JP4254508B2 - Gas turbine system - Google Patents

Description

  The present invention belongs to a technical field in which moisture is added to a gas turbine power generation system to achieve increased output and high efficiency of the system.

  As a conventional technique related to a gas turbine system using humidified air to which moisture is added by a spray nozzle, high-temperature water is sprayed by a nozzle on a pipe as an air flow path connecting a compressor and a regenerative heat exchanger (hereinafter referred to as a regenerator). A humidifier structure is described, and a spray system configuration that collects non-evaporated water in the humidifier and reuses the water is described (for example, see Patent Document 1).

  Furthermore, a structure is described in which a spray water heat exchanger is installed in the pipe connecting the compressor and the regenerator, the hot water is sprayed to the vertical humidifier with the spray water at a high temperature, and room temperature water is supplied to the intake air of the compressor. A structure for spraying is also described (for example, see Patent Document 2).

  A spray water heat exchanger is installed in the pipe connecting the compressor and the regenerator, and a heat exchanger that heats the spray water with the gas turbine exhaust gas is installed. A structure for generating humid air is described (for example, see Patent Document 3).

  In order to use humidified air to which moisture has been added, a method is described in which water or steam is injected into the regenerator that utilizes gas turbine exhaust heat (see, for example, Patent Document 4).

  A pipe that connects the compressor and regenerator is equipped with a humidifier that sprays high-temperature water with a spray nozzle and a heat exchanger that is provided downstream of the humidifier, and the connection position with the regenerator is changed depending on the outlet temperature of the humidifier (For example, refer to Patent Document 5).

  In order to configure the humidification system described above, a spray nozzle that atomizes and sprays fine water droplets is required. However, as a commercially available nozzle, there is one called “Moya Spray Nozzle M19” of Kyoritsu Alloy Manufacturing Co., Ltd. in Japan. The performance is such that the spray pressure is 7 MPa, the amount of water is 0.125 L / min, and the spray water droplet diameter is 16 μm in arithmetic mean (corresponding to about 25 μm in SMD) (for example, see Non-Patent Document 1). SMD is an index representing a sprayed water droplet diameter used in water droplet diameter measurement with a laser and is a Sauter mean particle diameter (Sauter mean diameter).

JP 2000-282894 A JP 2002-138852 A JP 2003-3861 A Japanese Patent Laid-Open No. 11-324710 JP 2001-132473 A Product catalog of Kyoritsu Alloy Mfg. Co., Ltd., CAT. NO. 9802-9901 “Moya Spray Nozzle M19”

  What is common to the conventional technology of the humidifier configuration installed in the middle of the piping as the air flow path connecting the compressor and regenerator in the gas turbine power generation system is that there are many components and high cost and large size is there. Moreover, in these conventional technologies, a spray nozzle that sprays fine water droplets is used as a humidifier configuration. However, in order to generate high-humidity air by spraying high-temperature air in a narrow area and instantly evaporating, fine water droplets are used. A spray nozzle that sprays a large amount of is required.

  Furthermore, in a gas turbine system using high-humidity air, a large amount of water is added to obtain humidified air, but the required humidification ratio cannot be obtained only by humidification between the compressor and the regenerator. Can be considered. There is a method of injecting water or steam in the middle of a regenerator using gas turbine exhaust heat, but there is a problem in thermal stress due to water injection distribution to the heat transfer tubes of the regenerator.

  Moreover, in the conventional humidification structure, since there are few mixing parts of high temperature air and spray water, heat exchange cannot fully be performed, but a humidification ratio is small, and it is possible that the humidifier exit temperature becomes high. If the humidifier outlet temperature becomes high, the effective utilization of gas turbine exhaust heat is impaired, and the efficiency may be lowered.

  An object of the present invention is to increase the amount of humidification into a gas turbine system.

  A first means for solving the problems of the present invention includes a compressor that compresses and discharges air sucked from an air chamber, an air flow path for passing compressed air discharged from the compressor, and the air flow path The combustor that is supplied with the compressed air and the fuel that has passed through the combustion chamber to perform a combustion action, the turbine that is driven by the combustion gas of the combustor, the generator that is driven by the turbine, and the compression that is performed by the exhaust gas A regenerative heat exchanger that heats air; an upstream header that distributes the compressed air to a heat transfer flow path of the regenerative heat exchanger; a first spraying means that sprays liquid into the air chamber; and A gas turbine system having a second spraying means for spraying liquid and a third spraying means for spraying liquid in the upstream header, and increasing the humidification ratio by spraying the liquid at a plurality of locations of the gas turbine system. The In addition, by spraying the liquid in the upstream header, the spray droplets are also distributed along with the distribution of the compressed air from the upstream header to the heat transfer flow path, and the spray droplets are efficient in the regenerative heat exchanger. The moisture in the compressed air can be increased by evaporation. In addition, compared with the case where liquid is directly put into the heat transfer flow path of the regenerative heat exchanger, the generation of thermal stress in the regenerative heat exchanger is reduced, and when there are multiple heat transfer flow paths of the regenerative heat exchanger, a plurality of heat transfer flow paths are used. The distribution structure to the heat transfer channel can be simplified.

The second means includes a compressor that compresses and discharges the air sucked from the air chamber, an air passage through which the compressed air discharged from the compressor passes, and the compressed air and fuel that have passed through the air passage. Are supplied with the combustion gas, the turbine driven by the combustion gas of the combustor, the generator driven by the turbine, and the regenerative heat exchanger that heats the compressed air with the exhaust gas, The compressed air is distributed to the heat transfer flow path of the regenerative heat exchanger, and an upstream header whose lower part is extended below the lowermost heat transfer flow path of the heat transfer flow path, and a liquid is supplied to the air chamber. A first spraying means for spraying, a second spraying means for spraying a liquid in the air flow path, or a third spraying means for spraying a liquid in the upstream header, At least one Spraying means spray pressure above 4 MPa, flow rate 1L /
a gas turbine system having a spray nozzle having a performance of not less than min and an average particle diameter of Sauter of 30 μm or less, supplying droplets in an atomized state having an average particle diameter of Sauter of 30 μm or less to the air chamber of 1 L / min or more. The amount of moisture that is sucked into the compressor accompanying the air in the air chamber is increased.

Third hand stage, a compressor compressing and discharging sucked from the air chamber the air, and an air flow passage through which compressed air discharged from said compressor, and the compressed air having passed through the said air passage A combustor that is supplied with fuel to perform a combustion operation, a turbine that is driven by combustion gas of the combustor, a generator that is driven by the turbine, and a regenerative heat exchanger that heats the compressed air with the exhaust gas An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger, a plurality of first spray means that can select a system for spraying and spraying liquid into the air chamber, and the air flow A plurality of second spraying means capable of selecting a system for spraying and spraying liquid in the road; and a plurality of third spraying means capable of selecting a system for spraying and spraying liquid in the upstream header; The This is a gas turbine system that sprays liquid at multiple locations in the gas turbine system to increase the humidification rate and distributes compressed air from the upstream header to the heat transfer flow path by spraying liquid into the upstream header. Accordingly, the spray droplets are distributed, and the moisture in the compressed air can be increased by the efficient evaporation of the spray droplets in the regenerative heat exchanger. In addition, compared with the case where liquid is directly put into the heat transfer flow path of the regenerative heat exchanger, the generation of thermal stress in the regenerative heat exchanger is reduced, and when there are multiple heat transfer flow paths of the regenerative heat exchanger, a plurality The distribution structure to the heat transfer channel can be simplified. Furthermore, by selecting the number of systems to be sprayed according to the spraying means for performing the liquid spraying and stopping and the liquid spraying of each spraying means of the first spraying means, the second spraying means, and the third spraying means, Humidification control according to the situation of the turbine system can be achieved by performing fine control of the degree of humidification.

