EP1068429B1 - Dampfturbine - Google Patents

Dampfturbine Download PDF

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Publication number
EP1068429B1
EP1068429B1 EP99924784A EP99924784A EP1068429B1 EP 1068429 B1 EP1068429 B1 EP 1068429B1 EP 99924784 A EP99924784 A EP 99924784A EP 99924784 A EP99924784 A EP 99924784A EP 1068429 B1 EP1068429 B1 EP 1068429B1
Authority
EP
European Patent Office
Prior art keywords
flow
steam
steam turbine
guidance element
flow guidance
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.)
Expired - Lifetime
Application number
EP99924784A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1068429A1 (de
Inventor
Matthias Geiger
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 EP1068429A1 publication Critical patent/EP1068429A1/de
Application granted granted Critical
Publication of EP1068429B1 publication Critical patent/EP1068429B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime 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
    • F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • 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
    • F01D25/30—Exhaust heads, chambers, or the like

Definitions

  • the invention relates to a steam turbine with one along an axis of rotation of an inlet area and one Exhaust area for steam extending flow channel for Steam, which flow channel faces the exhaust steam area an outlet opening expanded with an outlet diameter.
  • a steam turbine is typically used in a power plant to drive a generator and to generate superheated steam or in an industrial plant to drive a work machine used.
  • the steam turbine is called Flow medium serving steam supplied, which is under rendering relaxed work.
  • the steam can be expanded via an evaporation housing the steam turbine in a downstream condenser flow in and condense there.
  • a corresponding one Exhaust steam can flow axially or radially.
  • a steam turbine plant is usually provided for energy, which is a high pressure steam turbine, a medium pressure steam turbine and has a low pressure steam turbine which are connected to each other in terms of flow.
  • the Indian Low pressure steam turbine expanded steam becomes a condenser fed and condensed in this.
  • the efficiency Such a steam turbine plant is used by a large number determined by parameters, in particular the efficiency due to flow resistances occurring in the steam turbine system limited.
  • EP 0 345 700 A1 describes an outlet housing of a turbomachine, especially a steam turbine, indicated for reduction of energy losses due to eddies and detachments of the steam flow.
  • the outlet housing has a circular shape Diffuser on, at the extended end of two separate outflow channels are connected.
  • the rear one from the back of the case limited outflow channel runs straight and crosswise to the machine longitudinal axis.
  • the front outflow channel is over one running against the direction of flow in the diffuser Arch section guided and runs parallel downwards to the rear outflow channel. Both flow channels are separated from each other by a partition.
  • In the back Outflow channel is a spanning the entire width of the channel extending rear sloping wall at the bottom of the diffuser arranged from the diffuser to the partition enough.
  • a device for removing the propellant from axial turbines is disclosed in CH-326 301 A.
  • the propellant discharge space evaporation nozzle
  • an annular diffuser is connected upstream from the flows in the radial direction deflected propellant becomes.
  • the pressure in the last turbine stage can therefore be below the outflow pressure is reduced and pressure losses in this way be reduced in the outflow area.
  • the invention has for its object a steam turbine to be specified at which low flow losses occur.
  • a steam turbine which one extends along an axis of rotation and from an inlet area to an exhaust area for steam towards an outlet opening with an outlet diameter for Evaporation area has expanded flow channel solved that a flow guide assigned to the outlet opening provided for steam flowing out of the outlet opening is, which is the one hand on the outlet diameter out and on the other hand along an outflow direction in an outflow area, wherein the flow guide widened or substantially along the outflow direction has a constant width so that steam is on both sides the flow guide is feasible and downstream of the The steam is mixed, wherein the flow guide on an outer housing which borders an inner housing surrounding the flow channel surrounds.
  • the invention is based on the knowledge that at the Outlet opening of the expanded flow channel (axial-radial diffuser) there is an areal static pressure; which is larger than an area-based static Pressure further downstream, especially at an inflow level Condenser (condenser neck). This is a high Pressure loss before, which is particularly due to strong turbulence the flow arises which is caused by eddies becomes.
  • eddies can arise from the fact that Steam from the outlet opening on the one hand radially downwards and on the other hand is deflected radially upwards, the radial steam deflected upwards further deflected downwards and with the one that was already diverted downwards Steam flows together.
