EP3307988A1 - Refroidissement de rotor pour turbine à vapeur - Google Patents

Refroidissement de rotor pour turbine à vapeur

Info

Publication number
EP3307988A1
EP3307988A1 EP16734336.7A EP16734336A EP3307988A1 EP 3307988 A1 EP3307988 A1 EP 3307988A1 EP 16734336 A EP16734336 A EP 16734336A EP 3307988 A1 EP3307988 A1 EP 3307988A1
Authority
EP
European Patent Office
Prior art keywords
pressure
steam
medium
cooling
turbine
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Withdrawn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
EP16734336.7A
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
Publication of EP3307988A1 publication Critical patent/EP3307988A1/fr
Withdrawn legal-status Critical Current

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
    • 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

  • Rotor cooling for a steam turbine comprising a high ⁇ pressure turbine section comprising a plurality of rotor blades to ⁇ comprehensive rotatably mounted high pressure rotor having a thrust balance piston and which is arranged around the high pressure rotor high-pressure inner casing, wherein between the thrust balance piston and the high-pressure inner housing adedampfhoffm ge ⁇ forms and a medium-pressure turbine section, wherein the ⁇ tel horr horr part turbine comprises a medium-pressure rotor, wherein the medium-pressure rotor has an inflow, wherein a cooling line protrudes into the inflow, the technical fluid connected to the high pressure turbine part.
  • 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 by gas and / or air as the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
  • a steam turbine usually comprises a rotor-mounted rotatably mounted rotor which is arranged within a housing or housing jacket.
  • the rotor When flowing through the interior of the Strömungska ⁇ nals formed by the housing shell with heated and pressurized steam, the rotor is rotated by the blades through the steam in rotation.
  • the blades of the rotor are also referred to as moving blades.
  • the inner casing usually stationary vanes are suspended beyond which engage along an axial extension of the body in the interstices of the Ro ⁇ torschaufeln.
  • a vane is usually on held a first position along an inner side of the Dampfturbi ⁇ nen 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.
  • a row of vanes at said first location along the axial extent is also referred to as a vane grille or prong.
  • a number of rows of guide blades 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 egg ⁇ ner Leitschaufelsch and a blade row is also referred to as a blade stage.
  • the housing jacket of such a steam turbine may be formed from egg ⁇ ner number of housing segments.
  • the housing jacket 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 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 can be an inner casing and / or a guide vane carrier.
  • it may also be provided a turbine housing, which has no inner housing or no guide vane.
  • 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.
  • 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 operating limits of a rotor are reached by the areas subject to high thermal stress, such as the inflow area. With an increase in temperature of the resistance characteristic value of the materials of the rotors decreases überproportio ⁇ nal.
  • maximum permissible shaft diameters based on the load inside the shaft or maximum permissible centrifugal forces in the near-edge region of rotors which can lead to restrictions in particular for 60 Hz applications.
  • the problem is, however, that every cooling has a negative effect on the
  • Partial turbine efficiency has.
  • the use of cooling steam the pressure level is only slightly above that of the medium-pressure inflow, thus, while minimizing the required amount of cooling steam a known and effective technically expedient way. Since such a steam bypasst by only the reheat and the medium-pressure valves, but not active turbine stages , the influence of efficiency remains comparatively low. Particularly with comparatively ⁇ as large double-flow executed intermediate-pressure turbines is often the rotor axis, with respect to the integrity gan ⁇ -saving position, since there the combination of high Fliehkräf ⁇ th and high temperatures too high or creep strains
  • Inlet region of the medium-pressure turbine section is confronted with a relatively large temperature difference.
  • a temperature of a cooling steam whose temperature is higher than that of the high-pressure exhaust steam for cooling would suffi ⁇ chen.
  • the object of the invention is therefore to specify a steam turbine, which can be cooled better.
  • An essential feature of the proposed invention is to remove the cooling steam for the medium-pressure turbine section from the high-pressure turbine section, wherein the cooling steam is removed from thededampf Hurm, 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.
  • 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.
  • a further advantageous effect that the exergy losses arising un ⁇ ter Kunststoffaji temperature in the vapor mixture of two mass flows, to be lower. Furthermore adjusts to a smaller operating clearance to the log ⁇ obligations. Thus, both effects reduce the efficiency degree disadvantage of the medium-pressure shaft cooling.
  • For power plants with cascading Umleitsystem is another advantage of the use of the piston leakage steam for cooling, that the
  • the high-pressure part turbine has a live steam feed duct, wherein the high-pressure inner housing holds a plurality of vanes environmentally which are arranged such that along a Strö ⁇ flow direction, a flow channel with a plurality of blade stages each have a row of rotor blades and a row Guide vane, is formed, wherein the high-pressure inner housing ei ne compound, which is designed 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, wherein the high-pressure inner housing a cross -Rück Installationskanal which is selected as a communicating tube between the cooling steam space and egg NEM arranged according to a blade stage inflow space in the flow channel.
  • the high-pressure inner housing holds a plurality of vanes environmentally which are arranged such that along a Strö ⁇ flow direction, a flow channel with a plurality of blade stages each have a row of rotor blades and a row Guide vane, is
  • Show it: 1 shows a schematic representation of a steam turbine umfas ⁇ transmitting a high-pressure and intermediate-pressure turbine
  • FIG. 3 shows a schematic representation of a part of the high pressure turbine section ⁇ . Components with the same functionality receive the same reference characters.
  • FIG. 1 shows a high-pressure turbine part 1.
  • the high-pressure turbine part 1 comprises a plurality of rotor blades 2 (for reasons of clarity, FIG. 1 shows only one
  • the high pressure rotor 3 is rotatably mounted 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 9 is formed.
  • the high-pressure inner housing 8 is arranged around the high-pressure rotor 3 ⁇ .
  • the high-pressure turbine section 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 not shown in detail in FIG 1 Darge ⁇ .
  • the steam flows out of a discharge area 10 from the high-pressure turbine section 1.
  • the 1 shows further a ⁇ With telbert turbine section 11, an intermediate pressure rotor 12 and a housing disposed around the intermediate-pressure rotor 12 intermediate- Inner housing 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.
  • a rotor blade by the numeral 15 is only verse ⁇ hen.
  • the medium-pressure inner housing 13 meh ⁇ rere around the rotation axis 4 evenly distributed Leitschau ⁇ blades 16 on.
  • 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 one
  • Guide ring 19 having a first diagonal stage 20 which deflects the steam to a first flood 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.
  • the thrust balance piston 5 has an axis of rotation 26 in the direction of the high-pressure outer housing 7 back towards ⁇ side 27. Between the back 27 and the high pressure Outer housing 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 flow-technical connection of the further cooling steam space 28 with the cooling line (not shown in FIG. 3).
  • the high-pressure outer housing 7 and the high-pressure inner housing 8 are designed such that the high-pressure turbine part 1 egg ⁇ nen fresh steam supply duct 29 has.
  • the high-pressure inner housing 8 comprises a plurality of high-pressure guide vanes 30.
  • the high-pressure guide vanes 30 are arranged in such a way that along a flow direction 31 a flow channel 32 having a plurality of blade stages, each having a row of rotor blades and a row of stator vanes, is formed.
  • the high-pressure inner housing 8 has a connection 33, 34, 35, which is designed as a communicating tube between the Strömungska ⁇ nal 32 for a blade stage and a Schubaus stressesskol ⁇ ben-antechamber 36 of the high-pressure rotor 3 and the high-pressure inner housing 8.
  • the high-pressure inner casing 8 has a cross return passage 37, 9 and, arranged downstream of a blade stage inflow space 38 is formed in the flow channel 32 as a communicating pipe Zvi ⁇ rule theharidedampf syndromem.
  • 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. Between the high-pressure inner housing 8 and the high-pressure outer housing 7, a seal 52 is arranged, which separates the wei ⁇ directharidampfhoffm 28 of the compound 34.

