EP3850194A1 - Turbine à vapeur et procédé permettant de faire fonctionner celle-ci - Google Patents

Turbine à vapeur et procédé permettant de faire fonctionner celle-ci

Info

Publication number
EP3850194A1
EP3850194A1 EP19795107.2A EP19795107A EP3850194A1 EP 3850194 A1 EP3850194 A1 EP 3850194A1 EP 19795107 A EP19795107 A EP 19795107A EP 3850194 A1 EP3850194 A1 EP 3850194A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam
low
inner housing
process steam
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
EP19795107.2A
Other languages
German (de)
English (en)
Other versions
EP3850194B1 (fr
Inventor
Stefan PREIBISCH
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 Energy Global GmbH and Co KG
Original Assignee
Siemens Energy Global GmbH and Co KG
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 Energy Global GmbH and Co KG filed Critical Siemens Energy Global GmbH and Co KG
Publication of EP3850194A1 publication Critical patent/EP3850194A1/fr
Application granted granted Critical
Publication of EP3850194B1 publication Critical patent/EP3850194B1/fr
Active 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/005—Sealing means between non relatively rotating elements
    • 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
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • F01D25/14—Casings modified therefor
    • 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
    • F01K7/02—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 of multiple-expansion type
    • F01K7/025—Consecutive expansion in a turbine or a positive displacement engine
    • 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
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • 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
    • F05D2260/94—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF]
    • F05D2260/941—Functionality given by mechanical stress related aspects such as low cycle fatigue [LCF] of high cycle fatigue [HCF] particularly aimed at mechanical or thermal stress reduction

