JP5869173B2 - Steam turbine rotor - Google Patents

Description

  The present invention relates to a steam turbine rotor.

At present, in thermal power generation using a steam turbine, power generation is generally performed under steam conditions of 600 ° C. or lower. Under such steam conditions, high Cr steel (high chromium steel, ferritic heat resistant steel) such as 12Cr steel is often used as a main member such as a turbine rotor and a moving blade constituting the steam turbine.

However, in recent years, in order to meet the demand for CO ₂ emission reduction and further improvement in thermal efficiency, it is required to generate power under steam conditions of 700 ° C. or higher. However, if ferritic heat resistant steel is used under this steam condition, the high temperature strength of the main member will be insufficient.

  Therefore, in order to ensure higher high-temperature strength, a Ni-based alloy (nickel-based alloy) is used as the main member. However, when this Ni-based alloy is used, it is difficult to increase the size of the main member, and there is a disadvantage that the cost increases.

  In the following Patent Document 1, in order to increase the size and cost of the turbine rotor, a first member formed of a Ni-based alloy and a second member formed of high Cr steel are joined by welding. A turbine rotor is configured. And it is trying to ensure the intensity | strength of a junction part by using Ni base alloy of a specific composition.

International Publication No. 2009/154243

By the way, in general, a Ni-based alloy has properties of low thermal conductivity and a large coefficient of linear expansion. For this reason, at the time of starting of the steam turbine, the outside of the turbine rotor (Ni-based alloy) is heated at a higher temperature than the inside, resulting in a large thermal expansion, and thus there is a problem that excessive stress is generated inside the turbine rotor. .
On the other hand, when warming up is performed so that the temperature of the entire turbine rotor gradually increases, generation of thermal stress can be suppressed, but there is a problem that rapid start-up of the steam turbine is hindered.

  The present invention has been made in view of such circumstances, and it is an object of the present invention to permit quick start-up of a rotating machine and to suppress thermal stress generated in a rotor.

In order to achieve the above object, the present invention employs the following means.
That is, the rotor of the steam turbine according to the first aspect of the present invention is a high-medium pressure integrated steam turbine rotor formed by joining rotor members made of different materials in the axial direction. A first rotor member made of a Ni-based alloy, and the first rotor member has a high-pressure steam introducing portion on one side in the axial direction and on the other side in the axial direction. The first rotor member has a moving blade in a region through which the high-pressure steam passes from the high-pressure steam introduction part to the one end in the axial direction, and the intermediate-pressure steam A moving blade in a region through which the intermediate pressure steam passes from the introduction portion to the other end portion in the axial direction; and the first rotor member is disposed between the high pressure steam introduction portion and the intermediate pressure steam introduction portion. The high-pressure steam and the medium-pressure steam Having a seal portion for partitioning the said second rotor member is made of a material having a molding easier than the Ni-based alloy, the second rotor member, at both ends of the axial direction of the first rotor member One of the second rotor members that are joined to each other and joined to one end portion in the axial direction of the first rotor member has a high-pressure steam discharge portion, and the other of the first rotor member in the axial direction. The other second rotor member joined to the side end portion has an intermediate pressure steam discharge portion, and the one second rotor member extends from the joint end portion with the first rotor member to the high pressure steam discharge portion. The high pressure steam passes in one direction from the high pressure steam introduction part of the first rotor member to the high pressure steam discharge part of the one second rotor member. An area is formed and connected to the area The moving blades of the first rotor member and the moving blades of the one second rotor member, which are respectively arranged, constitute one high-pressure turbine chamber, and the intermediate pressure steam introducing portion of the first rotor member A region where the intermediate pressure steam passes in one direction is formed across the intermediate pressure steam discharge portion of the other second rotor member, and one intermediate pressure turbine is formed by the moving blades of the first rotor member disposed in the region. A chamber is formed, and in the high-pressure turbine chamber, the number of moving blade stages of the first rotor member is greater than the number of moving blade stages of the one second rotor member, and the room temperature serving as the operating region of the steam turbine from a temperature range up to 700 ° C., the average linear expansion coefficient of the first rotor member is in the range of ^{12.4 × 10 -6 /℃~14.5×10 -6 / ℃} , the second rotor member The average linear expansion coefficient is 11.2 × 1 ^-6 it is in the range of /℃~12.4×10 ^-6 / ℃.

