JPH08158806A - Turbine starting device - Google Patents

Abstract

PURPOSE: To control a relative difference in rotational speeds so as to remain in a synchronizable range, by connecting a midway point of a high-pressure-turbine exhaust pipe starting from an outlet port of a high-pressure turbine and ending at a boiler to an outlet port of a medium-pressure turbine by means of piping and by equipping a secondary-axis bypass valve on a midway point of the piping. CONSTITUTION: Rotational speed control during start-up of a turbine is carried out by means of steam volume flowing in a high-pressure turbine 1 while the steam volume is regulated by means of an opening of a sub valve 7 for a main steam-stop valve or a steam adjusting valve 8. The steam having passed through the sub valve 7 for the main steam-stop valve or the steam adjusting valve 8 is returned to a boiler 9 via a high-pressure-turbine exhaust pipe 14 after giving rotatory power to the high- pressure turbine 1 located on the side of a primary axis. A midway point of the high- pressure-turbine exhaust pipe 14 is connected to an outlet port of a medium-pressure turbine by means of piping 15a and a secondary-axis bypass valve 11 is equipped on a midway point of the piping 15a. A difference between a rotational speed of the primary axis and a rotational speed of the secondary axis can be thereby controlled so as to remain in a synchronizable range, and in its turn effective utilization of energy can be achieved.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a turbine starting device for a cross-compound machine, and more particularly to a turbine starting device for a two-axis synchronous injection of a generator.

[0002]

2. Description of the Related Art A conventional turbine starting device will be described with reference to the system diagram of FIG. As shown in the figure, the primary shaft is a high pressure turbine 1, a primary low pressure turbine 2, and a primary generator 3.
The secondary shaft is composed of the intermediate pressure turbine 4, the secondary low pressure turbine 5, and the secondary generator 6.

The primary generator 3 and the secondary generator 6 are electrically coupled to each other at an appropriate timing while the rotation is rising, and are introduced into the power transmission system as an integral generator. This electrical coupling is called biaxial synchronous closing, and it is necessary to make the difference in rotational speed between the primary generator 3 and the secondary generator 6 smaller than about 3 to 5% during the biaxial synchronous closing.

When the turbine is started, the primary shaft speed is controlled by adjusting the amount of steam introduced to the high pressure turbine 1 by the main steam stop valve auxiliary valve 7 or the steam control valve 8.

The steam expanded in the high-pressure turbine 1 and given a rotational force is heated by the boiler 9 and then guided to the intermediate-pressure turbine 4. At this time, when the rotation speed of the secondary shaft is lower than the rotation speed of the primary shaft, the opening of the speed matching valve 10 is controlled so that the intermediate pressure turbine 4 is supplied to the high pressure turbine 1 without changing the inflow steam amount of the primary shaft. The rotational speed of the secondary shaft was increased by increasing the amount of inflowing steam, and was controlled so as to approach the rotational speed of the primary shaft.

When the rotation speed of the secondary shaft is higher than that of the primary shaft, the opening degree of the valve secondary shaft bypass valve 11 provided in the middle of the secondary shaft bypass pipe 15j is controlled to control the primary shaft. By discharging a part of the intermediate-pressure turbine inlet steam to the condenser 12 without changing the amount of steam flowing into the high-pressure turbine 1, the amount of steam flowing into the intermediate-pressure turbine 4 is reduced to reduce the rotational speed of the secondary shaft. It was lowered and controlled to approach the rotation speed of the primary shaft.

However, the inlet steam of the intermediate-pressure turbine 4 is obtained by heating the outlet steam of the high-pressure turbine 1 in the boiler 9, and discharging this steam energy to the condenser 12 causes an increase in heat loss. .

Further, generally, in the first stage nozzle of the high-pressure turbine 1, the steam chamber is divided into four, as shown in FIG. 8, and the steam control valves 8a, 8a corresponding to the respective divided steam chambers.
8b, 8c and 8d are arranged. When the turbine is started, all four steam control valves 8a to 8d connected to each of the four divided steam chambers are fully opened.
The flow rate is controlled by the main steam stop valve sub-valve 7 arranged upstream of a to 8d, or the main steam stop valve 13 and the main steam stop valve sub-valve 7 are fully opened, and the valve opening characteristic diagram of FIG. As shown in (4), the flow rate was controlled by injecting steam from the entire circumference of the first stage of the turbine by simultaneously controlling the plurality of steam control valves 8a to 8d (hereinafter referred to as simultaneous control valve open).

