EP0953099B1 - Turbine a vapeur - Google Patents

Turbine a vapeur Download PDF

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Publication number
EP0953099B1
EP0953099B1 EP98904017A EP98904017A EP0953099B1 EP 0953099 B1 EP0953099 B1 EP 0953099B1 EP 98904017 A EP98904017 A EP 98904017A EP 98904017 A EP98904017 A EP 98904017A EP 0953099 B1 EP0953099 B1 EP 0953099B1
Authority
EP
European Patent Office
Prior art keywords
turbine
pressure
steam
pressure turbine
turbine section
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.)
Revoked
Application number
EP98904017A
Other languages
German (de)
English (en)
Other versions
EP0953099A1 (fr
Inventor
Ralf Bell
Armin Drosdziok
Mikhail Simkine
Ingo Stephan
Volker Simon
Ulrich Capelle
Jan-Erik MÜHLE
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
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First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=7817277&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0953099(B1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Siemens AG filed Critical Siemens AG
Publication of EP0953099A1 publication Critical patent/EP0953099A1/fr
Application granted granted Critical
Publication of EP0953099B1 publication Critical patent/EP0953099B1/fr
Anticipated expiration legal-status Critical
Revoked 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
    • F01D1/00—Non-positive-displacement machines or engines, e.g. steam turbines
    • F01D1/02—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines
    • F01D1/16—Non-positive-displacement machines or engines, e.g. steam turbines with stationary working-fluid guiding means and bladed or like rotor, e.g. multi-bladed impulse steam turbines characterised by having both reaction stages and impulse stages

