US20090136337A1 - Method and Apparatus for Improved Reduced Load Operation of Steam Turbines - Google Patents

Method and Apparatus for Improved Reduced Load Operation of Steam Turbines Download PDF

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Publication number
US20090136337A1
US20090136337A1 US11/944,991 US94499107A US2009136337A1 US 20090136337 A1 US20090136337 A1 US 20090136337A1 US 94499107 A US94499107 A US 94499107A US 2009136337 A1 US2009136337 A1 US 2009136337A1
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United States
Prior art keywords
flow
low pressure
steam
double
control system
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
US11/944,991
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English (en)
Inventor
Michael J. Boss
Kamlesh Mundra
Douglas Hofer
John Powers
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General Electric Co
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General Electric Co
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 General Electric Co filed Critical General Electric Co
Priority to US11/944,991 priority Critical patent/US20090136337A1/en
Assigned to GENERAL ELECTRIC COMPANY reassignment GENERAL ELECTRIC COMPANY ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: BOSS, MICHAEL J., MUNDRA, KAMLESH, POWERS, JOHN, HOFER, DOUGLAS
Priority to JP2008297624A priority patent/JP2009127627A/ja
Priority to DE102008037579A priority patent/DE102008037579A1/de
Priority to FR0858007A priority patent/FR2924157A1/fr
Priority to RU2008146607/06A priority patent/RU2008146607A/ru
Publication of US20090136337A1 publication Critical patent/US20090136337A1/en
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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K13/00—General layout or general methods of operation of complete plants
    • F01K13/02—Controlling, e.g. stopping or starting
    • 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
    • F01K7/165—Controlling means specially adapted therefor

