JPH0552124A - Gas turbine control device - Google Patents

Abstract

PURPOSE:To smoothly and surely perform also transfer or the like to 1-stage combustion control from 2-stage combustion control by performing stable control so that a device can well follow up relating to also load shutdown or the like, in the case of the gas turbine control device for 2-stage combustion operation. CONSTITUTION:A fuel control valve 39 for setting a supply amount of total gas fuel is provided in a position in the upstream from a branch point of a supply fuel pipe 35. Primary/secondary side fuel distributing valves 40, 41 for setting distribution ratio of supply fuel are respectively provided in primary/ secondary side supply fuel pipes 36, 37. A valve position control means B1 of outputting a gas turbine speed.load controlling valve position control signal to the fuel control valve 39 to set a total gas fuel supplying opening is provided. A distribution ratio control means B2 for outputting a distribution ratio setting signal to the primary/secondary side fuel distribution valves to set each valve opening, based on a low NOx relating data corresponding to the valve position control signal output from the valve position control means, is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a gas turbine control device for controlling NOx reduction of a gas turbine applied to a power plant or the like by two-stage combustion.

[0002]

2. Description of the Related Art Conventionally, liquid fuels such as light oil and kerosene have been widely used as gas turbine fuels, but recently, from the viewpoint of diversifying utilization of energy resources, vaporized liquefied natural gas (LN
G) and liquefied propane gas (LPG), etc. are burning, and the operation using gas fuel tends to increase. Such gas fuel combustion type gas turbines are expected to increase further in the future due to the progress of gas transportation technology and the prosperity of measures for energy consumption plans to balance various energy ratios by increasing the gas fuel ratio. Be done.

On the other hand, with respect to gas turbines, not only efficient operation but also social demands such as pollution control and environmental control are increasing, and it is particularly urgent to suppress nitrogen oxides (NOx). The generation of NOx is known to be due to the increase in combustion temperature, including local combustion in the gas turbine combustor. Measures have been taken to lower NOx by reducing the effective combustion temperature.

However, in the methods such as water injection and steam injection,
Since the combustion temperature as the average temperature in the combustor decreases, the combustion efficiency deteriorates, and the thermal efficiency of the gas turbine decreases.

Therefore, in recent years, instead of water injection or steam injection, a technique using a two-stage combustion system, which can reduce NOx while maintaining the thermal efficiency of the gas turbine, has been attracting attention. In the two-stage combustion method, the gas fuel is blown not only from the combustor inlet but also from the wake side of the combustor so that the fuel distribution in the combustor is made uniform and local high temperature is prevented to reduce low NOx. As a result, it is possible to maintain a high temperature as uniform as possible in the entire combustor without lowering the combustion temperature such as water injection or steam injection.

FIG. 5 shows a conventional example of a gas turbine control device in a gas turbine power generation system to which such a two-stage combustion system is applied.

Compressor 1, gas turbine 2 and generator 3
Are arranged coaxially, the fuel injected in the combustor 4 is burned by the air compressed by the compressor 1, and the combustion gas drives the gas turbine 2 to rotate. In this structure, one fuel supply pipe 5 led from a gas fuel supply source (not shown) is branched into two, and one of the branch pipes serves as a primary fuel supply pipe 6 for the combustor 4
Is connected to the most upstream side of the combustor 4, and the other side of the branch pipe is connected to the downstream side of the most upstream side of the combustor 4 as the secondary fuel supply pipe 7.

The fuel supply pipe 5 is provided with a total flow meter 8 and a fuel stop valve 9, the primary side fuel supply pipe 6 is provided with a primary side fuel control valve 10 and a primary side fuel flow meter 11, and a secondary side fuel. Secondary fuel control valves 12 are provided in the supply pipes 7, respectively. Then, a control command signal is output from the control device A to the primary side fuel control valve 10 and the secondary side fuel control valve 12, and thereby the primary side fuel supply pipe 6 and the secondary side fuel supply pipe 7 to the combustor 4. The distribution ratio of the supplied gas fuel is set, and the combustion control is performed so as to reduce the NOx amount of the exhaust gas.

