JP3045863B2 - Turbine controller and maintenance tool for turbine controller - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbine control device for controlling the power output of a turbine generator by controlling the speed of a turbine, and a maintenance tool for the turbine control device for inspecting and maintaining the turbine control device. .

[0002]

2. Description of the Related Art Speed control of a turbine such as a steam turbine and electric power control of a turbine generator are performed by controlling an opening of a steam control valve provided at a steam inlet of the turbine. Depending on the conditions of the steam flowing into the turbine and the design of the turbine body, the opening of the steam control valve at the rated output of the turbine and the no-load opening at the completion of turbine acceleration are determined. The control is performed by calculating an opening command from these main opening positions.

FIG. 4 shows a configuration diagram of a conventional turbine control device. In order to control the turbine 1, the steam control valve 2
The turbine control device 3 that adjusts the opening of the turbine multiplies the deviation between the speed setting value from the speed setting device 4 of the turbine and the actual turbine speed signal 5S by a speed control system gain (speed arbitration rate) 6 as a speed control system. To obtain the speed control command 7S. Also,
The load control command value 9S obtained by adding the speed control command 7S to the load set value 8S of the load setting device 8 for designating the turbine generator output, and the upper limiter of the load control command value 9S to control the turbine generator output. And the load limit value 10S from the load limiter 10 are input to the low value selection circuit 11. A flow / opening stroke conversion circuit for converting the steam control valve opening command 12S based on the inflow steam flow rate selected by the low value selection circuit 11 from a signal corresponding to the steam flow rate to an opening stroke of the steam control valve 2. At 13, the conversion command is converted to an opening command corresponding to the opening stroke, and a sensor signal 14 S indicating the opening of the steam control valve is similarly converted by the conversion circuit 15 to the opening stroke. It is composed of a control valve control circuit for controlling.

[0004] Here, the constants and gains of each circuit constituting the turbine control device 3 are determined by the above-mentioned main opening of the steam control valve. For example, the steam control valve opening conversion circuit 15
Then, the sensor signal 14S of the steam control valve opening is set so that the conversion from the start position of the steam control valve opening to the fully open position can be made 0 to 100%. The speed control system gain (speed arbitration rate) 6 is set so that the specified turbine rotational speed deviation corresponds to the deviation of the position of the turbine at the rated output (rated load) from the start of opening of the steam control valve. It must be. Also, the upper limit 8a of the load setting device 8
And the lower limit 8b, the no-load position bias 8c at the completion of the turbine speed increase, and the like, respectively, are obtained by multiplying the upper and lower limits of the allowable fluctuation range of the turbine rotational speed by the speed control gain, and adjusting the steam control at the time of turbine no-load output. It must be set to the valve opening. Then, the upper limit 10a and the lower limit 10 of the load limiter 10
b must be set above the fully open position and below the fully closed position of the steam control valve. As described above, the scale of each circuit constituting the turbine control device is calibrated by the main opening position of the steam control valve, and its constant and gain are determined. For this reason, if the main opening position of the steam control valve is shifted or incorrect, it is necessary to recalculate and re-adjust the constants and gains of the circuit in the control device accordingly.

[0005]

The output of the turbine controller is converted into actual steam control valve lift operation through a mechanical system. For this reason, if the turbine operation is continued for a long time, the main opening position of the steam control valve may be shifted due to mechanical backlash, a difference in valve expansion, or the like. Also, due to changes in the steam conditions flowing into the turbine and its operating conditions,
The main opening position of the steam control valve may be changed. In such a case, it is necessary to recalculate and re-adjust the constant and gain of each circuit of the turbine control device in accordance with the changed main opening position of the steam control valve. In particular, when the main opening position of the steam control valve shifts due to mechanical backlash or differential expansion of the valve, etc., unless the circuits in the turbine controller are readjusted, the turbine output during turbine control stabilization ( (Load) and the like, there is a possibility of deviation from the setting. Also, in order to readjust the circuit constants and gains in the turbine controller, the turbine operation must be stopped,
Had to be stopped.

Accordingly, the present invention solves the problem of complicated recalculation and readjustment due to a shift or change of the main position of the steam control valve, and a turbine control device and a maintenance tool for the turbine control device which easily realize the above-mentioned adjustment. The purpose is to provide.

