EP1793091A1 - Dampfturbine mit Lagerstreben - Google Patents

Dampfturbine mit Lagerstreben Download PDF

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Publication number
EP1793091A1
EP1793091A1 EP05026254A EP05026254A EP1793091A1 EP 1793091 A1 EP1793091 A1 EP 1793091A1 EP 05026254 A EP05026254 A EP 05026254A EP 05026254 A EP05026254 A EP 05026254A EP 1793091 A1 EP1793091 A1 EP 1793091A1
Authority
EP
European Patent Office
Prior art keywords
bearing
steam turbine
struts
steam
shaft
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Withdrawn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
EP05026254A
Other languages
German (de)
English (en)
French (fr)
Inventor
Henning Almstedt
Stefan Essink
Norbert Pieper
Mark-André Dr. Schwarz
Kais Sfar
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
Siemens AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Siemens AG filed Critical Siemens AG
Priority to EP05026254A priority Critical patent/EP1793091A1/de
Priority to RU2008126725/06A priority patent/RU2392450C2/ru
Priority to ES06819859T priority patent/ES2348678T3/es
Priority to PCT/EP2006/069094 priority patent/WO2007063088A1/de
Priority to US12/085,699 priority patent/US8550773B2/en
Priority to DE502006007506T priority patent/DE502006007506D1/de
Priority to JP2008542757A priority patent/JP4792507B2/ja
Priority to CN2006800450030A priority patent/CN101321929B/zh
Priority to AT06819859T priority patent/ATE474998T1/de
Priority to EP06819859A priority patent/EP1954922B1/de
Priority to PL06819859T priority patent/PL1954922T3/pl
Publication of EP1793091A1 publication Critical patent/EP1793091A1/de
Withdrawn legal-status Critical Current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
    • F01D9/00—Stators
    • F01D9/06—Fluid supply conduits to nozzles or the like
    • F01D9/065—Fluid supply or removal conduits traversing the working fluid flow, e.g. for lubrication-, cooling-, or sealing fluids
    • 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
    • F01D25/16—Arrangement of bearings; Supporting or mounting bearings in casings
    • F01D25/162—Bearing supports