[0009]

When steam is injected from the entire circumference of the first stage of the turbine in this way, the main steam stop valve auxiliary valve 7 or a plurality of steam control valves 8a to 8d used for flow rate control.
At the same time, the pressure loss increased, and the heat drop of the steam that could be used in the turbine became smaller, which increased energy loss. As described above, the conventional two-axis synchronous injection system of the generator has a problem that energy loss increases.

The present invention has been made in view of the above circumstances, and an object thereof is to control a relative rotational speed difference within a range in which synchronization can be performed when it is difficult to synchronize a biaxial generator. Another object is to provide a turbine starting device that effectively uses energy.

[0011]

In order to achieve the above object, the first aspect of the present invention provides a primary turbine in which a high pressure turbine, a primary low pressure turbine, a primary generator, and a primary generator are uniaxially connected.
A generator, a secondary turbine with a double-flow type medium-pressure turbine, a secondary low-pressure turbine, and a secondary generator connected to another shaft, and the exhaust of steam introduced into the high-pressure turbine to a boiler. , While guiding the steam exhaust of the boiler to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is introduced to the primary low-pressure turbine, the other of the double-flow intermediate-pressure turbine The outlet steam is connected to the secondary low pressure turbine by a pipe connection in a reheat regeneration cycle turbine starter, and the outlet of the high pressure turbine or the extraction pipe in the middle paragraph and the extraction pipe in the inlet of the low pressure turbine or the middle paragraph. It is characterized in that a pipe connecting the trachea and a valve for adjusting steam are provided in the middle of the pipe.

According to a second aspect of the present invention, a primary turbine / generator in which a primary generator is uniaxially coupled to a high pressure turbine, a primary low pressure turbine, a secondary flow intermediate pressure turbine, a secondary low pressure turbine and a secondary turbine. A secondary turbine / generator in which a generator is coupled to another one shaft, and exhaust of steam introduced into the high-pressure turbine are guided to a boiler, and exhaust of steam of this boiler is guided to the double-flow intermediate-pressure turbine, One outlet steam of the double-flow type medium-pressure turbine is guided to the primary low-pressure turbine,
In the turbine starter of the reheat regeneration cycle, the other outlet steam of the double-flow type medium-pressure turbine is pipe-connected so as to be guided to the secondary low-pressure turbine, and an extraction pipe and a condenser in the middle of the secondary turbine. It is characterized in that a pipe for connecting between and is provided with a valve for adjusting steam in the middle of the pipe.

According to a third aspect of the present invention, a high-pressure turbine, a primary low-pressure turbine, a primary turbine / generator in which a primary generator is uniaxially coupled, a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary turbine. A secondary turbine / generator in which a generator is coupled to another one shaft, and exhaust of steam introduced into the high-pressure turbine are guided to a boiler, and exhaust of steam of this boiler is guided to the double-flow intermediate-pressure turbine, One outlet steam of the double-flow type medium-pressure turbine is guided to the primary low-pressure turbine,
The other outlet steam of the double-flow type intermediate-pressure turbine is connected to the secondary low-pressure turbine in a turbine starter for a reheat regeneration cycle, which is connected to the secondary low-pressure turbine, and a lower pressure than the extraction pipe of the primary low-pressure turbine and the extraction pipe. It is characterized in that a pipe connecting between the turbine and the turbine extraction pipe and a valve for adjusting steam are provided in the middle of the pipe.

