JP2000282807A - Steam turbine equipment - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce elongation difference between a rotary part and a static part, and improve safety property and reliability by arranging an elongation difference reducing device for reducing the elongation difference between the rotary part and the static part, between a very high pressure and high temperature turbine and a very high pressure turbine. SOLUTION: A shaft coupling device 26 as a reducing device having an axial direction displacement absorbing mechanism for reducing elongation difference between a rotary part and a static part in a steam turbine facility, is installed between a very high pressure and extra super high temperature (SP) rotor 10 and a very high pressure(VHP)-high pressure(HP) rotor 11. The shaft coupling device 26 absorbs the elongation difference as a starting point at a thrust bearing 18b of a first bearing device 14, and an elongation difference as a starting point at a thrust bearing 18a of a third bearing device 16. Namely, a rotor long, rotor short, and a rated normal value becomes discontinuous at a position of the shaft coupling device 26 as a starting point at the thrust bearings 18a, 18b, almost the elongation difference of a VHP turbine 2 and an elongation difference of a HP turbine 3 does not affect the elongation difference of an SP turbine 1 and the elongation difference of the SP turbine 1 is suppressed in a low level.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to steam turbine equipment used in power plants and the like.

[0002]

2. Description of the Related Art High temperature and high pressure steam conditions in a thermal power plant are very important and fundamental factors that contribute to the improvement of the efficiency. Since the steam conditions for single-stage reheating at 24.1 MPa and 538/566 ° C were established as standard in Japan in the late 1960s, breakthroughs have been made until recently. Did not. However, since the oil crisis, energy saving has been strongly promoted, and rapid interest in the issue of global warming has increased the efficiency of thermal power plants.

[0003] In order to increase the power generation efficiency, it is most effective to increase the steam temperature of the steam turbine. The steam condition of the conventional steam turbine equipment is a steam temperature of 600 ° C. class or less, and it is difficult to further increase the temperature with the conventional material. At present, austenitic materials are used for steam turbine equipment having a steam temperature of 600 ° C or higher, but these austenitic materials are expensive and it is said that it is difficult to manufacture large-sized ones. .

[0004] Therefore, a steam turbine facility has been considered in which an ultra-high-pressure high-temperature turbine (SP turbine) using steam at 650 ° C or higher is added to a conventional steam turbine facility. This is to use steam of 650 ° C. or higher using an austenitic material only for the SP turbine, and operate the other steam turbines at a steam temperature of 650 ° C. or lower using conventionally used materials.

[0005]

However, as the casing volume of the steam turbine is increased and the operating conditions are also higher, the length and the diameter of the rotor shaft tend to become larger and larger. The difference in elongation due to the relative thermal expansion of the turbine casing and the rotor at the time of starting the turbine and at the time of low load has become so large that it cannot be ignored. In particular, in a steam turbine facility in which an SP turbine is added to a conventional steam turbine facility, it is conceivable that a difference in elongation due to thermal expansion becomes so large that it cannot be ignored.

To reduce the difference in elongation due to the relative thermal expansion of the turbine casing and the rotor, Japanese Patent Publication No. 55-148
There is one disclosed in Japanese Patent Publication No. 88. This is to reduce the difference in elongation by cooling the shaft seal with a low-pressure cabin spraying device, but the one that reduces the difference in elongation at high pressure and medium pressure has not been put to practical use.

In general, a material expands due to thermal expansion when the temperature increases. In particular, when the operating temperature range is wide and the overall length is long, such as in a steam turbine, the elongation due to thermal expansion is large.
A difference in elongation is generated between the rotor and the casing due to a difference in thermal expansion based on heat transfer between the rotor and the casing, a difference in heat conduction, a difference in material, and the like.

FIG. 10 is a configuration diagram of a steam turbine facility in which an SP turbine is added to a conventional steam turbine facility. S
The P turbines 1a and 1b are a conventional turbine equipment, a very high pressure turbine (VHP turbine) 2, a high pressure turbine (H
P turbine) 3, medium pressure turbine (IP turbine) 4a,
4b, and is connected to the VHP turbine 2 among the low-pressure turbines (LP turbines) 5a and 5b.

