WO2008148607A1 - Turbine having compact inflow housing thanks to internal control valves - Google Patents
Turbine having compact inflow housing thanks to internal control valves Download PDFInfo
- Publication number
- WO2008148607A1 WO2008148607A1 PCT/EP2008/055045 EP2008055045W WO2008148607A1 WO 2008148607 A1 WO2008148607 A1 WO 2008148607A1 EP 2008055045 W EP2008055045 W EP 2008055045W WO 2008148607 A1 WO2008148607 A1 WO 2008148607A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- control valve
- turbine
- nozzle group
- inlet
- nozzle
- Prior art date
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
- 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 with an inflow housing which has an inlet closable by a quick-acting valve for an incoming working fluid, a plurality of control valves and at least two nozzle groups, wherein the flow of the working medium from the inlet into the nozzle groups is 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.
- FIG. 2a of DE 1 915 267 A1 The inflow housing of a known steam turbine is shown in FIG. 2a of DE 1 915 267 A1.
- this housing model which is still produced today, are 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 are connected in parallel
- a circuit diagram of this arrangement is shown in the enclosed figure 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.
- This task is initially solved by dividing the control valves functionally into a primary Control valve and at least one secondary control valve. Further, 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 allows pipeline routes in the
- 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 always exposed to working medium when the primary control valve and the quick-acting valve are open. To increase performance, the downstream nozzle groups are switched successively via the secondary control valves.
- a preferred development of the invention provides, at least three series-connected nozzle groups in
- 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 radially to
- Rotary axis of the rotor can be arranged.
- 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.
- Advantage of this design is that the management of the
- the present invention is preferably applied in the field of axial-flow steam turbines.
- the present invention will now be described with reference to a
- Fig. 1 conventional valve circuit (prior art);
- Fig. 2 Valve circuit according to the invention
- Fig. 3 inflow housing, partially exploded, in perspective
- Fig. 4 inflow housing, partially exploded, in
- Fig. 5 section through inflow housing
- Fig. 6 Einströmgepatuse with two inlets.
- FIG. 1 shows schematically 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.
- Quick-closing valve 4 the flow fanned in 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 shown in FIG.
- 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
- 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.
- Actuating axes 11 of the secondary control valves extend radially to the axis of rotation of the rotor, so the housing center.
- the servomotors 12 of the actuators can be arranged outside the inflow housing 1.
- 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 half of the housing Ia and a lower half of the housing Ib, the inlet line 7 being an integral part of the lower half of the housing Ib.
- Primary control valve 8 and quick-acting valve 4 are arranged outside of the housing 1. It is therefore only a DampfZu Insertion 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 7.
- 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.
Abstract
Description
Claims
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
BRPI0812409-4A2A BRPI0812409A2 (en) | 2007-06-08 | 2008-04-25 | TURBINE WITH COMPACT INPUT FLOW ACCOMMODATION THANKS TO INTERNAL CONTROL VALVES |
CN200880019281A CN101680308A (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
EP08736568A EP2153029A1 (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
CA002689224A CA2689224A1 (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
US12/602,891 US20100178153A1 (en) | 2007-06-08 | 2008-04-25 | Turbine Having Compact Inflow Housing Thanks to Internal Control Valves |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP07011268.5 | 2007-06-08 | ||
EP07011268A EP2000632A1 (en) | 2007-06-08 | 2007-06-08 | Turbine with a compact inflow casing due to inner control valves |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2008148607A1 true WO2008148607A1 (en) | 2008-12-11 |
Family
ID=38668641
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/EP2008/055045 WO2008148607A1 (en) | 2007-06-08 | 2008-04-25 | Turbine having compact inflow housing thanks to internal control valves |
Country Status (6)
Country | Link |
---|---|
