JP2001059426A - Intake air cooling quantity control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrict the formation of condensed water to improve the cooling efficiency of a heat exchanger in the heat exchanger for cooling intake air sucked into an air compressor of a gas turbine device, and thereby enhance the combined efficiency of the gas turbine device. SOLUTION: A cooling quantity controlling means 30 for controlling the cooling quantity of a heat exchanger is provided in a gas turbine device. The cooling quantity controlling means 30 is provided with an intake air temperature detecting element 31 for detecting the temperature at the neighborhood of an intake outlet in a water-cooled heat exchanger 2, an intake air humidity detecting element 32 for detecting the intake air humidity at the neighborhood of an intake air inlet part, an operation part 33 for operating the dew-point temperature of the intake air from the detected value of the intake air humidity, and a control part 34 for reducing the rotating speed of a pump 18 when the intake air temperature is reduced lower than the dew-point temperature. Cooling water is supplied by a cooling water supply part 8 provided with an ice-thermal storage tank 16, and a refrigerator 17 for cooling the cooling water of the ice-thermal storage tank 16 to form ice.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a method of compressing intake air cooled by a heat exchanger with an air compressor, heating the compressed air with a combustion device, and introducing the obtained high-temperature and high-pressure gas into a gas turbine. The present invention relates to an intake air cooling amount control device for a gas turbine device.

[0002]

2. Description of the Related Art A gas turbine device is a gas turbine power generation device that generates electric power by connecting a generator, and further supplies the high-temperature exhaust gas to a steam generation device, and supplies the generated steam to a cooling and heating facility and other facilities using steam. Widely used for cogeneration systems. Such a gas turbine device includes an air compressor that draws in external air and compresses it, a combustion device that draws fuel into the compressed air to burn it, and a gas turbine driven by high-temperature and high-pressure gas from the combustion device. Generally, the air compressor and the gas turbine are directly connected by a common shaft.

[0003] The temperature of the intake air from the outside sucked into the air compressor has a great influence on the output of the gas turbine device. That is, if the intake air temperature rises during the daytime in summer or the like, the intake air density decreases accordingly, and the intake air amount compressed by the air compressor per unit time decreases. Therefore, the amount of intake air to the gas turbine also decreases, and the output decreases. Therefore, in order to solve such a problem of the output decrease, a method of cooling the intake air taken into the air compressor by a heat exchanger in advance has conventionally been adopted. Since the density of the intake air cooled by the heat exchanger increases, the output of the gas turbine device increases accordingly. For example, if the intake air temperature is reduced by about 15%, the output of the gas turbine device increases by about 10%.

FIG. 6 is a process flow diagram of a conventional gas turbine device employing an intake cooling system. The gas turbine device 1 includes a water-cooled heat exchanger 2, an air compressor 3, a combustion device 4, and a gas turbine 5, and a generator 6 is connected to the gas turbine 5. The intake air 7 taken in from the outside is cooled by exchanging heat with the cooling water circulating between the cooling water supply unit 8 and the heat exchanger 2, and then is introduced into the air compressor 3 through the pipe 9. Compressed air from the air compressor 3 is introduced into the combustion device 4 via a pipe 10. In the combustion device 4, the fuel tank 1
1. A high-temperature and high-pressure gas is generated by burning fuel supplied from a fuel supply unit including a pipe 12, a pump 13, and the like in compressed air. The high-temperature and high-pressure gas is introduced into the gas turbine 5 from the pipe 14, and the gas turbine 5 is driven by energy at the time of expansion. Usually, about 60% of the output of the gas turbine 5 is obtained as electric power, and about 40% is mainly consumed as driving energy of the air compressor 3. The high-temperature exhaust gas discharged from the gas turbine 5 is supplied to a pipe 15
To a steam generator (not shown).

