EP0894184A1 - Systeme de commande et procede pour l'introduction de vapeur de surcharge dans une turbine a vapeur - Google Patents

Systeme de commande et procede pour l'introduction de vapeur de surcharge dans une turbine a vapeur

Info

Publication number
EP0894184A1
EP0894184A1 EP97922832A EP97922832A EP0894184A1 EP 0894184 A1 EP0894184 A1 EP 0894184A1 EP 97922832 A EP97922832 A EP 97922832A EP 97922832 A EP97922832 A EP 97922832A EP 0894184 A1 EP0894184 A1 EP 0894184A1
Authority
EP
European Patent Office
Prior art keywords
steam
turbine
flow path
valve
control valve
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Withdrawn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
EP97922832A
Other languages
German (de)
English (en)
Inventor
Dietmar Bergmann
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
Publication of EP0894184A1 publication Critical patent/EP0894184A1/fr
Withdrawn legal-status Critical Current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
    • 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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/105—Final actuators by passing part of the fluid
    • 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 relates to a control arrangement for the steam supply of a steam turbine with a main flow path for steam, wherein a control valve is provided through which the flow cross section of the main flow path can be adjusted.
  • the invention further relates to a method for introducing overload steam into a steam turbine which has a plurality of turbine stages.
  • Steam turbines with partial impingement are partially designed so that they can temporarily deliver an output that exceeds their calculated design output. This increased power is applied to steam turbines which are operated with partial admission, as described in the book "Steam Turbines, Introduction m Construction and Operation” by Hans-Walter Roemer, W. Girardet, Essen, 1972, in Section 1, 7.3 and 7.4 is described.
  • a partial loading of the steam turbine is achieved via a plurality of valves connected in parallel, which can be opened one after the other, so that a volume of controllable live steam can be supplied to a first row of turbine guide vanes, the control stage.
  • the valves are connected to a common valve bar. A successive opening of the valves is controlled via its stroke.
  • An additional overload valve connected to the valve bar is provided to achieve a higher output in the short term.
  • the increased steam throughput is processed in fewer turbine stages, which results in a decrease in efficiency, albeit usually less, which, however, due to the increasing length of the subsequent stages - an increase in performance is achieved.
  • the object of the invention is to provide a control arrangement with which a partial steam flow, in particular for the introduction of overload steam into a steam turbine, can be provided.
  • a further object of the invention is to provide a method for introducing overload steam into a steam turbine.
  • the object directed to a control arrangement is achieved by a control arrangement for the steam supply to a steam turbine, which has a main flow path for steam, which has a flow cross section that can be adjusted by at least one control valve, through which a bypass flow path provided for steam with the main flow path is fluidically connectable.
  • the control valve thus fulfills a double function, namely the regulation of the steam quantity of the steam turbine and an overload initiation to increase the power of the turbine.
  • the secondary flow path is preferably completely open when the control valve also completely clears the flow cross section. With a completely open main flow path, the secondary flow path is therefore preferably always fully loaded with live steam, so that in this case a constant overload (increase in output) can be achieved.
  • a constant overload increase in output
  • This is particularly advantageous in the case of a throttle-controlled steam turbine.
  • steam can be overloaded into a drum of the steam turbine that receives the turbine shaft with blading.
  • a throttling at normal load must be carried out.
  • An overload of 5% requires throttling of approximately 5%. This would correspond to a deterioration in the specific heat consumption of the steam turbine of approximately 0.5% compared to operation without throttling.
  • the bypass flow path is in the case of partial loading, i.e. with completely or at least partially blocked
  • the control valve comprises a valve piston and a piston housing.
  • the piston housing has an inlet line branching from the main flow path to the valve piston and an outlet line leading from the valve piston into the secondary flow path.
  • the valve piston in turn has a secondary duct through which the inlet line can be connected to the outlet line in terms of flow technology.
  • the secondary channel is formed as an annular channel which is essentially rotationally symmetrical to the main axis.
  • the secondary duct is also possible, for example as a central bore or as a groove in the piston housing that can be closed by the piston.
  • the control valve is preferably a diffuser valve, in particular a seat diffuser valve. This can be combined with a quick-closing valve in the fresh steam feed of the steam turbine.
  • Valve piston and the valve stem connected to it can be made in one piece. Sliding surfaces on the valve spindle and the valve piston can be armored with stellite, for example, according to the plasma arc method.
  • the valve piston can be controlled via a hydraulic single drive.
  • the control arrangement is preferably arranged on a steam turbine, in particular a throttle-controlled steam turbine, which has a plurality of turbine stages.
