JP7077257B2 - Turbine controller, turbine control method, and turbine power generation equipment - Google Patents

Description

Embodiments of the present invention relate to a turbine control device, a turbine control method, and a turbine power generation facility.

In a reheatable turbine power generation facility having a turbine bypass system, a high-pressure turbine bypass pipe that branches the main steam introduced into the high-pressure turbine from the main steam pipe and guides it to the high-pressure turbine exhaust pipe, and a high-pressure turbine bypass pipe are provided. A high-pressure turbine bypass valve, a low-pressure turbine bypass pipe that branches a part of the reheated steam introduced into the medium- and low-pressure turbine from the reheat steam pipe and guides it to the water condensing device, and a low-pressure turbine provided in the low-pressure turbine bypass pipe. It is equipped with a bypass valve. Further, steam valves (steam control valve, intercept valve) for guiding steam to the high-pressure turbine and the medium-low pressure turbine are installed in the main steam pipe and the reheat steam pipe, respectively.

At the time of starting the turbine that starts this turbine power generation facility, the main steam bypasses the boiler, the high-pressure turbine, and the medium- and low-pressure turbine until the main steam generated in the boiler reaches the optimum conditions, and the condenser A high pressure turbine bypass valve and a low pressure turbine bypass valve are used to flow to. That is, by opening the high-pressure turbine bypass valve and the low-pressure turbine bypass valve while keeping each steam valve fully closed, the main steam from the boiler is the main steam pipe, the high-pressure turbine bypass pipe, the condensate steam pipe, and the low-pressure turbine. It is guided to the bypass pipe and the condenser in sequence. By doing so, it is possible to shorten the turbine start-up time and improve the efficiency of turbine start-up control.

By the way, in general, the adjustment between the actually measured opening degree and the opening degree command value in the steam valve is performed, for example, when the turbine is started. If this adjustment is performed when the temperature of the steam valve before guiding steam is sufficiently low, the opening of the steam valve cannot be controlled in consideration of the thermal expansion of the steam valve due to the heat from the main steam. Therefore, in order to take into account the thermal expansion of the steam valve due to the heat from the main steam, for example, a displacement detector is newly installed in the valve box that constitutes the steam valve, and steam passes through the high-pressure turbine bypass valve and the low-pressure turbine bypass valve. While bypassing, measure the elongation difference, which is the difference between the displacement of the valve box detected by the change measuring instrument and the displacement of the valve rod detected by the existing opening detector, and open using this elongation difference. The technique of adjusting the degree command value is known.

Japanese Unexamined Patent Publication No. 2018-80672

However, in the above-mentioned conventional technique, a displacement detector for measuring the displacement of the valve box in addition to the displacement of the valve stem is required. Therefore, when the expansion difference between the valve stem and the valve box cannot be measured, such as when the displacement detector fails, the opening degree of the steam valve cannot be controlled in consideration of thermal expansion.

Therefore, the problem to be solved by the present invention is to provide a turbine control device, a turbine control method, and a turbine power generation facility that can control a steam valve in consideration of the influence of thermal expansion without providing a new detector. That is.

In order to solve the above problems, the turbine control device of the embodiment is a turbine control device of a turbine power generation facility including a steam turbine that inflows main steam from a boiler through a main steam pipe in which a steam control valve is installed. Therefore, the steam flow rate opening conversion unit that calculates the opening signal, which is the target value of the opening of the steam control valve, based on the target value of the steam flow rate of the main steam flowing through the steam control valve, and the turbine start-up. A storage unit that stores the actual opening signal immediately before opening, which is the data of the actual opening measured by the opening detector of the steam control valve immediately before opening the steam control valve at the time, and the opening signal and the opening. The steam control valve is provided with an addition unit to which an opening signal is input and an opening target signal, which is an addition value of the opening signal and the actual opening signal immediately before opening, is output to the steam control valve.

According to the present invention, it is possible to provide a turbine control device, a turbine control method, and a turbine power generation facility capable of controlling a steam valve in consideration of the influence of thermal expansion without providing a new detector.

