for a valve and actuator monitoring system
US10066501B2 (en) 2016-08-31 2018-09-04 General Electric Technology Gmbh Solid particle erosion indicator module for a valve and actuator monitoring system
US10871081B2 (en) 2016-08-31 2020-12-22 General Electric Technology Gmbh Creep damage indicator module for a valve and actuator monitoring system
US10156153B2 (en) * 2016-08-31 2018-12-18 General Electric Technology Gmbh Advanced tightness test evaluation module for a valve and actuator monitoring system
US10233786B2 (en) 2017-03-28 2019-03-19 General Electric Technology Gmbh Actuator spring lifetime supervision module for a valve and actuator monitoring system
CN113062778A (zh) * 2021-03-22 2021-07-02 安徽新宁能源科技有限公司 一种汽轮机进气阀

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Also Published As

Publication number Publication date
EP1502010A1 (fr) 2005-02-02
WO2003093653A1 (fr) 2003-11-13
DE10219948A1 (de) 2003-11-13
DE50306508D1 (de) 2007-03-29
AU2003240766A1 (en) 2003-11-17
US7223065B2 (en) 2007-05-29
US20050063818A1 (en) 2005-03-24

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