FIG. 6 shows the configuration of a control unit A for performing such fuel flow rate ratio control. This control device A
Is a function generator 2 for obtaining a fuel distribution ratio m in the secondary fuel supply pipe 7 for low NOx combustion corresponding to the gas turbine output P.
1, a calculator 22 for determining the fuel distribution ratio 1-m in the primary side fuel supply pipe 6, and a valve position control signal n for speed / load control that sets the valve opening corresponding to the total gas fuel supply amount. Multipliers 23, 24 for multiplying the distribution ratios m, 1-m to obtain the opening degrees of the secondary side fuel control valve 12 and the primary side fuel control valve 10.
And the distribution ratio m, 1 based on the actual flow rate m ', 1-m'
Correction calculators 25 and 26 that correct −m, multipliers 27 and 28 that perform multiplication based on the correction values, and a minimum flow rate value S
In response to this, it has a low value priority circuit 29 for setting the minimum opening degree of the primary side fuel control valve 10.

However, during turbine operation, first, the gas turbine 2 is started to rotate by a starter (not shown) such as a motor arranged coaxially therewith, and the compressor 1
When the air purging in the gas turbine 2 by the above is completed, the fuel stop valve 9 and the primary side fuel control valve 10 are opened, and the gas fuel is supplied to the most upstream part of the combustor 4 and ignited.

After ignition, the gas turbine 2 is accelerated after a warm-up operation for a certain period of time, and after reaching the rated speed, the operation is performed in parallel with the power system until the load increases and the rated load is reached. The primary side fuel control valve 10 controls the gas fuel flowing into the combustor 4.

The primary fuel control valve 10 controls the flow rate of the gas fuel until the gas turbine 2 is ignited, accelerated, combined, increased in load, and operated under intermediate load. Note that the range of flow rate control required for each operation of the gas turbine 2 is extremely wide, and low speeds, such as during ignition and warm-up operations,
In the low flow rate region, the opening degree of the primary side fuel control valve 10 is extremely small, and control is likely to be unstable. Therefore, in order to avoid control instability, the fuel stop valve 9 is provided with a control function such that the downstream side fuel pressure thereof is proportional to the turbine speed, whereby the primary side fuel control valve 10 operates at a low turbine speed. While controlling so that the upstream pressure is kept low,
By setting the opening degree of the primary side fuel control valve 10 to be sufficiently large, the operation can be performed and the control instability can be avoided.

During ignition and warm-up operation of the gas turbine 2, the valve opening of the primary side fuel control valve 10 is controlled by a constant value signal, and is required for speed / load control when the speed is increased or the load is increased thereafter. It is controlled by a command signal from a gas turbine control circuit (not shown) so that the fuel flow rate can be obtained. The primary side fuel control valve 10 is set with a minimum opening signal of a certain value or more from the low value priority circuit 29 so that blowout in the combustor 4 does not occur in any operating state such as ignition. It

As described above, the speed / load control is performed by the primary side fuel control valve 10 up to the intermediate load of the gas turbine 2, but thereafter, from the high load operation to the rated load,
Both primary and secondary fuel control valves 10, 12 are used. That is, after the intermediate load, the speed / load control of the gas turbine 2 is performed by controlling the fuel flow rate ratio between the primary fuel supply pipe 6 and the secondary fuel supply pipe 7.

As a means for measuring the fuel flow rate, a primary flow meter 11 is used in the primary fuel supply pipe 6,
In the secondary fuel supply pipe, the fuel flow rate of each system is measured by (measured value of total flow meter 8)-(measured value of primary flow meter 11).

Here, the fuel injection to the load of the gas turbine 2 will be described with reference to FIGS.

Up to ignition, rated speed, no load, and intermediate load of the gas turbine, operation is performed only by fuel supply from the primary side fuel supply pipe 6. That is, the secondary side fuel control valve 1
2 is fully closed.

As the load on the gas turbine increases, FIG.
Since the NOx concentration also increases in proportion as shown in (C), the primary side fuel control valve 10 is narrowed down and the secondary side fuel valve 12 is opened at the switching point P1 of the gas turbine intermediate load. As shown in (B), the primary fuel flow rate ratio R1
(1-m) is reduced, and the secondary fuel flow rate ratio R
2 (m) is increased, whereby the primary fuel flow rate N1 is reduced and the secondary fuel flow rate N2 is increased, as shown in FIG. 7 (A).

By this operation, the two-stage combustion in the combustor is achieved, and the NOx concentration can be rapidly reduced as shown in FIG. 7 (C). This switching point P1 is the combustor 4
Of the intermediate load of the gas turbine 2 in accordance with the amount of NOx generated. The two-stage combustion mode is achieved by controlling the fuel flow rate ratio at each of the fuel control valves 10 and 12.