  • the turbine stages each comprise a row of moving blades and a row of guide vanes, the main flow path m ending in the first turbine stage in the flow direction, the so-called control stage, and the secondary flow path opening in a turbine stage located downstream of the control stage.
  • live steam which has essentially the same steam state as the live steam flowing into the control stage, is over the secondary flow path is fed directly to a turbine stage further downstream.
  • the state of steam is increased, in particular the pressure and the temperature, so that the runner is subjected to a higher load with a higher turbine output as a result.
  • the control arrangement is preferably at least partially cast with the turbine housing of the steam turbine.
  • the control valve which can be cast directly onto the turbine housing, and the secondary flow path, which can be designed, for example, as an overload line cast on or in the turbine housing, are suitable for this purpose.
  • the at least partial incorporation of the control arrangement into the turbine housing provides a particularly simple constructive design of a device for overload introduction with little constructive effort and increased mechanical safety.
  • a control valve can also be screwed to the turbine housing and the overload line drilled, welded or screwed to the turbine housing.
  • the object directed to a method for introducing overload steam into a steam turbine is achieved according to the invention in that when a control valve is completely opened, through which fresh steam can be throttled via a main flow path to the first turbine stage in the direction of flow, the so-called control stage, a secondary flow ⁇ is opened path through which a partial steam flow is branched off from the control valve and is fed to a turbine stage located downstream of the control stage.
  • the control valve thus has a double function in such a way that it serves on the one hand to regulate the amount of live steam acting on the control stage and on the other hand also enables a turbine stage located further downstream to be applied. This further loading is preferably carried out with a complete open the control valve and thus a full application of the steam turbine.
  • FIG. 1 shows a cross section through a steam turbine with a partially cast-on control arrangement
  • FIG. 2 shows a detail according to FIG. 1 on an enlarged scale
  • FIG. 3 shows a longitudinal section of a steam turbine directed along a turbine axis.
  • FIGS. 1, 2 and 3 are partially shown schematically and not to scale.
  • the reference symbols used in the figures each have the same meaning.
  • FIG. 1 shows a cross section through a steam turbine 11 with a control arrangement 1 for overload introduction of steam into a turbine stage 18 located downstream of a first turbine stage, the actuating stage 18a (see FIG. 3).
  • Each control valve 4 has a valve piston 4a directed along a main axis 15 and a piston housing 4b which at least partially surrounds the valve piston 4a.
  • the valve piston 4a is in the valve tilgephaseuse 4b displaceable along the main axis 15.
  • a main flow path 2 for steam for driving a turbine shaft 8 arranged in the turbine housing 9 and extending along a turbine axis 20 runs through each control valve 4 (see FIG. 3).
  • the main flow path 2 has a flow cross section 12 which can be adjusted by the valve piston 4a.
  • the valve piston 4a has an annular channel 7 which is essentially rotationally symmetrical with respect to the main axis 15.
  • the piston housing 4b has an inlet line 13 leading from the main flow channel 2 to the valve piston 4a.
  • the piston housing 4b On an opposite side of the inlet line 13, the piston housing 4b has an outlet line 14 which opens into a secondary flow path 3.
  • the secondary flow path 3 comprises an overload line 6 running in the turbine housing 9
  • the turbine housing 9 is cast in, drilled or designed as a pipeline and opens (see FIG. 3) into a turbine stage 18 arranged downstream of the setting stage 18a.
  • Each turbine stage 18, 18a has a row of guide vanes 17 and an adjacent row of rotor blades 16 lying downstream.
  • valve piston 4a is moved along the main axis 15 in accordance with the required power rating of the steam turbine 11 by an actuator (not shown), so that the flow cross section 12 has a corresponding throughput
  • Frsichdampf 19 allows into the steam turbine 11.
  • the valve piston 4a When the flow cross-section 12 is completely opened, the valve piston 4a is in a position or can be moved into a position along the main axis 15 in which the inlet line 13 is connected to the outlet line 14 in terms of flow technology via the secondary channel 7 designed as an annular channel .
  • the secondary channel 7 designed as an annular channel .
  • a partial flow of the steam 19 is conducted from the main flow path 2 into the secondary flow path 3 and an overload initiation is achieved. From the control valve 4, a live steam flow 19 is thus
  • the invention is characterized by a control arrangement in which, in a control valve which regulates the amount of live steam flowing into the steam turbine, a partial steam flow is additionally branched off from the live steam flow and fed to a downstream turbine stage for overload initiation.
  • a control valve which regulates the amount of live steam flowing into the steam turbine
  • a partial steam flow is additionally branched off from the live steam flow and fed to a downstream turbine stage for overload initiation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Control Of Turbines (AREA)

