EP1892384A1 - Diffuseur pour une turbine à vapeur - Google Patents

Diffuseur pour une turbine à vapeur Download PDF

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Publication number
EP1892384A1
EP1892384A1 EP06017831A EP06017831A EP1892384A1 EP 1892384 A1 EP1892384 A1 EP 1892384A1 EP 06017831 A EP06017831 A EP 06017831A EP 06017831 A EP06017831 A EP 06017831A EP 1892384 A1 EP1892384 A1 EP 1892384A1
Authority
EP
European Patent Office
Prior art keywords
diffuser
curvature
boundary wall
steam
steam turbine
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.)
Withdrawn
Application number
EP06017831A
Other languages
German (de)
English (en)
Inventor
Sascha Dr. Becker
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 EP06017831A priority Critical patent/EP1892384A1/fr
Publication of EP1892384A1 publication Critical patent/EP1892384A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape
    • F05D2250/71—Shape curved

Definitions

  • the invention relates to a diffuser for a steam turbine, wherein the diffuser has an outer boundary wall, which is designed for application to a steam outlet opening of the steam turbine.
  • the diffuser of a turbomachine in particular a steam turbine, is designed with a view to optimizing the turbine performance by the greatest possible pressure recovery.
  • a turbomachine in particular a steam turbine
  • the diffuser of a turbomachine is designed with a view to optimizing the turbine performance by the greatest possible pressure recovery.
  • today's steam turbines must deliver a required clamping performance with the lowest possible heat consumption.
  • a significant proportion of the clamping performance has in particular the low pressure (LP) power output.
  • Measures that affect the performance of the low-pressure power amplifier affect the overall performance of a turbo set.
  • a turbo set consists of a composition of different steam turbines, which are designed for different operating conditions.
  • the outflow area has a diffuser and a steam exhaust hood.
  • the diffuser should have the highest possible pressure recovery over a wide operating range.
  • the physical boundary conditions in the inlet of the diffuser are responsible for the achievable pressure recovery. Due to the output stage outflow, the boundary conditions are already highly inhomogeneous at the design point of the blading.
  • UU is also an operating state possible, in which the output stage permanently flows with a twist.
  • a swirl is understood as meaning a transverse component of the flow direction which is transverse to the main flow direction. In addition, it can be at a high set up a turbo set, that means, the flow direction after the power amplifier shows down, depending on Abdampfhaubendid to a strong variation of the flow sizes over the circumference.
  • a diffuser which is subdivided into different partial diffusers by incorporating baffles in the diffuser. By installing the baffles, the flow is deflected targeted.
  • axial diffusers which are formed with straight walls, are known in axially flowing turbines.
  • the axial diffusers have conical walls and can be referred to as a circular diffuser or cone diffuser because the geometric shape of these axial diffusers resembles a circular ring or a cone.
  • the invention begins, whose task is to provide a diffuser for a turbomachine, in particular steam turbine, with which a high pressure recovery can be achieved.
  • a diffuser for a steam turbine wherein the diffuser has an outer boundary wall has, which is designed for application to a steam outlet opening of the steam turbine, wherein the outer boundary wall is seen in cross-section S-shaped.
  • the S-shaped diffuser shape proposed here combines, so to speak, the advantages of axial diffusers and deflecting diffusers. Therefore, the diffuser efficiency is no longer dependent on the axial length of the Abdampfraumes, whereby the axial space between the final stage of the steam turbine and a capacitor can be shortened.
  • the proposed here new concept of an S-shaped diffuser is independent of a flow separation at the hub, which leads to a strong reduction of the diffuser efficiency in pure axial diffusers.
  • the last turbine stage of a low-pressure part of a steam turbine for deflecting diffusers is designed with deflection of the axially flowing steam in the radial direction to a laterally or below the steam turbine arranged condenser.
  • this leads to a high tendency to flow separation at the hub, which occurs, for example, in purely axially outflowing combined steam turbines. this will justified that these combination steam turbines have a strong tendency to radial deflection.
  • the outer boundary wall of the diffuser is seen in cross section, initially formed from the application point to the steam outlet from substantially parallel to a vapor flow direction, then initially curved in a radial direction, then formed a counter-curvature, wherein the counter-curvature is formed against the radial direction, wherein the radial direction is formed substantially perpendicular to a rotation axis.
