JP2003529701A - Supercharged gas turbine device, supercharged auxiliary device, supercharged gas turbine device operating method, high-pressure fluid transfer duct, and power generation facility - Google Patents

Abstract

(57) [Summary] A supercharging device (11) for a gas turbine power generation facility, comprising a supercharging fan (30, 32) and a turbine output for preventing overloading of a generator (28) at a low ambient temperature. And a controller (50) for limiting. The controller limits output through burner control, inlet temperature control, supercharging fan pressure control, and other methods. The device can be retrofitted to existing turbines without replacing the generator and associated components.

Description

Detailed Description of the Invention

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention mainly relates to a gas turbine power generation facility, and more particularly to a supercharger for improving the capacity of a gas turbine power generation facility at high ambient temperature. That is, the supercharging device uses a supercharging fan with a controller to pressurize the turbine intake air to enable operation with an existing turbine, and preferably combines the supercharging fan and the intake air cooling device.

[0002] It has been conventionally known that the capacity of a gas turbine decreases as the intake air temperature rises, and generally the capacity decreases at a rate of 0.4% per 1 ° F (0.56 ° C). The relationship is shown in FIG. Usually, the peak of the electric power demand coincides with the maximum ambient temperature, and thus such characteristics are particularly problematic in the gas turbine for power generation. Gas turbines, associated generators and power distribution equipment are typically rated at 40 ° F to 50 ° F.
Determined based on turbine capacity at intake air temperature (10 ° C). This low rated operating temperature means that the capacity decline at peak summer time reaches about 20 to 40% of the turbine capacity, depending on the design, local weather conditions, and individual turbine characteristics. To do.

Conventionally, various efforts have been known to cool the intake air of a turbine in order to reduce or eliminate the performance deterioration. The outline of these efforts is from June 11, 1990
Gas Turbine Aviation Engine Conference held in Brussels, Belgium on 14th
ASME (American Society of Mechanics) by Igor Ondryas et al.
ical Engineers) paper "Options for increasing gas turbine power by cooling intake air". The main cooling methods are direct and indirect vaporization (evaporation) cooling devices,
Examples include an electric vaporization compression device, an absorption device, a heat storage device, and the like.

Of these, the only method which is excellent in commercial use is the direct evaporative cooling apparatus. The direct evaporative cooling method has the advantages of low cost and simplicity, but the range of possible temperature drop is limited by the ambient wet bulb temperature. In the eastern part of the United States, depending on the local weather, the temperature of the intake air is 10 ° F (about 5.6 ° C) to 20 ° F (about 11. ° C) due to direct evaporative cooling.
1 ° C.) can be lowered. Greater temperature reductions are possible in dry, warm climates such as the southwestern United States. Although direct evaporative cooling is useful, it does not allow the turbine to operate at maximum design capacity. Over 50 years of exhaustive research and development of gas turbines have not provided an excellent way to deal with high ambient temperatures.

A method that is interesting but rarely used as a method for coping with these problems is described in R.M. W. Foster-Pegg, "Method of supercharging a gas turbine with a forced draft fan with vaporized intake air cooling" ASME 1965. This paper describes a method for increasing the turbine capacity by using a high-pressure fan to increase the intake pressure of a gas turbine with an evaporative cooler downstream thereof. While this approach has significant logical advantages, it requires a special sized generator with limited use only in new turbines. Also, the device uses a single fan with intake vanes for control, which reduces the efficiency of the device.

ASME paper by Kolp et al. “Advantages of air conditioning and supercharging of LM6000 gas turbine intake system” Gas Turbine Power Technology Journal, July 1995, Volume 117, 513
On page 527, the economics of supercharged cooling systems are introduced. According to the paper, evaporative cooling is very attractive, but the supercharging method, which requires a depreciation period of 10 years or more per cycle, is not so attractive. While the supercharging method may be more attractive for combined cycle facilities, it is still marginal in terms of economics. The supercharger described in this paper is nearly identical to that of the 1960s, and in contrast to decades of turbine development, the supercharger has made little progress.

One of the major problems of the prior art is that the supercharger is obliged to upsize associated generators and other auxiliary equipment. The cost of replacing generators and other ancillary equipment is so high that the possibility of existing facilities is completely ruled out. Even if it is a new facility, it is necessary to change the basic requirements of the generator, power distribution equipment, and related hardware.
A supercharger is not a viable option except in the early stages of the project. Kolp
Et al. In their paper (p. 520) "Unlike a supercharger, there is no need to upsize gas turbine plant equipment when adding an evaporative cooling system". As described above, it is common knowledge that the evaporative cooling device can be added to the existing power generation equipment, but the supercharger is not an option for retrofitting.

Other methods of controlling turbine capacity use variable speed compressors. U.S. Pat. Nos. 3,853,432 and 2,693,080 are included in the related patents. These devices have a wide range of control and are usually intended for use in the aircraft field. A major challenge with this system is the price and complexity of variable speed compressors. Another related issue is the reliability and maintenance of large gears required for the equipment. In the field of power generation these devices have little use.

A gas turbine intake air cooling method using atomization is another related art of the related art. See, for example, the minutes of the 28th Turbomachine Symposium, “Increase in Gas Turbine Power by Atomization Atomization”, 1999, by Meher-Homji and Mee. In addition to the benefits associated with intake air cooling, cooling the air in the compressor can further improve turbine performance through atomization. Due to the intake air cooling effect, there is an increase in the water mass flow capacity of about 5%, which corresponds to 1% of the air mass flow. It is also noted in the above article that atomized intake air cooling can improve compressor efficiency.

One limitation of atomization technology is the amount of atomization that the compressor can safely inhale. Too much water can cause corrosion and erosion problems and can cause other damage to the turbine compressor section. At least one turbine manufacturer is concerned about the impact on compressors and often does not warrant turbines with atomizers. Despite the several additional benefits spraying technology has over vaporization pads, concern over the potential negative impact on compressor performance has left the benefit of sprayer capabilities to the benefit of areas of humid coastal climate. It is limited to about 10% or less of many turbines used.

DISCLOSURE OF THE INVENTION In accordance with one preferred aspect of the present invention, an apparatus for improving gas turbine capacity at high ambient temperatures includes at least one supercharging fan for pressurizing the intake air of the turbine and maximum capacity of the turbine. Consists of a controller that limits the maximum capacity to the maximum capacity without a supercharger. Preferably, an air cooler that lowers the turbine intake air temperature is provided. The system of the present invention can be retrofitted to existing gas turbines or designed for new supercharged gas turbine systems.

[0012] A primary object and advantage of the present invention is to allow for increased summer peak turbine capacity while reducing post-installation costs for capacity-based equipment during peak summer periods. A related object of the invention is to make a relatively small device that is not extremely complicated and does not cause unacceptable reliability or maintenance problems. Another aim is to develop a supercharger that can actually be retrofitted to existing turbines.
According to another aspect of the invention, a supercharger for a gas turbine comprises a fan and an atomizer installed in the intake air flow of the turbine.

Detailed Description of the Preferred Embodiments FIG. 2A illustrates a preferred embodiment of the present invention. The gas turbine power generation facility 11 includes a gas turbine device 10 and a power generator 28. The gas turbine device 10 is a compressor 12
, Burner 14 and turbine 16. The turbine 16 is the compressor 12
Also, the common shaft 24 is shared with the generator 28. A compressor intake airflow 18 is blown to the compressor 12, and the intake airflow 18 is injected at high pressure to generate a pressurized burner intake airflow 20, which is supplied to the burner 14. Burner 14
Then heats the air in the pressurized burner intake stream 20 and supplies the heated turbine inlet stream 22 to the turbine 16. Upon receiving the heated intake air flow 22 sent, the turbine 16 rotates to rotate the shaft 24, and the generator 28 also rotates to generate electric power. Exhaust stream 26 exits turbine 16. This exhaust stream 26 is discharged directly into the atmosphere or, in the case of the combined cycle plant described in FIG. 13, sent to a steam boiler.

Although FIG. 2A illustrates a simple turbine system for purposes of illustration of the invention, more complex systems (such as double spool construction) can be used and will allow the invention to be used. The operating principle of does not change. As a matter of course, the gas turbine is usually provided with a device known to those skilled in the art such as a filter, a control device, and a safety device, but the description of the present invention does not show such a device or describe it in detail. Not not.

Intake stream 18 is sent to compressor 12 as follows. First supercharged fan 3
0 and the second supercharging fan 32 take in the ambient air 40 and pressurize it to the plenum 3
Supply to 8. Then, the compressed air passes through the air cooler 34 that cools the air to form the compressor intake air flow 18 and is sent to the compressor 12. Preferably, the air cooler 34 is a direct vaporization cooler for cooling and humidifying the air flow.
A structural example of an evaporative cooler is conventionally well known. Alternatives to air coolers include linear expansion vaporizers, cooling water / direct contact heat exchangers, indirect vaporizers, and other devices that reduce the temperature of the airflow. In the case of a cooling water coil, cooling water can be supplied from a vaporization compression cooling device or an absorption cooling device, or naturally occurring cooling water such as groundwater or bottom water can be supplied from a deep lake or sea. In the case of an absorption cooling device, the heat discharged from the turbine may be used as a heat source for driving the cooling device. The air cooler is preferably installed in the air flowing between the supercharging fan and the turbine, but can be installed upstream of the supercharging fan. The advantage of installing the air cooler on the downstream side of the supercharging fan is that the heat from the supercharging fan can be removed.