The steam turbine rotor according to the second aspect of the present invention is a high-medium-pressure integrated steam turbine rotor formed by joining rotor members made of different materials in the axial direction, and the first rotor member; A first rotor member made of a Ni-based alloy, and the first rotor member has a high-pressure steam introducing portion on one side in the axial direction and on the other side in the axial direction. The first rotor member has a moving blade in a region through which the high-pressure steam passes from the high-pressure steam introduction part to the one end in the axial direction, and the intermediate-pressure steam A moving blade in a region through which the intermediate pressure steam passes from the introduction portion to the other end portion in the axial direction; and the first rotor member is disposed between the high pressure steam introduction portion and the intermediate pressure steam introduction portion. And the high pressure steam and the medium pressure steam. Having a sealing portion off, the second rotor member are each the result of a material having a molding easier than Ni-based alloy, the second rotor member, both ends of the axial direction of the first rotor member One of the second rotor members that are joined and joined to one end portion of the first rotor member in the axial direction has a high-pressure steam discharge portion, and the other side of the first rotor member in the axial direction. The other second rotor member joined to the end portion has an intermediate pressure steam discharge portion, and the other second rotor member extends from the joint end portion with the first rotor member to the intermediate pressure steam discharge portion. The intermediate pressure steam passes through the high pressure steam in one direction from the high pressure steam introduction part of the first rotor member to the high pressure steam discharge part of the one second rotor member. Area to be formed and arranged in the area One blade of the first rotor member constitutes a high-pressure turbine chamber, and the intermediate-pressure steam flows from the intermediate-pressure steam introduction portion of the first rotor member to the intermediate-pressure steam discharge portion of the other second rotor member. A region passing in one direction is formed, and one intermediate-pressure turbine chamber is configured by the moving blades of the first rotor member and the moving blades of the other second rotor member that are arranged in series with the region. In the intermediate pressure turbine chamber, the number of blades of the first rotor member is greater than the number of blades of the second rotor member, and the temperature range from room temperature to 700 ° C., which is the operating region of the steam turbine, in the temperature range up to an average linear expansion coefficient of the first rotor member is in the range of ^{12.4 × 10 -6 /℃~14.5×10 -6 / ℃} , the average line of the second rotor member Expansion coefficient is 11.2 × 10 ^{− It} exists in the range of ⁶ / degrees C-12.4x10 < ^-6 > / degrees C.

ADVANTAGE OF THE INVENTION According to this invention, the quick starting of a rotary machine is accept | permitted and the thermal stress which arises in a rotor can be suppressed.
Further, according to the present invention, it is possible to obtain good operating performance and to prevent the rotor from being damaged.

1 is a schematic cross-sectional view of a high / intermediate pressure turbine T1 according to a first embodiment of the present invention, and is a meridional cross-sectional view including an axis P of the high / intermediate pressure turbine T1. It is an expanded sectional view of shaft 11 concerning an embodiment of the present invention. It is an enlarged sectional view of the shaft 11 _A of the high and intermediate pressure turbine T2 according to the second embodiment of the present invention. It is an enlarged sectional view of the shaft body 11 _B in the high and intermediate pressure turbine T3 according to the third embodiment of the present invention. It is an enlarged sectional view of the shaft body 11 _C in high and intermediate pressure turbine T4 according to the fourth embodiment of the present invention.

Embodiments of the present invention will be described below with reference to the drawings.
"First embodiment"
FIG. 1 is a schematic cross-sectional view of a high and medium pressure turbine (rotary machine) T1 according to a first embodiment of the present invention, and is a meridional cross section including an axis P of the high and medium pressure turbine T1. In the following description, the extending direction of the axis P is the “turbine axial direction (axial direction)”, the circumferential direction of the axis P is the “turbine circumferential direction”, and the radial direction of the axis P is the “turbine radial direction”. Called.

As shown in FIG. 1, the high and medium pressure turbine T1 includes a high-pressure turbine (rotary machine) 1A on one side in the turbine axial direction and a medium-pressure turbine (rotary machine) 1B on the other side in the turbine axial direction. Yes.
The high / medium pressure turbine T <b> 1 includes a rotor 10 and a stator 50.

  The rotor 10 includes a shaft body 11 that is rotatably supported, and a plurality of moving blade rows 12 (12A, 12B) that are configured on the shaft body 11.

  The shaft body 11 penetrates the stator 50 in the turbine axis direction, and both ends in the turbine axis direction are supported by bearing devices 91 and 92 disposed outside the stator 50. Other configurations of the shaft body 11 will be described in detail later.

