EP2606205A2 - Turbine à vapeur dotée d'un surchauffeur - Google Patents

Turbine à vapeur dotée d'un surchauffeur

Info

Publication number
EP2606205A2
EP2606205A2 EP11760733.3A EP11760733A EP2606205A2 EP 2606205 A2 EP2606205 A2 EP 2606205A2 EP 11760733 A EP11760733 A EP 11760733A EP 2606205 A2 EP2606205 A2 EP 2606205A2
Authority
EP
European Patent Office
Prior art keywords
steam
pressure part
low
control valve
volume flow
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
EP11760733.3A
Other languages
German (de)
English (en)
Other versions
EP2606205B1 (fr
Inventor
Richard Geist
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.)
Siemens AG
Original Assignee
Siemens 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 Siemens AG filed Critical Siemens AG
Publication of EP2606205A2 publication Critical patent/EP2606205A2/fr
Application granted granted Critical
Publication of EP2606205B1 publication Critical patent/EP2606205B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

Links

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
    • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/22—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 turbines having inter-stage steam heating
    • F01K7/24—Control or safety means specially adapted therefor
    • 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
    • F01D13/00—Combinations of two or more machines or engines
    • F01D13/02—Working-fluid interconnection of machines or engines
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F22—STEAM GENERATION
    • F22G—SUPERHEATING OF STEAM
    • F22G5/00—Controlling superheat temperature
    • F22G5/18—Controlling superheat temperature by by-passing steam around superheater sections
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/20—Heat transfer, e.g. cooling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2260/00—Function
    • F05D2260/60—Fluid transfer
    • F05D2260/606—Bypassing the fluid

