EP1862647A1 - Vorrichtung zur Steuerung der Öffnung eines Ein-Aus-Ventils eines Dampfturbinensystems über eine Umgehungsleitung - Google Patents

Vorrichtung zur Steuerung der Öffnung eines Ein-Aus-Ventils eines Dampfturbinensystems über eine Umgehungsleitung Download PDF

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Publication number
EP1862647A1
EP1862647A1 EP06126189A EP06126189A EP1862647A1 EP 1862647 A1 EP1862647 A1 EP 1862647A1 EP 06126189 A EP06126189 A EP 06126189A EP 06126189 A EP06126189 A EP 06126189A EP 1862647 A1 EP1862647 A1 EP 1862647A1
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EP
European Patent Office
Prior art keywords
cam
valve
section
opening
line
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.)
Withdrawn
Application number
EP06126189A
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English (en)
French (fr)
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
Original Assignee
Ansaldo Energia SpA
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Filing date
Publication date
Application filed by Ansaldo Energia SpA filed Critical Ansaldo Energia SpA
Publication of EP1862647A1 publication Critical patent/EP1862647A1/de
Withdrawn legal-status Critical Current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
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K7/18—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 the turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor

Definitions

  • the present invention relates to a device for controlling opening of an on-off valve of a steam turbine system with a bypass line parallel to a high-pressure turbine section.
  • the IV valves are opened before the CV valves : more specifically, when the CV valves begin opening, the IV valves are already open roughly 20 mm to allow the steam from the high-pressure section to flow into the RH steam line.
  • combination-cycle systems are not normally expected to operate at the rated load for prolonged periods of time, and so call for a high degree of flexibility.
  • the output load of a combination cycle depends on the "energy market", so the system must operate, not continuously, but at predetermined times according to market demand.
  • bypass line parallel to the high-pressure section is employed to facilitate startup and stoppage.
  • Ventilation is the phenomenon whereby the steam in said stages is heated as a result of poor efficiency of the high-pressure section caused by very low steam flow. Ventilation increases the temperature of the steam at the high-pressure section exhaust with respect to nominal values, thus resulting in turbine problems, and is directly proportional to the pressure at the high-pressure section exhaust.
  • DEHC electrohydraulic
  • a device for controlling opening of an on-off valve of a steam turbine system with a bypass line as claimed in Claim 1.
  • Number 1 in Figure 1 indicates a combination-cycle steam turbine system comprising a high-pressure first turbine section 2; a medium-pressure second turbine section 3; and a low-pressure third turbine section 4.
  • Section 2 is supplied by a line 7 with so-called SH steam, which is flow-regulated by a CV valve.
  • the outlet of section 2 communicates with the inlet of section 3 over a line 8 fitted with an RH heater.
  • the flow of so-called RH steam to section 3 is regulated by an IV valve downstream from the RH heater.
  • the outlet of section 3 communicates with the inlet of section 4 over a line 9; and a condenser 10 is provided at the outlet of section 4.
  • System 1 comprises a first bypass line 11, which connects line 8 to condenser 10, is parallel to the IV valve and to sections 3 and 4, and has a valve 12 for regulating the steam flow fed directly to condenser 10 without going through sections 3 and 4.
  • System 1 also comprises a second bypass line 13, which connects lines 7 and 8, is parallel to section 2 and to the CV valve, terminates upstream from the RH heater, and has a bypass valve 14 for regulating the steam flow fed directly to the RH heater and to section 3 without going through section 2.
  • Opening of the CV and IV valves during startup is controlled by a control device 20 shown partly in Figure 2.
  • Device 10 provides for mechanically regulating speed and load buildup by controlling opening of the CV and IV valves, in time with each other, by means of lever mechanisms 21 (shown partly).
  • lever mechanisms 21 the opening geometry and mode of the CV and IV valves are predetermined, rigidly defined, and mutually correlated, i.e. timing of the CV and IV valves is defined at the design stage.
  • Device 20 comprises a control member or so-called speed relay 22, the position of which determines the opening of the CV and IV valves. More specifically, speed relay 22 can be set as a function of the speed and load buildup requirements of system 1.
  • opening of the CV and IV valves is controlled in a definite sequence.
  • the established opening pattern of the CV and IV valves is shown in the Figure 3 graph, in which the y axis shows the degree of opening or lift of the valves expressed as a percentage, and the x axis shows displacement of speed relay 22 in millimetres.
  • Curve (c) shows the CV valve opening or lift pattern, and curve (b) the IV opening or lift pattern.
  • regulating device 20 produces predetermined valve opening patterns defined by curves (b) and (c).
  • device 20 comprises a transmission member or so-called secondary relay 24, which transmits control from a first portion 25 of lever mechanisms 21, activated by speed relay 22, to a second portion 26 of lever mechanisms 21, with controls opening of the IV valves in a manner not shown.
  • Secondary relay 24 determines the way in which opening of the CV and IV valves is correlated, and comprises: a single-acting actuator 27 with a rod 28, translation of which activates portion 26 of lever mechanisms 21; a control valve 29 with a piston 30 for regulating oil flow to actuator 27; a mechanical feedback system 31 activated by rod 28; and a lever 32 which activates piston 30.
  • the ends 34, 35 of lever 32 are hinged, about movable axes, to respective substantially vertical top rods 36, 37 forming part of portion 25 of lever mechanisms 21 and system 31 respectively.
  • An intermediate portion 38 of lever 32 is hinged about a movable axis to a bottom rod 39, which moves piston 30.
  • Rod 37 activates end 35 vertically in opposition to an elastic member 40, and is hinged at its top end to an intermediate portion 41 of a further lever 42 forming part of system 31.
  • lever 42 One end 43 of lever 42 is hinged to oscillate about a fixed axis, and the opposite end is fitted with a hinged cam-follower roller 48, which rolls along the outer periphery of a disk cam 50 also forming part of system 31.
  • Cam 50 is connected to rod 28 by a rack-and-pinion transmission, not shown in the drawings, and rotates about a respective fixed axis 51 in response to translation of rod 28.
  • Cam 50 which provides for mechanical position feedback of the IV valve, is designed to obtain the IV valve lift curve (b) shown in Figure 3.
  • cam 50 has a steeply sloping straight portion 52 ( Figure 4).
  • Portion 52 is connected, on one side, to a circular initial portion 53 by a connecting surface 54 of 16 mm in radius, equal to the radius of roller 48, and, on the other side, to a circular end portion 55 by a connecting surface 56.
  • cam 50 The profile of cam 50 is defined by the following movement of roller 48 (with respect to circular portion 53) as a function of the rotation angle of cam 50 (with respect to an initial angular position in which rod 28 is fully lowered) : Roller movement [mm] Cam rotation [°] 0 22 1,0 24 1,9 26 2, 9 28 4, 8 32 7, 6 37 11, 4 45 17, 1 85 22,8 148 28, 6 210 34,3 270
  • the profile of cam 50 so defined provides the necessary mechanical feedback to achieve optimum correlation between the opening of the CV and IV valves.
  • a more gradual IV valve opening curve than in curve (b) in Figure 3 is theoretically possible, provided the pressure angle A between cam 50 and roller 48 at the steepest point along the profile is less than 60°, to prevent roller 48 from sticking (pressure angle A is defined at the angle between the line perpendicular to the profile of cam 50, and the line tangent to the rotation axis of lever 42).
  • pressure angle A at the end of profile portion 52 i.e. the point at which pressure angle A is maximum, equals 56.4°.
  • device 20 ensures correct operation of a steam turbine by means of strictly preconfigured mechanical adjustment, thus enabling fast easy conversion of a system originally designed with no bypass.
EP06126189A 2005-12-15 2006-12-14 Vorrichtung zur Steuerung der Öffnung eines Ein-Aus-Ventils eines Dampfturbinensystems über eine Umgehungsleitung Withdrawn EP1862647A1 (de)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
ITTO20050873 ITTO20050873A1 (it) 2005-12-15 2005-12-15 Dispositivo per il comando di apertura di una valvola di intercettazione in un impianto di turbina a vapore provvisto di una linea di by-pass

Publications (1)

Publication Number Publication Date
EP1862647A1 true EP1862647A1 (de) 2007-12-05

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP06126189A Withdrawn EP1862647A1 (de) 2005-12-15 2006-12-14 Vorrichtung zur Steuerung der Öffnung eines Ein-Aus-Ventils eines Dampfturbinensystems über eine Umgehungsleitung

Country Status (2)

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EP (1) EP1862647A1 (de)
IT (1) ITTO20050873A1 (de)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010034659A2 (de) * 2008-09-24 2010-04-01 Siemens Aktiengesellschaft Dampfkraftanlage zur erzeugung elektrischer energie

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5191764A (en) * 1992-06-09 1993-03-09 Westinghouse Electric Corp. Governor valve positioning to overcome partial-arc admission limits
DE10042317A1 (de) * 2000-08-29 2002-03-14 Alstom Power Nv Dampfturbine und Verfahren zur Einleitung von Beipassdampf
US6457313B1 (en) * 2001-05-21 2002-10-01 Mitsubishi Heavy Industries, Ltd. Pressure and flow rate control apparatus and plant system using the same

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5191764A (en) * 1992-06-09 1993-03-09 Westinghouse Electric Corp. Governor valve positioning to overcome partial-arc admission limits
DE10042317A1 (de) * 2000-08-29 2002-03-14 Alstom Power Nv Dampfturbine und Verfahren zur Einleitung von Beipassdampf
US6457313B1 (en) * 2001-05-21 2002-10-01 Mitsubishi Heavy Industries, Ltd. Pressure and flow rate control apparatus and plant system using the same

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
HWA WOON BYEON ET AL: "DESIGNING A STANDARD THERMAL POWER PLANT FOR DAILY STARTUP/SHUTDOWNTHE HP BYPASS CONTROL AND SAFETY FUNCTION", ADVANCES IN INSTRUMENTATION AND CONTROL, INSTRUMENT SOCIETY OF AMERICA, RESEARCH TRIANGLE PARK, US, vol. 51, no. PART 2, 1996, pages 1295 - 1305, XP000639432, ISSN: 1054-0032 *

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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

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Publication number Publication date
ITTO20050873A1 (it) 2007-06-16

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