  • the steam first deflected upwards can be divided into two steam streams that flow downwards swirling and forming a vortex each. The origin of these pegs is above the outer one Inner housing that surrounds the flow channel.
  • the flow control element which flows on both sides Steam flows around, preferably extends only partially in the direction of the outflow into the outflow area, so that a mixing area downstream of the flow guiding element down to the inflow level of the condenser remains, ensuring adequate mixing and leveling the total steam flow is reached.
  • On the inflow plane of the condenser is therefore uniform Inflow before, which is a small load on the capacitor guaranteed.
  • the flow guide element extends completely here across the width of that formed by the outer housing Cross-section. This effectively mixes steam falling down at the top and steam flowing down Steam over the existing between the outer casing and inner casing Cross section avoided. A mixture of the in the Vortex braids from the downward flow of steam with the is thus immediately downward steam flow relocated to a further downstream area, whereby a Reduction in pressure loss is achieved.
  • a flow guide element assigned to the outlet opening is an equalization of the mass flow density distribution and a reduction in the vortex strength, especially in the area the mixing of the immediately flowing down Steam and the steam deflected from above.
  • This causes a reduction in pressure losses when flowing out of steam from the outlet opening into the evaporation area and thus contributes to an increase in the efficiency of the steam turbine at.
  • the outflow area which for example between the outlet opening and the inflow plane of a condenser is thus formed only downstream of the flow guiding element mixing of the steam flow is achieved.
  • This Mixing causes up to the inflow level of the condenser also an equalization of the steam flow, which leads to a uniform inflow and loading of the capacitor leads, especially of capacitor plates.
  • the flow guide element preferably extends along an outflow direction with constant width or widened along this outflow direction, especially with increasing Distance from the axis of rotation.
  • the flow control element is preferably geodesic below the axis of rotation arranged thereby effectively guiding the flow of the escaping steam is reached.
  • the steam turbine is preferably in a horizontal axis of rotation comprehensive level divisible and points in this Level a parting line.
  • the flow guide element is opposite to the axis of rotation preferably by a leading angle in the range between 70 ° and 110 °, in particular inclined between 85 ° and 95 °.
  • the flow guide element is inclined at an angle of approximately 90 °, i.e. it is axis normal to the axis of rotation. hereby is the influence of the vortex braids below the parting line the outflow of the widened flow channel (Diffuser) reduced steam flowing down. Consequently is also the formation of a shear flow between the immediate downward flowing steam and the first after the steam flowing out above is laid further downstream, with a corresponding Reduction of flow losses.
  • the flow guiding element is preferably immediately adjacent the outlet opening, whereby the flowing out of the outlet opening Steam after exiting the outlet through the Flow guide is guided. A mix and swirl of steam due to a spacing between the outlet opening and the flow guide element is thereby safely prevented.
  • the flow guide element is preferably essentially just what with the flow guide and for example an outer casing of the steam turbine with a flow channel flat walls is formed. It is also possible that Flow guide element with a curved surface accordingly the desired guidance of the steam for further reduction of flow losses.
  • the concrete form the flow guiding element can be determined by experiments as well determine three-dimensional flow calculations.
  • the flow guiding element is preferably made of sheet metal manufactured. This is a particularly simple constructive one Design of the flow guide, which it for example also allowed afterwards as part of maintenance work equip a steam turbine with a flow control element.
  • the flow guide element is preferably on the outer housing attached. This is one of a long-term stable Attachment of the flow guide also a stiffener of the outer casing of the steam turbine in the exhaust steam area.
  • the steam turbine is preferably as a low pressure steam turbine executed, which in particular executed two-flow is.
  • the flow guide element preferably serves to guide the flow towards a capacitor.
  • FIGS. 1 to 3 each have the same Importance.
  • Figure 1 is a longitudinal section of a low pressure steam turbine 1, which is carried out in two flows. She points a turbine shaft extending along an axis of rotation 2 7 on. In a middle area of the low pressure steam turbine 1 an inlet area 3 for steam 5 is provided, which steam 5 in particular via a not shown Overflow line from a medium-pressure steam turbine, also not shown flows in. On both sides and symmetrically the inlet area 3 extends along the axis of rotation 2 each have a flow channel 6 which is between the turbine shaft 7 and an inner casing surrounding the turbine shaft 7 11 is formed. In each flow channel 6 are alternating in series a plurality of guide vanes 16 and blades 15 arranged.
