KR101935637B1 - Combined cycle power generation system - Google Patents

Combined cycle power generation system Download PDF

Info

Publication number
KR101935637B1
KR101935637B1 KR1020160154023A KR20160154023A KR101935637B1 KR 101935637 B1 KR101935637 B1 KR 101935637B1 KR 1020160154023 A KR1020160154023 A KR 1020160154023A KR 20160154023 A KR20160154023 A KR 20160154023A KR 101935637 B1 KR101935637 B1 KR 101935637B1
Authority
KR
South Korea
Prior art keywords
pressure
steam
low
turbine
medium
Prior art date
Application number
KR1020160154023A
Other languages
Korean (ko)
Other versions
KR20180056148A (en
Inventor
김동섭
권현민
문성원
Original Assignee
인하대학교 산학협력단
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 인하대학교 산학협력단 filed Critical 인하대학교 산학협력단
Priority to KR1020160154023A priority Critical patent/KR101935637B1/en
Publication of KR20180056148A publication Critical patent/KR20180056148A/en
Application granted granted Critical
Publication of KR101935637B1 publication Critical patent/KR101935637B1/en

Links

Images

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
    • F01K23/00—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids
    • F01K23/02—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled
    • F01K23/06—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle
    • F01K23/10—Plants characterised by more than one engine delivering power external to the plant, the engines being driven by different fluids the engine cycles being thermally coupled combustion heat from one cycle heating the fluid in another cycle with exhaust fluid of one cycle heating the fluid in another cycle
    • 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
    • F01K11/00—Plants characterised by the engines being structurally combined with boilers or condensers
    • F01K11/02—Plants characterised by the engines being structurally combined with boilers or condensers the engines being turbines
    • 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
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C3/00—Gas-turbine plants characterised by the use of combustion products as the working fluid
    • F02C3/04—Gas-turbine plants characterised by the use of combustion products as the working fluid having a turbine driving a compressor
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
    • F02C—GAS-TURBINE PLANTS; AIR INTAKES FOR JET-PROPULSION PLANTS; CONTROLLING FUEL SUPPLY IN AIR-BREATHING JET-PROPULSION PLANTS
    • F02C6/00—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use
    • F02C6/18—Plural gas-turbine plants; Combinations of gas-turbine plants with other apparatus; Adaptations of gas-turbine plants for special use using the waste heat of gas-turbine plants outside the plants themselves, e.g. gas-turbine power heat plants
    • 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
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E20/00—Combustion technologies with mitigation potential
    • Y02E20/16—Combined cycle power plant [CCPP], or combined cycle gas turbine [CCGT]

Landscapes

  • 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)

Abstract

The present invention provides a cooling apparatus for a gas turbine blade, which includes a cooling air generating section separately from a gas turbine section, and supplies compressed air generated in a low-pressure compressor and a high-pressure compressor included in the cooling air generating section to cooling air of a gas turbine blade, Pressure condensed air flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled using the intermediate heat exchanger in which the condensed water flows and the compressor cooling power is reduced due to the precooling effect of the cooling air and the intermediate cooling effect of the cooling air, The performance of the gas turbine is improved and the heat recovered in the intermediate cooling process is transferred to the arrangement recovery cycle to improve the performance of the arrangement recovery cycle.

Figure R1020160154023

Description

{Combined cycle power generation system}

The present invention relates to a combined-cycle power generation system, and more particularly, to a combined-cycle power generation system that includes a cooling-air generating unit separately from a gas turbine unit, and compresses compressed air generated in the low-pressure compressor and the high- Pressure compressed air flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled by using an intermediate heat exchanger provided with cooling air and condensed water generated by condensation of the steam. The cooling effect of the cooling air and the intermediate cooling The present invention relates to a combined-cycle power generation system in which the performance of a gas turbine is improved over the conventional example cooling method, and the heat recovered in the intermediate cooling process is transferred to an arrangement recovery cycle to improve the performance of the arrangement recovery cycle .

Typical examples of the energy conversion apparatus include a gas turbine system or a steam turbine system that generates electricity using energy such as fuel.

Specifically, the gas turbine supplies fuel and air to burn the fuel, thereby driving the turbine using the high-temperature, high-pressure combustion gas generated thereby. The steam turbine uses a steam generator to heat the feed water Thereby generating steam, and then supplying the generated steam to the turbine to drive the steam turbine.

Efforts to improve the energy efficiency of systems have continued since the development of gas turbine power generation systems or steam turbine power generation systems that produce power through such gas turbines or generators connected to steam turbines.

