EP1502010A1 - Turbine a vapeur - Google Patents

Turbine a vapeur

Info

Publication number
EP1502010A1
EP1502010A1 EP03730179A EP03730179A EP1502010A1 EP 1502010 A1 EP1502010 A1 EP 1502010A1 EP 03730179 A EP03730179 A EP 03730179A EP 03730179 A EP03730179 A EP 03730179A EP 1502010 A1 EP1502010 A1 EP 1502010A1
Authority
EP
European Patent Office
Prior art keywords
valve
steam
steam turbine
control
pressure
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
EP03730179A
Other languages
German (de)
English (en)
Other versions
EP1502010B1 (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

Links

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, to a valve arrangement for supplying fresh steam to the steam turbine.
  • Steam turbines are known in which the fresh steam supply is regulated by nozzle regulation by means of a regulating stage, also called the first turbine stage.
  • a control stage has, for example, different sized exposure sectors, to which the live steam is fed via a live steam inlet with several control valves.
  • the control valves are preceded by a quick-closing valve.
  • Such an arrangement is described, for example, in the sales documentation of ABB Power Generation, Description No. HTGD N12018.
  • 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 turbines. Through different settings of the three or four control valves, the steam turbine can be operated at a plurality of part-load points and also within these part-load points
  • the sequentially actuatable control valves are either closed or opened completely or in a controlled manner.
  • Quick-closing valve and a downstream control valve Such steam turbines are described, for example, in the sales documentation of ABB Power Generation, Description No. HTGD 666 159 and a valve arrangement arranged therein for regulating the fresh steam supply in the same sales documentation, Description No. GMDT N06 014.
  • the live steam pressure can be variable in these steam turbines, for example in steam turbine systems for sliding pressure operation or in steam turbine systems, the circuit of which is combined with a gas turbine system.
  • the fresh steam pressure can also be set at a single pressure level for all operating loads.
  • valves in the steam turbine systems mentioned are preferably designed in such a way that valve vibrations are kept within limits due to an increased load and the longest possible damage-free operating life of the valve is guaranteed.
  • valves In the case of steam turbines without a control stage, and in particular those which are operated with a permanently set live steam pressure, the valves must be in throttled operation at all times in order to enable safe partial-load operation of the steam turbine. As a result, the valves are exposed to an increased load in comparison to the steam turbines with control stage. In the case of steam turbines without a control stage, the pressure is reduced exclusively via the valves, while in the case of steam turbines with a control stage the pressure is reduced via the valve and the upstream nozzles.
  • the quick-closing valves ensure safety for the live steam supply, but cannot perform a throttle function.
  • a steam turbine has a valve arrangement for regulating the live steam supply, which consists of two control or regulating valves which are connected in series.
  • the valve arrangement according to the invention enables a gradual reduction in the pressure loss via the two individual control valves during partial load operation, that is to say the energy converted during throttle operation is distributed to the two or more control valves.
  • the load on an individual control valve is thus greatly reduced compared to a valve arrangement with a quick-closing valve and only one control valve. This reduces the risk of valve vibrations and consequent possible valve damage.
  • the safety function of a quick-closing valve can be performed by the first control valve in the arrangement according to the invention, so that the safety provided by this valve arrangement is not reduced in comparison to the prior art.
  • valve arrangement according to the invention can be used in steam turbines both with and without a control stage. In steam turbines without a control stage, it particularly reduces the relatively high loads on the control valves. It is also suitable for steam turbines in fixed pressure operation and in operation with variable live steam pressure. Again, the valve arrangement according to the invention is particularly effective in steam turbines without a control stage and in particular in those in fixed-pressure operation, the reduction of valve vibrations caused by load.
  • the valve arrangement preferably has control valves of the type of a tubular valve or a relieved single-seat valve with a forward stroke.
  • the valve arrangement has the advantage that the problem of potential valve vibrations, in particular in the case of steam turbines without a control stage and in fixed-pressure operation, is solved by a simple arrangement of a single valve type and without loss of safety. It also offers the advantage that known control valves and actuators can be used. The same actuator is preferably used for all control or control valves.
  • FIG 1 is a diagram of a steam turbine plant in which the inventive
  • Valve arrangement for regulating the fresh steam supply is used
  • FIG. 2 shows a valve arrangement according to the invention with two series connected
  • FIG. 3 shows a valve arrangement according to the invention with two series connected
  • Control valves of the type of a preliminary stroke valve in a corner valve arrangement are provided.
  • FIG. 1 schematically shows a steam turbine system with a steam generator 1, which is connected to a steam turbine 3 via a live steam supply line 2.
  • the steam turbine 3 is coupled to a generator G.
  • the steam released in the turbine is fed to a condenser 4, the condensate occurring there being fed back to the water-steam cycle of the plant.
  • the feed line 2 has a valve arrangement 5 for regulating the
  • the valve arrangement here has a first control valve 6 and a second control valve 7 in the direction of flow, which are connected to one another in series.
  • the control valves 6 and 7 each have an actuator 6a or 7a, which are connected to a control or regulating device 8.
  • the two control valves can be set into a fully closed position, a fully open position or any partial open position.
  • the first control valve 6 can also take on the function of a quick-closing valve.
  • the live steam generated in the steam generator 1 has when entering the
  • Valve arrangement 5 has a live steam pressure PD I , which is gradually reduced there via the intermediate pressure P z to a steam pressure P D2 which corresponds to a full operating load or a predetermined partial load.
  • the actuators 6a and 7a can be designed, for example, as a hydraulic drive with an electrohydraulic converter.
  • Incoming electrical control signals Generate actuating movements on the throttle elements or blocking elements of the control valves 6 and 7.
  • FIG. 2 shows a first possible embodiment of the valve arrangement according to the invention, in which the control valves are designed as Rohn / entile.
  • the two control valves 6 and 7 can be combined in a common housing to form an assembly 20, which simplifies the installation effort when installed in the live steam supply line 2.
  • the two control valves 6 and 7 can expediently be of identical construction with identical or similar components. On the one hand, this allows the number of parts to be reduced and, on the other hand, the item price can be reduced by increasing the number of pieces.
  • the valve seats or diffusers 22 can be of the same or different design, as a result of which the flow cross sections of the two valves are either the same or different.
  • Both control valves 6 and 7 are designed here as single-seat angle valves without a preliminary stroke in the Rohn / entile type, which are flowed across at right angles to the valve stroke, while the outflow direction runs counter to the valve stroke direction.
  • the two control valves 6 and 7 in the assembly 20 shown here are arranged rotated by 90 ° with respect to one another. Accordingly, each control valve 6 contains a valve body 21 which cooperates with a valve seat 22 in its closed position. In FIG. 2, one valve body half in the closed position of the valve body 21 and the other valve body half in the maximum open position of the valve body 21 are shown for each valve body 21 with respect to a plane of symmetry 23 perpendicular to the plane of the drawing.
  • FIG. 3 shows a further embodiment of the invention
  • Ventilanordnunq Here it is in one with relieved single-seat valves with pre-stroke Corner valve arrangement designed. Similar to Figure 2, the two control valves 6 and 7 are rotated 90 ° to each other. Again, each control valve 6 contains a valve body 24, which cooperates with a valve seat 25 in its closed position. For each valve body 24 on the plane of symmetry 26, one half of the valve body is shown in the closed position of the valve body 24 and the other half of the valve body is shown in the maximum open position of the valve body 24.
  • valve arrangement according to the invention is operated as follows:
  • the live steam pressure P D1 set by the steam generator is present on the input side of the first control valve 6.
  • This pressure can either be a fixed predetermined pressure or a pressure which is variably predetermined by corresponding measures in the boiler system.
  • 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 D present on the inlet side is now. throttled to the current working pressure P D2 .
  • this takes place in two stages, the invention comprising two different methods for the first stage:
  • the first control valve 6 throttles the live steam pressure P D ⁇ to an intermediate pressure P z , this throttling being controlled.
  • control valve 6 is set to a valve lifting point, for example.
  • the resulting intermediate pressure is then variable depending on the live steam pressure P D ⁇ .
  • This intermediate pressure P z is expediently always somewhat higher than the maximum working pressure P D2 required by the steam turbine 3 -
  • the variable live steam pressure P D2 is regulated to a load-dependent intermediate pressure P z by means of the control valve 6.
  • the first control valve 6 is actuated, for example, by a control circuit, the command variable of which is expediently formed by the load-dependent intermediate pressure P z .
  • control deviations are determined by a target-actual comparison of the values of the intermediate pressure P z and compensated for by suitable control commands.
  • the second control valve 7 now throttles from the intermediate pressure P z to the working pressure P D2 , this throttling only taking place in a controlled manner.
  • a control circuit for the actuation of the second control valve 7 contains, for example, the performance of the steam turbine or the speed of the rotor of the machine as reference variables.
  • the working pressure P D2 is set according to these command variables. This means that control deviations, which are compensated for by a target-actual comparison of the values of the working pressure P D2 or the command variables according to which the working pressure is set, are compensated by suitable control commands.
  • the valve arrangement 5 in the invention manages with two simple control loops.
  • This construction reduces the effort for regulating and / or controlling the valve arrangement 5.
  • the two-stage throttling has the result that the maximum pressure differences individually applied to the control valves 6 and 7 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 entirely.
  • valve body 2 valve seat 3 plane of symmetry 4 valve body 5 valve seat 6 plane of symmetry