On the other hand, the cooling water supply unit 8 includes an ice heat storage tank 16,
A refrigerator 17 for cooling the cooling water in the ice heat storage tank 16 and a pump 18 for circulating the cooling water between the ice heat storage tank 16 and the heat exchanger 2
It has. Since the outside air temperature decreases at night, it is often unnecessary to cool the intake air in the heat exchanger 2. Thus, the refrigerator 17 is operated at night using electric power or the like to accumulate ice in the ice heat storage tank 16, and when the outside air temperature rises in the daytime or the like, the heat of melting of the ice is used for the heat exchanger 2. Supply low temperature cooling water. 19 and 20 are water pipes, 21 is a brine pipe, 22 is a brine pump, 23 is a cooling water flow control valve, 24 is a cooling water pipe, and 25 is a brine pipe around which ice is generated.

[0006]

The intake air sucked from the outside atmosphere contains a considerable amount of moisture as water vapor, and its content is particularly large in summer. Such moisture in the intake air is condensed when cooled below the dew point in the heat exchanger 2, and at this time a large amount of latent heat of condensation is released from the intake air, but the temperature does not decrease. As a result, the cooling efficiency of the heat exchanger 2 is reduced. descend. In general, since the heat exchanger 2 is always operated at a constant cooling capacity, condensed water increases during a high humidity period such as in summer, so that the intake air temperature does not decrease, and the expected increase in output for the cold heat consumption cannot be obtained. There's a problem. Accordingly, an object of the present invention is to solve such a problem, and an object of the present invention is to provide an intake air cooling amount control device therefor.

[0007]

According to a first aspect of the present invention, there is provided an air conditioner in which intake air cooled by a heat exchanger is compressed by an air compressor, and the compressed air is heated by a combustion device. A cooling amount control device for intake air in a gas turbine device that introduces a high-temperature high-pressure gas into a gas turbine. Further, a cooling amount suppressing means is provided for suppressing the water present in the intake air from being cooled below the dew point in the heat exchanger and condensing. By providing the cooling amount suppressing means for suppressing the water condensation in the intake air in the heat exchanger in this manner, it is possible to effectively avoid a decrease in the cooling efficiency, thereby improving the overall efficiency of the gas turbine device. Can be.

According to a second aspect of the present invention, there is provided a preferred embodiment of the intake air amount control apparatus according to the first aspect, wherein the heat exchanger is a water-cooled type, and cooling water is supplied to the heat exchanger. A cooling water supply unit for supplying is provided.The cooling water supply unit includes an ice storage tank, a refrigerator for cooling the cooling water in the ice storage tank, and a pump for circulating the cooling water between the ice storage tank and the heat exchanger. It is characterized by having. By providing such a cooling water supply unit, in addition to the effect of the first aspect of the present invention, the intake air can be efficiently cooled by effectively using inexpensive nighttime power.

According to a third aspect of the present invention, there is provided a preferred embodiment of the intake air cooling amount control device according to the first or second aspect, wherein the cooling amount suppressing means is provided near the intake outlet of the heat exchanger. An intake air temperature detector for detecting the temperature of the air, an intake air humidity detector for detecting the humidity near the air inlet of the heat exchanger, an arithmetic unit for calculating the dew point temperature of the air intake from the detected humidity value, and an air inlet outlet of the heat exchanger A control unit for controlling the cooling amount of the heat exchanger so that the temperature in the vicinity does not drop below the calculated dew point temperature value is provided. When the cooling amount suppressing means is configured as described above, in addition to the effects of the invention described in claim 1 or 2, it is possible to quickly and reliably suppress the generation of condensed water in the heat exchanger with simple components. .

A fourth aspect of the present invention is another preferred embodiment of the intake air cooling amount control apparatus according to the first or second aspect, wherein the cooling amount suppressing means is a heat exchanger. And a control unit for controlling the cooling amount of the heat exchanger so that the detected value does not exceed a preset value. It is characterized by the following. When the cooling amount suppressing means is configured as described above, in addition to the effect of the invention according to claim 1 or 2, the generation of condensed water in the heat exchanger can be more reliably suppressed with simple components. Can be. The invention according to claim 5 is a more preferred embodiment of the intake air cooling amount control device according to claim 4, wherein the condensed water generation amount detection unit includes a measurement tank that stores the condensed water, It has a liquid level detecting unit for detecting the liquid level in the measuring tank, and a condensed water discharging unit for discharging the condensed water in the measuring tank every predetermined time.
When the condensed water generation amount detecting section is configured as described above, the present invention is configured as follows.
In addition to the effects of the invention described in (1), the present apparatus can be configured more simply and inexpensively.

