JPH0988507A - Control method of turbine for water supply pump and controller thereof - Google Patents

Abstract

PROBLEM TO BE SOLVED: To move a degree of opening of a steam governing valve to a proper position speedily when a turbine drive steam source is changed over and enable stable control when water supply is controlled usually. SOLUTION: In a circuit which consists of a subtractor 31 which operates a command of the number of revolutions of a turbine for water supply pump and a deviation signal of the number of revolutions of the turbine and a proportional integration computing unit 32 which outputs a command for degree of opening of a steam governing valve based on the deviation signal, a compensation circuit consisting of a deviation large detector 33, a generator 34 of compensation amount of the steam governing valve, and an adder 35 is provided to add a compensation signal to the steam governing valve when a turbine drive steam source is changed over and control deviation is large.

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 a water feed pump of a thermal power plant, and more particularly to a control system when a control deviation is large.

[0002]

2. Description of the Related Art A turbine controller for a feed water pump inputs a turbine rotation speed command for the feed water pump from the feed water controller, performs a proportional integral calculation based on a deviation from an actual turbine rotation speed, and uses this result to adjust a steam control valve. It is operated to adjust the drive steam of the water supply pump turbine and control the rotation speed of the water supply pump turbine.

There are two types of drive steam for a feed water pump turbine: high-pressure steam and low-pressure steam. The low-pressure steam includes steam extracted from the steam flowing into the steam turbine for power generation (hereinafter abbreviated as extracted steam) and auxiliary steam from auxiliary boilers and other power generation boilers (hereinafter abbreviated as auxiliary steam). One of these two types of steam is switched and used.

That is, at the time of starting the plant until the steam turbine for power generation reaches a constant power output of the generator, the extracted steam cannot supply stable driving steam to the turbine for the feedwater pump, so that auxiliary steam is used to generate power. Extracted steam is used during normal operation after the steam turbine reaches a certain generator output. In addition, auxiliary steam is used when the output drops below a certain level, such as when the plant is stopped.

On the other hand, the high-pressure steam is used as a backup until the low-pressure steam is switched from the extracted steam of the steam turbine for power generation to the auxiliary steam. That is, when the steam flowing into the power generating steam turbine is shut off due to an accident in the electric system during the operation of the power generating steam turbine, the extracted steam of the power generating steam turbine cannot be supplied.

The high-pressure steam and the low-pressure steam are guided to the high-pressure steam control valve and the low-pressure steam control valve, respectively, and are supplied to the feed pump turbine. In the preceding stage of the low-pressure steam system, a steam main valve is installed in the extraction steam line from the power generation steam turbine and the auxiliary steam line from the boiler, and one of the main valves is opened to supply steam. A pressure adjusting valve is installed in the auxiliary steam line, and the pressure is adjusted to the same level as the extracted steam of the steam turbine for power generation used for normal operation.

The high-pressure steam control valve and the low-pressure steam control valve are controlled by the turbine control unit for the feed water pump via one operating end. First, the low-pressure steam control valve is opened, and then the low-pressure steam control valve is fully opened. The mechanism is such that the regulator valve opens.

In such a feed water turbine control device, as described in Japanese Patent Application Laid-Open No. 59-29704, a plurality of driving steams and respective control valves for controlling the driving steams are optimized. A proportional-integral operation circuit is installed and controlled by switching.

[0009]

As described above, in the conventional low pressure steam auxiliary steam line, in order to make the pressure equivalent to the extracted steam of the steam turbine for power generation used during normal operation, a pressure regulating valve is provided. It was installed.

By the way, the low-pressure steam control valve, which is the operation end of the turbine controller for the feed water pump to which the low-pressure steam is finally introduced, has a role of pressure adjustment, and the pressure adjustment valve of the auxiliary steam line may be omitted. it can. In this case, since the pressure of the auxiliary steam whose pressure is not adjusted is higher than that of the extracted steam, the turbine speed changes when the steam source is switched. Similar fluctuations in turbine speed also occur during backup with high-pressure steam and during sudden load reduction due to boiler auxiliary equipment failure.

