EP3850194A1 - Steam turbine and method for operating same - Google Patents

Steam turbine and method for operating same

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)
French (fr)
Other versions
EP3850194B1 (en
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/en
Application granted granted Critical
Publication of EP3850194B1 publication Critical patent/EP3850194B1/en
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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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

The invention relates to a steam turbine (1), having a low-pressure inner housing (NDIG) and a high-pressure inner housing (HDIG) within a steam turbine outer housing (20), a reheater (50) downstream of the HDIG (30) and upstream of the NDIG (40) wherein the first steam inlet section of the HDIG (30) faces the second steam inlet section of the NDIG (40), and a process steam deflection section (60) for deflecting process steam out of the first steam outlet section into a gap between an inner wall of the steam turbine outer housing and an outer wall of the HDIG (30) and of the NDIG, a high-pressure sealing shell (34) for sealing the upstream end-section of the HDIG (30), a low-pressure sealing shell (44) for sealing the upstream end-section of the NDIG (40), the high-pressure sealing shell (34) and the low-pressure sealing shell (44) being located adjacent to one another, and the HDIG (30) being designed such that process steam can be drawn from the HDIG and can be conveyed to a region between the high-pressure sealing shell (34) and the low-pressure sealing shell (44).

Description

Beschreibung description
Dampfturbine und Verfahren zum Betreiben derselben Steam turbine and method of operating the same
Die vorliegende Erfindung betrifft eine Dampfturbine nach dem Oberbegriff des unabhängigen Patentanspruchs 1 sowie ein Ver fahren zum Betreiben einer Dampfturbine nach dem Oberbegriff des unabhängigen Patentanspruchs 7. 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.
In Dampfkraftwerken wird zum Betreiben von Dampfturbinen als Arbeitsmedium Wasserdampf verwendet. Der Wasserdampf wird in einem Dampfkessel erwärmt und strömt als Prozessdampf über Rohrleitungen in die Dampfturbine. In der Dampfturbine wird die zuvor aufgenommene thermische Energie des Arbeitsmediums in Bewegungsenergie umgewandelt. Mittels der Bewegungsenergie wird üblicherweise ein Generator betrieben, welcher die er zeugte mechanische Leistung in elektrische Leistung umwan delt. Alternativ kann die Bewegungsenergie auch zum Antreiben von Maschinen bspw. Pumpen genutzt werden. Der entspannte und abgekühlte Prozessdampf strömt in einen Kondensator, wo er durch Wärmeübertragung in einem Wärmetauscher kondensiert und als Wasser erneut dem Dampfkessel zum Erhitzen zugeführt wird . In steam power plants, 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. By means of the kinetic energy, a generator is usually operated, which converts the mechanical power it produces into electrical power. Alternatively, 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.
Übliche Dampfturbinen weisen wenigstens einen Hochdruckteil und wenigstens einen Niederdruckteil auf, die auch als Hoch druck- bzw. Niederdruckstufe bezeichnet werden. Beim Nieder druckteil sinkt die Temperatur des Prozessdampfes stark ab, wodurch es zur teilweisen Kondensation des Prozessdampfes kommen kann. Der Niederdruckteil ist dabei sehr empfindlich hinsichtlich des Nässegehaltes des Prozessdampfes. Erreicht der Prozessdampf den Niederdruckteil der Dampfturbine mit ei nem Nässegehalt von ca. 8 bis 10 %, sind Maßnahmen zu ergrei fen, die den Nässegehalt des Prozessdampfes vor dem Eintritt in den Niederdruckteil auf ein zulässiges Maß reduzieren. 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. In the low pressure section, 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.
Um die Effizienz eines Dampfkraftwerkes zu erhöhen, wird der Prozessdampf vor dem Eintritt in den Niederdruckteil einer sogenannten Zwischenüberhitzung zugeführt. In der Zwischen überhitzung wird der Prozessdampf erneut erhitzt, so dass der Nässegehalt sinkt. Bei dieser Zwischenüberhitzung wird der gesamte Dampfmassenstrom nach dem Hochdruckteil aus der In order to increase the efficiency of a steam power plant, the process steam becomes one before entering the low-pressure part so-called reheating supplied. In the intermediate overheating process steam is heated again so that the moisture content drops. With this reheating, the entire steam mass flow after the high pressure part is from the
Dampfturbine entnommen, der Zwischenüberhitzung zugeführt und annähernd auf die Temperatur des Frischdampfes angehoben. An schließend wird der Prozessdampf dem Niederdruckteil zuge führt. Ohne eine solche Zwischenüberhitzung müsste die Dampf turbine angehalten werden, da auskondensierte Wassertropfen auf die sich drehenden Turbinenschaufeln auftreffen könnten und Schäden durch Tropfenerosion an den Turbinenschaufeln verursachen würden. Steam turbine removed, fed to reheating and raised to approximately the temperature of the live steam. The process steam is then fed to the low-pressure part. Without such intermediate overheating, the steam turbine would have to be stopped because condensed water droplets could hit the rotating turbine blades and cause damage by droplet erosion to the turbine blades.
Bei mehrstufigen Dampfturbinen wird neben einer Hochdruck- und einer Niederdruckstufe wenigstens eine Mitteldruckstufe verwendet. Hierbei wird zwischen den einzelnen Turbinenstufen jeweils eine solche Zwischenüberhitzung des Prozessdampfes durchgeführt. Dies führt zu einer höheren Effizienz, da mit tels des überhitzten Wasserdampfes effizienter mechanische Energie in den Turbinenstufen erzeugt werden kann. In multi-stage steam turbines, 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.
Bei der Implementierung von Zwischenüberhitzungssystemen in Dampfturbinen wird das Material an der Außenwand, insbesonde re zwischen den einzelnen Turbinenstufen hoch beansprucht. An der ersten Turbinenstufe wird der kältere Wasserdampf entnom men, dem Zwischenüberhitzer zugeführt und der aufgeheizte Prozessdampf der zweiten Turbinenstufe zugeführt. Dabei tre ten in der Außenwand im Übergangsbereich zwischen der ersten Turbinenstufe und der zweiten Turbinenstufe hohe Temperatur differenzen auf. Da das Ende der ersten Turbinenstufe, aus der der kalte Prozessdampf entnommen wird und der Beginn der zweiten Turbinenstufe, in welchem der heiße Prozessdampf aus dem Zwischenüberhitzer zugeführt wird, eng beieinander lie gen, treten dort hohe thermische Spannungen in der Außenwand auf. Dies kann zu Undichtigkeiten oder zu Rissen in der Au ßenwand führen. Ferner besteht die Gefahr, dass bei Entnahme des kalten Prozessdampfes aus der ersten Turbinenstufe Nass dampfparameter herrschen und sich dadurch an der Innenwand des Außengehäuses Kondensat bildet. Das Kondensat kühlt die Innenseite der Außenwandung zusätzlich ab. Somit wird die thermische Spannung an der Außenwand erhöht. Damit der über hitzte Prozessdampf keine schädlichen thermischen Spannungen verursacht, wird der überhitzte Prozessdampf zur Reduktion der thermischen Spannung abgekühlt. Dies wird üblicherweise in vorgeschalteten Einströmgehäusen durchgeführt. Diese zu sätzlichen Einströmgehäuse können allerdings zu Energiever lusten führen. When implementing reheat systems in steam turbines, the material on the outer wall, particularly between the individual turbine stages, is subjected to high stress. At the first turbine stage, 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. Furthermore, there is a risk that when the cold process steam is removed from the first turbine stage, wet steam parameters will prevail and therefore stick to the inner wall of the outer casing forms condensate. The condensate additionally cools the inside of the outer wall. This increases the thermal stress on the outer wall. To prevent the overheated process steam from causing harmful thermal stresses, the overheated process steam is cooled to reduce the thermal stress. This is usually done in upstream inflow housings. However, these additional inflow housings can lead to energy losses.