For reference, the liquid circulating through the system can be defined differently depending on the flow position. The liquid, which is condensed by the condenser and supplied to the steam generating means, is supplied to a plurality of condensed water and steam generating means The liquid that is converted into steam can be defined as feed water.

In particular, the combined-cycle power generation system, which uses heat from the exhaust gas produced after producing energy from the gas turbine to heat the steam turbine cycle water using HRSG (Heat Recovery Steam Generator), uses only a steam turbine or only a gas turbine It is a system whose efficiency is remarkably improved as compared with the power generation system used.

The prior art is disclosed in Japanese Patent Registration No. 10-1531931 (Jun. 22, 2015).

Conventional turbine cooling technology reduces the surface temperature of turbine blades by injecting a portion of the compressed air from the compressor into the turbine blades. The higher the performance of the gas turbine, the higher the compression ratio and the higher turbine inlet temperature Hereinafter, the temperature of the compressed air is high to provide a technique for cooling the compressed air.

To solve this problem, conventionally, cooling air added to the compressor is cooled by a separate cooler in order to pre-cool the cooling air for cooling the turbine blades. However, pre-cooling of the cooling air is necessary for increasing the pressure ratio and turbine inlet temperature , The energy is discarded as it is in the process of cooling the compressed air.

Accordingly, in order to solve the above-described problem, the present invention provides a cooling air generator separately from the gas turbine, and the compressed air generated in the low-pressure compressor and the high-pressure compressor included in the cooling air generator is supplied as cooling air for the gas turbine blade Pressure compressing air flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled using the intermediate heat exchanger in which the condensed water generated by the condensation of the steam flows, and the pre-cooling effect of the cooling air and the intermediate- The present invention provides a combined-cycle power generation system in which the performance of a gas turbine is improved as compared with the conventional pre-cooling method due to a decrease in power, and the heat recovered in the intermediate cooling process is transferred to an arrangement recovery cycle to improve the performance of the arrangement recovery cycle.

A combined-cycle power generation system according to the present invention includes a compressor for introducing outside air into a high pressure by a rotational force, a compressor connected to an outlet of the compressor, for introducing compressed air compressed by the compressor, A gas turbine section that is connected to the compressor and includes a gas turbine in which a high temperature and high pressure combustion gas discharged from the combustor generates a rotational force corresponding to the turbine blade; A steam turbine section driven by the steam generated in the batch recovery boiler section, and a steam turbine section driven by steam generated by the steam turbine section, A condenser for condensing the steam through the steam turbine section, Wherein the condenser includes a condenser connected to a line through which the fluid flows with the steam turbine portion and which condenses the fluid discharged from the steam turbine portion to discharge condensed water, A low pressure pump connected to the condensing water line and connected to the condensing water line at a low pressure, and a low pressure pump connected to the condensing water line at a low pressure to discharge the condensed water from the condensing water line at a low pressure; A medium pressure pump connected to a line through which the fluid flows to the deaeration device and to discharge the fluid deaerated through the deaeration device under a medium pressure; And a high-pressure pump for sending the fluid sent out under a medium pressure to a high pressure. And a cooling air generating unit for cooling the gas turbine by providing the generated cooling air to the gas turbine of the gas turbine unit, wherein the cooling air generator is driven by the rotational force of an electric motor using an external power source, A low pressure compressor for compressing and discharging outside air to a low pressure and a high pressure compressor driven by the torque of an electric motor using an external power source to compress the low pressure air discharged from the low pressure compressor to a high pressure and discharge the low pressure air, And an intermediate cooling heat exchanger for intermediate cooling the cooling air by heat exchange with low-pressure air discharged from the condenser and condensed water generated by condensing the steam in the condenser, wherein the steam turbine includes a low-pressure turbine generating a rotational force by low-pressure steam, An intermediate-pressure turbine generating a rotational force by the steam of the high-pressure steam, Pressure boiler is connected to a line through which the fluid flows with the low-pressure pump inside the exhaust passage, and a hot-water tank for heating the low-pressure condensate flowing through the inside by heat exchange with the exhaust gas, (Condensed water) is introduced through the deaerator into the exhaust pipe, and the fluid (condensed water) is heated by the heat exchange between the fluid (condensate) and the exhaust gas inside the exhaust pipe, Pressure condenser, which is connected to a line through which the fluid flows in the exhaust passage, and which is a fluid flowing along the inside of the exhaust passage, A first high pressure economizer for heating by heat exchange with the first high pressure economizer and for supplying the heated condensed water to the second high pressure economizer, A low pressure and hot air which is connected to a line through which the fluid flows with the low pressure evaporator and heats the low pressure steam flowing along the inside by heat exchange with the exhaust gas to supply the heated low pressure steam to the steam turbine section, Pressure condensate, which is a degassed fluid flowing along the inside of the furnace, is heated by heat exchange with the exhaust gas to generate steam, and the generated steam is supplied to the intermediate-pressure evaporator Pressure economizer and a medium pressure evaporator connected to a line through which the fluid flows with the medium pressure economizer in the exhaust passage to introduce steam generated through the medium pressure economizer and generate and supply a medium pressure steam using exhaust gas, And is connected to a line through which the fluid flows with the intermediate-pressure evaporator in the exhaust passage, Pressure steam is heated by heat exchange with the exhaust gas to mix the steam with the steam discharged from the high-pressure turbine to provide the first reheater, A second high pressure economizer connected to a line through which the fluid flows with the intermediate cooling heat exchanger and the first high pressure economizer and for heating the condensed water as a fluid flowing along the inside thereof by heat exchange with the exhaust gas and providing the condensed water to the high pressure evaporator; Pressure economizer and a second high-pressure economizer connected to the second high-pressure economizer through a line through which the fluid flows, the high-pressure steam is generated by heat exchange with the exhaust gas by flowing the fluid heated through the second high-pressure economizer, Pressure evaporator and a line through which the fluid flows with the medium pressure and the heat inside the exhaust passage, A first reheater for introducing a medium pressure steam heated by pressure and heat to reheat the medium pressure steam by heat exchange with the exhaust gas to provide reheated medium pressure steam to the second reheater, Pressure evaporator and a second high-pressure reheater for reheating the high-pressure steam flowing through the interior of the high-pressure evaporator by heat exchange with the exhaust gas to provide reheated high-pressure steam to the second high- Pressure reheating line and a line through which the fluid flows in the exhaust gas recirculation passage in the exhaust passage so as to introduce the intermediate-pressure steam reheated by the first reheater to heat-exchange the exhaust gas with the intermediate- A second reheater for reheating the second high-pressure reheater to provide reheated steam of a medium pressure to the steam turbine, and a second reheater for reheating the second high- It is connected to, and re-heating the high pressure of the steam that flows along the inside of the heat exchange with the exhaust gas, and a second high-pressure reboiler to provide vapor of the re-heated high-pressure parts of the steam turbine.

