JP2018066362A - Steam turbine and temperature control method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a steam turbine capable of setting a clearance between a rotor and an inner casing to an appropriate value, and a temperature control method.SOLUTION: A steam turbine 100 comprises: a rotor 1; an inner casing 2; stationary blades 14; an outer casing 3; a cooling and heating section 7 which has a heat medium passage 32A capable of causing a heat medium to flow therethrough and can cool or heat a general section 19; a heat medium supply section which can supply the heat medium to the heat medium passage 32A; a first measurement section which measures a temperature of a large heat capacity section; a second measurement section which measures a temperature of the general section 19; and a temperature control section which controls the heat medium supply section such that, based on a temperature difference between the temperature of the large heat capacity section measured by the first measurement section and the temperature of the general section 19 measured by the second measurement section, the temperature difference is equal to a predetermined threshold or less.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a steam turbine and a temperature control method.

  The steam turbine includes a rotor that rotates about an axis and a casing that covers the rotor. The rotor has a plurality of moving blades arranged around a rotor shaft extending in the axial direction about the axis. The casing is provided with a plurality of stationary blades arranged around the rotor on the upstream side of the moving blade.

  For example, Patent Document 1 describes a steam turbine having an inner casing to which a stationary blade is attached and an outer casing that covers the inner casing from the outside. In this steam turbine, a flow path is formed between the outer casing and the inner casing to distribute the working steam that has flowed through the working steam flow path between the inner casing and the rotor. Thereby, an outer casing and an inner casing are cooled with the working steam which flows through a flow path.

JP 2012-107618 A

  By the way, even when the flow path through which steam flows is formed between the outer casing and the inner casing as described above, depending on the operating condition of the steam turbine, the tip of the moving blade and the inner peripheral surface of the inner casing And the clearance between the tip of the stationary blade and the rotor may be inadvertently narrowed.

  This invention is made in view of the said situation, and provides the steam turbine and temperature control method which can set the clearance between a rotor side and an inner casing side to an appropriate value.

In order to solve the above problems, the following configuration is adopted.
According to the first aspect of the present invention, the steam turbine is provided with a plurality of moving blades on the outer peripheral surface, and rotates around the axis, and covers the rotor from the outside in the radial direction centered on the axis, A plurality of inner casings forming a first steam flow path through which steam circulates between the outer peripheral surface of the rotor and the inner peripheral surface of the inner casing, the first steam flow together with the plurality of blades A stationary blade disposed in the passage, a general part, and a large heat capacity part having a larger heat capacity than the general part, covers the inner casing from the outside in the radial direction, and communicates with the first steam channel. An outer casing in which a second steam flow path for circulating the steam is formed between the outer casing and the outer peripheral surface of the inner casing, and a heat medium passage through which a heat medium can flow. A cooling / heating part capable of cooling or heating the part, A heat medium supply unit capable of supplying a heat medium to the heat medium passage, a first measurement unit that measures the temperature of the large heat capacity unit, a second measurement unit that measures the temperature of the general unit, and the first measurement Based on the temperature difference between the temperature of the large heat capacity part measured by the part and the temperature of the general part measured by the second measurement part, the temperature difference is equal to or less than a preset threshold value. A temperature control unit that controls the medium supply unit.
Of the large heat capacity part and the general part of the outer casing, the general part is easier to heat and cool, so when the outer casing is heated by high-temperature steam during startup or when it stops from load operation, etc. A temperature difference is generated between the large heat capacity part and the general part. However, as in the first aspect of the present invention, the temperature control unit cools or heats the general part so that the temperature difference between the temperature of the general part and the large heat capacity part is not more than a preset threshold value. . Therefore, it is possible to suppress the deformation of the outer casing due to the temperature distribution in the large heat capacity portion and the general portion of the outer casing, so that the inner casing supported by the outer casing is displaced, and the moving blade and the inner casing are displaced. It is possible to suppress the clearance between the stator blade and the rotor between the stator blade and the rotor from becoming smaller than that during the load operation.
Therefore, the clearance can be set to an appropriate value regardless of the driving situation. Therefore, the clearance during the load operation can be further reduced, and the efficiency during the load operation can be improved.

According to the second aspect of the present invention, in the steam turbine according to the first aspect, the outer casing includes a lower half covering the lower half of the inner casing, an upper half covering the upper half of the inner casing, May be provided. Further, the large heat capacity portion includes a lower half flange portion that protrudes outward from the opening edge of the lower half portion, and an upper half flange that protrudes outward from the opening edge of the upper half portion and can be fixed to the lower half flange portion. It may be made up of parts.
By configuring in this way, the temperature of the general part of the upper half and the temperature of the general part of the lower half do not rise or fall excessively compared to the temperatures of the lower half flange and the upper half flange, respectively. It can be controlled by the temperature controller.

According to the third aspect of the present invention, the cooling / heating unit according to the first or second aspect may include a first heat medium passage extending along the axis as the heat medium passage.
By comprising in this way, a heat carrier can be poured in an axial direction. Therefore, the temperature variation of the general part in the axial direction can be suppressed.

According to the fourth aspect of the present invention, the cooling and heating unit according to the third aspect may include a plurality of the first heat medium passages spaced apart in the circumferential direction of the outer casing.
By comprising in this way, the temperature in the several position of a general part can be adjusted separately in the circumferential direction of an outer casing. Therefore, for example, even when the temperature in the circumferential direction of the general part is locally increased or decreased, the temperature in the circumferential direction of the general part can be made uniform.

According to the fifth aspect of the present invention, the cooling and heating unit according to the first or second aspect may include a second heat medium passage extending in a circumferential direction of the outer casing as the heat medium passage.
By comprising in this way, a heat carrier can be poured in the circumferential direction of an outer casing. Therefore, the temperature variation of the general part in the circumferential direction of the outer casing can be suppressed.

According to the sixth aspect of the present invention, the cooling and heating unit according to the fifth aspect may include a plurality of the second heat medium passages spaced apart in the axial direction.
By comprising in this way, the temperature in the several position of a general part can be adjusted separately in the axial direction of an outer casing. Therefore, for example, even when there is a position where the temperature locally rises or falls among a plurality of positions in the axial direction of the general part, the temperature in the axial direction of the general part can be made uniform. .

According to the seventh aspect of the present invention, the steam turbine according to any one of the third to fifth aspects may include a cooling and heating unit inside the general part.
By comprising in this way, a part of general part can be used as a cooling heating part. Therefore, for example, compared with the case where the cooling heating part is provided in the outer surface side of an outer casing, the enlargement of an outer casing can be suppressed.

According to the eighth aspect of the present invention, the steam turbine according to any one of the first to seventh aspects is for a large heat capacity part capable of flowing a heat medium capable of cooling or heating the large heat capacity part. You may provide the large heat capacity part cooling heating part which has the heat-medium channel | path.
By configuring in this way, the temperature of the large heat capacity part can be brought close to the temperature of the general part, so that the temperature difference between the large heat capacity part and the general part is larger than a preset threshold value. However, the temperature difference can be quickly reduced to a threshold value or less by both the cooling heating unit and the large heat capacity unit cooling heating unit.