It is a figure which shows the structure of the turbine power generation facility which concerns on 1st Embodiment. It is a figure which shows the structure of the turbine control device which concerns on 1st Embodiment. It is a figure which shows the structure of the turbine control device which concerns on the 2nd Embodiment. It is a figure which shows the structure of the turbine control device which concerns on 3rd Embodiment.

(First embodiment)
The turbine power generation facility according to the first embodiment will be described with reference to FIG. FIG. 1 is a diagram showing a configuration of a turbine power generation facility according to the first embodiment.

The turbine power generation facility 1 includes a boiler 10, a steam turbine 20, a reheater 30, a water recovery device 60, a generator 70, a main steam pipe P10, a low temperature reheat steam pipe P21, and a crossover pipe P22. , High temperature reheat steam pipe P30, high pressure turbine bypass pipe PB1, low pressure turbine bypass pipe PB2, main steam stop valve V10a, steam control valve V10b, intercept valve V30a, reheat steam stop valve V30b. A high-pressure turbine bypass valve VB1 and a low-pressure turbine bypass valve VB2 are provided. Further, although not shown in FIG. 1, the turbine power generation facility 1 further includes a turbine control device 100.

The boiler 10 heats water to generate main steam.

The steam turbine 20 includes a high-pressure turbine 21 provided on the upstream side, and a medium-pressure turbine 22 and a low-pressure turbine 23 provided on the downstream side of the high-pressure turbine 21. In the present embodiment, the case where each of the high, medium and low pressure steam turbines is provided is illustrated, but the configuration of the steam turbine 20 is not limited to this case. For example, a high and low pressure steam turbine is provided without the medium pressure turbine 22. It may have a configuration.

A main steam pipe P10 is provided between the boiler 10 and the high-pressure turbine 21, and a main steam stop valve V10a and a steam control valve V10b are installed in the main steam pipe P10. An opening degree detector 11 (not shown) is attached to the steam control valve V10b to constantly measure the opening degree of the steam control valve V10b.

A low temperature reheat steam pipe P21 is provided between the high pressure turbine 21 and the reheater 30. A high-temperature reheat steam pipe P30 is provided between the reheater 30 and the medium-pressure turbine 22, and an intercept valve V30a and a reheat steam stop valve V30b are installed in the high-temperature reheat steam pipe P30. Further, a crossover pipe P22 is provided between the medium pressure turbine 22 and the low pressure turbine 23.

The main steam generated in the boiler 10 is guided from the main steam pipe P10 to the high-pressure turbine 21 via the main steam stop valve V10a and the steam control valve V10b in sequence. The main steam is discharged as high-pressure exhaust after performing expansion work in each turbine paragraph (not shown) of the high-pressure turbine 21. This high-pressure exhaust is guided from the low-temperature reheat steam pipe P21 to the reheater 30, and then heated by the reheater 30 to become reheated steam. The reheated steam is guided from the high temperature reheated steam pipe P30 to the medium pressure turbine 22 via the intercept valve V30a and the reheated steam stop valve V30b in sequence. The reheated steam is discharged as medium pressure exhaust after performing expansion work in each turbine paragraph (not shown) of the medium pressure turbine 22, and is guided from the crossover pipe P22 to the low pressure turbine 23. The medium pressure exhaust is exhausted as low pressure exhaust after expansion work is performed in each turbine paragraph (not shown) of the low pressure turbine 23, and is condensed (condensed) by the condenser 60. The water (condensed water) condensed by the condenser 60 is guided to the boiler 10 again via a pipe (not shown).

In the steam turbine 20, the turbine rotors of the high-pressure turbine 21, the medium-pressure turbine 22, and the low-pressure turbine 23 are coaxially connected. When each turbine rotor rotates due to the expansion work of steam (main steam, reheated steam, or medium pressure exhaust) as a working fluid, the generator 70 is driven to generate electricity.

The high-pressure turbine bypass pipe PB1 connects the main steam pipe P10 and the low-temperature reheat steam pipe P21. Specifically, the high pressure turbine bypass pipe PB1 connects the position between the boiler 10 and the main steam stop valve V10a and the position between the high pressure turbine 21 and the reheater 30. Further, a high pressure turbine bypass valve VB1 is installed in the high pressure turbine bypass pipe PB1.

