JP5427506B2 - Intake humidity control apparatus for gas turbine, gas turbine and gas turbine combined cycle power plant including the same, and output increasing method - Google Patents

Description

  The present invention relates to an intake air humidity control device for a gas turbine, a gas turbine and a gas turbine combined cycle power plant including the same, and an output increasing method.

  2. Description of the Related Art Conventionally, in a power plant equipped with a gas turbine mainly composed of a compressor, a combustor, and a turbine, a gas turbine combined cycle (hereinafter referred to as “GTCC”) having exhaust heat utilization equipment utilizing exhaust heat exhausted from the turbine. The power plant is known. As a specific example, there is one that includes a boiler that uses exhaust heat of a gas turbine and a steam turbine that uses steam generated by the boiler. In this GTCC power generation plant, power generation can be performed by a steam turbine that uses exhaust heat of the turbine in addition to the gas turbine, so that the power generation efficiency can be improved as a whole.

  In such a GTCC power plant, the output is affected by the temperature of the intake air sucked into the compressor. That is, especially in the summer, the atmospheric temperature rises, so the density of the intake air decreases, the mass flow rate decreases, and the output decreases. In order to suppress such a decrease in output, some have a cooling device for cooling the intake air. By the way, when the intake air is cooled, when the temperature of the intake air becomes lower than the dew point temperature, water vapor in the intake air is condensed and mist is generated.

  In Patent Document 1 below, a corrosion resistant alloy is used for the moving blades, the stationary blades, and the like in order to prevent the moving blades, the stationary blades, etc. of the compressor from being damaged by the mist.

Japanese Patent Laid-Open No. 11-93692

  However, in the conventional technology, although a corrosion resistant alloy is used for the moving blade and the stationary blade, etc., there is a problem that the operation of the gas turbine becomes unstable only by delaying the progress of erosion.

  The present invention has been made in view of such circumstances, and the object thereof is to suppress damage to gas turbine components and to achieve stable operation of a gas turbine intake air humidity control apparatus, And it is providing the gas turbine provided with this, a gas turbine combined cycle power plant, and the output increase method.

In order to achieve the above object, the present invention employs the following means.
That is, an intake air humidity control apparatus for a gas turbine according to the present invention is an intake air humidity control apparatus for a gas turbine used in a gas turbine including a compressor, a combustor, and a turbine, and is sucked into the compressor from the outside. Provided in a suction flow path that is a flow path of the suction air , comprising moisture absorption means capable of absorbing moisture of the suction air and releasing the contained moisture to humidify the suction air , wherein the moisture absorption means includes a hygroscopic agent, A low moisture content hygroscopic reservoir that stores a relatively low moisture content hygroscopic agent among the hygroscopic agents, and a high moisture content hygroscopic agent that contains relatively high moisture content among the hygroscopic agents. a high water content desiccant reservoir which features a Rukoto which have a a spray unit for alternatively sprayed with the high moisture content desiccant and the low water content hygroscopic agent with respect to the suction air.
According to this configuration, there is provided a moisture absorbing means capable of absorbing moisture in the intake air and releasing the contained moisture to humidify the intake air. Therefore, when the humidity of the intake air is high and mist is generated, the mist is removed. Then, when the humidity of the intake air is low, the moisture contained in the intake air is released, and the intake air can be cooled by the latent heat of vaporization (heat of vaporization). Thereby, the mist which goes to the compressor inlet of a gas turbine can be removed, and the damage of the components of a gas turbine can be suppressed. Further, when the humidity of the intake air is low, the intake air can be further cooled to increase the mass flow rate, and the output of the gas turbine can be improved.
Thereby, a gas turbine and a gas turbine combined cycle power plant can be operated stably.

Further, moisture absorption means, the moisture absorbent, and low moisture containing desiccant reservoir, and a high water content desiccant reservoir, and a spraying unit, and the high water content desiccant and the low water content desiccant Since it has a spraying part that sprays alternatively, it is possible to switch between moisture absorption and humidification according to the humidity of the intake air by selecting and spraying a moisture absorbent with a low moisture content and a moisture absorbent with a high moisture content. it can.

Further, the high moisture content hygroscopic agent is formed by increasing the moisture content by absorbing the moisture of the suction air by the low moisture content hygroscopic agent dispersed in the suction flow path, the low moisture content hygroscopic agent is The high moisture content hygroscopic agent sprayed in the suction channel reduces the moisture content by releasing moisture into the suction air, and the moisture absorbing means absorbs the low moisture content moisture absorption from the suction channel. And a hygroscopic agent collecting mechanism for collecting the high moisture content hygroscopic agent from the suction flow path and sending it to the high moisture content hygroscopic agent storage unit. Features.
According to this configuration, the high moisture content hygroscopic agent absorbs moisture from the low moisture content hygroscopic agent, the low moisture content hygroscopic agent releases the moisture from the high moisture content hygroscopic agent, and the hygroscopic means absorbs the suction flow. Because it has a moisture absorbent recovery mechanism that collects the low moisture absorbent from the road and sends it to the moisture containing reservoir, and collects the high moisture absorbent from the suction channel and sends it to the moisture containing reservoir. A hygroscopic agent is circulated and used. Thereby, it is possible to improve the environmental performance without adding or discarding the hygroscopic material, and it is possible to save the use cost.

In addition, the moisture absorption means includes a drying device that releases the moisture contained by heating the moisture-absorbing agent containing low moisture with heat supplied from a heat source, and a water supply device that supplies moisture to the moisture-absorbing agent containing high moisture. And a moisture content adjusting device comprising:
According to this configuration, since the moisture content adjustment device including at least one of the drying device for drying the moisture content-absorbing agent and the water supply device for supplying moisture to the moisture content-containing moisture content is provided, a relatively wide range is provided. It becomes possible to respond more flexibly to intake air of temperature and a wide range of humidity.

Further, the drying device uses compressed air extracted from the compressor as a heat source.
According to this configuration, since the drying device uses the compressed air extracted from the compressor as a heat source, there is no need to add a new heat source, and maintenance and operation can be performed efficiently. In addition, energy efficiency is good.

Further, the drying device uses exhaust gas from the turbine as a heat source.
According to this configuration, since the drying device uses exhaust gas from the turbine as a heat source, energy efficiency is improved by effectively using the heat released to the outside.

In addition, the water adding device includes a water generator that cools water vapor generated by the drying device to generate fresh water, and supplies the fresh water to a high moisture content moisture absorbent.
According to this configuration, the water adding apparatus includes a condenser that cools water vapor generated when the low moisture content hygroscopic agent is heated by the drying device and generates fresh water, and supplies the fresh water to the high moisture content hygroscopic agent. Therefore, the water is circulated in the contained moisture adjusting device. Thereby, moisture added from the outside can be saved, and maintenance and operation can be performed efficiently.

In addition, a spray control unit that controls the spray unit based on the compressor inlet temperature of the intake air at the compressor inlet, the spray control unit, the compressor inlet temperature according to the required output of the gas turbine A required inlet temperature calculating unit for calculating the required inlet temperature, a dew point temperature calculating unit for calculating the dew point temperature of the intake air from the atmospheric humidity and the atmospheric temperature, and comparing the required inlet temperature and the dew point temperature. And an operation mode determination unit that determines that the low moisture content hygroscopic agent is sprayed when the required inlet temperature is lower than the dew point temperature.
According to this configuration, when the required inlet temperature is lower than the dew point temperature of the intake air, the spray control unit sprays the moisture-absorbing agent with a low moisture content on the intake air, so that the mist generated in the high-humidity intake air is removed. Remove and automatically absorb moisture.

In addition, a spray control unit that controls the spray unit based on the compressor inlet temperature of the intake air at the compressor inlet, the spray control unit, the compressor inlet temperature according to the required output of the gas turbine A required inlet temperature calculating unit for calculating the required inlet temperature, a dew point temperature calculating unit for calculating the dew point temperature of the intake air from the atmospheric humidity and the atmospheric temperature, and comparing the required inlet temperature and the dew point temperature. And an operation mode determination unit that determines to spray the high moisture-containing moisture absorbent when the required inlet temperature is higher than the dew point temperature.
According to this configuration, the spray control unit sprays the high moisture content moisture absorbent on condition that the required inlet temperature is higher than the dew point temperature, so the moisture content of the high moisture content moisture absorbent is automatically applied to the intake air. Can be released. Thereby, the low-humidity intake air can be automatically cooled.

