EP0326709B1 - Dampfturbine - Google Patents

Dampfturbine Download PDF

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Publication number
EP0326709B1
EP0326709B1 EP88121746A EP88121746A EP0326709B1 EP 0326709 B1 EP0326709 B1 EP 0326709B1 EP 88121746 A EP88121746 A EP 88121746A EP 88121746 A EP88121746 A EP 88121746A EP 0326709 B1 EP0326709 B1 EP 0326709B1
Authority
EP
European Patent Office
Prior art keywords
flow
steam
group
steam turbine
stage group
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
EP88121746A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0326709A1 (de
Inventor
Jan-Erik Bertilsson
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.)
ABB Asea Brown Boveri Ltd
Original Assignee
ABB Asea Brown Boveri Ltd
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 ABB Asea Brown Boveri Ltd filed Critical ABB Asea Brown Boveri Ltd
Publication of EP0326709A1 publication Critical patent/EP0326709A1/de
Application granted granted Critical
Publication of EP0326709B1 publication Critical patent/EP0326709B1/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
    • 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
    • F01D1/023—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 the working-fluid being divided into several separate flows ; several separate fluid flows being united in a single flow; the machine or engine having provision for two or more different possible fluid flow paths

Definitions

  • the invention is based on a steam turbine according to the preamble of patent claim 1.
  • the invention relates to a prior art as known from CH-A-211 167.
  • a multi-stage steam or gas turbine in the event of an overload, one or more pressure stages can be bridged by a bypass channel or by a bypass line in which a controllable valve is arranged. Only the remaining part of the steam or gas flows through the bridged pressure stages.
  • Regulating wheels with separately opening nozzle groups are used to control the output in steam turbine construction, because the efficiency that can be achieved in this way is better for the essential output range than in other systems.
  • the control wheel itself causes work to be extracted from the steam in such a way that the power control itself works optimally.
  • a compensation chamber is provided which enables the transition from partial loading to full loading.
  • the invention seeks to remedy this.
  • the invention as defined in claim 1, solves the problem of bringing about a smoothing of the flow during the transition from partial loading in the control stage to full loading of the remaining stages in a steam turbine which is operated in the partial load range with nozzle group control.
  • the effect of the proposal is that the steam flow is divided into two partial flows after the nozzle group. While a first partial flow acts on a first step group, the other partial flow flows via a bypass channel directly to the second step group, which is now also acted upon by the first partial flow and is therefore a fully acted on step group, in contrast to the step group solely acted upon by the first partial flow.
  • the main advantage of the invention can be seen in the fact that only a subset is applied to the first group of stages. This reduces the dynamic excitation of the blading to approx. 50%. Due to the fact that this partially loaded stage group receives a lower blade height due to the reduced mass flows, higher blade natural frequencies can be expected, which significantly reduces the risk of excitation.
  • the only figure shows the section between the nozzle group control and the first rows of blades of the turbine.
  • a section of a steam turbine can be seen, which shows the area between control wheel 2, nozzle 3 and the first rows of blades 11, 12 of the turbine.
  • the diameter of the control wheel 2 is larger than the diameter of the hub 1.
  • the difference in diameter must be kept such that the length of the overflow channel between the control stage and the reaction stage is acceptable in terms of construction costs, so that the channel volume is sufficient to completely homogenize the flow over the entire circumference of the channel.
  • this optimization itself can be dispensed with, because the steam flow is divided into two partial flows 4, 5 from the outlet of the control wheel 2, in the sense that the partial flow 5 flows through a bypass channel 8, in order then to act upon the stage group Turbine 11, 12 to merge with the other partial flow 4.
  • This second partial flow 4 initially acts on a first stage group 9, 10 of blades, which has a lower blade height than the other stage group 11, 12 provided downstream.
  • this is possible insofar as a reduced mass flow is applied to this first stage group 9, 10.
  • the advantages are eminent: the higher blade natural frequencies of this first stage group 9, 10 bring about a substantial reduction in the risk of excitation, as a result of which the second downstream stage group 11, 12 is subjected to a homogeneous flow.
  • Deflection elements 7 are provided which bring about a uniform distribution of the steam flow over the entire circumference.
  • the division of the steam flow into two partial flows 4, 5, in which the stage group 9, 10 initially acted upon by the partial flow 4 preferably consists of two blade stages, has the effect that the dynamic excitation of the turbine blading is reduced to approximately 50%.
  • the admixture of the partial stream 4 after the first stage group 9, 10 with the other partial stream 5 flowing through the bypass duct 8 takes place in such a way that the following stage group 11, 12 is acted upon almost completely by a single steam stream 6. This is achieved with the participation of the deflection elements 7 which have already been tightened.
  • a good admixture is further achieved in that the bypass channel 8 is designed spirally.
  • a channel 13 to the hub 1 is designed so that at a fourth valve point, i.e.
  • the steam flow initially acts on the first stage group 9, 10 for the most part.
  • An uneven flow with flow inhomogeneities is not to be feared in this operating mode, because in this case the steam flow is not influenced by the nozzle group control.
  • the steam flow is deflected upward in the direction of the bypass channel 8 by the swirl caused by the nozzle group control 2, 3, as a result of which the desired compensation of the flow irregularities resulting from the partial load is accomplished.
  • a distribution of the partial flow in the sense of achieving a flow homogeneity of the steam flow can also be achieved by installing throttle elements (not shown).

