JP2003227304A - Turbine control device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To prevent the number of revolutions from rising rapidly immediately after the start of a turbine. <P>SOLUTION: This turbine control device includes change rate deciding means 20, a signal generator 22, a lower value selector 7 and a switch 23. When an open status of a steam stop valve is detected based on a turbine start signal 53 indicating an open/close status of the steam stop valve, and it is detected that a change rate of the number of revolutions exceeds a preset value based on a signal 58 of the number of actual revolutions of a turbine, the means 20 outputs a switch signal 65 indicating the state. The signal generator 22 generates a command 62 for closing the valve that drives a steam governing valve in the direction of closing the valve. When a first command 55 of the number of revolutions and the command 62 are entered and a switch signal 65 is entered, and if the signal 65 is effected, the switch 23 outputs the command 62 to the selector 7 and a steam governing valve operator is driven to close the steam stop valve based on the command 62. If the switch signal 65 is not effected, the switch 23 outputs the command 55 to the selector 7. <P>COPYRIGHT: (C)2003,JPO

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 supplying steam to a turbine to start the turbine.

[0002]

2. Description of the Related Art Turbine control devices are used for reactor isolation cooling (Reactor) in, for example, a nuclear power plant.
Core Isolation Cooling (hereinafter abbreviated as RCIC) system, that is, in a state where the steam control valve is open, the steam stop valve upstream of the system is suddenly opened to allow steam to flow into the turbine and start the turbine. To be

This reactor isolation cooling system is installed mainly for the purpose of ensuring the required water level and cooling water amount in the reactor when the reactor is isolated from the main steam system and the water supply system. .

The structure of such an RCIC system will be described with reference to FIG. Before the RCIC system is activated, the steam control valve 14 is fully opened and the steam stop valve 13 is fully closed. When a turbine start request is generated, the steam stop valve 13 is fully opened by the steam stop valve operating unit 11. To be done.

As a result, the steam passes through the steam control valve 14 and is supplied to the turbine 16, and the turbine 16 starts rotating.

When the turbine 16 starts rotating, the hydraulic pump 15 directly connected to the turbine shaft is driven to secure the hydraulic pressure of the steam control valve operating unit 10, and the hydraulic pressure controls the valve opening degree of the steam control valve 14. Is possible.

By controlling the valve opening of the steam control valve 14, the amount of steam supplied to the turbine 16 is adjusted,
The number of revolutions of the turbine 16 (hereinafter, simply referred to as the number of revolutions) is controlled, and accordingly, the drive amount of the feed water pump 18 is controlled to adjust the feed water flow rate to the nuclear reactor.

As described above, the steam control valve 14 is controlled by the steam control valve operating device 10, and the control signal at that time is output as a steam control valve opening command 60 from the turbine control device 2 described later.

The turbine control device 2 changes the rate of rotation so that the turbine reaches the target rotation speed based on a rotation speed setting command that is set with a rotation speed higher than the rated rotation speed of the turbine as a target. Is set, the rotation speed is set based on the change rate, and the rotation speed setting means 35 that outputs the rotation speed as the first rotation speed command 55 and the first rotation speed command 55 are input and water is supplied by the water supply pump 18. The second rotation speed command 56 corresponding to the water supply flow rate is input, and the low value selection means 36 for selecting these low values and outputting them as the rotation speed command 57 and the rotation speed command 57 are input, and the actual turbine 16 is also input. The turbine actual rotation speed signal 58 indicating the rotation speed is input, these deviations are amplified with the optimum amplification degree for the rotation speed control, and this is output as the steam control valve opening degree command 60. Occurrence It has a step 37 and the like.

The rotation speed setting means 35 uses a rotation speed higher than the rated rotation speed of the turbine as a target rotation speed, and outputs the start rotation speed setting command 51 as a start rotation speed setting command 51. The steam speed control valve opening command 60 input to the valve operating device 10 sets a rotation speed opposite to the polarity in the valve opening direction, and outputs this as a stop rotation speed setting command 52. In accordance with a switching signal, and outputs the switching speed as a rotation speed setting command 54, and a change rate setting device 6 that sets a rotation speed change rate and outputs the rotation speed based on this as a first rotation speed command 55. Etc.

The low value selection means 36 is composed of a low value selector 7 which selects and outputs the signal having the smaller value out of a plurality of input signals.

The valve opening command generating means 37 sets the optimum amplification degree for controlling the number of revolutions by adding and subtracting the input signals and outputting the result as the number of revolutions deviation signal 59. The input signal is amplified by the amplification degree and is output as the steam control valve opening degree command 60.

With such a configuration, the opening of the steam stop valve 13 is mechanically detected by the position detector 12, and the detection result is input to the switch 5 as a turbine start signal 53.

When the steam stop valve 13 is opened and the turbine start signal 53 is established, the switch 5 outputs the start rotation speed setting command 51 as the rotation speed setting command 54.

On the other hand, when the steam stop valve 13 is fully closed and the turbine start signal 53 is not established, the stop rotation speed setting command 52 is output as the rotation speed setting command 54.

In the present specification, there are cases where the signal takes a binary value, such as the turbine start signal 53 and the rotational speed sudden increase signal 65. When this signal is "ON" (high level signal When), the signal is appropriately described as "established". Of course, this is a convenience
It is obvious that the signal may be "established" when it is "F" (when it is a low level signal).

The rotation speed setting command 54 is input to the change rate setting device 6, and the change rate of the rotation speed is set by the change rate setting device 6, and this is set as the first rotation speed command 55 by the low value selector 7. Is output to.

A second rotation speed command 56 indicating the rotation speed corresponding to the amount of water supplied by the water supply pump 18 from the water supply control system 1 is input to the low value selector 7, and the first speed is selected. The low value of the command 55 and the second rotation speed command 56 is selected by the low value selector 7 and output as the rotation speed command 57.

From the characteristics of the water supply pump 18, the water supply amount actually starts when the turbine 16 is several tens% of the rated speed.
It is from the time when it is above.

Further, the first rotation speed command 55 is set so that the steam control valve opening command 60 has a minimum rotation speed when the turbine is in the valve opening direction and a maximum rotation speed higher than the rated rotation speed. It is set.

Therefore, in the low value selector 7, from the start of starting the turbine 16 to the rotational speed at which water is supplied, the first value is selected.
The rotation speed command 55 is selected, and thereafter, the second rotation speed command 56 is selected and output as the rotation speed command 57.

The actual turbine rotational speed is detected by a rotational speed detector 17 provided close to the turbine shaft, and the detection result is output as a turbine actual rotational speed signal 58.

Then, the turbine actual rotation speed signal 58 and the rotation speed command 57 are input to the adder 8 to rotate the rotation speed command 5
A rotation speed deviation signal 59 obtained by subtracting the turbine actual rotation speed signal 58 from 7 is input to the coefficient unit 9.

The coefficient unit 9 amplifies the rotation speed deviation signal 59 with an optimum amplification degree for controlling the rotation speed of the turbine 16 and outputs it as a steam control valve opening degree command 60.
Output to 0.

The steam control valve controller 10 drives the steam control valve 14 in the valve opening direction when the polarity of the steam control valve opening command 60 is positive, and moves the steam control valve 14 in the valve closing direction when the polarity is negative. To drive.

Further, the steam control valve controller 10 changes the opening / closing speed of the steam control valve 14 in proportion to the magnitude of the steam control valve opening command 60 to adjust the opening / closing speed of the steam control valve 14.