Landscapes

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

Abstract

L'invention concerne une turbine à vapeur (3) présentant un ensemble soupape (5) servant à réguler l'apport de vapeur fraîche dans la turbine, ledit ensemble soupape étant composé de deux soupapes de régulation (6, 7) montées en série. Ces deux soupapes de régulation (6,7) permettent une diminution progressive de la pression de vapeur fraîche et assurent un fonctionnement fiable de la turbine lorsque cette dernière est fonctionne en charge partielle. L'ensemble soupape est particulièrement approprié pour des turbines à vapeur dépourvues d'étage de régulation, fonctionnant à une pression fixe.
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 true EP1502010A1 (fr) 2005-02-02
EP1502010B1 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
US10066501B2 (en) 2016-08-31 2018-09-04 General Electric Technology Gmbh Solid particle erosion 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
US10871081B2 (en) 2016-08-31 2020-12-22 General Electric Technology Gmbh Creep damage indicator module for a valve and actuator monitoring system
US10626749B2 (en) 2016-08-31 2020-04-21 General Electric Technology Gmbh Spindle vibration evaluation 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
US10151216B2 (en) 2016-08-31 2018-12-11 General Electric Technology Gmbh Insulation quality indicator 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
AU2003240766A1 (en) 2003-11-17
EP1502010B1 (fr) 2007-02-14
DE10219948A1 (de) 2003-11-13
DE50306508D1 (de) 2007-03-29
US7223065B2 (en) 2007-05-29
US20050063818A1 (en) 2005-03-24
WO2003093653A1 (fr) 2003-11-13

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