[0007]

SUMMARY OF THE INVENTION The first aspect of the present invention focuses on the fact that a recent turbine control device is constructed by digital technology using a microprocessor or the like. enter the key opening position was changed in the steam control valve within at least control valve for each circuit
Conversion constants and adjustment valve positions for performing range conversion
Speed control gain corresponding to the deviation of
By providing an automatic calibration circuit that recalculates and sets the set value related to the steam control valve opening stroke including the limit value , the steam in the turbine control device can be easily changed when the steam control valve position changes and online even during turbine operation. Adjustable valve opening stroke
It is designed to be able to calibrate each constant and gain related to peaking.

According to a second aspect of the present invention, a main opening position in which a steam control valve is changed is input into a maintenance tool for a turbine control device, so that at least the control valve of each control circuit can be operated.
Range conversion constants to perform di-conversion, deviation of the control valve position
The speed control gain corresponding to
By providing an automatic set value calculation circuit that calculates the set value related to the steam control valve opening stroke, and sets it in the turbine control device, the steam in the turbine control device can be easily and quickly changed when the steam control valve position is changed. Adjustable valve opening straw
It is possible to correct each constant and gain related to the loop.

[0009]

According to a first aspect of the present invention, a steam control valve opening stroke is controlled by inputting a main position of a steam control valve into a turbine control device.
The automatic calibration circuit that recalculates and sets the constants and gains related to the above causes a deviation in the position of the steam control valve due to mechanical backlash and differential expansion of the valve during long-term turbine operation. Also, easily and quickly by starting the automatic calibration circuit, the steam control valve in the turbine controller
Each constant and gain related to the opening stroke can be readjusted. Even when the conditions and operation of the turbine steam are changed, re-adjustment can be easily performed by inputting the changed steam control valve main position and activating the automatic calibration circuit. For this reason, adjustment at the time of turbine plant construction and inspection is also facilitated, and time can be reduced.

[0010] The second invention is, from the main position input of the steam control valve by a turbine controller maintenance tools, steam control
By providing an automatic set value calculation circuit that automatically calculates the constants and gains related to the valve opening stroke and sets them in the turbine controller, it is possible to prevent mechanical backlash and differential expansion of the valves during long-term turbine operation. even if misalignment of the steam control valve position, the correct steam control valve main position input to the turbine control device for maintenance tools, easily and steam in the turbine control system instantaneously by activating the automatic setting value calculation circuit
Each constant / gain related to the control valve opening stroke can be calculated and reset to the turbine control device. Similarly, when the conditions and operation of the turbine steam are changed, the changed steam control valve main position is input to the maintenance tool for the turbine control device and the automatic setting value calculation circuit is started to reset the settings. It can be done easily. For this reason, adjustment at the time of turbine plant construction and inspection is easy,
Time can be reduced.

[0011]

FIG. 1 is a block diagram of a first embodiment of the turbine control apparatus according to the present invention. The same components as those of the turbine control device of FIG. The feature of the present invention is that an automatic calibration circuit 16 is added. The automatic calibration circuit 16 has an external input
As 17S, the start signal and the sensor signal value 14S of the steam control valve opening degree for the main position of the changed steam control valve are input. Then, based on these inputs, the opening degree sensor signal 14S is set to 0 to 100% from the start of the steam control valve opening to the fully opening.
Range conversion constant of the conversion circuit 15 which converts the signal range to be
Number setting, speed control gain (speed arbitration rate) 6, load
As the upper and lower limits, the upper limit 8a and the lower limit 8 of the load setting device 8 are set.
b, the no-load position bias 8c, and the upper limit 10a and lower limit 10b of the load limiter 10 , ie, the steam control valve opening degree.
Recalculate the setting values related to the trokes and reset them.
This allows the turbine control device to continue turbine control corresponding to the changed steam control valve position. Here, the processing of the automatic calibration circuit 16 will be described.

The automatic calibration circuit 16 opens and closes the steam control valve from fully closed (or fully closed to fully closed), and at this time, the predetermined main positions of the control valve (full closed position, opening start position, no load position, rated load (Position, fully open position, etc.), and calculates the range conversion constant of the steam control valve from 0% to 100% from the start of opening to full opening. For example, suppose that the entire stroke of the control valve is 0 to 100 mm, and the above-described main position is detected with a value as shown in FIG. Of course, these detection values are unique depending on the plant and valve,
It is necessary to input the value which actually operated the control valve individually.

