EP2606205B1 - Turbine à vapeur dotée d'un surchauffeur - Google Patents

Turbine à vapeur dotée d'un surchauffeur Download PDF

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Publication number
EP2606205B1
EP2606205B1 EP11760733.3A EP11760733A EP2606205B1 EP 2606205 B1 EP2606205 B1 EP 2606205B1 EP 11760733 A EP11760733 A EP 11760733A EP 2606205 B1 EP2606205 B1 EP 2606205B1
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EP
European Patent Office
Prior art keywords
steam
volume flow
low
control valve
steam turbine
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.)
Not-in-force
Application number
EP11760733.3A
Other languages
German (de)
English (en)
Other versions
EP2606205A2 (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
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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

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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
    • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type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 patent claim 1 and a method for controlling the moisture content when entering the low-pressure part of a steam turbine according to the preamble of patent claim 5.
  • a generic steam turbine is for example in the US 5,850,739 A which represents the closest prior art to the present invention.
  • the DE 21 38 664 A1 discloses a method for mixed gas and steam operation of a gas turbine plant, wherein water fed into the combustion chamber into heating elements is vaporized and superheated at a pressure higher than the combustion chamber pressure and wherein the superheated steam is expanded in a steam turbine.
  • the object is achieved with respect to the steam turbine by the features of independent claim 1.
  • the object is achieved by the features of independent claim 5.
  • the steam turbine is improved in that by their design with regard to the design and controllability of the control valve, the entire steam mass flow either the reheat or the low-pressure part can be fed, and in addition, as in the closest prior art, only one Partial volume flow can be removed and this is supplied to the reheat. Subsequently, the reheated partial volume flow is supplied together with the remaining steam volume flow to the low-pressure part of the steam turbine. Due to the reheating of the partial volume flow, the total volume flow is brought to a permissible moisture content. However, only a comparatively low energy is needed to heat the partial volume flow.
  • the steam turbine according to the invention thus offers an energetically more favorable operation with an improved control range compared to the closest prior art.
  • 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.
  • At least one control valve is designed as an internal control valve.
  • the internal control valves that already regulate the volume flow between the high-pressure and low-pressure part of the steam turbine can be used and only need 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 steam turbine according to the invention provides that the steam volume flow, which is supplied to the reheat, is dependent on the humidity and / or the temperature of the steam after the high pressure part.
  • a permissible value is usually at a moisture content of 8 to 10 percent.
  • the wetness describes the water content, in the steam.
  • the moisture content is preferably determined at the outlet of the high-pressure part by measuring the temperature and / or the moisture content itself.
  • the measurement after the high-pressure part does not mean that it is absolutely necessary to measure directly at the outlet of the high-pressure part, but only that the measurement must take place between the end of the high-pressure part and the supply for intermediate heating, so that a corresponding partial volume flow can be supplied to the reheat.
  • the control valve may preferably be connected to a control unit, which makes a corresponding adjustment of the control valve due to the measured temperature and / or humidity, so that the necessary partial volume flow of the reheat 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 unnecessarily degrade the efficiency of the steam turbine.
  • the method thus differs from the closest prior art in that really only the necessary partial volume flow of reheating is supplied as it is determined based on the determination of the moisture content and / or the temperature of the steam after the high pressure part.
  • FIG. 1 schematically shows 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 standing under high pressure and high temperature steam is released and the relaxed to a lower pressure and a lower temperature steam is then forwarded to the low pressure part 2 of the steam turbine, where it is further relaxed and thereby further loses temperature and pressure.
  • a control valve 3 is arranged, which is preferably infinitely movable between two end positions. In the first end position of the control valve 3, the control valve 3 is fully open.
  • control valve 3 can be moved continuously between these two end positions. 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 steam volume flow V 0 is added directly to the low pressure part 2 via the control valve 3.
  • the partial volume flow V z is selected to be only as large as that to achieve a certain moisture content of the total volume flow V at the entrance of the low pressure part 2 is necessary.
  • the steam volume flow V z which is supplied to the reheat 4, is dependent on the humidity and / or the temperature of the steam after the high-pressure part 1. A moisture content of 8 to 10 percent should not be exceeded in the rule.
  • the regulation is carried out in such a way that, depending on the moisture content and / or the temperature, the control valve 3 is opened more or less strongly and thus a more or less large partial volume flow V z of the reheat 4 is added.
  • the steam which is supplied to the reheat 4 is thereby heated to a temperature at which the moisture of the entire steam volume flow V is lowered to a value permissible for the low-pressure part 2.
  • Decisive here is not the moisture content in the partial volume flow V z but in the total volume flow V. This must not exceed a permissible wetness content.
  • FIG. 1 shown block diagram the method for controlling the moisture content when entering the low pressure part 2 of the steam turbine are shown.
  • the moisture content and / or the temperature of the vapor to determine after the high pressure part 1.
  • the determination of the moisture content or the temperature must be carried out before the control valve 3 in order to be able to initiate suitable steps in order to reduce the moisture content or to increase the steam temperature.
  • the partial volume flow V z to be taken depends on the wet content and / or the temperature of the steam after the high-pressure part 1.
  • the partial volume flow V z which is supplied to the reheat 4, is set via the control valve 3. If the control valve 3 is moved in the closing direction, a stronger throttling takes place on the control valve 3, as a result of which more steam volume flow V z flows via the reheat 4.
  • Opening the control valve 3 ensures that a higher partial volume flow V 0 flows via the control valve 3 directly into the low-pressure part 2 of the steam turbine.
  • the partial volume flows V 0 and V z are brought together before the supply to the low pressure part 2 and mix, resulting in a homogeneous vapor flow V.
  • FIG. 2 shows an axial section through a steam turbine with a high pressure part 1 and a low pressure part 2.
  • the low pressure part 2 is formed in three stages.
  • the steam 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 inflow housing of the steam turbine in the high-pressure part 1 of the steam turbine and is initially relaxed there.
  • the so 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 valve.
  • FIG. 2 is the control valve 3 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 is relaxed here to the ambient pressure or a slight negative pressure and leaves the low pressure part 2 thereafter.
  • the control valve 3 is always one of its first end position, i. in the fully open position, when the coming out of the high-pressure part 1 steam flow V has 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, ie it is in its second end position, then the entire volume flow V is fed to a reheate 4. This case is in FIG. 3 shown in more detail.
  • FIG. 3 shows the in FIG. 2 illustrated steam turbine.
  • the control valve 3 is completely closed, so that the entire steam 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 )
  • the two partial volume flows V 0 / V z are in the inner housing the steam turbine mixed and enter as total volume flow V in the low pressure part 2 a.
  • the entire volume flow does not have to be added to a reheat if the moisture content in the volume flow exceeds a permissible value or the permissible steam temperature is not reached. Rather, it is sufficient to divert a partial volume flow from the volumetric flow and merely to supply it with reheating and then reassemble the two partial volumetric flows so that the total volumetric flow reaches permissible values with regard to the moisture content and the temperature before it is conducted into the low-pressure part of the steam turbine.
  • the efficiency and efficiency of the steam turbine increase significantly over the prior art.
  • the steam turbine according to the invention brings particularly great advantages in applications with widely varying steam parameters, such as e.g. in biomass or solar application.
  • the moisture content or the temperature of the steam can be adjusted by the steam turbine according to the invention very quickly to a permissible value.

