EA005393B1 - Gas turbine unit for generating power and a supercharging system therefor - Google Patents

Abstract

A supercharging system for gas turbine power plants (11) is disclosed. The system includes a supercharging fan (30, 32) and a controller (50) for limiting turbine power output to prevent overload of the generator (28) at lower ambient temperatures. The controller can limit power output by burner control, inlet temperature control, control of supercharging fan pressure and other options. The system can be retrofit on an existing turbine without replacing the generator and associated parts.

Description

This application claims priority based on provisional patent applications US No. 60/138848 dated June 10, 1999, 60/139894 dated June 22, 1999, 60/152277 dated September 3, 1999, 60/195207 dated October 13 1999 and 60/195302 of April 10, 2000. This application is a partial continuation of the pending application for US patent 09/388927 of September 2, 1999

FIELD OF THE INVENTION

The present invention relates to gas turbine power plants (power units or electric generators with a gas turbine drive), in particular to a pressurization system that increases the power of a turbogenerator (amount of generated electricity) at high ambient temperature. In such power plants (turbogenerators) there is usually an increase in air pressure at the inlet of the gas turbine compressor and a blower (fan) connected to the control device (regulator), which can be used to increase the power of existing turbines and preferably works together with the compressor located at the inlet turbines cooling system.

BACKGROUND OF THE INVENTION

It is known that the power of gas turbines decreases with increasing temperature of the air entering the compressor, and usually with increasing air temperature at the inlet to the compressor by 1 ° P, the turbine power decreases in accordance with the graph shown in FIG. 1, approximately 0.4%. Such a drop in the turbine power with increasing temperature of the air entering the compressor is especially unfavorable when using gas turbine plants (gas turbines) to generate electric energy, since usually the demand for electricity reaches its peak exactly at the time when the ambient temperature rises to its maximum level. Gas turbines, generators and distribution systems of gas turbine power units are usually calculated on the power of the turbine, which it develops at a temperature of air entering its compressor from 40 to 50 ° P. At such low design temperatures, the turbine power actually developed in the summer at high ambient temperatures can drop by 20-40% depending on the design of the turbogenerator, local weather conditions and characteristics of the gas turbine.

Currently, there are many different methods for cooling the air entering a gas turbine, which partially or completely avoid the turbine power drop caused by high air temperature. A detailed analysis of all these methods is contained in the article published in the proceedings of A8ME by Orboik ίη Sak Tigger Pohtid Aidshe Shaboi Imid 1i1e1 Αίτ SUSHid, 1 dog Oibguak et al. Brussels, Belgium. Alternative cooling methods include direct evaporative cooling and indirect (indirect) evaporative cooling, vapor compression cooling using electrical energy, absorption and cooling using thermal storage systems.

Of all currently known methods of cooling the air entering the turbine compressor on an industrial scale, only the direct evaporative cooling method can be used. The advantages of the direct evaporative cooling method include its low cost and ease of implementation, and the disadvantages are the limitations associated with determining the ambient temperature using a wet thermometer. For the eastern regions of the United States, direct evaporative cooling can, depending on local weather conditions, provide a decrease in temperature of air entering the turbine by 10-20 ° P. A higher temperature drop due to direct evaporative cooling can be expected in the southwestern United States with a hot, dry climate. Direct evaporative cooling, with all its advantages, does not allow, however, to use the turbine at full design capacity. Despite the intensive research of gas turbines over the past 50 years, and the success achieved with this, the problem of the operation of gas turbine power plants (turbogenerators) at high ambient temperatures still remains unresolved.

Of particular interest, but not actually implemented solution to the above problems was proposed by the ILU. Rocket-Redd in article 8 and й с й д о о о С ак ак ак ак Р ее ее ее ее ее ее ее ее ее Н Ра ик ик от от от от,,,,,,,,, published in A8ME in 1965. In this article, it is proposed to use a high-pressure blower from evaporative cooler. Theoretically, such a solution has great advantages, but its practical implementation is associated with the need to use a special-sized generator, for the drive of which it is necessary to create new gas turbines. In addition, the use of a single blower with adjustable blades proposed in this article reduces the efficiency of the entire gas turbine power unit.

Published in the works of A8ME in the journal 1oitia1 o £ Yeedsheyid £ from Sak TigShek aib Po \\ 'e in July 1995, issue 117, pages 513-527, article Ko1p et al. AbuaShadek o £ Ay Soib1boshid aib 8iretsyatdshdbshbb6bak6ak Sak 1 and 1e1 show the results of studies performed by the authors, according to

-1005393 sacred cost-effectiveness of boost and cooling systems. This article states that while evaporative cooling is a very efficient way of cooling the air entering the compressor of a gas turbine in terms of economic performance, the use of boost to increase turbine power for simple cycles is not economically feasible because it takes too long (up to 10 years) payback necessary for boosting equipment. A greater, albeit very insignificant, economic effect from the use of boost can be obtained in combined cycle plants. The boost systems discussed in this article are essentially the same as those developed in the 60s, and unlike turbines, which have been significantly improved in recent decades, they have not undergone any changes.

One of the serious problems that currently exist and associated with the use of boost is the need to increase the size of the generator and other auxiliary equipment of the gas turbine power unit (turbogenerator). The costs of replacing the generator and other auxiliary equipment of the power unit are so high that the use of conventional pressurization systems in existing gas turbine power plants (turbine generators) has virtually no economic effect. Even for new power units (electric power generators driven by a gas turbine), the boost can be economically justified only if the boost system is included in the design at the very initial design stage and if this does not require modernization of the generator itself, make changes to the distribution system or replace various accessories. An article by Ko1p et al. (P. 520) says that, in contrast to pressurization, evaporative cooling does not require an increase in the size of the equipment that is part of the gas turbine power plant (turbogenerator). The main conclusion that can be drawn on the basis of the above considerations is that for the modernization of existing gas turbine power plants they need to be equipped not with a boost system, but with an evaporative cooling system.

Another currently known method for controlling the power of a gas turbine is based on the use of a variable speed compressor. This method is proposed, in particular, in patents I8 3853432 and I8 2693080. The systems described in these patents have a wide range of regulation and are intended essentially for use in gas turbine engines of aircraft. The main problem inherent in such systems is associated with the high cost and complexity of a variable speed compressor. Other problems inherent in such systems are related to the reliability and complexity of operation of gear reducers used in them, which are large. It is for these reasons that such systems have not found appreciable use in gas turbine power plants designed to produce electrical energy.

Another well-known way to increase the power of a gas turbine by cooling the air entering its compressor is based on air humidification. Such a method is described, in particular, in an article by Meyet-Noshts aib Meee Sak Tithe Rho tsg LidteShayoi Lododshd about £ 1и1е1 Λίτ, published in 1999 in the materials of the 28th symposium on turbine equipment (28 ' ¹ ' ТитомасЫпет Зутроиш). In addition to the advantages associated with cooling the air at the inlet to the turbine compressor, humidification also improves the performance of the entire gas turbine unit by cooling the air inside the compressor. Indirect evaporative air cooling when 1% water is added to it based on the mass flow rate of air allows increasing the turbine power by approximately 5%. The article mentioned above also notes that indirect evaporative cooling of the air by means of its humidification also improves the efficiency of the compressor.

One of the limitations of this method of increasing the power of a gas turbine is associated with the amount of water dust, which, for safety reasons, may be contained in the air entering the compressor. The increased water content in the air can create problems associated with corrosion, erosion or other processes that can lead to failure of the compressor stage of the turbine. In most cases, at least the turbine manufacturer cannot guarantee its reliable operation when using a humidification system in it, which, in his opinion, can cause the compressor to fail prematurely. Despite the fact that air humidification has compared with evaporative cooling and a number of advantages, for reasons related to the possible negative effect of moisture on the compressor, the increase in the power of most turbines operating in coastal areas with a humid climate due to air humidification as a rule, does not exceed 10%.

SUMMARY OF THE INVENTION

In one preferred embodiment of the present invention, there is provided a system for increasing the power of a gas turbine at high ambient temperature, having at least one blower blower that increases the pressure of the air entering the compressor, and a control device or regulator that limits the maximum power of the turbine to the power that it develops naturally aspirated. In a preferred embodiment, the system according to the invention comprises an air cooler that reduces the temperature of the air entering the turbine compressor. Proposed in the invention system can be equipped with existing gas turbine

-2005393 installations (turbo-generators), and also use it for newly designed gas turbine power units with supercharging.

One of the fundamental features of the invention and one of its most significant advantages is the possibility of increasing the turbine power with maximum power consumption in the summer with virtually no additional investment related to the creation of a gas turbine power plant (turbogenerator), designed to operate in summer with maximum load. Other tasks solved by the present invention include the creation of a relatively compact, not very complex gas turbine power plant (turbogenerator), which has a sufficiently high reliability and relatively simple to operate. The present invention is also the creation of a supercharger, which can be successfully used to upgrade existing gas turbine power plants. A supercharger for a gas turbine (turbogenerator) according to the present invention consists of a blower and an air humidifier located at the inlet of the turbine compressor.

