EP0873466A1 - Arbre de turbine a vapeur a refroidissement interne - Google Patents

Arbre de turbine a vapeur a refroidissement interne

Info

Publication number
EP0873466A1
EP0873466A1 EP96946113A EP96946113A EP0873466A1 EP 0873466 A1 EP0873466 A1 EP 0873466A1 EP 96946113 A EP96946113 A EP 96946113A EP 96946113 A EP96946113 A EP 96946113A EP 0873466 A1 EP0873466 A1 EP 0873466A1
Authority
EP
European Patent Office
Prior art keywords
steam
turbine shaft
line
pressure
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.)
Granted
Application number
EP96946113A
Other languages
German (de)
English (en)
Other versions
EP0873466B1 (fr
Inventor
Heinrich Oeynhausen
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
Publication of EP0873466A1 publication Critical patent/EP0873466A1/fr
Application granted granted Critical
Publication of EP0873466B1 publication Critical patent/EP0873466B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

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
    • 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

Definitions

  • the invention relates to a turbine shaft of a steam turbine, in particular for the combined reception of high-pressure and medium-pressure blading, and a method for cooling the turbine shaft of a steam turbine.
  • a combined high and medium pressure turbine is suitable for a steam turbine with a lower to medium output, for example from 300 MW to 600 MW. Both the high-pressure rotor blades and the medium-pressure rotor blades are taken up by the turbine shaft.
  • the turbine shaft is housed in a single housing which has the associated guide vanes.
  • the common housing can have an inner housing and an outer housing, which are each divided horizontally and screwed together.
  • the fresh steam state characterized by the high pressure steam can currently be around 170 bar and 540 ° C. In the course of increasing the efficiency, a fresh steam state of 270 bar and 600 ° C can be aimed for.
  • High-pressure steam can be supplied to the high-pressure blading in a central region of the turbine shaft and flows through it to an outlet connection.
  • the steam which has been relaxed and cooled in this way, can be fed into a boiler and reheated there.
  • the steam state at the end of the high pressure part is referred to as cold reheating and the Steam condition after leaving the boiler is referred to as hot reheat.
  • the steam emerging from the boiler is fed to the medium-pressure blading.
  • the steam state can be 30 bar to 50 bar and 540 ° C, an increase to a steam state of approximately 50 bar to 60 bar and 600 ° C being sought.
  • the blades in the steam inflow region of both the high-pressure part and the medium-pressure part can be made from a nickel-based alloy.
  • constructive measures can be carried out in the steam inflow area, in which the turbine shaft is protected against direct contact with the steam by means of shaft shields.
  • the object directed to a turbine shaft of a steam turbine is achieved in that a turbine shaft, which extends along a rotation axis and has a jacket surface, has in its interior a cooling line for guiding cooling steam in the direction of the rotation axis, the cooling line on the one hand at least one outflow line leading to the jacket surface for guiding cooling steam to the jacket surface and on the other hand is connected to at least one inflow line for inflowing cooling steam into the cooling line.
  • a cooling line running inside the turbine shaft cooling steam can be guided in the direction of the axis of rotation through the turbine shaft and through the outflow line to the surface of the jacket, so that the turbine shaft in its interior as well as in the area exposed to high temperatures Jacket surface is coolable.
  • the cooling line can be inclined with respect to the axis of rotation or wound in relation thereto, whereby it enables cooling steam to be transported in the direction of the axis of rotation. Furthermore, it is also possible to cool the rotor blades anchored in the turbine shaft, in particular their blade roots. It goes without saying that, depending on the production of the cooling line, the outflow line and the inflow line can form part of the cooling line. Furthermore, it goes without saying that more than one cooling line can be provided, the cooling lines being connected to one another and each being connected to one or more outflow lines or inflow lines. It is also possible to arrange adjacent outflow lines in the direction of the axis of rotation at predeterminable intervals and to connect them to the cooling line.
  • Cooling of heavily temperature-stressed shaft sections can thus take place without considerable expenditure on pipes, housing bushings and integration into the turbine control.
  • This high design effort would be necessary, for example, when cooling a turbine shaft by means of cold steam from the outside through the housing and the guide vanes to the turbine shaft, in order to cool the jacket surface of the turbine shaft directly.