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Turbine Rotor Nozzle Sealing (AREA)
  • Control Of Turbines (AREA)
EP88121746A 1988-02-01 1988-12-28 Dampfturbine Expired - Lifetime EP0326709B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH332/88 1988-02-01
CH332/88A CH675146A5 (enrdf_load_stackoverflow) 1988-02-01 1988-02-01

Publications (2)

Publication Number Publication Date
EP0326709A1 EP0326709A1 (de) 1989-08-09
EP0326709B1 true EP0326709B1 (de) 1993-03-10

Family

ID=4184607

Family Applications (1)

Application Number Title Priority Date Filing Date
EP88121746A Expired - Lifetime EP0326709B1 (de) 1988-02-01 1988-12-28 Dampfturbine

Country Status (5)

Country Link
US (1) US4979873A (enrdf_load_stackoverflow)
EP (1) EP0326709B1 (enrdf_load_stackoverflow)
JP (1) JPH01224401A (enrdf_load_stackoverflow)
CH (1) CH675146A5 (enrdf_load_stackoverflow)
DE (1) DE3879170D1 (enrdf_load_stackoverflow)

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5676521A (en) * 1996-07-22 1997-10-14 Haynes; Christopher J. Steam turbine with superheat retaining extraction
EP1010857B1 (de) 1998-12-16 2003-06-04 ALSTOM (Switzerland) Ltd Modulare Dampfturbine mit Standardbeschaufelung
DE10102899A1 (de) * 2001-01-23 2002-08-08 Martin Ziegler Perpetuum Mobile der Dritten Art
DE102010042412A1 (de) * 2010-10-13 2012-04-19 Robert Bosch Gmbh Dampfturbine
JP5913910B2 (ja) * 2011-04-26 2016-04-27 国際計測器株式会社 直動アクチュエータ及び加振装置

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1090110A (en) * 1910-11-17 1914-03-10 Gen Electric Multistage turbine.
FR731766A (fr) * 1931-03-24 1932-09-08 Ljungstroms Angturbin Ab Dispositif applicable aux jeux d'aubes axiales de turbines à gaz ou à vapeur
DE663207C (de) * 1936-07-11 1938-08-01 Oskar Jebens Turbine, insbesondere fuer Schiffsanlagen, mit UEberbrueckung von Stufen
GB530022A (en) * 1938-06-17 1940-12-03 British Thomson Houston Co Ltd Improvements in and relating to elastic fluid turbines
CH211167A (de) * 1939-06-15 1940-08-31 Escher Wyss Maschf Ag Mehrstufige Dampf- oder Gasturbine, deren erstes Stufengefälle unterkritisch ist, und welcher zur Erhöhung der Leistungsfähigkeit zusätzliches Arbeitsmittel zugeführt wird.
US2269235A (en) * 1939-12-22 1942-01-06 Gen Electric Multistage elastic fluid turbine
DE831580C (de) * 1948-10-02 1952-02-14 Steinmueller Gmbh L & C Vorrichtung zur Foerderung staubhaltiger Gase mittels Axialgeblaese
US2952973A (en) * 1958-06-02 1960-09-20 Gen Motors Corp Turbofan-ramjet engine
DE2844681B1 (de) * 1978-10-13 1980-04-10 Blohm Voss Ag Entnahmekondensationsturbine
JPS5990703A (ja) * 1982-11-15 1984-05-25 Fuji Electric Co Ltd 蒸気タ−ビンの調速段
US4527387A (en) * 1982-11-26 1985-07-09 General Electric Company Particle separator scroll vanes

Also Published As

Publication number Publication date
CH675146A5 (enrdf_load_stackoverflow) 1990-08-31
DE3879170D1 (de) 1993-04-15
JPH01224401A (ja) 1989-09-07
EP0326709A1 (de) 1989-08-09
US4979873A (en) 1990-12-25

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