[0027]

However, due to the following reasons, the turbine actual rotation speed signal 58 may become larger than the first rotation speed command 55, and it is not shown in the figure that the increase in the dangerous rotation speed is detected. The overspeed detector operates to output a stop command to the steam stop valve operating device 11, and the rotation speed of the turbine 16 fluctuates, and it takes a long time to reach the target value. There is a problem in that the time constraint from the generation of the turbine start request to the securing of a predetermined amount of water supply may not be met.

That is, since the steam control valve 14 before starting is fully open, when the steam stop valve 13 is opened, the turbine 16 is opened.
Is supplied with the maximum amount of steam, and the rotation speed increases toward the maximum rotation speed.

At this time, the steam control valve 14 can be controlled by the steam control valve opening command 60 only after the rotational speed is increased to some extent and the hydraulic pressure of the hydraulic pump 15 is secured.

Further, the coefficient unit 9 sets the amplification degree to the rotation speed command 57.
Since the rotation speed controllability with respect to is optimized, the amplification degree is not set to a too large value, the value of the steam control valve opening degree command 60 is small at the time of startup, and the steam control valve 14 is set to a small value. It cannot be operated quickly in the valve closing direction.

Therefore, the turbine actual rotation speed signal 58 is the first
There is a possibility that the rotation speed command 55 becomes large, and the rotation speed fluctuates, causing the above-mentioned problem.

Therefore, the present invention prevents the excessive steam from flowing into the turbine by allowing the steam control valve to be rapidly operated in the valve closing direction when the rotational speed is rapidly increased immediately after the start-up. An object of the present invention is to provide a turbine control device that suppresses fluctuations in the actual turbine speed and can settle to a target speed in a short time.

[0033]

In order to solve the above-mentioned problems, the invention according to claim 1 is to operate a steam control valve, wherein a steam stop valve provided upstream of the steam control valve with the steam control valve opened. When the turbine is suddenly opened and steam is flowed into the turbine to which the water supply pump is connected to start the turbine and start water supply, the rotation speed is set higher than the rated rotation speed of the turbine. Based on the rotational speed setting command, the rate of change of the rotational speed is set so that the turbine reaches its target rotational speed, and the rotational speed is set based on the rate of change and output as the first rotational speed command. Setting means,
The first rotation speed command is input and the second rotation speed command indicating the rotation speed corresponding to the amount of water supplied by the water supply pump is input, and these low values are selected and output as the rotation speed command. Low value selection means, and the turbine speed command indicating the actual rotation speed of the turbine is input together with the rotation speed command, and these deviations are amplified with the optimum amplification degree for rotation speed control, In a turbine control device that has a valve opening command generation unit that outputs this as a steam control valve opening command and controls the rotational speed of the turbine so that a predetermined amount of water is supplied, the open / close state of the steam stop valve It was detected that the steam stop valve was opened based on the turbine start signal indicating that, and that the rate of change of rotation speed was greater than the preset value based on the turbine actual rotation speed signal. In that case A change rate determination means for outputting the signal shown as a switching signal, a signal generator for generating a valve full closing command for driving the steam control valve in the valve fully closing direction, and a switching signal and at least a valve full closing command are input. Then, when the switching signal is established, a valve full-close command is output, and the steam control valve actuator has a switching device that drives the steam stop valve to close based on the valve full-close command, and starts up. Immediately after the rotation speed suddenly rises, the steam control valve is operated rapidly in the valve closing direction to prevent excessive steam from flowing into the turbine, while suppressing fluctuations in the actual turbine rotation speed to reach the target rotation speed in a short time. It is characterized by being able to settle.

In the invention according to claim 2, the rotation speed setting means inputs the rotation speed setting command, the turbine actual rotation speed signal and the switching signal, and follows the turbine actual rotation speed signal when the switching signal is established. When the switching signal is not satisfied, the output changes from the first rotation speed command output at that time to the target rotation speed setting command. It is characterized by having a change rate setting device that outputs a first rotation speed command in which a rate is set.

According to a third aspect of the present invention, there is provided a switching device comprising:
When the rotation speed command and the valve full closing command are input, and the switching signal is input and the switching signal is established, the valve full closing command is output to the low value selection means, and the switching signal is not established. In this case, the first rotation speed command is output to the low value selection means.

According to a fourth aspect of the present invention, the steam control valve opening command and the valve full closing command are input to the switching device, and when the switching signal is input and the switching signal is established, the valve is fully closed. A command is output to the steam control valve controller, and when the switching signal is not established, a steam control valve opening command is output to the steam control valve controller.

According to a fifth aspect of the present invention, the rate of change determination means detects whether or not the rate of change of the rotational speed is larger than a preset value based on the turbine actual rotational speed signal, and the result is used as the rate of change. A change rate detector that outputs as a detection signal, performs a logical product operation of the turbine start signal and the change rate detection signal,
When the steam stop valve is opened and the rate of change of the rotation speed becomes larger than a preset value, a change rate logical product calculator that outputs a signal indicating a rapid increase in the rotation speed as a switching signal And having.

According to the sixth aspect of the present invention, the change rate determining means detects whether or not the change rate of the rotation speed is larger than a preset value based on the turbine actual rotation speed signal, and the result is used as the change rate. A change rate detector that outputs as a detection signal, performs a logical product operation of the turbine start signal and the change rate detection signal,
When the steam stop valve is in the open state, and the rate of change of the rotation speed becomes larger than a preset value, a change rate logical product calculator that outputs a rotation speed sudden increase signal indicating that,
When it detects that the steam stop valve is open based on the turbine start signal, it outputs a time-delay operation signal of a predetermined level for a preset time from that time, and a time-delay operation signal and rotation. When the steam product is opened and the rate of change of the rotational speed becomes larger than the preset value within the time set by the time-delay actuator, the AND operation is performed with the signal of sudden increase in number. Has a time-delay rate of change logical product operator that outputs a signal indicating that as a switching signal.

According to a seventh aspect of the present invention, the steam stop valve provided upstream of the steam control valve is suddenly opened by the steam control valve operator with the steam control valve opened, and the water supply pump is connected. When the turbine is started by supplying steam to the turbine and water supply is started, the target rotation of the turbine is based on the rotation speed setting command set to a rotation speed higher than the rated rotation speed of the turbine. Number of revolutions is set so that the number of revolutions is set, the number of revolutions is set on the basis of the change rate, and the first revolutions command is input, and the first revolutions command is input. The second rotation speed command indicating the amount of water supplied by the water supply pump is input, low value selection means for selecting these low values and outputting them as the rotation speed command, and the rotation speed command is input and also the turbine speed. Shows actual speed It has a valve opening command generation means for inputting a turbine actual rotation speed signal, amplifying these deviations with an optimum amplification degree for rotation speed control, and outputting this as a steam control valve opening command. In a turbine control device that controls the rotational speed of the turbine so that a predetermined amount of water is supplied, a differentiator that detects the rate of change of the turbine actual speed signal and a predetermined proportional to the rate of change that is detected by the differentiator. It has a coefficient unit that multiplies a constant and outputs it as a subtraction value signal, and an adder that subtracts the subtraction value signal from the first rotation speed command and inputs it when the first rotation speed command is input to the low value selecting means. It is characterized by

In the invention according to claim 8, the steam control valve provided upstream of the steam control valve is suddenly opened by the steam control valve operator in a state where the steam control valve is opened, and the water supply pump is connected. When the turbine is started by supplying steam to the turbine and water supply is started, the target rotation of the turbine is based on the rotation speed setting command set to a rotation speed higher than the rated rotation speed of the turbine. Number of revolutions is set so that the number of revolutions is set, the number of revolutions is set on the basis of the change rate, and the first revolutions command is input, and the first revolutions command is input. The second rotation speed command indicating the amount of water supplied by the water supply pump is input, low value selection means for selecting these low values and outputting them as the rotation speed command, and the rotation speed command is input and also the turbine speed. Shows actual speed The actual turbine speed signal is input, the adder that calculates these deviations and the deviation signal from the adder are amplified with the optimum amplification degree for controlling the speed, and this is added to the steam control valve opening command. In the turbine controller that controls the rotational speed of the turbine so that a predetermined amount of water is supplied, the rate of change of the actual turbine rotational speed signal. And a coefficient unit which multiplies the rate of change detected by the differentiator by a predetermined proportional constant and outputs the subtraction value signal to the adder.

