JPS5934405A - Warming device of steam turbine - Google Patents

Abstract

PURPOSE:To decrease both the warming time of a turbine and the temperature difference from high temperature steam flowing in the turbine at its starting so as to reduce thermal stress generated at starting of the turbine, by connecting warming steam pipes respectively to an intermediate stage part, main steam inlet side and an exhaust part side and controlling respective pressures of steam to be in a fixed relation during the warming time. CONSTITUTION:If pressure in the intemediate stage part of a turbine is increased to, for instance, 2 atg being a setting pressure of the first pressure setter, pressures of main steam in its inlet and exhaust parts are controlled to be maintained under a condition with the pressures lower than 2 atg respectively by prescribed values alpha2, alpha1, and if temperatures of metals in each part increase to approach a saturation temperature of the pressure, a preset value of the first pressure setter 55 is increased to an optional value, for instance, 4 atg. Then the pressures of steam are controlled to be maintained in a condition of 4 atg in the inlet part of warming steam, (4-alpha1) atg in the exhaust side and (4-alpha2) atg in the inlet side of main steam. Accordingly, a high pressure turbine or the like can be warmed to a saturation temperature of steam at a pressure of 4 atg.

Description

DETAILED DESCRIPTION OF THE INVENTION [Technical Field of the Invention] The present invention relates to a warming device for a steam turbine in a steam turbine plant.

[Technical background of the invention]

Recently, with the increase in the capacity of power plants, steam turbines have become larger, and there are also transformation plants whose role is to balance the supply and demand of electricity, and ultra-high pressure and high temperature power generation where steam conditions are further increased in pressure and temperature. Plants, etc. are being reviewed.

By the way, as mentioned above, the role of the above-mentioned transformer plants is to balance the supply and demand of electricity, so even though it is a large power generation plant, it is not possible to constantly operate at a high load as in the past. , the frequency of plant shutdowns increases depending on the difference between demand and supply. In addition, if the steam conditions are increased to high pressure and temperature, the steam turbine casing body will naturally become thicker and larger in shape, and the rotor diameter will also need to be larger in order to obtain sufficient strength against the centrifugal force caused by high-speed rotation. Become.

However, in a steam turbine that has such a large and complicated shape, if the inner surface temperature of the first stage casing is low at startup, it is necessary to remove the casing and rotor of the steam turbine 1ff before startup. Transition temperature (approximately 14o
It is necessary to warm the steam to 0c) or higher to prevent low-temperature brittle fracture and to reduce the temperature difference between the steam and the high-temperature steam flowing from the boiler at startup to alleviate excessive temperature changes.

FIG. 1 is a system diagram of a steam turbine plant equipped with a conventional warming device, in which high-temperature, high-pressure main steam generated in a boiler superheater 1 passes through a main steam pipe 2 to a main steam stop valve 3 and a steam control valve. It is introduced into the high pressure turbine 5 via the valve 4. The steam introduced into the high-pressure turbine 5 is thermally expanded there and processed 4), and is then led to the boiler reheater 7 by the low-temperature reheat steam pipe 6 and heated again. The heated reheat steam passes through a high temperature reheat steam pipe 8 and is supplied to an intermediate pressure turbine 11 via a reheat steam stop valve 9 and an intercept valve 10. After the steam supplied to the intermediate pressure turbine 11 performs work there, it is further introduced into the low pressure turbine 12 to perform work, and the steam supplied to the high pressure turbine 5. Intermediate pressure turbine 11 and low pressure turbine 1
A generator 13 connected to the rotor shaft of No. 2 is driven. On the other hand, the steam that has expanded and completed its work in the low-pressure turbine 12 is introduced into the condenser 14 and is condensed.