Definitions

  • the invention relates to a steam turbine with a high-pressure partial turbine and one fluidically connected to the latter Intermediate-pressure turbine.
  • Known steam turbines are used in action turbines (too Constant pressure turbines) and reaction turbines (also Called overpressure turbines). They have a turbine shaft with blades arranged on it and an inner housing with blades arranged between axially spaced barrels Guide vanes on.
  • the isentropic reaction degree r for a thermal Fluid machine the percentage distribution of the isentropic Enthalpy gradient in the blades to the entire isentropic Enthalpy gradient over a step consisting of vane ring and designated blade ring.
  • the classic overpressure level as well as the Equal pressure level applied. The latter usually with a slightly different degree of reaction r.
  • a constant pressure turbine is usually in Chamber construction and a pressure turbine in drum construction executed.
  • a chamber turbine has a housing, which through axially spaced shelves is divided into several chambers. In each of these chambers runs a disc-shaped impeller, on the outer circumference Blades are attached while the vanes are in the shelves are inserted.
  • An advantage of the chamber design is that the shelves at their inner edge quite effective using labyrinth seals against the turbine shaft can be sealed. Because the gasket knife is small, the gap cross sections and thus the Gap leakage currents small.
  • This type is known Turbines only with small degrees of reaction, i.e. large gradients and therefore uses a small number of stages. The pressure difference is on both sides of an impeller disc small degree of reaction low, in the limit case even zero. On Axial thrust exerted on the rotor remains low and can be taken up by a thrust bearing.
  • the blades are immediate in a drum turbine arranged on the circumference of a drum-shaped turbine shaft.
  • the Guide vanes are either directly in the housing of the steam turbine or used in a special guide vane carrier.
  • DE-AS 20 54 465 is a steam turbine in drum design described.
  • a pot-shaped outer housing one is the Turbine shaft carrying blades and a turbine shaft surrounding inner housing arranged.
  • the inner case carries the guide vanes. Via appropriate storage and centering points is the inner housing with the outer housing Recording an axial thrust connected.
  • the US-PS 1,092,947 relates to a multi-stage steam turbine with a high pressure, a medium pressure and a low pressure part.
  • the individual sub-turbines are in one arranged in a single housing.
  • the high pressure part which is made of a single stage, has a fixed guide vane on that between two on a common wheel disc arranged rows of blades is arranged. at the design of the high pressure part is therefore neither a chamber construction, nor a drum construction.
  • the medium pressure part is in chamber construction and the low pressure part executed in drum construction.
  • the low-pressure part is carried out in two channels.
  • a steam turbine with a high-pressure and a medium pressure part specified.
  • the high pressure part is in drum construction and the medium pressure part in chamber construction executed.
  • the two sub-turbines can both on a single wave as well as each on a separate Shaft be arranged and are each in its own housing arranged and fluidly connected to each other.
  • the high pressure part has an overpressure blading or a constant pressure blading.
  • DE-PS 448 247 is a combined drum and disc wheel turbine described for steam at which the last stage the turbine with disc wheels (chamber design) is.
  • the entire steam turbine including the drum type as well as the part made in chamber construction housed in a single turbine housing.
  • the object of the invention is to provide a steam turbine with a good To indicate efficiency.
  • the task is performed using a steam turbine a high pressure part turbine and one with the latter in terms of flow technology connected medium pressure partial turbine released, in which the high-pressure partial turbine in chamber design and the Medium pressure partial turbine is designed in a drum design.
  • the high-pressure and the medium-pressure turbine can both be single and double flow and in separate Outer housing as well as in a special common outer housing (Compact turbine) can be arranged.
  • An outer case the high pressure sub-turbine in a separate arrangement is preferred Pot-shaped, such as in the DE-AS 20 54 465 is described.
  • the outer case can too be carried out axially divided.
  • a version with separate Housing occurs, among other things, due to a low Step reaction (degree of reaction) and the chamber design of the High pressure sub-turbine has a small axial thrust. On Thrust compensation piston can therefore be omitted, so that leakage losses by emerging from the thrust compensating piston Steam can be avoided. This leads to an increase in Efficiency.
  • the medium-pressure sub-turbine is double-flow, so that a thrust compensation piston is also omitted here can.
  • a component becomes under a thrust compensation piston understood that due to its geometric shape when applied countering a resulting force with steam one of the turbine blades in a steam flow caused axial thrust.
  • An axial one caused by the medium-pressure turbine Thrust can be compensated by a thrust compensation piston. This is arranged so that the high-pressure blading in Axial direction of the turbine shaft seen between the thrust compensation piston and the medium pressure blading arranged is.
  • the High-pressure partial turbine in drum design and the medium-pressure partial turbine executed in chamber design the high-pressure turbine is executed in two flows. Both sub-turbines can in turn in a common outer housing as well be arranged in a separate outer housing. Also the medium-pressure turbine section can be double-flow.
  • Compact turbine passes through the medium pressure turbine, especially due to the low step response (Degree of reaction) and the chamber design, at most a small one axial thrust.
  • a thrust compensating piston for the medium pressure turbine can therefore be omitted.
  • To accommodate a axial thrust that can be caused by the high-pressure turbine section is a between the high pressure blading and the medium pressure blading arranged area of the turbine shaft (Intermediate floor) provided, which both for the medium pressure blading as well as the high pressure blading ring-shaped depression with corresponding radial end faces having. Since, for constructional reasons, a Compact turbine offers such an intermediate floor is through the omission of an additional medium-pressure thrust compensating piston the efficiency of the medium pressure turbine and thus of the entire steam turbine increased.
  • the medium-pressure turbine is preferably carried out in two passages, whereby an axial thrust of the medium pressure turbine is avoided is.
  • a thrust compensation piston is preferably provided for absorbing an axial thrust of the high pressure turbine. Leakage losses that may be specified in this are dependent on Area of application thanks to the good efficiency of the excess pressure blading the high-pressure partial turbine designed in a drum design balanced.