[0041]

BEST MODE FOR CARRYING OUT THE INVENTION Embodiments of the present invention will be described with reference to the drawings. It should be noted that the same components as those in the related art are designated by the same reference numerals and the description thereof will be appropriately omitted.

FIG. 1 is a partial block diagram of the turbine control device according to the first embodiment, and shows the configuration of a part added to the conventional configuration shown in FIG.

That is, the first rotation command 55, which is additionally provided between the change rate setting device 6 and the low value selector 7 shown in FIG. It is output to the selector 7 as a new first rotation speed command.

In the turbine controller according to the present embodiment, the signal generator 22 for generating the valve full-close command 62 corresponding to the full-close command for the steam control valve 14 and the switching signal input to the terminal C are generated. A switch 23 that outputs one input signal of a plurality of input signals, determines whether or not the rate of change of the actual turbine rotational speed is greater than a preset rate of change,
A change rate determination means 20 for outputting the determination result as a rotation speed sudden increase signal 65 is additionally provided.

The turbine actual rotation speed signal 58 from the rotation speed detector 17 is input to the change rate judging means 20, and the change rate thereof is larger than the change rate preset in the change rate judging means 20. A change rate detector 24 that detects whether or not the result is output as a change rate detection signal 64, a change rate detection signal 64, and a turbine start signal 53 that indicates that the steam stop valve 13 from the position detector 12 indicates the opening of the valve. It is formed by a change rate logical product calculator 25 which calculates a logical product of and and outputs the calculation result as a rotation speed sudden increase signal 65.

As shown in FIG. 1, the rotation speed sudden increase signal 65 is input to the switching signal input terminal C of the switch 23, and in this sense, the rotation speed sudden increase signal 65 acts as a switching signal. .

Next, the operation of the turbine control device 2 having such a configuration will be described with reference to the operation diagram shown in FIG. The figure shows a case where the rate of change of the actual turbine speed signal 58 between A and B is higher than the rate of change set in the rate of change detector 24 (hereinafter, the same applies to each embodiment. To).

The turbine actual rotation speed signal 58 and the turbine starting signal 53 are input to the change rate judging means 20, and when both of them are satisfied, the rotation speed sudden increase signal 65 is "ON".
Is output.

That is, when the rate of change of the actual turbine speed signal 58 is higher than the rate of change preset in the rate of change detector 24, the rate of change detection signal 64 of "ON" changes the logical product of the rate of change AND calculator. 25 is output.

Then, in the change rate logical product operator 25,
A logical operation of the turbine start signal 53 and the change rate detection signal 64 is performed, and the steam stop valve 13 starts opening the valve to be “ON”.
When the turbine start signal 53 of No. 2 is input and the change rate detection signal 64 of “ON” is input, the rotation speed sudden increase signal 65 of “ON” is output to the switch 23 as the switching signal (AB in FIG. 2). while).

The switch 23 receives the valve full-close command 62 corresponding to the full-close command for the steam control valve 14 from the signal generator 22 and the change rate of the rotational speed set by the change rate setting device 6 at the change rate. A certain first rotation speed command 55 is input, an input signal is selected according to the success or failure of the rotation speed sudden increase signal 65 that is a switching signal, and this is newly output as the first rotation speed command 63.

That is, when the rotation speed sudden increase signal 65 is established (when it is "ON"), the turbine actual rotation speed is rapidly increasing, so the steam control valve 14 is driven in the valve closing direction. The valve full-close command 62 is selected in order to suppress a sudden increase in the actual turbine rotation speed.

On the other hand, when the rotation speed sudden increase signal 65 is not established (when it is "OFF"), the first rotation speed command 55 is selected in order to perform the same processing as the conventional one.

In this way, the first rotation speed command 63 output from the switch 23 is switched according to the success or failure of the rotation speed sudden increase signal 65 and is input to the low value selector 7.

As a result, the second rotation speed command 56 and the first rotation speed command 63 from the water supply control system 1 are input to the low value selector 7, and these low values are selected. And outputs it as a rotation speed command 57.

At this time, if the rotation speed sudden increase signal 65 is satisfied and the valve full-close command 62 from the signal generator 22 is selected by the switch 23, the first rotation speed command 63 is set to the second rotation speed. Since it is set to be smaller than the command 56, the low value selector 7 selects the first rotation speed command 63.

When the rotation speed sudden increase signal 65 is not established, the switch 23 selects and outputs the first rotation speed command 55, so that the low value selector 7 outputs the first rotation speed command 55. Based on the first rotation speed command 63 and the second rotation speed command 56
And the low value command is output.

The rotation speed command 57 selected in this way
And the turbine actual rotation speed signal 58 from the rotation speed detector 17 are input to the adder 8, and the deviation between them is added to the rotation speed deviation signal 5
9 is output to the coefficient unit 9.

The coefficient unit 9 amplifies the rotation speed deviation signal 59 with an optimum amplification degree for controlling the rotation speed of the turbine 16 and outputs it as a steam control valve opening command 60 to the steam control valve operating unit 1.
Output to 0.

When the rotation speed sudden increase signal 65 is established, the rotation speed command 5 output from the low value selector 7
7 is a command based on the valve full-close command 62 that does not change with time from the signal generator 22. Since the rotation speed command 57 is set smaller than the turbine actual rotation speed signal 58, the polarity of the rotation speed deviation signal 59 is shown. Is a steam control valve opening command 60 that is negative and does not change over time (steam control valve opening command 60 between AB in FIG. 2).

On the other hand, when the rotation speed sudden increase signal 65 is not established, the change rate setting unit 6 is set to perform the original control.
The rotational speed deviation signal 5 depending on the magnitude of the rotational speed command 57 and the actual turbine rotational speed 58 based on the first rotational speed command 55 from
The polarity of 9 changes and its value also changes.

When the polarity of the steam control valve opening command 60 is positive, the steam control valve operating device 10 drives the steam control valve 14 in the valve opening direction at a valve opening speed according to its magnitude, and the polarity is negative. Occasionally, the steam control valve 14 has a valve closing speed according to its size.
Is driven in the valve closing direction.

As described above, when the actual turbine speed rapidly increases immediately after starting, the polarity of the steam control valve opening command 60 becomes negative, and the steam control valve 14 is forcibly driven in the valve closing direction, resulting in an excessive amount. It becomes possible to suppress the steam from flowing into the turbine 16.

Further, the success or failure of the rotational speed sudden increase signal 65 is judged only by the actual turbine rotational speed, and the signal generator 22
To the valve full closing command 6 corresponding to the full closing command of the steam control valve 14
Since 2 is output, regardless of the second rotation speed command 56 based on the water supply amount from the water supply pump 18 having a characteristic that the water supply amount does not start until the turbine 16 becomes tens% or more of the rated rotation speed. Instead, the rotation speed of the turbine 16 can be appropriately controlled.

Since such a rotation speed control can suppress a significant increase in the actual turbine rotation speed, fluctuations in the rotation speed can be suppressed, and the target rotation speed can be settled in a short time.

