US20150125266A1 - Steam Turbine Equipment - Google Patents

Steam Turbine Equipment Download PDF

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Publication number
US20150125266A1
US20150125266A1 US14/532,424 US201414532424A US2015125266A1 US 20150125266 A1 US20150125266 A1 US 20150125266A1 US 201414532424 A US201414532424 A US 201414532424A US 2015125266 A1 US2015125266 A1 US 2015125266A1
Authority
US
United States
Prior art keywords
steam
turbine
overload
pipe
steam 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.)
Abandoned
Application number
US14/532,424
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English (en)
Inventor
Yusuke Takahashi
Goingwon Lee
Koji Ogata
Nozomu OGASAWARA
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.)
Mitsubishi Power Ltd
Original Assignee
Mitsubishi Hitachi Power Systems Ltd
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 Mitsubishi Hitachi Power Systems Ltd filed Critical Mitsubishi Hitachi Power Systems Ltd
Assigned to MITSUBISHI HITACHI POWER SYSTEMS, LTD. reassignment MITSUBISHI HITACHI POWER SYSTEMS, LTD. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: LEE, GOINGWON, OGASAWARA, NOZOMU, OGATA, KOJI, TAKAHASHI, YUSUKE
Publication of US20150125266A1 publication Critical patent/US20150125266A1/en
Abandoned 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
    • 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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/023—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines the working-fluid being divided into several separate flows ; several separate fluid flows being united in a single flow; the machine or engine having provision for two or more different possible fluid flow paths
    • 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/18—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means
    • F01D1/20—Non-positive-displacement machines or engines, e.g. steam turbines without stationary working-fluid guiding means traversed by the working-fluid substantially axially
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C9/00—Controlling gas-turbine plants; Controlling fuel supply in air- breathing jet-propulsion plants
    • F02C9/16—Control of working fluid flow
    • F02C9/18—Control of working fluid flow by bleeding, bypassing or acting on variable working fluid interconnections between turbines or compressors or their stages
    • 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
    • F05D2260/606—Bypassing the fluid

