EP1774140B1 - Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur - Google Patents

Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur Download PDF

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Publication number
EP1774140B1
EP1774140B1 EP05769957A EP05769957A EP1774140B1 EP 1774140 B1 EP1774140 B1 EP 1774140B1 EP 05769957 A EP05769957 A EP 05769957A EP 05769957 A EP05769957 A EP 05769957A EP 1774140 B1 EP1774140 B1 EP 1774140B1
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EP
European Patent Office
Prior art keywords
steam
inner casing
rotor
balance piston
steam turbine
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
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EP05769957A
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German (de)
English (en)
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EP1774140A1 (fr
Inventor
Frank Deidewig
Yevgen Kostenko
Oliver Myschi
Michael Wechsung
Uwe Zander
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Siemens AG
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Siemens AG
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Priority to PL05769957T priority Critical patent/PL1774140T3/pl
Priority to EP05769957A priority patent/EP1774140B1/fr
Publication of EP1774140A1 publication Critical patent/EP1774140A1/fr
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Publication of EP1774140B1 publication Critical patent/EP1774140B1/fr
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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
    • 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

Definitions

  • the invention relates to a steam turbine with an outer housing and an inner housing, wherein the outer housing and the inner housing have a live steam supply channel, wherein a rotor having a thrust piston having a plurality of blades rotatably mounted within the inner housing, and the inner housing has a plurality of guide vanes arranged in such a way in that along a flow direction a flow channel with a plurality of blade stages, each having a row of blades and a row of vanes, is formed.
  • the invention further relates to a method for producing a steam turbine having an outer housing and an inner housing, wherein the outer housing and the inner housing have a live steam supply channel, wherein a rotor having a thrust balance piston comprising a plurality of rotor blades is rotatably mounted within the inner housing and on the inner housing a plurality of guide vanes such in that a flow channel is formed along a flow direction with a plurality of blade stages, each having a row of blades and a row of vanes, through which a vapor flows during operation.
  • 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.
  • An open cooling system that opens to the flow channel is, in gas turbines even without partial turbine external supply of cooling medium feasible.
  • an external supply for cooling medium should be provided. For this reason, the prior art relating to gas turbines can not be used for the assessment of the subject of the present application.
  • a steam turbine typically comprises a rotor-mounted rotatably mounted rotor disposed within a housing.
  • the rotor When flowing through the interior of the flow channel formed by the housing shell with heated and pressurized steam, the rotor is rotated by the vanes through the steam.
  • the blades of the rotor are also referred to as blades.
  • usually stationary guide vanes are suspended on the inner housing, which engage along an axial extent of the body in the interspaces of the rotor 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 stator blade row, which comprises a number of guide vanes, which are arranged along an inner circumference on the inside of the steam turbine housing.
  • Each vane has its blade radially inward.
  • a row of vanes at said first location along the axial extent is also referred to as a vane grille or crown.
  • a number of vane rows are connected in series. Accordingly, at a second location along the axial extent behind the first location, a further second blade is held along the inside of the steam turbine housing.
  • a pair of a vane row and a blade row is also referred to as a vane stage.
  • the housing jacket of such a steam turbine can be formed from a number of housing segments.
  • the stationary housing component of a steam turbine or a turbine part to understand that along the longitudinal direction of the steam turbine having an interior in the form of a flow channel, which is provided for the passage of the working medium in the form of vapor.
  • this can be an inner casing and / or a guide vane carrier.
  • it may also be provided a turbine housing, which has no inner housing or no guide vane.
  • Desirable is effective cooling in a steam turbine component, in particular for a steam turbine operated in the high temperature range.
  • the invention begins, whose object is a steam turbine and a method for their production, in which the steam turbine is cooled particularly effectively even in the high temperature range.
