US20140369815A1 - Control of low volumetric flow instabilites in steam turbines - Google Patents

Control of low volumetric flow instabilites in steam turbines Download PDF

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Publication number
US20140369815A1
US20140369815A1 US14/305,316 US201414305316A US2014369815A1 US 20140369815 A1 US20140369815 A1 US 20140369815A1 US 201414305316 A US201414305316 A US 201414305316A US 2014369815 A1 US2014369815 A1 US 2014369815A1
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United States
Prior art keywords
passages
rotor blades
flow
configuration according
vane carrier
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.)
Abandoned
Application number
US14/305,316
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English (en)
Inventor
Brian Robert Haller
Timothy Stephen Rice
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General Electric Technology GmbH
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Alstom Technology AG
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Publication date
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Assigned to ALSTOM TECHNOLOGY LTD reassignment ALSTOM TECHNOLOGY LTD ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: RICE, TIMOTHY STEPHEN, HALLER, BRIAN ROBERT
Publication of US20140369815A1 publication Critical patent/US20140369815A1/en
Assigned to GENERAL ELECTRIC TECHNOLOGY GMBH reassignment GENERAL ELECTRIC TECHNOLOGY GMBH CHANGE OF NAME (SEE DOCUMENT FOR DETAILS). Assignors: ALSTOM TECHNOLOGY LTD
Abandoned legal-status Critical Current

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    • 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
    • F01D5/10—Anti- vibration means
    • 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
    • F01D11/08—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator
    • F01D11/10—Preventing or minimising internal leakage of working-fluid, e.g. between stages for sealing space between rotor blade tips and stator using sealing fluid, e.g. steam
    • 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
    • F01D19/00—Starting of machines or engines; Regulating, controlling, or safety means in connection therewith
    • 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
    • F01D21/00—Shutting-down of machines or engines, e.g. in emergency; Regulating, controlling, or safety means not otherwise provided for
    • F01D21/003—Arrangements for testing or measuring
    • 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
    • F01D25/04—Antivibration arrangements
    • 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
    • F01D25/04—Antivibration arrangements
    • F01D25/06—Antivibration arrangements for preventing blade vibration
    • 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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • 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
    • F01D5/12—Blades
    • F01D5/14—Form or construction
    • F01D5/16—Form or construction for counteracting blade vibration
    • 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
    • F01D9/00—Stators
    • F01D9/02—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles
    • F01D9/04—Nozzles; Nozzle boxes; Stator blades; Guide conduits, e.g. individual nozzles forming ring or sector