In this case, in the turbine controller for the water supply pump, the control gain of the proportional-plus-integral calculation is increased,
Although the steam control valve can be quickly moved to an appropriate opening, on the other hand, the stability of water supply control during normal operation due to high gain is lacking. In addition, installing a proportional-plus-integral arithmetic circuit that is optimal for operating conditions, as in the past, not only complicates the configuration of the control device but also discontinues the amount of operation when switching the circuit, which is bumpless. It becomes difficult to control.

An object of the present invention is to provide a method for controlling a turbine for a water supply pump, which suppresses fluctuations in the rotational speed of the water supply pump turbine when switching the steam source, etc. and does not impair the stability of the water supply pump during normal operation. To provide.

An object of the present invention is to realize the above-mentioned control method by one control arithmetic circuit, maintain the continuity of control,
It is to provide a highly stable turbine control device for a water supply pump in bumpless.

[0014]

SUMMARY OF THE INVENTION The above-mentioned object of the present invention is to determine a manipulated variable by a proportional-plus-integral calculation based on a deviation between a turbine rotation speed command for a water supply pump from a water supply control device and an actual turbine rotation speed, and to supply a water supply pump. In the method of controlling the operating end for operating the control valve of the drive steam system of the steam turbine, in the method of controlling the rotation speed of the feedwater pump turbine in the thermal power plant, when the predetermined signal deviation exceeds a predetermined deviation range, This is achieved by adding the correction amount proportionally calculated with a gain higher than the control gain of the proportional-plus-integral calculation to correct the operation amount.

The signal deviation is the deviation between the turbine rotational speed command for the feed water pump and the actual turbine rotational speed, or
It is characterized in that it is the deviation between the boiler feed water pressure and the turbine driven feed water pump outlet pressure.

The deviation range is such that the signal deviation during normal operation is within that range, and the signal deviation during switching of the driving steam system or during sudden load reduction is set to exceed that range. And

Further, the control system of the turbine for the water supply pump to which the present invention is applied operates the steam control valve for adjusting the low pressure steam to be used by switching the two systems of the extraction steam from the steam turbine for power generation and the auxiliary steam. In the one provided with a proportional-integral calculation means for calculating the operation amount of the operating end from the difference between the end and the turbine rotation speed command for the water supply pump from the boiler water supply control device and the actual turbine rotation speed, the predetermined signal deviation becomes large. This can sometimes be realized by providing a correction calculation means for proportionally calculating the correction amount of the operating end in parallel with the proportional integration calculation means.

[0018]

[Operation] Since the deviation between the turbine rotational speed command for the water supply pump and the actual turbine rotational speed during normal operation is not large,
Stable control with low gain is possible. However, when the drive steam is switched, the turbine speed changes greatly due to the pressure change of the drive steam, so the deviation between the turbine speed command for the feed water pump and the actual turbine speed becomes large, and the low gain control circuit Therefore, the steam control valve cannot be quickly moved to an appropriate opening.

According to the configuration of the present invention, since the correction calculating means does not respond to a change in the feedwater turbine turbine speed command during normal operation, the steam control valve of the low gain proportional-integral calculation is used. Enables stable control.

On the other hand, when the drive steam is switched, the deviation between the rotation speed command and the actual turbine rotation speed becomes large and exceeds the control range during normal operation, making it difficult to follow up by the proportional-plus-integral arithmetic circuit. At this time, the operation end correction signal is added by the correction arithmetic circuit, the operation amount of the operation end increases rapidly while maintaining continuity, and the steam control valve is quickly adjusted to an appropriate opening degree. The fluctuation of the rotation speed is suppressed.

The operation / non-operation of the correction arithmetic circuit depends only on the signal deviation range, and since the correction amount is added to the normal proportional-integral calculation amount, the operation amount is controlled without step change. Continuity is maintained, and bumps provide highly stable control.