Next, a second embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 3 is a partial configuration diagram of the turbine control device according to the present embodiment, and illustrates a portion different from the conventional configuration of FIG.

That is, a signal generator 27, a switching unit 23, a change rate judging means 20, etc. are provided between the coefficient unit 9 and the steam control valve operating unit 10 shown in FIG. The signal from the signal generator 27 and the signal from the signal generator 27 are switched according to the conditions described later to be input to the steam control valve operating device 10.

In the above embodiment, in order to suppress the rapid increase in the actual turbine rotational speed immediately after starting,
When the rate of change of the actual turbine rotational speed becomes higher than the preset rate of change, the first rotational speed command from the rate of change setting device 6 corresponding to the full closing command of the steam control valve 14 is given priority. Based on the valve full-close command 62 corresponding to the full-close command for the steam control valve 14 from the signal generator 22, the steam control valve opening command 60
Is output and controlled.

However, the present invention is not limited to this, and the output of the steam control valve opening degree command 60 is performed in the same manner as in the conventional case, but in the case where the above-mentioned rapid increase of the actual turbine rotational speed occurs. As shown in FIG. 3, such control may be performed by inputting a signal from a signal generator 27, which will be described later, to the steam control valve operating device 10 instead of the steam control valve opening command 60.

Therefore, in the turbine control device 2, a signal generator 27 for generating the valve full-close command 67 for the steam control valve 14 and a plurality of input signals among a plurality of input signals according to the switching signal input to the terminal C are selected. Switching device 2 that outputs 1 input signal
3. The change rate determination means 20 that determines whether the rate of change of the actual turbine rotation speed is larger than a preset change rate and outputs the determination result as the rotation speed sudden increase signal 65 is different from the conventional configuration. Have been added.

The switch 23 and the change rate judging means 20
Is the same as the configuration according to the first embodiment, and the detection of the sudden increase in the actual turbine rotational speed immediately after the startup is also performed.

However, the signal generator 27 according to the present embodiment uses the steam control valve 14 instead of the steam control valve opening command 60.
The signal generator 22 according to the first embodiment is different in that the valve full-close command 62 corresponding to the full-close command of the steam control valve 14 is generated. ing.

That is, in the case of the first embodiment, the valve full closing command 62 from the signal generator 22 is sent through the low value selector 7, the adder 8, the coefficient unit 9, etc. to the steam control valve opening degree. The command 60 is generated, but in the case of the present embodiment, the signal generator 27 outputs the valve full-close command 67 corresponding to the steam control valve opening command 60.

As a result, the valve full closing command 67 for fully closing the steam control valve 14 is issued to the signal generator without considering what processing is performed by the low value selector 7, the adder 8 and the coefficient unit 9. Since the design can be made so that the data is output from 27, there is an advantage that the design becomes easy.

The steam control valve opening command 60 from the coefficient unit 9 and the valve full-close command 67 from the signal generator 27 are input to the switching device 23, and the rotation speed sudden increase signal 65 from the change rate judging means 20 is input. Either of them is output as the steam control valve opening degree command 72.

Therefore, as can be seen from the operation diagram shown in FIG. 4, the actual turbine speed rapidly increases and the rate of change of the actual turbine speed signal 58 becomes greater than the rate of change set in the rate detector 24. Between A and B, according to the conventional control, the steam control valve opening command 60 is monotonous and gradually decreases.
On the other hand, according to the present embodiment, this section is controlled by the steam control valve opening degree command 72 based on the valve full closing command 67 from the signal generator 27.

As described above, when the actual turbine rotational speed suddenly increases immediately after startup, the steam control valve 14 is forcibly driven in the valve closing direction to easily prevent excessive steam from flowing into the turbine 16. It becomes possible to do.

Further, the success or failure of the rotational speed sudden increase signal 65 is judged only by the actual turbine rotational speed, and the signal generator 27
Since the valve full-close command 72 is output from, even if the water supply amount actually starts due to the characteristics of the water supply pump 18 even when the turbine 16 reaches several tens% of the rated speed, Regardless of the characteristics of the water supply pump 18, the rotation speed of the turbine 16 can be appropriately controlled, and fluctuations of the rotation speed can be suppressed, so that the target rotation speed can be settled in a short time.

<Next, a third embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 5 is a partial block diagram of the turbine control device according to the present embodiment, and shows a portion different from the conventional configuration of FIG.

That is, a signal generator 22, a switch 23, and a change rate judging means 20 are provided between the change rate setter 6 and the low value selector 7 shown in FIG. The signal and the signal from the signal generator 22 are switched according to the conditions described later and input to the low value selector 7.

In the above-described first and second embodiments, when the rate of change of the actual turbine rotational speed becomes larger than the preset rate of change, based on the valve full closing command 62 from the signal generator 22 or the like. The steam control valve 14 was controlled to be fully closed.

On the other hand, in the present embodiment, such control is performed only for a predetermined time (the time set in the time-delay actuator 21 described later) after the steam stop valve 13 starts opening. The reliability is improved.

Therefore, in the turbine control device 2, the valve full closing command 6 corresponding to the full closing command of the steam control valve 14 is issued.
2, a signal generator 22 for generating 2, a switch 23 for switching an output signal in accordance with a switching signal input to the terminal C, and whether the rate of change of the actual turbine rotational speed is greater than a preset rate of change within a predetermined time. Change rate determination means 2 for detecting whether or not
0 is added to the conventional configuration.

The change rate determining means 20 detects whether or not the change rate of the actual turbine rotational speed is larger than a preset change rate, and outputs the result as a change rate detection signal 64. The detector 24, the change rate AND calculator 2 which calculates the logical product of the change rate detection signal 64 and the turbine start signal 53 and outputs this as the rotational speed sudden increase signal 65.
5. With the timing of the establishment of the turbine start signal 53 as the timing timing, the time-delay actuator 21 that outputs the time-delay operation signal 61 that is “ON” for a preset time, and the logical product of the time-delay operation signal 61 and the rotation speed sudden increase signal 65 Is provided, and the result is output as a timed revolution speed sudden increase signal 66.

As shown in FIG. 5, the time limit rotation speed sudden increase signal 66 is transmitted to the switching signal input terminal C of the switching device 23.
In this sense, the time limit rotation speed rapid increase signal 66 acts as a switching signal.

Next, the operation of the turbine control device 2 having such a configuration will be described with reference to the operation diagram shown in FIG.

As described in the previous embodiment, the logical product calculation of the turbine start signal 53 and the change rate detection signal 64 is performed by the change rate logical product calculator 25, and the rotational speed sudden increase signal 65 is obtained.
Is output.

On the other hand, the turbine starting signal 53 from the position detector 12 is also input to the time delaying device 21, and when the turbine starting signal 53 changes from "OFF" to "ON", that is, the steam stop valve 13 is turned on. When the valve opening is started, it is “ON” for a preset fixed time (between A and C in FIG. 6).
The time-delay operation signal 61 of 1 is output to the time-delay change rate AND calculator 26.

Then, the time change rate logical product operator 26 is
Both the time-delay operation signal 61 and the rotation speed sudden increase signal 65 are “O”.
When it is “N”, the time limit speed sudden increase signal 66 of “ON”
Is output to the switch 23 as a switching signal.

Therefore, when the actual turbine revolution speed rapidly increases (the revolution speed sudden increase signal 65 is “ON”) and it occurs within the time set by the time-delay actuator 21 from the start of the start (time-delay operation). When the signal 61 is “ON”, the time limit rotation speed rapid increase signal 66 is “ON”.

