EP0568905A1 - Obturateur à disque rotatif pour turbine à vapeur - Google Patents

Obturateur à disque rotatif pour turbine à vapeur Download PDF

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Publication number
EP0568905A1
EP0568905A1 EP19930106846 EP93106846A EP0568905A1 EP 0568905 A1 EP0568905 A1 EP 0568905A1 EP 19930106846 EP19930106846 EP 19930106846 EP 93106846 A EP93106846 A EP 93106846A EP 0568905 A1 EP0568905 A1 EP 0568905A1
Authority
EP
European Patent Office
Prior art keywords
channel
rotation
channel inputs
steam
angle
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
EP19930106846
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German (de)
English (en)
Other versions
EP0568905B1 (fr
Inventor
Dieter Henkelmann
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 Patent GmbH
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ABB Patent GmbH
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Publication date
Application filed by ABB Patent GmbH filed Critical ABB Patent GmbH
Publication of EP0568905A1 publication Critical patent/EP0568905A1/fr
Application granted granted Critical
Publication of EP0568905B1 publication Critical patent/EP0568905B1/fr
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
    • F01D17/00—Regulating or controlling by varying flow
    • F01D17/10—Final actuators
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/18—Final actuators arranged in stator parts varying effective number of nozzles or guide conduits, e.g. sequentially operable valves for 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
    • F01D17/12—Final actuators arranged in stator parts
    • F01D17/14—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits
    • F01D17/148—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of rotatable members, e.g. butterfly valves
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T137/00—Fluid handling
    • Y10T137/8593—Systems
    • Y10T137/86493—Multi-way valve unit
    • Y10T137/86718—Dividing into parallel flow paths with recombining
    • Y10T137/86743—Rotary

