EP1881164A1 - Vorrichtung für das Regulieren von Absperrventilen einer Dampfturbinenanlage - Google Patents

Vorrichtung für das Regulieren von Absperrventilen einer Dampfturbinenanlage Download PDF

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Publication number
EP1881164A1
EP1881164A1 EP06425509A EP06425509A EP1881164A1 EP 1881164 A1 EP1881164 A1 EP 1881164A1 EP 06425509 A EP06425509 A EP 06425509A EP 06425509 A EP06425509 A EP 06425509A EP 1881164 A1 EP1881164 A1 EP 1881164A1
Authority
EP
European Patent Office
Prior art keywords
hydraulic
steam
slide valve
distributor
turbine plant
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
EP06425509A
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English (en)
French (fr)
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EP1881164B1 (de
Inventor
Marco Bruzzone
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.)
Ansaldo Energia SpA
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Ansaldo Energia SpA
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Publication date
Application filed by Ansaldo Energia SpA filed Critical Ansaldo Energia SpA
Priority to EP06425509.4A priority Critical patent/EP1881164B1/de
Publication of EP1881164A1 publication Critical patent/EP1881164A1/de
Application granted granted Critical
Publication of EP1881164B1 publication Critical patent/EP1881164B1/de
Not-in-force 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/12—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled
    • F01K23/16—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engines being mechanically coupled all the engines being 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

