EP3511535A1 - Installation et procédé de fonctionnement d'une installation - Google Patents

Installation et procédé de fonctionnement d'une installation Download PDF

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Publication number
EP3511535A1
EP3511535A1 EP18150977.9A EP18150977A EP3511535A1 EP 3511535 A1 EP3511535 A1 EP 3511535A1 EP 18150977 A EP18150977 A EP 18150977A EP 3511535 A1 EP3511535 A1 EP 3511535A1
Authority
EP
European Patent Office
Prior art keywords
pressure
low
turbine
medium
speed
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP18150977.9A
Other languages
German (de)
English (en)
Inventor
Carmen Stüer
Gerta Zimmer
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP18150977.9A priority Critical patent/EP3511535A1/fr
Publication of EP3511535A1 publication Critical patent/EP3511535A1/fr
Withdrawn legal-status Critical Current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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
    • F01K7/18—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 turbine being of multiple-inlet-pressure type
    • F01K7/20—Control means specially adapted therefor
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/101—Regulating means specially adapted therefor
    • 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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • F01K23/106—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle with water evaporated or preheated at different pressures in exhaust boiler
    • F01K23/108—Regulating means specially adapted therefor
    • 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
    • F01K7/02—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 of multiple-expansion type
    • F01K7/025—Consecutive expansion in a turbine or a positive displacement engine