According to the ninth aspect of the present invention, the steam turbine according to any one of the first to eighth aspects includes a heating unit that heats at least one of the general part and the large heat capacity part, or the general part. And a cooling part that cools at least one of the large heat capacity part.
By comprising in this way, in addition to a cooling heating part, at least one of a general part and a large heat capacity part can be heated or cooled by a heating part or a cooling part.

According to a tenth aspect of the present invention, the steam turbine according to any one of the first to ninth aspects is disposed so as to be sandwiched between the general parts in the circumferential direction of the outer casing, and from the general part Also, a heat capacity expanding section having a large heat capacity may be provided.
Since this heat capacity expansion part has a larger heat capacity than the general part, there is little difference in heat capacity from the large heat capacity part. Therefore, it is difficult for a temperature difference to occur between the heat capacity expansion portion and the large heat capacity portion. And since the heat capacity expansion part is disposed so as to be sandwiched between the general parts, the temperature of the general part changes following the temperature change of the heat capacity expansion part. As a result, a temperature difference between the general part and the large heat capacity part is hardly generated, and deformation due to the temperature difference between the general part and the large heat capacity part can be suppressed.

According to an eleventh aspect of the present invention, a temperature control method includes an inner casing and an outer casing, and the outer casing includes a general part and a large heat capacity part having a larger heat capacity than the general part. A temperature difference between the temperature of the general part, the temperature of the large heat capacity part, and the temperature difference between the temperature of the general part and the temperature of the large heat capacity part in advance. Cooling or heating the general part so as to be equal to or lower than a set threshold value.
By comprising in this way, since the temperature difference of a general part and a large heat capacity part can be made into the threshold value set beforehand, a deformation | transformation of an outer casing can be suppressed. As a result, the clearance during the load operation can be further reduced, and the efficiency of the steam turbine can be improved.

According to a twelfth aspect of the present invention, in the temperature control method according to the eleventh aspect, the temperature difference between the temperature of the general part and the temperature of the large heat capacity part is not more than a preset threshold value. The step of heating the general part and cooling the large heat capacity part may be included.
By comprising in this way, the temperature difference of the temperature of a general part and the temperature of a large heat capacity part can be made small rapidly.

  According to the steam turbine and the temperature control method according to the present invention, the clearance between the moving blade and the casing and the clearance between the stationary blade and the rotor can be suppressed regardless of the operation state, and the clearance can be further increased during the load operation. Can be reduced.

It is sectional drawing which shows schematic structure of the steam turbine in 1st embodiment of this invention. It is sectional drawing orthogonal to the axis line of the steam turbine in 1st embodiment of this invention. It is a block diagram showing a schematic structure concerning temperature control of a steam turbine in a first embodiment of this invention. It is a flowchart of the temperature control method in 1st embodiment of this invention. It is sectional drawing corresponded in FIG. 1 in the modification of 1st embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in the modification of 1st embodiment of this invention. It is sectional drawing equivalent to FIG. 1 in 2nd embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in 2nd embodiment of this invention. It is sectional drawing equivalent to FIG. 1 in the modification of 2nd embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in the modification of 2nd embodiment of this invention. It is sectional drawing equivalent to FIG. 2 of the steam turbine in 3rd embodiment of this invention. It is a flowchart of the temperature control method in 3rd embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in the modification of 3rd embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in 4th embodiment of this invention. It is sectional drawing equivalent to FIG. 2 in 5th embodiment of this invention. It is sectional drawing equivalent to FIG. 1 which shows the steam turbine in the other aspect of 1st embodiment of this invention.

(First embodiment)
Next, a steam turbine according to a first embodiment of the present invention will be described with reference to the drawings.
FIG. 1 is a cross-sectional view showing a schematic configuration of a steam turbine according to a first embodiment of the present invention. FIG. 2 is a cross-sectional view orthogonal to the axis of the steam turbine in the first embodiment of the present invention. FIG. 3 is a block diagram showing a schematic configuration relating to temperature control of the steam turbine in the first embodiment of the present invention.
The steam turbine of this embodiment converts the thermal energy of steam into rotational energy and outputs it. For example, when this steam turbine is a steam turbine for power generation, the rotational energy output from the steam turbine is generated by the generator. Converted into electrical energy.

  As shown in FIGS. 1 to 3, the steam turbine 100 of the first embodiment includes a rotor 1, an inner casing 2, an outer casing 3, a bearing portion 4, a seal portion 5, and a main steam supply portion 6. And a cooling and heating unit 7, a heat medium supply unit 8, a temperature measurement unit 9, and a temperature control unit 10.

As shown in FIG. 1, the rotor 1 includes a rotor body 11 and a moving blade 12. The rotor 1 is rotatable around the axis Ar.
The rotor body 11 extends in the direction of the axis Ar. The rotor body 11 is disposed so as to penetrate the outer casing 3, and both end portions 11 a and 11 b are rotatably supported outside the outer casing 3.
The moving blade 12 is provided on the outer peripheral side of the rotor body 11. More specifically, a plurality of rotor blades 12 are provided in the rotor body 11 at intervals in the circumferential direction of the rotor body 11. These rotor blades 12 extend from the outer peripheral surface 11 c of the rotor body 11 in a radial direction centered on the axis Ar. Further, the moving blades 12 are provided in a plurality of stages at intervals in the axial line Ar direction at an intermediate portion of the rotor body 11 in the axial line Ar direction.

  The inner casing 2 forms a first steam passage 13 between the rotor 1 and the main steam that is a working fluid. The inner casing 2 covers the rotor 1 from the outer side in the radial direction of the rotor 1. The inner casing 2 in this embodiment covers only the middle part of the rotor 1 in the axis Ar direction from the outside.

  A stationary blade 14 is provided on the inner peripheral side of the inner casing 2. These stationary blades 14 are fixed to the inner casing 2 via, for example, a blade ring (not shown). A plurality of these stationary blades 14 are arranged at intervals in the circumferential direction around the axis Ar. The stationary blades 14 are provided in a plurality of stages at intervals in the direction of the axis Ar, and are arranged on the upstream side of the above-described moving blade stage in the direction in which the main steam flows.

  In the radial direction of the rotor 1, the clearance between the end portion of the stationary blade 14 and the rotor 1 is such that contact between the stationary blade 14 and the rotor 1 does not occur during startup, stoppage, and load operation. C1 is preset. Similarly, in the radial direction of the rotor 1, the clearance between the end portion of the moving blade 12 and the member disposed outside thereof is the same as that between the moving blade 12 and the inner side at the time of starting, stopping, and load operation. The clearance C2 is set in advance so that the contact with the casing 2 does not occur. Here, in the radial direction of the rotor 1 described above, the member disposed outside the end portion of the moving blade 12 is an inner peripheral surface of the inner casing 2 or a split attached to the inner peripheral surface of the inner casing 2. A member such as a ring can be exemplified.