Even if the actual turbine revolution speed suddenly increases (the revolution speed sudden increase signal 65 is “ON”), but it does not occur within the time set by the time delay actuator 21 from the start of the start (time delay operation). One of the rotation speed sudden increase signal 65 or the time-delay operation signal 61 such that the signal 61 is “OFF”)
Is OFF, the time limit rotation speed sudden increase signal 66 of “OFF” is output.

As a result, when the timed rotation speed rapid increase signal 66 is satisfied, the switch 23 drives the steam control valve 14 in the valve closing direction to suppress the rapid increase in the actual turbine rotation speed. Select the valve full closing command 62 from
This is output to the low value selector 7 as the first rotation speed command 63.

When the timed revolution speed sudden increase signal 66 is not satisfied, the first revolution command 5 which is the original revolution command is issued.
5 is selected, and this is output to the low value selector 7 described above as the first rotation speed command 63.

As a result, the second rotation speed command 56 and the first rotation speed command 63 from the water supply control system 1 are input to the low value selector 7, and these low values are selected. And outputs it as a rotation speed command 57.

At this time, when the rotation speed sudden increase signal 65 is satisfied and the valve full-close command 62 from the signal generator 22 is selected by the switch 23, the first rotation speed command 63 is changed to the second rotation speed. Since it is set to be smaller than the command 56, the low value selector 7 selects the first rotation speed command 63.

When the rotation speed sudden increase signal 65 is not established, the switch 23 selects and outputs the first rotation speed command 55, so that the low value selector 7 outputs the first rotation speed command 55. Based on the first rotation speed command 63 and the second rotation speed command 56
And the low value command is output.

The rotation speed command 57 thus selected
And the turbine actual rotation speed signal 58 from the rotation speed detector 17 are input to the adder 8, and the deviation between them is added to the rotation speed deviation signal 5
9 is output to the coefficient unit 9.

The coefficient unit 9 amplifies the rotational speed deviation signal 59 with an optimum amplification degree for controlling the rotational speed of the turbine 16 and outputs the steam control valve opening command 60 as a steam control valve operating unit 1.
Output to 0.

When the rotation speed sudden increase signal 65 is established, the rotation speed command 5 output from the low value selector 7 is output.
7 is a command based on the valve full-close command 62 that does not change with time from the signal generator 22. Since the rotation speed command 57 is set smaller than the turbine actual rotation speed signal 58, the polarity of the rotation speed deviation signal 59 is shown. Is a steam control valve opening command 60 that is negative and does not change over time (steam control valve opening command 60 between AB in FIG. 6).

On the other hand, when the rotation speed sudden increase signal 65 is not established, the change rate setting unit 6 is set to perform the original control.
The rotational speed deviation signal 5 depending on the magnitude of the rotational speed command 57 and the actual turbine rotational speed 58 based on the first rotational speed command 55 from
The polarity of 9 changes and its value also changes.

When the polarity of the steam control valve opening degree command 60 is positive, the steam control valve operating device 10 drives the steam control valve 14 in the valve opening direction at a valve opening speed corresponding to the magnitude thereof, and the polarity is negative. Occasionally, the steam control valve 14 has a valve closing speed according to its size.
Is driven in the valve closing direction.

As described above, when the actual turbine speed rapidly increases immediately after starting, the polarity of the steam control valve opening command 60 becomes negative, and the steam control valve 14 is forcibly driven in the valve closing direction, resulting in an excessive value. It becomes possible to suppress the steam from flowing into the turbine 16.

The success or failure of the revolution speed sudden increase signal 65 is judged only by the actual turbine revolution speed, and the signal generator 22
To the valve full closing command 6 corresponding to the full closing command of the steam control valve 14
Since 2 is output, regardless of the second rotation speed command 56 based on the water supply amount from the water supply pump 18 having a characteristic that the water supply amount does not start until the turbine 16 becomes tens% or more of the rated rotation speed. Instead, the rotation speed of the turbine 16 can be appropriately controlled.

Since such a rotation speed control can suppress a significant increase in the turbine actual rotation speed, fluctuations of the rotation speed can be suppressed, and the target rotation speed can be settled in a short time.

In particular, by limiting such control within a predetermined time (time measured by the time-delay actuator 21) after starting such control, the steam condition flowing into the turbine 16 is bad and the rotation speed condition is satisfied. Even if the rotation speed does not increase, it is possible to prevent the steam control valve 14 from being fully closed, and reliability is improved.

Next, a fourth embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 7 is a partial configuration diagram of the turbine control device according to the present embodiment, and illustrates a part different from the conventional configuration of FIG.

That is, a signal generator 27, a switching unit 23, and a change rate judging means 20 are provided between the coefficient unit 9 and the steam control valve operating unit 10 shown in FIG. The signal from the generator 27 is switched according to the conditions described later and input to the steam control valve operating device 10.

In the above-described third embodiment, in order to suppress a rapid increase in the actual turbine rotational speed within the time specified by the time-delaying actuator 21 immediately after startup, the rate of change of the actual turbine rotational speed is set. Is greater than a preset change rate, the steam from the signal generator 22 is given priority over the first rotation speed command from the change rate setting unit 6 corresponding to the full closing command of the steam control valve 14. The steam control valve opening degree command 60 is output and controlled based on the valve full closing command 62 corresponding to the full closing command of the control valve 14.

However, the present invention is not limited to this, and the output of the steam control valve opening degree command 60 is performed in the same manner as in the conventional case, but when the above-mentioned rapid increase in the actual turbine rotational speed occurs. As shown in FIG. 7, such control may be performed by inputting a signal from a signal generator 27, which will be described later, to the steam control valve operating unit 10 instead of the steam control valve opening command 60.

Therefore, in the turbine control device 2, the signal generator 27 for generating the valve full-close command 67 for the steam control valve 14 and the switch 23 for switching the output signal according to the switching signal input to the terminal C. A change rate determination means 20 for detecting whether or not the change rate of the actual turbine rotational speed is greater than a preset change rate within a predetermined time is additionally provided to the conventional configuration.

The rate-of-change determining means 20 detects whether the rate of change of the actual turbine rotational speed is larger than a preset rate of change, as in the case of the third embodiment. Change rate detector 2 for outputting as change rate detection signal 64
4. A change rate AND calculator 25 that calculates the logical product of the change rate detection signal 64 and the turbine start signal 53 and outputs this as the revolution speed sudden increase signal 65, the turbine start signal 53
Is established as the timing of timing, and the time-delay actuator 21 that outputs the time-delay operation signal 61 that is “ON” for a preset time, and the logical product of the time-delay operation signal 61 and the rotation speed sudden increase signal 65 is calculated. Result 66
And a time-delay change rate logical product operator 26 for outputting

Further, the switch 23 and the change rate judging means 20
The operation of the signal generator 2 is the same as that of the third embodiment.
7 is the same as the configuration according to the second embodiment.

The steam control valve opening command 60 from the coefficient unit 9 and the valve full closing command 67 from the signal generator 27 are input to the switching unit 23, and the rotation speed sudden increase signal 65 from the change rate judging unit 20 is input. Either of them is output as the steam control valve opening degree command 72.

Therefore, as can be seen from the operation diagram shown in FIG. 8, the actual turbine speed rapidly increases and the rate of change of the actual turbine speed signal 58 becomes greater than the rate of change set in the rate detector 24. , And from the time delay device 21 "O
Between A and B in which the time delay operation signal 61 of “N” is output, according to the conventional control, the control is performed by the steam control valve opening degree command 60 which is monotonous and gradually decreases, whereas in the present embodiment. According to the embodiment, this section is controlled by the steam control valve opening degree command 72 based on the valve full closing command 67 from the signal generator 27.