delete

delete

delete

The combined-cycle power generation system according to an embodiment of the present invention provides compressed air generated at a low pressure and a high pressure separately from the gas turbine as cooling air for a gas turbine blade, so that the consuming power of the compressor in the gas turbine is reduced, The performance of the gas turbine is improved.

Pressure refrigerant flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled using the intermediate heat exchanger in which the condensed water generated by the condensation of the steam flows, the cooling effect of the cooling air and the heat recovered in the intermediate cooling process So that the performance of the array recovery cycle is improved.

FIG. 1 is a schematic view illustrating a combined-cycle thermal power generation system according to an embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. Prior to this, terms and words used in the present specification and claims should not be construed as limited to ordinary or dictionary terms, and the inventor should appropriately interpret the concepts of the terms appropriately The present invention should be construed in accordance with the meaning and concept consistent with the technical idea of the present invention.

Therefore, the embodiments described in the present specification and the configurations shown in the drawings are merely the most preferred embodiments of the present invention, and are not intended to represent all of the technical ideas of the present invention. Therefore, It should be understood that there may be variations.

The present invention provides a cooling apparatus for a gas turbine blade, which includes a cooling air generating unit separately from a gas turbine unit, and supplies compressed air generated in a low-pressure compressor and a high-pressure compressor included in the cooling air generating unit to cooling air of a gas turbine blade, Pressure condensed air flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled using the intermediate heat exchanger in which the condensed water flows and the compressor cooling power is reduced due to the precooling effect of the cooling air and the intermediate cooling effect of the cooling air, The present invention relates to a combined-cycle power generation system in which the performance of a gas turbine is improved and a heat recovery cycle is performed in an intermediate cooling process to improve the performance of an arrangement recovery cycle.

The combined thermal power generation system according to an embodiment of the present invention includes a gas turbine unit 100, an arrangement recovering boiler unit 200, a steam turbine unit 300, a cooling air generating unit 400 and a condensing unit 500, First, the gas turbine unit 100 performs primary power generation. The gas turbine unit 100 includes a compressor 110 for introducing outside air into a high pressure by a rotational force like a conventional gas turbine unit, And a combustor 120 which is connected to the outlet and flows compressed air compressed by the compressor 110 to mix the fuel supplied from the outside and discharge the compressed high-temperature high-pressure combustion gas.

