EP2666977A1 - Installation de turbine à vapeur haute température à double réchauffage - Google Patents

Installation de turbine à vapeur haute température à double réchauffage Download PDF

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Publication number
EP2666977A1
EP2666977A1 EP12168611.7A EP12168611A EP2666977A1 EP 2666977 A1 EP2666977 A1 EP 2666977A1 EP 12168611 A EP12168611 A EP 12168611A EP 2666977 A1 EP2666977 A1 EP 2666977A1
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EP
European Patent Office
Prior art keywords
turbine
steam
intermediate pressure
pressure turbines
exit
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.)
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Application number
EP12168611.7A
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German (de)
English (en)
Inventor
Martin Reigl
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.)
General Electric Technology GmbH
Original Assignee
Alstom Technology 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 Alstom Technology AG filed Critical Alstom Technology AG
Priority to EP12168611.7A priority Critical patent/EP2666977A1/fr
Priority to US13/895,887 priority patent/US20130305719A1/en
Priority to JP2013106804A priority patent/JP5726233B2/ja
Priority to CN201310189114.0A priority patent/CN103422918B/zh
Publication of EP2666977A1 publication Critical patent/EP2666977A1/fr
Withdrawn legal-status Critical Current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
    • F01K21/00—Steam engine plants not otherwise provided for
    • 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
    • F01K7/22—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 the turbines having inter-stage steam heating

Definitions

  • the present invention relates to a high-temperature steam turbine power plant with double reheat driven by a main or live steam temperature of 650 degrees C or more in the first and second reheat and having a power output of 100 MW or more.
  • the steam power plants currently in operation have main steam temperatures of up to about 600 degrees C.
  • the power plant When operating at this or close to this temperature, the power plant is typically referred to as "supercritical", as the main steam pressure is above the critical pressure.
  • Efforts to improve the efficiency of supercritical power plants through increase of the steam temperature have been hampered to a large extent by the lack of suitable materials for the boilers, turbines and supply pipes. Conventional steel even when chromium based lose their stability below 650 degrees C.
  • the power plants designed to break the barrier as currently posed by the available materials are often referred to as ultra-supercritical or USC steam plants.
  • USC steam plants To achieve a steam temperature of above 650 degrees C and more, the parts exposed to the high temperature require Nickel based alloys which are expensive and difficult to forge into large forgings beyond the limit of 10 tons. This limit can be insufficient for the rotor of a large steam turbine plant, as described for example in the published United States Patent application no. 2008/0250790 A1 .
  • Double reheat systems have an additional return flow of the main steam path back to the boiler or reheater.
  • a return path directs the exit steam from a first or high pressure turbine back to the boiler for reheating before re-entering the turbine stages at a second or intermediate pressure.
  • a similar return path exists at the exit of the intermediate pressure turbine to reheat the steam before it enters at a second (lower) intermediate pressure or at a low pressure turbine stage.
  • Double reheat systems have been suggested as a means of further increasing the efficiency of USC steam plant.
  • a design of a double reheat USC power plant is described for example in an article by R. Blum, J. Bugge, and S. Kj ⁇ r, "AD700 innovations pave the way for 53 per cent efficiency" in Modern Power Systems, Nov 2008, pp. 15-19 .
  • a steam power plant including on a single rotor at least one high pressure turbine or turbine section having a steam exit connected in operation to a first steam reheater and at least two intermediate pressure turbines or turbine sections with a first of the at least two intermediate pressure turbines or turbine sections having a steam exit connected in operation to a second steam reheater and with a second of the at least two intermediate pressure turbines or turbine sections having a steam entry to receive steam from the second steam reheater and a steam exit connected to one or more low pressure turbines or turbine sections, whereby the at least two intermediate pressure turbines or turbine sections are each separated into a high temperature turbine or turbine section and into a low temperature turbine or turbine section.
  • a high temperature turbine or turbine section can receive reheated steam at temperatures above 650 degrees C, preferably above 700 degrees C. And hence the high temperature turbine or turbine section is at least partly manufactured from advanced materials such as Nickel based alloys.
  • the four turbines or turbine sections resulting from the separation of the intermediate turbines can be preferable recombined into double-flow turbines resulting in either a double-flow high temperature turbine, a double-flow low temperature turbine, or both.
  • the plant design 10 of FIG. 1 shows a known USC steam plant with double reheat.
  • live steam is produced from a water return cycle (not shown) and guided through the main steam feed pipe 121 and the main steam inlet valve 131 to a first turbine 14.
  • the turbine 14 is typically referred to as the high pressure or HP turbine.
  • the main steam path exits the HP turbine 14 through a pipe 122 , which in turn branches into the first reheater return pipe 123 .
  • the main steam flow is reheated before entering the feed pipe 124 and passing through the inlet valve 132 into the first intermediate pressure or IP turbine 161 .
  • the first IP turbine 161 is manufactured using essentially the same high-temperature resistant materials as the HP turbine 14 . From the exit of the first IP turbine 161 leads a return pipe 125 to the second reheater 152 .
  • the steam is again heated to a temperature close to or even above the original live steam temperature. After passing through the second reheater the steam enters into a steam feed pipe 126 and through a valve 133 into a second intermediate pressure turbine 162 .
  • the second IP turbine 162 is again manufactured using essentially the same high-temperature resistant materials as the HP turbine 14 and the first IP turbine 161 .
  • the steam at the exit of the second IP turbine 162 is guided into one or more low pressure or LP turbines 163 to be finally expanded to condensing conditions.
  • the LP turbine 163 is configured as a so-called "double -flow" turbine with two balanced branches in one inner casing.
  • All turbines share a single rotor shaft 17 which drives an electro-magnetic generator 18 , as known in the art.
  • the plant design 10 of FIG. 2A shows a USC steam plant with double reheat with a reheat system in accordance with an example of the present invention. Numerals of essentially equal components or components with similar functions are maintained with respect to FIG. 1 .
  • a steam generator or live steam boiler 11 to produce steam from a water return cycle (not shown) and guide it through the main steam feed pipe 121 and the main steam inlet valve 131 to a first turbine 14 .
  • the turbine 14 is a high pressure or HP turbine made of materials suitable for temperatures around 700 degrees Celsius and a main steam pressure P0 of about 350 bar.
  • the main steam path exits the HP turbine 14 through pipe 122 , which in turn branches into the first reheater return pipe 123 .
  • the main steam flow is reheated before entering the feed pipe 124 and passes through the inlet valve 132 into the first intermediate pressure or IP turbine 161 .
  • the first intermediate pressure or IP turbine 161 is in this example separated into a first high-temperature part 161-1 and a second low temperature part 161-2 .
  • separation the meaning is that the first high-temperature part 161-1 is housed within or surrounded by an inner casing separated from the inner casing of the second low temperature part 161-2 , which has its own inner casing.
  • step of separating the first intermediate pressure or IP turbine 161 into a first high-temperature part 161-1 and a second low temperature part 161-2 its most significant element is hence the step of housing both parts of the turbine in different inner casings (with different supply and exit lines).
  • the first high-temperature part 161-1 of the IP turbine 161 is manufactured using essentially the same high-temperature resistant materials as the HP turbine 14 while requiring less pressure resistance due to the reduced steam pressure from the first reheat cycle.
  • a feed pipe 128 connects the exit of the high-temperature part 161-1 to the second low temperature part 161-2 .
  • the second low temperature part 161-2 of the turbine 161 is no longer subject to the same high temperatures as the first part 161-1 , it can be built using more conventional materials as applied for example in the building of steam turbines for super-critical steam.
  • the second low temperature part 161-2 of the turbine 161 is shown as a double -flow turbine with two balanced branches in one inner casing. The exits of the second low temperature part 161-2 are combined into the return pipe 125 conveying the steam back to the second reheater 152 .
  • the separation of the first IP turbine 161 into first high-temperature part 161-1 and a second low temperature part 161-2 has the advantage of splitting the casing and turbine parts into high temperature components and low temperature components only. Neither is it required to manufacture a full IP turbine with high-temperature components nor is it necessary to weld together casings parts or other turbine parts made from high-temperature alloys on the one side and conventional alloys on the other side.
  • the welds between different alloys in a high-temperature steam environment are found to pose a risk for crack initiation and can be a major source of long-term defects in USC turbine plants.
  • the steam is again heated to a temperature around 720 or 730 degrees Celsius. After passing through the second reheater the steam enters into a steam feed pipe 126 and through a valve 133 into the second intermediate pressure turbine 162 .
  • the second IP turbine 162 is in this example also separated into a first high-temperature part 162-1 and a second low temperature part 162-2 .
  • the separation means that the first high-temperature part 162-1 is housed within or surrounded by an inner casing separated from the inner casing of the second low temperature part 162-2 , which has its own inner casing.
  • the first high-temperature part 162-1 of the IP turbine 162 is manufactured using essentially the same high-temperature resistant materials as the HP turbine 14 and the first high-temperature part 161-1 while requiring even less pressure resistance than the latter due to the reduced steam pressure from the second reheat cycle.
  • the feed pipe 129 connects the exit of the high-temperature part 162-1 to the second low temperature part 161-2 .
  • the second low temperature part 162-2 of the second IP turbine 162 is also no longer subject to the same high temperatures as the first part 162-1 , it can be built using more conventional materials as applied for example in the building of steam turbines for super-critical steam.
  • the second low temperature part 162-2 of the turbine 162 is shown as a double -flow turbine with two balanced branches in one inner casing.
  • the exits of the second low temperature part 161-2 are combined into the feed pipe 127 conveying the steam to the one or more low pressure or LP turbines 163 to be finally expanded to condensing conditions.
  • the LP turbine 163 is configured as a so-called "double -flow" turbine with two balanced branches in one inner casing.
  • the single double-flow turbine 163 represents any number of LP turbines such as one, two, three, four or five of such turbines depending on the overall mass flow rate of the steam through the plant.
  • All the turbines of FIG. 2A share a single rotor shaft 17 which drives an electro-magnetic generator 18 , as known in the art.
  • FIG. 2A The advantages gained by the implementation of a plant as shown in FIG. 2A can be furthered by combining the high temperature turbine parts 161-1 and 162-1 into a double-flow casing 164 with each part having its dedicated feed and exit pipes as shown in the example of FIG. 2B .
  • FIG. 2B numerals of essentially equal components or components with similar functions are maintained with respect to FIG. 2A .
  • the high temperature turbine parts 161-1 and 162-1 are shown combined into a double-flow turbine casing 164 .
  • the feed pipe 124 delivers the steam from the first reheater 151 to the first high temperature turbine part 161-1 of the double-flow turbine and the feed pipe 126 delivers the steam from the second reheater 151 to the second high temperature turbine part 162-1 of the double-flow turbine.
  • the exit of the first high temperature turbine part 161-1 of the double-flow turbine 164 is connected to the feed pipe 128 of the low temperature part 161-2 of the first intermediate pressure turbine.
  • the low temperature part 161-2 of the first intermediate pressure turbine is a double-flow turbine with its exits connected via the return pipe 125 to the second reheater 152 .
  • the exit of the second high temperature turbine part 162-1 of the double-flow turbine 164 is connected to the feed pipe 129 of the low temperature part 162- 2 of the second intermediate pressure turbine.
  • the low temperature part 162-2 of the second intermediate pressure turbine is a double-flow turbine with its exits combined into the feed pipe 127 conveying the steam to the one or more low pressure or LP turbines 163 to be finally expanded to condensing conditions.
  • the LP turbine 163 is configured as a so-called "double -flow" turbine with two balanced branches in one inner casing.
  • the single double-flow turbine 163 represents any number of LP turbines such as one, two, three, four or five of such turbines depending on the overall mass flow rate of the steam through the plant.
  • the second parts 161-2 , 162-2 of the first and second intermediate pressure turbines can be combined into a single double-flow turbine instead of forming two separate double-flow turbines as in the examples above.
  • double-flow turbine casing there are several variants possible including with common outer casing and common inner casing, but also a design with one inner casing and a piston and a blade carrier on the second side is possible; and a common inner inlet casing with blade carriers on both sides.
  • the invention may also comprise any individual features described or implicit herein or shown or implicit in the drawings or any combination of any such features or any generalisation of any such features or combination, which extends to equivalents thereof.
  • the breadth and scope of the present invention should not be limited by any of the above-described exemplary embodiments.
  • Alternative features serving the same, equivalent or similar purposes may replace each feature disclosed in the specification, including the drawings, unless expressly stated otherwise.

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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)
EP12168611.7A 2012-05-21 2012-05-21 Installation de turbine à vapeur haute température à double réchauffage Withdrawn EP2666977A1 (fr)

Priority Applications (4)

Application Number Priority Date Filing Date Title
EP12168611.7A EP2666977A1 (fr) 2012-05-21 2012-05-21 Installation de turbine à vapeur haute température à double réchauffage
US13/895,887 US20130305719A1 (en) 2012-05-21 2013-05-16 High-temperature steam turbine power plant with double reheat
JP2013106804A JP5726233B2 (ja) 2012-05-21 2013-05-21 二重再熱を行う高温蒸気タービン発電プラント
CN201310189114.0A CN103422918B (zh) 2012-05-21 2013-05-21 具有双重再热的高温蒸汽涡轮动力设备

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP12168611.7A EP2666977A1 (fr) 2012-05-21 2012-05-21 Installation de turbine à vapeur haute température à double réchauffage

Publications (1)

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EP2666977A1 true EP2666977A1 (fr) 2013-11-27

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EP12168611.7A Withdrawn EP2666977A1 (fr) 2012-05-21 2012-05-21 Installation de turbine à vapeur haute température à double réchauffage

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US (1) US20130305719A1 (fr)
EP (1) EP2666977A1 (fr)
JP (1) JP5726233B2 (fr)
CN (1) CN103422918B (fr)

Families Citing this family (11)

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Publication number Priority date Publication date Assignee Title
WO2014146861A1 (fr) * 2013-03-21 2014-09-25 Siemens Aktiengesellschaft Système de production d'énergie et procédé de fonctionnement
CN103821574B (zh) * 2014-03-14 2016-05-18 中国电力工程顾问集团华东电力设计院有限公司 一次再热增压汽机热力系统
CN104088677B (zh) * 2014-06-25 2016-03-02 北京越麓咨询有限责任公司 一种多级冲动式汽轮机的机内蒸汽再热器
CN105673093A (zh) * 2016-02-02 2016-06-15 哈尔滨汽轮机厂有限责任公司 一种高效700℃超超临界600mw等级四缸两排汽汽轮机
US10151216B2 (en) 2016-08-31 2018-12-11 General Electric Technology Gmbh Insulation quality indicator module for a valve and actuator monitoring system
US10544700B2 (en) 2016-08-31 2020-01-28 General Electric Technology Gmbh Advanced startup counter module for a valve and actuator monitoring system
US10156153B2 (en) 2016-08-31 2018-12-18 General Electric Technology Gmbh Advanced tightness test evaluation module for a valve and actuator monitoring system
US10626749B2 (en) 2016-08-31 2020-04-21 General Electric Technology Gmbh Spindle vibration evaluation module for a valve and actuator monitoring system
US10066501B2 (en) 2016-08-31 2018-09-04 General Electric Technology Gmbh Solid particle erosion indicator module for a valve and actuator monitoring system
US10871081B2 (en) 2016-08-31 2020-12-22 General Electric Technology Gmbh Creep damage indicator module for a valve and actuator monitoring system
US10233786B2 (en) 2017-03-28 2019-03-19 General Electric Technology Gmbh Actuator spring lifetime supervision module for a valve and actuator monitoring system

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DE1027210B (de) * 1956-09-18 1958-04-03 Siemens Ag Dampfturbine mit Zwischenueberhitzung
EP1445429A1 (fr) * 2003-02-07 2004-08-11 Elsam Engineering A/S Système de turbines à vapeur
US20080250790A1 (en) 2007-04-13 2008-10-16 Shinya Imano High-temperature steam turbine power plant
EP2180149A1 (fr) * 2008-08-11 2010-04-28 Mitsubishi Heavy Industries, Ltd. Ensemble turbine à vapeur

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FR1312886A (fr) * 1961-07-13 1962-12-21 Siemens Ag Centrale thermique du type gaz-vapeur
JP3582848B2 (ja) * 1994-03-14 2004-10-27 株式会社東芝 蒸気タービン発電プラント
US5404724A (en) * 1994-04-07 1995-04-11 Westinghouse Electric Corporation Boiler feedpump turbine drive/feedwater train arrangement
DE102007030764B4 (de) * 2006-07-17 2020-07-02 General Electric Technology Gmbh Dampfturbine mit Heizdampfentnahme

Patent Citations (4)

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Publication number Priority date Publication date Assignee Title
DE1027210B (de) * 1956-09-18 1958-04-03 Siemens Ag Dampfturbine mit Zwischenueberhitzung
EP1445429A1 (fr) * 2003-02-07 2004-08-11 Elsam Engineering A/S Système de turbines à vapeur
US20080250790A1 (en) 2007-04-13 2008-10-16 Shinya Imano High-temperature steam turbine power plant
EP2180149A1 (fr) * 2008-08-11 2010-04-28 Mitsubishi Heavy Industries, Ltd. Ensemble turbine à vapeur

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
R. BLUM; J. BUGGE; S. KJAER: "AD700 innovations pave the way for 53 per cent efficiency", MODERN POWER SYSTEMS, November 2008 (2008-11-01), pages 15 - 19

Also Published As

Publication number Publication date
CN103422918B (zh) 2015-08-12
JP5726233B2 (ja) 2015-05-27
US20130305719A1 (en) 2013-11-21
JP2013241934A (ja) 2013-12-05
CN103422918A (zh) 2013-12-04

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