First, an example of calculating a range conversion constant used for turbine control will be described with reference to FIG. The valve opening is a linear change, and the conversion constant A =
[100% full open] = 100, B = [(full open position)-(opening start position)] = 90-10 = 80, C = [opening start position] = 10
Is calculated. Then, using the values of A, B and C, the conversion formula of the conversion value y of the actual opening position input x to 0 to 100% is calibrated as follows.

Thus, the range of the opening position of the control valve can be calibrated for accurate range conversion to the actual opening, and the turbine can be controlled using the range-converted value. Here, the valve opening degree in FIG. 2 is expressed in mm, but the same applies to a voltage value and a current value corresponding thereto.

Next, the calculation of the calibration of the speed control gain (speed arbitration rate) will be described. The arbitration rate is set so that the specified speed deviation corresponds to the change from the no-load position of the control valve to the rated load position. Therefore, for example, if the arbitration rate is 5%, the speed deviation of 5% becomes the rated load from the no load at the control valve position. Therefore, the conversion constant D = [(rated load position) − (no load position)] = (70−2) from the input opening sensor signal.
0), E = [(fully open position)-(opening start position)] = (90
-10), F = [100% full open] = 100, G = [speed deviation%] = 5. And D, E, F and G
Is calibrated by using the value of the following equation as a conversion equation of the conversion value y of the actual speed difference x. For example, assuming now that the speed deviation x is 5%, (2)
From the formula And a request to open this 62.5% opening is output. This corresponds to the opening requirement of the control valve from the no-load position to the rated load position.

The calculation of the calibration of the no-load bias at the completion of the turbine acceleration will be described. This is obtained by converting the no-load position of the control valve by the above equation (1), and substituting x = [no-load position] = 20, Becomes That is, the opening and closing degree of the control valve 12.5% is the no-load position after the calibration.

The calculation of the calibration of the upper and lower bias values of the load setting device will be described. The speed control gain K =
Multiplying by (DF) / (EG), the no-load bias L = 1
Add 2.5% to calculate the upper and lower limit bias of the load setting device. For example, now, the allowable upper limit speed (HS
Assuming that S: High Speed Setpoint) is 107% and the allowable lower limit speed (LSS: Low Speed Setpoint) is 95%, the load setting unit upper limit bias P and lower limit bias Q are calculated and calibrated by the following conversion formulas. P = (HSS−100%) · K + L (4) Q = (LSS−100%) · K + L (5) In this case, Is calibrated as a signal equivalent to the opening and closing of the control valve.

Similarly, using the conversion constants calculated from the predetermined opening position of the steam control valve and the bias values calculated from them, substitute them into the conversion formulas of the upper limit bias and the lower limit bias of the load limiter, calculate and calibrate. .

The turbine control device 3 'of the present invention allows the correct steam control valve position to be maintained even if the steam control valve opening scale is misaligned due to backlash, differential expansion or changes in steam conditions or the like after a long period of operation of the turbine. Automatically and quickly open the steam control valve opening in the turbine controller by simply entering a few points .
It is possible to calibrate each constant and gain related to the troke . Thereby, readjustment before starting the turbine or at the time of inspection can be performed easily and in a short time. In addition, an automatic calibration circuit is provided in the turbine controller, which can be recalculated and set immediately upon startup, so that the turbine controller can be re-adjusted even during turbine operation, and the turbine stops. Since the steam control valve cannot be operated, it is possible to avoid an operation in which the steam control valve is shifted and the turbine output or the like at the time of turbine control stabilization is still shifted.