The compressor 110 includes an intake unit through which air flows and a discharge unit through which the compressed compressed air flows. The compressor 110 is connected to the multi-stage turbine 130 via an axis, and receives the rotational force of the turbine 130 , And the air introduced by the transmitted torque is compressed to a high pressure.

The compressed air compressed by the compressor 110 may be stored in a separate chamber (not shown), and then may be selectively supplied to the combustor 120 by opening or closing a valve.

The combustor 120 is connected to the discharge port of the compressor 110 to supply the compressed air compressed by the compressor 10 to mix the fuel provided from the outside to combust the fuel contained in the compressed air, And discharges the gas to the turbine 130 side.

The high temperature and high pressure exhaust gas discharged from the combustor 120 is discharged to the turbine 130 side so that the exhaust gas of high temperature and high pressure is discharged from the turbine 130 to the turbine 130, The turbine 130 rotates to generate a rotating force corresponding to the blade.

As the turbine 130 rotates as the turbine 130 is connected to the compressor 110, the compressor 110 also rotates to compress the air flowing into the compressor 110 by the rotational force of the turbine 130 .

At this time, the turbine 130 is preferably configured in multiple stages to maximize the efficiency of the gas turbine section 100.

Also, the combined-cycle power generation system according to an embodiment of the present invention includes a cooling air generator 400 for generating cooling air for cooling the turbine blades of the turbine 130 so as to improve the performance of the gas turbine .

The low-pressure compressor 410 includes a low-pressure compressor 410 and a low-pressure compressor 410. The low-pressure compressor 410 is connected to the low-pressure compressor through an additional line through which the fluid flows, And a high-pressure compressor 420 for compressing and discharging the low-pressure air discharged from the high-pressure compressor 420 to high-pressure.

The low pressure compressor 410 and the high pressure compressor 420 of the cooling air generator 400 are driven by the rotational force of an electric motor using an external power source without using the power generated by the gas turbine unit 100, .

Accordingly, the cooling air generating unit 400 compresses the external air introduced from the separate power source into low pressure and high pressure to generate cooling air, and supplies the generated low-pressure and high-pressure cooling air to the gas To provide a turbine to cool the blades of the gas turbine to improve the performance of the gas turbine.

The intermediate cooling heat exchanger 430 is connected to the low pressure compressor 410 and the high pressure compressor 420 through an intermediate cooling heat exchanger 430. The intermediate cooling heat exchanger 430 is connected to the low pressure compressor 410, And the condensed water generated by condensing the steam in the condensing part 500 flows into the inside to heat the low pressure air and the condensed water.

Therefore, the power consumption of the compressor is reduced due to the intermediate cooling effect of the cooling air, thereby improving the performance of the gas turbine over the conventional cooling method.

In addition, the arrangement of the exhaust gas generated in the gas turbine section 100 is recovered in the arrangement recovery boiler section 200, the steam is generated using the recovered arrangement, and the steam generated in the arrangement recovery boiler section 200 The steam turbine section 300 is driven.

Here, the steam turbine unit 300 performs secondary power generation, and includes a low pressure turbine 310 generating a rotational force with low pressure steam, a medium pressure turbine 320 generating a rotational force with medium pressure steam, And a high-pressure turbine (330) generating a rotating force by steam, wherein the first generator (140) and the second generator (340) are connected to the steam turbine section (100) The first generator 140 and the second generator 340 are generated by the generated power as the gas turbine section 100 and the steam turbine section 300 are driven.

The detailed description of the power generation process of the first generator 140 and the second generator 340 will be omitted.

The steam turbine part 300 according to an embodiment of the present invention is connected to a line through which the fluid flows to the condenser part 500 so as to send the steam through the steam turbine part 300 to the condenser part 500 do.

The condenser 500 includes a condenser 510 for introducing and condensing the steam through the steam turbine 300 so that the condensed water condensed in the condenser 510 is supplied to the batch recovery boiler 200 ). ≪ / RTI >

The condensing unit 500 is provided with a low pressure pump 520 for supplying condensed water to the batch boiler unit 200 at a low pressure, an intermediate pressure pump 540 for supplying condensed water at a high pressure, And a pump 550.

In addition, the condenser 510 according to one embodiment of the present invention provides cooling to the gaseous fluid (steam) sent from the steam turbine unit 300 like a conventional condenser, Pressure pump 520. The low-pressure pump 520 discharges the condensed water to a low pressure and supplies the condensed water to the batch recovery boiler 200. The low-

The low pressure condensate supplied through the low pressure pump 520 is supplied to a warmer 210 of the arrangement recovery boiler 200. The warmer 210 is connected to the low pressure pump 520, To heat the low-pressure condensate flowing along the inside by heat exchange with the exhaust gas.