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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 avec au moins une partie sous haute pression (1) et au moins une partie sous basse pression (2), dans laquelle entre la partie sous haute pression (1) et la partie sous basse pression (2) au moins une soupape de régulation (3) est disposée pour la limitation de la teneur en humidité au niveau de l'entrée de la turbine à basse pression à un niveau autorisé,
    dans laquelle la soupape de régulation (3) est mobile entre deux positions finales et dans laquelle
    - dans la première position finale de la soupape de régulation (3) le courant volumétrique de vapeur peut être amené intégralement à la partie sous basse pression (2) via l'au moins une soupape de régulation (3),
    - dans la deuxième position finale l'ensemble du courant volumétrique de vapeur peut d'abord être amené à un surchauffeur intermédiaire (4) et
    - dans au moins une autre position de commutation, qui se trouve entre la première et la deuxième position finale, un premier courant volumétrique partiel peut être amené au surchauffeur intermédiaire (4) et un deuxième courant volumétrique partiel peut être amené à la partie sous basse pression (2) sans surchauffe intermédiaire.
  2. Turbine à vapeur selon la revendication 1,
    caractérisée en ce que
    l'au moins une soupape de régulation (3) est configurée en tant que soupape de régulation interne.
  3. Turbine à vapeur selon la revendication 1 ou 2,
    caractérisée en ce que
    le courant volumétrique de vapeur qui est amené au surchauffeur (4) est dépendant de l'humidité et/ou de la température de la vapeur en aval de la partie sous haute pression (1).
  4. Turbine à vapeur selon l'une des revendications précédentes,
    caractérisée en ce que
    la vapeur qui est amenée au surchauffeur (4) est chauffée à une température à laquelle l'humidité dans la vapeur est abaissée à une valeur admissible pour la partie sous basse pression (2).
  5. Procédé de régulation de la teneur en humidité lors de l'entrée dans la partie sous basse pression (2) d'une turbine à vapeur, dans lequel la turbine à vapeur comprend en particulier une soupape de régulation (3) commutable selon l'une des revendications précédentes, caractérisé par les étapes suivantes :
    - détermination de la teneur en humidité et/ou de la température de la vapeur en aval de la partie sous haute pression (1),
    - lors du dépassement par le haut d'une teneur en humidité prédéfinie de la vapeur et/ou lors du dépassement par le bas d'une température de vapeur prédéfinie, extraction, d'au moins une partie, du courant volumétrique de vapeur,
    - chauffage du courant volumétrique de vapeur extrait jusqu'à une humidité et/ou une température prédéterminées,
    - amenée du courant volumétrique de vapeur à la partie sous basse pression (2) de la turbine à vapeur.
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 EP2606205A2 (fr) 2013-06-26
EP2606205B1 true EP2606205B1 (fr) 2016-08-31

Family

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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)

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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

Citations (1)

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Publication number Priority date Publication date Assignee Title
DE19506787A1 (de) * 1995-02-27 1996-08-29 Abb Management Ag Verfahren zum Betrieb einer Dampfturbine

Family Cites Families (5)

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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
US5850739A (en) * 1994-06-01 1998-12-22 Masnoi; Sergey Alexandrovich Steam turbine power plant and method of operating same
DE10039317A1 (de) * 2000-08-11 2002-04-11 Alstom Power Boiler Gmbh Dampferzeugeranlage

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19506787A1 (de) * 1995-02-27 1996-08-29 Abb Management Ag Verfahren zum Betrieb einer Dampfturbine

Also Published As

Publication number Publication date
EP2606205A2 (fr) 2013-06-26
WO2012041649A3 (fr) 2013-05-23
DE102010041627A1 (de) 2012-03-29
WO2012041649A2 (fr) 2012-04-05

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