EP1954922A1 - Turbine a vapeur a entretoises porteuses - Google Patents

Turbine a vapeur a entretoises porteuses

Info

Publication number
EP1954922A1
EP1954922A1 EP06819859A EP06819859A EP1954922A1 EP 1954922 A1 EP1954922 A1 EP 1954922A1 EP 06819859 A EP06819859 A EP 06819859A EP 06819859 A EP06819859 A EP 06819859A EP 1954922 A1 EP1954922 A1 EP 1954922A1
Authority
EP
European Patent Office
Prior art keywords
bearing
steam turbine
struts
shaft
strut
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
EP06819859A
Other languages
German (de)
English (en)
Other versions
EP1954922B1 (fr
Inventor
Henning Almstedt
Stefan Essink
Norbert Pieper
Mark-Andre 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 EP06819859A priority Critical patent/EP1954922B1/fr
Priority to PL06819859T priority patent/PL1954922T3/pl
Publication of EP1954922A1 publication Critical patent/EP1954922A1/fr
Application granted granted Critical
Publication of EP1954922B1 publication Critical patent/EP1954922B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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
    • 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 a Abdampfge- 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 ⁇ known from the prior art bearing supporting strut 18. This is designed as a solid body and has bores 34 to the internal receiving supply lines, such as sealing steam lines. 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 brace 18 by the direct Be aufschlagung with Turbinenabdampf.
  • the temperature of the exhaust steam can ren depending on the operating point strongly variie ⁇ , whereby the deformation behavior of the bearing strut 18 directly influenced.
  • the bearing strut arrangements known in the prior art are therefore sensitive to temperature influences from inside and outside. Therefore, sealing steam temperatures are limited to values of below 150 0 C in the art and seen large radial plays between the bearing struts and the exhaust-steam casing and the shaft bearing forth.
  • An object underlying the invention is to improve a steam turbine of the type mentioned in that thermodynamic efficiency advantages result for the entire turbine.
  • each of the at least two bearing aim for a disposed in the respective bearing strut for guiding a cooling cavity coolant and said cooling cavities of the at least two bearing struts are fluidically connected via a sealed connection from ⁇ cavity in the region of the shaft bearing.
  • the bearing struts can be effectively cooled by passing a suitable coolant from the inside.
  • a suitable coolant for cooling air as a coolant, convection may 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 passed through 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 can be generated for the entire turbine.
  • Ver ⁇ realization of the cooling system according to the invention the radial clearance can even be reduced so that the bearing ⁇ striving 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 0 C are in the steam turbine according to the invention possible. This reduces the complexity of the sealing steam system and therefore saves manufacturing and maintenance costs.
  • 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. So that the flow ⁇ dynamics of the exhaust steam mass flow is not affected.
  • 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 shaft bearing is held by means of at least three bearing struts
  • 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 directly to the corresponding portion of the strut surface along ge ⁇ be leads, which optimum cooling of the same. Due to the extent of the cooling cavities in the longitudinal direction of the respective bearing strut, the coolant can flow ⁇ technically particularly simple lead through the contiguous, flowed through by the coolant pressure chamber.
  • 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 proposed according to the invention cooling means for the bearing struts of the low pressure steam turbine made ⁇ light a partial explanatory by reducing the radial clearances especially before ⁇ increasing the thermodynamic efficiency, both during normal operation and in the 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 tra ⁇ low-pressure low-pressure turbine bearing struts are located directly in the low-pressure evaporative mass flow.
  • Fig. 1 is a cross-sectional view of an inventive
  • Fig. 2 is a detail view of the sectional view of a low pressure steam turbine in the loading shown in Fig. 1 ⁇ reaching a lower bearing supporting strut,
  • Fig. 3 is a detail view of that shown in Fig.l.
  • Fig. 4 is a cross-sectional view of a known from the prior art bearing bearing strut. 1 shows the structure of a low-pressure steam turbine 10 according to the invention.
  • 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. These are the lower bearing bearing struts 18 and the upper
  • Bearing strut 20 designed as a hollow body and welded directly between the outer Abdampfgekoruse 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 18 has a strut, the exhaust steam 12 with the shafts 14 connecting ⁇ seal housing, ⁇ solid executed bearing support 22.
  • this bearing support 22 extends in the longitudinal direction of the same as a ventilation duct running cooling cavity 24.
  • the bearing strut 18 is surrounded by a heat protection jacket 30 having a compensator 32 for
  • 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 connection ⁇ cavity 28 in the shaft seal housing 14 ⁇ mig respective cooling cavities 24 connects sternför all bearing struts, ie both the three lower bearing struts 18 and the upper bearing strut 20.
  • 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-gas casing 12.
  • a cooling cavity 24 designed as a ventilation channel is likewise guided along this, which opens via an opening 25 in the exhaust steam housing 12.
  • cooling cavity 24 of the OBE ⁇ ren bearing strut 20 accommodate the whole in the three supporting bearing struts 18 brought up cooling air flow is correspondingly larger the cross section of the cooling cavity 24 of the upper bearing strut 20th
  • Cooling air 26 is reduced compared to the cooling effect of the run in the bearing supporting struts 18 cooling air 26 since the temperature ⁇ is already heated structure of the cooling air 26 while passing through the lower bearing struts 18th
  • the cooling requirement of the upper bearing strut 20 is, however, lower, since it is exposed to lower mechanical loads as a non-bearing bearing strut and is therefore less susceptible to deformation.
  • the cooling system according to the invention as shown in Fig. 1, to operate. That is, the cooling air flow 26 should be directed from bottom to top, ie first pass through the lower bearing bearing struts 18 and only then the upper bearing strut 20.

