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EP1945911B1 - Turbine à gaz - Google Patents

Turbine à gaz Download PDF

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Publication number
EP1945911B1
EP1945911B1 EP06819128A EP06819128A EP1945911B1 EP 1945911 B1 EP1945911 B1 EP 1945911B1 EP 06819128 A EP06819128 A EP 06819128A EP 06819128 A EP06819128 A EP 06819128A EP 1945911 B1 EP1945911 B1 EP 1945911B1
Authority
EP
European Patent Office
Prior art keywords
steam
turbine
line
steam turbine
cooling
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.)
Not-in-force
Application number
EP06819128A
Other languages
German (de)
English (en)
Other versions
EP1945911A1 (fr
Inventor
Kai 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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP06819128A priority Critical patent/EP1945911B1/fr
Priority to PL06819128T priority patent/PL1945911T3/pl
Publication of EP1945911A1 publication Critical patent/EP1945911A1/fr
Application granted granted Critical
Publication of EP1945911B1 publication Critical patent/EP1945911B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • 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
    • F01D5/085—Heating, heat-insulating or cooling means cooling fluid circulating inside the rotor
    • 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
    • F01D25/12—Cooling
    • 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
    • F01D25/24—Casings; Casing parts, e.g. diaphragms, casing fastenings
    • 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
    • F01D3/04—Machines or engines with axial-thrust balancing effected by working-fluid axial thrust being compensated by thrust-balancing dummy piston or the like
    • 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 steam turbine having a housing, wherein a turbine shaft having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe for guiding Has cooling steam in the direction of the axis of rotation and the cooling line is connected to at least one inflow line for the inflow of cooling steam from the flow channel in the cooling line.
  • a steam turbine is understood to mean any turbine or sub-turbine through which a working medium in the form of steam flows.
  • gas turbines are traversed with gas and / or air as the working medium, which, however, is subject to completely different temperature and pressure conditions than the steam in a steam turbine.
  • gas turbines has steam turbines z. As the one part turbine incoming working fluid with the highest temperature at the same time the highest pressure. An open cooling system, as in gas turbines, is therefore not feasible without external supply.
  • a steam turbine typically includes a vaned rotatably mounted rotor disposed within a casing shell. When flowing through the flow space formed by the housing jacket with heated and pressurized steam, the rotor passes through the blades set the steam in rotation.
  • the rotor-mounted blades are also referred to as blades.
  • usually stationary guide vanes are mounted on the housing jacket, which engage in the intermediate spaces of the moving blades.
  • a vane is typically held at a first location along an interior of the steam turbine casing. In this case, it is usually part of a vane ring, which comprises a number of vanes, which are arranged along an inner circumference on the inside of the steam turbine housing. Each vane has its blade radially inward.
  • a vane ring at a location along the axial extent is also referred to as a vane row. Usually, a number of vane rows are arranged one behind the other.
  • the steam turbine shafts which are rotatably mounted in the steam turbines, are subjected to a great deal of thermal stress during operation.
  • the development and production of a steam turbine shaft is both expensive and time consuming.
  • Steam turbine shafts are considered to be the most stressed and expensive components of a steam turbine. This increasingly applies to high steam temperatures.
  • steam turbines in contrast to the gas turbine, have no compressor unit and, moreover, the shafts of the steam turbine are generally accessible only radially.
  • Piston area is to be understood as the area of a thrust balance piston.
  • the thrust balance piston acts in a steam turbine such that caused by the working fluid force the shaft is formed in one direction a counter force in the opposite direction.
  • a cooling of a steam turbine shaft is inter alia in the EP 0 991 850 B1 described.
  • a compact or high-pressure and medium-pressure turbine part is performed by a compound in the shaft through which a cooling medium can flow.
  • a disadvantage here is felt that between two different expansion sections no controllable bypass can be formed.
  • problems in transient operation are possible.
  • the object of the invention is therefore to provide a steam turbine, which can be operated at high steam temperatures.