As described above, when the actual turbine speed rapidly increases immediately after starting, the steam control valve 14 is forcibly driven in the valve closing direction to easily suppress excessive steam from flowing into the turbine 16. It becomes possible to do.

The success or failure of the revolution speed sudden increase signal 65 is determined only by the actual turbine revolution speed, and the signal generator 27
Since the valve full-close command 72 is output from, even if the water supply amount actually starts due to the characteristics of the water supply pump 18 even when the turbine 16 reaches several tens% of the rated speed, Regardless of the characteristics of the water supply pump 18, the rotation speed of the turbine 16 can be appropriately controlled, and fluctuations of the rotation speed can be suppressed, so that the target rotation speed can be settled in a short time.

In particular, by limiting the control within a predetermined time (the time measured by the time-delay actuator 21) after starting such control, the steam condition flowing into the turbine 16 is deteriorated.
Even if the rotation speed does not increase before the rotation speed condition is satisfied, it is possible to prevent the steam control valve 14 from being fully closed, and reliability is improved.

Further, since the signal generator 27 outputs the valve full closing command 67 corresponding to the steam control valve opening command 60, what kind of processing is performed by the low value selector 7, the adder 8 and the coefficient unit 9. There is an advantage that the design of the signal generator 27 can be facilitated without having to consider whether the signal generator 27 is used.

<Fifth Embodiment> Next, a fifth embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 9 is a partial block diagram of the turbine control device according to the present embodiment, and shows a portion different from the conventional configuration of FIG.

That is, the rate-of-change setting device 6 shown in FIG. 16 is changed to a rate-of-change setting device 19, and a signal generator 22, a switching device 23, and a switching device 23 are provided between the rate-of-change setting device 19 and the low value selector 7.
The change rate determination means 20 is provided.

In each of the embodiments described so far, when a rapid increase in the actual turbine rotational speed is detected immediately after startup, the steam control valve 14 is opened in the valve closing direction based on the valve full closing command 62 from the signal generator 22 or the like. When the turbine actual rotation speed is suppressed from being suddenly increased by driving the engine, and the sudden increase in the turbine actual rotation speed is not detected, the control is returned to the conventional control.

However, since there is a large difference between the actual turbine speed when the sudden increase in the actual turbine speed is no longer detected and the rotational speed command 57 based on the rotational speed setting command 54, an addition is made. The steam control valve opening command 60 from the device 8 may be accompanied by a large change, and the fluctuation of the rotation speed may not be sufficiently suppressed.

Therefore, in this embodiment, the fluctuation of the rotational speed can be suppressed more sufficiently.

Therefore, in the turbine control device 2, a plurality of signal generators 22 for generating a valve full-close command 62 corresponding to the full-close command for the steam control valve 14 and a plurality of switching signals input to the terminal C are used. Switch 23 that outputs one of the input signals, and the rate of change of the rotation speed is set based on the one input signal of the plurality of input signals according to the setting condition signal input to terminal B ′. Change rate setting device 19, which determines whether or not the change rate of the actual turbine rotational speed is greater than a preset change rate, and a change rate determining means 20 which outputs the determination result as a rotational speed sudden increase signal 65. Is added to the conventional configuration.

The rotation speed sudden increase signal 65 from the change rate judging means 20 is input to the terminal C of the switch 23 to act as a switch signal, and is also input to the terminal B'of the change rate setter 19. It works as a setting condition signal.

The change rate judging means 20, the signal generator 22, and the switch 23 have the same structure as described in the first embodiment and the like, but the change rate setter 19 is the conventional change rate setter 6. The difference is that the configuration is different from.

That is, the turbine actual rotation speed signal 58 and the rotation speed setting command 54 are input to the change rate setting device 19, and the turbine actual rotation speed signal is maintained while the rotation speed sudden increase signal 65 is "ON". The signal following 58 is used as the first rotation speed command 6
When the rotation speed sudden increase signal 65 is turned “OFF”, the first change is made at the change rate set in the change rate setting device 19 with the value of the rotation speed setting command 54 as the target. A rotation speed command 68 is output.

Next, the operation of the turbine control device 2 having such a configuration will be described with reference to the operation diagram shown in FIG.

When the revolution speed sudden increase signal 65 from the change rate judging means 20 is turned "ON", the change rate setter 19 follows the first turbine speed command 68 following the turbine actual speed signal 58.
Is output, but at this time, the switching unit 23 operates the signal generator 2
The valve full closing command 62 is selected from 2 and output.

However, while the rotation speed rapid increase signal 65 is "ON", the first rotation speed command 68 from the change rate setting device 19 is not output to the low value selector 7, but this Even in this case, the value of the first rotation speed command 68 is changing (see the chain double-dashed line between AB in FIG. 10).

Then, the rotation speed sudden increase signal 65 becomes "OF
When it becomes “F”, the switching unit 23 outputs the first rotation speed command 68 from the change rate setting unit 19 to the low value selector 7.

Therefore, the rotation speed sudden increase signal 65 becomes "OF".
As the first rotation speed command 68 immediately after "F", the first rotation speed command 68 that changes from the actual turbine rotation speed at that time to the target value of the rotation speed setting command 54 is output.

As described above, when the actual turbine rotational speed suddenly increases immediately after starting, the steam control valve 14 is forcibly driven in the valve closing direction to easily prevent excessive steam from flowing into the turbine 16. It becomes possible to do.

The success or failure of the revolution speed sudden increase signal 65 is determined only by the actual turbine revolution speed, and the signal generator 27
Since the valve full-close command 72 is output from, even if the water supply amount actually starts due to the characteristics of the water supply pump 18 even when the turbine 16 reaches several tens% of the rated speed, The rotation speed of the turbine 16 can be appropriately controlled regardless of the characteristics of the water supply pump 18.

Especially, the rotation speed sudden increase signal 65 is "OFF".
The first rotation speed command 68 immediately after is output is the first rotation speed command 68 that changes from the actual turbine rotation speed at that time to the value of the rotation speed setting command 54 as a target. It is possible to suppress fluctuations in the actual turbine rotation speed immediately after is turned off.

Next, a sixth embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 11 is a partial block diagram of the turbine control device according to the present embodiment, and shows a part different from the conventional structure of FIG.

That is, the change rate setting device 6 shown in FIG. 16 is replaced with a change rate setting device 19, and a signal generator 22, a switching device 23, and a switch 23 are provided between the change rate setting device 19 and the low value selector 7.
The change rate determination means 20 is provided.

The invention according to the present embodiment is different from the invention according to the fifth embodiment in that the time delay device 21 is provided as in the invention according to the second embodiment, and the invention is started. The control for fully closing the steam control valve 14 is performed only within a predetermined time.

Therefore, in the turbine control device 2, a plurality of signal generators 22 for generating the valve full-close command 62 corresponding to the full-close command for the steam control valve 14 and a plurality of switching signals input to the terminal C are used. Switch 23 that outputs one of the input signals, and the rate of change of the rotation speed is set based on the one input signal of the plurality of input signals according to the setting condition signal input to terminal B ′. A rate-of-change setting device 19 and a rate-of-change determining means 20 for determining whether or not the rate of change of the actual turbine speed within a predetermined time is greater than a preset rate of change and outputting the change rate determination means 20 are added to the conventional configuration. Has been done.

The rate-of-change judging means 20, the signal generator 22, the switch 23, and the rate-of-change setting device 19 have the same configurations as those described in the third embodiment and the like, but the time-delay operation device 21 is used.
A timed rotation speed rapid increase signal 66 indicating the result of the logical product operation of the time delay operation signal 61 from the change rate determination means 20 and the rotation speed rapid increase signal 65 from the change rate determination means 20 is input to the terminal C of the switch 23 to act as a switching signal. In addition, it is different in that it is input to the terminal B ′ of the change rate setting device 19 and acts as a setting condition signal.

