JPH10246127A - Gas turbine, combined cycle plant, and compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve an output and heat efficiency by spraying liquid drops to gas supplied to a compressor, and vaporizing the liquid drops sprayed while flowing down in the compressor, after a temperature of gas fed in the compressor is reduced more than an outside temperature. SOLUTION: Intake 6 is led to an intake chamber 10 bypassing a louver 9, water in a feed water tank 17 is injected from an injection nozzle 11 via a regulating valve 15 and a feed water means 13. In the case where air fed from an feed air means 12 is necessitated for injecting fine liquid drops, the regulating valve 14 is set to a prescribed opening, and a droplet diameter of sprayed liquid drop is regulated. The intake 6 forms spray flow including liquid drops, a part thereof is evaporated, the intake 6 is cooled, and then, it flows into a compressor. The liquid drops contained in the intake 6 is gasified in the compressor so as to cool compressed air. The compressed air is burnt while mixing with fuel in a combustor 5, and is formed as gas having a high temperature and high pressure. Then, the gas flows into a turbine 2, and an operation is carried out. Mechanical energy is converted into electric energy by a power generator 3, and is fed to a sending end 4.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine, and more particularly to a gas turbine for spraying droplets during intake of a compressor of a gas turbine.

[0002] The present invention also relates to a combined cycle plant that sprays liquid droplets during intake of a compressor constituting the combined cycle plant.

[0003] The present invention also relates to a compressor, and more particularly to a compressor for spraying liquid droplets during intake of the compressor.

[0004]

2. Description of the Related Art The output of a gas turbine decreases when the temperature rises in summer or the like, and various configurations have been described as a method of restoring the output.

[0005] JP-A-7-97933, Japanese Utility Model Publication No. 61-37794
Japanese Patent Application Laid-Open No. 5-195809 describes cooling of the intake air of a compressor.

Japanese Patent Application Laid-Open No. 61-283728 describes that water is supplied from a compressor inlet and a compressor intermediate stage in a combined system of a gasifier and a gas turbine.

Further, Japanese Utility Model Application Laid-Open No. Sho 56-43433 discloses that a hole for supplying water droplets is provided in a compressor, and Japanese Patent Application Laid-Open No. Hei 2-213133 discloses that a gas turbine is provided with two high-pressure and low-pressure compressors. And an intercooler between the compressors. Japanese Patent Application Laid-Open No. 6-10702 discloses that, for a compressor group including a plurality of compressor stages, water is supplied to an intermediate portion between an upstream compressor stage and a downstream compressor stage in order to reduce power consumption. A spraying technique is described.

[0008]

SUMMARY OF THE INVENTION
No. 7-97933, Japanese Utility Model Publication No. 61-37794, or
No. 5,195,809 merely discloses reducing the temperature of the intake air introduced into the compression machine to improve the output. Japanese Patent Application Laid-Open No. 61-283728 describes that droplets are vaporized during compression to be used as a medium for cooling turbine blades and that turbine cycle characteristics are improved. Are not achieved together.

In gas turbines, combined cycle plants and compressors, it is desired to achieve both an increase in output and an increase in thermal efficiency.

Further, Japanese Patent Application Laid-Open No. 6-10702 or
As described in Japanese Patent Application Laid-Open No. 2-21133, a specific facility is required in the high-pressure gas flow path in the middle part of the compressor in order to obtain both the effect of improving the output and the effect of improving the thermal efficiency. There was a problem that the size and size were increased. In addition, actual opening 56-4343
In JP-A-3, it was necessary to provide a special configuration for the casing and the stationary vane in the compressor.

In consideration of actual gas turbines, combined plants and compressors, it is required that the output and the thermal efficiency can be improved with simple equipment.

Therefore, the present invention provides a gas turbine and a combined gas turbine capable of realizing both an improvement in output and an improvement in thermal efficiency by spraying liquid droplets into intake air introduced into an inlet of a compressor with simple equipment suitable for practical use. It is an object to provide a plant and a press machine.

[0013]

Means for Solving the Problems A first method for solving the above problems is described below.
The invention of the compressor, which compresses and discharges the supplied gas,
In a gas turbine including a combustor in which gas and fuel discharged from the compressor are burned, and a turbine driven by combustion gas from the combustor, droplets are sprayed on gas supplied to the compressor. Then, the temperature of the gas entering the compressor is lower than the outside air temperature, the gas is introduced into the compressor together with the gas, the spraying device in which the sprayed droplets are vaporized while flowing down the compressor. It is characterized by having. This makes it possible to achieve both an improvement in output and an improvement in thermal efficiency by spraying liquid droplets into the intake air introduced into the inlet of the compressor, as needed, with simple equipment suitable for practical use.

According to a second aspect of the present invention, there is provided a compressor that sucks, compresses, and discharges a supplied gas, a combustor in which gas and fuel discharged from the compressor are burned, and a combustion gas driven by the combustion gas of the combustor. And a spray device for spraying droplets having a particle diameter of 50 μm or less mainly to the gas supplied to the compressor inlet on the upstream side of the compressor. Things.

[0015] Thus, fine droplets can be supplied to the compressor intake by simple equipment suitable for practical use, and water droplets can be satisfactorily placed on the intake air flow supplied to the compressor. It can be conveyed into the compressor from the compressor inlet. Furthermore, the droplets introduced into the compressor can be vaporized in a good condition. Thereby, the output of the gas turbine and the thermal efficiency can be improved.

According to a third aspect of the present invention, there is provided a compressor for compressing and discharging a supplied gas, a combustor for burning the gas and fuel discharged from the compressor, and driven by combustion gas from the combustor. A combined cycle plant comprising: a gas turbine including a turbine; an exhaust heat recovery boiler that generates steam using exhaust gas from the turbine as a heat source; and a steam turbine driven by generated steam from the exhaust heat recovery boiler. Spraying droplets on gas supplied to the compressor of the gas turbine, lowering the temperature of the gas entering the compressor from the outside air temperature, introducing the gas into the compressor, and flowing down the compressor. A spray device is provided, in which the sprayed droplets are vaporized.

Thus, it is possible to provide a combined cycle plant capable of improving the thermal efficiency while improving the output of the combined cycle plant according to demand at any time.

According to a fourth aspect of the present invention, in a compressor to which a gas is supplied and which compresses and discharges the supplied gas, droplets are sprayed on a gas supplied to an inlet of the compressor, and the compressed gas is supplied to the compressor. A spray device that lowers the temperature of an incoming gas from the outside air temperature, is introduced into the compressor together with the gas, and the sprayed droplets are vaporized while flowing down the compressor. I do.

Thus, the power of the compressor can be reduced by simple equipment suitable for practical use, and the output and the thermal efficiency can be improved.

According to a fifth aspect of the present invention, there is provided a droplet spraying device for spraying droplets during intake of a compressor, a compressor for compressing and discharging a supplied gas, and a gas and a fuel discharged from the compressor. In a droplet spraying device that sprays droplets on a gas supplied to the compressor of a gas turbine including a combustor in which a combustor is burned, and a turbine driven by combustion gas of the combustor, The temperature of the gas that is sprayed and enters the compressor is reduced from the outside air temperature, and the gas is introduced into the compressor together with the gas, and the sprayed droplets are vaporized while flowing down the compressor. Features.

As a result, it is possible to improve both the output and the thermal efficiency of the gas turbine or the like in which the present apparatus is arranged.

[0022]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS A first embodiment of the present invention will be described with reference to FIG.

As shown in FIG. 1, a gas turbine according to an embodiment of the present invention includes a compressor 1 for compressing and discharging gas, a combustor 5 to which gas compressed by the compressor is supplied, and a combustor 5.
And a power transmitting end 4 for transmitting electricity generated by the generator 3 connected to the turbine 2 shaft. The exhaust gas 7 from the gas turbine is discharged from the stack 8 into the atmosphere.

In the following embodiments, the case where the gas supplied to the compressor 1 is air will be described.

The compressor 1 is connected to an intake chamber 10 for taking in the intake air 6 supplied to the compressor 1. In addition, intake chamber 1
In general, a louver 9 is disposed at the upper end of the zero. The louver 9 arranges an air filter on the compressor side (the downstream side). Since the air filter is provided immediately after the position of the louver 9, the description is omitted.

Although FIG. 1 shows an embodiment in which the louver 9 is arranged on the upstream side of the intake chamber, when the air filter is located in the middle of the intake chamber, in this embodiment, the intake chamber 10 is located downstream of the air filter. 2 shows the intake flow path to the compressor inlet on the side.

In FIG. 1, the compressor 1, the turbine 2 and the generator 3 are coaxially connected.
It may be on a different axis from that of FIG.