The distribution ratio m to the secondary side fuel control valve 12 for maximally suppressing the NOx generation amount is as shown in FIG. 8 in the combustor 4 according to the operation data and test data so far. It is known that it is uniquely determined with respect to the combustion temperature T of. However, in reality, there is no sensor capable of measuring the combustion temperature T of the gas turbine 2 which reaches a thousand and several hundred degrees. Therefore, in order to know the accurate combustion temperature T, the gas turbine 2
It is necessary to calculate it from the exhaust gas temperature, compressor outlet pressure, etc.

Therefore, by utilizing the fact that the combustion temperature T is substantially proportional to the output P of the gas turbine 2, as shown in FIG. 6, the distribution ratio m of the secondary fuel control valve 12 to the output P of the gas turbine 2 is set. It is calculated by the function generator 21.

This distribution ratio setting signal m is multiplied by the valve position control signal n for controlling the speed and load of the gas turbine 2 in the multiplier 23, and the distribution ratio in each fuel control valve 10, 12 is determined. .. That is, n × (1−m) is multiplied by the primary side fuel control valve 10 and n × m is multiplied by the secondary side fuel control valve 12. Therefore, the total of the primary side and secondary side fuel control valves 10 and 12 is always controlled by the original valve position control signal n.

Next, the actual flow rate ratios m ', 1-m calculated from the flow rates N1, N2 detected by the fuel flow meters 9, 11, respectively.
′ Is a correction calculator 2 as a feedback signal of the flow rate
5, 26 are input. That is, up to this point, the relationship of m ′ = N ₂ / N = (N−N ₁ ) / N holds.

The functions of the correction calculators 25 and 26 are to set the flow ratios (m and 1-m) in the fuel control valves 10 and 12, respectively.
It is for correcting the actual flow rate ratio (m 'and 1-m'), and in the correction calculator 25, (1-m) / (1
−m ′) is calculated, and the valve position control signal n × (1-
By multiplying m) by the multiplier 27, the correction is applied to the control signal n × (1-m) of the preceding valve.

Similarly in the correction calculator 26, m / m '
Is calculated, and the valve position control signal n × m is multiplied by the multiplier 28 to correct the valve position control signal n × m.

In the primary side fuel control valve 10,
The minimum signal S for preventing blowout is input from the low value priority circuit 29 in any case, including when the load is cut off.

As described above, in the conventional example, the fuel control valves 10 and 12 control the speed and load of the gas turbine 2, and the flow ratio distribution control to the primary side and the secondary side of the combustor 4 is performed. Is going.

[0028]

However, the above-mentioned conventional techniques have various problems. That is, in FIG. 6, the correction calculators 25 and 26 perform the correction based on the actual flow rate, but the actual flow rate is as shown in FIG.
It is measured by the flow meters 9 and 11. A throttle mechanism such as an orifice is generally used as this flow meter, but it takes a considerable time such as several seconds to several tens of seconds until the flow becomes stable. Therefore, the correction signals 1-m ′ and m ′ to the correction calculators 25 and 26 mainly repeat cyclical fluctuations, which causes the opening degree of each of the fuel control valves 10 and 12 to cyclically change. Will fluctuate.

As a result, the speed and load of the gas turbine 2 also repeats fluctuations, and eventually the fuel control valve distribution ratio and the fuel control valve position control signal determined based on the speed and load of the gas turbine 2. Will also fluctuate. That is, both the set value and the feedback value of the fuel distribution ratio repeatedly fluctuate, and stable distribution ratio control cannot be performed. In this case, not only is the load applied to the combustor 4 and the life of the combustor 4 is shortened, but in some cases combustion oscillation in the combustor 4 is caused, which makes it impossible to continue the operation of the gas turbine 2. Problems such as possible problems may occur.

Further, in the case of load shedding, etc., it is necessary to instantaneously switch the fuel to the primary side. That is, the primary fuel control valve 10 is rapidly opened, and the secondary fuel control valve 12 is rapidly closed. Here, the distribution ratio setting is set by the gas turbine output actual (load) P as shown in FIG. 7, but this also always causes a certain time delay. As a result, not only the amount of NOx generated immediately after the load is suddenly increased, but in some cases, due to the sudden opening operation delay of the primary side flow control valve 10,
The gas turbine 2 may blow out.