The SP turbines 1a and 1b are SP casing 6, the VHP turbine 2 and the HP turbine 3 are VHP-H
P casing 7, IP turbines 4a and 4b are IP casing 8, LP turbine 5a is LP-A casing 9a,
The LP turbine 5b is housed in the LP-B casing 9b. Then, the SP rotor 10 of the SP turbine 1 has V
The HP turbine 2 and the VHP-HP rotor 11 of the HP turbine 3 are connected to each other.
1 is the IP rotor 12, the IP rotor 12 is the LP-A rotor 13a, and the LP-A rotor 13a is the LP-B rotor 1.
3b. These rotors are connected to a first bearing stand 14, a second bearing stand 15, a third bearing stand 16,
It is held by the bearing of the fourth bearing stand 17. The third bearing stand 16 is provided with a thrust bearing 18.

Further, an SP differential expansion meter 24 for measuring the differential expansion of the SP rotor 10 is provided at the tip of the SP rotor 10, and an LP differential differential meter 2 for measuring the differential expansion of the LP rotor 13.
5 is provided on the LP rotor 13.

Next, the difference in the axial elongation between the rotor and the casing will be described. Since the LP-A casing 9a and the LP-B casing 9b are heavy,
It is fixed to the foundation by LP-A fixed points A and LP-B fixed points B. Since the LP-A casing 9a, the IP casing 8, the VHP-HP casing 7, and the SP casing 6 are connected, the LP-A fixing point A is increased as the temperature increases.
The casing extends from to the left. On the other hand, the rotor starts from the thrust bearing 18 on the third bearing stand 16 and starts to rotate on the right side.
The P rotor 12, the LP-A rotor 13a and the LP-B rotor 13b extend, and the VHP-HP rotor 11 and the SP rotor 10 extend to the left.

FIG. 11 is an explanatory view of the difference in elongation and the axial gap of the turbine equipment in FIG. The vertical axis is the difference in growth,
The horizontal axis is the axial position of the rotor. Further, RL is a maximum elongation difference when the rotor is larger than the casing (rotor long), RS is a maximum elongation difference when the rotor is smaller than the casing (rotor short), and SS is an elongation difference during steady continuous operation (rotation). (Elongation difference rated steady value). As shown in FIG. 11, the rotor long RL, the rotor short RS, and the rated steady value SS all have a characteristic of expanding in the left-right direction starting from the position X0 of the thrust bearing 18.

Here, the clearance set value at each rotor shaft position is set with a margin with respect to the rotor long RL and the rotor short RS at that position. For example, the gap set value at the rotor shaft position X1 is the value A1 of the rotor long RL and the value A of the rotor short RS at the rotor shaft position X1.
In addition, from the viewpoint of safety, margins B1 and B2 are added to CL2 and CL2, respectively.

[0014] The effect of differential elongation on a steam turbine is very large. For example, it greatly affects a labyrinth packing (shaft sealing device) for preventing steam from leaking from a gap between the rotating part and the stationary part, and a gap part between the rotating part and the stationary part.

FIG. 12 is a schematic configuration diagram of the SP turbine 1. In the SP turbine 1, a labyrinth packing is provided between the SP casing 6 and the SP rotor 10 or between the nozzle 19 and the SP rotor 10, but the difference in elongation affects the labyrinth packing.
And the gap between the stationary portion and the rotating portion at the portion where the blade 20 is provided.

As shown in FIG. 13, between the SP casing 6 and the SP rotor 10, a sealing method using a packing ring 21 called a labyrinth packing is used to allow high-temperature and high-pressure steam to pass through a gap between the rotating part and the stationary part. To prevent leaks. The packing ring 21 is provided with a stationary portion side fin 22, and the SP rotor 10 is provided with a rotor side fin 23. The idea of this sealing method is to kill the velocity of the leaking steam by passing the steam through a maze-like path and reduce the leaking steam flow.

When the difference in elongation increases, the fin gaps x1 and x2 must be adjusted and the groove width x must be increased so that the rotor side fins 23 and the stationary part side fins 22 do not come into contact as shown in FIG. When the groove width x is increased, the steam passage becomes closer to a straight line from the maze, so that the steam speed does not decrease and much steam leaks. When the number of the packing rings 21 is increased to reduce the leakage, the lengths of the SP rotor 10 and the SP casing 6 only increase, and the difference in elongation further increases and the cost increases.

FIG. 15 is an explanatory view of a gap between the stationary portion and the rotating portion at the portion where the nozzle 19 and the blade 20 are provided.
As described above, the gap CL between the rotating part and the stationary part at each part is determined in consideration of the margin B1 and B2 for the rotor long RL or the rotor short RS. If the difference in elongation is large, the gap CL is increased from the viewpoint of safety and reliability. Then, the amount of leaked steam increases, which is a major cause of performance deterioration of the steam turbine.