According to a sixth aspect of the present invention, there is provided another preferred embodiment of the intake air cooling amount control device according to the first or second aspect, wherein the cooling amount suppressing means includes a cooling unit for cooling the heat exchanger. A control system that compares the temperature detection values of multiple temperature detectors arranged along the water pipe and controls the cooling amount of the heat exchanger so that the temperature detection value near the inlet of the heat exchanger changes discontinuously It is characterized by having a part. When the cooling amount suppressing means is configured in this way, in addition to the effects of the invention described in claim 1 or 2, it is possible to more reliably and precisely suppress the generation of condensed water. The invention according to claim 7 is a more preferred embodiment of the intake air cooling amount control device according to claim 6, wherein the condensed water temperature detection unit is provided close to a lower side of the cooling water pipe. And a temperature sensor disposed in the condensed water collecting section. When the condensed water temperature detecting section is configured as described above, in addition to the effect of the invention described in claim 6,
The temperature of the condensed water can be detected with high responsiveness, high accuracy, and efficiently.

[0012] The invention described in claim 8 is the third invention.
A preferred embodiment of the intake air cooling amount control device according to any one of claims 1 to 7, wherein the control unit performs sampling control (discrete control). In general, changes in temperature and humidity do not fluctuate greatly in a short time. Therefore, if the control unit is configured in this way, the control system in addition to the effect of the intake air amount control device according to any one of claims 3 to 7, Even when the time delay is large, good controllability can be ensured.

[0013]

Next, embodiments of the present invention will be described with reference to the drawings. FIG. 1 is a process flow chart for explaining an example of a cooling amount control device according to the present invention, and the same parts as those in FIG. 6 are denoted by the same reference numerals. FIG. 1 is provided with a cooling amount suppressing means 30 for suppressing the water present in the intake air 7 from being cooled below the dew point and condensed. This cooling amount suppressing means 3
0 denotes an intake air temperature detecting unit 31 provided near the intake outlet of the water-cooled heat exchanger 2; an intake humidity detecting unit 32 provided near the intake inlet; A microcomputer 33 for controlling the cooling amount of the heat exchanger 2 so that the temperature detection value of the intake air temperature detector 31 does not fall below the dew point temperature value calculated by the calculator 33; The control unit 34 includes a device and the like. In addition, a temperature sensor such as a thermocouple type or a resistance type can be used as the intake air temperature detecting unit 31, and a humidity sensor such as a capacitance type can be used as the intake air humidity detecting unit 32. Control unit 34
Is a comparison unit 35 composed of a differential amplifier or the like, and a comparison unit 35
Output control unit 36 that outputs a drive signal in accordance with the output signal of
It consists of. Note that the control unit 34 may have the function of the calculation unit 33.

Next, the operation of the apparatus shown in FIG. 1 and, in particular, the operation of the cooling amount suppressing means 30 will be described. When the intake air temperature falls below the dew point temperature, the output control unit 36
8 to output a control signal to reduce the number of revolutions of the induction motor, thereby reducing the flow rate of the cooling water transferred to the heat exchanger 2, thereby suppressing the amount of cooling in the heat exchanger 2 and reducing the intake air temperature. To rise. Next, when the intake air temperature changes so as to be higher than the dew point temperature, the output control unit 36 outputs a control signal for increasing the rotation speed of the pump 18 and transfers (circulates) the heat to the heat exchanger 2. The flow rate of the cooling water is increased, whereby the amount of cooling in the heat exchanger 2 increases, and the intake air temperature falls again. In this way, the cooling amount is controlled so as to prevent the intake air temperature in the vicinity of the intake outlet of the heat exchanger 2, that is, the portion where the temperature is reduced most from becoming lower than the dew point. Since the above temperature and humidity change relatively slowly, it is preferable that the control sensitivity of the control unit 34 be set relatively low. Since the cooling water supply unit 8 is the same as that in FIG. The pump 18 is driven by an induction motor whose rotation speed is controlled by, for example, an inverter composed of a thyristor circuit, and the inverter is provided in the output control unit 36 or the induction motor.