According to a fourth aspect of the present invention, a high-pressure turbine, a primary low-pressure turbine, a primary turbine / generator in which a primary generator is uniaxially coupled, a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary turbine. A secondary turbine / generator in which a generator is coupled to another one shaft, and exhaust of steam introduced into the high-pressure turbine are guided to a boiler, and exhaust of steam of this boiler is guided to the double-flow intermediate-pressure turbine, One outlet steam of the double-flow type medium-pressure turbine is guided to the primary low-pressure turbine,
In the turbine starter of the reheat regeneration cycle, the other outlet steam of the double-flow type medium-pressure turbine is connected by piping so as to be guided to the secondary low-pressure turbine, and the extraction pipe or the high-pressure pipe in the middle of the high-pressure turbine. It is characterized in that a pipe connecting between the outlet of the turbine and the condenser and a valve for adjusting steam are provided in the middle of the pipe.

According to a fifth aspect of the present invention, a high-pressure turbine, a primary low-pressure turbine, a primary turbine and a generator in which a primary generator is uniaxially coupled, a double-flow intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary turbine. A secondary turbine / generator in which a generator is coupled to another one shaft, and exhaust of steam introduced into the high-pressure turbine are guided to a boiler, and exhaust of steam of this boiler is guided to the double-flow intermediate-pressure turbine, One outlet steam of the double-flow type medium-pressure turbine is guided to the primary low-pressure turbine,
The other outlet steam of the double-flow type medium-pressure turbine is connected to the secondary low-pressure turbine by a pipe connection in a turbine starter of a reheat regeneration cycle, and the outlet of the medium-pressure turbine and the secondary low-pressure turbine are connected to each other. A feature is that a valve is provided in the middle of the connecting pipe.

[0016]

6. A primary turbine / generator in which a high-pressure turbine, a primary low-pressure turbine, and a primary generator are uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected to be guided to a next low-pressure turbine, a valve is provided in the middle of a pipe connecting the outlet of the intermediate-pressure turbine and the primary low-pressure turbine, A valve is provided in the middle of a pipe connecting the one outlet and the secondary low-pressure turbine.

According to a seventh aspect of the present invention, a high-pressure turbine, a primary low-pressure turbine, a primary turbine / generator in which a primary generator is uniaxially coupled, a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary turbine. A secondary turbine / generator in which a generator is coupled to another one shaft, and exhaust of steam introduced into the high-pressure turbine are guided to a boiler, and exhaust of steam of this boiler is guided to the double-flow intermediate-pressure turbine, One outlet steam of the double-flow type medium-pressure turbine is guided to the primary low-pressure turbine,
In a turbine starter for a reheat regeneration cycle, in which the other outlet steam of the double-flow type intermediate pressure turbine is connected so as to be guided to a secondary low pressure turbine, the outlet of the high pressure turbine and the inlet of the intermediate pressure turbine are connected to a boiler. A feature is that a pipe is directly connected without passing through a reheater and a valve is provided in the middle of the pipe.

The eighth aspect of the present invention comprises two shafts, a primary shaft of the primary turbine / generator and a secondary shaft of the secondary turbine / generator. Further, a plurality of steam control valves of the primary turbine are simultaneously opened / closed. In a turbine starter equipped with a control device capable of either sequential opening or closing, the metal temperature before boiler ignition, the main steam temperature before boiler ignition, and the boiler water before boiler ignition when the two axes of the generator are simultaneously turned on. It is characterized by further comprising a control device for detecting at least one of a temperature, a metal temperature before ventilation of the turbine, or a stop time, and controlling the steam control valve to be opened or closed simultaneously or sequentially.

[0019]

According to the present invention, it is not necessary to discharge the inlet steam of the intermediate-pressure turbine to the condenser as in the conventional case, so that energy loss can be reduced. Also, the primary axis,
No matter which rotation speed of the secondary shaft is high, twin-axis synchronization is possible, and unlike the conventional method, the medium-pressure turbine inlet steam with high energy is not discharged to the condenser to reduce energy loss. It is possible. Furthermore, by starting the turbine by sequentially opening the control valve, the rotational energy of the primary shaft rises compared to when it is started by the simultaneous opening of the control valve, and the rotational speed of the secondary shaft relatively decreases, so the condensate Since the amount of steam thrown into the vessel is reduced, it is possible to reduce energy loss.