The fourth hand stage, a compressor compressing and discharging sucked from the air chamber the air, and an air flow passage through which compressed air discharged from said compressor, and the compressed air having passed through the said air passage A combustor that is supplied with fuel to perform a combustion operation, a turbine that is driven by combustion gas of the combustor, a generator that is driven by the turbine, and a regenerative heat exchanger that heats the compressed air with the exhaust gas An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger, a first spraying means for spraying liquid into the air chamber, and a flow rate of the liquid supplied to the first spraying means. A first flow meter for measuring, a first measuring means for measuring the liquid drain liquid from the air chamber, a second spraying means for spraying the liquid into the air flow path, and the second spraying means The flow rate of the liquid to be measured A second flow meter, a second metering unit for metering the liquid drain liquid from the air flow path, a third spray unit for spraying the liquid into the upstream header, and the third spray unit. A gas turbine system comprising: a third flow meter for measuring a flow rate of the supplied liquid; and a third measuring unit for measuring a drain liquid of the liquid from the upstream header, and a plurality of locations of the gas turbine system In addition to increasing the humidification rate by spraying liquid with the liquid, spraying the liquid in the upstream header also causes the spray droplets to be distributed along with the distribution of the compressed air from the upstream header to the heat transfer flow path and regenerated The moisture in the compressed air can be increased by efficient evaporation of the spray droplets with the heat exchanger. In addition, compared with the case where liquid is directly put into the heat transfer flow path of the regenerative heat exchanger, the generation of thermal stress in the regenerative heat exchanger is reduced, and when there are multiple heat transfer flow paths of the regenerative heat exchanger, a plurality of The distribution structure to the heat transfer channel can be simplified. Furthermore, it is possible to grasp the entire humidification ratio of the turbine system based on the difference between the total sum measured by the first to third flow meters and the total sum measured by the first to third metering means.

  According to the present invention, a large amount of moisture can be contained in the air in the gas turbine system.

  The embodiment of the present invention includes means for solving the following five problems (A) to (E). (A) There is no nozzle that sprays a large amount of fine water droplets in the gas turbine system. (B) The required humidification ratio cannot be obtained only by humidification between the compressor and the regenerator of the gas turbine system. (C) The humidifier outlet temperature of the gas turbine system becomes high, and the gas turbine exhaust heat cannot be effectively used. (D) In the humidification method in which water is injected in the middle of the heat transfer tube of the regenerator of the gas turbine system, there is a problem in the thermal stress caused by the water injection distribution to the heat transfer tube. (E) There are many components for obtaining the required humidification ratio of the gas turbine system, which is large in size and high in cost.

  As a means for solving the problem (A), a high-pressure one-fluid atomizing nozzle previously developed by the inventors and applied for a patent in Japanese Patent Application No. 2002-319443 as a spray nozzle employed in a humidifying means of a gas turbine system is used. To do. This nozzle is small with a maximum diameter of about 9 mm, and its performance is a nozzle with a spray water volume of about 1 L / min, a spray water droplet diameter [SMD] of 20 μm or less, and a spray water volume of about 2 to 3 L / min. Spray nozzle droplet size [SMD] is 30 μm or less. These nozzles have 10 to 30 times the amount of water as compared to the haze spray nozzles shown in the prior art.

  Problems (B), (C), and (D) are solved by humidifying the compressor and regenerator of the gas turbine system as much as possible, and further humidifying the regenerator using the exhaust heat of the gas turbine. .

  Here, as a means for maximizing humidification between the compressor and the regenerator of the gas turbine system, a spray nozzle is installed in a piping portion that is a flow path of the compressed air between the compressor and the regenerator to finely adjust the high-temperature air flow. Spraying water droplets and evaporating them to humidify them, but if you just spray them, they are entrained in the flow of air, and heat exchange cannot be performed sufficiently, so the humidification ratio decreases and the humidifier outlet temperature also increases. Then, an orifice that generates a contracted flow is installed upstream from the position where the spray nozzle is installed, and high-temperature air and spray water droplets are sufficiently heat-exchanged in the mixing area using the pressure-reduced area generated downstream of the orifice to instantly evaporate. Adopt tube humidifier structure. This makes it possible to achieve maximum humidification between the compressor and the regenerator.

  In a high-humidity gas turbine system that adds moisture to the compressed air of the gas turbine system, i.e., the working fluid, the higher the humidity, the higher the efficiency can be achieved. Will occur and will adversely affect the flow path of the working fluid. Therefore, it is preferable that the humidification amount to the gas turbine system is slightly smaller than the humidity in the saturated air state.

  Considering these things, the humidification amount in the entire system is 14.1 wt% (weight ratio to the intake air flow rate). Here, humidification upstream of the compressor, i.e., intake air humidification, is 1.6 wt%, about 11% of the whole, and a pipe humidifier humidifying the compressed air between the compressor and the regenerative heat exchanger, about 7 wt%, about the whole It is 50%, and the humidification amount of about 39% is insufficient when the humidification amount of the entire system is 14.1 wt%.

  As a means for humidifying the shortage to the gas turbine system, in the embodiment of the present invention, a regenerative heat exchanger that uses exhaust heat of the gas turbine system (gas turbine exhaust heat and heat of compressed air supplied to the combustor). The structure is such that fine water droplets are sprayed directly on the header portion of the air inlet of the exchanger and uniformly flow into the heat transfer flow path of the regenerative heat exchanger. In this case as well, it is preferable to use the high-pressure one-fluid atomizing nozzle patented in Japanese Patent Application No. 2002-319443.

  Since the compressed air temperature after humidification that has passed through the above-mentioned tube humidifier is almost the vapor saturation temperature and does not contain any more moisture, new humidification between the compressor and the regenerative heat exchanger is not possible. Since it is difficult, the exhaust heat of the gas turbine system passing through the regenerative heat exchanger is used to evaporate and humidify the regenerator heat exchanger.

  As means for solving the problem (E), by constructing a high-humidity gas turbine system using the above-described means, a compact and compact system configuration with a small number of components can be achieved, and cost reduction can be achieved. be able to.

  Hereinafter, a high-humidity gas turbine system according to an embodiment of the present invention will be described in detail with reference to the illustrated embodiments. 1 is an overall structural diagram of a high-humidity gas turbine system according to an embodiment of the present invention, FIG. 2 is a shape diagram of a spray nozzle used in the high-humidity gas turbine system according to an embodiment of the present invention, and FIG. 3 is an embodiment of the present invention. 4 is a water droplet size distribution diagram when the amount of water of the spray nozzle used in the high-humidity gas turbine system is a parameter, FIG. 4 is a water droplet size distribution diagram when the spray pressure is a parameter, and FIG. 5 is the spray pressure of the nozzle used. FIG. 6 is a detailed view showing the installation and the spraying state of the intake spray nozzle in the air chamber, FIG. 7 is a detailed view of the intake spray nozzle mounting portion, and FIG. 8 is a structure provided in the pipe. FIG. 9 is a diagram showing the temperature of each part downstream of the spray nozzle as a result of testing with the system shown in FIG. 8, and FIG. 10 is a spray water droplet flow in a pipe humidifier structure in which no structure is provided in the pipe. Axial water droplet density map, diagram FIG. 1 is a diagram showing the test results of the evaporation limit humidification ratio under the complete evaporation condition in the system shown in FIG. 8, and FIG. 12 is a pipe humidifier structure according to the present invention in which an orifice for narrowing the flow path is installed upstream of the spray nozzle. FIG. 13 is a schematic view when a fine water droplet is sprayed from a nozzle installed in a header sandwiched by a flange in a high temperature air pipe. FIG. 13 is a pipe humidifier structure according to the present invention, a header is provided outside the high temperature air pipe, and a water supply pipe to the spray nozzle FIG. 14 is a schematic diagram in the case where fine water droplets are sprayed from the installation nozzle in a system in which an orifice for narrowing the flow path is installed upstream of the spray nozzle, and FIG. 14 is a schematic view of the present invention. FIG. 15 shows the temperature of each part downstream of the spray nozzle as a result of testing with the system shown in FIG. 12, which is the present invention, and FIG. 16 shows the shape of the orifice edge used in the system of FIG. FIG. 17 is a structural view of a regenerator in which a spray system according to the present invention is introduced, and FIG. 18 is a high view of the humidifier 700B structure and a pipe humidifier 700A structure in which no structure is provided in the pipe shown in FIG. It is a figure which shows the whole humidification ratio by the spraying system control in a moisture gas turbine system.

  As in the overall structure of the high-humidity gas turbine system shown in FIG. 1, the basic configuration of the normal gas turbine system includes an air chamber 1, a compressor 2, a combustor 3, a gas turbine 4, a generator 5, a power generation end 6, The air supplied through the air chamber 1 is heated and pressurized by the compressor 2 and sent as compressed air in the direction of the white arrow in FIG. 1 to be supplied to the combustor 3. In the high-humidity gas turbine system, as the humidification system, an intake spray humidification system 200 that sprays and humidifies fine water droplets 13 on the air chamber 1, an in-pipe spray humidification system 300 that humidifies high-temperature and high-pressure air discharged from the compressor 2, and a gas turbine. There is a regenerator humidification system 400 that sprays and humidifies at the inlet of the regenerative heat exchanger 7 that raises the temperature of the air that is supplied to the combustor 3 using the exhaust heat of the exhaust gas, and is configured to add high humidity to the air. .

The supply of spray water to each of these humidification systems is supplied from a common water supply facility 500 including a spray water supply tank 8, a high-pressure pump 9, and a water treatment device 10. In this common water supply equipment 500, each humidification system 200, with a high-pressure pump 9 from a spray water supply tank 8 in which water is stored.
It has a system configuration for supplying water as spray water to 300 and 400, and a control system for controlling the discharge pressure (P0) from the high-pressure pump 9 to a specified pressure by the bypass valve 11 is provided.

The high-temperature and high-pressure compressed air humidified by each of these humidification systems and the fuel supplied from the fuel supply system 100 are both supplied to the combustor 3 for combustion. The fuel supply system 100 includes a fuel supply flow path by piping for sending fuel from a fuel tank to a combustor by a fuel pump, a filter, a flow rate adjusting valve, a flow meter, and a pressure gauge installed in the piping. The flow rate adjustment valve is adjusted by a signal from the flow meter so as to obtain a flow rate, and an appropriate amount of fuel is supplied to the combustor 3.

  The blades of the gas turbine 4 are rotated by the combustion gas generated by the combustion action in the combustor 3, and the combustion gas becomes the gas turbine exhaust gas 37 and enters the regenerative heat exchanger as a heat source of the regenerative heat exchanger 7. Is then discharged from the regenerative heat exchanger 7 into the feed water heater 23 as a heat source, and then exhausted outside the gas turbine system.

  When the blades of the gas turbine 4 are rotationally driven by the combustion gas, the compressor 2 and the generator 5 connected in series with the turbine shaft equipped with the blades are driven, and the compressor 2 is renewed. Compressed air taken in from the air chamber 1 and compressed for combustion is supplied into the gas turbine system. Further, when the generator 5 is driven, electric power is generated and transmitted to the power generation end 6 of the generator 5, and the electric power is supplied from the power generation end 6 to the outside through an electric wire.

  Next, an intake spray humidification system 200 as the first spray means employed in the embodiment of the present invention will be described. An intake spray humidification system 200 that sprays fine water droplets 13 into the intake air 12 includes a filter 14, a flow control valve 15, a flow meter 16 as a first flow meter, a pressure gauge 17, a spray system selection valve 18, and a spray nozzle 600. It is equipped with piping connected to the discharge side of the pump 9. The piping is divided into two systems near the spray system selection valve 18, and one spray system selection valve 18 is provided for each system. The spray header 19 with which the spray nozzle 600 communicates is connected to the piping divided into the two systems so that the spray water in the spray water supply tank 8 can be supplied to the spray nozzle 600. The adjustment of the water amount of the fine water droplets 13 to be sprayed is adjusted by the selection of the spray system by opening and closing the spray system selection valve 18 and the flow rate control valve 15, but the pressure of the system to be sprayed is a pressure range in which the required spray water droplet diameter can be maintained. To control.

The required performance of the spray nozzle 600 used in this intake spray humidification system 200 is that the spray water droplet diameter is preferably 20 μm [SMD] or less from the maximum water droplet diameter accompanying the intake air flow, and the spray water amount should be as large as possible. It becomes. One of the commercially available one-fluid spray nozzles that almost satisfies the required specification of the sprayed water droplet diameter is the “moya spray nozzle M19” of Kyoritsu Alloy Co., Ltd., which is also shown in the prior art. The amount of spray water is about 0.125 L / min, which is a very small amount of water. Therefore, this intake spray humidification system 200 uses a high-pressure one-fluid atomizing nozzle that is shown in Japanese Patent Application No. 2002-319443 and that has a previously developed spray flow rate that satisfies a required spray water droplet diameter with a large flow rate.

FIG. 2 shows the shape of a high-pressure one-fluid atomizing nozzle. The high-pressure one-fluid atomizing nozzle 600 is fixed to the ends of the hollow cylindrical high-pressure water introduction pipe 601 and the high-pressure water introduction pipe 601 and has a small-hole jet outlet 602 provided at an angular interval of 90 degrees and each jet outlet. A nozzle tip component 604 having an inclined target 603 with an inclined portion facing 602, and a cylindrical cover 605 that is fixed to the high pressure water introduction pipe 601 and covers the circumference of the nozzle tip component 604 without contacting it, The high-pressure water 606 is ejected from each ejection port 602, and the fine water droplet 13 is obtained by making it collide with the inclination part of the front inclination target 603. FIG. The inclined target 603 has a cross shape as seen from the right side of FIG. 2 when viewed from the direction in which the fine water droplets 13 are discharged so that the inclined portion faces each jet port 602. By having such a structure, there are the following features (1) to (4).
(1) By providing a plurality of (four in this embodiment) jet ports 602, a free flow rate range from a small flow rate to a large flow rate can be set.
(2) Fine water droplets 13 can be obtained by ejecting high-pressure water from the ejection port 602 and causing it to collide with the inclined target 603.
(3) Since a structure in which high-pressure water is ejected from the ejection port 602 and collides with each inclined target 603 is formed, a gap 607 is formed between the sprayed water droplets, and the circulation of the outside air to the central portion of the sprayed water droplet is formed. In addition, depressurization at the center of the sprayed water droplets is avoided and the phenomenon that the spray range is reduced in a high temperature / high pressure atmosphere (cone collapse phenomenon) does not occur.
(4) With such a structure, it is possible to reduce the size of the nozzle. In actual production, the maximum nozzle diameter is 9 mm.

  The high-pressure one-fluid atomizing nozzle 600 is effective as a moisture addition nozzle for a high-humidity gas turbine system because of such characteristics.

  3, 4, and 5 show the spray characteristics of the high-pressure one-fluid atomizing nozzle 600.

  FIG. 3 shows the sprayed water droplet diameter distribution by the high-pressure one-fluid atomizing nozzle 600 having a spray water amount of 1, 2, 3 L / min. Here, the ejection pressure of each nozzle is 7 MPa. From this, the characteristics of this nozzle are that the spray water droplet diameter [SMD] is 20 μm or less with a 1 L / min nozzle, which is 10 times the amount of water jetted from the nozzle shown in the prior art, and the spray water droplet diameter with a 2, 3 L / min nozzle. It can be seen that [SMD] is 30 μm or less.

  FIG. 4 shows the sprayed water droplet diameter distribution associated with the ejection pressure of the high-pressure one-fluid atomizing nozzle 600 having a spray water amount of 1, 2, 3 L / min. From this, it can be seen that when the ejection pressure is 5 MPa or more, there is no difference in the diameter of the sprayed water droplet, and when the pressure is 4 MPa, the sprayed water droplet diameter increases. Therefore, the use range by this nozzle becomes a range whose ejection pressure is 5 MPa or more.

  FIG. 5 shows a flow rate characteristic in a use range where the sprayed water droplet diameter is constant (here, the ejection pressure is 5 to 9 MPa). From this, it can be seen that the change in the amount of water when the ejection pressure in the range of use is 5 to 9 MPa is ± 15% when 7 MPa is rated.

Therefore, as a characteristic of the high-pressure single-fluid atomizing nozzle 600, the flow rate range in which the spray pressure is 5 to 9 MPa and the sprayed water droplet diameter is constant is ± 15% based on 7 MPa. In addition, when the spray water droplet diameter needs to be 20 μm or less, a nozzle with a water amount of 1 L / min or less is used, and when the fog water droplet diameter needs to be 30 μm or less, a nozzle with a water amount of 2 to 3 L / min is used. .

  Since the intake spray humidification system 200 requires water droplets accompanying the intake air, the high pressure single fluid atomizing nozzle 600 having a spray pressure of 5 to 9 MPa, a spray water droplet diameter of 20 μm or less and a spray water amount of 1 L / min is preferably used. However, since it is not impossible to carry out even if the preferred sprayed water droplet diameter exceeds 20 μm or less, a nozzle having an ejection pressure of 4 MPa or more, a fog water droplet diameter of 30 μm or less, and a water amount of 2 to 3 L / min is used. Also good. A spray nozzle that can produce fine water droplets at a high pressure and a large capacity is used.

The intake spray humidification system 200 is intended to improve output decrease accompanying intake air temperature increase in summer, to reduce compressor power due to vaporization in the compressor, and to increase gas turbine output. Spray about 11% (1.6 wt%) of the total humidification of the system. For example, when the intake flow rate is 5 kg / s, a water amount of 4.8 L / min is humidified.
In the intake spray that humidifies the amount of water of 4.8 L / min, the above-described preferable 1 L / min high-pressure single-fluid atomizing nozzle 600 can be used to cover 5 nozzles. Even if 30% of the spray water is considered as water, 6 (6 L / min) is sufficient. If a plurality of systems are required from the viewpoint of controlling the spray amount, the number of nozzles is divided and installed. In addition, drain water due to adhesion of fine water droplets sprayed from the high-pressure one-fluid atomizing nozzle 600 to the inner wall of the air chamber 1 flows into the measuring tank 50 connected to the inside of the air chamber 1 by piping along the wall and is measured. The amount of water in the tank 50 is measured by a level meter 51 provided in the measuring tank 50. Such measuring means is the first measuring means. The measured water collected in the measuring tank 50 is discharged to the outside by opening a valve 52 provided in a pipe connected to the lower part of the measuring tank 50, and the discharged water is reused after being treated with water.

  6 and 7 show the structure of an intake spray humidification system 200 of the example in which the six nozzles are divided and installed in two systems. Here, FIG. 7 is a detailed view shown by part A in FIG. When the six nozzles are divided and installed in two systems, the three nozzles may be installed at equal intervals in each of the spray headers 19 that are pipes through which water to be sprayed passes. When the “moya spray nozzle M19” shown in the prior art is used and the water amount is about 6 L / min considering the drain water, 60 nozzles are required. When both are compared, in the case of the present embodiment using the high-pressure one-fluid atomizing nozzle (hereinafter referred to as a spray nozzle) 600 described in the embodiment of the present invention, the number of attachments becomes 1/10. There is an advantage in processing, production and assembly costs. Further, as shown in FIG. 7, as a method of attaching the spray nozzle 600, a seal that is used when screwing is used by attaching to a short pipe branched from the spray header 19 using a tightening type swage lock 20. The nozzle can be prevented from being clogged with a piece of tape or the like, and maintenance is facilitated.

  Next, the in-pipe spray humidification system 300 employed as the second spray means in the embodiment of the present invention will be described. As shown in FIG. 1, spraying is performed in a pipe serving as an air flow path of compressed air that communicates the compressed air discharge side of the compressor 2 and the upstream header 34 of the regenerative heat exchanger 7. The high-temperature high-pressure discharge air 21 to be discharged, that is, what humidifies the compressed air is the in-pipe spray humidification system 300. In-pipe spray humidification system 300 receives supply of spray water in spray water supply tank 8 from high-pressure pump 9 from common water supply equipment 500 through a pipe connected to the discharge side of high-pressure pump 9.

  The pipe branches at two branch points 22 and separates, and one of the pipes is heated by the heat of the exhaust gas by the feed water heater 23 via the feed water heater 23 provided at the position where the high temperature exhaust gas of the gas turbine system passes. It has a piping path that enters the valve 24. The other branched off at the branch point 22 has a piping path that directly enters the three-way valve 24 from the branch point 22.

  The spray water flowing into the three-way valve 24 through both piping paths is mixed and adjusted in temperature by the three-way valve 24. The temperature-adjusted spray water becomes fine water droplets from the spray nozzle 600 in the pipe humidification unit 700 via a pipe having the filter 25, the second flow meter 26, and the spray system selection valve 27 from the three-way valve 24. Sprayed. The piping from the three-way valve 24 to the spray nozzle 600 is branched into three systems on the way, and one spray system selection valve 27 is provided for each system. Thus, the spray nozzle 600 is connected to the piping of each of the three systems divided through the water injection pipe 700A4 so that the spray water in the spray water supply tank 8 can be supplied to the spray nozzle 600. Yes. The water amount of the spray water droplets is adjusted by selecting the spray system by opening and closing the spray system selection valve 27 and the three-way valve 24. The pressure of the system to be sprayed is controlled within a pressure range in which the required spray water droplet diameter can be maintained.

The three-way valve 24 mixes spray water from two directions with different temperatures, and the temperature and flow rate are adjusted by detection signals from the downstream thermometer 28 (T1) and the second flow meter 26 (F1). The temperature of the mixed spray water is adjusted to about 150 ° C., and the pressure is monitored by a pressure gauge 29 (P1). The humidified air 30 humidified by the tube humidifying unit 700 is injected into the upstream header 34 of the regenerative heat exchanger 7, but when excess water is injected, an amount of water that cannot be evaporated is generated. The amount of water that cannot evaporate flows into the measuring tank 31 connected to a pipe that communicates between the discharge side and the upstream header 34 of the compressor, and the level meter 32 connected to the measuring tank 31 measures the amount of water in the measuring tank 31. The Such weighing means is the second weighing means. The water accumulated in the measuring tank 31 is discharged outside by opening a valve 33 provided in a pipe connected to the lower part of the measuring tank 31 after measurement, and the discharged water is treated with water and reused.

  The intake spray humidification system 200 is intended to improve output decrease accompanying intake air temperature increase in summer, to reduce compressor power due to vaporization in the compressor, and to increase gas turbine output. The total humidification amount of the system (14.1 wt%: weight ratio to the intake flow rate) is as small as about 11% (1.6 wt%). On the other hand, since the in-pipe spray humidification system 300 aims at high output and high efficiency, a large amount of humidification is required. When the above-described intake spray humidification system 200 and in-pipe spray humidification system 300 cover the entire humidification amount, in-pipe spray humidification system 300 is approximately 12.5 wt% (amount of spray water in the case of intake 5 kg / s is 37.5 L / min). Need to be humidified.

  The required performance of the spray nozzle 600 used in this system is that the spray water droplet diameter [SMD] is 30 μm or less from the relationship of the evaporation rate, and the amount of spray water is as large as possible from the relationship of the installation space. One commercially available one-fluid spray nozzle is the “Moya Spray Nozzle M19” of Kyoritsu Alloy Manufacturing Co., Ltd., which is also shown in the above-mentioned prior art. This spray nozzle has a spray water amount of about 0.125 L / min. In addition, this nozzle is a type in which a water flow collides with the tip of a thin pin, and when used in a tube under a high temperature condition, it may be deformed by thermal expansion and the specified performance may not be obtained. Furthermore, since the flow rate is small, there is a problem that the total number of nozzles increases to 300.