Further, the correction calculating means of the present invention may perform the correction based on the deviation between the boiler feed water pressure and the turbine drive feed water pump outlet pressure. That is, during normal operation with a small load change rate, the boiler feed water pressure and the turbine drive feed water pump outlet pressure operate similarly with respect to the plant load change, and their deviations are small, so no correction output occurs. On the other hand, when switching the driving steam, the steam turbine speed for the water supply pump fluctuates greatly due to changes in steam pressure,
Since the turbine drive feed water pump outlet pressure fluctuates in proportion to this, the operation end correction signal by the correction arithmetic circuit is added, the operation amount is rapidly increased, and fluctuations in the pump rotational speed are suppressed.

[0023]

The first embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 1 shows the configuration of a turbine controller for a water supply pump according to the first embodiment, which is applied to a boiler water supply system including a drive steam line for a turbine for a water supply pump.

A water supply pump 1 for supplying water to the boiler 14,
A water supply pump steam turbine 2 for driving the water supply pump 1,
A high pressure steam control valve 5 for adjusting drive steam to the steam turbine 2, a low pressure steam control valve 6, an actuator 4 for operating the steam control valves 5 and 6 via a mechanical lever mechanism 40,
Turbine rotation speed command 1 for water supply pump from water supply controller 9
00 and rotation speed detector 2 of steam turbine 2 for feed water pump
The turbine rotation speed 101 from 0 is input and the steam control valve opening command 106 is output to the actuator 4. The feed water pump turbine control unit 3, the power generation steam turbine extraction steam line 111 and the auxiliary steam line 112 are switched to switch to a low pressure. In order to supply to the steam control valve 6, it comprises steam main valves 11 and 12 installed in each steam line, and a water supply outlet valve 10 installed in a water supply outlet of the water supply pump 1. In the present embodiment, the pressure adjustment valve is not installed in the auxiliary steam line 112.

The actuator 4 and the mechanical lever mechanism 40
First, the low pressure steam control valve 6 is opened, and after the full opening, the high pressure steam control valve 5 is opened to form an operating end common to each drive steam.

The feed water turbine turbine control unit 3 according to this embodiment shows a control circuit for supplying water to the boiler, and calculates a deviation signal 102 between the feed water pump turbine rotation speed command 100 and the feed water pump steam turbine rotation speed 101. Subtractor 31, a proportional-plus-integral calculator 32 that outputs the steam control valve manipulated variable 103 by a proportional-plus-integral operation that receives the deviation signal 102, and a large deviation detector 33 that inputs the deviation signal 102 and outputs a large deviation signal 104 , The steam control valve correction amount generator 34 that calculates the steam control valve correction amount 105 from the large deviation signal 104, the steam control valve operation amount 103 and the steam control valve correction amount 105 are added, and the steam control valve opening command 106 is given to the actuator 4. It is composed of an adder 35 for outputting This large deviation detector 3
3. A correction arithmetic circuit is composed of the steam control valve correction amount generator 34 and the adder 35.

FIG. 2 is a characteristic diagram of the proportional-plus-integral calculator 32, and FIG.
Shows a characteristic diagram of a turbine correction arithmetic circuit. The proportional-plus-integral calculator 32 outputs the steam control valve opening degree (operation amount) 103 calculated with the control gain of the gradient α in response to the input deviation signal.

The large deviation detector 33 of the correction circuit is shown in FIG.
As shown in (a), the output is zero when the absolute value of the input deviation signal is within the set value ± a, and a large deviation signal proportional to the deviation signal exceeding the set value ± a is output one-to-one. To do. As shown in FIG. 3B, the steam control valve correction amount generator 34 uses a low-pressure steam control valve opening when the extracted steam of the power generation steam turbine is used as drive steam and when the auxiliary steam is used as drive steam. The maximum deviation amount ± b of the low-pressure steam control valve opening of is set as the upper and lower limit values, and the slope β (β>
A steam control valve opening correction amount 104 proportionally calculated by the control gain of α) is output.

By the way, the deviation signal 102 output from the subtractor 31 changes according to the rotation speed command 100 output from the water supply control unit 9 according to the load change of the plant. During normal water supply operation, the deviation signal 102 has a small value within the ± a region of FIG. 3, and the deviation large signal 10 from the deviation large detector 33 is shown.
4 becomes zero. Therefore, the steam control valve opening command 106 output to the actuator 4 outputs the output signal 103 by the low control gain α of the proportional-plus-integral calculator 32 as it is,
It is controlled without being affected by the correction circuit.

