JP5473467B2 - Intake air cooling apparatus for gas turbine, gas turbine and gas turbine combined cycle power plant equipped with the same, and output increasing method - Google Patents

Description

  The present invention relates to an intake air cooling 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 technique, since the intake air is simply cooled, there is a problem that the refrigeration power is consumed to remove the latent heat of condensation caused by the generation of mist, resulting in inefficient operation. Further, since the generated mist may damage each component such as a moving blade and a stationary blade of the compressor, there is a problem that it is inefficient in terms of the number of service life.
On the other hand, if cooling of the intake air is uniformly restricted with priority given to efficient operation, there is a problem that a situation in which the demand for electric power cannot be met occurs.

  The present invention has been made in view of such circumstances, and an object of the present invention is to efficiently cool the intake air and appropriately meet the demand for electric power, An object of the present invention is to provide a gas turbine, a gas turbine combined cycle power plant, and a method for increasing output.

In order to achieve the above object, the present invention employs the following means.
That is, the gas turbine intake air cooling device according to the present invention is a gas turbine intake air cooling device used in a power generation gas turbine including a compressor, a combustor, and a turbine, and is sucked into the compressor from the outside. A heat exchanging means capable of cooling the intake air; and a cooling control section that cools the intake air by the heat exchanging means in accordance with a required output of the power generation gas turbine, the cooling control section including the compressor inlet The dew point output when the intake air compressor inlet temperature is operated at the dew point temperature is compared with the required output, and when the required output is large, the balance of power generation based on the set power price is predetermined. The compressor inlet temperature is set to be lower than the dew point temperature on condition that the above standard is satisfied.
According to this configuration, the compressor output temperature is made lower than the dew point temperature on the condition that the required output and the dew point output are compared and the balance due to power generation satisfies a predetermined standard. The dew point temperature can be avoided regardless of the balance associated with Thereby, since intake air is made into less than dew point temperature limitedly based on the balance accompanying electric power generation, intake air can be cooled economically. In addition, when the balance due to power generation satisfies a predetermined standard, the intake air is cooled below the dew point temperature, so that operation with a large output is not uniformly prohibited, and it is possible to appropriately respond to power demand. .
Accordingly, the intake air can be economically cooled and appropriately meet the power demand.

In the gas turbine intake air cooling device according to the present invention, the cooling control unit calculates a differential income based on a differential output that is a difference between the required output and the dew point output and the power price. And a difference cost calculation means for calculating a difference cost including a fuel difference cost according to the difference output, and whether the difference income and the difference cost are compared to make the compressor inlet temperature less than the dew point temperature. Determination means for determining whether or not.
According to this configuration, the difference income calculation means, the difference cost calculation means, and the determination means are provided, and the difference income and the difference cost are compared to determine whether or not the compressor inlet temperature is made lower than the dew point temperature. Therefore, it is possible to accurately determine the balance of power generation from the differential income and the differential cost, and to operate economically.

In the gas turbine intake air cooling device according to the present invention, the differential income calculating means calculates a dew point temperature calculating unit for obtaining the dew point temperature based on the temperature and humidity of external air, and calculates the dew point temperature calculating unit. A dew point output calculation unit for obtaining the dew point output based on the dew point temperature, and a difference output calculation for calculating the difference output based on the dew point output and the requested output calculated by the dew point output calculation unit. parts and the difference refrigeration power calculating means for calculating a difference refrigerating power which is required for cooling the intake air to the dew point temperature or RaKaname determined inlet temperature, and computed the difference output to said differential output calculation unit And a differential income calculating unit that calculates the differential income based on the differential refrigeration power calculated by the differential refrigeration power calculating means and the power price.
According to this configuration, since the dew point output calculation unit, the differential refrigeration power calculation unit, and the differential income calculation unit are provided, it is possible to relatively predict the reliability based on the temperature and humidity of the external air, the differential output, and the power price. It is possible to obtain differential income with high characteristics.

In the gas turbine intake air cooling apparatus according to the present invention, the differential cost calculation means calculates the fuel differential cost based on the differential output, the fuel price per unit calorific value, and the power generation efficiency. An arithmetic unit is provided.
According to this configuration, it is possible to obtain a fuel differential cost with relatively high prediction reliability based on the differential output, the fuel price per unit calorific value, and the power generation efficiency.