  When the spray nozzle 600 with a flow rate of 1 L / min is used in the in-tube spray humidification system, the total number of nozzles is 37.5 (38), but when a nozzle with a flow rate of 3 L / min is used, 12.5 (13) may be sufficient. If this 3L / min nozzle is used and three spray systems are constructed, 4.3 nozzles per system are sufficient, and a humidifying system can be constructed with a very small number. The spray nozzle 600 is a high-pressure one-fluid atomizing nozzle having an ejection pressure of 5 to 9 MPa, a spray water droplet diameter [SMD] of 30 μm or less, and an amount of spray water of 3 L / min, which was explained in the description of the intake spray humidification system 200. Of course, a high-pressure one-fluid atomizing nozzle having a spray pressure of 4 MPa, a spray water droplet diameter [SMD] of 20 μm or less, and a spray water amount of 1 L / min may be used.

  The premise of the in-pipe spray humidification system shown here is that the humidification (12.5 wt%) required in the in-pipe spray humidification system is obtained, but it has not been confirmed in practice. Then, the result verified about this in-pipe spray humidification system is described next.

FIG. 8 shows a test system of a pipe humidifier 700A in which a structure such as an orifice is not provided in the pipe.
Here, the spray nozzle 600 is installed toward the center of the pipe inside the ring header 700A3 which is in close contact with the surface of the flange 700A1 and is fastened and fixed by the bolt 700A2, and the tip of the nozzle is fixed in a state of slightly protruding into the pipe. The spray water in the spray water supply tank 8 sent by the high pressure pump 9 flows in after passing through the water injection pipe 700A4, and passes through the ring header 700A3 and the spray nozzle 600 in the high temperature and high pressure discharge air 21 from the compressor. Sprayed as fine water droplets 13. The sprayed fine water droplets 13 are heat-exchanged with the high-temperature and high-pressure discharge air 21 and are carried downstream as the humidified air 30, that is, to the upstream header 34 side of the regenerative heat exchanger 7. The diameter of the pipe 700A5, which is a flow path of compressed air downstream from the spray nozzle 600, is φ250 and the length is 5.5 m, and a number of thermometers (not shown) are installed in the pipe to measure the temperature distribution. .

  FIG. 9 shows the result of the test performed using the system shown in FIG. 8 and shows the temperature of each part downstream of the spray nozzle. As test conditions, the flow rate of the high-temperature high-pressure discharge air 21 which is compressed air is 5 kg / s, the pressure is 8 ata, and the temperature is 290 ° C. This is the rated condition of the gas turbine system with an intake air flow rate of 5 kg / s, and the pipe flow velocity at the time of rating is 18.5 m / s for a pipe of φ250. The spray water flowing from the water injection pipe 700A4 is 12.3 L / min, which is the amount of water that can be completely evaporated at a temperature of 150 ° C. In this case, the humidification ratio is 4 wt%, and if more water is injected, a drain is generated and the entire amount of injected water cannot be evaporated.

  The used spray nozzle 600 is a nozzle having a flow rate of 1 L / min at which the spray water droplet diameter [SMD] is 20 μm or less. Here, the vertical axis indicates the temperature of the humidified air, and the horizontal axis indicates the distance from the most downstream nozzle position. The installation positions of the thermometers shown here are: T1 is the tube center, T2 is near the radial tube center, T3 is near the radial tube wall, T4 is the upper tube inner wall, and T5 is the lower tube inner wall. .

  From this result, it can be seen that the temperature in the pipe 700A5 downstream of the spray nozzle 600 has a large variation and mixing is not performed well, and when the temperature around 5.5 m is observed, the temperature is much higher than the temperature of T5. I understand that. From this, when the humidification concentration in the radial direction of the pipe is predicted, it is understood that the humidification density in the radial direction of the pipe becomes thinner from the center to the upper part of the pipe, and the middle is near the side wall and the lower part is thicker. It can also be seen that the complete evaporation distance of the sprayed water droplets in the tube is about 4.5 m. Furthermore, as shown in FIG. 10, it can be predicted that the sprayed fine water droplets 13 are only flowed to the high-temperature high-pressure discharge air 21 from the compressor, and the mixing is not promoted.

  FIG. 11 shows the test results of the evaporation limit humidification ratio when the tube length downstream of the spray nozzle is 5.5 m and the sample is completely evaporated in the tube. The test conditions were a high-temperature high-pressure discharge air 21 having a pressure of 8 ata and a temperature of 290 ° C. Here, the horizontal axis represents the pipe flow velocity, and the rated flow velocity of the gas turbine system with the intake air flow rate of 5 kg / s is 18.5 m / s.

  From this result, it can be seen that in the tube humidifier 700A system in which no structure is provided in the tube, the humidification ratio at the rated flow rate is about 4 wt%. This is very small at 32% of the humidification ratio (12.5 wt%) provided by the in-pipe spray humidification system. However, when the pipe diameter is increased and the flow velocity in the pipe is about 7 m / s, humidification of about 7 wt% is possible. Even in that case, it is 56% of the required humidification amount and cannot cover the entire humidification amount.

  In the high-humidity gas turbine system, it is important to simplify the system configuration and to reduce the installation space as much as possible from the viewpoint of cost reduction. Therefore, there are problems such as increasing the tube diameter, increasing material and processing costs, and requiring a large installation space. Therefore, a structure has been devised in which the pipe diameter is φ250 and the amount of humidification is increased.

  FIG. 12 shows the structure of a tube humidifier 700B as an example of an embodiment of the present invention in which an orifice for narrowing the flow path is installed upstream of the spray nozzle. In this system, an orifice for narrowing the flow path is installed upstream of the spray nozzle of the pipe humidifier 700A shown in FIGS. As a configuration thereof, the spray nozzle 600 is installed toward the center of the pipe inside the ring header 700B3 which is in close contact with the surface of the flange 700B1 and is fastened and fixed by the bolt 700B2, and the nozzle tip is fixed in a state of slightly protruding into the pipe. . The spray water flows from the water injection pipe 700B4 and is sprayed as the fine water droplets 13 into the high-temperature and high-pressure discharge air 21 from the compressor via the ring header 700B3 and the spray nozzle 600. An orifice 700B6 that narrows the flow path is provided upstream of the spray nozzle 600, and a pressure reducing part 700B7 is formed downstream of the orifice 700B6 due to the contracted flow generated in the orifice part.

  The fine water droplets 13 sprayed from the spray nozzle 600 are sprayed on the decompression unit 700B7, and are taken up by the vortex 700B8 generated in the decompression unit 700B7 and carried to the mixing zone 700B9 formed at the center of the tube, and instantly hot air Is exchanged with heat to become humidified air 30 and conveyed downstream.

  The feature of this pipe humidifier 700B is that water droplets are sprayed on the pressure reducing part 700B7 formed by the contracted flow generated in the orifice 700B6 part, and are entrained in the vortex 700B8 generated in the pressure reducing part 700B7, and mixed in the central part of the pipe In the region 700B9, heat exchange with the high-temperature high-pressure discharge air 21 is performed instantaneously to increase the humidification amount. Further, as a structural feature, a ring header 700B3 to which a spray nozzle is attached is housed inside the flange 700B1 for compactness. However, when performing maintenance such as installation and removal of the spray nozzle, it is necessary to perform the work with the whole removed and disassembled.

