EP0953099A1 - Turbine a vapeur - Google Patents

Turbine a vapeur

Info

Publication number
EP0953099A1
EP0953099A1 EP98904017A EP98904017A EP0953099A1 EP 0953099 A1 EP0953099 A1 EP 0953099A1 EP 98904017 A EP98904017 A EP 98904017A EP 98904017 A EP98904017 A EP 98904017A EP 0953099 A1 EP0953099 A1 EP 0953099A1
Authority
EP
European Patent Office
Prior art keywords
turbine
pressure
medium
steam
sub
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
EP98904017A
Other languages
German (de)
English (en)
Other versions
EP0953099B1 (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
Family has litigation
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(A1) "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

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
    • 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 part-turbine and a medium-pressure part-turbine fluidically connected to the latter.
  • action turbines also called constant pressure turbines
  • reaction turbines also called constant pressure turbines
  • Called overpressure turbines They have a turbine shaft with rotor blades arranged thereon and an inner housing with guide blades arranged between axially spaced rotor blades.
  • the isentropic reaction degree r is the percentage distribution of the isentropic enthalpy gradient in the rotor blades to the total isentropic enthalpy gradient over a stage consisting of a guide vane ring and a rotor blade ring.
  • the classic overpressure stage and the constant pressure stage are predominantly used. The latter, however, usually with a degree of reaction r slightly different from zero.
  • a constant pressure turbine is usually designed in a chamber design and a positive pressure turbine in a drum design.
  • a chamber turbine has a housing, which is divided into several chambers by axially spaced intermediate floors. In each of these chambers runs a disk-shaped impeller, on the outer circumference of which the blades are attached, while the guide blades are inserted into the intermediate floors.
  • One advantage of the chamber design is that the intermediate floors can be sealed against the turbine shaft quite effectively by means of labyrinth seals. Since the sealing knife is small, the gap cross sections and thus the gap leakage currents also become small. In known turbines, this type of construction is only used for small degrees of reaction, i.e. large step favored and therefore low number of stages used. The pressure difference on both sides of an impeller disc is small with a low degree of reaction, in the limit case even zero. An axial thrust exerted on the rotor remains low and can be absorbed by an axial bearing.
  • the rotor blades are arranged directly on the circumference of a drum-shaped turbine shaft.
  • the guide vanes are either inserted directly into the housing of the steam turbine or in a special guide vane carrier.
  • the axial length and the effort for a single stage are less than for a chamber turbine, but the number of stages must be larger because the reaction stages process a smaller gradient.
  • the axial thrust that occurs in the blading is considerable.
  • One way of counteracting this axial thrust is to provide a compensating piston on the front of which the pressure of the outlet connector is given via a connecting line.
  • 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 arranged in a single housing.
  • the high-pressure part which consists of a single stage, has a fixed guide vane, which is arranged between two rows of rotor blades arranged on a common wheel disc.
  • the design of the high-pressure part is therefore neither a chamber construction nor a drum construction.
  • the medium pressure section is designed in a chamber design and the low pressure section in a drum design.
  • the low-pressure part is double-flow.
  • a steam turbine with a high-pressure and a medium-pressure part is specified in US Pat. No. 1,750,814.
  • the high-pressure section is designed in a drum design and the medium-pressure section in a chamber design.
  • the two sub-turbines can be arranged on a single shaft as well as on a separate shaft and are each arranged in a separate housing and connected to one another in terms of flow technology.
  • the high-pressure part has an overpressure blading or a constant pressure blading.
  • DE-PS 448 247 describes a combined drum and disk wheel turbine for steam, in which the last stage of the turbine is designed with disk wheels (chamber construction).
  • the entire steam turbine, including the drum-type and the chamber-type part, is housed in a single turbine housing.
  • the object of the invention is to provide a steam turbine with good efficiency.
  • the object is achieved by a steam turbine having a high-pressure sub-turbine and a medium-pressure sub-turbine which is fluidically connected to the latter, in which the high-pressure sub-turbine is designed in a chamber design and the medium-pressure sub-turbine in a drum design.
  • the high-pressure and the medium-pressure sub-turbine can be of single or double flow and can be arranged in separate outer casings and also in a special common outer casing (compact turbine).
  • An outer casing of the high-pressure turbine part with a separate arrangement is preferably pot-shaped, as described for example in DE-AS 20 54 465.
  • the outer housing can also be made axially divided. In a version with separate housings, due to, among other things, a low step reaction (degree of reaction) and the chamber design
  • High pressure sub-turbine has a small axial thrust.
  • a thrust compensation piston can therefore be dispensed with, so that leakage losses due to steam escaping from the thrust compensation piston are also avoided. This leads to an increase in efficiency.
  • the medium-pressure turbine part is preferably designed with two passages, so that a thrust compensation piston can also be omitted here.
  • a thrust compensating piston is understood here to mean a component which, due to its geometrical shape when subjected to steam, causes a resultant force in the opposite direction to cause an axial thrust caused by the turbine blades during a steam flow.
  • the steam turbine is designed with an outer housing in which both the high-pressure sub-turbine and the middle partial pressure turbine are accommodated (compact turbine), occurs in the high-pressure partial turbine in particular due to a low step reaction and the chamber design, at most a small axial thrust.
