EP1965043A1 - Cycle de turbine a vapeur - Google Patents

Cycle de turbine a vapeur Download PDF

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Publication number
EP1965043A1
EP1965043A1 EP06843008A EP06843008A EP1965043A1 EP 1965043 A1 EP1965043 A1 EP 1965043A1 EP 06843008 A EP06843008 A EP 06843008A EP 06843008 A EP06843008 A EP 06843008A EP 1965043 A1 EP1965043 A1 EP 1965043A1
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EP
European Patent Office
Prior art keywords
feed
steam
cycle
turbine
water
Prior art date
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Granted
Application number
EP06843008A
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German (de)
English (en)
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EP1965043B1 (fr
EP1965043A4 (fr
Inventor
Koichi Goto
Nobuo Okita
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Toshiba Corp
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Toshiba Corp
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Publication of EP1965043A4 publication Critical patent/EP1965043A4/fr
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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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating
    • F01K7/34—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steam systems, cycles or processes; Control means specially adapted for such systems, cycles or processes; Use of withdrawn or exhaust steam for feed-water heating the engines being of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/40—Use of two or more feed-water heaters in series
    • 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
    • F01K17/00—Using steam or condensate extracted or exhausted from steam engine plant
    • 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
    • F01K7/22—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 the turbines having inter-stage steam heating
    • 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
    • F01K7/34—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 of extraction or non-condensing type; Use of steam for feed-water heating
    • 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
    • F01K7/34—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 of extraction or non-condensing type; Use of steam for feed-water heating
    • F01K7/38—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 of extraction or non-condensing type; Use of steam for feed-water heating the engines being of turbine type