For example, the steam turbine equipment to which the SP turbine 1 shown in FIG. 11 is added has a total length longer by one SP turbine than the conventional steam turbine equipment. Therefore, the difference in expansion of the SP turbine 1 is added to the difference in expansion of the conventional steam turbine equipment, so that the difference in expansion is further increased. The SP turbine 1 is made of an austenitic material. However, since the austenitic material has a large elongation due to thermal expansion and a high operating temperature, the SP turbine 1 has
The difference in elongation between the P rotor 10 and the SP casing 6 is larger than that of the conventional steam turbine equipment.

Since the SP turbine 1 uses steam at a very high pressure, a large difference in elongation requires an increase in the gap, and a large amount of steam escapes without performing work. , Leading to significant performance degradation.

An object of the present invention is to provide a steam turbine facility capable of absorbing a difference in extension between a rotating part and a stationary part.

[0022]

According to a first aspect of the present invention, there is provided a steam turbine system comprising: an ultra-high-pressure high-temperature turbine driven at a steam temperature of 650 ° C. or higher; and an ultra-high-pressure turbine driven at a steam temperature of 650 ° C. or lower. , A high-pressure turbine, a medium-pressure turbine, and a low-pressure turbine, wherein the ultra-high-pressure high-temperature turbine is a steam turbine facility using a Ni-based alloy steel containing 35% or more of Ni for a material of a nozzle, a blade, and a rotor. A differential expansion device is provided between the high-pressure turbine and the ultra-high-pressure turbine to reduce the differential expansion between the rotating part and the stationary part.

In the steam turbine equipment according to the first aspect of the present invention, an ultra-high-temperature high-pressure turbine driven at a steam temperature of 650 ° C. or more and an ultra-high pressure turbine driven at a steam temperature of 650 ° C. or less are provided. The difference in elongation between the rotating part and the stationary part is reduced by the difference in elongation reduction device.

According to a second aspect of the present invention, there is provided a steam turbine system comprising: an ultra-high-pressure high-temperature turbine driven at a steam temperature of 650 ° C. or more; an ultra-high-pressure turbine driven at a steam temperature of 650 ° C. or less; A turbine, a low-pressure turbine, a first-stage reheater that reheats the bleed air of the ultrahigh-pressure turbine and supplies the ultra-high-pressure high-temperature turbine with a steam temperature of 650 ° C. or more, and reheats the bleed air of the high-pressure turbine to the medium-pressure turbine. A second-stage reheater for supplying a steam temperature of 650 ° C. or less, wherein the ultra-high pressure high-temperature turbine uses a Ni-based alloy steel containing 35% or more of Ni for a material of a nozzle, a blade, and a rotor. , A differential expansion reduction device for reducing a differential expansion between a rotating part and a stationary part is provided between the ultra-high-temperature high-pressure turbine and the ultra-high-pressure turbine.

In the steam turbine equipment according to the second aspect of the present invention, an ultra-high-temperature high-pressure turbine driven by steam having a steam temperature of 650 ° C. or more obtained by a boiler superheater or a first-stage reheater has a steam temperature of 650 ° C. The difference in elongation between the rotating part and the stationary part is reduced by an elongation difference reduction device provided between the ultrahigh-pressure turbine driven at a temperature of not more than ° C.

According to a third aspect of the present invention, in the steam turbine equipment according to the second aspect of the present invention, the ultra-high-pressure high-temperature turbine, the ultra-high-pressure turbine, the high-pressure turbine, the medium-pressure turbine, and the low-pressure turbine are tandem compounds having a single shaft. Or a cross-compound type in which the ultra-high-pressure high-temperature turbine, the ultra-high-pressure turbine, the high-pressure turbine, and the medium-pressure turbine are configured as one shaft, and the low-pressure turbine is configured as another shaft.

In the steam turbine equipment according to the third aspect of the present invention, in addition to the operation of the second aspect, an extension provided between the tandem compound type or the cross-compound type ultra-high-temperature high-pressure turbine and the ultra-high-pressure turbine is provided. The difference reduction device reduces the difference in elongation between the rotating part and the stationary part.