US (1) | US20100178153A1 (en) |
EP (2) | EP2000632A1 (en) |
CN (1) | CN101680308A (en) |
BR (1) | BRPI0812409A2 (en) |
CA (1) | CA2689224A1 (en) |
WO (1) | WO2008148607A1 (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009010608A1 (en) * | 2009-02-25 | 2010-08-26 | Siemens Aktiengesellschaft | Inflow housing for turbine i.e. steam turbine, has inflow channels including outlet areas such that two portions of working medium are delivered to interior volume of housing through outlet areas |
US8702376B2 (en) | 2009-10-12 | 2014-04-22 | Alstom Technology Ltd. | High temperature radially fed axial steam turbine |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102010041704A1 (en) | 2010-09-30 | 2012-04-05 | Siemens Aktiengesellschaft | Regulating valve for controlling flow volume inside pipeline, is arranged in pipeline rotatable around rotational axis and corresponding to its rotational position decontrols flow cross-section inside pipeline |
JP6448974B2 (en) * | 2014-10-03 | 2019-01-09 | 三菱日立パワーシステムズ株式会社 | Steam chamber of geothermal turbine, geothermal turbine provided with the same, and steam supply method of geothermal turbine |
US10480417B2 (en) * | 2016-07-14 | 2019-11-19 | Hamilton Sundstrand Corporation | Air turbine start system |
JP6938139B2 (en) * | 2016-11-28 | 2021-09-22 | 三菱パワー株式会社 | Steam turbine equipment |
CN113027544A (en) * | 2021-05-13 | 2021-06-25 | 西安热工研究院有限公司 | Equal-nozzle-number multi-arc-section high-regulation valve-nozzle group arrangement structure |
Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE676982C (en) * | 1937-11-02 | 1939-06-16 | Fried Krupp Germaniawerft Akt | High pressure single seat valve for steam turbines |
DE679924C (en) * | 1936-08-30 | 1939-08-17 | Erich Koepke | Switching device for steam turbines |
DE690631C (en) * | 1939-02-12 | 1940-05-03 | Siemens Schuckertwerke Akt Ges | |
DE1915267A1 (en) * | 1969-03-26 | 1970-10-15 | Siemens Ag | Turbine, especially steam turbine, with nozzle group control and single-flow box |
JPS57143106A (en) * | 1981-02-26 | 1982-09-04 | Toshiba Corp | Geothermal turbine |
JPS5990703A (en) * | 1982-11-15 | 1984-05-25 | Fuji Electric Co Ltd | Stage for adjusting speed of steam turbine |
Family Cites Families (6)
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 (en) * | 1992-05-04 | 1993-11-11 | Abb Patent Gmbh | Steam turbine with a rotary valve |
US6398518B1 (en) * | 2000-03-29 | 2002-06-04 | Watson Cogeneration Company | Method and apparatus for increasing the efficiency of a multi-stage compressor |
-
2007
- 2007-06-08 EP EP07011268A patent/EP2000632A1/en not_active Withdrawn
-
2008
- 2008-04-25 CA CA002689224A patent/CA2689224A1/en not_active Abandoned
- 2008-04-25 WO PCT/EP2008/055045 patent/WO2008148607A1/en active Application Filing
- 2008-04-25 EP EP08736568A patent/EP2153029A1/en not_active Withdrawn
- 2008-04-25 US US12/602,891 patent/US20100178153A1/en not_active Abandoned
- 2008-04-25 CN CN200880019281A patent/CN101680308A/en active Pending
- 2008-04-25 BR BRPI0812409-4A2A patent/BRPI0812409A2/en not_active Application Discontinuation
Patent Citations (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE679924C (en) * | 1936-08-30 | 1939-08-17 | Erich Koepke | Switching device for steam turbines |
DE676982C (en) * | 1937-11-02 | 1939-06-16 | Fried Krupp Germaniawerft Akt | High pressure single seat valve for steam turbines |
DE690631C (en) * | 1939-02-12 | 1940-05-03 | Siemens Schuckertwerke Akt Ges | |
DE1915267A1 (en) * | 1969-03-26 | 1970-10-15 | Siemens Ag | Turbine, especially steam turbine, with nozzle group control and single-flow box |
JPS57143106A (en) * | 1981-02-26 | 1982-09-04 | Toshiba Corp | Geothermal turbine |
JPS5990703A (en) * | 1982-11-15 | 1984-05-25 | Fuji Electric Co Ltd | Stage for adjusting speed of steam turbine |
Cited By (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102009010608A1 (en) * | 2009-02-25 | 2010-08-26 | Siemens Aktiengesellschaft | Inflow housing for turbine i.e. steam turbine, has inflow channels including outlet areas such that two portions of working medium are delivered to interior volume of housing through outlet areas |
DE102009010608B4 (en) * | 2009-02-25 | 2011-06-16 | Siemens Aktiengesellschaft | Design of the inflow chamber with radial inflow and distribution of live steam flow in 2 sections |
US8702376B2 (en) | 2009-10-12 | 2014-04-22 | Alstom Technology Ltd. | High temperature radially fed axial steam turbine |
Also Published As
Publication number | Publication date |
---|---|
CN101680308A (en) | 2010-03-24 |
EP2153029A1 (en) | 2010-02-17 |
US20100178153A1 (en) | 2010-07-15 |
EP2000632A1 (en) | 2008-12-10 |
CA2689224A1 (en) | 2008-12-11 |
BRPI0812409A2 (en) | 2014-12-02 |
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