EP1674669A1 - Procédé de refroidissement de turbine à vapeur - Google Patents

Procédé de refroidissement de turbine à vapeur Download PDF

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Publication number
EP1674669A1
EP1674669A1 EP04030350A EP04030350A EP1674669A1 EP 1674669 A1 EP1674669 A1 EP 1674669A1 EP 04030350 A EP04030350 A EP 04030350A EP 04030350 A EP04030350 A EP 04030350A EP 1674669 A1 EP1674669 A1 EP 1674669A1
Authority
EP
European Patent Office
Prior art keywords
steam
cooling
main
pressure
temperature
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Withdrawn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
EP04030350A
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German (de)
English (en)
Inventor
Heiner Dr. Edelmann
Detlef Dr. Haje
Werner-Holger Heine
Rudolf Kral
Michael Wechsung
Kai Dr. Wieghardt
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 EP04030350A priority Critical patent/EP1674669A1/fr
Publication of EP1674669A1 publication Critical patent/EP1674669A1/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Withdrawn legal-status Critical Current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
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/08—Cooling; Heating; Heat-insulation
    • 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
    • F01D3/00—Machines or engines with axial-thrust balancing effected by working-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
    • F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
    • F01D5/02—Blade-carrying members, e.g. rotors
    • F01D5/08—Heating, heat-insulating or cooling means
    • 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
    • F05D2220/00—Application
    • F05D2220/30—Application in turbines
    • F05D2220/31—Application in turbines in steam turbines
    • 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
    • F05D2260/20—Heat transfer, e.g. cooling
    • F05D2260/232—Heat transfer, e.g. cooling characterized by the cooling medium
    • F05D2260/2322—Heat transfer, e.g. cooling characterized by the cooling medium steam

