JP2016102415A - Turbine plant and intake air cooling method for turbine plant - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a turbine plant and an intake air cooling method for the turbine plant that enable improvement of air cooling efficiency.SOLUTION: A turbine plant includes: an air intake portion for sucking air from the atmosphere; a compressor for compressing the air sucked by the air intake portion to generate compressed air; a combustor for generating combustion gas by using the compressed air; a gas turbine for generating power by using the combustion gas; a steam turbine for generating power by using steam generate by using waste heat of the gas turbine; a cooling portion for cooling a bearing by circulating cooling oil in the bearing of the steam turbine; and an intake air cooling portion for cooling air by injecting mist generated by warming supply water upstream of the air intake portion. The intake air cooling portion includes a warming portion for warming supply water by using heat of at least one of the steam discharged from the steam turbine, the steam taken out from the steam generation portion, and the cooling portion.SELECTED DRAWING: Figure 2

Description

  The present invention relates to a turbine plant and a turbine plant intake air cooling method.

Combustion air supplied to the gas turbine is taken into the compressor of the gas turbine from the atmosphere through the intake duct. In such a compressor, in the summer when the outside air temperature rises, the mass of the air sucked into the compressor decreases as the air density decreases, and the compression ratio decreases.
Therefore, a technique for cooling combustion air by injecting mist to the intake side of the compressor is known (see, for example, Patent Document 1).

JP 2010-290443 A

  By the way, in the above-described technology for cooling the combustion air, it is desirable to improve the cooling efficiency of the intake air in order to realize a high compression ratio of the compressor. However, in the above prior art, the mist may not evaporate sufficiently in the air taken into the intake port from the atmosphere, and it is difficult to say that the cooling efficiency of the air is sufficient. Therefore, it is desired to provide a new technique for improving the air cooling efficiency.

  The present invention has been made in view of the above circumstances, and an object thereof is to provide a turbine plant and a turbine plant intake air cooling method capable of improving the cooling efficiency of air.

  The turbine plant of the present invention includes an intake section that sucks air from the atmosphere, a compressor that compresses the air sucked by the intake section and generates compressed air, and a combustion that generates combustion gas using the compressed air A cooling oil is circulated through a steam generator, a gas turbine that generates power by the combustion gas, a steam turbine that generates power by using steam generated by using exhaust heat of the gas turbine, and a bearing of the steam turbine A cooling unit that cools the bearing, and an intake cooling unit that cools the air by injecting mist generated by heating the feed water upstream of the intake unit. A heating unit that heats the feed water using heat of at least one of the steam discharged from the steam turbine, the steam taken out from the steam generation unit, and the cooling unit. And features.

According to the turbine plant of the present invention, mist having a small average particle diameter can be generated by heating the feed water in the heating section. As a result, the mist injected into the air can be reliably evaporated, and the cooling efficiency of the air can be improved by removing a large amount of latent heat of evaporation.
Moreover, since the heat of at least one of the steam turbine, the steam generation unit, and the cooling unit is effectively used as a heat source for the heating unit, a plant with high heat utilization efficiency is provided.

In the said turbine plant, it is preferable that the said heating part uses the exhaust heat of the said cooling oil whose temperature rose by cooling the said bearing. Furthermore, in the said turbine plant, it is desirable to further provide the heat exchange part which reduces the temperature of the said cooling oil by heat-exchanging the condensate from a condenser and the said cooling oil.
According to this configuration, since the temperature of the cooling oil is further reduced, the occurrence of seizure of the bearing can be prevented. In addition, since the condensate is preheated by the heat exchange unit, steam can be generated by efficiently recovering the exhaust heat of the cooling oil.

In the turbine plant, it is desirable that the heating unit is provided upstream of the heat exchange unit in the flow path of the cooling oil.
According to this structure, the heat of the comparatively high-temperature cooling oil before a heating part is used in a heat exchange part can be used. Therefore, water supply can be heated efficiently and mist can be generated.

In the turbine plant, it is preferable that the heating unit is provided downstream of the heat exchange unit in the flow path of the cooling oil.
According to this configuration, for example, even when the temperature of the cooling oil cannot be sufficiently reduced in the heat exchange unit, the heating unit uses the heat of the cooling oil, so the temperature of the cooling oil is reduced. It can be lowered sufficiently. Therefore, by preventing the bearing temperature from rising, it is possible to reliably prevent the bearing from being seized.

In the turbine plant, at least one of the steam discharged from the steam turbine and the steam taken out from the steam generation unit heats the feed water in the heating unit, and then cools the gas turbine. It is preferable to be used for.
According to this configuration, for example, a blade portion (a stationary blade or a moving blade) of a gas turbine that has reached a very high temperature can be efficiently cooled with steam that has been cooled by heating the feed water for generating mist. it can. Therefore, the product life of the gas turbine can be extended by reducing the load caused by the heat of the blades. In addition, the water supply for mist generation is heated and the steam temperature is lowered, so that it can be effectively used for cooling.

In the turbine plant, the steam turbine has a multistage structure including a high pressure turbine, an intermediate pressure turbine, and a low pressure turbine, and the heating unit uses the heat of the steam discharged from the high pressure turbine. It is preferable to warm the water supply. Furthermore, it is more preferable that the steam discharged from the high-pressure turbine and warming the feed water is supplied to the inlet of the intermediate-pressure turbine via the gas turbine.
If it does in this way, water supply can be heated efficiently using the exhaust heat of the steam turbine of a multistage structure. Mist can be generated by efficiently heating the feed water with relatively high-temperature steam discharged from the high-pressure turbine. Moreover, the steam which heated the water supply can be efficiently cooled by the temperature falling, and the temperature rises again by cooling the blade portion of the gas turbine. Therefore, the steam passing through the gas turbine is effectively used in an intermediate pressure turbine to which steam at a lower temperature and a lower pressure is supplied than the high pressure turbine.

In the turbine plant, the steam turbine has a multi-stage structure including a high pressure turbine, an intermediate pressure turbine, and a low pressure turbine, and the heating unit uses heat of the steam discharged from the intermediate pressure turbine. It is preferable to heat the water supply. Furthermore, it is more preferable that the steam discharged from the intermediate pressure turbine and warming the feed water is supplied to the inlet of the low pressure turbine via the gas turbine.
If it does in this way, using the exhaust heat of the steam turbine of a multistage structure, heating water can be heated efficiently and mist can be generated. In addition, mist can be generated by efficiently heating the feed water with relatively high-temperature steam discharged from the intermediate pressure turbine. The steam heated in the feed water can be efficiently cooled as the temperature decreases, and the temperature rises again as the blades of the gas turbine are cooled. Therefore, the steam that has passed through the gas turbine is effectively used in a low-pressure turbine that is supplied with steam at a lower temperature and lower pressure than the intermediate-pressure turbine.