Definitions

  • the present invention relates to steam turbine equipment.
  • JP-2006-161698-A describes the following technology as an overload operation device for a steam turbine, the device being capable of increasing the output power of the steam turbine while controlling the pressure of main steam.
  • This steam turbine includes a steam turbine high-pressure portion and a steam turbine reheat portion.
  • High pressure steam is introduced into the steam turbine high pressure portion via a main steam control valve and reheat steam is introduced into the steam turbine reheat portion via a reheat steam valve.
  • a pipe is made to branch off from the inlet side of the main steam control valve and thus provides communication, via an overload valve, between the inlet side of the main steam control valve and the inlet side of the steam turbine reheat portion.
  • a thermal power plant having a steam turbine is occasionally required to adjust the power generation output from a rated value according to an expected variation in power demand.
  • a method such as throttle governing, nozzle governing, and sliding pressure operation has heretofore been used as a technique for regulating power generation output of a thermal power plant.
  • Throttle governing is a method in which power generation output is adjusted by controlling the opening of a steam control valve to reduce steam and thereby changing a heat drop and a flow rate of steam.
  • the steam control valve is fully opened only during the operation at the maximum power generation output.
  • the power generation efficiency decreases due to a valve throttle loss.
  • a rated power generation output is lower than the maximum power generation output. Therefore, a valve throttle loss occurs during the operation at the rated power generation output, thereby decreasing the power generation efficiency below that during the operation at the maximum power generation output.
  • Nozzle governing is a method in which power generation output is adjusted by changing the number of steam control valves to change the number of nozzles jet steam with an effective head drop remaining constant and thereby controlling the flow rate of steam.
  • This method requires a control stage to be installed inside a steam turbine, the control stage having a mechanism which delivers air from only part of a group of nozzles to a turbine.
  • the installation of the control stage causes a decline in power generation efficiency.
  • Sliding pressure operation is a method in which a steam turbine is operated at a steam pressure corresponding to a required power generation output.
  • This method neither causes a throttle loss of a steam control valve nor requires a control stage to be installed, thereby improving power generation efficiency.
  • JP-2006-161698-A has a problem that the steam that passes through the overload valve and flows into the steam turbine is unlikely to diffuse in the circumferential direction of the turbine, which makes it hard to suppress a drift at a stage portion.
  • the present invention has been made in view of the above situations and aims to provide steam turbine equipment that can sharply adjust power generation output based on a variation in power demand while improving power generation efficiency during operation at a rated power generation output.
  • the present invention employs a configuration described in the claims, for example.
  • steam turbine equipment that includes: a main steam pipe for leading steam generated in a steam generating source to a steam turbine; a main steam control valve disposed in the main steam pipe; an overload steam pipe that branches from the main steam pipe and bypasses the steam control valve such that the steam generated in the steam generating source is led to a lower-pressure side of the steam turbine than a point where the main steam pipe connects to the steam turbine; an overload valve disposed in the overload steam pipe; and a slit portion through which the steam that has passed through the overload valve passes before flowing into a steam turbine stage portion, wherein the slit portion is configured such that its width in an axial direction of a turbine rotor 15 is smaller than an inside diameter of the overload steam pipe.
  • the present invention provides steam turbine equipment that can sharply adjust power generation output based on a variation in power demand while improving power generation efficiency during the operation at a rated power generation output.
  • FIG. 1 is a schematic diagram illustrating the entire configuration of steam turbine equipment according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view illustrating an example of a configuration of a high pressure turbine according to a first embodiment of the present invention.
  • FIG. 3 illustrates rotating blades and stationary blades located at a stage portion of the high pressure turbine according to the first embodiment of the present invention, as viewed from the outside in a turbine-radial direction.
  • FIG. 4 is a cross-sectional view illustrating an example of a configuration of a high pressure turbine according to a second embodiment of the present invention.
  • FIG. 1 is a schematic diagram illustrating the entire configuration of steam turbine equipment (a thermal power plant) according to an embodiment of the present invention.
  • FIG. 2 is a cross-sectional view illustrating an example of a configuration of a high pressure turbine according to a first embodiment of the present invention.
  • FIG. 3 illustrates rotating blades and stationary blades located at a stage portion of the high pressure turbine according to the first embodiment of the present invention, as viewed from the outside in a radial direction of the turbine.