Bei einer einschaligen bzw. eingehäusigen Dampfturbine mit Zwischenüberhitzung wird an zwei Stellen stark überhitzter Prozessdampf in die Turbine geleitet. Dabei wird insbesondere das Dampfturbinenaußengehäuse durch die auftretenden Tempera turen und Drücke thermisch stark belastet. In the case of a single-shell or single-casing steam turbine with reheating, superheated process steam is fed into the turbine at two points. In particular, the steam turbine outer casing is thermally stressed by the temperatures and pressures that occur.
Die auftretenden erforderlichen Parameter liegen jedoch häu fig über den möglichen Parametern einschaliger Turbinengehäu se. Die nicht vorveröffentlichte Patentanmeldung The required parameters, however, are often above the possible parameters of single-shell turbine housings. The unpublished patent application
DE 10 2017 211 295 der Anmelderin schlägt daher eine Dampf turbine sowie ein Verfahren zum Betreiben einer solchen DE 10 2017 211 295 of the applicant therefore proposes a steam turbine and a method for operating such a turbine
Dampfturbine vor, die die Nachteile weitgehend überwindet. Steam turbine before that largely overcomes the disadvantages.
Die Dampfturbine weist ein Dampfturbinenaußengehäuse auf. Ferner weist die Dampfturbine ein Hochdruckinnengehäuse mit einem ersten Prozessdampfeintrittsabschnitt und einem ersten Prozessdampfaustrittsabschnitt zum Leiten von Prozessdampf durch das Hochdruckinnengehäuse vom ersten Prozessdampfein trittsabschnitt zum ersten Prozessdampfaustrittsabschnitt in einer ersten ProzessdampfentSpannungseinrichtung auf. Weiter hin weist die Dampfturbine ein Niederdruckinnengehäuse mit einem zweiten Prozessdampfeintrittsabschnitt und einem zwei ten Prozessdampfaustrittsabschnitt zum Leiten von Prozess dampf durch das Niederdruckinnengehäuse vom zweiten Prozess dampfeintrittsabschnitt zum zweiten Prozessdampfaustrittsab schnitt in einer zweiten ProzessdampfentSpannungsrichtung auf. Außerdem weist die Dampfturbine einen Zwischenüberhitzer auf, der stromabwärts des Hochdruckinnengehäuses und stromab- wärts des Niederdruckinnengehäuses angeordnet ist, wobei das Hochdruckinnengehäuse und das Niederdruckinnengehäuse inner halb des Dampfturbinenaußengehäuses angeordnet sind. 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.
Das Hochdruckinnengehäuse und das Niederdruckinnengehäuse sind derart angeordnet, dass der erste Dampfeintrittsab- schnitt des Hochdruckinnengehäuses dem zweiten Dampfein trittsabschnitt des Niederdruckinnengehäuses zugewandt ist. Darunter, dass der erste Dampfeintrittsabschnitt des Hochdru ckinnengehäuses dem zweiten Dampfeintrittsabschnitt des Nie derdruckinnengehäuses zugewandt ist, versteht man, dass der erste Dampfeintrittsabschnitt des Hochdruckinnengehäuses in die entgegengesetzte Richtung oder im Wesentlichen in die entgegengesetzte Richtung wie der zweite Dampfeintrittsab schnitt des Niederdruckinnengehäuses zeigt, bzw. ausgerichtet ist. Entsprechend verläuft die erste ProzessdampfentSpan nungsrichtung entgegen oder im Wesentlichen entgegen zur zweiten ProzessdampfentSpannungsrichtung . 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. By the fact that the first steam inlet section of the high-pressure inner housing faces the second steam inlet section of the low-pressure inner housing, it is understood that the 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. Correspondingly, the first process steam relaxation direction runs in the opposite direction or essentially in the opposite direction to the second process steam relaxation direction.
Das Hochdruckinnengehäuse und das Niederdruckinnengehäuse sind somit derart angeordnet, dass eine Prozessdampfflutrich- tung durch das Hochdruckinnengehäuse entgegengesetzt, insbe sondere um 180° entgegengesetzt, zu einer Prozessdampfflut- richtung durch das Niederdruckinnengehäuse verläuft. 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.
Unter Verwendung einer solchen Dampfturbine kann überhitzter Prozessdampf, in Form von Frischdampf, in das entgegen einer Dampfrichtung gedrehte Hochdruckinnengehäuse zugeführt werden und bis auf das Druck- und Temperaturniveau einer sogenannten kalten Zwischenüberhitzung entspannt werden. Nachdem der Pro zessdampf aus dem Hochdruckinnengehäuse ausgetreten ist, kann der Prozessdampf zum Zwischenüberhitzer geführt werden. Zwi schenüberhitzter Prozessdampf aus dem Zwischenüberhitzer kann dann in das in eine HauptStrömungsrichtung gewandte Nieder druckinnengehäuse gleiten und dort bis auf Kondensationsdruck in der Dampfturbine entspannen. Unter dem Niederdruckinnengehäuse ist ein Innengehäuse zu verstehen, in welchem zumindest im Mittel ein niedrigerer Druck als im Hochdruckinnengehäuse herrscht bzw. entsteht. D.h., unter dem Niederdruckinnengehäuse kann auch insbesonde re ein Mitteldruckinnengehäuse verstanden werden. Using such a steam turbine, 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. After the process steam has escaped from the high pressure inner housing, 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.
Unter dem Prozessdampf ist Dampf, insbesondere Wasserdampf, zu verstehen, der während des Betriebs der Dampfturbine durch Bauteile der Dampfturbine strömt. 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.
Durch die Anordnung des Hochdruckinnengehäuses und des Nie- derdruckinnengehäuses können erregende Kräfte im Niederdru ckinnengehäuse minimiert werden, da lediglich die Druckdiffe renz aus der Zwischenüberhitzung wirkt. Prozessdampf kann zur weiteren Entspannung direkt in das nächste Bauteil, bspw. ein weiteres Niederdruckinnengehäuse, geleitet werden und muss nicht erst umgeleitet werden. 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.