The bypass damper 36 can supply air to the plenum 38 without passing through the supercharging fan when the supercharging fan is not operating. A first damper 42 is provided on the discharge side of the first supercharging fan 30. Similarly, a second damper 44 is provided on the discharge side of the second supercharging fan 32. A control signal from the sensor 52 is input to the controller 50, and the operation of the supercharging fans 30 and 32 is controlled according to this signal. Control inputs include intake air temperature, compressor outlet pressure, generator output power, ambient temperature, and the like. The controller may be as simple as a thermostat, but may be a computer (ie, microprocessor) that also controls and monitors turbine performance and other related electronics.

The dampers 42 and 44 and the bypass damper 36 function as a check valve that prevents the air from the gas turbine from flowing backward. Preferably, the damper opens in response to its lateral pressure gradient and, when there is no pressure gradient, returns to the closed position by gravity. 2B and 2C illustrate the manner in which the damper operates in response to different fan operating modes, as described in more detail below.

The first and second supercharging fans 30, 32 are preferably belt driven centrifugal fans or direct driven axial fans. In the case of centrifugal fans, it is preferable to incorporate backward tilted vanes in the design to maximize efficiency. This type of fan can deliver a design hydrostatic pressure of about 60 inches, which is approximately equal to the most demanded value in the commercial field. Although an engine or machine connection to the turbine itself is an optional method, power is typically supplied from an electric motor (preferably a three-phase induction motor) to drive the supercharging fan.

Although two supercharging fans are shown in FIGS. 2A-2C, more than two supercharging fans may be used, or one supercharging fan may be used. . With multiple turbochargers, you can adjust the turbine inlet pressure to increase in stages,
Such control cannot be performed with a single supercharging fan.

Preferably, the two supercharging fans have approximately the same pressure capacity, but the flow dimensions are not the same. The pre-charged fan has a large flow capability and preferably operates at a constant speed to reduce costs. The delayed supercharging fan has variable flow capability and regulates turbine inlet pressure as described in more detail below. Variable speed operation and, in the case of axial fans, variable pitch blades are preferred means of adjusting the supercharged fan flow. Suction blades are an alternative, but are not preferred due to their relatively low efficiency.

FIG. 3 shows another embodiment using an indirect evaporative cooler capable of approaching the ambient dew point temperature. This embodiment is similar in structure to the embodiment of FIG. 2 except that the indirect evaporative cooler 60 is installed in the air flowing between the plenum 38 and the gas turbine 10. As in the case of the above-described embodiment, the gas turbine power generation facility 11 includes the gas turbine device 10 and the power generator 28. Similarly, the gas turbine device 10 includes a compressor 12, a burner 14, and a turbine 16. The indirect evaporative cooler 60 uses a secondary airflow 62 which is exhausted from any evaporative cooler 68 disposed between the indirect evaporative cooler 60 and the turbine 10 to direct the incoming air to the turbine. Further, a part of the primary airflow 64 for further cooling is taken out. Turbine intake flow 6
6 consists of the remaining part of the primary airflow 64 and flows into the turbine 10. Secondary air flow 6
The second air is indirectly heated and humidified inside the indirect evaporative cooler 60 by the air flowing in from the plenum 38, and is discharged as an exhaust stream 65.

FIG. 4 illustrates another embodiment using a motor driven axial supercharging fan.
The supercharging fan 116 includes a motor 100 that drives an impeller 112, and these impeller and motor are housed in a housing 106. The motor 100 is preferably a three-phase induction motor, which is connected by electrical wires 110, 112, 114 to a normal power line via a switch contactor 104. When the contactor 104 is closed, the motor 100 is energized and the impeller 102 that increases the pressure of the exhaust flow 108 flowing into the turbine device 10 is driven. Opening the contactor 104 disconnects power to the motor 100, causing the impeller 102 to be driven solely by the exhaust stream 108, which acts as a pressure reducing valve to reduce the pressure of the exhaust stream 108.

Contactor 104 is a simple manual device. In this case, the operator determines when the surplus turbine capacity is appropriate and closes the switch to activate the supercharging fan. A thermostat 109, which controls the contactor 104 and can drive the supercharging fan 116 when the exhaust flow 108 exceeds a predetermined temperature, is preferably arranged in contact with the exhaust flow 108.
Since the thermostat 109 functions in this way to limit the turbine output power, overload of the gas turbine power generation equipment 11 is prevented in advance.

Higher degree of control is also possible. For example, variable-pitch blades are attached to a supercharging fan, and the blades are adjusted by a controller that detects pressure and temperature conditions and changes the blade pitch so that the turbine output becomes maximum. Nowadays, a very high degree of control is possible with a device equipped with a microprocessor. Additional mechanical hardware can be added to improve performance. For example, the pressure drop can be reduced through the supercharging fan when the supercharging fan is not energized. A direct evaporative cooler or other cooling means can be added to reduce the turbine inlet temperature.

The advantage of the device shown in FIG. 4 is its low cost and simplicity, which is especially important for small turbines. Careful evaluation of commercial use is required for optimal configuration. Although not preferred, the switch 104 may be omitted in special areas. For example, when moving a turbine from a cold region to a tropical region, it is desirable to add a supercharging fan that runs continuously while the turbine is operating. (In particular, adjust the turbine design conditions so that the supercharging fan can handle high ambient temperatures.)

Although slightly less preferred, another option is to drive the supercharging fan directly with the turbine. The simplest configuration is to make a direct mechanical connection with a shaft attached to the turbine. Typically, such an arrangement would require a reduction gear to allow the supercharging fan to operate at a much slower speed than the turbine. The speed of the fan can be changed by using an eddy current clutch or a mechanical clutch. Alternatively, there is a method of controlling the speed of the secondary shaft by using a differential gear mechanism, a brake, a generator, and other reactors to decelerate the fan. In this case, retrofitting existing turbines is difficult (possibly impossible) and the transmission and other mechanical components required for this method require regular maintenance. Therefore, this embodiment is more reliable and less desirable than the other embodiments.

FIG. 5 shows still another embodiment in which two supercharging fans are arranged in series. The first supercharging fan 216 includes the first impeller 202 housed in the first housing 206.
And the first motor 200. The first fan is located in the intake air flow 208 entering the compressor 12. The wires 210, 212, 214 are the switch 2
It is usually connected to the power line via 04. The second fan 236 is the first fan 21.
It is located upstream of 6. The second fan includes a second impeller 222 housed in a second housing 226 and a second motor 220. The second motor 220 is connected to the normal power line via the switch 224 and the electric wires 230, 232 and 234.

The operation and effects of the present invention will be described within the framework of the context of FIGS. 2A-2C, which shows a device operating with two supercharged fans connected in parallel. In FIG. 2A, both the first and second supercharging fans 30, 32 are operating and close the bypass damper 36 to prevent backward flow from the turbine. Both the first and second dampers 42, 44 are opened to allow the fan to flow air.

FIG. 2B shows an operating condition in which the first supercharging fan 30 is closed and the second supercharging fan 32 is opened. The bypass damper 36 is closed again. The second damper 44 remains open and closes the first damper 42. In FIG. 2C, both the supercharging fans 30 and 32 are stopped, and the respective dampers 42 and 44 are closed. The bypass damper 36 is opened to allow air to flow around the supercharging fans 30 and 32.

FIG. 6 illustrates the advantages of such a device. This figure is based on already published performance data for gas turbines. In the case of a basic device that does not have a supercharger or suction cooler, an output peak occurs at an ambient temperature of 40 ° F (about 4.4 ° C), and the performance deteriorates rapidly as the temperature rises. . From this figure, it can be seen that the capacity of the device of the present invention is almost flat, whereas the capacity of the conventional device decreases rapidly with increasing ambient temperature. The basic device is 100 MW at a temperature of 40 ° F (4.4 ° C) or less.
Although it is a simple cycle turbine that outputs the maximum electric power of, its capacity is significantly reduced as the ambient temperature rises. The device of the present invention also has a capacity of 100 MW, but maintains the capacity even when the ambient temperature rises.

The large basic unit or large basic unit with evaporative cooler is a single cycle turbine designed to match the device of the present invention at high ambient temperatures. The large basic device can also consist of a conventional supercharged turbine. The large basic unit with an evaporative cooler has the advantage of reducing the dimensional requirements of the turbine, which has a constant capacity at high ambient temperatures, due to the lower inlet temperature in the evaporative cooler. The performance of the large-scale basic device with an evaporative cooler is almost the same as that of the conventional supercharged turbine.

Conventional vaporized intake air cooling systems improve turbine performance at high ambient temperatures without increasing maximum output power at 40 ° F (about 4.4 ° C). Also, while conventional superchargers with evaporative coolers increase turbine output power at all ambient temperatures,
Gas turbine power generation facilities in low ambient temperature areas will cause overload.

In the present invention, turbine output is limited so as to obtain the advantages of a supercharger at high ambient temperature while preventing overload in power generation equipment in low ambient temperature areas. Due to this new feature, the output hardly changes even when the ambient temperature changes.