By the way, the low-temperature reheat steam pipe 6 includes an auxiliary steam main pipe 16 to which auxiliary steam is supplied from an auxiliary boiler or other auxiliary steam source 15, and a warming pressure control valve 17 and a stop valve 1.
It is connected by a warming steam pipe 19 having 8. On the other hand, a main steam pipe drain pipe 20 is connected to the downstream side of the steam control valve 4 of the main steam pipe 2, and high pressure casing drain pipes 22. An air bleed pipe drain pipe 23 is connected. Also, the low temperature reheat steam pipe 6 and the high temperature reheat steam pipe 8 each have a low temperature reheat steam pipe drain pipe 24. A high-temperature reheat steam pipe drain pipe 25 is connected, and each drain pipe has a drain valve 20a, 22a, 23a, 24a, respectively.
, 25a are provided.

Therefore, when warming up the turbine, the main steam stop valve 3. Steam control valve 4. While the main valves such as the reheat steam stop valve 9 and the intercept valve 10 are kept fully closed, the warming pressure control valve 17 and the stop valve 18
The auxiliary steam main pipe 6 is opened to supply warming steam from the low temperature reheat steam pipe 61F.

Then, the warming steam that has flowed into the low-temperature reheat steam pipe 6 flows into the high-pressure turbine 5, and at the same time flows into the boiler reheater 7, and further into the high-temperature reheat steam pipe 8, where it is reheated. The steam is shut off by the steam stop valve 9 and the entire system of the boiler reheater 7 is filled. On the other hand, the warming steam that has flowed into the high-pressure turbine 5 fills the high-pressure turbine 5, and at the same time, the high-pressure turbine 5 is sealed by the steam control valve 4 and the main steam stop valve 3.

Therefore, when the warming pressure control valve 17 is further opened to supply warming steam, the high pressure turbine 5 between the main steam stop valve 3 and the steam control valve 4 and the reheat steam stop valve 9
The pressure of the entire system of the boiler reheater 7 rises, and this pressure is maintained by the warming pressure control valve 17 at 4 to 5 atg, which is the saturated steam pressure at the target temperature of 150°C.

The steam sealed in the high pressure turbine 5, etc. is transferred to the high pressure turbine 5. Boiler reheater7. Furthermore, by coming into contact with low-temperature metal surfaces such as the low-temperature reheat steam pipe and the high-temperature reheat steam pipe 8, the retained heat is taken away, causing the metal temperature of each part to rise. As a result, the enthalpy of the steam decreases and a portion of the steam is converted into drain, but the drain generated at this time is drained from drain pipes installed at low points in various parts, that is, the main steam pipe drain pipe 20°, the high pressure casing drain pipe 21. Bleed pipe drain pipe 2
It is discharged together with a portion of the warming steam from the 3° low temperature reheat steam pipe drain pipe 24, the high temperature reheat steam pipe drain pipe n, etc. On the other hand, the pressure drop due to condensation of the sealed steam and the decrease in steam amount due to outflow from the drain pipe are supplemented by warming steam supplied by adjusting the opening degree of the warming pressure regulating valve 17.

In this way, each part of the high-pressure turbine and the like is uniformly warmed to the target temperature due to the contact between the warming steam and the low-temperature metal.

[Problems with background technology]

However, with respect to the high-pressure turbine 5, the boiler reheater 7 and the accompanying low-temperature reheat steam pipe 6. High temperature reheat steam pipe 8
There is a marked difference both in terms of volume and metal surface area, and is overwhelmingly large. For example, 600
A MW class θ) boiler has a volume exceeding 300 m3, whereas a high pressure turbine has a volume of around 80 m3. Therefore, there is naturally a corresponding difference in the metal area that comes into contact with the warming steam, and most of the warming steam is spent warming the boiler reheater 7 system, and the high-pressure turbine, which is the main target of warming, is used to warm the boiler reheater 7 system. 5, priority is given to warming, and as a result, the time required to bring the high-pressure turbine to the target temperature inevitably takes a long time.

In other words, if the high-pressure turbine is completely cold, it may take a whole day and night, and the high-pressure turbine 5
In the boiler reheater 7 system, the steam passage resistance is low due to its structural complexity, and steam tends to be difficult to flow toward the high-pressure turbine 5 side, which aggravates the above-mentioned phenomenon.