Unter einer Entspannungsrichtung ist eine Richtung zu verste hen, in welcher sich der Prozessdampf im Wesentlichen bewegt bzw. geleitet wird. D.h., wenn sich der Prozessdampf in einen Dampfturbinenabschnitt, bspw. von links nach rechts bewegt, ist darunter vereinfacht betrachtet eine lineare Entspan nungsrichtung nach rechts zu verstehen. Ferner ist vorliegend unter einer Entspannungsrichtung eine Druckrichtung von einem Hochdruckbereich in einen Niederdruckbereich bzw. in einen Druckbereich mit einem niedrigeren Druck als im Hochdruckbe reich zu verstehen. Entsprechend ist über einen stromaufwär- tigen Dampfturbinenabschnitt ein Abschnitt zu verstehen, der entgegen der Entspannungsrichtung angeordnet ist. An expansion direction is to be understood as a direction in which the process steam is essentially moved or directed. In other words, when the process steam moves into a steam turbine section, for example from left to right, it is simply understood to mean a linear expansion direction to the right. Furthermore, 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. Accordingly, a section upstream of a steam turbine section is to be understood as being arranged in a direction opposite to the expansion direction.
Die Tatsache, dass das Hochdruckinnengehäuse zunächst vom kalten Dampf, welcher zur Zwischenüberhitzung geführt wird, überströmt wird und anschließend vom heißen von der Zwischen überhitzung kommenden Dampf durchströmt wird, stellt immer noch eine hohe Herausforderung dar. Des Weiteren besteht die zu verhindernde Möglichkeit, dass der kalte zur Zwischenüber hitzung geführte Dampf aufgrund des Druckverlustes in der Zwischenüberhitzung in das Niederdruckinnengehäuse eingesaugt wird. Diese Nachteile des Standes der Technik versucht die vorliegende Erfindung zu beseitigen. The fact that the high-pressure inner casing is first flowed through by the cold steam which is led to the reheating, and then flowed through by the hot steam coming from the reheating, is still a great challenge. Furthermore, there is the possibility that the cold steam led to reheating due to the pressure loss in the Reheating is sucked into the low pressure inner housing. The present invention seeks to overcome these disadvantages of the prior art.
Hinsichtlich der erfindungsgemäßen Dampfturbine wird die Auf gabe gelöst durch die Merkmale des unabhängigen Patentan spruchs 1. Hinsichtlich des Verfahrens zum Betreiben einer solchen Dampfturbine wird die Aufgabe gelöst durch die Merk male des unabhängigen Patentanspruchs 7. With regard to the steam turbine according to the invention, the task is solved by the features of the independent patent claim 1. With regard to the method for operating such a steam turbine, the object is achieved by the features of independent claim 7.
Weitere Vorteile und Ausgestaltungen der Erfindung, die ein zeln oder in Kombination miteinander einsetzbar sind, sind Gegenstand der Unteransprüche. Further advantages and refinements of the invention, which can be used individually or in combination with one another, are the subject of the dependent claims.
Gemäß einem ersten Aspekt der Erfindung wird eine Dampfturbi ne zur Verfügung gestellt. Die Dampfmaschine weist ein Dampf turbinenaußengehäuse auf. Ferner weist die Dampfturbine ein Hochdruckinnengehäuse mit einem ersten Prozessdampfeintritts- abschnitt und einem ersten Prozessdampfaustrittsabschnitt zum Leiten von Prozessdampf durch das Hochdruckinnengehäuse vom ersten Prozessdampfeintrittsabschnitt zum ersten Prozess dampfaustrittsabschnitt in einer ersten Prozessentspannungs einrichtung auf. Des Weiteren weist die Dampfturbine ein Nie derdruckinnengehäuse mit einem zweiten Prozessdampfeintritts- abschnitt und einem zweiten Prozessdampfaustrittsabschnitt zum Leiten von Prozessdampf durch das Niederdruckinnengehäuse vom zweiten Prozessdampfeintrittsabschnitt zum zweiten Pro zessdampfaustrittsabschnitt in einer zweiten Prozessdampfent- spannungseinrichtung auf. Des Weiteren weist die Dampfturbine einen Zwischenüberhitzer zum Zwischenüberhitzen von Prozess dampf, welcher stromabwärts des Hochdruckinnengehäuses und stromaufwärts des Niederdruckinnengehäuses entnehmbar ist, auf. Wobei das Hochdruckinnengehäuse und das Niederdruckin nengehäuse innerhalb des Dampfturbinenaußengehäuses angeord net sind und das Hochdruckinnengehäuse und das Niederdruckin nengehäuse derart angeordnet sind, dass der erste Dampfein trittsabschnitt des Hochdruckinnengehäuses dem zweiten Dampf eintrittsabschnitt des Niederdruckinnengehäuses zugewandt ist und wobei ferner stromabwärts des Hochdruckinnengehäuses ein Prozessdampfumlenkabschnitt zum Umlenken von Prozessdampf aus den ersten Dampfaustrittsabschnitt in eine Richtung entgegen der ersten DampfentSpannungseinrichtung in einen Spalt, wel cher sich zwischen einer Innenwandung des Dampfturbinenaußen gehäuses und einer Außenwandung des Hochdruckinnengehäuses und zumindest abschnittsweise zwischen der Innenwandung des Dampfturbinenaußengehäuses und einer Außenwandung des Nieder- druckinnengehäuses erstreckt, ausgebildet ist. Und wobei an einem stromaufwärtigen Endabschnitt des Hochdruckinnengehäu ses, an welchem der erste Prozessdampfeintrittsabschnitt aus gestaltet ist, eine Hochdruckdichtschale zum zumindest teil weisen Abdichten des stromaufwärtigen Endabschnittes des Hochdruckinnengehäuses und an einem stromaufwärtigen Endab schnitt des Niederdruckinnengehäuses , an welchem der zweite Prozessdampfendabschnitt ausgestaltet ist, eine Niederdruck dichtschale zum zumindest teilweisen Abdichten des stromauf- wärtigen Endabschnitts des Niederdruckinnengehäuses angeord net sind, und wobei die Hochdruckdichtschale und die Nieder druckdichtschale benachbart zueinander angeordnet sind. Wobei das Hochdruckinnengehäuse erfindungsgemäß derart ausgebildet ist, dass Prozessdampf dem Hochdruckinnengehäuse entnehmbar und in einem Bereich zwischen der Hochdruckdichtschale und der Niederdruckdichtschale leitbar ist. Der Prozessdampf, der dem Hochdruckinnengehäuse entnehmbar ist, wird direkt auf Zwischenüberhitzungsparameter gedrosselt, ohne Arbeit zu ver richten. Hierdurch ist der Dampf deutlich wärmer als der Pro zessdampf, der innerhalb der ersten Dampfentspannungseinrich- tung entspannt wurde. Der entnommene Prozessdampf kann dadurch dazu genutzt werden, um ihn in einen Bereich der Hochdruckdichtschale und der Niederdruckdichtschale zu lei ten, um dort den Bereich und insbesondere das zweite Innenge häuse lokal zu erwärmen. Hierdurch kann es nicht zu sogenann ten Cold Spots am Rotor und im Bereich des zweiten Dampfein trittsabschnittes des Niederdruckinnengehäuses kommen. Hier durch ergibt sich eine sowohl rotormechanisch als auch rotor dynamisch positive Temperaturverteilung. Aufgrund der gerin geren thermisch getriebenen Verformung am Niederdruckinnenge- häuse können die Spiele zwischen dem Rotor der Dampfturbine und dem Innengehäuse kleiner eingestellt werden. Dies erhöht den Wirkungsgrad der Dampfturbine. Durch das aufgeprägte Tem peraturfeld können zudem höhere absolute Temperaturdifferen zen der Zwischenüberhitzung realisiert werden, was wiederum den Prozesswirkungsgrad der Gesamtanlage steigert. Der Ein satzbereich der Single-Case-Reheat-Turbine, d.h. der Turbine mit einem einzigen Außengehäuse wird hierdurch vergrößert. Dies hat deutliche Kostenvorteile im Vergleich zur alternati ven Multicase-Turbine, bei der mehrere Außengehäuse einge setzt werden. Somit können kostengünstigere Turbinen in einem breiteren Leistungsbereich angeboten werden. According to a first aspect of the invention, a steam turbine is provided. The steam engine has a steam turbine outer casing. 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 relaxation 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 device. Furthermore, 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. And, at an upstream end section of the high-pressure inner casing, on which the first process steam inlet section is designed, 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. As a result, 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. Due to the lower thermally driven deformation on the low pressure inner 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.