  • the steam turbine equipment of the present embodiment includes a high pressure turbine 7 , an intermediate pressure turbine 10 , a low pressure turbine 12 , a condenser 14 , and a generator 16 .
  • a boiler 1 is a fossil fuel boiler as one example of a steam generating source.
  • the boiler 1 burns fossil fuel to heat steam condensate fed from the condenser 14 , thereby generating high pressure and temperature steam.
  • a main steam pipe 2 is provided with a main steam stop valve 3 and a main steam control valve 4 .
  • An overload steam pipe 5 is connected to the main steam pipe 2 .
  • the overload steam pipe 5 bypasses the main steam control valve 4 and connects to a lower-pressure side of the steam turbine than a point where the main steam pipe 2 connects to the steam turbine.
  • An overload valve 6 is disposed in the overload steam pipe 5 .
  • the reheat steam reheated in the boiler 1 is led through a hot reheat pipe 9 to the intermediate pressure turbine 10 and drives the intermediate pressure turbine 10 .
  • the steam that has driven the intermediate pressure turbine 10 and decreased in pressure is led through an intermediate pressure exhaust pipe 11 to the low pressure turbine 12 and drives the low pressure turbine 12 .
  • the steam that has driven the low pressure turbine 12 and decreased in pressure is led through a low pressure turbine exhaust pipe 11 to the condenser 14 .
  • the condenser 14 which is provided with a cooling water pipe (not shown), condenses the steam into water by exchanging heat between the steam led into the condenser 14 and cooling water flowing through the cooling water pipe.
  • the water condensed in the condenser 14 is fed to the boiler 1 again.
  • the high pressure turbine 7 , the intermediate pressure turbine 10 , and the low pressure turbine 12 illustrated in FIG. 1 are coaxially coupled to one another by a turbine rotor 15 .
  • the generator 16 is connected to the turbine rotor 15 .
  • the generator 16 is driven by the rotary power of the high pressure turbine 7 , the intermediate pressure turbine 10 and the low pressure turbine 12 .
  • the output power of the high pressure turbine 7 , the intermediate pressure turbine 10 , and the low pressure turbine 12 is taken out as electric power (electric energy).
  • a main feature of the steam turbine equipment according to the present embodiment is to have a slit portion 31 through which the steam having flowed through the overload steam pipe 5 passes before flowing into the steam turbine stage portion.
  • the slit portion 31 is configured to have a width smaller than the inside diameter of the overload steam pipe 5 .
  • the slit portion 31 here in the present invention refers to a narrow gap through which steam passes.
  • a diaphragm outer ring 24 , a diaphragm inner ring 25 , fins 26 , a packing 27 , a casing 28 holding the diaphragm outer ring 24 , a seal ring 30 , a slit portion 31 , etc. are disposed in the vicinity of a steam inlet through which the steam from the overload steam pipe 5 flows into the high pressure turbine 7 .
  • the high pressure turbine 7 includes the turbine rotor 15 and rotating blades 22 mounted on the turbine rotor 15 .
  • the diaphragm of the high pressure turbine 7 includes the diaphragm outer ring 24 , the diaphragm inner ring 25 , and a stationary blade 23 located between the diaphragm inner ring 25 and the diaphragm outer ring 24 .
  • the stationary blade 23 and the rotating blade 22 constitute a stage of the steam turbine.
  • the diaphragm outer ring 24 is secured to the casing 28 or to a diaphragm outer ring 24 ′ of another adjacent stage.
  • the diaphragm outer ring 24 is provided with the fins 26 that form a seal between the diaphragm outer ring 24 and the tip of the rotating blade 22 to prevent steam leakage.
  • the diaphragm inner ring 25 is provided with the packing 27 that forms a seal between the diaphragm inner ring 25 and the rotor 15 to prevent steam leakage.
  • the overload steam pipe 5 is inserted into and fitted to the casing 28 with the seal rings 30 .
  • the outer surface of the overload steam pipe 5 contacts with the seal rings 30 , thereby preventing steam from leaking through the gap between the overload steam pipe 5 and the casing 28 .
  • the slit portion 31 is a turbine-axial gap formed between the diaphragm outer ring 24 and the casing 28 . As described above, the slit portion 31 is a narrow gap through which steam passes.
  • the diaphragm outer ring 24 and the casing 28 are arranged so that a width C of the slit portion 31 in the axial direction of the turbine rotor 15 is smaller than an inside diameter d of the overload steam pipe 5 (d>C).
  • the steam turbine equipment includes: the main steam control valve 4 disposed in the main steam pipe 2 leading from the boiler 1 to the steam turbine; the overload valve 6 disposed in the overload steam pipe 5 that bypasses the main steam control valve 4 and leads from the main steam pipe to the lower-pressure side of the steam turbine than a point where the main steam pipe 2 connects to the steam turbine; and the slit portion 31 through which the steam having flowed through the overload steam pipe 5 passes before flowing into the steam turbine stage portion.
  • the slit portion 31 is configured such that its width C in the axial direction of the turbine rotor 15 is smaller than the inside diameter d of the overload steam pipe 5 (d>C).