The turbine control device 2 having such a configuration is
As can be seen from the operation diagram shown in FIG. 12, the time delay device 21
Only when the timed operation signal 61 from is ON (between A and C in FIG. 12), the signal generator 22 performs control based on the valve full-close command 62 to change the actual turbine speed. The sudden rise is suppressed (between A and B in FIG. 12).

Therefore, for example, when the rate of change of the actual turbine rotational speed is detected as a rapid increase by the rate-of-change judging means 20 because the condition of the steam flowing into the turbine 16 is bad, the last minute state continues for a long time. Is the timed operation signal 6
By performing the fully closing control of the steam control valve 14 on condition that 1 is “ON”, it becomes possible to settle at the target rotation speed in a short time.

Further, the time limit rotation speed sudden increase signal 66 indicates "OF
When it becomes “F”, the first rotation speed command 68 is changed from the actual turbine rotation speed at that time to the target value of the rotation speed setting command 54.
Is output to the low value selector 7 as the first rotation speed command 63 (between B and D in FIG. 12), the time limit rotation speed sudden increase signal 66 is output.
It becomes possible to suppress the fluctuation of the actual turbine rotational speed after the switch is turned "OFF".

Next, a seventh embodiment of the present invention will be described with reference to the drawings. The same components as those in the above-described embodiment are designated by the same reference numerals and description thereof will be omitted as appropriate.

FIG. 13 is a partial block diagram of the turbine control device according to the present embodiment, and shows a portion different from the conventional configuration of FIG.

That is, a differentiator 29, a coefficient unit (KD) 30, and an adder 31 are provided in front of the low value selector 7 shown in FIG.
First rotation speed command 55 from coefficient of change setting device 6 and coefficient device 30
The subtraction value signal 73 from is added and input to the low value selector 7.

In each of the above-described embodiments, when the rate of change of the actual turbine rotation speed becomes larger than the preset rate of change, the steam control valve 62 is issued based on the valve full-close command 62 from the signal generator 22. It controlled so that 14 might be closed completely.

On the other hand, in the present embodiment, a value corresponding to the rate of change of the actual turbine revolution speed is calculated, and this value is calculated as the first value.
By reducing from the rotation speed command 55, a sudden increase in the actual turbine rotation speed is suppressed.

Therefore, in the turbine control device 2, the differentiator 29 that outputs a signal proportional to the rate of change of the actual turbine speed, the coefficient unit 30 that multiplies the input signal by a predetermined proportional constant, and the adder 31 and 31 are added to the conventional configuration.

Next, the operation of the turbine control device 2 having such a configuration will be described with reference to the operation diagram shown in FIG.

In the differentiator 29, the turbine actual rotation speed signal 58
Is input and the rate of change is output. Therefore, when the actual turbine rotational speed rapidly increases, the rate of change has a large value, and when the actual turbine rotational speed changes slowly, the rate of change has a small value.

The rate of change of the actual turbine speed signal 58 is input to the coefficient unit 30, multiplied by a preset proportional constant, and output to the adder 31 as a subtraction value signal 73.

The change rate setting unit 6 is added by the adder 31.
From the above, the deviation from the first rotation speed command 55 is calculated, and the result is output to the low value selector 7.

It is needless to say that the coefficient unit 30 is set so that the value subtracted by the adder 31 becomes substantially zero when the rate of change of the actual turbine rotational speed is small.

As described above, when the rapid increase rate of the turbine actual rotation speed is large, a large value is subtracted from the first rotation speed command 55, and the rotation speed obtained through the low value selector 7 and the adder 8 is increased. The number deviation signal 59 has a small value as shown in FIG. 14, and the steam control valve 14 can be suddenly closed.

In particular, as described above, when the steam control valve 14 is fully closed based on the valve full-close command 62 from the signal generator 22 when a rapid increase in the actual turbine rotational speed is detected, Although the sudden valve closing operation of the steam control valve 14 is performed, in the case of the present invention, as shown in FIG. 14, the rotation speed deviation signal 59 input to the coefficient unit 9 continuously changes, so that the actual turbine rotation speed is Even in the case of a sudden rise, the steam control valve 14 is continuously closed suddenly (see FIG. 14).
Between A and B), there is an advantage that the load fluctuation applied to the steam control valve 14 can be reduced.

Further, when the steam control valve 14 is fully closed based on the valve full-closing command 62 from the signal generator 22 when a rapid increase in the turbine actual rotation speed is detected, at least the turbine actual rotation speed suddenly increases. However, in the case of the present invention, such a sudden increase in the actual turbine rotational speed is essentially suppressed, so that the reliability can be further improved.

In the above description, the adder 31 is provided before the low value selector 7 so that the deviation between the first rotation speed command 55 and the subtraction value signal 73 is input to the low value selector 7. However, the present invention is not limited to this, and as shown in FIG. 15, the subtraction value signal 73 is input to the adder 8 so that the subtraction value signal 73 is subtracted from the output from the low value selector 7. May be.

In this case, since it is not necessary to additionally provide the adder 31, there is an advantage that the number of parts can be reduced.

[0165]

As described above, according to the present invention,
It detects that the steam stop valve is open based on the turbine start signal that indicates the open / close state of the steam stop valve, and the rate of change of the rotational speed is greater than the preset value based on the turbine actual rotational speed signal. When it is detected that the change rate determination means that outputs a signal indicating that as a switching signal, a signal generator that generates a valve full closing command to drive the steam control valve in the valve full closing direction, When the switching signal is input and at least the valve full closing command is input, and when the switching signal is satisfied, the valve full closing command is output, and the steam control valve actuator operates the steam stop valve based on the valve full closing command. Since a switching device that drives the valve to close is provided, when the rotation speed immediately after startup sharply increases, the steam control valve is rapidly operated in the valve closing direction to prevent excessive steam from flowing into the turbine, Turbulence of actual turbine speed Ete short time will be able to settle to the target rotational speed.

[Brief description of drawings]

FIG. 1 is a diagram showing a portion different from a conventional configuration of a turbine control device applied to the description of a first embodiment.

FIG. 2 is an operation diagram of the turbine control device shown in FIG.

FIG. 3 is a diagram showing a part different from the conventional configuration of the turbine control device applied to the description of the second embodiment.

FIG. 4 is an operation diagram of the turbine control device shown in FIG. 3.

FIG. 5 is a diagram showing a part different from the conventional configuration of the turbine control device applied to the description of the third embodiment.

FIG. 6 is an operation diagram of the turbine control device shown in FIG.

FIG. 7 is a diagram showing a part different from the conventional configuration of the turbine control device applied to the description of the fourth embodiment.

FIG. 8 is an operation diagram of the turbine control device shown in FIG. 7.

FIG. 9 is a diagram showing a part different from the conventional configuration of the turbine control device applied to the description of the fifth embodiment.

FIG. 10 is an operation diagram of the turbine control device shown in FIG. 9.

FIG. 11 is a diagram showing a part different from the conventional configuration of the turbine control device applied to the description of the sixth embodiment.

FIG. 12 is an operation diagram of the turbine control device shown in FIG. 11.

FIG. 13 is a diagram showing a portion different from the conventional configuration of the turbine control device applied to the description of the seventh embodiment.

FIG. 14 is an operation diagram of the turbine control device shown in FIG. 13.

FIG. 15 is a diagram showing a portion different from the conventional configuration of the turbine control device having a configuration alternative to FIG.

FIG. 16 is a diagram showing a configuration of a turbine control device applied to a description of a conventional technique.