Abstract

L'invention concerne un système de commande (1) pour fournir de la vapeur à une turbine à vapeur (11) présentant un trajet d'écoulement principal (2) destiné à la vapeur. Ce trajet d'écoulement principal (2) possède une section d'écoulement (12) réglable par au moins une soupape de réglage (4). Un trajet d'écoulement secondaire (3) peut être fluidiquement relié au trajet d'écoulement principal (2) par l'intermédiaire de la soupape de réglage (4). L'invention concerne également un procédé pour introduire de la vapeur de surcharge dans une turbine à vapeur (11), dans lequel, dans la soupape de réglage (4), une partie de l'écoulement de vapeur vive (19) est dérivée et fournie à un étage de turbine (18) situé en aval d'un étage de réglage (18a).
EP97922832A 1996-04-26 1997-04-14 Systeme de commande et procede pour l'introduction de vapeur de surcharge dans une turbine a vapeur Withdrawn EP0894184A1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE19616837 1996-04-26
DE19616837 1996-04-26
PCT/DE1997/000748 WO1997041335A1 (fr) 1996-04-26 1997-04-14 Systeme de commande et procede pour l'introduction de vapeur de surcharge dans une turbine a vapeur

Publications (1)

Publication Number Publication Date
EP0894184A1 true EP0894184A1 (fr) 1999-02-03

Family

ID=7792600

Family Applications (1)

Application Number Title Priority Date Filing Date
EP97922832A Withdrawn EP0894184A1 (fr) 1996-04-26 1997-04-14 Systeme de commande et procede pour l'introduction de vapeur de surcharge dans une turbine a vapeur

Country Status (7)

Country Link
EP (1) EP0894184A1 (fr)
JP (1) JP2000509457A (fr)
KR (1) KR20000065026A (fr)
CN (1) CN1221471A (fr)
CZ (1) CZ296898A3 (fr)
PL (1) PL329155A1 (fr)
WO (1) WO1997041335A1 (fr)

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN1245853A (zh) * 1999-07-06 2000-03-01 赫思厘 前冲式厕具
CN101094971B (zh) * 2004-11-02 2011-03-09 阿尔斯托姆科技有限公司 涡轮机装置的优化的涡轮机级以及设计方法
JP2010048216A (ja) * 2008-08-25 2010-03-04 Fuji Electric Systems Co Ltd 蒸気タービンの主蒸気流入部
JP5411087B2 (ja) * 2010-08-12 2014-02-12 株式会社日立製作所 蒸気タービンの弁装置及びその操作方法
EP2781690A1 (fr) * 2013-03-20 2014-09-24 Siemens Aktiengesellschaft Soupape pour une turbine à vapeur
JP6285692B2 (ja) * 2013-11-05 2018-02-28 三菱日立パワーシステムズ株式会社 蒸気タービン設備
EP3128136A1 (fr) 2015-08-07 2017-02-08 Siemens Aktiengesellschaft Introduction de surcharge dans une turbine a vapeur
DE102016215770A1 (de) * 2016-08-23 2018-03-01 Siemens Aktiengesellschaft Ausströmgehäuse und Dampfturbine mit Ausströmgehäuse
CN113700534A (zh) * 2021-08-31 2021-11-26 中国船舶重工集团公司第七0三研究所 大功率船舶汽轮机外旁通汽缸

Family Cites Families (8)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR965789A (fr) * 1950-09-21
FR404495A (fr) * 1909-06-26 1909-12-02 Pokorny & Wittekind Maschb Ag Turbine à vapeur à basse pression comportant deux turbines partielles montées sur un meme arbre
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.
CH583371A5 (fr) * 1975-04-30 1976-12-31 Bbc Brown Boveri & Cie
JPS5564405U (fr) * 1978-10-27 1980-05-02
AU537607B2 (en) * 1980-12-02 1984-07-05 Hitachi Limited Combined valve for use in a reheating steam turbine
US4403476A (en) * 1981-11-02 1983-09-13 General Electric Company Method for operating a steam turbine with an overload valve
US4753077A (en) * 1987-06-01 1988-06-28 Synthetic Sink Multi-staged turbine system with bypassable bottom stage

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
See references of WO9741335A1 *

Also Published As

Publication number Publication date
CZ296898A3 (cs) 1999-02-17
KR20000065026A (ko) 2000-11-06
WO1997041335A1 (fr) 1997-11-06
JP2000509457A (ja) 2000-07-25
CN1221471A (zh) 1999-06-30
PL329155A1 (en) 1999-03-15

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