Further, the spray control unit, based on the required inlet temperature calculated in the required inlet temperature calculating unit, a saturated water vapor pressure calculating unit that calculates a saturated water vapor pressure corresponding to the required inlet temperature, the atmospheric humidity Based on the atmospheric temperature, the atmospheric water vapor partial pressure calculating unit that calculates the water vapor partial pressure of the intake air, and based on the temperature of the high moisture-containing hygroscopic agent and the concentration of the high moisture-containing hygroscopic agent, A water vapor partial pressure on the solution surface that calculates a water vapor partial pressure on the surface of the moisture-containing hygroscopic agent, and the operation mode determination unit is configured such that the required inlet temperature is higher than the dew point temperature and the atmospheric temperature. Is higher than the required inlet temperature, the calculated water vapor partial pressure on the surface of the moisture-containing hygroscopic agent is smaller than the calculated saturated water vapor pressure, and the calculated water vapor content of the intake air. Than pressure Characterized in that for spraying the high water content desiccant is higher.
According to this configuration, the saturated water vapor pressure calculation unit, the atmospheric water vapor partial pressure calculation unit, and the solution surface water vapor partial pressure calculation unit, the operation mode determination unit is the calculated high moisture content moisture absorbent surface When the upper water vapor partial pressure is smaller than the calculated saturated water vapor pressure and higher than the calculated water vapor partial pressure of the intake air, the high moisture content moisture absorbent is sprayed. It becomes possible to spray a high moisture content hygroscopic agent. Thereby, suction air can be cooled and the output of a gas turbine can be improved effectively.

An intake air humidity control apparatus for a gas turbine according to the present invention is an intake air humidity control apparatus for a gas turbine used in a gas turbine including a compressor, a combustor, and a turbine, and is sucked into the compressor from the outside. Provided in a suction flow path, which is a flow path of suction air, includes moisture absorption means capable of absorbing moisture in the suction air and releasing the contained moisture to humidify the suction air, and the moisture absorption means is continuous in a circumferential shape. and a moisture absorber partially exposed to the suction passage with which, have a driving member for rotating the moisture absorber, the drive based on the compressor inlet temperature of the air sucked in the compressor inlet A drive control unit for driving and controlling the body, and a hygroscopic humidity measuring unit for measuring the humidity of the hygroscopic body, wherein the drive control unit is a request that is the compressor inlet temperature according to the required output of the gas turbine Inlet temperature and Is compared with the dew point temperature of the suction air, the request inlet temperature when it is lower than the dew point temperature is to expose a portion relatively low humidity of the moisture absorber to the suction passage Features.
According to this configuration, since the hygroscopic body that is continuous in a circumferential shape and part of the hygroscopic body is exposed to the suction flow path and the driving body that rotationally drives the hygroscopic body, the suction air has a relatively simple configuration. The humidity can be adjusted.

Further , the drive control unit compares the required inlet temperature with the dew point temperature of the intake air, and if the required inlet temperature is lower than the dew point temperature, a part of the hygroscopic body having relatively low humidity is sucked into the suction flow. Since it is exposed to the road, it is possible to automatically absorb moisture by removing mist generated in the high-humidity intake air with a relatively simple configuration.

In addition, a drive control unit that drives and controls the drive body based on a compressor inlet temperature of the intake air at the compressor inlet, and a moisture absorption body humidity measurement unit that measures the humidity of the moisture absorption body, the drive control unit includes: Further, on the condition that the required inlet temperature is higher than the dew point temperature, a part of the hygroscopic body having a relatively high humidity is exposed to the suction flow path.
According to this configuration, on the condition that the required inlet temperature is higher than the dew point temperature, a part of the hygroscopic body having a relatively high humidity is exposed to the suction flow path, so that it is automatically configured with a relatively simple configuration. In particular, the low-humidity intake air can be cooled.

The hygroscopic body is sheet-shaped.
According to this configuration, since the hygroscopic body is in the form of a sheet, a large surface area of the hygroscopic body can be ensured, and a part of the area exposed to the suction flow path can be kept small.

The hygroscopic body is disc-shaped.
According to this configuration, since the hygroscopic body has a disk shape, handling can be facilitated.

Further, a mist catcher is provided on the downstream side of the moisture absorbing means.
According to this configuration, since the mist catcher is provided on the downstream side of the moisture absorption means, it is possible to more reliably prevent the mist from being sucked into the gas turbine.

In addition, a gas turbine according to the present invention includes any one of the above-described gas turbine intake air humidity control apparatuses.
According to this configuration, since any one of the gas turbine intake air humidity control devices described above is provided, damage to the components of the gas turbine can be suppressed, and the output can be improved to achieve stable operation.

A gas turbine combined cycle power plant according to the present invention uses any one of the above-described gas turbine intake air humidity control devices, a gas turbine including a compressor, a combustor, and a turbine, and exhaust heat from the gas turbine. And waste heat utilization means.
According to this configuration, since any one of the gas turbine intake air humidity control devices described above is provided, damage to the components of the gas turbine can be suppressed, and the output can be improved to achieve stable operation.

The output increasing method according to the present invention is characterized in that any of the above-described gas turbine intake air cooling devices is additionally installed in an existing gas turbine or gas turbine combined cycle power plant.
According to this configuration, the plant output can be increased by relatively simple construction, and damage to the compressor due to mist can be prevented.

  According to the intake air humidity control apparatus for a gas turbine according to the present invention, it is possible to suppress damage to the components of the gas turbine and realize stable operation.

Moreover, according to the gas turbine which concerns on this invention, the damage of the components of a gas turbine is suppressed, and long life and stable operation | movement can be implement | achieved.
Further, according to the gas turbine combined cycle power plant according to the present invention, damage to the components of the gas turbine is suppressed, and stable power generation with a long life can be realized.
Further, according to the output increasing method according to the present invention, the plant output can be increased by relatively simple construction, and damage to the compressor due to mist can be prevented.

It is a schematic block diagram of GTCC power plant G1 concerning the embodiment of the present invention. It is a horizontal sectional view showing a schematic structure of the first heat exchanger 21 concerning the embodiment of the present invention. It is schematic structure sectional drawing of the 1st heat exchanger 21 which concerns on embodiment of this invention, Comprising: It is the II sectional view taken on the line in FIG. It is a block diagram which shows schematic structure of the cooling control part 24 of the intake-air-cooling apparatus 2 for gas turbines concerning embodiment of this invention. It is a figure which shows the criterion of the determination means 43 of the cooling control part 24 of the intake-air-cooling apparatus 2 for gas turbines which concerns on embodiment of this invention. It is a block diagram which shows schematic structure of the dispersion | distribution control part 60 of the intake-air humidity control apparatus 3 for gas turbines which concerns on embodiment of this invention. FIG. 3 is an explanatory diagram of the operation of the gas turbine intake air humidity control apparatus 3 according to the embodiment of the present invention, and is a diagram illustrating a relationship between the temperature T of the intake air A and the water vapor partial pressure Ps of the intake air A. In addition, the case of the operation mode which sprays the low moisture content hygroscopic agent 51a is shown. FIG. 3 is an explanatory diagram of the operation of the gas turbine intake air humidity control apparatus 3 according to the embodiment of the present invention, and is a diagram illustrating a relationship between the temperature T of the intake air A and the water vapor partial pressure Ps of the intake air A. In addition, it is the figure which showed the case of the operation mode which sprays the high moisture content moisture absorbent 51b. It is a schematic block diagram of GTCC power plant G2 which concerns on 2nd embodiment of this invention. It is a figure showing modification G2A of GTCC power plant G2 concerning a second embodiment of the present invention. It is a schematic block diagram of GTCC power plant G3 which concerns on 3rd embodiment of this invention. It is a schematic block diagram of GTCC power plant G4 which concerns on 4th embodiment of this invention.

Embodiments of the present invention will be described below with reference to the drawings.
FIG. 1 is a schematic configuration diagram of a GTCC power plant G1 according to an embodiment of the present invention. As shown in FIG. 1, the GTCC power plant G1 includes a power generation gas turbine 1, a gas turbine intake air cooling device 2, a gas turbine intake air humidity control device 3, a generator 4, a boiler, and a steam turbine. And a waste heat utilization means (not shown) schematically configured.