  An intake air cooling method for a turbine plant according to the present invention includes an intake section that sucks air from the atmosphere, a compressor that compresses the air sucked in the intake section and generates compressed air, and combustion gas using the compressed air , A gas turbine that generates power by the combustion gas, a steam generation unit that generates steam using exhaust heat of the gas turbine, and power generated by the steam generated by the steam generation unit An intake air cooling method for a turbine plant including a generated steam turbine, the cooling oil cooling a steam turbine bearing upstream of the intake air, the steam discharged from the steam turbine, and the steam The air is cooled by injecting mist generated by water supply heated using at least one of the steam taken out from the generator. That.

According to the intake air cooling method for a turbine plant of the present invention, mist having a small average particle diameter can be generated by heating the feed water. As a result, the mist injected into the air can be reliably evaporated, and the cooling efficiency of the air can be improved by removing a large amount of latent heat of evaporation.
Moreover, since the heat of at least one of the steam turbine, the steam generation unit, and the cooling unit is effectively used as the heat source of the heating unit, the heat use efficiency in the plant can be improved.

  According to the present invention, the cooling efficiency of air can be improved.

The figure which shows schematic structure of the gas turbine plant which concerns on 1st Embodiment. The top view which shows schematic structure of the gas turbine plant which concerns on 1st Embodiment. The figure which showed notionally the simulation result of the flow of the air with respect to the intake-air-cooling-device air intake which concerns on 1st Embodiment. The top view which shows the arrangement | positioning relationship between the building for intake and the injection nozzle which concern on 1st Embodiment. The figure which shows notionally the flow of the mist injected by the injection nozzle which concerns on 1st Embodiment. The top view which shows the principal part structure of the intake air cooling device which concerns on 1st Embodiment. The top view which shows schematic structure of the gas turbine plant which concerns on 2nd Embodiment. The top view which shows schematic structure of the gas turbine plant which concerns on 3rd Embodiment. The top view which shows schematic structure of the gas turbine plant which concerns on 4th Embodiment.

  Hereinafter, an embodiment according to a gas turbine plant of the present invention and an intake air cooling method of the gas turbine plant will be described with reference to the drawings. Note that the dimensions, materials, shapes, relative arrangements, and the like of the components described in this embodiment are not intended to limit the scope of the present invention unless otherwise specified, but are merely illustrative examples. Only.

  In the following description, an XYZ orthogonal coordinate system is set, and the positional relationship of each member will be described with reference to this XYZ orthogonal coordinate system. The predetermined direction in the horizontal plane is the X-axis direction, the direction orthogonal to the X-axis direction in the horizontal plane is the Y-axis direction, and the direction orthogonal to each of the X-axis direction and the Y-axis direction (that is, the vertical direction) is the Z-axis direction. To do.

(First embodiment)
FIG. 1 is a diagram illustrating a schematic configuration of a turbine plant according to the first embodiment. FIG. 2 is a plan view showing a schematic configuration of the turbine plant according to the present embodiment.
As shown in FIG. 1, the turbine plant 1 is generated by a compressor 2 that generates compressed air, a combustor 3 that generates combustion gas using the compressed air generated by the compressor 2, and a combustor 3. A gas turbine 4 that generates power by rotating with the combustion gas, an intake air cooling device 10, an exhaust heat recovery boiler 6 that supplies hot water using the exhaust gas discharged from the gas turbine 4 (generates steam), and It has. As shown in FIG. 2, the turbine plant 1 of the present embodiment further includes a steam turbine 8, a cooling unit 50, and a condenser 51, and constitutes a combined cycle power plant.

  The gas turbine 4 is connected to a generator 5, and power generated in the gas turbine 4 is converted into electric power by the generator 5. The exhaust heat recovery boiler 6 and the gas turbine 4 are connected via an exhaust duct 7.

  The steam turbine 8 generates power by rotating with the steam generated by the exhaust heat recovery boiler 6. In the present embodiment, the steam turbine 8 is connected to the generator 5, and the power generated by the steam turbine 8 is converted into electric power by the generator 5.

  In the steam turbine 8, friction is generated between the roller 8 and the bearing 8a when the roller with the moving blade rotates. In the present embodiment, the cooling unit 50 cools the bearing 8 a by circulating cooling oil through the bearing 8 a of the steam turbine 8. The cooling unit 50 has a circulation path 53 constituted by a pipe through which cooling oil flows. Circulation path 53 includes a first heat radiating portion 53a and a second heat radiating portion 53b.

  The condenser 51 collects the steam that rotationally drives the steam turbine 8, condenses it, and returns it to water. In this embodiment, the condenser 51 is arrange | positioned, for example in seawater, and it returns to water by cooling a vapor | steam with seawater. The exhaust heat recovery boiler 6 and the condenser 51 are connected via a flow path 40. The flow path 40 includes a first flow path 40 a that supplies steam from the exhaust heat recovery boiler 6 via the steam turbine 8 to the condenser 51, and a second flow that supplies water condensed in the condenser 51 to the steam turbine 8. Road 40b. Based on such a configuration, the water condensed in the condenser 51 is circulated to the exhaust heat recovery boiler 6 and supplied again to the steam turbine 8 as steam.

In the present embodiment, the second flow path 40 b has a heat absorption part 55. The heat absorption part 55 receives heat by heat exchange with the second heat radiation part 53 b of the circulation path 53.
Based on such a configuration, in the present embodiment, the heat absorbing portion 55 and the second heat radiating portion 53 b constitute the condensate cooler 52. Here, the condensate cooler 52 constitutes a heat exchanger according to the claim that cools the cooling oil by exchanging heat between the condensate and the cooling oil.

  The intake air cooling device 10 communicates with the intake building (intake unit) 11 that takes in air from outside (in the atmosphere) and the intake building 11 and introduces the air taken in from the outside to the intake side of the compressor 2. A duct (duct) 12 and a plurality of injection nozzles 13 that are disposed upstream of the intake building 11 and inject mist are provided. The intake building 11 constitutes a part of the equipment of the turbine plant 1.

  The intake building 11 is a cubic building and has six wall surfaces. The intake building 11 has an intake surface for intake of outside air on three wall surfaces. In the present embodiment, the intake building 11 has an intake port forming region that forms an intake surface on a wall surface 11a on the upstream side of two surfaces parallel to the XZ plane and wall surfaces 11b and 11c that are two surfaces parallel to the ZY plane. 20 are provided. The intake port forming region 20 in each of the wall surfaces 11a, 11b, and 11c includes a plurality of intake unit A that is opened to the atmosphere. In this embodiment, each intake unit A is composed of, for example, four air intakes 21 and has a rectangular shape in plan view. Based on such a configuration, the air intake building 11 has an air intake chamber in which air is formed from the atmosphere through the air intake port forming region 20 (air intake port 21) formed in the three wall surfaces 11a, 11b, and 11c. 14 can be introduced. The flow passage cross-sectional area of the intake chamber 14 is larger than that of the intake duct 12.