Definitions

  • the invention relates to a steam turbine according to the preamble of claim 1.
  • valves are used almost exclusively to control the steam, while slides are used relatively rarely as control elements.
  • One reason for this is probably the high reliability and the exact mechanism of action of valves and, on the other hand, the problems that have to be solved in the practical use of valves. So z. B. the static relief of slide valves which is almost a matter of course in today's valves is not readily possible. Furthermore, the sliding of ungreased, hot and possibly distorted components is fundamentally disadvantageous.
  • the first control stage has a plurality of nozzle groups, the steam flow to each of the nozzle groups being adjusted using a special control valve. It is customary to apply steam to one nozzle group after the other as the power requirement increases, which is done with the help of appropriately controlled control valves or through the control slots of a rotary valve. For a given load condition, therefore, a more or less large number of nozzle groups is generally fully charged, so that this does not result in throttling and the respective nozzles work with a favorable efficiency.
  • the object of the invention is to construct a steam turbine according to the type mentioned in the preamble of claim 1 in such a way that the channel body interacting with the rotary valve can be produced in a simple manner and can easily be adapted to different control tasks.
  • the division of the channel body into a base part and an adapter part results in a significant simplification of production.
  • the adapter part is designed as a ring which is relatively easy to manufacture and which connects the channels of the base part which have been expanded to form nozzle chambers via the channel inputs formed therein with the control slots of the rotary slide valve, provided that these are in a corresponding position.
  • the position and size of the respective channel inputs can be adapted to a desired control characteristic in such a way that several nozzles are combined to form a nozzle group or only very specific nozzles or nozzle groups are activated. This is achieved through their interaction with the control slots provided in the rotary valve.
  • control slots cover an angle of rotation that is at least as large as the channel inputs corresponding to them and that between the closing and opening of all channel inputs there is an angle of rotation which corresponds approximately to the angle of rotation that the channel inputs of a circular path cover.
  • the amount of this angle of rotation can be increased or decreased, depending on the size of the number of circular paths used by control slots and channel inputs.
  • the arrangement enables the simultaneous opening of several, at a uniform distance from each other over a rotation angle of 360 ° arranged nozzles.
  • a nozzle group is formed here, in which, however, it is not, as usual, several nozzles lying next to one another that are combined to form a group, but rather several nozzles uniformly distributed over the entire circumference. This requires a very even heating of the turbine housing and all other parts that are exposed to steam. It is disadvantageous, however, that with an increasing number of circular orbits to be provided with control slots, the arrangement becomes more complicated and with an increasing number of nozzle groups formed, the control characteristic becomes correspondingly coarser.
  • a second variant it is provided that between the opening and closing of all the channel inputs there is an angle of rotation which corresponds approximately to the sum of all angles of rotation which are covered by all the channel inputs arranged on their respective circular paths.
  • the channel inputs are offset from one another on their circular path with respect to the control slots corresponding to them, so that after all the channel inputs of the first circular path have been completely opened, those of the second and subsequently any further circular paths are opened.
  • This enables a very fine-tuned control characteristic, since only one nozzle or one nozzle group is opened one after the other.
  • a disadvantage of this arrangement is that there is a loss of cross-section, since it is not possible to open nozzles in succession over a rotation angle of 360 ° with only one rotary valve.
  • the angle of rotation that cannot be used for the nozzle control could, however, be made usable by opening a bypass after opening all the nozzles, which could be opened by a correspondingly offset control slot.
  • the rotary slide valve is designed as a double slide valve with two mutually overlapping partial slide valves, each of which is provided with control slots, and, starting from the closed position, a first partial slide valve driven to a rotary movement over a non-driven second partial slide valve rotates a predetermined first angle of rotation. At the end of this angle of rotation, the first slide element must grasp the second slide element and take it over a predetermined second angle of rotation.
  • the control slots of the first slide element and the control slots of the second slide element are arranged with respect to one another and correspond to the channel inputs in such a way that one channel input after the other is opened when the first slide element rotates. The channel inputs are closed in the reverse order.
  • the adapter part which is relatively easy to manufacture, must be adapted to the structural conditions of its surroundings. It must be anchored to the base part as precisely and tightly as possible. If necessary, it can extend into the area of the roller bearing rings provided for the rotary slide valve, so that it is then expedient to harden it at least in the area of the receptacles provided for the roller bearing rings.
  • the radial rotary valve has the advantage that it is statically relieved when steam is applied evenly over its entire circumference and thus the wear is kept within limits even with a plain bearing.
  • a disadvantage is the steam deflection required in an axially flow-through turbine. In this regard, preference is given to the axial rotary slide valve, although this can only be relieved of static load by relatively complicated designs and the bearings generally have to absorb the full mass pressure.
  • the control stage of a steam turbine shown in FIGS. 1 and 2 lies at the interface between two turbine parts with different pressures.
  • This is an extraction steam turbine in which the extraction takes place via an extraction channel 5 before the control stage.
  • To control the steam flow rate is an as Radial rotary valve trained rotary valve 1 is provided, which is rotatably mounted on a channel body 2, and this in turn is flange-mounted on a fixed guide vane carrier 3. The entire arrangement is enclosed by a turbine housing 4.