Definitions

  • the present invention relates to a configuration of the last stage in a steam turbine for controlling rotating flow instabilities in the last stage rotor blades when the steam turbine operates at low volumetric flow conditions, particularly during starting and low load conditions.
  • Stalling is a known phenomenon based on the sudden decrease of the load exerted onto a profile subjected to a flow: in steam turbines, the stalling phenomenon induces rotating flow instabilities in the rotor blades, particularly in the last stage rotor blades.
  • the flow structure In steam turbines, during starting and low load conditions (up to around 10% of the design mass flow), the flow structure is very disorderly, particularly in the low pressure stage of the steam turbine: this flow is centrifuged radially outwards in the rotor blades, the flow being centrifuged radially inwards in the stator blades.
  • this flow is centrifuged radially outwards in the rotor blades, the flow being centrifuged radially inwards in the stator blades.
  • At low load conditions there is high flow incidence onto the last stage rotor blades, which can cause flow separation from the rotor blades surface and flow instabilities, these instabilities are commonly found to rotate at about one half of the blade rotational speed.
  • the flow field also contains large toroidal vortex structures are set up. These rotating instabilities can couple with the natural frequency of the rotor blades and produce undesirable vibration effects.
  • the invention is oriented towards solving these problems.
  • the present invention relates to a configuration for controlling flow instabilities in steam turbines when they operate at low volumetric conditions, particularly during starting and low load conditions.
  • the configuration of the invention comprises a plurality of passages located in the last stage vane carrier of the low pressure stage of the steam turbine, these passages being located at specific positions at the vane carrier: through these passages, a fluid is blown onto the rotating blades to counteract rotating flow instabilities in them.
  • the number of passages and their specific positions are defined in such a way that the fluid blown is directed towards the rotor blades and preventing the excitation.
  • the passages are shaped circumferentially in order to increase the circumferential coverage of each passage.
  • the fluid blown through the passages into the rotor blades is such that the swirl injection angle incident on the rotor blades forms an angle from zero to ⁇ 90 degrees.
  • the positive angle being taken in the direction of the turbine rotor rotation, with zero degrees being axial, wherein in the axial/radial plane the jet is directed downwards from the outer flow boundary.
  • FIG. 1 shows the characteristics of low flow in a steam turbine. Radial movements of the through flow can be seen together with the recirculation zones created;
  • FIG. 2 shows an embodiment of the invention where the passages are shaped in the circumferential direction to increase the flow coverage for each passage provided;
  • FIG. 3 shows schematically the configuration of the invention for controlling flow instabilities in the last stage rotor blades of a steam turbine when the turbine operates at low volumetric conditions
  • FIGS. 4 a,b,c shows the influence of injection swirl angle on Volumetric flow versus fractional Speed and Vibration amplitude
  • FIG. 5 shows the influence of blowing mass flow on dynamic blade stress.
  • the present invention relates to a configuration 10 for controlling flow instabilities in the last stage rotor blades 2 of a steam turbine when the turbine operates at low volumetric conditions, particularly during starting and low load conditions.
  • the configuration 10 is such that a plurality of passages 20 are located in the vane carrier 1 of the last stage of the steam turbine, these passages 20 being located at specific positions at the circumference of the vane carrier 1 . Through these passages 20 , a fluid is blown onto the rotor blades 2 .
  • the number of passages 20 and their specific positions are defined in such a way that the fluid blown through the passages 20 is directed towards the rotor blades 2 avoiding rotating stability problems in these last stage rotor blades 2 that produce undesired vibration effects on them.
  • FIG. 1 shows the flow pattern in the last stage low pressure vane carrier 1 during starting and low load conditions (up to around 10% of the design mass flow), showing that the flow structure is very disorderly.
  • the through flow in the vane carrier 1 adopts a wavy shape, as shown in FIG. 1 , existing large toroidal vortex structures 30 : the last stage low pressure vane carrier 1 actually acts as a radial pump and there is net energy input to the stage.
  • a solution is to use water sprays injected in the exhaust diffuser to cool the exhaust casing vane carrier walls and last stage blades, but this solution has not been found to be reliable.
  • the purpose of the configuration 10 of the invention is to design the passages 20 to eliminate the rotating flow instabilities in the last stage rotor blades 2 during starting and low load conditions of the steam turbine.
  • the positions of the passages 20 upstream of the last stage rotor blade 2 is such that the injection flow is directed through the last stage vane carrier 1 to approximately 80% last stage blade height, as measured from the blade platform to the tip, so as to blow into the torodial vortex 30 typically formed upstream of the rotor blade 2 tip region.
  • FIGS. 4 a , 4 b and 4 c shows a series of tests that demonstrate the surprising effect that a negative injection angle results in a more stable and steady separated flow, decoupled from resonance can be seen.
  • the tests were carried out in a one third scale model low pressure steam turbine over a range of mass flow rates and condenser pressure. During the tests measurement were made of last stage blade stress using a strain gauge located on the surface of the last stage blade. Results of these measurements are shown as lines representation vibrational amplitude in FIGS. 4 a , 4 b and 4 c.
  • An additional dynamic pressure sensor acting as a microphone, was additional located in the flow to detect the formation of the rotating events that can give rise to blade vibration. From the pressure signal it was possible to determine frequency, which is transformable into fractional speed, and represent this as spheres in FIGS. 4 a , 4 b and 4 c . The amplitude from the pressure sensor was then used in FIGS. 4 a , 4 b and 4 c to define the size of the grey spheres on each of the graphs.
  • the fluid injected from the passages 20 which preferably is steam, is such that the injection angle incident on the rotor blades 2 forms an angle from zero to ⁇ 90 degrees, the negative angle being taken in the direction counter to the turbine rotor rotation.
  • the preferred injection angle range is ⁇ 45 to ⁇ 75 degrees, the most preferred injection angle being ⁇ 60 degrees.
  • the flow injected from the passages 20 is up to 10% of the mainstream flow.
  • the number of passages 20 relative to the number of rotor blades 2 is set to provide sufficient stabilization of the rotating events. In the case of the test results given, 12 passages were used. Other embodiments of this invention may use a different number of passages to obtain sufficient stabilization.
  • the passages are equally spaced around the circumference. In an alternative embodiment the passages are unevenly spaced around the circumference for enhanced performance or for practical considerations.
  • the following parameters influence the performance of the configuration 10 of the invention maintaining the trajectory length of the fluid blown from the passages 20 as small as possible; maintaining the velocity of the fluid injected as high as possible; and maximizing the circumferential extent of the passages 20 in the vane carrier 1 .
  • the passages 20 are circumferentially shaped to increase the circumferential coverage in the vane carrier 1 as shown in FIG. 2 .