The gas turbine intake air cooling apparatus according to the present invention, the difference refrigeration power calculating means, before Symbol required inlet temperature and the based on the dew point temperature, calculates the specific enthalpy difference of specific enthalpy difference calculation section, the A differential refrigeration capacity calculation section that calculates a differential refrigeration capacity from the specific enthalpy difference calculated by the specific enthalpy difference calculation section and the flow rate of the intake air, the differential refrigeration capacity calculated by the differential refrigeration capacity calculation section, and the suction And a differential refrigeration power calculation unit that calculates the differential refrigeration power based on a coefficient of performance of a refrigerator that supplies cold water that performs heat exchange to the air to the heat exchange means.
According to this configuration, the specific enthalpy difference is obtained based on the required inlet temperature and the dew point temperature, the differential refrigeration capacity is obtained from the specific enthalpy difference and the flow rate of the intake air, and the differential refrigeration capacity and the coefficient of performance of the refrigerator are obtained. Based on the above, the differential refrigeration power with relatively high prediction reliability can be obtained.

Further, in the gas turbine intake air cooling device according to the present invention, the cooling control unit determines that the determination unit has the required output larger than the dew point output and the differential income larger than the differential cost. In this case, the compressor inlet temperature is made lower than the dew point temperature.
According to this configuration, when the cooling control unit determines that the required output is larger than the dew point output and the difference income is larger than the differential cost, the compressor inlet temperature is made lower than the dew point temperature. Therefore, since the intake air is limited to a temperature lower than the dew point temperature when the balance is in the black, it is possible to appropriately respond to the power demand by performing the high output operation only when the profit can be obtained.
Therefore, it is possible to economically operate and appropriately meet the power demand.

In addition, a gas turbine according to the present invention includes any one of the above-described gas turbine intake air cooling devices.
According to this configuration, since any one of the above-described gas turbine intake air cooling devices is provided, it is possible to maintain power generation output at high temperatures and economically generate power and appropriately meet power demand.

In addition, a gas turbine combined cycle power plant according to the present invention includes any one of the above-described gas turbine intake air cooling devices, a power generation gas turbine including a compressor, a combustor, and a turbine, and exhaust heat from the gas turbine. The exhaust heat utilization means to be used is provided.
According to this configuration, since any one of the above gas turbine intake air cooling devices and the power generation gas turbine is provided, it is possible to generate power economically and appropriately meet the power demand.

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, it is possible to economically operate the existing power generation gas turbine, appropriately meet the power demand, and easily increase the output.

According to the gas turbine intake air cooling device of the present invention, it is possible to economically operate and appropriately meet the power demand.
Moreover, according to the gas turbine for power generation which concerns on this invention, it can respond to an electric power demand appropriately while producing electric power economically.
Moreover, according to the gas turbine combined cycle power plant concerning this invention, while being able to generate electric power economically, it can respond to an electric power demand appropriately.
Moreover, according to the reconstruction method of the existing gas turbine plant which concerns on this invention, while being able to generate electric power economically, it can respond to an electric power demand appropriately.

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.

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 exchange means) 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 T _d may be obtained from an NC diagram (for example, “known in“ How to read and use a thorough master air diagram ”, edited by the Air Conditioning and Sanitation Engineering Society, 1998, pp16, etc.). It is good also as a structure calculated | required directly from a dew point thermometer instead of the temperature calculating part 41a.

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 on-solution water vapor partial pressure calculating unit (humectant water vapor partial pressure calculating unit) 65 receives the hygroscopic agent temperature _{TL of} the high moisture-containing hygroscopic agent 51b input from the hygroscopic agent temperature measuring unit 68 and the hygroscopic agent concentration measuring unit 67. high and moisture concentration _{X L} of water containing desiccant 51b, prestored Duhring diagram in the storage unit 69 that is input from (((3) in FIG. 6)) (for example, "absorption chiller and heat pump", Takada fall one Author, 1989, Xing English Kasha, p.10 ") and on the basis, 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. 4, the required inlet temperature calculation unit 41 e 1 receives the input required output W _PR and the required inlet temperature T _PR that is the compressor inlet temperature T _IN necessary to obtain the required output W _PR. From the predetermined relationship ((1) in FIG. 4), the required inlet temperature _TPR is calculated.

Next, the specific enthalpy difference calculating unit 41e2 calculates the dew point temperature T calculated by the dew point temperature calculating unit 41a based on the input atmospheric humidity φ, the atmospheric temperature T _amb, and the NC diagram stored in the storage unit 25 in advance. _The specific enthalpy difference Δh is calculated based on _d , the required inlet temperature _TPR, and the NC diagram ((2) in FIG. 4) stored in the storage unit 25 in advance.