  FIG. 13 shows the structure of a pipe humidifier 700C which is an example of the present invention, which is different from the pipe humidifier 700B shown in FIG. The structure is such that the pipe type ring header 700C3 to which the injection system 700C4 installed outside the pipe is connected is connected to the ring header 700C3, the fastening joint 700C2, the pipe 700C1, and the spray nozzle 600 are fixed and the humidified air 30 is sealed. The tightening joint 700C11 and the protrusion 700C10 for fixing the tightening joint 700C11. By setting it as such a structure, the structure in a pipe humidifier can be made the same structure as said 700B. In addition, with this structure, as a new feature, the spray nozzle 600 can be detached as a single unit, so that maintenance of the spray nozzle 600 and adjustment of the nozzle position can be performed with each nozzle.

  When the position of the spray nozzle is the same as that of 700B, similarly to the pipe humidifier 700C, fine water droplets 13 are formed in the decompression unit 700C7 formed by the contracted flow generated in the orifice 700C6 and generated in the decompression unit 700C7. The heat can be exchanged with the high-temperature high-pressure discharge air 21 instantaneously in the mixing zone 700C9 formed in the central portion of the pipe by being caught in the vortex 700C8.

  FIG. 14 shows the shape of the orifice edge used in the system of the pipe humidification structures 700B and 700C according to the embodiment of the present invention. When the orifices 700B6 and 700C6 are installed in the pipe, pressure loss occurs. As a method of reducing this pressure loss as much as possible, the upstream edge of the orifice is processed, and the shape is shown in (1) and (2) in the figure. Here, (1) is obtained by deleting the upstream edge of the orifice at an acute angle, and (2) is obtained by rounding the upstream edge of the orifice. Thereby, the pressure loss generated in the orifice portion can be remarkably reduced.

FIG. 15 shows the temperature of each part downstream of the spray nozzle as a result of using the structure of (1) shown in FIG. 14 with the orifice edge in the structure of the pipe humidifier 700B according to the embodiment of the present invention. As test conditions, the flow rate of the high-temperature high-pressure discharge air 21 is 5 kg / s, the pressure is 8 ata, and the temperature is 290 ° C. This is a rated condition of the gas turbine system with an intake air flow rate of 5 kg / s, and the pipe flow velocity at rated time is 18.5 m / s for a pipe of φ250. The spray water flowing from the water injection pipe 700B4 is 19.8 L / min, which is the amount of water that can be completely evaporated at a temperature of 150 ° C. In this case, the humidification ratio is 6.6 wt%. The spray nozzle 600 used has a spray water droplet diameter [SMD] of 30.
It is a nozzle with a flow rate of 3 L / min that is not more than μm. Here, the vertical axis represents the humidified air temperature, and the horizontal axis represents the distance from the most downstream nozzle position.

The installation positions of the thermometers shown here are T1 at the tube center, T2 near the tube center in the radial direction,
T3 is closer to the radial tube wall, T4 is the upper tube inner wall, and T5 is the lower tube inner wall. From this result, the temperature change of each part downstream of the spray nozzle is smaller in variation than the tube humidifier 700A having the structure not provided with the orifice shown in FIG. 9, and the most downstream (5.5 m) at the measured temperature. ) Is completely evaporating despite the fact that the temperature indication is almost close to the complete evaporation temperature, and the injected water was increased by 61% from 12.3 L / min to 19.8 L / min. It can be seen that the evaporation distance is also shortened from 4.5 m to 2.5 m.

  From this, it is understood that mixing is performed instantaneously due to the effect of installing the orifice, and heat exchange with high-temperature air is performed with high efficiency. Although the temperature indication at the most downstream (5.5 m) at the measured temperature does not drop to the complete evaporation limit temperature, there is some margin, but the maximum humidification ratio is about 7 wt% due to excess heat. From these, it is considered that installing an orifice upstream of the spray nozzle is effective as a means for increasing the humidification ratio.

FIG. 16 shows a comparison of test results in a tube humidifier 700B structure according to an embodiment of the present invention and a tube humidifier structure in which no structure is provided in the tube shown in 700A. The test conditions were a high-temperature high-pressure discharge air 21 pressure of 8 ata and a temperature of 290 ° C. Here, the horizontal axis represents the flow velocity in the pipe, and the vertical axis represents the complete evaporation limit humidification ratio in the pipe humidifier system.

Here, the rated flow velocity of the gas turbine system with an intake air flow rate of 5 kg / s is 18.5.
m / s was written. As a test result, the complete evaporation limit humidification ratio (A) in the tube humidifier structure (opening ratio: 1) where no structure is provided in the tube shown in 700A and the opening ratio of the orifice 700B6 used in the tube humidifier 700B structure ( The characteristics of two types (B: aperture ratio 0.36, C: aperture ratio 0.23) with different area ratios are shown.

From this result, in the pipe humidifier 700A system in which no structure is provided in the pipe (φ250), the complete evaporation limit humidification ratio at the rated flow rate is about 4 wt%, but the orifice 700B6 is provided and the opening ratio is 0.36. It can be seen that it is about 5.2 wt% and about 7 wt% when the aperture ratio is 0.23. As described above with reference to FIG. 15, the limit of evaporative humidification is about 7 wt% based on the amount of heat of the high-temperature high-pressure discharge air 21, and the limit humidification can be obtained when the opening ratio is 0.23.
It can be seen that a humidifier ratio of 7 wt%, which is the limit of evaporative humidification, can be obtained by increasing the tube diameter and reducing the flow rate to about 7 m / s even in a tube humidifier structure where no structure is provided in the tube shown in 700A. However, a large installation area is required, and there remains a problem in downsizing.

  In the pipe spray humidification system here, an example in which the water injection system is three systems has been shown. However, since the intake air amount increases when a large capacity gas turbine system is used, water is injected into the pipe humidification unit 700 and the pipe humidification unit 700. Multiple water injection systems are also required.

  As described above, the in-pipe spray humidification system 300 according to the embodiment of the present invention is shown. From the above results, the limit humidification ratio is about 7 wt%, and the humidification ratio (1.6 wt%) of the intake spray humidification system described above. In total, it is 8.6 wt%, and the required humidification ratio of 14.1 wt% is not yet 5.5 wt%. In the present invention, the regenerative heat exchanger 7 that heats the humidified air from the pipe humidifier with the exhaust heat of the gas turbine 4 and raises it to a necessary temperature is used in the present invention for humidifying this extraordinary amount.

  Next, the regenerator humidification system 400 as the 3rd spraying means by the Example of this invention is demonstrated. Here, description will be made using the entire structure of the high-humidity gas turbine system in FIG. 1 and the regenerative heat exchanger 7 structure in which the spray system shown in FIG. 17 is introduced. The regenerative heat exchanger 7 shown here has a structure (plate fin structure) in which heat exchanging portions are stacked as an example.

  The humidified air 30 that has been humidified to near the humidified saturation concentration by the tube humidifying unit 700 and has become low temperature (about 130 ° C.) flows into the upstream header 34 of the regenerative heat exchanger 7. The humidified air 30 that has flowed in passes through the rectifying plate 35 installed in the upstream header 34, flows into the stacked heat transfer flow paths 36 in the regenerative heat exchanger 7, and is heated in the regenerative heat exchanger 7. Heat is exchanged with the exhaust gas 37 and supplied to the combustor 3 via the downstream header 38 of the regenerative heat exchanger 7. However, in the regenerative heat exchanger 7, it is necessary to add moisture as described above. is there.

  The humidified air 30 that has flowed into the upstream header 34 of the regenerative heat exchanger 7, that is, the compressed air humidified by the air compressed by the compressor, has a humidified saturation concentration, so that fine water droplets are sprayed on the humidified air 30. However, increase in humidification cannot be expected. Therefore, in the regenerator humidifying system 400 according to the embodiment of the present invention, the rectifying plate 35 that rectifies the humidified air 30 that has entered the upstream header is provided in the upstream header 34, and the humidified air 30 flows more than the rectifying plate 35. The spray nozzle 600 is installed downstream of the heat transfer passage 7 and the fine water droplets 13 are sprayed toward the inlet of the heat transfer passage 36 of the regenerative heat exchanger 7.