  Each of the plurality of blade arrays 12 (12A, 12B) is configured by arranging a plurality of blades constrained on the outer periphery of the shaft body 11 in the turbine circumferential direction. The plurality of blade rows 12A are disposed in the high-pressure turbine 1A, and the plurality of blade rows 12B are disposed in the intermediate-pressure turbine 1B.

  The stator 50 includes an outer casing casing 60, an inner casing casing 70 (70A, 70B), and a stationary blade row 52 (52A, 52B).

The outer casing casing 60 includes a casing wall 60a that partitions the inner space 61 from the outside, and a partition wall 60b that partitions the inner space 61 into two in the turbine axial direction. The partition wall 60b is disposed at the approximate center in the turbine axial direction in the internal space 61. The internal space 61 is divided into a high-pressure turbine chamber 61A on one side in the turbine axial direction and an intermediate-pressure turbine chamber on the other side in the turbine axial direction. It is divided into 61B.
On the casing wall 60a of the outer casing casing 60, in the high pressure turbine 1A, a plurality of introduction nozzles 63A formed on the other side in the turbine axis direction and discharge nozzles 64A formed on one side in the turbine axis direction are provided. Is formed. In addition, a plurality of introduction nozzles 63B formed on one side in the turbine axial direction and discharge nozzles 64B formed on the other side in the turbine axial direction are formed on the casing wall 60a in the intermediate pressure turbine 1B. Yes.
The outer casing casing 60 is inserted into the rotor 10 and projects both ends of the rotor 10 (shaft body 11) from both ends of the casing wall 60a in the turbine axial direction.
Note that gaps formed between the casing wall 60a and both ends of the rotor 10 are sealed by sealing devices 93A and 93B, respectively. Further, a gap formed between the partition wall 60b and the center side of the rotor 10 is sealed with seal members 94A and 94B.

The inner casing 70 (70A, 70B) is a cylindrical member that is open at both ends, and includes a stationary blade retaining ring 71 that retains the stationary blade row 52 (52A, 52B) on the inner periphery.
The inner casing casing 70A is disposed in the high pressure turbine 1A, and the inner casing casing 70B is disposed in the intermediate pressure turbine 1B. The inner casing casings 70A and 70B are respectively restrained by the inner wall of the casing wall 60a and the partition wall 60b of the outer casing casing 60. These inner casing casings 70A and 70B are respectively inserted into the rotor 10 and surround the periphery of the outer periphery 10a of the rotor 10. An annular flow path (flow) is formed between the outer periphery 10a of the rotor 10 and the stationary blade holding ring 71. Road) 3 (3A, 3B) extends in the turbine axial direction.

The other end opening portion of the inner casing 70A on the other side in the turbine axial direction is abutted against and closed by the partition wall 60b and is sealed between the rotor 10 by a seal member 94A.
On the other end opening portion side of the inner casing 70A, a manifold (working fluid introduction portion) 3a extending in the turbine circumferential direction and communicating with the annular flow path 3 is defined between the seal member 94A and the outer periphery of the shaft body 11. doing. The manifold 3a is inserted into each introduction nozzle 63A and communicates with a connecting pipe 80A that is airtightly connected to the inner casing casing 70A, and high pressure steam (working fluid) is discharged from the boiler B through the connecting pipe 80A. ) S1 (about 700 ° C.) is supplied. The manifold 3 a is a part that introduces the high-pressure steam S <b> 1 into the annular flow path 3, and is a part where the high-pressure steam S <b> 1 supplied to the high-pressure turbine 1 </ b> A first contacts the rotor 10. That is, in the high-pressure turbine 1 </ b> A during operation, among the parts of the rotor 10, the part exposed to the manifold 3 a has the highest temperature.
Note that one end opening portion of the inner casing 70A is opened toward one side in the turbine axial direction.

The inner casing casing 70B has both ends open in the turbine axial direction. A flange portion 70a extending in a bowl shape from the outer peripheral portion of the inner casing casing 70 is formed on one side of the inner casing casing 70B in the turbine axial direction, and this flange portion 70a is an inner wall of the casing wall 60a. The manifold 3b is demarcated around the open end. Medium pressure steam (working fluid) S2 (about 700 ° C.) is supplied from the boiler B to the manifold 3b via a connecting pipe 80B inserted into each introduction nozzle 63B.
On the other hand, in the internal casing casing 70B, one side of the shaft body 11 in the turbine axial direction is covered with a seal member 94B. That is, the intermediate pressure steam S2 supplied to the manifold 3b is introduced into the annular flow path 3B along the seal member 94B, and the exposed portion (working fluid introduction portion) 3c from the seal member 94B of the rotor 10 is formed. The intermediate pressure steam S2 is the first contact portion. That is, in the intermediate pressure turbine 1B during operation, the exposed portion 3c is the highest temperature from the seal member 94B in each part of the rotor 10.