The present invention has been made in view of the above circumstances, and can perform stable control even in the two-stage combustion operation and can well follow the load shedding and the like, and the two-stage combustion control. It is an object of the present invention to provide a gas turbine control device that can smoothly and reliably perform the transition from 1 to 1-stage combustion control.

[0032]

In order to achieve the above-mentioned object, the present invention branches one fuel supply pipe introduced from a gas fuel supply source, and one of the branch pipes is a primary fuel supply pipe. As the upstream side of the gas turbine combustor, and the other side of the branch pipe is connected as a secondary side fuel supply pipe to the downstream side of the upstream side of the combustor to supply the primary side and the secondary side fuel. In a gas turbine control device that controls the gas fuel supplied from the pipe to the combustor to a distribution ratio that reduces the NOx amount of the exhaust gas, set the total gas fuel supply amount at a position upstream of the branch point of the fuel supply pipe. And a fuel control valve for setting a distribution ratio of the supplied fuel to the primary side and secondary side fuel supply pipes, respectively. negative Based on the valve position control means that outputs the valve position control signal for load control and sets the opening for total gas fuel supply, and the low NOx relational data corresponding to the valve position control signal output from this valve position control means Distribution ratio control means for outputting a distribution ratio setting signal to the respective primary side and secondary side fuel distribution valves and setting the respective valve opening is provided.

[0033]

According to the present invention, the valve having the speed / load control function of the gas turbine and the valve for distributing the fuel are independent from each other, and the fuel control valve has the speed / load control function of the gas turbine, Since the primary side and secondary side fuel distribution valves have the fuel distribution function of the two-stage combustor,
The problems that have occurred in the past are solved, and stable two-stage combustion control can be performed.

That is, since the distribution ratio setting signal to each fuel distribution valve is provided only by the valve position control signal, the disturbance due to the delay of the feedback from the fuel flow meter as in the prior art can be avoided.

Moreover, since the distribution ratio setting signal is substantially proportional to the valve control signal, optimum low NOx combustion can be performed.

Further, even when the load is cut off, the fuel distribution valves are switched according to the valve position control signal which is rapidly reduced, so that a rapid response of each fuel distribution valve can be expected, and the gas turbine blows off. As a result, reliable control can be performed.

[0037]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS An embodiment of the present invention will be described below with reference to FIGS.

As shown in FIG. 1, the compressor 31, the gas turbine 32 and the generator 33 are coaxially arranged,
Fuel injected in the combustor 34 is combusted by the air compressed by the compressor 31, and the combustion gas drives the gas turbine 32 to rotate.

Further, one fuel supply pipe 35 led from the gas fuel supply source is branched into two, and one of the branch pipes is connected as the primary side fuel supply pipe 36 to the most upstream side of the gas turbine combustor 34. In addition, the other of the branch pipes is connected as a secondary fuel supply pipe 37 to the downstream side of the most upstream side of the combustor 34.

In this embodiment, in this embodiment, the fuel stop valve 38 is provided at a position upstream of the branch point of the fuel supply pipe 35.
And a fuel control valve 39 for setting the total gas fuel supply amount
Is provided. Further, in the primary side fuel supply pipe 36 and the secondary side fuel supply pipe 37, a primary side fuel distribution valve 40 and a secondary side fuel distribution valve 41 that set the distribution ratio of the supplied fuel.
Are provided respectively. The fuel flow meter used in the prior art is not provided.

Then, valve position control means B1 for outputting a valve position control signal for speed / load control of the gas turbine to the fuel control valve 39 to set the opening for total gas fuel supply,
Based on the low NOx related data corresponding to the valve position control signal output from the valve position control means, a distribution ratio setting signal is output to the primary and secondary side fuel distribution valves 40 and 41 to set the respective valve opening degrees. There is provided a control device B comprising a distribution ratio control means B2.

As shown in FIG. 2, the controller B has a function generator 42 and a calculator 43. Then, a fuel control valve valve position control signal (hereinafter simply referred to as a valve position control signal) n for performing speed / load control of the gas turbine is input to the control device B, and the fuel control valve 39
Are controlled by the valve position control signal n.

The valve position control signal n is the function generator 42.
Entered in. Since the valve position control signal n has a proportional or linear relationship with the load of the gas turbine 32 (see FIG. 8), the fuel distribution ratio is determined from the valve position control signal n based on the relationship data obtained in advance. It

Then, the function generator 42 outputs a signal of the distribution ratio m to the secondary side fuel distribution valve 41, and the calculator 43 calculates the distribution ratio of 1-m to the primary side fuel distribution valve 40. A signal of the distribution ratio 1-m is output from the calculator 43.