[0020]

BRIEF DESCRIPTION OF THE DRAWINGS FIG. FIG. 1 is a system configuration diagram of a first embodiment (corresponding to claim 1) of the present invention. As shown in the figure, the primary shaft comprises a high pressure turbine 1, a primary low pressure turbine 2 and a primary generator 3, and the secondary shaft comprises a medium pressure turbine 4, a secondary low pressure turbine 5 and a secondary generator 6. It is configured. Primary generator 3
The secondary generator 6 and the secondary generator 6 are electrically coupled at an appropriate time during the rotation increase, and are input to the power transmission system as an integral generator. This electrical connection is called twin-axis synchronous closing, and the difference in the number of revolutions of the primary generator 3 and the secondary generator 6 is 3 to 5% when the double-axis synchronous closing is performed.
It must be smaller than the degree.

The rotation speed control at the time of starting the turbine is controlled by the amount of steam flowing into the high-pressure turbine 1, and this amount of steam is controlled by adjusting the opening degree of the main steam stop valve auxiliary valve 7 or the steam control valve 8. . The steam that has passed through the main steam stop valve auxiliary valve 7 or the steam control valve 8 gives a rotational force to the high pressure turbine 1 arranged on the primary shaft side, and then is returned to the boiler 9 through the high pressure turbine exhaust pipe 14.

The steam heated in the boiler 9 gives a rotating force to the intermediate pressure turbine 4 arranged on the secondary shaft side,
Two outlets of the intermediate-pressure turbine 4, that is, one outlet is guided to the primary low-pressure turbine 2 arranged on the primary shaft side to give a rotational force to the primary shaft, and the other outlet is arranged on the secondary shaft side. After being guided to the secondary low-pressure turbine 5 and imparting a rotational force to the secondary shaft, it is discharged to a condenser (not shown).
The above description is the same as that described in the related art of FIG.

The present embodiment differs from the turbine starting device of the cross compound machine shown in FIG. 13 in that the high pressure turbine exhaust pipe 14 from the outlet of the high pressure turbine 1 to the boiler 9 is connected to the outlet of the intermediate pressure turbine 4. Piping 15a
The secondary shaft bypass valve 11 is provided in the middle of the pipe 15a. Therefore, similarly to the conventional example, in this embodiment as well, the intermediate pressure turbine 4 has two outlets, one of which is connected to the primary low-pressure turbine 2 side and the other of which is connected to the secondary low-pressure turbine 5 side (either outlet may be used. ) Is provided.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side when the two shafts are synchronously closed, the secondary shaft bypass valve 11 is opened and the secondary shaft is arranged on the secondary shaft. The amount of steam flowing into the pressure turbine 4 is reduced. As a result, the rotational force on the secondary shaft side is reduced, and the rotational speed of the secondary shaft is reduced. Therefore, it is not necessary to discharge the inlet steam of the medium-pressure turbine 4 having high energy to the condenser 12 as in the conventional case,
It is possible to reduce energy loss.

FIG. 2 is a system configuration diagram of a second embodiment (corresponding to claim 2) of the present invention. FIG. 1 which this embodiment has already described.
3 is different from the conventional example in that the pipe 15b connecting the middle of the extraction of the secondary low-pressure turbine 5 to the condenser 12
And the secondary shaft bypass valve 1 provided in the middle of the pipe 15b
1 and the extraction valve 24 from the middle of the extraction of the primary low-pressure turbine 2.
And a pipe connected to the middle of the pipe 15b via the bleed valve 23. Since the other points are the same, the same portions are denoted by the same reference numerals and duplicate description will be omitted.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side when the two shafts are synchronized, the secondary shaft bypass valve 11 is opened and the secondary shaft arranged on the secondary shaft is opened. The amount of steam passing through the next low-pressure turbine 5 is reduced. As a result, the rotational force on the secondary shaft side is reduced, and the rotational speed of the secondary shaft is reduced. At this time, it is necessary to fully close the extraction valve 23 on the secondary low-pressure turbine 5 side or the extraction valve 24 on the primary low-pressure turbine 2 side so as not to extract air from the primary low-pressure turbine 2 side. in this way,
According to this embodiment, without discharging conventional medium pressure turbine inlet steam having high energy to the condenser,
Since the steam of the low pressure turbine with small energy is discharged, it is possible to reduce energy loss.

