EP2601382A1 - Sperrschaltung bei dampfturbinen zur nassdampfabsperrung - Google Patents
Sperrschaltung bei dampfturbinen zur nassdampfabsperrungInfo
- Publication number
- EP2601382A1 EP2601382A1 EP11761538.5A EP11761538A EP2601382A1 EP 2601382 A1 EP2601382 A1 EP 2601382A1 EP 11761538 A EP11761538 A EP 11761538A EP 2601382 A1 EP2601382 A1 EP 2601382A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- steam
- steam turbine
- balance piston
- pressure
- thrust balance
- 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
Links
Classifications
-
- 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
-
- 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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
-
- 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
- F01D25/007—Preventing corrosion
-
- 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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
-
- 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
- F05D2260/60—Fluid transfer
- F05D2260/608—Aeration, ventilation, dehumidification or moisture removal of closed spaces
-
- 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
- F05D2260/95—Preventing corrosion
Definitions
- the invention relates to a steam turbine comprising a rotatably mounted rotor, an inner housing and arranged between the rotor and the inner housing high-pressure flow passage, the rotor having a thrust balance piston, wherein the steam turbine has a Schubaus Dermatskolben- line, wherein the thrust balance piston line opens into a thrust balance piston antechamber.
- steam turbines are divided into a plurality Operaturbi ⁇ NEN, such as a high, intermediate and low pressure turbine section.
- the aforementioned sub-turbines differ essentially in that the steam parameters such as temperature and pressure of the incoming steam are different.
- a high-pressure turbine part experiences the highest steam parameters and is thus subjected to the highest thermal load.
- the effluent from the high-pressure turbine section steam is reheated via a reheater and flowed in a medium-pressure turbine section, the steam flows after flowing through the medium-pressure turbine section in the low-pressure turbine section without reheating.
- each turbine section has its own housing.
- the high ⁇ pressure turbine part and the medium-pressure turbine part in a common outer housing are housed.
- part turbines in which the medium-pressure part and the Never ⁇ derdruckteil are arranged together in an outer housing.
- the turbine sections are formed with a rotor, an inner housing arranged around the rotor and an outer housing.
- the rotor comprises blades, which together with the attached arrange ⁇ ten vanes in the inner housing a flow channel.
- the high-pressure turbine sections are designed to be single-flow, with the result that a comparatively high thrust as a result of the steam pressure on the rotor leads in one direction. Therefore, the rotors are usually formed with thrust balance piston. By flow of the thrust balance piston at a defined location, a pressure is generated, which leads to a
- the high temperatures require the use of materials that withstand the high temperatures and pressures. Also nickel base based steels or high percentage chromium
- Such components would result in corrosion and erosion upon exposure to wet steam coupled with high flow velocity. This issue is currently addressed by taking relatively costly measures.
- One of the measures would be, for example, the use of high-chromium materials or the use of coatings, which are applied to the components and thus avoid corrosion and erosion.
- the steam flowing out of the flow channel which is essentially a wet Steam is, that means that in the steam small Was ⁇ serpizer have formed, flows to components in the steam turbine, which lead to damage, such as a Corro ⁇ sion or erosion of the component. It is known to keep this wet steam away from the components by means of protective shields.
- the object of the invention is to avoid corrosion and erosion damage caused by wet ⁇ steam.
- a steam turbine comprising a rotatably mounted rotor, an inner housing and a first flow channel arranged between the rotor and the inner housing, wherein the rotor has a thrust balance piston, wherein the steam turbine has a thrust balance piston steam line, wherein the thrust balance steam line in a Schubaus convincedskolbenvorraum opens, wherein the steam turbine has a wet steam line, which produces a fluidic connection between a gap space and a first pressure chamber, wherein the gap space between the rotor and the inner housing is arranged.
- the turbine has a second flow channel, wherein the thrust balance piston steam line with the second
- a vapor which may be a superheated steam, passes from the second
- the thrust balance piston is typically a portion of the rotor with a radius ideally selected for the desired thrust balance at an axial location corresponding pressure level.
- the vestibule is located in front of a radial lateral surface.