Definitions

  • the present invention relates to a steam turbine cycle having an improved cycle thermal efficiency.
  • the superheated steam may be an ultra supercritical pressure fluid.
  • the main steam 16 which has flown into a high pressure turbine 1, expands and flows therethrough, while a pressure and a temperature thereof are lowered.
  • the steam expands and flows through the intermediate pressure turbine 2, while a pressure and a temperature thereof are lowered. Then, the steam flows into a low pressure turbine 3.
  • the steam expands and flows through the low pressure turbine 3, while a pressure and a temperature thereof are lowered. A part of the steam often becomes a saturated steam as a liquid water.
  • the saturated steam is cooled by a condenser 10 by using sea water or atmospheric air 23, so that the saturated steam becomes a condensed water 25.
  • the condensed water 25 is sent to a feed heater 6 by a condensing pump 11 to become a boiler feed water 14.
  • the intermediate pressure turbine 2 and the low pressure turbine 3 constitute a reheating turbine 24.
  • Fig. 1 eight feed heaters 6 are illustrated.
  • the boiler feed water 14 is heated by a bleed steam 20 bled from bleeding positions 31 in channels of the intermediate pressure turbine 2 and the low pressure turbine 3.
  • a bleed steam of a higher pressure is flown into the feed heater 6 of a higher pressure.
  • the low pressure turbine 3 is illustrated as a double flow pressure turbine, and a steam is bled from only one of the low pressure turbine 3. However, a steam is actually bled from both the low pressure turbines 3 and merged. The merged steam flows into the feed heater 6. It is possible to bleed a steam from one of the low pressure turbines 3, depending on the feed heater 6.
  • the feed heater 6 is classified into a feed heater of a surface type and a feed heater of a mixing type.
  • a feed heater of a surface type the bleed steam 20 is condensed by exchanging heats with a feed water via a heat transmission surface to become a drain water 15.
  • the drain water 15 sequentially flows from the feed heater 6 of a higher pressure to the feed heater 6 of a lower pressure.
  • the drain water 15 in the feed heater 6 of the lowest pressure flows into the condenser 10.
  • the drain water 15 may be merged into a feed water by a drain water pump 13.
  • a bleed steam is directly mixed with a feed water to heat the same.
  • a deaerator 9 for deaerating oxygen or the like which is dissolved in a feed water is included in the feed heater of a mixing type.
  • a feed pump 12 In order to send a feed water to a feed heater 6 of a higher pressure, a feed pump 12 is disposed directly downstream of the feed heater of a mixing type.
  • a bleed steam to the feed heater of a mixed type is an intermediate-pressure turbine exhaust bleed steam 32, another steam is possible.
  • the deaerator 9 may be omitted. Even when the deaerator 9 is omitted, the feed pump 12 is disposed on a suitable position between the plurality of feed heaters 6. A feed water sequentially heated in all of the feed heaters 6 flows into the boiler 4.
  • the high pressure turbine 1, the intermediate pressure turbine 2, and the low pressure turbine 3 are connected to each other by a single rotation shaft 19, and are connected to a generator 18.
  • a steam expands in the high pressure turbine 1, the intermediate pressure turbine 2, and the high pressure turbine 3, so that enthalpy of the steam is converted into a shaft power, whereby electric power is generated by the generator 18. It is possible not to connect the respective turbines to the single generator 18 by connecting the turbines by the single rotation shaft 19.
  • Fig. 1 illustrates the low pressure turbine 3 as a double flow pressure turbine in which a flow-in steam is divided into two and the divided steams flow into the two low pressure turbines 3.
  • the flow-in steam may be divided into four, or may not be divided.
  • the intermediate pressure turbine 2 is illustrated as a single flow pressure turbine, the intermediate pressure turbine 2 may be a double flow pressure turbine.
  • Fig. 1 shows that the intermediate pressure turbine 2 and the low pressure turbine 3 are separated turbines, a single reheating turbine 24 is possible.
  • Both of a regenerative cycle using the bleed steam 20, and a reheating cycle in which the high-pressure exhaust steam 21 heated by the reheater 5 flows into the reheating turbine 24, are modified Rankine cycles, and improve a thermal efficiency from a simple Rankine cycle.
  • a thermal efficiency is substantially equal to a value obtained by dividing an amount of generated power by an amount of boiler heat input.
  • a cycle thermal efficiency varies depending on a temperature and a flowrate of each bleed steam 20.
  • a temperature of steam has been recently more and more increased, whereby a cycle thermal efficiency has been improved.
  • Non-Patent Document "Steam Turbine Performance and Economics" written by Bartlett
  • the object of the present invention is to provide a steam turbine cycle of an improved cycle thermal efficiency.
  • the invention according to claim 1 is a steam turbine cycle comprising a high pressure turbine, a reheating turbine, a boiler, feed heaters for heating a feed water to the boiler by a bleed steam from the high pressure turbine and the reheating turbine, a feed pump, and a condenser, the steam turbine cycle being a single-stage reheating cycle where a working fluid is water and using a Rankine cycle which is a regenerative cycle, wherein a steam temperature at an outlet of the boiler is 590°C or more, and a temperature increase ratio between: a feed-water temperature increase in a first feed heater corresponding to a bleed steam from an exhaust steam of the high pressure turbine; and an average of feed-water temperature increases in second feed heaters where a pressure of the feed water is lower than that of the first feed heater; falls within 1.9 - 3.5.