T1 indicates the intake air temperature 20 before entering the compressor 1, T2 indicates the compressor outlet air temperature 21, T3 indicates the combustion temperature 22, and T4 indicates the exhaust gas temperature 23 discharged from the turbine 2.

Unless otherwise noted, in the numbers described below, the same numbers as those described above indicate the same objects.

The first embodiment further includes a spray device for ejecting fine droplets into the suction chamber 10. For example, a spray nozzle 11 is provided. The Zautor average particle size (SMD) of the ejected droplet is, for example, about 10 μm. The water supply means 13 is connected to the spray nozzle 11. When the spray nozzle 11 is provided with atomizing means for obtaining such fine droplets, only the water supply means 13 may be connected, but in addition to the spray nozzle 11, an atomizing means is provided. You may do so. The structure provided with the atomizing means will be described in detail in the second embodiment.

The water supply means 13 is a control valve 1 for adjusting the flow rate.
5, water supply pump 16, water supply tank 17, water supply tank 17
And a water supply device 18 for supplying water to the water supply device.

The control valve 15 outputs a signal based on the output of the generator 3 and a load command signal Pd25 through an adder to form the control valve 15.
Function generator 24 that outputs an opening signal and other commands such as
Is electrically connected to For example, it is communicated by a signal cable 26 or the like. In some cases, the load request signal 25 may be directly introduced into the function generator 24.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10
And the water in the water supply tank 17 is filled with the control valve 15 having a predetermined opening degree.
, Fine droplets are ejected from the spray nozzle 11 through the water supply means 13. Air supply means 12 for ejecting fine droplets
When air supply is required, the control valve 14 is also opened at a predetermined opening to adjust the particle size of the spray droplets. The intake air 6 forms a spray flow including droplets, and is partially evaporated to cool the intake air before flowing into the compressor 1. Droplets included in the intake air are vaporized inside the compressor 1 to cool the compressed air.

FIG. 4 shows the temperature distribution of the compressed air in the compressor. The air temperature T21 at the outlet of the compressor 1 is lower in the case of spraying water and evaporating water drops in the compressor 1 than in the case of not mixing water drops 27. It also drops continuously in the compressor.

After the droplets are substantially vaporized in the compressor 1,
The compressed air mixes with the fuel in the combustor 5 and burns, and becomes a high-temperature and high-pressure gas that flows into the turbine 2 to perform work. The mechanical energy is converted into electric energy by the generator 3 and supplied to the power transmission end 4. The exhaust gas 7 after the work is released from the stack 8 to the atmosphere.

According to this embodiment, the output can be improved and the thermal efficiency can be improved.

The output power increasing mechanism according to this embodiment is qualitatively
It can be adjusted as follows.

1) Cooling the intake air on the iso-wet bulb temperature line in the suction chamber 10 introduced into the compressor 1; 2) Cooling the internal gas by vaporizing the droplets introduced into the compressor 1; 3) the difference between the amount of working fluid passing through the compressor 2 and the turbine 2 corresponding to the amount of vaporization in the compressor 1, 4) the increase in the low-pressure specific heat of the air-fuel mixture due to the incorporation of steam having a large constant-pressure specific heat, and the like.

FIG. 11 schematically shows the arrangement of the spray nozzle 11 in the suction chamber 10.

A large number of spray nozzles 11 are arranged in a predetermined assumed section of the intake passage. For example, it is arranged on a plane substantially perpendicular to the flow direction of the intake air. Adjacent spray nozzle 1
The intervals 1 are arranged so as to be evenly spaced in the longitudinal direction of the cross section of the intake passage. In addition, they are arranged so as to be evenly spaced in the lateral direction of the cross section of the intake passage. As a whole, as shown in the figure, a large number can be arranged in a region excluding the vicinity of the wall surface of the intake chamber constituting the intake passage.

The spacing between adjacent spray nozzles can be similarly arranged in other embodiments.

Thus, water droplets can be uniformly dispersed in the intake air carried into the compressor inlet.

A conventional intake air cooling device having a spray nozzle generally has a recovery device for recovering most of the sprayed liquid and a large-scale circulation system for supplying the spray liquid to the spray nozzle 11 again. In the embodiment, there is an advantage that it is not necessary to provide such a large-scale facility.

The spray nozzle 11 is located downstream of the air filter of the louver 9. Thereby, the droplet can be stably supplied to the compressor 1 while being carried on the flow of the intake air. This is because it is possible to suppress the possibility that water droplets are attached to the air filter of the louver 9 and clogging is caused by supplying liquid droplets to the upstream side.

The spray nozzle 11 is connected to the suction chamber 10.
It is preferable to dispose the compressor at a distance from the inlet of the compressor 1 in consideration of the amount of vaporization when flowing through the inside. When a so-called IGV is arranged at the inlet of the compressor 1, it is upstream of the IGV.
If a silencer or the like is provided, the spray nozzle is located downstream of the silencer or the like.

On the other hand, the pressure vertical machine 1 and the suction chamber 1
When the spray nozzle 11 is arranged near the boundary of 0, it becomes easy to grasp the particle diameter of the droplet entering the compressor when fine droplets can be sprayed.

For example, salt drops can be vaporized from the first stage.

FIG. 8 is a detailed structural view of a gas turbine equipped with the present invention. The spray droplets ejected into the intake air by the spray nozzle 11 ride on the airflow and flow in from the compressor inlet. The average air flow velocity of the intake air flowing through the intake chamber is, for example, 20 m
/ S. The droplet 37 moves between the blades of the compressor 1 along a streamline. In the compressor, the intake air is heated by adiabatic compression, and the heat causes the droplets to evaporate from the surface while being transported to the downstream blade side while reducing the particle diameter. In this process, the latent heat of vaporization required for vaporization is supplied from the air in the compressor, so that the temperature of the air in the compressor is lower than when the present invention is not applied (see FIG. 4). If the droplets have a large particle diameter, they collide with the blades and casing of the compressor 1 and vaporize by obtaining heat from the metal, which may hinder the effect of reducing the temperature of the working fluid. Therefore, from such a viewpoint, it is preferable that the particle diameter of the droplet is small.

The spray droplets have a particle size distribution. From the viewpoint of suppressing collision with the compressor 1, the blades and the casing, and preventing erosion of the blades, the droplets to be sprayed mainly have a particle size of 50 μm or less. From the viewpoint of further reducing the influence on the blade, the maximum particle size is preferably set to 50 μm or less.

Furthermore, from the viewpoint that the smaller the particle size, the more evenly the droplets can be distributed in the inflowing air and the occurrence of a temperature distribution in the compressor is suppressed. M) is preferably 30 μm or less. Since the droplets ejected from the spray nozzle have a particle size distribution, it is not easy to measure at the maximum particle size. Therefore, in practice, the droplets are measured with the Sautor average particle size (SDM) as described above. Can be adapted. It is preferable that the particle size is small, but since a spray nozzle for producing droplets having a small particle size requires a high-precision manufacturing technique, the practical range of the particle size is up to the lower limit that can be made technically small. . Therefore, from such a viewpoint, for example, the lower limit of the main particle size, the maximum particle size, or the average particle size is 1 μm, respectively. In addition, since the energy required for production is often increased as the droplet size becomes smaller,
The lower limit may be determined in consideration of the energy used for manufacturing the droplet. When the size of the contact surface is small enough to float in the atmosphere and hardly fall, the condition of the contact surface is generally good.

The weight flow rate of the working fluid increases as the droplets evaporate. When vaporization is completed in the compressor, the gas in the compressor 1 is further subjected to adiabatic compression. At that time, the constant pressure specific heat of the steam has a value about twice that of air near the typical temperature (300 ° C.) in the compressor. Therefore, in terms of heat capacity, it is about twice the weight of the vaporized water droplet in terms of air. There is an effect equivalent to increasing air as a working fluid. That is, there is an effect of lowering the outlet air temperature T2 'of the compressor (the effect of increasing the temperature).
In this way, the effect of lowering the air temperature at the compressor outlet due to the vaporization of water droplets in the compressor is produced. Since the power of the compressor is equal to the difference in the enthalpy of the air at the inlet and outlet of the compressor and the air enthalpy is proportional to the temperature, when the air temperature at the outlet of the compressor decreases, the required power of the compressor can be reduced.