In order to adjust the flow rate of the cooling water, a control valve may be provided and controlled instead of changing the rotation speed of the pump 18 as described above. In this case, as shown by a dashed line in FIG. 1, cooling of the cooling water from the ice heat storage tank 16 to the ice heat storage tank 16 from the pump suction side of a water pipe 19 for supplying cooling water from the ice heat storage tank 16 to the heat exchanger 2. The water pipe 20 for returning water is connected by a bypass pipe 27, and a control valve 37 provided in the bypass pipe 27 is controlled by the output control unit 36. At that time, the rotation speed of the pump 18 is kept constant, and the flow control valve 23 is set to an appropriate opening degree. When the detected value of the intake air temperature falls below the dew point temperature value, the output control unit 36 increases the opening degree of the control valve 37 to increase the bypass flow rate that has become warm through the heat exchanger 2, and the ice heat storage tank The temperature of the cooling water transferred to the heat exchanger 2 is increased by decreasing the flow rate from the heat exchanger 16. Conversely, when the detected temperature of the intake air rises above the dew point temperature, the output control unit 36 decreases the opening degree of the control valve 37 to reduce the warmed bypass flow rate, and reduces the flow rate from the ice heat storage tank 16. The temperature of the cooling water transferred to the heat exchanger 2 is decreased by increasing the temperature.

FIG. 2 is a process flow chart for explaining another example of the cooling amount control device according to the present invention, and the same parts as those in FIG. 1 are denoted by the same reference numerals. In this example, another type of cooling amount suppressing means 40 is provided which suppresses the water existing in the intake air 7 from being cooled below the dew point and condensed. The cooling amount suppressing means 40 is provided with a condensed water generation amount detecting unit 41 for detecting the amount of condensed water generated per unit time in the water-cooled heat exchanger 2, and the detected value does not exceed a preset value. A control unit 42 for controlling the amount of cooling of the heat exchanger 2 includes, for example, a device combining an amplifier and a microcomputer. Condensed water generation amount detector 41
A measuring tank 43 for storing condensed water generated in the heat exchanger 2, a working transformer type liquid level detecting unit 44 for detecting the level of condensed water in the measuring tank 43, and a measuring tank 43. It has a condensed water discharge part 45 for discharging the condensed water in the inside at predetermined time intervals.

A drain pipe 46 communicating with the bottom of the heat exchanger 2 is connected to the upper part of the measuring tank 43, a condensed water discharging part 45 is connected to the bottom of the measuring tank 43, and the condensed water discharging part 45 is It is constituted by a pipe 47 and a control valve 48. The working transformer type liquid level detecting unit 44 is commonly used in this field, and has a magnetic permeability μ such as a float 44 a disposed in a measuring tank 43 and a rod-shaped iron or the like attached to the tip of a connecting rod of the float 44 a. And a ring-shaped primary and secondary coil 44c through which the rod-shaped magnetically permeable body 44b is inserted (the primary coil is omitted in the drawing). Then, a signal corresponding to the insertion position of the rod-shaped magnetically permeable member 44b into the secondary coil 44c is output from the liquid level detection unit 44 to the control unit 42.