  In the present embodiment, at least a part of the plurality of air intakes 21, for example, the louvers 22 defining the plurality of intake units A are formed on the wall surfaces 11 a, 11 b, 11 c of the intake building 11. Has been. The louver 22 is composed of a long plate-like member extending in the Z direction with respect to the wall surfaces 11a, 11b, and 11c. In the present embodiment, six louvers 22 are installed along the X direction on the wall surface 11a, and two louvers 22 are installed along the Y direction on the wall surfaces 11b and 11c. That is, in the present embodiment, the intake port forming region 20 in the wall surface 11 a is partitioned into seven regions by the louver 22, and the intake port forming region 20 in the wall surfaces 11 b and 11 c is partitioned into three regions by the louver 22. Has been. Three intake units A are arranged in each region defined by the louvers 22 in the intake port formation region 20 formed on the wall surfaces 11a, 11b, and 11c. The number of louvers 22 is appropriately set depending on the size of the intake building 11 and the size or number of the air intake 21 (intake unit A), and is not limited to the present embodiment.

  The louver 22 is for preventing rain and snow from entering the air intake 21 of the intake building 11 directly. As described above, the intake building 11 includes the louver 22 so that the air taken into the air intake 21 can be efficiently taken in. The louver 22 also functions as a capturing member that captures mist that is ejected from the ejection nozzle 13 and remains in the air as will be described later.

  The injection nozzle 13 is disposed around the intake building 11. The injection nozzle 13 injects, from the mist injection port 13a, mist M in the form of a mist of a liquid such as water into the air taken into the air intake 21.

  The injection nozzle 13 is connected to a pipe 15 for supplying the liquid that becomes the mist to be injected to the injection nozzle 13, and the liquid is discharged from the tank 17 by the pump 16 through the pipe 15. 13 is supplied. The injection nozzle 13 is installed at the predetermined position (a position outside the opening end of the air intake port 21a or a plane overlapping the intake port formation region 20) by being attached to the pipe 15. The pipe 15 may be fixed to a fixing member extending from the intake building 11 in a region not shown, or may be installed via a fixing member different from the intake building 11.

  Incidentally, in order to achieve a high compression ratio of the compressor 2 in the turbine plant 1, it is important to improve the cooling efficiency by the intake air cooling device 10. Here, the cooling efficiency of the intake air cooling device 10 is defined by the ratio of the amount of mist M that evaporates to the amount of mist M injected from the injection nozzle 13. That is, in order to improve the cooling efficiency by the intake air cooling device 10, it is necessary to increase the evaporation amount of the mist M injected from the injection nozzle 13.

In order to increase the evaporation amount of the mist M, the average particle diameter of the mist M is important. In order to increase the evaporation amount of the mist M, the present inventors paid attention to the boiling phenomenon at the time of phase change from liquid to gas in addition to considering the air flow to the air intake 21. When boiling occurs inside the liquid, bubbles rapidly grow and a force that breaks the liquid film acts to reduce the average particle diameter of the mist.
This phenomenon has been reported in the literature ("C203 Gas Turbine Increased Output System Using Solar Heat", Proceedings of 18th Power and Energy Technology Symposium (13.6.20, 21, Chiba), Japan Society of Mechanical Engineers (No.13-10), p. 299-300).

  In this embodiment, the structure including the heating part 9 which heats the water supply for the intake air cooling device 10 to generate the mist M is adopted. The intake air cooling device 10 normally injects mist generated by heating a water supply of about 6 Mpa and about 20 ° C. to about 60 ° C. to 80 ° C. by the heating unit 9. The mist generated by heating the feed water in this way undergoes boiling under reduced pressure. In addition, the viscosity coefficient of the mist M changes from before the heating (temperature, for example, 853 μPa · s at 27 ° C.) to after the heating (for example, 424 μPa · s at the temperature of 67 ° C.), and the surface tension before the heating (for example, Since the temperature is changed from 202.8 ° C. (72.8 dyne / cm) to after heating (for example, 60 ° C., 66.2 dyne / cm), the condition for reducing the average particle diameter of the mist is satisfied. Thus, in this embodiment, it is possible to generate and inject mist M having a small average particle diameter by heating.

  In the present embodiment, the heating unit 9 uses heat of the cooling oil that has cooled the bearing 8 a of the steam turbine 8 (exhaust heat of the cooling unit 50). The heating unit 9 includes a heat absorption unit 9a and a heat dissipation unit 9b. The heat absorption part 9a absorbs heat by exchanging heat directly or indirectly with the first heat radiation part 53a of the circulation path 53 through which the cooling oil that has become relatively high temperature by cooling the bearing 8a flows.

  The first heat radiating portion 53 a is provided on the upstream side of the condensate cooler 52 (heat absorbing portion 55) in the circulation path 53. Therefore, the heat absorption part 9a of the heating part 9 can efficiently absorb heat from the relatively high-temperature cooling oil immediately after being discharged from the bearing 8a.

  The heat radiating portion 9b thermally connected to the heat absorbing portion 9a supplies the heat absorbed by the heat absorbing portion 9a from the first heat radiating portion 53a (cooling oil) to the pipe 15. In the present embodiment, as described above, since heat is efficiently absorbed from the cooling oil in the heat absorbing section 9a, the liquid (water supply) in the pipe 15 is efficiently heated (heated) by the heating section 9.

  Furthermore, the present inventors paid attention to injecting mist in consideration of the flow of air to the air intake 21 in order to increase the evaporation amount of mist M. In the following description, the air intake 21 formed in the wall surface 11a will be described as an example, but similar simulation results are obtained for the air intake 21 formed in the wall surfaces 11b and 11c. Details are omitted.

  FIG. 3 is a diagram conceptually showing the simulation result of the air flow with respect to the air intake 21. FIG. 3 (a) shows the air with respect to the air intake 21 in the intake port formation region 20 formed on the wall surface 11a. FIG. 3B shows the air flow from the Z-axis direction to the air intake 21 of the intake port formation region 20 formed on the wall surface 11a. The simulation result when viewed is shown. In the following description, for the sake of convenience, the intake unit A arranged from the upper side to the lower side in the vertical direction (Z direction) of the intake port forming region 20 formed in the wall surface 11a is arranged in this order in the intake unit Az1, Az2, Az3. Sometimes called. In addition, the intake unit A arranged from one side (−X side) to the other side (+ X side) in the horizontal direction (X direction) of the intake port formation region 20 formed on the wall surface 11a in this order is Ax1, Ax2. , Sometimes referred to as Ax3.