  Here, the role of the rectifying plate 35 is to uniformly distribute the humidified air 30 flowing into the upstream header 34 in the upstream header 34 and stabilize the fine water droplets 13. Thereby, the fine water droplets 13 flowing into the heat transfer channel 36 can be evenly distributed. Water droplets liquefied by collision with the structure and fine water droplets from the spray nozzle 600 are also accompanied by the humidified air 30 and mixed in the heat transfer flow path 36 of the regenerative heat exchanger 7. The mixed large water droplets are also heat-exchanged by the exhaust gas 37 (about 680 ° C.) of the gas turbine and are evaporated in the regenerative heat exchanger 7. The exhaust gas 37 of the gas turbine has a sufficient amount of heat, and can evaporate mixed water droplets and further raise the temperature. The high-temperature humidified air 39 (about 630 ° C.) humidified and heated in the regenerative heat exchanger 7 is supplied to the combustor 3 via the downstream header 38 of the regenerative heat exchanger 7.

The spray water supply system to the regenerator humidification system 400 receives supply of spray water in the spray water supply tank 8 from the common water supply facility 500 by the high-pressure pump 9 through a pipe, and the pipe is divided into two at the branch point 22. One enters the three-way valve 40 via a feed water heater 23 arranged so as to be in contact with the high temperature exhaust gas of the turbine system. The other enters the three-way valve 40 directly from the branch point 22. The spray water mixed and temperature-adjusted by the three-way valve 40 is upstream of the regenerative heat exchanger 7 via a pipe having a filter 41, a flow meter 42 as a third flow meter, and a spray system selection valve 43. After being supplied to the spray nozzle 600 installed in the side header 34, the fine water droplets 13 are sprayed from the spray nozzle 600. The piping provided with the spray system selection valve 43 is branched into two systems upstream from the spray system selection valve 43, and the spray system selection valve 43 is provided for each system piping, and is distributed to the piping for each system. The spray nozzle 600 is connected in communication. The three-way valve 40 mixes two fluids of spray water having different temperatures, and the temperature and flow rate are adjusted by signals from the downstream thermometer 44 (T2) and flow meter 42 (F2). The temperature of the mixed fluid is adjusted to about 150 ° C., and the pressure is monitored by a pressure gauge 45 (P2).

  In the intake spray humidification system 200 and the in-pipe spray humidification system 300 in the gas turbine having the intake amount of 5 kg / s, the insufficient humidification amount (5.5 wt%) is 16.5 L / min as the spray water amount. In this regenerator humidifying system 400, the sprayed water droplets do not immediately evaporate, but the one that flows into the heat transfer flow path 36 of the regenerative heat exchanger 7 evaporates, but the inner wall of the upstream header 34 of the regenerative heat exchanger 7 Drain water should be taken from spray water that comes into contact with etc. In order to avoid the drain water from concentrating and flowing into the lowermost heat transfer flow path 36, in the embodiment of the present invention, the upstream side of the height direction dimension (H) of the heat exchange portion of the regenerative heat exchanger 7. The header 34 part was slightly extended (L) downward.

This avoids concentration of inflow of drain water into the lowermost heat transfer channel 36. In consideration of this drain water, the amount of water increased by 50% (24.75 L / min) is sprayed here. In the two-line spray, when the above-described 1 L / min spray nozzle 600 is used, twelve nozzles per one line and six nozzles per one line in four lines are required. The drain water generated in the upstream header 34 of the regenerative heat exchanger 7 flows into the measuring tank 46 through a pipe communicating with the lower part of the upstream header 34, and a level meter 47 installed in the measuring tank 46. Measure the flow rate of drain water at The drain water amount generated in the upstream header 34 is measured by such third measuring means. The water accumulated in the measuring tank 46 is discharged to the outside by opening a valve 48 provided in a pipe communicating with the bottom of the measuring tank 46, and the discharged drain water is reused after being treated with water.

As described above, the intake spray humidification system 200, the in-pipe spray humidification system 300, and the regenerator humidification system 400 are shown here as the humidification system of the high-humidity gas turbine system. When the total humidification is 100%, the humidification ratio in these humidification systems is 11% maximum in the intake spray humidification system 200, 50% maximum in the pipe spray humidification system 300, and 39% maximum in the regenerator humidification system 400. . This distribution increases the number of in-pipe spray humidification systems 300 and decreases the number of regenerator humidification systems 400 because the temperature difference in heat exchange in the regeneration heat exchanger 7 (exhaust gas temperature 680 ° C., spray water temperature 150 ° C., temperature difference 530 (° C.) is the largest, and the thermal stress on the structure of the regenerative heat exchanger 7 is also large, so the soundness of the regenerative heat exchanger is taken into consideration.

  If the humidification system of the gas turbine system is configured in this way, it is inexpensive in terms of cost, can be made compact, can maintain soundness, and can obtain the necessary humidification.

  Next, spray system control of each humidification system 200, 300, 400 of the above-described high-humidity gas turbine system will be described. Here, the spray system control will be described by taking as an example a spray humidification system in which the intake spray humidification system 200 is composed of two systems, the in-pipe spray humidification system 300 is composed of three systems, and the regenerator humidification system 400 is composed of two systems. As for the intake air flow rate and humidification conditions, the rated intake flow rate is 5 kg / s and the rated humidification rate is 14.1 wt%. Table 1 shows the system configuration conditions during rated humidification.

  Here, the actual spray water amount in the intake spray is a water amount in consideration of the drain water amount (about 30%) due to adhesion to the wall of the air chamber 1. Further, the actual spray water amount in the regenerator humidification is a water amount in consideration of the drain water amount (about 50%) due to adhesion to the wall generated at the inlet portion of the heat transfer passage 36. The number of spray nozzles per system in each humidification system is 3 for the intake spray humidification system and 12 for the regenerator spray humidification system. However, in the tube spray humidification system, the number of nozzles for the number of systems cannot be equalized. Two lines are two and one line is three. The spray pressure of the spray nozzle was 5-9 MPa as shown in FIG.

  FIG. 18 shows the overall humidification ratio by spray system control of a high-humidity gas turbine system in which the intake spray humidification system 200 is composed of two systems, the in-pipe spray humidification system 300 is composed of three systems, and the regenerator humidification system 400 is composed of two systems. The number of systems described in the lower part of FIG. 18 represents the number of systems for spraying spray water, and the number of systems to be sprayed is selected by opening and closing the spray system selection valves 18, 27 and 43. In addition, the intake air humidification described in the lower part of FIG. 18 represents the intake air spray humidification system 200, the tube humidification represents the in-tube spray humidification system 300, and the in-regenerator spray represents the regenerator humidification system 400.

  In FIG. 18, the vertical axis represents the humidification ratio of the entire system when the humidification ratio (14.1 wt%) at the time of rating is 100%, and the horizontal axis represents an operating system based on system linkage. Of the systems shown in FIG. 18, the intake spray has an effect of cooling the compressor intake air and reducing power, so that one system is always in an operating state. From this it can be seen that the overall humidification rate of the high humidity gas turbine system can be continuously varied. Therefore, any partial load operation can be handled.

A high-efficiency, high-humidity gas turbine system can be provided by incorporating each of these spray humidification systems in the gas turbine system.
(1) According to the embodiment of the present invention, it is possible to humidify a necessary amount for intake of a gas turbine with a simple structure, and to achieve high efficiency of a high-humidity gas turbine system.
(2) According to the embodiment of the present invention, since the necessary amount of humidification can be performed without changing the size of the basic configuration of the gas turbine system, the gas turbine system can be made compact.
(3) The installation of a spray nozzle capable of spraying fine water droplets at a high flow rate as shown in Japanese Patent Application No. 2002-319443 directly on the piping of the humidification site eliminates the need for a large external humidification tower and other costs. And simplification.
(4) According to the embodiment of the present invention, it is possible to continuously control the humidification ratio corresponding to the operation mode of the gas turbine system according to the power load demand, and it is possible to cope with any partial load operation.
(5) According to the embodiment of the present invention, it is possible to avoid a decrease in output due to a rise in intake air temperature in the summer of the gas turbine system, so that high-efficiency operation is possible regardless of the season.
(6) The maximum amount of humidification with the in-pipe spray humidification system can reduce the amount of spray in the upstream header of the regenerative heat exchanger, and the number of spray systems in the upstream header can be increased to make it evenly fine. Since water droplets flow in, the heat stress in the heat transfer flow path in the regenerative heat exchanger can be reduced, and the soundness of the regenerative heat exchanger can be secured.