Definitions

  • the invention relates to a steam turbine with an exhaust steam housing for guiding a Abdampfmassenstroms, a shaft bearing for supporting a turbine shaft and at least two bearing struts, by means of which the shaft bearing is attached to the exhaust steam housing.
  • FIG. 4 shows a cross-sectional view of a bearing support strut 18 known from the prior art. It is designed as a solid body and has bores 34 for internal reception of supply lines, such as e.g. Sealing steam pipes on. Between the supply lines and the bearing strut 18 only a small clearance is provided, which is why an internal heat transfer between the supply lines, in particular sealing steam lines and the bearing strut 18 takes place. Also from the outside, there is a heat input to the bearing strut 18 by the direct application of turbine exhaust steam.
  • supply lines such as e.g. Sealing steam pipes on.
  • the temperature of the Abdampfmassenstroms can vary greatly depending on the operating point, whereby the deformation behavior of the bearing strut 18 is directly influenced.
  • the bearing strut arrangements known in the prior art are therefore sensitive to temperature influences from inside and outside. In the prior art, therefore, sealing steam temperatures are limited to values below 150 ° C, and provided large radial clearance between the bearing struts and the exhaust steam housing or the shaft bearing.
  • An object of the invention is to improve a steam turbine of the type mentioned in that thermodynamic efficiency advantages for the entire turbine arise.
  • each of the at least two bearing struts has a arranged in the respective bearing strut cooling cavity for guiding a coolant and the cooling cavities of the at least two bearing struts are fluidly connected via a closed connection cavity in the region of the shaft bearing.
  • Coolant for example, is cooling air in question, in which case the cooling cavities of the bearing struts are then designed as ventilation cavities through which cooling air flows.
  • the bearing struts can be effectively cooled by passing a suitable coolant from the inside.
  • a suitable coolant from the inside.
  • convection can cause internal cooling air flow through the bearing struts.
  • ambient air is sucked through at least one of the bearing struts, passed through the connecting cavity and discharged by another bearing strut back to the environment.
  • the heat can be dissipated within the bearing struts and the influence of the temperature of the Abdampfmassenstroms outside the bearing struts and / or the temperature of running within the bearing struts supply media to the deformation behavior of the bearing struts are minimized.
  • the radial clearance to the shaft bearing and Abdampfgephaseuse be designed smaller and less conservative.
  • thermodynamic efficiency advantages for the entire turbine can be generated.
  • the radial play can even be reduced so that the bearing struts can be welded directly between the outer Abdampfgephaseuse and an inner shaft seal housing of the shaft bearing.
  • higher sealing steam temperatures can now be admitted in sealing steam lines laid within the bearing struts than was customary in the prior art. Sealing steam temperatures above 150 ° C are in the steam turbine according to the invention possible. This reduces the complexity of the sealing steam system and therefore saves costs in manufacture and maintenance.
  • the cooling cavities of the at least two bearing struts each have an opening facing the exhaust steam housing.
  • these openings are arranged on the exhaust steam housing facing the ends of the bearing struts.
  • the cooling cavities of the at least two bearing struts and the connecting cavity form a pressure chamber enclosed by the exhaust steam flow of the steam turbine.
  • the shaft bearing has a shaft seal housing and the connecting cavity is disposed within the shaft seal housing.
  • the connection cavity is formed by means of leads routed outside a shaft seal housing.
  • the connection cavity is formed within the shaft bearing.
  • the connecting cavity is channel-shaped, in particular in the case of at least three bearing struts designed as a star-shaped channel system.
  • the connection cavity can forward the coolant particularly well between the bearing struts.
  • At least one of the bearing struts is arranged in the lower portion of the steam turbine and thus formed as a bearing bearing strut.
  • the inventive cooling of this bearing bearing strut by means of a guided in a cooling cavity coolant is particularly advantageous in such a bearing bearing strut because of the large mechanical forces acting thereon.
  • at least two bearing struts are designed as bearing bearing struts, and are thus arranged in the lower portion of the steam turbine.
  • the weight of the turbine shaft mounted in the shaft bearing is thereby distributed over a plurality of bearing struts, which in turn enables a reduction of the radial play.
  • the at least two bearing struts are each formed as a hollow body.
  • the interior of the hollow body forms the corresponding cooling cavity.
  • the cooling effect of the guided in the cooling cavity coolant to the bearing strut is particularly high, as it flows along the outer wall of the hollow body.
  • the cooling cavities each extend along at least a portion of the corresponding strut surfaces in the longitudinal direction of the respective bearing strut.
  • the coolant can be performed directly on the corresponding portion of the strut surface along, allowing optimal cooling of the same. Due to the extent of the cooling cavities in the longitudinal direction of the respective bearing strut, the coolant can be fluidly particularly easily guided by the contiguous, flowed through by the coolant pressure chamber.
  • At least one sealing steam line is arranged within the ventilation channels.
  • the steam turbine is designed as a low-pressure turbine with axial outflow.
  • the heat transfer through the exhaust steam mass flow to the bearing struts has an especially negative effect on embodiments used in the prior art.
  • the cooling device provided according to the invention for the bearing struts of the low-pressure steam turbine enables a particularly advantageous increase in the thermodynamic efficiency by reducing the radial play, both in normal operation and in transient operation of the turbine.
  • the shaft bearing is designed as a rear shaft bearing of the low-pressure steam turbine.
  • the rear shaft bearing and the supporting low-pressure steam turbine bearing struts are located directly in the low-pressure exhaust steam mass flow.
  • the low-pressure steam turbine 10 has an outer exhaust steam housing 12 and an inner shaft seal housing 14.
  • the shaft seal housing 14 includes a rear shaft bearing 16 for receiving a turbine shaft not shown in the drawing.
  • the shaft seal housing 14 is attached to the exhaust steam housing 12 via three lower bearing bearing struts 18 and an upper bearing strut 20.
  • the lower bearing bearing struts 18 and the upper bearing strut 20 are designed as a hollow body and welded directly between the outer Abdampfgephase 12 and the inner shaft seal housing 14.
  • FIG. 2 shows a detail of the low-pressure steam turbine shown in FIG. 1 in the region of one of the three lower bearing bearing struts 18.
  • the bearing strut 18 has a solid support bearing 22 connecting the exhaust steam housing 12 with the shaft seal housing 14. Furthermore, the bearing strut 18 is surrounded by a heat protection jacket 30, which has a compensator 32 to compensate for a change in length of the heat protection jacket 30. Via an access in the exhaust steam housing 12, cooling air 26 is sucked into the cooling cavity 24 of the bearing strut 18 via an opening 25 in the cooling cavity 24.
  • the cooling air 26 enters into a connecting cavity 28 of the shaft seal housing 14 after flowing through the cooling cavity 24.
  • the connecting cavity 28 in the shaft seal housing 14 connects star-shaped respective cooling cavities 24 of all bearing struts, ie both the three lower bearing struts 18 and the upper bearing strut 20. This creates a closed by Abdampfmassenstrom, with cooling air flowed through so-called Lagersterndruckraum, the cooling cavities 24 of all bearing struts 18 and 20 and the connecting cavity 28 of the shaft seal housing 14 includes.
  • the lower supporting bearing struts 18 are all flowed through with shaft seal housing side sucked fresh air, which is then completely discharged through the non-supporting upper bearing strut 20 back to the environment.
  • FIG. 3 also shows a section of the low-pressure steam turbine 10 in the region of the upper bearing strut 20.
  • This also contains a massively designed bearing support 22 connecting the inner shaft seal housing 14 to the outer exhaust housing 12.
  • a cooling cavity 24 designed as a ventilation channel is likewise guided along the latter an opening 25 opens into the exhaust steam housing 12. Since the cooling cavity 24 of the upper bearing strut 20 must accommodate the entire brought in the three supporting bearing struts 18 cooling air flow, the cross section of the cooling cavity 24 of the upper bearing strut 20 is dimensioned correspondingly larger.
  • the cooling effect of guided in the cooling cavity 24 of the upper bearing bar 20 cooling air 26 is reduced compared to the cooling effect of the guided in the bearing bearing struts 18 cooling air 26, since the temperature of the cooling air 26 is already heated when passing through the lower bearing struts 18.
  • the cooling requirement of the upper bearing brace 20 is, however, lower, since this is exposed as a non-bearing bearing strut lower mechanical loads and therefore less susceptible to deformation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Support Of The Bearing (AREA)
EP05026254A 2005-12-01 2005-12-01 Dampfturbine mit Lagerstreben Withdrawn EP1793091A1 (de)