  • the diameter of the turbine shaft area (intermediate floor), which is arranged between the high-pressure blading and the medium-pressure blading and is designed as a thrust compensating piston can be made small, in particular it can be smaller than the diameter of the turbine shaft in the area of the drum construction of the medium-pressure Part turbine. This also enables a reduction in leakage losses in the area of the seal between the medium-pressure sub-turbine and the high-pressure sub-turbine (smaller circular area of the sealing gaps), which leads to an increase in the efficiency of the steam turbine.
  • An axial thrust caused by the medium-pressure turbine section can be compensated by a thrust compensation piston. This is arranged so that the high-pressure blading, viewed in the axial direction of the turbine shaft, is arranged between the thrust compensation piston and the medium-pressure blading.
  • the high-pressure sub-turbine is designed in a drum design and the medium-pressure sub-turbine is designed in a chamber design, the high-pressure sub-turbine being designed with two flows.
  • Both partial turbines can in turn be arranged in a common outer housing and in a separate outer housing.
  • the medium-pressure turbine section can also be double-flow.
  • a small axial thrust occurs at most through the medium-pressure partial turbine, in particular due to the low step reaction (degree of reaction) and the chamber design.
  • a thrust compensation piston for the medium-pressure turbine section can therefore be omitted.
  • an area of the turbine shaft (intermediate floor) arranged between the high-pressure blading and the medium-pressure blading is provided, which has an annular depression with corresponding radial end faces for both the medium-pressure blading and the high-pressure blading. Since such an intermediate floor is available for a compact turbine for design reasons, the efficiency of the medium-pressure partial turbine and thus of the entire steam turbine is increased due to the omission of an additional medium-pressure thrust compensation piston.
  • the medium-pressure sub-turbine is preferably designed with two passages, as a result of which axial thrust of the medium-pressure sub-turbine is avoided.
  • a thrust compensating piston is preferably provided to absorb an axial thrust of the high-pressure sub-turbine. Depending on the area of application, any leakage losses which may be called therein are compensated for by a good efficiency of the excess pressure blading of the high-pressure part-turbine, which is constructed as a drum.
  • the weak reaction stages (stages with a low degree of reaction in the case of chamber construction) lead to a rapid pressure reduction and to a correspondingly rapid increase in the specific volume and thus in the flow cross sections and blade heights.
  • the turbine stages following in the direction of flow each comprising a guide vane structure and a rotor blade arrangement arranged downstream in the direction of flow, there are lower secondary losses and less in comparison to an overpressure stage
  • a steam turbine according to the invention is particularly suitable for use in a coal-fired steam power plant. With the steam turbine, electrical outputs from approx.
  • the live steam state can be between 50 bar and 300 bar with a temperature of up to 630 ° C.
  • the temperature can also be higher in the case of further developments in the materials sector, particularly with regard to the turbine shaft and turbine housing.
  • FIG. 1 shows a steam turbine 1 with a single outer housing 4.
  • a turbine shaft 6 directed along a turbine axis 15 is guided through the outer housing 4.
  • This turbine shaft 6 is sealed off from the outer housing 4 at the bushings (not shown) with respective shaft seals 9.
  • a high-pressure sub-turbine 2 in drum construction is arranged within the housing 4. It comprises a high-pressure blading with blades 11 connected to the turbine shaft 6 and with a high-pressure interior Housing 14 connected schematically illustrated guide vanes 12.
  • a medium-pressure turbine section 3 is also arranged in a chamber construction with rotor blades 11 and guide vanes 12, which are shown schematically for the sake of clarity.
  • the turbine shaft 6 has at one end a shaft coupling 10 for coupling to a generator or a low-pressure partial turbine, not shown. Axially between the high-pressure blading and the medium-pressure blading is an area 13 (intermediate floor) of the turbine shaft 6 which serves to compensate for thrust and is sealed off from the inner housing 14 by a corresponding shaft seal 9. Between the intermediate floor 13 and the high-pressure turbine section 2 and the medium-pressure turbine section 3, the turbine shaft 6 has a respective recess 13a, through which end faces are formed on the intermediate floor 13. One of these depressions 13a is connected to an inflow region 7b of the medium-pressure turbine section 3 and the other depression 13a is connected to a steam inlet 7a of the high-pressure turbine section 2.
  • the high-pressure turbine section 2 which is designed in a drum design and has an excess pressure blading, leads to an axial thrust in the direction of the steam outlet 8a. This is compensated for via the intermediate floor 13a and the end faces formed by the recesses 13a, since the pressure drop across the high-pressure blading, ie from steam inlet 7a to steam outlet 8a, corresponds in magnitude to the pressure difference across the intermediate floor 13 between steam inlet 7a and steam inlet 7b.
  • the medium-pressure turbine section 3 is of a chamber construction with an essentially tr
  • the high-pressure sub-turbine 2 is designed in a chamber design and the medium-pressure sub-turbine 3 in a drum design. In the high-pressure turbine section 2 there is therefore only a slight axial thrust, so that a thrust compensation piston 5 can be disregarded.
  • the high-pressure sub-turbine is designed in a drum design and the medium-pressure sub-turbine in a chamber design.
  • An intermediate base designed as a thrust compensation piston 5 is arranged axially between the steam inlet 7a and the housing 4a. This is fluidly connected on the housing side to the steam outlet 8a, so that the pressure difference between steam inlet 7a and steam outlet 8a essentially corresponds to the pressure drop in the axial direction via the thrust compensating piston 5.
  • the invention is characterized by a steam turbine with a medium-pressure sub-turbine and a high-pressure sub-turbine, the high-pressure sub-turbine being constructed in a drum design and the medium-pressure sub-turbine in a chamber design or vice versa.
  • the partial turbines can be arranged in one housing (compact turbine) or in two separate housings. Depending on the area of application (steam pressure, steam temperature,