  • the weak reaction stages lead for both embodiments of the invention (Stages with low degree of reaction in chamber construction) to a rapid reduction in pressure and accordingly rapid increase in specific volume and thus the flow cross-sections and blade heights.
  • Stages with low degree of reaction in chamber construction to a rapid reduction in pressure and accordingly rapid increase in specific volume and thus the flow cross-sections and blade heights.
  • those in the flow direction subsequent turbine stages each comprising a guide vane structure and a downstream one in the flow direction Blade arrangement, compared to an overpressure stage lower secondary losses and lower Leakage losses through sealing gaps between the Blades and a turbine wall and the guide vanes and the turbine shaft are formed.
  • the steam turbine in particular live steam condition (Temperature, pressure) of the steam supplied to the steam turbine as well as the requirements for mass flow and one to be achieved thermal and electrical power, cause weak reaction levels in chamber design a higher efficiency as overpressure stages in drum design or vice versa.
  • the medium pressure turbine is also a low pressure turbine resettable.
  • a steam turbine according to the invention is particularly suitable for use in a coal-fired Steam power plant. With the steam turbine are electrical Outputs of approx. 50 MW to over 1500 MW can be achieved.
  • the Live steam condition can be between 50 bar and 300 bar with a temperature of up to 630 ° C. Taking the temperature for further developments in the materials sector, in particular regarding turbine shaft and turbine housing, are also higher can.
  • FIG. 1 shows a steam turbine 1 with a single outer housing 4.
  • the outer casing 4 Through the outer casing 4 is one along a turbine axis 15 directed turbine shaft 6 out.
  • This turbine shaft 6 is on the bushings not shown with respective shaft seals 9 with respect to the outer housing 4 sealed.
  • Inside the housing 4 is a High-pressure turbine section 2 arranged in a drum design. she includes high pressure blading with the turbine shaft 6 connected blades 11 and with a high pressure inner housing 14 connected schematically illustrated guide vanes 12.
  • Inside the inner housing 14 is still one Medium-pressure turbine section 3 in chamber design with blades 11 and guide vanes 12, which are schematic for the sake of clarity are shown arranged.
  • the turbine shaft 6 has a shaft coupling 10 for coupling at one end a generator or not shown Low-pressure turbine.
  • Axial between the high pressure blading and the medium pressure blading is a area 13 (intermediate floor) of the thrust compensation Turbine shaft 6 formed, which is opposite the inner housing 14 sealed by a corresponding shaft seal 9 is.
  • the Turbine shaft 6 has a respective recess 13a through which End faces are formed on the intermediate floor 13.
  • One of these Recesses 13a is with an inflow region 7b Medium pressure turbine part 3 and the other recess 13a with a steam inlet 7a of the high pressure turbine section 2 connected.
  • a live steam flowing into the steam inlet 7a for example a pressure of about 170 bar and a temperature of 560 ° C flows through the blades in the axial direction the high-pressure turbine section 2 through and at a lower Pressure from a steam outlet 8a of the high pressure part turbine 2 out. From there, the now partially relaxed comes Steam in a reheat, not shown, and will of the steam turbine 1 via the steam inlet 7b of the medium-pressure sub-turbine 3 fed again.
  • the drum construction High-pressure turbine section 2 with overpressure blading leads to an axial thrust in the direction of the steam outlet 8a. This is via the intermediate floor 13a and end faces formed by the depressions 13a, because the pressure drop across the high pressure blading, i.e.
  • the medium pressure turbine 3 is in a chamber construction with an essentially Equidistant blading carried out.
  • the reheated flowing into the steam inlet 7b and through the medium-pressure turbine 3 axially flowing steam leaves the steam turbine 1 through a steam outlet 8b Medium-pressure turbine section 3.
  • the medium-pressure turbine section 3 there is only a slight axial thrust.
  • Another Thrust compensating pistons can therefore be omitted.
  • FIG. 2 shows a steam turbine 1 in a longitudinal section a housing 4 in which a high-pressure turbine section 2 in chamber design and a medium-pressure sub-turbine 3 in the drum design is arranged.
  • an intermediate floor analogous to Figure 1 13 arranged. Since compared to the embodiment Figure 1, the high-pressure turbine section 2 a significantly lower Generated axial thrust, the intermediate floor 13 has a smaller one Diameter and a small depression on the medium pressure side 13a.
  • a thrust compensation piston 5 is provided, which via a Pressure line 16 with the steam outlet 8b of the medium-pressure turbine 3 is connected.
  • This thrust compensation piston 5 is arranged on the steam outlet side to the high-pressure turbine section 2, so that this axially between the thrust compensating piston 5 and the Intermediate floor 13, i.e. the medium-pressure turbine 3 arranged is.
  • the steam turbine 1 can be analogous to the embodiment 1 downstream of a low-pressure turbine his.
  • 3 and 4 each show a steam turbine 1 a high-pressure turbine section 2 with an outer casing 4a and a medium-pressure turbine section 3 axially spaced therefrom with an outer housing 4b.
  • the medium pressure turbine part 3 is executed in two passages.
  • One passed through the outer case 4a Turbine shaft 6a of the high-pressure sub-turbine 2 is via a shaft coupling 10 with one through the outer housing 4b of the medium-pressure turbine 3 guided turbine shaft 6b coupled.
  • 3 shows the high-pressure turbine section 2 in chamber design and the medium pressure turbine part 3 in drum design executed. Occurs in the high-pressure turbine section 2 therefore at most a small axial thrust, so that from a thrust compensation piston 5 can be disregarded.
  • the high-pressure turbine part is of the drum type and the medium pressure partial turbine in chamber design executed.
  • this is also part of the housing connected to the steam outlet 8a so that the pressure difference between steam inlet 7a and steam outlet 8a substantially the pressure drop in the axial direction via the thrust compensation piston 5 corresponds.
  • the invention is characterized by a steam turbine with a Medium pressure turbine and a high pressure turbine, the high-pressure sub-turbine in drum design and the Medium pressure partial turbine in chamber design or vice versa is.
  • the turbine parts can be in one housing (Compact turbine) or arranged in two separate housings his.
  • steam pressure, steam temperature, Steam mass flow and thermal or electrical power the steam turbine is a combination with particularly good ones Efficiency by taking advantage of both the chamber design as well as the drum design.