Landscapes

  • 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)

Abstract

L'invention concerne une turbine à vapeur et un procédé pour faire fonctionner cette turbine. La turbine à vapeur comprend une partie haute pression (1) et une partie moyenne pression (11) à double flux séparée, une vapeur de refroidissement sortant de la partie haute pression (1) de la turbine pour pénétrer dans la partie moyenne pression (11) de la tubrine. La vapeur de refroidissement est prélevée d'une chambre à vapeur de refroidissement (9) qui se trouve entre un piston d'équilibrage de poussée (5) et un boîtier intérieur haute pression (8), et introduite dans une conduite de refroidissement (24) dans une rainutre de décharge de rotor (25) qui se trouve dans une zone d'entrée de flux moyenne pression (17) de la partie moyenne pression de la turbine.
EP16734336.7A 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur Withdrawn EP3307988A1 (fr)

Applications Claiming Priority (2)

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
PCT/EP2016/065295 WO2017029008A1 (fr) 2015-08-14 2016-06-30 Refroidissement de rotor pour turbine à vapeur

Publications (1)

Publication Number Publication Date
EP3307988A1 true EP3307988A1 (fr) 2018-04-18

Family

ID=53835987

Family Applications (2)

Application Number Title Priority Date Filing Date
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 Before (1)

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

Country Status (4)

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

Families Citing this family (6)

* 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
CN109162772B (zh) 2018-11-06 2024-03-19 上海电气电站设备有限公司 一种汽轮机及其内冷却方法
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

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS59153901A (ja) * 1983-02-21 1984-09-01 Fuji Electric Co Ltd 蒸気タ−ビンロ−タの冷却装置
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
EP0991850B1 (fr) * 1997-06-27 2002-02-13 Siemens Aktiengesellschaft Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine
EP1788191B1 (fr) * 2005-11-18 2014-04-02 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour le refroidissement d'une turbine à vapeur
US7874795B2 (en) * 2006-09-11 2011-01-25 General Electric Company Turbine nozzle assemblies
EP2554789A1 (fr) * 2011-08-04 2013-02-06 Siemens Aktiengesellschaft Turbine à vapeur comprenant un piston de compensation

Also Published As

Publication number Publication date
WO2017029008A1 (fr) 2017-02-23
CN107923246B (zh) 2020-04-21
JP2018527505A (ja) 2018-09-20
EP3130748A1 (fr) 2017-02-15
CN107923246A (zh) 2018-04-17

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