Definitions

  • the present invention relates to a device for regulating the intercept valves of a steam-turbine plant.
  • the present invention relates to a device for regulating the intercept valves of a steam-turbine plant connected to a high-power turbogenerator for the production of electric power.
  • a steam-turbine plant comprises: a boiler for the production of superheated steam; a high-pressure turbine; a medium-pressure turbine; at least one low-pressure turbine; a circuit for supplying steam comprising a first connection branch between the boiler and the high-pressure turbine, a second connection branch between the high-pressure turbine and the medium-pressure turbine; control valves arranged along the first branch; and intercept valves arranged along the second branch.
  • a steam-turbine plant of the type described above is supplied with superheated steam and can be equipped with a boiler with a high capacity of thermal modulation, for example a gas boiler, or else with a boiler with a low capacity of thermal modulation, such as for example a fluid-bed boiler designed to burn solid fuel characterized by a low calorific value and by a slow combustion that determines long stay times of the solid fuel in the boiler.
  • a boiler with a high capacity of thermal modulation for example a gas boiler
  • a boiler with a low capacity of thermal modulation such as for example a fluid-bed boiler designed to burn solid fuel characterized by a low calorific value and by a slow combustion that determines long stay times of the solid fuel in the boiler.
  • a steam-turbine plant with boiler with low capacity of modulation of the thermal power must necessarily comprise a hydraulic circuit having: a first by-pass branch, which is provided with a first by-pass valve, designed to exclude totally or in part the supply of steam to the high-pressure turbine; and a second by-pass branch, which is provided with a second by-pass valve designed to exclude totally or at least in part the supply of steam to the medium-pressure and low-pressure turbines.
  • modulation is obtained via partialization of the control valves, with simultaneous partialization (complementary to the partialization of the control valves) of the first by-pass valve, and partialization of the intercept valves, with simultaneous partialization (complementary to the partialization of the control valves) of the second by-pass valve.
  • the first and second by-pass branches and the respective first and second by-pass valves are not necessary, and the intercept valves are valves of an on-off type because, both in the stage of startup and in steady-state conditions, the regulation of just the control valves enables control of the entire steam-turbine plant.
  • the intercept valves are opened practically instantaneously, whilst the progressive increase of the flow rate of steam is regulated via the modulation of the boiler and the partialization of the control valves.
  • the aim of the present invention is to provide a device for regulating the intercept valves of a steam-turbine plant that is free from the drawbacks of the known art.
  • the present invention relates to a device for regulating the intercept valves of a steam plant, the regulating device comprising: a hydraulic circuit designed to supply a linear hydraulic actuator for actuating a first mechanical system of levers for simultaneously opening and closing the intercept valves; and a hydraulic power distributor designed to supply the linear hydraulic actuator selectively; the regulating device being characterized in that it comprises a control device, designed to control the hydraulic power distributor as a function of a signal correlated to the modes of operation of the steam-turbine plant so as to partialize, without solution of continuity, opening of the intercept valves between a position of complete closing and a position of maximum opening.
  • the reference numeral 1 designates as a whole an installation for the production of electric power.
  • the installation 1 comprises: a steam-turbine plant 2; a high-power turbogenerator 3; and a regulating device 4, designed to manage the steps of startup and of arrest of the plant 2 and to regulate the plant 2 during operation in steady-state conditions.
  • the steam-turbine plant 2 comprises: a shaft 5, which can turn about an axis A; a high-pressure turbine 6, a medium-pressure turbine 7, and two low-pressure turbines 8; a circuit 9 for circulation of the steam; a boiler 10 for generation of steam; a heater 11 for heating the steam at output from the high-pressure turbine 6; and a condenser 12 for condensing the steam at output from the low-pressure turbines 8.
  • the shaft 5 is common to the high-pressure turbine 6, to the medium-pressure turbine 7, to the low-pressure turbines 8, as well as to the rotor (not illustrated in the attached figures) of the turbogenerator 3.
  • the circuit 9 comprises: a branch 13 for connection between the boiler 10 and the high-pressure turbine 6 for supplying superheated steam (designated by SH) at a pressure of approximately 150 bar; a branch 14 for connection between the high-pressure turbine 6 and the heater 11 for supplying steam at a pressure of approximately 10 bar to the heater 11; a branch 15 for connection between the heater 11 and the medium-pressure turbine 7 for supplying reheated steam (designated by RH) at a pressure of approximately 10 bar; a branch 16 for connection between the medium-pressure turbine 7 and the common inlet to the two low-pressure turbines 8 at a pressure of approximately 4 bar; and two branches 17 for connection between the low-pressure turbines 8 and the condenser 12.
  • SH superheated steam
  • RH reheated steam
  • the circuit 9 comprises a by-pass branch 18 for connecting the branch 13 directly to the branch 14 and excluding totally or in part the supply of steam to the high-pressure turbine 6, and a by-pass branch 19 for connecting the branch 15 directly to at least one of the branches 17 so as to exclude totally or in part the supply of steam to the medium-pressure turbine 7, and to the low-pressure turbines 8.