Definitions

  • the present application relates generally to steam turbines and more particularly to the improved performance of steam turbines at reduced-load, part-load, or off-design operating conditions.
  • Steam turbines are mechanical devices that convert the thermal energy of pressurized steam into rotational mechanical work.
  • large steam turbines generally include several sections, such as a high pressure section, an intermediate pressure section, and a low pressure section. Within each section, multiple stages may be used in the expansion of the steam.
  • the sections of large steam turbines possess various design characteristics so as to permit the extraction of the largest possible amount of energy from the expansion of steam through the turbine sections. It is common practice to introduce initially high pressure steam into a high pressure section of the steam turbine. Steam exiting the high pressure section of the turbine is then directed to a reheater before being introduced into a low pressure section of the turbine, where it continues its expansion. In many turbines the steam passes through an intermediate pressure section before being introduced into a low pressure section.
  • the annulus area of each stage must increase in order to convert efficiently the thermal energy of the steam to rotational mechanical work. This is accomplished by lengthening the turbine blades or buckets from stage to stage, by increasing the diameter of the rotor upon which the blades are mounted, by adding two or more flow paths in parallel, or combinations thereof.
  • the choice of the single-flow or the double-flow low pressure section design may depend on the volume of steam designed to flow though the low pressure section at normal, full-load conditions.
  • the best performance of low pressure steam path design may be achieved when steam velocity exiting the last stage buckets of the low pressure section is about 600 feet per second. Lower or higher velocities may degrade the performance of the steam turbine.
  • the annulus area of the last stage buckets may be increased or reduced. If steam flow volumes are large enough, however, increasing the length of the turbine blades or the diameter of the rotor upon which the blades are mounted may not be feasible or desirable. Instead, a double-flow section may be used in order to increase the exit annulus area of the low pressure section.
  • double-flow low pressure section may be used in parallel.
  • approximately equal portions of the steam flow may be introduced to each of the double-flow low pressure sections.
  • Steam turbines are designed to operate efficiently under normal, full-load operating conditions. In some circumstances such as a reduced demand for electricity, however, the steam flow to the turbine is reduced for economic reasons. When the flow is reduced below design conditions, the performance of the low pressure section of the steam turbine may drop significantly due to large separation at the hub of the last stage buckets. Exhaust hood performance also may decline. The low steam path efficiency and poor exhaust hood performance may cause poor turbine efficiency at reduced-load, low-load, or off-design operating conditions.
  • the present application provides a method of operating a steam turbine at reduced load, including providing a number of low pressure sections, providing a flow control system operable to limit the flow of steam to at least one of the number of low pressure sections, and operating the flow control system to limit the flow of steam to the at least one of the number of low pressure sections when the load is below a predetermined value.
  • Another embodiment of the present application provides a method of operating a steam turbine at reduced load, including providing one double-flow low pressure section having two steam flow paths, providing a flow control system operable to limit the flow of steam to at least one of the two flow paths, and operating the flow control system to limit the flow of steam to the at least one of the two flow paths
  • a further embodiment of the present application provides a steam turbine.
  • the steam turbine may include a number of low pressure sections and a flow control system operable to limit the flow of steam to at least one of the number of low pressure sections.
  • FIG. 1 is a schematic view of a steam turbine having two double-flow low pressure sections in accordance with an embodiment of the present application as described herein.
  • FIG. 2 is a schematic view of a steam turbine having three double-flow low pressure sections in accordance with an embodiment of the present application as described herein.
  • FIG. 3 is a schematic view of a steam turbine having one double-flow low pressure section in accordance with an embodiment of the present application as described herein.
  • FIG. 1 shows a schematic view of a steam turbine 10 of an embodiment of the present application.
  • Pressurized steam is supplied to the turbine 10 from a steam source 11 , such as, for example, a boiler.
  • Energy sources for generating steam may include, but are not limited to, fossil fuel, nuclear, geothermal, solar thermal electric, and biomass energy sources.
  • the steam initially is introduced to a high pressure section 12 of the turbine 10 . After the steam flow exits the high pressure section 12 of the turbine 10 , the flow may pass to a reheater 13 where additional thermal energy may be added. In other embodiments the steam may be returned to a boiler where additional superheat may be added.
  • the steam may be introduced to a moisture separator to remove any moisture forming in the steam in the high pressure section of the turbine.
  • the steam may pass to an intermediate pressure section after the steam flow exists the reheater 13 .
  • a crossover pipe 14 may direct the steam flow to a first double-flow low pressure section 15 and a second double-flow low pressure section 16 .
  • a flow control system 17 may be provided, which is operable to limit the flow of steam to both of the two low pressure sections.
  • the flow control system 17 may include a first valve 18 , located at the inlet of the first double-flow low pressure section 15 , and a second valve 19 , located at the inlet of the second double-flow low pressure section 16 .
  • the flow control system 17 may include any device that can regulate, halt, or control the flow of steam to at least one of the number of low pressure sections by closing or partially obstructing the flow path of the steam to at least one of the low pressure sections.
  • the flow control system 17 may include a butterfly valve, poppet valve, or a hinged lid or other movable part that closes or modifies the steam flow path.
  • the flow control system 17 may include only one valve disposed at the inlet of one of the low pressure sections.
  • the flow control system 17 may include a valve disposed between the inlet of the first double-flow low pressure section 15 and the inlet of the second double-flow low pressure section 16 .
  • the flow control system 17 is operable to limit the flow of steam to at least one of the number of low pressure sections.
  • the flow control system 17 may limit the flow of steam to at least one of the two double-flow low pressure sections.
  • the predetermined load at which the flow begins to be limited is a function of the particular design and operating conditions. In general, this load is selected such that the overall output of the low pressure section is maximized.
  • the second valve 19 may be closed significantly to limit the flow to the second double-flow low pressure section 16 .
