EP0088944B1 - Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung - Google Patents
Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung Download PDFInfo
- Publication number
- EP0088944B1 EP0088944B1 EP83102038A EP83102038A EP0088944B1 EP 0088944 B1 EP0088944 B1 EP 0088944B1 EP 83102038 A EP83102038 A EP 83102038A EP 83102038 A EP83102038 A EP 83102038A EP 0088944 B1 EP0088944 B1 EP 0088944B1
- Authority
- EP
- European Patent Office
- Prior art keywords
- shaft
- steam
- steam turbine
- flow
- nozzles
- 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
Links
Images
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
- F01D3/00—Machines or engines with axial-thrust balancing effected by working-fluid
- F01D3/02—Machines or engines with axial-thrust balancing effected by working-fluid characterised by having one fluid flow in one axial direction and another fluid flow in the opposite direction
-
- 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
- F01D25/08—Cooling; Heating; Heat-insulation
-
- 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
- F01D5/00—Blades; Blade-carrying members; Heating, heat-insulating, cooling or antivibration means on the blades or the members
- F01D5/02—Blade-carrying members, e.g. rotors
- F01D5/08—Heating, heat-insulating or cooling means
Definitions
- the invention relates to an axially loaded steam turbine according to the preamble of claim 1.
- Such a steam turbine is known from FR-A-851 531.
- a shaft shield is arranged in the region of the steam inflow taking place in the axial center, which shaft shield is attached to the radially inner ends of the guide vanes of the first guide vane rings of both flows.
- the shaft shield enclosing the shaft at a distance is formed on the outer circumference in such a way that the steam flowing in in the radial direction is divided equally between the two floods and deflected in the axial direction. The shaft shielding thus prevents an immediate flow against the shaft surface by the steam flowing in in the radial direction.
- the invention is based on the object, in an axially loaded steam turbine of the type mentioned, to further reduce the thermal stresses of the shaft in the region of the steam inflow, likewise without the use of cooling steam generated externally to the turbine, but in this case the shaft shielding ring itself as a device for pressure and Take advantage of lowering the temperature of the live steam.
- a small partial flow of the total inflowing steam is fed through tangentially arranged nozzles to the shaft area under the shaft shield.
- the speed at which this partial flow enters the annular channel formed between the shaft and the shaft shield corresponds to the gradient processed in the first guide vane ring.
- the nozzles introduced into the shaft shielding are aligned with respect to the direction of rotation of the shaft in such a way that the swirl flow which forms in the ring channel leads the shaft circumferential speed.
- the boundary layer temperature on the shaft corresponds to the static temperature of the steam which is reduced by the increase in the kinetic energy, increased by the proportion of the damming temperature of the comparatively low relative speed between the swirl flow and the shaft circumferential speed. Effective cooling of the shaft in the area of the steam inflow and in the area of the blade attachment of the first blade ring can thus be achieved by the nozzles introduced tangentially into the shaft shield.
- incoming partial flow is then divided equally into two swirl flows, which each flow in the axial direction along the shaft up to the first rotor blade ring.
- a further improvement in the cooling effect can be achieved in that the first stage is designed as a weak reaction stage or, in the case of a double-flow version, that the first stage is designed as a weak reaction stage in both floods. This is intended to process as large a gradient as possible in the first guide vane ring, so that the static temperature of the partial flow introduced into the ring channel is reduced as much as possible by the corresponding increase in the kinetic energy.
- the cross section of the nozzles is dimensioned such that the steam mass flow entering the annular duct is approximately 3% of the total steam mass flow supplied in the region of the steam inflow.
- the nozzles 8 are designed such that, seen in the direction of rotation of the shaft indicated by the arrow 9, they open tangentially into the annular channel 4 formed between the shaft 5 and the shaft shield 6. Since the partial flow diverted from the inflowing steam enters tangentially into the ring channel 4 through the nozzles 8, a swirl flow indicated by the arrow 10 forms there, which leads the wave circumferential speed.
- the swirl flow 10 is then divided into two swirl flows starting from the axial center M, which are indicated in FIG. 1 by the arrows 11 and 11 'and along the shaft 5 as far as the rotor blades 12 and 12' of the respective first rotor blade ring of the two floods.
- the speed at which the partial flow diverted from the incoming steam enters the nozzles 8 thus corresponds to the gradient processed in the first guide vane ring of the two floods, and this speed of entry can be increased by eliminating the respective first stage as a weak reaction stage.
- the shaft shield 6 prevents a direct flow against the surface of the shaft 5 by the hot steam flowing radially in the direction of the arrow 1.
- the boundary layer temperature of the swirl flows 10 or 11 and 11 'in the ring channel 4 corresponds to the static temperature of the steam reduced by the increase in the kinetic energy, increased by the accumulation temperature portion of the relative speed between the swirl flow 10 or 11 and 11' and the shaft circumferential speed.
- the congestion temperature proportion is low, since the relative speed mentioned is also comparatively low due to the selected orientation of the nozzles 8.
- the steam mass flow entering the annular duct 4 through the nozzles 8 is approximately 3% of the total steam mass flow supplied through the inflow duct 2.