At this time, the hot water heater 210 is preferably disposed inside an exhaust passage (not shown) through which exhaust gas flows, and condensed water flowing along the inside of the hot water heater 210 is heated by heat exchange with the exhaust gas .

The condensed water heated by the hot water heater 210 is vented by a deaerator 530 and the deaerator 530 is connected to a line through which the fluid flows with the hot water heater 210 And removes air from the condensed water heated through the hot water heater 210, that is, removes air from the condensed water.

Here, the deaerator 530 according to an embodiment of the present invention applies heat to the condensed water to remove the air contained in the condensed water, as in the case of conventional deaerators. At this time, low-pressure steam is supplied to the deaerator 530 as a heat source To remove the air contained in the condensed water.

The fluid with the air removed by the deaerator 530 is supplied to the medium pressure pump 540 and the low pressure evaporator 220 of the batch recovery boiler 200.

Here, the exhaust heat recovery boiler 200 according to one embodiment of the present invention includes an exhaust passage (not shown) through which the exhaust gas discharged from the gas turbine 100 flows, One side of the exhaust gas passage is connected to a portion of the gas turbine section 100 through which the exhaust gas is discharged, and the other side of the exhaust gas passage is connected to an exhaust port for discharging the exhaust gas to the outside.

The low pressure evaporator 220 includes a low pressure evaporator 220 and a low pressure evaporator 220. The low pressure evaporator 220 is connected to a line through which the fluid flows with the deaerator 530. [ (Condensed water) through the deaerator 530 to heat the fluid (condensed water) by heat exchange between the fluid (condensed water) and the exhaust gas inside the low-pressure evaporator 220, And discharges the fluid as low-pressure steam.

At this time, the generated low-pressure steam is diverged and supplied to the deaerator 530 and the low-pressure steam generator 230, respectively. The low-pressure steam supplied to the deaerator 530 is supplied to the condenser water as a heat source of the deaerator 530 It is used as a catalyst to remove the air contained.

The low-pressure and high-pressure heater 230 heats the introduced low-pressure steam by heat exchange with the exhaust gas. The low-pressure steam heater 230 is disposed inside the exhaust gas passage and is connected to a line through which the fluid flows with the low- Pressure steam flowing through the steam turbine 300 by heat exchange with the exhaust gas, and provides the heated low-pressure steam to the steam turbine section 300.

The low pressure steam supplied to the steam turbine unit 300 is used as a power source for driving the low pressure turbine 310 of the steam turbine unit 300 and the low pressure steam used as a power source of the low pressure turbine unit 310 The steam is sent to the condenser 500 for condensation.

The condensed water, which is a fluid branched from the deaerator 530 to the medium pressure pump 540, is delivered as a high pressure pump 550 and a medium pressure economizer 241 while being delivered as medium pressure through the medium pressure pump 540 Pressure condenser 241 is disposed inside the exhaust passage and is connected to a line through which the fluid flows with the medium pressure pump 540. The medium pressure condenser 241 is a deaerated fluid flowing along the inside of the exhaust passage, To generate steam, and provides the generated steam to the intermediate-pressure evaporator 221.

The intermediate pressure evaporator 221 is connected to a line through which the fluid flows to the intermediate pressure economizer 241 in the exhaust passage to introduce steam generated through the intermediate pressure economizer 241 to generate steam of a medium pressure using the exhaust gas .

The medium pressure steam generated by the intermediate pressure evaporator 221 is supplied to the medium pressure and heat exchanger 231. The medium pressure and heat exchanger 231 is disposed inside the exhaust passage and flows through the medium pressure evaporator 221 Pressure steam flowing along the inside thereof is heated by heat exchange with the exhaust gas, and the heated medium-pressure steam is mixed with the steam discharged from the high-pressure turbine 330 to be supplied to the first reheater 250 to provide.

The first reheater 250 is connected to a line through which the fluid flows with the medium pressure and the heat exchanger 231 in the exhaust passage to introduce the medium pressure steam heated by the medium pressure and heat exchanger 231, The steam of the intermediate pressure is reheated by the heat exchange with the gas, and the reheated steam of the intermediate pressure is supplied to the second reheater 251.

The second reheater 251 is connected to a line through which the fluid flows with the first reheater 250 in the exhaust passage to introduce a medium pressure steam reheated by the first reheater 250 And reheats the medium-pressure steam by heat exchange with the exhaust gas to provide reheated steam of a medium pressure to the steam turbine section 300.