Brief Description of the Drawings

The accompanying description of the drawings shows:

in FIG. 1 is a graph of turbine power versus ambient temperature;

in FIG. 2A-2B are diagrams of a gas turbine power unit, which is made in accordance with one of the preferred embodiments of the invention and includes an air cooler located behind the blower, which increases the pressure of the air entering the turbine compressor;

in FIG. 3 is a diagram of a gas turbine power unit made in accordance with another preferred embodiment of the invention, in which a cooler with indirect (indirect) evaporative cooling is used;

in FIG. 4 is a diagram of a gas turbine power unit, made according to another embodiment of the invention, in which an axial blower is used to pressurize the air;

in FIG. 5 is a diagram of a gas turbine power unit, made according to another embodiment of the invention, in which several blowers are used to pressurize the air;

in FIG. 6 is a graph of turbine power versus air temperature for various embodiments of a gas turbine power unit;

in FIG. 7A and 7B are diagrams illustrating the operating principles of a turbogenerator proposed in the invention, showing the control characteristics of a compressor of a gas turbine unit with external turbine characteristics superimposed on them;

in FIG. 8A and 8B are graphs showing the external characteristics of the blowers with the external characteristics of the gas turbine unit superimposed on them, explaining the principle of using several blowers to control the air pressure at the compressor inlet;

in FIG. 9 is a graph of the maximum pressure of the blower blower versus air temperature at the inlet to the compressor;

in FIG. 10 is a diagram of a gas turbine power unit made in accordance with another embodiment of the invention, in which a change in the characteristics of a gas turbine is carried out by supplying the hot air leaving the compressor back to the compressor inlet;

in FIG. 11 is a diagram of a gas turbine power unit, made in accordance with another embodiment of the invention, in which the turbine is controlled by adjusting the gas parameters at the outlet of the combustion chamber;

in FIG. 12 is a diagram of a gas turbine power unit, made in accordance with another embodiment of the invention, in which the turbine is controlled by controlling the temperature at the inlet to the compressor;

in FIG. 13 is a diagram of a combined cycle operating unit in accordance with one embodiment of the present invention (a power unit with a gas and steam turbine);

in FIG. 14 is a diagram of a gas turbine power unit made in accordance with a preferred embodiment of the invention, in which a conventional cooling tower and a cooling coil are used to cool the compressed air by an air blower;

in FIG. 15 is a perspective view in perspective of the high pressure duct used in the gas turbine power unit of the present invention; FIG. 16A and 16B are an end view and a cross-section, respectively, of an air duct diffuser accelerating an air stream, a general view of which is shown in FIG. fifteen;

in FIG. 17A and 17B are perspective views in perspective of FIG. 15, 16A and 16B of the duct connecting the blower to the gas turbine unit, and in FIG. 18 is a diagram of a gas turbine power unit in accordance with another preferred embodiment of the invention, in which the supercharger of a gas turbine pressurization system comprises, in addition to a blower, a humidifier located at the inlet of the turbine compressor.

-3005393

Preferred Embodiments

In FIG. 2A is a diagram of a gas turbine power unit (electric power generator driven by a gas turbine) constructed in accordance with a preferred embodiment of the present invention. The turbogenerator 11, which is the main element of the gas turbine power unit, consists of a gas turbine 10 and a generator 28. The gas turbine 10 consists of a compressor stage (compressor) 12, a combustion chamber 14 and a turbine stage (turbine) 16. The turbine stage 16 has a common shaft 24 s the compressor 12 and the generator 28. The compressor 12 compresses the incoming air 18, and compressed in the compressor to the appropriate pressure, the air 20 enters the combustion chamber 14. The air 20 entering the combustion chamber 14 is heated, and the hot air leaving the combustion chamber 22 enters the turbine 16. The hot air entering the turbine 22 drives the turbine rotor 24, and with it the generator rotor 28, which generates electrical energy. The exhaust air 26 is discharged from the turbine 16. The exhaust air 26 can simply be discharged into the atmosphere or supplied to the steam generator described below with reference to FIG. 13 operating on a combined cycle power unit with gas and steam turbines.

Shown in FIG. 2A, the diagram of the simplest gas turbine power unit in design allows to reveal all the main features and principles of operation of the turbogenerator proposed in the present invention with a boost system, which, obviously, can have a more complex structure (in particular, a twin-shaft gas turbine), but work the same way the very principle. In this regard, it should be noted that a gas turbine usually has filters, controls, protection devices and other equipment well known to specialists, not related to the principles embodied in the invention and therefore not shown in the drawings and not considered in detail in the description below.

Air 18 is supplied to the inlet of the compressor 12 as follows. Ambient air 40 is supplied by two blowers 30 and 32 to the receiver 38 of compressed air. The compressed air collected in the receiver passes through a cooler 34 and in the form of cooled pre-compressed air 18 is supplied to the inlet of the compressor 12. As a cooler 34, it is preferable to use a direct evaporation cooler that cools and moisturizes the air entering it. The designs of such evaporative coolers are well known. To cool the air entering the turbine compressor, you can also use direct cooling coils, water-cooled coils or mixing heat exchangers, coolers with indirect (indirect) evaporation or other devices designed to reduce the temperature of the air passing through them. The water used in water-cooled coils can be cooled in vapor compression refrigerators, absorption refrigerators or taken from natural sources of cold water, in particular from artesian wells or from the bottom of deep lakes or seas. When cooling the air supplied to the compressor of a gas turbine in an absorption refrigerator, the heat of the gases passed through the turbine can be used as the heat necessary for the refrigerator to operate. The air cooler should preferably be located between the blower blowers and the turbine (compressor), although in principle it can also be installed at the inlet of the blower. The advantage of the first option (installing a cooler behind the blowers) is that in this case it can be used to take heat from the air added to it during compression in pressure blowers.

The presence of a bypass or bypass damper 36 in the system allows the ambient air to flow into the receiver 38 when the boost system is inactive, bypassing the blowers. At the outlet of the first blower 30, a first damper 42 is installed. Exactly the same (second) damper 44 is installed at the outlet of the second blower 32. The operation of the blowers 30 and 32 is controlled by a control device 50 (controller), which receives a signal from the compressor installed at the inlet sensor turbines 52. As signals supplied to the controller, one can use signals from the air temperature sensor at the compressor inlet, the air pressure sensor at the compressor output, the generator output power sensor, and the temperature sensor ambient air. The control device (controller) can be performed on the basis of a simple thermostat or a computer (in particular a microprocessor) and other electronic devices that can be used to control and regulate the characteristics of the turbine.

The dampers 42 and 44 and the bypass damper 36 operate as check valves preventing the back flow of air from the gas turbine through the receiver to the blowers or directly to the atmosphere. The dampers open depending on the differential pressure and, in the absence of a differential pressure, return by gravity to the closed position. In FIG. 2B and 2B show the operation of valves at different operating modes of blowers, which is discussed in more detail below.

The first and second pressure blowers 30 and 32 are preferably in the form of belt-driven centrifugal fans or axial fans directly connected to the drive motor. To increase the efficiency of centrifugal fans, they usually use backward curved blades. Fans of this type can develop pressures up to 60 inches of water. Art. and for this indicator, they usually satisfy the requirements for them. For when

-4005393 water blowers usually use electric motors, preferably three-phase asynchronous motors, although in principle other motors or various mechanical devices connecting the fans to the turbine rotor can be used for this purpose.

Instead of the two shown in FIG. 2A and 2B of the blower fans, three or more fans, as well as just one fan, can be used in the turbine pressurization system of the invention. In a pressurization system with a large number of fans, unlike a system with a single fan, the pressure at the inlet to the turbine compressor can be adjusted in steps.

It is advisable that in a pressurization system with two discharge fans, the fans have different capacities, but operate at approximately the same pressure. The first (main) fan should have greater performance and work, in order to reduce costs, at a constant speed. The second (additional) fan must be made adjustable and used to control the air pressure at the inlet to the turbine compressor, which is described in more detail below. To control the fan performance, a variable speed drive is usually used or, for axial fans, variable pitch rotary blades. The use of rotary blades installed at the inlet of the fan to control the fan performance is possible, but undesirable due to their relatively low efficiency.

In FIG. 3 shows a diagram of a supercharged gas turbine power unit made in accordance with another embodiment of the invention, in which an indirect evaporative cooler is used. The gas turbine power unit made according to this embodiment of the invention differs from the power unit, the circuit of which is shown in FIG. 2, only by the presence in it of a cooler 60 with indirect evaporative cooling, which is located between the receiver 38 and the gas turbine 10. In this power unit, the turbogenerator 11 also consists of a gas turbine 10 and a generator 28. The gas turbine 10 consists of a compressor stage (compressor) 12, the combustion chamber 14 and the turbine stage (turbine) 16. In the cooler 60 with indirect evaporative cooling, a secondary air stream 62 is used, which is taken from the main air stream 64 at the outlet of the optional cooler 68 with direct m evaporation, which is located between the intercooler 60 to the indirect evaporative cooling unit and a gas turbine 10 and for additional cooling of the air entering the turbine compressor. At the inlet of the compressor of the turbine 10, cooled air 66 is supplied, remaining from the main stream 64 of cooled air after the secondary air stream 62 is taken from it. The secondary air stream 62 is heated and humidified in the cooler 60 with indirect evaporative cooling by the air entering it from the receiver 38, and is discharged into the atmosphere as a stream of exhaust air 65.

In FIG. 4 shows another embodiment of the boost system according to the invention, in which this embodiment uses an axial discharge fan driven by an electric motor. The blower fan 116 in this embodiment of the invention has an impeller 102, which is driven by an electric motor 100 arranged with it in the same housing 106. It is preferable to use a three-phase asynchronous electric motor as a fan drive motor connected through an contactor 104 by wires 110, 112 and 114c to an external electrical network. When the contactor 104 is closed, the motor 100 is turned on, which drives the fan impeller 102, forcing compressed air 108 to a certain pressure into the gas turbine 10. When the contactor 104 is opened, the electric motor 100 is de-energized, and the fan impeller 102, which continues to rotate under the influence of through the air flow fan 108, reduces the pressure of the air 108 entering the turbine.

The contactor 104 can be made in the form of a simple device with manual control by which the operator can at any time turn on the fan drive motor, thereby increasing the power of the turbine. In a preferred embodiment of the invention, a thermostat 109 is used to control the contactor 104, which is preferably located in the flow of air entering the turbine 108 and turns on (through the contactor) a blower fan 116 at a time when the temperature of the air entering the turbine 108 reaches a predetermined value. Such a control system of the motor of the blower fan, based on the use of thermostat 109, allows to limit the generation of electricity and protect the turbogenerator 11 from possible overload.

You can control the boost system in more complex ways. So, in particular, for blowing air into the turbine, you can use a fan with adjustable blades connected to a control device or regulator, which, depending on the pressure and temperature of the air, changes the angle of inclination of the fan blades and puts it into operation corresponding to the maximum power generation in peak mode. Based on the currently existing microprocessors, you can create more complex control systems. System performance can be improved through the use of various mechanical devices. So, for example, to reduce the drop in air pressure in the boost system with a de-energized fan, a damper can be used to direct air to bypass the fan. To reduce the temperature of the air entering the turbine in

-5005393 cooling system, you can use an optional cooler with direct evaporative cooling or another cooling device.