Next, the differential refrigeration capacity calculation unit 41e3 calculates the differential refrigeration capacity ΔH from the calculated specific enthalpy difference Δh and the flow rate G _IN of the intake air A given from the gas turbine control device 1e.

The differential refrigeration power calculating portion 41e4 has a differential refrigerating capacity ΔH that is calculated, based on the coefficient of performance COP given from the refrigerator control unit 22a, it calculates a difference refrigerating power increment [Delta] W _IN.

On the other hand, the dew point temperature calculation unit 41 a calculates the dew point temperature T _d calculated 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 calculated by the dew point temperature calculation unit 41a is supplied to the specific enthalpy difference calculation unit 41e2 as described above.

Then, the 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 .

Next, the difference output calculation unit 41c, based on the dew point output W _PDT calculated by the dew point output calculation unit 41b and the request output W _PR input from the outside based on the power demand during operation, the dew point output W P It calculates a difference output ΔW of the _PDT and the required output _{W PR.} The difference output ΔW is supplied to the difference income calculation unit 41d and the fuel difference cost calculation unit 42a.

Difference income calculation unit 41d includes a differential output [Delta] W that is calculated on the difference output computing section 41c, the difference between the calculated difference frozen power [Delta] W _IN to differential cooling capacity calculation unit 41E3, which is previously stored in the storage unit 25 multiplied by the power price _{P E,} it calculates the difference between revenue INC. The calculated difference income INC is supplied to the determination unit 43.

Fuel difference cost calculation unit 42a includes a differential output [Delta] W that is calculated on the difference output calculation unit 41c, the difference between the calculated difference frozen power [Delta] W _IN to differential freezing power calculation unit 41E4, stored in advance in the storage unit 25 and fuel prices P _F per unit calorific value, on the basis of the power supplied from the gas turbine control device 1e efficiency E _{G (in} FIG. 4 (3)), calculates a fuel difference cost C _F. The calculated fuel differential cost _CF is supplied to the determination unit 43.

Determining means 43 determines, large required output _{W PR} than the dew point output _{W PDT,} and than the difference cost _{C C} whether or not the difference income INC large.

Then, based on the determination result of the determination unit 43, the cooling control unit 24, when W _PR ≦ W _PDT , (difference income INC−difference cost C _C ) ≦ 0 (the balance is deficit or 0) when, 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 . That is, in this case, since the required output W _PR is below the dew point output W _PDT, dare bad operating range efficiency, it is not necessary to obtain a large output. Therefore, it is not necessary for the intake air A to be lower than the dew point temperature _Td .

In addition, when W _PR > W _PDT , the cooling control unit 24 sets the intake air A to be less than the dew point temperature T _d when (difference income INC−difference cost C _C ) ≦ 0 (balance is in red or 0). Without operating, operate at dew point temperature _Td . That is, in this case, the required output W _PR is above the dew point output W _PDT, although there need to respond to power demand, and a differential income INC ≦ difference cost C _C, or balance is zero, If the intake air A is less than the dew point temperature T _d, it will be red. If the intake air A is less than the dew point temperature T _d , it is inefficient. Accordingly, the intake air A is operated at the dew point temperature _Td so that the most output can be obtained in an efficient operation range.

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 . That is, there is a need to meet power demand, has a difference income INC <difference cost C _C, since the surplus if operation by the suction air A to below the dew point temperature T _d, is economical.

As described above, according to the GTCC power plant G1, by comparing the output at the required output W _PR and dew point temperature T _d, the condition that the balance due to the generation satisfies a predetermined criterion, the compressor Since the inlet temperature T _IN is _lower than the dew point temperature T _PDT , it is possible to avoid the compressor inlet temperature T _IN being _lower than the dew point temperature T _d regardless of the balance due to power generation. Thereby, since the suction air A is limited below the dew point temperature _Td based on the balance accompanying power generation, the suction air A can be cooled economically. 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.
Therefore, the intake air A can be economically cooled and appropriately meet the power demand.

Also, if provided with a differential revenue calculation unit 41 and the differential cost calculation means 42 and decision means 43 compares the difference revenue INC and the difference cost C _C, the compressor inlet temperature T _IN to below the dew point temperature T _d since determining whether a balance associated with power generation from the difference revenue INC and the difference cost C _C is accurately determined, which is economically possible to operate.

Also, the dew-point temperature calculating section 41a, so and a dew-point output computing unit 41b and the differential output calculating section 41c and the difference revenue calculation unit 41d, and the atmospheric temperature _{T amb} and the atmospheric humidity φ required output _{W PR} and electricity price _{P E} Based on the above, it is possible to obtain the differential income INC having relatively high prediction reliability.