The medium-pressure steam supplied to the steam turbine unit 300 is used as a power source for driving the medium-pressure turbine 320 of the steam turbine unit 300, and the medium-pressure steam used as the power source of the medium- Pressure turbine 310 and the low-pressure turbine 310. The low-pressure turbine 310 is connected to the low-

The condensed water sent out from the intermediate pressure pump 540 is sent to the intermediate cooling heat exchanger 430 and the first high pressure economizer 240 while being raised to a high pressure through the high pressure pump 550, The cooling heat exchanger 430 internally exchanges the low-pressure air discharged from the low-pressure compressor 410 and the high-pressure pump 550 with the high-pressure pump 550, and the low-pressure air is intermittently cooled to preheat the condensed water .

At this time, the condensed water through the intermediate cooling heat exchanger 430 is supplied to the second high pressure economizer 242.

The first high-pressure economizer 240 is disposed inside the exhaust passage and is connected to a line through which the fluid flows with the high-pressure pump 550. The high-pressure condenser, which is a fluid flowing along the interior of the exhaust passage, And provides the heated condensed water to the second high-pressure economizer 241. The second high-

The second high pressure economizer 241 is also disposed inside the exhaust passage and connected to a line through which the fluid flows with the intermediate cooling heat exchanger 430 and the first high pressure economizer 240, The condensed water is heated by heat exchange with the exhaust gas and is supplied to the high-pressure evaporator 222.

In addition, the high-pressure evaporator 222 is disposed inside the exhaust gas inlet side of the exhaust passage and connected to a line through which the fluid flows with the second high-pressure economizer 241, so that the second high-pressure economizer 241 And generates high-pressure steam by heat exchange with the exhaust gas, thereby providing the first high-pressure reheater 232 with steam.

The high pressure steam generated in the high pressure evaporator 222 is supplied to the first high pressure reheater 232. The first high pressure reheater 232 is disposed inside the exhaust passage and the high pressure evaporator 222, The steam is reheated by heat exchange with the exhaust gas, and the reheated high-pressure steam is supplied to the second high-pressure reheater 233.

The second high-pressure reheater 233 is also connected to a line through which the fluid flows with the first high-pressure reheater 232 and is disposed inside the exhaust passage. The high-pressure steam flowing along the interior of the second high- And reheated high-pressure steam is supplied to the steam turbine section 300. The steam turbine section 300 is a steam turbine section.

The high pressure steam supplied to the steam turbine unit 300 is used as a power source for driving the high pressure turbine 330 of the steam turbine unit 300 and the high pressure steam used as a power source of the high pressure turbine unit 330 Is supplied to the intermediate pressure turbine (320) through the first reheater (250).

Therefore, the combined-cycle power generation system according to an embodiment of the present invention includes a cooling air generator separately from the gas turbine, and the compressed air generated in the low-pressure compressor and the high-pressure compressor included in the cooling air generator is cooled Pressure compressed air flowing from the low-pressure compressor to the high-pressure compressor is intermittently cooled by using an intermediate heat exchanger in which condensed water generated by the condensation of the steam flows and is supplied to the air and the intermediate cooling effect of the cooling air The performance of the gas turbine is improved more than that of the conventional example cooling method, and the heat recovered in the intermediate cooling process is transferred to the arrangement recovery cycle to improve the performance of the arrangement recovery cycle.

While the present invention has been described with reference to exemplary embodiments, it is to be understood that the invention is not limited to the disclosed exemplary embodiments, but, on the contrary, is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims. Accordingly, the true scope of the present invention should be determined by the technical idea of the appended claims.

100: gas turbine section
110: compressor
120: Combustor
130: Turbine
200: Sequence recovery boiler section
210: hot water machine
220: Low pressure evaporator
221: Medium pressure evaporator
222: High-pressure evaporator
230: Low pressure and heat
231: Heavy pressure and heat
232: First High Pressure Reheater
233: Second High Pressure Reheating
240: First High Pressure Economizer
241: Medium pressure economizer
242: second high pressure economizer
250: 1st reheating
251: Second reheating
300: steam turbine section
310: Low pressure turbine
320: Medium pressure turbine
330: High pressure turbine
340: second generator
400: cooling air generating unit
410: Low pressure compressor
420: High pressure compressor
430: Intermediate cooling heat exchanger
500: condenser
510: condenser
520: Low pressure pump
530: Deaerator
540: Medium pressure pump
550: High pressure pump

Claims (5)