FIG. 3 is a block diagram of one embodiment of a maintenance tool for a turbine control device according to the second invention. The same components as those of the turbine control device of FIG. A feature of the present invention is that an automatic set value calculation circuit 18a is added to the maintenance tool 18 for the turbine control device. Automatic set value calculation circuit 18
a inputs the sensor signal value of the steam control valve opening degree with respect to the main position of the changed steam control valve as the start signal as the external input 19S. And by those inputs,
Les conversion circuit 15 for converting the opening degree sensor signals to a fully open from the start of opening the steam control valve in signal range to 0 to 100%
Parameter setting and speed control gain (speed arbitration rate)
6. Upper and lower limits of the load setting device 8 as upper and lower limit values related to the load.
a, lower limit 8b, no-load position bias 8c, and the upper limit 10a and lower limit 10b of the load limiter 10 , that is,
The set value related to the valve opening stroke is recalculated and reset. This allows the turbine control device to continue turbine control corresponding to the changed steam control valve position. Here, the processing of the automatic set value calculation circuit 18a will be described.

The automatic set value calculation circuit 18a opens and closes the steam control valve from fully closed (or fully closed to full closed), and sets predetermined main positions of the control valve (full closed position, opening start position, no load position, (Rated load position, fully open position, etc.), and calculates the range conversion constant of the steam control valve from 0% to 100% from the start of opening to full opening. For example, it is assumed that the entire stroke of the control valve is 0 to 100 mm, and the above-described main position is detected with a value as shown in FIG. Of course, these detected values are unique depending on the plant and the valve, so it is necessary to input a value that actually operates the adjusting valve individually.

First, an example of calculating the range conversion constant used for turbine control will be described with reference to the case of FIG. The valve opening is a linear change, and the conversion constant A =
[100% full open] = 100, B = [(full open position)-(opening start position)] = 90-10 = 80, C = [opening start position] = 10
Is calculated. Then, using the values of A, B and C, the conversion formula of the conversion value y of the actual opening position input x to 0 to 100% is calibrated as follows.

Thus, the range of the opening position of the control valve can be calibrated to an accurate range conversion to the actual opening, and the turbine can be controlled using the value obtained by the range conversion. Here, the valve opening degree in FIG. 2 is expressed in mm, but the same applies to a voltage value and a current value corresponding thereto.

Next, the calculation of the calibration of the speed control gain (speed arbitration rate) will be described. The arbitration rate is set so that the specified speed deviation corresponds to the change from the no-load position of the control valve to the rated load position. Therefore, for example, if the arbitration rate is 5%, the speed deviation of 5% becomes the rated load from the no load at the control valve position. Therefore, the conversion constant D = [(rated load position) − (no load position)] = (70−2) from the input opening sensor signal.
0), E = [(fully open position)-(opening start position)] = (90
-10), F = [100% full open] = 100, G = [speed deviation%] = 5. And D, E, F and G
Is calibrated by using the value of the following equation as a conversion equation of the conversion value y of the actual speed difference x. For example, assuming now that the speed deviation x is 5%, (2)
From the formula And a request to open this 62.5% opening is output. This corresponds to the opening requirement of the control valve from the no-load position to the rated load position.

The calculation of the calibration of the no-load bias when the turbine speed-up is completed will be described. This is obtained by converting the no-load position of the control valve by the above equation (1), and substituting x = [no-load position] = 20, Becomes That is, the opening and closing degree of the control valve 12.5% is the no-load position after the calibration.

The calculation of the calibration of the upper and lower limit bias values of the load setting device will be described. The speed control gain K =
Multiplying by (DF) / (EG), the no-load bias L = 1
Add 2.5% to calculate the upper and lower limit bias of the load setting device. For example, now, the allowable upper limit speed (HS
Assuming that S: High Speed Setpoint) is 107% and the allowable lower limit speed (LSS: Low Speed Setpoint) is 95%, the load setting unit upper limit bias P and lower limit bias Q are calculated and calibrated by the following conversion formulas. P = (HSS−100%) · K + L (4) Q = (LSS−100%) · K + L (5) In this case, Is calibrated as a signal equivalent to the opening and closing of the control valve.

Similarly, using the conversion constants calculated from the predetermined opening position of the steam control valve and the bias values calculated from them, substitute them into the conversion formulas of the upper limit bias and the lower limit bias of the load limiter, calculate and calibrate. .