Eine Ausgestaltung der Erfindung sieht vor, dass die Hoch druckdichtschale so ausgebildet ist, dass ein vorgebbarer Le ckage-Massenstrom über die Hochdruckdichtschale in einem Be reich zwischen der Hochdruckdichtschale und der Niederdruck dichtschale leitbar ist. Dadurch, dass die Hochdruckdicht schale so ausgebildet ist, dass ein hinreichend großer Dampf massenstrom (Leckage-Strom) durch die Hochdruckdichtschale in den Bereich zwischen der Hochdruckdichtschale und der Nieder druckdichtschale leitbar ist, kann der Zwischenraum zwischen den beiden Dichtschalen entsprechend erwärmt werden, so dass die rotormechanischen und rotordynamischen Eigenschaften hin sichtlich der Temperatur positiv beeinflusst werden, so dass keine Cold Spots am Rotor entstehen und der Bereich des zwei ten Prozessdampfeintrittsabschnitts entsprechend vorgewärmt wird. Auf die zusätzliche Ausbildung von Leitungen und Durch brüchen innerhalb der ersten Entspannungseinrichtung kann so mit verzichtet werden, wodurch sich der konstruktive Aufwand deutlich verringert. Im Prinzip wird der an sich vorhandene Leckage-Strom der Hochdruckdichtschale zum Erwärmen verwen det, wobei die Hochdruckdichtschale so ausgelegt werden muss, dass der Leckage-Massenstrom höher ist, als dies technisch bedingt notwendig wäre. Der Leckage-Massenstrom lässt sich dabei einfach über eine entsprechnde Vergrößerung des Spaltes zwischen den Dichtschalen und dem Rotor bestimmen bzw. ein stellen . Eine weitere Ausgestaltung der Erfindung sieht vor, dass die Hochdruckdichtschale und die Niederdruckdichtschale derart ausgebildet und aufeinander abgestimmt sind, dass der Lecka ge-Massenstrom über die Hochdruckdichtschale größer ist, als der Leckage-Massenstrom über die Niederdruckdichtschale . Vor zugsweise ist dabei der Leckage-Massenstrom über die Hoch druckdichtschale mindestens 30 %, vorzugsweise mindestens 50 % größer als der Leckage-Massenstrom über die Niederdruck dichtschale. Durch die Differenz der Massenströme ergibt sich ein Sperrmassenstrom, der ein Eindringen des kalten Zwischen überhitzungsdampfes in die Niederdruckdichtschale und damit in die zweite Entspannungseinrichtung verhindert. Der heiße Leckage-Massenstrom aus der ersten Entspannungseinrichtung sorgt dabei für ein Vorheizen des Rotors zwischen der ersten Dichtschale und der zweiten Dichtschale und für ein Vorhei zen, insbesondere des zweiten Prozessdampfeintrittsabschnitts an der zweiten Entspannungseinrichtung. One embodiment of the invention provides that 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. On the additional formation of lines and breakthroughs within the first expansion device can be dispensed with, which significantly reduces the design effort. In principle, 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.
Eine weitere Ausgestaltung der Erfindung sieht vor, dass an einem stromabwärtigen Endabschnitt des Niederdruckinnengehäu- ses ein Dichtsteg zum Abdichten eines Dampfturbinenbereiches zwischen dem stromabwärtigen Endabschnitt des Niederdruckin- nengehäuses und dem Dampfturbinenaußengehäuse ausgestaltet ist. Bei der vorliegenden Dampfturbine wird das Niederdrucki- nnengehäuse während eines Betriebs mit Prozessdampf umströmt. Während das Hochdruckinnengehäuse zum Niederdruckinnengehäuse durch den Dichtsteg getrennt ist, der vorzugsweise als inte grierter Dichtsteg am stromabwärtigen Endabschnitt des Nie- derdruckinnengehäuses ausgestaltet ist. Unter Verwendung des Dichtstegs kann auf eine innere Dichtschale am stromabwärti- gen Endabschnitt des Niederdruckinnengehäuses verzichtet wer den. Der Dichtsteg weist einen deutlich weniger komplexen Aufbau wie eine Dichtschale auf. An dieser Stelle sei er wähnt, dass vorliegend unter einer Dichtschale eine dem Stand der Technik übliche Dichtschale zu verstehen ist, welche vor liegend deshalb nicht im Detail beschrieben wird. Eine weitere Ausgestaltung der Erfindung sieht vor, dass der Zwischenüberhitzer außerhalb des Dampfturbinenaußengehäuses angeordnet ist. Dies ist insbesondere mit Blick auf die Mon tage, Demontage, Wartung und Reparatur von Vorteil. 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. In the present steam turbine, process steam flows around the low-pressure inner casing during operation. While the high-pressure inner housing is separated from the low-pressure inner housing by the sealing web, which is preferably designed as an integrated sealing web at the downstream end section of the low-pressure inner housing. Using the sealing web, 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. At this point he should be aware that in the present case a sealing shell is to be understood as a sealing shell customary in the prior art, which is therefore not described in detail before lying down. 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.