  • a steam turbine with a housing, wherein a turbine piston having a thrust balance piston rotatably mounted within the housing and directed along a rotation axis, wherein a flow channel between the housing and the turbine shaft is formed, wherein the turbine shaft in its interior a cooling pipe to Having leadership of cooling steam in the direction of the axis of rotation and the cooling line on the one hand at least one inflow line is connected to the inflow of cooling steam from the flow channel into the cooling line, the cooling line being connected to at least one outflow line for guiding cooling steam to a thrust-compensating piston skirt surface, the steam turbine having a return line for returning a mixed vapor formed from the cooling steam and a compensation piston leakage, formed, wherein the return flows into the flow channel.
  • a steam turbine with a steam turbine shaft which is in each case hollow in the hot during operation and is provided with an internal cooling.
  • the invention is based on the aspect that during operation expanded steam is guided through the shaft interior to the balance piston and there cools the highly stressed compensation piston.
  • the proposed cooling option especially those steam turbine shafts can be cooled, which have a balance piston.
  • a K partial turbine is to be understood as meaning a compact partial turbine which has a high-pressure and medium-pressure region located on a steam turbine shaft.
  • the advantage of the invention is to be seen, inter alia, that the steam turbine shaft can be formed on the one hand creep stable and on the other hand reacts flexibly to thermal loads. For example, during a load change in which a higher thermal load can occur, the cooling causes the thermal load of the shaft to eventually decrease. This is especially true for the areas that are particularly thermally stressed, such. B. the inflow or the balance piston.
  • the invention is based on the aspect that the cooling steam is mixed with a compensation piston leakage steam and this mixed steam is again supplied to the flow channel to continue to work there.
  • the efficiency of the steam turbine thereby increases.
  • a hollow steam turbine shaft has a lower mass compared to a solid shaft and thus also a lower heat capacity a solid shaft and a larger flowed surface. As a result, a rapid warm-up of the steam turbine shaft is possible.
  • Another aspect of the invention is that the creep strength of the material used for the steam turbine shaft is increased by the improved cooling.
  • the creep rupture strength can be increased by a factor greater than 2 compared to a solid shaft, so that the above-described voltage increase is overcompensated. This leads to an extension of the field of application of the steam turbine shaft.
  • the radial clearance can be reduced by the diameter of the hollow shaft is increased by radial centrifugal forces.
  • the radial centrifugal force is proportional to the square of the speed. An increase in the speed thus causes a reduction of radial play, which leads to an increase in the overall efficiency of the steam turbine.
  • Another aspect of the invention is that hollow shafts can be produced inexpensively.
  • the housing comprises an inner housing and an outer housing.
  • High-pressure turbine sections as well as medium-pressure and compact turbine sections are among the most thermally stable steam turbines.
  • high-pressure, medium-pressure and compact turbine sections with an inner housing are arranged on the vanes and formed around the inner housing arranged outer housing.
  • the turbine shaft has at least two regions made of different materials in the axial direction.
  • thermally stressed areas is usually high quality material used.
  • 10% chromium steel can be used in the thermally stressed areas.
  • 1% chromium steel can be used in the areas of low thermal stress 1% chromium steel.
  • the turbine shaft has three regions of different materials in the axial direction.
  • the two outer regions are made of the same material.
  • targeted material can be selected for the respective area of the steam turbine shaft of different thermal load.
  • the areas comprising different materials are welded together.
  • the welding creates a stable turbine shaft.
  • the regions consisting of different materials are connected to one another by means of a Hirth toothing.
  • the main advantage of the Hirth toothing is the particularly high thermal flexibility of the turbine shaft. Another advantage is that this usually leads to the turbine shaft can be made quickly.
  • the turbine shaft can be formed inexpensively.
  • the two outer regions are designed as a solid shaft and the intermediate region lying between them as a hollow shaft. It is equally advantageous if the regions consisting of different materials are connected to one another by means of a flange connection. This can be helpful during revision work because the different areas can be easily separated from each other.
  • the areas comprising different materials are welded together by at least one weld.