Definitions

  • the invention relates to a method for cooling a steam turbine and a steam turbine plant.
  • the efficiency of a steam turbine is mainly influenced by an enthalpy gradient of the flow medium.
  • great efforts are being made to provide the ability to form a steam turbine such that the inlet of the steam turbine is suitable for higher temperatures.
  • Current steam turbines are designed for flow medium temperatures in the inlet for up to 620 ° to 630 ° C.
  • One of the technical problems to be solved is to find a suitable cooling concept for the steam turbine used.
  • a steam turbine plant which is designed for power supply, composed of different sub-turbines, the sub-turbines are designed for different states of the flow medium.
  • a steam turbine plant has a high-pressure turbine section, a medium-pressure turbine section and a low-pressure turbine section.
  • the fresh steam flowing into the high-pressure turbine section has temperatures of up to 620 ° to 630 ° C and pressures of up to 300 bar.
  • the flow medium from the high-pressure turbine usually flows into a reheater unit, where the flow medium is heated again to a temperature of about 600 ° to 620 ° C.
  • the flow medium then flows into the medium-pressure turbine section and from there into the low-pressure turbine section.
  • the energy of the flow medium is in this case converted into rotational energy of a rotor which is coupled to a generator.
  • the high-pressure turbine section is equipped with a reaction blading, which is the rule, the expansion of the supplied flow medium to forces acting in the axial direction along a shaft of the steam turbine.
  • a thrust balance piston is also part of the shaft seal and described for example in DE 197 01 020 A1 and in DE 68 097 08 U1.
  • the thrust balance piston is thereby acted upon at one end face with live steam, resulting in a counterforce, the so-called thrust balancing force. Since a relatively large loading surface is required, the diameter of the piston is comparatively large. The large diameter leads to a high centrifugal acceleration.
  • the flow medium is throttled over the located on the lateral surface of the piston shaft seal and also wets the rear end wall.
  • the piston is therefore exposed to high temperatures during operation.
  • the high temperatures lead to a reduced strength of the piston.
  • the piston is thus subject to significant restrictions in terms of material selection. As a rule, a high-quality material must be used. Since the piston is generally made in one piece with the shaft, significantly higher costs.
  • a suitable thrust balance piston it is cooled in some embodiments of a steam turbine.
  • a steam turbine Such cooling is described in WO 01/86121 A1.
  • the steam generator cooling steam is removed, the temperature is smaller and the pressure is greater than that of the live steam.
  • the disadvantage here is that the cooling steam usually has a constant temperature.
  • the Inventors have recognized that feeding the cooling steam leads to a sudden temperature gradient in the components to be cooled. These sudden temperature differences lead to undesirable temperature cycles and reduce the overall life of the steam turbine.
  • high-pressure steam turbines do not become active, i. cooled by separately supplied cooling medium.
  • the cooling is achieved here by suitable design of the expansion of the live steam.
  • the live steam flowing into a steam turbine is first expanded exclusively by stationary parts, such as, for example, guide rings or radially acting guide vanes, and is cooled by about 10 K. This expanded steam then acts on rotating components.
  • the incoming steam is passed through the outer casing by means of a separate diffuser. The outer housing is then subjected to a teilspand investigating cooling medium of lower temperature.
  • Cooling can also be done by a central cavity through which a cooling steam flows and is fed from there to the areas to be cooled.
  • the disadvantage here is that the bore usually has to be arranged at the point of highest component stress, which adversely affects the strength.
  • the object of the present invention is to provide suitable cooling for a steam turbine, in particular cooling for a thrust balance piston.
  • this object is achieved by a method in which at least one first cooling steam having a first temperature and a first pressure is taken from a first region of a steam generator and having a second having a second temperature and a second pressure Cooling steam is mixed to a main cooling steam having a main cooling temperature and a main cooling pressure and flows into a cooling inlet opening of the steam turbine.
  • cooling according to the invention By removing the cooling steam from the steam generator can be dispensed with a separate, complex cooling circuit.
  • the cooling according to the invention is therefore easy to implement.
  • the proposed solution according to the invention can therefore be retrofitted with little effort into existing facilities.
  • An essential aspect of the invention is that the cooling steam is taken at several points of a steam cycle.
  • An at least first cooling steam can be taken between a separator and a superheater of the steam generator. Alternatively, a removal from a superheater collector of the steam generator between individual superheater elements is possible.
  • the first cooling steam in this case has a first temperature and a first pressure. Further cooling vapors can be taken between further superheaters of the steam generator.
  • a second cooling steam is added to this first cooling steam or optionally first and further cooling vapors.
  • the main cooling steam thus produced has a main cooling temperature and a main cooling pressure flowing through a cooling inlet opening into the steam turbine. The main cooling temperatures and the main cooling pressure are dependent on the mixing ratio of the first cooling steam with the optionally further cooling vapors and the second cooling steam.
  • the pressure difference between the main cooling steam and the live steam can correspond approximately to the pressure loss of the bypassed superheater elements.
  • the pressure of the cooling steam is about 1 to 10 bar, in particular about 2 to 7 bar higher than the pressure of the live steam.
  • the temperature of the cooling steam is lower in this embodiment according to the number of bypassed superheater elements as the temperature of the live steam. As a result, a cooling steam at a lower temperature and greater pressure than the live steam is reliably provided.