On the other hand, during the switching operation of the driving steam of the water feed pump steam turbine, the turbine rotation speed 101 of the water feed pump changes significantly due to changes in the steam pressures of the extraction steam and the auxiliary steam. At this time, since the deviation signal 102 output from the subtractor 31 exceeds the ± a region in FIG. 3, the large deviation detector 33 outputs the large deviation signal 104 proportional to the deviation signal 102 of ± a or more. Steam control valve correction amount generator 34
Outputs the steam control valve correction amount 106 by the high control gain β with respect to the input large deviation signal 104. And FIG.
As shown in (c), the steam control valve opening amount command 106 obtained by adding the steam control valve correction amount 106 and the output signal 103 of the proportional-plus-integral calculator 33 is output to the actuator 4.

As a result, the steam control valve 6 at the time of switching is
A large opening change amount that cannot be followed by the low-gain output of the proportional-plus-integral calculator 32 is quickly moved from the correction circuit by addition of the correction amount by the high control gain, and adjusted to an appropriate opening amount. At this time, since the operation amount before and after the correction does not change in steps and maintains continuity, bumpless control can be realized. Moreover, the influence of the correction circuit can be completely avoided during normal operation, and the stability of the feedwater pump turbine control system is ensured by the proportional-plus-integral calculation circuit of the control gain optimized during normal operation.

FIG. 6 shows the operating characteristics of the plant according to this embodiment in comparison with the conventional one. The solid line in the figure shows the characteristics of this embodiment, and the dotted line shows the characteristics of the conventional example.

When the steam turbine for power generation does not reach a constant power output of the generator (before the point A), the turbine 2 for water feed pump is driven by the low pressure steam from the auxiliary steam line 112, and the extraction steam line Since the steam pressure is higher than the extracted steam from 111, the opening degree of the low pressure steam control valve 6 is controlled to a low position.

Here, the driving steam is switched from the auxiliary steam to the extraction steam. That is, when the main valve 11 of the extraction steam line 111 is opened and the main valve 12 of the auxiliary steam line 112 is closed, the driving steam pressure decreases, and therefore the turbine speed also becomes A.
Point ⇒ It decreases like point B. Conventionally, the proportional-plus-integral calculator 3
Since the output is made only by 2, the proportional-plus-integral calculator 32 is applied to the deviation between the rotation speed command from the water supply controller 9 and the actual rotation speed command.
The opening of the low-pressure steam control valve 6 is gradually increased by the output of a low control gain from, but the turbine deviation for the feedwater pump further decreases during this period, so the control deviation is within a predetermined range (±
Since it increased more than point a) (point B ⇒) and increased as shown in the figure (point C ⇒), it took a long time to establish a stable rotation speed.

However, in the present embodiment, when the control deviation increases and exceeds the predetermined range (+ a) at point B, the correction circuit operates and the opening of the low pressure steam control valve 6 is rapidly increased with the output of the high control gain. Ascend (point B ⇒ point C). Along with this, the turbine speed also rises, and the control deviation is again in the predetermined range (+ a) at point C.
Converges to The correction circuit becomes inoperative, and the control again shifts to the control by the proportional-plus-integral calculator 32 only.

When the generator steam turbine reduces the generator output and switches the low-pressure steam source of the feedwater pump turbine from the extracted steam to the auxiliary steam, the operation reverse to the above is performed. That is, when the number of rotations of the feedwater turnbin increases due to the switching, and the control deviation exceeds the predetermined range (-a), the auxiliary circuit of the present embodiment operates to rapidly decrease the opening degree of the low-pressure steam control valve 6. However, fluctuations in the rotational speed of the feedwater pump turbine are converged in a short time.