On the other hand, the low-pressure turbine bypass pipe PB2 connects the high-temperature reheat steam pipe P30 and the condenser 60. Specifically, the low pressure turbine bypass pipe PB2 connects the position between the reheater 30 and the intercept valve V30a to the condenser 60. Further, a low pressure turbine bypass valve VB2 is installed in the low pressure turbine bypass pipe PB2.

At the time of starting the turbine for starting the turbine power generation facility 1, the main steam from the boiler 10 is guided to the condenser 60 by bypassing the steam turbine 20 until the steam generated in the boiler 10 reaches the optimum conditions. Therefore, the high pressure turbine bypass pipe PB1 and the low pressure turbine bypass pipe PB2 are used. Specifically, the main steam from the boiler 10 passes from the main steam pipe P10 through the high-pressure turbine bypass pipe PB1, and is sequentially guided to the reheater 30 via the high-pressure turbine bypass valve VB1 and the low-temperature reheat steam pipe P21. This main steam is guided from the reheater 30 to the condenser 60 via the high temperature reheat steam pipe P30, the low pressure turbine bypass pipe PB2 and the low pressure turbine bypass valve VB2.

Then, when the main steam generated in the boiler 10 is in the optimum condition and the turbine is started, the flow rate of the main steam flowing through the steam control valve V10b and the flow rate of the steam (reheated steam) flowing through the intercept valve V30a. While maintaining the optimum ratio with, increase the steam flow rate flowing into the steam turbine. This makes it possible to drive the steam turbine at a desired steam flow rate.

Before starting the turbine, the main steam stop valve V10a, steam control valve V10b, intercept valve V30a, and reheat steam stop valve V30b are fully closed, and the high pressure turbine bypass valve VB1 and low pressure turbine bypass valve VB2 are pressure controlled. Operates in response to driving. Then, at the time of turbine reset, the main steam stop valve V10a is fully opened and the intercept valve V30a is opened. At the start of startup, the operation of opening the sub-valve of the steam control valve V10b and the reheat steam stop valve V30b is started, and the main valve of the reheat steam stop valve V30b is fully opened with the sub-valve fully open, and then the main valve is fully opened. Open the intercept valve V30a. Then, when the specified load is reached, the intercept valve V30a is fully opened, and the steam control valve V10b is operated to control the load. During load operation, the high-pressure turbine bypass valve VB1 and the low-pressure turbine bypass valve VB2 are fully closed.

The turbine control device 100 controls the operation of each valve constituting the turbine power generation facility 1. Here, the details of the turbine control device 100 in the first embodiment will be described with reference to FIG. FIG. 2 shows the configuration of the turbine control device 100 according to the first embodiment. In the following description, the steam control valve V10b is illustrated as a control target by the turbine control device 100, but the control target of the turbine control device 100 is not only the steam control valve V10b, but also, for example, the main steam stop valve V10a and intercept. The valve V30a or the reheat steam stop valve V30b may be used. This relationship is similarly established in other embodiments described later.

As shown in FIG. 2, the turbine control device 100 includes a rotation speed conversion unit 101, a steam flow rate opening degree conversion unit 102, a one-shot circuit 103, a storage unit 104, an addition unit 105, and a subtraction unit 106. Be prepared.

The rotation speed conversion unit 101 converts the turbine rotation speed signal S20 into the steam flow rate signal S101. Specifically, when the turbine rotation speed signal S20 is input to the rotation speed conversion unit 101, the rotation speed conversion unit 101 deviates from the target rotation speed and the actual rotation speed of the steam turbine 20 indicated by the turbine rotation speed signal. A constant gain (1 / k and k are speed adjustment rates) is integrated with respect to the above, and the steam flow rate signal S101 is output. This steam flow rate signal S101 is a target value of the steam flow rate of the main steam flowing through the steam control valve V10b.