  • the temperature of the main cooling steam may be, for example, between about 350 ° C to 500 ° C.
  • the main cooling steam enters through a passage opening in an area in front of the balancing piston of the high-pressure turbine part. From there it flows over the piston area provided with sealing tips, which is also referred to as piston leakage steam. In this case, only so much main cooling steam is fed that likewise a portion of the live steam flows over the piston, which is also referred to by the term mangle mixture. This ensures that, in contrast to excess cooling, firstly no main cooling steam enters the main flow and, secondly, a moderate temperature gradient occurs in the main components.
  • the area in front of the balance piston is designed as a mixing area in which the cooling steam is mixed with the live steam before it enters the piston.
  • the main cooling steam is passed through the outer housing before entering all passage openings. This guidance of the main cooling steam cools the outer housing, the inner housing outside and in the piston area and the rotor in the piston area.
  • An essential aspect of the invention is that a suitable temperature control and for the reduction of load changes due to temperature changes during transient operation mixing of the cooling medium from different steam conditions prior to its entry into the high-pressure turbine part is possible.
  • the task of the mixture is firstly to provide a main cooling steam with a temperature suitable for the operating state and the component of the steam turbine to be cooled.
  • a temperature suitable for the operating state and the component of the steam turbine should not be colder than the main components when starting the main cooling steam.
  • the maximum permissible temperature of the Main cooling steam to be limited.
  • differential temperatures between the component and the main cooling steam should be maintained within permitted limits.
  • a corresponding temperature level should be set.
  • the main cooling steam is to be provided, with which a rapid cooling is possible while maintaining permissible exemption limits.
  • the inventive provision of the main cooling steam temperature jumps, as they arise by switching from one coolant source to another, avoided.
  • Suitable sampling points are especially before entering the upstream part of the turbine superheater parts of the steam generator, after exiting the steam generator z. B. in the live steam collector or in the main steam line before or from the main steam valve and before entering the steam generator at all.
  • increased pressure of the main cooling steam acts this supporting on the inner casing of the high-pressure turbine part, which is advantageous for the design of the inner casing screw connection.
  • the second cooling steam can be removed from a second region of the steam generator.
  • the second cooling steam can be removed from a live steam line connected to a live steam opening of the steam turbine.
  • the main cooling steam can have a main cooling temperature and a main cooling pressure which in a maximum case corresponds to the live steam temperature and the live steam pressure and, in a minimal case, to the first temperature and the first pressure of the first cooling steam.
  • the main cooling temperature and the main cooling pressure are adjusted by changing the flow of the at least first and the second cooling steam.
  • Another aspect of the invention is to regulate the flow parameters of the at least first cooling steam and the second cooling steam via a control unit.
  • the object is likewise achieved by a steam turbine plant, the steam turbine plant having at least one steam turbine and a condenser fluidically connected to the steam turbine, wherein the condenser is fluidically connected to at least one feedwater pump, wherein a steam generator is fluidically arranged between the feedwater pump and the steam turbine such a closed water-steam cycle is formed, wherein the steam generator is designed to generate live steam at a live steam temperature and a live steam pressure and this live steam flows through a live steam line into a live steam inlet opening into the steam turbine, the steam turbine having a cooling inlet opening , which is designed such that a main cooling steam flowing through the cooling inlet opening thermally stressed components of the steam turbine cools, wherein the water-steam cycle at least a first Au slass for a first temperature and a first pressure having first cooling steam and a second outlet for a second temperature and a second pressure having second cooling steam, wherein a mixing device for mixing the at least first cooling steam with the second cooling steam with the main cooling steam is provided.
  • One advantage of the invention is, inter alia, that the main cooling steam through the mixing device can assume a variable temperature range and the main cooling pressure can also assume a variable range.
  • the guidance and use of a main cooling steam is improved, in particular with regard to stresses in transient operation of the steam turbine plant. Both cold-start and warm-start processes are considered, in which the new solution achieves a reduction of the occurring stresses and in some cases the start-up times. With the invention, less expensive materials can be used in the currently used parameters of live steam.
  • the outlet for the at least first cooling steam and the second cooling steam is provided in the region of the steam generator.
  • the outlet for the at least first cooling steam can be provided in the region of the steam generator and the outlet for the second cooling steam can be provided in the region of the live steam line.
  • outlets for the at least first cooling steam and the second cooling steam may be provided in a superheater part of the steam generator.
  • the outlet for the second cooling steam may be provided in the region of the main steam line.
  • One aspect of the invention is that, depending on the embodiment of the steam generator, a suitable location can be found to obtain a first or second or more cooling vapors.
  • the at least first and second outlet is fluidly connected via an at least first or second line to a main cooling steam line and the main cooling steam line connected to the cooling inlet opening.
  • a first valve is taken into account for adjusting the flow of the at least first cooling steam in the at least first line and a second valve for adjusting the second cooling steam in the second line.