  • sufficient steam flow may be allowed to pass through the second valve 19 in order to prevent windage heating in the second double-flow low pressure section 16 .
  • Limiting steam flow to the second double-flow low pressure section 16 may cause a corresponding increase in flow to the first double-flow low pressure section 15 , thereby increasing the efficiency of the first double-flow low pressure section 15 .
  • the increase in efficiency of the first double-flow low pressure section 15 increases the overall efficiency of the low pressure section of the steam turbine 10 at reduced-load, low-load, or off-design conditions.
  • the flow control system 17 may be operated to direct a flow of steam to at least one of the low pressure sections sufficient to produce a steam exit velocity from the low pressure section of between about 500 feet per second and about 700 feet per second.
  • the specific flow rate range may vary with the size and configuration of the turbine 10 as a whole.
  • the relative flow of steam through the two double-flow low pressure sections may be adjusted using the flow control system 17 in order to maximize overall turbine efficiency.
  • each flow end of the first double-flow low pressure section 15 and the second double-flow low pressure section 16 it may discharged to a condenser 20 or otherwise used.
  • FIG. 2 shows a schematic view of a steam turbine 27 in accordance with an embodiment of the present application.
  • the steam turbine of FIG. 2 may have three double-flow low pressure sections. Pressurized steam is supplied to the turbine 27 from the steam source 11 . The steam initially is introduced to the high pressure section 12 of the turbine 27 . After the steam flow exits the high pressure section 12 of the turbine 27 , it may pass to the reheater 13 where additional thermal energy is added. After the steam flow exits the reheater 13 , the crossover pipe 14 directs the steam flow to the first double-flow low pressure section 15 , the second double-flow low pressure section 16 , and a third double-flow low pressure section 21 .
  • the flow control system 17 may be provided to limit the flow of steam to each of the three low pressure sections. In another embodiment, the flow control system 17 may only be operable to limit the flow of steam to one or two of the number of low pressure sections.
  • the flow control system 17 may include the first valve 18 , located at the inlet of the first double-flow low pressure section 15 , the second valve 19 , located at the inlet of the second double-flow low pressure section 16 , and a third valve 22 , located at the inlet of the third double-flow low pressure section 21 .
  • the flow control system 17 limits the flow of steam to at least one of the three double-flow low pressure sections.
  • the third valve 22 may be closed significantly to limit the flow to the third double-flow low pressure section 21 .
  • sufficient steam flow may be allowed to pass through the third valve 22 in order to prevent windage heating in the third double-flow low pressure section 21 .
  • Limiting steam flow to the third double-flow low pressure section 21 may cause a corresponding increase in flow to the first double-flow low pressure section 15 and the second double-flow low pressure section 16 , thereby increasing the efficiency of the first double-flow low pressure section 15 and the second double-flow low pressure section 16 .
  • the increase in efficiency of the first double-flow low pressure section 15 and the second double-flow low pressure section 16 may increase the overall efficiency of the low pressure section of the steam turbine 27 at reduced-load, low-load, or off-design conditions.
  • both the second valve 19 and third valve 22 may be closed significantly to limit the flow to the second double-flow low pressure section 16 and third double-flow low pressure section 21 .
  • sufficient steam flow may be allowed to pass through the second valve 19 and third valve 22 in order to prevent windage heating in the second double-flow low pressure section 16 and third double-flow low pressure section 21 .
  • Limiting steam flow to the second double-flow low pressure section 16 and third double-flow low pressure section 21 may cause a corresponding increase in flow to the first double-flow low pressure section 15 , thereby increasing the efficiency of the first double-flow low pressure section 15 .
  • the increase in efficiency of the first double-flow low pressure section 15 may increase the overall efficiency of the low pressure section of the steam turbine 27 at reduced-load, low-load, or off-design conditions.
  • the flow control system 17 may be operated to direct a flow of steam to at least one of the low pressure sections sufficient to produce a steam exit velocity from the low pressure section of between about 500 feet per second and about 700 feet per second.
  • the specific flow rate range may vary with the size and configuration of the turbine 10 as a whole.
  • the relative flow of steam through the three double-flow low pressure sections may be adjusted using the flow control system 17 in order to maximize overall turbine efficiency. After the steam exits each flow end of the first double-flow low pressure section 15 , the second double-flow low pressure section 16 , and the third double-flow low pressure section 21 , it may be discharged to a condenser 20 or otherwise used.
  • FIG. 3 shows a schematic view of a steam turbine 28 having one double-flow low pressure section in accordance with an embodiment of the present application.
  • Pressurized steam may be supplied to the turbine 28 from the steam source 11 .
  • the steam initially is introduced to the high pressure section 12 of the turbine 28 .
  • the crossover pipe 14 may direct the steam flow to the first double-flow low pressure section 15 .
  • the double-flow low pressure section 15 may have a first steam flow path 23 and a second steam flow path 24 .
  • the flow control system 17 may be provided to limit the flow of steam to at least one of the two flow paths.
  • the flow control system 17 may include a first valve 25 , located at the inlet of the first flow path 23 , and a second valve 26 , located at the inlet of the second flow path 24 .
  • the flow control system 17 limits the flow of steam to at least one of the two flow paths.
  • the second valve 26 may be closed significantly to limit the flow to the second flow path 24 .
  • sufficient steam flow may be allowed to pass through the second valve 26 in order to prevent windage heating in the second flow path 24 .
  • Limiting steam flow to the second flow path 24 may cause a corresponding increase in flow to the first flow path 23 , thereby increasing the overall efficiency of the first double-flow low pressure section 15 at reduced-load, low-load, or off-design conditions.
  • the flow control system 17 may be operated to direct a flow of steam to at least one flow path sufficient to produce a steam exit velocity from the flow path of between about 500 feet per second and about 700 feet per second.
  • the specific flow rate range may vary with the size and configuration of the turbine 28 as a whole.
  • the relative flow of steam through the two flow paths may be adjusted using the flow control system 17 in order to maximize overall turbine efficiency. After the steam exits each flow end of the first double-flow low pressure section 15 , it may be discharged to a condenser 20 or otherwise used.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
US11/944,991 2007-11-26 2007-11-26 Method and Apparatus for Improved Reduced Load Operation of Steam Turbines Abandoned US20090136337A1 (en)