  The inner casing 2 is formed with an inner steam inlet 15 through which main steam flows into the first steam channel 13 from the radially outer side. The inner steam inlet 15 is disposed on the side close to the first end portion 11a of the inner casing 2 in the axis Ar direction. Further, the inner casing 2 is formed with an inner discharge port 16 for discharging main steam at the end 2a opposite to the inner steam inlet 15 in the axis Ar direction. On the other hand, an inner through portion 17 through which the rotor 1 passes is formed at the end 2b on the opposite side of the inner discharge port 16 in the direction of the axis Ar. The main steam that has flowed into the first steam flow path 13 from the inner steam inlet 15 flows along the axis Ar from the inner steam inlet 15 toward the inner outlet 16, and from the inner outlet 16 to the outside of the inner casing 2, that is, the inner side. It is discharged to the second steam flow path 18 between the casing 2 and the outer casing.

  The outer casing 3 is disposed so as to cover the inner casing 2 from the outside. In other words, the inner casing 2 is disposed in an internal space defined by the outer casing 3. The outer casing 3 forms a second steam flow path 18 between the outer casing 3 and the inner casing 2. The outer casing 3 includes a general part 19 and a flange part (large heat capacity part) 20.

  The outer casing 3 in this embodiment includes an upper half 21 and a lower half 22. The upper half 21 covers the upper half of the inner casing 2, and the lower half 22 covers the lower half of the inner casing 2. That is, the outer casing 3 has a shape that can be divided into an upper half 21 and a lower half 22 with a horizontal plane passing through the axis Ar as a boundary.

The outer casing 3 supports the inner casing 2 in a fixed manner. An outer steam inlet 23 and an outer steam outlet 24 are formed in the outer casing 3. The outer steam inlet 23 communicates with the inner steam inlet 15 of the inner casing 2. Further, the outer steam outlet 24 communicates with the second steam flow path 18. With such a configuration, the main steam supplied from the main steam supply unit 6 flows into the first steam channel 13 from the outer steam inlet 23 through the inner steam inlet 15. Further, the main steam discharged from the inner discharge port 16 is discharged from the outer steam outlet 24 to the outside of the outer casing 3 through the second steam flow path 18 formed between the outer casing 3 and the inner casing 2. Is done.
The outer casing 3 is formed with through portions 25 through which the rotor body 11 described above penetrates at both end portions 3a and 3b in the axis Ar direction.

  As shown in FIG. 2, the flange portion 20 includes an upper half flange portion 26 formed on the upper half portion 21 and a lower half flange portion 27 formed on the lower half portion 22. The upper half flange portion 26 is formed so as to protrude outward from the opening edge 28 of the upper half portion 21. The upper half flange portion 26 is formed over the entire circumference of the opening edge 28. Similarly, the lower half flange portion 27 is formed so as to protrude outward from the opening edge 29 of the lower half portion 22. In this embodiment, the upper half flange portion 26 and the lower half flange portion 27 respectively include mating surfaces 30 and 31 extending in the horizontal direction. The upper half flange portion 26 and the lower half flange portion 27 are coupled by bolts (not shown) or the like in a state where the respective mating surfaces 30 and 31 are abutted.

  The general portion 19 in this embodiment is a portion other than the flange portion 20, and is formed thinner than the flange portion 20 in a cross section (see FIG. 2) orthogonal to the axis line Ar. Therefore, the flange portion 20 has a larger heat capacity than the general portion 19. The outer casing 3 in this embodiment is formed of a metal such as stainless steel.

  Here, in this embodiment, the supported portion is formed so that the upper half flange portion 26 protrudes outside the lower half flange portion 27 described above (not shown). The supported portion (not shown) is supported from below by a support portion (not shown) extending in the vertical direction. The lower surface of the supported portion (not shown) and the upper surface of the supporting portion (not shown) are horizontal surfaces, and the supported portion (not shown) is supported by the supporting portion (not shown). Usually, the lower surface of the supported portion (not shown) and the upper surface of the supporting portion (not shown) are in close contact with each other in parallel.

  On the other hand, when a large temperature difference is generated between the general portion 19 and the flange portion 20 of the outer casing 3, the lower surface of the supported portion is caused by the difference in elongation in the axis Ar direction between the general portion 19 and the flange portion 20. There is a case where the upper surface of the support portion is in an oblique contact state. Then, the outer casing 3 may be displaced either up or down, and the relative position between the rotor 1 and the inner casing 2 may change. Although the case where the supported portion (not shown) is formed in the upper half flange portion 26 has been described as an example, the case where the supported portion (not shown) is formed in the lower half flange portion 27 is also possible. Also in this case, the outer casing 3 is displaced either up or down in the same manner as described above.

  The seal portion 5 is installed in a gap between the rotor 1 that is a rotating body and the inner casing 2 and the outer casing 3 that are stationary bodies. The seal portion 5 suppresses the movement of the working fluid in the direction of the axis Ar in the vicinity of the outer peripheral surface 11 c of the rotor 1. The seal portions 5 in this embodiment are respectively installed in the two through portions 25 of the outer casing 3 and the inner through portions 17 of the inner casing 2.

  The main steam supply unit 6 generates steam using, for example, exhaust heat of a gas turbine (not shown), and the steam is supplied to the first steam described above via a main steam pipe (not shown). Supply to the flow path 13. Generally, a main steam valve (not shown) is provided in the main steam pipe, and main steam corresponding to the opening degree of the main steam valve is supplied to the first steam channel 13.

  The cooling heating unit 7 has a heat medium passage 32 through which a heat medium can flow. According to the cooling and heating unit 7, the general unit 19 can be cooled or heated by flowing a heat medium through the heat medium passage 32. As shown in FIGS. 1 and 2, the cooling and heating unit 7 in the first embodiment includes a first heat medium passage 32 </ b> A that extends in the axis Ar direction as the heat medium passage 32. The cooling and heating unit 7 is formed so as to protrude outward from the outer peripheral surface of the general unit 19. The cooling heating unit 7 in the first embodiment exemplifies a case where the outline of the first heat medium passage 32A in the cross section orthogonal to the axis Ar is a quadrilateral shape, but is not limited to this shape.

  As shown in FIG. 2, a plurality of cooling and heating units 7 are provided at intervals in the circumferential direction of the outer casing 3. The cooling heating part 7 in this 1st embodiment has illustrated the case where the upper half part 21 and the lower half part 22 are provided 3 each. Further, the cooling and heating unit 7 is arranged at equal intervals between the left flange portion 20 and the right flange portion 20 as viewed from the direction of the axis Ar in the circumferential direction of the outer casing 3. In the cooling and heating unit 7 formed in this way, the heat medium supply unit 8 is connected to one end in the axis Ar direction via a heat medium supply pipe (not shown) (see FIG. 3). Moreover, the other end part in the axis line Ar direction of the cooling heating part 7 is connected to the discharge pipe (not shown). In other words, the heat medium flowing into the first heat medium passage 32A from the heat medium supply pipe (not shown) is exchanged with the general part 19 and then discharged through the discharge pipe (not shown).