An advantage of the system shown in FIG. 4, is its low cost and simplicity, which is especially important for small turbines. To choose the best version of the system, it is necessary to carefully consider all aspects of the problem associated with its implementation and, first of all, with its cost. In some cases, although this is undesirable, you can refuse to use the contactor 104 in the system. In the case when, for example, a turbine operating in an area with a cold climate is supposed to be used in areas with a tropical climate, it is advisable to equip the pressurization system with another discharge fan continuously running while the turbine is running. (It is very important that such a fan can be adjusted in accordance with the characteristics of the turbine at high ambient temperatures.)

A less preferred, albeit possible, embodiment of the pressurization system is a variant with a blower fan, which is driven directly from the turbine rotor. Structurally, this option is implemented most simply with a mechanical connection of the fan shaft with the turbine rotor. However, in reality, in such a scheme, it is necessary to use a gearbox, which allows to reduce the fan speed to a speed lower than the turbine speed. To connect the turbine rotor to the fan shaft, you can use an electromagnetic clutch or mechanical clutch to change the fan speed. To reduce the speed of the fan, differential gears can also be used, connecting the fan to the brake, generator or other device that uses mechanical power, with which you can adjust the speed of the corresponding gear shaft. However, it should be borne in mind that such devices are quite difficult (or even impossible) to integrate into existing turbines, and gears and other mechanical devices, in addition, require constant maintenance. Therefore, this version of the pressurization system cannot be recognized as reliable and efficient as other options proposed in the present invention.

In FIG. 5 shows another embodiment of a possible embodiment of the inventive pressurization system with two discharge fans operating in series. The first blower fan 216 consists of a first impeller 202 and a first drive motor 200, which are located in the first housing 206. The first fan is located in the air stream 208, which is supplied to the inlet of the turbine compressor 12. The first motor 200 is connected by wires 210, 212, and 214 through a contactor 204 to an external electrical network. The second fan 236 is located in front of the first fan 216. The second fan 236 consists of a second impeller 222 and a second drive motor 220, which are located in the second housing 226. The second motor 220 is connected by wires 230, 232 and 234 through a contactor 224 to an external electrical network.

Below with reference to FIG. 2A. 2B and 2B, which show systems with two discharge fans operating in parallel, the principle of operation and advantages of the system proposed in the invention are considered. In the circuit shown in FIG. 2A, both discharge fans 30 and 32 are operating, and the bypass damper 36 is closed, and therefore air cannot enter the fans from the turbine. In this case, the first and second shutters 42 and 44 are open, and the air pumped by the fans passes into the turbine.

In the circuit shown in FIG. 2B, the first discharge fan 30 is turned off, and the second discharge fan 32 is turned on. Bypass damper 36 remains closed. In this case, the second shutter 44 is open, and the first shutter 42 is closed. And finally, in the diagram shown in FIG. 2B, both discharge fans 30 and 32 are turned off, and their shutters 42 and 44 are closed. In this case, the bypass damper 36 is open, and air enters the turbine bypassing the fans 30 and 32.

In FIG. 6 is a graph illustrating all the advantages of such a boost system. These graphs are based on published data for gas turbines. In a gas turbine power unit selected as the basic version, in which there is no pressurization and internal cooling of the air, the turbine can develop maximum power at an ambient temperature of less than 40 ° P, after which its maximum power starts to drop rapidly with increasing temperature. Unlike the basic version, in which the power of the turbine begins to fall rapidly with increasing temperature above 40 ° P, the power of the turbine of a power unit made in accordance with the present invention is practically independent of the ambient temperature. In the basic version of the power unit, one gas turbine was used, in which at an ambient temperature less than 40 ° P, the maximum power is about 100 MW and begins to noticeably decrease with increasing temperature. In the power unit constructed in accordance with the present invention, the same turbine can develop a power of 100 MW at almost any ambient temperature.

The characteristics of the power unit proposed in the invention at high temperatures were also compared with the characteristics of a larger power unit, made according to the basic version scheme, as well as a larger power unit, made according to the basic version scheme, but with an evaporative cooler installed in it. A turbine with a supercharging made according to a well-known scheme was installed in a larger power unit. Use in a larger evaporative cooling unit

-6005393 a la, which reduces the temperature of the air entering the turbine, allows for a given turbine power generation and operation in peak mode at high temperatures to reduce the turbine dimensions. According to its characteristics, a larger power unit with an evaporative cooler, made according to the basic version scheme, practically does not differ from the known gas-turbine power units with a boost system.

Conventional evaporative cooling of the air at the turbine inlet, without increasing the maximum power generation in peak mode at 40 ° E, can improve the external characteristics of the turbine at higher temperatures. The use of a conventional discharge fan together with an evaporative cooler further increases the generation of electricity at any ambient temperature, which creates the risk of overloading a gas turbine power unit at low ambient temperatures.

The solution proposed in the present invention allows to limit the generation of electricity, while retaining all the advantages that the use of pressurization for the operation of the turbine at elevated ambient temperatures gives, and protects the gas turbine power unit from possible overloads at low ambient temperature. The generation of electricity in the proposed power unit (turbogenerator) with a change in ambient temperature varies within very limited limits.

In the table. Figure 1 shows (obtained on the basis of the data given in the above article by Co1p et al.) Data allowing cost-comparison of turbo-generators with the pressurization system proposed in the present invention with turbo-generators made according to conventional schemes. From the data given in this table it follows that the cost of equipping a turbogenerator with a new boost system is approximately half the cost of creating a turbogenerator with an increased maximum turbine power. The increase in the cost of a turbogenerator with evaporative air cooling by 1 kW associated with the installation of boost equipment on it is about $ 300 per kW, while the cost of creating a new turbogenerator with an increased maximum turbine power is about $ 700 per kW. The simultaneous use of an evaporative cooler and a boost system makes it possible to increase the maximum turbine power during peak operation in summer by more than 30%. The control system proposed in the present invention allows the creation of a turbogenerator, the generation of electricity which practically does not change with a decrease in ambient temperature, which eliminates the need to increase the size of the generator and all associated auxiliary equipment. The data in the table confirm all the advantages of the present invention when creating new power plants. When modernizing existing turbine generators, the cost of installing conventional pressure fans on them increases by at least an order of magnitude, since in order to increase electricity production at low ambient temperatures, it is necessary to replace not only the generator itself, but also all associated auxiliary equipment.

Table 1. Comparison of the cost of various options

Cost Power (kW) at peak load Power increase (kW) at peak load Cost increase per kW Peak Turbine basic option $ 21,260,400 30372 30372 $ 700 PLUS evaporative cooler $ 220,000 36180 5808 $ 38 plus boost system $ 1,386,000 40749 4569 $ 303 plus a larger generator and other equipment $ 580,550 40749 0 infinitely large value Combined Turbo Generator main option $ 38,885,000 38885 38885 $ 1000 plus evaporative cooler $ 220,000 47415 8530 $ 26 plus boost system $ 1,386,000 53183 5768 $ 240 plus a larger generator and other equipment $ 1796238 53183 0 infinitely large value

-7005393

In the table. 2 shows data reflecting how much the boost fan improves the characteristics of the turbogenerator. From the table, in particular, it can be seen that the power consumed by the fan is 1.24 MW, while electricity generation increases by 4 MW. In other words, in its pure form, electricity generation increases by 2.8 MW. This result indicates that boost can significantly increase the generation of electricity from turbo-generators operating in peak loads.

Table 2. Comparison of power generation of different options for turbo-generators with a capacity of 100 MW

Basic version Cooler only Extra fan only Additional fan and cooler Inlet static pressure change (inches water) 0 -0.5 10 9.5 Turbine inlet air temperature, ° E 95 77 99.9 78.7 The effect of temperature changes on electricity generation (MW) 0 7.20 -1.96 6.5 The effect of static pressure on power generation 0 -0.30 6.00 5.70 Additional fan drive power 0 0.00 -1.24 -1.24 Net change in electricity generation (MW) 0 6.90 2.80 10.96

(Assumptions: 8 STM / kW, 95 ° T for a dry thermometer, 75 ° T for a wet thermometer, fan efficiency - 80%, motor efficiency - 95%, 0.4% change in kW / (T , 0.6% change in kW / inch water column; cooler efficiency - 90%)

The data presented in the table indicate that the simultaneous use of a blower fan for turbine pressurization and an evaporative cooler in a turbogenerator can significantly increase power generation. As noted above, the use of only one discharge fan to pressurize a turbine without an air cooling system can increase power generation by 2.8 MW. On the other hand, installing the same fan on a turbine with a direct evaporative cooling cooler allows you to increase electricity generation by 4.06 MW. Thus, the effect of using a discharge fan together with a cooler is almost 50% higher than the effect that gives only one fan (without a cooler). Based on the analysis of the data presented in the table, it can be concluded that the combined use of a boost system and an air cooling system in a turbogenerator gives a greater effect than their separate use, and therefore is most preferable.

From the above table. 2 of the data it follows that a significant effect from the boost system can be obtained even when the fan increases the static air pressure at the turbine inlet by only 10 inches of water. Art. Greater effect can be achieved by using pressure fans that create higher static pressure. In a number of cases, optimal results can be obtained when the static pressure created by the boost system at the turbine inlet exceeds 60 inches of water. Art.

In FIG. 7A and 7B show compressor control characteristics that allow one to evaluate how the present invention improves turbine power. The vertical axis shows the relative pressure at the entrance to the turbine, which is equal to the ratio of the pressure at the entrance to the turbine to atmospheric pressure. The horizontal axis represents the flow coefficient, which is calculated by the following equation:

tUv flow coefficient = δ ’

-8005393 where t is the mass flow rate of air passing through the turbine, δ is the pressure at the compressor inlet divided by normal atmospheric pressure, and θ is the absolute temperature at the compressor inlet divided by the calculated absolute temperature.