  • the main steam control valve 4 When the turbine is required to operate at a rated power generation output, the main steam control valve 4 is fully opened and the overload valve 6 is fully closed. This can eliminate a throttle loss at the main steam control valve 4 , thereby improving power generation efficiency.
  • the main steam control valve 4 When the turbine is required to operate at a power generation output exceeding a rated value, the main steam control valve 4 is fully opened and the overload valve 6 is opened in accordance with the required power generation output. This can easily achieve the power generation output exceeding the rated value.
  • the power generation output can be sharply adjusted by use of the steam control valve 4 and the overload valve 6 .
  • the present embodiment is configured such that the width C of the slit portion 31 in the axial direction of the turbine rotor 5 is smaller than the inside diameter d of the overload steam pipe 5 .
  • the steam that has passed through the overload valve 6 and flowed into the steam turbine is decelerated before passing through the slit portion 31 . Therefore, the steam can be diffused easily in the circumferential direction of the turbine after flowing into the steam turbine, thereby suppressing the drift at the stage portion.
  • the steam that has just flowed into the steam turbine from the overload valve 6 is higher in temperature than the steam at the stage portion that has passed through the slit portion 31 . Therefore, temperature increases at the stage portion, thereby reducing the material strength at the stage portion. This phenomenon becomes conspicuous especially when an intensive local increase in temperature occurs due to a large drift at the stage portion.
  • the present embodiment can suppress the drift at the stage portion as described in item (4). Therefore, a local increase in temperature at the stage portion can be avoided, thereby preventing the material strength from being reduced.
  • FIG. 3 shows absolute velocity V of steam that flows out from the stationary blade 23 ′ when the overload valve 6 is fully closed; relative velocity W, relative to the rotating blade 22 ′, of the steam that flows out from the stationary blade 23 ′ when the overload valve 6 is fully closed; absolute velocity V′ of steam that flows out from the stationary blade 23 ′ when the overload valve 6 is opened; relative velocity W′, relative to the rotating blade 22 ′, of the steam that flows out from the stationary blade 23 ′ when the overload valve 6 is opened; the rotating velocity U of the rotating blade 22 ′; and an angle ⁇ between the relative velocity W′ and the inlet portion of the rotating blade.
  • the present embodiment as described in the item (4) can suppress the drift at the stage portion. Therefore, a loss in the energy of the steam can be reduced, thereby improving the efficiency in power generation.
  • the slit portion 31 is formed between the diaphragm outer ring 24 and the casing 28 .
  • the slit portion can be formed between two casings.
  • the slit portion can also be formed between the diaphragm outer rings of two adjacent stages. Alternatively, two or more of the configurations of these slit portions can be used in combination.
  • the first embodiment describes the case where the overload steam pipe 5 is fitted to the casing 28 .
  • the present invention can also be applied to the case where the overload steam pipe 5 is being welded to the casing 28 .
  • FIG. 4 is a cross-sectional view illustrating an example of a configuration of a high pressure turbine according to the second embodiment of the present invention by way of example.
  • the steam turbine equipment of the present embodiment illustrated in FIG. 4 is different from the steam turbine equipment of the first embodiment in the configuration of a slit portion and a method of connecting an overload steam pipe to a steam turbine.
  • the slit portion 31 of the first embodiment is composed of the turbine-axial gap between the diaphragm outer ring 24 and the casing 28 .
  • a slit portion 41 of the present embodiment as illustrated in FIG. 4 is composed of a turbine-axial gap between a first inner casing 42 and a second inner casing 42 ′ and a turbine-axial gap between a diaphragm outer ring 43 and a diaphragm outer ring 43 ′.
  • the overload steam pipe 5 of the first embodiment is fitted to the casing 28 , whereas an overload steam pipe 5 A of the present embodiment is welded to an outer casing 45 .
  • the second embodiment of the steam turbine equipment of the present invention can achieve almost the same advantages as those of the first embodiment of the steam turbine equipment described above.
  • the present invention is not limited to the above embodiments and includes various modifications in a range not departing from the gist thereof.
  • the present invention includes not only the steam turbine equipment that has all the configuration described in each one of the above embodiments but also steam turbine equipment with a part of the configuration omitted.
  • a part of the configuration according to a certain one of the embodiments can be added to the configuration according to another embodiment or be replaced with a part of the configuration according to another embodiment.
  • the above embodiments exemplify the case where the high pressure turbine 7 , the intermediate turbine 10 , and the low pressure turbine 12 which are coupled with one another drive the generator 16 .
  • the turbines 7 , 10 , 12 may individually drive the generators that are respectively connected to the shafts of the turbines 7 , 10 , 12 .
  • a couple of any two of the three turbines 7 , 10 , 12 may drive a generator.
  • the present invention can be applied to a steam turbine of a combined cycle system.

