EP3130748A1 - Refroidissement de rotor pour une turbine a vapeur - Google Patents

Refroidissement de rotor pour une turbine a vapeur Download PDF

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Publication number
EP3130748A1
EP3130748A1 EP15181031.4A EP15181031A EP3130748A1 EP 3130748 A1 EP3130748 A1 EP 3130748A1 EP 15181031 A EP15181031 A EP 15181031A EP 3130748 A1 EP3130748 A1 EP 3130748A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam
medium
cooling
rotor
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Withdrawn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
EP15181031.4A
Other languages
German (de)
English (en)
Inventor
Norbert Pieper
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 EP15181031.4A priority Critical patent/EP3130748A1/fr
Priority to JP2018507526A priority patent/JP2018527505A/ja
Priority to EP16734336.7A priority patent/EP3307988A1/fr
Priority to CN201680047736.1A priority patent/CN107923246B/zh
Priority to PCT/EP2016/065295 priority patent/WO2017029008A1/fr
Publication of EP3130748A1 publication Critical patent/EP3130748A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • 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
    • 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
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • 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

Definitions

  • the invention relates to a steam turbine comprising a high-pressure turbine part comprising a multi-rotor rotatably mounted high-pressure rotor with a thrust balance piston and arranged around the high pressure rotor high pressure inner housing, wherein between the thrust balance piston and the high pressure inner housing, a cooling steam space is formed and a Medium-pressure turbine part, wherein the medium-pressure turbine section includes a medium-pressure rotor, wherein the medium-pressure rotor has an inflow, wherein a cooling line protrudes into the inflow, which is fluidly connected to the high-pressure turbine section.
  • the invention relates to a method for operating a steam turbine.
  • a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
  • gas turbines are traversed with gas and / or air as a working medium, which, however, is subject to completely different temperature and pressure conditions, as the steam in a steam turbine.
  • a steam turbine typically comprises a rotor-mounted rotatably mounted rotor disposed within a housing.
  • the rotor When flowing through the interior of the flow channel formed by the housing shell with heated and pressurized steam, the rotor is rotated by the vanes through the steam.
  • the blades of the rotor are also referred to as blades.
  • usually stationary guide vanes are suspended on the inner housing, which engage along an axial extent of the body in the interspaces of the rotor blades.
  • a vane is usually on held a first position along an inner side of the steam turbine housing. In this case, it is usually part of a stator blade row, which comprises a number of guide vanes, which are arranged along an inner circumference on the inside of the steam turbine housing.
  • Each vane has its blade radially inward.
  • a row of vanes at said first location along the axial extent is also referred to as a vane grille or crown.
  • a number of vane rows are connected in series. Accordingly, at a second location along the axial extent behind the first location, a further second blade is held along the inside of the steam turbine housing.
  • a pair of a vane row and a blade row is also referred to as a vane stage.
  • the housing jacket of such a steam turbine can be formed from a number of housing segments.
  • the housing shell of the steam turbine is to be understood as meaning, in particular, the stationary housing component of a steam turbine or a partial turbine, which has an interior space in the form of a flow channel along a longitudinal direction of the steam turbine, which is provided for flowing through with the working medium in the form of steam.
  • This may be an inner casing and / or a vane carrier, depending on the steam turbine type.
  • it may also be provided a turbine housing, which has no inner housing or no guide vane.
  • Steam turbines usually include a high-pressure turbine section, a medium-pressure turbine section and a low-pressure turbine section.
  • a live steam first flows into the high-pressure turbine section and then flows to the medium-pressure turbine section and then to the low-pressure turbine section.
  • Steam turbines are used in steam power plants, such as in fossil-fired steam power plants.
  • fossil-fired steam power plants the demands on the efficiencies to be achieved increase.
  • inlet temperatures of up to 630 ° are desirable.
  • Such high temperatures lead to a high thermal stress of the materials for the rotor and for the housing.
  • the limits of use of a rotor are achieved by the thermally highly stressed areas, such as the inflow area.
  • a temperature of a cooling steam whose temperature is higher than that of the high-pressure exhaust steam would be sufficient for cooling.
  • the object of the invention is therefore to provide a steam turbine, which can be better cooled. This is achieved by a steam turbine according to claim 1, further, the object is achieved by a method according to claim 10.
  • An essential feature of the proposed invention is to take the cooling steam for the medium-pressure turbine section from the high-pressure turbine section, wherein the cooling steam is removed from the cooling steam space, which is removed between the thrust balance piston and the high pressure inner housing.
  • this cooling steam consists of partially-expanded steam, this is cool enough to cool the medium-pressure rotor.
  • cooling steam in this case a cooling steam is used, which is used for cooling the high-pressure turbine section.
  • This cooling steam is also referred to as internal cooling steam.
  • This internal cooling steam is used for external cooling of the medium pressure range. This leads to a minimization of the undesired negative influence on the turbine efficiency by minimizing the cooling mass flow requirement and thus also minimizing the expenditure on equipment.