  • the flow channel 6 widens from the inlet area 3 along the axis of rotation 2 to an evaporation area 4. Assigned to the evaporation area 4 the flow channel 6 has an outlet opening 8. Geodesically below the outlet opening 8 is a flow guide element 10 arranged, which is in a plane that is perpendicular or slightly inclined (up to 15 °, preferably up to 5 °) to the Axis of rotation 2 is along along an outflow direction 14 extends below.
  • the inner housing 11 is of an outer housing Surround 12, which has a boundary for the evaporation area 4 forms and the flow deflection and guidance of the the outlet opening 8 escaping steam 5 is used. Outside of the outer housing 12, the turbine shaft 7 is on corresponding Bearings 17 not explained in more detail.
  • a capacitor 13 for Condensation of the steam 5 arranged below the outer housing 12 .
  • This capacitor 13 has a capacitor housing 21, shown schematically a large number of cooling tubes 18 are arranged, through the cooling liquid during the operation of the condenser 13, especially cooling water flows.
  • a condensate drain 22 is arranged below the cooling tubes 18 , in which the Operation of the condenser on the outside of the cooling tubes 18 formed condensate drips.
  • the capacitor 13 is in each case an open at the bottom, after above formed by walls inclined like a roof Air cooler 19 is provided.
  • Each air cooler 19 is included one from his ridge suction line 20 with a Vacuum pump not shown connected.
  • the steam 5 flows through the Flow channel 6. After exiting the outlet opening 8 in into the evaporation area 4, a partial flow of the steam 5 becomes led upwards and a further partial flow downwards.
  • the upward partial flow is above the outlet opening 8 deflected downwards and flows in an unspecified Outflow area 4A downstream of the two flow guide elements 10 in the capacitor 13.
  • the partial stream of steam flowing upwards 5 is particularly at the apex of the inner housing 11 each split into two steam streams. This split Steam flows swirl and form one Vortex braid from the vertex of the inner housing 11 to in the area of the respective flow guide element 10 extends.
  • Each flow control element 10 creates a spatial separation this vortex braid with the one straight out of the outlet opening 8 downward flowing steam 5 reached. hereby the training in the area of the flow guide elements 10 a shear flow between the vertebrae and the immediate one prevents downward flowing steam 5, whereby a reduction in pressure loss when flowing into the Capacitor 13 is reached.
  • the outlet opening 8 has one circular cross section with an outlet diameter 9 on.
  • the steam turbine 1 is with respect to a horizontal plane 23, in which the axis of rotation 2 lies divisible.
  • the flow guide element 10 is geodetically below this Horizontal plane 23 arranged and expanded in the outflow direction 14 with increasing distance from the horizontal plane 23. It is also possible for the flow guiding element 10 in the outflow direction at least partially or predominantly has a constant width. It can also continue only at a distance from the horizontal plane 23 to the outlet opening 8 connect.
  • the flow guide element 10 encloses semicircular the outlet opening 8 to the horizontal plane 23 approaches and widens up to the outer housing 12. It is firmly connected to the outer housing 12, for example screwed or welded. This makes both Stiffening of the outer housing 12 in the evaporation area 4 as well a permanent attachment of the flow guide segment 10 is achieved.
  • FIG. 3 shows a section of the evaporation area 4 in the direction to the capacitor 13 geodetically below the axis of rotation 2 shown.
  • the flow of steam 5 is shown by arrows, wherein the length of the arrows is a measure of the flow velocity the steam 5 represents. It can be seen that the behind the last blade 15, steam escaping 5 in the evaporation area 4 is deflected downwards by approx. 90 ° and is braked at the same time.
  • To redirect the steam 5 is both an extension of the inner housing 11 and a corresponding configuration of the outer housing 12 intended. At the extension of the inner housing 11 closes the flow guide element 10, whereby between the flow guide element 10 and outer housing 12 a channel area for the steam 5 thus deflected is formed.
  • the flow control element 10 is opposite the axis of rotation 2 by a leading angle ⁇ inclined, which is preferably in the range between 70 ° and 110 °, in the case shown is about 90 °. geodesic below the flow guide element 10, the flow of the downward deflected steam 5 with the flow of the first upwards and then downwards deflected steam 5 together. The interaction of these two partial flows with one another by the arrangement of the guide segment 10 compared to the case, in which no flow guide element 10 is provided, clearly reduced. This will also form a Shear flow at least significantly reduced and therefore one Reduction in pressure loss achieved.
EP99924784A 1998-04-06 1999-04-06 Dampfturbine Expired - Lifetime EP1068429B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19815375 1998-04-06
DE19815375 1998-04-06
PCT/DE1999/001043 WO1999051858A1 (de) 1998-04-06 1999-04-06 Dampfturbine