  As shown in FIG. 3A, the intake unit Az <b> 1 (the air intake 21) disposed on the outer edge of the intake port formation region 20 in the vertical direction (+ Z direction) is Thus, it was confirmed that an air flow K1 was generated from the outside. Such an air flow K1 is considered to be caused by, for example, the air outside the intake building 11 flowing toward the air intake 21 having a relatively low pressure. On the other hand, a uniform air flow K2 is generated along the + Y direction in the intake units Az2 and Az3 installed separately from the intake unit Az1 arranged on the outer edge, that is, on the lower side in the vertical direction. It could be confirmed. Thus, it was confirmed that in the intake port formation region 20 formed on the wall surface 11a, different air flows K1 and K2 occur depending on the position of the intake unit A in the vertical direction.

  The same phenomenon occurs in the horizontal direction (X direction) of the intake port formation region 20. Specifically, as shown in FIG. 3 (b), the intake units Ax1 and Ax3 (air intake 21) arranged at both outer edges in the horizontal direction (X direction) of the intake port formation region 20 are also provided. It has been confirmed that the air flow K1 is generated from the outside. On the other hand, it was confirmed that a uniform air flow K2 along the + Y direction was generated in the intake unit Ax2 different from the intake unit Ax1.

  Therefore, for example, even if the intake unit Az1 injects mist from a position facing the intake unit Az1, the air containing the mist flows into the lower intake units Az2 and Az3 and enters the intake unit Az1. A sufficient amount of mist cannot be supplied to the air taken in.

  Further, for example, when the intake units Ax1 and Ax3 inject mist from a position facing the intake units Ax1 and Ax3, the air containing the mist flows into the central intake unit Ax2, and the intake unit Az1 Insufficient mist can be supplied to the air taken in.

  As described above, in the intake port formation region 20, the air flows K1 and K2 differ depending on the position of the intake unit A, so that the amount of mist injected into the air partially differs. Therefore, the air sucked into the intake port formation region 20 cannot be effectively cooled, resulting in a decrease in cooling efficiency. Note that this phenomenon is the same for the air intake ports 21 formed in the wall surfaces 11b and 11c, and the air flows K1 and K2 differ depending on the position of the intake unit A.

  In response to such a problem, the intake air cooling device 10 according to the present embodiment solves the above problem by adopting a configuration in which the injection nozzle 13 includes the first injection nozzle 13A and the second injection nozzle 13B. Yes.

FIG. 4 is a plan view showing an arrangement relationship between the intake building 11 and the injection nozzle 13 in the intake air cooling device 10 according to the present embodiment. FIG. 5 is a diagram conceptually showing the flow of mist injected by the injection nozzle 13. Specifically, FIG. 5A shows a simulation result when the flow of mist with respect to the air intake port 21 in the air inlet formation region 20 formed in the wall surface 11a is viewed from the X-axis direction. b) shows the simulation result when the flow of mist with respect to the air inlet 21 of the inlet port formation area 20 formed in the wall surface 11a is viewed from the Z-axis direction.
FIG. 4 shows an arrangement example of the wall surface 11 a and the injection nozzle 13. In the following description, the arrangement of the injection nozzle 13 with respect to the wall surface 11a will be described with reference to FIG. 4, but the arrangement of the injection nozzle 13 with respect to the wall surfaces 11b and 11c is also performed based on the same conditions as shown in FIG. The details are omitted here.

  As shown in FIG. 4, the first injection nozzle 13 </ b> A has an air intake port 21 a (the first intake port 21 a) corresponding to the outer edge portion of the intake port formation region 20 in a plan view of the intake building 11, that is, in a plan view of the wall surface 11 a. 1 intake port), that is, outside the opening end of the intake units Az1 and Ax1 including the air intake port 21a and upstream of the intake port formation region 20 (upstream side in the introduction direction of outside air). Has been. Note that the air intake port 21a corresponding to the outer edge portion of the intake port formation region 20 refers to the air intake port 21 in the region indicated by hatching in FIG. In the present embodiment, the first injection nozzle 13A is disposed outside the opening end of the air intake port 21a. However, the first injection nozzle 13A may be installed on the opening end.

  Further, the second injection nozzle 13B is a position that overlaps the intake port formation region 20 in a plan view of the wall surface 11a, and is upstream of the intake port formation region 20 (upstream side in the introduction direction of outside air). ). In this embodiment, the 2nd injection nozzle 13B is arrange | positioned in the position corresponding to the center part of the intake unit A, for example. Note that the number of the first injection nozzles 13A and the second injection nozzles 13B (hereinafter sometimes collectively referred to as nozzles 13A and 13B) is the diffusion range of the mist M injected from the nozzles 13A and 13B. It is preferable to determine in consideration. In the present embodiment, the nozzles 13A and 13B are arranged so that the mist injection port 13a is directed 180 degrees opposite to the intake direction (+ Y direction).

  In the present embodiment, the louver 22 is composed of a plate-like member having a plane parallel to the YZ plane. In addition, the plurality of nozzles 13A and 13B are installed in a plane parallel to the plane of the plate-like louver 22, for example. That is, the plurality of nozzles 13A and 13B are installed in a plane parallel to the YZ plane. The positional relationship between the nozzles 13A and 13B and the louver 22 is not limited to the above. For example, the nozzles 13 </ b> A and 13 </ b> B may be installed such that the mist injection port is located on a plane that intersects a plane parallel to the plane of the louver 22 (a plane parallel to the YZ plane). In this case, the injected mist M is diffused toward the louver 22 so that the mist M is easily attached to the louver 22. The mist M adhering to the louver 22 evaporates by touching the air that passes through the louvers 22 and is sucked into the air intake 21. Therefore, it is possible to cool the air taken into the air intake 21 more efficiently.

  As shown in FIGS. 5A and 5B, the mist M injected from the first injection nozzle 13A disposed outside the opening ends of the intake units Az1, Ax1, Ax3 As a result of being taken in well into the air of the flow K1 that is entrained from the outside of the air, it generally evaporates until it is drawn into the intake units Az1, Ax1, Ax3 (air intake 21). Thereby, the air taken into the inlet units Az1, Ax1, Ax3 is cooled by the latent heat of vaporization (heat of vaporization) when the mist M evaporates.

  On the other hand, as shown in FIGS. 5A and 5B, the mist M injected from the second injection nozzle 13B arranged at a position overlapping the intake port forming region 20 in a plane is one along the + Y direction. By being taken in well by such an air flow K2, it generally evaporates until it is sucked into the intake units Az2, Az3, Ax2 (air intake 21). Thereby, the air taken into the inlet units Az2, Az3, Ax2 is cooled by the latent heat of vaporization (heat of vaporization) when the mist M evaporates.

  As described above, according to the intake air cooling device 10 according to the present embodiment, even when the air flows K1 and K2 are different depending on the position of the air intake 21, the first injection nozzle 13A and the second injection nozzle 13B. By providing the injection nozzle 13 including the mist, it is possible to uniformly supply the mist throughout the air.

