EP2101042A1 - Turbine à vapeur dotée de frettes - Google Patents

Turbine à vapeur dotée de frettes Download PDF

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Publication number
EP2101042A1
EP2101042A1 EP08004394A EP08004394A EP2101042A1 EP 2101042 A1 EP2101042 A1 EP 2101042A1 EP 08004394 A EP08004394 A EP 08004394A EP 08004394 A EP08004394 A EP 08004394A EP 2101042 A1 EP2101042 A1 EP 2101042A1
Authority
EP
European Patent Office
Prior art keywords
inner housing
steam turbine
housing
shrink
outer housing
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Withdrawn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
EP08004394A
Other languages
German (de)
English (en)
Inventor
Andreas Ulma
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 EP08004394A priority Critical patent/EP2101042A1/fr
Publication of EP2101042A1 publication Critical patent/EP2101042A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • 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
    • F01D25/26—Double casings; Measures against temperature strain in casings
    • 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
    • F01D11/00—Preventing or minimising internal leakage of working-fluid, e.g. between stages
    • F01D11/003—Preventing or minimising internal leakage of working-fluid, e.g. between stages by packing rings; Mechanical seals
    • 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
    • F05D2260/30—Retaining components in desired mutual position
    • 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
    • F05D2260/30—Retaining components in desired mutual position
    • F05D2260/37—Retaining components in desired mutual position by a press fit connection