  • the at least first valve and the second valve are connected to a control unit, wherein the control unit is designed to control flow parameters of the at least first cooling steam and the second cooling steam.
  • the control unit is designed to control flow parameters of the at least first cooling steam and the second cooling steam.
  • a controlled removal of cooling steam from the steam generator is provided for the first time in terms of temperature and pressure, wherein the temperature of the cooling steam is smaller and the pressure is greater than that of the live steam. It is thus a simple cooling allows, in particular a very efficient cooling of the piston provided for thrust balance.
  • FIG. 1 schematically shows a steam turbine plant with a steam turbine 1.
  • the steam turbine 1 has a high-pressure turbine section 2, a medium-pressure turbine section 3 and a low-pressure turbine section 4.
  • the steam turbine plant shown in FIG. 1 represents a plant according to the prior art.
  • the steam turbine plant is designed with a shaft train 5.
  • the shaft train 5 is connected to a generator 6.
  • the generator 6 is designed to generate electrical energy.
  • a coupling to the electrical supply network is not shown in detail.
  • the high-pressure turbine part 2 has a live steam inlet opening 7. Through this live steam inlet opening 7, a live steam flows into the high-pressure turbine part 2.
  • the live steam inlet opening 7 is connected to a main steam line 8, in which a main valve 9 is arranged.
  • the main valve 9 controls the flow of live steam through the main steam line 8 in the high-pressure turbine section 2.
  • the live steam flows through a blading of the high-pressure turbine section 2 and then flows out of the high-pressure turbine section 2 out into a reheater 10.
  • the low-pressure turbine section 4 the steam is then continue to relax and cool.
  • the steam, which has been expanded and cooled to a comparatively low temperature and low pressure then flows via an exhaust steam line 12 into a condenser 13. In the condenser 13, the steam condenses again to water.
  • a feedwater pump 14 the water is pumped to a preheater 15.
  • the water is heated and conveyed to the steam generator 16.
  • the steam generator 16 the water in various heating surfaces and superheater parts 17, 18, 19, 20, 21, 22 is converted into steam or the steam temperature is increased gradually.
  • FIG. 2 shows an embodiment of a steam turbine plant according to the invention.
  • the steam turbine plant has a first line 23, in which a first valve 24 is arranged. Furthermore, the steam turbine plant has a second line 25, in which a second valve 26 is arranged.
  • the first line 23 and the second line 25 are fluidically connected to a common line 27.
  • This common line 27 flows through another valve 28 and is then connected to a third line 29, in which a third valve 30 is arranged.
  • the third line 29 is fluidically connected to the main steam line 8.
  • the first cooling steam is mixed with the second cooling steam to form a main cooling steam.
  • the main cooling steam flows via a main cooling line 32 into a cooling inlet opening 33 in the high-pressure part turbine 2.
  • the first cooling steam can be taken from a collector 19 here.
  • Another cooling steam can be removed from another collector 18.
  • the temperature and the pressure of the cooling steam flowing in the common line 27 can be adjusted by the valves 24 and 26.
  • the temperature of the main cooling steam is adjusted via the valves 28 and 30.
  • FIG. 3 shows a further embodiment of the steam turbine plant.
  • the second cooling steam is not taken from the main steam line 8 but from a third header 17 of the steam generator 16.
  • the third header 17 is the third via a line 34, in which a fourth valve 35 is arranged, fluidly connected to the first cooling steam.
  • a further mixing device 36 is designed such that the at least first cooling steam is mixed with the second cooling steam and flows via the main cooling steam line 32 into the cooling inlet opening 33.
  • FIG. 2 as well as FIG. 3 take account of control units not shown in more detail, which are designed in such a way that the flow parameters, in particular the flow rate of the cooling vapors, can be regulated.
  • FIG. 4 shows a high-pressure turbine part 2.
  • the high-pressure turbine part 2 has an outer housing 37. Within the outer housing 37, an inner housing 38 is arranged. Within the inner housing 38, a rotor 39 is rotatably mounted. On the rotor 39 blades are arranged.
  • the main cooling steam flows in via the cooling inlet opening 33.
  • the main cooling steam spreads in this space 40 and flows via a bore 41 into a region 42 in front of a thrust balance piston 43.
  • Fresh steam flows into the high-pressure turbine part 2 via an inlet 44.
  • the thrust balance piston 43 is cooled by the main cooling steam.
  • the main cooling steam flows through a number of holes 41 in the region 42 to ensure a uniform temperature distribution.
  • the inflow of the main cooling steam should be controlled by suitable valves that meet safety requirements. Quick closing and adjusting operations of the valve 9 require corresponding operations for the valves 24, 26, 28. It is to ensure control technology that in case of failure of the main cooling steam, the operation of the steam turbine 1 is interrupted.
  • the temperature of the main cooling steam is to be determined and supervised such that a premature condensation or droplet formation in the flow even at partial loads is excluded and that overheating of the components, in particular of the rotor 39 and the inner housing 38 for all relevant load cases is also excluded.
  • valves 24, 26, 28, 30, 35 can be adjusted such that at partial loads an over- or under-proportional amount of main cooling steam is introduced.
  • the cooling system can also be advantageously used for preheating purposes by feeding suitable medium during the starting process. This can also be taken from other points of the water-steam circuit than the later actual main cooling steam. Likewise, this process could be used for rapid cooling.
EP04030350A 2004-12-21 2004-12-21 Procédé de refroidissement de turbine à vapeur Withdrawn EP1674669A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP04030350A EP1674669A1 (fr) 2004-12-21 2004-12-21 Procédé de refroidissement de turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP04030350A EP1674669A1 (fr) 2004-12-21 2004-12-21 Procédé de refroidissement de turbine à vapeur

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EP1674669A1 true EP1674669A1 (fr) 2006-06-28

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1911933A1 (fr) * 2006-10-09 2008-04-16 Siemens Aktiengesellschaft Rotor pour une turbomachine
WO2008104465A2 (fr) * 2007-02-26 2008-09-04 Siemens Aktiengesellschaft Procédé de fonctionnement d'une turbine à vapeur à plusieurs étages
EP2067933A3 (fr) * 2007-08-31 2011-01-05 Siemens Aktiengesellschaft Concept de sécurité pour une turbine à vapeur
EP2412937A1 (fr) * 2010-07-30 2012-02-01 Siemens Aktiengesellschaft Turbine à vapeur et procédé de refroidissement de celle-ci
US9677414B2 (en) 2011-06-27 2017-06-13 Ihi Corporation Waste heat power generator

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54153904A (en) * 1978-05-26 1979-12-04 Hitachi Ltd Cooling mechanism for rotor of reheated steam turbine plant
JPS5510058A (en) * 1978-07-10 1980-01-24 Hitachi Ltd Revolution-shaft cooling method for high pressure turbine
JPH01190903A (ja) * 1988-01-25 1989-08-01 Hitachi Ltd 蒸気タービンのクーリング蒸気温度制御装置
JPH09317405A (ja) * 1996-05-29 1997-12-09 Toshiba Corp 蒸気タービンの高圧初段動翼植込部の冷却装置
EP1154123A1 (fr) * 2000-05-10 2001-11-14 Siemens Aktiengesellschaft Procédé de refroidissement pour l'arbre d'une turbine à vapeur à haute pression

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS54153904A (en) * 1978-05-26 1979-12-04 Hitachi Ltd Cooling mechanism for rotor of reheated steam turbine plant
JPS5510058A (en) * 1978-07-10 1980-01-24 Hitachi Ltd Revolution-shaft cooling method for high pressure turbine
JPH01190903A (ja) * 1988-01-25 1989-08-01 Hitachi Ltd 蒸気タービンのクーリング蒸気温度制御装置
JPH09317405A (ja) * 1996-05-29 1997-12-09 Toshiba Corp 蒸気タービンの高圧初段動翼植込部の冷却装置
EP1154123A1 (fr) * 2000-05-10 2001-11-14 Siemens Aktiengesellschaft Procédé de refroidissement pour l'arbre d'une turbine à vapeur à haute pression

Non-Patent Citations (4)

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Title
PATENT ABSTRACTS OF JAPAN vol. 004, no. 017 (M - 091) 9 February 1980 (1980-02-09) *
PATENT ABSTRACTS OF JAPAN vol. 004, no. 037 (M - 004) 27 March 1980 (1980-03-27) *
PATENT ABSTRACTS OF JAPAN vol. 013, no. 484 (M - 886) 2 November 1989 (1989-11-02) *
PATENT ABSTRACTS OF JAPAN vol. 1998, no. 04 31 March 1998 (1998-03-31) *

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008043663A1 (fr) * 2006-10-09 2008-04-17 Siemens Aktiengesellschaft Rotor pour une turbomachine
EP1911933A1 (fr) * 2006-10-09 2008-04-16 Siemens Aktiengesellschaft Rotor pour une turbomachine
CN101622424B (zh) * 2007-02-26 2013-06-19 西门子公司 用于运行多级的蒸汽涡轮机的方法
WO2008104465A2 (fr) * 2007-02-26 2008-09-04 Siemens Aktiengesellschaft Procédé de fonctionnement d'une turbine à vapeur à plusieurs étages
EP1998014A2 (fr) * 2007-02-26 2008-12-03 Siemens Aktiengesellschaft Procédé destiné au fonctionnement d'une turbine à vapeur multiple
EP1998014A3 (fr) * 2007-02-26 2008-12-31 Siemens Aktiengesellschaft Procédé destiné au fonctionnement d'une turbine à vapeur multiple
WO2008104465A3 (fr) * 2007-02-26 2009-01-29 Siemens Ag Procédé de fonctionnement d'une turbine à vapeur à plusieurs étages
US8713941B2 (en) 2007-02-26 2014-05-06 Siemens Aktiengesellschaft Method for operating a multi-step steam turbine
EP2067933A3 (fr) * 2007-08-31 2011-01-05 Siemens Aktiengesellschaft Concept de sécurité pour une turbine à vapeur
CN103052768A (zh) * 2010-07-30 2013-04-17 西门子公司 蒸汽轮机以及用于冷却这种蒸汽轮机的方法
WO2012013531A1 (fr) * 2010-07-30 2012-02-02 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour refroidir une turbine à vapeur
EP2412937A1 (fr) * 2010-07-30 2012-02-01 Siemens Aktiengesellschaft Turbine à vapeur et procédé de refroidissement de celle-ci
US9677414B2 (en) 2011-06-27 2017-06-13 Ihi Corporation Waste heat power generator

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