However, the gas turbine 32 is controlled by the valve position control signal n to the fuel control valve 39 until the load control is reached through the ignition in the combustor 34, the speed control of the gas turbine 32, and the inclusion thereof. ..

From the time when the load of the gas turbine 32 starts to increase until it reaches the intermediate load, "0" is output from the function generator 42 to the secondary side fuel distribution valve 41 based on the valve position control signal n. Therefore, operation is performed with the primary fuel distribution valve 40 fully open and the secondary fuel distribution valve 41 fully closed.

When the preset valve position control signal value is reached, the secondary side fuel control valve 41 is controlled by the output signal from the function generator 42, and the two-stage combustion is performed. A low NOx operation is realized by this two-stage combustion, and the operation thereof is the same as in the case of the conventional example, so the description thereof will be omitted, but in the present embodiment, fuel control having the speed / load control function of the gas turbine 32 is performed. Since the valve 39 and the primary-side fuel distribution valve 40 and the secondary-side fuel distribution valve 41 that distribute gas fuel are independent of each other, the fuel control valve 39 has a speed / load control function of the gas turbine 32. On the other hand, by providing the fuel distribution function of the combustor 34 to the primary-side and secondary-side fuel distribution valves 40 and 41, the problems that have occurred conventionally can be solved, and stable two-stage combustion control can be performed. become.

That is, the distribution ratio setting signal to each of the fuel distribution valves 40 and 41 is performed based on the valve position control signal n.
Since the conventional fuel flow meter is not used, disturbances due to feedback delay can be avoided.

Moreover, since the distribution ratio setting signal is substantially proportional to the valve control signal, optimum low NOx combustion can be performed.

When the load is cut off or the like, the valve position control signal n suddenly decreases, so the primary side fuel distribution valve 4
0 is opened rapidly, and the secondary fuel distribution valve 41 is closed rapidly. That is, the total opening of the primary-side and secondary-side fuel distribution valves 40 and 41 is maintained to be a constant opening during normal two-stage combustion operation and load shedding, and the primary-side fuel distribution valve is maintained. The opening / closing operation of 40 and the secondary side fuel distribution valve 41 is always opposite (if one is an opening operation, the other is a closing operation).

According to the above embodiment, each fuel distribution valve 4
The distribution ratio setting signal to 0, 41 is performed without disturbance because it is performed only by the valve position control signal n, and since it is approximately proportional to the valve control signal n, optimum low NOx combustion is performed and, in addition, load shedding etc. Even if there is, the fuel distribution valves are switched in accordance with the valve position control signal that rapidly decreases, so that each distribution valve 4
A rapid response of 0, 41 can be expected, and reliable control without blowout to the gas turbine 32 can be performed.

FIG. 3 shows another embodiment.

In this embodiment, it is possible to correct the flow coefficient at each distribution ratio of each fuel distribution valve 40, 41, and it is also possible to make correction by manual setting.

That is, as shown in FIG.
Between the function generator 42 and the calculator 43, a primary side fuel distribution valve correction function generator 44, a secondary side fuel distribution valve correction function generator 45, an adder 46, a correction coefficient calculation circuit 47,
The manual setting device 48, the switching device 49 and the multiplier 50 are provided.

During operation, the distribution ratio setting signal m from the function generator 42 is input to the primary side fuel distribution valve correction function generator 44 and the secondary side fuel distribution valve correction function generator 45, and the distribution ratio The flow coefficient c of the primary fuel distribution valve 40 and the flow coefficient c ′ of the secondary fuel distribution valve 41 are obtained. Both of these output values are added by the adder 46, whereby the total flow coefficient of the distribution valves 40, 41 is obtained.

Next, the correction coefficient calculation circuit 47 performs correction based on the actual flow coefficient of each of the distribution valves 40 and 41. The correction coefficient is multiplied by the multiplier 50, and the distribution ratio of the secondary fuel distribution valve 41 can be corrected. That is, with such a circuit configuration, each fuel distribution valve 40, 4
The distribution based on only the stroke ratio of 1 can be corrected by the actual flow coefficient ratio, and the accuracy of the distribution ratio can be improved.

Therefore, according to this embodiment, a lower NO
It becomes possible to perform control aiming at x (approaching the control curve in FIG. 6).