  • the invention according to claim 2 is a steam turbine cycle comprising a high pressure turbine, a reheating turbine, a boiler, feed heaters for heating a feed water to the boiler by a bleed steam from the high pressure turbine and the reheating turbine, a feed pump, and a condenser, the steam turbine cycle being a single-stage reheating cycle where a working fluid is water and using a Rankine cycle which is a regenerative cycle, wherein a steam temperature at an outlet of the boiler is 590°C or more, and a specific enthalpy increase ratio between: a specific enthalpy increase in a feed water in a first feed heater corresponding to a bleed steam from an exhaust steam of the high pressure turbine; and an average of specific enthalpy increases in feed waters in second feed heaters where a pressure of the feed water is lower than that of the first feed heater; falls within 1.9 - 3.5.
  • the invention according to claim 3 is a steam turbine cycle comprising a high pressure turbine, a reheating turbine, a boiler, feed heaters for heating a feed water to the boiler by a bleed steam from the high pressure turbine and the reheating turbine, a feed pump, and a condenser, the steam turbine cycle being a single-stage reheating cycle where a working fluid is water and using a Rankine cycle which is a regenerative cycle, wherein a steam temperature at an outlet of the boiler is 590°C or more, and a temperature increase ratio between: a feed-water temperature increase in a first feed heater corresponding to a bleed steam from an exhaust steam of the high pressure turbine; and an average of feed-water temperature increases in feed heaters other than the first feed heater; falls within 1.9 - 3.5.
  • the invention according to claim 4 is a steam turbine cycle comprising a high pressure turbine, a reheating turbine, a boiler, feed heaters for heating a feed water to the boiler by a bleed steam from the high pressure turbine and the reheating turbine, a feed pump, and a condenser, the steam turbine cycle being a single-stage reheating cycle where a working fluid is water and using a Rankine cycle which is a regenerative cycle, wherein a steam temperature at an outlet of the boiler is 590°C or more, and a specific enthalpy increase ratio between: a specific enthalpy increase in a feed water in a first feed heater corresponding to a bleed steam from an exhaust steam of the high pressure turbine; and an average of specific enthalpy increases in feed heaters other than the first feed heater; falls within 1.9 - 3.5.
  • Fig. 1 is a view of the first embodiment of the present invention.
  • the steam turbine cycle in this embodiment includes a high pressure turbine 1, a reheating turbine 24, a boiler 4, feed heaters 6 for heating a feed water to the boiler 4 by a bleed steam from the high pressure turbine 1 and the reheating turbine 24, a feed pump 12, and a condenser 10.
  • the steam turbine cycle in this embodiment is a single-stage reheating cycle where a working fluid is water and uses a Rankine cycle which is a regenerative cycle.
  • a steam temperature at an outlet of the boiler 4 is 590°C or above.
  • feed-water temperature increases in the first feed heater 7 and the second feed heaters 8 can be adjusted.
  • temperatures of the high-pressure turbine exhaust bleed steam 22 and an intermediate-pressure turbine exhaust bleed steam 32 exhaust specifications of the high pressure turbine 1 and the intermediate pressure turbine 2 have to be changed.
  • a feed water temperature at an inlet of the boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that the temperature increase ratio falls within 1.9 - 3.5.
  • the temperature increase ratio between a feed-water temperature increase in the first feed heater 7 and an average of feed-water temperature increases in the second feed heaters 8 may vary within a certain range, depending on the number of the feed heaters 6, a mechanical difference in a steam turbine such as an exhaust loss, a value corresponding to a power generation output in a power plant, a difference in a minute structure, and so on.
  • the non-patent document describes that an optimum specific enthalpy ratio is 1.8.
  • a specific enthalpy increase ratio of 1.8 is not practical as to a range of a temperature increase ratio.
  • An output of the steam turbine is a sum of "a heat drop, i.e., a specific enthalpy decrease amount x seam mass flowrate" at each stage of each turbine.
  • a heat drop i.e., a specific enthalpy decrease amount x seam mass flowrate
  • an efficiency of a regenerative cycle can be improved, when a temperature at the inlet of the boiler 4 of the boiler feed water 14 is higher. Namely, both the efficiencies have to be considered.
  • the high-pressure turbine exhaust bleed steam 22 is a steam that has a low specific enthalpy although a pressure thereof is relatively high.
  • the high-pressure turbine exhaust bleed steam 22 is not a bleed steam bled from a steam which has been heated by the reheater 5.
  • a thermal efficiency of the overall cycle can be improved.
  • a temperature increase ratio has a certain optimum value at which a thermal efficiency is maximized.
  • This optimum value is preferable when the temperature increase ratio is sufficiently higher than 1.
  • This optimum value varies depending on conditions of the main steam 16, and it is presumed that the value becomes higher as to a steam of a higher temperature.
  • a steam turbine cycle in this embodiment includes a high pressure a high pressure turbine 1, a reheating turbine 24, a boiler 4, feed heaters 6 for heating a feed water to the boiler 4 by a bleed steam from the high pressure turbine 1 and the reheating turbine 24, a feed pump 12, and a condenser 10.
  • the steam turbine cycle in this embodiment is a single-stage reheating cycle where a working fluid is water and uses a Rankine cycle which is a regenerative cycle.