Gemäß einem weiteren Aspekt der vorliegenden Erfindung wird ein Verfahren zum Betreiben einer wie vorstehend im Detail dargestellten Dampfturbine zur Verfügung gestellt. Damit bringt ein erfindungsgemäßes Verfahren die gleichen Vorteile mit sich, wie sie ausführlich mit Bezug auf die erfindungsge mäße Dampfturbine beschrieben worden sind. Das Verfahren weist die folgenden Schritte auf: According to a further aspect of the present invention, a method for operating a steam turbine as shown in detail above is provided. Thus, 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:
- Leiten von Prozessdampf von einer Prozessdampfquelle - Directing process steam from a process steam source
durch den ersten Prozessdampfeintrittsabschnitt in das Hochdruckinnengehäuse,  through the first process steam inlet section into the high pressure inner housing,
- Leiten des Prozessdampfes vom ersten Prozessdampfein  - Introducing the process steam from the first process steam
trittsabschnitt zum ersten Prozessdampf  step to the first process steam
austrittsabschnitt , und  outlet section, and
- Leiten des Prozessdampfes durch den ersten Prozessdampf austrittsabschnitt aus dem Hochdruckinnengehäuse über den Prozessdampfumlenkabschnitt und den Spalt zum Zwi schenüberhitzer sowie,  - Guiding the process steam through the first process steam outlet section from the high pressure inner housing over the process steam deflection section and the gap to the intermediate superheater and
- Entnehmen eines Teiles des Prozessdampfes aus dem Hoch druckinnengehäuse entspannen dieses Teils des Prozess dampfes auf Zwischenüberhitzungsparameter und Einleiten des entnommenen Prozessdampfes in dem Bereich zwischen der Hochdruckdichtschale und der Niederdruckdichtschale .  - Removing part of the process steam from the high pressure inner housing relax this part of the process steam to reheat parameters and initiate the removed process steam in the area between the high-pressure sealing shell and the low-pressure sealing shell.
Durch das Verfahren ergibt sich eine rotormechanische und ro tordynamische positive Temperaturverteilung. Durch das aufge prägte Temperaturfeld können höhere absolute Temperaturdiffe renzen der Zwischenüberhitzung realisiert werden und damit der Gesamtwirkungsgrad erhöht werden. 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.
Eine Ausgestaltung des Verfahrens sieht vor, dass der entnom mene Prozessdampf (Leckage-Dampfes) , über die Hochdruckdicht schale in den Bereich zwischen der Hochdruckdichtschale und der Niederdruckdichtschale geleitet wird. Hierdurch kann das erfindungsgemäße Verfahren mit geringem konstruktivem Aufwand und damit kostengünstig realisiert werden. Die Umrüstung be stehender Dampfturbinen auf den beschriebenen Prozess ist mit einfachen Mitteln zu bewerkstelligen. 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. As a result, 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.
Weitere, die Erfindung verbessernde Maßnahmen ergeben sich aus den nachfolgenden Beschreibungen zu verschiedenen Ausfüh rungsbeispielen der Erfindung, welche in den Figuren schema tisch dargestellt sind. Sämtliche aus den Ansprüchen, der Be schreibung oder der Zeichnung hervorgehenden Merkmale Further measures improving the invention result from the following descriptions of various exemplary embodiments of the invention, which are shown schematically in the figures. All features arising from the claims, the description or the drawing
und/oder Vorteile, einschließlich konstruktiver Einzelheiten und räumlicher Anordnungen können sowohl für sich als auch in den verschiedenen Kombinationen erfindungswesentlich sein. Es zeigt : and / or advantages, including structural details and spatial arrangements, may be essential to the invention both individually and in the various combinations. It shows :
Figur 1 den prinzipiellen Aufbau einer erfindungsgemäßen Figure 1 shows the basic structure of an inventive
Dampfturbine ;  Steam turbine;
Figur 2 die Detailansicht Z, in der das erfindungsgemäße  Figure 2 shows the detailed view Z, in which the invention
Verfahren näher erläutert wird.  Procedure is explained in more detail.
Figur 1 zeigt den prinzipiellen Aufbau einer erfindungsgemä ßen Dampfturbine 1. Die Dampfturbine 1 weist ein Dampfturbi nenaußengehäuse 20 auf, in welchem sich ein Hochdruckinnenge- häuse 30, ein Niederdruckinnengehäuse 40 in Form eines Mit- teldruckinnengehäuses sowie ein weiteres Niederdruckinnenge häuse 90 befindet. Stromaufwärts zum Hochdruckinnengehäuse 30 ist eine Frischdampf- bzw. Prozessdampfquelle 10 zum Zuführen von Prozessdampf zum Hochdruckinnengehäuse 30 angeordnet. Das Hochdruckinnengehäuse 30 weist einen ersten Prozessdampfein- trittsabschnitt 31 und einen ersten Prozessdampfaustrittsab- schnitt 32 zum Leiten von Prozessdampf durch das Hochdruckin nengehäuse 30 vom ersten Prozessdampfeintrittsabschnitt 31 zum ersten Prozessdampfaustrittsabschnitt 32 in einer ersten ProzessdampfentSpannungseinrichtung 33 auf. Das Nieder druckinnengehäuse 40 weist einen zweiten Prozessdampfein trittsabschnitt 41 und einen zweiten Prozessdampfaustrittsab schnitt 42 zum Leiten von Prozessdampf durch das Niederdru- ckinnengehäuse 40 vom zweiten Prozessdampfeintrittsabschnitt 41 zum zweiten Prozessdampfaustrittsabschnitt 42 in einer zweiten ProzessdampfentSpannungseinrichtung 43 auf. Die 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. The
Dampfturbine 1 weist ferner einen Zwischenüberhitzer 50 auf, der stromabwärts des Hochdruckinnengehäuses 30 und stromauf wärts des Niederdruckinnengehäuses 40 angeordnet ist. Die An ordnung bezieht sich dabei nicht auf eine räumliche, sondern auf eine strömungstechnische Anordnung. 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.
Wie in Figur 1 dargestellt, sind das Hochdruckinnengehäuse 30 und das Niederdruckinnengehäuse 40 derart angeordnet, dass der erste Dampfeintrittsabschnitt 31 des Hochdruckinnengehäu ses 30 dem zweiten Dampfeintrittsabschnitt 41 des Niederdru ckinnengehäuses 40 zugewandt ist. As shown in FIG. 1, 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.
Stromabwärts des Hochdruckinnengehäuses 30 weist die Dampf turbine 1 einen Prozessdampfumlenkabschnitt 60 zum Umlenken von Prozessdampf aus dem ersten Dampfaustrittsabschnitt 32 in eine Richtung entgegen der ersten Dampfentspannungs- einrichtung 33 in einen Spalt 70 der Dampfturbine 1 auf. Der Spalt 70 erstreckt sich zwischen dem Dampfturbinenaußengehäu se 20 und dem Hochdruckinnengehäuse 30 sowie zumindest ab schnittsweise zwischen dem Dampfturbinengehäuse 20 und dem Niederdruckinnengehäuse 40. An einem stromabwärtigen Endab schnitt des Niederdruckinnengehäuses 40 ist ein Dichtsteg 80 zum Abdichten eines Dampfturbinenbereichs zwischen dem strom- abwärtigen Endabschnitt des Niederdruckinnengehäuses 40 und dem Dampfturbinenaußengehäuse 20 ausgestaltet. Der Zwischen überhitzer 50 ist außerhalb des Dampfturbinenaußengehäuses 20 angeordnet. Das Hochdruckinnengehäuse 30 und das Niederdru ckinnengehäuse 40 sind als separate Bauteile in einem gemein samen Dampfturbinenaußengehäuse 20 bereitgestellt. 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. 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.