The relative air pressure at the turbine inlet is equal to the pressure at the compressor outlet divided by atmospheric pressure. In the considered example, it is assumed that the influence of the pressure drop in the combustion chamber and other non-essential factors are taken into account in the external characteristics of the compressor and turbine (detailed information on this can be found in the 10th chapter of the book В1а111с Рипбатей1а1к о £ Сак ТигЫиек).

Curve 300 represents the compressor response under design conditions, and curve 301 represents the compressor response at peak inlet temperature. Curve 302 represents the turbine response under design conditions, and curve 303 represents the turbine response at peak inlet temperature. The point 304 of intersection of the characteristics of the compressor (curve 300) and the turbine (curve 302) characterizes the calculated mode of operation of the gas turbine. The point 305 of the intersection of the characteristics of the compressor (curve 301) and the turbine (curve 303) characterizes the operation mode of the gas turbine at the peak value of the inlet temperature. Straight line 306 characterizes all possible modes of operation of a gas turbine at various inlet temperatures. The straight line rising up 307 characterizes the maximum possible modes of stable operation of the compressor.

The power developed by the turbine at high air temperature (point 305) is much less than the power developed by the turbine under design conditions (point 304). With increasing air temperature at the turbine inlet, the speed of sound increases, as a result of which the Mach number of the compressor decreases, and its external characteristic shifts to the left to the region of lower mass flow rates. A decrease in air mass flow with increasing temperature also occurs due to a decrease in its density. As a result of these changes, not only the mass air flow rate is reduced, but also the relative pressure at the turbine inlet, which, obviously, reduces the energy that causes its rotation. It is possible to increase the energy under the action of which the turbine rotates by cooling the air.

In FIG. 7B shows how the system of the invention makes it possible to increase turbine power at peak ambient temperatures. When preliminarily compressing the air entering the compressor, which increases the relative pressure at the turbine inlet, and increasing the temperature at the compressor inlet, the possible compressor operation modes are determined by its external characteristic, shown in the graph in the form of curve 310. The external temperature also changes due to a small temperature increase turbine characteristic (straight line 312). In this case, the operation mode of the gas turbine will be determined by the point 314 of intersection of the external characteristic of the turbine (straight line 312) with the external characteristic of the compressor (curve 310). In this mode, a gas turbine with supercharging (with a blower fan) will work, but without a cooling system for the air entering it. All possible pressure (and flow) operating modes of a gas turbine thus constructed are determined by the position of points lying on a straight line 318. An increase in the output power of the turbine also occurs due to an increase in air density, which occurs when it is precompressed in the discharge fan.

With evaporative cooling and a decrease in the temperature of the air entering the compressor, the external characteristics of the compressor and turbine change, which is reflected by curve 316 and a straight line 320. When boosting and cooling the air entering the turbine, the operating point 322 of the turbine will lie at the intersection of curve 316 (external characteristic of the compressor ) and direct 320 (external turbine characteristic). Such an analysis of the combined operation of the compressor and the turbine makes it possible to approximately estimate the initial design power of the gas turbine while using the pressurization system and the air cooling system at the turbine inlet. In this case, the limiting values of the turbine power, as well as its operating pressure and the design power of the turbogenerator can be set taking into account the capabilities of the turbine, generator and other equipment of the power unit. With the appropriate choice of the parameters of the discharge fan and the cooler installed at the compressor inlet, it is possible to ensure that the output power of the turbine at any ambient temperature does not exceed its rated power.

In FIG. Figure 8A shows the external characteristics of a pressurization system, which consists of discharge fans operating in parallel, creating the necessary overpressure at the turbine inlet. In parallel operation of the fans, both fans operate at the same pressure, and their costs are summed with each other. The external characteristic of the main (first) fan is shown in FIG. 8A in the form of a curve 350. The external characteristic of the turbine at a flow rate slightly varying depending on the inlet pressure has the form of an almost vertical straight line 356. The operation mode of the gas turbine in this case is determined by the point 358 of intersection of the external characteristic of the fan (curve 350) with the external characteristic of the turbine ( straight line 356). Operating point 358 corresponds to the operation of only one fan.

-9005393

Shown in FIG. 8A curve 352 represents the first external characteristic of the second (additional) fan when it is operating at maximum speed. Curve 364 is an external characteristic of the boost system with two fans working together. When two fans work together, the gas turbine operation mode will be determined by the position of the point 366 of intersection of the external characteristic of the boost system (curve 364) with the external characteristic of the turbine (straight line 356). The second external characteristic of the second (additional) fan during its operation with low revolutions is depicted in FIG. 8A in the form of curve 354, and the external characteristic of the pressurization system with the first fan operating normally and the second fan operating at low revolutions is shown in FIG. 8A in the form of a curve 360. The gas turbine operating mode in this case will be determined by the position of point 362 lying at the intersection of the external characteristics of the turbine and the boost system, in which the second fan operates at low revolutions.

In FIG. 8B shows the external characteristics of a system with two identical fans operating in series. Curve 372 in FIG. 8B shows the external characteristic of one fan. With one fan running, the turbine will operate in a mode determined by the position of point 378 of the intersection of its external characteristic with the external characteristic of the fan. Curve 374 in FIG. 8B shows the external characteristic of the boost system with two fans operating in series. With two fans operating in series, the turbine will operate in the mode determined by the position of point 376.

In FIG. Figure 9 shows, by way of example, the relationship between the maximum pressure generated by the boost system and the temperature of the air entering the turbine, which can be used to control the blower fans. The pressure generated by the fans is controlled by means of a control device or a regulator, which receives a signal proportional to the temperature of the air entering the turbine. This method of regulating the pressure of the fans allows you to simply increase the operating power of the turbine to a maximum level. The greatest effect of this method of regulating fans can be obtained by modernizing existing turbogenerators, since this completely or almost completely eliminates the need to make changes to the existing regulation system of the turbogenerator.

The invention suggests the possibility of more complex ways of regulating a turbogenerator. Thus, in particular, another preferred embodiment of the inventive control system of the turbogenerator 421 shown in FIG. 10 is a system in which a portion of the compressor compressed air is fed back to the compressor inlet. Shown in FIG. 10, the turbine generator consists of a gas turbine 432 and a generator 426. In turn, the gas turbine 432 consists of a combustion chamber 422, a compressor 420 and a turbine 424, which has a common rotor 430 with the compressor. The air 440 entering the compressor 420 is compressed in the compressor, and compressed into compressor 442 air enters the combustion chamber. The air 442 entering the combustion chamber 422 is heated in the combustion chamber, and the hot air 444 leaving the combustion chamber enters the turbine 424. The turbine 424 is driven into rotation by an air stream discharged therefrom in the form of an exhaust air stream 446. The turbogenerator also contains other devices well known to those skilled in the art and therefore not shown in the drawing, including the supporting frame (housing), bearings, monitoring devices, etc. In addition to the gas turbine, a steam turbine, as well as various multi-shaft turbines, can also be used to drive the generator.

The turbine 424 drives the compressor 420 and the generator 426, which have a common rotor 430 with it. The electric power generated by the generator is transmitted to the electric network through a transformer 428 connected to the generator by wires 436.

The blower fan 423 compresses the incoming air 453, and the compressed air 455 enters the first evaporative cooler 425. The main elements of the first evaporative cooler 425 are the pump 437 and the inside of the evaporator 435 coated with the corresponding material. The compressed air 455 entering the first evaporative cooler 425 leaves from it in the form of cold compressed air 440, which is fed to the turbine inlet.

The blower fan, the static pressure at the outlet of which is about 60 inches of water, is preferably made in the form of a centrifugal or axial fan. The air compressed by the fan 455 and the compressed air 440 cooled in the cooler pass through air ducts designed for such a high pressure; preferred embodiments of such ducts are shown in FIG. 15, 16A, 16B, 17A and 17B and are discussed in detail below.

A second evaporative cooler 434 is installed at the inlet of the blower fan 423. The main elements of this cooler are also the inside of the evaporator 434 coated with the appropriate material and the pump 436, which pumps water through the evaporator, in which water evaporates on the surface moistened with water, accompanied by cooling of the outside air passing through the evaporator , the cooled stream of which 453 enters the inlet of the blower fan 423. Evaporative coolers also have a sump with a float valve SG controlling the water level in the sump, and a device which avoid the salinity of water in a closed cooling circuit periodically bleeds out of it a small amount of water.

-10005393

As a cooler in the system of the invention, any of the evaporative coolers currently available in the industry can be used, which are well known and therefore do not require a detailed description. In addition, in addition to the direct evaporative cooling chillers shown in the drawings, for operation of the turbogenerator proposed in the invention with a boost system, as already noted above, indirect evaporative cooling coolers or evaporators with combined direct and indirect evaporative cooling can be used.

A key distinguishing feature of the turbogenerator proposed in the present invention is the ratio between the dimensions of the supercharged gas turbine used in it and the dimensions of the generator and associated auxiliary equipment. So, in particular, in the turbogenerator proposed in the invention, the dimensions of the generator and turbine are selected so that, with peak loads in the summer, the generator runs at almost full power. (In contrast to the existing gas turbine power units, the dimensions of the generator and auxiliary equipment are selected on the basis that it should develop maximum power with a boost system operating at maximum load in winter, when the inlet air temperature does not exceed 40 ° P, with a gradual decrease in power with increasing ambient temperature). To this end, the turbogenerator proposed in the present invention uses a special turbine power control system at low ambient temperatures, which protects the generator from possible overload.

In the inventive control system, there is a control device or regulator 460, which receives a signal 468 from a current sensor 462, which measures the current of the generator. As such a regulator 460, one can use either a conventional turbogenerator regulator, which ensures safe operation of the turbogenerator at rated power, or a regulator made in the form of a separate (stand-alone) unit. As a current sensor, it is preferable to use a current transformer that produces an AC signal. Other types of sensors, such as voltage sensors, optical sensors, or sensors with an RF output signal, can be used as a sensor installed on the generator.