  • the inflow line and the outflow line are integrated in the Hirth toothing.
  • the Hirth toothing which may have a trapezoidal, rectangular or triangular toothing, be made with a recess formed as an inflow and / or outflow line.
  • This has a very easy way to form an inflow and / or outflow line.
  • the recess in the trapezoidal, rectangular or triangular toothing can be adapted depending on the calculated passage volume of the cooling steam.
  • the production of such recesses on a Hirth toothing is relatively simple and can also be carried out quickly. This results in cost advantages.
  • the return line is arranged within the outer housing.
  • the return line can also be designed as a bore in the inner housing.
  • FIG. 1 is a section through a high-pressure turbine part 1 according to the prior art shown.
  • the high-pressure turbine part 1 as an embodiment of a steam turbine comprises an outer housing 2 and an inner housing 3 arranged therein.
  • a turbine shaft 5 is rotatably mounted about an axis of rotation 6.
  • the turbine shaft 5 includes blades 7 disposed in grooves on a surface of the turbine shaft 5.
  • the inner case 3 has guide vanes 8 arranged in grooves on its inner surface.
  • the guide 8 and blades 7 are arranged such that in a flow direction 13, a flow channel 9 is formed.
  • the high-pressure turbine section 1 has an inflow region 10, through which live steam flows into the high-pressure turbine section 1 during operation.
  • the live steam may have steam parameters above 300 bar and above 620 ° C.
  • the relaxing in the flow direction 13 live steam flows alternately past the guide 8 and blades 7, relaxes and cools down.
  • the steam loses in this case to internal energy, which is converted into rotational energy of the turbine shaft 5.
  • the rotation of the turbine shaft 5 finally drives a generator, not shown, for power supply.
  • the high pressure turbine part 1 may drive other plant components other than a generator, such as a compressor, a propeller, or the like.
  • the steam flows through the flow channel 9 and flows out of the high-pressure turbine section 1 from the outlet 33.
  • the steam exerts an action force 11 in the flow direction 13. The result is that the turbine shaft 4 would perform a movement in the flow direction 13.
  • FIG. 2 a section of a steam turbine 1 is shown.
  • the steam turbine has an outer casing 2, an inner casing 3 and a turbine shaft 5.
  • the steam turbine 1 has moving blades 7 and guide vanes 8. live steam passes through the inflow region 10 via a diagonal stage 15 in the flow channel 9. The steam relaxes and cools down. The internal energy of the steam is converted into rotational energy of the turbine shaft 5.
  • the cooling line 17 is in this case formed as a cavity within the turbine shaft 5.
  • Other embodiments are conceivable. So z. Example, instead of a cavity 17 form a line, not shown, within the turbine shaft 5.
  • the turbine shaft 5 is rotatably mounted within the housing 2, 3 and directed along a rotation axis 6. Between the housing 2, 3 and the turbine shaft 5, a flow channel 9 is formed.
  • the cooling line 17 is in this case designed to guide cooling steam in the direction of the axis of rotation 6.
  • the cooling line 17 is on the one hand fluidly connected to at least one inflow line 16.
  • the inflow line 16 is designed for the inflow of cooling steam from the flow channel 9 into the cooling line 17.
  • the inflow line 16 may in this case be aligned radially with respect to the axis of rotation 6.
  • Other embodiments of the inflow line 16 are conceivable.
  • the inflow line 16 can be designed to be inclined perpendicular to the axis of rotation 6.
  • the cooling line 16 could run in a spiral shape from the flow channel 9 to the cooling line 17.
  • the cross section of the cooling line 16 can vary from the flow channel 9 to the cooling line 17.
  • the cooling line 17 is connected to at least one outflow line 18 for guiding the cooling steam onto a thrust balance piston skirt surface 19.
  • the effluent from the discharge line 18 cooling steam is distributed on the thrust balance piston skirt surface 19 and cools this off.
  • the housing 2, 3 comprises an inner housing 3 and an outer housing 2.
  • the cooling steam flowing out of the discharge line 18 flows in two directions. On the one hand in the direction of the main flow direction 13 and the other in one of the main flow 13 opposite direction.
  • a portion of the live steam flows via the inflow region 10 between the inner casing 3 and the turbine shaft 5 in the direction of the thrust balance piston 4.
  • This so-called piston leakage steam 20 mixes with the cooling steam flowing out of the outflow line and is returned to the flow channel 9 by means of a return line 21. It makes sense that this return line 21 begins between inflow 10 and the outlet of the discharge line 18.