  The power generation gas turbine 1 compresses the intake air A sucked from the atmosphere (external air) into the compressor 1a, supplies the compressed air to the combustor 1b, and mixes it with the fuel F in the combustor 1b for combustion. Thus, by generating combustion gas and supplying it into the turbine 1c, it is possible to rotate the rotor 1d with a blade structure (not shown) and generate power with the generator 4. Further, the combustion gas flowing through the turbine 1c is supplied to exhaust heat utilization means (boiler, etc.) (not shown) as exhaust gas g1, and steam is generated using the exhaust heat.

The gas turbine intake air cooling device 2 includes a first heat exchanger (heat exchanger) 21, a refrigerator 22, a second heat exchanger 23, cold water C1, cooling water C2, a cooling control unit 24, A storage unit 25 (see FIG. 4), an atmospheric temperature measurement unit 26, and an atmospheric humidity measurement unit 27 are provided.
The 1st heat exchanger 21 is provided in the suction flow path from the exterior to the compressor 1a inlet, and heat-exchanges between the cold water C1 and the suction air A which flow through the inside. The heat received by the cold water C1 from the intake air A is released to the outside through the refrigerator 22, the cooling water C2, and the second heat exchanger 23.
Note that means other than the refrigerator 22 may be used as long as the intake air A can be cooled by the first heat exchanger 21.

2 is a horizontal sectional view showing a schematic configuration of the first heat exchanger 21, and FIG. 3 is a sectional view taken along the line II in FIG.
As shown in FIGS. 2 and 3, the first heat exchanger 21 includes a pipe line 31 that also serves as a suction flow path, a plurality of heat transfer pipes 32, and a drain 33.

  The pipe line 31 intersects the gravity direction with the gravity direction, and constitutes a suction flow path for the suction air A along a substantially horizontal direction. As shown in FIG. 1, the intake air A that has passed through the pipe line 31 is sucked into the compressor 1 a via the gas turbine intake humidity control device 3.

  As shown in FIG. 3, the heat transfer tube 32 is erected so as to penetrate the pipe line 31 vertically in the gravitational direction, and each axis is directed in the substantially gravitational direction.

As shown in FIG. 2, the plurality of heat transfer tubes 32 are arranged in a staggered manner in the horizontal direction in the flow path.
Specifically, some of the plurality of heat transfer tubes 32 are spaced apart in the flow channel width direction (direction intersecting the gravity direction and the airflow direction) (the gravity direction and the airflow direction). As shown in FIG. 3, four (35A to 35D) are superposed on the heat transfer tube stages 35 arranged in a row at intervals in the airflow direction. In each of the heat transfer tube stages 35A to 35D, as shown in FIG. 2, the distance L between the centers of the heat transfer tubes 32 adjacent to each other in the flow path width direction is not more than twice the outer diameter D of the heat transfer tube 32 (L ≦ 2D). ) Is set.
As shown in FIG. 2, the heat transfer tube stages 35 (35A to 35D) adjacent to each other in the airflow direction are arranged with a gap in the flow path width direction being shifted. More specifically, of the two heat transfer tube stages 35 (for example, 35A and 35B) adjacent to each other in the airflow direction, the center of the heat transfer tube 32 of the heat transfer tube stage 35 (for example, 35B) on the downstream side of the airflow is When viewed from the air flow direction, the heat transfer tube stage 35 (for example, 35A) on the upstream side of the air flow is located at the center of the interval between the heat transfer tubes 32 adjacent to each other in the flow path width direction (in other words, in the middle of the center-to-center distance L). It is arranged to do.

Further, the arrangement of the heat transfer tube stages 35A to 35D at each end in the flow path width direction is as shown in FIG. 2, where the wall surface distance from the heat transfer tube 32 to the flow wall 31a at each end is S. It is set as follows. First, the wall surface spacing S in the heat transfer tube stages 35A and 35C is set to be equal to or smaller than the outer diameter D of the heat transfer tube 32 (S ≦ D).
The wall surface spacing S between the heat transfer tube stages 35B and 35D is set to be much smaller than the outer diameter D (S << D).
Thus, in the two heat transfer tube stages 35 (35A to 35D) adjacent to each other in the airflow direction (for example, 35A and 35B), when viewed from the airflow direction, one of the heat transfer tube stages 35 (for example, 35B) A part of the outer peripheral surface of the heat transfer tube 32 at one end in the channel width direction is set so as to be positioned within the wall surface interval S of the other heat transfer tube stage 35 (for example, 35A).

  When such a plurality of heat transfer tubes 32 are set so that the cooling effect of the heat transfer tube 32 on the upstream side of the airflow is greater than that of the heat transfer tube 32 on the downstream side of the airflow, effective cooling is possible on the upstream side as viewed from the airflow direction. However, effective droplet recovery is performed on the downstream side, which is preferable. Specifically, the temperature of the cold water C1 flowing through each heat transfer tube 32 is set to the heat transfer tube stage 35A <35B <35C <35D. As another method for setting the heat transfer tube 32 on the upstream side of the air flow so that the cooling effect is larger than that on the heat transfer tube 32 on the downstream side of the air flow, cold water in the heat transfer tube 32 may be provided by a method such as providing an orifice at the heat transfer tube inlet. The flow rate of C1 may be the heat transfer tube stage 35A> 35B> 35C> 35D, or the surface roughness of the heat transfer tube 32 may be the heat transfer tube stage 35A> 35B> 35C> 35D.

  The drain 33 is provided in the lower part of the pipe line 31 on the downstream side of the heat transfer pipe stage 35D. A suction pump (not shown) is connected to the drain 33. In addition, the lower part of the pipe line 31 is inclined so as to gradually go downward from the upstream side of the heat transfer pipe stage 35 </ b> A toward the drain 33.

Returning to FIG. 1, the cooling control unit 24 of the gas turbine intake air cooling apparatus 2, a suction air A is cooled by the first heat exchanger 21 in accordance with the required output W _PR of power generation gas turbine 1. The cooling control unit 24 compares the dew point output W _PDT and the required output W _PR when the compressor inlet temperature T _IN of the intake air A at the inlet of the compressor 1a is operated at the dew point temperature T _d and the required output W _PR. in is large, balance associated with power generation on the basis of the set electricity price P _E is the condition that satisfies a predetermined criterion, the compressor inlet temperature T _iN to below the dew point temperature T _d.

FIG. 4 is a block diagram showing a schematic configuration of the cooling control unit 24 of the gas turbine intake air cooling device 2.
Cooling control unit 24, a required output _{W PR} and differential revenue calculation means 41 for calculating a difference income INC based on the difference output ΔW and electricity price _{P E} is the difference between the dew point output _{W PDT,} saturation dew point temperature _{T d} difference cost calculating means for calculating a fuel difference cost C _F is the fuel cost increment power generation gas turbine 1 when air is cooled to the required output W _PR is the compressor inlet temperature T _iN corresponding to the required inlet temperature T _PR 42, by comparing the difference revenue INC and the difference cost C _C, and a determination means 43 whether or not to below the dew point temperature T _d of the compressor inlet temperature T _iN.
In the present embodiment, of the difference cost C _C consisting of consumable costs and fuel differential cost C _F etc. of the blade or the like, and fiction fuel differential cost C _F occupying most as the difference cost C _C.

  The differential income calculation means 41 includes a dew point temperature calculation unit 41a, a dew point output calculation unit 41b, a differential output calculation unit 41c, a differential income calculation unit 41d, and a differential refrigeration power calculation unit 41e.

The dew point temperature calculation unit 41 a calculates the dew point temperature T _d from the atmospheric humidity φ input from the atmospheric humidity measurement unit 27 and the atmospheric temperature T _amb input from the atmospheric temperature measurement unit 26. The dew point temperature _Td may be obtained from the above-described NC diagram (for example, known in “How to read and use the thorough master air diagram”, edited by the Air Conditioning and Sanitation Engineering Society, 1998, pp16, etc.). Instead of the dew point temperature calculation unit 41a, a configuration in which the dew point thermometer is directly obtained may be used.

Dew point output calculation unit 41b calculates the dew point output W _PDT is output when the compressor inlet temperature T _IN from dew point temperature T _d calculated in dew point temperature calculating section 41a becomes dew point temperature T _d. Incidentally, correspondence between the dew point temperature _{T d} and dew point output _{W PDT,} for example, "Gas Turbine Theory 5th Edition" , Sarabanamuttoo, HIH, et al. , 2001 ", etc. Alternatively, it may be obtained from an experiment or a trial run.

Difference output calculation unit 41c, the operation and the dew point output _{W PDT} that is calculated on the dew point output calculation unit 41b, based on the required output _{W PR,} the difference output ΔW which is the difference between the dew point output _{W PDT} and the required output _{W PR} To do.