The controller 460 provides a control signal 464 to the damper actuator 450, which controls the flow of warm compressed air 452, which is returned to the compressor inlet, taken from the air 442, which is supplied from the compressor to the combustion chamber. The controller 460 also provides control signals 466 and 467 to the pumps 436 and 437, respectively, and the control signal 465 of the blower fan 423. In this embodiment, the pumps and the fan can be controlled according to the simplest scheme (on / off), however, in principle, the control system may be more complex, based on the regulation of the speed of the pumps and fan, their regulation with the help of inlet blades or on the use of pumps and fans with rotary blades.

Since the system proposed in the invention is designed to obtain maximum turbogenerator power at peak loads in summer, when the ambient temperature drops and the turbine output power increases, the power generated by the generator can exceed its maximum rated power. When the ambient temperature drops, the signal level 468 increases, which enters the controller 460 from the generator current sensor 462. The controller, in response to this signal, turns off the pump 436, which pumps cooling water through the second evaporative cooler 470, as a result of which the temperature of air 453 entering the discharge fan increases almost to the ambient temperature of the dry thermometer. With a further drop in ambient temperature, the regulator optimally opens the damper 450, and part of the warm air leaving the compressor 452 is returned to the compressor inlet, where this warm air is mixed with cold air 440, which enters the compressor from the fan. A further drop in ambient temperature is accompanied by a further opening of the damper with a corresponding decrease in the generator current, which gradually switches to work in the nominal peak load mode in summer.

At that moment, when the ambient temperature drops to the minimum design level, according to the signals 465 and 467 coming from the controller 460 to the fan and pump, the fan 423 and pump 437 of the first evaporative cooler 425 are turned off and, as a result, the pressurization system is completely turned off . After the boost system is turned off, controller 460 may, at signal 464, completely shut off the damper 450.

A diagram of another embodiment of a gas turbine power unit (turbogenerator) of the present invention is shown in FIG. 11. Similar to the embodiment shown in FIG. 10, a signal 468 from the generator current sensor 462 is supplied to the controller 474, and in response to this signal, the controller provides a control signal 466 to the pump 436. In this embodiment, however, the controller 474 not only controls the damper that controls the flow of warm compressed air from compressor output back to the compressor inlet, but also gives a control signal 472 to the combustion chamber 422, the turbine output depends on the operation mode of which. It is preferable to integrate 474 into a conventional re

-11005393 of walking, ensuring the safe operation of the turbogenerator in normal mode, although in principle it can also be performed as a separate unit.

The control system in the embodiment shown in FIG. 11 operates in the same way as the control system in the embodiment shown in FIG. 10. If the ambient temperature drops and the generator current increases correspondingly, the controller 474 switches off the pump 436 by a signal from the current sensor, thereby stopping the operation of the second evaporative cooler 470. If, however, the generator current does not decrease to a value corresponding to the generator power at peak power consumption in summer time, the controller 474 on the control signal 472 issued by it to the combustion chamber reduces the temperature of the hot gases entering the turbine from the combustion chamber 422. With a further decrease in ambient temperature, the controller, while turning off the blower fan 423 and the first evaporative cooler 425, completely disconnects the entire charge system from the turbogenerator.

In FIG. 12 is a diagram of yet another embodiment of a gas turbine power unit (turbogenerator) according to the invention, in which the output of the turbine is controlled by a heater by changing the temperature of the air entering the compressor. In this embodiment, a signal 490 is supplied to the controller 484 from a temperature sensor 488, which measures the temperature of the air 440 at the compressor inlet. The controller 484 provides a control signal 482 to a heater 480 installed prior to the compressor, from which the heated air 486 then flows to the compressor 420. (A heater located in front of the evaporative cooler can also be installed between the evaporative cooler 470 and compressor 420, provided that it made of materials that are not subject to intense corrosion when exposed to high temperature moist air).

There are many different embodiments of such a heater. In the simplest version, it can be made in the form of a gas burner. As a heater, you can also use a boiler with a liquid-air heat exchanger, in which air is heated by the water heated in the boiler. The third option is the use of a heat exchanger, in which the air supplied to the compressor is heated by exhaust gases from the turbine 446. (This option is the most economical and therefore, at a low cost of the heat exchanger, the most preferred). To heat the air, you can also use electric heaters, which in principle is undesirable due to their low efficiency. The cheapest way to heat the air 440 supplied to the compressor is to supply part of the exhaust gas 446 to the compressor, although in many cases this solution may not be acceptable due to problems associated with corrosion of the compressor 420 or other components of the turbogenerator. The heater, irrespective of its type, must be adjustable and must maintain the temperature of the heated air 486 leaving it at approximately constant level.

In the embodiment shown in FIG. 12, the control system is designed to maintain at a minimum level of air temperature 453 at the inlet to the discharge fan. When the ambient temperature drops, the controller 484 turns off the pump 436, which pumps water through the evaporative cooler 470, which stops cooling the air passing through it. With a further decrease in the ambient temperature, the controller 484 provides a control signal 482 to the heater 480, which, having received this signal, turns on and maintains the air temperature 453 at the inlet to the fan at the required level.

As shown in FIG. In the 13th embodiment, the power unit proposed in the invention operates in a combined cycle using two turbines simultaneously - gas and steam. This power unit 506 has an additional steam turbine installation 498, in which the heat of the exhaust gases of a gas turbine 424 is used to generate additional electric energy. The steam turbine installation 498 includes a steam boiler 504, a steam turbine 500, a condenser 502, and a condensate feed water pump 503. At the power unit there is another closed loop in which a liquid-air heat exchanger 491 is installed, connected by a water pump 492 to a heat exchanger 496, which Values for heating the water circulating in the circuit due to the heat emerging from the gas turbine. A pump 492 pumps water 512 (liquid) through a heat exchanger 496, in which water draws heat from a stream of 508 gases passing through a steam turbine boiler 508. The pump into which the control signal 494 from the controller 484 enters regulates the flow of water 512 in a closed circuit, thereby regulating the temperature of the air 486, which enters from the heater to the outlet of the evaporative cooler 470. As in the embodiment shown in FIG. 12, the controller can, at the first stage of regulating the temperature of the air entering the turbine, turn off the second evaporative cooler 470, and then, if necessary, completely disconnect the entire charge system from the gas turbine.

(In the embodiment described above, the heat of the exhaust gas 508 of the gas turbine passing through the steam turbine boiler was used as heat to heat the air entering the charging system, however, however, some elements of the installation must be made of corrosion-resistant materials that could withstand exposure to nitrogen and possibly sulfuric acid. One solution to this problem would be to use plastic pipes, which,

-12005393 however, does not withstand high temperatures. To reduce the temperature of the gases passing through such pipes, the gases leaving the gas turbine can be mixed with the ambient air, reducing their temperature to the temperature that the plastic pipes could withstand. To heat water, which is used to heat the surrounding air, a gas-liquid type heat exchanger can also be used, in which heat is transferred from gas to liquid. In order to avoid problems associated with the formation of acid condensate, a certain amount of an appropriate acid neutralizing agent (e.g. sodium bicarbonate) can be added to the liquid (water). In this case, it is also advisable to mix the exhaust gases from the gas turbine with a certain amount of ambient air.)

A turbine power unit, the circuit of which is shown in FIG. 13, not only allows to increase the generation of electricity at high ambient temperatures, but also has increased efficiency, which, as is known, in turbine generators operating in the combined cycle increases slightly with increasing air temperature at the compressor inlet. In this regard, it should be noted that shown in FIG. 13, the closed-loop variant, in which the heat of the exhaust gases of the turbine is used, is not the only possible embodiment of the proposed turbine power unit operating in a combined cycle. In this case, in particular, to heat the air entering the pressurization system, a steam turbine condenser 502 can be used. Another possible solution is to use an air-air heat exchanger in which the air entering the pressurization system is heated by the gases leaving the gas turbine.

The above diagrams show various options for a possible implementation of the proposed in the present invention gas turbine power unit (turbogenerator). In this regard, it should be noted that as feedback signals in the control system described above, it is possible to use not only the signal from the generator current sensor or the signal from the air temperature sensor at the compressor inlet, but also signals characterizing other parameters of the turbogenerator operation. Such parameters that characterize the operation of the turbogenerator that can be used in the control system include, in particular, generator power, dry ambient temperature, humid ambient temperature, torque, and a number of other parameters.

Use in the circuits shown in FIG. 10-13, the second evaporative cooler, located before the discharge fan, is not necessary, and it can be abandoned without a noticeable change in the characteristics of the power unit. In this case, however, it should be borne in mind that the use of a second evaporative cooler, which allows increasing the pressure created by the discharge fan at high ambient temperature, provides the possibility of some increase in the output power of the power unit.

It should also be noted that in some cases you can refuse to use the first evaporative cooler, which, however, will lead to a more noticeable change in the characteristics of the power unit. Therefore, it is advisable to do this only if there is a special need, for example, with a lack of water and / or in the absence of free space to accommodate this cooler.

It should be further noted that in all the options considered above, the optimal way to control the blower fan is to simply turn it on and off. The blower fan can also be controlled in more complex ways, for example, by using a variable-speed drive or by using fans with rotary blades, which, although they allow a certain decrease in the power consumed by the fan, are nevertheless not preferred, since it is advisable to regulate the turbine output operating mode of the combustion chamber or air temperature at the inlet to the compressor.

In FIG. 14 shows another preferred embodiment of a gas turbine power unit of the present invention with an indirect (indirect) evaporative cooling system and a speed-controlled drive of a blower fan of a turbine pressurization system. Shown in FIG. 14, the variable-speed drive 550 of the fan is powered by an external AC network and supplies variable voltage with an adjustable frequency to the induction motor 552. The output shaft 554 of the motor 552 is connected to the discharge fan 556. The discharge fan draws in ambient air and supplies compressed air 558 to the cooling coil 560. The cooling coil the coil, which is a water-air heat exchanger, cools the air without humidifying it. The cold air exiting the coil 570 enters the evaporative cooler 425, the construction of which is described above.

The cooling coil 560 is connected by a pipe 562 to the pump 564 and the cooling tower 566 and forms a closed circuit with them, which acts as a cooler with indirect evaporative cooling. The cooling tower is preferably made in the form of a cooling tower with an injection fan, in which water can be cooled to a temperature close to the ambient temperature of the wetted thermometer.