The control unit 42 includes a differentiator and its holding device 42d, a comparing unit 42a such as a difference signal amplifier, and a liquid level setting unit 4.
2b and an output control section 42c, and further outputs an open drive signal to the control valve 48 at preset time intervals. The signal of the differentiator is held by the hold device from a little before the open drive signal of the control valve 48 until the + signal appears in the differentiator after the open drive signal, and the control operation of the control valve 48 by the output control unit 42c is not performed. It has become. In this example, the liquid level of the measuring tank 43 is detected by a float method. Alternatively, a water pressure gauge may be provided at the bottom of the measuring tank 43, and the liquid level may be detected by an output signal of the water pressure gauge. it can. Further, for example, 2
It is also possible to arrange the electric resistance detecting rod upright and detect the liquid level from the electric resistance between the terminals. Further, instead of providing the measurement tank 43 as described above, for example, a weight detection method using a measuring tank supported by a weight detection unit such as a load cell may be adopted. In this case, a flexible pipe 47 and a condensed water discharge section 45 composed of a control valve 48 are connected to the bottom of the measuring tank.
The weight detecting unit detects the weight of the condensed water flowing in from the air at every measurement time.

Next, the operation of the cooling amount suppressing means 40 in FIG. 2 will be described. A signal for closing the control valve 48 is output from the control unit 42 according to the programmed measurement start signal. Then, the condensed water generated in the heat exchanger 2 flows into the measuring tank 43 from the pipe 46 and gradually raises the liquid level. The control unit 42 outputs a signal to open the control valve 48 for a predetermined time (that is, a time for sufficiently discharging the condensed water in the measurement tank 43) at predetermined time intervals. The amount of condensed water generated per unit time in the heat exchanger 2 can be detected by detecting the rising speed of the liquid level rising during the measurement period) by the differentiator of the liquid level detection unit 44.

For example, the humidity of the intake air rises, the amount of condensed water generated per unit time in the heat exchanger 2 increases, and the differential detection value of the liquid level detecting section 44 during the measurement period is used as the liquid level setting section 42
When the value exceeds a preset value in b, the output control unit 42c outputs a control signal for decreasing the rotation speed of the pump 18 according to a signal from the comparison unit 42a. The pump 18 is driven by an induction motor whose speed is controlled by an inverter or the like constituted by a thyristor circuit as in the example of FIG. Instead of controlling the pump 18, a control valve 37 similar to that of the example of FIG.
Can be provided to control it. Conversely, when the humidity of the intake air decreases and the amount of condensed water generated per unit time in the heat exchanger 2 decreases, and the rising speed of the liquid level detection unit 44 during the measurement period falls below a preset value, the output Control unit 4
2c outputs a control signal to increase the rotation speed of the pump 18. When draining water from the measuring tank, the differential signal is held at the previous value and no control operation is performed.

FIG. 3 is a process flow chart for explaining still another example of the cooling amount control device according to the present invention, and the same parts as those in FIG. 1 are denoted by the same reference numerals. The cooling amount suppressing means 50 in this example is a cooling water pipe 24 of the water-cooled heat exchanger 2.
Is detected so that the position at which the temperature distribution changes discontinuously and greatly (the steepest temperature position), that is, the portion where the amount of condensed gas starts or increases, is located near the intake outlet. Is controlled. The cooling amount suppressing means 50 includes a plurality of condensed water temperature detectors 51 arranged at predetermined intervals from the intake inlet side to the outlet side so as to be substantially in contact with the cooling water pipe 24, and the temperature detection values arranged adjacent thereto. Are sequentially compared, and a control unit 52 such as a microcomputer for controlling the cooling amount of the heat exchanger so that the two detected temperatures near the intake outlet of the heat exchanger 2 change discontinuously is provided. Note that the condensed water temperature detector 51 may be the same as the intake air temperature detector 31 in the example of FIG.

The control unit 52 outputs a drive signal corresponding to an output signal of the comparison unit 52a, a temperature difference setting unit 52b, and a comparison unit 52a including, for example, a difference signal amplifier similar to the control unit 34 of FIG. And an output control unit 52c. Comparison section 5
Switching means 52d such as a multiplexer for automatically switching the outputs of the plurality of condensed water temperature detectors 51 are connected to 2a, and the difference between the two adjacent temperature detectors 51 and the temperature difference setter 52b are set. The temperature difference values are compared one after another. Note that the difference signal between adjacent signals may be detected from the signals from the respective thermometers, and the maximum signal may be detected from among them.