  • the object is achieved with an initially mentioned steam turbine with an outer housing and an inner housing, wherein the outer housing and the inner housing have a live steam supply channel, wherein a thrust balance piston having rotor comprising a plurality of rotor blades rotatably mounted within the inner housing, and the inner housing a plurality of vanes arranged such that along a flow direction, a flow channel having a plurality of blade stages, each having a row of blades and a row of vanes, is formed, wherein the inner housing has a connection, as a communicating tube between the flow channel after a blade stage and a Schubaus Dermavorraum between the thrust balance piston of the rotor and the inner housing is formed, wherein the inner housing has a cross-return passage, which acts as a communicating Röh is formed between a sealing space between the rotor and the inner housing and a arranged after a blade stage inflow space in the flow channel and wherein the cross-return passage away from the sealing space substantially perpen
  • connection comprises a return channel, which is designed as a communicating tube between a space between the inner housing and outer housing and the flow channel according to a blade stage.
  • the connection further comprises, in an advantageous embodiment, a supply channel formed as a communicating tube between the space between the inner housing and outer housing and a thrust balance piston antechamber between the thrust balance piston of the rotor and the inner housing.
  • the invention is based on the finding that flow medium, in this case steam, can be removed after a certain number of turbine stages and this expanded and cooled steam can be introduced into a thrust balance piston antechamber.
  • the invention is based on the idea that for steam turbines designed for the highest steam parameters, it is important to design both the rotor against high temperatures and housing parts, such as the inner housing or the outer housing and their screw connection for high temperatures and pressures.
  • the outer side of the inner housing, its screw and the inside of the outer housing undergoes a lower temperature.
  • other and possibly less expensive materials can be used for the outer housing as well as for the inner housing and their fittings. It is also conceivable that the outer housing can be made thinner.
  • the return channel and the supply channel are designed such that always steam flows from the flow channel in the thrust balance piston antechamber.
  • the thrust balance piston antechamber is arranged in an axial direction between thrust balance piston and inner housing.
  • the steam flowing into the thrust balance piston antechamber meets on the one hand the task of applying force to the thrust balance and on the other a cooling of the thrust balance piston, especially in high-pressure turbine sections, particularly thermally stressed.
  • the return channel and the supply channel are formed substantially perpendicular to the flow direction in the inner housing.
  • the space between the inner housing and the outer housing is in this case designed to connect the return channel to the supply channel.
  • Production-related aspects are in the foreground for this arrangement.
  • vertical alignment changes are avoided from housing to turbine axis, since the forced flow achieved by the space between the inner and outer outer housing uncontrolled formation of natural convection associated temperature stratification of the housings are avoided.
  • a steam flowing into the steam turbine flows for the most part through the flow channel.
  • a small part of the live steam does not flow through the flow channel, but through a sealing space which is arranged between the rotor and the inner housing.
  • This part of the steam is also referred to as leakage steam and leads to a loss of efficiency of the steam turbine.
  • This leakage steam which has approximately live steam temperature and live steam pressure, thermally stresses the rotor and the inner housing in the sealing space.
  • This hot and under high pressure sealing steam is passed through the cross-return passage from the sealing space through the inner housing back into the flow channel after a blade stage and expands below.
  • an overload introduction leading through the outer housing and inner housing opens in the influx room.
  • the return channel is connected to the flow channel after a recirculation vane stage and the cross recirculation channel is connected to the flow channel for a cross recirculation vane stage, the cross recirculation vane stage being located downstream of the recirculation vane stage in the flow channel flow direction.
  • the recycle vane stage is the fourth vane stage and the cross-return vane stage is the fifth vane stage.
  • the cross-return vane stage is the fifth vane stage.
  • the object directed to the method is achieved by a method for producing a steam turbine having an outer housing and an inner housing, wherein the outer housing and the inner housing have a live steam supply channel, wherein a rotor having a thrust balance piston and a plurality of rotor blades is rotatably mounted within the inner housing and at the inner housing a plurality of vanes are arranged such that a flow channel along a flow direction with a plurality of blade stages, each having a row of blades and a number of vanes is formed, through which a steam flows during operation, wherein steam after a blade stage via a connection in a flows between the thrust balance piston of the rotor and the inner housing located Schubaus damagesskolbenvorraum.