Landscapes

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

Abstract

L'invention concerne une turbine à vapeur (1) comprenant une turbine partielle haute pression (2) et une turbine partielle moyenne pression (3) en communication fluidique avec cette dernière. La turbine partielle haute pression (2) est de type à compartiments et la turbine partielle moyenne pression (3) de type à tambour. En variante, la turbine partielle moyenne pression (3) est de type à compartiments et la turbine partielle haute pression (2) de type à tambour.
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 true EP0953099A1 (fr) 1999-11-03
EP0953099B1 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)

Families Citing this family (18)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
ES2278821T3 (es) 2002-02-06 2007-08-16 Siemens Aktiengesellschaft Turbomaquina con regiones de paletas de alta presion y de baja presion.
WO2003087564A1 (fr) 2002-04-11 2003-10-23 Haase Richard A Procedes, processus, systemes et appareils de la technologie de combustion de l'eau pour la combustion d'hydrogene et d'oxygene
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
EP2686521B1 (fr) 2011-03-18 2015-01-14 Alstom Technology Ltd Procede de reequipement d'une turbine a vapeur a double flux
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
DE102017005615A1 (de) 2017-06-14 2018-12-20 Erol Kisikli Turbine
DE102017211295A1 (de) * 2017-07-03 2019-01-03 Siemens Aktiengesellschaft Dampfturbine und Verfahren zum Betreiben derselben

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Also Published As

Publication number Publication date
DE59803727D1 (de) 2002-05-16
US6305901B1 (en) 2001-10-23
CN1092746C (zh) 2002-10-16
EP0953099B1 (fr) 2002-04-10
JP2001508149A (ja) 2001-06-19
WO1998031921A1 (fr) 1998-07-23
CN1242817A (zh) 2000-01-26
DE19700899A1 (de) 1998-07-23

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