The difference income calculation unit 41d is a power price stored in advance in the storage unit 25 as a difference between the difference output ΔW calculated by the difference output calculation unit 41c and the power increment ΔW _IN calculated by the difference refrigeration power calculation means 41e. multiplied by the P _E, it calculates the difference between revenue INC.
The power price P _E, the more recent ones are preferred.

  The differential refrigeration power calculation means 41e includes a required inlet temperature calculation unit 41e1, a specific enthalpy difference calculation unit 41e2, a differential refrigeration capacity calculation unit 41e3, and a differential refrigeration power calculation unit 41e4.

Request inlet temperature calculation section 41e1 includes a required output W _PR which is input from the outside based on the operating time of the power demand, is stored in advance in the storage unit 25, the required output W compressor inlet temperature required to obtain a _PR T predetermined relationship with a _iN request inlet temperature _{T PR} and the required output _{W PR} (in Fig. 4 (1)) from, and calculates the required inlet temperature _{T PR.}
Here, the electric power demand includes electric power that can be sold. For example, when electric power can be sold by private power generation, the electric power that can be sold or the rest of the electric power sold to the customer by the electric power company In the case where power can be sold to other electric power companies, the electric power that can be sold to other electric power companies is included.
The predetermined relationship between the required output W _PR and the required inlet temperature T _PR is, for example, “Gas Turbine Theory 5th Edition”, Sarabanamuttoo, HIH, et al. , 2001 "etc. can be used.

The specific enthalpy difference calculation unit 41e2 calculates the dew point temperature T _d calculated by the dew point temperature calculation unit 41a from the atmospheric temperature T _amb input from the atmospheric temperature measurement unit 26 and the atmospheric humidity φ input from the atmospheric humidity measurement unit 27. and request the inlet temperature calculation unit NC diagram stored in advance in the storage unit 25 from the computed required inlet temperature T _PR to 41e1 (in FIG. 4 (2), as known above) based on the dew-point temperature T calculates the specific enthalpy difference Δh in the case of cooling _d of the saturated air to the required inlet temperature T _PR.

Differential cooling capacity calculating portion 41e3 calculates the difference refrigerating capacity ΔH obtained by the product of the flow rate G _IN of the computed specific enthalpy difference Δh and the suction air A to a specific enthalpy difference calculation section 41E2. As illustrated in FIG. 4, the flow rate G _IN of the intake air A may be obtained from the gas turbine control device 1 e, or a separate gas turbine intake air flow rate calculation unit may be provided so that the intake air from the compressor inlet temperature T _IN it may be configured for calculating the flow rate _{G iN} of a. In the case of providing a gas turbine intake flow rate calculation unit, for example, “Gas Turbine Theory 5th Edition”, Sarabanamuttoo, HIH, et al. , It can be calculated the flow rate _{G IN} of the suction air A using the method depicted in 2001 "or the like.

Difference refrigeration power calculating portion 41e4, based on the difference refrigerating capacity ΔH that is calculated on the difference refrigerating capacity calculating portion 41e3 and the COP of the refrigerator 22, and calculates the freezing mobility increment [Delta] W _IN. As shown in FIG. 4, the coefficient of performance COP of the refrigerator 22 may be provided from the refrigerator control device 22 a or may be provided from the storage unit 25.

The differential cost calculation means 42 includes a fuel differential cost calculation unit 42a.
Fuel difference cost calculation unit 42a includes a differential output ΔW that is calculated on the difference output calculation unit 41c, per unit calorific value stored in advance in the storage unit 25 the fuel price P _F and the power generation efficiency E _{G (in} FIG. 4 (3 )) And the fuel differential cost _CF is calculated. The power generation efficiency E _G, as illustrated in FIG. 4, may be configured to provide a gas turbine control device 1e.
Incidentally, the power generation efficiency E _G is a value obtained by dividing the fuel heating value to inject the output (W) of GTCC power plant G1 not deducted frozen mobility (Q).

FIG. 5 is a diagram illustrating the determination criteria of the determination unit 43.
The determination unit 43 determines whether or not the required output W _PR is larger than the dew point output W _PDT and the differential income INC is larger than the differential cost C _C (fuel differential cost C _F ).

Based on the determination result of the determination unit 43, the cooling control unit 24, when W _PR ≦ W _PDT , is (difference income INC−difference cost C _C ) ≦ 0 (balance is deficit or 0), and, (differential revenue INC- difference cost _C C)> 0 ... (balance black) at both time, without the suction air a to below the dew point temperature _{T d,} is operated at a dew point temperature _{T d} above.

Further, in the case of W _PR > W _PDT , when (difference income INC−difference cost C _C ) ≦ 0 (the balance is in red or 0), the intake air A is not made less than the dew point temperature T _d , and the dew point temperature T Drive at _d .
On the other hand, in the case of W _PR > W _PDT , when (difference income INC−difference cost C _C )> 0... (Balance is in black), the intake air A is cooled below the dew point temperature T _d .

Returning to FIG. 1, the gas turbine intake air conditioning device 3 is arranged between the gas turbine intake air cooling device 2 and the compressor 1 a in the suction flow path, and is sucked into the compressor 1 a. A moisture absorption means 50 capable of absorbing moisture in the air A and releasing the contained moisture to humidify the intake air A is provided.
The hygroscopic means 50 includes a hygroscopic agent 51, a low moisture content hygroscopic agent storage unit 52, a high moisture content hygroscopic agent storage unit 53, a spraying unit 54, and a spraying control unit 60.

As the hygroscopic agent 51, a liquid material such as a LiBr aqueous solution or a powder material such as a powdered silica gel can be used.
In this hygroscopic agent 51, a low moisture content hygroscopic agent 51a having a relatively small moisture content and a high moisture content hygroscopic agent 51b having a relatively large moisture content are separately stored.

  The low moisture content hygroscopic storage part 52 stores the low moisture content hygroscopic agent 51a. This low moisture content hygroscopic storage part 52 has a valve body 52a and a pipe line 52b for a funnel-shaped recovery hole (not shown) formed in the lower part of the suction flow path, and a valve body 52c and a pipe for a spray part 54. The paths 52d are connected to each other.

  The high moisture content hygroscopic storage part 53 stores the high moisture content hygroscopic agent 51 b having a relatively large moisture content in the hygroscopic agent 51. This high moisture content hygroscopic storage part 53 has a valve body 53a and a pipe line 53b for a funnel-shaped recovery hole (not shown) formed in the lower part of the suction flow path, and a valve body 53c and a pipe for a spray part 54. The paths 53d are connected to each other.

  The valve body 53a, the pipe line 53b, the valve body 52a, and the pipe line 52b described above constitute a hygroscopic agent recovery mechanism 55.

  The spraying part 54 is provided in the upper part of the suction flow path, and when the valve bodies 52c and 53c are selectively switched by the spraying control part 60, the low moisture content hygroscopic agent 51a and the high moisture content hygroscopic agent 51b are provided. Alternatively, select and spray toward the suction air A.

FIG. 6 is a block diagram showing a schematic configuration of the spray control unit 60 of the gas turbine intake humidity control apparatus 3.
The spraying control unit 60 switches and controls the spraying unit 54. Moreover, the dispersion | distribution control part 60 absorbs the water | moisture content of the suction air A, when the low moisture content hygroscopic agent 51a is sprayed, the high moisture content hygroscopic agent 51b which contained the increased moisture content is stored in the high moisture content hygroscopic agent storage part. 53. More specifically, the valve body 52a is closed, the valve body 53a is opened, and the high-moisture-containing moisture absorbent 51b accumulated in the lower part of the suction flow path is introduced into the pipe line 53b from a funnel-shaped recovery hole (not shown), The high moisture content hygroscopic agent storage unit 53 is introduced.

  On the other hand, when the high moisture content hygroscopic agent 51b is sprayed, the low moisture content hygroscopic agent 51a whose moisture content is reduced by releasing moisture into the suction air A is introduced into the low moisture content hygroscopic agent storage unit 52. More specifically, the valve body 52a is opened, the valve body 53a is closed, and the low moisture content hygroscopic agent 51a accumulated in the lower part of the suction flow path is introduced into the pipe line 52b from a funnel-shaped recovery hole (not shown), It introduces into the low moisture content hygroscopic storage part 52.

  The spray control unit 60 includes a required inlet temperature calculation unit 61, a dew point temperature calculation unit 62, a saturated water vapor pressure calculation unit 63, an atmospheric water vapor partial pressure calculation unit 64, a solution surface water vapor partial pressure calculation unit 65, And an operation mode determination unit 66.