A compressor for introducing outside air into the chamber by a rotational force to compress the chamber at a high pressure;
A combustor connected to an outlet of the compressor for introducing the compressed air compressed by the compressor to mix fuel supplied from the outside and discharging compressed high-temperature high-pressure combustion gas;
A gas turbine section that is connected to the compressor and includes a gas turbine in which a high-temperature, high-pressure combustion gas discharged from the combustor generates rotational force corresponding to the turbine blade;
An arrangement recovery boiler unit for generating steam using the arrangement of the exhaust gas generated in the gas turbine unit;
A steam turbine section driven by steam generated in the batch recovery boiler section;
A first generator and a second generator that generate power by the power of the gas turbine section and the steam turbine section;
And a condensing portion for condensing the steam through the steam turbine portion and re-supplying the steam to the batch recovery boiler portion,
A condenser connected to a line through which the fluid flows with the steam turbine section and discharging condensed water by condensing the fluid discharged from the steam turbine section;
A low pressure pump connected to a line through which the fluid flows with the condenser and to discharge the condensed water discharged from the condenser to a low pressure;
A deaerator connected to a line through which the fluid flows with the batch recovery boiler portion and removes air from the condensate through the batch recovery boiler portion;
A medium pressure pump connected to the deaerator through a line through which the fluid flows, and delivering the deaerated fluid through the deaerator at a medium pressure;
And a high-pressure pump connected to the medium-pressure pump through a line through which the fluid flows, and for sending out the medium-pressure fluid to the high pressure,
And a cooling air generator for cooling the gas turbine by supplying outside air to generate air by compressing the air to generate cooling air and supplying the generated cooling air to the gas turbine of the gas turbine portion,
The cooling air generator includes a low-pressure compressor driven by a rotational force of an electric motor using an external power source and compressing and discharging the introduced external air to a low pressure;
A high pressure compressor driven by a rotational force of an electric motor using an external power source and compressing and discharging the low pressure air discharged from the low pressure compressor to a high pressure;
And an intermediate cooling heat exchanger for intermediate-cooling the low-pressure air discharged from the low-pressure compressor and the condensed water generated by condensing the steam in the condenser,
Wherein the steam turbine comprises: a low pressure turbine generating a rotational force with low pressure steam; A medium pressure turbine generating a torque by means of steam of medium pressure; And a high-pressure turbine generating a rotating force by high-pressure steam,
The boiler comprising: a hot water tank connected to a line through which the fluid flows with the low pressure pump in the exhaust passage to heat low-pressure condensed water flowing through the inside of the exhaust pipe by heat exchange with the exhaust gas;
(Condensed water) is introduced through the deaerator to flow the fluid (condensed water) through the heat exchange between the fluid (condensate) and the exhaust gas inside the exhaust passage, A low-pressure evaporator for generating low-pressure steam by heating to discharge the fluid as low-pressure steam;
Pressure condenser which is connected to a line through which the fluid flows with the high-pressure pump in the exhaust passage and which heats the high-pressure condensate, which is a fluid flowing along the inside, through heat exchange with the exhaust gas, and supplies the heated condensate to the second high-pressure economizer 1 high pressure economizer;
Pressure steam is supplied to the steam turbine section by heating the low-pressure steam flowing through the inside thereof by heat exchange with the exhaust gas and supplying the heated low-pressure steam to the steam turbine section, With heat;
Pressure condensate, which is a degassed fluid flowing along the inside of the exhaust passage, is heated by heat exchange with the exhaust gas to generate steam, and the generated steam is supplied to the intermediate-pressure evaporator Pressure economizer;
A middle pressure evaporator connected to a line through which the fluid flows with the medium pressure economizer in the exhaust passage to introduce steam generated through the intermediate pressure economizer and generate and supply a medium pressure steam using exhaust gas;
Pressure steam which flows in the inside of the exhaust passage through a line through which the fluid flows with the medium-pressure evaporator, heats the medium-pressure steam flowing through the inside of the exhaust passage by heat exchange with the exhaust gas, Medium pressure and hot air to provide a first reheater by mixing;
A second high-pressure evaporator that is connected to the intermediate cooling heat exchanger and the first high-pressure economizer through a line through which the fluid flows, inside the exhaust passage, for heating the condensed water, which is a fluid flowing along the interior thereof, An economizer;
And a second high pressure economizer connected to the second high pressure economizer through a line through which the fluid flows, the fluid heated by the second high pressure economizer is introduced into the exhaust passage to generate high pressure steam by heat exchange with the exhaust gas, A high pressure evaporator provided with heat;
Pressure steam is introduced into the exhaust passage through a line through which the fluid flows with the medium pressure and the heat, the medium-pressure steam heated by the medium pressure and the heat is introduced into the exhaust passage, the medium-pressure steam is primarily reheated by heat exchange with the exhaust gas, A first reheater for supplying the steam of the intermediate pressure to the second reheater;
Pressure steam to the second high-pressure reheater, the second high-pressure reheater being connected to the high-pressure evaporator through a line through which the fluid flows, and reheating the high-pressure steam flowing through the inside of the exhaust passage by heat exchange with the exhaust gas, A first high-pressure reheater;
Pressure steam which is reheated by the first reheater to flow into the exhaust pipe and is reheated by reheating the intermediate-pressure steam by heat exchange with the exhaust gas, A second reheater for providing reheated steam of a medium pressure to the steam turbine section;
Pressure steam that flows through the inside of the exhaust passage and is connected to a line through which the fluid flows, and reheats the high-pressure steam flowing through the inside of the exhaust passage by heat exchange with the exhaust gas to supply reheated high-pressure steam to the steam turbine section And a second high-pressure reheater operatively connected to the second high pressure reheater. delete delete delete delete
KR1020160154023A 2016-11-18 2016-11-18 Combined cycle power generation system KR101935637B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
KR1020160154023A KR101935637B1 (en) 2016-11-18 2016-11-18 Combined cycle power generation system