- the thrust balance piston steam line is connected to a steam source that has a certain vapor at a pressure and a temperature. This steam mixes with the effluent from the high-pressure turbine section steam and passes between the thrust balance piston and the inner housing in a space between the inner housing and the outer housing. At the point where the steam flows out between the rotor and the inner housing, the outer housing is heavily stressed in terms of erosion and corrosion. According to the invention, the steam turbine is now carried out with a wet steam line.
- wet steam line opens into a gap, which is located between the inner housing and the rotor. At this point from the high pressure turbine flow channel flowing from ⁇ wet steam flows in the direction of thrust-compensating piston.
- This wet steam line is fluidically connected to a first pressure chamber, wherein in this first pressure chamber, a lower pressure prevails than in the gap. As a result, the wet steam in this gap space is almost completely sucked off and removed in the wet steam line. The mixing of the wet steam with the steam in the thrust balance piston antechamber is thereby drastically reduced.
- the outer housing can thus be made of a material having a lower Korro ⁇ sions- and erosion resistance. This will lead to a cheaper version of the outer housing.
- the first pressure chamber is arranged in the second flow channel, wherein the first pressure chamber has a pressure which is less than the pressure in the gap space. This leads to the wet steam entering the gap from the high-pressure turbine section flows via the wet steam line into the first pressure chamber. Thus, the unwanted wet steam, before it could ever get to the outer casing, sucked and discharged into the two ⁇ th flow channel.
- Figure 1 shows a cross section through an inventive
- FIG. 2 shows an enlarged detail in the region of the thrust balance piston of the steam turbine from FIG. 1.
- the steam turbine 1 shows a cross section of a steam turbine 1.
- the steam turbine 1 comprises a combined high pressure and with ⁇ tel founded turbine section 2.
- the essential feature of Dampftur ⁇ bine 1 is that a common outer casing 3 around the vertical ⁇ pressure and intermediate- Partial turbine 2 is arranged.
- the steam turbine 1 comprises a rotor 4, on which a first loading area 5, which is arranged in a high-pressure flow channel 6.
- the rotor 5 further comprises a second blading region 7, which is arranged in a medium-pressure flow channel 8.
- Both the high pressure Strö ⁇ flow duct 6 and the intermediate-pressure flow passage 8 comprise a plurality of arranged on the rotor 4, is not provided with reference numerals blades on and in an inner casing 9 arranged not provided with reference numerals guide vanes.
- the terms high-pressure and intermediate-pressure turbine be ⁇ pull to the steam parameters of the incoming vapor.
- the pressure of the flow into the high pressure turbine section ⁇ the vapor is greater than the pressure of air flowing into the intermediate-pressure turbine ⁇ vapor.
- high pressure and Medium-pressure turbine parts also differ in that the steam flowing out of the high-pressure turbine section is reheated in a reheater and then flows into the medium-pressure turbine section.
- the steam turbine 1 shown in Figure 1 is characterized by a common inner housing 9 for the first Beschau ⁇ felungs Scheme 5 and the second Blade 7 from.
- a vapor flows into a high pressure Einströmbe ⁇ rich 10.
- the steam flows through the first blading region 5 corresponds long in a first flow direction.
- the steam flows out into a high-pressure outflow region 12 out of the steam turbine.
- the steam present in the high-pressure outflow region 12 has temperature and pressure values which differ from the temperature and pressure values of the steam in the high-pressure inflow region 10. In particular, the temperature and pressure due to expansion of the vapor clotting ⁇ ger have become.
- the steam present in the high-pressure outflow region 12 has such temperature and pressure values that this steam can be referred to as wet steam.
- the majority of the wet steam flows out of the steam turbine 1 via the high-pressure outflow region 12. However, a residual leakage flow remains, which is arranged in a gap 13 between the rotor 4 and the inner housing 9. This wet steam located in the gap 13 flows in the first flow direction 11 and strikes a thrust balance piston 14.
- the thrust balance piston 14 has a thrust balance piston antechamber 15, in which a superheated steam flows. This superheated steam is located in the thrust balance piston antechamber 15, between the thrust balance piston 14 and a rear wall 16 of the inner housing 9 is arranged. The superheated steam located in the thrust balance piston antechamber 15 leads to an axially acting force on the thrust balance piston 14 and thus on the rotor 4.
- a gap 17 Between the inner housing 9 and the rotor 4 in the region of the thrust balance piston 14 is a gap 17. Through this gap, a vapor can flow, which enters an intermediate space 18 which is located between the outer housing 3 and the inner housing 9. A wet steam present in the gap 17 could lead to an increased risk of corrosion and erosion of the outer housing 3.
- a wet steam line According to the invention now arranged in the steam turbine 1 19, which establishes a fluidic Ver ⁇ bond between the gap space 13 and a first pressure chamber 20 with the gap 13 between the rotor 4 and the inner casing 9 is disposed.
- the first pressure chamber 20 be ⁇ found in the second blading region 7, in particular in a second flow passage 21.
- the embodiment illustrated in Figure 1 shows that the first pressure chamber 20 is arranged in the area of the second flow channel 21st
- the pressure in this first pressure chamber 20 should be such that the pressure for the wet steam in the gap 13 is greater than in the first pressure chamber 20, so that a pressure gradient in the wet steam line 19 prevails, which causes the wet steam from the gap 13 to first pressure chamber 20 passes.
- the thrust balance piston 14 extends in a radial direction 22, which is formed substantially perpendicular to the rotation axis 23.
- the thrust balance piston steam line 24 is provided with a
- Steam source 25 fluidly connected. As shown in FIG. 1, the inflow region 26 forms the vapor source 25. This in the inflow region 26 into the medium-pressure sub-turbine incoming steam is superheated steam entering the thrust balance piston antechamber 15. In an alternative embodiment, the steam source 25 may also be arranged outside the steam turbine 1.
- the inner housing 9 has a feed opening 27, with which the wet steam line 19 can be connected.
- FIG. 2 shows an enlarged section of the high-pressure outflow region 12 of the high-pressure turbine part.
- Inner housing 9 is formed such that a high pressure Ausström Scheme 12 is enclosed and in the region of the gap 13 against the rotor 4 is applied.
- the gap 13 should be as small as possible so that the wet steam located in the high-pressure outflow region 12 does not flow out over the gap 13.
- the majority of the wet steam will pass through the high-pressure discharge area 12 to a reheater.
- a lesser part passes as leakage flow between the rotor 4 and the inner housing 9 in the gap space 13. Therefore, a not-shown cavity is arranged in the inner housing 9, which is connected to the gap space 13. About this cavity and the wet steam line 19, the leakage flow is sucked out, so to speak.
- the drive for this Ab ⁇ suction the first pressure chamber 20 having a lower pressure than the pressure in the gap 13 is a further flow of the leakage flow is formed from wet steam in the
- Gap space 13 in the direction of the thrust balance piston antechamber 15 is prevented in that the largest part of the wet steam in the wet steam line 19 is sucked off.