Definitions

  • the invention relates to a system comprising a gas turbine, a generator, a steam turbine having a high and medium pressure turbine part and a low pressure turbine part and a turn engine, wherein the steam turbine and the turn engine have a common shaft.
  • the invention relates to a method for operating a system, wherein the system comprises a steam turbine, wherein the steam turbine has a high and medium pressure turbine section and a low pressure turbine section, wherein the high and medium pressure turbine section and the low pressure turbine part a have common shaft.
  • the hot exhaust gases from the gas turbine are used to heat a so-called heat recovery steam generator.
  • the heat recovery steam generator is designed for the vaporization of liquid water to steam, which is required for the operation of a steam turbine.
  • the steam turbine and the gas turbine are used here in general for driving one or more electric generators for generating electrical energy.
  • the plant can be operated as a combined heat and power, in which the provision of steam as heating steam for district heating applications or as process steam in the chemical or other industries is a design target. In this case, part of the steam is withdrawn from the water vapor conversion process.
  • a plant, in particular a gas and steam turbine plant can be designed as a so-called single-shaft system.
  • the gas turbine, the generator and the steam turbine is designed with a torque-transmitting common shaft.
  • the steam turbine in this case comprises a high-pressure, medium-pressure and low-pressure turbine part.
  • the high-pressure and medium-pressure turbine part can be designed in a common housing.
  • the output of the high pressure turbine section is fluidly connected to a reheater to heat the effluent steam from the high pressure turbine section to a higher temperature, which then flows into the intermediate pressure turbine section.
  • the effluent from the medium-pressure turbine section steam flows by means of an overflow into the low-pressure turbine section.
  • the overflow line is usually designed such that a partial mass flow is removed as heating or process steam. It is here, for example, from the EP 1 904 731 known to arrange a clutch between the low-pressure turbine section and the medium-pressure turbine section to mechanically decouple the low-pressure turbine section from the medium-pressure turbine section.
  • the problem here is that delays the shutdown of the low-pressure turbine section by decoupling the low-pressure turbine section of the medium-pressure turbine section, the drag torque of the clutch or steam leakage in the damper in the overflow, which can set an undefined spin speed of the low-pressure turbine section.
  • the vacuum is usually broken behind the low-pressure turbine section. This allows a negative moment to be used by ventilation for faster departure. However, in a lower speed range this is no longer effective.
  • the object of the invention is to provide an improved system.
  • a system comprising a gas turbine, a generator, a steam turbine having a high and medium pressure turbine part and a low pressure turbine part and a turn engine, the steam turbine and the turn engine having a common shaft, the turn engine is designed to drive the common shaft.
  • the object is likewise achieved by a method for operating a plant, the plant having a steam turbine, wherein the steam turbine has a high and medium pressure turbine section and a low pressure turbine section, wherein the high and medium pressure turbine section and the low pressure turbine section have a common shaft, wherein the steam turbine is operated for steam supply or a certain Betreibungtagen such that the low-pressure turbine part is mechanically decoupled from the shaft with a second clutch.
  • the turn motor is typically an electric motor that is used at standstill to rotate the shaft at low speeds, such as 1 Hz, to protect the steam turbine from curling. At standstill, the steam turbine is not flown with steam.
  • the turn engine is used here as a brake.
  • the rotational speed of the shaft can be regulated in such a way that unfavorable speed windows are not or quickly traversed.
  • the turn motor is raised to a predefined speed after the decoupling of the turn motor from the low-pressure turbine section. As soon as the low-pressure turbine section reaches this speed, the coupling between the turn engine and the low-pressure turbine section intervenes.
  • the turn-motor is then switched to a braking mode and thereby reduces the speed of the low-pressure turbine part in a more favorable speed window, for example, 1 Hz, from which the turbine can be started at a later date.
  • the low-pressure turbine section and the high-pressure and medium-pressure turbine sections are coupled in such a way that a predefined or desired dome angle is achieved.
  • the high pressure and medium pressure sub-turbine is operated at a number of operation, such as 50 or 60 Hz, and the low pressure sub-turbine is started by steaming until a speed at which it can be coupled is reached, using a method to achieve the desired differential angle between the high pressure and medium pressure wave and the low pressure wave.
  • the high and medium pressure turbine sections are downshifted, reducing speed.
  • the turn motor would take over the function of the angle-controlled coupling at low speeds as a control element.
  • the turn engine accelerates the low-pressure turbine section to a predefined speed during the run-out of the high-pressure and medium-pressure turbine sections.
  • an angle-controlled coupling takes place, in which a desired differential angle between the medium-pressure wave and the low-pressure wave is achieved.
  • the turn motor is switched to braking mode and reduces the speed of the low-pressure turbine part in a more favorable speed window, such as 1 Hz, the turbine can then be started at a later date.
  • the FIGURE shows a schematic view of a plant 1 according to the invention.
  • the plant 1 comprises a steam turbine 2.
  • the steam turbine 2 has a high-pressure turbine section 3, a medium-pressure turbine section 4 and a low-pressure turbine section 5.
  • the high-pressure turbine section 3, the medium-pressure turbine section 4 and the low-pressure turbine part 5 are arranged on a common shaft 6.
  • the high-pressure turbine section 3 and the medium-pressure turbine section 4 may be formed in a common housing. Via a live steam line 7 and a live steam valve 8, a live steam first flows into the high-pressure turbine section 3 and from there via an outlet 9 as a cold reheater steam 10 to a reheater, not shown, wherein the cold reheater steam 10 is heated in the reheater and as a hot reheater steam 11th flows in an access line 13 with a valve 12 to the inlet of the medium-pressure turbine section 4. In the medium-pressure turbine section 4, the steam is further relaxed. The temperature and the pressure of the steam are reduced.
  • the medium-pressure steam flows from an outlet 15 of the medium-pressure turbine section 4 into an overflow line 16 to an inlet 17 of the low-pressure turbine section 5.
  • a first valve 18, which is designed as a butterfly valve is arranged in series with the first valve 18, a third valve 19 is arranged. Parallel to the third valve 19, a second valve 20 is arranged in a bypass line 21.
  • the overflow line 16 has a branch 22 for the removal of heating or process steam, wherein the ratio of the two partial mass flows generated in this way can be regulated by two valves 18 and 23 or 24 arranged in the respective line branch.
  • the removable in the branch 22 as needed heating or process steam is supplied via a steam line 25 to a technical facility or an industrial plant, not shown here. If no heating or process steam is needed, the valve 24 or 23 is closed, which then the entire the medium-pressure turbine section 4 leaving steam mass flow with the valve 18 open, 19 and 20 of the low-pressure turbine section 5 is supplied.
  • the turn motor 26 may be an electric motor, which transmits a torque to the shaft 6 via a first clutch 27, in particular SSS clutch. Between the medium-pressure turbine part 4 and the low-pressure turbine part 5, a second clutch 28, in particular SSS clutch is arranged. Between the high-pressure turbine part 3 and the gas turbine and generator, not shown, a third clutch 29 is arranged.
  • Appendix 1 is operated as described below.
  • the steam turbine 2 is supplied with a live steam via the main steam line 7, wherein the thermal energy of the steam is converted into rotational energy of the rotor and flows through the high-pressure turbine section 3, the medium-pressure turbine section 4 and the low-pressure turbine section 5.
  • a process or heating steam is decoupled via the steam line 25.
  • the amount of steam removed from the steam line 25 depends on the setting of the valves 24, 23, 18, 19 and 21. If the maximum amount of steam for the heating or process steam is made available, it is possible according to the invention to decouple the low-pressure turbine part 5 via the second clutch 28 from the shaft 6.
  • the low-pressure turbine part 5 is then shut down to a low turn speed, which may be 1 Hz.
  • the steam from the outlet 15 of the medium-pressure turbine section 4 then flows completely into the steam line 25.
  • the speed of the low-pressure turbine part 5 decreases from the operating speed (for example, 60 or 50 Hz) to a lower speed.
  • the problem here is that due to the natural leakage of the low pressure turbine part 5 vibrations that can cause damage. Therefore, it is desirable to avoid certain speeds as possible or to drive through quickly.
  • a control may operate the turn motor 26 such that the transmitted brake torque from the turn motor 26 to the low pressure turbine sub-turbine 5 varies with time.
  • the turn-motor 26 is therefore operated in such a way that the change in the rotational speed takes place in such a way that disturbing vibrations of the low-pressure turbine part 5 are avoided.
  • the first clutch 27 is disengaged, which means that no torque is transmitted from the turn engine 26 to the low-pressure turbine part 5.
  • the low-pressure turbine part 5 runs from the operating speed to a target speed.
  • the target speed is a speed that the turn motor 26 can reach.
  • the turn-motor 26 is accelerated to this target speed and as soon as the speed of the low-pressure turbine part 5 has reached the speed of the turn-motor 26, engages the first clutch 27 such that a mechanical coupling between the low-pressure turbine part 5 and the turn -Motors 26 takes place.
  • the turn motor 26 is then operated so that the rotational speed of the turn motor 26 and the low pressure turbine part 5 is reduced to a turn speed, which may for example be 1 Hz.
  • the system 1 is operated in such a way that the live steam still flows via the live steam line 7 into the high and medium pressure turbine section 4, where the thermal energy of the steam is converted into rotational energy and at the outlet 15 of the medium-pressure turbine section 4 the effluent steam, which has a lower thermal energy than at the entrance of the high-pressure turbine section 3 (as process steam) via the steam line 25 to a non supplied closer technical plant or an industrial operation.
  • the low pressure turbine part 5 is hereby rotated at the turn speed.
  • the first valve 18, the second valve 20 and the third valve 19 are closed in this case.
  • the second clutch 28 between the low-pressure turbine section 5 and the medium-pressure turbine section 4 engages again.
  • a first scenario via suitable positions of the valves 24, 23, 18, 19 and 20 again a steam from the output 15 of the medium-pressure turbine section to the medium-pressure turbine section, the first clutch 27 is released from the turn motor 26.
  • the rotational speed of the low-pressure turbine part 5 increases and upon reaching the rotational speed of the medium-pressure turbine section 4, the second clutch 28 engages such that a desired differential angle between the low-pressure turbine section 5 and the high-pressure and medium-pressure turbine section. 4 is reached.
  • the coupling takes place by means of the second clutch 28 between the high-pressure and medium-pressure turbine section 3, 4 and the low-pressure turbine section 5 at low speeds.
  • the system 1 is present in a first operating phase, in which the low-pressure turbine part 5 is mechanically decoupled from the high-pressure and medium-pressure turbine sections 3, 4.
  • the speed of the low-pressure turbine part 5 is comparatively low and corresponds to a turn-speed, which is achieved by means of the turn-motor 26.
  • the speed is in this case about 1 Hz.
  • the second operating phase follows, in which the high and medium pressure turbine section 3, 4 is coupled via the second clutch 28 with the low pressure turbine section 5.
  • the speed of the high and medium pressure turbine section 3, 4 is changed from the operating speed to a low speed. This is done essentially by a leakage of the high and medium pressure turbine section 3, 4.
  • the speed of the high and medium pressure turbine section 3, 4 runs from the operating speed to a lower speed such.
  • the coupling speed is between the operating speed and the turn speed.
  • the speed of the low-pressure turbine part 5 is increased from the turn speed by means of the turn-motor 26 to the predefined coupling speed.
  • the low-pressure turbine section 5 is mechanically coupled to the high-pressure and medium-pressure turbine sections 3, 4 a predefined angle between the rotor of the low pressure turbine part 5 and the rotor of the high and medium pressure turbine section 3, 4 achieved.
  • the entire now coupled shaft 6 may be shut down to a low park speed and ramped up from this park speed at a later time.
  • the turn motor 26 is used here as a controller.

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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)
EP18150977.9A 2018-01-10 2018-01-10 Installation et procédé de fonctionnement d'une installation Withdrawn EP3511535A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP18150977.9A EP3511535A1 (fr) 2018-01-10 2018-01-10 Installation et procédé de fonctionnement d'une installation

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP18150977.9A EP3511535A1 (fr) 2018-01-10 2018-01-10 Installation et procédé de fonctionnement d'une installation

Publications (1)

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EP3511535A1 true EP3511535A1 (fr) 2019-07-17

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EP18150977.9A Withdrawn EP3511535A1 (fr) 2018-01-10 2018-01-10 Installation et procédé de fonctionnement d'une installation

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114934818A (zh) * 2022-05-25 2022-08-23 西安热工研究院有限公司 一种高位机组、高位机组运行方法及高低位汽轮机系统

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4426354A1 (de) * 1994-07-25 1996-02-01 Abb Management Ag Kombianlage
US6047548A (en) * 1996-05-14 2000-04-11 Siemens Aktiengesellschaft Gas and steam turbine plant and method for operating the same
JP2004137912A (ja) * 2002-10-15 2004-05-13 Mitsubishi Heavy Ind Ltd ガスタービン複合発電プラント
EP1591628A1 (fr) * 2004-04-30 2005-11-02 Siemens Aktiengesellschaft Centrale combinée et méthode de refroidissement de ladite centrale
EP1904731A1 (fr) 2005-07-15 2008-04-02 Siemens Aktiengesellschaft Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner
US20120223532A1 (en) * 2010-09-03 2012-09-06 Alstom Technology Ltd Steam turbine plant
EP2700790A1 (fr) * 2012-08-21 2014-02-26 Siemens Aktiengesellschaft Centrale électrique comprenant une turbine à gaz, un générateur et une turbine à vapeur et procédé de son opération
EP2813675A1 (fr) 2013-06-14 2014-12-17 Siemens Aktiengesellschaft Procédé de couplage d'une turbine à vapeur et d'une turbine à gaz avec un angle différentiel souhaité
EP2910742A1 (fr) 2014-02-20 2015-08-26 Siemens Aktiengesellschaft Procédé de couplage d'une turbine à vapeur et d'une turbine à gaz avec un angle différentiel
EP3147672A1 (fr) 2015-09-22 2017-03-29 Siemens Aktiengesellschaft Procede et agencement de determination de la vitesse et de l'ange de deux arbres
EP3246536A1 (fr) 2016-05-17 2017-11-22 Siemens Aktiengesellschaft Procede de synchronisation d'une turbine au reseau electrique
EP3246538A1 (fr) 2016-05-18 2017-11-22 Siemens Aktiengesellschaft Procede de couplage d'une turbine a vapeur et d'une turbine a gaz avec reglage de l'angle differentiel souhaite a l'aide d'une acceleration de consigne
EP3252281A1 (fr) 2016-05-31 2017-12-06 Siemens Aktiengesellschaft Synchronisation d'une turbine a l'aide d'un reseau a courant alternatif selon une trajectoire theorique pour l'angle differentiel theorique

Patent Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4426354A1 (de) * 1994-07-25 1996-02-01 Abb Management Ag Kombianlage
US6047548A (en) * 1996-05-14 2000-04-11 Siemens Aktiengesellschaft Gas and steam turbine plant and method for operating the same
JP2004137912A (ja) * 2002-10-15 2004-05-13 Mitsubishi Heavy Ind Ltd ガスタービン複合発電プラント
EP1591628A1 (fr) * 2004-04-30 2005-11-02 Siemens Aktiengesellschaft Centrale combinée et méthode de refroidissement de ladite centrale
EP1904731A1 (fr) 2005-07-15 2008-04-02 Siemens Aktiengesellschaft Installation a turbine a gaz et a vapeur, ainsi que procede pour la faire fonctionner
US20120223532A1 (en) * 2010-09-03 2012-09-06 Alstom Technology Ltd Steam turbine plant
EP2700790A1 (fr) * 2012-08-21 2014-02-26 Siemens Aktiengesellschaft Centrale électrique comprenant une turbine à gaz, un générateur et une turbine à vapeur et procédé de son opération
EP2813675A1 (fr) 2013-06-14 2014-12-17 Siemens Aktiengesellschaft Procédé de couplage d'une turbine à vapeur et d'une turbine à gaz avec un angle différentiel souhaité
EP2910742A1 (fr) 2014-02-20 2015-08-26 Siemens Aktiengesellschaft Procédé de couplage d'une turbine à vapeur et d'une turbine à gaz avec un angle différentiel
EP3147672A1 (fr) 2015-09-22 2017-03-29 Siemens Aktiengesellschaft Procede et agencement de determination de la vitesse et de l'ange de deux arbres
EP3246536A1 (fr) 2016-05-17 2017-11-22 Siemens Aktiengesellschaft Procede de synchronisation d'une turbine au reseau electrique
EP3246538A1 (fr) 2016-05-18 2017-11-22 Siemens Aktiengesellschaft Procede de couplage d'une turbine a vapeur et d'une turbine a gaz avec reglage de l'angle differentiel souhaite a l'aide d'une acceleration de consigne
EP3252281A1 (fr) 2016-05-31 2017-12-06 Siemens Aktiengesellschaft Synchronisation d'une turbine a l'aide d'un reseau a courant alternatif selon une trajectoire theorique pour l'angle differentiel theorique

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114934818A (zh) * 2022-05-25 2022-08-23 西安热工研究院有限公司 一种高位机组、高位机组运行方法及高低位汽轮机系统
CN114934818B (zh) * 2022-05-25 2023-09-01 西安热工研究院有限公司 一种高位机组、高位机组运行方法及高低位汽轮机系统

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