  • the circuit 9 comprises: control valves 20, which are commonly referred to as CVs and are arranged in parallel along the branch 13 for regulating the flow of steam to the high-pressure turbine 6; a by-pass valve 21 set along the by-pass branch 18; intercept valves 22, which are commonly referred to as IVs and are arranged in parallel along the branch 15 for regulating the flow of steam to the medium-pressure turbine 7 and to the low-pressure turbines 8; and a by-pass valve 23 along the by-pass branch 19.
  • the circuit 9 also comprises an emergency valve 24 of an on-off type, set along the branch 13 upstream of the control valves 20, and an emergency valve 25 of an on-off type, set along the branch 15 upstream of the intercept valves 22.
  • control valves 20 are illustrated as a single valve; however, the control valves 20 are generally eight in number and are arranged in parallel along the branch 13.
  • intercept valves 22 are illustrated as a single valve; however, the intercept valves 22 are generally two in number and are arranged in parallel along the branch 15 according to what is illustrated in greater detail in Figure 2.
  • the boiler 10 is of the fluid-bed type and is designed to be supplied with solid fuels characterized by a low calorific value and by a long stay in the boiler. Consequently, the thermal power supplied by the boiler 10 can be varied over times that are very long and certainly inadequate for the needs of regulation of the plant 2.
  • the heater 11 is designed to heat the steam at output from the high-pressure turbine 6 prior to supply of the steam to the medium-pressure turbine 7.
  • the regulating device 4 has the functions of: regulating the flow rate of the steam; preventing the shaft 5 from exceeding a given threshold of angular velocity; and modulating the flow of steam during startup of the installation 1.
  • the regulating device controls the control valves 20, the intercept valves 22, the by-pass valves 21, 23, and the emergency valves 24 and 25.
  • the regulating device 4 comprises a hydraulic circuit 26 and a control unit 27.
  • the by-pass valves 21 and 23 are actuated by a pneumatic circuit (not illustrated in the attached figures) and are controlled by the control unit 27.
  • the hydraulic circuit 26 comprises: a pump 28 that supplies oil under pressure to a valve 29 of an on-off type, referred to as "safety block”; a valve 30 of an on-off type, referred to as “mechanical overspeed trip device” and connected in series to the valve 29; a load limiter 31; a control device 32 for controlling the intercept valves 22; a hydraulic power distributor 33; a hydraulic power actuator 34; and a tank 35 for collecting the oil.
  • the regulating device 4 comprises: a mechanical system of levers 36, which is actuated by the control device 32 and is designed to actuate the hydraulic power distributor 33 that modulates the supply of the oil coming from the pump 28 to the hydraulic actuator 34; and a mechanical system of levers 37 that is connected to the hydraulic actuator 34 and is able to actuate simultaneously the two intercept valves 22 arranged in parallel.
  • the regulating device 4 interacts mechanically with the shaft 5 through the valve 30 and the control device 32.
  • the mechanical overspeed trip valve 30 is actuated mechanically as a function of the velocity of the shaft 5.
  • a mechanical trip of a known type and not illustrated in the attached figures, closes the valve 30 and controls closing of the emergency valves 24 and 25 according to modalities that are known and not illustrated in the attached figures.
  • the regulating device 32 is controlled by: a tachometric member 38, sensitive to the angular velocity of the shaft 5; the oil at output from the load limiter 31; and the control unit 27.
  • the load limiter 31 is a device of a known type, which is able to regulate the pressure of the oil of the hydraulic circuit 26 downstream of the load limiter 31 itself between zero and a maximum value as a function of values at the point of delivery.
  • the control unit 27 via a signal SA, controls the state of the "safety block” valve 29, which is normally open and is closed only in the case of faulty operation (pressure, temperature of the steam, etc. outside ranges of acceptability).
  • the signal SM is a signal correlated to the modes of operation of the plant 2: the startup stage, the steady-state stage, the arrest stage; and to other parameters of operation of the plant 2, such as, for example, the commissioning of the plant 2.
  • the regulating device 4 differs from a known regulating device as regards the presence of the control device 32 that enables modulation of the intercept valves 22, which otherwise would follow a law of opening of an on-off type.
  • control device 32 comprises: a frame F; a regulating hydraulic distributor 39, co-operating with the tachometric member 38; a hydraulic cylinder 40, which is actuated by the hydraulic distributor 39 and is connected to the mechanical system of levers 36; and a linear electrical actuator 41, which is driven by the signal SM and is connected to the regulating hydraulic distributor 39 and to the mechanical system of levers 36.
  • the hydraulic distributor 39 is a three-way distributor comprising a liner 42 fixed to the frame F, a slide valve 43, which can slide in a direction D1 within the liner 42 and a slide valve 44, which can slide in the direction D1 within the slide valve 43.
  • the slide valve 43 is actuated by the linear electrical actuator 41 and, in feedback, by the mechanical system of levers 36, whilst the slide valve 44 is actuated by the tachometric member 38 as a function of the velocity of the shaft 5.
  • the slide valve 43 is mobile between two end positions, namely, a position of closing of supply (illustrated in Figure 3) and a position of supply, and between a plurality of intermediate positions, which are able to partialize the flow of oil to the hydraulic cylinder 40.
  • the slide valve 44 is coaxial to the slide valve 43 and to the liner 42 and is able to perform slight displacements in the direction D1 with respect to a position of equilibrium so as to supply and discharge the hydraulic cylinder 40 in a selective way.
  • the hydraulic cylinder 40 is a single-acting cylinder fixed to the frame F that comprises a piston 45 fixed to a stem 46 and a spring 47 for counteracting the displacement of the piston 45 caused by the inflow of oil into the hydraulic cylinder 40.
  • the stem 46 is connected to the mechanical system of levers 37, along which is set a damper 48.
  • the piston 45 and the stem 46 are mobile in the direction D1.
  • the tachometric member 38 comprises: a shaft 49, which can turn about its own axis A1, parallel to the direction D1, with respect to the frame F; two eccentric rotating masses 50, which are hinged to an extension to the shaft 49; a spring 51, connected to the two rotating masses 50; and two levers 52, fixed to the masses 50.
  • the shaft 49 is connected, via a motor reducer (not illustrated in the attached figures), to the shaft 5.
  • a motor reducer not illustrated in the attached figures
  • the spring 51 is calibrated to operate in a given range of velocities of around 3000 r.p.m., which is the theoretical value imposed on the rotation of the rotor (not illustrated) of the turbogenerator 3.
  • the linear electrical actuator 41 is coupled to a rod 53 parallel to the direction D1 and mobile in the direction D1.
  • the mechanical system of levers 36 comprises two stems 54 and 55, between which is set the damper 48.
  • the stem 55 actuates the hydraulic power distributor 33 directly, whilst the stem 54 is hinged to a lever 56, which is transverse to the direction D1 and is in turn hinged to the stem 46, to a rod 57 parallel to the direction D1,
  • a lever 58 Pivoted at the top end ( Figure 3) of the rod 57 is a lever 58, which is transverse to the direction D1 and hinged to which are hinged two rods 59 and 60 parallel to the direction D1.
  • the rod 60 is in turn hinged to a bracket 61 fixed to the frame F, whilst the rod 59 is hinged to a lever 62, transverse to the direction D1.
  • the lever 62 is hinged to the rod 53, in an end area, and to the slide valve 43, in a median area.
  • the mechanical system of levers 36 brings about actuation of the linear hydraulic power distributor 33 as a function of the position assumed by the piston 45 of the cylinder 40 and determines the position of the slide valve 43 as a function of the position assumed by the rod 53 following upon actuation of the linear hydraulic actuator 41 and of the position assumed by the stem 54.
  • each displacement of the piston 45 in a given direction brings about a displacement of the slide valve 43 aimed at limiting the displacement of the piston 45 itself.
  • the linear electrical actuator 41 In steady-state operating conditions, the linear electrical actuator 41 is in a fixed position. If the velocity of the shaft 5 exceeds a threshold value, the tachometric member 38 brings about a displacement of the slide valve 44 in the direction opposite to the direction D1, which sends into discharge part of the oil contained in the cylinder 40. Consequently, also the stems 54 and 55 shift in the direction opposite to the direction D1, so causing a partial choking of the intercept valves 22 (not illustrated in Figure 3) and the slowing-down of the shaft 5.
  • the mechanical system of levers 36 brings about a displacement of the rod 59 in the direction opposite to the direction D1 and a displacement in the direction opposite to the direction D1 of the slide valve 43, with partial or total closing of the discharge of the oil from the cylinder 40.
  • the displacement of the slide valve 43 can be such as to set the hydraulic distributor 39 in a position of supply of oil to the cylinder 40. This feedback system enables rapid restoration of the velocity of the shaft 5 that has been set.
  • the control device 32 is driven, via the electrical signal SM, by the oil at a modulated pressure supplied by the load limiter 31 and by the tachometric member 38 sensitive to the velocity, which is of no effect in the stage of startup of the steam-turbine plant 2.
  • the linear hydraulic actuator 41 is actuated for displacing the slide valve 43 in the direction opposite to the direction D1 so as to supply the cylinder 40 and bring about a displacement of the stems 46, 54 and 55 in the direction D1 and consequent opening of the valves.
  • the mechanical system of levers 36 brings about a displacement of the slide valve 43 in the direction D1, with the tendency to shut off supply of the oil to the cylinder 40.
  • the mechanical system of levers 46 guarantees in this way a progressive supply of oil to the cylinder 40 in combination with the signal SM for controlling the linear electrical actuator 41.
  • the control device 32 enables, in the stage of startup of the steam-turbine plant 2, a progressive opening of the intercept valves 22 according to what is illustrated in the diagram of Figure 4, which gives on the ordinate the percentage of opening as a function of time T.
  • the curve IV (dashed line) shows a preferred law of opening of the intercept valves 22, whilst the curve CV shows a preferred law of opening of the control valves 20.
  • the time T1 is the instant at which the switch of the turbogenerator 3 is set in the closed condition.
  • the controlled opening of the intercept valves 22 and the control in steady-state conditions of the intercept valves 22 themselves are rendered possible thanks to the insertion of the control device 32 in a known regulating device 4, without requiring the replacement of the intercept valves 22.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP06425509.4A 2006-07-21 2006-07-21 Vorrichtung für das Regulieren von Absperrventilen einer Dampfturbinenanlage Not-in-force EP1881164B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06425509.4A EP1881164B1 (de) 2006-07-21 2006-07-21 Vorrichtung für das Regulieren von Absperrventilen einer Dampfturbinenanlage