  • the steam coming from the low-pressure part of the steam turbine flows through the rotary valve 1 in the area of a control slot 11 and passes via a channel inlet 12 of the channel body 2 into a nozzle chamber 14 and from here to a nozzle 15, in order to be directed from there to a control wheel 16 with control wheel blades 17 and finally to drive the rotor blades 19 lying between guide blades 18 and thus the turbine rotor 20.
  • the special design of both the rotary slide valve 1 and the channel body 2 enables a very fine-tuned nozzle group control.
  • the rotary slide valve 1 has two control slots 11a, 11b which are arranged on adjacent circular paths and are offset by 180 ° to one another and correspond to the channel inputs 12 of the channel body 2.
  • three channel inputs 12a, 12b, 12c lie on a corresponding circular path provided with the same radius as the control slot 11b, but offset by an angle of rotation of 180 °.
  • three further channel inputs 12d, 12e, 12f lie on a circular path with the same radius as the control slot 11a, again offset by an angle of rotation of 180 °.
  • the rotary valve 1 shows a position of the rotary valve in which it has opened the channel inputs 12, the rotary valve 1 according to FIG. 2 is in a position rotated by 180 ° in which all the channel inputs 12 are closed.
  • the control slot would be first 11a meet the channel entrance 12f and the control slot 11b meet the channel entrance 12a.
  • the nozzle groups connected to the channel inlets 12a, 12f would therefore be the first to be supplied with steam.
  • the rotary slide valve could be opened more and more, the channel inputs 12e, 12b next being captured by the control slots 11a, 11b. After moving the rotary valve 1 over a rotation angle of 180 °, all the channel inputs 12 would be fully open.
  • roller bearing rings 10 which can be constructed as axial needle rims for an axial rotary valve or as radial needle rings for a radial rotary valve.
  • the roller bearing rings 10 are arranged so that the control slots 11 on the one hand and the channel inputs on the other come to lie between them and this results in the best possible support for the rotary valve.
  • an inner roller bearing ring 10b lying near the axis and an outer roller bearing ring 10a lying outside are therefore required.
  • a toothed ring 9 is provided in the area of the outer edge of the axial rotary slide valve 1 even outside the outer roller bearing ring 10a. into which a drive pinion 8 engages, which is connected via a flexible cardan shaft 7 to a servo motor 6, which enables the rotary movement of the rotary valve 1 and is fastened to the turbine housing 4.
  • the rotary valve 1 and also the channel body 2 can be assembled with its adapter part 2a and its base part 2b over the shaft during assembly, these are horizontally divided into rotary valve halves 1a, 1b and channel body halves.
  • the roller bearing rings which can otherwise correspond to commercially available designs, must be divided horizontally.
  • Parting joint flanges such as the rotary slide joint part flange 13 shown here, make it possible to connect the two halves that belong together.
  • FIG. 1 also shows how the rotary valve 1 is anchored to the channel body 2 with a cam or collar 22 on the one hand and in an annular groove 21 of the channel body 2.
  • the channel body in turn is flanged to the guide vane carrier 3 with screws 23.
  • the two roller bearing rings 10a, 10b are largely sunk in the channel body 2.
  • the channel body 2 By dividing the channel body 2 into a base part 2b and an adapter part 2a, the latter forms with the channel inputs 12 provided in it a connection between the control slots 11 of the rotary valve 1 and the channels of the base part 2b widened into nozzle chambers 14.
  • the insertion and connection of the adapter part 2a on the base part 2b must be done in a known manner so that there is no leakage between the two parts. Otherwise, the adapter part can be adapted to the design environment, taking into account a design suitable for production. So it can possibly extend into the area of the rolling bearing rings, in which case it makes sense the adapter part 2a would be subjected to a limited or complete hardening.
  • FIGS. 3 to 12 show purely schematic representations of certain constellations of the control slots arranged on several circular paths, indicated only by lines, and of the channel inputs corresponding to them.
  • the channel inputs are also made visible, although these are actually covered when the rotary slide valve is viewed from above. In both examples, the rotary valve 1 is in the closed position.
  • the first control slot S1 which extends over an angle of rotation of 270 °, will meet the first channel inputs K1 and open them one after the other.
  • the second control slot S2 which extends over an angle of rotation of 180 °, will meet the second channel inputs K2 and also open them one after the other.
  • control slots SS1 to SS 4 which are arranged on four circular paths, which are offset by 90 ° to each other and extend over an angle of rotation of 90 °, so that they form an angle overall cover from 360 °, the first channel entrance of the channel inputs KA1 to KA4. So two opposite channel entrances are opened twice, which leads to the application of four symmetrically arranged nozzles or nozzle groups.
  • FIGS. 9 to 12 show the various opening positions of the rotary valve 1 after a further 90 ° rotation in order to open the rotary valve in the clockwise direction.
  • the first slide valve 1a is driven clockwise by a servo motor, while the second slide valve 1b remains in its position.
  • the first control slot SL1 first meets a third control slot SL3 of the second slide element 1b and opens the channel inputs KE1 arranged underneath, as shown in FIGS. 9 and 10.
  • all channel inputs KE1 below the control slots SL3 are opened.
  • the two slide elements 1a and 1b are now connected to one another and rotated further together by a driver designed in a known manner, the control slots SL1 and SL2 being located above the control slots SL3 and SL4.
  • the opening of the second channel inputs KE2 now beginning, as shown in FIGS. 11 and 12, is easily understandable.
  • the double slide it is possible to control all the nozzles or groups of nozzles individually one after the other.
  • the driver must be designed so that when the rotary slide 1 is turned back into the closed position, it only releases the connection of the two slide members 1a, 1b after an angle of rotation of 180 °.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP19930106846 1992-05-04 1993-04-28 Obturateur à disque rotatif pour turbine à vapeur Expired - Lifetime EP0568905B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4214773 1992-05-04
DE19924214773 DE4214773A1 (de) 1992-05-04 1992-05-04 Dampfturbine mit einem Drehschieber zur Steuerung des Dampfdurchsatzes