  • the outer boundary wall thus describes in cross-section, viewed from the contact point to the outlet opening, substantially initially a convex region which merges into a concave region.
  • the boundary wall may have straight walls.
  • curvature and counter curvature are formed over a length which corresponds essentially to 10% to 12% of the total length of the diffuser.
  • radius of the outer boundary wall from the contact point to the steam outlet opening to the transition of the straight wall shows a radius increase between 10% and 20%.
  • curvature and counter-curvature are each described as part of a circular arc.
  • the low-pressure (ND) steam turbine has a rotor 8 rotatably mounted about a rotation axis 5.
  • the rotor 8 has various blades 3, which are arranged in the direction of a longitudinal axis.
  • vanes 2 are arranged on the inner housing 9 .
  • a flow medium flows via the inflow region 11 into the flow channel 12 of the low-pressure (ND) steam turbine.
  • the flow medium passes through the runner 3 and guide vanes 2 in the outflow area 13.
  • FIG. 2 shows a side view of a diffuser 4.
  • the diffuser shown in FIG 4 is one of the formed according to the prior art.
  • This diffuser 4 has a first region 6, which rests against the last turbine stage 14 of a steam turbine.
  • the diffuser 4 so to speak, adjoins the application point 15 at a steam outlet opening 16.
  • Flow calculations have shown that the diffuser geometry shown in FIG. 2 has a strong separation on the hub 17.
  • the diffuser 4 is formed such that the outer boundary wall 18 shows a straight course.
  • FIG. 3 shows a partial section of the diffuser from FIG. 2.
  • a flow medium in the diffuser 4 At the hub 17 and the outer boundary wall 18, the flow is guided along. The flow is thereby slowed down, whereby the pressure is increased.
  • the thus braked steam is finally passed to a condenser.
  • the diffuser 4 shows a perspective view of the diffuser 4 according to the invention.
  • the essential difference from FIG. 3 is that at the contact point 15 the course of the outer boundary wall 18 is not straight, but S-shaped 20 is formed.
  • the flow medium first flows into the diffuser 4 in a main flow direction 21 and has the possibility of being strongly deflected on the outer boundary wall 18 in the region of the S-shaped design of the diffuser. Flow calculations have shown that the flow thereby results in less separation at the hub 17.
  • the diffuser 4 has an outer boundary wall 18, which is designed for application to a steam outlet opening 22 of the steam turbine 1, wherein the outer boundary wall 18 seen in cross-section S-shaped 20 is formed.
  • FIG. 5 shows a cross-sectional view of the diffuser from FIG. 4.
  • the diffuser 4 is characterized in that the outer boundary wall 18 seen in cross-section initially from the application point 15 to the steam outlet opening 21 is formed substantially parallel to a steam flow direction 21, then initially curved in a radial direction 23 and then has a counter-curvature 24, the is formed against the radial direction 23, wherein the radial direction 23 is formed substantially perpendicular to a rotation axis 25.
  • the axis of rotation may coincide with the direction of vapor flow 21.
  • the curvature 26 and counter-curvature 24 is formed over a length which corresponds essentially to 10% to 12% of the total length of the diffuser 4.
  • the total length of the diffuser 4 extends from the application point 15 to the application point to the capacitor.
  • the total length 27 may be several meters.
  • the curvature 26 and counter curvature 24 may be described as parts of a circular arc. After the curvature 26 and countercurve 24, the course of the outer boundary wall corresponds to a straight line 28.
  • FIG 7 is a perspective view of the diffuser 4 can be seen, which is formed according to the prior art with a straight course of the outer boundary wall 18.
  • FIG. 8 shows a diffuser 4 according to the invention, which is essentially characterized in that the outer boundary wall 18 at the contact point 15 shows an S-shaped profile 20.
  • the diffuser 4 has a boundary wall 18, which at the application point 15 to the steam outlet opening 22 has a substantially circular course with a radius r A and in the course of the boundary wall, the radius after the curvature 26 and countercurve 24 substantially between 110% and 120%. of the radius r A shows.
  • the diffusers shown here are not only suitable for steam turbines, but also for turbomachines such as gas turbines.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
EP06017831A 2006-08-25 2006-08-25 Diffuseur pour une turbine à vapeur Withdrawn EP1892384A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06017831A EP1892384A1 (fr) 2006-08-25 2006-08-25 Diffuseur pour une turbine à vapeur

