EP2431570A1 - Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung - Google Patents

Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung Download PDF

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Publication number
EP2431570A1
EP2431570A1 EP10177090A EP10177090A EP2431570A1 EP 2431570 A1 EP2431570 A1 EP 2431570A1 EP 10177090 A EP10177090 A EP 10177090A EP 10177090 A EP10177090 A EP 10177090A EP 2431570 A1 EP2431570 A1 EP 2431570A1
Authority
EP
European Patent Office
Prior art keywords
steam
steam turbine
pressure
balance piston
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.)
Withdrawn
Application number
EP10177090A
Other languages
German (de)
English (en)
French (fr)
Inventor
Henning Almstedt
Peter Dumstorff
Martin Kuhn
Thomas Müller
Rudolf PÖTTER
Norbert Thamm
Uwe Zander
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP10177090A priority Critical patent/EP2431570A1/de
Priority to EP11761538.5A priority patent/EP2601382B1/de
Priority to PCT/EP2011/065909 priority patent/WO2012035047A1/de
Priority to CN201180044360.6A priority patent/CN103097663B/zh
Priority to US13/823,143 priority patent/US9726041B2/en
Publication of EP2431570A1 publication Critical patent/EP2431570A1/de
Withdrawn legal-status Critical Current

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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 channel, the rotor having a thrust balance piston, the steam turbine having a thrust balance piston line, the thrust balance piston line opens into a thrust balance piston antechamber.
  • steam turbines are divided into several sub-turbines, such as e.g. a high pressure, medium pressure and low pressure turbine part.
  • 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 section and the medium-pressure turbine part in a common outer housing are housed.
  • part turbines in which the medium-pressure part and the low-pressure part 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 moving blades, which form a flow channel with the guide vanes arranged in the inner housing.
  • 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 counter thrust, which holds the rotor substantially force-free in the axial direction.
  • the high temperatures require the use of materials that withstand the high temperatures and pressures.
  • Nickel base based steels or high percentage chromium steels are also suitable for use at high temperatures.
  • the components of a steam turbine must be made relatively resistant to corrosion, since some components are flown with wet steam at the same time high flow velocity of the steam. 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
  • 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, the rotor having a thrust balance piston, the steam turbine having a thrust balance steam line, wherein the thrust balance steam line opens into a thrust balance piston antechamber the steam turbine has a wet steam line which produces a fluidic connection between a gap space and a first pressure space, wherein the gap space is arranged between the rotor and the inner housing.
  • the thrust balance steam line directs steam into a thrust balance piston anvil which, as a result of the pressure, exerts a force on the rotor to compensate for thrust.
  • 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 steam line is connected to a source of steam having a particular 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.
  • the steam turbine is now carried out with a wet steam line.
  • This wet steam line opens into a gap, which is located between the inner housing and the rotor.
  • the wet steam flowing out of the high-pressure turbine part flow channel flows in the direction of the thrust balance 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 present in this gap space is virtually 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.
  • An outflow of a mixed vapor formed from the wet steam and the steam in the thrust balance piston antechamber is thereby almost prevented, so that virtually no mixing steam flows between the thrust balance piston and the inner housing to the outer housing.
  • the outer housing can thus be made of a material having a lower corrosion and erosion resistance. This will lead to a cheaper version of the outer housing.
  • the turbine has a second flow channel, wherein the thrust balance steam line is fluidically connected to the second inflow region or another pressure chamber.
  • a vapor which may be superheated steam, passes from the second flow passage via the thrust balance piston steam line to the thrust balance piston antechamber.
  • 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 that in the Gap was wet steam from the high-pressure turbine section via the wet steam line flows into the first pressure chamber. Thus, the unwanted wet steam, before it could ever reach the outer housing, sucked and discharged into the second flow channel.
  • the FIG. 1 shows a cross-section of a steam turbine 1.
  • the steam turbine 1 comprises a combined high-pressure and medium-pressure turbine part 2.
  • the essential feature of the steam turbine 1 is that a common outer housing 3 is arranged around the high-pressure and medium-pressure turbine section 2.
  • the steam turbine 1 comprises a rotor 4, on which a first blading region 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 flow channel 6 and the medium-pressure flow channel 8 comprise a plurality of rotor blades 4, which are not provided with reference numerals, and guide vanes, which are not provided with reference symbols, arranged in an inner housing 9.
  • high pressure and medium pressure turbine parts refer to the steam parameters of the incoming steam.
  • the pressure of the incoming into the high-pressure turbine section steam is greater than the pressure of the in the medium-pressure turbine section incoming steam.
  • high-pressure and medium-pressure turbine sections 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.
  • steam turbine 1 is characterized by a common inner housing 9 for the first blading region 5 and the second blading region 7.
  • steam flows into a high-pressure inflow region 10. From there, the steam flows through the first impingement region 5 in a first flow direction 11. After flowing through the first blading region 5, 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 values have become lower due to expansion of the steam.
  • 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.
  • this wet steam contains the smallest condensed water particles. These smallest water particles in the wet steam at high speeds in an impact on a component of the steam turbine 1 lead to erosion and corrosion damage.
  • the majority of the wet steam flows out of the steam turbine 1 via the high-pressure outflow region 12.
  • 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, which is arranged between the thrust balance piston 14 and a rear wall 16 of the inner housing 9.
  • 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 passes into a gap 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 19 is now arranged in the steam turbine 1, which establishes a fluidic connection between the gap space 13 and a first pressure space 20, the gap space 13 being arranged between the rotor 4 and the inner housing 9.
  • the first pressure chamber 20 is located in the second Beschaufelungs Scheme 7, in particular in a second flow channel 21. Das in FIG. 1 illustrated embodiment shows that the first pressure chamber 20 is arranged in the region of the second flow channel 21. Also, 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 fluidly connected to a steam source 25.
  • the inflow region 26 forms the steam source 25th
  • This steam which flows into the medium-pressure turbine section in the inflow region 26, is a superheated steam which enters the thrust balance piston antechamber 15.
  • 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.
  • the FIG. 2 shows an enlarged section of the high pressure Ausström Schemes 12 of the high pressure turbine section.
  • the inner housing 9 is designed such that a high-pressure outflow region 12 is enclosed and rests in the region of the gap space 13 with respect to the rotor 4.
  • 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.
  • the first pressure space 20 which has a lower pressure than the pressure in the gap space 13, serves as the drive for this suction. Further flow of the leakage flow formed in the gap 13 in the direction of the thrust balance piston chamber 15 is prevented by the greater part of the wet steam flowing 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.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP10177090A 2010-09-16 2010-09-16 Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung Withdrawn EP2431570A1 (de)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP10177090A EP2431570A1 (de) 2010-09-16 2010-09-16 Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung
EP11761538.5A EP2601382B1 (de) 2010-09-16 2011-09-14 Sperrschaltung bei dampfturbinen zur nassdampfabsperrung
PCT/EP2011/065909 WO2012035047A1 (de) 2010-09-16 2011-09-14 Sperrschaltung bei dampfturbinen zur nassdampfabsperrung
CN201180044360.6A CN103097663B (zh) 2010-09-16 2011-09-14 蒸汽涡轮机
US13/823,143 US9726041B2 (en) 2010-09-16 2011-09-14 Disabling circuit in steam turbines for shutting off saturated steam