Definitions

  • the invention relates to a steam turbine, comprising a rotatably mounted rotor, an inner housing arranged around the rotor and an outer housing arranged around the inner housing, wherein the inner housing has an inner housing upper part and an inner housing lower part, wherein shrink rings for compressing the inner housing lower part and the inner housing upper part are arranged.
  • shrink rings in steam turbine construction.
  • the shrink rings are in this case arranged around the inner casing of the steam turbine in order to hold this together at the high pressures occurring and to mechanically stabilize the inner casing.
  • Shrink joints have over the screw advantages of a more favorable voltage curve and, an improvement in the symmetry, which experiences a comparatively strong disturbance compared to screw.
  • the inner housing is arranged in a designed as a pot outer housing and closed with a lid, so to speak.
  • the inner casing of a steam turbine must be very thick-walled at very large pressure differences between the incoming steam and the surrounding steam be, which leads to an enlargement of the Operafugenflansche and the partial joint screws.
  • large flanges and large part-joint screws lead to a disturbance of symmetry.
  • a larger housing deformation and thus a greater radial play demand is to be expected.
  • the object of the invention is to provide a steam turbine which is suitable for very high live steam pressures.
  • a steam turbine comprising a rotatably mounted rotor, an inner housing arranged around the rotor and an outer housing arranged around the inner housing, the inner housing having an inner housing upper part and an inner housing lower part, wherein shrink rings are arranged for compressing the inner housing lower part and the inner housing upper part, wherein a seal is disposed on at least one shrink ring, the seal sealing a gap between the shrink ring and the outer housing.
  • the segment is arranged in a groove mounted on the inner housing. This only requires a simple and quick to be carried out processing of the inner housing. As a result, a quick implementation of securing the shrink ring against axial displacement is possible.
  • At least a second shrink ring is provided, which comprises a seal to the outer housing. Between the first shrink ring and the second shrink ring, a first pressure space is formed.
  • a third shrink ring is arranged such that a second pressure space is formed between the third shrink ring and the second shrink ring.
  • a plurality of pressure chambers may be formed to equalize the pressure differential from a first location between the inner housing and the outer housing and a downstream lower second location as seen in the axial direction at a lower pressure.
  • a blading area is arranged, wherein this blading area comprises a plurality of guide vanes and rotor blades.
  • bores are arranged in the inner housing, which fluidly connects the blading region with the first or second pressure chamber. This makes it possible to pressurize the pressure chamber with steam to form a certain pressure. By adjusting the pressure in the pressure chamber, suitable pressure conditions can be created, which makes the selection and configuration of the steam turbine components, such as. B. the outer housing and the inner housing, can be specifically selected.
  • the number of pressure chambers may be greater or less than two.
  • the bores can also be mounted in the outer housing in an alternative embodiment.
  • the bore is mounted in such a way in the outer housing, that a connection from the first or second pressure chamber to an external steam supply is formed.
  • an axial securing shrink ring is arranged around the inner housing, wherein the Axialommesschrumpfring rests on the outer housing to prevent axial displacement of the inner housing relative to the outer housing. Since high axial forces, which can lead to a displacement of the inner housing, in particular in high-pressure turbine sections in single-flow construction, suitable precautions must be taken to prevent this.
  • a suitable advantageous embodiment of the invention provides a solution, as a displacement of the inner housing can be effectively prevented.
  • a Axialommesschrumpfring is disposed against the outer housing such that a movement of the inner housing in an axial direction leads to a force which is transmitted via the shrink ring on the outer housing. The Axialommesschrumpfring experiences a counter force from the outer housing, which effectively prevents displacement of the inner housing.
  • the outer housing has a projection, wherein the Axialtechnischsschrumpfring rests against the projection.
  • the production of a projection is a comparatively easy way to accomplish a connection between the Axialtechnischsschrumpfring and the outer housing.
  • a seal is arranged between the projection and the axial securing shrink ring. This will prevents high-pressure, high-temperature steam from reaching an area designed for lower temperatures. The high temperatures could cause damage at these points.
  • the outer housing is designed as a pot housing.
  • the gradation of the pressures within the pot housing by means of, for example, piston rings which are arranged on the shrink rings, very well possible.
  • the piston rings are not disturbed by any parting joints both in the shrink ring and on the sliding surface in the pot housing.
  • the inner housing with the shrink rings and the rotor is in this case arranged in an assembly step in the form of a pot housing outer housing.
  • the substantially axially symmetrical pot housing can naturally withstand a high internal pressure.
  • a lid is arranged so to speak on the pot and firmly connected with screws or similar connection means with the outer housing.
  • FIG. 1 shows a cross-sectional view of a high pressure turbine part 20 as an embodiment of a steam turbine.
  • the high-pressure turbine part 20 is formed substantially rotationally symmetrical to a rotation axis 21.
  • Essential components of the high-pressure turbine part 20 are the rotor 22, the inner housing 23 and an outer housing 3.
  • the inner housing 23 may be made of two different materials, which are welded together at a weld 24.
  • the inner housing 23 thus has a first inner housing part 1 and a second inner housing part 2.
  • the materials of the inner housing part 1 and the second inner housing part 2 are different.
  • the steam Since, during operation, the steam first flows in the inflow region 25 between the first inner housing part 1 and the rotor 22, it is subjected to a higher thermal load than the second inner housing part 2, since the steam in the axial direction in the flow direction 26 becomes more relaxed and cooler.
  • the material for the first inner housing part 1 should therefore have heat-resistant properties.
  • the material of the second inner housing part 2 may be made of a lower heat-resistant material than with respect to the material of the first inner housing part 1.
  • the rotor 22 may also be formed of two different materials. To save material, only the thermally stressed area with a high temperature resistant material, such as nickel-based manufactured.
  • the rotor is formed from an inflow rotor part 27 and two outer rotor parts 28, 29.
  • the inflow rotor part 27 is welded to the outer rotor part 29 at a first rotor welding point 30.
  • the inflow rotor part 27 is welded to the outer rotor part 28 at a second rotor welding point 31.
  • the inflow rotor part 27 is made of a more heat-resistant material than the two outer rotor parts 28, 29.
  • the inner housing 23 is in this case divided into two and comprises an inner housing lower part, which is not shown in the figure, and an inner housing upper part 34.
  • shrink rings 4 are arranged around the inner housing 23.
  • FIG. 1 are a total of seven shrink rings 4, 5, 6 shown.
  • z. B five shrink rings 4 are arranged in the region of the blading channel 32 and carry about half of the live steam pressure.
  • the forces from the internal pressure of the live steam, which prevails in the blading channel 32, are absorbed by the shrink rings 4.
  • 25 partial joint screws 7 can be attached in the region of the inflow. Between the shrink rings 4 and the outer housing 3 seals 9 are provided.
  • the pressure in the first pressure chamber 35 and in the second pressure chamber 36 can be selectively adjusted by making bores in the inner housing 23 in fluid communication with the blading channel 32.
  • the holes are in the FIG. 1 not shown in detail.
  • the holes can be arranged distributed over the circumference. Another possibility is to provide the outer housing 3 with holes in order to establish a fluidic connection between the first pressure chamber 35 or the second pressure chamber 36 with an external steam supply.
  • a displacement of the shrink rings 4 in the flow direction 26 is prevented by segments 8.
  • the segments 8 are in Flow direction 26 seen after a shrink ring 4 arranged in a groove 37. An axial displacement due to the pressure difference before and after the shrink ring 4 is thus effectively avoided.
  • the Axialommesschrumpfring 5 is seen in the flow direction 26 arranged in front of the inflow 25 and takes over the function of the axial fixation of the inner housing 23 and is sealed by a seal 10 to the outer housing 3 out.
  • the seal 10 may be, for example, a U-ring seal.
  • a threaded ring 13 transmits from the inner housing 23 resulting axial thrust forces. Instead of the threaded ring 13 screws can be used.
  • the outer housing 3 is designed as a pot housing, which means that the outer housing 3 does not comprise an axial parting line.
  • the outer housing 3 is closed by means of a lid 38.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP08004394A 2008-03-10 2008-03-10 Turbine à vapeur dotée de frettes Withdrawn EP2101042A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP08004394A EP2101042A1 (fr) 2008-03-10 2008-03-10 Turbine à vapeur dotée de frettes