The steam flow rate opening degree conversion unit 102 converts the steam flow rate signal S101 into the steam control valve opening degree signal S102 (opening degree signal). In the present embodiment, the data of the opening degree of the steam control valve V10b corresponding to the steam flow rate signal S101 is obtained from the relationship between the steam flow rate obtained in advance and the opening degree of the steam control valve V10b, and the opening degree is adjusted by steam. It is output as a valve opening signal S102. The steam control valve opening signal S102 is a target value of the steam control valve V10b output based on the steam flow rate signal S101.

The turbine start command signal S103 is input to the one-shot circuit 103 from the outside. When the turbine start command signal S103 is input (immediately before opening the steam control valve V10b), the one-shot circuit 103 outputs the actual opening signal S11a immediately before opening from the opening detector 11 to the storage unit 104. The actual opening signal S11a immediately before opening is the opening degree of the steam control valve V10b measured by the opening degree detector 11 immediately before opening the steam control valve V10b.

The storage unit 104 stores the actual opening signal S11a immediately before opening from the opening detector 11. Specifically, when the turbine start command signal S103 is input to the one-shot circuit 103, the storage unit 104 inputs the actual opening signal S11a immediately before opening from the opening detector 11 via the one-shot circuit 103. To. The actual opening signal S11a immediately before opening is output as the actual opening signal S104 immediately before opening to the addition unit 105 described later (S104 = S11a).

The addition unit 105 adds the steam control valve opening signal S102 input from the steam flow rate opening degree conversion unit 102 and the actual opening signal S104 (S11a) immediately before opening input from the storage unit 104. That is, the addition unit 105 sends the steam control valve opening signal S102 from the steam flow rate opening conversion unit 102 the actual opening signal S11a immediately before opening, which is the opening degree of the steam control valve V10b immediately before opening the steam control valve V10b. In addition, the steam control valve opening signal S102 from the steam flow rate opening conversion unit, which is the target value of the opening of the steam control valve V10b, is corrected. Then, the addition unit 105 outputs the opening target signal S105, which is the result of the addition processing, to the subtraction unit 106 (S105 = S102 + S104 = S102 + S11a).

The subtraction unit 106 subtracts the opening target signal S105 and the actual opening signal S11b from the opening detector 11. This actual opening degree signal S11b is the opening degree of the current steam control valve V10b. Then, the subtraction unit 106 outputs the opening command signal S106, which is the result of the subtraction process, to the steam control valve V10b (S106 = S105-S11b). The opening degree of the steam control valve V10b is controlled based on the opening degree command signal S106.

For example, expressed as a percentage of the steam control valve V10b when fully opened, the actual opening signal S11a immediately before opening has an opening of 0.1%, the steam control valve opening signal S102 has an opening of 50%, and the actual opening signal. Consider the case where S11b shows an opening of 5.3%, respectively. In this case, the opening target signal S105 is 50.1% obtained by adding the actual opening signal S11a immediately before opening and the steam control valve opening signal S102, and the opening command signal S106 is the actual opening signal S11b from this value. It becomes 44.8% after subtraction, and the opening command signal S106 instructing to open the opening of the steam control valve V10b by 44.8% is output to the steam control valve V10b.

According to the first embodiment described above, the turbine control device 100 uses the steam immediately before opening actual opening signal S11a, which is the opening measured by the opening detector 11 immediately before opening the steam control valve V10b. The steam control valve opening signal S102, which is the target value of the control valve V10b, is corrected, and the opening command signal 106 to the steam control valve V10b is output based on the corrected opening target signal S105. Therefore, even if the valve stem or valve box (both not shown) constituting the steam control valve V10b is thermally expanded by the main steam flowing through the main steam pipe P10 before the turbine is started, the effect of the steam control valve V10b is taken into consideration. The opening can be controlled.

In this embodiment, the case where the opening degree detector 11 constantly measures the opening degree of the steam control valve V10b is illustrated, but the opening degree detector 11 is at least immediately before opening the steam control valve V10b and. It suffices to measure the opening degree of the steam control valve V10b immediately before the subtraction process by the subtraction unit 106, and it is not always necessary to constantly measure the opening degree of the steam control valve V10b. As a modification of the present embodiment, for example, an opening degree detection command unit is newly provided in the turbine control device 100, and the opening degree detection command unit is opened immediately before opening the steam control valve V10b and immediately before the subtraction process by the subtraction unit 106. A signal for detecting the opening degree of the steam control valve V10b may be output to the degree detector 11.