Publications (2)

Publication Number Publication Date
EP1068429A1 EP1068429A1 (de) 2001-01-17
EP1068429B1 true EP1068429B1 (de) 2004-06-16

Family

ID=7863757

Family Applications (1)

Application Number Title Priority Date Filing Date
EP99924784A Expired - Lifetime EP1068429B1 (de) 1998-04-06 1999-04-06 Dampfturbine

Country Status (7)

Country Link
US (1) US6447247B1 (zh)
EP (1) EP1068429B1 (zh)
JP (1) JP4249903B2 (zh)
KR (1) KR20010042504A (zh)
CN (1) CN1165670C (zh)
DE (1) DE59909753D1 (zh)
WO (1) WO1999051858A1 (zh)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6450474B1 (en) 2000-03-09 2002-09-17 Lord Corporation X-configuration engine mounting with locking end plates
US6783321B2 (en) 2002-11-06 2004-08-31 General Electric Company Diffusing coupling cover for axially joined turbines
JP4557787B2 (ja) * 2005-04-28 2010-10-06 株式会社東芝 蒸気タービン
US7640724B2 (en) * 2006-01-25 2010-01-05 Siemens Energy, Inc. System and method for improving the heat rate of a turbine
US20110088379A1 (en) * 2009-10-15 2011-04-21 General Electric Company Exhaust gas diffuser
US8439633B2 (en) * 2010-01-04 2013-05-14 General Electric Company Hollow steam guide diffuser having increased pressure recovery
US8475125B2 (en) * 2010-04-13 2013-07-02 General Electric Company Shroud vortex remover
US9249687B2 (en) 2010-10-27 2016-02-02 General Electric Company Turbine exhaust diffusion system and method
CN104718350B (zh) * 2012-10-11 2016-06-22 三菱日立电力系统株式会社 冷凝器
JP6113586B2 (ja) * 2013-06-27 2017-04-12 株式会社東芝 復水器
KR101811223B1 (ko) 2013-08-28 2017-12-21 가부시끼가이샤 도시바 증기 터빈
JP2015105867A (ja) * 2013-11-29 2015-06-08 株式会社東芝 シュラウド支持装置およびシュラウド支持装置改造方法
EP3048264A1 (en) * 2015-01-23 2016-07-27 Alstom Technology Ltd Method for retrofitting steam turbine
JP6847673B2 (ja) * 2017-01-17 2021-03-24 株式会社東芝 タービン排気室
FR3075871A1 (fr) * 2017-12-21 2019-06-28 Denis Marchand Turbine a absorption pour la transformation de chaleur en energie ou en froid.
TW202019330A (zh) * 2018-10-12 2020-06-01 義大利商辛巴利集團公司 用於熱飲料製備的蒸汽分配設備
CN114508392B (zh) * 2021-12-29 2023-07-18 东方电气集团东方汽轮机有限公司 一种汽轮机高压进汽室结构

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NL191037A (zh) * 1953-10-23
US3120374A (en) * 1962-08-03 1964-02-04 Gen Electric Exhaust scroll for turbomachine
US3149470A (en) * 1962-08-29 1964-09-22 Gen Electric Low pressure turbine exhaust hood
US4557113A (en) * 1984-06-15 1985-12-10 Westinghouse Electric Corp. Single low pressure turbine with zoned condenser
US4567729A (en) * 1984-09-17 1986-02-04 Westinghouse Electric Corp. Method of forming a zone condenser with a single low pressure double flow turbine
CS272676B1 (en) * 1988-06-07 1991-02-12 Stastny Miroslav Outlet branch for bladed machine
US5257906A (en) * 1992-06-30 1993-11-02 Westinghouse Electric Corp. Exhaust system for a turbomachine
DE4325457C1 (de) * 1993-07-29 1994-07-28 Man B & W Diesel Ag Abströmgehäuse einer Axialturbine
US5518366A (en) * 1994-06-13 1996-05-21 Westinghouse Electric Corporation Exhaust system for a turbomachine
JP3776580B2 (ja) * 1998-01-19 2006-05-17 三菱重工業株式会社 軸流タービンの排気装置

Also Published As

Publication number Publication date
DE59909753D1 (de) 2004-07-22
WO1999051858A1 (de) 1999-10-14
JP4249903B2 (ja) 2009-04-08
CN1296549A (zh) 2001-05-23
JP2002510769A (ja) 2002-04-09
EP1068429A1 (de) 2001-01-17
US6447247B1 (en) 2002-09-10
KR20010042504A (ko) 2001-05-25
CN1165670C (zh) 2004-09-08

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