FIG. 3 is a system configuration diagram of a third embodiment (corresponding to claim 3) of the present invention. FIG. 1 which this embodiment has already described.
3 is different from the conventional example in that there is a pipe 15c connecting the outlet of the intermediate pressure turbine 4 to the primary low pressure turbine 2,
A secondary shaft bypass valve 11 is provided in the middle of the pipe 15c, a stop valve 25 is provided at the outlet pipe of the intermediate-pressure turbine 4, and a branch point of the pipe connected to the primary low-pressure turbine 2 is located in the middle of the stop valve 25. This is the point on the secondary low-pressure turbine 5 side of the two outlets of the pressure turbine 4, and the other points are the same, so the same parts will be denoted by the same reference numerals and redundant description will be omitted.

In this embodiment, when the rotation speed of the secondary shaft side is higher than the rotation speed of the primary shaft side when the two shafts are synchronously closed, the stop valve 2 is used.
5 is fully closed and the secondary shaft bypass valve 11 is opened to extract a part of the inlet steam of the secondary low-pressure turbine 5 to reduce the amount of steam flowing into the secondary low-pressure turbine 5 and to reduce the secondary low-pressure. The steam extracted from the inlet of the turbine 5 is caused to flow in the middle of the primary low-pressure turbine 2 to increase the amount of steam passing through the primary low-pressure turbine 2. As a result, the rotational force on the secondary shaft side decreases, the rotational speed of the secondary shaft decreases, and at the same time the rotational force of the primary low-pressure turbine increases, so the rotational speed of the primary shaft increases and the rotational speed of the primary shaft increases. The difference between the number and the number of rotations of the secondary shaft is reduced. As described above, according to the present embodiment, it is possible to reduce energy loss without discharging the medium-pressure turbine inlet steam having high energy to the condenser as in the conventional case.

FIG. 4 is a system configuration diagram of a fourth embodiment (corresponding to claim 4) of the present invention. FIG. 1 which this embodiment has already described.
3 differs from the conventional example in that the pipe 15d connected from the outlet of the high-pressure turbine 1 to the condenser 12 and the pipe 15d
Since the secondary shaft bypass valve 11 is provided in the middle of d and the other points are the same, the same portions are denoted by the same reference numerals and duplicate description will be omitted.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side when the two shafts are synchronously closed, the secondary shaft bypass valve 11 is opened to open the inlet of the intermediate pressure turbine 4. A part of the steam is extracted to reduce the amount of steam flowing into the intermediate pressure turbine 4. As a result, the rotational force on the secondary shaft side decreases, the rotational speed of the secondary shaft decreases, and the rotational speed difference between the primary shaft and the secondary shaft decreases. As described above, according to the present embodiment, it is possible to reduce energy loss without discharging the medium-pressure turbine inlet steam having high energy to the condenser as in the conventional case.

FIG. 5 is a system configuration diagram of the fifth embodiment (corresponding to claim 5) of the present invention. FIG. 1 which this embodiment has already described.
3 is different from the conventional example in that the secondary crossover valve 22 is provided in the middle of the secondary crossover pipe 21 connected to the secondary low pressure turbine 5 among the outlets of the intermediate pressure turbine 4. Since the points are the same, the same reference numerals are given to the same portions, and duplicate description will be omitted.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side at the time of synchronously closing the two shafts, the secondary crossover valve 22 is narrowed down to an intermediate opening degree, and The inlet steam of the low pressure turbine 5 is reduced. As a result, the rotational force on the secondary shaft side decreases, the rotational speed of the secondary shaft decreases, and the rotational speed difference between the primary shaft and the secondary shaft decreases. As described above, according to the present embodiment, it is possible to reduce energy loss without discharging the medium-pressure turbine inlet steam having high energy to the condenser as in the conventional case.