Table 1 shows a price comparison (based on Kolp et al.) Of the supercharger of the present invention and the conventional device. From this table, it can be seen that the cost of adding a new turbocharger is less than half the cost of adding the peak turbine output. The cost increase required to add a supercharger to a device with an evaporative cooler is about $ 300 per kilowatt [about 37,
The cost for constructing a new peak turbine power generation facility is 700 dollars (about 86,800 yen) per kilowatt. Combining an evaporative cooler with a supercharger will give a turbine capacity of 30% at peak summer
More than that. Since the peak power output of the turbine at low ambient temperatures is unchanged, the control method of the present invention does not require a larger generator or associated hardware. From this analysis it can be seen that the present invention provides a great advantage for the new installation. In the case of the retrofit, since the generator and related equipment must be replaced in order to control the output increase in low ambient temperature conditions, the cost of adding to the conventional supercharger will differ by at least one digit.

[0035]

[Table 1]

Table 2 shows how power generation equipment performance is improved by adding a supercharging fan. For the example in the table, the supercharged fan increases the turbine output by almost 4 MW or more with a power consumption of only 1.24 MW. As a result, about 2.8 on the net.
The output of the MW increases. This simple analysis shows that a supercharged fan can significantly improve the peak power output of a gas turbine.

[0037]

[Table 2]

[8 CFM (cubic feet per minute) / kW, dry bulb temperature 95 ° F. (about 35 ° C.), wet bulb temperature 75 ° F. (about 23.9 ° C.), fan motor efficiency 95%, rate of change 0. 4%
kW / ° F, change rate 0.6% kW / inch (about 2.54 cm) H ₂ O, cooler efficiency 90%]

From this table, it can be seen that the supercharging fan and the evaporative cooler work synergistically to increase the turbine output. As described above, by adding a supercharging fan to the turbine without a cooling device, the output of 2.80 MW increases. On the other hand, if the same fan is added to the turbine with a direct evaporative cooler, the capacity of 4.06 MW will increase. In this way, the effect of the supercharging fan is about 50% or more greater when the cooler is installed than when the cooler is not installed. From this analysis it can be seen that the combined effect is greater than the sum of the effects of the individual components and is particularly desirable.

From Table 2, it can be seen that a significant improvement is possible in the case of a supercharged fan with a static pressure of about 10 inches (about 25.4 cm). This can be further improved in the case of a supercharged fan with a higher static pressure. In many facilities, the optimum boost pressure is 60 inches (about 152.5
Cm) Static pressure may be exceeded.

7A and 7B are compressor diagrams showing the improvement in turbine capacity obtained according to the present invention. The vertical axis is the turbine pressure ratio, which is the turbine inlet pressure divided by the atmospheric pressure. The horizontal axis is the mass flow rate variable and is calculated from the following formula.

[0042] m is the turbine mass flow rate, δ is the compressor inlet pressure divided by the standard atmospheric pressure, and θ is the compressor inlet absolute temperature divided by the design absolute temperature.

The pressure ratio is the compressor discharge pressure divided by the atmospheric pressure. For this analysis, the effects of burner pressure drop and other secondary factors are grouped with compressor and turbine performance (for background information on component matching, see Blaze's Gas Turbine Fundamentals Chapter 10).

The compressor curve 300 shows the performance of the compressor under design conditions,
Compressor curve 301 shows turbine performance at peak inlet temperature. The turbine straight line 302 indicates the turbine performance under the design condition.
Shows turbine performance at peak inlet temperature. The intersection of the compressor curve 300 and the turbine straight line 302 defines the design operating point 304. Compressor curve 301 and turbine straight line 303 are operating points 305 at peak inlet temperature. Destination 306 shows possible turbine operating points at different inlet temperatures. The surge destination 307 indicates the stable operation limit of the compressor.

At operating point 305, turbine capacity is significantly reduced from design operating point 304.
As the inlet temperature increases, so does the speed of sound in the air, which reduces the compressor Mach number and moves the compressor curve to the left side of the figure. Moreover, as the temperature increases, the air density decreases, which further reduces the mass flow rate. These fluctuations reduce the compressor pressure ratio and mass flow rate, reducing the energy available to drive the turbine. Cooling the air restores turbine capacity.

FIG. 7B shows how the new device can improve turbine performance at peak ambient temperatures. When the air that flows into the compressor is pressurized, the turbine pressure ratio and the compressor inlet temperature increase, and the compressor curve 310 appears. The new turbine straight line 312 shows a slightly higher temperature. The intersection of turbine straight line 312 and compressor curve 310 defines operating point 314. This operating point corresponds to the case where operation is performed using a supercharging fan without performing suction cooling. Driving line 318 shows possible operating conditions at different operating pressures. Another advantage of high pressure air is increased air density, which further increases capacity.

The other compressor curve 316 and turbine straight line 320 correspond to the compressor inlet temperature obtained with the evaporative cooler. The operating point 322 at the intersection of the compressor curve 316 and the turbine straight line 320 corresponds to the operating condition of the supercharging fan and the inlet cooling. From this analysis, it is possible to approach the original design capability of the gas turbine by combining the inlet cooling and the pressurization. The limit of turbine capacity is the allowable operating pressure and output of turbines and generators. These factors usually prevent the supercharger fan and the intake cooler from delivering turbine power much higher than the turbine design power.

FIG. 8A shows how the parallel supercharging fan operates to create the turbine inlet pressure range. In parallel operation, the two fans have the same lateral pressure and their flows merge. Leading fan curve 350 is for the leading fan. The gas turbine straight line 356 is substantially vertical because the air flow through the turbine varies only slightly with inlet pressure. The operating point 358 is at the intersection of the leading fan curve 350 and the turbine straight line 356. This operating point 358 corresponds to the case of operating with one fan.

The first delayed fan curve 352 corresponds to the performance of the delayed fan at maximum speed. Fan curve 364 corresponds to operating both fans. Fan curve 36
The intersection of 4 and the turbine straight line is the operating point 366 which corresponds to the case where both fans are operating. The second delay fan curve 354 represents the fan performance at low speed,
Fan curve 360 represents the operation of two corresponding fans. The operating point 362 is
This shows an operating situation in which two fans are operating and the delay fan is at a low speed.

FIG. 8B shows an operating condition in which two similar fans are arranged and operated in series. The fan curve 372 corresponds to the situation where only one fan is operating. The intersection of the fan curve and the turbine straight line 370 represents the operating point 378 of one fan. The fan curve 374 corresponds to the situation where two fans are operating. An operating point 376 indicates a turbine operating state in which two fans are operating.

FIG. 9 shows a simple relationship between the maximum supercharging pressure used for controlling the supercharger and the inlet temperature. The controller can adjust the supercharger pressure using the compressor inlet temperature. The result is a very simple controller that maximizes turbine performance. This method is very useful for controlling retrofit turbochargers, since it requires almost no changes to the existing control equipment of the gas turbine power plant.

More advanced control and driving methods also belong to the scope of the present invention. For example, FIG. 10 shows another preferred embodiment in which a recirculation device is provided around the compressor to control the performance of the gas turbine power generation facility 421. This gas turbine power generation facility includes a gas turbine device 432 and a power generator 426. The gas turbine device 432 is a burner 422.
, A compressor 420 and a turbine 424, and a common shaft 430 shared by them. Compressor intake air stream 440 enters compressor 420 and is compressed to produce burner intake air stream 442. As the burner 422 heats the stream 442, a burner exhaust stream / turbine inlet stream 444 that enters the turbine 424 is created. Turbine 424 extracts power from the stream that is exhausted as exhaust 446. This gas turbine power generation facility also includes a structure, a bearing, a control device, and other parts which are not shown in the figure because they are well known in the art. The power generation facility may have a bottom steam cycle device or a multi-shaft device.

Turbine 424 drives compressor 420 and generator 426, which also shares shaft 430. Electric power is supplied from the generator to the electric power grid through the electric wire 436 and the transformer 428.

The supercharged fan 423 compresses the fan intake air flow 453 and generates a pressurized air flow 455 that flows into the first evaporative cooler 425. The first evaporative cooler 425 includes a pump 437 and a vaporization pad 435. The first evaporative cooler 425 cools the pressurized air flow 455 to produce a compressor intake air flow 440.

The supercharged fan supplies a static pressure of about 60 inches (about 152.4 cm) of water and may preferably be a centrifugal fan or an axial fan. Pressurized air flow 455 and compressor intake air flow 440 are confined to ducts corresponding to this pressure, see FIGS. 15 and 16A below.
, 16B, 17A, 17B, a preferred duct configuration will be described.

The second evaporative cooler 470 is arranged upstream of the supercharging fan 423. The evaporative cooler is composed of a vaporization pad 434 and a pump 436, which circulates water along the surface of the pad to moisten the surface before it is sent to the supercharged fan 423 as a fan intake flow 453. The air flow 451 is cooled by vaporization. Each evaporative cooler may be provided with a liquid reservoir with a float valve for adjusting the water surface, and means for discharging a small part of the circulating water to prevent the accumulation of salt.

Evaporative coolers are commercially available from many companies, and therefore their details are omitted. Also,
Although a direct evaporative cooler is shown, an indirect evaporative cooler or an indirect-direct evaporative cooler may be used.

The main feature of the present invention is to make the supercharged gas turbine, the generator, and related equipment relatively small. In particular, the generator and supercharged turbine are sized to allow the generator to operate at its maximum capacity during peak summer hours (as opposed to conventional designs, where the generator and auxiliary machines are It is based on maximum supercharging power under winter conditions, typically 40 ° F (about 4.4 ° C) or less inlet temperature, and performance "deteriorates" above ambient conditions as ambient temperature increases). Accordingly, the present invention comprises means for controlling turbine capacity at low ambient temperatures to prevent generator overload.