Am stromaufwärtigen Endabschnitt des Hochdruckinnengehäuses 30, an welchem der erste Prozessdampfeintrittsabschnitt 31 ausgestaltet ist, ist eine Hochdruckdichtschale 34 zum teil weise Abdichten des stromabwärtigen Endabschnittes des Hoch druckinnengehäuses 30 angeordnet. Außerdem ist am stromauf- wärtigen Endabschnitt des Niederdruckinnengehäuses 40, an welchem der zweite Prozessdampfeintrittsabschnitt 41 ausge staltet ist, eine Niederdruckdichtschale 44 zum teilweise Ab dichten des stromaufwärtigen Endabschnittes des Niederdrucki nnengehäuses 40 angeordnet. Die Hochdruckdichtschale 34 und die Niederdruckdichtschale 44 sind benachbart zueinander an geordnet. An einem stromabwärtigen Endabschnitt des Hochdru- ckinnengehäuses 30, an welchem der erste Prozessdampfaus trittsabschnitt 32 ausgestaltet ist, ist eine weitere Hoch druckdichtschale 35 zum zumindest teilweise Abdichten des stromabwärtigen Endabschnittes des Hochdruckinnengehäuses 30 angeordnet. Die Hochdruckdichtschale 34 ist derart ausgelegt und ausgebildet, dass über sie ein vorgebbarer Leckage- Massenstrom austreten und in den Bereich 110 zwischen der Hochdruckdichtschale 34 und der Niederdruckdichtschale 44 leitbar ist. Bei vorgegebenem Dampfdruck und Dampftemperatur kann die Dichtschale bzw. der Dichtspalt so ausgelegt werden, dass ein vorgebbarer Leckage-Massenstrom durch die Dichtscha le hindurchtritt. Die Hochdruckdichtschale 34 und die Nieder druckdichtschale 44 sind so aufeinander abgestimmt, dass der Leckage-Massenstrom über die Hochdruckdichtschale 34 größer ist als der Leckage-Massenstrom über die Niederdruckdicht schale 44. Vorzugsweise ist der Leckage-Massenstrom über die Hochdruckdichtschale 34 mindestens 30 %, vorzugsweise mindes tens 50 % größer als der Leckage-Massenstrom über die Nieder druckdichtschale 44. At the upstream end section of the high pressure inner housing 30, on which the first process steam inlet section 31 is configured, a high pressure sealing shell 34 is arranged for partially sealing the downstream end section of the high pressure inner housing 30. In addition, the upstream present end portion of the low-pressure inner housing 40, on which the second process steam inlet portion 41 is designed, 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. At a downstream end section of the high-pressure inner housing 30, on which the first process steam outlet section 32 is configured, 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. For a given steam pressure and steam temperature, 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.
Figur 2 zeigt eine Detailansicht Z aus Figur 1. An Hand der Figur 2 und mit Bezugnahme auf Figur 1 und den dazu gemachten Beschreibungen wird nachfolgend ein erfindungsgemäßes Verfah ren zum Betreiben einer erfindungsgemäßen Dampfturbine erläu tert . FIG. 2 shows a detailed view Z from FIG. 1. With reference to FIG. 2 and with reference to FIG. 1 and the descriptions made therefor, a method according to the invention for operating a steam turbine according to the invention is explained below.
Um den Spalt zwischen der Welle 100 und den stromaufwärtigen Endabschnitt des Hochdruckinnengehäuses 30 abzudichten, ist eine Hochdruckdichtschale 34 am Endabschnitt des Hochdruckin nengehäuses 30 angeordnet. Zur Abdichtung des Spaltes zwi schen dem stromaufwärtigen Endabschnitt des Niederdruckinnen- gehäuses 40 und der Welle 100 ist eine Niederdruckdichtschale 44 angeordnet. Die Hochdruckdichtschale 34 und die Nieder druckdichtschale 44 sind benachbart zueinander angeordnet. Während des Betriebs der Dampfturbine wird zunächst Prozess dampf von der Prozessdampfquelle 10 durch den ersten Prozess dampfeintrittsabschnitt 31 in das Hochdruckinnengehäuse 30 geleitet. Anschließend wird der Prozessdampf vom ersten Pro zessdampfeintrittsabschnitt 31 zum ersten Prozessdampfaus trittsabschnitt 32 geleitet und danach durch den ersten Pro zessdampfaustrittsabschnitt 32 aus dem Hochdruckinnengehäuse 30 über den Prozessdampfumlenkabschnitt 60 in den Spalt 70 zum Zwischenüberhitzer 50 geleitet. Hierbei wird der Prozess dampf durch den Spalt 70 zum Kühlen des Dampfturbinenaußenge häuses 20 bzw. der Dampfturbine 1 entlang des Hochdruckinnen- gehäuses 30 sowie entlang des Niederdruckinnengehäuses 40 ge leitet. Nachdem der Prozessdampf im Zwischenüberhitzer 50 bei gleichem Druck auf eine vordefinierte Temperatur erhitzt wur de, wird der erhitzte bzw. überhitzte Prozessdampf aus dem Zwischenüberhitzer 50 durch den zweiten Prozessdampfein trittsabschnitt 41 in das Niederdruck- bzw. Mitteldruckinnen- gehäuse geleitet. Von dort wird der Prozessdampf bei gleich bleibender Entspannungsrichtung in das weitere Niederdruckin- nengehäuse 90 gleitet. Dort kann der Prozessdampf weiter ent spannen und schließlich kondensieren. Um zu verhindern, dass der abgekühlte Dampf, welcher der Zwischenüberhitzung 50 zu geführt wird aufgrund des Druckverlustes in der Zwischenüber hitzung in den Spalt zwischen der Hochdruckdichtschale 34 und der Niederdruckdichtschale 44 sowie in das Niederdruckinnen- gehäuse 40 eingesaugt wird, wird Dampf aus dem ersten Hoch druckinnengehäuse 30 Dampf entnommen und direkt auf Zwischen überhitzungsparameter gedrosselt, ohne Arbeit zu verrichten und dieser Dampf direkt in den Spalt zwischen der Hochdruck dichtschale 34 und der Niederdruckdichtschale 44 geleitet. In order to seal the gap between the shaft 100 and the upstream end section of the high-pressure inner housing 30, a high-pressure sealing shell 34 is arranged at the end section of the high-pressure inner housing 30. To seal the gap between the upstream end portion of the low pressure inner housing 40 and the shaft 100, a low pressure sealing shell 44 is arranged. The high pressure sealing shell 34 and the low pressure sealing shell 44 are arranged adjacent to one another. During the operation of the steam turbine, process steam is first passed from the process steam source 10 through the first process steam inlet section 31 into the high-pressure inner housing 30. 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. Here, 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. After the process steam in the reheater 50 has been heated to a predefined temperature at the same pressure, 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. From there, 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. In order to prevent the cooled steam, which is fed to the intermediate superheat 50 due to the pressure loss in the intermediate superheat, into the gap between the high-pressure sealing shell 34 and the low-pressure sealing shell 44 and into the low-pressure inner housing 40, 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.