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP10177090A EP2431570A1 (de) 2010-09-16 2010-09-16 Dampfturbine mit einem Schubausgleichskolben und Nassdampfabsperrung

Publications (1)

Publication Number Publication Date
EP2431570A1 true EP2431570A1 (de) 2012-03-21

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 After (1)

Application Number Title Priority Date Filing Date
EP11761538.5A Not-in-force EP2601382B1 (de) 2010-09-16 2011-09-14 Sperrschaltung bei dampfturbinen zur nassdampfabsperrung

Country Status (4)

Country Link
US (1) US9726041B2 (zh)
EP (2) EP2431570A1 (zh)
CN (1) CN103097663B (zh)
WO (1) WO2012035047A1 (zh)

Families Citing this family (4)

* Cited by examiner, † Cited by third party
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

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2326112A (en) * 1941-11-11 1943-08-10 Westinghouse Electric & Mfg Co Turbine apparatus
EP1035301A1 (de) * 1999-03-08 2000-09-13 Asea Brown Boveri AG Ausgleichskolben für den axialen Schubausgleich einer Welle von einer Turbine
US6695575B1 (en) * 1999-08-27 2004-02-24 Siemens Aktiengesellschaft Turbine method for discharging leakage fluid
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

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1344193A (en) * 1918-09-05 1920-06-22 Allis Chalmers Mfg Co Balancing device
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

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2326112A (en) * 1941-11-11 1943-08-10 Westinghouse Electric & Mfg Co Turbine apparatus
EP1035301A1 (de) * 1999-03-08 2000-09-13 Asea Brown Boveri AG Ausgleichskolben für den axialen Schubausgleich einer Welle von einer Turbine
US6695575B1 (en) * 1999-08-27 2004-02-24 Siemens Aktiengesellschaft Turbine method for discharging leakage fluid
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

Also Published As

Publication number Publication date
EP2601382A1 (de) 2013-06-12
CN103097663A (zh) 2013-05-08
US9726041B2 (en) 2017-08-08
US20130170956A1 (en) 2013-07-04
EP2601382B1 (de) 2014-08-13
CN103097663B (zh) 2015-08-19
WO2012035047A1 (de) 2012-03-22

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