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP06017831A EP1892384A1 (fr) 2006-08-25 2006-08-25 Diffuseur pour une turbine à vapeur

Publications (1)

Publication Number Publication Date
EP1892384A1 true EP1892384A1 (fr) 2008-02-27

Family

ID=37694094

Family Applications (1)

Application Number Title Priority Date Filing Date
EP06017831A Withdrawn EP1892384A1 (fr) 2006-08-25 2006-08-25 Diffuseur pour une turbine à vapeur

Country Status (1)

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EP (1) EP1892384A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2967461A1 (fr) * 2010-11-16 2012-05-18 Gen Electric Diffuseur de gaz d'echappement a basse pression pour turbine a vapeur
US8506233B2 (en) 2009-09-14 2013-08-13 Alstom Technology Ltd. Axial turbine and method for discharging a flow from an axial turbine

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1187432B (de) * 1960-11-19 1965-02-18 Theodor Helmbold Dr Ing Diffusor mit Fuehrungsmulden fuer die Hauptstroemung beruehrende Potentialwirbel
GB1000767A (en) * 1963-05-08 1965-08-11 Int Research & Dev Co Ltd Diffusers for fluids
FR1415204A (fr) * 1963-11-29 1965-10-22 Bristol Siddeley Engines Ltd Perfectionnements apportés aux turbines et compresseurs à flux axial
GB1125049A (en) * 1964-12-22 1968-08-28 Bbc Brown Boveri & Cie Improvements in and relating to fluid diffusers
FR2497883A1 (fr) * 1981-01-09 1982-07-16 Etri Sa Ventilateur electrique axial de type plat
EP0345700A1 (fr) * 1988-06-07 1989-12-13 SKODA koncernovy podnik Carter d'échappement pour turbomachine
US5110560A (en) * 1987-11-23 1992-05-05 United Technologies Corporation Convoluted diffuser
EP0695874A1 (fr) * 1994-08-03 1996-02-07 ROLLS-ROYCE plc Un turboréacteur et un diffuseur pour celui-ci
EP1178183A2 (fr) * 2000-07-31 2002-02-06 Alstom (Switzerland) Ltd Turbine à vapeur à basse pression avec un diffuseur à canaux multiples

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE1187432B (de) * 1960-11-19 1965-02-18 Theodor Helmbold Dr Ing Diffusor mit Fuehrungsmulden fuer die Hauptstroemung beruehrende Potentialwirbel
GB1000767A (en) * 1963-05-08 1965-08-11 Int Research & Dev Co Ltd Diffusers for fluids
FR1415204A (fr) * 1963-11-29 1965-10-22 Bristol Siddeley Engines Ltd Perfectionnements apportés aux turbines et compresseurs à flux axial
GB1125049A (en) * 1964-12-22 1968-08-28 Bbc Brown Boveri & Cie Improvements in and relating to fluid diffusers
FR2497883A1 (fr) * 1981-01-09 1982-07-16 Etri Sa Ventilateur electrique axial de type plat
US5110560A (en) * 1987-11-23 1992-05-05 United Technologies Corporation Convoluted diffuser
EP0345700A1 (fr) * 1988-06-07 1989-12-13 SKODA koncernovy podnik Carter d'échappement pour turbomachine
EP0695874A1 (fr) * 1994-08-03 1996-02-07 ROLLS-ROYCE plc Un turboréacteur et un diffuseur pour celui-ci
EP1178183A2 (fr) * 2000-07-31 2002-02-06 Alstom (Switzerland) Ltd Turbine à vapeur à basse pression avec un diffuseur à canaux multiples

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US8506233B2 (en) 2009-09-14 2013-08-13 Alstom Technology Ltd. Axial turbine and method for discharging a flow from an axial turbine
DE102010044819B4 (de) 2009-09-14 2022-12-15 General Electric Technology Gmbh Axialturbine und ein Verfahren zum Abführen eines Stroms von einer Axialturbine
FR2967461A1 (fr) * 2010-11-16 2012-05-18 Gen Electric Diffuseur de gaz d'echappement a basse pression pour turbine a vapeur
JP2012107617A (ja) * 2010-11-16 2012-06-07 General Electric Co <Ge> 蒸気タービン用の低圧排出ガスディフューザ

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