Preferably, the controller 460 includes a current sensor 46 for detecting the generator current.
The current signal 468 from 2 is input. The controller 460 preferably has the normal capabilities and safety features of a gas turbine power plant, and may be a stand alone unit. The current sensor is preferably a current transformer, in which case the signal is an alternating current. In addition, a sensor that outputs a voltage signal, an optical signal, a high frequency output signal, or another type of signal may be used.

A damper control signal 464 is output from the controller 460 to the damper 450 to control the flow of the heating airflow 452, and the heating airflow is the burner intake air flow 442.
And then circulates through the damper 450 to the compressor intake. In addition, the controller 460 sends the pump control signal 466 to the pump 436.
A pump control signal 467 is output to 37 and a fan control signal 465 is output to the supercharging fan 423. Control of the pump and fan of the present embodiment may be simple control such as on / off control, but shift control by a shift drive, intake vanes or variable pitch vanes may be used.

Since the apparatus of the present invention is sized to maximize turbine / generator performance at peak summer temperatures, the generator output will increase when ambient temperature decreases and turbine output increases. At the beginning, the maximum design output is exceeded. Therefore, when the ambient temperature decreases, the current sensor 462 detects the generator current signal 468 corresponding thereto and transmits this signal to the controller 460. First, the controller responds by turning off the pump 436, whereby the second evaporative cooler 470 is stopped and the fan intake air flow 45
Bring 3 to ambient dry bulb temperature. If the ambient temperature drops further, an appropriate control response is initiated to open the damper 450 and mix the compressor exhaust heated air 452 with the compressor inlet flow 440. If the ambient temperature still decreases, open the damper further to limit the generator current to the level of peak summer performance.

If the ambient temperature still decreases, the controller 460 outputs the fan control signal 465 and the pump control signal 467 to stop the supercharging fan 423 and the pump 437 for the first evaporative cooler 425. Signal stops the entire supercharger. Next, the damper control signal 464 may be output from the controller 460 to close the damper 450.

A more preferred embodiment of the turbine device of the present invention is shown in FIG. Similar to the embodiment of FIG. 10, the controller 474 receives the current signal 468 from the current sensor 462 that detects the generator current, while the controller 474 outputs the pump control signal 466 to the pump 436. Instead of adjusting the damper to return the heated compressor exhaust to the intake, the controller 474 controls the burner control signal 4
72 to the burner 422, which regulates the burner output and thus the turbine output. The controller 474 preferably incorporates normal operation control and safety control for gas turbine power generation equipment, but the controller may be a stand-alone unit.

The control method used in the embodiment of FIG. 11 is almost the same as the control method of the embodiment of FIG. When the ambient temperature decreases and the output generator current increases as a result, the controller 474 turns off the pump 436 to stop the second evaporative cooler 474 to deal with it. If the generator current is still above the summer peak design output, controller 474 adjusts burner control signal 472 to reduce the output of burner 422 to accommodate. If the ambient temperature still decreases, the controller operates the supercharger fan 423 and the first evaporative cooler 42 so that the power generation equipment operates without a supercharger at all.
Turn off 5 together.

FIG. 12 shows yet another embodiment of the present invention in which the heater inlet temperature is adjusted to control the turbine output using a heater. Compressor intake air flow 440
A temperature signal 490 from a temperature sensor 488 installed inside is input to the controller 480. The controller 484 outputs a heater control signal 482 to the heater 480 upstream of the compressor inlet, which outputs a heated air stream 486 to the compressor 420. (The heater is preferably installed on the upstream side of the evaporative cooler, but if the heater is made of a material that can handle air with high relative humidity without being extremely corroded, it may be placed between the evaporative cooler 470 and the compressor 420. You may install it.)

There are many options for implementing a heater. A simple one is to use a gas burner. The next option is to use a boiler with a gas-liquid heat exchanger. A third option is to utilize a heat exchanger that recovers heat from turbine exhaust 446. (This option is the most efficient and is preferred unless the installation cost is too high). The electric heater is the fourth option, but it is not preferable because it is inefficient. Finally, blowing a portion of the exhaust 446 to the compressor inlet flow 440 is a low cost fifth option, which can cause corrosion problems for the compressor 420 and other components. Any type of heating air stream 48
Its power must be adjustable to maintain 6 at a nearly constant temperature.

The control method used in the embodiment shown in FIG. 12 is to maintain the minimum temperature of the supercharging fan intake air flow 453. When the ambient temperature decreases, the controller 484 stops the pump 436 and the evaporative cooler 470 to deal with it. If the ambient temperature further decreases, the controller 484 outputs the heater control signal 482 to turn on the heater 480 and adjust its output to maintain the required temperature of the fan intake air flow 453.

FIG. 13 illustrates another similar embodiment that is particularly suitable for combined cycle power plants. The combined cycle gas turbine power generation facility 506 includes an auxiliary steam cycle device 498 that uses the waste heat of the turbine 424 to generate surplus power. The steam cycle device 498
It is composed of a boiler 504, a steam turbine 500, a storage battery 502, and a water absorption pump 503 which are connected to each other in the same circulation path. Pump 492 and heat recovery heat exchanger 496
A gas-liquid heat exchanger 491 is installed in the attached fluid loop. The pump 492 circulates the heat transfer liquid 512 via the heat recovery heat exchanger 496. The heat exchanger absorbs heat from the exhaust stream 508. The signal 494 for adjusting the flow of the heat transfer liquid 512 is the controller 4
Input to 84 to the pump to control the temperature of the heated air stream 486 entering the evaporative cooler 470. As in the embodiment of FIG. 12, the controller may turn off the second evaporative cooler 470 that controls the turbine inlet temperature as the first step, and then stop the entire supercharging device.

(However, when the exhaust stream 508 is used as a heat source, erosion is a concern, and a corrosion-resistant material is required to treat nitric acid and, in some cases, sulfuric acid. One of them is plasticity for various conduits. It is possible to use materials, but the temperature limits of plastics are usually relatively low, so it may be desirable to mix ambient air with the exhaust to enable utilization of plastics to reduce maximum temperature. Direct contact gas-liquid heat exchangers are also an option, the liquid should contain a suitable neutralizing agent (such as sodium bicarbonate) to prevent the problem of acidic concentrates, and the exhaust stream It may be desirable to mix with ambient air to reduce maximum operating temperature.)

Since the combined cycle power generation facility actually improves its efficiency only slightly at high compressor inlet temperature, the device structure of FIG. 13 not only improves the overall power generation capacity at high ambient temperature, but also improves efficiency. Let's do it. FIG. 13 shows a heat transfer loop for waste heat recovery and many other configurations are possible. For example, the heat from the battery 502 is used to warm the intake flow. Placing an air heat exchanger between the exhaust and intake air streams is also an option.

The embodiments described above represent possible configurations of the invention. In the above embodiment, the generator current or the compressor inlet temperature is used as the feedback control variable,
Similar results are obtained with other variables. For example, the control input value is the generator power,
It may have ambient dry-bulb temperature, ambient wet-bulb temperature, shaft torque, or other input value.

Further, although FIGS. 10 to 13 show the second evaporative cooler arranged upstream of the supercharging fan, this equipment is optional and there is no significant change in performance even if it is removed. The second evaporative cooler improves the pressure performance of the supercharging fan at high ambient temperatures, but increases the power output.

The use of the first evaporative cooler is optional to a certain extent, but if it is removed, the performance is greatly deteriorated. Therefore, it is desirable to remove the first evaporative cooler only when water and / or space is very limited.

Finally, the simple on / off control is the preferred control method for the supercharging fan in the above embodiment. More advanced controls with variable speed drives and variable pitch fan blades are also available, which may save some energy. However, means are already available to adjust the power output by controlling the burner temperature or the inlet temperature.

FIG. 14 shows a preferred embodiment in which an indirect evaporative cooling device and a variable speed drive for a supercharging fan are incorporated. As shown in FIG. 14, electric power is supplied from the power grid to the variable speed drive 550, and the variable speed drive 550 supplies variable frequency AC power to the induction motor 522. The induction motor 522 drives a shaft 554 that drives a supercharging fan 556. The supercharger fan takes in ambient air and supplies a pressurized air stream 558 to the cooling coil 560. A cooling coil is a water-air heat exchanger that cools air without adding water. The cooled airflow 570 is discharged from the coil and flows into the evaporative cooler 425 configured as described above.

The cooling coil 560 is connected to the pump 564 and the cooling tower 566 to form a circulation path, and the circulation path functions as an indirect evaporative cooler. Preferably, the cooling tower is a forced draft wet tower capable of cooling to a temperature near the wet bulb ambient temperature.

(In areas where adequate water absorption is limited, a dry tower may be used to remove the evaporative cooler. In this case, the dry cooling tower and coil assembly may be installed between ambient temperature and supercharged fan exhaust air. Functions as a simple heat exchanger.

Other heat exchangers and cooling structures are possible. For example, the cooling tower and cooling coils can be replaced by an air heat exchanger located between the ambient air flow and the supercharged fan exhaust. in this case,
A direct evaporative cooler is installed on the upstream side of the heat exchanger, that is, on the ambient air side for further cooling. Such a configuration is possible but not preferred because it requires a large heat exchange area and a large pressure differential between the two air streams, which necessitates a large and expensive heat exchanger.