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
KR1020160154023A KR101935637B1 (en) 2016-11-18 2016-11-18 Combined cycle power generation system

Publications (2)

Publication Number Publication Date
KR20180056148A KR20180056148A (en) 2018-05-28
KR101935637B1 true KR101935637B1 (en) 2019-01-04

Family

ID=62451663

Family Applications (1)

Application Number Title Priority Date Filing Date
KR1020160154023A KR101935637B1 (en) 2016-11-18 2016-11-18 Combined cycle power generation system

Country Status (1)

Country Link
KR (1) KR101935637B1 (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR102256414B1 (en) * 2019-09-02 2021-05-26 비에이치아이(주) Heat recovery boiler system
KR102526789B1 (en) * 2021-05-03 2023-04-27 인하대학교 산학협력단 Combined cycle power generation system

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014009606A (en) * 2012-06-28 2014-01-20 Mitsubishi Heavy Ind Ltd Cooling system of turbine blade and gas turbine

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014009606A (en) * 2012-06-28 2014-01-20 Mitsubishi Heavy Ind Ltd Cooling system of turbine blade and gas turbine

Also Published As

Publication number Publication date
KR20180056148A (en) 2018-05-28

Similar Documents

Publication Publication Date Title
EP3284920B1 (en) Hybrid generation system using supercritical carbon dioxide cycle
US8938966B2 (en) Storage of electrical energy with thermal storage and return through a thermodynamic cycle
CA2714761C (en) Dual reheat rankine cycle system and method thereof
JP3681434B2 (en) Cogeneration system and combined cycle power generation system
EP2607634B1 (en) Method for operating a combined cycle power plant
JPH09503263A (en) Cooling device for gas turbine cooling medium in gas / steam turbine complex
RU2644801C2 (en) Thermodynamic system of the combined cycle for the development of mechanical energy and the method of development of mechanical energy and of driving the turbomachine
JP2009299682A (en) System for recovering waste heat generated by auxiliary system of turbo machine
WO2010087126A1 (en) Power plant
JP2001214759A (en) Gas turbine combined cycle
CN101705849B (en) Self-coupling cold source heat pump circulating device of low-temperature exhaust heat power generating system in low temperature exhaust steam condensation process
CN102628381A (en) System and method for using gas turbine intercooler heat in a bottoming steam cycle
US10309259B2 (en) CO2 power generation system
KR20140085001A (en) Energy saving system for using waste heat of ship
CN103821571A (en) Novel thermal power generation system and working method
KR101935637B1 (en) Combined cycle power generation system
JP3905967B2 (en) Power generation / hot water system
CN105765179A (en) Selective pressure kettle boiler for rotor air cooling applications
KR101753526B1 (en) Combined cycle power generation system
RU2412359C1 (en) Operating method of combined cycle plant
KR20210104067A (en) District heating network including heat pump unit and heat pump unit
KR101967024B1 (en) Supercritical CO2 power generation system of direct fired type
CN102046929A (en) Integration of an air separation apparatus and of a steam reheating cycle
JP2022161839A (en) Combined cycle power plant having serial heat exchangers
RU2561770C2 (en) Operating method of combined-cycle plant

Legal Events

Date Code Title Description
A201 Request for examination
E902 Notification of reason for refusal
AMND Amendment
E601 Decision to refuse application
AMND Amendment
X701 Decision to grant (after re-examination)