Each of the plurality of stationary blade rows 52 (52A, 52B) is configured by arranging the stationary blades restrained by the stationary blade holding ring 71 of the inner casing casing 70 (70A, 70B) in the turbine circumferential direction. Yes.
The stationary blade row 52A is arranged so as to alternate with the moving blade row 12A from the other side in the turbine axial direction toward the one side in the annular flow path 3A of the high-pressure turbine 1A. The stationary blade row 52B is disposed in the annular flow path 3B of the intermediate pressure turbine 1B so as to alternate with the moving blade row 12B from one side to the other side in the turbine axial direction.

FIG. 2 is an enlarged cross-sectional view of the shaft body 11.
As shown in FIG. 2, the shaft body 11 is configured by joining rotor members 20, 30, and 40 to each other in the turbine shaft direction. More specifically, the rotor members 20, 30, and 40 are axially formed as a whole by being joined in the above order in a state where the respective axis lines are overlapped with the axis line P.

The rotor member (second rotor member) 20 has a small diameter portion 21 formed with a relatively small diameter and a large diameter portion 22 formed with a relatively large diameter.
In the large diameter portion 22, one end portion 20a on one side in the turbine axial direction is recessed in a dish shape, and the other end portion 20b is connected to, for example, the end portion of the rotor _RL of the low pressure turbine (see FIG. 1).

The rotor member (second rotor member) 40 has a small diameter portion 41 formed with a relatively small diameter and a large diameter portion 42 formed with a relatively large diameter.
In the rotor member 40, the other end portion 40b on the other side of the rotor member 40 in the turbine axial direction is recessed in a dish shape, and the one end portion 40a is connected to, for example, the end portion of the rotor _RVH of the ultrahigh pressure turbine (see FIG. 1).
The material of the rotor members 20 and 40 is, for example, high Cr steel, and is formed by forging, for example. As this high Cr steel, for example, those having the compositions of 1-1 and 1-2 shown in Table 1 below can be suitably used. High Cr steels having these compositions have an average linear expansion coefficient from room temperature to 700 ° C. of approximately 11.2 × 10 ⁻⁶ / ° C. to 12.4 × 10 ⁻⁶ ° C.
Of course, high Cr steel having a composition other than that shown in Table 1 may be used.

なお、表１における％は、重量％を意味する。

In Table 1, “%” means “% by weight”.

なお、表２における％は、重量％を意味する。 The rotor member (first rotor member) 30 has both end portions (joint end portions) 30a and 30b in the turbine axial direction recessed in a dish shape.
The rotor member 30 is made of a Ni-based alloy and has a relatively low thermal conductivity and a high linear expansion coefficient. As this Ni-based alloy, for example, those having the compositions of 2-1 2-2, 2-3, 2-4, 2-5 and 2-6 shown in Table 2 below can be suitably used. The Ni-based alloys having these compositions have an average linear expansion coefficient from room temperature to 700 ° C. of approximately 12.4 × 10 ⁻⁶ / ° C. to 14.5 × 10 ⁻⁶ ° C. Low compared to alloys.
Of course, a Ni-based alloy having a composition other than that shown in Table 2 may be used.

In Table 2, “%” means “% by weight”.

One end 30 a of the rotor member 30 is joined by welding in a state of being abutted against the other end 40 b of the rotor member 40. Further, the other end 30 b of the rotor member 30 is joined by welding in a state of being abutted with the one end 20 a of the rotor member 20.
The joints at both end portions 30a and 30b in the turbine axial direction of the rotor member 30 may be set as small as possible in the thickness d as long as the necessary strength is ensured in the operating state of the high and medium pressure turbine T1. desirable.

As shown in FIG. 2, the interior of the rotor member 30 is formed hollow. More specifically, a hole 31 formed with a constant inner diameter D1 extends in the turbine axis direction on the axis P, and the one end 30a and the other end 30b communicate with each other. That is, the rotor member 30 has a smaller heat capacity than when the rotor member 30 is formed solid (when the hole 31 is not formed).
The thickness of each part in the turbine axial direction center side where the hole 31 of the rotor member 30 is formed is such that the ratio value of the inner diameter D1 to the outer diameter D2 becomes 1/2 or more, and the turbine of the rotor member 30 It is formed so as to be equal to or greater than the thickness d of both end portions 30a and 30b in the axial direction.