In regions of the climate where freezing is likely to be a problem, pipes, cooling coils and cooling towers need to be subjected to appropriate anti-freezing treatment. Possible protection measures include thermal insulation, heater installation, running water installation, use of brine in cooling coils with water-brine heat exchangers. (The water-brine heat exchanger has the added benefit of separating cooling tower related fouling from the cooling coil, and can be equipped with a suitable filter to reduce fouling of the system without secondary loops.)

In this embodiment, the controller 568 prevents overloading the gas turbine at low ambient temperatures. A temperature signal from a temperature sensor 573 installed in the compressor intake flow at the compressor intake port is input to the controller 568. The controller also receives a pressure signal 574 from a pressure sensor 575 located within the pressurized air stream 558. Since the pressure fluctuation caused by the air flow flowing between the supercharging fan 556 and the gas turbine device 432 is small, the pressure sensor 5
75 may be installed anywhere within this air flow.

A speed control signal 578 is output from the controller 568 to the variable speed drive 550. This signal regulates the speed of the supercharging fan to maintain optimum supercharging pressure. The controller also outputs an output signal 576 to the pump 564 in the cooling tower loop and an output signal 580 to the pump 437 in the evaporative cooler. Normally, these output signals perform simple on / off control.

Although a variable frequency drive is used to control fan speed in this example, there are many other ways to adjust the available fan output. For example, US Pat.
7,854, the electromechanical variable speed drive and co-pending provisional application No. 60/164
Examples include a 590 eddy current clutch, a DC motor, a variable pitch fan blade, and a variable intake fan.

This embodiment has an important advantage that air of relatively low temperature can be supplied to the gas turbine device. The wet-bulb temperature of the air flowing into the cooling tower is not affected by the energy supplied from the supercharging fan. Therefore, the cooling coil can cool the air flow 558 to a temperature close to the ambient wet bulb temperature without adding water. The evaporative cooler 425 can then further cool and humidify the air stream. As a result, the airflow entering the turbine system is 10 ° F lower than when using a simple direct evaporative cooler. Due to this temperature decrease, the output of the gas turbine further increases by about 2.5%. Generally, the cooling tower fan and the pump consume only about 10% of this capacity increase, so that the actual capacity of this apparatus is improved by 2% or more.

More complex cooling devices are possible. For example, a mechanical cooling device, a dry cooling device, an absorption cooling device, or the like may be used instead of the direct evaporative cooling device. Cooling systems that utilize groundwater or cold lake or seawater are another option. With such a device, it is possible to obtain a lower temperature and further improve the capacity. The disadvantage of this method is the complexity of the additional cooling device and its cost.

As described above, the pressurized air flow and the compressor intake air flow are contained in a duct capable of withstanding relatively high temperatures, and FIG. 15 shows a preferred embodiment of such duct equipment in detail. The inner duct 610 is installed inside the circular outer duct 611, and the flow path 612 equalizes the pressure of the fluid flowing in the inner duct and the pressure of the space 615 between the two ducts. (In this example, the fluid is air, but the duct equipment assembly may be used to carry some high pressure fluid). Preferably, the space 615 may be filled with a fluid and made of a porous material such as fiberglass or open cell bubbles. Porous fillers have the advantage of helping to reduce noise and support ducts.

The flow path 612 for uniformizing the lateral pressure of the internal duct may be a simple hole or may be a continuous hole having a perforated surface. Further, this flow path may be a gap or a small opening common to non-sealed duct equipment. The absolute requirement for the design of the flow path 612 is that it allows a sufficient fluid velocity when passing and ensures that excess pressure is generated in the inner duct even if leakage occurs between the circular outer duct and the outside air. It is something that can be prevented. A pressure relief valve should be provided in this flow path to reduce the risk of damage to the internal duct in the event of leakage.

Although FIG. 15 shows a rectangular inner duct, the inner duct may have a shape other than a circular shape in practice, and may be a large flat surface if there is no concern about excessive strength requirement. All that the internal duct has to deal with are the events related to fluid movement within the duct, such as pressure drop, velocity pressure, turbulence, etc.

Preferably the outer duct has a circular cross section which minimizes material requirements. An ellipse or an ellipse can be used, but such a shape is not preferable because the strength condition is increased. Large circular ducts may be provided with corrugations or other reinforcements to increase rigidity and reduce damage from wind and accidental loads.

Metals such as steel and aluminum can be cited as typical components of the duct. Other materials include plastics, wood, ceramics and the like. Materials are selected based on factors such as strength, cost, and compatibility with the particular fluid flowing in the duct.

16A and 16B are front and cross-sectional views of an intermediate duct used to connect two different size ducts. The annular conical outer duct 620 contains a tetrahedral or pyramidal inner duct 621. A flow path 622 is provided on the wall surface of the internal duct 621 to make the internal pressure of the internal duct 621 and the pressure of the space 623 between the two ducts uniform. The intermediate duct assembly can be used as a diffuser or a flow accelerator depending on the direction of fluid flow. Furthermore, FIGS.
Shows the basic structure of the high-pressure duct of the present invention, but in reality, the present invention can be applied to specific duct shapes such as an L-shaped joint, a T pipe joint, and an intermediate duct.

17A and 17B show the use of such duct equipment, in particular in a gas turbine supercharger. FIG. 17A illustrates a cooler without a supercharger in which an evaporative cooler 630 is directly attached to the end of a rectangular duct 631 that supplies air to the intake of a gas turbine. The rectangular duct 631 is designed to carry a pressure differential of only a few inches (with respect to ambient pressure) of the water column.

A corresponding supercharging structure is shown in FIG. 17B. Fan 635 increases static air pressure to a very high pressure level, typically about 60 inches (152.4 cm) of water. A fan 635 is connected to the end piece of the diffuser duct 636.
This diffuser duct is connected to a straight duct 637 containing an evaporative cooler and a contraction duct 638. Each of these ducts consists of a circular duct containing a rectangular inner duct.

[0093]   This duct installation has several advantages over the prior art.   -Material weight and cost are reduced compared to the conventional rectangular duct.   ・ Lower pressure drop than the conventional circular duct used for rectangular members.   -Simplified shape and easy to assemble.   -It can be retrofitted to low pressure duct equipment to withstand high pressure.

These advantages are particularly desirable in gas turbine superchargers. High pressure [about 60 inches (
Due to the water column] and the large duct shape [30 feet (about 914.4 cm duct diameter)], an extremely robust rectangular duct that requires a very large amount of material for reinforcement is required. The novel duct structure of the present invention does not require a rectangular duct that withstands high gas pressures, thus significantly reducing material costs and weight. In addition, the existing evaporative cooler and associated ducts can be used, significantly reducing the installation cost of the turbocharger. While the invention is very attractive for use in gas turbine superchargers, it can also be used in air conditioners and other industrial and commercial applications that require mobile gases and liquids.

FIG. 18 illustrates another preferred embodiment of the present invention using an atomizer installed in the intake flow of a gas turbine. The gas turbine power generation facility 121 includes a compressor 120 and an expander 124 that are fixed to a shaft 130 that drives a power generator 126. Airflow 191 enters a compressor where the air is compressed and combustor 122
Is supplied to. The combustor heats the air and supplies it to the expander 124. The expander extracts work from the expanding gas and drives the compressor and generator.

The supercharger 190 is installed upstream of the gas turbine power generation equipment. The supercharger includes the fan 140, the first sprayer 149, and the second sprayer 16 provided inside the duct 147.
It consists of zero. The first atomizer is upstream of the fan, while the second atomizer is between the fan and turbine.

The fan 140 includes a hub 141 and a fan blade 142. This fan is fixed to the motor shaft 144. The motor 146 is the motor shaft 1
By driving 44, the fan 140 is driven. This fan is preferably a variable pitch axial fan. The hub 141 is a mechanism that adjusts the pitch of the fan blades 142 to adjust the fan output air pressure and flow.

The motor is preferably a three-phase induction motor or another motor. Another option is to drive the fan directly from the main turbine, which eliminates the need for a motor. Independent prime movers for fans such as secondary gas, steam turbines, and internal combustion engines are an option but are not preferred. An important advantage of electric motors is their relative ease of installation on existing gas turbines.

The fan output is about 60 inches (about 152.4 cm) static pressure. The optimum pressure will depend on the available fan, generator capacity, turbine capacity utilization and other factors.

The multi-stage axial flow fan of FIG. 18 can generate this static pressure. A centrifugal fan or a single-stage axial fan can also be selected. Since variable pitch blades are usually not an option when using centrifugal fans, variable speed drives are the preferred means of controlling fan capacity. Variable intake blades and dampers are also options, but they are less efficient. The variable speed fan can also replace the axial fan.

The first sprayer 149 includes a first manifold 156, a second manifold 158,
It consists of a third manifold 160. The first pump 150 for the first manifold
Pressurized water is supplied from. Similarly, the second pump 152 and the third pump 154 supply pressurized water to the second manifold 158 and the third manifold 160, respectively. The pump outlet pressure is preferably in the range of about 1000-3000 psi. The steam of water 164 is supplied to the pump inlet. This water is preferably filtered and desalted. The air flow 148 is taken into the duct 147 via the first sprayer 149.

The second atomizer 169 is installed upstream of the fan. Like the first atomizer, the second atomizer also consists of multiple manifolds and pumps. The fourth, fifth and sixth manifolds 176, 178 and 180 are connected to the fourth, fifth and sixth pumps 170, 172 and 174, respectively. The mist 182 is generated by the action of the pressurized water in the nozzle in the manifold.

The sprayer has a large degree of freedom in design. For example, the number of manifolds in each atomizer is somewhat arbitrary. The larger the number, the easier it will be to control the amount of mist produced, and the more redundancy will be created. On the other hand, if the number of manifolds is small, the installation is easy and the cost can be reduced. Moreover, the manifolds do not have to have the same capacity.

As far as the atomizer capacity is concerned, it is preferred that it is such that the air is almost saturated at the fan outlet. The second atomizer further saturates the air and the compressor 12
Add more water to cool the inside of the 0. The total amount of water added to the airflow is preferably a saturated amount from the inlet to the compressor plus about 0 to 2% of the air flow rate.

The controller 161 controls the operation of the supercharger 190. The basic approach is to reduce fan pressure and fog production at low ambient temperatures to prevent overloading of generators and other components of gas turbine power plants. Fan inlet temperature sensor 1
A signal is input from the 82 and the fan outlet temperature sensor 184 to the controller. When the ambient wet bulb temperature decreases, a signal is output from the fan inlet temperature sensor to the controller, and the signal output reduces the pitch of the fan blades to reduce the fan capacity. The lower temperature also reduces the amount of water needed to saturate the air, thus allowing the controller 160 to turn off part of the atomizer pump.

When the temperature approaches the freezing point, the first atomizer pump can be stopped to prevent ice formation. The second atomizer may remain active if the capacity of the generator or other components is adequate.

At very low temperatures at which supercharging cannot take place, the fan and atomizer are stopped, allowing the fan to rotate freely in the air stream. A bypass damper may be provided around the fan to reduce the pressure drop width of the turbine under these conditions.

There are numerous variations on this basic embodiment. For example, the second atomizer may be removed if the turbine compressor is particularly sensitive to water droplets. In this case, the controller can regulate the amount of mist generated from the first atomizer to ensure that the water droplets are completely vaporized before reaching the turbine.

There is also a method of removing the first atomizer. Such a modification will result in relatively little performance degradation if the capacity of the second atomizer is increased to compensate.

There are many options for fan selection. For example, dual fans may be desirable in some areas. The dual fan can provide redundancy to improve the reliability of the device. They can use common components to reduce costs or allow for more sophisticated control options.

Fixed fan output is another simple alternative control method. This method is an option when the generator is sized to handle the full power output of the turbine under normal conditions. This option is possible if other turbine capacity control means, such as combustor output regulation or intake flow heating means, can prevent overloading of the generator and other components.

Similar to the case of the conventional gas turbine power generation equipment, this device is also usually provided with a filter and a silencer. Normally the operation of the fan and atomizer is not affected by dust,
The location of the filter is primarily a matter of convenience. Fog will cause some increase in pressure drop in the filter, in which case it is usually preferred to place the filter upstream of the atomizer. The silencer is preferably installed upstream of the fan to prevent noise diffusion.

This device offers a significant increase in capacity. For a conventional vaporization padded supercharger with 90% effectiveness and a 60 inch hydrostatic supercharge, the capacity ranges from 20% to 30%. A further 10% increase in capacity can be achieved with spray inlet cooling. Also, the atomization can effectively obtain 100% evaporative cooling efficiency, which lowers the theoretical fan output demand value by several percent. As a result, depending on the climate and the specific design limits of the gas turbine power generation equipment, the capacity of the equipment is 20% -40%.
You can increase more.

Advantages of the Present Embodiment There are several important advantages to the preferred embodiment of the present invention. 1) Substantial increase in capacity: This device allows a capacity increase of 20% to 40% in most gas turbines. 2) Low price: The price of fans and atomizers is significantly lower than the price of new turbine capacity. 3) Miniaturization: The large vaporization pad required for the conventional supercharger has been removed, so the size and cost of the vaporization cooler and related duct equipment are greatly reduced. 4) Simple retrofitting: This equipment can be installed in an existing turbine because it is small and can be used in existing power generation equipment. 5) Improved controller: The controller allows the device to match the maximum capacity of the gas turbine power plant over a wide range of ambient temperature conditions. 6) Decrease in fan output: A mist that cools the air as it passes through the fan is created in the first atomizer, which reduces the theoretical fan output required for a given pressure increase or mass flow rate. 7) Simplification: The present invention uses only a few simple components. 8) Reliability: In the present invention, a proven reliable component is used. Further, even if a defect of a component or other problem occurs, it is possible to continue operating the gas turbine power generation facility without a supercharger.

In general, the advantages of superchargers for gas turbines are significant and numerous. The most important of these are: -a large increase in turbine performance at high ambient temperatures-a large increase in performance even in wet climates-low installation costs-simple design-compact design-universal control・ Can be retrofitted to existing gas turbine ・ Bypass damper can operate turbine without supercharging fan ・ Multiple fans and dampers enable redundancy for reliable operation. -The blower and cooling means work synergistically to significantly improve performance.

Overall, this device represents a major advance in gas turbine technology. The simplicity and low cost of this device are particularly desirable in the power generation sector, which currently faces significant performance degradation at high ambient temperatures. Although the present invention has been described above, it will be apparent to those skilled in the art that the present invention can be modified in various ways without departing from the spirit and scope of the invention. All such modifications are within the scope of the claims.

Applicant claims benefits based on the following applications. US application No. 60 / 138,848 (filed June 10, 1999) US application No. 60 / 139,894 (filed June 22, 1999) US application No. 60 / 152,277 (filed September 3, 1999) US application No. 60 / 159,207 (filed on October 13, 1999) U.S. application No. 60 / 195,302 (filed on April 10, 2000) Also, this application is U.S. application No. 09 / 388,927 (filed on September 2, 1999) ) Is a continuation application.

[Brief description of drawings]

FIG. 1 is a characteristic diagram showing the relationship between turbine performance and ambient temperature.

FIG. 2A is a schematic diagram of one preferred embodiment of the present invention having an air cooler downstream of a supercharging fan that compresses air entering a gas turbine.

FIG. 2B is a schematic diagram of a preferred embodiment of the invention having an air cooler downstream of a supercharging fan that compresses air entering a gas turbine.

FIG. 2C is a schematic diagram of a preferred embodiment of the invention having an air cooler downstream of a supercharging fan that compresses air entering a gas turbine.

FIG. 3 is a schematic view showing another preferred embodiment of the present invention using an indirect evaporative cooler.

FIG. 4 is a schematic view showing another embodiment of the present invention using an axial fan.

FIG. 5 is a schematic view showing still another embodiment of the present invention using a series fan.

FIG. 6 is a characteristic diagram comparing temperature variable turbine performances of a plurality of different turbine devices.

FIG. 7A is a schematic compressor diagram showing the operating principle of the device of the present invention.

FIG. 7B is a schematic compressor diagram showing the operating principle of the device of the present invention.

FIG. 8A is a fan curve characteristic diagram showing how to change the inlet pressure of a gas turbine using a double fan.

FIG. 8B is a fan curve characteristic diagram showing how to change the inlet pressure of a gas turbine using a double fan.

FIG. 9 is a characteristic diagram of maximum supercharging pressure as a function of turbine inlet temperature.

FIG. 10 is a schematic diagram showing another embodiment of the present invention in which the compressed air output from the compressor is fed back to the compressor intake flow to adjust the gas turbine performance.

FIG. 11 is a schematic diagram showing another embodiment of the present invention for controlling the turbine output by adjusting the burner output.

FIG. 12 is a schematic diagram showing another embodiment of the present invention for controlling the turbine output by adjusting the compressor inlet temperature.

FIG. 13 is a schematic diagram showing an embodiment of the present invention used in a combined cycle (gas turbine / steam turbine) power generation facility.

FIG. 14 is a schematic diagram showing a preferred embodiment of the present invention in which air discharged from a supercharging fan is cooled using a cooling tower and a cooling coil.

FIG. 15 is a perspective view showing a preferred structure of the high-pressure duct facility for the present invention.

FIG. 16A is an end view showing the structure of the diffuser / flow accelerator portion of the duct equipment configured as shown in FIG. 15.

16B is a cross-sectional view showing a structure of a diffuser / flow accelerator portion of the duct equipment configured as shown in FIG.

FIG. 17A is a perspective view showing how the duct equipment structure shown in FIGS. 15, 16A, and 16B is applied to a supercharging fan assembly.

FIG. 17B is a perspective view showing how the duct equipment structure shown in FIGS. 15, 16A, and 16B is applied to the supercharging fan assembly.

FIG. 18 is a schematic diagram of another preferred embodiment of the present invention in which a gas turbine supercharger includes a fan and an atomizer installed in the intake flow of the turbine.