As described above, regarding the correction circuit according to the present embodiment,
The operation in response to the deviation increase due to the switching of the low pressure steam source has been described. However, an increase in control deviation in the turbine controller for the water supply pump is also caused by the inflow steam cutoff of the generator steam turbine due to an accident in the electric system, or a sudden decrease in load due to a failure in the boiler auxiliary equipment. The correction circuit of the present embodiment can be applied to such fluctuation factors.

That is, when the power generation steam turbine inflow cutoff occurs due to an accident in the electric system while using the extracted steam of the power generation steam turbine as drive steam, the control end of the turbine controller is controlled from the low pressure regulator valve 6 to the boiler. The control shifts to the opening control of the high pressure control valve 5 using the outlet steam, and then the control is switched from the high pressure steam control valve 6 to the low pressure control valve 6 using the auxiliary steam. In this case, since the steam pressure greatly changes between the extracted steam and the outlet steam of the boiler, and between the outlet steam of the boiler and the auxiliary steam, the actual rotation speed of the feed-water pump steam turbine fluctuates significantly, and as described above. The correction circuit works to move the operating end rapidly, and the fluctuation of the rotation speed is converged in a short time.

Further, in the operation of rapidly reducing the load due to the failure of the auxiliary boiler, the turbine speed command from the water supply controller 9 fluctuates significantly more than in the normal operation, so that the large deviation signal is detected. Similarly, the correction circuit operates.

As described above, the water supply pump turbine control apparatus according to the first embodiment of the present invention is a proportional-integral calculation circuit based on the deviation between the water supply pump turbine rotation speed command from the water supply control unit and the actual turbine rotation speed. In parallel with this, a high control gain correction circuit that corrects the operating end when the control deviation is large is provided, so fluctuations in the rotational speed due to deviation increase when switching between the auxiliary steam, which is the low-pressure drive steam source, and the extracted steam are prevented. The opening of the steam control valve can be quickly adjusted and converged by the output of the correction circuit. In addition, since the influence of the correction circuit is avoided during normal operation, a stable control system with a low control gain can be constructed.

Next, a second embodiment of the present invention will be described.

FIG. 4 shows the construction of a turbine control device for a feed water pump according to the second embodiment, which is applied to a boiler feed water system similar to that of the first embodiment. Note that a plurality of boiler water supply systems 113 are usually installed.

The difference between this embodiment and FIG. 1 is that the correction arithmetic circuit includes a boiler feed water pressure signal 109 from the boiler feed water pressure detector 22 and a turbine driven feed pump from the outlet pressure detector 21 of the turbine driven feed pump 1. Outlet pressure signal 10
The second subtractor 36 for calculating the deviation of 8 is added.

FIG. 5 shows the characteristics of the large deviation detector. As shown in the figure, the deviation signal output from the subtractor 36 is -c or less,
A large deviation signal is output when + d or more. Where c ≠
The reason for setting d is that the pump outlet pressure 108 becomes higher than the boiler feed water pressure 109 by a certain value in the normal water supply state, and the origin is moved to the negative side accordingly.

The boiler feed water pressure responds to not only the feed water but also other operating conditions, but it changes in proportion to the plant load. As for the outlet pressure of the turbine driven feed water pump, the feed water control unit 9 changes the feed water pump turbine rotation speed command 100 in response to the load of the plant, and the actual turbine rotation speed follows this, so that the response load is reduced and the plant load is reduced. It changes in proportion.

Therefore, during normal operation with a small load change rate, the boiler feed water pressure and the turbine drive feed water pump outlet pressure operate similarly with respect to the plant load change, and the subtractor 3
The deviation signal 107 due to 6 becomes a value within the range -c to + d in FIG. 5, and the output 104 of the large deviation detector 33 becomes zero.
Therefore, the steam control valve opening command 10 to the actuator 4
6, the output 103 of the proportional-plus-integral calculator 32 is output as it is.