  • a partial flow of the cooling steam can be directed in the direction of the main flow 13 and lock the piston leakage 20. In this way, the above-described cooling of the piston surface 18 is ensured.
  • This mixed steam formed from the cooling steam and a compensating piston leakage steam is flowed in at a suitable point in the flow channel 9 in order to perform work there.
  • the return line 21 may be formed as an external line within the outer housing 2.
  • the return line 21 may also be formed as a bore within the inner housing 3.
  • FIG. 3 a turbine shaft 5 is shown.
  • the turbine shaft 5 is made of a material that takes into account the thermal stresses.
  • the turbine shaft 5 is formed of a material.
  • FIG. 4 a further turbine shaft 5 is shown, wherein this turbine shaft 5 in the flow direction 13 has at least two regions made of different materials.
  • the turbine shaft 5 in the axial flow direction 13 may comprise three regions 24, 23, 22 made of different materials.
  • the central region 22 may for example be made of a temperature-resistant 10% chromium steel and the two outer regions 23 and 24 made of the same material such. B. 1% chromium steel.
  • the turbine shaft 5 is connected by means of welded joints 25 and 26.
  • the turbine shaft 5 can be designed as a hollow shaft in its central region 22 and in its outer regions 23, 24 as a solid shaft.
  • the turbine shaft 5 can be made of different materials existing areas 22, 23, 24 by means of a flange 40 with each other, wherein the inflow line 16 and the discharge line 18 is integrated in the flange connection.
  • FIG. 5 an alternative embodiment of the turbine shaft 5 is shown.
  • the difference to the in FIG. 4 shown turbine shaft is that in FIG. 5 shown turbine shaft 5 is composed by means of a Hirth toothing 27, 28.
  • a tie rod 29 must be formed, which is arranged such that the two outer regions 23 and 24 are pressed against the central region 22.
  • the central region 22 comprises one or more sections which are tubular or disk-shaped are and each may contain one or more blade stages:
  • the turbine shaft 5 by means of a Hirth toothing 30, 31 connected to each other, wherein the inflow line 16 and the discharge line 18 in the Hirth toothing 30, 31 is integrated.
  • FIG. 7 a further alternative embodiment of the turbine shaft 5 is shown.
  • the turbine shaft 5 comprises at least two regions 22 'and 23' formed of different materials.
  • the area 23 ' is flanged to the area 22'.
  • the screwing takes place by means of suitable expansion shank bolts 39.
  • the flange connection 40 is centered according to the prior art.
  • a thread 41 for grasping the screw 39 is formed in the region 22 '.
  • the screwing of the region 23 'with the region 22' preferably takes place from the cooler side.
  • FIG. 8 is a sectional view of the bolted connection from the FIG. 7 to see. It can also be seen in this illustration that the discharge line 18 integrates into the connection through recesses. This is in a perspective view of a part of the turbine shaft 5 in the FIG. 5 shown.
  • FIG. 10 is a perspective view of a Hirth toothing 30, 31 to see.
  • the middle region 2 in this case has one according to FIG. 10 illustrated Hirth toothing 30, 31 on.
  • the two outer regions 24 and 23 made of different materials likewise have a Hirth toothing 30, 31.
  • FIG. 11 is a cross-sectional view of the Hirth serration 30, 31 can be seen.
  • the left part is, for example, the left region 24 and the right part of the central region 22 is connected to one another via the Hirth toothing 30.
  • the inflow line 16 is integrated in the Hirth toothing.
  • FIG. 11 illustrated cross-sectional illustration may also represent the discharge line 18.
  • the left-hand region would be the middle region 22 and the right-hand region 23 connected via the Hirth toothing 31.
  • the outflow line 18 is integrated in the Hirth toothing 30, 31.
  • In the FIG. 11 illustrated embodiment has a triangular toothing.
  • the inflow line 16 or the outflow line 18 is formed via recesses 32 of the Hirth toothing 30, 31.
  • Possible embodiments of the Hirth toothing are a trapezoidal, rectangular or triangular toothing. Other embodiments are possible.
  • the temperature is plotted in a linear scale of 400 to 600 ° C.
  • the creep rupture strength R m is 200,000 h in a linear scale of 30 to 530 N mm 2 applied.
  • the upper curve 37 shows the temperature behavior for the material 30 CrMoNiV5-11 and the lower curve 38 shows the temperature behavior for the material X12CrMoWVNbN10-1-1.
  • the invention is not limited to the formation of a high-pressure turbine section as an embodiment of a steam turbine 1, the turbine shaft 5 according to the invention can also be used in a medium-pressure or a compact turbine section (high pressure and medium pressure within a housing). Likewise, the turbine shaft 5 can be used in other types of steam turbine.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Organic Low-Molecular-Weight Compounds And Preparation Thereof (AREA)

Claims (14)

  1. Turbine ( 1 ) à vapeur comprenant un carter ( 2, 3 ),
    dans laquelle un arbre ( 5 ) de turbine ayant un piston ( 4 ) de compensation de la poussée est monté tournant dans le carter ( 2, 3 ) et est dirigé le long d'un axe ( 6 ) de révolution,
    dans laquelle un canal ( 9 ) d'écoulement est formé entre le carter ( 2, 3 ) et l'arbre ( 5 ) de la turbine,
    dans laquelle l'arbre ( 5 ) de la turbine a à l'intérieur un conduit ( 17 ) de refroidissement pour faire passer de la vapeur de refroidissement dans la direction de l'axe ( 6 ) de révolution et le conduit ( 17 ) de refroidissement communique, d'une part, avec au moins un conduit ( 16 ) d'entrée pour faire entrer de la vapeur de refroidissement d'un canal ( 9 ) d'écoulement dans le conduit ( 17 ) de refroidissement dans laquelle,
    le conduit ( 17 ) de refroidissement communique, d'autre part, avec au moins un conduit ( 18 ) de dérivation pour faire passer de la vapeur de refroidissement sur une surface ( 19 ) latérale du piston de compensation de la poussée,
    caractérisé par
    un conduit ( 21 ) de retour pour retourner une vapeur mixte formée de la vapeur de refroidissement sortant du conduit ( 18 ) d'évacuation et d'une partie d'une vapeur fraîche qui passe, comme vapeur de fluide du piston de compensation, entre le carter ( 2, 3 ) et l'arbre ( 5 ) de la turbine dans la direction du piston ( 4 ) de compensation de la poussée,
    le conduit ( 21 ) de retour débouchant dans le canal ( 9 ) d'écoulement.
  2. Turbine ( 1 ) à vapeur suivant la revendication 1,
    dans laquelle le carter ( 2, 3 ) comprend un carter ( 3 ) intérieur et un carter ( 2 ) extérieur.
  3. Turbine ( 1 ) à vapeur suivant l'une des revendications 1 ou 2,
    dans laquelle l'arbre ( 5 ) de la turbine a, dans la direction ( 34 ) axiale, au moins deux parties en des matériaux différents.
  4. Turbine ( 1 ) à vapeur suivant la revendication 1, 2 ou 3,
    dans laquelle l'arbre ( 5 ) de la turbine a, dans la direction ( 34 ) axiale, trois parties ( 22, 23, 24 ) en des matériaux différents.
  5. Turbine ( 1 ) à vapeur suivant la revendication 4,
    dans laquelle les deux parties ( 23, 24 ) extérieures sont en le même matériau.
  6. Turbine ( 1 ) à vapeur suivant la revendication 3, 4 ou 5,
    dans laquelle les parties comprenant des matériaux ( 22, 23, 24 ) différents sont soudées entre elles.
  7. Turbine ( 1 ) à vapeur suivant la revendication 3, 4, 5 ou 6,
    dans laquelle les parties ( 23, 24 ) sont constituées sous la forme d'un arbre plein et la partie ( 22 ) sous la forme d'un arbre creux.
  8. Turbine ( 1 ) à vapeur suivant la revendication 3, 4, 5 ou 7,
    dans laquelle les parties en des matériaux ( 22, 23, 24 ) différents sont assemblées entre elles au moyen d'un crantage ( 30, 31 ) de Hirth.
  9. Turbine ( 1 ) à vapeur suivant la revendication 3, 4, 5 ou 7,
    dans laquelle les parties en des matériaux ( 22, 23, 24 ) différents sont assemblées entre elles au moyen d'un bridage ( 40 ).
  10. Turbine ( 1 ) à vapeur suivant la revendication 8,
    dans laquelle le conduit ( 16 ) d'entrée et le conduit ( 18 ) d'évacuation sont intégrés dans un crantage ( 30, 31 ) de Hirth.
  11. Turbine ( 1 ) à vapeur suivant la revendication 9,
    dans laquelle le conduit ( 16 ) d'entrée et le conduit ( 18 ) d'évacuation sont intégrés dans le bridage ( 40 ).
  12. Turbine ( 1 ) à vapeur suivant la revendication 8,
    dans laquelle le crantage ( 30, 31 ) de Hirth a une denture trapézoïdale rectangulaire ou triangulaire ayant un évidement ( 32 ) formé en conduit ( 16 ) d'entrée et/ou en conduit ( 18 ) d'évacuation.
  13. Turbine ( 1 ) à vapeur suivant l'une des revendications précédentes,
    dans laquelle le conduit ( 21 ) de retour est disposé à l'intérieur du carter ( 2 ) extérieur.
  14. Turbine ( 1 ) à vapeur suivant l'une des revendications précédentes,
    dans laquelle le conduit ( 21 ) de retour est constitué sous la forme d'un trou dans le carter ( 2 ) intérieur.
EP06819128A 2005-10-31 2006-10-24 Turbine à gaz Not-in-force EP1945911B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06819128A EP1945911B1 (fr) 2005-10-31 2006-10-24 Turbine à gaz
PL06819128T PL1945911T3 (pl) 2005-10-31 2006-10-24 Turbina parowa