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Application Number Priority Date Filing Date Title
EP06425509.4A EP1881164B1 (de) 2006-07-21 2006-07-21 Vorrichtung für das Regulieren von Absperrventilen einer Dampfturbinenanlage

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EP1881164A1 true EP1881164A1 (de) 2008-01-23
EP1881164B1 EP1881164B1 (de) 2016-09-14

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2131013A1 (de) * 2008-04-14 2009-12-09 Siemens Aktiengesellschaft Dampfturbinensystem für ein Kraftwerk
WO2010034659A2 (de) * 2008-09-24 2010-04-01 Siemens Aktiengesellschaft Dampfkraftanlage zur erzeugung elektrischer energie
EP2331815A1 (de) * 2008-09-10 2011-06-15 United Technologies Corporation Kältemittelbetriebenes ventil für ein geothermie-kraftwerk
RU2778264C1 (ru) * 2022-02-25 2022-08-17 Общество с ограниченной ответственностью "Винтовые машины - энергия" Электростанция на базе водогрейной котельной
EP4321738A1 (de) * 2022-05-26 2024-02-14 General Electric Technology GmbH System und verfahren zur hydraulischen betätigung von haupt- und bypassventilen einer dampfturbine

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0178617A1 (de) * 1984-10-15 1986-04-23 Hitachi, Ltd. Dampfkraftanlage mit Turbinenbypassanlage
US4598551A (en) * 1985-10-25 1986-07-08 General Electric Company Apparatus and method for controlling steam turbine operating conditions during starting and loading
JPS62101809A (ja) * 1985-10-29 1987-05-12 Hitachi Ltd 再熱系を有する一軸コンバインドプラント
US5203160A (en) * 1990-10-18 1993-04-20 Kabushiki Kaisha Toshiba Combined generating plant and its start-up control device and start-up control method
US5361585A (en) * 1993-06-25 1994-11-08 General Electric Company Steam turbine split forward flow
DE10042317A1 (de) * 2000-08-29 2002-03-14 Alstom Power Nv Dampfturbine und Verfahren zur Einleitung von Beipassdampf

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP0178617A1 (de) * 1984-10-15 1986-04-23 Hitachi, Ltd. Dampfkraftanlage mit Turbinenbypassanlage
US4598551A (en) * 1985-10-25 1986-07-08 General Electric Company Apparatus and method for controlling steam turbine operating conditions during starting and loading
JPS62101809A (ja) * 1985-10-29 1987-05-12 Hitachi Ltd 再熱系を有する一軸コンバインドプラント
US5203160A (en) * 1990-10-18 1993-04-20 Kabushiki Kaisha Toshiba Combined generating plant and its start-up control device and start-up control method
US5361585A (en) * 1993-06-25 1994-11-08 General Electric Company Steam turbine split forward flow
DE10042317A1 (de) * 2000-08-29 2002-03-14 Alstom Power Nv Dampfturbine und Verfahren zur Einleitung von Beipassdampf

Cited By (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2131013A1 (de) * 2008-04-14 2009-12-09 Siemens Aktiengesellschaft Dampfturbinensystem für ein Kraftwerk
WO2009127523A3 (de) * 2008-04-14 2009-12-23 Siemens Aktiengesellschaft Dampfturbinensystem für ein kraftwerk
EP2331815A1 (de) * 2008-09-10 2011-06-15 United Technologies Corporation Kältemittelbetriebenes ventil für ein geothermie-kraftwerk
EP2331815A4 (de) * 2008-09-10 2014-04-09 United Technologies Corp Kältemittelbetriebenes ventil für ein geothermie-kraftwerk
WO2010034659A2 (de) * 2008-09-24 2010-04-01 Siemens Aktiengesellschaft Dampfkraftanlage zur erzeugung elektrischer energie
EP2213847A1 (de) * 2008-09-24 2010-08-04 Siemens Aktiengesellschaft Dampfkraftanlage zur Erzeugung elektrischer Energie
WO2010034659A3 (de) * 2008-09-24 2010-08-26 Siemens Aktiengesellschaft Dampfkraftanlage zur erzeugung elektrischer energie
CN102165145A (zh) * 2008-09-24 2011-08-24 西门子公司 用于产生电能的蒸汽动力设备
RU2481477C2 (ru) * 2008-09-24 2013-05-10 Сименс Акциенгезелльшафт Паросиловая установка для генерирования электрической энергии
US8925321B2 (en) 2008-09-24 2015-01-06 Siemens Aktiengesellschaft Steam power plant for generating electrical energy
RU2778264C1 (ru) * 2022-02-25 2022-08-17 Общество с ограниченной ответственностью "Винтовые машины - энергия" Электростанция на базе водогрейной котельной
EP4321738A1 (de) * 2022-05-26 2024-02-14 General Electric Technology GmbH System und verfahren zur hydraulischen betätigung von haupt- und bypassventilen einer dampfturbine

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