EP2000632A1 - Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile - Google Patents

Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile Download PDF

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Publication number
EP2000632A1
EP2000632A1 EP07011268A EP07011268A EP2000632A1 EP 2000632 A1 EP2000632 A1 EP 2000632A1 EP 07011268 A EP07011268 A EP 07011268A EP 07011268 A EP07011268 A EP 07011268A EP 2000632 A1 EP2000632 A1 EP 2000632A1
Authority
EP
European Patent Office
Prior art keywords
control valve
turbine
nozzle group
secondary control
working medium
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Withdrawn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
EP07011268A
Other languages
German (de)
English (en)
French (fr)
Inventor
Walter Gehringer
Richard Geist
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
Siemens Corp
Original Assignee
Siemens AG
Siemens Corp
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, Siemens Corp filed Critical Siemens AG
Priority to EP07011268A priority Critical patent/EP2000632A1/de
Priority to CA002689224A priority patent/CA2689224A1/en
Priority to BRPI0812409-4A2A priority patent/BRPI0812409A2/pt
Priority to CN200880019281A priority patent/CN101680308A/zh
Priority to EP08736568A priority patent/EP2153029A1/de
Priority to US12/602,891 priority patent/US20100178153A1/en
Priority to PCT/EP2008/055045 priority patent/WO2008148607A1/de
Publication of EP2000632A1 publication Critical patent/EP2000632A1/de
Withdrawn legal-status Critical Current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
    • 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
    • F01D17/141—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path
    • F01D17/145—Final actuators arranged in stator parts varying effective cross-sectional area of nozzles or guide conduits by means of shiftable members or valves obturating part of the flow path by means of valves, e.g. for steam turbines

Definitions

  • the present invention relates to a turbine having an inflow housing, which has an inlet for an inflowing working medium, a plurality of control valves and at least two nozzle groups, the flow of the working medium from the inlet into the nozzle groups being controllable by means of the control valves.
  • the inflow housing is the part of the turbine housing into which the working medium flows into the turbine and in which the working medium is directed onto the rotor.
  • the inflow housing comprises a plurality of nozzle groups, which extend around the rotor in a ring-shaped manner on a common diameter. Each nozzle group combines several nozzles that are directed at the rotor.
  • the working medium flowing in through the inlet is directed into the nozzle groups, exits the nozzles and flows through the rotor blades of the rotor.
  • the division of the nozzles into nozzle groups is used to regulate the output.
  • the total mass flow rate and thus the performance of the turbine can be controlled by varying the nozzle groups acted upon with working fluid.
  • the distribution of the working medium to the individual nozzle groups and the individual mass flow rate per nozzle group is controlled by the control valves.
  • a quick-closing valve is provided, which closes the inlet and thus can prevent the total flow through the turbine.
  • the inflow housing of a known steam turbine is in FIG. 2a of the DE 1 915 267 A1 shown.
  • the Control valves in a so-called valve housing or valve box above the actual turbine housing.
  • the working medium flows in laterally through an inlet, passes through a quick-acting valve and enters the valve box, from which five supply lines connected in parallel each branch off via a control valve to five nozzle groups.
  • Each nozzle group thus has its own supply line and its own control valve.
  • the respective supply lines and valves are connected in parallel.
  • a circuit diagram of this arrangement is shown in the attached FIG. 1 ,
  • the linearly guided valve spindles of the control valves are usually driven in each case with an individual motor and not, as shown in this publication, via a control bar.
  • control valves are arranged outside the turbine housing and connected via welded pipes or pipe bends with the nozzle housing.
  • the separated from the inflow housing live steam flow is thus performed by comparatively long pipes to the nozzle groups.
  • the present invention has the object, a turbine of the type mentioned so on to form that their Einströmgephaseuse builds as compact as possible, and that flow losses are reduced by long lines.
  • This task is initially solved by the fact that the control valves are divided functionally into a primary control valve and at least one secondary control valve.
  • the inlet is to be connected to the first nozzle group via an inlet pipe, wherein the inlet pipe is to be guided by the primary control valve such that the flow of the working medium along the inlet pipe is controllable by means of the primary control valve.
  • the secondary control valve connects the first nozzle group to the second nozzle group in such a way that the flow of the working medium from the first nozzle group into the second nozzle group is controllable by means of the secondary control valve.
  • the present invention is based on the basic idea of no longer controlling the individual nozzle groups with control valves connected in parallel, but of connecting the nozzle groups in series via the secondary control valves. This measure basically makes it possible to save pipeline passages in the inflow housing and thus achieve a more compact design. The pipelines also reduce the flow losses.
  • the valve position of the primary control valve is decisive, since this can control the entire flow of the working fluid through the turbine. Since the first nozzle group is connected directly to the inlet via the primary control valve and the quick-acting valve, the first nozzle group is with the primary control valve open and
  • a preferred embodiment of the invention provides to provide at least three series-connected nozzle groups in the inflow, so that at least two secondary control valves are required, which connect the first with the second and the second with the third nozzle group. In order to allow the power control even smaller steps, it is also advisable to provide a fourth or fifth nozzle group; the number of secondary control valves needed would consequently increase to three or four.
  • the start-up of such a turbine is preferably carried out by the following steps:
  • the quick-action valve is initially opened, whereby the pressure of the working medium builds up to the valve seat of the primary control valve.
  • the first nozzle group is directly controlled by the primary control valve.
  • the turbine is triggered and brought to operating speed.
  • the main control valve is opened, thus releasing the cross section for the entire mass flow of the working medium. Since the mass flow rate is capped by the nozzle cross sections of the first group, the performance of the turbine remains constant when the maximum mass flow rate is reached.
  • the first secondary control valve is opened, so that the current now also reaches the second nozzle group.
  • the mass flow rate increases as a result. If the turbine has further, downstream nozzle groups, these are connected later by opening the respective secondary control valves.
  • the interconnection of the individual nozzle groups according to the invention makes it possible to arrange the shut-off elements of the secondary control valves directly between the annular sector-shaped nozzle groups extending around the rotor, that is to say on the same diameter as the nozzle groups.
  • the flow paths in the inflow housing are thereby further shortened.
  • the installation space of the inflow housing can be significantly reduced in this design by the fact that the actuation axes of the secondary control valves are arranged radially to the axis of rotation of the rotor.
  • the actuating travel of the shut-off devices is then not tangential to the diameter of the nozzle groups, but rather radially. Of the necessary outer diameter of the inflow is thereby lowered.
  • the shut-off elements of the secondary control valves are designed as rotationally switchable control valves, so that the actuating axis is an axis of rotation.
  • the rotary shut-off valves take up less space than linear shut-off valves, require lower actuation forces and need not be completely sealed.
  • the use of rotationally connected, not completely sealing shut-off devices is also possible because the secondary control valves no quick-closing function is required. This quick-closing function is taken over by the quick-acting valve and the downstream primary control valve.
  • the inflow housing of the turbine according to the invention is designed substantially annular and divided into at least two housing halves, wherein the inlet conduit is an integral part of a housing half.
  • the advantage of this design is that the line of the working medium can be welded without flange connection, that only one influx into the turbine housing with piston ring has to be sealed, and that all components warm up well during the starting phase.
  • two housing halves, each with an integrated inlet can be provided to double the nominal diameter of the Zudampfan gleiches total.
  • the present invention is preferably applied in the field of axial-flow steam turbines.
  • FIG. 1 schematically shows the valve circuit of a conventional steam turbine, as it is known from the document mentioned.
  • the housing of the turbine comprises an inflow housing 1, in which the rotor, not shown, is rotatably mounted. Impacted with working medium, the rotor over four nozzle groups 21, 22, 23, 24, which extend in an annular sector on a common diameter D around the rotor around.
  • the working medium - in the case of a steam turbine water vapor - flows through an inlet 3 in the inflow 1 a.
  • a quick-acting valve 4 is arranged, by means of which the inlet 3 can be quickly closed in emergencies.
  • the flow fanned into four supply lines 51, 52, 53, 54 which connect the inlet 3 respectively with the nozzle groups 21, 22, 23, 24.
  • the flow of the working medium through the supply lines 51, 52, 53, 54 is controlled by respective control valves 61, 62, 63, 64.
  • the nozzle groups 21 to 24 are thus connected in parallel via their respective supply lines 51 to 54 and the associated control valves 61 to 64.
  • the wiring according to the invention is in FIG. 2 shown.
  • the inlet 3 live steam connection
  • the inlet line 7 is passed through a primary control valve 8, which controls the total flow through the turbine.
  • the primary control valve 8 is advantageously equipped with a pre-stroke, which can be realized for example by a parallel-connected Vorhub valve (not shown).
  • Quick-acting valve 4, primary control valve 8 and first nozzle group 21 are thus connected in series via the inlet line 7.
  • the series connection continues into the second 22, third 23 and fourth nozzle groups 24.
  • the second nozzle group 22 is connected to the first nozzle group 21 exclusively connected via a first secondary control valve 91.
  • the connection from the second nozzle group 22 to the third nozzle group 23 takes place in the same way via a second secondary control valve 92, the connection in the fourth nozzle group 24 according to a third secondary control valve 93rd
  • the shut-off elements 10 of the secondary control valves 91, 92, 93 are located on the same diameter D as the nozzle groups 21, 22, 23, 24. Thus, a particularly compact design of the inflow housing 1 is achieved.
  • the actuating axes 11 of the secondary control valves extend radially to the axis of rotation of the rotor, so the housing center. By these measures, the servomotors 12 of the actuators can be arranged outside the inflow housing 1.
  • FIGS. 3 to 5 Concrete design proposals of this construction are in the FIGS. 3 to 5 seen.
  • the secondary control valves 91, 92, 93 are to be actuated rotationally, so that the shut-off elements 10 are rotary valves.
  • the servomotors 12 are placed on the inflow housing 1, ie in the pressure-free region. It must be sealed only the housing leaving the actuator axis 11, which is easy to fall in axes of rotation.
  • the inflow housing 1 itself is therefore substantially annular and significantly more compact than in the prior art, since it accommodates only the nozzle groups 21, 22, 23 and the shut-off elements 10.
  • the inflow housing 1 is cast and divided into an upper housing half 1a and a lower housing half 1b, wherein the inlet conduit 7 is an integral part of the lower housing half 1b.
  • Quick-action valve 4 are arranged outside of the housing 1. It is therefore only a steam supply in the turbine housing with piston rings seal. The steam line can therefore be welded without flange connection.
  • FIG. 6 shows an inflow housing with two integrated inlet lines.
  • the internal control valves 10 need only low actuating forces and in particular no quick-closing device, since they are connected in series with the primary control valve 8 and the quick-closing valve 4.
  • the internal control valves without opening the turbine housing and be installed.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Control Of Turbines (AREA)
EP07011268A 2007-06-08 2007-06-08 Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile Withdrawn EP2000632A1 (de)

Priority Applications (7)

Application Number Priority Date Filing Date Title
EP07011268A EP2000632A1 (de) 2007-06-08 2007-06-08 Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile
CA002689224A CA2689224A1 (en) 2007-06-08 2008-04-25 Turbine having compact inflow housing thanks to internal control valves
BRPI0812409-4A2A BRPI0812409A2 (pt) 2007-06-08 2008-04-25 Turbina que tem alojamento de fluxo de entrada compacto graças a válvulas de controle interno
CN200880019281A CN101680308A (zh) 2007-06-08 2008-04-25 由于处于里面的调节阀而具有紧凑的进流壳体的涡轮机
EP08736568A EP2153029A1 (de) 2007-06-08 2008-04-25 Turbine mit kompaktem einströmgehäuse dank innen liegender regelventile
US12/602,891 US20100178153A1 (en) 2007-06-08 2008-04-25 Turbine Having Compact Inflow Housing Thanks to Internal Control Valves
PCT/EP2008/055045 WO2008148607A1 (de) 2007-06-08 2008-04-25 Turbine mit kompaktem einströmgehäuse dank innen liegender regelventile

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP07011268A EP2000632A1 (de) 2007-06-08 2007-06-08 Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile

Publications (1)

Publication Number Publication Date
EP2000632A1 true EP2000632A1 (de) 2008-12-10

Family

ID=38668641

Family Applications (2)

Application Number Title Priority Date Filing Date
EP07011268A Withdrawn EP2000632A1 (de) 2007-06-08 2007-06-08 Turbine mit kompaktem Einströmgehäuse dank innen liegender Regelventile
EP08736568A Withdrawn EP2153029A1 (de) 2007-06-08 2008-04-25 Turbine mit kompaktem einströmgehäuse dank innen liegender regelventile

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP08736568A Withdrawn EP2153029A1 (de) 2007-06-08 2008-04-25 Turbine mit kompaktem einströmgehäuse dank innen liegender regelventile

Country Status (6)

Country Link
US (1) US20100178153A1 (pt)
EP (2) EP2000632A1 (pt)
CN (1) CN101680308A (pt)
BR (1) BRPI0812409A2 (pt)
CA (1) CA2689224A1 (pt)
WO (1) WO2008148607A1 (pt)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010041704A1 (de) 2010-09-30 2012-04-05 Siemens Aktiengesellschaft Regelventil zur Regelung eines Volumenstromes

Families Citing this family (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102009010608B4 (de) * 2009-02-25 2011-06-16 Siemens Aktiengesellschaft Gestaltung der Einströmkammer mit radialer Zuströmung und Aufteilung des Frischdampfstroms in 2 Abschnitten
ITMI20091740A1 (it) * 2009-10-12 2011-04-13 Alstom Technology Ltd Turbina a vapore assiale alimentata radialmente ad alta temperatura
JP6448974B2 (ja) * 2014-10-03 2019-01-09 三菱日立パワーシステムズ株式会社 地熱タービンの蒸気室、これを備えた地熱タービン、および地熱タービンの蒸気供給方法
US10480417B2 (en) * 2016-07-14 2019-11-19 Hamilton Sundstrand Corporation Air turbine start system
JP6938139B2 (ja) * 2016-11-28 2021-09-22 三菱パワー株式会社 蒸気タービン装置
CN113027544A (zh) * 2021-05-13 2021-06-25 西安热工研究院有限公司 一种等喷嘴数多弧段高调阀-喷嘴组布置结构

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE676982C (de) * 1937-11-02 1939-06-16 Fried Krupp Germaniawerft Akt Hochdruckeinsitzventil fuer Dampfturbinen
DE679924C (de) * 1936-08-30 1939-08-17 Erich Koepke Schaltvorrichtung fuer Dampfturbinen
DE690631C (pt) * 1939-02-12 1940-05-03 Siemens Schuckertwerke Akt Ges
DE1915267A1 (de) * 1969-03-26 1970-10-15 Siemens Ag Turbine,insbesondere Dampfturbine,mit Duesengruppenregelung und Einstroemkasten
JPS57143106A (en) * 1981-02-26 1982-09-04 Toshiba Corp Geothermal turbine
JPS5990703A (ja) * 1982-11-15 1984-05-25 Fuji Electric Co Ltd 蒸気タ−ビンの調速段

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1473690A (en) * 1922-05-31 1923-11-13 Oscar H Wolner Serial-flow turbine
US2304993A (en) * 1941-06-20 1942-12-15 Westinghouse Electric & Mfg Co Steam turbine apparatus
US2376212A (en) * 1945-03-22 1945-05-15 Gen Electric Elastic fluid turbine arrangement
US4456032A (en) * 1982-01-18 1984-06-26 Elliott Turbomachinery Company, Inc. Fluid admission valve structure
DE4214775A1 (de) * 1992-05-04 1993-11-11 Abb Patent Gmbh Dampfturbine mit einem Drehschieber
US6398518B1 (en) * 2000-03-29 2002-06-04 Watson Cogeneration Company Method and apparatus for increasing the efficiency of a multi-stage compressor

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE679924C (de) * 1936-08-30 1939-08-17 Erich Koepke Schaltvorrichtung fuer Dampfturbinen
DE676982C (de) * 1937-11-02 1939-06-16 Fried Krupp Germaniawerft Akt Hochdruckeinsitzventil fuer Dampfturbinen
DE690631C (pt) * 1939-02-12 1940-05-03 Siemens Schuckertwerke Akt Ges
DE1915267A1 (de) * 1969-03-26 1970-10-15 Siemens Ag Turbine,insbesondere Dampfturbine,mit Duesengruppenregelung und Einstroemkasten
JPS57143106A (en) * 1981-02-26 1982-09-04 Toshiba Corp Geothermal turbine
JPS5990703A (ja) * 1982-11-15 1984-05-25 Fuji Electric Co Ltd 蒸気タ−ビンの調速段

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102010041704A1 (de) 2010-09-30 2012-04-05 Siemens Aktiengesellschaft Regelventil zur Regelung eines Volumenstromes

Also Published As

Publication number Publication date
CN101680308A (zh) 2010-03-24
US20100178153A1 (en) 2010-07-15
BRPI0812409A2 (pt) 2014-12-02
EP2153029A1 (de) 2010-02-17
WO2008148607A1 (de) 2008-12-11
CA2689224A1 (en) 2008-12-11

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