  • the turbine shaft according to the invention is particularly suitable for designing a combined high-pressure and medium-pressure turbine shaft for a steam turbine. This is particularly so since the steam inflow area of the medium-pressure part of a steam turbine is a critical point in turbine design. Since, in comparison to the high-pressure part in the medium-pressure part, lower vapor pressures result in significantly higher volume flows and so that larger shaft diameters and longer blades are required, the thermomechanical stress on the blade roots and the shaft is greater in the medium-pressure part than in the high-pressure part.
  • the material characteristics of the turbine shaft are also similar, which makes the medium-pressure part more critical than the high pressure due to the higher thermomechanical loads Part is to be assessed.
  • the turbine shaft according to the invention in which the turbine shaft in the medium-pressure part can be cooled by cooling steam both in its interior, particularly in the middle of the shaft, and on its jacket surface, in particular in the area of the blade roots.
  • the cooling steam is preferably led from the high-pressure part through the cooling line into the medium-pressure part, the steam already flowing through the pressure difference between the high-pressure part and the medium-pressure part.
  • This pressure difference between the steam outlet area of the high-pressure part and the steam inlet area of the medium-pressure part is between 4 bar and 6 bar, for example.
  • the cooling line is preferably a bore which is largely parallel to the axis of rotation and which is in particular a central bore.
  • a cooling line designed as a bore is particularly simple and can also be produced subsequently in the turbine shaft.
  • the bore is preferably closed downstream of the connection point with the outflow line, in particular by a plug. This ensures that cooling steam flowing in through the inflow line can be completely removed from the turbine shaft through the outflow line.
  • the medium-pressure tubular shaft has the outflow line or the outflow lines in the vicinity of the blades of the steam inflow region of the medium-pressure part, which ensures cooling, in particular of the blade roots, of these particularly thermally stressed blades.
  • the inflow line like the outflow line, preferably connects the jacket surface to the cooling line.
  • cooling steam in particular steam from a steam turbine
  • the inflow line can be guided from the jacket surface at one end of the turbine shaft through the interior of the turbine shaft into the central region of the turbine shaft.
  • the inflow line and / or the outflow line are or are preferably an essentially radial bore. Such a bore can be easily carried out even after the turbine shaft has been produced, such a bore being connectable precisely to a cooling line designed as an axial bore.
  • the diameter of a hole and the number of several holes for the inflow line and the outflow line depend on the amount of steam provided for cooling.
  • the turbine shaft has recesses on the jacket surface for receiving turbine blades, the outflow line preferably opening into one of these recesses.
  • the recesses can be made somewhat larger than the feet of the respective blade, so that a space is formed between a corresponding base and the turbine shaft, into which steam can flow for cooling the blade root. This space can also be formed by channels which are connected to the outflow line and / or to one another
  • a stub leads to the jacket surface of the turbine shaft.
  • cooling of the casing surface and thus the turbine shaft is also achieved from the outside. This is particularly in the steam inflow area of the medium pressure part of a combined .
  • High-pressure medium-pressure turbine shaft advantageous. This results in cooling of the turbine shaft from the inside in the region of the high-pressure part, in the region of a shaft seal between the high-pressure part and the medium-pressure part, and in the particularly stressed steam inflow region of the medium-pressure part, including the blade roots of the given the first row of blades of the medium-pressure part.
  • the turbine shaft is therefore preferably suitable for a steam turbine in which the high-pressure part and the medium-pressure part are accommodated in a common housing.
  • the outflow line opens into the steam inflow region of the medium-pressure rotor blades, so that in this region both the turbine shaft and the rotor blades, including the rotor blade feet, are cooled.
  • the inflow line preferably connects the steam outlet region of the high-pressure rotor blades to the cooling line, as a result of which steam can be guided from the steam outlet region of the high-pressure part through the interior of the turbine shaft into the medium-pressure part.
  • the object directed to a method for cooling a turbine shaft of a steam turbine is solved for a turbine shaft which carries both the high-pressure rotor blades and the medium-pressure rotor blades in that steam from the steam area of the high-pressure rotor blades, i.e. is led from the high-pressure part through the interior of the turbine shaft to the steam inflow region of the medium-pressure rotor blades.
  • the steam flow in the interior of the turbine shaft can be regulated by suitable dimensioning of a corresponding cooling line, which is in particular designed as a bore, so that it also extends over a wide area