The working fluid (air) pressurized by the compressor is:
After being heated by the combustion of the fuel in the combustor, it flows into the turbine to perform expansion work. This work is called the turbine shaft power and is equal to the enthalpy difference between the inlet and outlet air of the turbine. The amount of injected fuel is controlled so that the gas temperature at the turbine inlet does not exceed a predetermined temperature. For example, the turbine inlet temperature is calculated from the actual measured value of the exhaust gas temperature at the turbine outlet and the pressure P _{cd at} the compressor outlet, and the fuel flow rate to the combustor 5 is controlled so that the calculated value becomes equal to the value before application of the present invention. You. When the combustion temperature constant control is performed, as described above, the amount of injected fuel increases by an amount corresponding to the decrease in the gas temperature T2 'at the compressor outlet. Further, if the combustion temperature is constant and the weight ratio of the water spray is about several percent of the intake air, the pressure at the turbine inlet and the compressor outlet pressure do not change substantially before and after the spraying, so that the gas temperature T4 at the turbine outlet is not changed. Also does not change. Therefore, the export power of the turbine does not change before and after spraying. On the other hand, since the net output of the gas turbine is obtained by subtracting the power of the compressor from the shaft output of the turbine, after all, by applying the present invention, the net output of the gas turbine is reduced by the reduced power of the compressor. Can increase.

The electric output Q _E of the turbine 2 is
From the shaft output Cp (T3-T4) of the compressor 1 to the work Cp (T
2-T1), which can be approximately expressed by the following equation.

[0054]

Q _E / Cp = T3-T4- (T2-T1) (Equation 1) Normally, the combustion temperature T3 is operated so as to be constant, so that the gas turbine outlet temperature T4 does not change and the turbine Is also constant. At this time, when the compressor outlet temperature T2 drops to T2 '(<T2) due to the mixing of water spray, the increased output T2-T equivalent to the decrease in compressor work.
2 'will be obtained. On the other hand, the efficiency η of the gas turbine is approximately given by the following equation.

[0055]

(Equation 2)

In this case, since T2 '<T2, the second term on the right-hand side becomes smaller, and it can be seen that the efficiency is improved by water spraying. In other words, the thermal energy Cp (T4
−T1) (numerator in the second term of Equation 2) is not much different before and after the application of the present invention, while the input fuel energy Cp (T3-T
2 ′) is Cp (T2−T2 ′) when applying the present invention.
That is, the compressor work increases as the compressor work decreases. On the other hand, as described above, the decrease in the compressor work is equal to the increase in the output, so that the increase in the fuel substantially contributes to the increase in the output of the gas turbine. That is, the increased output has a thermal efficiency of 100%. For this reason, the thermal efficiency of the gas turbine can be improved. As described above, in this embodiment, in order to reduce the work of the compressor, which is not specified in the related art for cooling the intake air, water spray is mixed into the intake air of the compressor 1 to increase the total output of the gas turbine. Can be planned. On the other hand, in the prior art in which water is injected into the inlet of the combustor 5, the output is increased by increasing the working fluid.
Work is not reduced, so efficiency is reduced.

FIG. 7 shows the thermal cycle of the present invention in comparison with other thermal cycles. The area of the closed region in the cycle diagram represents the gas turbine output per unit intake flow rate, that is, the specific output. Each number in the figure indicates the working fluid at each location in the corresponding cycle diagram. In FIG. 7, 1 is the compressor inlet, 1 'is the inlet to the intercooler exiting the first stage compressor, 1 "is the inlet of the second stage compressor exiting the intercooler, 2 is the Brayton cycle At the combustor inlet at 2 'exits the second stage compressor and at the combustor inlet,
Reference numeral 3 denotes an inlet of the turbine after exiting the combustor, and reference numeral 4 denotes a turbine outlet.

The temperature T-entropy S diagram in the lower part of FIG.
A comparison of the characteristics when the value of the temperature T-entropy S at the positions 1, 3 and 4 in each cycle is fixed is shown.

As can be seen from the figure, the magnitude of the specific output was determined by spraying the above-mentioned fine water droplets in the suction chamber of the compressor and introducing the water droplets from the inlet of the compressor as in this embodiment. Interim cooling cycle as shown in 6-10702,
The order is the normal Brayton cycle. In particular, the difference from the intercooling cycle is derived from the fact that water droplets introduced into the compressor are continuously vaporized from the inlet of the compressor in the present invention, which appears in the shape of the cycle.

Although the thermal efficiency of the intermediate cooling cycle is inferior to the Brayton cycle, the present embodiment is superior to the Brayton cycle as described above, and therefore the present invention has higher thermal efficiency than the intermediate cooling cycle.

Generally, as the position where the spray droplets evaporate in the compressor 1 is closer to the inlet of the compressor 1, the temperature of the air at the outlet of the compressor 1 decreases, which is advantageous from the viewpoint of increasing the output and improving the efficiency. Therefore, in the method of mixing the spray with the intake air 6, the smaller the spray particle size is, the more effective. This is because the spray evaporates quickly after flowing into the compressor 1. Further, the spray droplets float in the air and are smoothly introduced into the compressor along with the intake air.

Therefore, it is preferable that the droplets ejected from the spray nozzle 11 have such a size that substantially all of the droplets are vaporized by the outlet of the compressor 1. Realistically, 1
It may be lower than 00% but up to the upper limit achievable by the above configuration. In practice, it is sufficient that 90% or more is vaporized at the compressor outlet.

For example, when the outlet pressure P _cd of the compressor 1 is 0.8
At 4 MPa, when the vaporization ratio is calculated in consideration of the correlation between the absolute humidity at the outlet of the compressor 1 estimated from the outside air condition and the measured value of the absolute humidity at the EGV position, the droplets are 95% by the outlet of the compressor. It was vaporizing.

The time required for air to pass through the compressor is short. During this time, from the viewpoint of satisfactorily vaporizing the droplets and increasing the vaporization efficiency, the Sautor average particle size (SDM) is 30 μm.
The following is desirable.

Since a spray nozzle for producing droplets having a small particle size requires a high-precision manufacturing technique, the lower limit of the particle size is the lower limit that can be reduced technically. For example, 1μ
m.

This is because if the droplets are too large, it is difficult to achieve good vaporization of the droplets by the compressor.

The introduction amount of the droplet can be adjusted by the temperature and humidity or the degree of the output increase. In consideration of the amount of the sprayed droplets vaporizing from the spraying point to the compressor inlet, 0.2 wt% or more of the intake mass flow rate can be introduced. The upper limit is set from the viewpoint that the function of the compressor can be maintained satisfactorily. For example, the upper limit may be 5 wt%, and the introduction range may be less than this.

Adjustment can be made in consideration of the summer season, drying conditions, etc., but in order to further increase the output, etc., 0.8 wt% or more and 5 w
t% or less can be introduced.

In order to reduce the temperature of the air introduced into the compressor inlet, only droplets (for example, 100 to 15) are introduced into the introduced air.
In this embodiment, it is sufficient to spray a small amount of droplets, as compared with a conventional droplet spraying unit of the type in which water is collected and used again for spraying.

The maximum amount of the spray water consumed is when the output reduced at the time of high temperature in summer is restored to the rated value. Pressurized air consumption when supplying air during spray generation is
The power consumption cannot be ignored, and it is desirable that the water consumption is less than the standard. Therefore, if the particle size condition is satisfied, it is more economical to supply no air in order to produce droplets of the above particle size.

According to this embodiment, it is possible to provide a power plant capable of suppressing output fluctuation throughout the year by adjusting the spray flow rate according to the outside air temperature. For example, the opening degree of the control valve 15 is adjusted so that the spray flow rate increases when the temperature of the air introduced into the compressor is higher than when the air temperature is low.

In addition, it is preferable to perform an operation to supply the droplets at the time of the equal combustion temperature operation. Thereby, the output can be improved while improving the efficiency.

Further, in a gas turbine that does not generate power and in a gas turbine for obtaining torque by driving the gas turbine, the combustion temperature can be lowered to lower the turbine shaft output. In particular, this embodiment is applied during partial load operation,
Fuel can be saved.

In this embodiment, the output can be adjusted in accordance with the required load even in a range not less than the output restricted by the outside air temperature.

Further, since the output can be improved without increasing the combustion temperature, a gas turbine having a long life can be provided.

According to this embodiment, the gas in the compressor can be cooled. Therefore, when using this to use compressor bleed air for cooling the blades of the gas turbine, the amount of bleed air for cooling can be reduced. Further, since the amount of working fluid in the gas turbine can be increased by doing so, high efficiency and increased output can be expected.

In FIG. 1, the required load signal Pd25 can be set to a rated value to automatically control the spray flow rate.

Next, the operation method and control of the gas turbine will be described.

When increasing the gas turbine output, the step of increasing the amount of spray liquid from the spray nozzle 11 and the amount of fuel supplied to the combustor are increased. Further, when the gas turbine output is reduced, the amount of the spray liquid is reduced, and the amount of fuel supplied to the combustor is reduced.

When increasing the gas turbine output, the amount of fuel supplied to the combustor after the amount of spray liquid is increased is increased. Conversely, when decreasing the gas turbine output, the amount of fuel supplied to the combustor is reduced before the amount of the spray liquid from the spray nozzle 11 is reduced.