The maintenance tool 18 for a turbine control device according to the second aspect of the present invention allows the steam control valve opening scale to be displaced due to play after a long operation of the turbine, a difference in elongation, or a change in steam conditions or the like. Just input a few correct steam control valve positions and automatically and quickly
It is possible to calibrate each constant and gain related to the steam control valve opening stroke . Thereby, readjustment before starting the turbine or at the time of inspection can be performed easily and in a short time. In addition, an automatic calibration circuit is provided in the turbine controller, which can be recalculated and set immediately upon startup, so that the turbine controller can be re-adjusted even during turbine operation, and the turbine stops. Since the steam control valve cannot be operated, it is possible to avoid an operation in which the steam control valve is shifted and the turbine output or the like at the time of turbine control stabilization is still shifted.

As described above, in the above-described embodiment, the re-calibration of each constant and gain related to the steam control valve opening stroke of the main circuit of the turbine control has been described, but the steam control valve position is used. The calibration of the setting of the self-diagnosis circuit described above can be similarly applied.

[0030]

As described above, according to the turbine control apparatus and the maintenance tool for the turbine control apparatus of the present invention, the operation of the steam control valve mechanical system, such as play and differential expansion, steam conditions, etc., is changed, and steam control is performed. Even if the position of the valve shifts, it is easy to readjust the constants and gains related to the steam control valve opening stroke in the turbine control device so that the correct position can be easily and quickly controlled. it can. This also has the effect of significantly shortening the inspection and adjustment time of the turbine control device, saving labor, and increasing the operating time by online adjustment during turbine operation.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of a turbine control device according to a first embodiment of the present invention;

FIG. 2 is a configuration diagram of a maintenance tool for a turbine control device according to a second embodiment of the present invention;

FIG. 3 is a diagram showing input points of a steam control valve opening sensor signal according to the first and second embodiments of the present invention;

FIG. 4 is a configuration diagram of a conventional turbine control device.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 ... Turbine 2 ... Steam control valve 3, 3 '... Turbine controller 4 ... Speed setting device 5 ... Turbine rotation speed 6 ... Speed control system gain (speed arbitration rate) 7S ... Speed control command 8 ... Load setting device 8a ... Load Upper limit of setting unit 8b: Lower limit of load setting unit 8c: No-load position bias 9S: Load control command 10: Load limiter 10a: Upper limit of load limiter 10b: Lower limit of load limiter 11: Low value selection circuit 12S: Opening / closing of steam control valve Command 13: Flow rate / opening stroke conversion circuit 14S: Steam control valve opening sensor signal 15: Sensor / opening stroke conversion circuit 16: Automatic calibration circuit 17S, 19S: External input 18: Maintenance tool for turbine control device 18a: Automatic Set value calculation circuit

Continuation of the front page (56) References JP-A-3-85303 (JP, A) JP-A-61-72804 (JP, A) JP-A-3-37340 (JP, A) JP-A-63-83546 (JP, A) , A) Hikaru Hei 2-59240 (JP, U) (58) Field surveyed (Int. Cl. ⁷ , DB name) F01D 17/00

Claims (2)

(57) [Claims] A turbine control device for controlling the flow rate of steam flowing into a steam turbine by a steam control valve to control the speed of the turbine or to control the load on the generator, wherein the valve stroke of the steam control valve is adjusted from zero to an upper limit value. Means for operating within a range, means for detecting and storing opening signals at a plurality of predetermined valve opening positions associated with the valve operating means, and a valve opening command signal based on the opening signals at the plurality of points. range for performing range conversion of at least control valve for
Means for calculating a set value related to the steam control valve opening stroke including the conversion constant , the speed control gain corresponding to the deviation of the control valve position, and the upper and lower limit values related to the load, and the calculated set value as a new value. A turbine control device comprising an automatic calibration circuit comprising a setting unit. 2. A turbine control device maintenance tool for inspecting and maintaining a turbine control device for controlling a turbine speed control or a generator load control by adjusting a flow rate of steam flowing into a steam turbine by a steam control valve. Valve operating means for operating the valve stroke of the valve in a range from zero to an upper limit value, means for detecting and storing opening signals at a plurality of predetermined valve opening positions associated with the valve operating means,
A range conversion constant for performing range conversion of at least the control valve from the opening signal at the plurality of points to the valve opening command signal.
Number , a speed control gain corresponding to the deviation of the control valve position, and means for calculating a set value related to the steam control valve opening stroke including upper and lower limit values related to the load, and these calculated set values as new values. A maintenance tool for a turbine control device, comprising: an automatic set value calculation circuit comprising a setting unit.