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

Claims (7)

  1. Turbine (1) à vapeur ayant une partie (2) de turbine haute pression et une partie (3) de turbine moyenne pression communiquant du point de vue de la technique de l'écoulement avec cette dernière, la partie (2) de turbine haute pression étant réalisée suivant un mode de construction en chambre et la partie (3) de turbine moyenne pression suivant un mode de construction en tambour.
  2. Turbine (1) à vapeur suivant la revendication 1, dans laquelle la partie (2) de turbine haute pression est réalisée à deux flux.
  3. Turbine (1) à vapeur ayant une partie (2) de turbine haute pression et une partie (3) de turbine moyenne pression communiquant du point de vue de la technique des fluides avec cette demière, la partie (2) de turbine haute pression étant réalisée en mode de construction en tambour, la partie (3) de turbine moyenne pression étant réalisée en mode de construction en chambre et la partie (2) de turbine haute pression étant réalisée à deux flux.
  4. Turbine (1) à vapeur suivant l'une des revendications précédentes, comprenant une enveloppe (4) extérieure dans laquelle sont disposée la partie (2) de turbine haute pression et la partie (3) de turbine moyenne pression.
  5. Turbine (1) à vapeur suivant la revendication 4, dans laquelle il est prévu un piston (5) de compensation de la poussée destiné à compenser une poussée axiale de la partie (3) de turbine moyenne pression et la partie (2) de turbine haute pression est disposée axialement entre la partie (3) de turbine moyenne pression et un piston (5) de compensation de la poussée.
  6. Turbine (1) à vapeur suivant la revendication 1 ou 3, dans laquelle la partie (2) de turbine haute pression a une enveloppe (4a) extérieure, notamment en forme de pot, et la partie (3) de turbine moyenne pression a une enveloppe (4) extérieure à distance axiale de l'enveloppe (4a).
  7. Turbine (1) à vapeur suivant la revendication 6, dans laquelle la partie (3) de turbine moyenne pression est réalisée à deux flux.
EP98904017A 1997-01-14 1998-01-09 Turbine a vapeur Revoked EP0953099B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19700899A DE19700899A1 (de) 1997-01-14 1997-01-14 Dampfturbine
DE19700899 1997-01-14
PCT/DE1998/000062 WO1998031921A1 (fr) 1997-01-14 1998-01-09 Turbine a vapeur