FIG. 6 is a plan view showing a main configuration of the intake air cooling device 10.
As shown in FIG. 6, the intake air cooling device 10 includes a filter member (capturing member) 18 provided in the intake chamber 14 (intake building 11) and a dust filter member 19.

  The filter member 18 is provided on the wall surface of the intake chamber 14 and captures the mist M ejected from the ejection nozzle 13 that does not adhere to the louver 22 and does not evaporate and flies with the air. It is for collecting. As the filter member 18, for example, a long fiber glass fiber pad is preferably used. According to this, it is possible to hold more mist M collected in the filter member 18 and cool the air more efficiently by evaporation of the mist M in the filter member 18. The filter member 18 may be a cooling medium used in a conventional evaporative cooler, and is not particularly limited.

  The dust filter member 19 is for removing dust in the air sucked from the intake chamber 14. The dust filter member 19 is preferably provided on the downstream side of the filter member 18. According to this, since the mist M can be captured by the filter member 18 before the mist reaches the dust filter member 19 for removing the dust, the dust collected when the dust filter member 19 is wet by the mist M is filmed. It is possible to prevent the occurrence of a problem that the pressure loss increases.

  As the dust filter member 19, for example, any of the following three types can be used. In the first type, one medium performance filter is provided. The second type includes an intermediate performance filter and an HEPA filter (High Efficiency Particulate Air filter) provided at a predetermined distance downstream from the intermediate performance filter. The third type is composed of a medium performance filter and a HEPA filter that is integrated with the medium performance filter on the downstream side of the medium performance filter without a predetermined distance.

  The filter member 18 may be composed of a plurality of (for example, two) members. In this case, one filter member 18 is installed in the intake chamber 14 on the upstream side of the dust filter member 19 and on the side close to the air intake 21 (hereinafter sometimes referred to as the upstream side). The filter member 18 may be installed in the intake chamber 14 on the upstream side of the dust filter member 19 and the side close to the dust filter member 19 (hereinafter sometimes referred to as the downstream side).

  Moreover, it is preferable that the filter member 18 installed on the upstream side is made of a filter medium having a coarser mesh than the filter member 18 arranged on the downstream side. In this way, for example, even if the mist M injected into the air does not adhere to the louver 22 and does not evaporate and enters the air intake 21, it remains in the air. The mist M having a relatively large particle diameter can be collected in advance by the upstream filter member 18, and the small mist M flying without being collected by the upstream filter member 18 is downstream. It is possible to reliably collect by the filter member 18 on the side. Therefore, it is possible to more reliably prevent a decrease in compression efficiency due to the mist M entering the compressor 2 side.

  Then, while describing operation | movement of the turbine plant 1 provided with the said structure, one Example of the intake-air cooling method of this invention is also demonstrated.

  The turbine plant 1 compresses the air taken in by the intake air cooling device 10 by the compressor 2, generates combustion gas by the combustor 3 using the compressed air generated by the compressor 2, and the combustor 3 The gas turbine 4 is rotated by the generated combustion gas. The generator 5 converts the power generated in the gas turbine 4 into electric power.

  The intake air cooling device 10 injects mist M into the atmosphere from the first injection nozzle 13A disposed outside the opening ends of the intake units Az1, Ax1, and Ax3. As a result, the mist M injected from the first injection nozzle 13 </ b> A advances downstream by being satisfactorily taken into the air of the flow K <b> 1 that is drawn from the outside of the intake port formation region 20.

  Further, the intake air cooling device 10 injects the mist M into the atmosphere from the second injection nozzle 13 </ b> B disposed at a position overlapping the intake port formation region 20 in a plane. As a result, the mist M injected from the second injection nozzle 13B advances downstream by being well taken into the air of the uniform flow K2.

  In this embodiment, as shown in FIG. 2, the average particle diameter of the mist M is reduced by heating the mist-generated water in the heating unit 9 (heat dissipating unit 9b). Therefore, the mist M taken into the air flow K1 is sufficiently evaporated until it is sucked into the intake units Az1, Ax1, Ax3 (air intake 21). Further, the mist M taken into the air of the uniform flow K2 is sufficiently evaporated before entering the air inlet 21 of the inlet units Az2, Az3, Ax2 (see FIG. 4). Therefore, a large amount of latent heat of evaporation is taken away from the air, and the cooling efficiency of the air can be improved.

  As described above, according to the present embodiment, the mist M is satisfactorily evaporated in the air that is sucked into the intake port formation region 20 and includes different flows K1 and K2. it can. Therefore, high cooling efficiency can be obtained by generating sufficient latent heat of vaporization in the entire air sucked from the plurality of air intake ports 21.

  The exhaust gas (exhaust gas) discharged from the gas turbine 4 is supplied to the exhaust heat recovery boiler 6 through the exhaust duct 7. The exhaust heat recovery boiler 6 uses the exhaust gas discharged from the gas turbine 4 to generate steam. The steam generated by the exhaust heat recovery boiler 6 is supplied to the steam turbine 8 via the flow path 40 (first flow path 40a). The steam turbine 8 generates power by rotating with the steam generated by the exhaust heat recovery boiler 6. The generator 5 converts the power generated in the steam turbine 8 into electric power.

  The steam that rotationally drives the steam turbine 8 is supplied to the condenser 51 through the flow path 40 (first flow path 40a). The condenser 51 condenses the recovered steam and returns it to water.

  In the present embodiment, the cooling oil and heat flowing through the second heat radiating portion 53b of the circulation path 53 in the condensate cooler 52 in which the water (condensate) condensed in the condenser 51 is provided in the middle of the second flow path 40b. Exchange. Specifically, the cooling oil flowing in the circulation path 53 is cooled and the temperature is lowered by the heat deprived to the heat absorbing portion 55 side in the second heat radiating portion 53b.

  In the present embodiment, the temperature of the cooling oil flowing through the circulation path 53 is lowered by the heat removal by the heating unit 9 (heat absorption unit 9a) in the first heat radiation unit 53a. Therefore, the circulation path 53 is cooled by radiating the cooling oil flowing through the first heat radiating portion 53a and the second heat radiating portion 53b in a stepwise manner. Accordingly, the steam turbine 8 is stably supplied with the cooling oil maintained at a low temperature with respect to the bearing 8a.

  On the other hand, the water (condensate) flowing in the second flow path 40b is heated by removing heat from the second heat radiating part 53b side in the heat absorbing part 55 (condensate cooler 52), and the temperature rises. Water (condensate) heated by the condensate cooler 52 is circulated to the exhaust heat recovery boiler 6 via the flow path 40 (second flow path 40b), and is again supplied to the steam turbine 8 as steam. . In the present embodiment, the water (condensate) preheated by the condensate cooler 52 is supplied to the exhaust heat recovery boiler 6 as described above. Therefore, the exhaust heat recovery boiler 6 can use relatively high-temperature water during steam generation, so that energy efficiency during steam generation can be improved.