Further, in the present embodiment, as shown in FIG. 3, the input signal to the multiplier 50 can be switched to the manual setting unit 48 side by operating the switching unit 49, so that the correction by the automatic flow coefficient is performed. In addition, the distribution ratio can be set manually according to the actual operation.

FIG. 4 shows still another embodiment.

In this embodiment, the output signals to the fuel distribution valves 40 and 41 are individually corrected, and a secondary side fuel distribution valve correction function is generated for the secondary side fuel distribution valve 41. 51, secondary side correction coefficient calculation circuit 52 and multiplier 53
However, for the primary side fuel distribution valve 40, the primary side fuel distribution valve correction function generator 54 and the primary side correction coefficient calculation circuit 55 are used.
And a multiplier 56 are provided respectively.

Thus, in each of the above embodiments, the total stroke of the two fuel distribution valves 40, 41 is controlled so as to always have a constant value. The correction can be made according to the flow coefficient of the distribution valves 40 and 41.

That is, according to the present embodiment, the correction is performed so as to obtain the required valve stroke without suppressing the total stroke of the fuel distribution valves 40 and 41. Therefore, the correction is more precise than that of the embodiment of FIG. Control can be performed.

In the above embodiments, a simple gas turbine system has been described as an example of a gas turbine, but the present invention also applies to a combined cycle gas turbine system combining a gas turbine and a steam turbine, for example. The same applies as described above. In this case, at a constant rotation speed during the acceleration of the gas turbine, operations such as holding the rotation speed of the shaft are added until the exhaust heat recovery boiler is warmed up.

[0064]

As described above, according to the present invention, the valve having the speed / load control function of the gas turbine and the valve for distributing the fuel are independent of each other. While having the speed / load control function, the primary and secondary fuel distribution valves have the fuel distribution function of the two-stage combustor, so that stable two-stage combustion control can be performed.
Disturbance due to the delay of feedback from the fuel flow meter as in the past can be avoided, and since the distribution ratio setting signal is substantially proportional to the valve control signal, optimum low NOx combustion can be performed, and Even when the load is cut off, each fuel distribution valve is switched in accordance with the rapidly decreasing valve position control signal, so that a quick response of each fuel distribution valve can be made and blowout of the gas turbine does not occur. Reliable control can be performed.

[Brief description of drawings]

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

FIG. 2 is a circuit diagram showing a control device of the same embodiment.

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

FIG. 4 is a circuit diagram showing still another embodiment of the present invention.

FIG. 5 is a system diagram showing a conventional example.

6 is a diagram showing the control device of FIG.

7A is a diagram showing a fuel flow rate in each system with respect to a combustion temperature of a gas turbine, FIG. 7B is a diagram showing a fuel flow rate ratio in each system, and FIG. 7C is a diagram showing a NOx generation amount.

FIG. 8 is a view showing a fuel flow rate ratio with respect to a gas turbine output.

[Explanation of symbols]

34 Combustor 35 Fuel Supply Pipe 36 Primary Fuel Supply Pipe 37 Secondary Fuel Supply Pipe 39 Fuel Control Valve 40 Primary Fuel Distribution Valve 41 Secondary Fuel Distribution Valve B (B1, B2) Control Device (Valve Position Control Means , Distribution ratio control means)

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁵ Identification code Office reference number FI technical display location G05D 27/00 Z 7314-3H

Claims (1)

[Claims] 1. A fuel supply pipe led from a gas fuel supply source is branched, and one of the branch pipes is connected as a primary fuel supply pipe to the most upstream side of a gas turbine combustor,
The other of the branch pipes is connected as a secondary fuel supply pipe downstream of the most upstream side of the combustor, and the gas fuel supplied from the primary and secondary fuel supply pipes to the combustor is NOx of the exhaust gas. In a gas turbine control device that controls the distribution ratio to reduce the amount, a fuel control valve that sets a total gas fuel supply amount is provided at a position upstream of a branch point of the fuel supply pipe, and the primary side and the secondary side are provided. The primary side and secondary side fuel distribution valves for setting the distribution ratio of the supplied fuel are respectively provided in the side fuel supply pipe, and a valve position control signal for speed / load control of the gas turbine is output to the fuel control valve to output total gas fuel. Based on the valve position control means for setting the opening for supply and the low NOx relational data corresponding to the valve position control signal output from the valve position control means, the primary side and the secondary side fuel distribution valves are Distribution ratio setting signal outputs a gas turbine control device characterized by providing a distribution ratio control means for setting the respective valve opening.