Definitions

  • the present invention relates to a steam turbine according to the preamble of independent claim 1 and to a method for operating a steam turbine according to the preamble of independent claim 7.
  • steam is used as the working medium to operate steam turbines.
  • the water vapor is heated in a steam boiler and flows as process steam through pipes into the steam turbine.
  • the previously absorbed thermal energy of the working medium is converted into kinetic energy in the steam turbine.
  • a generator is usually operated, which converts the mechanical power it produces into electrical power.
  • the kinetic energy can also be used to drive machines, for example pumps.
  • the relaxed and cooled process steam flows into a condenser, where it condenses by heat transfer in a heat exchanger and is returned to the steam boiler for heating as water.
  • Conventional steam turbines have at least one high-pressure part and at least one low-pressure part, which are also referred to as high-pressure or low-pressure stages.
  • the temperature of the process steam drops sharply, which can lead to partial condensation of the process steam.
  • the low-pressure part is very sensitive to the moisture content of the process steam. If the process steam reaches the low-pressure part of the steam turbine with a moisture content of approx. 8 to 10%, measures must be taken to reduce the moisture content of the process steam to an acceptable level before entering the low-pressure part.
  • the process steam becomes one before entering the low-pressure part so-called reheating supplied.
  • reheating supplied.
  • the intermediate overheating process steam is heated again so that the moisture content drops.
  • At least one medium pressure stage is used in addition to a high pressure and a low pressure stage.
  • Such an intermediate superheating of the process steam is carried out between the individual turbine stages. This leads to higher efficiency, since the superheated steam can be used to generate mechanical energy more efficiently in the turbine stages.
  • the material on the outer wall is subjected to high stress.
  • the colder water vapor is removed, fed to the reheater and the heated process steam is fed to the second turbine stage.
  • High temperature differences occur in the outer wall in the transition area between the first turbine stage and the second turbine stage. Since the end of the first turbine stage, from which the cold process steam is removed, and the beginning of the second turbine stage, in which the hot process steam is supplied from the reheater, are close together, high thermal stresses occur in the outer wall. This can lead to leaks or cracks in the outer wall.
  • the steam turbine has an outer steam turbine housing. Furthermore, the steam turbine has a high-pressure inner casing with a first process steam inlet section and a first process steam outlet section for guiding process steam through the high-pressure inner casing from the first process steam inlet section to the first process steam outlet section in a first process steam release device. Furthermore, the steam turbine has a low-pressure inner casing with a second process steam inlet section and a second process steam outlet section for guiding process steam through the low-pressure inner casing from the second process steam inlet section to the second process steam outlet section in a second process steam relaxation direction. In addition, the steam turbine has a reheater, which is located downstream of the high-pressure inner housing and downstream. is arranged downward of the low-pressure inner housing, the high-pressure inner housing and the low-pressure inner housing being arranged within half of the steam turbine outer housing.
  • the high pressure inner housing and the low pressure inner housing are arranged such that the first steam inlet section of the high pressure inner housing faces the second steam inlet section of the low pressure inner housing.
  • first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing
  • first steam inlet section of the high-pressure inner housing points in the opposite direction or essentially in the opposite direction to the second steam inlet section of the low-pressure inner housing is.
  • the first process steam relaxation direction runs in the opposite direction or essentially in the opposite direction to the second process steam relaxation direction.
  • the high-pressure inner housing and the low-pressure inner housing are thus arranged in such a way that a process steam flow direction through the high-pressure inner housing runs opposite, in particular through 180 °, to a process steam flow direction through the low-pressure inner housing.
  • superheated process steam in the form of live steam, can be fed into the high-pressure inner casing rotated counter to a steam direction and can be expanded down to the pressure and temperature level of a so-called cold reheat.
  • the process steam can be led to the reheater.
  • Intermediate superheated process steam from the reheater can then slide into the low-pressure inner casing facing a main flow direction and relax there up to the condensation pressure in the steam turbine.
  • the low-pressure inner housing is to be understood as an inner housing in which, at least on average, a lower pressure prevails or arises than in the high-pressure inner housing. Ie, the low-pressure inner housing can also be understood to mean in particular a medium-pressure inner housing.
  • Process steam is understood to mean steam, in particular water steam, which flows through components of the steam turbine during operation of the steam turbine.
  • the arrangement of the high-pressure inner housing and the low-pressure inner housing enables exciting forces in the low-pressure inner housing to be minimized, since only the pressure difference from the intermediate overheating acts.