An example of the operation when the gas turbine is in the base load operation state will be described.

The operation control when operating at a constant combustion temperature can be performed as follows. The amount of spray water is calculated so as to correspond to the target output based on the load request signal 25, and the function generator 24 issues a command to the control valve 15 to increase the opening. A predetermined amount of water is supplied through the control valve 15 to the spray nozzle 11.
The function generator generates a command to increase the opening degree from the function generator by calculating the amount of compressed air necessary to obtain a predetermined particle size, and sprays the compressed air.
Through the spray nozzle 11. During this time, the fuel flow is kept constant. Next, the process proceeds to the exhaust gas temperature control, and the fuel flow rate is increased so that the combustion temperature (an estimated value can be used) becomes equal to the target value.

The exhaust gas temperature control line for giving the target exhaust gas temperature during operation may be one expressed by a function of the compressor discharge pressure _Pcd and the spray amount, or may be a normal control line without spray. Alternatively, a value obtained by adding an appropriate bias to the target exhaust gas temperature estimated from the normal control line can be used.

When the output of the gas turbine reached in this way has a deviation from the target value, when the output is increased according to the above-described procedure, the amount of spray is increased, and then the control is shifted to the exhaust gas temperature control. On the other hand, when the output is reduced, the fuel flow rate is first reduced, and then the spray amount is reduced.

By providing the function generator 24 for controlling in this way, the output can be increased or decreased while preventing the combustion temperature from exceeding the allowable value.

When the output is decreased, the spray amount is reduced sufficiently more slowly than in the case where the spray amount is increased when the output is increased, and the fuel flow rate is reduced according to the same exhaust temperature control as when the output is increased. Is also good.

As described above, instead of continuously changing the spray amount in order to achieve the target output, the spray amount is measured for the outside air condition such as the outside air temperature and humidity, and the output increase is determined based on the values. The operation may be performed with a predetermined spray amount set in consideration of the above. For example, the spray amount or the like is calculated as a function of the outside air temperature, humidity, or the like, and is set in accordance with a desired output increase amount.
As a result, it is also possible to perform a spray amount fixed operation that does not follow minute output fluctuations and temperature fluctuations. This method has an effect that operation control becomes easy. Further, preferably, the external air condition is measured again after a lapse of a predetermined time after the setting, and the spray amount is reset, so that the output rise amount can be adjusted relatively easily in accordance with the external air condition.

The operation of the gas turbine can be regarded as the control of a water droplet spraying device that sprays water droplets on intake air supplied to the compressor 1 of the gas turbine. By operating the water droplet spray device as described above, the above-described effect can be provided to the gas turbine in which the water droplet spray device is arranged.

A second embodiment will be described with reference to FIG.

The second embodiment is different from the first embodiment mainly in that atomizing means for obtaining droplets having the fine particle diameter is provided together with the spray nozzle 11. For example, the spray nozzle 11 is provided with a means for supplying pressurized air.

Specifically, in addition to the spray nozzle 11 provided with the water supply means 13, an air supply means 12 for supplying pressurized air to the spray nozzle 11 is provided. The air supply means 12 is provided with a pressurizer 29 for supplying pressurized air separately from the compressor 1.
And a path for guiding pressurized air from the control nozzle 14 to the spray nozzle 11 through the control valve 14. Further, a control valve 14 for controlling a gas flow rate to the spray nozzle 11 is provided. In the case of this embodiment, a control valve 14a for adjusting the supply amount of the pressurized air to the spray nozzle is provided.

The control valves 14 and 15 output a signal based on the output of the generator 3 and a load command signal Pd25 through an adder.
It is electrically connected to a function generator 24 that outputs opening signals and other commands for the control valves 14 and 15 and the like. For example, it is communicated by a signal cable 26 or the like. In some cases, the load request signal 25 may be directly introduced into the function generator 24.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
And the water in the water supply tank 17 is filled with the control valve 15 having a predetermined opening degree.
Through the water supply means 13 to the spray nozzle 11. At the same time, pressurized air generated from the pressurizer 29 is supplied to the spray nozzle 11 through the control valve 14 having a predetermined opening. Then, fine droplets are ejected from the spray nozzle 11. The nozzle may be capable of adjusting the supply air and the supply liquid amount to adjust the particle diameter in a desired range among the above-described ranges. The intake air 6 includes a droplet and forms a spray flow, and a part of the air is evaporated to cool the intake air, and then flows into the compressor 1. Droplets contained in the intake
It vaporizes inside the compressor 1 and cools the compressed air.

After the droplets are substantially vaporized in the compressor 1,
The compressed air mixes with the fuel in the combustor 5 and burns, and becomes a high-temperature and high-pressure gas that flows into the turbine 2 to perform work. The mechanical energy is converted into electric energy by the generator 3 and supplied to the power transmission end 4. The exhaust gas 7 after the work is released from the stack 8 to the atmosphere.

By arranging the separate pressurizer 29,
Since the power of the compressor is not reduced, there may be an effect from the viewpoint of arrangement and power saving in addition to the effect of improving the output of the gas turbine and improving the thermal efficiency of the gas turbine.

Although not shown in FIG.
May be supplied from an atomizing compressor for driving a gas turbine.

As the nozzle, for example, an internal mist type air mist nozzle which can obtain a droplet having a desired particle size can be used.

During the operation and control of the gas turbine, when the output of the gas turbine is increased, the amount of air supplied to the spray nozzle 11 is increased along with the increase in the amount of spray water as described above. The size of the droplets to be produced can be made to be a desired size.

To reduce the output, the spray nozzle 11
The amount of liquid supplied to the spray nozzle 11 and the amount of air supplied to the spray nozzle 11 are reduced to adjust the particle diameter of the droplet.

In order to facilitate the operation, the amount of air and the amount of liquid supplied to the spray nozzle 11 are not adjusted.
Alternatively, only the supply liquid amount may be adjusted while keeping the air amount constant.

At this time, the amount of supplied air is adjusted so that a desired droplet diameter is obtained when the maximum allowable liquid amount is supplied. As a result, when the amount of the spray liquid is less than the maximum amount of the spray liquid, the diameter of the droplet is smaller than that at the time of the maximum amount of the spray water, so that favorable conditions can be obtained.

Further, in addition to the above-described pressurizer 29 or instead of not providing the separate pressurizer 29, the following configuration can be adopted.

The air supply means 12 branches from a path for bleeding air from the intermediate stage of the compressor 1 and communicating with the spray nozzle 11 or a path for flowing the compressed air discharged from the compressor 1 to the spray nozzle. 11 is provided.
The path is provided with a control valve 14b for the supply amount of pressurized air. It is possible to have a cooler 19 for adjusting the compressed air to a desired temperature in response to a request such as effective spraying.

In the case of disposing it together with the pressurizer 29, first, bleed air or discharge air from the intermediate stage is used.
By using the compressed air from the pressurizer 29 for the shortage, the power of the separate pressurizer 29 can be reduced. In addition, when this configuration is used instead of the pressurizer 29, the equipment can be simplified.

In the configuration in which the compressed air discharged from the intermediate stage of the compressor 1 or the discharged air is supplied for atomizing the droplets as described above, when the plant is started or when the outside air temperature is extremely low, , By supplying only air supply,
In the former, it is possible to operate with reduced NOx emissions,
In the latter case, it is possible to raise the intake air temperature and to perform an operation capable of preventing icing.

More specifically, in the configuration provided with the control valve 14b, the control valve 15 is closed, and only the control valve 14b is opened to blow out a desired amount of intake air.

By supplying the fuel from the spray nozzle 11, it is possible to uniformly jet into the intake air, and the temperature distribution of the intake air can be made uniform.

A third embodiment will be described with reference to FIG.

The third embodiment is different from the first or second embodiment in that a water collecting device 31 is further provided at the exhaust part of the turbine 2 to collect the water in the exhaust gas and spray water. The main difference is that a path for supplying the water recovered by the water recovery device 31 to the water supply tank 17 is provided so that the water can be reused.

As the recovery device, a device utilizing various principles such as condensation of water vapor by cooling or physical adsorption can be applied.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
After the water collected by the water collecting device is once stored in a water supply tank, fine water droplets are ejected from a spray nozzle 11 through a water supply means 13 through a control valve 15 having a predetermined opening degree. When air supply from the air supply means 12 is required to eject fine droplets, the particle size of the spray droplets is adjusted by opening the control valve 14 at a predetermined opening. The intake air 6 includes a droplet and forms a spray flow, and a part of the air is evaporated to cool the intake air, and then flows into the compressor 1. Droplets included in the intake air are vaporized inside the compressor 1 to cool the compressed air.