Priority Applications (11)

Application Number Priority Date Filing Date Title
EP05026254A EP1793091A1 (de) 2005-12-01 2005-12-01 Dampfturbine mit Lagerstreben
RU2008126725/06A RU2392450C2 (ru) 2005-12-01 2006-11-30 Паровая турбина с распорками для подшипника
ES06819859T ES2348678T3 (es) 2005-12-01 2006-11-30 Turbina de vapor con barras de apoyo.
PCT/EP2006/069094 WO2007063088A1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben
US12/085,699 US8550773B2 (en) 2005-12-01 2006-11-30 Steam turbine having bearing struts
DE502006007506T DE502006007506D1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben
JP2008542757A JP4792507B2 (ja) 2005-12-01 2006-11-30 軸受支柱付き蒸気タービン
CN2006800450030A CN101321929B (zh) 2005-12-01 2006-11-30 配有轴承支撑体的汽轮机
AT06819859T ATE474998T1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben
EP06819859A EP1954922B1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben
PL06819859T PL1954922T3 (pl) 2005-12-01 2006-11-30 Turbina parowa z zastrzałami łożyskowymi

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP05026254A EP1793091A1 (de) 2005-12-01 2005-12-01 Dampfturbine mit Lagerstreben

Publications (1)

Publication Number Publication Date
EP1793091A1 true EP1793091A1 (de) 2007-06-06

Family

ID=36593748

Family Applications (2)

Application Number Title Priority Date Filing Date
EP05026254A Withdrawn EP1793091A1 (de) 2005-12-01 2005-12-01 Dampfturbine mit Lagerstreben
EP06819859A Not-in-force EP1954922B1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP06819859A Not-in-force EP1954922B1 (de) 2005-12-01 2006-11-30 Dampfturbine mit lagerstreben

Country Status (10)

Country Link
US (1) US8550773B2 (zh)
EP (2) EP1793091A1 (zh)
JP (1) JP4792507B2 (zh)
CN (1) CN101321929B (zh)
AT (1) ATE474998T1 (zh)
DE (1) DE502006007506D1 (zh)
ES (1) ES2348678T3 (zh)
PL (1) PL1954922T3 (zh)
RU (1) RU2392450C2 (zh)
WO (1) WO2007063088A1 (zh)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8979477B2 (en) * 2011-03-09 2015-03-17 General Electric Company System for cooling and purging exhaust section of gas turbine engine
US9194246B2 (en) 2011-09-23 2015-11-24 General Electric Company Steam turbine LP casing cylindrical struts between stages
PL220729B1 (pl) 2011-10-03 2015-12-31 Gen Electric Układ turbiny gazowej
US9039346B2 (en) * 2011-10-17 2015-05-26 General Electric Company Rotor support thermal control system
US9085995B2 (en) * 2012-04-18 2015-07-21 Hamilton Sundstrand Corporation Anti-vortex shedding generator for APU support
US9376934B2 (en) 2012-08-24 2016-06-28 General Electric Company Cooling circuit for reducing thermal growth differential of turbine rotor and shell supports
WO2014105602A1 (en) 2012-12-29 2014-07-03 United Technologies Corporation Heat shield for a casing
US10294819B2 (en) 2012-12-29 2019-05-21 United Technologies Corporation Multi-piece heat shield
US9631517B2 (en) 2012-12-29 2017-04-25 United Technologies Corporation Multi-piece fairing for monolithic turbine exhaust case
US10378370B2 (en) 2012-12-29 2019-08-13 United Technologies Corporation Mechanical linkage for segmented heat shield
US9982561B2 (en) * 2012-12-29 2018-05-29 United Technologies Corporation Heat shield for cooling a strut
EP2853759A1 (en) 2013-09-30 2015-04-01 Siemens Aktiengesellschaft Oil bearing with drain system, gas turbine comprising such an oil bearing
US20150354382A1 (en) * 2014-06-06 2015-12-10 General Electric Company Exhaust frame cooling via strut cooling passages
US10247035B2 (en) 2015-07-24 2019-04-02 Pratt & Whitney Canada Corp. Spoke locking architecture
US10443449B2 (en) 2015-07-24 2019-10-15 Pratt & Whitney Canada Corp. Spoke mounting arrangement
US10920612B2 (en) 2015-07-24 2021-02-16 Pratt & Whitney Canada Corp. Mid-turbine frame spoke cooling system and method
CN105257347B (zh) * 2015-11-17 2019-01-15 上海电气电站设备有限公司 轴向排汽排汽缸轴承座冷却结构
CN105275511B (zh) * 2015-11-17 2018-01-19 上海电气电站设备有限公司 轴承座落地支撑的轴向排汽排汽缸