Publications (2)

Publication Number Publication Date
EP0953099A1 EP0953099A1 (fr) 1999-11-03
EP0953099B1 true EP0953099B1 (fr) 2002-04-10

Family

ID=7817277

Family Applications (1)

Application Number Title Priority Date Filing Date
EP98904017A Revoked EP0953099B1 (fr) 1997-01-14 1998-01-09 Turbine a vapeur

Country Status (6)

Country Link
US (1) US6305901B1 (fr)
EP (1) EP0953099B1 (fr)
JP (1) JP2001508149A (fr)
CN (1) CN1092746C (fr)
DE (2) DE19700899A1 (fr)
WO (1) WO1998031921A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6851927B2 (en) 2002-02-06 2005-02-08 Siemens Aktiengesellschaft Fluid-flow machine with high-pressure and low-pressure regions
DE102017005615A1 (de) 2017-06-14 2018-12-20 Erol Kisikli Turbine

Families Citing this family (16)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
PL372916A1 (en) 2002-04-11 2005-08-08 Richard A. Haase Water combustion technology-methods, processes, systems and apparatus for the combustion of hydrogen and oxygen
US6752589B2 (en) * 2002-10-15 2004-06-22 General Electric Company Method and apparatus for retrofitting a steam turbine and a retrofitted steam turbine
GB2409002A (en) * 2003-12-08 2005-06-15 Siemens Power Generation Ltd Thrust balance piston fitted between high and low pressure paths in a turbine.
GB0416931D0 (en) * 2004-07-29 2004-09-01 Alstom Technology Ltd Axial flow steam turbine assembly
GB0416932D0 (en) * 2004-07-29 2004-09-01 Alstom Technology Ltd Axial flow steam turbine assembly
CN100340740C (zh) * 2004-09-17 2007-10-03 北京全三维动力工程有限公司 一种超高压冲动式汽轮机
EP1788191B1 (fr) 2005-11-18 2014-04-02 Siemens Aktiengesellschaft Turbine à vapeur et procédé pour le refroidissement d'une turbine à vapeur
US8186168B2 (en) * 2008-07-18 2012-05-29 Rolls-Royce Corporation Thrust balance of rotor using fuel
JP2010174795A (ja) * 2009-01-30 2010-08-12 Mitsubishi Heavy Ind Ltd タービン
EP2431570A1 (fr) * 2010-09-16 2012-03-21 Siemens Aktiengesellschaft Turbine à vapeur comprenant un piston d'équilibrage de poussée et blocage de vapeur saturé
ES2534296T3 (es) * 2011-03-18 2015-04-21 Alstom Technology Ltd. Método para actualizar el diseño de una turbina de vapor de doble flujo
US8342009B2 (en) * 2011-05-10 2013-01-01 General Electric Company Method for determining steampath efficiency of a steam turbine section with internal leakage
US8834114B2 (en) 2011-09-29 2014-09-16 General Electric Company Turbine drum rotor retrofit
CN102678184B (zh) * 2012-05-04 2014-10-15 上海励辰机械制造有限公司 微型强力双涡轮气涡轮机
EP2662535A1 (fr) 2012-05-07 2013-11-13 Siemens Aktiengesellschaft Rotor pour une turbine à vapeur et turbine à vapeur correspondante
DE102017211295A1 (de) * 2017-07-03 2019-01-03 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betreiben derselben

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6851927B2 (en) 2002-02-06 2005-02-08 Siemens Aktiengesellschaft Fluid-flow machine with high-pressure and low-pressure regions
DE102017005615A1 (de) 2017-06-14 2018-12-20 Erol Kisikli Turbine

Also Published As

Publication number Publication date
CN1092746C (zh) 2002-10-16
JP2001508149A (ja) 2001-06-19
DE59803727D1 (de) 2002-05-16
DE19700899A1 (de) 1998-07-23
EP0953099A1 (fr) 1999-11-03
WO1998031921A1 (fr) 1998-07-23
CN1242817A (zh) 2000-01-26
US6305901B1 (en) 2001-10-23

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