Further, based on the fuel price P _F per differential output ΔW and the unit heating value and power generation efficiency E _G, prediction reliability relatively can be obtained a high fuel differential cost C _F.

Further, the specific enthalpy difference Δh is obtained based on the required inlet temperature _TPR and the dew point temperature _Td , the differential refrigeration capacity ΔH is obtained from the specific enthalpy difference Δh and the flow rate G _IN of the intake air A, and this differential refrigeration capacity is obtained. based on the coefficient of performance COP of ΔH and the refrigerator, the prediction reliability relatively can be obtained a high differential refrigeration power [Delta] W _iN.

The cooling control unit 24, evaluation unit 43 has a larger required output _{W PR} than the dew point output _{W PDT,} and, when it is determined that there is a large difference income INC than the difference cost _{C C,} the compressor inlet temperature _{T IN} the so to below the dew point temperature T _d, since balance is less than the dew point temperature T _d of the limiting suction air a in the case of a surplus, only if it can benefit by performing the high output operation properly It becomes possible to meet the power demand.
Therefore, it is possible to economically operate and appropriately meet the power demand.

  Further, since the gas turbine intake air cooling device 2 is provided, it is possible to maintain power generation output at a high atmospheric temperature and generate power economically, and to appropriately meet power demand.

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 airflow adheres to the heat transfer tube 32 on the downstream side of the airflow and falls downward in the direction of gravity.
Further, since the plurality of heat transfer tubes 32 are arranged such that the cooling effect of the heat transfer tubes 32 located on the upstream side of the airflow is greater than that of the heat transfer tubes 32 located on the downstream side of the airflow, the heat transfer tubes 32 are located on the upstream side of the airflow. Mist generation is relatively active in the heat transfer tubes 32, and generation of mist is relatively suppressed in the heat transfer tubes 32 located on the downstream side of the airflow, so that the mist is more effectively captured by the heat transfer tubes 32 on the downstream side of the airflow. Be collected.
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 power generation gas turbine 1 from sucking mist without adding another device on the flow path of the cooled intake air A.

  Further, since the plurality of heat transfer tubes 32 are arranged in a zigzag shape, the suction air A that has passed through the gap in the flow path width direction of the heat transfer tube stage 35 on the upstream side of the airflow is transferred to the heat transfer tube stage 35 on the downstream side of the airflow. The heat transfer tube 32 can be sufficiently brought into contact. Thereby, the cooling effect and the mist capturing effect can be enhanced.

  Furthermore, since the moisture absorption means 50 that can absorb moisture of the intake air A and release the contained moisture to humidify the intake air A is provided, when mist is generated, the mist can be absorbed. When it is low, it becomes possible to cool the suction air A by releasing the contained water. Thereby, the mist which goes to the compressor 1a inlet of a gas turbine can be removed, and the damage of the components of the gas turbine 1 for electric power generation can be suppressed. Further, when the humidity of the intake air A is low, the intake air A can be further cooled, and the output of the power generation gas turbine 1 can be improved.

  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, the coefficient of performance COP stored in the storage unit 25 may be configured to update the storage of the storage unit 25 by feeding back the refrigeration capacity and the actually consumed power.
The data stored in the storage unit 25 and the storage unit 69 may be stored in advance or may be directly input each time. Further, all the data of the NC diagram 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 by calculation each time. .

In the above-described embodiment, only the fuel differential cost C _F is assumed to be the differential cost C _C so that the fuel differential cost C _F = the differential cost C _C. However, the differential cost C _{C is changed} to the fuel differential cost C _F. It is good also as what combined the consumption cost concerning consumption of a wing etc. Note that the consumption cost can be obtained by multiplying, for example, the consumption rate obtained from the analysis or experimental result and the time of operation at a temperature lower than the dew point temperature _Td .

  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 existing power generation gas turbine can be economically operated and appropriately powered. The demand can be met and the output can be easily increased.

  In the above-described embodiment, the first heat exchanger 21 is provided as the heat exchange means for cooling the intake air A, but other configurations may be adopted.