Priority Applications (5)

Application Number Priority Date Filing Date Title
US11/944,991 US20090136337A1 (en) 2007-11-26 2007-11-26 Method and Apparatus for Improved Reduced Load Operation of Steam Turbines
JP2008297624A JP2009127627A (ja) 2007-11-26 2008-11-21 蒸気タービンの縮小負荷運転の改善のための方法及び装置
DE102008037579A DE102008037579A1 (de) 2007-11-26 2008-11-24 Verfahren und Vorrichtung für einen verbesserten Betrieb von Dampfturbinen bei verringerter Last
FR0858007A FR2924157A1 (fr) 2007-11-26 2008-11-25 Procede et dispositif pour le fonctionnement ameliore a charge reduite de turbines a vapeur
RU2008146607/06A RU2008146607A (ru) 2007-11-26 2008-11-25 Способ и устройство для усовершенствованной работы паровых турбин при пониженной нагрузке

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
US11/944,991 US20090136337A1 (en) 2007-11-26 2007-11-26 Method and Apparatus for Improved Reduced Load Operation of Steam Turbines

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US20090136337A1 true US20090136337A1 (en) 2009-05-28

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US11/944,991 Abandoned US20090136337A1 (en) 2007-11-26 2007-11-26 Method and Apparatus for Improved Reduced Load Operation of Steam Turbines

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US (1) US20090136337A1 (ru)
JP (1) JP2009127627A (ru)
DE (1) DE102008037579A1 (ru)
FR (1) FR2924157A1 (ru)
RU (1) RU2008146607A (ru)