- the temperature drop in the area of the shaft 5 below the shaft shield 6 is 20 ° K at the beginning of the swirl field in the axial center M and at 10 to 15 ° K at the respective end of the swirl field compared to the temperature of the incoming steam.
- the increase in consumption required for this cooling of the shaft is approximately 0.06% and thus corresponds to the values which can be achieved with external cooling by cooling steam introduced from the outside.
- the slight reduction in the cooling effect at the respective end of the swirl field can possibly be avoided by an additional row of blades arranged on the shaft 5. This row of moving blades arranged in the axial center M and in the annular channel 4 could expediently be designed as a free jet turbine.
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Turbine Rotor Nozzle Sealing (AREA)
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
AT83102038T ATE16303T1 (de) | 1982-03-16 | 1983-03-02 | Axial beaufschlagte dampfturbine, insbesondere in zweiflutiger ausfuehrung. |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE3209506 | 1982-03-16 | ||
DE19823209506 DE3209506A1 (de) | 1982-03-16 | 1982-03-16 | Axial beaufschlagte dampfturbine, insbesondere in zweiflutiger ausfuehrung |
Publications (2)
Publication Number | Publication Date |
---|---|
EP0088944A1 EP0088944A1 (de) | 1983-09-21 |
EP0088944B1 true EP0088944B1 (de) | 1985-10-30 |
Family
ID=6158377
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP83102038A Expired EP0088944B1 (de) | 1982-03-16 | 1983-03-02 | Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung |
Country Status (9)
Country | Link |
---|---|
US (1) | US4571153A (es) |
EP (1) | EP0088944B1 (es) |
JP (1) | JPS58167802A (es) |
AR (1) | AR229899A1 (es) |
AT (1) | ATE16303T1 (es) |
BR (1) | BR8301277A (es) |
DE (2) | DE3209506A1 (es) |
ES (1) | ES520606A0 (es) |
IN (1) | IN158028B (es) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6048169A (en) * | 1996-06-21 | 2000-04-11 | Siemens Aktiengesellschaft | Turbine shaft and method for cooling a turbine shaft |
CN107002494A (zh) * | 2014-10-15 | 2017-08-01 | 西门子公司 | 涡轮轴的可控冷却 |
Families Citing this family (21)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS59153901A (ja) * | 1983-02-21 | 1984-09-01 | Fuji Electric Co Ltd | 蒸気タ−ビンロ−タの冷却装置 |
DE3424139C2 (de) * | 1984-06-30 | 1996-02-22 | Bbc Brown Boveri & Cie | Gasturbinenrotor |
US4764084A (en) * | 1987-11-23 | 1988-08-16 | Westinghouse Electric Corp. | Inlet flow guide for a low pressure turbine |
DE19620828C1 (de) * | 1996-05-23 | 1997-09-04 | Siemens Ag | Turbinenwelle sowie Verfahren zur Kühlung einer Turbinenwelle |
US6595117B1 (en) * | 1999-08-04 | 2003-07-22 | The Frymaster Corporation | High speed variable size toaster |
US6854954B2 (en) * | 2003-03-03 | 2005-02-15 | General Electric Company | Methods and apparatus for assembling turbine engines |
US20070065273A1 (en) * | 2005-09-22 | 2007-03-22 | General Electric Company | Methods and apparatus for double flow turbine first stage cooling |
US7322789B2 (en) * | 2005-11-07 | 2008-01-29 | General Electric Company | Methods and apparatus for channeling steam flow to turbines |
EP1895094B1 (de) * | 2006-08-25 | 2010-09-29 | Siemens Aktiengesellschaft | Drallgekühlte Rotor-Schweissnaht |
US7874795B2 (en) * | 2006-09-11 | 2011-01-25 | General Electric Company | Turbine nozzle assemblies |
US8317458B2 (en) * | 2008-02-28 | 2012-11-27 | General Electric Company | Apparatus and method for double flow turbine tub region cooling |
US8096748B2 (en) * | 2008-05-15 | 2012-01-17 | General Electric Company | Apparatus and method for double flow turbine first stage cooling |
US8167535B2 (en) * | 2008-07-24 | 2012-05-01 | General Electric Company | System and method for providing supercritical cooling steam into a wheelspace of a turbine |
US8414252B2 (en) * | 2010-01-04 | 2013-04-09 | General Electric Company | Method and apparatus for double flow turbine first stage cooling |
US8657562B2 (en) * | 2010-11-19 | 2014-02-25 | General Electric Company | Self-aligning flow splitter for steam turbine |