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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)
  • Control Of Turbines (AREA)
US14/532,424 2013-11-05 2014-11-04 Steam Turbine Equipment Abandoned US20150125266A1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2013229512A JP6285692B2 (ja) 2013-11-05 2013-11-05 蒸気タービン設備
JP2013-229512 2013-11-05

Publications (1)

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US20150125266A1 true US20150125266A1 (en) 2015-05-07

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Application Number Title Priority Date Filing Date
US14/532,424 Abandoned US20150125266A1 (en) 2013-11-05 2014-11-04 Steam Turbine Equipment

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US (1) US20150125266A1 (ru)
EP (1) EP2873804A1 (ru)
JP (1) JP6285692B2 (ru)
CN (1) CN104675457B (ru)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20180306050A1 (en) * 2015-10-28 2018-10-25 Mitsubishi Heavy Industries Compressor Corporation Valve device and steam turbine equipment
US10301975B2 (en) * 2015-08-07 2019-05-28 Siemens Aktiengesellschaft Overload introduction into a steam turbine
CN111963265A (zh) * 2020-08-25 2020-11-20 鄂尔多斯市君正能源化工有限公司热电分公司 一种发电用锅炉燃烧过程及机组协调控制优化的方法

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3296506A1 (de) * 2016-09-20 2018-03-21 Siemens Aktiengesellschaft Anordnung zur zuleitung eines zusatzmassenstroms in einen hauptmassenstrom
EP3301267A1 (de) * 2016-09-29 2018-04-04 Siemens Aktiengesellschaft Verfahren und vorrichtung zum betreiben eines turbosatzes

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2235547A (en) * 1938-06-17 1941-03-18 Gen Electric Elastic fluid turbine
JP2006161698A (ja) * 2004-12-08 2006-06-22 Toshiba Corp 蒸気タービンの過負荷運転装置および蒸気タービンの過負荷運転方法
US7651318B2 (en) * 2006-04-28 2010-01-26 Kabushiki Kaisha Toshiba Steam turbine
JP2013194720A (ja) * 2012-03-23 2013-09-30 Hitachi Ltd 蒸気タービン設備

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GB530022A (en) * 1938-06-17 1940-12-03 British Thomson Houston Co Ltd Improvements in and relating to elastic fluid turbines
NL8104872A (nl) * 1980-11-06 1982-06-01 Hitachi Shipbuilding Eng Co Systeem voor het benutten van hoogovengas.
JPS6039852B2 (ja) * 1981-06-09 1985-09-07 富士電機株式会社 蒸気タ−ビンの過負荷蒸気流入機構
CN1221471A (zh) * 1996-04-26 1999-06-30 西门子公司 用于将过负荷蒸汽导入汽轮机中的控制装置和方法
ES2370949T3 (es) * 2008-07-16 2011-12-26 Siemens Aktiengesellschaft Válvula controlada por fluído para una turbina de gas y para una cámara de combustión.
JP2010242673A (ja) * 2009-04-08 2010-10-28 Toshiba Corp 蒸気タービンシステム及びその運転方法
JP5367497B2 (ja) * 2009-08-07 2013-12-11 株式会社東芝 蒸気タービン

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2235547A (en) * 1938-06-17 1941-03-18 Gen Electric Elastic fluid turbine
JP2006161698A (ja) * 2004-12-08 2006-06-22 Toshiba Corp 蒸気タービンの過負荷運転装置および蒸気タービンの過負荷運転方法
US7651318B2 (en) * 2006-04-28 2010-01-26 Kabushiki Kaisha Toshiba Steam turbine
JP2013194720A (ja) * 2012-03-23 2013-09-30 Hitachi Ltd 蒸気タービン設備

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10301975B2 (en) * 2015-08-07 2019-05-28 Siemens Aktiengesellschaft Overload introduction into a steam turbine
US20180306050A1 (en) * 2015-10-28 2018-10-25 Mitsubishi Heavy Industries Compressor Corporation Valve device and steam turbine equipment
US10605114B2 (en) * 2015-10-28 2020-03-31 Mitsubishi Heavy Industries Compressor Corporation Valve device and steam turbine equipment
CN111963265A (zh) * 2020-08-25 2020-11-20 鄂尔多斯市君正能源化工有限公司热电分公司 一种发电用锅炉燃烧过程及机组协调控制优化的方法

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JP6285692B2 (ja) 2018-02-28
CN104675457B (zh) 2016-09-28
EP2873804A1 (en) 2015-05-20
CN104675457A (zh) 2015-06-03
JP2015090087A (ja) 2015-05-11

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AS Assignment

Owner name: MITSUBISHI HITACHI POWER SYSTEMS, LTD., JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:TAKAHASHI, YUSUKE;LEE, GOINGWON;OGATA, KOJI;AND OTHERS;REEL/FRAME:034531/0067

Effective date: 20141107

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION