CA2625470A1 - Method for heating a steam turbine - Google Patents
Method for heating a steam turbine Download PDFInfo
- Publication number
- CA2625470A1 CA2625470A1 CA002625470A CA2625470A CA2625470A1 CA 2625470 A1 CA2625470 A1 CA 2625470A1 CA 002625470 A CA002625470 A CA 002625470A CA 2625470 A CA2625470 A CA 2625470A CA 2625470 A1 CA2625470 A1 CA 2625470A1
- Authority
- CA
- Canada
- Prior art keywords
- steam
- turbine section
- pressure turbine
- pressure
- 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.)
- Abandoned
Links
- 238000000034 method Methods 0.000 title claims abstract description 21
- 238000010438 heat treatment Methods 0.000 title abstract 2
- 230000000717 retained effect Effects 0.000 abstract 2
- 230000003190 augmentative effect Effects 0.000 abstract 1
- 230000000149 penetrating effect Effects 0.000 abstract 1
- 239000012530 fluid Substances 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 230000006735 deficit Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000012802 pre-warming Methods 0.000 description 1
- 229920006395 saturated elastomer Polymers 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
-
- 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
- F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
- F01D25/08—Cooling; Heating; Heat-insulation
- F01D25/10—Heating, e.g. warming-up before starting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K13/00—General layout or general methods of operation of complete plants
- F01K13/02—Controlling, e.g. stopping or starting
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01K—STEAM ENGINE PLANTS; STEAM ACCUMULATORS; ENGINE PLANTS NOT OTHERWISE PROVIDED FOR; ENGINES USING SPECIAL WORKING FLUIDS OR CYCLES
- F01K7/00—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
- F01K7/16—Steam engine plants characterised by the use of specific types of engine; Plants or engines characterised by their use of special steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being only of turbine type
- F01K7/165—Controlling means specially adapted therefor
-
- 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
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T50/00—Aeronautics or air transport
- Y02T50/60—Efficient propulsion technologies, e.g. for aircraft
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Control Of Turbines (AREA)
Abstract
The invention relates to a method for heating a steam turbine (8) comprising a medium-pressure turbine section (2) and/or a low-pressure turbine section (6), the discharge end of the medium-pressure turbine section (2) being provided with a catchment device (7). According to the inventive method, steam penetrating the medium-pressure turbine section (2) during a starting process is retained at an outlet (3) by means of the catchment device (7) in such a way that the pressure of the steam increases in the medium-pressure turbine section (2). The steam that is discharged from the medium-pressure turbine section (2) is retained, thus increasing the pressure and the temperature of the steam. Heat transfer from the steam to the thick-walled parts located on the medium-pressure turbine section (2) and the shaft of the medium-pressure turbine section is augmented, thus reducing the starting time of the steam turbine.
Description
Description Method for warming-up a steam turbine The invention relates to a method for warming-up a steam turbine which comprises an intermediate-pressure turbine section and/or low-pressure turbine section, wherein the intermediate-pressure turbine section on the outlet side has an accumulating device.
A steam turbine is also referred to as a turbomachine. Water turbines, steam and gas turbines, wind wheels, centrifugal pumps and centrifugal compressors and also propellers, are brought together under the collective term of turbomachines.
Common to all these machines is that they serve for the purpose of extracting energy from a fluid in order to drive another machine with it, or vice versa to supply energy to a fluid in order to increase its pressure.
A turbine section which on the inlet side is exposed to admission of superheated steam, which can have temperatures of up to 6200 C and a pressure of up to 300 bar, is understood by a high-pressure turbine section in this application. The aforementioned temperature and pressure specifications are only reference values. Turbine sections, which are designed for higher temperatures and for higher pressures, can also be referred to as high-pressure turbine sections. An intermediate-pressure turbine section is customarily exposed to admission of superheated steam which has a temperature of 600 C and a pressure of about 140 bar. A low-pressure turbine section is customarily exposed to admission of steam which issues from the intermediate-pressure turbine section. The steam which issues from the low-pressure turbine section is finally collected in a condenser and converted into water again. As a rule, the steam which issues from the high-PCT/EP2006/067254 - la -pressure turbine section is heated in a reheater and is fed into the intermediate-pressure turbine section.
In local power supply, it is of great importance that the steam turbines which are formed for driving the generators are able to be run up to the nominal speeds as quickly as possible. The nominal speeds are at 50 or 60 Hz. However, other nominal speeds are also known.
In the course of this, it is problematical that the shafts and other thick-walled components in steam turbines have to be prewarmed in a controlled manner before loading with full operating parameters in order to prevent impermissible stresses in the components.
The turbine shafts of intermediate-pressure turbine sections are customarily run up against a vacuum. That means, a comparatively low pressure prevails on the outlet side of the intermediate-pressure turbine section. For this reason, the saturation temperature and the density of the throughflowing steam in the intermediate-pressure turbine section is low.
Consequently, the heat yield to the shaft by means of the steam is low, which leads to a delay when prewarming an intermediate-pressure turbine section. Consequently, the starting time of the steam turbine is altogether extended. A starting time which is too long is considered to be an impairment.
It is the object of the invention, therefore, to disclose a method with which a steam turbine can be quickly warmed up.
The object is achieved by means of a method for warming-up a steam turbine which comprises an intermediate-pressure turbine section and/or low-pressure turbine section, wherein the intermediate-pressure turbine section on the outlet side has an accumulating device, wherein during a starting process steam which flows through the intermediate-pressure turbine section is accumulated at an outlet by means of the accumulating device in such a way that the pressure of the steam in the PCT/EP2006/067254 - 2a -intermediate-pressure turbine section is increased in such a way that the saturation temperature of the steam is increased.
The invention is based inter alia upon the aspect that by means of a controlled accumulating of the steam flow at the outlet of the intermediate-pressure turbine section during the starting process of the steam turbine, the pressure is increased. For example, by means of closing a flap the pressure at the outlet of the intermediate-pressure turbine section is increased. Increasing the pressure leads to the saturation temperature of the steam being increased. The heat transfer values are particularly high in the case of saturated steam. These heat transfer values are higher than in the case of convective warming-up. Therefore, the temperature of the steam in the case of saturation is decisive for the heat yield to the shaft. For example, the temperature without the accumulating according to the invention is at about 800 C and about 0.5 bar. By means of accumulating the outlet side steam of the intermediate-pressure turbine section at the accumulating device, for example to 4 bar, a saturation temperature of the steam of 144 C ensues as a result of this.
The heat transfer to the shaft which is arranged in the steam turbine is consequently increased which results in the shaft being warmed-up comparatively quickly.
Furthermore, due to the higher steam density, a subsequent convective superheating of an intermediate-pressure turbine section shaft is also accelerated.
By means of this measure according to the invention, with the heat being able to be introduced quicker into an intermediate-pressure turbine section shaft, the starting process of a steam turbine can be shortened during a cold start by up to an hour.
In an advantageous development, the accumulating device is arranged in the overflow line. The overflow line in this case is a line which fluidically connects the outlet of the intermediate-pressure turbine section to the inlet of a low-pressure turbine section.
PCT/EP2006/067254 - 3a -By means of this measure, it is comparatively simple to increase the pressure on the outlet side of an intermediate-pressure turbine section.
In a further advantageous development, the accumulating device is formed with controllability.
Consequently, the warming-up process of the steam turbine can be controlled. For example, a steam mass flow, which flows discontinuously into the intermediate-pressure turbine section, could be varied by means of the controllable accumulating device in such a way that the heat yield to the thick-walled components of the intermediate-pressure turbine section occurs at the same time.
The temperature, the pressure and/or the steam mass flow could be used as input values for controlling the accumulating device.
In a further advantageous development, the accumulating device is formed as a pivotable flap. The forming of a pivotable flap is a comparatively inexpensive measure with which the desired effect, specifically the accumulating of steam, is achieved.
In a further advantageous development, the steam on the outlet side of the intermediate-pressure turbine section is accumulated to pressure values of between 3 and 5 bar, and temperature values of between 1300 C and 150 C.
It has been shown that with these pressure and temperature values the heat yield of the steam to the intermediate-pressure turbine section shaft is particularly high.
Exemplary embodiments of the invention are subsequently described in more detail with reference to the drawings. In this case, components which are provided with the same designations have the same principle of operation.
In this case, in the drawing:
Figure 1 shows a schematic representation of an intermediate-pressure turbine section and a low-pressure turbine section.
In Figure 1, a schematic representation of a steam turbine 8 is shown. A steam turbine can comprise a high-pressure turbine section, intermediate-pressure turbine section and/or a low-pressure turbine section. The steam turbine which is shown in the figure comprises an intermediate-pressure and a low-pressure turbine section. As a rule, live steam flows into a high-pressure turbine section, which is not shown in the figure, and is expanded there, and cooled down to a lower temperature. This expanded and cooled-down steam is heated to a higher temperature in a reheater, which is not shown in more detail in Figure 1, and then fed into an intermediate-pressure turbine section 2 via a line 1. The steam which flows into the intermediate-pressure turbine section 2 expands, wherein the pressure and the temperature of the steam drop in the process.
On the outlet side of the intermediate-pressure turbine section 2, the expanded steam flows from an outlet 3 via an overflow line 4 into an inlet 5 of a low-pressure turbine section 6.
The intermediate-pressure turbine section 2 and low-pressure turbine section 6, which are shown in Figure 1, are to be seen as part of a steam turbine. For the sake of clarity, the high-pressure turbine section, the reheater, the condenser and various units, such as a pump, are not shown in more detail.
An accumulating device 7 is arranged in the overflow line 4.
The accumulating device 7 can be formed with controllability and/or as a pivotable flap. During a starting process, the accumulating device 7 is operated in such a way that the steam which issues at the outlet 3 is accumulated in front of the control flap, as a result of which the pressure of the steam is increased. Consequently, the saturation temperature of the steam is increased, which leads to an increase of the temperature transfer values of the steam to the intermediate-pressure turbine shaft of the intermediate-pressure turbine section 2. The intermediate-pressure turbine shaft is not shown in more detail.
It has been shown that the steam on the outlet side should be accumulated to values of between 3 and 5 bar, and 1300 C and 1500 C, in order to maintain good heat transfer values.
The starting process of a steam turbine is shortened by about one hour as a result.
A steam turbine is also referred to as a turbomachine. Water turbines, steam and gas turbines, wind wheels, centrifugal pumps and centrifugal compressors and also propellers, are brought together under the collective term of turbomachines.
Common to all these machines is that they serve for the purpose of extracting energy from a fluid in order to drive another machine with it, or vice versa to supply energy to a fluid in order to increase its pressure.
A turbine section which on the inlet side is exposed to admission of superheated steam, which can have temperatures of up to 6200 C and a pressure of up to 300 bar, is understood by a high-pressure turbine section in this application. The aforementioned temperature and pressure specifications are only reference values. Turbine sections, which are designed for higher temperatures and for higher pressures, can also be referred to as high-pressure turbine sections. An intermediate-pressure turbine section is customarily exposed to admission of superheated steam which has a temperature of 600 C and a pressure of about 140 bar. A low-pressure turbine section is customarily exposed to admission of steam which issues from the intermediate-pressure turbine section. The steam which issues from the low-pressure turbine section is finally collected in a condenser and converted into water again. As a rule, the steam which issues from the high-PCT/EP2006/067254 - la -pressure turbine section is heated in a reheater and is fed into the intermediate-pressure turbine section.
In local power supply, it is of great importance that the steam turbines which are formed for driving the generators are able to be run up to the nominal speeds as quickly as possible. The nominal speeds are at 50 or 60 Hz. However, other nominal speeds are also known.
In the course of this, it is problematical that the shafts and other thick-walled components in steam turbines have to be prewarmed in a controlled manner before loading with full operating parameters in order to prevent impermissible stresses in the components.
The turbine shafts of intermediate-pressure turbine sections are customarily run up against a vacuum. That means, a comparatively low pressure prevails on the outlet side of the intermediate-pressure turbine section. For this reason, the saturation temperature and the density of the throughflowing steam in the intermediate-pressure turbine section is low.
Consequently, the heat yield to the shaft by means of the steam is low, which leads to a delay when prewarming an intermediate-pressure turbine section. Consequently, the starting time of the steam turbine is altogether extended. A starting time which is too long is considered to be an impairment.
It is the object of the invention, therefore, to disclose a method with which a steam turbine can be quickly warmed up.
The object is achieved by means of a method for warming-up a steam turbine which comprises an intermediate-pressure turbine section and/or low-pressure turbine section, wherein the intermediate-pressure turbine section on the outlet side has an accumulating device, wherein during a starting process steam which flows through the intermediate-pressure turbine section is accumulated at an outlet by means of the accumulating device in such a way that the pressure of the steam in the PCT/EP2006/067254 - 2a -intermediate-pressure turbine section is increased in such a way that the saturation temperature of the steam is increased.
The invention is based inter alia upon the aspect that by means of a controlled accumulating of the steam flow at the outlet of the intermediate-pressure turbine section during the starting process of the steam turbine, the pressure is increased. For example, by means of closing a flap the pressure at the outlet of the intermediate-pressure turbine section is increased. Increasing the pressure leads to the saturation temperature of the steam being increased. The heat transfer values are particularly high in the case of saturated steam. These heat transfer values are higher than in the case of convective warming-up. Therefore, the temperature of the steam in the case of saturation is decisive for the heat yield to the shaft. For example, the temperature without the accumulating according to the invention is at about 800 C and about 0.5 bar. By means of accumulating the outlet side steam of the intermediate-pressure turbine section at the accumulating device, for example to 4 bar, a saturation temperature of the steam of 144 C ensues as a result of this.
The heat transfer to the shaft which is arranged in the steam turbine is consequently increased which results in the shaft being warmed-up comparatively quickly.
Furthermore, due to the higher steam density, a subsequent convective superheating of an intermediate-pressure turbine section shaft is also accelerated.
By means of this measure according to the invention, with the heat being able to be introduced quicker into an intermediate-pressure turbine section shaft, the starting process of a steam turbine can be shortened during a cold start by up to an hour.
In an advantageous development, the accumulating device is arranged in the overflow line. The overflow line in this case is a line which fluidically connects the outlet of the intermediate-pressure turbine section to the inlet of a low-pressure turbine section.
PCT/EP2006/067254 - 3a -By means of this measure, it is comparatively simple to increase the pressure on the outlet side of an intermediate-pressure turbine section.
In a further advantageous development, the accumulating device is formed with controllability.
Consequently, the warming-up process of the steam turbine can be controlled. For example, a steam mass flow, which flows discontinuously into the intermediate-pressure turbine section, could be varied by means of the controllable accumulating device in such a way that the heat yield to the thick-walled components of the intermediate-pressure turbine section occurs at the same time.
The temperature, the pressure and/or the steam mass flow could be used as input values for controlling the accumulating device.
In a further advantageous development, the accumulating device is formed as a pivotable flap. The forming of a pivotable flap is a comparatively inexpensive measure with which the desired effect, specifically the accumulating of steam, is achieved.
In a further advantageous development, the steam on the outlet side of the intermediate-pressure turbine section is accumulated to pressure values of between 3 and 5 bar, and temperature values of between 1300 C and 150 C.
It has been shown that with these pressure and temperature values the heat yield of the steam to the intermediate-pressure turbine section shaft is particularly high.
Exemplary embodiments of the invention are subsequently described in more detail with reference to the drawings. In this case, components which are provided with the same designations have the same principle of operation.
In this case, in the drawing:
Figure 1 shows a schematic representation of an intermediate-pressure turbine section and a low-pressure turbine section.
In Figure 1, a schematic representation of a steam turbine 8 is shown. A steam turbine can comprise a high-pressure turbine section, intermediate-pressure turbine section and/or a low-pressure turbine section. The steam turbine which is shown in the figure comprises an intermediate-pressure and a low-pressure turbine section. As a rule, live steam flows into a high-pressure turbine section, which is not shown in the figure, and is expanded there, and cooled down to a lower temperature. This expanded and cooled-down steam is heated to a higher temperature in a reheater, which is not shown in more detail in Figure 1, and then fed into an intermediate-pressure turbine section 2 via a line 1. The steam which flows into the intermediate-pressure turbine section 2 expands, wherein the pressure and the temperature of the steam drop in the process.
On the outlet side of the intermediate-pressure turbine section 2, the expanded steam flows from an outlet 3 via an overflow line 4 into an inlet 5 of a low-pressure turbine section 6.
The intermediate-pressure turbine section 2 and low-pressure turbine section 6, which are shown in Figure 1, are to be seen as part of a steam turbine. For the sake of clarity, the high-pressure turbine section, the reheater, the condenser and various units, such as a pump, are not shown in more detail.
An accumulating device 7 is arranged in the overflow line 4.
The accumulating device 7 can be formed with controllability and/or as a pivotable flap. During a starting process, the accumulating device 7 is operated in such a way that the steam which issues at the outlet 3 is accumulated in front of the control flap, as a result of which the pressure of the steam is increased. Consequently, the saturation temperature of the steam is increased, which leads to an increase of the temperature transfer values of the steam to the intermediate-pressure turbine shaft of the intermediate-pressure turbine section 2. The intermediate-pressure turbine shaft is not shown in more detail.
It has been shown that the steam on the outlet side should be accumulated to values of between 3 and 5 bar, and 1300 C and 1500 C, in order to maintain good heat transfer values.
The starting process of a steam turbine is shortened by about one hour as a result.
Claims (8)
1. A method for warming-up a steam turbine (8), which comprises an intermediate-pressure turbine section (2), wherein the intermediate-pressure turbine section (2) on the outlet side has an accumulating device (7), characterized in that during a starting process, steam which flows through the intermediate-pressure turbine section (2) is accumulated at an outlet (3) by means of the accumulating device in such a way that the pressure of the steam in the intermediate-pressure turbine section (2) is increased in such a way that the saturation temperature of the steam is increased.
2. The method as claimed in claim 1, in which the accumulating device (7) is arranged in the overflow line (4).
3. The method as claimed in claim 1 or 2, in which the accumulating device (7) is formed with controllability.
4. The method as claimed in claim 1, 2 or 3, in which the accumulating device (7) is formed as a pivotable flap.
5. The method as claimed in one of claims 1 to 3, in which the steam is accumulated on the outlet side to values of between 3 and 5 bar, and 130° C and 150° C.
6. A steam turbine plant, which comprises an intermediate-pressure turbine section (2), characterized by an accumulating device (7), which is arranged on the outlet side on the intermediate-pressure turbine section (2).
7. The steam turbine plant as claimed in claim 6, wherein the accumulating device (7) is formed as a pivotable flap.
8. The steam turbine plant as claimed in claim 6 or 7, wherein the accumulating device (7) is arranged in an overflow line (4).
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| EP05022279.3 | 2005-10-12 | ||
| EP05022279A EP1775429A1 (en) | 2005-10-12 | 2005-10-12 | Method for warming-up a steam turbine |
| PCT/EP2006/067254 WO2007042523A2 (en) | 2005-10-12 | 2006-10-11 | Method for heating a steam turbine |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CA2625470A1 true CA2625470A1 (en) | 2007-04-19 |
Family
ID=36282973
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA002625470A Abandoned CA2625470A1 (en) | 2005-10-12 | 2006-10-11 | Method for heating a steam turbine |
Country Status (10)
| Country | Link |
|---|---|
| US (1) | US20090288415A1 (en) |
| EP (2) | EP1775429A1 (en) |
| JP (1) | JP2009511812A (en) |
| KR (1) | KR20080054439A (en) |
| CN (1) | CN101351621B (en) |
| BR (1) | BRPI0617303A2 (en) |
| CA (1) | CA2625470A1 (en) |
| RU (1) | RU2392452C2 (en) |
| TW (1) | TW200734528A (en) |
| WO (1) | WO2007042523A2 (en) |
Families Citing this family (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| ES2743247T3 (en) * | 2010-01-12 | 2020-02-18 | Siemens Ag | Turbine with heating system, and corresponding solar power plant and operating procedure |
| DE102013205979A1 (en) * | 2013-04-04 | 2014-10-09 | Siemens Aktiengesellschaft | Optimization of cold starts in thermal power plants, in particular in steam turbine or gas and steam turbine power plants (combined cycle power plants) |
| EP3249183A1 (en) * | 2016-05-23 | 2017-11-29 | Siemens Aktiengesellschaft | Method for heating a valve |
| US10577962B2 (en) | 2016-09-07 | 2020-03-03 | General Electric Company | Turbomachine temperature control system |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US1499697A (en) * | 1919-11-01 | 1924-07-01 | Vaporackumulator Ab | Steam-accumulator apparatus for steam plants |
| US1923251A (en) * | 1931-05-22 | 1933-08-22 | Bauer Gustav | Gas or steam turbine casing |
| US2874711A (en) * | 1953-02-04 | 1959-02-24 | Rateau Soc | Control of high-power turbines |
| DE1228623B (en) * | 1963-07-23 | 1966-11-17 | Sulzer Ag | Steam power plant with forced steam generator and reheater |
| US3375665A (en) * | 1964-06-24 | 1968-04-02 | Georg Gyarmathy | Method and arrangement for utilizing steam power in steam power plants |
| DE2029830C3 (en) * | 1970-06-18 | 1974-04-11 | Steag Ag, 4300 Essen | Procedure for heating the main steam line and the reheater line of steam turbine systems |
| CH635401A5 (en) * | 1978-08-31 | 1983-03-31 | Bbc Brown Boveri & Cie | BLOCK STEAM DEVICE AND USE THEREOF. |
| DE3137379C2 (en) * | 1980-12-23 | 1985-11-14 | Saarbergwerke AG, 6600 Saarbrücken | Process for supplying district heating networks with heat and a thermal power plant |
| JPS5810104A (en) * | 1981-07-10 | 1983-01-20 | Hitachi Ltd | Turbine plant and control thereof |
| DE3408937A1 (en) * | 1984-01-31 | 1985-08-08 | BBC Aktiengesellschaft Brown, Boveri & Cie., Baden, Aargau | COMBINED GAS / VAPOR POWER PLANT |
| FR2560636B1 (en) * | 1984-03-01 | 1988-07-08 | Alsthom Atlantique | TURBINE BODY FOR URBAN HEATING |
| JPS61237802A (en) * | 1985-04-12 | 1986-10-23 | Hitachi Ltd | Warming-up method for steam turbine |
| JP2633720B2 (en) * | 1990-10-12 | 1997-07-23 | 株式会社東芝 | Pre-warming method for steam turbine |
| DE19506787B4 (en) * | 1995-02-27 | 2004-05-06 | Alstom | Process for operating a steam turbine |
| EP0853214B1 (en) * | 1997-01-10 | 2004-03-10 | Framatome ANP GmbH | Method and apparatus for superheating steam |
| DE19808596A1 (en) * | 1998-02-28 | 1999-09-02 | Babcock Kraftwerksrohrleitungs | Preheating and drainage method for high pressure steam line of steam power station |
| EP1191192A1 (en) * | 2000-09-26 | 2002-03-27 | Siemens Aktiengesellschaft | Method and apparatus for preheating and dewatering of turbine stage steam conduits |
| JP2002341947A (en) * | 2001-05-21 | 2002-11-29 | Mitsubishi Heavy Ind Ltd | Pressure flow rate controller |
| JP4363955B2 (en) * | 2003-10-27 | 2009-11-11 | 株式会社東芝 | Butterfly valve type steam valve and steam turbine plant using the same |
| JP2005226500A (en) * | 2004-02-10 | 2005-08-25 | Chugoku Electric Power Co Inc:The | Method for stopping power plant |
| EP1775431A1 (en) * | 2005-10-12 | 2007-04-18 | Siemens Aktiengesellschaft | Method for warming-up a steam turbine |
-
2005
- 2005-10-12 EP EP05022279A patent/EP1775429A1/en not_active Withdrawn
-
2006
- 2006-10-11 US US12/083,257 patent/US20090288415A1/en not_active Abandoned
- 2006-10-11 BR BRPI0617303-9A patent/BRPI0617303A2/en not_active IP Right Cessation
- 2006-10-11 RU RU2008118368/06A patent/RU2392452C2/en not_active IP Right Cessation
- 2006-10-11 WO PCT/EP2006/067254 patent/WO2007042523A2/en active Application Filing
- 2006-10-11 CN CN2006800374624A patent/CN101351621B/en not_active Expired - Fee Related
- 2006-10-11 JP JP2008535015A patent/JP2009511812A/en active Pending
- 2006-10-11 EP EP06794008A patent/EP1934433A2/en not_active Withdrawn
- 2006-10-11 CA CA002625470A patent/CA2625470A1/en not_active Abandoned
- 2006-10-11 KR KR1020087011077A patent/KR20080054439A/en active Search and Examination
- 2006-10-12 TW TW095137536A patent/TW200734528A/en unknown
Also Published As
| Publication number | Publication date |
|---|---|
| KR20080054439A (en) | 2008-06-17 |
| EP1934433A2 (en) | 2008-06-25 |
| RU2392452C2 (en) | 2010-06-20 |
| US20090288415A1 (en) | 2009-11-26 |
| JP2009511812A (en) | 2009-03-19 |
| BRPI0617303A2 (en) | 2011-07-19 |
| CN101351621B (en) | 2012-12-05 |
| EP1775429A1 (en) | 2007-04-18 |
| WO2007042523A2 (en) | 2007-04-19 |
| CN101351621A (en) | 2009-01-21 |
| TW200734528A (en) | 2007-09-16 |
| WO2007042523A3 (en) | 2007-09-13 |
| RU2008118368A (en) | 2009-11-20 |
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