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)
EP06819859A 2005-12-01 2006-11-30 Turbine a vapeur a entretoises porteuses Not-in-force EP1954922B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP06819859A EP1954922B1 (fr) 2005-12-01 2006-11-30 Turbine a vapeur a entretoises porteuses
PL06819859T PL1954922T3 (pl) 2005-12-01 2006-11-30 Turbina parowa z zastrzałami łożyskowymi

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
EP05026254A EP1793091A1 (fr) 2005-12-01 2005-12-01 Turbine à vapeur avec des entretoises pour le palier
PCT/EP2006/069094 WO2007063088A1 (fr) 2005-12-01 2006-11-30 Turbine a vapeur a entretoises porteuses
EP06819859A EP1954922B1 (fr) 2005-12-01 2006-11-30 Turbine a vapeur a entretoises porteuses

Publications (2)

Publication Number Publication Date
EP1954922A1 true EP1954922A1 (fr) 2008-08-13
EP1954922B1 EP1954922B1 (fr) 2010-07-21

Family

ID=36593748

Family Applications (2)

Application Number Title Priority Date Filing Date
EP05026254A Withdrawn EP1793091A1 (fr) 2005-12-01 2005-12-01 Turbine à vapeur avec des entretoises pour le palier
EP06819859A Not-in-force EP1954922B1 (fr) 2005-12-01 2006-11-30 Turbine a vapeur a entretoises porteuses

Family Applications Before (1)

Application Number Title Priority Date Filing Date
EP05026254A Withdrawn EP1793091A1 (fr) 2005-12-01 2005-12-01 Turbine à vapeur avec des entretoises pour le palier

Country Status (10)

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

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9194246B2 (en) 2011-09-23 2015-11-24 General Electric Company Steam turbine LP casing cylindrical struts between stages

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US8979477B2 (en) * 2011-03-09 2015-03-17 General Electric Company System for cooling and purging exhaust section of gas turbine engine
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
US9631517B2 (en) 2012-12-29 2017-04-25 United Technologies Corporation Multi-piece fairing for monolithic turbine exhaust case
WO2014105603A1 (fr) 2012-12-29 2014-07-03 United Technologies Corporation Bouclier thermique en plusieurs pièces
EP2938863B1 (fr) 2012-12-29 2019-09-25 United Technologies Corporation Liaison mécanique destinée à un écran thermique segmenté
WO2014105602A1 (fr) 2012-12-29 2014-07-03 United Technologies Corporation Bouclier thermique pour carter
US9982561B2 (en) * 2012-12-29 2018-05-29 United Technologies Corporation Heat shield for cooling a strut
EP2853759A1 (fr) 2013-09-30 2015-04-01 Siemens Aktiengesellschaft Palier à huile avec système de drainage, turbine à gaz comportant un palier à huile
US20150354382A1 (en) * 2014-06-06 2015-12-10 General Electric Company Exhaust frame cooling via strut cooling passages
CA2936180A1 (fr) 2015-07-24 2017-01-24 Pratt & Whitney Canada Corp. Systeme et methode de refroidissement multi ailette
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
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

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Publication number Priority date Publication date Assignee Title
US9194246B2 (en) 2011-09-23 2015-11-24 General Electric Company Steam turbine LP casing cylindrical struts between stages

Also Published As

Publication number Publication date
US20100054927A1 (en) 2010-03-04
JP4792507B2 (ja) 2011-10-12
CN101321929B (zh) 2011-01-26
CN101321929A (zh) 2008-12-10
WO2007063088A1 (fr) 2007-06-07
EP1954922B1 (fr) 2010-07-21
ATE474998T1 (de) 2010-08-15
US8550773B2 (en) 2013-10-08
JP2009517592A (ja) 2009-04-30
EP1793091A1 (fr) 2007-06-06
PL1954922T3 (pl) 2010-12-31
DE502006007506D1 (de) 2010-09-02
RU2392450C2 (ru) 2010-06-20
RU2008126725A (ru) 2010-01-10
ES2348678T3 (es) 2010-12-10

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