Publications (2)

Publication Number Publication Date
EP0568905A1 true EP0568905A1 (fr) 1993-11-10
EP0568905B1 EP0568905B1 (fr) 1995-08-09

Family

ID=6458174

Family Applications (1)

Application Number Title Priority Date Filing Date
EP19930106846 Expired - Lifetime EP0568905B1 (fr) 1992-05-04 1993-04-28 Obturateur à disque rotatif pour turbine à vapeur

Country Status (3)

Country Link
US (1) US5383763A (fr)
EP (1) EP0568905B1 (fr)
DE (2) DE4214773A1 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010052041A1 (fr) 2008-11-10 2010-05-14 Siemens Aktiengesellschaft Turbine avec boîtier compact d'admission grâce à des vannes de régulation situées à l'intérieur

Families Citing this family (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB2376723B (en) * 2001-06-20 2004-12-08 Rolls Royce Plc Tandem guide vane
EP1273762B1 (fr) * 2001-07-02 2008-03-26 Ansaldo Energia S.P.A. Système de réglage du premier étage d'une turbine à vapeur
US7214029B2 (en) * 2004-07-01 2007-05-08 Richter Donald L Laminar air turbine
DE102010042412A1 (de) * 2010-10-13 2012-04-19 Robert Bosch Gmbh Dampfturbine
EP2716877B1 (fr) * 2012-10-02 2018-11-28 Siemens Aktiengesellschaft Étage adaptatif pour chutes de pression élevées dans une turbine et turbine
US11156152B2 (en) 2018-02-27 2021-10-26 Borgwarner Inc. Waste heat recovery system with nozzle block including geometrically different nozzles and turbine expander for the same
IT202100022412A1 (it) * 2021-08-27 2023-02-27 Nuovo Pignone Tecnologie Srl Valvola a griglia bilanciata per estrazione di vapore

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1894117A (en) * 1931-10-15 1933-01-10 Gen Electric Elastic fluid turbine
US3209537A (en) * 1960-05-02 1965-10-05 Bendix Corp Motive fluid control for a re-expansion gas turbine engine
CH487334A (de) * 1969-03-07 1970-03-15 Le Metallichesky Zd Im Xxii Si Absperrorgan für den Dampfweg einer Dampfturbine
EP0508067A1 (fr) * 1991-04-08 1992-10-14 Asea Brown Boveri Ag Dispositif de réglage de la section d'écoulement dans une turbomachine

Family Cites Families (12)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US707727A (en) * 1901-05-10 1902-08-26 Richard Schulz Steam-turbine.
US793540A (en) * 1905-02-13 1905-06-27 Elmer K Purvis Steam-turbine.
US1291322A (en) * 1917-07-19 1919-01-14 Ljungstroems Angturbin Ab Elastic-fluid turbine.
US1544285A (en) * 1923-08-13 1925-06-30 Westinghouse Electric & Mfg Co Bleeder turbine
US2184661A (en) * 1936-10-30 1939-12-26 B F Sturtevant Co Elastic fluid turbine
US2186952A (en) * 1938-06-21 1940-01-16 Gen Electric Elastic fluid turbine
US3589829A (en) * 1969-03-13 1971-06-29 Anatoly Alexandrovich Schetini Shutoff device for steam path of steam turbine
US3669562A (en) * 1971-01-12 1972-06-13 Westinghouse Electric Corp Extraction turbine with a servo actuated balanced grid valve for extraction control
DD134128B1 (de) * 1977-12-14 1981-12-30 Werner Birke Dampfturbine ohne geregelte entnahme,insbesondere in eingehaeusiger ausfuehrung
JPS56165704A (en) * 1980-05-22 1981-12-19 Toshiba Corp Rotary disc valve
SU916767A1 (ru) * 1980-07-07 1982-03-30 Kh Ts K B Glavenergoremonta Регулирующая диафрагма паровой турбины 1
JPS597707A (ja) * 1982-07-07 1984-01-14 Hitachi Ltd 抽気加減弁装置

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1894117A (en) * 1931-10-15 1933-01-10 Gen Electric Elastic fluid turbine
US3209537A (en) * 1960-05-02 1965-10-05 Bendix Corp Motive fluid control for a re-expansion gas turbine engine
CH487334A (de) * 1969-03-07 1970-03-15 Le Metallichesky Zd Im Xxii Si Absperrorgan für den Dampfweg einer Dampfturbine
EP0508067A1 (fr) * 1991-04-08 1992-10-14 Asea Brown Boveri Ag Dispositif de réglage de la section d'écoulement dans une turbomachine

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN vol. 006, no. 50 (M-120)3. April 1982 & JP-56 165 704 ( TOSHIBA CORP ) 19. Dezember 1981 *

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2010052041A1 (fr) 2008-11-10 2010-05-14 Siemens Aktiengesellschaft Turbine avec boîtier compact d'admission grâce à des vannes de régulation situées à l'intérieur

Also Published As

Publication number Publication date
DE4214773A1 (de) 1993-11-11
US5383763A (en) 1995-01-24
DE59300444D1 (de) 1995-09-14
EP0568905B1 (fr) 1995-08-09

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