Hierdurch kann lokal das Niederdruckinnengehäuse 40 sowie der Bereich 110 der Welle 100, welcher zwischen der Hochdruck dichtschale 34 und der Niederdruckdichtschale 44 liegt, lokal erwärmt werden. Um den heißen Dampf dem Hochdruckinnengehäuse 30 zu entnehmen, kann eine Öffnung im Hochdruckinnengehäuse 30 und eine entsprechende Rohrleitung vorgesehen werden. Be sonders einfach und ohne konstruktiven zusätzlichen Aufwand kann der Dampf dem Innengehäuse allerdings über die Hoch druckdichtschale 34 entnommen werden. Hierzu muss der Spalt der Hochdruckdichtschale 34 entsprechend ausgelegt sein. Der heiße Dampf kann dann aus dem Hochdruckinnengehäuse 30 direkt in den Zwischenraum zwischen der ersten Hochdruckdichtschale 34 und der zweiten Niederdruckdichtschale 44 gelangen. Da der Dampf, der über die Hochdruckdichtschale 34 ausströmt nahezu Frischdampfparameter aufweist, kann er dazu genutzt werden, den Bereich 110 zwischen der Hochdruckdichtschale 34 und der Niederdruckdichtschale 44 zu erwärmen. Hierdurch ergibt sich rotordynamisch und rotormechanisch eine positive Temperatur verteilung. Auf der Außenseite des Niederdruckinnengehäuses 40 ist der Druck höher, als auf der Innenseite, Grund hierfür ist der Druckverlust im Spalt, welcher zur Zwischenüberhit zung 50 führt. Der Prozessdampf, der dem Hochdruckinnengehäu se 30 entnommen wird und in dem Bereich 110 zwischen der Hochdruckdichtschale 34 und der Niederdruckdichtschale 44 ge leitet wird, wird somit in das Niederdruckinnengehäuse 40 eingesaugt und sorgt dabei für eine Erwärmung des Niederdru ckinnengehäuse 40. Die Hochdruckdichtschale 34 und die Nie derdruckdichtschale 44 sind so aufeinander abgestimmt, dass der Prozessdampf, welcher über die Hochdruckdichtschale 34 ausströmt mindestens 30 %, vorzugsweise mindestens 50 % grö ßer ist als der Leckage-Massenstrom über die Niederdruck dichtschale 44. Die Differenz der Massenströme führt dazu, dass ein Sperrmassenstrom entsteht, welcher das Eindringen von kaltem, zum Zwischenüberhitzer 50 strömenden Dampf in die Hochdruckdichtschale 34 verhindert. As a result, 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. Around the hot steam the high pressure inner casing 30, an opening in the high-pressure inner housing 30 and a corresponding pipeline can be provided. Be particularly simple and without additional design effort, the steam can be removed from the inner housing via the high pressure sealing shell 34. For this purpose, 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. Since 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. 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.

Claims

Patentansprüche Claims
1. Dampfturbine (1), aufweisend ein Dampfturbinenaußengehäuse (20), ein Hochdruckinnengehäuse (30) mit einem ersten Pro zessdampfeintrittsabschnitt (31) und einem ersten Prozess dampfaustrittsabschnitt (32) zum Leiten von Prozessdampf durch das Hochdruckinnengehäuse (30) vom ersten Prozess dampfeintrittsabschnitt (31) zum ersten Prozessdampfaus trittsabschnitt (32) in einer ersten ProzessdampfentSpan nungsrichtung (33), ein Niederdruckinnengehäuse (40) mit einem zweiten Prozessdampfeintrittsabschnitt (41) und ei nem zweiten Prozessdampfaustrittsabschnitt (42) zum Leiten von Prozessdampf durch das Niederdruckinnengehäuse (40) vom zweiten Prozessdampfeintrittsabschnitt (41) zum zwei ten Prozessdampfaustrittsabschnitt (42) in einer zweiten ProzessdampfentSpannungsrichtung (43) , und einen Zwischen überhitzer (50), zum zwischenüberhitzen von Prozessdampf welcher stromabwärts des Hochdruckinnengehäuses (30) und stromaufwärts des Niederdruckinnengehäuses (40) entnehmbar ist, wobei 1. steam turbine (1), comprising a steam turbine outer casing (20), a high pressure inner casing (30) with a first process steam inlet section (31) and a first process steam outlet section (32) for guiding process steam through the high pressure inner casing (30) from the first process steam inlet section ( 31) to the first process steam outlet section (32) in a first process steam relaxation direction (33), a low pressure inner housing (40) with 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 release direction (43), and an intermediate superheater (50) for reheating process steam which can be removed downstream of the high-pressure inner housing (30) and upstream of the low-pressure inner housing (40), wherein
das Hochdruckinnengehäuse (30) und das Niederdruckinnenge häuse (40) innerhalb des Dampfturbinenaußengehäuses (20) angeordnet sind,  the high pressure inner casing (30) and the low pressure inner casing (40) are arranged inside the steam turbine outer casing (20),
das Hochdruckinnengehäuse (30) und das Niederdruckinnenge häuse (40) derart angeordnet sind, dass der erste Dampf eintrittsabschnitt (31) des Hochdruckinnengehäuses (30) dem zweiten Dampfeintrittsabschnitt (41) des Niederdrucki nnengehäuses (40) zugewandt ist,  the high-pressure inner housing (30) and the low-pressure inner housing (40) are arranged such 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),
stromabwärts des Hochdruckinnengehäuses (30) ein Prozess- dampfumlenkabschnitt (60) zum Umlenken von Prozessdampf aus dem ersten Dampfaustrittsabschnitt (32) in eine Rich tung entgegen der ersten DampfentSpannungsrichtung (33) in einen Spalt (70), welcher sich zwischen einer Innenwandung des Dampfturbinenaußengehäuses (20) und einer Außenwandung des Hochdruckinnengehäuses (30) und zumindest abschnitts weise zwischen der Innenwandung des Dampfturbinenaußenge häuses (20) und einer Außenwandung des Niederdruckinnenge häuses (40) erstreckt, ausgebildet ist, an einem stromaufwärtigen Endabschnitt des Hochdruckinnen- gehäuses (30), an welchem der erste Prozessdampfeintritts- abschnitt (31) ausgestaltet ist, eine Hochdruck downstream of the high-pressure inner housing (30), a process steam deflecting section (60) for deflecting process steam from the first steam outlet section (32) in a direction opposite to the first steam release direction (33) into a gap (70) which is located between an inner wall of the steam turbine outer casing ( 20) and an outer wall of the high-pressure inner housing (30) and at least in sections between the inner wall of the steam turbine outer housing (20) and an outer wall of the low-pressure inner housing (40), high pressure at an upstream end section of the high-pressure inner housing (30), on which the first process steam inlet section (31) is configured
dichtschale (34) zum zumindest teilweisen Abdichten des stromaufwärtigen Endabschnitts des Hochdruckinnengehäuses (30) und an einem stromaufwärtigen Endabschnitt des Nie- derdruckinnengehäuses (40), an welchem der zweite Prozess dampfeintrittsabschnitt (41) ausgestaltet ist, eine Nie derdruckdichtschale (44) zum zumindest teilweisen Abdich ten des stromaufwärtigen Endabschnitts des Niederdruckin- nengehäuses (40) angeordnet sind, und wobei die Hochdruck dichtschale (34) und die Niederdruckdichtschale (44) be nachbart zueinander angeordnet sind, dadurch gekennzeichnet, dass  Sealing shell (34) for at least partially sealing the upstream end section of the high-pressure inner housing (30) and, at least partially, a low-pressure sealing shell (44) on an upstream end section of the low-pressure inner housing (40), on which the second process steam inlet section (41) is designed Sealing the upstream end section of the low-pressure inner housing (40) are arranged, and wherein the high-pressure sealing shell (34) and the low-pressure sealing shell (44) are arranged adjacent to one another, characterized in that
das Hochdruckinnengehäuse (30) derart ausgebildet ist, dass Prozessdampf dem Hochdruckinnengehäuse (30) entnehm bar und in einen Bereich (110) zwischen der Hochdruck dichtschale (34) und der Niederdruckdichtschale (44) leit bar ist.  the high-pressure inner housing (30) is designed such that process steam can be removed from the high-pressure inner housing (30) and can be conducted into an area (110) between the high-pressure sealing shell (34) and the low-pressure sealing shell (44).