After the droplets are substantially vaporized in the compressor 1,
The compressed air mixes with the fuel in the combustor 5 and burns, and becomes a high-temperature and high-pressure gas that flows into the turbine 2 to perform work. The mechanical energy is converted into electric energy by the generator 3 and supplied to the power transmission end 4. The exhaust gas 7 after the work is released from the stack 8 to the atmosphere.

According to the third embodiment, in addition to the effect of improving the gas turbine output and improving the thermal efficiency of the gas turbine,
Water can be used effectively and water can be saved.

In a gas turbine plant having the waste heat recovery boiler 30, the water recovery efficiency can be improved by disposing the water recovery device 31 at the outlet of the waste heat recovery boiler 30.

The fourth embodiment will be described with reference to FIG.

The fourth embodiment is different from the first embodiment or the second embodiment in that the fuel of the combustor 5 is converted to liquefied natural gas (LN).
G). For this reason, in addition to the configuration of the first embodiment or the second embodiment, a liquefied natural gas storage unit 33 which also has a role as a cold heat source is arranged, and supplied from the natural gas storage unit 33 as the water recovery device 31. A heat exchanger 32 for elevating the temperature of the natural gas to be vaporized and a passage 34 for guiding the vaporized natural gas to the combustor 5 are provided. The heat exchanger 32 is installed to use the exhaust gas of the gas turbine.

Further, in the heat exchanger 32, the moisture in the exhaust gas is recovered. In addition, a path for supplying the water collected by the heat exchanger 32 to the water supply tank 17 is provided to collect the water in the exhaust gas and reuse it as spray water.

Here, by performing the same operation as in the above-described embodiment, in addition to the effect of improving the gas turbine output and the heat efficiency of the gas turbine, the effect of eliminating the need for LNG vaporization equipment and recovering water is produced. . It also makes effective use of unused energy.

A fifth embodiment will be described with reference to FIG. This embodiment is a gas turbine in which water spray to intake air and intake air cooling equipment are combined.

The fifth embodiment is different from the first or second embodiment in that an air cooler 35 connected to an external cooling source 36 is additionally provided on the back of the louver 9. The cooling medium is configured to be circulated by the pump 42. The air cooler 35 can be arranged on the front surface of the louver 9.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
Then, the water is cooled by passing through the air cooler 35, and the water in the water supply tank 17 passes through the control valve 15 having a predetermined opening degree, and fine droplets are ejected from the spray nozzle 11 through the water supply means 13. When air supply from the air supply means 12 is required to eject fine droplets, the particle size of the spray droplets is adjusted by opening the control valve 14 at a predetermined opening. The intake air 6 includes a droplet and forms a spray flow, and a part of the air is evaporated to cool the intake air, and then flows into the compressor 1. Droplets included in the intake air are vaporized inside the compressor 1 to cool the compressed air.

After the droplets are substantially vaporized in the compressor 1,
The compressed air mixes with the fuel in the combustor 5 and burns, and becomes a high-temperature and high-pressure gas that flows into the turbine 2 to perform work. The mechanical energy is converted into electric energy by the generator 3 and supplied to the power transmission end 4. The exhaust gas 7 after the work is released from the stack 8 to the atmosphere.

In this facility, in addition to the effect of improving the output of the gas turbine and improving the thermal efficiency of the gas turbine obtained in the first embodiment, the weight of the intake air is increased by cooling the intake air, and the work of the compressor 1 is reduced by spraying water. Therefore, the output is increased by a synergistic effect. Typically, by increasing the capacity of the air cooler 35 to a dew point at which intake air cooling can operate efficiently, a large increase in power can be obtained while saving water. This embodiment is advantageous for application to an area where drought is expected in summer.

A sixth embodiment will be described with reference to FIG. The sixth embodiment clearly shows that the position of the spray nozzle 11 is located closer to the louver 9 of the intake chamber than the first embodiment or the second embodiment. . FIG.
5 shows the position of the spray nozzle 11 more easily. FIG. 2 shows an air supply means 1 for supplying pressurized intake air.
2 is described, but the air supply means 12 may not be provided as in the first embodiment as long as the above-described desired droplets can be obtained.

From the viewpoint of promoting vaporization before flowing into the compressor 1 and increasing the efficiency of cooling the intake air, it is preferable to dispose the spray nozzle 11 away from the inlet of the compressor 1 as described above.

More specifically, it is appropriate that the spray nozzle 11 is arranged at any one of the following positions (11a or 11b).

[0127] 1. When the intake chamber 10 is provided with the silencer 41 (1) The spray nozzle 11a is arranged downstream of the silencer.

As a result, it is possible to prevent the soundproofing material from being wet by the silencer. By the time we introduce the compressor,
It is preferable to set the distance to the compressor in consideration of the flight distance of the droplets.

(2) Alternatively, the spray nozzle 11b is arranged upstream of the silencer.

For example, by disposing the louver 9 near the louver 9 in the intake chamber, the distribution of water droplets in the intake air before entering the compressor can be made more uniform. Further, when the louver 9 is wider than the suction chamber 10 downstream thereof, the installation or maintenance of the nozzle 11 is easy.

[0131] 2. When the intake chamber 10 is not provided with a silencer It is located between the louver 9 and the inlet of the compressor 1. It is preferable that a distance to the compressor is set before the liquid is introduced into the compressor in consideration of a flight distance in which the droplets evaporate.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
To the silencer, if there is a silencer,
The water in the water supply tank 17 passes through the control valve 15 having a predetermined opening,
Fine droplets are ejected from the spray nozzle 11 via the water supply means 13. When air supply from the air supply means 12 is required to eject fine droplets, the particle size of the spray droplets is adjusted by opening the control valve 14 at a predetermined opening. The intake air 6 forms a spray flow including droplets, and cools the intake air before flowing into the compressor 1. Droplets contained in the intake air are vaporized inside the compressor 1,
Cool compressed air.

Accordingly, the output of the gas turbine can be more efficiently recovered by the synergistic effect of the two principles of the increase in the intake air mass flow rate due to the cooling of the intake air and the decrease in the compressor work.

More specifically, if the spray nozzles are arranged in the intake chamber at a distance from the compressor inlet by an appropriate distance,
Since a part of the spray water evaporates and cools the intake air to a temperature near the wet bulb temperature, the same effect is produced to a greater or lesser extent than when an air cooler is installed in the intake passage. Compressor 1 and compressor 1
The working fluid of the compressor 1 can be effectively cooled both outside and outside, and the increased output can be increased when the spray nozzle 11 is disposed near the compressor inlet when the distance is greater.

FIGS. 5 and 6 show the state change of the working fluid and the relationship between the intake air temperature and the intake air mass flow rate in the process in which the outside air is guided to the compressor 1 and compressed.

FIG. 5 shows a state change when the outside air condition is 30 ° C. and 70% humidity (RH).

The outside air condition is indicated by a point A. Assuming that the state of the outside air is humidified and cooled along the iso-wet bulb temperature line to reach a saturated wet state before flowing into the compressor, the intake air moves to the state B at the inlet of the compressor 1. The humidity of the gas introduced into the compressor 1 by spraying the droplets is preferably increased to about 90% or more from the viewpoint of increasing vaporization before the introduction of the compressor. From the viewpoint of further cooling the intake air, it is preferable to further set it to 95% or more. The droplets that have not been vaporized in the intake chamber 10 are continuously vaporized during the compression process from B to C.
Assuming that the vaporization process keeps a saturated state, the boiling is completed in the state C, and in the process from C to D, a single-layer compression process starts and the temperature rises. Assuming that the vaporization is an isentropic change, the end point of boiling reaches the supersaturated state of state C '. Actually, since the vaporization rate from the droplet is finite, it is considered that the state change is thermally non-equilibrium and deviates from the saturation line and follows the locus of the broken line. On the other hand, in the normal compression process, the state changes from A to D '.
Follow the trajectory of.

In FIG. 5, assuming that the temperature at A is T1 and the temperature at B is T1 ', the increase in the intake air flow due to the temperature drop from T1 to T1' is shown schematically in FIG. From W to W '. The remaining droplets are supplied to the compressor 1
By being introduced into the inside and being vaporized, the work of the compressor 1 is reduced.

FIG. 9 shows the relationship between the amount of water spray and the rate of increase of the gas turbine output. FIG. 9A shows a change in the output relative value with respect to the intake air temperature, and FIG. 9B shows a relationship between the spray amount and the increased output.