  • Process steam can be passed directly into the next component, for example another low-pressure inner housing, for further expansion and does not have to be diverted first.
  • An expansion direction is to be understood as a direction in which the process steam is essentially moved or directed.
  • a pressure direction from a high-pressure region to a low-pressure region or to a pressure region with a lower pressure than in the high-pressure region is to be understood here as a direction of expansion.
  • a section upstream of a steam turbine section is to be understood as being arranged in a direction opposite to the expansion direction.
  • a steam turbine is provided.
  • the steam engine has a steam turbine outer casing.
  • the steam turbine has a high-pressure inner casing with a first process steam inlet section and a first process steam outlet section for guiding process steam through the high-pressure inner casing from the first process steam inlet section to the first process steam outlet section in a first process relaxation device.
  • the steam turbine has a low-pressure inner casing with a second process steam inlet section and a second process steam outlet section for guiding process steam through the low-pressure inner casing from the second process steam inlet section to the second process steam outlet section in a second process steam relaxation device.
  • the steam turbine has a reheater for reheating process steam, which can be removed downstream of the high-pressure inner housing and upstream of the low-pressure inner housing.
  • the high-pressure inner housing and the low-pressure inner housing are arranged within the steam turbine outer housing and the high-pressure inner housing and the low-pressure inner housing are arranged such that the first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing and further downstream of the high-pressure inner housing, a process steam deflection section for deflecting process steam from the first steam outlet section in a direction opposite to the first steam expansion device into a gap which is between an inner wall of the steam turbine outer casing and an outer wall of the high-pressure inner casing and at least in sections between the inner wall and outer wall of the steam turbine extends an outer wall of the low-pressure inner housing, is formed.
  • a high-pressure sealing shell for at least partially sealing the upstream end section of the high-pressure inner casing and at an upstream end section of the low-pressure inner casing, on which the second process steam end section is configured, a low pressure Sealing shell for at least partially sealing the upstream end section of the low-pressure inner housing are arranged, and wherein the high-pressure sealing shell and the low-pressure sealing shell are arranged adjacent to one another.
  • the high-pressure inner housing is designed according to the invention in such a way that process steam can be removed from the high-pressure inner housing and can be conducted in a region between the high-pressure sealing shell and the low-pressure sealing shell.
  • the process steam which can be taken from the high-pressure inner casing, is throttled directly to reheat parameters without doing any work.
  • the steam is significantly warmer than the process steam that was expanded within the first steam relaxation device.
  • the removed process steam can thereby be used to lead it into an area of the high-pressure sealing shell and the low-pressure sealing shell, in order to locally heat the area and in particular the second inner housing there. This cannot result in so-called cold spots on the rotor and in the region of the second steam inlet section of the low-pressure inner housing. This results in a temperature distribution that is positive both in terms of rotor mechanics and rotor dynamics.
  • the play between the rotor of the steam turbine and the inner casing can be set smaller. This increases the efficiency of the steam turbine.
  • the impressed temperature field also enables higher absolute temperature differences of the reheat to be realized, which in turn increases the process efficiency of the overall system.
  • the area of application of the single-case reheat turbine, ie the turbine with a single outer casing, is thereby enlarged. This has significant cost advantages compared to the alternative multicase turbine, in which several outer casings are used. In this way, cheaper turbines can be offered in a wider performance range.
  • the high-pressure sealing shell is designed such that a predeterminable leakage mass flow can be conducted via the high-pressure sealing shell in a region between the high-pressure sealing shell and the low-pressure sealing shell. Because the high-pressure sealing shell is designed in such a way that a sufficiently large steam mass flow (leakage current) can be conducted through the high-pressure sealing shell into the area between the high-pressure sealing shell and the low-pressure sealing shell, the space between the two sealing shells can be heated accordingly, so that The rotor mechanical and rotor dynamic properties are positively influenced with regard to the temperature, so that no cold spots occur on the rotor and the area of the second process steam inlet section is preheated accordingly.
  • the existing leakage flow of the high-pressure sealing shell is used for heating, whereby the high-pressure sealing shell must be designed so that the leakage mass flow is higher than would be technically necessary.
  • the leakage mass flow can be easily determined or adjusted by increasing the gap between the sealing shells and the rotor accordingly.
  • a further embodiment of the invention provides that the high-pressure sealing shell and the low-pressure sealing shell are designed and matched to one another in such a way that the leakage mass flow through the high-pressure sealing shell is greater than the leakage mass flow through the low-pressure sealing shell.