FIG. 6 is a system configuration diagram of a sixth embodiment (corresponding to claim 6) of the present invention. FIG. 1 which this embodiment has already described.
3 is different from the conventional example in that the primary crossover pipe 1 connected to the primary low-pressure turbine 2 at the outlet of the intermediate-pressure turbine 4 is connected.
The primary crossover valve 20 is provided in the middle of 9 and the secondary crossover valve 22 is provided in the middle of the secondary crossover pipe 21 connected to the secondary low-pressure turbine 5, and the other points are the same. The same portions will be denoted by the same reference symbols and redundant description will be omitted.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side when the two shafts are synchronously closed, the secondary crossover valve 22 is narrowed down to an intermediate opening degree, and The inlet steam of the low pressure turbine 5 is reduced. As a result, the rotational force on the secondary shaft side decreases, the rotational speed of the secondary shaft decreases, and the rotational speed difference between the primary shaft and the secondary shaft decreases.

On the contrary, when the rotation speed on the primary shaft side is higher than the rotation speed on the secondary shaft side, the inlet steam of the primary low-pressure turbine 2 is reduced by narrowing the primary crossover valve 20 to an intermediate opening degree. As a result, the rotational force on the primary shaft side is reduced, the rotational speed of the primary shaft is reduced, and the rotational speed difference between the primary shaft and the secondary shaft is reduced. As described above, according to the present embodiment, it is possible to perform biaxial synchronization regardless of whether the rotational speed of the primary shaft or the secondary shaft is high, and to condense the medium pressure turbine inlet steam having high energy as in the conventional case. It is possible to reduce energy loss without discharging it to the vessel.

FIG. 7 is a system configuration diagram of an embodiment of the present invention (corresponding to claim 7). The present embodiment is different from the conventional example shown in FIG. 13 which has already been described, except that the exhaust pipe 14 of the high-pressure turbine 1 is different.
And the reheater bypass pipe 2 connecting the inlet of the medium pressure turbine 4
6 and the reheater bypass pipe 26 in the middle of the reheater bypass pipe 26
Since 7 is provided and the other points are the same, the same portions are denoted by the same reference numerals and duplicate description will be omitted.

In this embodiment, when the rotational speed on the secondary shaft side is higher than the rotational speed on the primary shaft side when the two shafts are synchronously closed, the low-temperature high-pressure turbine 1 is opened by opening the reheater bypass valve 27.
The exhaust gas of 1 is merged with the inlet of the intermediate pressure turbine 4. As a result, the inlet energy on the secondary shaft side decreases and the rotation speed on the secondary shaft side decreases, so the rotation speed of the secondary shaft decreases and the difference between the rotation speed of the primary shaft and the rotation speed of the secondary shaft decreases. Less. As described above, according to the present embodiment, it is possible to reduce energy loss without discharging the medium-pressure turbine inlet steam having high energy to the condenser as in the conventional case.

FIG. 11 is a control logic diagram of the eighth embodiment (corresponding to claim 8) of the present invention. Usually, the first-stage nozzle at the turbine inlet has four steam chambers as shown in FIG. 8, and steam control valves 8a to 8a connected to the respective steam chambers.
d is arranged. FIG. 9 shows the valve opening characteristics of the steam control valves 8a to 8d, that is, the characteristics of each valve that is simultaneously opened.
FIG. 10 shows the characteristics of each valve in which the adjustable valve is sequentially opened. In the conventional start control, the control valve is started with the control valve opening / closing characteristic of FIG. 9 in which the control valve is opened simultaneously.

In the present embodiment, when starting the turbine, the metal temperature before boiler ignition is t1 ° C or more, the main steam temperature is t2 ° C or more, the boiler water temperature before boiler ignition is t3 ° C or more, the turbine metal temperature is t4 ° C or more, or the stop time is h hours. If at least one of the following plant conditions is satisfied, select "Sequential opening / closing of control valve" for controlling multiple valves in order as control valve control method. Otherwise, select multiple control valve control methods. Select “simultaneous opening / closing of control valve” to control valves simultaneously.

Next, the operation of this embodiment will be described.
Normally, the primary shaft speed is controlled by adjusting the amount of steam flowing into the high-pressure turbine by the steam control valve, but if the steam chamber of the first stage nozzle shown in FIG. 8 is completely divided into four equal parts. Assuming that it is started by "simultaneous opening of control valve", when starting by "sequential opening of control valve",
The inlet pressure of the stage nozzle becomes about 4 times.