According to a fourth aspect of the present invention, there is provided an ultra-high pressure high-temperature turbine driven at a steam temperature of 650 ° C. or higher, a high-pressure turbine, a medium-pressure turbine, and a low-pressure turbine driven at a steam temperature of 650 ° C. or lower. Reheats the bleed air of the high pressure turbine, and the steam temperature of the medium pressure turbine is 650 ° C.
A reheater to be supplied as described above, wherein the ultra-high-pressure high-temperature turbine is a steam turbine facility using a Ni-based alloy steel containing 35% or more of Ni in a material of a nozzle, a blade, and a rotor; Steam turbine equipment, characterized in that a differential expansion reduction device that reduces differential expansion between a rotating part and a stationary part is provided between the ultrahigh-pressure turbine and the ultrahigh-pressure turbine.

In the steam turbine equipment according to the fourth aspect of the present invention, an ultra-high-temperature high-pressure turbine driven by steam having a steam temperature of 650 ° C. or higher obtained by the boiler superheater and a steam temperature of 65 ° C.
A differential expansion reduction device provided between the high-pressure turbine driven at 0 ° C. or lower reduces a differential expansion between the rotating part and the stationary part.

According to a fifth aspect of the present invention, in the steam turbine equipment according to the fourth aspect, the ultra-high pressure high temperature turbine, the high pressure turbine, the medium pressure turbine, and the low pressure turbine are tandem compound types each having a single shaft, or The ultra-high pressure high-temperature turbine, the high-pressure turbine, and the medium-pressure turbine are configured as a single shaft, and the low-pressure turbine is a cross-compound type configured as another single shaft.

In the steam turbine equipment according to a fifth aspect of the present invention, in addition to the function of the fourth aspect of the present invention, a differential expansion provided between a tandem compound type or a cross compound type ultra-high-temperature high-pressure turbine and a high-pressure turbine is provided. The reduction device reduces the difference in elongation between the rotating part and the stationary part.

According to a sixth aspect of the present invention, in the steam turbine equipment according to any one of the first to fifth aspects, the differential expansion reduction device comprises the ultra-high pressure high temperature turbine rotor and the ultra high pressure turbine rotor. And a shaft coupling device provided with an axial displacement absorbing mechanism.

According to a sixth aspect of the present invention, in addition to the operation of the first aspect of the present invention, in addition to the operation of the first to fifth aspects, the ultra-high-pressure high-temperature turbine rotor and the ultra-high-pressure turbine rotor The provided shaft coupling device absorbs axial displacement and reduces the difference in extension between the rotating part and the stationary part.

According to a seventh aspect of the present invention, in the steam turbine equipment according to any one of the first to fifth aspects, the differential expansion reduction device changes a position of a stationary portion of the ultra-high pressure high temperature turbine. It is a stationary part moving device to be operated.

In the steam turbine equipment according to a seventh aspect of the present invention, in addition to the operation of any one of the first to fifth aspects, the position of the stationary part of the ultra-high-pressure high-temperature turbine is determined by the stationary part moving device. It is changed to reduce the difference in elongation between the rotating part and the stationary part.

[0036]

Embodiments of the present invention will be described below. FIG. 1 is a configuration diagram of a steam turbine facility according to a first embodiment of the present invention. In this first embodiment,
In the steam turbine equipment shown in FIG. 10, a shaft coupling device 26 as a differential expansion reduction device for reducing a differential expansion between a rotating portion and a stationary portion includes an SP rotor 10 and a VHP-HP rotor 11.
And is additionally provided between them.

The SP turbine 1 is driven at a steam temperature of 650 ° C. or higher, and the VHP turbine 2, HP turbine 3, IP turbine 4, and LP turbine 5 are driven at a steam temperature of 650 ° C. or lower. The SP turbine 1 is formed by using a Ni-based alloy steel containing 35% or more of Ni as a material of a nozzle, a blade, and a rotor.

The shaft coupling device 26 has an axial displacement absorbing mechanism for absorbing the axial displacement and reducing the difference in extension between the rotating part and the stationary part. Further, in addition to the thrust bearing 18 a of the third bearing device 16, the thrust bearing 18
b is provided. With the provision of the thrust bearing 18b, the SP differential expansion meter 24 is provided on the shaft coupling device 26 side, and the VHP differential differential meter 2 is sandwiched between the shaft coupling device 26.
7 is additionally provided.

FIG. 2 is an explanatory view of the shaft coupling device 26. As shown in FIG. 2, the shaft coupling device 26 includes the SP rotor 10 and the V
The first bearing device 14 is provided between the first bearing device 14 and the HP-HP rotor 11, and absorbs a difference in extension between the thrust bearing 18 a and the third bearing device 16. Other configurations are the same as those of the steam turbine equipment shown in FIG. 10, and therefore, the same elements are denoted by the same reference numerals and description thereof will be omitted.