Request inlet temperature calculation unit 61 requests the inlet temperature is the same configuration as the arithmetic unit 41e1, the required output W _PR inputted from the outside, pre stored in the storage unit 69 and the required output W _PR required inlet temperature T _{PR Is} calculated from the predetermined relationship ((1) in FIG. 6).
The required inlet temperature calculation unit (41e1, 61) is provided in each of the spraying control unit 60 and the cooling control unit 24. However, the required inlet temperature calculation unit (41e1, 61) is provided only in one side, the other is omitted, and the other is omitted. It is good also as a structure.

The dew point temperature calculation unit 62 includes an atmospheric temperature T _amb input from the atmospheric temperature measurement unit 56, an atmospheric humidity φ input from the atmospheric humidity measurement unit 57, and an NC diagram previously stored in the storage unit 69 (FIG. 6). The dew point temperature _Td of the intake air A is calculated from (2)).
Note that the same NC diagram as that stored in the storage unit 25 described above can be used.
In addition, the dew point temperature calculation unit (41a, 62) is configured to be provided in each of the spray control unit 60 and the cooling control unit 24. However, the dew point temperature calculation unit (41a, 62) is provided in only one and the other is omitted, and the other is omitted. It is good.

Saturated vapor pressure calculating unit 63, NC diagram stored in the storage unit 69 on the basis of the ((2) in FIG. 6), the suction air corresponding to the operation on the request inlet temperature calculation unit 61 requests the inlet temperature T _PR A saturated water vapor pressure E of A is calculated.

The atmospheric water vapor partial pressure calculation unit 64 is an NC diagram (in FIG. 6) stored in advance in the storage unit 69 and the atmospheric temperature T _amb and the atmospheric humidity φ input from the atmospheric temperature measurement unit 56 and the atmospheric humidity measurement unit 57. Based on (2)), the water vapor partial pressure PS _amb of the intake air A is calculated.

The solution surface water vapor partial pressure calculation unit (solution surface water vapor partial pressure calculation unit) 65 includes a hygroscopic agent temperature _{TL of} the high moisture-containing hygroscopic agent 51b input from the hygroscopic agent temperature measurement unit 68, and a hygroscopic agent concentration measurement unit. a moisture concentration _{X L} of the high water content desiccant 51b input from 67, pre-stored Duhring diagram in the storage unit 69 (((3) in FIG. 6)) (for example, "absorption chiller and heat pump" Takada fall one Author, 1989, Xing English Kasha, based on the p.10 "), and calculates the water vapor partial pressure PS _L on the surface of the high moisture content moisture absorbent 51b.

The operation mode determination unit 66 compares the required inlet temperature _TPR with the dew point temperature _Td, and in the operation mode in which the low moisture content hygroscopic agent 51a is sprayed when the required inlet temperature _TPR is lower than the dew point temperature _Td. Judge that there is.
Further, the operation mode determination unit 66 compares the required inlet temperature _TPR with the dew point temperature _Td, and when the required inlet temperature _TPR is higher than the dew point temperature _Td , the operation mode determination unit 66 is input from the atmospheric temperature measurement unit 56. when the atmospheric temperature _{T amb} ((6) in FIG. 6) is higher than the required inlet temperature _{T PR,} water vapor partial pressure PS _L on the calculated high water content desiccant 51b surface, the saturated vapor pressure calculating section 63 An operation mode in which the high moisture content moisture absorbent 51b is sprayed when it is smaller than the calculated saturated water vapor pressure E and higher than the calculated water vapor partial pressure PS _amb of the intake air A (E> PS _L > PS _amb ). It is determined that

Next, the operation of the GTCC power plant G1 having the above configuration will be described.
First, as shown in FIG. 6, the required inlet temperature calculation unit 61, a required output W _PR input, a request inlet temperature T _PR is the compressor inlet temperature T _IN necessary to obtain the required output W _PR From the predetermined relationship, the required inlet temperature _TPR is calculated.

Next, the dew point temperature calculation unit 62 includes the atmospheric temperature T _amb input from the atmospheric temperature measurement unit 56, the atmospheric humidity φ input from the atmospheric humidity measurement unit 57, and the NC diagram stored in the storage unit 69 in advance. The dew point temperature _Td is calculated from the above.

The operation mode determination unit 66 compares the calculated required inlet temperature _TPR with the calculated dew point temperature T _d, and if the required inlet temperature T _PR is lower than the dew point temperature T _d , that is, the intake air A When mist occurs, it is determined that the operation mode is to spray the moisture-absorbing agent 51a containing low moisture.

  When the operation mode determination unit 66 determines that the operation mode is to spray the low moisture content hygroscopic agent 51a, the spray control unit 60 opens the valve body 52c and opens the valve body 53c as shown in FIG. The low moisture content moisture absorbent 51a is sprayed from the spraying part 54 toward the suction air A. The sprayed low moisture content hygroscopic agent 51a becomes a high moisture content hygroscopic agent 51b by absorbing the mist of the suction air A, and accumulates in the lower part of the suction channel. The spraying control unit 60 closes the valve body 52a, opens the valve body 53a, and introduces the high-moisture-containing moisture absorbent 51b accumulated in the lower part of the suction passage into the pipe line 53b from a funnel-shaped recovery hole (not shown), The high moisture content hygroscopic agent storage unit 53 is introduced.

  FIG. 7 is a diagram showing the relationship between the temperature T of the intake air A and the water vapor partial pressure Ps of the intake air A, and is a diagram showing the case of the operation mode in which the low moisture content hygroscopic agent 51a is sprayed. In addition, the saturated vapor pressure line B1 and the water vapor partial pressure line B2 of the low moisture content hygroscopic agent 51a are shown on the graph.

  As shown in FIG. 7, when the intake air A at the temperature T1 is cooled by the gas turbine intake air cooling device 2, the water vapor partial pressure PS remains constant, and the temperature T2 decreases (plot (1) → plot (2 )). At this time, if the saturated vapor pressure line B1 is exceeded, moisture contained in the intake air A is condensed and mist is generated. When the moisture-absorbing agent 51a containing low moisture is sprayed on the intake air A, the mist of the intake air A is absorbed and the water vapor partial pressure Ps decreases at the temperature T2 (plot (2) → plot (3)). . Thus, the suction air A flows into the compressor 1a in a state where the water vapor partial pressure Ps is reduced and the mist is removed. Then, the gas turbine 1 is driven by the intake air A in which mist is not generated, and the erosion generated on the moving blades or the like due to this driving becomes very small. Further, since the intake air A is cooled to the temperature T2, the output of the gas turbine 1 is improved.

As shown in FIG. 6, the required inlet temperature calculation unit 61 continues to calculate the required inlet temperature _TPR , and the dew point temperature calculation unit 62 continues to calculate the dew point temperature T _d of the intake air A.

The operation mode determination unit 66 compares the calculated required inlet temperature _TPR with the calculated dew point temperature _Td, and when the required inlet temperature _TPR is higher than the dew point temperature _Td (that is, in the intake air A). In the case where no mist is generated), when the atmospheric temperature T _amb input by the atmospheric temperature measuring unit 56 is higher than the calculated required inlet temperature T _PR , is the operation mode for spraying the high moisture content hygroscopic agent 51b? Determine whether or not.
When the atmospheric temperature T _amb is lower than the required inlet temperature T _PR , the mass flow rate is not reduced and the required output of the gas turbine 1 is satisfied, so there is no need to cool the intake air A, It is not necessary to cool the intake air A by releasing the moisture of the high moisture content moisture absorbent 51b. For this reason, when the atmospheric temperature T _amb is equal to or lower than the required inlet temperature T _PR , the high moisture content hygroscopic agent 51 b is not sprayed on the intake air A.

The operation mode determination unit 66 determines whether or not the operation mode is the operation mode in which the high moisture content hygroscopic agent 51b is sprayed. The saturated water vapor pressure E and the water vapor partial pressure PS _amb of the intake air A and the high moisture content hygroscopic agent 51b are determined. determining based on the water vapor partial pressure PS _L on the surface. Saturated water vapor pressure E and water vapor partial pressure PS _amb of suction air A, water vapor partial pressure PS _L on the surface of the high moisture content moisture absorbent 51b is calculated as follows, are input to the operation mode determination unit 66 The

Saturated vapor pressure calculating unit 63, suction of the NC diagram previously stored in the storage unit 69, based on the request inlet requested is calculated on the temperature calculation section 61 inlet temperature T _PR, corresponding to the request inlet temperature T _PR The saturated water vapor pressure E of the air A is calculated.