(In areas with water shortages, instead of the usual wet cooling tower, you can use the so-called dry cooling tower and generally abandon evaporative cooling. In this case, a dry cooling tower

-13005393 and the coil will operate as a normal heat exchanger, in which heat is exchanged between the ambient air and the air leaving the discharge fan.)

In addition to the above, other structural solutions of the cooling system and the use of other heat exchangers are possible. So, in particular, the cooling tower and cooling coil can be replaced with an air-to-air heat exchanger, passing ambient air and air leaving the discharge fan through it. In this case, the air cooler with direct evaporative cooling should be installed before this heat exchanger in the line through which the surrounding air passes, thereby ensuring its additional cooling. Although such schemes are possible, they are nevertheless not preferred, since they require the creation of a large, expensive heat exchanger with a large heat exchange surface and a large pressure difference of the air flows passing through it.

In places of possible freezing of water, special measures have to be taken to protect pipelines, a cooling coil and a cooling tower. To do this, you can use various thermal insulation and heaters, systems for draining water from the cooling circuit and brine in a water-brine type heat exchanger. (The use of a water-salt solution type heat exchanger simultaneously solves another problem related to the formation of dirt deposits in the pipes of the cooling coil that enter the water when it is cooled in the cooling tower and the need to use appropriate filters in single-circuit systems.)

In this embodiment, regulator 568 protects the turbogenerator from overload at low ambient temperatures. The controller 568 receives a signal 572 from a temperature sensor 573 installed at the compressor inlet and measures the temperature of the air 440 entering the compressor. The controller also receives a signal 574 from a pressure sensor 575 that measures the pressure of the compressed air 558 at the outlet of the fan. A pressure sensor 575 can be installed anywhere in the installation between the blower fan 556 and the gas turbine 432, since the drop in air pressure in the air line connecting them is quite small.

The controller 568 provides a speed control signal 578 to the variable speed drive 550 of the variable speed drive fan motor. As a result of a corresponding change in the fan speed in the pressurization system, the optimum air pressure is constantly maintained. The controller also provides a control signal 576 to a pump 564 installed in a closed cooling water circuit including a cooling tower and a control signal 580 to a pump 437 installed in an evaporative cooler.

Usually these signals simply turn the pump on or off.

In addition to the variable frequency drive described above, other various methods can be used to change the air flow rate of the discharge fan. Such methods include, in particular, the method proposed in I8 patent 5947854 and in provisional patent application US 60/164590 and based on the use of an electromechanical variable drive, as well as methods based on the use of eddy current couplings, DC motors, rotary fans blades, adjustable inlet guide vanes, etc. etc.

A significant advantage of this option is the ability to deliver relatively cold air to the gas turbine. The compression of the air in the discharge fan does not have any effect on the air temperature measured by the wetted thermometer at the inlet to the cooling system. Therefore, the air 558 entering the cooling coil can be cooled in it to a temperature close to the ambient temperature using a wet thermometer without increasing air humidity. In the evaporative cooler 425 behind the coil, the air is further cooled and humidified. As a result, the air entering the gas turbine may have a temperature that is approximately 10 ° P lower than the temperature of the air when it is simply cooled in a cooler with direct evaporative cooling. Such a decrease in the temperature of the air entering the turbine makes it possible to increase the amount of electricity generated by the turbogenerator by approximately 2.5%. Since usually about 10% of the additional electricity received is spent on cooling tower fan operation and pump operation, the net increase in the electricity generated by the turbo-generator in this embodiment is at least 2%.

The cooling system of the air injected into the gas turbine can be more complex. So, in particular, instead of a cooler with direct evaporative cooling, mechanical, desiccant (moisture absorbing) or absorption cooling systems can be used. Another possible option is to use groundwater or cold water from a lake or ocean in a cooling system. Such systems make it possible to use air with significantly lower temperatures for boosting the turbine, thereby increasing the useful power of the turbogenerator. The disadvantage of such systems is their complexity and the need for additional investment.

As already noted above, air ducts for compressed air and air entering the turbine must be able to withstand a relatively high pressure and must therefore have a suitable design, a preferred embodiment of which is shown in FIG. 15. In the made according to this option duct, which consists of an inner pipe 610 and

-14005393 round outer pipe 611, there is a channel 612, designed to equalize the pressure of the fluid flowing through the inner pipe and filling the free space 615 between the inner and outer pipes. (In the system of the present invention, compressed air passes through such a pipeline, however, the same pipeline design can also be used to pump any liquids under high pressure.) It is preferable to fill the free space 615 between the pipes with a liquid or porous material, such as fiberglass, open cell foam or other similar material. The porous material not only reduces the noise created by the air passing through the pipeline, but also increases the bearing capacity of the entire pipeline.

Channel 612, designed to equalize the pressure acting on the walls of the inner pipe, can be made in the form of one or more simple holes or in the form of pores in the material of which the inner pipe is made. Channel 612 can also be made in the form of cracks or crevices or small holes, which are often used for the passage of fluid in leaking pipelines. The main requirement that channel 612 must meet is its large throughput, which could limit the increase in pressure in the inner pipe when fluid leaks from the outer cylindrical pipe into the surrounding space. In the channel connecting the inner pipe with the space located between it and the outer pipe, it is advisable to install a safety valve that operates at a certain pressure in the inner pipe and protects it from destruction when a leak occurs in the outer pipe.

The inner pipe, which should not have high strength, can have in cross section not only the one shown in FIG. 15 is a rectangular shape, but also any other shape different from a circle and formed, for example, by large flat surfaces. The strength requirements of the inner pipe are limited by a small pressure difference acting on its inner and outer surfaces, high-speed pressure, turbulence and other factors, one way or another connected with the fluid flowing through it.

In order to save material, the outer pipe should preferably have a circular cross section. The use of a pipe with a different cross-section, in particular oval or elliptical, is possible, but not desirable, since the problems associated with the strength of the pipe increase significantly. Larger pipes can be made with ring stiffeners or other reinforcing elements, which can increase the stiffness of the pipe and its strength against wind or other random loads.

Typically, pipes are made of metal, in particular steel or aluminum. Other materials that can be used to make the pipes of the duct described above include plastics, wood, ceramics, etc. The choice of a particular material depends on a number of factors, such as the strength of the pipe, its cost, and the compatibility of the material with the fluid flowing through the pipes.

In FIG. 16A and 16B respectively show a front view and a cross section of a transition pipe that can be used to connect pipes of various sizes. This pipe consists of an outer pipe 620, made in the form of a cone with a round cross section, and an inner pipe 621 located in it, made in the form of a tetrahedron or pyramid. In the wall of the inner pipe 621, a channel 622 is made for the passage of fluid, which is designed to equalize the pressure of the fluid flowing through the inner pipe and the pressure in the free space 623 between the inner and outer pipes. Depending on the direction of fluid flow, such a transition pipe can be used either as a diffuser or as a confuser increasing the speed of the fluid flowing through the pipe. It should be noted that the present invention is not limited to those shown in FIG. 15, 16A and 16B, the main options for the implementation of the high pressure duct proposed in it are extended to pipes of any geometry, including elbows, tees, adapters, etc.

In FIG. 17A and 17B show a duct structure designed specifically for a gas turbine pressurization system. In FIG. 17A shows one cooler 630 without a blower fan, made in the form of a direct evaporative cooling cooler 630, which is located at the end of a rectangular duct 631, through which air enters the gas turbine inlet. Rectangular duct 631 is designed for differential pressure (the difference between the air pressure inside the duct and atmospheric pressure) not exceeding a few inches of water.

In FIG. 17B shows a duct connecting a discharge fan to a gas turbine. Fan 635 increases the static air pressure to a very high level, typically exceeding 60 inches of water. A fan 635 is connected to one of the ends 639 of the diffuser 636. The other end of the diffuser is connected by a straight pipe 637, inside which an evaporative cooler is located, to the confuser 638. Each of these sections of the duct consists of an outer pipe round in cross section and a pipe with a rectangular transverse inside section.

The duct proposed in the invention has, in comparison with conventional ducts, a number of significant advantages listed below:

-15005393

- less weight and lower cost (compared to conventional ducts with a rectangular cross section),

- less pressure drop compared to conventional ducts with a circular cross section and elements with a rectangular cross section,

- simplicity of geometry and simplicity in the design and manufacture and

- the possibility of modernizing existing ducts in order to increase the pressure of the air passing through them.

Such advantages of the inventive duct are manifested primarily when it is used in a gas turbine pressurization system. High pressures (about 60 inches of water) and large sizes (over 30 feet in diameter) require the use of rectangular ducts with high strength in a gas turbine pressurization system, the manufacture of which is associated with a very high consumption of materials. The design proposed in the invention eliminates the need for rectangular ducts that withstand high gas pressure, and can significantly reduce the consumption and cost of materials necessary for the manufacture of the duct, as well as its weight. The solution proposed in the present invention also allows for the modernization of existing gas turbine power plants to use their coolers and pipes and creates the prerequisites for a significant reduction in the cost of equipping a gas turbine with a boost system. In addition to pressurization systems for gas turbine plants, the air duct design proposed in the invention can be used in air conditioning systems, as well as in other industrial or commercial systems that require pumping gases or liquids.

In FIG. 18 shows yet another embodiment of a gas turbine power unit according to the invention, which provides for the use of foggers, in which a water fog is formed moistening the air entering the gas turbine. The turbogenerator 121, which is the main element of the power unit, consists of a compressor 120 and a turbo expander 124, which are rigidly connected by a shaft 130 to a generator 126. The compressor compresses the air entering it 191 and delivers it to the combustion chamber 122. Hot gases generated in the combustion chamber enter the turbo expander 124. The energy of the gases entering the turbo expander is converted into mechanical energy, which is expended on the drive of the compressor and generator.

At the inlet of the turbogenerator, a turbine pressurization system 190 is located. The turbine pressurization system 190 consists of a blower fan 140, a first humidifier or fogger 149 and a second fogger 169, which are located inside the duct 147. The first fogger is located at the inlet to the fan, and the second between the fan and the turbine.