  • Another advantageous effect is that the exergetic losses that occur when mixing two steam mass flows of different temperature, turn out to be lower. Furthermore, a smaller operating clearance is established at the seals. Thus, both effects reduce the efficiency level disadvantage of medium pressure shaft cooling.
  • another advantage of using the piston leakage steam for cooling is that the fluctuations in the cooling steam temperature (fed from the space behind the thrust balance piston) are lower.
  • the steam turbine is developed in such a way that a high-pressure outer housing is arranged around the high-pressure rotor and the high-pressure inner housing, wherein the thrust balance piston has a back in the direction of rotation to the high-pressure outer housing facing back and between the back and the outer housing, a further cooling steam space is formed, which is fluidically connected to the cooling steam space.
  • the high-pressure turbine part has a live steam supply duct
  • the high-pressure inner housing comprises a plurality of guide vanes arranged such that along a flow direction a flow duct with a plurality of blade stages, one row of rotor blades and one row of stator vanes, is formed
  • the high-pressure inner housing has a connection, which is formed as a communicating tube between the flow channel after a blade stage and the thrust balance piston of the high-pressure rotor and high-pressure inner housing
  • the high-pressure inner housing has a cross-return passage, which a communicating tube is selected between the cooling steam space and an inflow space arranged downstream of a vane stage in the flow channel.
  • the FIG. 1 shows a high pressure turbine part 1.
  • the high pressure turbine part 1 comprises a plurality of blades 2 (for clarity, is in FIG. 1 only one blade provided with the reference numeral 2.
  • the high-pressure rotor 3 is rotatably supported about a rotation axis 4.
  • the high-pressure rotor 3 comprises a thrust balance piston 5, which is arranged between an inflow region 6 and an outer housing 7. Between the thrust balance piston 5 and a high-pressure inner housing 8, a cooling steam space 9 is formed.
  • the high-pressure inner housing 8 is arranged around the high-pressure rotor 3.
  • the high-pressure turbine part 1 has a high-pressure inflow region 6, through which hot steam flows during operation.
  • the hot incoming steam then flows through several high pressure blades and high pressure vanes.
  • the thermal energy of the steam is converted into rotational energy of the rotor 3 in this case.
  • the bearing of the rotor 3 is in the FIG. 1 not shown in detail.
  • the steam flows out of a discharge area 10 out of the high-pressure turbine section 1.
  • the FIG. 1 further shows a medium-pressure turbine section 11, which has a medium-pressure rotor 12 and a medium-pressure inner housing arranged around the medium-pressure rotor 12 13 has.
  • the medium-pressure inner housing 13 is arranged in a medium-pressure outer housing 14.
  • the medium-pressure rotor 12 comprises a plurality of blades 15 distributed over the circumference. For reasons of clarity, only one blade is provided with the reference numeral 15. Furthermore, the medium-pressure inner housing 13 has a plurality of guide vanes 16 evenly distributed about the rotation axis 4. For reasons of clarity, only one vane is provided with the reference numeral 16. A medium-pressure steam flows into a medium-pressure inflow region 17. This vapor flows in a medium-pressure inflow direction 18, which is approximately perpendicular to the axis of rotation 4.
  • the medium-pressure inflow steam in this case meets a guide ring 19, which has a first diagonal stage 20, which deflects the steam to a first flow 21. Furthermore, the steam flows via a second diagonal stage 22 to a second tide 23.
  • the guide ring 19 comprises a first guide ring 19a and a second guide ring 19b. Furthermore, the guide ring 19 has a cooling line into which the cooling steam is introduced and through which the cooling steam flows. This cooling steam line 24 protrudes into a space which is formed by the guide ring 19 and the relief groove 25 of the medium-pressure rotor.
  • the cooling line 24 is fluidically connected to the cooling steam space 9 and the further cooling steam space 28.
  • FIG. 2 shows the inflow region of the medium-pressure turbine part 11th
  • the thrust balance piston 5 has a back 27 pointing in the direction of rotation axis 26 to the high pressure outer housing 7. Between the back 27 and the high-pressure outer casing 7, a further cooling steam space 28 is formed, which is fluidically connected to the cooling steam space 9.
  • the high pressure outer housing 7 has a line for the fluidic connection of the further cooling steam space 28 with the cooling line (in FIG. 3 Not shown).
  • the high-pressure outer casing 7 and the high-pressure inner casing 8 are formed such that the high-pressure part turbine 1 has a live steam supply passage 29.
  • the high pressure inner casing 8 includes a plurality of high pressure vanes 30.
  • the high pressure vanes 30 are arranged such that along a flow direction 31 is formed a flow channel 32 having a plurality of blade stages each having a row of blades and a row of vanes.
  • the high-pressure inner housing 8 has a connection 33, 34, 35, which is formed as a communicating tube between the flow channel 32 after a blade stage and a thrust balance piston antechamber 36 of the high-pressure rotor 3 and the high-pressure inner housing 8.
  • the high-pressure inner housing 8 has a cross return channel 37, which is designed as a communicating tube between the cooling steam space 9 and an inflow space 38 arranged in the flow channel 32 after a vane stage.
  • the cross-return channel 37 may also be formed as a communicating tube between the thrust balance piston antechamber 36 and arranged after a blade stage inflow space 38 in the flow channel 32.
  • the guide ring 19 has a non-contact seal (eg labyrinth seal 39), both in the first flow 21 and in the second flow 23.
  • a non-contact seal eg labyrinth seal 39