FIG. 3 is a block diagram showing a schematic configuration relating to temperature control of the steam turbine in the first embodiment of the present invention.
As shown in FIG. 3, the heat medium supply unit 8 supplies a cooling medium or a heating medium, which is a heat medium, toward the cooling heating unit 7. The cooling medium is a heat medium that can cool the general part 19 when the steam turbine 100 is started. As this cooling medium, air fed by a compressor or the like can be used. The heating medium is a heating medium that can heat the general part 19 when the steam turbine 100 stops. As this heating medium, steam generated by an auxiliary boiler or the like can be used. The heat medium supply unit 8 can selectively supply the cooling medium and the heating medium toward the cooling heating unit 7 in accordance with a control command from the temperature control unit 10. Further, the heat medium supply unit 8 can linearly adjust the supply amount of the heat medium to the plurality of cooling heating units 7. Furthermore, the heat medium supply unit 8 can individually adjust the supply amount of the heat medium to the plurality of cooling heating units 7.

As shown in FIGS. 2 and 3, the temperature measuring unit 9 measures the temperature of the outer casing 3. The measurement result of the temperature measurement unit 9 is output toward the temperature control unit 10. The temperature measurement unit 9 includes a first measurement unit 9a and a second measurement unit 9b.
The first measurement unit 9 a measures the temperature of the flange unit 20. More specifically, the first measuring portion 9a is attached to the left and right flange portions 20 sandwiching the axis Ar in the cross section orthogonal to the axis Ar. In this embodiment, the case where the 1st measurement part 9a is attached to the side surface of the flange part 20 is illustrated.

  The second measuring unit 9 b measures the temperature of the general unit 19. More specifically, the second measurement unit 9 b measures the temperature of the outer peripheral surface 19 a of the general unit 19. A plurality of second measuring portions 9b are installed at intervals in the circumferential direction of the general portion 19. The second measuring unit 9b in this embodiment illustrates a case where three are provided in each of the upper half 21 and the lower half 22. These 2nd measurement parts 9b can measure the temperature of each position where the some cooling heating part 7 is arrange | positioned separately.

  The temperature control unit 10 controls the heat medium supply unit 8 based on the temperature difference between the temperature of the flange unit 20 and the temperature of the general unit 19. More specifically, the temperature control unit 10 obtains a temperature difference between the temperature of the flange unit 20 measured by the first measurement unit 9a and the temperature of the general unit 19 measured by the second measurement unit 9b. Furthermore, the temperature control unit 10 controls the supply of the heat medium by the heat medium supply unit 8 so that the temperature difference is equal to or less than a preset threshold value.

  Here, the temperature control unit 10 in this embodiment obtains the temperature difference between the measurement results of the six second measurement units 9b with respect to the measurement results of the two first measurement units 9a so that all are equal to or less than the threshold value. A heat medium having an appropriate flow rate is supplied to each cooling and heating unit 7 individually. The temperature control unit 10 supplies the heat medium based on the temperature difference between the average temperature measured by the plurality of first measurement units 9a and the average temperature measured by the plurality of second measurement units 9b. The unit 8 may be controlled.

(Temperature control method of the first embodiment)
Next, a temperature control method using a steam turbine having the above-described configuration will be described with reference to the drawings. Note that the temperature control method in the first embodiment can be performed by, for example, executing a program recorded on a recording medium by the computer system of the temperature control unit 10 (the following embodiments and modifications are also described below). The same).

FIG. 4 is a flowchart of the temperature control method in the first embodiment of the present invention.
As shown in FIG. 4, first, the temperature control unit 10 determines whether or not the operating state of the steam turbine 100 is at startup (step S01). For example, the determination as to whether or not the engine is being started can be performed by determining whether or not the elapsed time since the operation input for starting the steam turbine 100 is greater than or equal to a predetermined threshold. Further, at the time of start-up, it means an operation state from when the main steam is not supplied to the steam turbine 100 until the load operation starts.

  As a result of this determination, when it is determined that the system is at the time of startup (Yes in step S01), the temperature control unit 10 acquires the temperature of the flange unit 20 from the first measurement unit 9a (step S02) and the second measurement. The temperature of the general part 19 is acquired from the part 9b (step S03). In addition, the timing which acquires the temperature of the flange part 20 and the general part 19 is not restricted to said order, For example, you may be simultaneous.

  Next, the temperature control unit 10 calculates a temperature difference between the temperature of the flange unit 20 and the temperature of the general unit 19 (step S04). And the temperature control part 10 determines whether this calculated temperature difference is below a preset threshold value (step S05). Here, the preset threshold value is a temperature difference threshold value for determining that the outer casing 3 can be deformed.

As a result of this determination, when it is determined that the temperature difference is not less than or equal to the threshold value (No in step S05), the temperature control unit 10 supplies the cooling medium to the cooling and heating unit 7 so that the temperature difference is less than or equal to the threshold value. . Thereby, the general part 19 is cooled.
If it is determined that the temperature difference is equal to or smaller than the threshold value (Yes in step S05), the general control unit 19 does not need to be cooled, and the temperature control unit 10 temporarily ends the series of control processes described above.

  Here, when the supply of the high-temperature main steam is started when the steam turbine 100 is started, the temperature of the general part 19 is higher than that of the flange part 20 having a larger heat capacity than the general part 19. Thus, when the temperature rise of the general part 19 is fast, the general part 19 has a larger thermal elongation than the flange part 20. Therefore, the outer casing 3 is deformed. Then, the inner casing 2 supported by the outer casing 3 is displaced. That is, by making the above-mentioned temperature difference equal to or less than the threshold value, the inner casing 2 is not displaced as a result.

  The cooling of the general part 19 by the cooling medium is continued until the temperature difference becomes equal to or less than the threshold value or until the steam turbine 100 shifts to the load operation.

  On the other hand, when it is determined that the steam turbine 100 is not at startup (No in step S01), the temperature control unit 10 determines whether or not the steam turbine 100 is stopped. For example, the determination as to whether or not the vehicle is stopped can be performed by determining whether or not the elapsed time after the operation input for stopping the steam turbine 100 is greater than or equal to a predetermined threshold value. Here, at the time of stop means an operation state from the state where the load operation is performed until the rotor 1 is completely stopped. In addition, when stopping, there are a stop by performing a stop operation for load operation and a so-called trip that is a stop due to occurrence of an abnormality.

If it is determined that the steam turbine 100 is not stopped (No in step S07), the temperature control unit 10 is in an operating state that is neither at the start time nor at the stop time, that is, during the load operation. Is temporarily terminated.
On the other hand, when it is determined that the steam turbine 100 is stopped (Yes in Step S07), the temperature control unit 10 acquires the temperature of the flange portion 20 from the first measurement unit 9a (Step S08), and The temperature of the general part 19 is acquired from the second measuring part 9b (step S09).

  Next, the temperature control unit 10 calculates a temperature difference between the temperature of the flange unit 20 and the temperature of the general unit 19 (step S10). And the temperature control part 10 determines whether this calculated temperature difference is below a preset threshold value (step S11). Here, the preset threshold value is a threshold value of a temperature difference for determining that the outer casing 3 can be deformed, similarly to the above-described threshold value.

As a result of this determination, if it is determined that the temperature difference is not less than or equal to the threshold value (No in step S11), the temperature control unit 10 supplies the heating medium to the cooling and heating unit 7 so that the temperature difference is less than or equal to the threshold value. . Thereby, the general part 19 is heated.
Further, when it is determined that the temperature difference is equal to or less than the threshold (Yes in step S11), it is not necessary to heat the general unit 19, and therefore the temperature control unit 10 temporarily ends the series of control processes described above.

  Here, when the supply of the high-temperature main steam is stopped when the steam turbine 100 is stopped, the temperature of the general part 19 is earlier than that of the flange part 20 having a larger heat capacity than that of the general part 19. Thus, when the temperature drop of the general part 19 is fast, the general part 19 contracts more than the flange part 20. Therefore, the outer casing 3 is deformed. Then, the inner casing 2 supported by the outer casing 3 is displaced. That is, as in the case of startup, the above-described temperature difference is set to be equal to or smaller than the threshold value, and as a result, the inner casing 2 is not displaced.

  The heating of the general part 19 by the heating medium is continued until the temperature difference becomes equal to or less than the threshold value or until the rotor 1 of the steam turbine 100 is completely stopped.

  Therefore, according to the steam turbine 100 of the first embodiment described above, the temperature control unit 10 causes the temperature difference between the temperature of the general part 19 and the flange part 20 to be equal to or less than a preset threshold value. 19 is cooled or heated. Therefore, it can suppress that temperature distribution arises in the flange part 20 and the general part 19 of the outer casing 3, and the outer casing 3 deform | transforms. Then, the deformation of the outer casing 3 causes the inner casing 2 supported by the outer casing 3 to be displaced, so that the clearance C2 between the moving blade 12 and the inner casing 2 or the clearance between the stationary blade 14 and the rotor 1 is achieved. It can suppress that C1 becomes smaller than during load operation. As a result, the clearance between the rotor 1 side and the inner casing 2 side can be set to an appropriate value.

  Further, even when the outer casing 3 includes the upper half 21 and the lower half 22, the upper half 21 and the lower half 22 are compared with the temperatures of the lower half flange 27 and the upper half flange 26. The temperature control unit 10 can control the temperature so that the temperature of each of the general parts 19 does not rise or fall too much.

Furthermore, the heat medium can flow in the direction of the axis Ar by the first heat medium passage 32A. Therefore, the temperature variation of the general part 19 in the axis line Ar direction can be suppressed.
A plurality of first heat medium passages 32 </ b> A are formed in the circumferential direction of the outer casing 3. Therefore, the temperature of the several position in the circumferential direction of the outer casing 3 can be adjusted separately. Thereby, even if there is a part where the temperature locally rises or falls in the general part 19, the temperature in the circumferential direction of the general part 19 can be made uniform.

(Modification of the first embodiment)
FIG. 5 is a cross-sectional view corresponding to FIG. 1 in a modification of the first embodiment of the present invention. FIG. 6 is a cross-sectional view corresponding to FIG. 2 in a modification of the first embodiment of the present invention.
In 1st embodiment mentioned above, the case where the cooling heating part 7 was formed so that it might protrude outside from the general part 19 was demonstrated. However, as in the modification examples shown in FIGS. 5 and 6, the cooling and heating unit 7 may be provided inside the general unit 19. That is, the first heat medium passage 32 </ b> B in this modification is formed inside the general portion 19.

  A part of the general part 19 can be used as the cooling and heating part 7 by forming the first heat medium passage 32B as in the modification of the first embodiment. Therefore, for example, compared with the case where the cooling and heating unit 7 is provided so as to protrude to the outer surface side of the outer casing 3, the enlargement of the outer casing 3 can be suppressed.

  The first heat medium passage 32B shown in the modification of the first embodiment may be used in combination with the first heat medium passage 32A shown in the first embodiment.

(Second embodiment)
Next, a second embodiment of the present invention will be described with reference to the drawings. The steam turbine 200 according to the second embodiment differs from the steam turbine 100 according to the first embodiment described above only in the configuration of the cooling and heating unit 7. Therefore, the same portions as those in the first embodiment described above are described with the same reference numerals, and redundant descriptions are omitted.

FIG. 7 is a cross-sectional view corresponding to FIG. 1 in the second embodiment of the present invention. FIG. 8 is a cross-sectional view corresponding to FIG. 2 in the second embodiment of the present invention.
As shown in FIG. 7, the steam turbine 200 according to the second embodiment is similar to the steam turbine 100 according to the first embodiment described above, with the rotor 1, the inner casing 2, the outer casing 3, and the bearing portion 4. The seal part 5, the main steam supply part 6, the cooling heating part 207, the heat medium supply part 8, the temperature measurement part 9, and the temperature control part 10 are mainly provided.

  As shown in FIGS. 7 and 8, the cooling and heating unit 207 has a heat medium passage through which a heat medium can flow as in the first embodiment. The cooling and heating unit 207 is formed so as to protrude outward from the outer peripheral surface of the general unit 19. According to the cooling and heating unit 207, the general unit 19 can be cooled or heated by flowing a heat medium through the heat medium passage. The cooling and heating unit 207 in the second embodiment includes a second heat medium passage 33A that extends in the circumferential direction of the outer casing 3 around the axis Ar as a heat medium passage.

A plurality of cooling and heating units 207 are provided at intervals in the direction of the axis Ar of the outer casing 3. Further, the cooling and heating unit 207 is formed so as to extend between the left flange portion 20 and the right flange portion 20 as viewed from the axis Ar direction in the circumferential direction of the outer casing 3.
In the second embodiment, the cooling and heating unit 207 is connected to the heat medium supply unit 8 via a supply pipe at an intermediate position between the left and right flanges 20 when viewed from the direction of the axis Ar. That is, the heat medium supplied to the cooling and heating unit 7 is diverted toward the left and right flange portions 20 at the intermediate position. Moreover, the cooling heating part 7 has both ends in the circumferential direction of the outer casing 3 connected to a discharge pipe (not shown). That is, the heat medium that has flowed into the second heat medium passage 33A from the supply pipe exchanges heat with the general portion 19, and is then discharged through a discharge pipe (not shown).

  The heat medium supply unit 8 supplies a cooling medium or a heating medium to the cooling heating unit 7 as a heat medium. As in the first embodiment, the cooling medium is a heat medium that can cool the general part 19 when the steam turbine 200 is started. As this cooling medium, air fed by a compressor or the like can be used. The heating medium is also a heating medium that can heat the general part 19 when the steam turbine 200 is stopped, as in the first embodiment. As this heating medium, steam generated by an auxiliary boiler or the like can be used. The heat medium supply unit 8 can selectively supply the cooling medium and the heating medium toward the cooling heating unit 207.

  The heat medium supply unit 8 can supply the heat medium with different supply amounts to the plurality of cooling and heating units 207 via valves or the like. Further, the heat medium supply unit 8 can linearly adjust the amount of supply of the heat medium. Further, the heat medium supply unit 8 can individually adjust the supply amount of the heat medium to the plurality of cooling heating units 207.