In addition, as mentioned above, in high-temperature, high-pressure turbines, the casing is thick and the rotor diameter is small, so the metal temperature at the surface that comes into contact with the steam reaches the target of 150°C.
Another problem is that there is no effective and effective means for quickly bringing the entire area up to the outer surface of the casing or the center of the rotor to the target temperature.

As mentioned above, the pressure of the high-pressure turbine during warming is maintained at 4 to 5 atg, but this pressure is the saturated steam pressure since the target temperature is 150°C, and the turbine shaft This is because there is a restriction due to the thrust force applied in the direction.

(9), 11 In other words, the rotating body of a steam turbine has a structure that allows it to absorb the axial elongation caused by thermal expansion caused by temperature rise to a certain extent, and the axial force is supported by the thrust bearing. are doing. Therefore, if the difference in elongation between this axial elongation and the casing becomes abnormal, it may cause abnormal wear of the thrust bearing.

In addition, thrust bearings are designed based on the maximum thrust force generated during operation of a steam turbine, and do not take into account irregular conditions for the turbine such as warming. Therefore, when thrust force is generated by warming the turbine, it is naturally necessary to perform the warming within the range allowed by the thrust bearing.

Moreover, in a high-pressure turbine, the areas to which the thrust force due to internal pressure is applied are different at the steam inlet and outlet, and the thrust force is naturally applied to the rotating body in one direction, and the force due to the flow of warming steam is also the same as the thrust force. The pressure during warming cannot be increased indefinitely because the pressure is added up (lO). Therefore, the steam temperature is naturally limited, and the current situation is that it takes quite a long time to raise the temperature of the entire casing and rotating body to the target temperature, that is, to complete warming.

Furthermore, as the warming steam temperature is limited as mentioned above, there is a difference between the steam temperature from the boiler (approximately 350 to 400°C) at the time of turbine startup, and thermal stress still occurs in the loaf part etc. at the time of startup. There are also other problems.

[Purpose of the invention]

In view of these points, the present invention eliminates the restriction on the warming temperature and shortens the warming time, and also reduces the temperature difference between the turbine and the high-temperature steam flowing in from the boiler at the time of startup, thereby reducing the thermal stress generated at the time of startup. An object of the present invention is to provide a steam turbine warming device that can reduce the amount of heat generated by the engine and extend the life of the turbine.

[Summary of the invention]

The present invention provides a first warming steam pipe connected to an intermediate stage of a turbine and having one end connected to a warming steam source or a condenser; corresponds to the first warming steam pipe, and is connected to the condenser or the warming steam source, and the intermediate stage of the turbine, the main steam inlet and the exhaust part. Each warming steam pipe is provided with a pressure detector for detecting the pressure, and each warming steam pipe is actuated by a detection signal from each of the pressure detectors to respectively adjust the pressure in the intermediate stage section, the main steam inlet section, and the exhaust section. The turbine is equipped with a pressure control valve that balances the pressure of each of the above parts during warming of the turbine, thereby performing warming while maintaining the balance of the thrust force and the balance between the forward flow rate and reverse flow rate of the warming steam. It is characterized by:

[Embodiments of the invention]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

In FIG. 2, reference numeral 30 denotes a high-pressure turbine, to which main steam is supplied through a main steam pipe 31 through a main steam stop valve 32 and a steam control valve 33 during operation, and the high-pressure The steam that has performed work in the turbine 30 is led to a reheater 35 through a low-temperature reheat steam pipe 34, where it is reheated and then sent to a medium-pressure turbine (not shown) through a high-temperature reheat steam pipe 36. Ru.