FIG. 4 is a schematic diagram showing an example of the condensed water temperature detecting section 51. The condensed water temperature detecting section 51 includes a condensed water collecting section 53 provided as close as possible to a lower side of the fin 24a protruding outside the cooling water pipe 24, and a condensed water collecting section 53.
Has a temperature sensor 54 disposed therein. Condensate collection unit 5
Reference numeral 3 denotes a funnel-shaped receiving portion 53a for collecting condensed water falling from a portion (area) of the cooling water pipe 24 to be detected, and a small-diameter drainage channel 53b extending downward from the central bottom of the receiving portion 53a. A drain pipe (not shown) is connected to the outlet side of the drain channel 53b. The temperature sensor 54 is disposed in the drain 53b. Note that the temperature sensor 54 is desirably a sheath type having a small diameter from the viewpoint of responsiveness. The condensed water drops from the outer peripheral portion of the cooling water pipe 24, is collected in the receiving portion 53a, and is discharged to the outside through the drain passage 53b. The temperature of the condensed water passing through the drain 53b is detected by the temperature sensor 54.

FIG. 5 is a diagram showing an example of a change in the detected temperature value detected by a plurality of (seven in this example) temperature sensors 54 arranged from the inlet side to the outlet side of the heat exchanger 2. The detected temperature value of the portion where a large amount of condensed water is generated is close to the condensed water temperature, and the detected temperature value of the portion where the condensed water is substantially zero or hardly generated is close to the intake air temperature. And since the temperature of the condensed water is lower than the temperature of the intake air, the position (region) where the condensed water is generated from the detected temperature values
You can know. In the illustrated example, the detection values of the fourth and fifth temperature sensors 54 from the inlet side are largely discontinuous, and the generation of condensed water has started considerably upstream from near the outlet side of the heat exchanger 2. Is shown. The temperature gradient can also be known from the ratio of the temperature change on the vertical axis to the position change on the horizontal axis.

Next, the operation of the cooling amount suppressing means 50 in FIG. 3 will be described. When the temperature difference value between the two adjacent condensed water temperature detection units 51 becomes smaller than the set temperature difference value, the control unit 52 starts from the cooling water pipe 24 where the condensed water temperature detection units 51 are disposed. It is determined that condensed water is generated or increased on the downstream side, and a control signal corresponding to the generated condensed water is output. The detected temperature values of the two adjacent condensed water temperature detectors 51 and the condensed water temperature detectors 5
It is also possible to calculate the temperature gradient between the intervals (distance) of 1 and determine and control that condensed water is generated or increased in a portion (region) where the temperature gradient value exceeds a preset value. . In that case, the interval between each adjacent condensed water temperature detecting section 51 is stored in advance in a storage section provided in the control section 52, and the stored value and the temperatures of the two adjacent condensed water temperature detecting sections 51 are calculated. To calculate the temperature gradient.
The comparator 52a compares and controls the temperature gradient with a preset temperature gradient set value.

For example, when the humidity of the intake air increases, the position where the condensed water is generated or increased moves upstream from a preset position near the outlet side of the heat exchanger 2. Then, the output control unit 52c outputs a control signal for decreasing the rotation speed of the pump 18, whereby the cooling amount of the heat exchanger 2 is reduced, and the condensed water is set at a position set near the outlet side of the heat exchanger 2. The generation or increment point returns. Conversely, when the humidity of the intake air decreases, the position where the condensed water is generated or increased moves further downstream than a preset position near the outlet side of the heat exchanger 2. Such a state means that the cooling amount of the heat exchanger 2 is too small. Therefore, contrary to the above, the output control unit 52c outputs a control signal for increasing the rotation speed of the pump 18, and returns the generation or increase position of the condensed water to the vicinity of the set outlet side in the heat exchanger 2.