  • the leakage mass flow through the high-pressure sealing shell is preferably at least 30%, preferably at least 50% larger than the leakage mass flow through the low-pressure sealing shell.
  • the difference between the mass flows results in a blocking mass flow which prevents the cold intermediate superheating steam from entering the low-pressure sealing shell and thus the second expansion device.
  • the hot leakage mass flow from the first expansion device ensures preheating of the rotor between the first sealing shell and the second sealing shell and preheating, in particular the second process steam inlet section on the second expansion device.
  • a further embodiment of the invention provides that a sealing web for sealing a steam turbine region between the downstream end section of the low-pressure inner casing and the steam turbine outer casing is configured on a downstream end section of the low-pressure inner casing.
  • process steam flows around the low-pressure inner casing during operation.
  • the sealing web which is preferably designed as an integrated sealing web at the downstream end section of the low-pressure inner housing.
  • an inner sealing shell on the downstream end section of the low-pressure inner housing can be dispensed with.
  • the sealing web has a significantly less complex structure than a sealing shell.
  • a further embodiment of the invention provides that the reheater is arranged outside the outer casing of the steam turbine. This is particularly advantageous with regard to assembly, disassembly, maintenance and repair.
  • a method for operating a steam turbine as shown in detail above is provided.
  • a method according to the invention has the same advantages as have been described in detail with reference to the steam turbine according to the invention.
  • the process has the following steps:
  • the process results in a rotor mechanical and rotor dynamic positive temperature distribution. Due to the imprinted temperature field, higher absolute temperature differences of reheating can be realized and thus the overall efficiency can be increased.
  • An embodiment of the method provides that the removed process steam (leakage steam) via the high-pressure sealing shell in the area between the high-pressure sealing shell and the low pressure sealing shell is directed.
  • the method according to the invention can be implemented with little design effort and thus inexpensively.
  • the conversion of existing steam turbines to the process described can be accomplished with simple means.
  • Figure 1 shows the basic structure of an inventive
  • FIG. 2 shows the detailed view Z, in which the invention
  • FIG. 1 shows the basic structure of a steam turbine 1 according to the invention.
  • the steam turbine 1 has a steam turbine outer housing 20 in which there is a high-pressure inner housing 30, a low-pressure inner housing 40 in the form of a medium-pressure inner housing and another low-pressure inner housing 90.
  • a live steam or process steam source 10 for supplying process steam to the high pressure inner housing 30 is arranged upstream of the high pressure inner housing 30.
  • the high-pressure inner housing 30 has a first process steam inlet section 31 and a first process steam outlet section 32 for guiding process steam through the high pressure inner housing 30 from the first process steam inlet section 31 to the first process steam outlet section 32 in a first process steam relaxation device 33.
  • the low-pressure inner housing 40 has a second process steam inlet section 41 and a second process steam outlet section 42 for guiding process steam through the low-pressure Inner housing 40 from the second process steam inlet section 41 to the second process steam outlet section 42 in a second process steam relaxation device 43.
  • Steam turbine 1 also has a reheater 50, which is arranged downstream of the high-pressure inner housing 30 and upstream of the low-pressure inner housing 40.
  • the arrangement does not refer to a spatial, but to a fluidic arrangement.
  • the high-pressure inner housing 30 and the low-pressure inner housing 40 are arranged in such a way that the first steam inlet section 31 of the high-pressure inner housing 30 faces the second steam inlet section 41 of the low-pressure inner housing 40.
  • the steam turbine 1 Downstream of the high-pressure inner housing 30, the steam turbine 1 has a process steam deflection section 60 for deflecting process steam from the first steam outlet section 32 in a direction opposite the first steam relaxation device 33 into a gap 70 of the steam turbine 1.
  • the gap 70 extends between the steam turbine outer housing 20 and the high-pressure inner housing 30 and at least from section between the steam turbine housing 20 and the low-pressure inner housing 40.
  • a sealing web 80 At a downstream end section of the low-pressure inner housing 40 there is a sealing web 80 for sealing a steam turbine region between the downstream end section of the Low pressure inner housing 40 and the steam turbine outer housing 20 is configured.
  • the intermediate superheater 50 is arranged outside the steam turbine outer casing 20.
  • the high pressure inner housing 30 and the low pressure inner housing 40 are provided as separate components in a common steam turbine outer housing 20.
  • a high pressure sealing shell 34 is arranged for partially sealing the downstream end section of the high pressure inner housing 30.
  • a low-pressure sealing shell 44 for partially sealing off the upstream end portion of the low-pressure inner housing 40.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are arranged adjacent to one another.
  • a further high-pressure sealing shell 35 is arranged for at least partially sealing the downstream end section of the high-pressure inner housing 30.
  • the high-pressure sealing shell 34 is designed and designed such that a predeterminable leakage mass flow emerges through it and can be conducted into the region 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44.