  • the steam flows to the blade stage via a return channel located in the inner housing in a space between the inner housing and outer housing and from there via a supply channel located in the inner housing in the located between the thrust balance piston of the rotor and the inner housing Schubaus Dermatour.
  • the live steam temperatures are between 550 ° C to 600 ° C and the temperature of the steam flowing into the recirculation duct is between 520 ° C and 550 ° C. It is also advantageous that the steam flows at temperatures between 550 ° C to 600 ° C in the overload discharge. It is equally advantageous that the steam flows at temperatures between 540 ° C to 560 ° C in the cross-return passage.
  • FIG. 1 is a cross section through a steam turbine 1 according to the prior art shown.
  • the steam turbine 1 has an outer housing 2 and an inner housing 3.
  • the inner housing 3 and the outer housing 2 do not have one closer to the live steam supply channel shown.
  • the rotor is rotationally symmetrical about a rotation axis 6.
  • the rotor 5 comprises a plurality of rotor blades 7.
  • the inner casing 3 has a plurality of stator blades 8. Between the inner housing 3 and the rotor 5, a flow channel 9 is formed.
  • a flow channel 9 comprises a plurality of blade stages, each of which is formed by a row of rotor blades 7 and a row of stator blades 8.
  • Fresh steam flows into an inflow opening 10 via the main steam supply duct and flows from there in a flow direction 11 through the flow duct 9, which runs essentially parallel to the axis of rotation 6.
  • the live steam expands and cools down. Thermal energy is converted into rotational energy.
  • the rotor 5 is set in a rotational movement and can drive a generator for electrical power generation.
  • a thrust balance piston 4 is formed such that a thrust balance piston antechamber 12 is formed.
  • a thrust balance piston antechamber 12 By supplying steam into the thrust balance piston antechamber 12 creates a counterforce, which counteracts a thrust 13.
  • FIG. 2 is a partial section of a steam turbine 1 to see.
  • steam flows over the live steam supply channel not shown in the input space 10.
  • the live steam supply is represented symbolically by the arrow 13.
  • the live steam usually has temperatures of up to 600 ° C and a pressure of up to 258 bar.
  • the live steam flows in the flow direction 11 through the flow channel 9. After a blade stage, the steam flows via a connection 14, 15, 16, which serves as a communicating tube between the flow channel 9 and a thrust balance piston 4 of the rotor 5 and the inner housing. 3
  • the steam flows through a return channel 14, which is formed as a communicating tube between a space 15 between the inner housing 3 and the outer housing 2 and the flow channel 9 for a blade stage, in the space 15 between the inner housing 3 and outer housing 2.
  • the in space 15 between Inner housing 3 and outer housing 2 located steam now has a temperature of 532 ° C and a pressure of 176 bar.
  • the steam flows via a supply channel 16, which serves as a communicating tube between the space 15 between the inner housing 3 and outer housing 2 and the thrust balance piston antechamber 12 between the thrust balance piston 4 of the rotor 5 and the inner housing 3 in the thrust balance piston antechamber 12th
  • the thrust balance piston antechamber 12 in an axial direction 17 between thrust balance piston 4 and inner housing 3 is arranged.
  • a fresh steam flowing into the space 10 flows for the most part in the flow direction 11 into the flow channel 9.
  • a smaller part flows as a leak vapor into a sealing space 18.
  • the leakage steam flows essentially in an opposite direction 19.
  • the leakage steam flows through a cross-return duct 20 acting as a communicating tube between a between the sealing chamber 18 between the rotor 5 and the housing 3 and arranged after a blade stage inlet space 26 in the flow channel 9 in the flow channel 9.
  • the cross-return passage 20 is in this case from the sealing chamber 18 away in substantially perpendicular to the flow direction 11, after a deflection 21 substantially parallel to the flow direction 11 and after a second deflection 22 substantially perpendicular to the flow direction 11 is formed.
  • the inner housing and outer housing may be formed with an overload introduction, not shown.
  • In the overload discharge flows external steam, which is symbolized by the arrow 23.
  • the recirculation passage 14 is connected to the flow passage 9 downstream of a recirculation vane stage 24, and the cross recirculation passage 20 is connected to the flow passage 9 downstream of a cross return vane stage 25.
  • the cross-return vane stage 25 is in this case arranged in the flow direction 11 of the flow channel 9 after the return vane stage 24.
  • the recycle vane stage 24 is the fourth vane stage and the cross-return vane stage is the fifth vane stage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Control Of Turbines (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)