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP15181031.4A 2015-08-14 2015-08-14 Refroidissement de rotor pour une turbine a vapeur Withdrawn EP3130748A1 (fr)

Priority Applications (5)

Application Number Priority Date Filing Date Title
EP15181031.4A EP3130748A1 (fr) 2015-08-14 2015-08-14 Refroidissement de rotor pour une turbine a vapeur
JP2018507526A JP2018527505A (ja) 2015-08-14 2016-06-30 蒸気タービンのロータ冷却
EP16734336.7A EP3307988A1 (fr) 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur
CN201680047736.1A CN107923246B (zh) 2015-08-14 2016-06-30 用于蒸汽轮机的转子冷却
PCT/EP2016/065295 WO2017029008A1 (fr) 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15181031.4A EP3130748A1 (fr) 2015-08-14 2015-08-14 Refroidissement de rotor pour une turbine a vapeur

Publications (1)

Publication Number Publication Date
EP3130748A1 true EP3130748A1 (fr) 2017-02-15

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EP15181031.4A Withdrawn EP3130748A1 (fr) 2015-08-14 2015-08-14 Refroidissement de rotor pour une turbine a vapeur
EP16734336.7A Withdrawn EP3307988A1 (fr) 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP16734336.7A Withdrawn EP3307988A1 (fr) 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur

Country Status (4)

Country Link
EP (2) EP3130748A1 (fr)
JP (1) JP2018527505A (fr)
CN (1) CN107923246B (fr)
WO (1) WO2017029008A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3879078A4 (fr) * 2018-11-06 2022-08-31 Shanghai Electric Power Generation Equipment Co., Ltd. Turbine à vapeur et son procédé de refroidissement interne

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2018188997A (ja) * 2017-04-28 2018-11-29 株式会社東芝 蒸気タービンプラント、その組立方法及び送気配管
CN109236379A (zh) * 2018-09-11 2019-01-18 上海发电设备成套设计研究院有限责任公司 一种内部蒸汽冷却的高参数汽轮机的双流高温转子
DE102018219374A1 (de) * 2018-11-13 2020-05-14 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betreiben derselben
CN109826675A (zh) * 2019-03-21 2019-05-31 上海电气电站设备有限公司 汽轮机冷却系统及方法
KR102510537B1 (ko) * 2021-02-24 2023-03-15 두산에너빌리티 주식회사 링 세그먼트 및 이를 포함하는 터보머신

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3406071A1 (de) * 1983-02-21 1984-08-23 Fuji Electric Co., Ltd., Kawasaki Einrichtung zur kuehlung der rotoren von dampfturbinen
JPH09125909A (ja) * 1995-10-30 1997-05-13 Mitsubishi Heavy Ind Ltd 複合サイクル用蒸気タービン
WO1999000583A1 (fr) * 1997-06-27 1999-01-07 Siemens Aktiengesellschaft Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine
EP1788191A1 (fr) * 2005-11-18 2007-05-23 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour le refroidissement d'une turbine à vapeur
US20100221108A1 (en) * 2006-09-11 2010-09-02 General Electric Turbine nozzle assemblies
WO2013017634A1 (fr) * 2011-08-04 2013-02-07 Siemens Aktiengesellschaft Turbine à vapeur comprenant un piston d'équilibrage de poussée

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3406071A1 (de) * 1983-02-21 1984-08-23 Fuji Electric Co., Ltd., Kawasaki Einrichtung zur kuehlung der rotoren von dampfturbinen
JPH09125909A (ja) * 1995-10-30 1997-05-13 Mitsubishi Heavy Ind Ltd 複合サイクル用蒸気タービン
WO1999000583A1 (fr) * 1997-06-27 1999-01-07 Siemens Aktiengesellschaft Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine
EP1788191A1 (fr) * 2005-11-18 2007-05-23 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour le refroidissement d'une turbine à vapeur
US20100221108A1 (en) * 2006-09-11 2010-09-02 General Electric Turbine nozzle assemblies
WO2013017634A1 (fr) * 2011-08-04 2013-02-07 Siemens Aktiengesellschaft Turbine à vapeur comprenant un piston d'équilibrage de poussée

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATERSON A N ET AL: "STEAM TURBINES FOR ADVANCED STEAM CONDITIONS", TECHNICAL REVIEW GEC ALSTHOM, GEC ALSTHOM, PARIS, FR, no. 17, 1 June 1995 (1995-06-01), pages 1 - 16, XP000526077, ISSN: 1148-2893 *

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3879078A4 (fr) * 2018-11-06 2022-08-31 Shanghai Electric Power Generation Equipment Co., Ltd. Turbine à vapeur et son procédé de refroidissement interne
US11746674B2 (en) 2018-11-06 2023-09-05 Shanghai Electric Power Generation Equipment Co., Ltd. Steam turbine and method for internally cooling the same

Also Published As

Publication number Publication date
JP2018527505A (ja) 2018-09-20
WO2017029008A1 (fr) 2017-02-23
CN107923246B (zh) 2020-04-21
EP3307988A1 (fr) 2018-04-18
CN107923246A (zh) 2018-04-17

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