The fan 140 has a shaft 141 with a hub and blades 142. The fan shaft is rigidly connected to the shaft 144 of the drive motor 146. The motor 146 rotates the shaft 144 and drives the fan shaft with blades fixed on its hub. As a fan, it is preferable to use an axial fan with rotary blades. The rotation mechanism of the blades 142, which is designed to control the pressure and flow rate of the fan, is usually located inside the hub of the shaft 141.

As the drive motor of the fan, it is preferable to use a three-phase asynchronous electric motor or some other electric motor. The gas turbine itself can also be used as a fan drive, by directly connecting its rotor to the fan shaft (it is obvious that this solution eliminates the need to use a separate electric motor for the fan drive). Other embodiments of the fan drive are possible (although less preferred), in particular the use of a separate gas turbine, steam turbine or internal combustion engine to drive the fan. The most optimal of all possible options is the option with a separate electric motor, which can be relatively simply installed on an existing gas turbine.

The static air pressure at the fan outlet is typically about 60 inches of water. The optimal pressure value depends on the characteristics of the fan, generator power, turbine power, and a number of other factors.

Such static pressure in the boost system can create the one shown in FIG. 18 multi-stage axial fan. Centrifugal and single-stage axial fans can also be used to create the required pressure. Centrifugal fans usually do not use rotary blades, and therefore their performance is usually controlled by changing the speed of rotation using an adjustable drive. Other, however less effective, methods associated with the use of inlet guide vanes with rotary blades or conventional dampers can also be used to control fan performance. A variable speed drive can also be used to control axial fans.

The first fogger 149 consists of the first, second and third collectors 156, 158 and 160, respectively. Each collector has spray nozzles generating water dust (fog) 162. Water is supplied to the first collector under excessive pressure by the first pump 150.

-16005393

Similarly, the second pump 152 and the third pump 154 supply pressurized water to the second and third collectors 158 and 160, respectively. The water pressure at the pump outlet should preferably be from 1000 to 3000 psi. The water supplied to the inlet of each pump is indicated on the diagram by 164. Typically, the fogging pumps operate on filtered, salt-free water. In this embodiment, the air 148, which is sucked by the fan into the duct 147, first passes through the first fogger 149.

A second fogger 169 is located behind the fan. Like the first fogger, the second fogger consists of several headers and pumps. The fourth, fifth, and sixth collectors 176, 178, and 180 available in this fogger are connected to the fourth, fifth, and sixth pumps 170, 172, and 174, respectively. The pumps supplying the spray nozzles of water available in the manifolds under excessive pressure are accompanied by the formation of water dust (fog ) 182.

Structurally, foggers can be performed in different ways. So, in particular, each fogger can have any arbitrarily selected number of collectors. A large number of collectors makes it easier to control the amount of fog generated and to have a certain number of spare collectors in the system. On the other hand, with fewer collectors, the problems of their installation are easier to solve and, as is obvious, the cost of the system is reduced. It should also be noted that the collectors do not have to have the same (in terms of the amount of fog generated in them) performance.

If we talk about the performance of foggers, the first fogger should provide close to full saturation with moisture of air at the outlet of the fan. In the air passed through the second fogger, completely saturated with moisture should contain some excess moisture to help cool the air in the compressor 120. The total amount of water added to the air should be slightly larger (up to 2% of the mass air flow) of the amount of water needed to completely saturation of air with moisture at the inlet to the compressor.

The operation of the boost system 190 is controlled by a regulator 161. The regulator reduces air pressure and the amount of fog contained therein at low ambient temperatures and protects the generator and other elements of the gas turbine power unit from overload. This controller receives signals from a sensor 182, which measures the temperature at the inlet to the fan, and a sensor 184, which measures the temperature of the air at the outlet of the fan. When the ambient temperature drops along the wetted thermometer, the sensor installed at the fan inlet gives a corresponding signal to the controller, which in turn gives a signal to the rotation mechanism of the blades to reduce the pitch between the blades and reduce the fan performance. The lower the ambient temperature by the wetted thermometer, the less water is required to completely saturate the air with moisture, and therefore, when the ambient temperature decreases, the controller 160 turns off some of the fogging pumps.

When the ambient temperature approaches the freezing temperature of the water, all the pumps of the first fogger turn off in order to avoid ice formation. The second fogger can continue to work under these conditions, unless its operation leads to an overload of the generator and other associated power unit equipment.

At very low ambient temperatures, when the gas turbine can operate normally without any boost, the fan and foggers must be turned off (while the fan can continue to rotate in the flow of air passing through it). In order to avoid a too large drop in air pressure at the turbine inlet, a damper can be installed in the system to direct ambient air to the turbine bypassing the idle fan.

Various changes can be made to the main option discussed above. So, in particular, in cases where the operation of the turbine compressor substantially depends on the droplets of water contained in the air, the second fogger can generally be excluded from the equipment available in the pressurization system. In this case, with the help of the regulator, the amount of water dust entering the air in the first fogger can be maintained at such a level that all water droplets contained in it can completely evaporate before air enters the gas turbine.

Another possible, although less preferable, embodiment of the pressurization system described above is one in which the first fogger is missing. In order to avoid a noticeable deterioration in the characteristics of the turbogenerator due to the absence of the first fogger, the productivity of the second fogger should be accordingly increased.

The choice of fan for the system described above is also not limited to any one particular option. In some cases, you can, for example, install several fans in the boost system. The presence of a large number of fans in the pressurization system creates a certain reserve and increases the reliability of the system. The presence of common parts in a system with a large number of fans can reduce the cost of the system and use a more complex and more efficient control system in it.

-17005393

It is also possible to create a boost system with a fixed fan capacity. Such a solution may be optimal in cases where the generator is designed for the full power of the turbine under normal operating conditions. Such a solution may also be possible in turbine generators with another turbine power control system that protects the generator and other equipment of the power unit from overload and based, for example, on regulating the operation of the combustion chamber or heating the air entering the turbine.

In the pressurization system of existing gas turbine power plants (turbogenerators), various filters and silencers are usually used. The operation of the fan and foggers is essentially independent of the amount of dust contained in the air, and therefore, when choosing a filter installation location, you should be guided in the first place by such factors as ease of access to it. It is preferable to install the filter directly at the inlet of the fogger, since the water droplets contained in the air slightly increase the pressure drop across the filter. To reduce the noise level to the fan, it is advisable to install a muffler.

The proposed boost system can significantly increase the power of the gas turbine. When using in the system of pressurization a conventional discharge fan with a pressure of about 60 inches of water. and a conventional evaporative cooler with a coefficient of efficiency of about 90%, the increase in turbogenerator power can be from 20 to 30%. The use of foggers for air cooling provides an additional increase in power by at least another 10%. The formation of fog allows you to increase the efficiency of the evaporative cooler to 100% and theoretically reduces the power consumed by the fan by several percent. Depending on the climatic conditions and the specific design of the turbogenerator (gas turbine power unit), the pressurization system proposed in the invention allows to increase the useful power of the turbine by 20-40% or even more.

Advantages of the Invention

The present invention in a preferred embodiment has the following significant advantages:

1) a large increase in the power of the turbogenerator: the system proposed in the invention allows to increase the power of most gas turbines by 20-40%;

2) low cost: the cost of a fan and a humidification system (fogging) is much less than the cost of creating a new turbine;

3) compactness: the refusal to use the large evaporative cooler required for systems with conventional pressure fans allows reducing the size and cost of the evaporative cooler and the duct connected to it;

4) ease of modernization of existing power units (turbogenerators): the small size of the proposed boost system and the ability to use an existing generator make it easy to integrate the proposed boost system into existing turbines;

5) a more advanced control system: the control system proposed in the invention enables the turbogenerator to operate with maximum power generation in a wide range of ambient temperatures;

6) reduction of fan power: the presence in the system of the first fogger, which generates water dust, which cools the air passing through the fan, allows theoretically reducing its power at a given pressure and given fan performance;

7) the simplicity of the system: the supercharging system proposed in the invention consists of only a few simple components;

8) high reliability: in the proposed system only proven, highly reliable units are used; in addition, in the event of failure of certain elements of the system or for any other reason, a gas turbine power plant (power unit or turbogenerator) can continue to operate without any pressurization system.

The pressurization system for gas turbines proposed in the invention itself has significant and numerous advantages, the most important of which are the following:

- a large increase in turbine power at high ambient temperatures,

- the ability to provide a large increase in turbine power even in areas with a humid climate,

- low investment

- simplicity of design,

- compactness,

- the possibility of flexible regulation,

- the possibility of using to modernize existing gas turbines,

- the ability to work without a blower fan (due to the use of a bypass damper),

- high reliability achieved through the use of a large number of fans and dampers, allowing you to create a certain margin in the system for its capabilities, and

-18005393

- Big power savings due to the combined operation of the blower and the cooling system.

Based on the foregoing, it can be concluded that the solution proposed in the present invention is a major improvement in the technology of gas turbines. Due to its simplicity and low cost, the system proposed in the present invention can find very wide application in plants designed to produce electricity, which currently do not have the necessary characteristics at elevated ambient temperatures. For specialists in this field it is obvious that the above description does not limit the scope of the present invention, which can be implemented on the basis of the above description in a variety of and numerous variations. However, it should be noted that all these possible changes and improvements to the above options should remain within the scope of the claims below.