Claims (16)

  1. Turbine (1) à vapeur ayant un carter (2) extérieur et un carter (3) intérieur,
    dans laquelle le carter (2) extérieur et le carter (3) intérieur ont un canal (10) d'apport de vapeur fraîche,
    dans laquelle un rotor (5) ayant un piston (4) de compensation de la poussée et comprenant plusieurs aubes (7) mobiles est monté tournant à l'intérieur du carter (3) intérieur,
    le carter (3) intérieur a plusieurs aubes (8) directrices disposées de façon à former le long d'une direction (11) d'écoulement un canal (9) d'écoulement ayant plusieurs étages d'aubes qui ont, respectivement, une rangée d'aubes (7) mobiles et une rangée d'aubes (8) directrices,
    dans laquelle le carter (3) intérieur a une liaison (14, 15, 16) qui est constituée sous la forme d'un tube communiquant entre le canal (9) d'écoulement après un étage d'aubes et une antichambre (12) de piston de compensation de la poussée entre le piston (4) de compensation de la poussée du rotor (5) et le carter (3) intérieur,
    caractérisée en ce que
    le carter (3) intérieur a un canal (20) de retour en croix, qui est constitué sous la forme d'un tube communiquant entre un espace (18) d'étanchéité entre le rotor (5) et le carter (3) intérieur et un espace (26) d'afflux dans le canal (9) d'écoulement disposé après un étage d'aubes.
  2. Turbine (1) à vapeur suivant la revendication 1,
    caractérisée en ce que
    la liaison (14, 15, 16) comprend un canal (14) de retour, qui est constitué sous la forme d'un tube communiquant entre un espace (15) entre le carter (3) intérieur et le carter (2) extérieur et le canal (9) d'écoulement après un étage d'aubes et la liaison comprend un canal (16) d'afflux qui est constitué sous la forme d'un tuyau communiquant entre l'espace (15) entre le carter (3) intérieur et le carter (2) extérieur et une antichambre (12) de piston de piston de compensation de la poussée entre le piston (4) de compensation de la poussée du rotor (5) et le carter (3) intérieur.
  3. Turbine (1) à vapeur suivant la revendication 1 ou 2,
    caractérisée en ce que
    l'antichambre (12) de piston de compensation de la poussée est disposée dans une direction (17) axiale entre le piston (4) de compensation de la poussée et le carter (3) intérieur.
  4. Turbine (1) à vapeur suivant la revendication 1, 2 ou 3,
    caractérisée en ce que
    le canal (14) de retour et le canal (16) d'afflux sont sensiblement perpendiculairement à la direction (11) d'écoulement dans le carter (3) intérieur et l'espace (15) entre le carter (3) intérieur et le carter (2) extérieur est constitué pour la liaison du canal (14) de retour avec le canal (16) d'afflux.
  5. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    caractérisée en ce que
    le canal (20) de retour en croix est constitué en partant de l'espace (18) d'étanchéité sensiblement perpendiculairement à la direction (11) d'écoulement, après une déviation (21) sensiblement parallèlement à la direction (11) d'écoulement et après une deuxième déviation (22) sensiblement perpendiculairement à la direction (11) d'écoulement.
  6. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    caractérisée par un conduit (23) de surcharge passant dans le carter (2) extérieur et le carter (3) intérieur et débouchant dans l'espace (26) d'afflux.
  7. Turbine (1) à vapeur suivant l'une des revendications précédentes,
    caractérisée en ce que
    le canal (14) de retour communique avec le canal (9) d'écoulement après un étage (24) d'aubes de retour et le canal (20) de retour en croix communique avec le canal (9) d'écoulement après un étage (25) d'aubes de retour en croix, l'étage (25) d'aubes de retour en croix étant disposé dans la direction (11) d'écoulement du canal (9) d'écoulement après l'étage (24) d'aubes de retour.
  8. Turbine (1) à vapeur suivant la revendication 7,
    caractérisée en ce que
    l'étage (24) d'aubes de retour est le quatrième étage d'aubes et l'étage (25) d'aubes de retour en croix est le cinquième étage d'aubes.
  9. Procédé pour faire fonctionner une turbine (1) à vapeur ayant un carter (2) extérieur et un carter (3) intérieur,
    dans laquelle le carter (2) extérieur et le carter (3) intérieur ont un canal (10) d'afflux de vapeur fraîche,
    dans laquelle un rotor (5) ayant un piston (4) de compensation de la poussée et comprenant plusieurs aubes (7) mobiles est monté tournant dans le carter (3) intérieur et sur le carter (3) intérieur sont montées plusieurs aubes (8) directrices, de sorte que
    un canal (9) d'écoulement est formé le long d'une direction (11) d'écoulement ayant plusieurs étages d'aubes qui ont, respectivement, une rangée d'aubes (7) mobiles et une rangée d'aubes (8) directrices, canal dans lequel une vapeur passe en fonctionnement,
    dans laquelle de la vapeur passe après un étage d'aubes par une liaison (14, 15, 16) dans une antichambre (12) de piston de compensation de la poussée se trouvant entre le piston (4) de compensation de la poussée du rotor (5) et le carter (3) intérieur,
    caractérisé en ce
    qu'une vapeur se trouvant dans un espace (18) d'étanchéité se trouvant entre le rotor (5) et le carter (3) intérieur passe par un canal (20) de retour en croix dans un espace (26) d'afflux disposé après un étage d'aubes.
  10. Procédé suivant la revendication 9,
    caractérisé en ce que
    la vapeur passe, après l'étage d'aubes en passant par un canal (14) de retour se trouvant dans le carter (3) intérieur, dans un espace (15) compris entre le carter (3) intérieur et le carter (2) extérieur et de là va, par un canal (16) d'afflux se trouvant dans le carter (3) intérieur, dans l'antichambre (12) de piston de compensation de la poussée se trouvant entre le piston (4) de compensation de la poussée du rotor (5) et le carter (3) intérieur.
  11. Procédé suivant la revendication 10,
    caractérisé en ce que
    l'on obtient une compensation de la poussée par la vapeur dans l'antichambre (12) de piston de compensation de la poussée.
  12. Procédé suivant la revendication 9,
    caractérisé en ce
    qu'une vapeur de surcharge passe en passant par un conduit (23) de surcharge dans l'espace (26) d'afflux.
  13. Procédé suivant l'une des revendications 9 à 12,
    caractérisé en ce que
    la vapeur passe dans le canal (10) d'apport de vapeur fraîche en ayant des températures de vapeur fraîche comprises entre 550°C et 600°C.
  14. Procédé suivant l'une des revendications 9 à 13,
    caractérisé en ce que
    la vapeur passe dans le canal (14) de retour en ayant des températures comprises entre 520°C et 550°C.
  15. Procédé suivant la revendication 12, 13 ou 14,
    caractérisé en ce que
    la vapeur de surcharge passe dans le conduit (23) de surcharge en ayant des températures comprises entre 550°C et 600°C.
  16. Procédé suivant l'une des revendications 9 à 15,
    caractérisé en ce que
    la vapeur passe dans le canal (20) de retour en croix en ayant des températures comprises entre 540°C et 660°C.
EP05769957A 2004-08-02 2005-07-14 Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur Active EP1774140B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PL05769957T PL1774140T3 (pl) 2004-08-02 2005-07-14 Turbina parowa i sposób eksploatacji turbiny parowej
EP05769957A EP1774140B1 (fr) 2004-08-02 2005-07-14 Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP04018285A EP1624155A1 (fr) 2004-08-02 2004-08-02 Turbine à vapeur et procédé d'opération d'une turbine à vapeur
PCT/EP2005/053375 WO2006015923A1 (fr) 2004-08-02 2005-07-14 Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur
EP05769957A EP1774140B1 (fr) 2004-08-02 2005-07-14 Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur

Publications (2)

Publication Number Publication Date
EP1774140A1 EP1774140A1 (fr) 2007-04-18
EP1774140B1 true EP1774140B1 (fr) 2008-03-19

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP04018285A Withdrawn EP1624155A1 (fr) 2004-08-02 2004-08-02 Turbine à vapeur et procédé d'opération d'une turbine à vapeur
EP05769957A Active EP1774140B1 (fr) 2004-08-02 2005-07-14 Turbine a vapeur et procede pour faire fonctionner une turbine a vapeur

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP04018285A Withdrawn EP1624155A1 (fr) 2004-08-02 2004-08-02 Turbine à vapeur et procédé d'opération d'une turbine à vapeur

Country Status (14)

Country Link
US (1) US8202037B2 (fr)
EP (2) EP1624155A1 (fr)
JP (1) JP4662562B2 (fr)
KR (1) KR101239792B1 (fr)
CN (1) CN100575671C (fr)
AT (1) ATE389784T1 (fr)
BR (1) BRPI0514080A (fr)
CA (1) CA2575682C (fr)
DE (1) DE502005003358D1 (fr)
ES (1) ES2302555T3 (fr)
MX (1) MX2007001450A (fr)
PL (1) PL1774140T3 (fr)
RU (1) RU2351766C2 (fr)
WO (1) WO2006015923A1 (fr)

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US20080213085A1 (en) 2008-09-04
ES2302555T3 (es) 2008-07-16
RU2351766C2 (ru) 2009-04-10
CN101052782A (zh) 2007-10-10
KR101239792B1 (ko) 2013-03-06
EP1624155A1 (fr) 2006-02-08
BRPI0514080A (pt) 2008-05-27
JP2008508471A (ja) 2008-03-21
ATE389784T1 (de) 2008-04-15
CA2575682A1 (fr) 2006-02-16
MX2007001450A (es) 2007-04-19
RU2007107799A (ru) 2008-09-10
DE502005003358D1 (de) 2008-04-30
US8202037B2 (en) 2012-06-19
JP4662562B2 (ja) 2011-03-30
PL1774140T3 (pl) 2008-08-29
CN100575671C (zh) 2009-12-30
EP1774140A1 (fr) 2007-04-18
KR20070047315A (ko) 2007-05-04
CA2575682C (fr) 2009-11-17

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