  By the way, the temperature of the seawater in which the condenser 51 is arranged varies depending on the season. Especially in summer, the temperature of the seawater is high, so the temperature of the condensed water may be relatively high. If the water temperature after condensation becomes high, the condensate cooler 52 (heat absorption part 55) will not be able to absorb heat from the second heat radiation part 53b well. Then, relatively high-temperature cooling oil is supplied to the bearing 8a by the circulation path 53, and the bearing 8a is not sufficiently cooled and seizure occurs, which may cause malfunction of the steam turbine 8.

  On the other hand, in this embodiment, since the heating unit 9 (heat absorption unit 9a) absorbs heat from the cooling oil in advance as described above, the capacity of the condensate cooler 52 is insufficient, for example, in summer. Even in this case, it is possible to prevent the problem that the temperature of the cooling oil becomes high. Therefore, according to the present embodiment, since the cooling oil kept at a low temperature is stably supplied to the bearing 8a regardless of the season, the reliability that prevents the occurrence of malfunction such as seizure in the steam turbine 8 is prevented. A high plant can be provided.

  Further, according to the turbine plant 1 according to the present embodiment, in addition to the power generation by the gas turbine 4, the power generation by the steam turbine 8 rotated by the steam generated using the exhaust heat of the gas turbine 4 can be performed. A plant capable of combined cycle power generation with high energy efficiency can be provided.

  Further, since the intake air cooling device 10 includes the louver 22, it is possible to prevent rain, snow, or wind from directly entering the air intake 21. A part of the mist M ejected from the ejection nozzle 13 is captured by adhering to the louver 22. That is, the louver 22 functions as a capturing member that captures a part of the mist M. The mist M adhering to the louver 22 evaporates by touching the air that passes through the louvers 22 and is sucked into the air intake 21. Therefore, it is possible to cool the air taken into the air intake 21 more efficiently.

  Further, since the intake air cooling device 10 is provided with the filter member 18 on the downstream side of the injection nozzle 13, for example, the mist M injected into the air does not adhere to the louver 22 and does not evaporate. Even if it has entered the intake 21, the mist M remaining in the air can be captured by the filter member 18. Therefore, when the air passes through the filter member 18, the mist M captured by the filter member 18 is evaporated to increase the cooling efficiency of the air, while the mist M enters the compressor 2 side to reduce the compression efficiency. It is possible to prevent the occurrence of malfunctions such as.

  In addition, since the intake air cooling device 10 includes the dust filter member 19, it is possible to reliably remove the dust contained in the air sucked from the intake chamber 14. Therefore, it is possible to prevent a problem that the compression efficiency is reduced due to the dust being guided to the compressor 2 side.

  As described above, according to the turbine plant 1 according to the present embodiment, since the intake air cooling device 10 that injects the heated mist M is provided, the cooling efficiency of the air guided to the compressor 2 is improved. High output can be obtained.

(Second Embodiment)
Subsequently, a second embodiment of the present invention will be described. The difference between the present embodiment and the first embodiment is the structure of the cooling unit. Therefore, in the following, the configuration of the cooling unit will be mainly described, the same reference numerals are given to the same configurations and members as those in the above embodiment, and the detailed description thereof will be omitted or simplified.

  FIG. 7 is a plan view showing a schematic configuration of the turbine plant in the second embodiment. As shown in FIG. 7, the turbine plant 1 </ b> A according to the present embodiment includes a compressor 2, a combustor 3, a gas turbine 4, a steam turbine 8, a cooling unit 50, a condenser 51, and intake air cooling. This is a combined cycle power plant including the apparatus 10 and the exhaust heat recovery boiler 6.

  In the present embodiment, the first heat radiating portion 53 a is provided on the downstream side of the condensate cooler 52 (heat absorbing portion 55) in the circulation path 53. In this embodiment, the 2nd thermal radiation part 53b (condensate cooler 52) absorbs heat from the comparatively high temperature cooling oil immediately after discharged | emitted from the bearing 8a. The 1st thermal radiation part 53a supplies the heat | fever of the cooling oil after heat exchange with the condensate cooler 52 to the heating part 9 (heat absorption part 9a) side.

  According to this configuration, the temperature of the condensed water (condensate) becomes high due to the high seawater temperature as in summer, for example, and the temperature of the cooling oil cannot be sufficiently lowered by the condensate cooler 52. However, the heat of the cooling oil can be utilized by the heating unit 9 (heat absorption unit 9a). Thereby, even if it is a case where the capacity | capacitance of the condensate cooler 52 is insufficient like a summer, for example, generation | occurrence | production of the problem that the temperature of a cooling oil becomes high by the heating part 9 is prevented. Therefore, since the cooling oil kept at a low temperature is stably supplied to the bearing 8a regardless of the season, it is possible to provide a highly reliable plant that prevents the occurrence of malfunction such as seizure in the steam turbine 8. it can.

  According to the turbine plant 1A according to the present embodiment, in addition to the power generation by the gas turbine 4, the power generation by the steam turbine 8 rotated by the steam generated by using the exhaust heat of the gas turbine 4 can be performed. It is possible to provide a plant capable of high combined cycle power generation.

  Also in this embodiment, since the mist M having a small average particle diameter can be generated and injected by heating the feed water, the mist M injected into the air can be efficiently evaporated. Therefore, the air cooling efficiency can be further improved.

(Third embodiment)
Subsequently, a third embodiment of the present invention will be described. The difference between this embodiment and the said 1st, 2nd embodiment is the heat source of a heating part. Therefore, in the following, the configuration of the heating unit will be mainly described, the same reference numerals are given to the same configurations and members as those in the above embodiment, and the detailed description thereof will be omitted or simplified.

  FIG. 8 is a plan view showing a schematic configuration of the turbine plant in the third embodiment. As shown in FIG. 8, the turbine plant 1 </ b> B according to the present embodiment includes a compressor 2, a combustor 3, a gas turbine 4, a steam turbine 8, a condenser 51, an intake air cooling device 10, A combined cycle power plant including a heat recovery boiler 6.

  In the present embodiment, the steam turbine 8 includes a high-pressure turbine 80, an intermediate-pressure turbine 81, and a low-pressure turbine 82. The high-pressure turbine 80, the intermediate-pressure turbine 81, and the low-pressure turbine 82 are arranged in this order from the upstream side to the downstream side in the steam flow direction from the exhaust heat recovery boiler 6 side to the condenser 51 side.

  In the present embodiment, the exhaust heat recovery boiler 6 supplies steam to the high-pressure turbine 80, the intermediate-pressure turbine 81, and the low-pressure turbine 82, respectively. For example, the exhaust heat recovery boiler 6 supplies steam at 500 to 600 ° C. and 150 atm to the inlet 80 a of the high pressure turbine 80 through the high pressure channel 71, and steam at 300 to 400 ° C. and 100 atm through the medium pressure channel 72. The steam at 250 to 350 ° C. and 50 atm is supplied to the inlet 82 a of the low pressure turbine 82 through the low pressure flow path 73. As a result, the high-pressure turbine 80, the intermediate-pressure turbine 81, and the low-pressure turbine 82 each generate power. A part of the steam discharged from the outlet 80b of the high-pressure turbine 80 is returned to the exhaust heat recovery boiler 6 through the flow path 76, reheated, and then supplied to the steam turbine 8 side. Further, the steam discharged from the outlet 81 b of the intermediate pressure turbine 81 is supplied to the inlet 82 a of the low pressure turbine 82 by joining the low pressure passage 73.

  In the turbine plant 1B of the present embodiment, the combustion gas generated in the combustor 3 becomes very high temperature (for example, 1500 ° C.), so the blade portions (static blades and moving blades) of the gas turbine 4 are very high temperature. It becomes. For this reason, the blade parts (stator blades and moving blades) are consumed by being exposed to high heat, resulting in a shortened product life.

On the other hand, in the present embodiment, the blades (the stationary blades and the moving blades) are cooled using the heat of the steam discharged from the steam turbine 8. In the present embodiment, a part of the steam discharged from the outlet 80 b of the high pressure turbine 80 is supplied to the blade portion of the gas turbine 4 through the flow path 70. Here, the temperature of the steam discharged from the outlet 80b of the high-pressure turbine 80 is, for example, about 300 ° C to 400 ° C. The compressed air supplied into the turbine via the flow path 70 is sufficiently low in temperature as compared with the blade portion. Therefore, the steam exhausted from the outlet 80b can sufficiently cool the wing parts (the stationary blades and the moving blades).
Thereby, it is possible to extend the life of these products by reducing the load caused by the heat of the blade parts (stator blades and moving blades).

  Further, in the present embodiment, the heating unit 9 uses the heat of steam discharged from the outlet 80 b of the high-pressure turbine 80. The heating unit 9 includes a heat absorption unit 9a and a heat dissipation unit 9b. The heat absorption part 9a absorbs heat by exchanging heat directly or indirectly with the heat dissipation part 70a of the flow path 70 through which the steam discharged from the outlet 80b flows.

  The heat radiating part 9b thermally connected to the heat absorbing part 9a supplies the heat absorbed by the heat absorbing part 9a from the heat radiating part 70a (steam) to the pipe 15. In the present embodiment, as described above, since heat is efficiently absorbed from the cooling oil in the heat absorbing section 9a, the liquid (water supply) in the pipe 15 is efficiently heated (heated) by the heating section 9.

  In the present embodiment, the heat radiating portion 70 a is provided on the upstream side of the gas turbine 4 in the flow path 70. Therefore, the heat absorption part 9a of the heating part 9 can efficiently absorb heat from the steam at a relatively high temperature (about 300 ° C. to 400 ° C.) immediately after being discharged from the outlet 80b. The temperature of the steam is lowered by the heat absorption by the heat absorbing portion 9a. Therefore, since the flow path 70 supplies low temperature steam to the blade portion of the gas turbine 4, it is possible to further improve the cooling efficiency of the blade portion (the stationary blade and the moving blade).

  Here, the temperature of the steam discharged from the outlet 80 b of the high-pressure turbine 80 is lower than the initial temperature (300 ° C. to 400 ° C.) through the heating unit 9. However, the temperature of the steam that has absorbed heat by cooling the blades of the gas turbine 4 rises again. The flow path 70 supplies the steam that has passed through the heating unit 9 and the gas turbine 4 to the inlet 81 a of the intermediate pressure turbine 81. Specifically, the flow path 70 joins the intermediate pressure flow path 72 to supply the steam supplied from the exhaust heat recovery boiler 6 together with the steam that has passed through the gas turbine 4 to the inlet 81 a of the intermediate pressure turbine 81.

  As described above, according to the present embodiment, the steam discharged from the high-pressure turbine 80 is used for heating the feed water for generating mist by the heating unit 9 and cooling the blades of the gas turbine 4. The turbine 81 can be effectively used. Therefore, the steam turbine 8 can use the steam generated by the exhaust heat recovery boiler 6 without waste. That is, according to the turbine plant 1B of the present embodiment, high energy efficiency is provided.

  Then, operation | movement of the turbine plant 1B provided with the said structure is demonstrated. The exhaust gas (exhaust gas) discharged from the gas turbine 4 is supplied to the exhaust heat recovery boiler 6 through the exhaust duct 7. The exhaust heat recovery boiler 6 uses the exhaust gas discharged from the gas turbine 4 to generate steam. The steam generated by the exhaust heat recovery boiler 6 is supplied to the steam turbine 8 via the flow path 40 (first flow path 40a). The steam turbine 8 generates power by rotating with the steam generated by the exhaust heat recovery boiler 6. The generator 5 converts the power generated in the steam turbine 8 into electric power.

  Here, the steam discharged from the outlet 80b of the high-pressure turbine 80 of the steam turbine 8 is heated after supplying the water for mist generation by the heating unit 9 and cooling the blades of the gas turbine 4. By being supplied to the inlet 81a of the pressure turbine 81, it is reused.

  Moreover, the steam which rotationally driven the steam turbine 8 is supplied to the condenser 51 via the flow path 40 (1st flow path 40a). The condenser 51 condenses the recovered steam and returns it to water.

  As described above, according to the present embodiment, the heat of the steam discharged from the steam turbine 8 (high pressure turbine 80) is effectively used for heating the feed water for generating mist and extending the life of the blades of the gas turbine 4. Can be used. Further, since the steam discharged from the high-pressure turbine 80 is effectively used by the intermediate-pressure turbine 81, the steam generated by the exhaust heat recovery boiler 6 can be used without waste.

(Fourth embodiment)
Subsequently, a fourth embodiment of the present invention will be described. The difference between this embodiment and 3rd Embodiment is the position which takes out steam from a steam turbine, ie, the surrounding structure of a heating part. Therefore, in the following, the peripheral configuration of the heating unit will be mainly described, the same reference numerals are given to the same configurations and members as those in the above embodiment, and the detailed description thereof will be omitted or simplified.

  FIG. 9 is a plan view showing a schematic configuration of a turbine plant in the fourth embodiment. As shown in FIG. 9, the turbine plant 1 </ b> C according to the present embodiment includes a compressor 2, a combustor 3, a gas turbine 4, a steam turbine 8, a cooling unit 50, a condenser 51, and intake air cooling. This is a combined cycle power plant including the apparatus 10 and the exhaust heat recovery boiler 6.