Claims (44)

CLAIM 1. A supercharged gas turbine for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which heats up in the combustion chamber and expands in the turbine, which the energy of the compressed air entering it is brought into rotation and drives the generator, which generates electrical energy, a boost system with at least one discharge m fan, which increases the pressure of the air entering the gas turbine, and allows you to increase the power of the turbine and thereby the amount of electric energy generated by the generator, and a regulator, while the peak power consumption in the summer, the calculated pressure increase in the boost system corresponds to the output power of the turbine , which approximately coincides with the rated power of the generator and in which the regulator controls at least one of the installation parameters and controls the slave at least one of the elements of the system in such a way that, when the ambient temperature decreases, the turbine output with a working boost system, which in the absence of such regulation increases with decreasing ambient temperature, does not exceed the level corresponding to the maximum calculated value of the electric energy generated by the generator . 2. The gas turbine installation according to claim 1, in which the regulator controls the temperature of the air at the entrance to the gas turbine. 3. The gas turbine installation according to claim 2, in which the regulator controls the operation of at least one discharge fan, depending on the temperature of the air entering the gas turbine. 4. The gas turbine installation according to claim 1, in which the regulator controls the air pressure at the entrance to the gas turbine. 5. The gas turbine installation according to claim 4, in which the regulator controls the operation of at least one discharge fan, depending on the air pressure at the inlet of the gas turbine. 6. The gas turbine installation according to claim 1, in which the pressurization system comprises two or more parallel blowing fans that pump air into the receiver, from which it enters the gas turbine inlet, while the receiver has a bypass damper that allows the installation to operate naturally aspirated into a turbine compressed by air fans. 7. The gas turbine installation according to claim 1, in which the boost system comprises two or more fans operating in series. 8. The gas turbine installation according to claim 1, in which the pressurization system comprises a first air cooler, which is located between at least one discharge fan and a gas turbine, and is designed to cool the air entering the gas turbine. 9. The gas turbine installation of claim 8, in which a direct evaporative cooling cooler is used as an air cooler. 10. The gas turbine installation according to claim 1, also containing a fogger, which is located before entering the turbine compressor and forms water dust consisting of small droplets, the presence of which in the air entering the turbine will reduce its temperature. 11. The gas turbine installation of claim 8, in which the regulator controls the operation of the first air cooler, depending on at least one installation parameter controlled by it. 12. The gas turbine installation according to claim 11, in which an indirect evaporative cooling cooler is used as the first air cooler, which is installed in a closed cooling circuit including a pump and a cooling tower. 13. The gas turbine installation according to item 12, in which a cooling tower with a discharge fan is used as a cooling tower. -19005393 14. The gas turbine installation according to claim 11, further comprising a second air cooler located at least to one blower fan therein, the controller controlling the operation of the second air cooler depending on at least one parameter of the installation controlled by it. 15 Gas turbine installation according to claim 1, in which the controller controls the temperature of the ambient air. 16. The gas turbine installation according to clause 15, in which the regulator controls the operation of at least one discharge fan, depending on the ambient temperature. 17. The gas turbine installation according to claim 1, in which the regulator controls the electrical energy generated by the generator, and depending on it controls the operation of at least one of the elements of the installation. 18. The gas turbine installation according to claim 1, in which there is an air circulation system, through which part of the air compressed by the compressor enters the gas turbine inlet, and the regulator controls the operation of this circulation system depending on at least one installation parameter controlled by it. 19. The gas turbine installation according to claim 1, in which the regulator controls the operation of the combustion chamber depending on at least one parameter of the installation controlled by it. 20. The gas turbine installation according to claim 1, further comprising an air heater located upstream of the compressor, wherein the controller controls the operation of the air heater depending on at least one installation parameter controlled by it. 21. The gas turbine installation according to claim 20, in which the regulator controls the temperature of the air entering the turbine and, depending on it, controls the operation of the heater. 22. The gas turbine installation according to claim 20, in which the air heater comprises a first heat exchanger through which a heat transfer fluid passes, which also passes through a second heat exchanger in which it is heated, taking heat from the exhaust gases of the turbine. 23. The gas turbine installation according to claim 22, which is a combined cycle installation and further comprises a unit with a steam turbine generator that generates additional electric energy through the use of heat from the exhaust gases of a gas turbine. 24. The gas turbine installation according to claim 1, further comprising a device for changing the pressure at the outlet of the boost system, which is connected to a regulator, which reduces the pressure at the outlet of the boost system so that when the ambient temperature decreases, the output power of the turbine, which in the absence of such regulation increases with decreasing ambient temperature, does not exceed the level corresponding to the maximum calculated value of the electric energy generated by the generator. 25. The gas turbine installation according to paragraph 24, in which the device for changing the pressure at the outlet of the pressurization system contains an adjustable drive that drives at least one blower fan present in the pressurization system. 26. The gas turbine installation according to paragraph 24, in which an axial fan with rotary blades is used as a blower fan. 27. The gas turbine installation according to claim 1, further comprising a bypass damper, which, when the discharge fan is idle, directs the air entering the turbine to bypass the fan. 28. The gas turbine installation according to claim 1, also containing an electric motor that drives the discharge fan. 29. A supercharged gas turbine for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which the energy of the compressed air entering it is brought into rotation and drives the generator, which generates electrical energy, a boost system with at least one discharge fan, which increases the pressure of the air entering the gas turbine, and a fogger, which forms dust from small droplets of water that evaporate and reduce the temperature of the air entering the gas turbine, which allows to increase the output power of the turbine and thereby the amount of electric energy generated by the generator , and a regulator that controls the operation of the fogger and regulates the amount of water added to the air so that when the external conditions change, the moisture content entering the compressor air was such that the maximum output power of the turbine does not exceed its maximum rated capacity. 30. The gas turbine installation according to clause 29, containing also a device for changing the magnitude of the increase in pressure in the boost system, which is controlled by the regulator so that when changing According to external conditions, the moisture content in the air entering the compressor remained such that the maximum output power of the turbine did not exceed its maximum rated power. 31. The gas turbine installation according to claim 30, wherein the axial fan is used as the blower, and the device for changing the pressure increase in the boost system is a device that adjusts the angle (pitch) of the rotor blades of the fan. 32. The gas turbine installation according to clause 29, also containing a bypass damper that allows you to direct air bypassing the discharge fan and supply air to the inlet of the gas turbine when the discharge fan is idle. 33. The gas turbine installation according to clause 29, in which the fogger is located before the discharge fan. 34. The gas turbine installation according to claim 33, wherein the amount of water added to the air by the fogging agent is greater than that necessary to saturate the air leaving the discharge fan with moisture. 35. The gas turbine installation according to clause 34, in which the amount of water added to the air by the fogger is less than that necessary to saturate the air leaving the discharge fan. 36. The gas turbine installation according to clause 34, also containing a second fogger, located behind the discharge fan. 37. The gas turbine installation according to clause 36, in which the regulator turns off the fogger, located before the blower fan, and includes a fogger, located behind the blower fan, allowing the installation to work in conditions when the ambient temperature becomes close to the freezing temperature, and preventing the formation of ice at the inlet to the discharge fan, while cooling the air entering the turbine to a temperature at which at the inlet to the compressor is not formed I am ice. 38. A supercharged gas turbine for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which the energy of the compressed air entering it is driven into rotation and drives the generator, which generates electrical energy, a pressurization system with an axial discharge fan m with rotary blades, which increases the pressure of the air entering the gas turbine, and allows you to increase the output power of the turbine and thereby the amount of electric energy generated by the generator, and a regulator that controls the operation of the axial discharge fan with rotary blades, changing the pressure created by the boost system, so that when the ambient temperature changes, the output power of the turbine, which in the absence of such regulation increases with decreasing temperature ry ambient air does not exceed a value corresponding to the maximum rated power of the gas turbine. 39. A supercharged gas turbine for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which the energy of the compressed air entering it is driven into rotation and drives the generator, which generates electrical energy, a boost system containing at least two working sequentially axial discharge fans with rotary blades, a fogger that generates water dust from small droplets of water in the air stream that evaporates and cools the air entering the gas turbine, and a regulator that controls the fogger to control the amount of water dust in the air, and controls the pitch of the rotor blades of the fans, while the pressurization system increases the air pressure at the inlet to the turbine and increases the power of the turbine and thereby the amount of generated for generators of electrical energy, and the controller controls the fogger and regulates step fan variable vanes so that at changing ambient conditions the moisture content of the air entering the compressor and the turbine maximum power output does not exceed the limits corresponding to the maximum rated power of the turbine. 40. A turbine pressurization system of a gas turbine installation for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which Under the action of the energy of the compressed air entering it, it is rotated and the generator, which generates electrical energy, is rotated, and such a pressurization system has at least one rotary vane axial discharge fan that increases the pressure of the air entering -21005393 gas turbine, and allows you to increase the output power of the turbine and thereby the amount of electric energy generated by the generator, and a regulator that controls the operation of the axial discharge fan with rotary blades, changing the pressure created by the boost system, so that when the ambient temperature changes, the output the power of the turbine, which in the absence of such regulation increases with decreasing ambient temperature, did not exceed the value corresponding to the maximum oh the estimated power of the gas turbine. 41. The pressurization system according to claim 40, further comprising an electric motor that drives an axial discharge fan with rotary blades. 42. A turbine pressurization system of a gas turbine installation for generating electric energy, having an electric energy generator and a gas turbine that contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which Under the action of the energy of the compressed air entering it, it is rotated and the generator, which generates electrical energy, is rotated, and such a pressurization system has at least one discharge fan, which increases the pressure of the air entering the gas turbine, a fogger, which forms dust from small droplets of water that evaporate and lower the temperature of the air entering the gas turbine, which allows to increase the output power of the turbine and thereby the amount of generator electrical energy, and a regulator that controls the operation of the fogger and regulates the amount of water added to the air so that when the external Under the conditions, the moisture content in the air entering the compressor remained such that the maximum output power of the turbine did not exceed its maximum rated power. 43. The turbine pressurization system of a gas turbine installation for generating electric energy, having an electric energy generator and a gas turbine, which contains a compressor, a combustion chamber and a turbine and in which the compressor compresses the air entering the gas turbine, which is heated in the combustion chamber and expands in the turbine, which Under the action of the energy of the compressed air entering it, it is rotated and the generator, which generates electrical energy, is rotated, and such a pressurization system has at least one variable speed blower that increases the pressure of the air entering the gas turbine, and a regulator that controls the speed of the blower and changes the pressure created by the boost system so that when the ambient temperature drops, the turbine output the absence of such regulation increases with decreasing ambient temperature, did not exceed the value corresponding to the maximum rated power gas turbine features. 44. The pressurization system according to claim 43, further comprising an electric motor that is connected to a rotationally controlled blower driven by it.