  • a steam temperature at an outlet of the boiler 4 is 590°C or above.
  • each bleed steam 20 and each bleed position 31 By adjusting a flowrate of each bleed steam 20 and each bleed position 31, specific enthalpy increases in the feed waters in the first feed heater 7 and the second feed heaters 8 can be adjusted.
  • exhaust specifications of the high pressure turbine 1 and the intermediate pressure turbine 2 have to be changed.
  • a feed water temperature at an inlet of the boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a specific enthalpy increase ratio falls within 1.9 - 3.5.
  • a specific enthalpy increase ratio may vary within a certain range, depending on the number of the feed heaters 6, a mechanical difference in a steam turbine such as an exhaust loss, a value corresponding to a power generation output in a power plant, a difference in a minute structure, and so on.
  • the non-patent document describes that an optimum specific enthalpy ratio is 1.8. However, this document does not refer to a temperature of the main steam 16. Thus, since a different temperature of the main steam 16 is assumed, an optimum value of a specific enthalpy increase ratio is considered to be different.
  • a specific enthalpy increase ratio has a certain optimum value at which a thermal efficiency is optimized. This optimum value is preferable when the specific enthalpy increase ratio is sufficiently higher than 1. This optimum value varies depending on conditions of the main steam 16, and it is presumed that the value becomes higher as to a steam of a higher temperature.
  • the steam turbine cycle in this embodiment includes a high pressure turbine 1, a reheating turbine 24, a boiler 4, a feed heaters 6 for heating a feed water to the boiler 4 by a bleed steam from the high pressure turbine 1 and the reheating turbine 24, a feed pump 12, and a condenser 10.
  • the steam turbine cycle in this embodiment is a single-stage reheating cycle where a working fluid is water and uses a Rankine cycle which is a regenerative cycle.
  • a steam temperature at an outlet of the boiler 4 is 590°C or more.
  • the feed heaters other than the first heed heater 7 mean the second feed heaters 8 where a pressure of the feed water is lower than that of the first feed heater 7, and a third feed heater 26 where a pressure of the feed water is higher than that of the first feed heater 7.
  • the third feed heater 26 heats a feed water by a bleed steam from the high pressure turbine 1.
  • feed-water temperature increases in the first feed heater 7, the second feed heaters 8, and the third feed heater 26 can be adjusted.
  • temperatures of the high-pressure turbine exhaust bleed steam 22 and an intermediate-pressure turbine exhaust bleed steam 32 exhaust specifications of the high pressure turbine 1 and the intermediate pressure turbine 2 have to be changed.
  • a feed water temperature at an inlet of the boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a temperature increase ratio falls within 1.9 - 3.5.
  • a feed temperature increase ratio between: a feed-water temperature increase in the first heater 7; and an average of feed-water temperature increases in the feed heaters 8 and 26 other than the first feed heater 7; may vary within a certain range, depending on the number of the feed heater 6, a mechanical difference in a steam turbine such as an exhaust loss, a value corresponding to a power generation output in a power plant, a difference in a minute structure, and so on.
  • FIG. 1 A fourth embodiment of the present invention is described with reference to Fig. 1 .
  • the steam turbine cycle in this embodiment includes a high pressure turbine 1, a reheating turbine 24, a boiler 4, feed heaters 6 for heating a feed water to the boiler 4 by a bleed steam from the high pressure turbine 1 and the reheating turbine 24, a feed pump 12, and a condenser 10.
  • the steam turbine cycle in this embodiment is a single-stage reheating cycle where a working fluid is water and uses a Rankine cycle which is a regenerative cycle.
  • a steam temperature at an outlet of the boiler 4 is 590°C or more.
  • each bleed steam 20 and each bleed position 31 By adjusting a flowrate of each bleed steam 20 and each bleed position 31, specific enthalpy increases in feed waters in the first feed heater 7, the second feed heaters 8, and the third feed heater 26 can be adjusted.
  • specific enthalpies of the high-pressure turbine exhaust bleed steam 22 and an intermediate-pressure turbine exhaust bleed steam 32 exhaust specifications of the high pressure turbine 1 and the intermediate pressure turbine 2 have to be changed.
  • a feed water temperature at an inlet of the boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a specific enthalpy increase ratio falls within 1.9 - 3.5.
  • a specific enthalpy increase ratio between: a specific enthalpy increase of a feed water in the first feed heater 7; and an average of specific enthalpy increases of feed waters in the feed heaters 8 and 26 other than the first feed heater 7 may vary within a certain range, depending on the number of the feed heaters 6, mechanical differences in the steam turbines such as an exhaust loss, a value corresponding to a power generation output in a power plant, differences in minute structures, and so on.
  • a fifth embodiment of the present invention is described with reference to Fig 1 .
  • the fifth embodiment shown in Fig. 1 differs from the first embodiment in that feed-water temperature increases in the second feed heaters 8 are calculated in consideration of a feed-water temperature increase by a feed pump 12.
  • Other structures of the fifth embodiment are substantially the same as those of the first embodiment.
  • a feed water temperature at an inlet of a boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was fond that a cycle thermal efficiency becomes maximum under conditions that a temperature increase ratio falls within 1.9 - 3.5.