DESCRIPTION OF SYMBOLS 1 ... Gas turbine 1a for electric power generation ... Compressor 1b ... Combustor 1c ... Turbine 2 ... Intake cooling device 21 for gas turbines ... First heat exchanger (heat exchange means)
22 ... Refrigerator 41 ... Differential income calculating means 41a ... Dew point temperature calculating part 41b ... Dew point output calculating part 41c ... Differential output calculating part 41d ... Differential income calculating part 41e ... Differential refrigeration power calculating means 41e1 ... Required inlet temperature calculating part 41e2 ... specific enthalpy difference computation unit 41E3 ... differential cooling capacity calculating portion 41E4 ... difference refrigerating power calculation unit 42 ... differential cost calculation means 42a ... fuel difference cost calculator 43 ... judging means C C _... difference cost C F _... fuel differential cost E _G ... Power generation efficiency G1 ... GTCC power plant P _E ... Electric power price P _F ... Fuel price T _d ... Dew point temperature COP ... Performance coefficient G _IN ... Suction air flow rate INC ... Differential income T _IN ... Compressor inlet temperature _TPR ... Required inlet temperature W _PR ... Required output _TPDT ... Dew point temperature T _amb ... Atmospheric temperature _WPDT ... Dew point output A ... Suction air

Claims (10)

  An intake air cooling device for a gas turbine used in a power generation gas turbine including a compressor, a combustor, and a turbine, the heat exchange means capable of cooling the intake air sucked into the compressor from the outside, and the power generation A cooling control unit that cools the intake air by the heat exchanging means according to a required output of the gas turbine, and the cooling control unit operates a compressor inlet temperature of the suction air at the compressor inlet at a dew point temperature. The dew point output is compared with the required output, and when the required output is large, the compressor inlet temperature is determined on the condition that the balance due to power generation satisfies a predetermined standard based on the set power price. Is set to be lower than the dew point temperature. The cooling controller is
A difference income calculating means for calculating a difference income based on the difference output and the power price which is a difference between the required output and the dew point output;
Differential cost calculating means for calculating a differential cost including a fuel differential cost according to the differential output;
The gas turbine according to claim 1, further comprising: a determination unit that compares the differential income with the differential cost and determines whether or not the compressor inlet temperature is lower than the dew point temperature. Intake cooling system. The differential income calculating means is
A dew point temperature calculation unit for obtaining the dew point temperature based on the temperature and humidity of the external air;
Based on the dew point temperature calculated by the dew point temperature calculation unit, a dew point output calculation unit for obtaining the dew point output;
Based on the dew point output calculated by the dew point output calculation unit and the required output , a difference output calculation unit that calculates the difference output;
And differential refrigeration power calculating means for calculating a difference refrigerating power which is required for cooling the intake air to the dew point temperature or RaKaname determined inlet temperature,
A differential income calculation unit that calculates the differential income based on the differential output calculated by the differential output calculation unit, the differential refrigeration power calculated by the differential refrigeration power calculation means, and the power price. The intake-air cooling apparatus for a gas turbine according to claim 2. The differential cost calculation means includes a fuel differential cost calculation unit that calculates the differential fuel cost based on the differential output, the fuel price per unit calorific value, and the power generation efficiency. An intake air cooling device for a gas turbine as described in 1. The differential refrigeration power calculating means includes:
Based on the previous SL request inlet temperature and the dew point temperature, and the specific enthalpy difference calculator for calculating the specific enthalpy difference,
A differential refrigeration capacity calculator that calculates a differential refrigeration capacity from the specific enthalpy difference calculated by the specific enthalpy difference calculator and the flow rate of the intake air;
The differential refrigeration power is calculated based on the differential refrigeration capacity calculated by the differential refrigeration capacity calculation unit and a coefficient of performance of a refrigerator that supplies cold heat that performs heat exchange to the intake air to the heat exchange means. The intake-air cooling apparatus for a gas turbine according to claim 3, further comprising a differential refrigeration power calculation unit.   The said differential cost calculating means is provided with the fuel differential cost calculating part which calculates the said fuel differential cost based on the said differential output, the fuel price per unit calorific value, and power generation efficiency. Inlet air cooling system for gas turbine. The cooling control unit determines that the compressor inlet temperature is lower than the dew point temperature when the determination unit determines that the required output is greater than the dew point output and the difference income is greater than the difference cost. The intake-air cooling apparatus for a gas turbine according to any one of claims 2 to 6 , wherein the intake-air cooling apparatus is for a gas turbine. A gas turbine comprising the gas turbine intake air cooling device according to any one of claims 1 to 7 . An intake air cooling device for a gas turbine according to any one of claims 1 to 7 ,
A power generation 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. A method for increasing output, comprising: adding an intake air cooling device for a gas turbine according to any one of claims 1 to 7 to an existing gas turbine or a gas turbine combined cycle power plant.

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