On the other hand, when the drive steam of the water feed pump steam turbine is switched between the extracted steam of the power generation steam turbine and the auxiliary steam, the rotational speed of the water feed pump steam turbine varies greatly due to changes in the steam pressure. The outlet pressure 108 of the turbine driven feed water pump 1 fluctuates in proportion to. As a result, the deviation signal 107 of the subtractor 36 exceeds the -c to + d region, and the deviation large signal 104 from the large deviation detector 33 is input to the correction signal from the steam control valve correction amount generator 34 having a high control gain. The quantity 105 is output. The steam control valve opening degree command 106 added with this correction amount allows the steam control valve opening degree to be moved rapidly. Needless to say, the present invention can be applied even when the rotational speed changes due to other factors such as backup with high-pressure steam.

As shown in FIG. 6, the correction according to the second embodiment uses the fluctuation of the feed water pump outlet pressure due to the fluctuation of the rotational speed of the feed water pump steam turbine and the deviation due to the boiler feed water pressure which does not fluctuate much. Strictly speaking, the responsivity is slightly lowered as compared with the first embodiment, but practically the same operating characteristics can be realized. Further, the signals of the boiler feed water pressure and the turbine drive feed water pump outlet pressure are signals used in the boiler control device, and the configuration of this embodiment is easy.

[0050]

According to the method for controlling a turbine for a water supply pump of the present invention, during normal operation in which the control deviation is within a predetermined range, the operating end operation amount is output and controlled by a low-gain proportional-plus-integral calculation. If the deviation exceeds the specified range, the manipulated variable is output by adding the correction amount proportionally calculated with a high gain, so the fluctuation of the turbine speed due to the sudden change of the driving steam pressure or the load can be suppressed quickly and bumplessly. In addition, it is effective in maintaining the stability of water supply control during normal operation.

According to the control apparatus for a water supply pump turbine of the present invention, a correction amount with a high gain is provided in parallel with a low-gain proportional-plus-integral calculation means optimized during normal operation when the control deviation exceeds a predetermined range. Since the correction means for proportionally calculating is provided, even when the driving steam pressure or the load fluctuates rapidly, it can be easily controlled by one control arithmetic unit that does not require switching, and the simple and highly reliable system can be configured. is there.

[Brief description of drawings]

FIG. 1 is a configuration diagram of a turbine control device for a water supply pump showing a first embodiment of the present invention.

FIG. 2 is a characteristic diagram of a large control deviation detector according to the first embodiment.

FIG. 3 is a characteristic diagram of the steam control valve correction amount generator according to the first embodiment.

FIG. 4 is a configuration diagram of a turbine control device for a water feed pump showing a second embodiment of the present invention.

FIG. 5 is a characteristic diagram of the control deviation large detector according to the second embodiment.

FIG. 6 is a dynamic characteristic diagram showing the operation of the boiler water supply system before and after the application of the present invention.

[Explanation of symbols]

1 ... Water pump, 2 ... Steam turbine for water pump, 3 ...
Turbine controller for feed pump, 4 ... Actuator,
5 ... High-pressure steam control valve, 6 ... Low-pressure steam control valve, 9 ... Water supply control device, 10 ... Water supply outlet valve, 11, 12 ... Steam main valve, 1
4 ... Boiler, 20 ... Rotation speed detector, 21 ... Outlet pressure detector of water supply pump, 22 ... Boiler feed water pressure detector, 31,
36 ... Subtractor, 32 ... Proportional-integral calculator, 33 ... Large deviation detector, 34 ... Steam adjusting valve correction amount generator, 35 ... Adder,
40 ... Mechanical lever mechanism, 110 ... High-pressure steam line, 1
11 ... Extraction steam line, 112 ... Auxiliary steam line, 11
3 ... Other pump water supply system.