Incidentally, a first warming steam pipe 40 is connected to the intermediate stage portion of the high-pressure turbine 30, and has one end connected to a warming steam source 37 and a warming steam inlet pressure control valve 38 and a stop valve 39 provided in the middle. There is. Also,
A second warming steam pipe 43 having a stop valve 41 and a warming steam ratio/pressure control valve 42 is connected to the downstream side of the steam control valve 33 , and further a high temperature reheat steam pipe 36
A third warming steam pipe 46 having a stop valve 44 and a warming steam ratio/pressure control valve 45 is connected to the upstream side of the reheat steam stop valve (not shown). One end of each of the warming steam pipes 43 and 46 is connected to a condenser 47.

In addition, a pressure detector 4 is installed in the first warming steam pipe 40.
8 is provided, and pressure detectors 49 and 50 are also provided at the initial stage section and the exhaust section of the high pressure turbine 30, respectively. In the figure, reference numerals 51, 52, and 53 are drain pipes connected to the downstream side of the steam control valve 33, the inlet of the high-pressure turbine, and the low-temperature reheat steam pipe 34, respectively.

The warming steam input pressure control valve 38. The opening of the warming steam ratio pressure control valves 42, 45 is controlled by the pressure detectors 4B, 49, 50, respectively, so that the pressures of the intermediate stage section, first stage section, and exhaust section of the turbine are respectively predetermined related pressures. controlled as follows.

That is, FIG. 3 is a control block diagram showing an example of a control device for each of the control valves described above, in which the detection signal from the pressure detector 48 is combined with the setting signal from the first pressure setting device 55 and the comparator 5.
6, and the difference signal is applied to the regulator 57, and the output signal from the regulator 57 controls the opening degree of the warming steam inlet pressure control valve 3B and the pressure at the intermediate stage of the turbine to the first pressure setting. The pressure is controlled to a preset pressure by the device 55.

Further, the detection signal of the pressure calibrator 50 is compared with the difference between the setting signal of the first pressure setting device 55 and the setting signal of the second pressure setting device 59 in the comparator 58, and the deviation signal is adjusted. The output signal from the regulator 60 controls the opening degree of the warming steam pressure control valve 45, and the pressure difference between the intermediate stage section and the exhaust section of the turbine is controlled by the second pressure setting device. The pressure is controlled to the pressure set in step 59.

Similarly, the detection signal of the pressure detector 49 is also compared in the comparator 61 with the difference between the setting signal of the first pressure setting device 55 and the setting signal of the third pressure setting device 62, and the deviation signal is adjusted. The output signal from the regulator 63 controls the opening degree of the warming steam pressure regulating valve 42, and the pressure difference between the intermediate stage section and the first stage section of the turbine is controlled by the third pressure setting device. The pressure is controlled to be equal to the pressure set at 62.

Therefore, during warming before starting the turbine, the main steam stop valve 32. The main valves such as the steam control valve 33 and the reheat steam stop valve (not shown) are kept fully open, and the stop valves 39, 41, and 44 are opened.

Then, the high pressure turbine 3CW before warming>'y-
The inside of the sink is in communication with the condenser 47 through a system of drain pipes 51, 52, 53, etc., so the pressure is in a vacuum region, and the metal parts are completely cold, so the pressure detector 48
Since the signal from is sufficiently low compared to the given set pressure,
The warming steam type low pressure sub-control valve 38 is opened, and warming steam is supplied from the warming steam source 37 to the intermediate stage portion of the turbine. Therefore, for example, if the set pressure of the first pressure setting device 55 is set to 2 atg, the warming steam inlet pressure control valve 38 is kept open until the pressure at the intermediate stage of the turbine reaches 2 atg.

On the other hand, the warming steam that has flowed into the middle stage of the high-pressure turbine 30 sequentially flows to the first stage side and the exhaust side of the turbine, and starts warming the casing and rotor. In this case, both ohming steam outlet pressure control valves 42
, 45 has not yet reached sufficient pressure on both the main steam inlet side and the exhaust side of the turbine, so the warming steam B pressure control valve 45 on the exhaust side is (2-α1) atg.
The warming steam pressure control valve 42 on the main steam inlet side is fully closed until the pressure reaches (2-α2)at.
It is fully closed until the pressure reaches g. In addition, here α□,
α2 is the set pressure of the second pressure setter and the third pressure setter, respectively.