  In the present embodiment, the steam discharged from the outlet 81 b of the intermediate pressure turbine 81 is supplied to the blade portion of the gas turbine 4 through the flow path 75. Here, the temperature of the steam discharged from the outlet 81 b of the intermediate pressure turbine 81 is, for example, about 250 ° C. to 300 ° C. The compressed air supplied into the turbine via the flow path 75 is sufficiently low in temperature as compared with the blade portion. For this reason, the steam discharged from the outlet 81b can sufficiently cool the wings (the stationary blades and the moving blades), and thus the life of the wings can be extended.

  In the present embodiment, the heating unit 9 uses the heat of the steam discharged from the outlet 81 b of the intermediate pressure turbine 81. The heat absorption part 9a of the heating part 9 absorbs heat by exchanging heat directly or indirectly with the heat radiation part 75a of the flow path 75 through which the steam discharged from the outlet 81b flows.

  In this embodiment, the heat absorption part 9a of the heating part 9 can efficiently absorb heat from the relatively high temperature (about 250 ° C. to 300 ° C.) steam discharged from the outlet 81b. The temperature of the steam is lowered by the heat absorption by the heat absorbing portion 9a. Therefore, since the flow path 75 supplies low-temperature steam to the blade portion of the gas turbine 4, the cooling efficiency of the blade portion (the stationary blade and the moving blade) can be further improved.

  Here, the temperature of the steam discharged from the outlet 81b of the intermediate pressure turbine 81 is lower than the initial temperature (250 ° C. to 300 ° C.) through the heating unit 9. However, the temperature of the steam that has absorbed heat by cooling the blades of the gas turbine 4 rises again. The flow path 75 supplies the steam that has passed through the heating unit 9 and the gas turbine 4 to the inlet 82 a of the low-pressure turbine 82. Specifically, the flow path 75 joins the low pressure flow path 73 that supplies the steam from the exhaust heat recovery boiler 6 to the inlet 82 a of the low pressure turbine 82.

  According to this configuration, the steam discharged from the intermediate pressure turbine 81 is used for heating the feed water for generating mist by the heating unit 9 and cooling the blades of the gas turbine 4, and then effectively used by the low pressure turbine 82. can do. Therefore, the steam turbine 8 can use the steam generated by the exhaust heat recovery boiler 6 without waste.

  As described above, also in the turbine plant 1C according to the present embodiment, the heat of steam discharged from the steam turbine 8 (intermediate pressure turbine 81) is effectively used as a heat source of the heating unit 9, so that heat utilization efficiency is high. Is provided.

  In addition, this invention is not limited to the said embodiment, In the range which does not deviate from the main point of invention, it can change suitably. For example, the heat source for heating the water supply for generating mist is not limited to the above embodiment, and a combination of the configurations of the embodiments may be adopted as the heat source for the heating unit. Moreover, you may make it heat the water supply for producing | generating mist M using the heat | fever of a boiler for hot water supply, or a heat pump apparatus. In particular, if the water supply for generating the mist M is heated using a heat pump device, the energy efficiency of the entire plant can be improved.

  Moreover, in the said embodiment, although the case where the louver 22 was comprised from the long plate-shaped member extended along a Z direction was mentioned as an example in the building 11 for intake, the shape of the louver 22 is not limited to this, For example, you may be comprised from the long plate-shaped member extended along an X direction or a Y direction. Further, the intake building 11 may not have the louver 22.

DESCRIPTION OF SYMBOLS 1,30 ... Turbine plant, 2 ... Compressor, 3 ... Combustor, 4 ... Gas turbine, 5 ... Generator, 6 ... Waste heat recovery boiler (exhaust heat recovery part), 8 ... Steam turbine, 9 ... Heating part , 7 ... Exhaust duct, 10 ... Intake cooling device (intake cooling part), 13 ... Injection nozzle, 21 ... Air intake (intake part), 50 ... Cooling part, 51 ... Condenser, 52 ... Condensate cooler (heat) Exchanger), M ... Mist.

Claims (11)

An air intake section for inhaling air from the atmosphere;
A compressor that compresses the air taken in by the intake section and generates compressed air;
A combustor that generates combustion gas using the compressed air;
A gas turbine that generates power by the combustion gas;
A steam turbine that generates power by steam generated using exhaust heat of the gas turbine;
A cooling section for cooling the bearing by circulating cooling oil to the bearing of the steam turbine;
An intake air cooling unit that cools the air by injecting mist generated by heating the water supply upstream of the intake unit, and
The intake air cooling unit includes a heating unit that heats the water supply using heat of at least one of the steam discharged from the steam turbine, the steam taken out from the steam generation unit, and the cooling unit. Turbine plant. The turbine plant according to claim 1, wherein the heating unit uses exhaust heat of the cooling oil whose temperature is increased by cooling the bearing. The turbine plant according to claim 2, further comprising a heat exchanging unit that lowers the temperature of the cooling oil by exchanging heat between the condensate from the condenser and the cooling oil. The turbine plant according to any one of claims 1 to 3, wherein the heating unit is provided upstream of the heat exchange unit in the flow path of the cooling oil. The turbine plant according to any one of claims 1 to 3, wherein the heating unit is provided downstream of the heat exchange unit in the cooling oil flow path. The at least one of the steam discharged from the steam turbine and the steam taken out from the steam generation unit is used for cooling the gas turbine after heating the water supply in the heating unit. The turbine plant as described in any one of -5. The steam turbine has a multi-stage structure including a high pressure turbine, a medium pressure turbine, and a low pressure turbine;
The turbine plant according to any one of claims 1 to 6, wherein the heating unit heats the water supply using heat of the steam discharged from the high-pressure turbine. The turbine plant according to claim 7, wherein the steam discharged from the high-pressure turbine and warming the feed water is supplied to an inlet of the intermediate-pressure turbine via the gas turbine. The steam turbine has a multi-stage structure including a high pressure turbine, a medium pressure turbine, and a low pressure turbine;
The turbine plant according to any one of claims 1 to 6, wherein the heating unit heats the water supply using heat of the steam discharged from the intermediate pressure turbine. The turbine plant according to claim 9, wherein the steam discharged from the intermediate pressure turbine and warming the feed water is supplied to an inlet of the low pressure turbine via the gas turbine. An air intake section that sucks air from the atmosphere, a compressor that compresses the air sucked by the air intake section and generates compressed air, a combustor that generates combustion gas using the compressed air, and the combustion gas A turbine plant comprising: a gas turbine that generates power; a steam generation unit that generates steam using exhaust heat of the gas turbine; and a steam turbine that generates power by the steam generated by the steam generation unit. An intake air cooling method,
On the upstream side of the intake section, water is heated using at least one of the cooling oil that has cooled the bearing of the steam turbine, the steam discharged from the steam turbine, and the steam taken out from the steam generation section. A method for cooling an intake air of a turbine plant, wherein the air is cooled by injecting mist generated by the above.

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