Then, the effect | action of the high intermediate pressure turbine T1 which consists of the said structure is demonstrated using figures.
First, when the high intermediate pressure turbine T1 is started, the high pressure steam S1 flows into the high pressure turbine 1A and the intermediate pressure steam S2 flows into the intermediate pressure turbine 1B.

  As shown in FIG. 1, for example, high-pressure turbine 1 </ b> A is supplied with high-pressure steam S <b> 1 reheated by boiler B after passing through an ultrahigh-pressure turbine (not shown) to manifold 3 a via connection pipe 80 </ b> A. Then, the high-pressure steam S1 is introduced into the annular flow path 3A along the rotor member 30, and imparts rotational force to the rotor 10 by flowing through the moving blade row 12A and the stationary blade row 52A in order. The high-pressure steam S1 passing through the annular flow path 3A is discharged from the high-pressure turbine 1A via the discharge nozzle 64A and sent to the boiler B.

On the other hand, for example, to the intermediate pressure turbine 1B, the intermediate pressure steam S2 that has been discharged from the high pressure turbine 1A and then reheated by the boiler B is supplied to the manifold 3b via the connecting pipe 80B.
Then, the intermediate pressure steam S2 is introduced from the manifold 3b into the annular flow path 3B along the seal member 94B, and rotates in the rotor 10 by sequentially flowing through the moving blade row 12B and the stationary blade row 52B in the annular flow path 3B. Giving power. The intermediate pressure steam S2 passing through the annular flow path 3B is discharged from the intermediate pressure turbine 1B via the discharge nozzle 64B and sent to the boiler (not shown).

At this time, since the heat capacity is reduced because the inside of the rotor member 30 in the rotor 10 is hollow, the temperature difference between the outside and the inside in the rotor member 30 (more precisely, the meat part). It's hard to get stuck.
In other words, since the rotor member 30 is formed hollow, the distance of the heat transfer path from the outer peripheral end to the inner peripheral end of the rotor member 30 is shorter than when the rotor member 30 is formed solid. The heat transmitted from the high-pressure steam S <b> 1 to the outer peripheral end of the rotor member 30 is quickly conducted (arrived) to the inner peripheral end of the rotor member 30. For this reason, the temperature gradient in the turbine radial direction becomes gentle inside the rotor member 30, and the inside and outside of the rotor member 30 have the same temperature.

In proportion to the temperature difference between the outside and the inside of the rotor member 30, the difference in thermal expansion between the outside and the inside of the rotor member 30 is also slight. For this reason, the thermal stress which arises in the inside of the rotor member 30 is suppressed significantly.
While continuing such a state, the rotor member 30 is generally heated to the temperature of the operation state of the high and medium pressure turbine T1.
And the high intermediate pressure turbine T1 transfers to a steady state from a starting state. After shifting to the steady state, the rotor member 30 rotates at a constant temperature as a whole.

  As described above, according to the high and medium pressure turbine T1, the rotor member 30 made of the Ni-based alloy is hollow in the entire turbine axial direction, so that the rotor is compared with the case where the interior is solid. The heat capacity of the member 30 is reduced. Accordingly, when the high-medium pressure turbine T1 is quickly started, the temperature difference generated between the outside and the inside of the rotor member 30 is suppressed, and the rotor member 30 is generally heated. Thereby, the thermal stress which arises inside the rotor member 30 can be suppressed. Therefore, rapid start-up of the high / medium pressure turbine T1 can be allowed and thermal stress generated in the rotor 10 can be suppressed.

  Further, since the shaft body 11 is adjacent to the rotor member 30 in the turbine axial direction and includes rotor members 20 and 40 made of high Cr steel, the rotor is compared with the case where the entire shaft body 11 is formed of a Ni-based alloy. The cost of 10 can be suppressed. Furthermore, the rotor 10 can be easily manufactured by forming a part of the shaft body 11 with a high Cr steel having excellent formability as compared with the Ni-based alloy.

Further, when the rotor member 30 is formed of the Ni-based alloy having the composition shown in Table 2, the average linear expansion coefficient from room temperature to 700 ° C. is smaller than that of the Ni-based alloy having another composition. Thereby, as compared with Ni-based alloys having other compositions, it is difficult for thermal elongation to occur in the rotor member 30, so that thermal stress generated inside the rotor member 30 can be further suppressed.
Further, by forming the rotor members 20 and 40 with high Cr steel having the composition shown in Table 1 and forming the Ni base alloy having the composition shown in Table 2 on the rotor member 30, the difference in mutual linear expansion coefficient is small. Become. As a result, the strength of the joint between the rotor members 20 and 40 and the rotor member 30 can be ensured.

  Further, since the thickness of the rotor member 30 on the center side in the turbine axial direction is formed so that the value of the ratio of the inner diameter D1 to the outer diameter D2 is 1/2 or more, the outer side and the inner side of the rotor member 30 are formed. And the thermal stress generated in the rotor member 30 can be further suppressed. On the other hand, the thickness of the rotor member 30 at the center side in the turbine axial direction is formed so as to be equal to or greater than the thickness d of both end portions 30a and 30b in the turbine axial direction of the rotor member 30, so that necessary strength is ensured. be able to.

Furthermore, since the high and medium pressure turbine T1 according to the present invention includes the rotor 10, even if a Ni-based alloy is used in a steam condition of 700 ° C. or higher, rapid startup of the high and medium pressure turbine T1 is permitted, and the rotor 10 is suppressed. As a result, good operating performance can be obtained and damage to the rotor 10 can be prevented. Then, it is possible to sufficiently meet the demands of the steam S1, S2 relatively high temperature (about 700 ° C.) CO ₂ emissions by setting the reduction and further improvements in thermal efficiency of.

“Second Embodiment”
Hereinafter, a second embodiment of the present invention will be described with reference to the drawings. In the following description and the drawings used for the description, the same components as those already described are denoted by the same reference numerals, and redundant description is omitted.

Figure 3 is an enlarged sectional view of the shaft 11 _A of the second embodiment according to the high and intermediate pressure turbine (rotary machine) T2 of the present invention.
While the shaft body 11 of the first embodiment described above has the rotor member 30 formed integrally, as shown in FIG. 3, the shaft body 11 of the high and medium pressure turbine T2 according to the present embodiment. _{In A} , rotor members (first rotor members) 32 </ b> A and 32 </ b> B are disposed at positions corresponding to the rotor member 30.

The rotor members 32A and 32B are made of a Ni-based alloy like the rotor member 30, and both end portions (joint end portions) 32a and 32b in the turbine axial direction are recessed in a dish shape. Each of the rotor members 32A and 32B is formed hollow.
One end 32a of the rotor member 32A is joined by welding in a state of being abutted with the other end 40b of the rotor member 40.
One end 32d of the rotor member 32B is joined by welding in a state of being abutted against the one end 20a of the rotor member 20.
Further, the other end portion 32b of the rotor member 32A and the other end portion 32c of the rotor member 32B are joined together by welding (joint material welding) in a state of abutting each other.

The rotor member 32A has a hole 31A formed on the axis P with a constant inner diameter D1 extending in the turbine axis direction. In the rotor member 32B, a hole 31B formed with a constant inner diameter D3 (≠ inner diameter D1) extends in the turbine axis direction on the axis P.
That is, the rotor members 32A and 32B have different inner diameters.

According to the high and medium pressure turbine T2, the main effects of the first embodiment described above can be obtained, and the manifold 3a and the exposed portion 3c have different inner diameters (D1 ≠ D3). In addition, the temperature distribution can be adjusted in each of the exposed portions 3c (the high pressure turbine 1A and the intermediate pressure turbine 1B).
Even if the rotor members 32A and 32B have the same inner diameter, the main effects of the first embodiment described above can be obtained.

"Third embodiment"
Hereinafter, a third embodiment of the present invention will be described with reference to the drawings. In the following description and the drawings used for the description, the same components as those already described are denoted by the same reference numerals, and redundant description is omitted.

Figure 4 is an enlarged sectional view of the shaft body 11 _B in the third embodiment according to the high and intermediate pressure turbine (rotary machine) T3 of the present invention.
Whereas shaft 11 _A of the second embodiment described above has had a rotor member 32B containing hole 31B, as shown in FIG. 4, a shaft body 11 of the high and intermediate pressure turbine T3 according to the present embodiment _B Has a solid rotor member 33 instead of the rotor member 32B.
The rotor member 33 is made of a Ni-based alloy, with one end (joining end) 33a being abutted against the other end 32b of the rotor member 32A, and the other end 33b being one end of the rotor member 20. In the state of being abutted against 20a, each is joined by welding.

According to the high / medium pressure turbine T3, the main effect of the first embodiment and the second embodiment described above can be obtained in the rotor member 32A, and the inside of the rotor member 33 is formed solid. The rigidity of the rotor member 33 can be increased in the pressure turbine 1B.
The rotor member 33 may be hollow (rotor member 32B) and the rotor member 32A may be solid.

"Fourth embodiment"
Hereinafter, a fourth embodiment of the present invention will be described with reference to the drawings. In the following description and the drawings used for the description, the same components as those already described are denoted by the same reference numerals, and redundant description is omitted.

Figure 5 is an enlarged sectional view of the shaft 11 _C high and intermediate in pressure turbine (rotary machine) T4 according to the fourth embodiment of the present invention.
Second Embodiment of the shaft 11 _A is hole 31A as described above, while the 31B had rotor member 32A are respectively formed at a constant inner diameter D1, D3, and 32B, as shown in FIG. 5, shaft body 11 _C the high and intermediate pressure turbine T4 according to the present embodiment, the hole 35A formed in the respective rotor member (first rotor member) 34A inside diameter of 35B are different at each site of the turbine axis, the 34B Yes doing.

For example, the hole 35A of the rotor member 34A is formed in a tapered shape so that the inner diameter gradually decreases from the other side in the turbine axial direction toward the one side.
The hole 35B of the rotor member 34B is formed in a tapered shape so that the inner diameter gradually decreases from one side in the turbine axial direction to the other side, for example.

  According to the high and medium pressure turbine T4, the main effects of the first embodiment and the second embodiment described above can be obtained, and the inner diameters of the rotor members 34A and 34B (holes 35A and 35A, 35B) are different from each other, the temperature of the rotor members 34A and 34B (the high-pressure turbine 1A and the intermediate-pressure turbine 1B) can be adjusted in the turbine axial direction.

In the present embodiment, the hole 35A is tapered so that the inner diameter gradually decreases from one side in the turbine axis direction toward the other side, but from the other side in the turbine axis direction toward the one side. You may form so that an internal diameter may become small gradually. Further, there may be a portion formed with a constant inner diameter in a part of the hole 35A. Further, there may be a portion that decreases after the inner diameter of the hole 35A increases in the turbine axial direction. The same applies to the hole 35B.
Similarly to the present embodiment, the inner diameter of each hole in the first embodiment to the third embodiment may be changed in the turbine axial direction.

Note that the operation procedure shown in the above-described embodiment, various shapes and combinations of the constituent members, and the like are examples, and various modifications can be made based on design requirements and the like without departing from the gist of the present invention.
For example, in the above-described embodiment, the end portions of the rotor members 20, 30, 40, 32A, 32B33, 34A, and 34B in the turbine axial direction are formed in a dish shape, but a recess is formed in the turbine axial direction in other shapes. May be. Moreover, you may form in flat shape, without forming a hollow in a flat turbine axial direction.

  Moreover, although the case where this invention was applied to the high intermediate pressure turbines T1-T4 was demonstrated in embodiment mentioned above, you may apply this invention to the turbine of another pressure range. Moreover, you may apply this invention to rotary machines other than a turbine.

1A ... High-pressure turbine (rotary machine)
1B ... Medium pressure turbine (rotary machine)
3 (3A, 3B) ... annular channel (channel)
3a ... Manifold (working fluid introduction part)
3c: Exposed part (working fluid introduction part)
10 ... rotor 10a ... outer periphery 20 ... rotor member (second rotor member)
30 ... Rotor member (first rotor member)
30a, 30b ... Both ends (joint ends)
32A, 32B ... rotor member (first rotor member)
32a, 32b ... both ends (joint ends)
32c, 32d ... both ends (joint ends)
33 ... Rotor member (first rotor member)
33a ... one end (joint end)
34A ... Rotor member (first rotor member)
34B ... Rotor member (first rotor member)
40 ... Rotor member (second rotor member)
50 ... Stator P ... Axis d ... Thickness D1, D3 ... Inner diameter D2 ... Outer diameter S1 ... High pressure steam (working fluid)
S2 ... Medium pressure steam (working fluid)
T1, T2, T3, T4 ... High and medium pressure turbine (rotary machine)

Claims (2)