  • Adequate cooling is guaranteed. Since there is also a pressure ⁇ difference between the high-pressure part and the medium-pressure part in the part-load range of the steam turbine, proper functioning of the method is also guaranteed in the part-load range.
  • a cooling line designed as an axial, preferably central, bore the tangential stresses inside the turbine shaft may rise to approximately twice as compared to a turbine shaft without a bore. This possibly higher load on the turbine shaft is compensated for by the significantly improved material properties due to the internal cooling of the turbine shaft.
  • FIG. 1 shows a longitudinal section through a combined high-pressure, medium-pressure turbine in a housing with a turbine shaft and
  • the turbine shaft 1 shows a turbine shaft 1 which extends along an axis of rotation 2 and which is arranged in an outer housing 22 surrounding an inner housing 21.
  • the turbine shaft 1 has a central region 28 which contains a shaft seal 24 with the inner housing 21.
  • the high-pressure part 23 of the steam turbine connects to the middle region 28 on the left.
  • To the right of the central region 28 is the medium-pressure part 25 of the steam turbine.
  • the high-pressure part 23 with the high-pressure blading 13 has a high-pressure steam inflow region 27 directly adjoining the shaft seal 24, from which the inflowing high-pressure steam flows through a steam region 17 of the high-pressure blading 13 and through a steam outlet area 16 leaves the outer housing 22 to a boiler, not shown, in which an intermediate overheating takes place.
  • the reheated steam 6 enters the outer housing 22 and the inner housing 21 again via a steam inflow region 15 of the medium-pressure part 25, which adjoins the shaft seal 24 directly to the right. It flows through a medium-pressure blading 14 adjoining the steam inflow region 15 of the medium-pressure part 25 to the right.
  • the medium-pressure blading 14 is followed by an outflow connection 26, through which the steam 6 can be guided to a low-pressure steam turbine (not shown).
  • the flow of steam 6 described is indicated by flow arrows 29.
  • the turbine shaft 1 has a central bore 5a coinciding with the axis of rotation 2, which extends through the medium-pressure part 25 to through the high-pressure part 23.
  • the central bore 5a is connected in the steam outlet area 16 of the high-pressure part 23 to a jacket surface 3 of the turbine shaft 1 by a plurality of inflow lines 8.
  • the inflow lines 8 are designed as radial bores 8a, as a result of which "cold" steam can flow from the high-pressure part 23 into the central bore 5a.
  • the central bore 5a is also connected to a plurality of outflow lines 7 in a medium-pressure part 25 in the area of the first rows of blades.
  • outflow lines 7 each extend from recesses 10 of the casing surface 3 for receiving rotor blades 11 to the central bore 5a.
  • the outflow lines 7 are also essentially radially running bores 7a. Downstream of the outflow lines 7, the central bore 5a is sealed off by a stopper 9.
  • the part of the bore 5a lying between the outflow lines 7 and the inflow lines 8 thus forms a cooling line 5 through which steam 6 flows from the high-pressure part 23 into the steam inflow region 15 of the medium-pressure part 25.
  • This vapor 6 has a significantly lower one Temperature as the superheated steam flowing into the steam inflow region 15, so that effective cooling of the first rows of blades of the medium-pressure part 25 and the jacket surface 3 is ensured in the area of these rows of blades.
  • FIG. 2 shows the steam inflow region 15 of the medium-pressure part 25 on an enlarged scale.
  • Corresponding rotor blades 11 with their blade roots 18 are arranged in the recesses 10 of the turbine shaft 1.
  • the recesses 10 each have channels 20 around the blade feet 18, the channels 20 being connected on the one hand to the outflow lines 7 running radially to the axis of rotation 2 and on the other hand each to a branch line 12.
  • the stub 12 leads from the recess 10 to the jacket surface 3, so that the
  • Branch line 12 is opposite a guide vane 19 of the steam turbine.
  • the steam 6 flowing from the high-pressure part 23 through the outflow lines 7 reaches the channels 20 of the recesses 10 and thus cools the blade feet 18 arranged in a corresponding recess 10.
  • the steam 6 flows from the channels 20 through a respective branch line 12 to the outer surface 3 of the turbine shaft 1 and thus also cools the outer surface 3 between adjacent blades 11 in the direction of the axis of rotation 2.
  • the invention is characterized by a turbine shaft which carries both the blades of a high-pressure part and the blades of a medium-pressure part of a steam turbine.
  • the turbine shaft has at least one cooling line which is connected to the high-pressure part via at least one inflow line and to the steam inflow region of the medium-pressure part via at least one outflow line.
  • the inflow line, the cooling line and the outflow line form a line system inside the turbine shaft, through which "cold" steam from the high pressure part to the thermomechanically highly stressed steam inflow area of the medium pressure part is feasible.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)