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Control Of Turbines (AREA)
US14/305,316 2013-06-17 2014-06-16 Control of low volumetric flow instabilites in steam turbines Abandoned US20140369815A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
EP13172223 2013-06-17
EP13172223.3 2013-06-17

Publications (1)

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US20140369815A1 true US20140369815A1 (en) 2014-12-18

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US14/305,316 Abandoned US20140369815A1 (en) 2013-06-17 2014-06-16 Control of low volumetric flow instabilites in steam turbines

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US (1) US20140369815A1 (de)
EP (1) EP2816199B1 (de)
JP (1) JP6239447B2 (de)
CN (1) CN104234757B (de)
IN (1) IN2014DE01617A (de)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10662802B2 (en) 2018-01-02 2020-05-26 General Electric Company Controlled flow guides for turbines
CN112699505A (zh) * 2020-12-28 2021-04-23 哈尔滨汽轮机厂有限责任公司 一种用于核电机组低压缸长叶片的动应力有限元计算方法
CN113153453A (zh) * 2021-03-02 2021-07-23 哈尔滨工业大学 汽轮机末级叶片容积流量估计方法、颤振预警方法及系统和装置
US11193942B2 (en) * 2014-12-09 2021-12-07 Anna Villarreal Methods and devices for female health monitoring
US11199095B2 (en) * 2019-10-31 2021-12-14 General Electric Company Controlled flow turbine blades

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JP6916755B2 (ja) * 2018-03-09 2021-08-11 三菱重工業株式会社 回転機械
WO2019236062A1 (en) 2018-06-05 2019-12-12 Siemens Energy, Inc. Arrangement of a last stage with flow blockers and corresponding method for suppressing rotating flow instability cells

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US7744343B2 (en) * 2006-09-21 2010-06-29 General Electric Company Method and apparatus for controlling the operation of a steam turbine
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11193942B2 (en) * 2014-12-09 2021-12-07 Anna Villarreal Methods and devices for female health monitoring
US10662802B2 (en) 2018-01-02 2020-05-26 General Electric Company Controlled flow guides for turbines
US11199095B2 (en) * 2019-10-31 2021-12-14 General Electric Company Controlled flow turbine blades
CN112699505A (zh) * 2020-12-28 2021-04-23 哈尔滨汽轮机厂有限责任公司 一种用于核电机组低压缸长叶片的动应力有限元计算方法
CN113153453A (zh) * 2021-03-02 2021-07-23 哈尔滨工业大学 汽轮机末级叶片容积流量估计方法、颤振预警方法及系统和装置

Also Published As

Publication number Publication date
EP2816199B1 (de) 2021-09-01
IN2014DE01617A (de) 2015-06-19
CN104234757A (zh) 2014-12-24
CN104234757B (zh) 2016-10-05
EP2816199A3 (de) 2015-03-04
JP6239447B2 (ja) 2017-11-29
JP2015001228A (ja) 2015-01-05
EP2816199A2 (de) 2014-12-24

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