For example, the calculation conditions are as follows.
3% relative humidity, compressor air flow characteristics 417 kg / s, compressor polytrop efficiency 0.915, turbine adiabatic efficiency 0.8
9, These values are obtained when the combustion temperature is 1290 ° C., the compressor bleed amount is 20%, the discharge pressure is 1.48 MPa, and the vaporization stage pressure is 0.25 MPa. When room temperature water is sprayed, 0.35% of the intake flow rate is vaporized in the intake chamber before flowing into the compressor. As a result, the intake air temperature is reduced and the air density is increased, and as a result, the intake air mass flow rate of the compressor is increased by several percent,
Contributes to increased power of gas turbines. The remainder of the spray water is sucked into the compressor as droplets along with the airflow and vaporized inside, thereby contributing to a reduction in work of the compressor.

2.3% The rate of improvement in thermal efficiency during spraying is 2.8% as a relative value. The amount of water consumed to restore the gas turbine output to the output during 5 ° C. base load operation is about 2.3 wt% of the intake mass flow rate. As described above, the breakdown of the increased output when the operation for restoring the gas turbine output to the maximum value is about 35% based on the cooling before entering the compressor 1 and about 35% based on the cooling due to the internal vaporization of the compressor. About 3
7%, the difference between the amount of working fluid passing through the turbine and the compressor,
And the increase in low pressure specific heat due to the inclusion of water vapor was estimated to be about 28%.

Although not shown on the scale of the figure, it is possible to further increase the amount of spray water to obtain an increased output up to the authorized output level at a spray flow rate of about 5 wt%. As the spray amount increases, the effect of vaporizing water droplets in the compressor 1 has a greater effect on the output increase than the effect (cooling effect) outside the compressor 1.

FIG. 12 shows the relationship between the spray amount and the difference between the compressor outlet temperatures before and after spraying. It can be seen that vaporization and cooling before entering the compressor 1 can be performed efficiently with a small flow rate.
The ultimate humidity of the intake air flowing into the inlet of the compressor 1 was about 95%. The solid line shows two conditions that the absolute humidity of the outlet gas of the compressor 1 and the enthalpy of the outlet gas of the compressor 1 obtained by assuming that all the liquid droplets flowing into the compressor 1 are vaporized are equal to the values before spraying. Shows the difference between the outlet gas temperature of the compressor 1 calculated from the above and the temperature before spraying. This line is without power reduction. However, the actual value indicated by a white circle (broken line for easy understanding) is higher than this, and power reduction actually exists. This is because the amount of temperature drop due to vaporization is amplified in the compression process in the paragraphs after the vaporization point.

From this, it is preferable that the amount of the droplet introduced into the compressor 1 by the spray nozzle 11 is larger at the former stage than at the latter stage.
It is considered that the liquid droplets introduced into the liquid are mainly vaporized in the former stage to be effective in reducing the power.

The droplets are sprayed to such an extent that the temperature of the compressed air discharged from the compressor 1 is lowered by 5 ° C. or more from before the spraying.
From the viewpoint of further increasing the output, the temperature is reduced to 25 ° C. or more. The upper limit can be determined from a practical point of view. For example, it is appropriate to set the temperature to 50 ° C. or less.

The seventh embodiment will be described with reference to FIG.

The seventh embodiment differs from the first or second embodiment in that a mechanism for controlling the temperature of the spray water droplet is provided.

In the seventh embodiment, for example, a combined plant is used. In addition to the configuration of the gas turbine described above, the exhaust heat recovery boiler 3 using the exhaust gas of the turbine 2 as a heat source
0 is set. Although not shown, a steam turbine driven by steam generated by the exhaust heat recovery boiler 30 is provided. Further, at least a generator driven by a gas turbine or a steam turbine is provided. Air supply means 12
Is provided with a path for supplying steam generated in the exhaust heat recovery boiler 30 to the spray nozzle 11, and a control valve 14c is disposed in the path.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
And the water in the water supply tank 17 is filled with the control valve 15 having a predetermined opening degree.
, And fine droplets are ejected from the spray nozzle 11 through the force water means 13. At this time, the steam supply amount is controlled by the control valve 14.
Adjust with c.

When the compressed air is supplied to the spray nozzle 11 at the same time, the spray nozzle 11
The amount of compressed air can be adjusted by the control valve 14a in the path to the compressed air.

As a result, the heating temperature can be adjusted.
Adjust the temperature of the spray droplets. A spray flow including the intake air 6 and droplets having a desired temperature is formed, and after cooling the intake air, flows into the compressor 1. Droplets included in the intake air are vaporized inside the compressor 1 to cool the compressed air.

According to this embodiment, the output of the gas turbine of the first embodiment and the thermal efficiency of the gas turbine can be improved, and the vaporization rate of the droplet can be controlled by adjusting the temperature of the spray liquid. it can. If the water temperature is raised, the vaporization of the droplets can be shifted to the front stage of the compressor. As a result, the workload of the compressor 1 can be further reduced. The temperature of the water droplets to be sprayed fluctuates depending on the conditions, or a practical range of 10 to 80 ° C. is practical. As a method of controlling the water temperature, in addition to a method of causing steam to flow into the spray nozzle, control of the bleed gas temperature of the compressor, and control by providing a temperature control means such as a heater 51 at an appropriate place of the water supply means 13 It is also possible to take the method of doing.

When the air supply means 12 is not provided, it is effective to provide the heater 51. The method of supplying steam shown in the figure is effective in a combined plant, particularly a cogeneration plant, because steam can be effectively used. This is effective because the steam of the exhaust heat recovery boiler 30 can be used without disposing a separate heating means or the like.
Incidentally, a separate steam generating means may be provided.

Alternatively, it is effective to mix a flammable liquid having a high vapor partial pressure into the spray water. For example, a mixed liquid of water and alcohol is ejected from the spray nozzle 11. For example, antifreeze is used. When glycerin or ethylene glycol is added to water to form a spray, the spray is volatilized at a low temperature, so that the effect of reducing the power of the compressor is great. In addition, since the freezing point is lowered, there is no fear of freezing of droplets even in winter or the like.

As a specific configuration, glycerin or ethylene glycol can be added to the water supply tank 17 at the time of winter or the like to prepare a mixed solution.

The eighth embodiment will be described with reference to FIG. The gas turbine of the present embodiment can improve the thermal efficiency even at the time of partial load.

The eighth embodiment is different from the first or second embodiment mainly in that steam is supplied to the intake air introduced into the compressor 1.

Specifically, a path is provided for supplying the steam generated in the exhaust heat recovery boiler 30 to the air supply means 12 so that the steam supplied from the spray nozzle 11 can be ejected.

The intake air 6 passes through the louver 9 and passes through the intake chamber 10.
, The control valve 15 is closed, and the steam generated in the exhaust heat recovery boiler 30 is supplied from the control valve 14 c having a predetermined opening to the air supply means 12.
Through the spray nozzle 11. If the air supply means 12 is not provided and only the water supply means 13 is provided, the water vapor is supplied from the water supply means 13 to the spray nozzle 11 instead of the water supply from the water supply tank 17 (not shown). Is also good. Alternatively, although not shown, a separate steam supply nozzle to which steam generated in the exhaust heat recovery boiler 30 may be provided in addition to the spray nozzle 11. The amount and temperature of steam to be ejected to the intake air vary depending on the steam source, but are adjusted according to the target intake air temperature entering the compressor 1.

The intake air 6 having reached a desired temperature flows into the compressor 1.

According to the eighth embodiment, the following can be mentioned as a method of improving the thermal efficiency in the partial load operation.

For example, in a winter season or the like, when the power demand is so small that a partial load operation has to be performed, by injecting steam into the intake air as described above, the intake air temperature is about 10 ° C., for example. Can be supplied to the compressor 1 after being raised to about 50 ° C.

By injecting steam into the inlet of the compressor, the temperature of the intake air can be raised, so that the density of the air decreases and the mass flow rate of the intake air of the compressor decreases. The turbine output can be reduced. This is because the base load operation can be performed while avoiding the partial load operation of the gas turbine.

In this embodiment, even when the required load is reduced and the output is reduced, the operation can be performed with higher thermal efficiency than the conventional partial load operation method such as IGV adjustment, so that the demand is reduced according to the season. Sometimes effective. Especially,
In a plant such as a combined cycle plant or a cogeneration plant that generates steam from gas turbine exhaust gas, surplus steam can be contributed to power generation, so that the surplus steam can be effectively used.

In some cases, separate steam generating means may be provided instead of steam from the exhaust heat recovery boiler.

A ninth embodiment will be described with reference to FIG.

This embodiment is different from the first or second embodiment in that a means such as a nozzle for feeding compressed air to the intermediate stage of the compressor is further provided.