Further, in the present embodiment, the case where the control target of the turbine control device 100 is the steam control valve V10b has been described as an example, but as a modification of the present embodiment, the steam control valve V10b and the intercept valve V30a are used. It may be controlled so that the ratio of the steam flow rate flowing through each is optimized.

Further, in the present embodiment, the case where the turbine start command signal S103 is input to the one-shot circuit 103 from the outside immediately before the steam control valve V10b is opened has been described as an example. Immediately before warming of the steam control valve V10b, the one-shot circuit 103 may be configured to input a command signal immediately before warming from the outside.

The same applies to other embodiments described later with respect to these modified examples.

(Second embodiment)
The turbine power generation facility according to the second embodiment will be described with reference to FIG. FIG. 3 is a diagram showing the configuration of the turbine control device 100 according to the second embodiment. Hereinafter, the parts different from the first embodiment will be described, and the other parts will be given the same drawing numbers as those of the first embodiment, and the description thereof will be omitted.

As shown in FIG. 3, the turbine control device 100 according to the second embodiment includes a rotation speed conversion unit 101, a steam flow rate opening degree conversion unit 102, a one-shot circuit 103, a storage unit 104, and an addition unit 105. And a subtraction unit 106 and an actual opening degree evaluation unit 117 immediately before opening. That is, the second embodiment is different from the first embodiment in that the turbine control device 100 further includes the actual opening degree evaluation unit 117 immediately before opening.

The actual opening degree evaluation unit 117 immediately before opening is provided between the storage unit 104 and the addition unit 105. When the actual opening signal S104 (S11a) immediately before opening, which is input from the storage unit 104, exceeds the predetermined opening, the actual opening immediately before opening evaluation unit 117 evaluates the predetermined opening and then the actual opening signal immediately before opening. It is output to the addition unit 105 as S117. The predetermined opening degree referred to here is a value set in advance in the actual opening degree evaluation unit 117 immediately before opening. On the other hand, when the actual opening signal S104 immediately before opening is equal to or less than a predetermined opening, the actual opening signal S104 immediately before opening is directly evaluated and then output to the addition unit 105 as the actual opening signal S117 immediately before opening.

For example, when the predetermined opening is 0.2% and the actual opening signal S11a immediately before opening is 0.3%, expressed as a percentage of the steam control valve V10b when fully opened, the actual opening immediately before opening is Since the signal S11a is larger than the predetermined opening degree, the actual opening degree evaluation unit 117 immediately before opening evaluates the opening degree (predetermined opening degree) of 0.2% and sets the actual opening degree signal S117 immediately before opening to the adding unit 105. Output.

On the other hand, when the predetermined opening is 0.2% and the actual opening signal S104 (S11a) immediately before opening is 0.1%, expressed as a percentage of the steam control valve V10b when fully opened, immediately before opening. Since the actual opening signal S104 is smaller than the predetermined opening, the actual opening evaluation unit 117 immediately before opening evaluates the opening of 0.1% (actual opening signal S104 immediately before opening) and then the actual opening signal immediately before opening. It is output to the addition unit 105 as it is as S117.

The addition unit 105 adds the steam control valve opening signal S102 and the actual opening signal S117 immediately before opening after evaluation, and outputs the result opening target signal S115 to the subtraction unit 106 (S115 = S102 + S117). .. Further, the subtraction unit 106 subtracts the opening target signal S115 and the actual opening signal S11b from the opening detector 11 and outputs the resulting opening command signal S116 to the steam control valve V10b. (S116 = S115-S11b).

According to the second embodiment described above, the actual opening just before opening evaluation unit 117 is provided between the storage unit 104 and the adding unit 105, and the actual opening just before opening is a reference value due to the positional deviation of the opening detector 11. Even when the opening signal S11a shows an excessively large value, the opening of the steam control valve V10b can be controlled by correcting this reference value.