2. Dampfturbine (1) nach Anspruch 1, 2. steam turbine (1) according to claim 1,
dadurch gekennzeichnet, dass  characterized in that
die Hochdruckdichtschale so ausgebildet ist, dass ein vor- gebbarer Leckagemassenstrom über die Hochdruckdichtschale (34) in einen Bereich (110) zwischen der Hochdruckdicht schale (34) und der Niederdruckdichtschale (44) leitbar ist .  the high-pressure sealing shell is designed such that a predeterminable leakage mass flow can be conducted via the high-pressure sealing shell (34) into an area (110) between the high-pressure sealing shell (34) and the low-pressure sealing shell (44).
3. Dampfturbine (1) nach Anspruch 2, 3. steam turbine (1) according to claim 2,
dadurch gekennzeichnet, dass  characterized in that
die Hochdruckdichtschale (34) und der Niederdruckdicht schale (44) derart ausgebildet und aufeinander abgestimmt sind, dass der Leckagemassenstrom über die Hochdruck dichtschale (34) größer ist als ein Leckagemassenstrom über die Niederdruckdichtschale (44). the high-pressure sealing shell (34) and the low-pressure sealing shell (44) are designed and matched to one another in such a way that the leakage mass flow through the high-pressure sealing shell (34) is greater than a leakage mass flow through the low-pressure sealing shell (44).
4. Dampfturbine (1) nach Anspruch 3, 4. steam turbine (1) according to claim 3,
dadurch gekennzeichnet, dass  characterized in that
der Leckagemassenstrom über die Hochdruckdichtschale (34) mindestens 30% vorzugsweise mindestens 50% größer ist als der Leckagemassenstrom über die Niederdruckdichtschale (44) .  the leakage mass flow through the high-pressure sealing shell (34) is at least 30% preferably at least 50% greater than the leakage mass flow through the low-pressure sealing shell (44).
5. Dampfturbine (1) nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass 5. Steam turbine (1) according to one of the preceding claims, characterized in that
an einem stromabwärtigen Endabschnitt des Niederdruckin- nengehäuses (40) ein Dichtsteg (80) zum Abdichten eines Dampfturbinenbereichs zwischen dem stromabwärtigen Endab schnitt des Niederdruckinnengehäuses (40) und dem Dampf turbinenaußengehäuse (20) ausgestaltet ist.  at a downstream end section of the low-pressure inner casing (40) a sealing web (80) for sealing a steam turbine region between the downstream end section of the low-pressure inner casing (40) and the steam turbine outer casing (20) is designed.
6. Dampfturbine (1) nach einem der voranstehenden Ansprüche, dadurch gekennzeichnet, dass 6. Steam turbine (1) according to one of the preceding claims, characterized in that
der Zwischenüberhitzer außerhalb des Dampfturbinenaußenge häuses (20) angeordnet ist.  the reheater is arranged outside the steam turbine outer housing (20).
7. Verfahren zum Betreiben einer Dampfturbine (1) nach einem der voranstehenden Ansprüche, aufweisend die Schritte:7. A method for operating a steam turbine (1) according to one of the preceding claims, comprising the steps:
- Leiten von Prozessdampf von einer Prozessdampfquelle (10) durch den ersten Prozessdampfeintrittsabschnitt (31) in das Hochdruckinnengehäuse (30), - guiding process steam from a process steam source (10) through the first process steam inlet section (31) into the high pressure inner housing (30),
- Leiten des Prozessdampfes vom ersten Prozessdampfein trittsabschnitt (31) zum ersten Prozessdampfaustrittsab schnitt (32), und  - Guiding the process steam from the first process steam inlet section (31) to the first process steam outlet section (32), and
- Leiten des Prozessdampfes durch den ersten Prozessdampf austrittsabschnitt (32) aus dem Hochdruckinnengehäuse (30) über den Prozessdampfumlenkabschnitt und den Spalt (70) zum Zwischenüberhitzer (50)  - Guiding the process steam through the first process steam outlet section (32) from the high pressure inner housing (30) via the process steam deflection section and the gap (70) to the reheater (50)
- entnehmen eines Teils des Prozessdampf aus dem Hochdru ckinnengehäuse (30), entspannen dieses Teils des Pro zessdampfes auf Zwischenüberhitzungsparameter und ein leiten des entnommenen Prozessdampfes in den Bereich (110) zwischen der Hochdruckdichtschale (34) und der Niederdruckdichtschale (44). - Remove part of the process steam from the high-pressure inner housing (30), relax this part of the process steam to reheat parameters and direct the process steam removed into the area (110) between the high-pressure sealing shell (34) and the low-pressure sealing shell (44).
8. Verfahren zum Betreiben einer Dampfturbine (1) nach An spruch 7, 8. A method for operating a steam turbine (1) according to claim 7,
dadurch gekennzeichnet, dass  characterized in that
der entnommene Prozessdampf Leckagedampf ist, welcher über die Hochdruck-Dichtschale (34) in den Bereich ( 110 ) zwischen der Hochdruckdichtschale (34) und der Niederdruckdicht schale (44) geleitet wird.  The process steam removed is leakage steam which is passed via the high-pressure sealing shell (34) into the region (110) between the high-pressure sealing shell (34) and the low-pressure sealing shell (44).
EP19795107.2A 2018-11-13 2019-10-15 Steam turbine and method for operating same Active EP3850194B1 (en)

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