Therefore, when the pressure in the intermediate stage of the turbine rises to 2 atg, which is the set pressure of the first pressure setting device, the warming steam inlet pressure control valve 38 enters a control state to maintain that pressure, and (b) The pressure in the main steam inlet and the exhaust part are controlled and maintained at a pressure state lower by a predetermined pressure than the two atg, respectively, by the pressure regulating valves 42 and 45, and excess steam is discharged from both the ohming steam outlet and the pressure regulating valves 42, 45. It is then discharged to the condenser. During this time, some of the steam that has flowed into the turbine casing comes into contact with low-temperature metals, which removes the heat it possesses and turns it into drains, which are then transferred to the condenser 4 by each drain pipe.
It is discharged at 7.

In this case, the discharge of the above-mentioned excess steam is necessary in order to prevent the IF from accumulating in the casing, etc., since there is a large amount of steam that becomes a drain inside the casing, etc.
Although it is unavoidable, in the range where thrust bearings are permissible from the viewpoint of energy saving, the second and third pressure setting devices 59 and 62 force the warming steam pressure control valves 45 and 42. It can also be completely closed.

In this way, the metal temperature of each part increases with respect to the pressure 2atg set by the first pressure setting device 55, approaches the saturation temperature of that pressure (and further increases the temperature of the metal at the first pressure setting device 55). Increase the setting value to an arbitrary value, for example 4 atg.

Then, by the same operation as described above, the state is maintained at 4 atg at the warming steam inlet, (4-α1) ajg at the exhaust side, and (4-α2) atg at the main steam inlet side. Therefore, high-pressure turbines, etc.
It is warmed up to the saturation temperature of the atg vapor.

By gradually changing the set pressure of the first pressure setting device in this way, warming to the target temperature can be achieved.

FIG. 4 is a diagram showing the relationship between turbine metal temperature and warming steam pressure versus time, where the curve shown by a broken line is the warming pressure and temperature rise curve in a conventional device, and curve A is the turbine σ ) Warming steam pressure 1 curve AI is the turbine internal metal temperature 2 curve Ao is the turbine external metal temperature. Further, the curve shown by the solid line is the warming steam pressure and temperature rise curve by the device of the present invention, and the curve B is the warming steam pressure of the turbine,
Curve B■ is the turbine internal metal temperature, and curve BO is the turbine external metal temperature.

As can be seen from Fig. 5, in the conventional device, curve A cannot raise the pressure above the specified pressure, and the turbine external metal temperature (curve A, o) is lower than the turbine internal metal temperature (curve Ar). There is no other way but to wait for the temperature to follow the pressure, and it is impossible to raise the temperature shown by the curve AO*AI above the temperature corresponding to the pressure shown by the curve A.

On the other hand, curve B shows that by arbitrarily increasing the setting value of the warming steam pressure while observing the metal temperature status of each part of the turbine, the turbine can be warmed to an arbitrary temperature level as shown by curves BT and Bo.
You can increase the warming effect in a short time.

In this way, when the metal temperature of each part rises to the target temperature T'C and stabilizes, the set pressure of the first pressure setting device is lowered to the original value and the warming steam is cut off. The pressure inside the turbine, etc. is released, and the warming steam system is completely cut off from the turbine's driving steam system, thereby completing the warming of the turbine and making it possible to prepare for startup of the turbine.

By the way, Figure 5 shows the schedule from the start of the steam turbine to reaching the target load, and the relationship between the steam temperature and the turbine metal temperature (represented by the metal temperature after the first stage). The axis shows time and the vertical axis shows temperature.