- the superheated steam entering the thrust balance piston antechamber 15 via a thrust balance piston line 24 will spread in two directions. First, the superheated steam will spread in the direction of the gap 17 and eventually hit the outer casing 3. Another part of the superheated steam flows in the direction of the gap 13 and, like the wet steam, is sucked out via the wet steam line 19 to the first pressure chamber 20.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Abstract
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP11761538.5A EP2601382B1 (de) | 2010-09-16 | 2011-09-14 | Sperrschaltung bei dampfturbinen zur nassdampfabsperrung |
Applications Claiming Priority (3)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP10177090A EP2431570A1 (de) | 2010-09-16 | 2010-09-16 | Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung |
PCT/EP2011/065909 WO2012035047A1 (de) | 2010-09-16 | 2011-09-14 | Sperrschaltung bei dampfturbinen zur nassdampfabsperrung |
EP11761538.5A EP2601382B1 (de) | 2010-09-16 | 2011-09-14 | Sperrschaltung bei dampfturbinen zur nassdampfabsperrung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP2601382A1 true EP2601382A1 (de) | 2013-06-12 |
EP2601382B1 EP2601382B1 (de) | 2014-08-13 |
Family
ID=43598251
Family Applications (2)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10177090A Withdrawn EP2431570A1 (de) | 2010-09-16 | 2010-09-16 | Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung |
EP11761538.5A Not-in-force EP2601382B1 (de) | 2010-09-16 | 2011-09-14 | Sperrschaltung bei dampfturbinen zur nassdampfabsperrung |
Family Applications Before (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP10177090A Withdrawn EP2431570A1 (de) | 2010-09-16 | 2010-09-16 | Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung |
Country Status (4)
Country | Link |
---|---|
US (1) | US9726041B2 (de) |
EP (2) | EP2431570A1 (de) |
CN (1) | CN103097663B (de) |
WO (1) | WO2012035047A1 (de) |
Families Citing this family (4)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2565419A1 (de) * | 2011-08-30 | 2013-03-06 | Siemens Aktiengesellschaft | Kühlung für eine Strömungsmaschine |
EP2565401A1 (de) * | 2011-09-05 | 2013-03-06 | Siemens Aktiengesellschaft | Verfahren zur Temperaturausgleichung in einer Dampfturbine |
JP6132737B2 (ja) * | 2013-10-09 | 2017-05-24 | 株式会社東芝 | 蒸気タービン |
DE102016215770A1 (de) * | 2016-08-23 | 2018-03-01 | Siemens Aktiengesellschaft | Ausströmgehäuse und Dampfturbine mit Ausströmgehäuse |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US1344193A (en) * | 1918-09-05 | 1920-06-22 | Allis Chalmers Mfg Co | Balancing device |
US2326112A (en) * | 1941-11-11 | 1943-08-10 | Westinghouse Electric & Mfg Co | Turbine apparatus |
US2920867A (en) * | 1957-01-22 | 1960-01-12 | Westinghouse Electric Corp | Reheat turbine apparatus |
DE19700899A1 (de) * | 1997-01-14 | 1998-07-23 | Siemens Ag | Dampfturbine |
EP1035301A1 (de) * | 1999-03-08 | 2000-09-13 | Asea Brown Boveri AG | Ausgleichskolben für den axialen Schubausgleich einer Welle von einer Turbine |
WO2001016467A1 (de) * | 1999-08-27 | 2001-03-08 | Siemens Aktiengesellschaft | Turbine sowie verfahren zur abführung von leckfluid |
EP1624155A1 (de) * | 2004-08-02 | 2006-02-08 | Siemens Aktiengesellschaft | Dampfturbine und Verfahren zum Betrieb einer Dampfturbine |
EP1806476A1 (de) * | 2006-01-05 | 2007-07-11 | Siemens Aktiengesellschaft | Turbine für ein thermisches Kraftwerk |
EP2154332A1 (de) * | 2008-08-14 | 2010-02-17 | Siemens Aktiengesellschaft | Verminderung der thermischen Belastung eines Aussengehäuses für eine Strömungsmaschine |
-
2010
- 2010-09-16 EP EP10177090A patent/EP2431570A1/de not_active Withdrawn
-
2011
- 2011-09-14 WO PCT/EP2011/065909 patent/WO2012035047A1/de active Application Filing
- 2011-09-14 EP EP11761538.5A patent/EP2601382B1/de not_active Not-in-force
- 2011-09-14 US US13/823,143 patent/US9726041B2/en not_active Expired - Fee Related
- 2011-09-14 CN CN201180044360.6A patent/CN103097663B/zh not_active Expired - Fee Related
Non-Patent Citations (1)
Title |
---|
See references of WO2012035047A1 * |
Also Published As
Publication number | Publication date |
---|---|
CN103097663B (zh) | 2015-08-19 |
EP2601382B1 (de) | 2014-08-13 |
US9726041B2 (en) | 2017-08-08 |
WO2012035047A1 (de) | 2012-03-22 |
CN103097663A (zh) | 2013-05-08 |
EP2431570A1 (de) | 2012-03-21 |
US20130170956A1 (en) | 2013-07-04 |
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