The atmospheric water vapor partial pressure calculation unit 64 includes an atmospheric temperature T _amb input from the atmospheric temperature measurement unit 56, an atmospheric humidity φ input from the atmospheric humidity measurement unit 57, and an NC diagram stored in advance in the storage unit 69. Based on the above, an atmospheric water vapor partial pressure PS _amb is calculated.

The water vapor partial pressure calculation unit 65 on the solution surface includes the hygroscopic temperature _{TL of} the high moisture-containing hygroscopic agent 51b input from the hygroscopic agent temperature measurement unit 68 and the high moisture-containing hygroscopic agent input from the hygroscopic agent concentration measurement unit 67. 51b and desiccant concentration _{X L} of, based on the previously stored Duhring diagram in the storage unit 69, calculates a water vapor partial pressure PS _L on the surface of the high moisture content moisture absorbent 51b.

The operation mode determining section 66, when the atmospheric temperature T _amb is higher than the required inlet temperature T _PR, water vapor partial pressure PS _L on the calculated high water content desiccant 51b surface, than the calculated saturated water vapor pressure E _Is smaller and is higher than the calculated water vapor partial pressure PS _amb of the intake air A, it is determined that the operation mode is to spray the high moisture content hygroscopic agent 51b.
That is, in the range less than the saturated water vapor pressure E, if the water vapor partial pressure PS _L on a high water content desiccant 51b surface is higher than the water vapor partial pressure PS _amb suction air A, the high water content desiccant 51b The contained water is released to the suction air A, and the suction air A is cooled by the latent heat of vaporization (heat of vaporization).

  FIG. 8 is a diagram showing the relationship between the temperature T of the intake air A and the water vapor partial pressure Ps of the intake air A, and is a diagram showing the case of the operation mode in which the high moisture content hygroscopic agent 51b is sprayed. In addition, the saturated vapor pressure line B3 and the water vapor partial pressure line B4 of the high moisture content hygroscopic agent 51b are shown on the graph.

  As shown in FIG. 8, when the intake air A at the temperature T4 is cooled by the gas turbine intake air cooling device 2, the water vapor partial pressure remains constant and decreases to the temperature T5 (plot (4) → plot (5). ). When the high moisture content hygroscopic agent 51b is sprayed on the suction air A, the moisture content is released, and the vapor partial pressure Ps of the suction air A rises while decreasing from the temperature T5 to T6 due to latent heat of vaporization (plot). (5) → Plot (6)). Thus, the further cooled intake air A flows into the compressor 1a in a state where mist is not generated. And the output of GTCC power plant G1 increases by mass flow increasing.

The operation mode determining section 66, when the atmospheric temperature T _amb is higher than the required inlet temperature T _PR, water vapor partial pressure PS _L on the calculated high water content desiccant 51b surface, calculating the saturated vapor pressure calculating section 63 When it is smaller than the calculated saturated water vapor pressure E and higher than the calculated water vapor partial pressure PS _amb of the intake air A, it is determined that it is an operation mode in which the high moisture content moisture absorbent 51b is sprayed (E> PS _L > PS _amb ).
In the case that does not satisfy the above relationship, for example, if that is the relationship between the water vapor partial pressure PS _amb water vapor partial pressure PS L _<suction air A on the high water content desiccant 51b surface of the suction air A Since moisture is absorbed by the high moisture content hygroscopic agent 51b, the high moisture content hygroscopic agent 51b is not sprayed.

As described above, according to the first embodiment, since the moisture absorption means 50 capable of absorbing moisture of the intake air A and releasing the contained moisture to humidify the intake air A is provided, mist is contained in the intake air A. When it occurs, this mist can be absorbed, and when the humidity of the intake air A is low, the contained air is released to cool the intake air A. Thereby, the mist which goes to the compressor 1a inlet of the gas turbine 1 can be removed, and the damage of the components of the gas turbine 1 can be suppressed. Further, when the humidity of the intake air A is low, the intake air A can be further cooled to increase the mass flow rate, and the output of the gas turbine 1 can be improved.
Thereby, the gas turbine 1 and the GTCC power plant G1 can be operated stably.

  Further, the hygroscopic means 50 alternatively includes a hygroscopic agent 51, a low moisture content hygroscopic agent storage unit 52, a high moisture content hygroscopic agent storage unit 53, a low moisture content hygroscopic agent 51a, and a high moisture content hygroscopic agent 51b. Since the low-moisture-containing hygroscopic agent 51a and the high-moisture-containing hygroscopic agent 51b are selected and dispersed, operation is performed by switching between moisture absorption and humidification according to the humidity of the intake air A. Can do.

  Further, the high moisture content hygroscopic agent 51b absorbs moisture from the low moisture content hygroscopic agent 51a, the low moisture content hygroscopic agent 51a releases moisture from the high moisture content hygroscopic agent 51b, and the hygroscopic means 50 absorbs the moisture. Moisture absorption that collects the low moisture content hygroscopic agent 51 a from the flow path and sends it to the low moisture content hygroscopic storage unit 52, and collects the high moisture content hygroscopic agent 51 b from the suction flow channel and sends it to the high moisture content hygroscopic storage unit 53 Since the agent recovery mechanism 55 is provided, the hygroscopic agent 51 is circulated and used. Thereby, without adding or discarding the hygroscopic agent 51, it is possible to improve the environmental performance, and it is possible to save the use cost.

Moreover, spraying control unit 60, when the required inlet temperature T _PR is less than the dew point temperature T _d of the suction air A, since the sprayed low moisture containing desiccant 51a to the suction air A, generated in the suction air A Removes mist and automatically absorbs moisture.

Further, since the spray control unit 60 sprays the high moisture-containing moisture absorbent 51b on condition that the required inlet temperature _TPR is higher than the dew point temperature _Td , the moisture contained in the high moisture-containing moisture absorbent 51b is supplied to the suction air A. In contrast, it can be released automatically. Thereby, cooling of the suction air A can be performed automatically.

  In addition, since the spray control unit 60 includes the required inlet temperature calculation unit 61, the dew point temperature calculation unit 62, and the operation mode determination unit 66, it is possible to obtain a determination with relatively high reliability.

Moreover, it has a saturated water vapor pressure calculation unit 63, an atmospheric water vapor partial pressure calculation unit 64, and a water vapor partial pressure calculation unit 65 on the solution surface, and the operation mode determination unit 66 calculates the surface of the high moisture content moisture absorbent 51b. water vapor partial pressure PS _L above is smaller than the calculated saturated water vapor pressure E, and, since the sprayed high water content hygroscopic agent 51b is higher than the water vapor partial pressure PS _amb of the computed intake air a, Based on more accurate conditions, the high moisture content hygroscopic agent 51b can be sprayed. Thereby, since the suction air A is further cooled in a state where mist is not generated, the mass flow rate is increased and the output can be improved.

Furthermore, since the first heat exchanger 21 capable of cooling the intake air A includes a plurality of heat transfer tubes 32 and the plurality of heat transfer tubes 32 are arranged in a staggered manner, the intake air A is cooled below the dew point temperature _Td. In this case, the mist generated by being cooled by the heat transfer tube 32 located on the upstream side of the air flow adheres to the heat transfer tube 32 on the downstream side of the air flow and falls and is collected in the downward direction of the gravity. In addition, the plurality of heat transfer tubes 32 are disposed so that the cooling effect of the heat transfer tubes 32 positioned on the upstream side of the airflow is greater than that of the heat transfer tubes 32 positioned on the downstream side of the airflow. The generation of mist is relatively active in the heat transfer tubes 32, and the generation of mist is relatively suppressed in the heat transfer tubes 32 located on the downstream side of the airflow. Thereby, even if mist is generated with the cooling of the suction air A, the ratio of capturing the mist by the heat transfer pipe 32 itself that cools the suction air A increases, so that the mist flows downstream of the airflow. Can be deterred.
Therefore, it is possible to prevent the gas turbine 1 from sucking mist without adding another device on the flow path of the cooled intake air A.