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP05023760A EP1780376A1 (fr) 2005-10-31 2005-10-31 Turbine à vapeur
EP06819128A EP1945911B1 (fr) 2005-10-31 2006-10-24 Turbine à gaz
PCT/EP2006/067717 WO2007051733A1 (fr) 2005-10-31 2006-10-24 Turbine à gaz

Publications (2)

Publication Number Publication Date
EP1945911A1 EP1945911A1 (fr) 2008-07-23
EP1945911B1 true EP1945911B1 (fr) 2009-12-02

Family

ID=35985854

Family Applications (2)

Application Number Title Priority Date Filing Date
EP05023760A Withdrawn EP1780376A1 (fr) 2005-10-31 2005-10-31 Turbine à vapeur
EP06819128A Not-in-force EP1945911B1 (fr) 2005-10-31 2006-10-24 Turbine à gaz

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP05023760A Withdrawn EP1780376A1 (fr) 2005-10-31 2005-10-31 Turbine à vapeur

Country Status (11)

Country Link
US (1) US8128341B2 (fr)
EP (2) EP1780376A1 (fr)
JP (1) JP4662570B2 (fr)
KR (1) KR101014151B1 (fr)
CN (1) CN101300405B (fr)
AT (1) ATE450693T1 (fr)
DE (1) DE502006005550D1 (fr)
ES (1) ES2336610T3 (fr)
PL (1) PL1945911T3 (fr)
RU (1) RU2410545C2 (fr)
WO (1) WO2007051733A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8128341B2 (en) 2005-10-31 2012-03-06 Siemens Aktiengesellschaft Steam turbine

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US8282349B2 (en) * 2008-03-07 2012-10-09 General Electric Company Steam turbine rotor and method of assembling the same
DE102008022966B4 (de) * 2008-05-09 2014-12-24 Siemens Aktiengesellschaft Rotationsmaschine
EP2211017A1 (fr) * 2009-01-27 2010-07-28 Siemens Aktiengesellschaft Rotor doté d'un espace creux pour une turbomachine
JP2011069307A (ja) * 2009-09-28 2011-04-07 Hitachi Ltd 蒸気タービンロータ、それを用いた蒸気タービン
EP2333239A1 (fr) 2009-12-08 2011-06-15 Alstom Technology Ltd Procédé de fabrication d'un rotor de turbine à vapeur et rotor associé
CN102695850B (zh) * 2009-12-21 2015-10-21 三菱日立电力系统株式会社 单流式涡轮机的冷却方法及装置
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RU2410545C2 (ru) 2011-01-27
CN101300405A (zh) 2008-11-05
CN101300405B (zh) 2013-05-29
DE502006005550D1 (de) 2010-01-14
KR101014151B1 (ko) 2011-02-14
US8128341B2 (en) 2012-03-06
EP1945911A1 (fr) 2008-07-23
EP1780376A1 (fr) 2007-05-02
US20090185895A1 (en) 2009-07-23
ATE450693T1 (de) 2009-12-15
JP2009513866A (ja) 2009-04-02
JP4662570B2 (ja) 2011-03-30
KR20080068893A (ko) 2008-07-24
PL1945911T3 (pl) 2010-05-31
WO2007051733A1 (fr) 2007-05-10
ES2336610T3 (es) 2010-04-14
RU2008121935A (ru) 2009-12-10

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