1 is an overall structural diagram of a high humidity gas turbine system according to an embodiment of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS It is a shape figure of the spray nozzle used for the high humidity gas turbine system by the Example of this invention, Comprising: (a) A figure shows sectional drawing, (b) figure represents the right view of (a) figure. It is a water droplet diameter distribution map when the amount of spray water of the spray nozzle used is used as a parameter. It is a water droplet diameter distribution map when the spray pressure of the spray nozzle to be used is used as a parameter. It is a figure which shows the ratio of the amount of spray water with respect to the spray pressure of a use nozzle. It is a perspective view which shows the installation of the spray nozzle in the air chamber and the spray condition by the Example of this invention. It is detail drawing by the partial cross section display of the A section of FIG. It is sectional drawing of the spraying part of the in-pipe spray humidification system by the Example of this invention. FIG. 8A is a graph showing the temperature of each part downstream of the spray nozzle, and FIG. 8B is a diagram showing the temperature measurement position. It is a figure which shows the axial direction water droplet distribution of the sprayed water droplet flow in the pipe humidifier structure which does not provide a structure in a pipe | tube. It is a graph which shows the test result of the evaporation limit humidification ratio on perfect evaporation conditions by the structure shown in FIG. In the tube humidifier structure according to the embodiment of the present invention in which the orifice for narrowing the flow path is installed upstream of the spray nozzle, the situation is shown when fine water droplets are sprayed from the nozzle installed in the header sandwiched by the flange in the high temperature air pipe It is a cross-sectional schematic diagram. A system in which a header is provided outside a high-temperature air pipe in a pipe humidifier structure according to an embodiment of the present invention, a water supply pipe is connected to the spray nozzle, and an orifice that narrows the flow path is installed upstream of the spray nozzle. FIG. 6 is a schematic cross-sectional view showing the situation when fine water droplets are sprayed from the installation nozzle. It is a shape figure of the orifice edge used by the structure of FIG.12 and FIG.13 which is an Example of this invention. FIG. 12A is a graph showing the temperature of each part downstream of the spray nozzle and FIG. 12B is a diagram showing the temperature measurement position as a result of testing with the configuration shown in FIG. 12 according to the present invention. It is a graph which shows the comparison of the test result in the pipe humidifier 700B structure shown in FIG. 12 which is an Example of this invention, and the pipe humidifier 700A structure which does not provide a structure in the pipe | tube shown in FIG. It is a perspective view by the principal part section display of the regeneration heat exchanger part which has the regenerator spray humidification system by the example of the present invention. It is a graph which shows the whole humidification ratio by spray system control in the high humidity gas turbine system by the Example of this invention.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 1 ... Air chamber, 2 ... Compressor, 3 ... Combustor, 4 ... Gas turbine, 5 ... Generator, 6 ... Power generation end, 7 ... Regenerative heat exchanger, 8 ... Spray water supply tank, 9 ... High pressure pump, 10 DESCRIPTION OF SYMBOLS ... Water treatment apparatus, 11 ... Bypass valve, 12 ... Intake air, 13 ... Fine water droplet, 14, 25, 41 ... Filter, 15 ... Flow control valve, 16, 26, 42 ... Flow meter, 17 ... Pressure gauge, 18, 27 , 43 ... Spray system selection valve, 19 ... Spray header, 20 ... Swage lock, 21 ... High temperature / high pressure discharge air, 22 ... Branch point, 23 ... Feed water heater, 24, 40 ... Three-way valve, 28, 44 ... Thermometer 29, 45 ... Pressure gauge, 30 ... Humidified air, 31 ... Metering tank, 32, 47 ... Level meter, 33, 48 ... Valve, 34 ... Upstream header, 35 ... Current plate, 36 ... Heat transfer channel, 37 ... Gas turbine exhaust gas, 38 ... downstream header, 39 ... high temperature Air, 46 ... Metering tank, 100 ... Fuel supply system, 200 ... Intake spray humidification system, 300 ... In-pipe spray humidification system, 400 ... Regenerator humidification system, 500 ... Common water supply equipment, 600 ... High pressure one-fluid atomizing nozzle (spray) Nozzle), 700... Tube humidifier.

Claims (4)

A compressor for compressing and discharging the air sucked from the air chamber;
An air flow path for passing compressed air discharged from the compressor;
A combustor that is supplied with the compressed air and fuel that has passed through the air flow path and performs a combustion action;
A turbine driven by combustion gas of the combustor;
A generator driven by the turbine;
A regenerative heat exchanger for heating the compressed air with the combustion gas;
An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger;
First spraying means for spraying a liquid into the air chamber;
A second spraying means for spraying liquid into the air flow path;
Third spraying means for spraying liquid into the upstream header;
A gas turbine system. A compressor for compressing and discharging the air sucked from the air chamber;
An air flow path for passing compressed air discharged from the compressor;
A combustor that is supplied with the compressed air and fuel that has passed through the air flow path and performs a combustion action;
A turbine driven by combustion gas of the combustor;
A generator driven by the turbine;
A regenerative heat exchanger for heating the compressed air with the combustion gas;
An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger, and has a lower portion extending below the heat transfer flow path at the lowest stage of the heat transfer flow path;
At least one of first spraying means for spraying liquid into the air chamber, second spraying means for spraying liquid into the air flow path, or third spraying means for spraying liquid into the upstream header. Having spraying means;
The at least one spraying means is a gas turbine system having a spray nozzle having a spray pressure of 4 MPa or more, a flow rate of 1 L / min or more, and a Sauter average particle size of 30 μm or less. A compressor for compressing and discharging the air sucked from the air chamber;
An air flow path for passing compressed air discharged from the compressor;
A combustor that is supplied with the compressed air and fuel that has passed through the air flow path and performs a combustion action;
A turbine driven by combustion gas of the combustor;
A generator driven by the turbine;
A regenerative heat exchanger for heating the compressed air with the combustion gas;
An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger;
A plurality of systems of first spraying means capable of selecting a system for spraying and spraying liquid into the air chamber;
A plurality of systems of second spraying means for freely selecting a system to spray and spray liquid in the air flow path;
A plurality of third spraying means capable of selecting a system to spray and spray liquid in the upstream header;
A gas turbine system. A compressor for compressing and discharging the air sucked from the air chamber;
An air flow path for passing compressed air discharged from the compressor;
A combustor that is supplied with the compressed air and fuel that has passed through the air flow path and performs a combustion action;
A turbine driven by combustion gas of the combustor;
A generator driven by the turbine;
A regenerative heat exchanger for heating the compressed air with the combustion gas;
An upstream header that distributes the compressed air to the heat transfer flow path of the regenerative heat exchanger;
First spraying means for spraying a liquid into the air chamber;
A first flow meter for measuring a flow rate of the liquid supplied to the first spraying means;
First metering means for metering the liquid drain liquid from the air chamber;
A second spraying means for spraying liquid into the air flow path;
A second flow meter for measuring a flow rate of the liquid supplied to the second spraying means;
A second metering means for metering the liquid drain liquid from the air flow path;
Third spraying means for spraying liquid into the upstream header;
A third flow meter for measuring the flow rate of the liquid supplied to the third spraying means;
Third metering means for metering the liquid drain liquid from within the upstream header;
A gas turbine system.

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