Further, according to the GTCC power plant G1, the compressor output temperature T _IN is set on the condition that the required output W _PR is compared with the output at the dew point temperature T _d and that the balance due to power generation satisfies a predetermined standard. because it below the dew point temperature T _d, it is possible to prevent the compressor inlet temperature T _iN is the balance and independent below the dew point temperature T _d due to the power generation. As a result, the suction air A is limited to a temperature _lower than the dew point temperature _Td based on the balance of power generation, so that the suction air A can be efficiently cooled. In addition, when the balance due to power generation satisfies a predetermined standard, the intake air A is cooled to a temperature _lower than the dew point temperature _Td. It becomes possible.

  In addition, since the gas turbine intake humidity control device 3 is provided, damage to the components of the gas turbine 1 can be suppressed, and the output can be improved to achieve stable operation.

(Second embodiment)
FIG. 9 is a schematic configuration diagram of a GTCC power plant G2 according to the second embodiment of the present invention.
In FIG. 9, the same components as those in FIGS. 1 to 8 are denoted by the same reference numerals, and description thereof is omitted.

  As shown in FIG. 9, the GTCC power plant G2 includes a moisture content adjustment device 70 that includes a drying device 71 that dries the low moisture content hygroscopic agent 51a and a water addition device 72 that supplies moisture to the high moisture content hygroscopic agent 51b. The mist catcher 100 is provided.

  As shown in FIG. 9, the drying device 71 performs heat exchange with the exhaust gas g1 of the turbine 1c in the third heat exchanger 71a, and the heat received by the third heat exchanger 71a from the exhaust gas g1 is supplied to the heater 71b. It has come to be. The heater 71b is provided in the low moisture content hygroscopic reservoir 52 and heats the low moisture content hygroscopic agent 51a so that the low moisture content hygroscopic agent 51a has a predetermined concentration (content of moisture content).

  As shown in FIG. 9, the moisture content adjusting device 70 includes a condenser 73, generates fresh water from water vapor introduced from the low moisture content hygroscopic reservoir 52, and the high moisture content hygroscopic agent 51b is predetermined. The fresh water generated by using the water adding device 72 is supplied to the high moisture content hygroscopic agent storage unit 53 so that the concentration (content of moisture content) becomes. When the fresh water is insufficient, the water adding device 72 is supplemented with fresh water separately.

  The mist catcher 100 employs collision separation, and mechanically separates the mist from the intake air A. Instead of the mist catcher 100, a filter or the like may be used.

  According to the second embodiment, since the moisture content adjusting device 70 including the drying device 71 that dries the low moisture content hygroscopic agent 51a and the hydration device 72 that supplies moisture to the high moisture content hygroscopic agent 51b is provided. Therefore, it is possible to respond more flexibly to intake air in a wide range of temperature and humidity. For example, even if weather conditions with high humidity continue for a long time, it is possible to absorb moisture continuously by operating the drying device 71.

Further, since the drying device 71 uses the exhaust gas g1 from the turbine 1c as a heat source, the energy efficiency is improved by effectively using the heat released to the outside.
A part of the exhaust gas g1 from the turbine 1c may be used as the heat source, or the entire exhaust gas g1 may be used.
Further, the exhaust gas g1 after using exhaust heat in a boiler or the like may be used as a heat source, or may be steam from a boiler or steam turbine of exhaust heat utilization means.

  The moisture content adjusting device 70 includes a condenser 73 that cools (condenses) the water vapor generated by the drying device 71 to generate fresh water, and supplies the fresh water to the high moisture content moisture absorbent 51b using the water adding device 72. Therefore, the moisture is circulated in the contained moisture adjusting device 70. Thereby, the water | moisture content which adds a water | moisture content from the outside can be saved, and maintenance and operation can be performed efficiently.

  Further, since the mist catcher 100 is provided on the downstream side of the moisture absorbing means 50, it is possible to more reliably prevent the mist from being sucked into the gas turbine 1.

  As described above, it is desirable to provide both the drying device 71 and the water adding device 72 to adjust the humidity of the intake air A. However, only one of the drying device 71 and the water adding device 72 is provided to adjust the humidity. You may make it the structure to perform.

FIG. 10 is a diagram illustrating G2A, which is a modification of the GTCC power plant G2.
As shown in FIG. 10, the configuration of the third heat exchanger 71a performs heat exchange with the compressed air g2 extracted from the compressor 1a, and supplies the heat received from the compressed air g2 to the heater 71b. .

  According to this configuration, since the drying device 71 uses the compressed air g2 extracted from the compressor 1a as a heat source, there is no need to newly add a heat source, and maintenance and operation can be performed efficiently.

(Third embodiment)
FIG. 11 is a schematic configuration diagram of a GTCC power plant G3 according to the third embodiment of the present invention. In FIG. 11, the same components as those in FIGS. 1 to 10 are denoted by the same reference numerals, and description thereof is omitted.

As shown in FIG. 11, the GTCC power plant G <b> 3 includes moisture absorption means 80.
The moisture absorbing means 80 includes a sheet-like moisture absorbing body 81, a driving body 82 that drives the moisture absorbing body 81 with a roller, a moisture absorbing body humidity measuring unit 83, and a drive control unit 84 that controls the driving body 82. .

The hygroscopic body 81 is continuous in a circumferential shape and a part thereof is exposed to the suction flow path.
The driving body 82 is composed of a plurality of rollers, and a hygroscopic body 81 is wound around the driving body 82.
The moisture absorption body humidity measuring unit 83 is provided immediately before the moisture absorption body 81 is introduced into the suction flow path.

Drive control unit 84 has the same configuration as the cooling control unit 24 in the first embodiment described above, by comparing the required inlet temperature T _PR, and a dew point temperature T _d of the suction air A, required inlet temperature If T _PR is less than the dew point temperature T _d exposes a portion relatively low humidity of the moisture absorber 81 to the suction passage.
Conversely, on the condition that the required inlet temperature _TPR is higher than the dew point temperature _Td , a part of the hygroscopic body 81 having a relatively high humidity is exposed to the suction flow path.

  According to the third embodiment, since it has the hygroscopic body 81 that is continuous in a circumferential shape and part of the hygroscopic body 81 is exposed to the suction flow path, and the driving body 82 that rotationally drives the hygroscopic body 81, it is relatively simple. The humidity of the intake air A can be adjusted with a simple configuration.

The drive control unit 84 compares the dew-point temperature T _d of the requested inlet temperature T _PR and the suction air A, when the required inlet temperature T _PR is less than the dew point temperature T _d, of the moisture absorber 81 Since a part with relatively low humidity is exposed to the suction flow path, the mist generated in the suction air A can be automatically removed and absorbed by a relatively simple configuration.

Further, on the condition that the required inlet temperature _TPR is higher than the dew point temperature _Td , a part of the hygroscopic body 81 having a relatively high humidity is exposed to the suction flow path, so that it is automatically configured with a relatively simple configuration. Thus, the intake air A can be cooled.

  Moreover, since the moisture absorption body 81 is a sheet form, while being able to ensure the surface area of the moisture absorption body 81 large, the one part area exposed to a suction flow path can be restrained small.

(Fourth embodiment)
FIG. 12 is a schematic configuration diagram of a GTCC power plant G4 according to the fourth embodiment of the present invention.
In FIG. 12, the same components as those in FIGS. 1 to 11 are denoted by the same reference numerals, and description thereof is omitted.

As shown in FIG. 12, the GTCC power plant G <b> 4 includes moisture absorption means 90.
The moisture absorbing means 90 includes a disk-shaped moisture absorbing body 91, a driving body 92 that rotationally drives the moisture absorbing body 91, a moisture absorbing body humidity measuring section 83, and a drive control section 94 that controls the driving body 92. doing.

  According to the fourth embodiment, since the hygroscopic body 91 has a disk shape, handling can be facilitated.

Note that the operation procedure shown in the above-described embodiment, various shapes and combinations of the constituent members, and the like are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.
For example, all of the NC diagram data may be stored, or only the relationship between the temperature and the saturation pressure may be stored, and other data such as the dew point temperature _Td may be obtained each time by calculation. .
The data stored in the storage units 25 and 69 may be stored in advance, but may be directly input each time.

  Further, if the above-described gas turbine intake air cooling device 2 is additionally installed in an existing gas turbine or a gas turbine combined cycle power plant, the plant output can be increased by relatively simple construction, and the compressor is damaged by mist. Can be prevented.