Definitions

  • the invention relates to a steam turbine according to the preamble of claim 1 and a method for controlling the moisture content of a steam turbine according to the preamble of Pa ⁇ tentencies 5.
  • Conventional steam turbines have at least one high-pressure section and a low pressure part. With the low-pressure part, the temperature of the steam drops very sharply, resulting in partial condensation of the steam. However, the low-pressure part is very sensitive to the moisture content of the steam. Reaches the vapor in the low pressure part of the turbine ei ⁇ ne wetness of approximately 8 to 10 percent, measures to ergrei ⁇ fen, which reduce the moisture content of the steam prior to entering the low pressure part to an acceptable level is.
  • the steam is supplied for this purpose before entering the low-pressure part of a reheatening.
  • the steam is heated, so that the moisture content decreases.
  • the reheat fed and raised to approximately the temperature of the live steam.
  • the steam is then fed to the low-pressure part. Without a sol ⁇ che reheat steam turbine would have to be stopped because condensed water droplets may impinge on the rotating turbine blades and thus would cause damage to the turbine.
  • the total steam flow is first fed to a reheat and - in at least one other switching position, which is located between the first and second end position, a first partial volume flow of the reheat is supplied and a second partial volume flow without reheat the low pressure part can be fed.
  • the steam turbine is improved to the effect that by the control valve and its design no longer the entire steam flow rate must be supplied to the intermediate overheating when reaching a certain moisture content, but that only a partial volume flow is removed and this is the intermediate superheating is supplied. Subsequently, the temporarily heated partial volume flow is fed together with the remaining steam volume flow to the low-pressure part of the steam turbine.
  • the control valve can be infinitely adjusted between the first and the second end position, so that the partial volume flow supplied to the reheat can be selected steplessly.
  • Steam turbine regulate be used and need only be provided with the appropriate supply and discharge lines for reheating.
  • the internal control valves also have the advantage that they can be accommodated very space-saving in the housing of the steam turbine.
  • a further advantageous embodiment of the invention provides that the steam volume flow, which is supplied to the intermediate overheating, is dependent on the moisture and / or the temperature of the steam after the high-pressure part. It is as described previously necessary that the Nässege holding does not exceed ⁇ the steam before entering the low-pressure part of a permissible value. This value is übli ⁇ chate at a moisture content of 8 to 10 percent. The wetness describes the water content, ie in the steam. To ensure that this does not exceed the permissible value, the moisture content is preferably at the outlet of the high-pressure part by measuring the temperature and / or Moisture content determined by itself.
  • the measurement after the high ⁇ pressure part does not mean that necessarily must be measured directly at the outlet of the high pressure part, but only that the measurement between the end of the high pressure part and the supply must be made for reheating, so that a corresponding partial volume flow of the reheat can be supplied.
  • the control valve can preferably be connected to a Re ⁇ geliki, which makes a corresponding adjustment of the Re ⁇ gelventils due to the measured temperature and / or humidity, so that the necessary partial volume flow of the reheatening is supplied.
  • a further advantageous embodiment of the invention provides that the steam, which is supplied to the reheat, is heated to a temperature at which the moisture in the steam is lowered to a value permissible for the low-pressure part. Conveniently, the steam is not heated above this level, otherwise more energy is consumed for reheat than is necessary. This would the efficiency of the steam turbine unnecessarily 29lech ⁇ ter.
  • the inventive method for controlling the moisture content on entering the low-pressure part of a steam turbine where ⁇ particular includes a switchable control valve in the steam turbine is characterized by the following steps:
  • the method thus differs from the prior art in that really only the necessary partial volume flow of the reheat is supplied and not as previously the total steam volume flow. By removing a previously determined partial volume flow, a particularly efficient operation of the steam turbine can be ensured. As a result, the efficiency of the steam turbine over the prior art is significantly improved. Further advantages and embodiment of the invention will be described below with reference to FIGS.
  • Figure 1 is a circuit diagram of a steam turbine according to the invention
  • Figure 2 is a sectional view of the steam turbine according to the invention in operation without reheat and
  • Figure 3 is a sectional view of the turbine according to the invention during operation with reheat.
  • FIG. 1 shows schematically the block diagram of a steam turbine according to the invention.
  • the steam turbine comprises at least one high-pressure part 1 and one low-pressure part 2.
  • the live steam initially flows via an inlet valve 5 into the high-pressure part 1 of the steam turbine.
  • the un ⁇ ter high pressure and high temperature is standing steam relaxes and is expanded to a lower pressure and a nied- complicated temperature steam is then passed to the low pressure part 2 of the steam turbine where it is further expanded and thereby further to temperature and pressure loses.
  • a control valve 3 is arranged, which is preferably infinitely movable between two ⁇ end positions.
  • the control valve 3 In the first end position of the control valve 3, the control valve 3 is fully ⁇ constantly open, whereby the entire steam flow V from the high-pressure part 2 is completely supplied via the control valve 3 to the Never ⁇ derdruckteil 2. In its second end position, the control valve 3 is completely closed, so that the entire steam volume flow V is guided by the high-pressure part 1 via a reheat 4, where it is heated and then fed to the low-pressure part 2. In the interim ⁇ rule overheating 4 is essentially a heat exchanger. By heating the steam volume flow V, the moisture in the steam volume flow V is reduced.
  • the control valve 3 can be moved continuously between these two Endpo ⁇ sitions. In this case, depending on the position of the control valve 3, a more or less large vapor volume flow V z is conducted via the reheat 4 and the remaining vapor volume flow Vo is added directly to the low-pressure part 2 via the control valve 3.
  • the sectionvolu ⁇ menstrum V z is chosen only as large as necessary to achieve a certain moisture content of the total volume flow V at the entrance of the low pressure part 2. Characterized that only a partial volume flow V z of the SwissGerman- overheating 4 is supplied, the result is an energetically günsti ⁇ ger operation of the steam turbine. A heating of the total steam flow V as this is still necessary, can be omitted.
  • the vapor volume flow V z, which rule overheating of the intermediate 4 is supplied, is dependent on the moisture and / or temperature of the steam to the high pressure part 1. A moisture content of 8 to 10 percent should not be exceeded in the re ⁇ gel.
  • the regulation takes place so that the control valve 3 is more or less open, depending on the moisture content and / or the tempering temperature ⁇ and so a more or less large part of the volume flow V z reheat 4 is added.
  • the steam, which is supplied to the reheat 4, is doing to a
  • the method for controlling the moisture content on entering the low-pressure part of the steam turbine 2 ge ⁇ shows to be short on the basis of the shown in Figure 1 block diagram.
  • it is initially not ⁇ agile, to determine the moisture content and / or the temperature of the steam to the high pressure part. 1
  • the determination of the moisture content or the temperature must be carried out before the control ⁇ valve 3, so as to be able to initiate suitable steps NEN to reduce the moisture content or to increase the steam temperature.
  • the to be removed Partial volume flow V z depends on the wetness content and / or the temperature of the steam after the high-pressure part 1.
  • the partial volume flow V z which is the reheate 4 supplied, is set via the control valve 3. If the control valve 3 is moved in the closing direction, there is a stronger throttling on the control valve 3, whereby more Dampfvolu ⁇ menstrom V z flows through the reheater 4.
  • FIG. 2 shows an axial section through a steam turbine with a high-pressure part 1 and a low-pressure part 2.
  • the never ⁇ derdruckteil 2 is formed in three stages. Based on the figure 2, the vapor flow V is to be displayed at fully open control valve 3.
  • the steam volume flow V first enters via an inlet valve 5 and the Einströmge ⁇ housing the steam turbine in the high pressure part 1 of the steam turbine ⁇ ne and is initially relaxed there. The thus relaxed steam leaves the high pressure part 2 and flows through the control ⁇ valve 3, which is formed in the embodiment as an internal control gel.
  • control valve 3 is in a first end position in which it is fully open. As a result, it represents only a very low flow resistance, so that the entire steam flow V flows completely through the control valve 3, directly into the low-pressure part 2 of the steam turbine ⁇ and relaxed to the ambient pressure or a slight negative pressure and then the Nie ⁇ derdruckteil 2 leaves.
  • the control valve 3 is always one of its first end position, ie in the fully open position, when coming from the high pressure part 1 steam flow V a permissible value in terms of its wetness and / or temperature. If the permissible temperature is exceeded or the permissible moisture content of the steam is exceeded, the control valve 3 is closed more or less strongly.
  • control valve 3 If the control valve 3 is completely closed, i. if it is in its second end position, then the entire volume flow V is fed to a reheate 4. This case is shown in more detail in FIG.
  • FIG. 3 shows the steam turbine shown in FIG. In this setting, the control valve 3 is completely ge ⁇ closed so that all of the vapor volume flow V of the reheat 4 is supplied and is heated there.
  • the moisture content in the steam is reduced to a permissible value and the steam is then supplied to the low-pressure part 2.
  • first end position (FIG. 2) and the second end position (FIG. 3) there are preferably any number of intermediate positions in which a partial volume flow Vo of the steam is added directly to the low-pressure part 2 via the control valve 3 and a second partial volume flow V z via the intermediate superheating 4 is first heated and then the low pressure part 3 of the steam turbine is added.
  • the two partial volume flows Vo / V z are mixed in the inner casing of the steam turbine and enter as a total volume flow V in the low-pressure part 2 a.
  • the inventive steam turbine does not need as previously the case, the entire flow of a reheat be added if the moisture content exceeds a permissible value in the volume flow or the permissible steam Tempe ⁇ temperature is not reached.
  • the steam turbine according to the invention is very productive ago ⁇ parts in applications with widely fluctuating steam parameters, such as the case of biomass or solar application.
  • the moisture content or the temperature of the steam can be adjusted by the fiction, ⁇ modern steam turbine very quickly to a permissible value.

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 comprenant au moins une partie haute pression (1) et au moins une partie basse pression (2); au moins une soupape de régulation (3) étant disposée entre la partie haute pression (1) et la partie basse pression (2). La soupape de régulation (3) est mobile, de préférence, en continu entre deux positions terminales : dans une première position terminale de la soupape de régulation, le flux volumétrique de vapeur peut être entièrement cédé à la partie basse pression (2) par ladite au moins une soupape de régulation (3) et, dans une deuxième position terminale, la totalité du flux volumétrique de vapeur est d'abord cédé à un surchauffeur (4) et dans au moins une autre position de commutation située entre la première et la deuxième position, un premier flux volumétrique partiel peut être cédé au surchauffeur (4) et un deuxième flux volumétrique partiel peut être cédé à la partie basse pression (2) sans surchauffeur. L'invention concerne également un procédé de régulation de la teneur en humidité à l'entrée de la partie basse pression (2) d'une turbine à vapeur, la turbine comportant une soupape de régulation (3) commutable.
EP11760733.3A 2010-09-29 2011-09-05 Turbine à vapeur dotée d'un surchauffeur Not-in-force EP2606205B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE201010041627 DE102010041627A1 (de) 2010-09-29 2010-09-29 Dampfturbine mit Zwischenüberhitzung
PCT/EP2011/065283 WO2012041649A2 (fr) 2010-09-29 2011-09-05 Turbine à vapeur dotée d'un surchauffeur

Publications (2)

Publication Number Publication Date
EP2606205A2 true EP2606205A2 (fr) 2013-06-26
EP2606205B1 EP2606205B1 (fr) 2016-08-31

Family

ID=44675556

Family Applications (1)

Application Number Title Priority Date Filing Date
EP11760733.3A Not-in-force EP2606205B1 (fr) 2010-09-29 2011-09-05 Turbine à vapeur dotée d'un surchauffeur

Country Status (3)

Country Link
EP (1) EP2606205B1 (fr)
DE (1) DE102010041627A1 (fr)
WO (1) WO2012041649A2 (fr)

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2647802A1 (fr) * 2012-04-04 2013-10-09 Siemens Aktiengesellschaft Centrale électrique et procédé destiné au fonctionnement d'une centrale électrique
DE102014201502A1 (de) 2014-01-28 2015-07-30 Siemens Aktiengesellschaft Dampfturbine
EP3026230A1 (fr) * 2014-11-26 2016-06-01 Siemens Aktiengesellschaft Procédé de fonctionnement d'une unité de turbine, centrale à vapeur ou centrale à cycle combiné ainsi qu'utilisation d'un dispositif d'étranglement
DE102014225608A1 (de) 2014-12-11 2016-06-16 Siemens Aktiengesellschaft Vorrichtung und Verfahren zur Regelung eines Dampfmassenstroms bei einer Dampfturbine
DE102015218368A1 (de) 2015-09-24 2017-03-30 Siemens Aktiengesellschaft Dampfturbine mit Zwischenüberhitzung
RU187281U1 (ru) * 2018-10-17 2019-02-28 Общество с ограниченной ответственностью "Геотерм-М" Геотермальная турбоустановка
CN113323731A (zh) * 2021-06-29 2021-08-31 西安热工研究院有限公司 一种三缸三排汽机组的高效灵活性供热系统

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Publication number Priority date Publication date Assignee Title
US2586510A (en) * 1948-10-05 1952-02-19 Westinghouse Electric Corp Reheater control for turbine apparatus
FR1527695A (fr) * 1966-02-03 1968-06-07 Stein & Roubaix S A Installation thermique
DE2138664C3 (de) * 1971-07-23 1974-01-24 Gebrueder Sulzer Ag, Winterthur (Schweiz) Gas-Dampfturbinenanlage
WO1995033127A1 (fr) * 1994-06-01 1995-12-07 Masnoi, Sergei Sergeevich Procede d'utilisation d'une installation de turbine a vapeur et installation de turbine a vapeur destinee a la mise en oeuvre dudit procede
DE19506787B4 (de) * 1995-02-27 2004-05-06 Alstom Verfahren zum Betrieb einer Dampfturbine
DE10039317A1 (de) * 2000-08-11 2002-04-11 Alstom Power Boiler Gmbh Dampferzeugeranlage

Non-Patent Citations (1)

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Title
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Also Published As

Publication number Publication date
EP2606205B1 (fr) 2016-08-31
WO2012041649A2 (fr) 2012-04-05
DE102010041627A1 (de) 2012-03-29
WO2012041649A3 (fr) 2013-05-23

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