Therefore, the curve Ts shows the main steam temperature from the boiler,
The main steam temperature increases as the turbine or boiler load increases, and reaches the rated main steam temperature at acid intermediate load. Further, the curve TM shows the change in the representative metal temperature of the turbine due to warming in the conventional device, whereas the curve Tyt shows the change in the representative metal temperature of the turbine when warming is performed by the device of the present invention, and is similar to the above-mentioned curve. In the present invention, the temperature of each metal part can be warmed to a higher state before starting the turbine than in the conventional apparatus, so that the starting point of the curve TM' is higher than the curve TM.

Therefore, if we assume that the schedule for starting the turbine in the upper stage of FIG. 5 is the same, there are three major differences between curve TM and curve TM'.

In other words, the width of the temperature change in the metal part is larger for the curve TM than for the curve TM', and also for the rate of temperature change, which represents the speed of temperature change in the metal, the curve TM is larger than the curve TM', and furthermore, the curve TM is larger than the curve TM'. Ts is the main steam temperature at
Regarding the difference between the temperature of the metal part and the temperature of the metal part, the curve TM is similarly larger than the curve TM'.

From these facts, it can be seen that the thermal stress level generated in the turbine when starting the turbine is much smaller in the case of curve TM' than in the case of curve TM', that is, in the case of the present invention. .

In addition, Figure 6 shows the lifetime consumption index of the turbine, which serves as an indicator for the operation of the steam turbine.
The lifetime consumption of the turbine is determined by the width ΔT of the temperature change of the metal part and the rate of temperature change of the metal part, as shown in the figure. Each value on the curve of the graph represents an index of life consumption, and this 1 cycle is defined as one cycle of starting and stopping the turbine.
It is the life index consumed per cycle.

As can be seen from the graph in Figure 6, if the consumption over the lifespan is the same, if the temperature change range of the metal part is large, the temperature change rate needs to be small, and the temperature change with the same temperature change range is necessary. If the rate is a dog, it means consuming a large lifespan.

As is clear from the above, if the temperature change width by the conventional device is △T, then the temperature change width part T by the present invention
' becomes smaller than ΔT, resulting in the following effect.

In other words, if the values of the same lifetime consumption rate, for example, 0.03%, are made different, the temperature change rate can be set high in the case of the present invention, and the time from starting the turbine to reaching the target load can be shortened. be able to.

On the other hand, if the temperature increase rate is the same and compared with the prior art, the temperature change width ΔT' can be kept to a value even smaller than the life consumption rate of 0.3ch.

Incidentally, in the above embodiment, the warming steam inlet section is provided in the intermediate stage of the turbine, and this intermediate stage is designed to absorb rotational torque generated in the forward rotation direction due to the flow of warming steam from the inlet to the exhaust side of the high-pressure turbine. and,
A paragraph is selected in which the difference between the rotational torques generated in the opposite rotational direction due to the flow of warming steam from the inlet to the main steam pipe side satisfies the following relationship so that the turning gear will not be dislocated.

1 Forward rotation side torque - Reverse rotation side torque 1 < Turning disengagement required torque The range that satisfies the above relationship includes the range where the forward rotation side l・lux is smaller than the reverse rotation side torque, so it is not a single point but a wide range. Therefore, you can select any paragraph you want. Therefore, if a dedicated entry port is provided in the high-pressure casing as an inlet for warming steam, or if there is an appropriate bleed system within the range that satisfies the above relationship, it is possible to use this bleed pipe.

Further, in the above embodiment, the warming steam introduction part is set at one point in the middle stage of the high-pressure casing, but it may be introduced at a plurality of points separately, for example, into the upper half and the lower half. Furthermore, the flow of the warming steam is reversed to that in the above embodiment, that is, one end of the first warming steam pipe is connected to the condenser for releasing the warming steam, and the second warming steam pipe is connected to the condenser.
．． One end of the third warming steam pipe may be connected to a warming steam source, and the warming steam may be introduced from the warming steam pipe into the high pressure turbine.