  • the sealing shell or the sealing gap can be designed such that a predeterminable leakage mass flow passes through the sealing shell.
  • the high-pressure sealing shell 34 and the low-pressure sealing shell 44 are coordinated with one another in such a way that the leakage mass flow through the high-pressure sealing shell 34 is greater than the leakage mass flow through the low-pressure sealing shell 44.
  • the leakage mass flow through the high-pressure sealing shell 34 is preferably at least 30%, preferably at least 50% greater than the leakage mass flow through the low pressure sealing shell 44.
  • FIG. 2 shows a detailed view Z from FIG. 1.
  • a high-pressure sealing shell 34 is arranged at the end section of the high-pressure inner housing 30.
  • a low pressure sealing shell 44 is arranged to seal the gap between the upstream end portion of the low pressure inner housing 40 and the shaft 100.
  • the high pressure sealing shell 34 and the low pressure sealing shell 44 are arranged adjacent to one another.
  • the process steam is then passed from the first process steam inlet section 31 to the first process steam outlet section 32 and then passed through the first process steam outlet section 32 from the high-pressure inner housing 30 via the process steam deflection section 60 into the gap 70 to the reheater 50.
  • the process steam is passed through the gap 70 for cooling the steam turbine outer housing 20 or the steam turbine 1 along the high-pressure inner housing 30 and along the low-pressure inner housing 40.
  • the heated or superheated process steam from the reheater 50 is passed through the second process steam inlet section 41 into the low-pressure or medium-pressure inner housing.
  • the process steam is slid into the further low-pressure inner housing 90 while the direction of expansion remains the same.
  • the process steam can further relax there and finally condense.
  • steam is drawn from the first high pressure inner housing 30 steam removed and throttled directly to overheating parameters without performing any work and this steam passed directly into the gap between the high-pressure sealing shell 34 and the low-pressure sealing shell 44.
  • the low-pressure inner housing 40 and the region 110 of the shaft 100 which lies between the high-pressure sealing shell 34 and the low-pressure sealing shell 44, can be locally heated.
  • the high pressure inner casing 30 an opening in the high-pressure inner housing 30 and a corresponding pipeline can be provided.
  • the steam can be removed from the inner housing via the high pressure sealing shell 34.
  • the gap of the high-pressure sealing shell 34 must be designed accordingly. The hot steam can then pass from the high-pressure inner housing 30 directly into the space between the first high-pressure sealing shell 34 and the second low-pressure sealing shell 44.
  • the steam that flows out via the high-pressure sealing shell 34 has almost live steam parameters, it can be used to heat the area 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44. This results in a positive temperature distribution in terms of rotor dynamics and rotor mechanics.
  • the pressure On the outside of the low pressure inner housing 40, the pressure is higher than on the inside, the reason for this is the pressure loss in the gap, which leads to the intermediate overheating 50.
  • the process steam which is taken from the high-pressure inner housing 30 and is conducted in the region 110 between the high-pressure sealing shell 34 and the low-pressure sealing shell 44, is thus sucked into the low-pressure inner housing 40 and thereby heats up the low-pressure inner housing 40.
  • the high-pressure sealing shell 34 and the Never derdruckdichtschale 44 are coordinated so that the process steam, which flows out through the high pressure sealing shell 34 is at least 30%, preferably at least 50% larger than the leakage mass flow through the low pressure sealing shell 44.
  • the difference in mass flows leads to a blocking mass flow arises, which prevents the penetration of cold steam flowing to the reheater 50 into the high-pressure sealing shell 34.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne une turbine à vapeur (1) comprenant un carter intérieur basse pression (NDIG) et un carter intérieur haute pression (HDIG) à l'intérieur d'un carter extérieur (20) de turbine à vapeur, un resurchauffeur (50) en aval du HDIG (30) et en amont du NDIG (40), la première partie d'entrée de vapeur du HDIG (30) étant tournée vers la deuxième partie d'entrée de vapeur du NDIG (40), et une partie de déviation de vapeur industrielle (60) servant à la déviation de la vapeur industrielle à partir de la première partie de sortie de vapeur dans un interstice entre une paroi intérieure du carter extérieur de turbine à vapeur et une paroi extérieure du HDIG (30) et du NDIG, une enveloppe d'étanchéité haute pression (34) servant à réaliser l'étanchéité de la partie d'extrémité du HDIG (30) située en amont, une enveloppe d'étanchéité basse pression (44) servant à réaliser l'étanchéité de la partie d'extrémité du NDIG (40) située en amont, l'enveloppe d'étanchéité haute pression (34) et l'enveloppe d'étanchéité basse pression (44) étant adjacentes l'une à l'autre, et le HDIG (30) étant réalisé de telle sorte que de la vapeur industrielle puisse être prélevée du HDIG et puisse être guidée dans une région entre l'enveloppe d'étanchéité haute pression (34) et l'enveloppe d'étanchéité basse pression (44).
EP19795107.2A 2018-11-13 2019-10-15 Turbine à vapeur et procédé permettant de faire fonctionner celle-ci Active EP3850194B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102018219374.6A DE102018219374A1 (de) 2018-11-13 2018-11-13 Dampfturbine und Verfahren zum Betreiben derselben
PCT/EP2019/077895 WO2020099054A1 (fr) 2018-11-13 2019-10-15 Turbine à vapeur et procédé permettant de faire fonctionner celle-ci

Publications (2)

Publication Number Publication Date
EP3850194A1 true EP3850194A1 (fr) 2021-07-21
EP3850194B1 EP3850194B1 (fr) 2023-09-13

Family

ID=68387268

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19795107.2A Active EP3850194B1 (fr) 2018-11-13 2019-10-15 Turbine à vapeur et procédé permettant de faire fonctionner celle-ci

Country Status (7)

Country Link
US (1) US11560812B2 (fr)
EP (1) EP3850194B1 (fr)
JP (1) JP7263514B2 (fr)
CN (1) CN113015845B (fr)
DE (1) DE102018219374A1 (fr)
PL (1) PL3850194T3 (fr)
WO (1) WO2020099054A1 (fr)

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DE102013219771B4 (de) * 2013-09-30 2016-03-31 Siemens Aktiengesellschaft Dampfturbine
JP5955345B2 (ja) * 2014-01-27 2016-07-20 三菱日立パワーシステムズ株式会社 蒸気タービンを含む熱機関の流体シール構造
CN104533550B (zh) 2014-11-03 2016-06-01 章礼道 能提供全部给水回热抽汽的二次再热汽轮机超高压缸
EP3130748A1 (fr) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Refroidissement de rotor pour une turbine a vapeur
DE102015219391A1 (de) * 2015-10-07 2017-04-13 Siemens Aktiengesellschaft Verfahren zum Betreiben eines Gas-und-Dampf-Kombinationskraftwerks
US20180080324A1 (en) * 2016-09-20 2018-03-22 General Electric Company Fluidically controlled steam turbine inlet scroll
JP6771665B2 (ja) * 2016-12-22 2020-10-21 シーメンス アクティエンゲゼルシャフト ガスタービン吸気システムを有するパワープラント
JP6736511B2 (ja) * 2017-03-28 2020-08-05 三菱重工業株式会社 翼異常検出装置、翼異常検出システム、回転機械システム及び翼異常検出方法
DE102017211295A1 (de) 2017-07-03 2019-01-03 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betreiben derselben
US20200156283A1 (en) * 2017-08-02 2020-05-21 Basf Se A process for producing a three-dimensional green body by a fused filament fabrication (fff) process

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JP7263514B2 (ja) 2023-04-24
WO2020099054A1 (fr) 2020-05-22
CN113015845A (zh) 2021-06-22
EP3850194B1 (fr) 2023-09-13
BR112021008477A2 (pt) 2021-08-03
US11560812B2 (en) 2023-01-24
JP2022509766A (ja) 2022-01-24
US20210396154A1 (en) 2021-12-23
DE102018219374A1 (de) 2020-05-14
CN113015845B (zh) 2023-08-04

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