FIG. 3 is an explanatory diagram of a difference in elongation and an axial gap in the steam turbine equipment according to the first embodiment of the present invention. As shown in FIG. 3, the rotor long RL, the rotor short RS, and the rated steady value SS are all the thrust bearings 18a.
From the position X0a of the thrust bearing 18b and the position of the shaft coupling device 26 are discontinuous.
Therefore, the difference in expansion between the VHP turbine 2 and the HP turbine 3 does not affect the difference in expansion between the SP turbine 1 at all.
Thereby, the difference in elongation of the SP turbine 1 is suppressed to a low level.

Next, a second embodiment of the present invention will be described. FIG. 4 is a configuration diagram of the steam turbine equipment according to the second embodiment of the present invention. The second embodiment is different from the first embodiment shown in FIG. 1 in that a stationary part moving device 28 as a differential expansion reduction device for reducing a differential expansion between a rotating part and a stationary part is an SP rotor 10. And VHP-HP rotor 11
And is additionally provided between them. The stationary part moving device 28 changes the position of the stationary part of the SP turbine 1 and reduces the difference in extension between the rotating part and the stationary part.

In the second embodiment, the casing connected from the SP turbine 1 to the LP-A turbine 4a is opened by the SP casing 6 to be independent. The independent SP casing 6 can be moved in the axial direction by the stationary part moving device 28. Stationary part moving device 28
The first bearing stand 14 is composed of a front bearing stand 14a and a rear bearing stand 14B, and can be moved in the axial direction by a hydraulic or motor (not shown). That is, based on information from the SP differential expansion meter 24 and the VHP differential expansion meter 27, the differential expansion is controlled by moving in the axial direction by a hydraulic pressure, a motor, or the like (not shown). Other configurations are the same as those of the steam turbine equipment shown in FIG. 1, and therefore, the same components are denoted by the same reference numerals and description thereof will be omitted.

FIG. 5 is an explanatory diagram of the difference in elongation and the axial gap in the steam turbine equipment according to the second embodiment of the present invention. FIG. 4 shows the difference in elongation when the SP casing 6 is moved and controlled by the stationary part moving device 28 (the front bearing stand 14a and the rear bearing stand 14b) so that the value of the SP elongation difference meter 24 becomes zero.

As shown in FIG. 5, the rotor long RL, the rotor short RS, and the rated steady value SS are the same as those of the thrust bearing 1.
8 is discontinuous at the position of the stationary part moving device 28, starting from the position X0 of position 8. Therefore, when the casing control according to the second embodiment is used, the difference in extension between the SP turbine 1 and the VHP turbine 2 and the HP turbine 3 is S.
It has no effect on the difference in elongation of the P turbine 1. This allows
The difference in elongation of the SP turbine 1 can be kept low.

Next, FIG. 6 is a configuration diagram of a tandem compound type two-stage reheat steam turbine facility in which the SP turbine 1 is independently installed. It is also possible to provide a shaft coupling device 26 and a stationary portion moving device 28 as a device for reducing the difference in extension between the rotating portion and the stationary portion. Although the illustration of the differential expansion reduction device is omitted in FIG. 6, the differential expansion reduction device is S as in the first embodiment and the second embodiment.
It is provided between the P turbine 1 and the VHP turbine 2.

In FIG. 6, the SP turbine 1 is installed independently, and 35% of Ni is used for the material of the nozzle, the blade, and the rotor.
It is configured so that high-temperature strength can be maintained by using the Ni-based alloy steel containing above. And SP turbine 1 is VH
The SP turbine 1, the VHP turbine 2, the HP turbine 3, the IP turbine 4, the LP turbines 5 a and 5 b, and the generator 32 are connected by a single shaft to form a tandem compound type.

The steam having a steam temperature of 650 ° C. or more is supplied from the boiler superheater 29 to the SP turbine 1 and driven. S
The steam that has completed the work in the P turbine 1 becomes steam at 650 ° C. or lower and is led to the VHP turbine 2 and the HP turbine 3. The steam that has completed the work in the VHP turbine 2 is reheated in the first stage reheater 30, and the reheated steam has a steam temperature of 65.
When the temperature reaches 0 ° C. or higher, it is guided to the SP turbine 1.

On the other hand, the steam that has finished its work in the HP turbine 2 is reheated in the second stage reheater 31 and supplied to the IP turbine 4. The steam supplied to the IP turbine 4 is steam having a steam temperature of 650 ° C. or less. Hereinafter, the steam that has completed the work in the IP turbine 4 is the LP-A turbine 5a and the LP-B
It is supplied to the turbine 5b.

As described above, the SP turbine 1 of the tandem compound type steam turbine equipment is provided with the boiler superheater 29.
And a steam having a steam temperature of 650 ° C. or more flowing from the first stage reheater 30, and steam turbines other than the SP turbine 1, namely, the VHP turbine 2, the HP turbine 3, the IP turbine 4
The steam whose steam temperature is suppressed to 650 ° C. or less flows through the LP-A turbine 5a and the LP-B turbine 5b.

Next, FIG. 7 is a configuration diagram of a cross-compound type two-stage reheat steam turbine facility in which the SP turbine 1 is independently installed. It is also possible to provide a shaft coupling device 26 and a stationary portion moving device 28 as a device for reducing the difference in extension between the rotating portion and the stationary portion. Although illustration of the differential expansion reduction device is omitted in FIG. 7, the differential expansion reduction device is SP as in the first embodiment and the second embodiment.
It is provided between the turbine 1 and the VHP turbine 2.

In FIG. 7, the SP turbine 1 is installed independently, and 35% of Ni is used for the material of the nozzle, the blade and the rotor.
It is configured so that high-temperature strength can be maintained by using the Ni-based alloy steel containing above. And SP turbine 1 is VH
P turbine 2, SP turbine 1, VHP turbine 2, HP turbine 3, IP turbine 4, generator 32
a is constituted by one shaft, and the LP turbines 5a, 5a
b, the generator 32b is of a cross-compound type composed of another single shaft. Other steam flow configurations are:
Since they are the same as those shown in FIG. 6, the same elements are denoted by the same reference numerals and description thereof will be omitted.

As described above, the SP turbine 1 of the cross-compound type steam turbine equipment is provided with the boiler superheater 29.
And a steam having a steam temperature of 650 ° C. or more flowing from the first-stage reheater 30, and steam turbines other than the SP turbine 1, that is, the VHP turbine 2, the HP turbine 3, the IP turbine 4,
The steam whose steam temperature is suppressed to 650 ° C. or less flows through the LP-A turbine 5a and the LP-B turbine 5b.

Next, FIG. 8 is a block diagram of a tandem compound type single-stage reheat steam turbine equipment in which the SP turbine 1 is independently installed. The installation of the VHP turbine 2 is omitted, and the SP turbine 1 is replaced with the HP turbine 3. Tandem compound type single-stage reheat steam turbine equipment connected to

For such a one-stage reheated steam turbine facility, a shaft coupling device 26 and a stationary part moving device 28 as a differential expansion reduction device for reducing the differential expansion between the rotating part and the stationary part.
It is also possible to provide. Although illustration of the differential expansion reduction device is omitted in FIG. 8, the differential expansion reduction device is provided between the SP turbine 1 and the HP turbine 3.

In FIG. 8, the SP turbine 1 is installed independently, and 35% of Ni is used for the material of the nozzle, the blade and the rotor.
It is configured so that high-temperature strength can be maintained by using the Ni-based alloy steel containing above. And the SP turbine 1 is HP
The SP turbine 1, the HP turbine 3, the IP turbine 4, the LP turbines 5a and 5b, and the generator 32 are connected by a single shaft to form a tandem compound type.

The steam having a steam temperature of 650 ° C. or more is supplied from the boiler superheater 29 to the SP turbine 1 and driven. S
The steam that has finished work in the P turbine 1 is led to the HP turbine 3. The steam supplied to the HP turbine 4 has a steam temperature
It is steam of 650 ° C or less. The steam that has completed the work in the HP turbine 2 is reheated in the first stage reheater 30 and
Supplied to The steam supplied to the IP turbine 4 is steam having a steam temperature of 650 ° C. or less. Hereinafter, IP turbine 4
Completed the work at LP-A turbine 5a and LP-A
It is supplied to the B turbine 5b.

As described above, the SP turbine 1 of the tandem compound type steam turbine equipment has the boiler superheater 29
Steam having a temperature of 650 ° C. or higher flows from the steam turbines other than the SP turbine 1, ie, the HP turbine 3 and the IP turbine.
The steam whose steam temperature is suppressed to 650 ° C. or lower flows through the turbine 4, the LP-A turbine 5a, and the LP-B turbine 5b.