The temperature measuring unit 9 measures the temperature of the outer casing 3. The measurement result of the temperature measurement unit 9 is output toward the temperature control unit 10. The temperature measurement unit 9 includes a first measurement unit 9a and a second measurement unit 9b.
The first measurement unit 9 a measures the temperature of the flange unit 20. More specifically, the first measuring portion 9a is attached to the left and right flange portions 20 sandwiching the axis Ar in the cross section orthogonal to the axis Ar. Also in the second embodiment, as in the first embodiment, the case where the first measurement unit 9a is attached to the side surface of the flange portion 20 is illustrated.

  The second measuring unit 9 b measures the temperature of the general unit 19. More specifically, the second measurement unit 9 b measures the temperature of the outer peripheral surface of the general unit 19. A plurality of second measuring portions 9b are provided at intervals in at least the axial direction of the general portion 19. These second measuring units 9b can individually measure the temperature at each position where the plurality of cooling heating units 207 are arranged in the direction of the axis Ar of the outer casing 3. In addition, you may make it provide the 2nd measurement part 9b in this 2nd embodiment in the circumferential direction along the cooling heating part 207. In FIG.

  The temperature control unit 10 controls the heat medium supply unit 8 based on the temperature difference between the temperature of the flange unit 20 and the temperature of the general unit 19. More specifically, the temperature control unit 10 obtains a temperature difference between the temperature of the flange unit 20 measured by the first measurement unit 9a and the temperature of the general unit 19 measured by the second measurement unit 9b. Furthermore, the temperature control unit 10 controls the supply of the heat medium by the heat medium supply unit 8 so that the temperature difference is equal to or less than a preset threshold value. Here, the temperature control unit 10 in this embodiment obtains the temperature difference between the measurement results of the eight second measurement units 9b with respect to the measurement results of the two first measurement units 9a so that all are equal to or less than the threshold value. An appropriate flow rate of heat medium is supplied to each cooling and heating unit 207 individually. The temperature control unit 10 supplies the heat medium based on the temperature difference between the average temperature measured by the plurality of first measurement units 9a and the average temperature measured by the plurality of second measurement units 9b. The unit 8 may be controlled.

  The temperature control method in the second embodiment only replaces the first heat medium passage in the first embodiment described above with a second heat medium passage. Detailed description of the temperature control method in the second embodiment is omitted.

  According to the steam turbine 200 of the second embodiment described above, unlike the first embodiment, the second heat medium passage 33 </ b> A extends in the circumferential direction of the outer casing 3. Can flow. As a result, temperature variations of the general portion 19 in the circumferential direction of the outer casing 3 can be suppressed.

  Further, the temperatures at a plurality of positions of the general portion 19 can be individually adjusted in the direction of the axis Ar of the outer casing 3. Therefore, for example, even when there is a position where the temperature locally rises or falls among a plurality of positions of the general part 19 in the axis Ar direction, the temperature of the general part 19 in the axis Ar direction is made uniform. Can be planned.

(Modification of the second embodiment)
FIG. 9 is a sectional view corresponding to FIG. 1 in a modification of the second embodiment of the present invention. FIG. 10 is a cross-sectional view corresponding to FIG. 2 in a modification of the second embodiment of the present invention.
In the second embodiment described above, the case where the cooling and heating unit 207 is formed so as to protrude outward from the general unit 19 has been described. However, similarly to the modification of the first embodiment, in the second embodiment, the cooling and heating unit 7 may be provided inside the general part 19 as in the modification shown in FIGS. That is, the second heat medium passage may be formed inside the general portion 19.
A part of the general part 19 can be used as the cooling heating part 7 by forming the second heat medium passage as in the modification of the second embodiment. Therefore, for example, compared with the case where the cooling and heating unit 7 is provided so as to protrude to the outer surface side of the outer casing 3, the enlargement of the outer casing 3 can be suppressed.

(Third embodiment)
Next, a third embodiment of the present invention will be described with reference to the drawings. The steam turbine of this third embodiment differs from the steam turbine of the first embodiment described above in the configuration of the flange portion 20. Therefore, the same portions as those in the first embodiment described above are described with the same reference numerals, and redundant descriptions are omitted.
FIG. 11 is a cross-sectional view corresponding to FIG. 2 of the steam turbine in the third embodiment of the present invention.
As shown in FIG. 11, in addition to the configuration of the steam turbine of the first embodiment, the steam turbine of the third embodiment includes a flange cooling heating unit (a large heat capacity unit cooling heating unit) that can cool or heat the flange unit 20. 34). The flange cooling / heating unit 34 has a flange-portion heat medium passage through which a cooling medium capable of cooling the flange portion 20 and a heating medium capable of heating the flange portion 20 can selectively flow.

  The steam turbine 300 of the third embodiment shown in FIG. 11 illustrates a case where a plurality of flange cooling and heating units 34 are provided inside the flange unit 20. That is, the flange portion heat medium passage 35 is formed inside the flange portion 20. The flange part heat medium passages 35 are arranged in the vicinity of the outer surface of the flange part 20 in a cross section orthogonal to the axis Ar, and a plurality of the heat medium passages 35 are arranged side by side along the outer surface of the flange part 20. Yes.

  Here, similarly to the first embodiment, the heat medium supply unit 8 is configured to be able to supply a heat medium to the cooling heating unit 7 that cools or heats the general unit 19, and also to the flange cooling heating unit 34. The heat medium can be supplied. When the type of the heat medium supplied to the cooling and heating unit 7 provided in the general unit 19 is a cooling medium, the heating medium is supplied to the flange cooling and heating unit 34. Similarly, when the type of the heat medium supplied to the cooling / heating unit 7 provided in the general unit 19 is a heating medium, the cooling medium is supplied to the flange cooling / heating unit 34.

(Temperature control method of the third embodiment)
Next, the temperature control method by the steam turbine of 3rd embodiment provided with the structure mentioned above is demonstrated, referring drawings. In addition, the temperature control method in this third embodiment performs temperature control also about the flange part 20 in addition to the temperature control method in 1st embodiment mentioned above. That is, since the cooling and heating of the general part 19 are the same temperature control method as in the first embodiment, detailed description thereof is omitted here. In the temperature control method of the third embodiment, the general part 19 is heated when the flange part 20 is cooled, and the flange part 20 is cooled when the general part 19 is heated.

FIG. 12 is a flowchart of the temperature control method in the third embodiment of the present invention. In the flowchart of FIG. 12, the same processes as those in the flowchart of FIG.
As shown in FIG. 12, when the steam turbine is at startup (Yes in step S01), the temperature control unit 10 performs steps S01 to S05. That is, a temperature difference between the temperature of the flange portion 20 and the temperature of the general portion 19 is obtained, and it is determined whether or not this temperature difference is equal to or less than a preset threshold value.

  If the temperature control unit 10 does not determine that the temperature difference between the general unit 19 and the flange unit 20 is equal to or less than a preset threshold value (No in step S05), the temperature difference is equal to or less than the threshold value. Then, a heating medium is supplied to the flange cooling and heating unit 34 (step S106). At this time, the cooling medium is simultaneously supplied to the cooling and heating unit 7 of the general unit 19.

  On the other hand, when the steam turbine is not starting but stopping (Yes in step S07), the temperature control unit 10 performs steps S08 to S11. When the temperature control unit 10 does not determine that the temperature difference between the general portion 19 and the flange portion 20 is equal to or less than a preset threshold value (No in step S11), the temperature difference is equal to or less than the threshold value. Then, a cooling medium is supplied to the flange cooling / heating unit 34 (step S112). At this time, the heating medium is simultaneously supplied to the cooling and heating unit 7 of the general unit 19.

  Therefore, according to the third embodiment described above, the flange cooling / heating unit 34 can actively bring the temperature of the flange 20 having a large heat capacity close to the temperature of the general unit 19. Therefore, when the temperature difference between the flange part 20 and the general part 19 becomes larger than a preset threshold value, the cooling / heating unit 7 cools or heats only the general part 19 to make the temperature difference equal to or less than the threshold value. Rather, the temperature difference between the flange portion 20 and the general portion 19 can be quickly reduced to a threshold value or less.

(Modification of the third embodiment)
FIG. 13 is a sectional view corresponding to FIG. 2 in a modification of the third embodiment of the present invention.
In 3rd Embodiment mentioned above, although the case where the flange cooling heating part 34 was provided in the inside of the flange part 20 was demonstrated, it is not restricted to this structure. For example, another flange cooling and heating unit 134 may be provided separately along the outer peripheral surface of the flange portion 20 (in other words, the meridian of the flange portion 20) as in the modification shown in FIG. The other flange cooling / heating unit 134 is provided with another flange part heat medium passage 135, and by flowing a heat medium through the other flange part heat medium passage 135, the flange part 20 having a larger heat capacity can be used. Cooling or heating can be performed quickly. The flange cooling / heating unit 34 described above may be omitted, and the flange unit 20 may be cooled or heated only by the other flange cooling / heating unit 135.

(Fourth embodiment)
Next, a fourth embodiment of the invention will be described with reference to the drawings. The steam turbine according to the fourth embodiment is provided with a heater with respect to the above-described embodiments. For this reason, the same portions as those in the above-described embodiments are denoted by the same reference numerals, and redundant description is omitted. In the fourth embodiment, a heater is provided as an example for the steam turbine provided with the cooling heating unit 7 in the modification of the first embodiment and the flange cooling heating unit 34 of the third embodiment. explain.

FIG. 14 is a cross-sectional view corresponding to FIG. 2 in the fourth embodiment of the present invention.
As shown in FIG. 14, in the steam turbine 400 according to the fourth embodiment, the cooling and heating unit 7 is provided in the general part 19, and the flange cooling and heating part 34 is provided in the flange part 20.
The steam turbine 400 includes a heater 40. As the heater 40, for example, an induction heater can be used.

The heater 40 includes a general heater 40a and a flange heater 40b. The temperature control unit 10 controls the temperatures of the general heater 40a and the flange heater 40b.
The general part heater 40 a heats the general part 19, and the flange part heater 40 b heats the flange part 20. The temperature control section 10 does not use the general section heater 40a and the flange section heater 40b at the same time. For example, when the steam turbine 400 is started, the flange section heater 40b is used to heat only the flange section 20 and steam. When the turbine 400 is stopped, only the general part 19 is heated using the general part heater 40a.

The temperature control unit 10 controls the temperature of the general part heater 40a and the flange part heater 40b, and simultaneously controls the heat medium supply unit in the first embodiment and the third embodiment described above. That is, the temperature control unit 10 in the fourth embodiment uses both the heat medium and the heater 40 to control the temperature so that the temperature difference between the general unit 19 and the flange unit 20 is equal to or less than a preset threshold value. Is going. In addition, it is not restricted to the structure heated together using a heat medium and the heater 40, For example, you may make it use only the heater 40 regarding heating.
In addition, in 4th embodiment, the case where the heater 40 was provided in both the general part 19 and the flange part 20 was demonstrated. However, the heater 40 may be provided on either the general part 19 or the flange part 20.

  In the fourth embodiment, the heater 40 that is a heating unit is attached to the outer casing 3. However, a cooling unit that performs cooling may be attached to at least one of the general part 19 and the flange part 20. . In this case, the general part 19 may be cooled by the cooling part when the steam turbine 400 is started, and the flange part 20 may be cooled by the cooling part when the steam turbine 400 is stopped. As the cooling unit, for example, a Peltier element or the like can be used.

  Therefore, according to the fourth embodiment, in addition to the cooling heating unit 7 and the flange cooling heating unit 34, at least one of the general part 19 and the flange part 20 can be heated by the heater 40. The heater 40 can raise and lower the temperature more quickly than heating using a heat medium. As a result, the temperature difference between the general portion 19 and the flange portion 20 can be quickly reduced to a predetermined threshold value or less.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described with reference to the drawings. The steam turbine 500 according to the fifth embodiment is different from the first embodiment described above only in that ribs are provided as the heat capacity expansion portion. Therefore, the same portions as those in the first embodiment described above are described with the same reference numerals, and redundant descriptions are omitted.

FIG. 15 is a sectional view corresponding to FIG. 2 in the fifth embodiment of the present invention.
As shown in FIG. 15, the outer casing 3 in the fifth embodiment is formed with ribs (heat capacity expanding portions) 50 so as to be sandwiched between the general portions 19 in the circumferential direction about the axis Ar. The rib 50 is formed so as to protrude outward from the general part 19, and has a larger heat capacity than the general part 19. The ribs 50 in the fifth embodiment are provided on both the upper half 21 and the lower half 22. These ribs 50 are respectively arranged at the centers of the left and right flange portions 20 in the circumferential direction of the outer casing 3 in a cross section orthogonal to the axis Ar. Further, the rib 50 in the fifth embodiment has a heat capacity equivalent to that of the flange portion 20, and continuously extends in the direction of the axis Ar.

  In the fifth embodiment, the case where one rib 50 is provided in each of the upper half 21 and the lower half 22 has been described. However, the number of ribs 50 provided in the upper half 21 and the lower half 22 is not limited to one. Moreover, although the case where the rib 50 was formed to extend continuously in the direction of the axis Ar has been described, it may be formed intermittently.

  Therefore, according to the fifth embodiment, since the heat capacity of the rib 50 and the heat capacity of the flange portion 20 are equal, a temperature difference hardly occurs between the rib 50 and the flange portion 20. And since the rib 50 is arrange | positioned so that it may be pinched | interposed into the general part 19, the temperature of the general part 19 follows the temperature change of the rib 50. FIG. As a result, the temperature difference between the general portion 19 and the flange portion 20 is less likely to occur, and deformation due to the temperature difference between the general portion 19 and the flange portion 20 can be suppressed.

The present invention is not limited to the configurations of the above-described embodiments and modifications, and can be changed in design without departing from the scope of the invention.
For example, in each embodiment mentioned above, the steam turbine provided with the outer casing 3 which accommodates one type of turbine was described as an example. However, the steam turbine is not limited to the steam turbine described in each embodiment described above.

FIG. 16 is a cross-sectional view corresponding to FIG. 1 and showing a steam turbine according to another aspect of the first embodiment of the present invention.
For example, the present invention can be applied to a steam turbine 600 as shown in FIG. A steam turbine 600 shown in FIG. 16 accommodates a high-pressure turbine 601 and an intermediate-pressure turbine 602 in the outer casing 3. In the steam turbine 600, the steam discharged from the high-pressure turbine 601 is reheated by a reheating device (not shown) and then supplied to the intermediate pressure turbine 602.

  The high-pressure turbine 601 and the intermediate-pressure turbine 602 include an inner casing 2 that is integrally formed. The inner casing 2 is supported by the outer casing 3 in the same manner as the inner casing 2 of each embodiment described above. The high-pressure turbine 601 and the intermediate-pressure turbine 602 are provided with a common rotor 1. The rotor 1 is provided with a moving blade 12a for a high-pressure turbine and a moving blade 12b for an intermediate-pressure turbine at different positions in the axis Ar direction. The inner casing 2 includes a plurality of stationary blades 14a disposed on the upstream side of the high pressure turbine blade 12a and a plurality of stationary blades disposed on the upstream side of the intermediate pressure turbine blade 12b. 14b is attached.

  According to such a steam turbine 600, the main steam flows from the high-pressure steam inlet 23A of the outer casing 3 into the inner casing 2 on the high-pressure turbine 601 side. Then, after exiting the inner casing 2, it is once discharged from the high-pressure steam outlet 24 </ b> A to the outside of the steam turbine 600, and after passing through a reheating device (not shown), then the intermediate pressure from the intermediate-pressure steam inlet 23 </ b> B of the outer casing 3. It flows into the inner casing 2 on the turbine 602 side. And after exiting an inner casing, it is discharged | emitted from the intermediate pressure steam outlet 24B outside.

  In addition, in FIG. 16, although the case where the cooling heating part of 1st embodiment was applied to the steam turbine provided with the high pressure turbine 601 and the intermediate pressure turbine 602 was demonstrated, the cooling shown to 2nd embodiment to 5th embodiment. You may employ | adopt suitably the heating part 7, the flange cooling heating part 34, the heater 40, and the rib 50. FIG.

Moreover, in 1st embodiment mentioned above, the case where the heat medium supply part 8 adjusts the supply amount of the heat medium with respect to the several cooling heating part 7 linearly was demonstrated. However, the supply amount of the heat medium may be adjustable in stages. The heat medium supply unit 8 may be configured to adjust the supply amount of the heat medium to the cooling heating unit 7 so that the heat medium can be intermittently supplied.
Furthermore, in each embodiment, although the case where the flange part 20 was a large heat capacity part was demonstrated to an example, a large heat capacity part is not restricted to the flange part 20. FIG. What is necessary is just to be a location where heat capacity is partially large in the outer casing 3.

  Furthermore, the configurations shown in the first embodiment to the fifth embodiment and the modifications may be used in appropriate combination.

DESCRIPTION OF SYMBOLS 1 Rotor 2 Inner casing 3 Outer casing 4 Bearing part 5 Seal part 6 Main steam supply part 7,207 Cooling heating part 8 Heat medium supply part 9 Temperature measurement part 10 Temperature control part 11 Rotor main body 12 Rotor blade 13 First steam flow path 14 Stator Blade 15 Inner Steam Inlet 16 Inner Discharge Port 17 Inner Through Port 18 Second Steam Flow Channel 19 General Portion 20 Flange Portion 21 Upper Half 22 Lower Half 23 Outer Steam Inlet 24 Outer Steam Outlet 25 Through Port 26 Upper Half Flange Portion 27 Lower half flange portion 28, 29 Opening edge 30, 31 Mating surface 32 Heat medium passage 32A, 32B First heat medium passage 33A, 33B Second heat medium passage 34 Flange cooling heating portion 35 Heat medium passage 134 for flange portion, etc. Flange cooling and heating unit 135 Heat medium passage 40 for other flange portion Heater 50 Rib 100, 200, 300, 400, 500, 600 Steam turbine

Claims (12)

A plurality of rotor blades provided on the outer peripheral surface, and a rotor rotating around an axis;
An inner casing that covers the rotor from a radially outer side centered on the axis and forms a first steam flow path through which steam flows between the rotor and the outer peripheral surface;
A plurality of stator blades provided on the inner peripheral surface of the inner casing and disposed in the first steam flow path together with the plurality of rotor blades;
A second steam flow having a general part and a large heat capacity part having a larger heat capacity than the general part, covering the inner casing from the outside in the radial direction, and communicating the steam in communication with the first steam channel An outer casing forming a path with the outer peripheral surface of the inner casing;
A cooling medium heating section capable of cooling or heating the general section;
A heat medium supply unit capable of supplying a heat medium to the heat medium passage;
A first measuring unit for measuring the temperature of the large heat capacity unit;
A second measuring part for measuring the temperature of the general part;
Based on the temperature difference between the temperature of the large heat capacity part measured by the first measurement part and the temperature of the general part measured by the second measurement part, the temperature difference is less than or equal to a preset threshold value. A temperature control unit for controlling the heat medium supply unit,
A steam turbine comprising: The outer casing is
A lower half covering the lower half of the inner casing;
An upper half covering the upper half of the inner casing,
The large heat capacity part is:
A lower half flange portion protruding outward from an opening edge of the lower half portion;
The steam turbine according to claim 1, further comprising: an upper half flange portion that protrudes outward from an opening edge of the upper half portion and can be fixed to the lower half flange portion. The cooling and heating unit is
The steam turbine according to claim 1, further comprising a first heat medium passage extending along the axis as the heat medium passage. The cooling and heating unit is
The steam turbine according to claim 3, comprising a plurality of the first heat medium passages spaced apart from each other in a circumferential direction of the outer casing. The cooling and heating unit is
The steam turbine according to claim 1, further comprising a second heat medium passage extending in a circumferential direction of the outer casing as the heat medium passage. The cooling and heating unit is
The steam turbine according to claim 5, comprising a plurality of the second heat medium passages spaced apart in the axial direction.   The steam turbine according to any one of claims 3 to 6, wherein the cooling and heating unit is provided inside the general part.   The steam according to any one of claims 1 to 7, further comprising a large heat capacity part cooling and heating unit having a heat medium passage for a large heat capacity part capable of flowing a heat medium capable of cooling or heating the large heat capacity part. Turbine.   The heating part which heats at least one of the general part and the large heat capacity part, or the cooling part which cools at least one of the general part and the large heat capacity part is provided. Steam turbine.   The steam turbine according to any one of claims 1 to 9, further comprising a heat capacity expansion portion that is disposed so as to be sandwiched between the general portions in a circumferential direction of the outer casing and has a larger heat capacity than the general portions. A steam turbine temperature control method comprising an inner casing and an outer casing, wherein the outer casing includes a general part and a large heat capacity part having a larger heat capacity than the general part,
Measuring the temperature of the general part;
Measuring the temperature of the large heat capacity part;
Cooling or heating the general part so that the temperature difference between the temperature of the general part and the temperature of the large heat capacity part is not more than a preset threshold value;
Including temperature control method.   The method according to claim 11, further comprising: heating the general part and cooling the large heat capacity part so that a temperature difference between the temperature of the general part and the temperature of the large heat capacity part is equal to or less than a preset threshold value. The temperature control method described.

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