In the ninth embodiment, the same basic configuration as in the first embodiment can be applied. A flow control valve 47 is provided in a line 59 for feeding the compressed air supplied from the compressed air source 43 to an intermediate stage of the compressor 1. The compressed air is supplied from a compressed air source 43. This compressed air source 4
3 can be supplied from an externally installed compressor or an atomizing compressor for fuel injection. Alternatively, although the effect is slightly inferior, air may be recirculated from the discharge section of the compressor 1. In this case, the lower the temperature of the air supply, the higher the efficiency. Therefore, it is desirable to provide the cooling means 48 in the middle of the air supply line 59.

When the water droplets 37 evaporate in the compressor 1 to cool the air, the density of the air increases, and the axial flow velocity 46 decreases. Therefore, as shown in FIG. 10, the velocity triangle is distorted, and the air flow to the wing 45 deviates from the design value as shown by 46a to 46b, and the flow separates along the wing surface. The heat insulation efficiency is reduced. When the heat insulation efficiency decreases, the discharge temperature of the compressor 1 increases, and as a result, the effect of reducing the work of the compressor decreases. This phenomenon is considered to be more remarkable as the amount of spray water increases, so that the amount of spray is limited in practical terms. In order to solve this, it is only necessary to recover the axial flow velocity by sending air to the compressor 1. The position of the air supply is effective when the vaporization of the water droplet is almost completed. It is desirable that this air supply amount be a function of the spray amount so that the orbital velocity is maintained at the design value even if the spray amount changes.

In response to the increase in the target output based on the load request signal 25, the opening of the water flow control valve 15 is increased by the command signal from the function generator 24, and the opening of the flow control valve 47 is increased. I do.

The amount of water supplied from the regulating valve 15 and the amount of compressed air supplied from the flow regulating valve 47 can be represented by a monotonically increasing function.

When the output is reduced, control is performed so as to decrease the respective valve openings.

In this way, the restriction on the spray amount is eased, and the compressor power reduction per unit air flow is increased in order not to reduce the heat insulation effect. Furthermore, an increase in the working fluid due to the air supply also has the effect of increasing the power increase of the gas turbine.

The tenth embodiment of the present invention will be described with reference to FIG.

This embodiment relates to a gas turbine of a type in which the bleed air of the compressor 1 is supplied to a cooling flow path formed in the turbine blades to cool the turbine blades, and corresponds to the temperature of the bleed air of the compressor. Thus, the bleed air flow rate is controlled.

Instead of sending compressed air to the middle stage of the compressor 1 for cooling the turbine blades, the amount of air extracted from the extraction line 56 of the compressor 1 provided for cooling the turbine blades is determined by the amount of the extracted gas. By decreasing in proportion to the temperature drop,
The flow rate after the bleeding stage can be substantially increased.

Accordingly, the flow control valve 5 is connected to the bleed line 56.
An electric valve with 5 or an intermediate opening is provided.

When the water droplets evaporate in the compressor 1 to cool the air, the temperature of the bleed air drops, so that the required amount of air for the bleed compressor to cool the blades of the turbine is small. The relationship between the monotonically decreasing function of the bleed volume control valve 55 and the command signal from the medium-term volume control function generator 58 corresponding to the decrease of the target bleed volume based on the temperature signal of the temperature detector 57 that detects the bleed temperature can do.

When a motor-operated valve with an intermediate opening is used, the opening of the valve is adjusted to a predetermined value according to the bleed air temperature when it reaches a set value.

By reducing the amount of bleed air, it is possible to increase the compressor air volume in the paragraphs after the bleed point, so that the axial flow speed is recovered, the adiabatic efficiency of the compressor is improved, and the gas temperature at the compressor outlet is reduced. The power of the compressor per unit air volume is reduced. Also,
As the amount of air supplied to the turbine increases, the shaft output increases. These effects further increase both power and thermal efficiency.

With respect to the embodiment relating to the gas turbine, the gas turbine is used, and further, an exhaust heat recovery boiler that generates steam using exhaust gas from the turbine as a heat source, and is driven by steam generated by the exhaust heat recovery boiler. And a combined cycle plant including the steam turbine.

Thus, the output of the combined cycle plant and the thermal efficiency can be improved with the simple apparatus suitable for practical use as described above.

Further, in each of the above embodiments, the reduction in the power required of the compressor can be reduced even when viewed as a single compressor.
It can be realized by a simple device.

Specifically, the above-described main effects described above can be obtained by spraying the above-described fine droplets on the intake air supplied to the compressor inlet and vaporizing the same in the compressor. In this case, as the gas flowing into the compressor as intake air, in addition to air, ammonia, chlorofluorocarbon and the like can be applied. As the droplet to be sprayed, in the case of air, water or the like can be applied as shown in the example of the gas turbine described above. Liquid ammonia can be sprayed in the case of a compressor using ammonia as the intake air, and liquid Freon can be sprayed in the case of using a fluorocarbon gas as the intake air.

In comparison with the case where the droplets and sprays are not contained in the intake air entering the compressor, a part of the air is vaporized before entering the inlet of the compressor 1 to cool the intake air, and water droplets continuously flow from the inlet of the compressor. Therefore, the gas temperature in the compressor continuously decreases. Also, the discharge temperature decreases. Furthermore, the weight flow rate increased due to the vaporization of the droplets introduced into the compressor in the compression vertical machine, and when the vaporization was almost completed in the compressor, the gas in the compressor was subjected to adiabatic compression and increased as a working fluid. Has the same effect as. As the spray amount is increased, the compressor power ratio (isentropic compression work of dry air / compression work in isentropic two-phase compression process including vaporization of droplets) can be further reduced.

Further, in each of the above-described embodiments, even when viewed as a liquid spraying device for spraying liquid droplets into the intake air of a compressor of a gas turbine, it is easy to improve the output and the thermal stress of the gas turbine provided with the device. It can be realized by a simple device.

[0187]

According to the present invention, a gas turbine and a combined gas turbine capable of realizing both an improvement in output and an improvement in thermal efficiency by spraying liquid droplets into intake air introduced into the inlet of a compressor with simple equipment suitable for practical use. A plant, a compressor and a droplet spraying device can be provided.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of an embodiment of the present invention.

FIG. 2 is a diagram showing one embodiment of the present invention.

FIG. 3 is a diagram showing one embodiment of the present invention.

FIG. 4 is a diagram showing a temperature distribution of compressed air in the compressor.

FIG. 5 is a diagram showing a relationship between air temperature and absolute humidity in a compression process.

FIG. 6 is a diagram showing a relationship between intake air temperature and intake air mass flow rate.

FIG. 7 is a comparison of a thermal cycle diagram between the present invention and another method.

FIG. 8 is a detailed structural view of a gas turbine.

FIG. 9 is a graph showing the relationship between the amount of water spray and the rate of increase in gas turbine output.

FIG. 10 shows the relationship between axial flow velocity and velocity triangle.

FIG. 11 is a schematic view of an arrangement of a spray nozzle in an intake chamber.

FIG. 12 is a schematic diagram of a compressor outlet temperature difference before and after spraying.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... turbine, 3 ... Generator, 4 ... Transmission end
5: Combustor, 6: Intake, 7: Exhaust, 8: Stack, 9 ...
Louver, 10 ... intake chamber, 11 ... spray nozzle, 12 ... air supply means, 13 ... water supply means, 14, 15 ... control valve, 16 ... water supply pump, 17 ... water supply tank, 19 ... cooler, 20 ... intake temperature, 21: compressor outlet air temperature, 22: combustion temperature,
23 ... Exhaust temperature, 24 ... Function generator, 25 ... Load request signal, 29 ... Pressurizer, 30 ... Exhaust heat recovery boiler, 31 ... Moisture recovery device, 32 ... Heat exchanger, 35 ... Air cooler, 36 ...
External cold heat source, 37 ... droplets, 48 ... cooling means.