In this manner, by maintaining the position of generation or increase of the condensed water in the region set near the outlet side of the heat exchanger 2 at all times, it is possible to eliminate the excess and deficiency of the cooling amount, and Production can be minimized or minimized. The pump 18 in FIG. 3 is driven by an induction motor whose rotation speed is controlled by an inverter or the like constituted by a thyristor circuit, as in the example of FIG. Also, instead of controlling the pump 18, FIG.
It is also possible to provide a control valve 37 similar to that of the example and control it.

In the embodiments described above, the control unit 34 shown in FIG. 1, the control unit 42 shown in FIG. 2, and the control unit 5 shown in FIG.
2 can select an appropriate system from so-called continuous control systems such as proportional control, proportional integral control, and proportional integral derivative control depending on the characteristics of the control system. However, it is preferable to adopt a sampling control (discrete control) method for the control of the heat exchanger in which the control system (temperature change and humidity change) has a large time delay and the time is relatively gentle. In general, sampling control is a process in which a control deviation between an input value and a set value is extracted and held at fixed time intervals, and the control signal is repeatedly changed according to the control deviation. Optimum control can be performed by adapting to the occurrence period of the disturbance element or the like. Therefore, by using the sampling control method for the control unit 34, the control unit 42, and the control unit 52, it is easy to secure optimal controllability.

[0029]

As described above, according to the cooling amount control device of the first aspect, it is possible to effectively suppress a decrease in cooling efficiency by suppressing water condensation in the intake air in the heat exchanger.
Thereby, the overall efficiency of the gas turbine device can be improved. According to the cooling amount control device of the second aspect, in addition to the effects of the first aspect, the intake air can be efficiently cooled by effectively using the cheap midnight power.
According to the cooling amount control device described in claim 3, in addition to the effects of the invention described in claim 1 or 2, the generation of condensed water in the heat exchanger is quickly and reliably suppressed with simple components. be able to.

According to the cooling amount control device of the fourth aspect, in addition to the effects of the first or second aspect, the generation of condensed water in the heat exchanger can be more reliably achieved with simple components. Can be suppressed. According to the cooling amount control device described in claim 5, in addition to the effect of the invention described in claim 4, the present device can be configured more simply and inexpensively. According to the cooling amount control device described in claim 6, in addition to the effects of the invention described in claim 1 or 2, it is possible to more reliably and precisely suppress the generation of condensed water. According to the cooling amount control device described in claim 7, in addition to the effect of the invention described in claim 6, the temperature of the condensed water can be efficiently detected with high accuracy and responsiveness. According to the cooling amount control device of the eighth aspect, in addition to the effect of the cooling amount control device for intake air according to any one of the third to seventh aspects, good control can be performed even when there is a large time delay in the control system. Nature can be secured.

[Brief description of the drawings]

FIG. 1 is a process flow chart for explaining an example of a cooling amount control device of the present invention.

FIG. 2 is a process flow chart for explaining another example of the cooling amount control device of the present invention.

FIG. 3 is a process flow chart for explaining still another example of the cooling amount control device of the present invention.

FIG. 4 is a schematic diagram showing one example of a temperature detection unit 51 in FIG. 3;

FIG. 5 is a diagram showing an example of a change in condensed water temperature detected by a plurality of temperature sensors 54 arranged from the inlet side to the outlet side of the heat exchanger 2 in FIG. 3;

FIG. 6 is a process flow chart for explaining an example of a gas turbine device employing a conventional intake air cooling system.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Gas turbine apparatus 2 Heat exchanger 3 Air compressor 4 Combustion apparatus 5 Gas turbine 6 Generator 7 Intake 8 Cooling water supply part 9 Pipe 10 Pipe 11 Fuel tank 12 Pipe 13 Pump 14 Pipe 15 Pipe 16 Ice storage tank 17 Refrigerator Reference Signs List 18 pump 19 water pipe 20 water pipe 21 brine pipe 22 brine pump 23 flow regulating valve 24 cooling water pipe 24a fin 25 brine pipe 30 cooling amount suppression means 31 intake temperature detection unit 32 intake humidity detection unit 33 arithmetic unit 34 control unit 35 comparison Unit 36 Output control unit 40 Cooling amount suppression means 41 Condensed water generation amount detection unit 42 Control unit 42a Comparison unit 42b Liquid level setting unit 42c Output control unit 42d Differentiator and its holding device 43 Measurement tank 44 Liquid level detection unit 44a Float 44b Bar-shaped magnetically permeable material 44c Secondary coil 45 Condensation Water discharge unit 46 Pipe 47 Pipe 48 Control valve 50 Cooling amount suppression unit 51 Condensed water temperature detection unit 52 Control unit 52a Comparison unit 52b Temperature difference setting unit 52c Output control unit 52d Switching unit 53 Condensed water collection unit 53a Receiving unit 53b Drainage channel 54 Temperature Sensor

Continuing from the front page (72) Inventor Eiji Sekiya 5-37-1, Kamata, Ota-ku, Tokyo Toshiba Plant Construction Co., Ltd. (72) Inventor Rikiya Yanagiya 5-37-1, Kamata, Ota-ku, Tokyo Toshiba Plant Construction Co., Ltd.

Claims (8)

[Claims] An intake air cooled by a heat exchanger is compressed by an air compressor, and the compressed air is heated by a combustion device.
A cooling amount control device for intake air in a gas turbine device 1 in which the obtained high-temperature and high-pressure gas is introduced into a gas turbine 5, wherein moisture present in intake air 7 is cooled to a dew point or lower by a heat exchanger 2. A cooling amount control device for intake air, comprising cooling amount suppressing means 30, 40, 50 for suppressing condensation. 2. The heat exchanger 2 is of a water-cooling type, and a cooling water supply unit 8 for supplying cooling water to the heat exchanger 2 is provided. The cooling water supply unit 8 includes an ice heat storage tank 16 and an ice heat storage A refrigerator 17 for cooling the cooling water in the tank 16, an ice heat storage tank 16 and the heat exchanger 2;
The intake air cooling amount control device according to claim 1, further comprising a pump (18) for circulating cooling water therebetween. 3. An intake air temperature detector 31 for detecting a temperature near the air inlet of the heat exchanger 2 and an air humidity detector 32 for detecting humidity near the air inlet of the heat exchanger 2. A calculation unit 33 that calculates the dew point temperature of the intake air from the detected humidity value, and a control unit 34 that controls the cooling amount of the heat exchanger 2 so that the temperature near the intake outlet does not drop below the calculated dew point temperature value. The intake air cooling amount control device according to claim 1 or 2, further comprising: 4. A condensed water generation amount detecting section for detecting a condensed water generation amount per unit time in the heat exchanger, wherein the detected value does not exceed a preset value. Control unit 4 for controlling the cooling amount of heat exchanger 2
The intake air cooling amount control device according to claim 1 or 2, further comprising: 5. A condensed water generation amount detecting unit 41, a measuring tank 43 for storing condensed water, a liquid level detecting unit 44 for detecting a liquid level in the measuring tank 43, and a condensing water in the measuring tank 43. The intake air cooling amount control device according to claim 4, further comprising a condensed water discharge unit (45) for discharging water at predetermined time intervals. 6. A plurality of condensed water temperature detectors (5) arranged along the cooling water pipe (24) of the heat exchanger (2).
And a control unit for controlling the cooling amount of the heat exchanger so that the detected temperature value changes discontinuously near the intake outlet of the heat exchanger by comparing the detected temperature values with the detected temperature value. 1
Alternatively, the cooling amount control device for intake air according to claim 2. 7. The condensed water temperature detecting section 51 includes: a cooling water pipe 2;
7. The intake air cooling amount control device according to claim 6, further comprising a condensed water collecting unit 53 provided close to a lower side of the fourth unit 4, and a temperature sensor 54 disposed in the condensed water collecting unit 53. 8. The intake air cooling amount control device according to claim 3, wherein the control units (34, 42, 52) perform sampling control.