─────────────────────────────────────────────────── ─── Continuation of the front page (51) Int.Cl. ⁶ Identification number Office reference number FI technical display location G05B 13/02 G05B 13/02 B (72) Inventor Takumi Kawai 5-2 Omika-cho, Hitachi City, Ibaraki Prefecture No. 1 Stock company Hitachi Ltd. Omika factory

Claims (10)

[Claims] 1. A control valve of a driving steam system of a steam turbine for a water supply pump is operated by obtaining an operation amount by a proportional integral calculation based on a deviation between a turbine speed command for the water supply pump from a water supply control device and an actual turbine speed. In the method of controlling the operating end and controlling the rotation speed of the feedwater pump turbine in the thermal power plant, when a predetermined signal deviation exceeds a predetermined deviation range,
A method for controlling a turbine for a water supply pump, comprising: adding a correction amount proportionally calculated with a gain higher than a control gain of the proportional-plus-integral calculation to correct the operation amount. 2. The method for controlling a turbine for a water supply pump according to claim 1, wherein the signal deviation is a deviation between the turbine rotation speed command for the water supply pump and the actual turbine rotation speed. 3. The method for controlling a turbine for a feed water pump according to claim 1, wherein the signal deviation is a deviation between a boiler feed water pressure and a turbine drive feed water pump outlet pressure. 4. The deviation range according to claim 1, 2 or 3, wherein the signal deviation during normal operation is within that range, and the signal deviation during switching of the drive steam system or during sudden load reduction is within that range. A method for controlling a turbine for a water supply pump, which is set so as to exceed a range. 5. An operating end for operating a steam control valve for adjusting low pressure steam used by switching between two systems of extracted steam from a steam turbine for power generation (hereinafter referred to as “extracted steam”) and auxiliary steam, and boiler feedwater control. The turbine rotation speed command of the water supply pump in the thermal power plant is controlled by providing the proportional-integral calculation means for calculating the operation amount of the operating end from the deviation between the turbine rotation speed command for the water supply pump from the device and the actual turbine rotation speed. In the apparatus, a controller for a feed water pump turbine is provided, in parallel with the proportional-plus-integral calculation means, a correction calculation means for calculating a correction amount of the operating end when a predetermined signal deviation becomes large. 6. The correction calculation means according to claim 5, wherein when the signal deviation is a deviation between the feedwater pump turbine rotation speed command and the actual turbine rotation speed or another deviation, a predetermined deviation range is set. Large deviation detecting means for outputting a deviation of a value exceeding 0, correction amount calculating means for proportionally calculating the correction amount from the output of the large deviation detecting means having a control gain higher than that of the proportional-plus-integral calculating means, and A control device of a turbine for a water supply pump, comprising: an addition unit that adds the correction amount and outputs the addition amount to the operation end. 7. The feed pump according to claim 6, wherein the correction computing means includes subtraction means for obtaining a deviation between the boiler feed water pressure and the turbine drive feed water pump outlet pressure in the case of the other deviation. Turbine control device. 8. The deviation range according to claim 6 or 7, wherein the signal deviation exceeds the range when the two systems are switched or when the load is rapidly reduced due to a failure of a boiler auxiliary machine. A characteristic control device for a water supply pump turbine. 9. Two types of steam, low-pressure steam that is used by switching between two systems of steam extracted from a steam turbine for power generation and auxiliary steam, and high-pressure steam from a boiler outlet are used as drive steam, and the low-pressure steam is used. First open the steam control valve for adjusting each high-pressure steam from the low-pressure steam control valve, and after the low-pressure steam control valve reaches full opening, open the high-pressure steam control valve, and rotate the turbine for the water supply pump from the boiler water supply control device. In a device for controlling the rotation speed of a water supply pump turbine in a thermal power plant, the apparatus includes a proportional-integral calculation means for calculating an operation amount of the operation end from a deviation between a number command and an actual turbine rotation speed, If the signal deviation between the number command and the actual turbine speed or the signal deviation between the boiler feed water pressure and the turbine drive feed water pump outlet pressure exceeds a predetermined deviation range. Large deviation detecting means for outputting a value, correction amount calculating means for proportionally calculating a correction amount from the output of the large deviation detecting means having a control gain higher than that of the proportional-plus-integral calculating means, the operation amount and the correction amount Is provided in parallel with the proportional-plus-integral calculation means, and a control device for a feed water pump turbine is provided. 10. The signal deviation during normal operation is within the deviation range, and the signal deviation during switching of the steam used as the driving steam or during a rapid decrease in load is outside the deviation range. As described above, the control apparatus for the turbine for the water supply pump, wherein the deviation range of the deviation large detection means is set.