Abstract

L'invention concerne un arbre de turbine (1), en particulier pour turbine à vapeur haute pression-basse pression combinée, montée dans un bâti commun (22). L'arbre de turbine présente, à l'intérieur (4), une conduite de refroidissement (5) pour le guidage de la vapeur de refroidissement (6). La conduite de refroidissement (5) est connectée, d'une part, à une conduite de sortie (7) et, d'autre part, à une conduite d'amenée (8). On obtient ainsi un refroidissement par vapeur de l'arbre (1) d'une turbine à vapeur combinée haute pression-moyenne pression, par amenée de vapeur provenant de la partie haute pression, via la conduite de sortie (7) et la conduite d'amenée (8), vers la partie moyenne pression (23). L'invention concerne en outre un procédé de refroidissement d'un arbre (1) d'une turbine à vapeur.
EP96946113A 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne Expired - Lifetime EP0873466B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19600821 1996-01-11
DE19600821 1996-01-11
PCT/DE1996/002490 WO1997025521A1 (fr) 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne

Publications (2)

Publication Number Publication Date
EP0873466A1 true EP0873466A1 (fr) 1998-10-28
EP0873466B1 EP0873466B1 (fr) 2002-11-20

Family

ID=7782539

Family Applications (1)

Application Number Title Priority Date Filing Date
EP96946113A Expired - Lifetime EP0873466B1 (fr) 1996-01-11 1996-12-20 Arbre de turbine a vapeur a refroidissement interne

Country Status (8)

Country Link
US (1) US6010302A (fr)
EP (1) EP0873466B1 (fr)
JP (1) JP2000502775A (fr)
KR (1) KR19990077142A (fr)
AT (1) ATE228202T1 (fr)
DE (1) DE59609893D1 (fr)
ES (1) ES2187687T3 (fr)
WO (1) WO1997025521A1 (fr)

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO1999000583A1 (fr) * 1997-06-27 1999-01-07 Siemens Aktiengesellschaft Arbre de turbine a vapeur avec refroidissement interne et procede pour refroidir un arbre de turbine
CN1143946C (zh) * 1997-09-26 2004-03-31 西门子公司 叶片机械用壳体
DE59711075D1 (de) * 1997-12-24 2004-01-15 Alstom Schweiz Ag Baden Kombinierte Mehrdruck-Dampfturbine
EP1378630A1 (fr) * 2002-07-01 2004-01-07 ALSTOM (Switzerland) Ltd Turbine à vapeur
US7488153B2 (en) * 2002-07-01 2009-02-10 Alstom Technology Ltd. Steam turbine
US8156757B2 (en) * 2006-10-06 2012-04-17 Aff-Mcquay Inc. High capacity chiller compressor
US8105032B2 (en) * 2008-02-04 2012-01-31 General Electric Company Systems and methods for internally cooling a wheel of a steam turbine
US8397534B2 (en) * 2008-03-13 2013-03-19 Aff-Mcquay Inc. High capacity chiller compressor
JP5433183B2 (ja) 2008-08-07 2014-03-05 株式会社東芝 蒸気タービンおよび蒸気タービンプラントシステム
US8251643B2 (en) * 2009-09-23 2012-08-28 General Electric Company Steam turbine having rotor with cavities
CH701914A1 (de) * 2009-09-30 2011-03-31 Alstom Technology Ltd Dampfturbine mit Entlastungsnut am Rotor im Bereich des Schubausgleichskolbens.
US8591180B2 (en) * 2010-10-12 2013-11-26 General Electric Company Steam turbine nozzle assembly having flush apertures
US9297277B2 (en) 2011-09-30 2016-03-29 General Electric Company Power plant
US9151163B2 (en) * 2012-11-29 2015-10-06 Mtu Aero Engines Gmbh Turbomachine rotor disk
US9702261B2 (en) 2013-12-06 2017-07-11 General Electric Company Steam turbine and methods of assembling the same
EP3130767A1 (fr) * 2015-08-14 2017-02-15 Siemens Aktiengesellschaft Turbine à vapeur à haute et moyenne pression combinée

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DE959868C (de) * 1953-07-17 1957-03-14 Schilling Estate Company Laufradanordnung fuer Verpuffungsbrennkraftturbinen hoher Drehzahl
FR1143040A (fr) * 1954-09-10 1957-09-25 Henschel & Sohn Gmbh Rotor de turbine refroidi pour températures élevées des gaz
GB809268A (en) * 1955-12-31 1959-02-18 Oerlikon Maschf Improvements in or relating to turbines
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US4571935A (en) * 1978-10-26 1986-02-25 Rice Ivan G Process for steam cooling a power turbine
JPS5934402A (ja) * 1982-08-20 1984-02-24 Hitachi Ltd 蒸気タ−ビンのロ−タ装置
DE3310396A1 (de) * 1983-03-18 1984-09-20 Kraftwerk Union AG, 4330 Mülheim Md-dampfturbine in einflutiger bauweise fuer eine hochtemperaturdampfturbinenanlage mit zwischenueberhitzung
DE4324034A1 (de) * 1993-07-17 1995-01-19 Abb Management Ag Gasturbine mit gekühltem Rotor
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Also Published As

Publication number Publication date
DE59609893D1 (de) 2003-01-02
ATE228202T1 (de) 2002-12-15
US6010302A (en) 2000-01-04
EP0873466B1 (fr) 2002-11-20
JP2000502775A (ja) 2000-03-07
KR19990077142A (ko) 1999-10-25
WO1997025521A1 (fr) 1997-07-17
ES2187687T3 (es) 2003-06-16

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