As a modification of the present embodiment, for example, a metal temperature detecting unit for detecting the metal temperature of the steam control valve V10b is provided, and a predetermined opening degree is set for each metal temperature with respect to the actual opening degree evaluation unit 117 immediately before opening. Each may be set. With such a configuration, a predetermined opening degree can be appropriately changed according to the metal temperature input from the metal temperature detection unit to the actual opening degree evaluation unit 117 immediately before opening, and the valve bar constituting the steam control valve V10b can be used. It is possible to control the opening degree of the steam control valve V10b by taking into account the influence of thermal expansion of the valve box (both not shown) in more detail. Further, instead of the metal temperature detection unit, a steam temperature detection unit that detects the temperature of the main steam flowing through the steam control valve V10b may be provided, or a configuration in which these may be combined may be provided.

(Third embodiment)
The turbine power generation facility according to the third embodiment will be described with reference to FIG. FIG. 4 is a diagram showing the configuration of the turbine control device 100 according to the third embodiment. Hereinafter, the parts different from the first and second embodiments will be described, and the other parts will be given the same drawing numbers as those of the first and second embodiments, and the description thereof will be omitted.

As shown in FIG. 4, the turbine control device 100 according to the third embodiment includes a rotation speed conversion unit 101, a steam flow rate opening degree conversion unit 102, a one-shot circuit 103, a storage unit 104, and a first unit. A subtraction unit 126 and a second subtraction unit 127 are provided. That is, in the third embodiment, the first and second points are that the turbine control device 100 includes the first subtraction unit 126 instead of the adder 105, and the second subtraction unit 127 instead of the subtraction unit 106, respectively. Is different from the embodiment of.

The first subtraction unit 126 subtracts the actual opening degree signal S104 (S11a) immediately before opening input from the storage unit 104 and the actual opening degree signal S11b input from the opening degree detector 11. That is, the first subtraction unit 126 opens the current steam control valve V10b by using the actual opening signal S11a immediately before opening, which is the opening degree of the steam control valve V10b immediately before opening the steam control valve V10b, as an offset value. Correct the degree. Then, the first subtraction unit 126 outputs the corrected steam control valve actual opening signal S126 (corrected actual opening degree signal), which is the result of the subtraction process, to the second subtraction unit 127 (S126 = S11b-S104 = S11b). -S11a).

The second subtraction unit 127 subtracts the steam control valve opening signal S102 input from the steam flow rate opening degree conversion unit 102 and the correction steam control valve actual opening signal S126 input from the first subtraction unit 126. To process. Then, the second subtraction unit 127 outputs the opening command signal S127, which is the result of the subtraction process, to the steam control valve V10b (S127 = S102-S126). The opening degree of the steam control valve V10b is controlled based on the opening degree command signal S127.

For example, expressed as a percentage of the steam control valve V10b when fully opened, the actual opening signal S11a immediately before opening has an opening of 0.1%, the steam control valve opening signal S102 has an opening of 50%, and the actual opening signal. Consider the case where S11b shows an opening of 5.3%, respectively. In this case, the corrected steam control valve actual opening signal S126 is 5.2% obtained by subtracting the actual opening signal S11a immediately before opening from the actual opening signal S11b, and the opening command signal S127 is from the steam control valve opening signal S102. The corrected steam control valve actual opening signal S126 is subtracted to obtain 44.8%, and the opening command signal S106 instructing to open the opening of the steam control valve V10b by 44.8% is output to the steam control valve V10b. To.

According to the third embodiment described above, immediately before opening the steam control valve V10b, the actual opening signal S11a immediately before opening, which is the opening degree of the steam control valve V10b measured by the opening detector 11, is used as an offset value. Therefore, the opening degree of the current steam control valve V10b is corrected, and the opening command signal S127 to the steam control valve V10b is output based on the corrected steam control valve actual opening signal S126 which is the corrected opening. Therefore, even if the valve stem and valve box (both not shown) that make up the steam control valve V10b are thermally expanded by the steam from the start of the turbine, the opening degree of the steam control valve V10b should be controlled in consideration of the influence. Can be done.

Although some embodiments of the present invention have been described, these embodiments are presented as examples and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other embodiments, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are also included in the scope of the invention described in the claims and the equivalent scope thereof.