[Explanation of symbols]

  10 Gas turbine equipment   11 Gas turbine power generation equipment   12 compressor   14 burners   16 turbine   18 Inspiratory flow   20 Pressurized burner intake flow   24 common shaft   26 Exhaust flow   28 generator   30 First Supercharged Fan   32 Second supercharged fan   38 Plenum   42 first damper   44 Second damper   50 controller

─────────────────────────────────────────────────── ─── Continued Front Page (51) Int.Cl. ⁷ Identification Code FI Theme Coat (Reference) F02C 7/08 F02C 7/08 B 7/143 7/143 9/28 9/28 B F04D 27/00 101 F04D 27/00 101M 101P 101X 101Y 29/38 29/38 B (31) Priority claim number 09 / 388,927 (32) Priority date September 2, 1999 (1999.9.2) (33) Priority Priority claiming United States (US) (31) Priority claim number 60 / 152,277 (32) Priority date September 3, 1999 (1999.9.3) (33) Priority claiming United States (US) ( 31) Priority claim number 60 / 159,207 (32) Priority date October 13, 1999 (October 13, 1999) (33) Priority claim country United States (US) (31) Priority claim number 09 / 475,154 (32) Priority date December 30, 1999 (December 30, 1999) (33) Priority claim United States (US) (31) Priority claim number 60 / 195,302 (32) Priority date April 10, 2000 (April 10, 2000) (33) Priority claim United States (US) (81) Designated countries EP (AT, BE, CH, CY, DE, DK, ES, FI, FR, GB, GR, IE, IT, LU, MC, NL, PT, SE), OA ( BF, BJ, CF, CG, CI, CM, GA, GN, GW, ML, MR, NE, SN, TD, TG), AP (GH, GM, KE, LS, MW, MZ, SD, SL, SZ, TZ, UG, ZW), EA (AM, AZ, BY, KG, KZ, MD, RU, TJ, TM), AE, AG, AL, AM, AT, AU, AZ, BA, BB, BG, BR, BY, CA, CH, CN, CR, CU, CZ, DE, DK, DM, DZ, EE, ES, FI, GB, GD, GE, GH, G , HR, HU, ID, IL, IN, IS, JP, KE, KG, KP, KR, KZ, LC, LK, LR, LS, LT, LU, LV, MA, MD, MG, MK, MN, MW, MX, MZ, NO, NZ, PL, PT, RO, RU, SD, SE, SG, SI, SK, SL, TJ, TM, TR, TT, TZ, UA, UG, US, UZ, VN , YU, ZA, ZW F terms (reference) 3G081 BA02 BA11 BB00 BC07 DA21 DA22 DA23 3H021 AA01 AA02 AA06 AA08 BA06 CA09 DA03 DA17 DA22 EA12 3H033 AA02 AA16 AA17 BB08 CC02 DD02 DD20 EE15

Claims (81)

[Claims] 1. A supercharged power generation gas turbine device, comprising a gas turbine auxiliary device and a generator, wherein the gas turbine auxiliary device comprises a compressor, a burner, and a gas turbine, and the gas turbine auxiliary device intake flow is compressed by the compressor. Then, heat with the burner, expand with the turbine,
A gas turbine auxiliary device and a generator for rotating the turbine, which in turn drives the generator to generate electricity, and a supercharging auxiliary device for controlling the pressure of the gas turbine auxiliary device intake flow. A supercharging auxiliary device that includes at least one supercharging fan for increasing the output of the turbine, thereby increasing the electric output of the generator, and a system controller. Monitor at least one system variable and control the operation of at least one system component so that the turbine output, which decreases as the ambient temperature decreases and decreases as the ambient temperature decreases, does not exceed the maximum summer supercharging output A supercharged power generation gas turbine device characterized by the above. 2. The supercharged power generation gas turbine apparatus according to claim 1, wherein the system controller monitors a temperature of the turbine auxiliary device intake air flow. 3. The supercharged power generation gas turbine apparatus according to claim 2, wherein the system controller controls the operation of the at least one supercharging fan as a function of temperature of the turbine auxiliary device intake air flow. 4. The supercharged power generation gas turbine apparatus according to claim 1, wherein the system controller monitors the pressure of the turbine auxiliary device intake air flow. 5. The supercharged power generation gas turbine apparatus according to claim 4, wherein the system controller controls the operation of the at least one supercharging fan as a function of pressure of the turbine auxiliary device intake flow. 6. The supercharging auxiliary device includes two or more supercharging fans connected in parallel, the supercharging fan compresses a plenum from which the turbine auxiliary device intake air flow is taken, and the plenum is the turbine. The supercharged power generation gas turbine apparatus according to claim 1, further comprising a bypass damper that permits the operation of the auxiliary apparatus intake air flow without compressing the supercharging fan. 7. The supercharged power generation gas turbine apparatus according to claim 1, wherein the supercharge auxiliary apparatus includes two or more supercharge fans connected in series. 8. The supercharging auxiliary device includes a first air cooler installed between the at least one supercharging fan and the gas turbine auxiliary device to cool the gas turbine auxiliary device intake air flow. The supercharged power generation gas turbine apparatus according to claim 1, characterized by having. 9. The supercharged power generation gas turbine apparatus according to claim 8, wherein the first air cooler comprises a direct evaporative cooler. 10. The secondary airflow is taken out from the gas turbine auxiliary device intake air stream and returned to the first air cooler to improve the cooling performance of the first air cooler. Supercharged gas turbine equipment. 11. The supercharged gas turbine apparatus of claim 8, wherein the system controller controls operation of the first air cooler as a function of the at least one monitoring system variable. 12. The supercharger according to claim 11, wherein the first air cooler is an indirect evaporative cooler, and the indirect evaporative cooler is provided in a circulation path composed of a pump and a cooling tower. Power generation gas turbine equipment. 13. The supercharged power generation gas turbine apparatus according to claim 12, wherein the cooling tower is a forced draft wet tower. 14. A secondary air cooler installed upstream of the at least one supercharging fan, wherein the system controller also controls the operation of the secondary air cooler of the at least one monitoring system variable. The supercharged gas turbine apparatus according to claim 11, wherein the supercharged gas turbine apparatus is controlled as a function. 15. The supercharged power generation gas turbine apparatus according to claim 1, wherein the system controller monitors an ambient temperature. 16. The supercharged gas turbine apparatus of claim 15, wherein the system controller controls operation of the at least one supercharger fan as a function of ambient temperature. 17. The supercharged gas turbine of claim 1, wherein the system controller monitors the electrical output of the generator and controls the operation of the at least one system component as a function thereof. apparatus. 18. A recirculation flow device directs a portion of a compressor exhaust flow to the gas turbine device intake flow and the system controller controls operation of the recirculation flow device as the at least one monitoring system variable. The supercharged power generation gas turbine device according to claim 1. 19. The supercharged gas turbine apparatus of claim 1, wherein the system controller controls operation of the burner as a function of the at least one monitoring system variable. 20. The air flow heater installed upstream of the compressor, the system controller controlling the operation of the air flow heater as a function of the at least one monitoring system variable. Supercharged gas turbine equipment. 21. The supercharged gas turbine apparatus of claim 20, wherein the system controller monitors the temperature of the gas turbine auxiliary system intake flow and controls the operation of the airflow heater as a function thereof. . 22. The airflow heater comprises a first heat exchanger in which a heat exchange fluid circulates, the heat exchange fluid circulates in a second heat exchanger in which the heat exchange fluid flows from the gas turbine. 21. The supercharged power generation gas turbine device according to claim 20, wherein the waste heat is discharged. 23. The apparatus comprises combined power generation equipment and further comprises an auxiliary steam cycle auxiliary apparatus, wherein the auxiliary steam cycle auxiliary apparatus uses waste heat from the gas turbine to generate additional power. 23. The supercharged power generation gas turbine device according to claim 22. 24. The supercharged power generation gas turbine apparatus according to claim 1, wherein the supercharging auxiliary device has a variable drive for driving the at least one supercharging fan. 25. The gas turbine auxiliary device and the generator are existing ones,
The supercharged power generation gas turbine apparatus according to claim 1, wherein the supercharging auxiliary apparatus and the system controller are installed afterward. 26. A supercharging auxiliary device for a supercharged power generation gas turbine device, wherein the supercharging power generation gas turbine device includes a gas turbine auxiliary device and a generator, and the gas turbine auxiliary device is a compressor, a burner, or a gas turbine. The gas turbine auxiliary device intake air flow is compressed by the compressor, heated by the burner, expanded by the turbine and rotated by the turbine, whereby the turbine drives the generator to generate electricity. The supercharging auxiliary device includes at least one supercharging fan increasing the pressure of the gas turbine auxiliary device intake flow to increase the output of the turbine and the electric output of the generator, and a system controller. The system controller is configured to reduce the ambient temperature, and as the ambient temperature decreases, As turbine output to pressure it does not exceed the maximum supercharging output of summer, at least one of the supercharging assisting apparatus characterized by controlling the operation of at least a single system components monitors the system variables. 27. The supercharging auxiliary device according to claim 26, wherein the system controller monitors a temperature of the turbine auxiliary device intake air flow. 28. The supercharge assist system of claim 27, wherein the system controller monitors the operation of at least one of the supercharge fans as a function of temperature of the turbine assist intake air flow. 29. The supercharge assist system of claim 26, wherein the system controller monitors the pressure of the turbine assist intake air flow. 30. The supercharging aid of claim 29, wherein the system controller controls the operation of at least one of the supercharging fans as a function of pressure of the turbine aid intake air flow. 31. Two or more supercharging fans connected in parallel, wherein the supercharging fan compresses a plenum for extracting the turbine auxiliary device intake air flow, the plenum being for supercharging the turbine auxiliary device intake air flow. 27. The supercharge assist device according to claim 26, further comprising a bypass damper that permits the operation of the device without being compressed. 32. The supercharging auxiliary device according to claim 26, wherein the device comprises two or more supercharging fans connected in series. 33. The supercharging fan auxiliary device includes a first air cooler installed between the at least one supercharging fan and the gas turbine auxiliary device to cool the gas turbine auxiliary device intake air flow. 27. The supercharging auxiliary device according to claim 26, comprising: 34. The supercharging auxiliary device according to claim 33, wherein the first air cooler comprises a direct evaporative cooler. 35. The secondary airflow is taken out from the gas turbine auxiliary device intake air stream and returned to the first air cooler to improve the cooling performance of the first air cooler. Supercharging auxiliary device. 36. The supercharge assist device of claim 33, wherein the system controller controls operation of the first air cooler as a function of the at least one monitoring system variable. 37. The first air cooler is in an indirect evaporative cooler, and the indirect evaporative cooler is provided in a circulation path composed of a pump and a cooling tower. Supercharging auxiliary device. 38. The supercharging auxiliary device according to claim 37, wherein the cooling tower is a forced draft wet tower. 39. A secondary air cooler installed upstream of the at least one supercharging fan, wherein the system controller also controls operation of the secondary air cooler of the at least one monitoring system variable. The supercharging auxiliary device according to claim 36, wherein the supercharging auxiliary device is controlled as a function. 40. The supercharging auxiliary device according to claim 26, wherein the system controller monitors an ambient temperature. 41. The supercharging assistance device of claim 40, wherein the system controller controls operation of the at least one supercharging fan as a function of ambient temperature. 42. The supercharging auxiliary device according to claim 26, wherein the system controller monitors the electrical output of the generator and controls the operation of the at least one system component as a function thereof. 43. The recirculation flow device directs a portion of the compressor exhaust flow to the gas turbine device intake flow and the system controller controls the operation of the recirculation flow device as the at least one monitoring system variable. 27. The supercharging auxiliary device according to claim 26. 44. The controller of claim 26, wherein the controller controls operation of the burner as a function of the at least one monitoring system variable.
Supercharging auxiliary device described. 45. The auxiliary device further comprises an airflow heater located upstream of the compressor, the system controller controlling operation of the airflow heater as a function of the at least one monitoring system variable. The supercharging auxiliary device according to claim 26. 46. The supercharge assist system of claim 45, wherein the system controller monitors the temperature of the gas turbine assist system intake flow and controls the operation of the air flow heater as a function thereof. 47. The airflow heater comprises a first heat exchanger in which a heat exchange fluid circulates, and inside the second heat exchanger in which the heat exchange fluid absorbs waste heat from the gas turbine. The supercharging auxiliary device according to claim 45, characterized in that a replacement fluid circulates. 48. A combined power generation facility is further provided, and an auxiliary steam cycle auxiliary device is further provided, and the auxiliary steam cycle auxiliary device generates additional power by utilizing waste heat from the gas turbine. 27. The supercharging auxiliary device according to claim 26. 49. A method of operating a supercharged gas turbine system, wherein at least one system variable is monitored and at least one of the systems is monitored to prevent exceeding the maximum summer supercharged output of the system when ambient temperature decreases. A method for operating a supercharged power generation gas turbine device, characterized by controlling the operation of system components of a stand. 50. A high pressure fluid carrying duct comprising an inner conduit installed in an outer conduit, the inner conduit having a polygonal cross section, the outer conduit having an arcuate cross section, A space is formed between the conduit and the outer conduit, and a flow path is formed on the wall surface of the inner conduit for fluid movement and for equalizing the internal pressure of the inner conduit and the pressure of the space. Characteristic high-pressure fluid transfer duct. 51. The duct for conveying high pressure fluid according to claim 50, wherein the inner conduit has a rectangular cross section. 52. A high pressure fluid transfer duct according to claim 51, wherein said inner conduit has a tetrahedral cross section or a pyramidal cross section in a flow diffuser or flow accelerator duct. 53. The high-pressure fluid transport duct according to claim 50, wherein the outer duct has a circular cross section. 54. A flow diffuser or flow accelerator duct, wherein the outer conduit has a conical cross section.
The high-pressure fluid transport duct described. 55. The high-pressure fluid transport duct according to claim 50, wherein the flow path is selected from an opening, a series of openings, and a perforated surface. 56. The high-pressure fluid transport duct according to claim 50, wherein the space is filled with a fluid or a porous material. 57. The high pressure fluid carrier of claim 50, wherein the inner conduit is supported within the outer conduit by the vertices of the inner conduit engaging the inner surface of the outer conduit. duct. 58. A supercharged power generation gas turbine device, which is a gas turbine auxiliary device and a generator, wherein the gas turbine auxiliary device includes a compressor, a burner, and a gas turbine, and the gas turbine auxiliary device intake flow is compressed by the compressor. Then, heat with the burner, expand with the turbine,
A gas turbine auxiliary device and a generator for rotating the turbine, which in turn drives the generator to generate electricity, and a supercharging auxiliary device for controlling the pressure of the gas turbine auxiliary device intake flow. A supercharging auxiliary device for increasing the output of the turbine and the electric output of the generator, and a system controller, the system controller comprising at least one supercharging fan for increasing the ambient temperature; A system controller that monitors at least one system variable and controls the operation of at least one system component so that the turbine output, which increases as time goes by, does not exceed the maximum summer supercharging output; A duct for blowing air, comprising an inner conduit installed in an outer conduit, Has a polygonal cross section, the outer conduit has an arcuate cross section, and a space is formed between the inner conduit and the outer conduit. A supercharged power generation gas turbine apparatus comprising: a duct in which a flow path for equalizing the internal pressure and the pressure in the space is formed. 59. A supercharged gas turbine power generation facility, which is a gas turbine power generation device, includes a compressor, a burner, and a gas turbine, and compresses an intake flow sent to the gas turbine power generation device by the compressor,
Heating with the burner, expanding with the turbine, rotating the turbine,
As a result, the turbine drives the generator to generate electricity, and a plurality of superchargers arranged upstream of the generator to increase the pressure of the intake flow supplied to the generator. A power generation facility that is composed of a fan. 60. The power generation facility according to claim 59, wherein the plurality of supercharging fans have a parallel flow configuration. 61. The power generation equipment according to claim 60, further comprising means for preventing the supercharging fan from flying away from the gas turbine when the supercharging fan is not operating, and preventing it from flying away from the gas turbine power generator. . 62. The power generation facility according to claim 61, wherein the plurality of supercharging fans have different air flow capacities. 63. The power plant of claim 62, further comprising a controller that controls operation of the supercharging fan to limit gas turbine capacity at low ambient temperatures. 64. The device according to claim 63, further comprising means for changing the capacity of at least one supercharging fan in response to a signal from the controller.
The described power generation equipment. 65. The power generation equipment according to claim 64, wherein the capacity changing means has means for changing a speed of the at least one supercharging fan. 66. The power generation facility according to claim 59, further comprising an air cooler installed in an airflow between the supercharging fan and the gas turbine power generator. 67. The power generation facility according to claim 59, wherein the plurality of supercharging fans have a serial flow type configuration. 68. The power generation facility according to claim 67, wherein the supercharging fan is an axial fan. 69. The method of claim 68, further comprising a controller that controls operation of the fan to limit gas turbine capacity at low ambient temperatures.
The described power generation equipment. 70. The power generation facility according to claim 67, wherein the supercharging fans have substantially equal airflow capacity. 71. The device according to claim 69, further comprising means for changing the capability of at least one supercharging fan in response to a signal from the controller.
The described power generation equipment. 72. The power generation equipment according to claim 71, wherein the capacity changing means includes a fan speed changing means. 73. The power generation facility according to claim 72, wherein the capacity changing means has means for changing a fan blade pitch. 74. The power generation facility according to claim 59, further comprising a bypass damper that causes an air flow around the supercharging fan when not operating. 75. The power generation equipment according to claim 59, further comprising a circular duct that forms a flow path between the supercharging fan and the gas turbine power generation equipment. 76. In a gas turbine power generation facility including a gas turbine power generation device including a compressor, a burner, and a gas turbine, the intake flow sent to the device is compressed by the compressor, heated by the burner, and expanded by the turbine. To rotate the turbine, which in turn drives the generator to generate electricity, and also increases the pressure of the intake flow sent to the compressor to supply pressurized intake air to the compressor. A power generation facility including a device, the power generation facility including a duct having a circular cross section that forms a flow path for the pressurized intake flow between the supercharger and the gas turbine power generation facility. 77. A supercharged power generation gas turbine device, which is a gas turbine auxiliary device and a generator, wherein the gas turbine auxiliary device includes a compressor, a burner, and a gas turbine, and the gas turbine auxiliary device intake flow is compressed by the compressor. Then, heat with the burner, expand with the turbine,
A gas turbine auxiliary device and a generator for rotating the turbine, which in turn drives the generator to generate electricity, and a supercharging auxiliary device for controlling the pressure of the gas turbine auxiliary device intake flow. A supercharging auxiliary device for increasing the output of the turbine and the electric output of the generator by at least one supercharging fan for increasing, and for humidifying and cooling the intake air stream before flowing into the compressor. A supercharged gas turbine system comprising: at least one atomizer installed upstream of the gas turbine auxiliary system intake flow to provide a mist source. 78. The supercharged power generation gas turbine system according to claim 77, wherein the at least one atomizer is upstream of the fan. 79. The supercharged gas turbine system according to claim 77, wherein the at least one atomizer is between the fan and the compressor. 80. A second sprayer is further provided, said at least one sprayer is installed upstream of said sprayer, and said second sprayer is arranged between said fan and said compressor. 77. A supercharged power generation gas turbine device according to item 77. 81. A system controller is further provided, wherein the system controller reduces at least one system variable so that the turbine output, which increases as the ambient temperature decreases, does not exceed the maximum supercharging output in summer. 79. The supercharged gas turbine apparatus of claim 77, wherein the supercharged gas turbine apparatus is monitored and controls operation of at least one system component.