Referring to FIG. 12, the steam control valve inlet pressure P1 and the first stage nozzle inlet pressures P2 and P3 will be described below.
Is the pressure drop due to the steam control valve. Compared to the first stage nozzle inlet pressure P3 when activated by "control valve simultaneous opening", the first stage nozzle inlet pressure P2 when activated by "regulated valve sequential opening" is about 4 times the pressure of the high pressure turbine. Since the outlet pressure P4 is almost unchanged, "simultaneous opening of the regulating valve"
In contrast to the adiabatic heat drop E3 in the case of starting with, the adiabatic heat drop E1 in the case of starting with "sequential adjustment valve open" becomes large. Therefore, if the secondary shaft speed becomes higher than the primary shaft speed when starting with "simultaneous opening of the control valve",
By starting by "sequential opening of the control valve", the rotational speed of the primary shaft to which the high-pressure turbine is connected increases, and the rotational speed difference between the primary shaft and the secondary shaft decreases. It should be noted that E2 indicates an effective heat drop when the control valves are sequentially opened, and E4 indicates an effective heat drop when the control valves are simultaneously opened.

By the way, in the prior art, in order to reduce the rotational speed of the intermediate-pressure turbine, part of the driving steam was discarded from the inlet of the intermediate-pressure turbine to the condenser. However, in the present embodiment, the rotational energy of the primary shaft is increased by 2 to 3% as compared with the case of starting by "simultaneous opening and closing of the adjusting valve" by performing the starting by "sequential opening and closing of the adjusting valve". The rotation speed of the shaft decreases. For this reason, the amount of steam to be discarded in the condenser is reduced, so that the loss can be reduced.

[0043]

As described above, according to the present invention,
Since the energy of steam can be effectively used, it is possible to provide a turbine starter having high energy efficiency.

[Brief description of drawings]

FIG. 1 is a system configuration diagram of a first embodiment of the present invention.

FIG. 2 is a system configuration diagram of a second embodiment of the present invention.

FIG. 3 is a system configuration diagram of a third embodiment of the present invention.

FIG. 4 is a system configuration diagram of a fourth embodiment of the present invention.

FIG. 5 is a system configuration diagram of a fifth embodiment of the present invention.

FIG. 6 is a system configuration diagram of a sixth embodiment of the present invention.

FIG. 7 is a system configuration diagram of a seventh embodiment of the present invention.

FIG. 8 is a view showing the arrangement of a first stage nozzle and a regulator valve of a high pressure turbine.

FIG. 9 is a valve opening characteristic diagram at the time of the “sequential adjustment valve opening” operation.

FIG. 10 is a valve opening characteristic diagram at the time of “simultaneous opening of the control valve” operation.

FIG. 11 is a control block diagram of an eighth embodiment of the present invention.

[Fig. 12] "Sequential opening of control valve" and "Simultaneous opening of control valve"
Expansion diagram of high pressure turbine steam in the case of.

FIG. 13 is a system configuration diagram of a conventional technique.

[Explanation of symbols]

1 ... High-pressure turbine, 2 ... Primary low-pressure turbine, 3 ... Primary generator, 4 ... Medium-pressure turbine, 5 ... Secondary low-pressure turbine, 6 ...
Secondary generator, 7 ... Main steam stop valve, sub valve, 8, 8a, 8b,
8c, 8d ... Steam control valve, 9 ... Boiler, 10 ... Speed matching valve, 11 ... Secondary shaft bypass valve, 12 ... Condenser, 13 ... Main steam stop valve, 14 ... High pressure turbine exhaust pipe,
15a, 15b, 15c, 15d, 15j ... Secondary shaft bypass pipe, 19 ... Primary crossover pipe, 20 ... Primary crossover valve, 21 ... Secondary crossover pipe, 22 ... Secondary crossover valve, 23, 24 ... Bleed valve, 25 ... Stop valve, 26
… Reheater bypass pipe, 27… Reheater bypass valve, P1…
Control valve inlet pressure, P2, P3, ... High pressure turbine first stage nozzle inlet pressure, P4 ... High pressure turbine outlet pressure, E1, E
3 ... Adiabatic heat drop, E2, E4 ... Effective heat drop.