1. 1. Turbine power generation equipment, 10. Boiler, 11. Opening detector, 20. Steam turbine, 30. Reheater, 60. Condenser, 70. Generator, 100. Turbine controller, 101. Rotation speed converter, 102. Steam flow rate opening converter, 103. One-shot circuit, 104. Memory unit, 105. Addition part, 106. Subtractor 117. Actual opening evaluation unit immediately before opening, 126. First subtraction part 127. Second subtraction part, P10. Main steam pipe, P21. Low temperature reheat steam tube, P22. Crossover tube, P30. High temperature reheat steam tube, PB1. High pressure turbine bypass pipe, PB2. Low pressure turbine bypass pipe, V10a. Main steam stop valve, V10b. Steam control valve, V30a. Intercept valve, V30b. Reheat steam stop valve, VB1. High pressure turbine bypass valve, VB2. Low pressure turbine bypass valve

Claims (5)

A turbine control device for turbine power generation equipment equipped with a steam turbine that allows main steam from a boiler to flow in through a main steam pipe equipped with a steam control valve.
A steam flow rate opening conversion unit that calculates an opening signal, which is a target value of the opening of the steam control valve, based on a target value of the steam flow rate of the main steam flowing through the steam control valve.
A storage unit that stores the actual opening signal immediately before opening, which is the data of the actual opening measured by the opening detector of the steam control valve immediately before opening the steam control valve at the time of starting the turbine.
An addition unit to which the opening signal and the actual opening signal immediately before opening are input and an opening target signal which is an addition value of the opening signal and the actual opening signal immediately before opening is output to the steam control valve.
Equipped with
The actual opening signal immediately before opening is input from the opening detector, and the actual opening signal immediately before opening is compared with a preset predetermined opening, and the actual opening signal immediately before opening is the predetermined. When it is smaller than the opening degree, the actual opening degree signal immediately before opening is output to the storage unit, and when the actual opening degree signal immediately before opening is equal to or more than the predetermined opening degree, the predetermined opening degree is stored in the storage unit. A turbine control device further equipped with an actual opening evaluation unit immediately before opening that outputs to the unit. The steam turbine on the upstream side, which allows the main steam from the boiler to flow in through the main steam pipe equipped with the steam control valve,
A reheater that inflows the steam discharged from the steam turbine on the upstream side and heats the steam, and
A steam turbine on the downstream side that allows reheated steam heated by the reheater to flow in through a reheated steam pipe equipped with an intercept valve.
It is a turbine control device of a turbine power generation facility equipped with
A steam flow rate opening conversion unit that calculates an opening signal, which is a target value of the opening of the intercept valve, based on a target value of the steam flow rate of the reheated steam flowing through the intercept valve.
A storage unit that stores the actual opening signal immediately before opening, which is the data of the actual opening measured by the opening detector of the intercept valve immediately before opening the intercept valve at the time of starting the turbine.
An addition unit to which the opening signal and the actual opening signal immediately before opening are input and an opening target signal which is an addition value of the opening signal and the actual opening signal immediately before opening is output to the intercept valve.
Equipped with
The actual opening signal immediately before opening is input from the opening detector, and the actual opening signal immediately before opening is compared with a preset predetermined opening, and the actual opening signal immediately before opening is the predetermined. When it is smaller than the opening degree, the actual opening degree signal immediately before opening is output to the storage unit, and when the actual opening degree signal immediately before opening is equal to or more than the predetermined opening degree, the predetermined opening degree is stored in the storage unit. A turbine control device further equipped with an actual opening evaluation unit immediately before opening that outputs to the unit. The opening target signal and the actual opening signal measured by the opening detector are input, and an opening command signal which is a difference value between the opening target signal and the actual opening signal is used as the steam control valve. The turbine control device according to claim 1, further comprising a subtraction unit for output. The opening target signal and the actual opening signal measured by the opening detector are input, and an opening command signal which is a difference value between the opening target signal and the actual opening signal is output to the intercept valve. The turbine control device according to claim 2, further comprising a subtraction unit. A turbine power generation facility including the turbine control device according to any one of claims 1 to 4.

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