Furthermore, the part corresponding to the high-pressure casing may be separated into an ultra-high pressure part and a high-pressure part to be warmed.
Even in this case, the same effect can be obtained by replacing the high-pressure casing with an ultra-high-pressure casing.

〔Effect of the invention〕

As explained above, in the present invention, warming steam pipes are connected to the intermediate stage section, the main steam inlet side, and the exhaust section side of the turbine, respectively, and warming steam is introduced from the intermediate stage section and exhausted from the other warming steam pipes. Alternatively, warming steam is introduced from the warming steam pipe connected to the main steam inlet side and the exhaust side and exhausted from the intermediate stage part, and the pressure of the intermediate stage part and the main steam inlet side and exhaust side are Since the pressure relationship is controlled to be constant during warming, the thrust force due to the pressure of the warming steam can be reduced.
It is possible to increase the warming vapor pressure. Therefore, the warming steam temperature can be increased accordingly, and even the thick outer surface of the casing can be actively heated, making it possible to warm the average temperature to a high level in a shorter time than in the past. can. Therefore, the difference in temperature from the main steam flowing in at the time of startup can be reduced, and thermal stress at the time of turbine startup can be reduced, reducing life consumption and making it possible to start the turbine more safely. Moreover, when the warming steam is introduced from the intermediate stage of the turbine, the turbine is warmed preferentially over the reheater, etc., and the turbine can be warmed efficiently.

[Brief explanation of drawings]

Fig. 1 is a system diagram showing an outline of a conventional steam turbine warming device, Fig. 2 is a schematic system diagram of a warming device of the present invention, and Fig. 3 is a block diagram of a control device for warming steam inlet pressure and outlet pressure control valves. Figure 4 is a diagram showing changes in warming steam pressure and temperature;
The figure is a graph showing the schedule from the start of the steam turbine to reaching the target load and the relationship between the temperature of the metal part of the turbine and the steam temperature, and FIG. 6 is a graph showing the lifetime consumption index of the turbine. 30... High pressure turbine, 37... Warming steam source, 38... Warming steam hole [1 pressure control valve, 4
0...First warming steam pipe, 42...B pressure control valve for warming steam, 43...Second warming steam pipe, 45...B pressure leg valve for warming steam, 46...・Third warming steam pipe, 48, 4
9, 50...pressure detector, 55...first pressure setting device, 59...second pressure setting device, 62...third pressure setting device. Applicant's agent Kiyoshi Inomata (27) 1st item, 2nd item, 83 Figure 2, 4th item, 5th item 6'' ΔLΔT -C 33-

Claims (1)

[Claims] 1. A first warming steam pipe connected to the intermediate stage of the turbine and having one end connected to a warming steam source or a condenser, and connected to the main steam inlet and exhaust of the turbine, respectively. first and third warming steam pipes connected at one end to a condenser or a warming steam source in correspondence with the upper air first warming steam pipe; an intermediate stage of the turbine; a main steam inlet; A pressure detector detects the pressure in the exhaust section, and each warming steam pipe is activated by a detection signal from each of the pressure detectors to respectively adjust the pressure in the intermediate stage section, main steam inlet section, and exhaust section. By balancing the pressure of each of the above parts during warming of the turbine, warming is performed while maintaining the balance of thrust force and the balance between the forward flow rate and reverse flow rate of the warming steam. It is characterized by
Steam turbine warming device. 2. The first warming steam pipe is a warming steam introduction pipe, and the second. Claim 1, wherein the third warming steam pipe is a warming steam relief pipe.
A warming device for a steam turbine according to paragraph 1. 36, the first warming steam pipe is a warming steam relief pipe, and the second. 2. The steam turbine warming device according to claim 1, wherein the third warming steam pipe is a warming steam introduction pipe. 4. The steam turbine warming device according to any one of claims 1 to 3, wherein the second warming steam pipe is connected to the main steam pipe. 5. The steam turbine warming device according to any one of claims 1 to 3, wherein the third warming steam pipe is connected to a boiler reheat steam pipe.