 ─────────────────────────────────────────────────── ─── Continuation of the front page (72) Inventor Hideto Tsuuchi 66-2 Horikawa-cho, Saiwai-ku, Kawasaki-shi, Kanagawa Toshiba Engineering Co., Ltd.

Claims (8)

[Claims] 1. A primary turbine / generator having a high-pressure turbine, a primary low-pressure turbine, and a primary generator uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In the turbine starter of the reheat regeneration cycle pipe-connected so as to be guided to the next low-pressure turbine, between the outlet of the high-pressure turbine or the extraction pipe in the middle paragraph and the inlet of the low-pressure turbine or the extraction pipe in the middle paragraph. A turbine starter characterized in that a pipe for connection and a valve for adjusting steam are provided in the middle of the pipe. 2. A primary turbine / generator having a high-pressure turbine, a primary low-pressure turbine, and a primary generator uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In the turbine starter of the reheat regeneration cycle connected so as to be guided to the next low-pressure turbine, the pipe connecting the extraction pipe and the condenser in the middle of the secondary turbine, and the steam in the middle of this pipe. A turbine starter characterized in that a valve for adjusting is provided. 3. A primary turbine / generator in which a high-pressure turbine, a primary low-pressure turbine, and a primary generator are uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected so as to be guided to a next low-pressure turbine, a pipe connecting between an extraction pipe of the primary low-pressure turbine and a turbine extraction pipe lower in pressure than the extraction pipe, and this pipe. A turbine starter characterized in that a valve for adjusting steam is provided midway. 4. A primary turbine / generator in which a high-pressure turbine, a primary low-pressure turbine, and a primary generator are uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected so as to be guided to a next low-pressure turbine, a bleed pipe in the middle of the high-pressure turbine or a pipe connecting an outlet of the high-pressure turbine and a condenser. A turbine starter characterized in that a valve for adjusting steam is provided in the middle of the pipe. 5. A primary turbine / generator in which a high-pressure turbine, a primary low-pressure turbine, and a primary generator are uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected so as to be guided to a next low-pressure turbine, a valve is provided in the middle of a pipe connecting the outlet of the intermediate-pressure turbine and the secondary low-pressure turbine. Turbine starter. 6. A primary turbine / generator in which a high-pressure turbine, a primary low-pressure turbine, and a primary generator are uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected to be guided to a next low-pressure turbine, a valve is provided in the middle of a pipe connecting the outlet of the intermediate-pressure turbine and the primary low-pressure turbine, A turbine starting device characterized in that a valve is provided in the middle of a pipe connecting one outlet to the secondary low-pressure turbine. 7. A primary turbine / generator having a high-pressure turbine, a primary low-pressure turbine, and a primary generator uniaxially coupled together,
A secondary turbine / generator in which a double-flow type intermediate-pressure turbine, a secondary low-pressure turbine, and a secondary generator as well as another secondary shaft are coupled to each other, and the exhaust gas of the steam introduced into the high-pressure turbine is guided to a boiler. The steam exhaust is guided to the double-flow intermediate-pressure turbine, one outlet steam of the double-flow intermediate-pressure turbine is guided to the primary low-pressure turbine, and the other outlet steam of the double-flow intermediate-pressure turbine is two. In a turbine starter for a reheat regeneration cycle, which is pipe-connected so as to be guided to a next low-pressure turbine, a pipe that directly connects the outlet of the high-pressure turbine and the inlet of the intermediate-pressure turbine without passing through a boiler reheater, A turbine starter characterized in that a valve is provided in the middle of the pipe. 8. A primary shaft of a primary turbine / generator and a secondary shaft of a secondary turbine / generator, which are two shafts, and a plurality of steam control valves of the primary turbine are simultaneously opened or closed or sequentially opened or closed. In a turbine starter equipped with a control device that is also capable of, when the two axes of the generator are simultaneously turned on, the metal temperature before boiler ignition, the main steam temperature before boiler ignition, the boiler water temperature before boiler ignition, and the turbine before ventilation A turbine starter comprising a control device that detects at least one value of a metal temperature and a stop time and controls the steam control valve to open and close simultaneously or sequentially.