  • a temperature increase ratio may vary within a certain range, under influences of a heat generation difference caused by a mechanical difference in the feed pump 12.
  • FIG. 1 differs from the first embodiment in that feed-water specific enthalpy increases in the second feed heaters 8 are calculated in consideration of a feed-water specific enthalpy increase by a feed pump 12.
  • Other structures of the sixth embodiment are substantially the same as those of the first embodiment.
  • the feed pump 12 increases a pressure of a feed water, and simultaneously heats the feed water, as described in the third embodiment, so that a specific enthalpy of the feed water is increased.
  • a specific enthalpy increase an average specific enthalpy increase in each of the second feed heaters 8 is calculated.
  • This embodiment can be carried out, in the above-described fourth embodiment, by calculating specific enthalpy increases of feed waters in the feed heaters 8 and 26 other than a first feed heater 7, in consideration of a specific enthalpy increase in a feed water by the feed pump 12.
  • a feed water temperature at an inlet of a boiler 4 is generally defined by the boiler 4.
  • a feed-water temperature value being fixed, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a specific enthalpy increase ratio falls within 1.9 - 3.5.
  • a specific enthalpy increase ratio may vary within a certain range, under influences of a heat generation difference caused by a mechanical difference in the feed pump 12.
  • a cycle thermal efficiency can be increased, similarly to the second and fourth embodiments.
  • the eight feed heaters 6 in total are used and a cycle structure is made such that a temperature increase ratio falls within 1.9 - 3.5. This is because, in a large heat power plant, the number of the feed heaters 6 is preferably eight from an economical point of view.
  • Fig. 1 steam is bled at two positions from the intermediate pressure turbine 2 including exhaust of steam, and steam is bled at four positions from the low pressure turbine 3.
  • the total number of the bleed positions is six, the number and the positions are not limited thereto.
  • a bleed steam to the aerator 9 is the intermediate-pressure turbine exhaust bleed steam 32, but is not limited thereto.
  • the number of the feed heaters 6 being limited to eight, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a temperature increase ratio falls within 1.9 - 3.5.
  • the eight feed heaters 6 in total are used and a cycle structure is made such that a specific enthalpy increase ratio falls within 1.9 - 3.5. This is because, in a large heat power plant, the number of the feed heaters 6 is preferably eight from an economical point of view.
  • Fig. 1 steam is bled at two positions from the intermediate pressure turbine 2 including exhaust of steam, and steam is bled at four positions from the low pressure turbine 3.
  • the total number of the bleed positions is six, the number and the positions are not limited thereto.
  • a bleed steam to the aerator 9 is the intermediate-pressure turbine exhaust bleed steam 32, but is not limited thereto.
  • the number of the feed heaters 6 being limited to eight, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a specific enthalpy increase ratio falls within 1.9 - 3.5.
  • FIG. 2 the same parts as those of Fig. 1 are shown by the same reference numbers, and their detailed description is omitted.
  • the nine feed heaters 6 in total are used, and a cycle structure is made such that a temperature increase ratio falls within 1.9 - 3.5.
  • the number of the feed heaters 6 is preferably eight from an economical point of view, there is a case in which the number of the feed heaters 6 is preferably nine, with a view to more increasing an efficiency, an output, and a temperature of a main steam.
  • Fig. 2 steam is bled at three positions from an intermediate pressure turbine 2 including exhaust of steam, and steam is bled at four positions from a low pressure turbine 3.
  • the total number of the bleed positions is seven, the number and the positions are not limited thereto.
  • a bleed steam to a deaerator 9 is an intermediate pressure turbine exhaust steam 32, but is not limited thereto.
  • the number of the feed heaters 6 being limited to nine, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a temperature increase ratio falls within 1.9 - 3.5.
  • the nine feed heaters 6 in total are used, and a cycle structure is made such that a specific-enthalpy increase ratio falls within 1.9 - 3.5.
  • the number of the feed heaters 6 is preferably eight from an economical point of view, there is a case in which the number of the feed heaters 6 is preferably nine, with a view to more increasing an efficiency, an output, and a temperature of a main steam.
  • Fig. 2 steam is bled at three positions from an intermediate pressure turbine 2 including exhaust of steam, and steam is bled at four positions from a low pressure turbine 3.
  • the total number of the bleed positions is seven, the number and the positions are not limited thereto.
  • a bleed steam to a deaerator 9 is an intermediate pressure turbine exhaust steam 32, but is not limited thereto.
  • the number of the feed heaters 6 being limited to nine, an optimization calculation was conducted. Then, it was found that a cycle thermal efficiency becomes maximum under conditions that a specific enthalpy increase ratio falls within 1.9 - 3.5.
  • a cycle structure is made such that a steam temperature at an outlet of the boiler 4 is 600°C or more. This is because, when a temperature of the main steam 16 is 600°C or above, a more significant effect can be expected. Namely, an effect of improving a cycle thermal efficiency due to an increased temperature of the main steam 16 is not damaged by set conditions of a bleed steam 20 but can be fully exerted.

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Engine Equipment That Uses Special Cycles (AREA)
  • Control Of Turbines (AREA)
  • Control Of Steam Boilers And Waste-Gas Boilers (AREA)
EP06843008.1A 2006-01-20 2006-12-21 Cycle de turbine a vapeur Expired - Fee Related EP1965043B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2006012124A JP4621597B2 (ja) 2006-01-20 2006-01-20 蒸気タービンサイクル
PCT/JP2006/325524 WO2007083478A1 (fr) 2006-01-20 2006-12-21 Cycle de turbine a vapeur

Publications (3)

Publication Number Publication Date
EP1965043A1 true EP1965043A1 (fr) 2008-09-03
EP1965043A4 EP1965043A4 (fr) 2014-07-02
EP1965043B1 EP1965043B1 (fr) 2016-03-09

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Application Number Title Priority Date Filing Date
EP06843008.1A Expired - Fee Related EP1965043B1 (fr) 2006-01-20 2006-12-21 Cycle de turbine a vapeur

Country Status (6)

Country Link
US (1) US20090094983A1 (fr)
EP (1) EP1965043B1 (fr)
JP (1) JP4621597B2 (fr)
KR (1) KR20080038233A (fr)
CN (1) CN101300407B (fr)
WO (1) WO2007083478A1 (fr)

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2008119784A2 (fr) * 2007-03-30 2008-10-09 Siemens Aktiengesellschaft Ensemble muni d'une turbine à vapeur et d'un condensateur
AU2011236050B2 (en) * 2010-10-19 2014-03-13 Kabushiki Kaisha Toshiba Steam turbine plant
RU2560510C1 (ru) * 2014-03-11 2015-08-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ работы тепловой электрической станции
RU2562724C1 (ru) * 2014-05-06 2015-09-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ утилизации тепловой энергии, вырабатываемой тепловой электрической станцией
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JP5672450B2 (ja) * 2011-02-25 2015-02-18 株式会社ササクラ 造水装置および造水方法
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RU2560607C1 (ru) * 2014-04-07 2015-08-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ работы тепловой электрической станции
RU2562730C1 (ru) * 2014-05-06 2015-09-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ утилизации тепловой энергии, вырабатываемой тепловой электрической станцией
CN104358596B (zh) * 2014-10-31 2016-05-18 中国大唐集团科学技术研究院有限公司 多汽轮机联合发电超超临界机组
CN110206601A (zh) * 2019-06-04 2019-09-06 大唐郓城发电有限公司 一种汽轮机进气保护装置
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US9399929B2 (en) 2010-10-19 2016-07-26 Kabushiki Kaisha Toshiba Steam turbine plant
US9458739B2 (en) 2010-10-19 2016-10-04 Kabushiki Kaisha Toshiba Steam turbine plant
RU2560510C1 (ru) * 2014-03-11 2015-08-20 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ работы тепловой электрической станции
RU2562724C1 (ru) * 2014-05-06 2015-09-10 Федеральное государственное бюджетное образовательное учреждение высшего профессионального образования "Казанский государственный энергетический университет" (ФГБОУ ВПО "КГЭУ") Способ утилизации тепловой энергии, вырабатываемой тепловой электрической станцией

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EP1965043B1 (fr) 2016-03-09
JP4621597B2 (ja) 2011-01-26
WO2007083478A1 (fr) 2007-07-26
EP1965043A4 (fr) 2014-07-02
KR20080038233A (ko) 2008-05-02
US20090094983A1 (en) 2009-04-16
CN101300407A (zh) 2008-11-05
CN101300407B (zh) 2011-01-19

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