[Explanation of symbols]

1 Water supply control system 2 turbine control device 5,23 switch 6 Change rate setting device 7 Low value selector 8,31 adder 9,30 coefficient unit 10 Steam control valve actuator 12 Position detector 13 Steam stop valve 14 Steam control valve 16 turbine 17 rpm detector 18 Water pump 19 Change rate setting device 20 Change rate judgment means 21 Time limit actuator 22,27 Signal generator 24 Change rate detector 25 Change rate logical product calculator 26 Time-Delay Change Rate AND Operation Unit 29 Differentiator 35 Rotation speed setting means 36 Low price selection means

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Hideki Yugami             No. 1 Toshiba-cho, Fuchu-shi, Tokyo Toshiba Corporation             Fuchu Office F-term (reference) 3G071 AA02 AB02 AB06 BA02 CA01                       DA05 EA02 FA02 GA04 HA01                       HA04 JA02

Claims (8)

[Claims] 1. A steam stop valve provided upstream of the steam control valve with the steam control valve opened is suddenly opened by a steam control valve operating device to allow steam to flow into a turbine connected to a water supply pump. When starting the water supply by starting the turbine by doing so that the turbine to its target speed based on the speed setting command set to a rotation speed higher than the rated rotation speed of the turbine, A rotation speed setting unit that sets a change rate of the rotation speed, sets the rotation speed based on the change rate, and outputs the rotation speed as a first rotation speed command, and the first rotation speed command is input and water is supplied by the water supply pump. The second rotation speed command indicating the rotation speed corresponding to the supplied water amount is input, and low speed selection means for selecting these low values and outputting them as a rotation speed command is input. With the actual rotation of the turbine The turbine actual rotation speed signal indicating the number is input, and these deviations are amplified with an optimum amplification degree for rotation speed control, and a valve opening command generation means for outputting this as a steam control valve opening command is provided. In the turbine control device that controls the rotation speed of the turbine so that a predetermined amount of water is supplied, the steam stop valve is opened based on a turbine start signal indicating an open / closed state of the steam stop valve. Detect that, and
When it is detected that the rate of change of the number of revolutions is greater than a preset value based on the turbine actual number of revolutions signal, a rate of change determination means for outputting a signal indicating that as a switching signal, A signal generator that generates a valve full-close command for driving the steam control valve in the valve fully-closed direction, and at least the valve full-close command is input when the switching signal is input and the switching signal is satisfied. A turbine control device comprising: a switch that outputs the valve full-close command and causes the steam control valve operating device to drive the steam stop valve to close the valve based on the valve full-close command. 2. The rotation speed setting means inputs the rotation speed setting command, the turbine actual rotation speed signal and the switching signal, and follows the turbine actual rotation speed signal when the switching signal is satisfied. Is output as the first rotation speed command, and when the switching signal does not hold,
A change rate setting device for outputting the first rotation speed command, in which a change rate is set so that the output changes from the first rotation speed command output at that time to the rotation speed setting command as a target, is provided. The turbine control device according to claim 1, wherein: 3. The valve full closing command when the first rotation speed command and the valve full closing command are input to the switching device, and the switching signal is input and the switching signal is satisfied. 3. The turbine control according to claim 1, wherein the low speed selecting means outputs the first rotation speed command to the low value selecting means when the switching signal is not satisfied. apparatus. 4. The switch is input with the steam control valve opening degree command and the valve full closing command, and when the switching signal is input and the switching signal is satisfied, the valve full closing is performed. A command is output to said steam control valve operating device, and when said switching signal is not established, said steam control valve opening command is output to said steam control valve operating device.
The described turbine control device. 5. The change rate determination means detects whether or not the change rate of the rotation speed is greater than a preset value based on the turbine actual rotation speed signal, and uses the result as a change rate detection signal. A rate-of-change detector that outputs, and performs a logical product operation of the turbine start signal and the rate-of-change detection signal, the steam stop valve is in an open state, and the rate of change of the rotational speed is a preset value. The turbine control according to any one of claims 1 to 4, further comprising: a change rate logical product calculator that outputs a rotation speed sudden increase signal indicating the change as the switching signal when it becomes larger. apparatus. 6. The change rate determination means detects whether or not the change rate of the rotation speed is greater than a preset value based on the turbine actual rotation speed signal, and uses the result as a change rate detection signal. A rate-of-change detector that outputs, and performs a logical product operation of the turbine start signal and the rate-of-change detection signal, the steam stop valve is in an open state, and the rate of change of the rotational speed is a preset value. When it becomes larger, a rate-of-change AND operator that outputs a rotation speed sudden increase signal indicating that, and when it is detected that the steam stop valve is opened based on the turbine start signal, From that time, a time-delay operation device that outputs a time-delay operation signal of a predetermined level for a preset time and a logical product operation of the time-delay operation signal and the rotation speed sudden increase signal are performed, and the time-delay operation device is set. In time, said When the steam stop valve is in the open state and the rate of change of the number of revolutions is larger than a preset value, a time-varying rate-of-change logical product calculator that outputs a signal indicating this as the switching signal 5. The method according to claim 1, further comprising:
The turbine control device according to item 1. 7. A steam stop valve provided upstream of the steam control valve with the steam control valve opened is suddenly opened by a steam control valve operating device to allow steam to flow into a turbine connected to a water supply pump. When starting the water supply by starting the turbine by doing so that the turbine to its target speed based on the speed setting command set to a rotation speed higher than the rated rotation speed of the turbine, A rotation speed setting unit that sets a change rate of the rotation speed, sets the rotation speed based on the change rate, and outputs the rotation speed as a first rotation speed command, and the first rotation speed command is input and water is supplied by the water supply pump. Low value selecting means for inputting a second rotation speed command indicating the supplied water amount, selecting these low values and outputting them as a rotation speed command,
The turbine speed signal indicating the actual rotation speed of the turbine is input together with the rotation speed command, and these deviations are amplified with an optimum amplification degree for controlling the rotation speed. A turbine control device having a valve opening command generation means for outputting as an opening command and controlling the rotational speed of the turbine so that a predetermined amount of water is supplied, wherein the rate of change of the turbine actual rotational speed signal is detected. A differentiator, a coefficient unit that multiplies the rate of change detected by the differentiator by a predetermined proportional constant and outputs the subtracted value signal, and when the first rotation speed command is input to the low value selecting means, A turbine control device comprising: an adder for subtracting the subtraction value signal from the first rotation speed command and inputting the subtraction value signal. 8. A steam control valve provided upstream of the steam control valve with the steam control valve opened is suddenly opened by a steam control valve operating device to allow steam to flow into a turbine connected to a water supply pump. When starting the water supply by starting the turbine by doing so that the turbine to its target speed based on the speed setting command set to a rotation speed higher than the rated rotation speed of the turbine, A rotation speed setting unit that sets a change rate of the rotation speed, sets the rotation speed based on the change rate, and outputs the rotation speed as a first rotation speed command, and the first rotation speed command is input and water is supplied by the water supply pump. Low value selecting means for inputting a second rotation speed command indicating the supplied water amount, selecting these low values and outputting them as a rotation speed command,
The turbine speed command indicating the actual turbine speed is input together with the turbine actual speed signal, and an adder for calculating these deviations and a deviation signal from the adder are optimal for controlling the speed. Of the turbine opening speed so that a predetermined amount of water can be supplied. In a turbine control device for controlling the above, a differentiator for detecting a rate of change of the turbine actual rotation speed signal, and a rate of change detected by the differentiator are multiplied by a predetermined proportional constant and output as a subtraction value signal to the adder. A turbine control device comprising: a coefficient unit.