EP3056663A1 (de) * | 2015-02-10 | 2016-08-17 | Siemens Aktiengesellschaft | Axial beaufschlagte Dampfturbine, insbesondere in zweiflutiger Ausführung |
DE102015215144B4 (de) * | 2015-08-07 | 2017-11-09 | MTU Aero Engines AG | Vorrichtung und Verfahren zum Beeinflussen der Temperaturen in Innenringsegmenten einer Gasturbine |
JP6204966B2 (ja) * | 2015-12-24 | 2017-09-27 | 三菱日立パワーシステムズ株式会社 | 蒸気タービン |
DE112016006048T5 (de) * | 2015-12-24 | 2018-09-20 | Mitsubishi Hitachi Power Systems, Ltd. | Dampfturbine |
JP6204967B2 (ja) * | 2015-12-24 | 2017-09-27 | 三菱日立パワーシステムズ株式会社 | 蒸気タービン |
US20180080324A1 (en) * | 2016-09-20 | 2018-03-22 | General Electric Company | Fluidically controlled steam turbine inlet scroll |
Family Cites Families (18)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CA536533A (en) * | 1957-01-29 | E. P. Johnson William | Gas turbines | |
CH159225A (de) * | 1930-11-04 | 1932-12-31 | Escher Wyss Maschf Ag | Kreiselpumpe. |
FR851531A (fr) * | 1938-03-15 | 1940-01-10 | Turbine à double circulation à admission intérieure | |
US3147951A (en) * | 1961-05-29 | 1964-09-08 | Garrett Corp | Fluid pressure operated turbine |
DE1962031U (de) * | 1963-01-18 | 1967-06-15 | Siemens Ag | Dampfturbine. |
CH430757A (de) * | 1963-01-18 | 1967-02-28 | Siemens Ag | Dampfturbine |
US3232580A (en) * | 1963-07-18 | 1966-02-01 | Birmann Rudolph | Centripetal turbine |
US3291447A (en) * | 1965-02-15 | 1966-12-13 | Gen Electric | Steam turbine rotor cooling |
US3429557A (en) * | 1966-06-30 | 1969-02-25 | Gen Electric | Steam turbine rotor cooling arrangement |
NL139802B (nl) * | 1968-05-31 | 1973-09-17 | Stork Koninklijke Maschf | Turbine voor een compressibel medium. |
DE2140490A1 (de) * | 1971-07-26 | 1973-02-01 | Bbc Brown Boveri & Cie | Einrichtung zur kuehlung des rotors einer dampfturbine |
DE2213071B2 (de) * | 1972-03-17 | 1975-05-28 | Kraftwerk Union Ag, 4330 Muelheim | Leitschaufelloser Leitkanal zur Drallerzeugung vor dem ersten Laufschaufelkranz von Turbinen |
JPS5650084B2 (es) * | 1972-04-26 | 1981-11-26 | ||
US3994630A (en) * | 1974-08-21 | 1976-11-30 | International Harvester Company | Monorotor turbine and method of cooling |
JPS5215907A (en) * | 1975-07-29 | 1977-02-05 | Toshiba Corp | Reheat steam turbine rotor cooling system |
JPS5374608A (en) * | 1976-12-15 | 1978-07-03 | Hitachi Ltd | Cooling device for steam turbine |
JPS5423805A (en) * | 1977-07-26 | 1979-02-22 | Toshiba Corp | Reheating-turbine rotor overheat preventive device |
DE2928487A1 (de) * | 1979-07-14 | 1981-02-05 | Philips Patentverwaltung | Verfahren zur messung der relativen feuchte eines messgutes mit hilfe von mikrowellen im ghz-bereich |
-
1982
- 1982-03-16 DE DE19823209506 patent/DE3209506A1/de not_active Withdrawn
-
1983
- 1983-02-03 IN IN128/CAL/83A patent/IN158028B/en unknown
- 1983-02-04 AR AR292051A patent/AR229899A1/es active
- 1983-03-02 AT AT83102038T patent/ATE16303T1/de not_active IP Right Cessation
- 1983-03-02 DE DE8383102038T patent/DE3361096D1/de not_active Expired
- 1983-03-02 EP EP83102038A patent/EP0088944B1/de not_active Expired
- 1983-03-14 JP JP58042082A patent/JPS58167802A/ja active Granted
- 1983-03-15 US US06/475,458 patent/US4571153A/en not_active Expired - Lifetime
- 1983-03-15 ES ES520606A patent/ES520606A0/es active Granted
- 1983-03-15 BR BR8301277A patent/BR8301277A/pt unknown
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US6048169A (en) * | 1996-06-21 | 2000-04-11 | Siemens Aktiengesellschaft | Turbine shaft and method for cooling a turbine shaft |
US6102654A (en) * | 1996-06-21 | 2000-08-15 | Siemens Aktiengesellschaft | Turbomachine and method for cooling a turbomachine |
CN107002494A (zh) * | 2014-10-15 | 2017-08-01 | 西门子公司 | 涡轮轴的可控冷却 |
Also Published As
Publication number | Publication date |
---|---|
JPS58167802A (ja) | 1983-10-04 |
BR8301277A (pt) | 1983-11-22 |
EP0088944A1 (de) | 1983-09-21 |
ES8401567A1 (es) | 1983-12-16 |
AR229899A1 (es) | 1983-12-30 |
ES520606A0 (es) | 1983-12-16 |
DE3361096D1 (en) | 1985-12-05 |
ATE16303T1 (de) | 1985-11-15 |
US4571153A (en) | 1986-02-18 |
DE3209506A1 (de) | 1983-09-22 |
IN158028B (es) | 1986-08-16 |
JPH0440522B2 (es) | 1992-07-03 |
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