DESCRIPTION OF SYMBOLS 1a ... Compressor 1b ... Combustor 1c ... Turbine 2 ... Intake air cooling device 3 for gas turbines ... Intake humidity control device 21 for gas turbines ... First heat exchanger (heat exchanger)
DESCRIPTION OF SYMBOLS 50 ... Hygroscopic means 51a ... Low moisture content hygroscopic agent 51b ... High moisture content hygroscopic agent 52 ... Low moisture content hygroscopic agent storage part 53 ... High moisture content hygroscopic agent storage part 54 ... Scattering part 55 ... Hygroscopic agent collection mechanism 60 ... Scattering control Unit 61 ... Required inlet temperature calculation unit 62 ... Dew point temperature calculation unit 63 ... Saturated water vapor pressure calculation unit 64 ... Atmospheric water vapor partial pressure calculation unit 65 ... On-solution water vapor partial pressure calculation unit 66 ... Operation mode determination unit 70 ... Contained water content adjustment Device 71 ... Drying device 72 ... Hydrating device 73 ... Condenser 80 ... Hygroscopic means 81 ... Hygroscopic body 82 ... Driver 83 ... Hygroscopic body humidity measuring unit 84 ... Drive control unit 90 ... Hygroscopic means 91 ... Hygroscopic body 92 ... Driver 94 ... drive control unit A ... air sucked E ... saturated vapor pressure G1, G2, G2A, G3, G4 ... power plant g1 ... exhaust gas 100 ... mist catcher PS L _... steam partial pressure _{T d} ... dew-point temperature T _{PR ...} request substitution Temperature T _{IN ...} compressor inlet temperature W _{PR ...} request output

Claims (17)

An intake air humidity control apparatus for a gas turbine that is used in a gas turbine including a compressor, a combustor, and a turbine, and is provided in a suction flow path that is a flow path of suction air that is sucked into the compressor from the outside. Comprising moisture absorption means capable of absorbing moisture in the intake air and releasing the contained moisture to humidify the intake air ;
The hygroscopic means includes a hygroscopic agent, a low-moisture-containing hygroscopic reservoir that stores the low-moisture-containing hygroscopic agent with relatively low moisture content in the hygroscopic agent, and the relative moisture content in the hygroscopic agent. A high moisture content hygroscopic reservoir for storing a high moisture content hygroscopic agent, and a spraying portion for alternatively spraying the low moisture content hygroscopic agent and the high moisture content hygroscopic agent to the intake air. An intake air humidity control apparatus for a gas turbine, comprising: The high moisture content hygroscopic agent, the low moisture content hygroscopic agent sprayed in the suction flow path, the moisture content is increased by absorbing the moisture of the suction air,
The low moisture content hygroscopic agent is formed by reducing the moisture content by releasing the moisture into the suction air by the high moisture content hygroscopic agent dispersed in the suction flow path,
The moisture absorbing means collects the low moisture content hygroscopic agent from the suction flow path and sends it to the low moisture hygroscopic storage section, and also collects the high moisture content moisture absorbent from the suction flow path to obtain the high moisture content. The intake air humidity control device for a gas turbine according to claim 1 , further comprising: a hygroscopic agent recovery mechanism that sends the hygroscopic agent storage unit. The moisture absorbing means includes at least one of a drying device that releases moisture by heating the low moisture content hygroscopic agent with heat supplied from a heat source, and a water supply device that supplies moisture to the high moisture content hygroscopic agent. The intake moisture conditioning apparatus for gas turbine according to claim 1, further comprising a moisture content adjustment apparatus having one of the two . The intake air humidity control apparatus for a gas turbine according to claim 3 , wherein the drying device uses compressed air extracted from the compressor as a heat source. The intake air humidity control apparatus for a gas turbine according to claim 3 or 4 , wherein the drying device uses exhaust gas from the turbine as a heat source. The spraying apparatus, the water vapor generated by the drying device is cooled on a water generator for generating fresh water, among claims 3 to 5, characterized in that to supply the fresh water to the high water content desiccant The intake air humidity control apparatus for gas turbines as described in any one of Claims. A spray control unit for controlling the spray unit based on a compressor inlet temperature of the suction air at the compressor inlet;
The spray control unit is a required inlet temperature calculation unit that calculates a required inlet temperature that is the compressor inlet temperature according to the required output of the gas turbine,
A dew point temperature calculation unit for calculating the dew point temperature of the intake air from the atmospheric humidity and the atmospheric temperature;
An operation mode determination unit that compares the required inlet temperature with the dew point temperature and determines to spray the low moisture content moisture absorbent when the required inlet temperature is lower than the dew point temperature, An intake air humidity control apparatus for a gas turbine according to any one of claims 1 to 6 . A spray control unit for controlling the spray unit based on a compressor inlet temperature of the suction air at the compressor inlet;
The spray control unit is a required inlet temperature calculation unit that calculates a required inlet temperature that is the compressor inlet temperature according to the required output of the gas turbine,
A dew point temperature calculation unit for calculating the dew point temperature of the intake air from the atmospheric humidity and the atmospheric temperature;
An operation mode determination unit that compares the required inlet temperature with the dew point temperature and determines to spray the high moisture-containing moisture absorbent when the required inlet temperature is higher than the dew point temperature, An intake air humidity control apparatus for a gas turbine according to any one of claims 1 to 7 . The spray control unit, based on the required inlet temperature calculated in the required inlet temperature calculating unit, a saturated water vapor pressure calculating unit that calculates a saturated water vapor pressure corresponding to the required inlet temperature,
Based on the atmospheric humidity and the atmospheric temperature, an atmospheric water vapor partial pressure calculation unit that calculates the water vapor partial pressure of the intake air;
Based on the temperature of the high moisture content hygroscopic agent and the concentration of the high moisture content hygroscopic agent, and having a water vapor partial pressure calculation unit on the solution surface for calculating the partial pressure of water vapor on the surface of the high moisture content hygroscopic agent,
The operation mode determination unit, when the required inlet temperature is higher than the dew point temperature, and the atmospheric temperature is higher than the required inlet temperature, the calculated partial pressure of water vapor on the high moisture-containing moisture absorbent surface but the smaller than the calculated saturated vapor pressure, and to claim 7 or 8, characterized in that for spraying the high water content desiccant is higher than the water vapor partial pressure of the computed intake air The intake air humidity control apparatus for a gas turbine as described. An intake air humidity control apparatus for a gas turbine that is used in a gas turbine including a compressor, a combustor, and a turbine, and is provided in a suction flow path that is a flow path of suction air that is sucked into the compressor from the outside. Comprising moisture absorption means capable of absorbing moisture in the intake air and releasing the contained moisture to humidify the intake air ;
The moisture absorbing means may possess a moisture absorption body part with contiguous circumferentially is exposed to the suction flow path, and a drive member for rotationally driving the moisture absorber,
A drive control unit that drives and controls the drive body based on a compressor inlet temperature of the intake air at the compressor inlet, and a hygroscopic humidity measurement unit that measures the humidity of the hygroscopic body,
The drive control unit compares the required inlet temperature, which is the compressor inlet temperature corresponding to the required output of the gas turbine, with the dew point temperature of the intake air, and the required inlet temperature is less than the dew point temperature. In the case, an intake air humidity control apparatus for a gas turbine , wherein a part of the moisture absorbing body having a relatively low humidity is exposed to the suction flow path . A drive control unit that drives and controls the driver based on a compressor inlet temperature of the suction air at the compressor inlet;
A hygroscopic humidity measuring unit for measuring the humidity of the hygroscopic body,
The said drive control part exposes a part with comparatively high humidity among the said moisture absorption bodies to the said suction flow path on condition that the said request | requirement inlet_port | entrance temperature is higher than the said dew point temperature. 10. An intake air humidity control apparatus for a gas turbine according to 10 . The intake air humidity control apparatus for a gas turbine according to claim 10 or 11 , wherein the hygroscopic body has a sheet shape. The intake air humidity control device for a gas turbine according to claim 10 or 11 , wherein the moisture absorber is disk-shaped. Gas turbine intake humidity control apparatus according to any one of claims 1 to 1 3, characterized in that it comprises a mist catcher to the downstream side of the moisture absorbing means. Gas turbine with an intake humidity control apparatus for a gas turbine as claimed in any one of claims 1 1 4. An intake humidity control apparatus for a gas turbine as claimed in any one of claims 1 1 4,
A gas turbine comprising a compressor, a combustor, and a turbine;
A gas turbine combined cycle power plant comprising exhaust heat utilization means for utilizing exhaust heat from the gas turbine. Power augmentation method of additionally provided an intake humidity control apparatus for a gas turbine according to any one of the existing gas turbine or gas turbine combined cycle power plant of claims 1 1 4.

Images