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP08004394A EP2101042A1 (fr) 2008-03-10 2008-03-10 Turbine à vapeur dotée de frettes

Publications (1)

Publication Number Publication Date
EP2101042A1 true EP2101042A1 (fr) 2009-09-16

Family

ID=40328979

Family Applications (1)

Application Number Title Priority Date Filing Date
EP08004394A Withdrawn EP2101042A1 (fr) 2008-03-10 2008-03-10 Turbine à vapeur dotée de frettes

Country Status (1)

Country Link
EP (1) EP2101042A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN109026206A (zh) * 2018-07-19 2018-12-18 哈尔滨汽轮机厂有限责任公司 一种带蜗壳进汽式高压内缸的整体高压核电汽轮机
EP3453848A1 (fr) * 2017-09-08 2019-03-13 Siemens Aktiengesellschaft Turbine à vapeur dotée d'une chambre de piquage

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE908254C (de) * 1949-02-17 1954-04-05 Licentia Gmbh Axial-Dampf-oder-Gasturbine mit ins Gehaeuse eingesetztem Tragmantel fuer die Leitschaufelscheiben
DE2054465A1 (de) * 1970-11-05 1972-05-10 Kraftwerk Union Ag Einrichtung zur radial-zentrisch wärmebeweglichen Lagerung und Zentrierung der inneren an äußeren Gehäuse schalen bei Turbomaschinen, insb. Dampfturbinen
US3844675A (en) * 1972-04-17 1974-10-29 Kraftwerk Union Ag Plural shell axial turbine for operation with high pressure, high temperature steam
EP0566478A1 (fr) * 1992-04-17 1993-10-20 Gec Alsthom Electromecanique Sa Carter haute pression pour turbine à vapeur
EP0965732A1 (fr) * 1998-06-15 1999-12-22 Asea Brown Boveri AG Anneau de sertissage avec prise de vapeur pour turbine
EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE908254C (de) * 1949-02-17 1954-04-05 Licentia Gmbh Axial-Dampf-oder-Gasturbine mit ins Gehaeuse eingesetztem Tragmantel fuer die Leitschaufelscheiben
DE2054465A1 (de) * 1970-11-05 1972-05-10 Kraftwerk Union Ag Einrichtung zur radial-zentrisch wärmebeweglichen Lagerung und Zentrierung der inneren an äußeren Gehäuse schalen bei Turbomaschinen, insb. Dampfturbinen
US3844675A (en) * 1972-04-17 1974-10-29 Kraftwerk Union Ag Plural shell axial turbine for operation with high pressure, high temperature steam
EP0566478A1 (fr) * 1992-04-17 1993-10-20 Gec Alsthom Electromecanique Sa Carter haute pression pour turbine à vapeur
EP0965732A1 (fr) * 1998-06-15 1999-12-22 Asea Brown Boveri AG Anneau de sertissage avec prise de vapeur pour turbine
EP1744017A1 (fr) * 2005-07-14 2007-01-17 Siemens Aktiengesellschaft Turbine combinée à vapeur et procédé de fonctionnement d'une turbine combinée à vapeur

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3453848A1 (fr) * 2017-09-08 2019-03-13 Siemens Aktiengesellschaft Turbine à vapeur dotée d'une chambre de piquage
WO2019048184A1 (fr) * 2017-09-08 2019-03-14 Siemens Aktiengesellschaft Turbine à vapeur à chambre de soutirage
CN111065796A (zh) * 2017-09-08 2020-04-24 西门子股份公司 具有排气腔的汽轮机
CN109026206A (zh) * 2018-07-19 2018-12-18 哈尔滨汽轮机厂有限责任公司 一种带蜗壳进汽式高压内缸的整体高压核电汽轮机

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