In a high-medium pressure integrated steam turbine rotor formed by axially joining rotor members made of different materials,
A first rotor member;
A second rotor member,
The first rotor member is made of a Ni-based alloy,
The first rotor member has a high-pressure steam introduction part on one side in the axial direction, and an intermediate-pressure steam introduction part on the other side in the axial direction,
The first rotor member has a moving blade in a region through which the high-pressure steam passes from the high-pressure steam introduction portion to one end portion in the axial direction, and the other side in the axial direction from the intermediate-pressure steam introduction portion. Having a moving blade in a region through which the intermediate pressure steam to the end passes,
The first rotor member has a seal portion that partitions the high pressure steam and the intermediate pressure steam between the high pressure steam introduction portion and the intermediate pressure steam introduction portion,
The second rotor member is made of a material that is easier to mold than the Ni-based alloy,
The second rotor member are respectively joined to both ends of the axial direction of the first rotor member,
One of the second rotor members joined to one end of the first rotor member in the axial direction has a high-pressure steam discharge part,
The other second rotor member joined to the other end portion in the axial direction of the first rotor member has an intermediate pressure steam discharge portion,
The one second rotor member has a moving blade in a region through which the high-pressure steam passes from a joint end with the first rotor member to the high-pressure steam discharge unit,
A region through which the high-pressure steam passes in one direction is formed from the high-pressure steam introduction portion of the first rotor member to the high-pressure steam discharge portion of the one second rotor member, and the regions are arranged continuously to the region. One moving blade of the first rotor member and the moving blade of the one second rotor member constitute one high-pressure turbine chamber,
A region through which the intermediate pressure steam passes in one direction is formed from the intermediate pressure steam introduction portion of the first rotor member to the intermediate pressure steam discharge portion of the other second rotor member, and the region is disposed in the region. One intermediate pressure turbine chamber is constituted by the rotor blades of the first rotor member,
In the high-pressure turbine chamber, the number of blades of the first rotor member is greater than the number of blades of the first rotor member,
In the temperature range of from room temperature to the operating region of the steam turbine to 700 ° C., the first rotor range average linear expansion coefficient of 12.4 × ^{10 -6} /℃~14.5×10 ^-6 / ℃ member an inner rotor of a steam turbine, wherein the average linear expansion coefficient of the second rotor member is in the range of ^{11.2 × 10 -6 /℃~12.4×10 -6 / ℃} . In a high-medium pressure integrated steam turbine rotor formed by axially joining rotor members made of different materials,
A first rotor member;
A second rotor member,
The first rotor member is made of a Ni-based alloy,
The first rotor member has a high-pressure steam introduction part on one side in the axial direction, and an intermediate-pressure steam introduction part on the other side in the axial direction,
The first rotor member has a moving blade in a region through which the high-pressure steam passes from the high-pressure steam introduction portion to one end portion in the axial direction, and the other side in the axial direction from the intermediate-pressure steam introduction portion. Having a moving blade in a region through which the intermediate pressure steam to the end passes,
The first rotor member has a seal portion that partitions the high pressure steam and the intermediate pressure steam between the high pressure steam introduction portion and the intermediate pressure steam introduction portion,
The second rotor member is made of a material that is easier to mold than the Ni-based alloy,
The second rotor member are respectively joined to both ends of the axial direction of the first rotor member,
One of the second rotor members joined to one end of the first rotor member in the axial direction has a high-pressure steam discharge part,
The other second rotor member joined to the other end portion in the axial direction of the first rotor member has an intermediate pressure steam discharge portion,
The other second rotor member has a moving blade in a region through which the intermediate pressure steam passes from a joint end with the first rotor member to the intermediate pressure steam discharge part,
A region where the high-pressure steam passes in one direction is formed from the high-pressure steam introduction portion of the first rotor member to the high-pressure steam discharge portion of the one second rotor member, and the first rotor is disposed in the region. A high pressure turbine chamber is constituted by the moving blades of the members,
A region through which the intermediate-pressure steam passes in one direction is formed from the intermediate-pressure steam introduction portion of the first rotor member to the intermediate-pressure steam discharge portion of the other second rotor member, and the regions are arranged continuously to the region. A medium pressure turbine chamber is constituted by the moving blade of the first rotor member and the moving blade of the other second rotor member,
In the intermediate pressure turbine chamber, the number of blades of the first rotor member is greater than the number of blades of the other second rotor member,
In the temperature range of from room temperature to the operating region of the steam turbine to 700 ° C., the first rotor range average linear expansion coefficient of 12.4 × ^{10 -6} /℃~14.5×10 ^-6 / ℃ member an inner rotor of a steam turbine, wherein the average linear expansion coefficient of the second rotor member is in the range of ^{11.2 × 10 -6 /℃~12.4×10 -6 / ℃} .

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