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB623615A (en) * 1947-05-06 1949-05-19 Frederick William Walton Morle Improvements in or relating to gas-turbine-engines
GB819111A (en) * 1957-10-25 1959-08-26 Blackburn & Gen Aircraft Ltd Improvements in and relating to the supporting members of the shaft bearing of fluidengines
GB1455974A (en) * 1974-04-09 1976-11-17 Bbc Sulzer Turbomaschinen Gas turbine plant
EP0509802A1 (en) * 1991-04-16 1992-10-21 General Electric Company Tip clearance control apparatus

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Publication number Priority date Publication date Assignee Title
FR2646469B1 (fr) * 1989-04-28 1991-07-05 Alsthom Gec Systeme de supportage du rotor dans une turbine a echappement axial avec le palier cote echappement integre a la fondation
CH685448A5 (de) * 1991-03-28 1995-07-14 Asea Brown Boveri Ag Ansaldo C Dampfturbogruppe.
JP2954797B2 (ja) * 1992-10-05 1999-09-27 株式会社東芝 蒸気タ−ビンの強制冷却装置
DE19615011A1 (de) * 1995-07-19 1997-01-23 Siemens Ag Bauteil für einen Abgasstutzen einer Strömungsmaschine, insbesondere einer Dampfturbine
US5819525A (en) * 1997-03-14 1998-10-13 Westinghouse Electric Corporation Cooling supply manifold assembly for cooling combustion turbine components
US6430931B1 (en) * 1997-10-22 2002-08-13 General Electric Company Gas turbine in-line intercooler
US6224327B1 (en) * 1998-02-17 2001-05-01 Mitsubishi Heavy Idustries, Ltd. Steam-cooling type gas turbine
JP4527824B2 (ja) * 1998-12-22 2010-08-18 ゼネラル・エレクトリック・カンパニイ タービンロータの軸受用冷却系
JP2002309906A (ja) * 2001-04-11 2002-10-23 Mitsubishi Heavy Ind Ltd 蒸気冷却型ガスタービン
JP2003206701A (ja) * 2002-01-11 2003-07-25 Mitsubishi Heavy Ind Ltd ガスタービンのタービンローターおよびガスタービン
DE10355738A1 (de) * 2003-11-28 2005-06-16 Alstom Technology Ltd Rotor für eine Turbine

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB623615A (en) * 1947-05-06 1949-05-19 Frederick William Walton Morle Improvements in or relating to gas-turbine-engines
GB819111A (en) * 1957-10-25 1959-08-26 Blackburn & Gen Aircraft Ltd Improvements in and relating to the supporting members of the shaft bearing of fluidengines
GB1455974A (en) * 1974-04-09 1976-11-17 Bbc Sulzer Turbomaschinen Gas turbine plant
EP0509802A1 (en) * 1991-04-16 1992-10-21 General Electric Company Tip clearance control apparatus

Also Published As

Publication number Publication date
PL1954922T3 (pl) 2010-12-31
ATE474998T1 (de) 2010-08-15
RU2008126725A (ru) 2010-01-10
DE502006007506D1 (de) 2010-09-02
US8550773B2 (en) 2013-10-08
JP4792507B2 (ja) 2011-10-12
WO2007063088A1 (de) 2007-06-07
JP2009517592A (ja) 2009-04-30
CN101321929A (zh) 2008-12-10
CN101321929B (zh) 2011-01-26
RU2392450C2 (ru) 2010-06-20
EP1954922A1 (de) 2008-08-13
US20100054927A1 (en) 2010-03-04
ES2348678T3 (es) 2010-12-10
EP1954922B1 (de) 2010-07-21

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