Cited By (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100146970A1 (en) * 2008-03-07 2010-06-17 Clean Energy Systems, Inc. Method and system for enhancing power output of renewable thermal cycle power plants
US20100326084A1 (en) * 2009-03-04 2010-12-30 Anderson Roger E Methods of oxy-combustion power generation using low heating value fuel
US20110247333A1 (en) * 2010-04-13 2011-10-13 General Electric Company Double flow low-pressure steam turbine
US20140216035A1 (en) * 2013-02-05 2014-08-07 Alstom Technology Ltd Steam power plant with a second low-pressure turbine and an additional condensing system
US20140283518A1 (en) * 2011-04-15 2014-09-25 Doosan Babcock Limited Turbine system
CN104204425A (zh) * 2012-04-04 2014-12-10 西门子公司 发电厂和用于运行发电厂的方法
CN104471199A (zh) * 2012-07-12 2015-03-25 西门子公司 用于支持电网频率的方法

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JP5792663B2 (ja) * 2012-03-07 2015-10-14 ヤンマー株式会社 船舶の廃熱回収システム
JP6778475B2 (ja) * 2015-07-01 2020-11-04 アネスト岩田株式会社 発電システムおよび発電方法
US11644015B2 (en) 2021-04-02 2023-05-09 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
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US11493029B2 (en) 2021-04-02 2022-11-08 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11359576B1 (en) 2021-04-02 2022-06-14 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11592009B2 (en) 2021-04-02 2023-02-28 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power at a drilling rig
US11480074B1 (en) 2021-04-02 2022-10-25 Ice Thermal Harvesting, Llc Systems and methods utilizing gas temperature as a power source
US11421663B1 (en) 2021-04-02 2022-08-23 Ice Thermal Harvesting, Llc Systems and methods for generation of electrical power in an organic Rankine cycle operation
US11255315B1 (en) 2021-04-02 2022-02-22 Ice Thermal Harvesting, Llc Controller for controlling generation of geothermal power in an organic Rankine cycle operation during hydrocarbon production
US11486370B2 (en) 2021-04-02 2022-11-01 Ice Thermal Harvesting, Llc Modular mobile heat generation unit for generation of geothermal power in organic Rankine cycle operations

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Cited By (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20100146970A1 (en) * 2008-03-07 2010-06-17 Clean Energy Systems, Inc. Method and system for enhancing power output of renewable thermal cycle power plants
US8631658B2 (en) * 2008-03-07 2014-01-21 Clean Energy Systems, Inc. Method and system for enhancing power output of renewable thermal cycle power plants
US20100326084A1 (en) * 2009-03-04 2010-12-30 Anderson Roger E Methods of oxy-combustion power generation using low heating value fuel
US20110247333A1 (en) * 2010-04-13 2011-10-13 General Electric Company Double flow low-pressure steam turbine
US9631520B2 (en) * 2011-04-15 2017-04-25 Doosan Babcock Limited Turbine system
US20140283518A1 (en) * 2011-04-15 2014-09-25 Doosan Babcock Limited Turbine system
CN104204425A (zh) * 2012-04-04 2014-12-10 西门子公司 发电厂和用于运行发电厂的方法
JP2015515573A (ja) * 2012-04-04 2015-05-28 シーメンス アクティエンゲゼルシャフト 発電所および発電所設備を運転するための方法
US9574462B2 (en) 2012-04-04 2017-02-21 Siemens Aktiengesellschaft Method for operating a power plant installation
CN104471199A (zh) * 2012-07-12 2015-03-25 西门子公司 用于支持电网频率的方法
US20150135721A1 (en) * 2012-07-12 2015-05-21 Siemens Aktiengesellschaft Method for supporting a mains frequency
AU2014200595B2 (en) * 2013-02-05 2015-10-29 General Electric Technology Gmbh Steam power plant with a second low-pressure turbine and an additional condensing system
US20140216035A1 (en) * 2013-02-05 2014-08-07 Alstom Technology Ltd Steam power plant with a second low-pressure turbine and an additional condensing system
US9752461B2 (en) * 2013-02-05 2017-09-05 General Electric Technology Gmbh Steam power plant with a second low-pressure turbine and an additional condensing system

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FR2924157A1 (fr) 2009-05-29
RU2008146607A (ru) 2010-05-27
DE102008037579A1 (de) 2009-05-28
JP2009127627A (ja) 2009-06-11

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