Next, FIG. 9 is a configuration diagram of a cross-compound type single-stage reheat steam turbine equipment in which the SP turbine 1 is independently installed, and the installation of the VHP turbine 2 is omitted.
The P turbine 1 is a cross-compound type single-stage reheat steam turbine facility connected to the HP turbine 3.

For such a one-stage reheated steam turbine facility, a shaft coupling device 26 and a stationary part moving device 28 as a differential expansion reduction device for reducing the differential expansion between the rotating part and the stationary part.
It is also possible to provide. Although illustration of the differential expansion reduction device is omitted in FIG. 9, the differential expansion reduction device is provided between the SP turbine 1 and the HP turbine 3.

In FIG. 9, the SP turbine 1 is installed independently, and 35% of Ni is used for the material of the nozzle, the blade, and the rotor.
It is configured so that high-temperature strength can be maintained by using the Ni-based alloy steel containing above. And the SP turbine 1 is HP
The turbine is connected to the turbine 3, and the SP turbine 1, the HP turbine 3, the IP turbine 4, and the generator 32a are configured as a single shaft, and the LP turbines 5a, 5b, and the generator 32b are configured as a cross-compound type configured as another single shaft. Has become.
Other configurations of the steam flow are the same as those shown in FIG. 8, and therefore, the same elements are denoted by the same reference numerals and description thereof will be omitted.

As described above, the SP turbine 1 of the cross-compound type steam turbine equipment is provided with the boiler superheater 29.
Steam having a temperature of 650 ° C. or higher flows from the steam turbines other than the SP turbine 1, ie, the HP turbine 3 and the IP turbine.
The steam whose steam temperature is suppressed to 650 ° C. or lower flows through the turbine 4, the LP-A turbine 5a, and the LP-B turbine 5b.

As described above, when the shaft coupling device 26 is provided as the differential expansion reduction device, the shaft coupling device 26 absorbs the elongation of the rotor and reduces the differential expansion. On the other hand, when the stationary part moving device 28 is provided, the casing is moved in the axial direction of the rotor based on information such as a differential expansion meter, so that the extension of the rotor and the casing is not affected by the extension of other casings. The difference can be adjusted.

[0063]

As described above, according to the present invention, S
In the steam turbine equipment having the P turbine, the difference in expansion between the rotating part and the stationary part is provided with a differential expansion reducing device, so that the difference in expansion between the rotating part and the stationary part is suppressed. By reducing the difference in elongation, the amount of leaking steam is reduced, and the performance of the steam turbine is improved. Therefore, safety and reliability are also improved.

[Brief description of the drawings]

FIG. 1 is a configuration diagram of a steam turbine facility according to a first embodiment of the present invention.

FIG. 2 is an explanatory diagram of a shaft coupling device as a differential expansion reduction device according to the first embodiment of the present invention.

FIG. 3 is an explanatory diagram of a difference in elongation and an axial gap in the steam turbine equipment according to the first embodiment of the present invention.

FIG. 4 is a configuration diagram of a steam turbine facility according to a second embodiment of the present invention.

FIG. 5 is an explanatory diagram of a difference in elongation and an axial gap in a steam turbine facility according to a second embodiment of the present invention.

FIG. 6 is a configuration diagram of a tandem compound-type two-stage reheat steam turbine facility in which an SP turbine is independently installed.

FIG. 7 is a configuration diagram of a cross-compound type two-stage reheat steam turbine facility in which an SP turbine is independently installed.

FIG. 8 is a configuration diagram of a tandem compound type single-stage reheat steam turbine facility in which an SP turbine is independently installed.

FIG. 9 is a configuration diagram of a cross-compound type single-stage reheat steam turbine facility in which an SP turbine is independently installed.

FIG. 10 is a configuration diagram of a steam turbine facility in which an SP turbine is added to a conventional steam turbine facility.

FIG. 11 is an explanatory diagram of a difference in elongation and an axial gap in the steam turbine equipment of FIG. 10;

FIG. 12 is a schematic configuration diagram of an SP turbine.

FIG. 13 is an explanatory diagram of a labyrinth packing.

FIG. 14 is an explanatory diagram of a gap of a labyrinth packing.

FIG. 15 is an explanatory diagram of a gap between a blade and a nozzle.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 SP turbine 2 VHP turbine 3 HP turbine 4 IP turbine 5 LP turbine 6 SP casing 7 VHP-HP casing 8 IP casing 9 LP-A casing 10 SP rotor 11 VHP-HP rotor 12 IP rotor 13 LP rotor 14 1st bearing stand 15 2nd bearing stand 16 3rd bearing stand 17 4th bearing stand 18 Thrust bearing 19 Nozzle 20 Blade 21 Packing ring 22 Stationary part side fin 23 Rotor side fin 24 SP differential expansion meter 25 LP differential expansion meter 26 Shaft coupling device 27 VHP Differential elongation meter 28 Stationary part moving device 29 Boiler superheater 30 First stage superheater 31 Second stage superheater 32 Generator

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Kenichi Okuno 2-4, Suehirocho, Tsurumi-ku, Yokohama-shi, Kanagawa Prefecture F-term in Toshiba Keihin Works (reference) 3G071 AA00 AA01 AA03 AA08 AB01 BA21 DA00 FA07

Claims (7)

[Claims] 1. An ultra-high pressure high-temperature turbine driven at a steam temperature of 650 ° C. or more, an ultra-high pressure turbine driven at a steam temperature of 650 ° C. or less, a high-pressure turbine, a medium-pressure turbine, and a low-pressure turbine. A high-pressure high-temperature turbine is a steam turbine facility using a Ni-based alloy steel containing 35% or more of Ni as a material for a nozzle, a blade, and a rotor. Steam turbine equipment provided with a differential expansion reduction device for reducing differential expansion with a section. 2. An ultra-high-pressure high-temperature turbine driven at a steam temperature of 650 ° C. or higher, an ultra-high-pressure turbine, a high-pressure turbine, a medium-pressure turbine, a low-pressure turbine driven at a steam temperature of 650 ° C. or lower, and the ultra-high-pressure turbine A first-stage reheater that reheats the bleed air and supplies the ultra-high-pressure high-temperature turbine with a steam temperature of 650 ° C. or more, and a first-stage reheater that reheats the bleed air of the high-pressure turbine and supplies the medium-pressure turbine with a steam temperature of 650 ° C. or less A steam turbine facility using a Ni-based alloy steel containing 35% or more of Ni for a material of a nozzle, a blade, and a rotor, wherein the ultra-high-pressure high-temperature turbine includes Steam turbine equipment, characterized in that a differential expansion reduction device for reducing a differential expansion between a rotating part and a stationary part is provided between the high-pressure turbine and the high-pressure turbine. 3. The ultra-high pressure high temperature turbine, the ultra high pressure turbine, the high pressure turbine, the medium pressure turbine, and the low pressure turbine,
A tandem compound type configured with a single shaft, or a cross-compound type configured with the ultra-high-pressure high-temperature turbine, the ultra-high-pressure turbine, the high-pressure turbine, and the medium-pressure turbine configured as a single shaft and the low-pressure turbine configured as another single shaft. The steam turbine equipment according to claim 2, wherein 4. An ultra-high-pressure high-temperature turbine driven at a steam temperature of 650 ° C. or more, a high-pressure turbine, a medium-pressure turbine, and a low-pressure turbine driven at a steam temperature of 650 ° C. or less; A reheater that supplies the medium-pressure turbine with a steam temperature of 650 ° C. or more, wherein the ultra-high-pressure high-temperature turbine is made of Ni,
Turbine equipment using a Ni-based alloy steel containing 35% or more of the following, between the ultra-high-temperature and high-pressure turbine and the ultra-high-pressure turbine, provided with a differential expansion reduction device for reducing the differential expansion between the rotating part and the stationary part Steam turbine equipment. 5. The ultra-high-pressure high-temperature turbine, the high-pressure turbine, the medium-pressure turbine, and the low-pressure turbine are tandem compound types configured as a single shaft, or the ultra-high-pressure high-temperature turbine, the high-pressure turbine, and the medium-pressure turbine are configured as a single shaft. The steam turbine equipment according to claim 4, wherein the low-pressure turbine is a cross-compound type constituted by another single shaft. 6. The apparatus according to claim 1, wherein the differential expansion reduction device is a shaft coupling device provided between the ultra-high-pressure high-temperature turbine rotor and the ultra-high-pressure turbine rotor and having an axial displacement absorbing mechanism. The steam turbine equipment according to claim 5. 7. The apparatus according to claim 1, wherein the differential expansion reduction device is a stationary part moving device that changes a position of a stationary part of the ultra-high pressure high temperature turbine. Steam turbine equipment.