──────────────────────────────────────────────────の Continued on the front page (51) Int.Cl. ⁶ Identification code FI F02C 6/18 F02C 6/18 A 9/18 9/18

Claims (35)

[Claims] 1. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, the droplets are sprayed on the gas supplied to the compressor, the temperature of the gas entering the compressor is lowered from the outside air temperature, and the gas is introduced into the compressor together with the gas, and the inside of the compressor is discharged. A gas turbine, comprising: a spray device configured to evaporate the sprayed droplets while flowing down. 2. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas from the combustor. In a gas turbine, spraying droplets on a gas supplied to the compressor, vaporizing a part of the gas before being introduced into the compressor, and introducing the gas into the compressor together with the gas, A gas turbine, comprising: a spray device configured to further vaporize droplets introduced into the compressor while flowing down the interior of the compressor. 3. The gas turbine according to claim 1, wherein the gas is air, and an intake chamber provided with an air filter through which air supplied to the compressor flows is disposed upstream of the compressor. A gas turbine, wherein the spray device is arranged in an intake chamber and downstream of the air filter. 4. The gas turbine according to claim 1, wherein the gas is air, and the air supplied to the compressor flows through the intake chamber, which includes an air filter and a silencer downstream of the air filter. A gas turbine arranged upstream of a compressor, wherein the spray device is arranged in the intake chamber and downstream of the silencer. 5. The gas turbine according to claim 1, wherein the gas is air, and an intake chamber provided with an air filter through which air supplied to the compressor flows is disposed upstream of the compressor. A gas turbine, wherein the spray device is arranged in an intake chamber and near a boundary with the compressor. 6. The gas turbine according to claim 1, further comprising cooling means for cooling gas supplied to the compressor, on an upstream side of the spraying device. 7. The gas turbine according to claim 1, wherein a water recovery means for recovering water contained in the exhaust gas is disposed in a path of the exhaust gas flowing out of the turbine, and the recovered water is supplied to the spray device. A gas turbine comprising: 8. The gas turbine according to claim 7, wherein said water recovery means is a heat exchanger using liquefied natural gas as a refrigerant. 9. The gas turbine according to claim 1, wherein the droplet contains water and alcohol. 10. The gas turbine according to claim 1, further comprising a control device that controls an amount of droplets sprayed from said spraying device in accordance with a gas turbine output. 11. The gas turbine according to claim 1, wherein the humidity of the gas introduced into the compressor is increased to 90% or more by spraying the droplets. 12. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A gas turbine, comprising: a spraying device for spraying droplets having a particle diameter of 50 μm or less mainly to a gas supplied to the compressor, on an upstream side of the compressor. 13. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A gas turbine, comprising: a spray device for spraying droplets having an average particle diameter of 30 μm or less to a gas supplied to the compressor, on an upstream side of the compressor. 14. A compressor for compressing and discharging supplied gas, a combustor for burning air and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, a spray device for spraying droplets to be sprayed on air supplied to the compressor and evaporating in the compressor is disposed upstream of the compressor, and the spray device atomizes the droplets. A gas turbine, comprising: atomizing means for causing a gas to be atomized. 15. A compressor for compressing and discharging supplied air, a combustor for burning air and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, a spray device for spraying droplets to air supplied to the compressor is disposed upstream of the compressor, and the spray device supplies a pressurized gas for atomizing the droplets. A gas turbine comprising pressurized gas supply means. 16. A compressor for compressing and discharging supplied air, a combustor for burning air and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, a spray device for spraying droplets to air supplied to the compressor is disposed upstream of the compressor, and an intermediate stage of the compressor and the spray device are communicated with each other. A gas turbine, comprising: a path for supplying bleed air to the spray device; and a regulating valve provided in the path for supplying the bleed air. 17. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, a spray device that sprays droplets vaporized in the compressor onto a gas supplied to the compressor is arranged upstream of the compressor, and the spray device sprays the droplets. ,
A gas turbine, wherein the temperature of gas discharged from the compressor is lowered by 5 ° C. or more from before spraying the droplets. 18. A compressor for compressing and discharging supplied air, a combustor for burning air and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. An air filter and a silencer provided downstream of the air filter, wherein an intake chamber through which air supplied to the compressor flows is arranged upstream of the compressor; A gas turbine provided downstream of the silencer for spraying droplets on air supplied to the compressor. 19. The gas turbine according to claim 18, further comprising a temperature increasing means for increasing a temperature of the liquid in a supply path of the liquid supplied to the spraying device. 20. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A gas turbine, comprising: a spraying device for spraying liquid supplied to the compressor and vaporizing the liquid in the compressor; and adjusting a temperature of the liquid in a supply path of the liquid supplied to the spraying device. A gas turbine, comprising: a temperature control device that performs temperature control. 21. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A gas turbine, characterized in that a steam supply means for supplying steam to a gas supplied to the compressor is provided upstream of the compressor. 22. A compressor for compressing and discharging the supplied gas, a combustor for burning the gas and fuel discharged from the compressor, and a turbine driven by the combustion gas of the combustor. In the gas turbine, a spray device for spraying liquid supplied to the compressor and evaporating droplets in the compressor is disposed upstream of the compressor, and the spray device has a weight flow rate of the gas. 0.2 or more to 5.
A gas turbine characterized by spraying droplets of 0 wt% or less. 23. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A gas turbine, comprising: a spray device for spraying droplets on gas supplied to the compressor, on an upstream side of the compressor; and a pressurized gas supply unit for supplying a pressurized gas to an intermediate stage of the compressor. A gas turbine comprising: 24. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. In the gas turbine, a spray device for spraying droplets to gas supplied to the compressor is provided on an upstream side of the compressor, and the amount of droplets sprayed from the spray device is adjusted according to a gas turbine output. A gas turbine comprising a control device for controlling. 25. A compressor for compressing and discharging the supplied gas, a combustor for burning gas and fuel discharged from the compressor, a turbine driven by combustion gas of the combustor, A gas turbine comprising: a turbine blade having a cooling gas flow path inside a gas turbine therein; and a cooling path for guiding bleed air of the compressor to a cooling flow path of the turbine blade. A gas turbine provided with a spraying device for spraying liquid droplets onto the gas to be blown, and a control device for controlling the flow rate of the bleeding air in accordance with the temperature of the bleeding air of the compressor. . 26. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, a turbine driven by combustion gas from the combustor, A spray device for spraying droplets onto a gas supplied to a compressor, the method comprising: operating a gas turbine in accordance with a gas turbine output. Characteristic method of operating gas turbine. 27. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A combined cycle plant comprising: a gas turbine, a waste heat recovery boiler that generates steam using exhaust gas from the turbine as a heat source, and a steam turbine driven by generated steam from the waste heat recovery boiler. The droplets are sprayed on the gas supplied to the compressor, the temperature of the gas entering the compressor is lowered from the outside air temperature, the gas is introduced into the compressor together with the gas, and the spray is generated while flowing down the compressor. A combined cycle plant comprising a spraying device for causing the discharged droplets to evaporate. 28. A compressor for compressing and discharging the supplied gas, a combustor for burning gas and fuel discharged from the compressor, a turbine driven by combustion gas of the combustor, The droplets are sprayed on the gas supplied to the compressor, a part of the gas is vaporized before the gas is introduced into the compressor, and the gas is introduced into the compressor together with the gas, while flowing down the compressor. A gas turbine provided with a spray device for further evaporating droplets introduced into the compressor; an exhaust heat recovery boiler for generating steam using exhaust gas from the turbine as a heat source; and an exhaust heat recovery boiler And a steam turbine driven by generated steam. 29. A compressor to which a gas is supplied and which compresses and discharges the supplied gas, wherein droplets are sprayed on a gas supplied to an inlet of the compressor, and a temperature of the gas entering the compressor. Lower than the outside air temperature,
A compressor, comprising: a spray device that is introduced into the compressor together with the gas so that the sprayed droplets are vaporized while flowing down the compressor. 30. A compressor to which a gas is supplied and which compresses and discharges the supplied gas, wherein the gas supplied to the inlet of the compressor mainly has a particle diameter of 50%.
A compressor characterized in that a spraying device for spraying droplets of μm or less is arranged upstream of the compressor. 31. A compressor to which a gas is supplied and which compresses and discharges the supplied gas, wherein a gas supplied to an inlet of the compressor is sprayed, and droplets vaporized in the compressor are sprayed. A compressor that is disposed upstream of the compressor, and the spraying device includes atomizing means for atomizing the droplets. 32. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A droplet spraying device for spraying droplets onto a gas supplied to the compressor of a gas turbine, wherein the droplets are sprayed, the temperature of the gas entering the compressor is lowered from the outside air temperature, and the gas is cooled together with the gas. A droplet spraying device, wherein the droplets are introduced into a compressor, and the sprayed droplets are vaporized while flowing down in the compressor. 33. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. Droplet spraying device for spraying droplets on a gas supplied to the compressor from an upstream side of the compressor of a gas turbine, wherein the droplets mainly spray particles having a particle size of 50 μm or less. Drop spray device. 34. A compressor for compressing and discharging supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. A droplet spraying device for spraying droplets on a gas supplied to the compressor from an upstream side of the compressor of the gas turbine, wherein the droplets are droplets vaporized in the compressor, and A droplet spraying device comprising: atomizing means for atomizing the droplet. 35. A compressor for compressing and discharging a supplied gas, a combustor for burning gas and fuel discharged from the compressor, and a turbine driven by combustion gas of the combustor. Spraying device for spraying droplets on gas supplied to the compressor from the upstream side of the compressor of the gas turbine, wherein the control device controls the amount of droplets sprayed according to the output of the gas turbine. A droplet spraying device comprising: