Patent Publication Number: US-11655723-B2

Title: Rotating machine

Description:
FIELD 
     The present invention relates to a rotating machine where a sealing device for suppressing leakage of fluid is disposed between a stationary side and a rotation side. 
     BACKGROUND 
     For example, a steam turbine has a structure in which a rotor is rotatably supported by a bearing in a casing and a plurality of stages of rotor blades are fixed to the rotor, and on the other hand, a plurality of stages of stator blades are fixed to the casing between the respective stages of rotor blades. When the steam is supplied from a supply port of the casing, the steam passes through the rotor blades and the stator blades so as to drive and rotate the rotor through the respective stages of rotor blades, and then, the steam is discharged from a discharge port. 
     In such a steam turbine, in order to suppress the leakage and flow of the steam in an axial direction between the casing and a tip of the rotor blade, a sealing device is provided between the casing and the tip of the rotor blade. This sealing device is usually a labyrinth seal. A labyrinth seal is formed by a plurality of seal fins provided on the tip of the rotor blade or an inner surface of the casing. By forming a gap between the seal fins and the inner surface of the casing or the tip of the rotor blade, the pressure ratio before and after each seal fin is reduced so that the leakage flow rate is suppressed. 
     The flow of the steam leaking from the sealing device joins the mainstream of the steam passing through the rotor blades or the stator blades. The mainstream of the steam passing through the rotor blades is the flow along the axial direction of the rotor, and the flow of the steam leaking from the sealing device without passing through the rotor blades is inclined from an inner circumferential surface of the casing toward the rotor and swirled in a circumferential direction of the rotor by the stator blades. In this case, it is important to make the flow of the steam leaking from the sealing device smoothly join the mainstream of the steam so as to reduce the mixing loss at this joining portion and suppress the decrease in performance. One example of such a technique is described in Patent Literature 1 below. 
     CITATION LIST 
     Patent Literature 
     Patent Literature 1: Japanese Patent No. 5985351 
     SUMMARY 
     Technical Problem 
     In the axial flow turbine according to Patent Literature 1 described above, a swirling flow adjustment chamber is provided on the downstream side of the seal fin, and in this swirling flow adjustment chamber, a plurality of shielding plates extending in the axial direction and the radial direction of the rotor are fixed. Therefore, in the flow of the steam swirling in the circumferential direction that leaks from the sealing device without passing through the rotor blades, the velocity component in the circumferential direction is reduced by the shielding plates and therefore, the flow of the steam leaking from the sealing device can smoothly join the mainstream of the steam. In the conventional axial flow turbine, however, the shielding plate has a plate shape extending in the axial direction and the radial direction of the rotor; therefore, when the flow of the steam along the circumferential direction collides with the shielding plate, a separation vortex may be generated in a connection portion of the shielding plate and pressure loss may occur. 
     The present invention has been made in order to solve the above problem, and an object is to provide a rotating machine for improving the performance by reducing the mixing loss at the joining portion in a manner that the fluid leaking from the sealing device joins smoothly the mainstream of the fluid. 
     Solution to Problem 
     In order to achieve the object, a rotating machine according to the present invention includes a casing having a hollow shape; a rotator rotatably supported in the casing; a stator blade fixed to an inner peripheral portion of the casing; a rotor blade fixed to an outer peripheral portion of the rotator while being displaced from the stator blade in an axial direction of the rotator; a sealing device disposed between the inner peripheral portion of the casing and a tip of the rotor blade; a swirling flow generation chamber provided along a circumferential direction of the rotator on a downstream side of the sealing device in the casing in a fluid flow direction; and a plurality of guiding members provided at predetermined intervals in the swirling flow generation chamber in the circumferential direction of the rotator. The guiding members each include a first guiding surface that is inclined in the circumferential direction with respect to the axial direction of the rotator. 
     Therefore, when the fluid is supplied into the casing, the mainstream of the fluid passes through the stator blades and the rotor blades, thereby rotating the rotor blades; on the other hand, a part of the fluid flows between the casing and the tip of the rotor blades after passing through the stator blades. However, the sealing device functions to suppress the leakage of the fluid. In this case, the sealing device leaks a part of the fluid and this leakage fluid swirls in the swirling flow generation chamber and then joins the mainstream of the fluid having passed through the stator blades and the rotor blades. Here, since the leakage fluid leaking from the sealing device passes through the stator blades but does not pass through the rotor blades, the leakage fluid has the velocity component in the circumferential direction. The guiding members provided in the swirling flow generation chamber includes the first guiding surface that is inclined in the circumferential direction with respect to the axial direction of the rotator. Therefore, the leakage fluid with the velocity component in the circumferential direction swirls in the radial direction after the first guiding surface of the guiding member reduces the velocity component in the circumferential direction, and then joins the mainstream of the fluid. In addition, since the first guiding surface is inclined, when the leakage fluid with the velocity component in the circumferential direction collides with this first guiding surface, the separation vortex at the connection portion of the guiding member in the swirling flow generation chamber is reduced and the occurrence of the pressure loss is suppressed. As a result, by making the fluid leaking from the sealing device smoothly join the mainstream of the fluid, the mixing loss at the joining portion can be reduced and the performance can be improved. 
     In the rotating machine according to the present invention, the first guiding surface is provided along a swirling direction of fluid leaking from the sealing device. 
     Therefore, since the first guiding surface is provided along the swirling direction of the fluid leaking from the sealing device, the leakage fluid with the velocity component in the circumferential direction is smoothly guided along the first guiding surface. 
     Accordingly, the separation vortex in the swirling flow generation chamber is reduced and the occurrence of the pressure loss can be suppressed. 
     In the rotating machine according to the present invention, an end portion of the first guiding surface on the downstream side in the fluid flow direction is inclined to a downstream side in the rotational direction of the rotator with respect to the axial direction of the rotator. 
     Therefore, since the end portion of the first guiding surface on the downstream side in the fluid flow direction is inclined to the downstream side in the rotational direction of the rotator, the leakage fluid with the velocity component in the circumferential direction is smoothly guided along the first guiding surface. 
     Accordingly, the separation vortex in the swirling flow generation chamber is reduced and the occurrence of the pressure loss can be suppressed. 
     In the rotating machine according to the present invention, the guiding members each include an extension portion extending from the swirling flow generation chamber to an upstream side in the fluid flow direction, and the first guiding surface is formed on a surface of the extension portion on a downstream side in the rotational direction of the rotator. 
     Therefore, since the first guiding surface is formed on the surface of the extension portion on the downstream side in the rotational direction of the rotator, the leakage fluid with the velocity component in the circumferential direction is smoothly guided along the first guiding surface. Accordingly, the separation vortex in the swirling flow generation chamber is reduced and the occurrence of the pressure loss can be suppressed. 
     In the rotating machine according to the present invention, the first guiding surface includes a base end surface extending from the casing side to the upstream side in the fluid flow direction, and a front end surface curved from the base end surface to the upstream side in the fluid flow direction and an upstream side in the rotational direction of the rotator. 
     Therefore, since the base end surface extending to the upstream side in the fluid flow direction and the front end surface curved to the upstream side in the rotational direction of the rotator are provided as the first guiding surface, when the leakage fluid with the velocity component in the circumferential direction is smoothly guided along the curved front end surface, the velocity component in the circumferential direction is reduced, and then, when the leakage fluid is guided to the base end surface along the fluid flow direction, the leakage fluid whose velocity component in the circumferential direction is reduced can be discharged properly from the swirling flow generation chamber. 
     In the rotating machine according to the present invention, the first guiding surface includes a base end surface extending from the casing side to the upstream side in the fluid flow direction and the downstream side in the rotational direction of the rotator, and a front end surface curved from the base end surface to the upstream side in the fluid flow direction and an upstream side in the rotational direction of the rotator. 
     Therefore, since the base end surface extending to the upstream side in the fluid flow direction and the downstream side in the rotational direction of the rotator and the front end surface curved to the upstream side in the rotational direction of the rotator are provided as the first guiding surface, when the leakage fluid with the velocity component in the circumferential direction is smoothly guided along the curved front end surface, the velocity component in the circumferential direction is reduced, and then, when the leakage fluid is guided to the base end surface extending to the downstream side in the rotational direction, the leakage fluid whose velocity component in the circumferential direction is reduced can be discharged properly from the swirling flow generation chamber. 
     In the rotating machine according to the present invention, an end portion of the extension portion on the upstream side in the fluid flow direction has a curved shape. 
     Therefore, since the end portion of the extension portion has the curved shape, the separation when the leakage fluid with the velocity component in the circumferential direction collides with the extension portion can be suppressed, and accordingly, by guiding the leakage fluid smoothly to the first guiding surface, the velocity component in the circumferential direction can be reduced. 
     In the rotating machine according to the present invention, the sealing device includes a seal fin extending from one of the inner peripheral portion of the casing and the tip of the rotor blade to the other and forming a gap, an inclination angle between the first guiding surface and the axial direction of the rotator is largest at a position facing the gap on the downstream side in the fluid flow direction, and the inclination angle becomes smaller to an outside and an inside in a radial direction of the rotator. 
     Therefore, since the inclination angle at the first guiding surface is the largest at the position facing the gap on the downstream side in the fluid flow direction, and the inclination angle becomes smaller to the outside and the inside, the velocity component in the circumferential direction of the leakage fluid with the velocity component in the circumferential direction is reduced when the leakage fluid collides with the first guiding surface at the position where the inclination angle is the largest, and then when the leakage fluid is guided at the position where the inclination angle is the smallest, the leakage fluid whose velocity component in the circumferential direction is reduced can be discharged properly from the swirling flow generation chamber. 
     In the rotating machine according to the present invention, a length of the interval between the guiding members that are adjacent in the circumferential direction of the rotator is smallest at the position facing the gap on the downstream side in the fluid flow direction and becomes larger to the outside and the inside in the radial direction of the rotator. 
     Therefore, since the length of the interval between the guiding members that are adjacent in the circumferential direction of the rotator is the smallest at the position corresponding to the gap and becomes larger to the outside and the inside, the velocity component in the circumferential direction of the leakage fluid with the velocity component in the circumferential direction is reduced when the leakage fluid collides with the position where the interval between the guiding members is the smallest, and then when the leakage fluid is guided at the position where the interval between the guiding members is the largest, the velocity of the leakage fluid whose velocity component in the circumferential direction is reduced in the swirling flow generation chamber can be reduced and the swirling flow with the proper velocity can be generated. 
     In the rotating machine according to the present invention, a length of the interval between the guiding members that are adjacent in the circumferential direction of the rotator is largest at the position facing the gap on the downstream side in the fluid flow direction and becomes smaller to the outside and the inside in the radial direction of the rotator. 
     Therefore, since the length of the interval between the guiding members that are adjacent in the circumferential direction of the rotator is the largest at the position corresponding to the gap and becomes smaller to the outside and the inside, the velocity component in the circumferential direction of the leakage fluid with the velocity component in the circumferential direction is reduced when the leakage fluid collides with the position where the interval between the guiding members is the largest, and then when the leakage fluid is guided at the position where the interval between the guiding members is the smallest, the velocity of the leakage fluid whose velocity component in the circumferential direction is reduced in the swirling flow generation chamber can be increased and the swirling flow with the proper velocity can be generated. 
     In the rotating machine according to the present invention, the guiding members each include a second guiding surface on a surface on an upstream side in the rotational direction of the rotator, and an end portion of the second guiding surface on the downstream side in the fluid flow direction is inclined to a downstream side in the rotational direction of the rotator with respect to the axial direction of the rotator. 
     Therefore, since the second guiding surface is formed on the surface on the upstream side in the rotational direction of the rotator and the end portion of the second guiding surface on the downstream side in the fluid flow direction is inclined to the downstream side in the rotational direction of the rotator, the leakage fluid with the velocity component in the circumferential direction is guided smoothly along the second guiding surface and accordingly, the separation vortex in the swirling flow generation chamber is reduced and the occurrence of the pressure loss can be suppressed. 
     In the rotating machine according to the present invention, the guiding members each include a second guiding surface on a surface on an upstream side in the rotational direction of the rotator, and an end portion of the second guiding surface on the downstream side in the fluid flow direction is inclined to the upstream side in the rotational direction of the rotator with respect to the axial direction of the rotator. 
     Therefore, since the second guiding surface is formed on the surface on the upstream side in the rotational direction of the rotator and the end portion of the second guiding surface on the downstream side in the fluid flow direction is inclined to the upstream side in the rotational direction of the rotator, the leakage fluid with the velocity component in the circumferential direction is guided smoothly along the second guiding surface and accordingly, the separation vortex in the swirling flow generation chamber is reduced and the occurrence of the pressure loss can be suppressed. 
     In the rotating machine according to the present invention, the swirling flow generation chamber includes an inner circumferential surface of the casing, a first wall surface facing the sealing device in the casing on the downstream side in the fluid flow direction, and a second wall surface facing the inner circumferential surface of the casing on an inside in the radial direction of the rotator, and the guiding members are fixed to the inner circumferential surface of the casing, the first wall surface, and the second wall surface. 
     Therefore, since the swirling flow generation chamber is formed by the inner circumferential surface of the casing, the first wall surface, and the second wall surface and the guiding member is fixed to the inner circumferential surface of the casing, the first wall surface, and the second wall surface, the leakage fluid from the sealing device can generate the swirling flow with the proper shape in the swirling flow generation chamber and can smoothly join the mainstream of the fluid. 
     Advantageous Effects of Invention 
     By the rotating machine according to the present invention, by making the fluid leaking from the sealing device smoothly join the mainstream of the fluid, the mixing loss at the joining portion can be reduced and the performance can be improved. 
    
    
     
       BRIEF DESCRIPTION OF DRAWINGS 
         FIG.  1    is a cross-sectional view of a main part for describing the flow of steam in a steam turbine as a rotating machine according to a first embodiment. 
         FIG.  2    is a cross-sectional view taken along II-II in  FIG.  1   , illustrating the flow of leakage steam with respect to a guiding member. 
         FIG.  3    is a cross-sectional view of a main part of a steam turbine, illustrating a modification of the first embodiment. 
         FIG.  4    is a schematic view illustrating the steam turbine according to the first embodiment. 
         FIG.  5    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a second embodiment. 
         FIG.  6    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a third embodiment. 
         FIG.  7    is a cross-sectional view illustrating the flow of the leakage steam with respect to the guiding member, illustrating a modification of the third embodiment. 
         FIG.  8    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a fourth embodiment. 
         FIG.  9    is a cross-sectional view illustrating the flow of the leakage steam with respect to the guiding member, illustrating a modification of the fourth embodiment. 
         FIG.  10    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a fifth embodiment. 
         FIG.  11    is a cross-sectional view of a main part for describing the flow of the steam in a steam turbine as a rotating machine according to a sixth embodiment. 
         FIG.  12    is a cross-sectional view taken along XII-XII in  FIG.  11    for describing the shape of the guiding member. 
         FIG.  13    is a cross-sectional view taken along XIII-XIII in  FIG.  12   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  14    is a cross-sectional view taken along XIV-XIV in  FIG.  12   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  15    is a cross-sectional view for describing the shape of a guiding member, illustrating a modification of the sixth embodiment. 
         FIG.  16    is a cross-sectional view for describing the shape of a guiding member according to a seventh embodiment. 
         FIG.  17    is a cross-sectional view for describing the shape of a guiding member, illustrating a modification of the seventh embodiment. 
         FIG.  18    is a cross-sectional view for describing the shape of a guiding member according to an eight embodiment. 
         FIG.  19    is a cross-sectional view taken along XIX-XIX in  FIG.  18   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  20    is a cross-sectional view taken along XX-XX in  FIG.  18   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  21    is a cross-sectional view for describing the shape of a guiding member, illustrating a first modification of the eighth embodiment. 
         FIG.  22    is a cross-sectional view taken along XXII-XXII in  FIG.  21   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  23    is a cross-sectional view taken along XXIII-XXIII in  FIG.  21   , illustrating the flow of the leakage steam with respect to the guiding member. 
         FIG.  24    is a cross-sectional view of a guiding member, illustrating a second modification of the eighth embodiment. 
         FIG.  25    is a cross-sectional view of the guiding member, illustrating the second modification of the eighth embodiment. 
     
    
    
     DESCRIPTION OF EMBODIMENTS 
     Preferred embodiments of a rotating machine according to the present invention are hereinafter described in detail with reference to the attached drawings. Note that the embodiments do not limit the present invention and in a case where there are a plurality of embodiments, the embodiments may be combined. 
     First Embodiment 
       FIG.  4    is a schematic view illustrating a steam turbine according to the present embodiment. In the following description, the axial direction of a rotor is expressed as A, the radial direction of the rotor is expressed as R, and the circumferential direction of the rotor is expressed as C. 
     In the example of the present embodiment, the rotating machine according to the present invention is a steam turbine. As illustrated in  FIG.  4   , a steam turbine  10  includes a casing  11 , a rotor (rotator)  12 , stator blades  13 , rotor blades  14 , and sealing devices  15 . 
     The casing  11  has a hollow shape, and the rotor  12  is disposed inside the casing  11  along a horizontal direction. The rotor  12  is supported rotatably by a bearing  20  provided to the casing  11  using a center axis O as a center. The stator blades  13  are fixed to an inner peripheral portion of the casing  11  at predetermined intervals in the axial direction A of the rotor  12 . A plurality of rotor discs  21  are fixed to an outer peripheral portion of the rotor  12  at predetermined intervals in the axial direction A, and the rotor blades  14  are fixed to an outer peripheral portion of each rotor disc  21 . The stator blades  13  and the rotor blades  14  are disposed along the radial direction R of the rotor  12  at predetermined intervals in the circumferential direction of the rotor  12 , and disposed alternately along the axial direction A of the rotor  12 . 
     The casing  11  includes a steam inlet  22  on one end portion side thereof in the axial direction A. The steam inlet  22  communicates with a blade cascade part  24  where the stator blades  13  and the rotor blades  14  are arranged through a steam passage  23 . This blade cascade part  24  communicates with a steam discharge port  26  through an exhaust hood  25 . 
     In addition, the rotor  12  includes a seal member  27  between each end portion thereof in the axial direction A and the casing  11 . Each seal member  27  is disposed more internally than each bearing  20 , that is, on the stator blade  13  and rotor blade  14  side. Furthermore, the sealing device  15  is provided between a tip of the rotor blade  14  on the outside in the radial direction R and the inner peripheral portion of the casing  11 . 
     Therefore, after steam S is supplied from the steam inlet  22  to the blade cascade part  24  through the steam passage  23 , this steam S passes through the stator blades  13  and the rotor blades  14  and accordingly, the rotor  12  is driven and rotated through the rotor blades  14 , so that a power generator, which is not illustrated, connected to this rotor  12  is driven. After that, the steam S that has driven the rotor blades  14  is discharged from the steam discharge port  26  through the exhaust hood  25 . 
     Here, the relation among the casing  11 , the stator blades  13 , the rotor blades  14 , and the sealing devices  15  in the aforementioned steam turbine  10  is described in detail.  FIG.  1    is a cross-sectional view of a main part for describing the flow of the steam in the steam turbine as the rotating machine according to the first embodiment, and  FIG.  2    is a cross-sectional view taken along II-II in  FIG.  1   , illustrating the flow of the leakage steam with respect to a guiding member. 
     As illustrated in  FIG.  1    and  FIG.  2   , the sealing device  15  is provided between the casing  11  and the tip of the rotor blade  14 . The sealing device  15  is to suppress the leakage of the flow of the steam (fluid) S that flows from a high-pressure side H to a low-pressure side L along the axial direction A of the rotor  12  between the casing  11  and the tip of the rotor blade  14 . Here, the steam S flows from the high-pressure side H to the low-pressure side L, and mainstream steam S 1  flows along a steam flow direction A 1  so as to pass through the stator blades  13  and the rotor blades  14 . In addition, the mainstream steam S 1  having passed through the stator blade  13  partially flows to the sealing device  15  between the casing  11  and the tip of the rotor blade  14 , and leakage steam S 2  that leaks from the sealing device  15  is generated. This leakage steam S 2  passes through the stator blade  13  but does not pass through the rotor blade  14 ; therefore, the leakage steam S 2  has a velocity component in the circumferential direction C. 
     That is to say, the mainstream steam S 1  is the flow in the axial direction A that hardly has the velocity component in the circumferential direction C, and flows with an absolute velocity vector V 1  on a leading edge side of the stator blade  13 . The mainstream steam S 1  is accelerated or turned when passing between the vanes of the stator blades  13 , and has an absolute velocity vector V 2  with the velocity component in the circumferential direction C, and flows out from a trailing edge side of the stator blade  13 . The steam S flowing out from the stator blades  13  mostly collides with the rotor blades  14 , so that the rotor  12  together with the rotor blades  14  are rotated at a predetermined rotation velocity in a rotational direction C 1 . In this case, the steam S is decelerated and turned when passing through the rotor blades  14 , and has an absolute velocity vector V 3  along the axial direction A that hardly has the velocity component in the circumferential direction C. 
     On the other hand, the absolute velocity vector V 2  of the steam S having passed between the blades of the stator blades  13  has the velocity component in the circumferential direction C, and the leakage steam S 2  that leaks from the sealing device  15  without passing through the rotor blades  14  has its velocity changing due to the viscous friction of the side wall or the cover or the acceleration/deceleration of a seal fin, which is described below, but is the flow with the velocity component in the circumferential direction C. Therefore, when the leakage steam S 2  joins the mainstream steam S 1  with the absolute velocity vector V 3  that hardly has the velocity component in the circumferential direction C, the mixing loss occurs at the joining portion. 
     Here, although the impulse turbine in which the mainstream steam S 1  hardly has the velocity component in the circumferential direction C has been described; however, even in a reaction turbine in which the mainstream steam S 1  has the velocity component in the circumferential direction C, the mixing loss occurs in the joining portion like the impulse turbine because the mainstream steam S 1  and the leakage steam S 2  are different in direction vector. The present invention is also applicable to, and still effective in this reaction turbine. 
     The steam turbine  10  according to the first embodiment includes a swirling flow generation chamber  31  and a plurality of guiding members  32 . The swirling flow generation chamber  31  is provided along the circumferential direction C of the rotor  12  on the downstream side of the sealing device  15  in the casing  11  in the steam flow direction A 1 . The guiding members  32  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  32  has a first guiding surface  33  that is inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The stator blades  13  are provided in a manner that a base end portion thereof positioned on the outside in the radial direction R is fixed to the inner peripheral portion of the casing  11 , while the rotor blades  14  are provided in a manner that a base end portion thereof positioned on the inside in the radial direction R is fixed to the outer peripheral portion of the rotor  12  (see  FIG.  4   ). The rotor blades  14  are disposed between the stator blades  13  disposed at predetermined intervals in the axial direction A. In the rotor blade  14 , a shroud  41  is provided at the tip that is positioned on the outside in the radial direction R. The sealing device  15  is disposed between the inner peripheral portion of the casing  11  and an outer peripheral portion of the shroud  41  in the rotor blade  14 . 
     The casing  11  includes a recessed portion  42  on an inner circumferential surface  11   a  opposite to the outer peripheral portion of the shroud  41 . The recessed portion  42  is an annular groove that is provided along the circumferential direction C of the rotor  12 . The shroud  41  of the rotor blade  14  is disposed in the recessed portion  42  of the casing  11 . The sealing device  15  includes a plurality of seal fins  43 ,  44 , and  45 . The seal fins  43  and  44  are provided in a manner that a base end portion thereof is fixed to an inner circumferential surface  42   a  of the recessed portion  42  in the casing  11 , and a tip thereof extends toward an outer circumferential surface  41   a  of the shroud  41  of the rotor blade  14 . The seal fin  45  is provided between the seal fins  43  and  44  in a manner that a base end portion thereof is fixed to the outer circumferential surface  41   a  of the shroud  41  of the rotor blade  14  and a tip thereof extends toward the inner circumferential surface  42   a  of the recessed portion  42  in the casing  11 . 
     The seal fins  43 ,  44 , and  45  are provided at predetermined intervals in the axial direction A of the rotor  12 . The seal fins  43 ,  44 , and  45  are provided along the circumferential direction C of the rotor  12 . There is a predetermined gap secured between the tip of the seal fins  43  and  44  and the outer circumferential surface  41   a  of the shroud  41 . In addition, there is a predetermined gap secured between the tip of the seal fin  45  and the inner circumferential surface  42   a  of the recessed portion  42 . These predetermined gaps have substantially the same size. Note that the seal fins  43 ,  44 , and  45  may be more than the aforementioned fins or may be attached at other positions. 
     The recessed portion  42  of the casing  11  is longer than the shroud  41  of the rotor blade  14  in the axial direction A. That is to say, the recessed portion  42  is provided ranging from the upstream side of the leading edge of the rotor blade  14  in the steam flow direction A 1  to the downstream side of the trailing edge of the rotor blade  14  in the steam flow direction A 1 . The swirling flow generation chamber  31  is provided on the downstream side of the trailing edge of the rotor blade  14  in the steam flow direction A 1  in the recessed portion  42 . The swirling flow generation chamber  31  includes an inner circumferential surface  46  of the casing  11  (recessed portion  42 ), a first wall surface  47  facing the sealing device  15  in the casing  11  on the downstream side in the steam flow direction A 1 , and a second wall surface  48  facing the inner side of the inner circumferential surface  11   a  of the casing  11  in the radial direction R of the rotor  12  (see  FIG.  4   ). 
     That is to say, the inner circumferential surface  46  exists on the outside of the inner circumferential surface  42   a  of the recessed portion  42  in the radial direction R, and continues along the circumferential direction C. The first wall surface  47  is a surface parallel to the radial direction R and orthogonal to the inner circumferential surface  46 , and continues along the circumferential direction C. The casing  11  includes a protrusion  49  extending to the upstream side (recessed portion  42  side) in the steam flow direction A 1  from the inner circumferential surface  11   a  of the casing  11  on the downstream side of the steam flow direction A 1  in the recessed portion  42 . The second wall surface  48  is provided on the outside of the protrusion  49  in the radial direction R, is parallel to the inner circumferential surface  46  and orthogonal to the first wall surface  47 , and continues along the circumferential direction C. 
     The guiding member  32  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  33  provided to the guiding member  32  is provided along the swirling direction of the leakage steam S 2  that leaks from the sealing device  15 . An end portion of the first guiding surface  33  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. 
     The guiding member  32  includes a solid or hollow extension portion  51  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  33  is formed on a surface of the extension portion  51  on the downstream side in the rotational direction C 1 . The guiding member  32  includes a second guiding surface  52  on a surface thereof on the upstream side in the rotational direction C 1 . The second guiding surface  52  is provided along the axial direction A. 
     That is to say, the guiding member  32  includes the extension portion  51  extending from the first wall surface  47  to the upstream side in the steam flow direction A 1 . The extension portion  51  is provided along the radial direction R, and has one end portion in the radial direction R fixed to the inner circumferential surface  46  and the other end portion fixed to the second guiding surface  52 . The extension portion  51  has a cross-sectional shape that is like a right angled triangle (see  FIG.  2   ), includes the first guiding surface  33  along the radial direction R on the downstream side in the rotational direction C 1 , and includes the second guiding surface  52  along the radial direction R on the upstream side in the rotational direction C 1 . The end portion of the first guiding surface  33  on the downstream side in the steam flow direction A 1  is inclined by a predetermined inclination angle θ 1  to the downstream side in the rotational direction C 1  with respect to the axial direction A, and also inclined by a predetermined inclination angle with respect to the first wall surface  47 . 
     This predetermined inclination angle θ 1  is set in accordance with the angle where the leakage steam S 2  with the velocity component in the circumferential direction C enters with respect to the guiding member  32 . The angle where the leakage steam S 2  with the velocity component in the circumferential direction C enters is set in accordance with the shape of the stator blade  13 . The predetermined inclination angle θ 1  is greater than 0° and less than 90°, and is preferably in the range of 30° to 50°. The second guiding surface  52  is parallel to the axial direction A and is perpendicular to the first wall surface  47 . 
     Therefore, when the steam S is supplied into the casing  11  and the rotor blades  14  are rotated, the steam S flows along the steam flow direction A 1  from the high-pressure side H to the low-pressure side L. Here, the steam S flows so that the mainstream steam S 1  passes through the stator blades  13  and the rotor blades  14  and a part of the steam S flows to the sealing device  15  provided between the casing  11  and the tip of the rotor blade  14  without passing through the rotor blades  14 . This sealing device  15  suppresses the leakage of the steam S; however, the steam S partially leaks and the leakage steam S 2  is generated. The leakage steam S 2  leaking from the sealing device  15  is swirled in the swirling flow generation chamber  31  and joins the mainstream steam S 1  having passed through the stator blade  13  and the rotor blade  14 . 
     Here, the leakage steam S 2  leaking from the sealing device  15  passes through the stator blade  13  but does not pass through the rotor blade  14 ; therefore, the leakage steam S 2  has the velocity component in the circumferential direction C. The leakage steam S 2  with the velocity component in the circumferential direction C becomes swirling flow steam S 3  with a center axis along the circumferential direction C in the swirling flow generation chamber  31 . That is to say, the leakage steam S 2  collides with the first guiding surface  33  and the second guiding surface  52  of the guiding member  32 . Then, since the first guiding surface  33  is inclined in the circumferential direction, a part of the leakage steam S 2  is guided smoothly to the first guiding surface  33  and another part thereof is guided to the second guiding surface  52 . Since the leakage steam S 2  is guided to the first guiding surface  33  and the second guiding surface  52 , the velocity component in the circumferential direction C is reduced and after that, since the leakage steam S 2  is guided to the first wall surface  47 , the leakage steam S 2  becomes the swirling flow steam S 3  that swirls in the swirling flow generation chamber  31  on the inner circumferential surface  46  side. 
     The swirling flow steam S 3  that has swirled in the swirling flow generation chamber  31  passes between the shroud  41  and the protrusion  49  and as leakage steam S 4  whose velocity component in the circumferential direction C is reduced, smoothly joins the mainstream steam S 1  having passed through the rotor blade  14 . In addition, since the first guiding surface  33  is inclined, the angle between the first guiding surface  33  and the first wall surface  47  is obtuse. Therefore, when the leakage steam S 2  with the velocity component in the circumferential direction C collides with the first guiding surface  33 , after the velocity component in the circumferential direction C is reduced, the leakage steam S 2  is guided to the first guiding surface  33  and the first wall surface  47  and becomes the swirling flow steam S 3 ; however, the separation vortex at the connection portion between the first guiding surface  33  and the first wall surface  47  is reduced and the occurrence of pressure loss here is suppressed. 
     In the aforementioned description, the guiding member  32  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 ; however, the structure is not limited to this example.  FIG.  3    is a cross-sectional view of a main part of a steam turbine, illustrating a modification of the first embodiment. 
     In a modification of the rotating machine according to the first embodiment, the swirling flow generation chamber  31  is provided on the downstream side of the trailing edge of the rotor blade  14  in the recessed portion  42  in the steam flow direction A 1  as illustrated in  FIG.  3   . The swirling flow generation chamber  31  includes the inner circumferential surface  46  of the casing  11  (recessed portion  42 ), and the first wall surface  47  facing the sealing device  15  in the casing  11  on the downstream side in the steam flow direction A 1 . In this modification, neither the protrusion  49  nor the second wall surface  48  (both are illustrated in  FIG.  1   ) is provided. 
     Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C becomes the swirling flow steam S 3  in the swirling flow generation chamber  31 . That is to say, the leakage steam S 2  collides with the first guiding surface  33  and the second guiding surface  52  of the guiding member  32 . Then, since the first guiding surface  33  is inclined in the circumferential direction, a part of the swirling flow steam S 3  is guided smoothly to the first guiding surface  33  and another part thereof is guided to the second guiding surface  52 . Since the leakage steam S 2  is guided to the first guiding surface  33  and the second guiding surface  52 , the velocity component in the circumferential direction C is reduced and after that, since the leakage steam S 2  is guided to the first wall surface  47 , the leakage steam S 2  becomes the swirling flow steam S 3  that swirls in the swirling flow generation chamber  31  on the inner circumferential surface  46  side. The swirling flow steam S 3  having swirled in the swirling flow generation chamber  31  passes between the shroud  41  and the inner circumferential surface  11   a  of the casing  11 , and as the leakage steam S 4  whose velocity component in the circumferential direction C is reduced, smoothly joins the mainstream steam S 1  having passed through the rotor blade  14 . 
     The rotating machine according to the first embodiment includes the casing  11  having a hollow shape, the rotor  12  rotatably supported in the casing  11 , the stator blades  13  fixed to the inner peripheral portion of the casing  11 , the rotor blades  14  fixed to the outer peripheral portion of the rotor  12  while being displaced from the stator blades  13  in the axial direction A of the rotor  12 , the sealing devices  15  each disposed between the inner peripheral portion of the casing  11  and the tip of the rotor blade  14 , the swirling flow generation chamber  31  provided along the circumferential direction C of the rotor  12  on the downstream side of the sealing device  15  in the casing  11  in the steam flow direction A 1 , and the guiding members  32  provided in the swirling flow generation chamber  31  at the predetermined intervals in the circumferential direction C of the rotor  12 . The guiding member  32  includes the first guiding surface  33  that is inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C becomes the swirling flow steam S 3  whose velocity component in the circumferential direction C is reduced by the first guiding surface  33  of the guiding member  32  and can join the mainstream steam S 1 . Since the first guiding surface  33  is inclined, when the leakage steam S 2  with the velocity component in the circumferential direction C is guided to the first guiding surface  33 , the separation vortex at the connection portion of the guiding member  32  in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss is suppressed. As a result, by making the leakage steam S 2  (S 5 ) leaking from the sealing device  15  join the mainstream steam S 1  smoothly, the mixing loss at the joining portion can be reduced and the performance can be improved. 
     In the rotating machine according to the first embodiment, the first guiding surface  33  is provided along the swirling direction of the steam S leaking from the sealing device  15 . Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided smoothly along the first guiding surface  33  and the separation vortex in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss can be suppressed. 
     In the rotating machine according to the first embodiment, the end portion of the first guiding surface  33  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided smoothly along the first guiding surface  33  and the separation vortex in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss can be suppressed. 
     In the rotating machine according to the first embodiment, the guiding member  32  includes the extension portion  51  extending from the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1  and the first guiding surface  33  is formed on a surface of the extension portion  51  on the downstream side in the rotational direction C 1  of the rotor  12 . Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided smoothly along the first guiding surface  33 , and thus, the separation vortex in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss can be suppressed. 
     In the rotating machine according to the first embodiment, the swirling flow generation chamber  31  includes the inner circumferential surface  46  of the casing  11 , the first wall surface  47  facing the sealing device  15  in the casing  11  on the downstream side in the steam flow direction A 1 , and the second wall surface  48  facing the inner circumferential surface  46  of the casing  11  on the inside in the radial direction R of the rotor  12 . The guiding member  32  is fixed to the inner circumferential surface  46  of the casing  11 , the first wall surface  47 , and the second wall surface  48 . Therefore, the leakage steam S 2  from the sealing device  15  can generate the swirling flow with a proper shape in the swirling flow generation chamber  31  and can smoothly join the mainstream steam S 1 . 
     Second Embodiment 
       FIG.  5    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a second embodiment. Note that the basic structure of the second embodiment is similar to that of the aforementioned first embodiment, and is described using  FIG.  1   . The member with the function similar to that in the aforementioned first embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the second embodiment, as illustrated in  FIG.  1    and  FIG.  5   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  60 . The swirling flow generation chamber  31  is similar to that in the first embodiment. The guiding members  60  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  60  includes a first guiding surface  61  and a second guiding surface  62  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The guiding member  60  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  61  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  60  includes a solid or hollow extension portion  63  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  61  is formed on a surface of the extension portion  63  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  61  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. 
     On the other hand, the second guiding surface  62  is formed on a surface of the extension portion  63  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  62  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     The end portion of the first guiding surface  61  on the downstream side in the steam flow direction A 1  is inclined by the predetermined inclination angle θ 1  to the downstream side in the rotational direction C 1  with respect to the axial direction A, and is also inclined at a predetermined inclination angle with respect to the first wall surface  47 . On the other hand, the end portion of the second guiding surface  62  on the downstream side in the steam flow direction A 1  is inclined by a predetermined inclination angle θ 2  to the downstream side in the rotational direction C 1  with respect to the axial direction A, and is also inclined at a predetermined inclination angle with respect to the first wall surface  47 . The predetermined inclination angle θ 1  is larger than the predetermined inclination angle θ 2 . The predetermined inclination angle θ 1  and the predetermined inclination angle θ 2  are set in accordance with the angle where the leakage steam S 2  with the velocity component in the circumferential direction C enters with respect to the guiding member  60 . 
     Therefore, the leakage steam S 2  leaking from the sealing device  15  becomes the swirling flow steam S 3  with the center axis along the circumferential direction C in the swirling flow generation chamber  31 . That is to say, the leakage steam S 2  collides with the first guiding surface  61  and the second guiding surface  62  of the guiding member  60 . Then, the first guiding surface  61  and the second guiding surface  62  are inclined in the circumferential direction and accordingly, the leakage steam S 2  is guided smoothly to the first guiding surface  61  and the second guiding surface  62 . Since the leakage steam S 2  is guided to the first guiding surface  61  and the second guiding surface  62 , the velocity component in the circumferential direction C is reduced and after that, since the leakage steam S 2  is guided to the first wall surface  47 , the leakage steam S 2  becomes the swirling flow steam S 3  that swirls in the swirling flow generation chamber  31  on the inner circumferential surface  46  side. 
     The swirling flow steam S 3  that has swirled in the swirling flow generation chamber  31  becomes the leakage steam S 4  whose velocity component in the circumferential direction C is reduced, and smoothly joins the mainstream steam S 1  having passed through the rotor blade  14 . In addition, since the first guiding surface  61  is inclined, the angle between the first guiding surface  61  and the first wall surface  47  is obtuse. Therefore, when the leakage steam S 2  with the velocity component in the circumferential direction C collides with the first guiding surface  61 , after the velocity component in the circumferential direction C is reduced, the leakage steam S 2  is guided to the first guiding surface  61  and the first wall surface  47  and becomes the swirling flow steam S 3 ; however, the separation vortex at the connection portion between the first guiding surface  61  and the first wall surface  47  is reduced and the occurrence of pressure loss here is suppressed. In addition, since the second guiding surface  62  is inclined, when the leakage steam S 2  with the velocity component in the circumferential direction C collides with the second guiding surface  62 , the velocity component in the circumferential direction C is reduced. Then, since the swirling flow steam S 3  guided by the first guiding surface  61  and the first wall surface  47  and the swirling flow steam S 3  guided by the second guiding surface  62  and the first wall surface  47  join as appropriate, the swirling flow steam S 3  whose velocity component in the circumferential direction C is reduced can be obtained. 
     In the rotating machine according to the second embodiment, the guiding member includes the second guiding surface  62  on the surface on the upstream side in the rotational direction C 1  of the rotor  12 , and the end portion of the second guiding surface  62  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     Therefore, since the leakage steam S 2  with the velocity component in the circumferential direction C is smoothly guided along the second guiding surface  62 , the separation vortex in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss can be suppressed. 
     Third Embodiment 
       FIG.  6    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a third embodiment. Note that the basic structure of the third embodiment is similar to that of the aforementioned first embodiment, and is described using  FIG.  1   . The member with the function similar to that in the aforementioned first embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the third embodiment, as illustrated in  FIG.  1    and  FIG.  6   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  70 . The swirling flow generation chamber  31  is similar to that in the first embodiment. The guiding members  70  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  70  includes a first guiding surface  71  and a second guiding surface  72  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The guiding member  70  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  71  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  70  includes an extension portion  73  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  71  is formed on a surface of the extension portion  73  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  71  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. 
     On the other hand, the second guiding surface  72  is formed on a surface of the extension portion  73  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  72  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     The first guiding surface  71  includes a base end surface  71   a  extending from the first wall surface  47  of the casing  11  to the upstream side in the steam flow direction A 1 , and a front end surface  71   b  curved from this base end surface  71   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . Therefore, the base end surface  71   a  of the first guiding surface  71  is parallel to the axial direction A, and the front end surface  71   b  thereof is curved and inclined to the upstream side in the rotational direction C 1  with respect to the axial direction A. 
     On the other hand, the second guiding surface  72  includes a base end surface  72   a  extending from the first wall surface  47  of the casing  11  to the upstream side in the steam flow direction A 1 , and a front end surface  72   b  curved from this base end surface  72   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . Therefore, the base end surface  72   a  of the second guiding surface  72  is parallel to the axial direction A, and the front end surface  72   b  thereof is curved and inclined to the upstream side in the rotational direction C 1  with respect to the axial direction A. In this case, the extension portion  73  of the guiding member  70  has a plate shape, and the thickness is the same or becomes smaller in the range of the base end portion side to the tip side. 
     Note that the shape of the guiding member  70  is not limited to the aforementioned shape.  FIG.  7    is a cross-sectional view illustrating the flow of the leakage steam with respect to the guiding member, illustrating a modification of the third embodiment. 
     In the modification of the third embodiment, as illustrated in  FIG.  1    and  FIG.  7   , a guiding member  80  includes a first guiding surface  81  and a second guiding surface  82  inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  80  includes an extension portion  83  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  81  is formed on a surface of the extension portion  83  on the downstream side in the rotational direction C 1 . The second guiding surface  82  is formed on a surface of the extension portion  83  on the upstream side in the rotational direction C 1 . 
     The first guiding surface  81  includes a base end surface  81   a  extending from the first wall surface  47  of the casing  11  to the upstream side in the steam flow direction A 1  and the downstream side in the rotational direction C 1  of the rotor  12 , and a front end surface  81   b  curved from this base end surface  81   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . On the other hand, the second guiding surface  82  includes a base end surface  82   a  extending from the first wall surface  47  of the casing  11  to the upstream side in the steam flow direction A 1  and the downstream side in the rotational direction C 1  of the rotor  12 , and a front end surface  82   b  curved from this base end surface  82   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . 
     In the rotating machine according to the third embodiment, the first guiding surface  71  includes the base end surface  71   a  extending from the casing  11  side to the upstream side in the steam flow direction A 1 , and the front end surface  71   b  curved from this base end surface  71   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . 
     The leakage steam S 2  with the velocity component in the circumferential direction C is guided smoothly along the curved front end surface  71   b , so that the velocity component in the circumferential direction C is reduced and after that, the leakage steam S 2  is guided to the base end surface  71   a  along the steam flow direction A 1 , so that the leakage steam S 2  whose velocity component in the circumferential direction C is reduced can be discharged from the swirling flow generation chamber  31  as appropriate. 
     In the rotating machine according to the third embodiment, the first guiding surface  81  includes the base end surface  81   a  extending from the casing  11  side to the upstream side in the steam flow direction A 1  and the downstream side in the rotational direction C 1  of the rotor  12 , and the front end surface  81   b  curved from the base end surface  81   a  to the upstream side in the steam flow direction A 1  and the upstream side in the rotational direction C 1  of the rotor  12 . 
     Therefore, since the leakage steam S 2  with the velocity component in the circumferential direction C is smoothly guided along the curved front end surface  81   b , the velocity component in the circumferential direction C is reduced, and after that, since the leakage steam S 2  is guided to the front end surface  81   a  extending to the downstream side in the rotational direction C 1 , the leakage steam S 2  whose velocity component in the circumferential direction C is reduced can be discharged from the swirling flow generation chamber  31  as appropriate. 
     Fourth Embodiment 
       FIG.  8    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a fourth embodiment. Note that the basic structure of the fourth embodiment is similar to that of the aforementioned first embodiment, and is described using  FIG.  1   . The member with the function similar to that in the aforementioned first embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the fourth embodiment, as illustrated in  FIG.  1    and  FIG.  8   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  90 . The swirling flow generation chamber  31  is similar to that in the first embodiment. The guiding members  90  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  90  includes a first guiding surface  91  that is inclined in the circumferential direction C with respect to the axial direction A of the rotor  12  and a second guiding surface  92  that is parallel to the axial direction A of the rotor  12 . 
     The guiding member  90  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  91  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  90  includes a solid or hollow extension portion  93  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  91  is formed on a surface of the extension portion  93  on the downstream side in the rotational direction C 1 . The second guiding surface  92  is formed on a surface of the extension portion  93  on the upstream side in the rotational direction C 1 . 
     An end portion of the extension portion  93  on the upstream side in the steam flow direction A 1  has a curved shape. That is to say, the extension portion  93  includes a curved portion  94  at a tip where the first guiding surface  91  and the second guiding surface  92  intersect. 
     The shape of the guiding member  90  is not limited to the aforementioned shape.  FIG.  9    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a modification of the fourth embodiment. 
     In the modification of the fourth embodiment, as illustrated in  FIG.  1    and  FIG.  9   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  100 . The swirling flow generation chamber  31  is similar to that in the first embodiment. The guiding members  100  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  100  includes a first guiding surface  101  and a second guiding surface  102  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The guiding member  100  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  101  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  100  includes a solid or hollow extension portion  103  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  101  is formed on a surface of the extension portion  103  on the downstream side in the rotational direction C 1 . The second guiding surface  102  is formed on a surface of the extension portion  103  on the upstream side in the rotational direction C 1 . 
     An end portion of the extension portion  103  on the upstream side in the steam flow direction A 1  has a curved shape. That is to say, a curved portion  104  is provided at a tip of the extension portion  103  where the first guiding surface  101  and the second guiding surface  102  intersect. 
     In the rotating machine according to the fourth embodiment, an end portion of each of the extension portions  93  and  103  on the upstream side in the steam flow direction A 1  has a curved shape. Therefore, when the leakage steam S 2  with the velocity component in the circumferential direction C collides with the extension portions  93  and  103 , the leakage steam S 2  is guided smoothly to the first guiding surfaces  91  and  101  and the second guiding surfaces  92  and  102  by the curved portions  94  and  104 , and the separation here can be suppressed. By smoothly guiding the leakage steam S 2  to the first guiding surfaces  91  and  101 , the velocity component in the circumferential direction C can be reduced. 
     Fifth Embodiment 
       FIG.  10    is a cross-sectional view illustrating the flow of the leakage steam with respect to a guiding member according to a fifth embodiment. Note that the basic structure of the fifth embodiment is similar to that of the aforementioned first embodiment, and is described using  FIG.  1   . The member with the function similar to that in the aforementioned first embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the fifth embodiment, as illustrated in  FIG.  1    and  FIG.  10   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  110 . The swirling flow generation chamber  31  is similar to that in the first embodiment. The guiding members  110  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  110  includes a first guiding surface  111  and a second guiding surface  112  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The guiding member  110  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  111  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  110  includes a solid or hollow extension portion  113  extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  111  is formed on a surface of the extension portion  113  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  111  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. On the other hand, the second guiding surface  112  is formed on a surface of the extension portion  113  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  112  on the downstream side in the steam flow direction A 1  is inclined to the upstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     In the rotating machine according to the fifth embodiment, the guiding member  110  includes the second guiding surface  112  on the surface on the upstream side in the rotational direction C 1  of the rotor  12 , and the end portion of the second guiding surface  112  on the downstream side in the steam flow direction A 1  is inclined to the upstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided smoothly to the second guiding surface  112  and thus, the separation vortex in the swirling flow generation chamber  31  is reduced and the occurrence of pressure loss can be suppressed. 
     Sixth Embodiment 
       FIG.  11    is a cross-sectional view of a main part for describing the flow of the steam in a steam turbine as a rotating machine according to a sixth embodiment,  FIG.  12    is a cross-sectional view taken along XII-XII in  FIG.  11    for describing the shape of the guiding member,  FIG.  13    is a cross-sectional view taken along XIII-XIII in  FIG.  12   , illustrating the flow of the leakage steam with respect to the guiding member, and  FIG.  14    is a cross-sectional view taken along XIV-XIV in  FIG.  12   , illustrating the flow of the leakage steam with respect to the guiding member. Note that the basic structure of the sixth embodiment is similar to that of the aforementioned first embodiment, and is described using  FIG.  1   . The member with the function similar to that in the aforementioned first embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the sixth embodiment, as illustrated in  FIG.  11    to  FIG.  14   , the steam turbine  10  includes the casing  11 , the rotor  12 , the stator blades  13 , the rotor blades  14 , the sealing devices  15 , the swirling flow generation chamber  31 , and a plurality of guiding members  120 . The guiding members  120  are provided in the swirling flow generation chamber  31  at predetermined intervals in the circumferential direction C of the rotor  12 . In addition, the guiding member  120  includes a first guiding surface  121  and a second guiding surface  122  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . 
     The guiding member  120  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  121  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  120  includes an extension portion  123  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  121  is formed on a surface of the extension portion  123  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  121  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. 
     On the other hand, the second guiding surface  122  is formed on a surface of the extension portion  123  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  122  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     In the sealing device  15 , there is a gap secured between the seal fin  44  and the shroud  41  on the most downstream side of the leakage steam S 2 , and the leakage steam S 2  flows into the swirling flow generation chamber  31  through the gap between the seal fin  44  and the shroud  41 . The inclination angle θ 1  between the first guiding surface  121  and the axial direction A of the rotor  12  is the largest at the position facing this gap on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     That is to say, the inclination angle θ 1  of the first guiding surface  121  is the largest at the position facing the gap of the sealing device  15  in the axial direction A. On the other hand, the inclination angle θ 1  of the first guiding surface  121  is the smallest on the outside and inside in the radial direction R of the rotor  12 , that is, at the connection position to the inner circumferential surface  46  and the connection position to the second wall surface  48 , which is 01=0°. The inclination angle θ 1  continuously changes because the position of the first guiding surface  121  facing the gap of the sealing device  15  in the axial direction A, the connection position to the inner circumferential surface  46 , and the connection position to the second wall surface  48  continue with the curved surface twisted in the three-dimensional direction. In this case, the guiding member  120  (first guiding surface  121 ) is parallel to the radial direction R of the rotor  12  at the position where the guiding member  120  is fixed to the first wall surface  47 , and has such a shape that the inclination angle θ 1  is different in the radial direction R from the position of being fixed to the first wall surface  47  to the front end. 
     In addition, the extension portion  123  as the guiding member  120  has the same thickness in the axial direction A and the radial direction R of the rotor  12 . Therefore, in a manner similar to the first guiding surface  121 , the inclination angle θ 2  between the second guiding surface  122  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     The leakage steam S 2  leaking from the sealing device  15  becomes the swirling flow steam S 3  with the center axis along the circumferential direction C in the swirling flow generation chamber  31 . That is to say, the leakage steam S 2  collides with the first guiding surface  121  and the second guiding surface  122  of the guiding member  120 . Then, since the first guiding surface  121  and the second guiding surface  122  are inclined in the circumferential direction as illustrated in  FIG.  11    and  FIG.  13   , the leakage steam S 2  is guided smoothly to the first guiding surface  121  and the second guiding surface  122 . Since the leakage steam S 2  is guided to the first guiding surface  121  and the second guiding surface  122 , the velocity component in the circumferential direction C is reduced and after that, since the leakage steam S 2  is guided to the first wall surface  47 , the leakage steam S 2  becomes the swirling flow steam S 3  that swirls in the swirling flow generation chamber  31  on the inner circumferential surface  46  side. 
     That is to say, the leakage steam S 2  leaking from the gap of the sealing device  15  is guided to the first guiding surface  121  and the second guiding surface  122  that are inclined in the circumferential direction, so that the velocity component in the circumferential direction C is reduced. The leakage steam S 2  whose velocity component in the circumferential direction C is divided by the swirling flow generation chamber  31  into swirling flow steam S 31  that swirls to the outside in the radial direction R of the rotor  12  and swirling flow steam S 32  that swirls to the inside in the radial direction R of the rotor  12 . The swirling flow steam S 31  that swirls to the outside swirls in the swirling flow generation chamber  31  and partially joins the swirling flow steam S 32  that swirls on the inside. As illustrated in  FIG.  11    and  FIG.  14   , the swirling flow steam S 31  that swirls to the outside and the swirling flow steam S 32  that swirls to the inside hardly have the velocity component in the circumferential direction C, and are guided to the first guiding surface  121  and the second guiding surface  122  that are not inclined in the circumferential direction, so that the swirling flow steam S 31  is discharged first as appropriate. The swirling flow steam S 31  is discharged first and joins to form the swirling flow steam S 3 . While the swirling flow steam S 3  is guided to the end portion of the shroud  41 , the swirling flow steam S 3  smoothly joins the mainstream steam S 1  having passed through the rotor blade  14  as the leakage steam S 4 . 
     Note that the shape of the guiding member  120  is not limited to the aforementioned shape.  FIG.  15    is a cross-sectional view for describing the shape of a guiding member expressing a modification of the sixth embodiment. 
     In the modification of the sixth embodiment, as illustrated in  FIG.  11    and  FIG.  15   , a guiding member  130  includes a first guiding surface  131  and a second guiding surface  132  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  130  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The guiding member  130  includes an extension portion  133  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  131  is formed on a surface of the extension portion  133  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  131  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. On the other hand, the second guiding surface  132  is formed on a surface of the extension portion  133  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  132  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     The inclination angle θ 1  between the first guiding surface  131  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . The inclination angle θ 1  of the first guiding surface  131  is the largest at the position facing the gap of the sealing device  15  in the axial direction. On the other hand, the inclination angle θ 1  of the first guiding surface  131  is the smallest on the outside and inside in the radial direction R of the rotor  12 , that is, at the connection position to the inner circumferential surface  46  and the connection position to the second wall surface  48 . The inclination angle θ 1  continuously changes because the first guiding surface  131  continues with the curved surface twisted in the three-dimensional direction among the position facing the gap of the sealing device  15  in the axial direction, the connection position to the inner circumferential surface  46 , and the connection position to the second wall surface  48 . In this case, the guiding member  130  (first guiding surface  131 ) is parallel to the radial direction R of the rotor  12  at the position where the guiding member  130  is fixed to the first wall surface  47 , and has such a shape that the inclination angle θ 1  is different in the radial direction R from the position of being fixed to the first wall surface  47  to the front end. 
     The extension portion  133  as the guiding member  130  has the same thickness in the axial direction A and the radial direction R of the rotor  12 . In a manner similar to the first guiding surface  131 , the inclination angle θ 2  between the second guiding surface  132  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     In the rotating machine according to the sixth embodiment, the gap is formed between the seal fin  44  and the shroud  41  in the sealing device  15 . The inclination angle θ 1  between the first guiding surfaces  121  and  131  and the axial direction A of the rotor  12  is the largest at the position facing the gap on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided to the position where the inclination angle θ 1  is the largest on the first guiding surfaces  121  and  131 , and after that, is guided to the position where the inclination angle θ 2  is the smallest; accordingly, the leakage steam S 2  whose velocity component in the circumferential direction C is reduced in the swirling flow generation chamber  31  can join as appropriate the mainstream steam S 1  by the first guiding surfaces  121  and  131 . 
     Seventh Embodiment 
       FIG.  16    is a cross-sectional view for describing the shape of a guiding member according to a seventh embodiment. Note that the basic structure of the seventh embodiment is similar to that of the aforementioned sixth embodiment, and is described using  FIG.  11   . The member with the function similar to that in the aforementioned sixth embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the seventh embodiment, as illustrated in  FIG.  11    and  FIG.  16   , a guiding member  140  includes a first guiding surface  141  and a second guiding surface  142  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  140  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  141  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  140  includes an extension portion  143  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  141  is formed on a surface of the extension portion  143  on the downstream side in the rotational direction C 1 . On the other hand, the second guiding surface  142  is formed on a surface of the extension portion  143  on the upstream side in the rotational direction C 1 . 
     The inclination angle θ 1  between the first guiding surface  141  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . The inclination angle θ 1  continuously changes because the first guiding surface  121  continues with the curved surface twisted in the three-dimensional direction among the position facing the gap of the sealing device  15  in the axial direction A, the connection position to the inner circumferential surface  46 , and the connection position to the second wall surface  48 . In this case, the guiding member  140  (first guiding surface  141 ) is parallel to the radial direction R of the rotor  12  at the position where the guiding member  140  is fixed to the first wall surface  47 , and has such a shape that the inclination angle θ 1  is different in the radial direction R from the position of being fixed to the first wall surface  47  to the front end. 
     The extension portion  143  as the guiding member  140  has the same thickness in the axial direction A and the radial direction R of the rotor  12 . In a manner similar to the first guiding surface  141 , the inclination angle θ 2  between the second guiding surface  142  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     Note that the shape of the guiding member  140  is not limited to the aforementioned shape.  FIG.  17    is a cross-sectional view for describing the shape of a guiding member according to a modification of the seventh embodiment. 
     In the modification of the seventh embodiment, as illustrated in  FIG.  11    and  FIG.  17   , a guiding member  150  includes a first guiding surface  151  and a second guiding surface  152  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  150  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The guiding member  150  includes an extension portion  153  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  151  is formed on a surface of the extension portion  153  on the downstream side in the rotational direction C 1 . On the other hand, the second guiding surface  152  is formed on a surface of the extension portion  153  on the upstream side in the rotational direction C 1 . 
     The inclination angle θ 1  between the first guiding surface  151  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . The inclination angle θ 1  continuously changes because the second guiding surface  152  continues with the curved surface twisted in the three-dimensional direction among the position facing the gap of the sealing device  15  in the axial direction, the connection position to the inner circumferential surface  46 , and the connection position to the second wall surface  48 . In this case, the guiding member  150  (first guiding surface  151 ) is parallel to the radial direction R of the rotor  12  at the front end position, and has such a shape that the inclination angle θ 1  is different in the radial direction R from the front end to the position of being fixed to the first wall surface  47 . 
     The extension portion  153  as the guiding member  150  has the same thickness in the axial direction A and the radial direction R of the rotor  12 . In a manner similar to the first guiding surface  151 , the inclination angle θ 2  between the second guiding surface  152  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     In the rotating machine according to the seventh embodiment, the gap is formed between the seal fin  44  and the shroud  41  in the sealing device  15 . The inclination angle θ 1  between the first guiding surfaces  141  and  151  and the axial direction A of the rotor  12  is the largest at the position facing the gap on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     Therefore, the leakage steam S 2  with the velocity component in the circumferential direction C is guided to the position where the inclination angle θ 1  is the largest on the first guiding surfaces  141  and  151 , and after that, is guided to the position where the inclination angle θ 2  is the smallest; accordingly, the leakage steam S 2  whose velocity component in the circumferential direction C is reduced in the swirling flow generation chamber  31  can join as appropriate with the mainstream steam S 1  by the first guiding surfaces  141  and  151 . 
     Eighth Embodiment 
       FIG.  18    is a cross-sectional view for describing the shape of a guiding member according to an eight embodiment,  FIG.  19    is a cross-sectional view taken along XIX-XIX in  FIG.  18   , illustrating the flow of the leakage steam with respect to the guiding member, and  FIG.  20    is a cross-sectional view taken along XX-XX in  FIG.  18   , illustrating the flow of the leakage steam with respect to the guiding member. Note that the basic structure of the eighth embodiment is similar to that of the aforementioned sixth embodiment, and is described using  FIG.  11   . The member with the function similar to that in the aforementioned sixth embodiment is denoted by the same reference symbol and the detailed description is omitted. 
     In the eighth embodiment, as illustrated in  FIG.  11    and  FIG.  18    to  FIG.  20   , a guiding member  160  includes a first guiding surface  161  and a second guiding surface  162  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  160  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  161  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  160  includes an extension portion  163  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  161  is formed on a surface of the extension portion  163  on the downstream side in the rotational direction C 1 . An end portion of the first guiding surface  161  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  with respect to the axial direction A. 
     On the other hand, the second guiding surface  162  is formed on a surface of the extension portion  163  on the upstream side in the rotational direction C 1 . An end portion of the second guiding surface  162  on the downstream side in the steam flow direction A 1  is inclined to the downstream side in the rotational direction C 1  of the rotor  12  with respect to the axial direction A of the rotor  12 . 
     The inclination angle θ 1  between the first guiding surface  161  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     That is to say, the inclination angle θ 1  of the first guiding surface  161  is the largest at the position facing the gap of the sealing device  15  in the axial direction. On the other hand, the inclination angle θ 1  of the first guiding surface  161  is the smallest on the outside and inside in the radial direction R of the rotor  12 , that is, at the connection position to the inner circumferential surface  46  and the connection position to the second wall surface  48 , which is θ 1 =0°. The inclination angle θ 1  continuously changes because the first guiding surface  161  continues with the curved surface twisted in the three-dimensional direction among the position facing the gap of the sealing device  15  in the axial direction A, the connection position to the inner circumferential surface  46 , and the connection position to the second wall surface  48 . In this case, the guiding member  160  (first guiding surface  161 ) is parallel to the radial direction R of the rotor  12  at the position where the guiding member  160  is fixed to the first wall surface  47 , and has such a shape that the inclination angle θ 1  is different in the radial direction R from the position of being fixed to the first wall surface  47  to the front end. 
     In addition, in a manner similar to the first guiding surface  161 , the inclination angle θ 2  between the second guiding surface  162  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     The thickness of the guiding member  160  in the circumferential direction C of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the thickness of the guiding member  160  in the circumferential direction C of the rotor  12  becomes smaller to the outside and the inside in the radial direction R of the rotor  12 . Therefore, the length of the interval between the guiding members  160  that are adjacent in the circumferential direction C of the rotor  12  is the smallest at the position facing the gap on the downstream side in the steam flow direction A 1  and becomes larger to the outside and the inside in the radial direction R of the rotor  12 . That is to say, the length L 1  of the interval between the guiding members  160  that are adjacent at the position facing the gap of the sealing device  15  is smaller than the length L 2  of the interval between the guiding members  160  that are adjacent at the connection position to the inner circumferential surface  46  and the connection position to the second wall surface  48 . In other words, L 1 &lt;L 2  is satisfied. 
     The leakage steam S 2  leaking from the sealing device  15  becomes the swirling flow steam S 3  with the center axis along the circumferential direction C in the swirling flow generation chamber  31 . That is to say, the leakage steam S 2  collides with the first guiding surface  161  and the second guiding surface  162  of the guiding member  160 . Then, since the first guiding surface  161  and the second guiding surface  162  are inclined in the circumferential direction at the intermediate portion in the radial direction R as illustrated in  FIG.  18    and  FIG.  19   , the leakage steam S 2  is guided smoothly to the first guiding surface  161  and the second guiding surface  162  and becomes the swirling flow steam S 3  whose velocity component in the circumferential direction C is reduced. Here, since neither the first guiding surface  161  nor the second guiding surface  162  is inclined in the circumferential direction on the outside and the inside in the radial direction R as illustrated in  FIG.  18    and  FIG.  20   , the swirling flow steam S 3  discharged from the swirling flow generation chamber  31  becomes the leakage steam S 4  that hardly has the velocity component in the circumferential direction C and smoothly joins the mainstream steam S 1 . 
     Incidentally, the leakage steam S 2  leaking from the gap of the sealing device  15  changes in velocity in accordance with the shape of the sealing device  15 . On the other hand, the mainstream steam S 1  maintains the velocity constant regardless of the shape of the sealing device  15 . The velocity of the leakage steam S 2  varies depending on the number and the shape of the seal fins  43 ,  44 , and  45 , the gap size between the seal fins  43  and  44  and the shroud  41 , the gap size between the seal fin  45  and the recessed portion  42 , and the like. When the gap size is small, the velocity of the leakage steam S 2  becomes fast and when the gap size is large, the velocity of the leakage steam S 2  becomes slow. In the present embodiment, the length of the interval between the guiding members  160  that are adjacent in the circumferential direction C of the rotor  12  is the largest on the outside and the inside in the radial direction R of the rotor  12 ; therefore, when the leakage steam S 2  is discharged from the swirling flow generation chamber  31 , the flow path, that is, the interval between the guiding members  160  that are adjacent becomes large and the velocity of the leakage steam S 2  decreases to become close to the velocity of the mainstream steam S 1 . Therefore, the leakage steam S 4  smoothly joins the mainstream steam S 1 . 
     Note that the shape of the guiding member  160  is not limited to the aforementioned shape.  FIG.  21    is a cross-sectional view for describing the shape of a guiding member according to a first modification of the eighth embodiment,  FIG.  22    is a cross-sectional view taken along XXII-XXII in  FIG.  21   , illustrating the flow of the leakage steam with respect to the guiding member, and  FIG.  23    is a cross-sectional view taken along XXIII-XXIII in  FIG.  21   , illustrating the flow of the leakage steam with respect to the guiding member.  FIG.  24    and  FIG.  25    are cross-sectional views illustrating a guiding member according to a second modification of the eighth embodiment. Note that  FIG.  24    and  FIG.  25    correspond to  FIG.  22    and  FIG.  23   , respectively. 
     In the first modification of the eighth embodiment, as illustrated in  FIG.  21    to  FIG.  23   , a guiding member  170  includes a first guiding surface  171  and a second guiding surface  172  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The guiding member  170  is fixed to the inner circumferential surface  46 , the first wall surface  47 , and the second wall surface  48 . The first guiding surface  171  is provided along the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The guiding member  170  includes an extension portion  173  with a plate shape extending from the first wall surface  47  of the swirling flow generation chamber  31  to the upstream side in the steam flow direction A 1 . The first guiding surface  171  is formed on a surface of the extension portion  173  on the downstream side in the rotational direction C 1 . The second guiding surface  172  is formed on a surface of the extension portion  173  on the upstream side in the rotational direction C 1 . 
     The inclination angle θ 1  between the first guiding surface  171  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . In a manner similar to the first guiding surface  171 , the inclination angle θ 2  between the second guiding surface  172  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 2  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     The thickness of the guiding member  170  in the circumferential direction C of the rotor  12  is the smallest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the thickness of the guiding member  170  in the circumferential direction C of the rotor  12  becomes larger to the outside and the inside in the radial direction R of the rotor  12 . Therefore, the length of the interval between the guiding members  160  that are adjacent in the circumferential direction C of the rotor  12  is the largest at the position facing the gap on the downstream side in the steam flow direction A 1  and becomes smaller to the outside and the inside in the radial direction R of the rotor  12 . That is to say, the length L 1  of the interval between the guiding members  160  that are adjacent at the position facing the gap of the sealing device  15  is larger than the length L 2  of the interval between the guiding members  160  that are adjacent at the connection position to the inner circumferential surface  46  and the connection position to the second wall surface  48 . In other words, L 1 &gt;L 2  is satisfied. 
     In the case of this modification, the length of the interval between the guiding members  160  that are adjacent in the circumferential direction C of the rotor  12  is the smallest on the outside and the inside in the radial direction R of the rotor  12 ; therefore, when the leakage steam S 2  is discharged from the swirling flow generation chamber  31 , the flow path, that is, the interval between the guiding members  160  that are adjacent becomes small and the velocity of the leakage steam S 2  increases to become close to the velocity of the mainstream steam S 1 . Therefore, the leakage steam S 4  smoothly joins the mainstream steam S 1 . 
     In the second modification of the eighth embodiment, as illustrated in  FIG.  24    to  FIG.  25   , the guiding member  160  includes a first guiding surface  161  and a second guiding surface  162  that are inclined in the circumferential direction C with respect to the axial direction A of the rotor  12 . The first guiding member  161  is provided in the swirling direction of the leakage steam S 2  leaking from the sealing device  16 . The first guiding surface  161  is formed on a surface of the extension portion  163  on the downstream side in the rotational direction C 1 . The second guiding surface  162  is formed on a surface of the extension portion  163  on the upstream side in the rotational direction C 1 . The inclination angle θ 1  between the first guiding surface  161  and the axial direction A of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1 , and the inclination angle θ 1  becomes smaller to the outside and inside in the radial direction R of the rotor  12 . 
     An end portion of the extension portion  163  on the upstream side in the steam flow direction A 1  has a curved shape. That is to say, a curved portion  164  is provided at a tip of the extension portion  163  where the first guiding surface  91  and the second guiding surface  92  intersect. Note that an end portion of the extension portion  173  according to the first modification on the upstream side in the steam flow direction A 1  may have a curved shape. 
     In the rotating machine according to the eighth embodiment, the length of the interval between the guiding members  160  and  170  that are adjacent in the circumferential direction C of the rotor  12  is the smallest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1  and is larger to the outside and the inside in the radial direction R of the rotor  12 . In addition, the length of the interval between the guiding members  160  and  170  that are adjacent in the circumferential direction C of the rotor  12  is the largest at the position facing the gap of the sealing device  15  on the downstream side in the steam flow direction A 1  and is smaller to the outside and the inside in the radial direction R of the rotor  12 . 
     Therefore, when the leakage steam S 2  with the velocity component in the circumferential direction C is guided to the guiding members  160  and  170 , the velocity component in the circumferential direction C is reduced. After that, when the swirling flow steam S 3  is discharged from the swirling flow generation chamber  31 , the steam passes through the outside and inside in the radial direction of the guiding members  160  and  170 , so that the velocity is adjusted to become the proper velocity by decreasing or increasing. Accordingly, the velocity of the leakage steam S 4  is adjusted in accordance with the velocity of the mainstream steam S 1 , and the leakage steam S 4  can smoothly join the mainstream steam S 1 . 
     In the rotating machine according to the eighth embodiment, the end portion of the extension portion  163  on the upstream side in the steam flow direction A 1  has a curved shape. Therefore, when the leakage steam S 2  with the velocity component in the circumferential direction C collides with the extension portion  163 , the leakage steam S 2  is smoothly guided to the first guiding surface  161  and the second guiding surface  162  by the curved portion  164 . Thus, the separation here can be suppressed. By smoothly guiding the leakage steam S 2  to the first guiding surface  161 , the velocity component in the circumferential direction C can be reduced. 
     In the aforementioned embodiments, the guiding member is provided in the entire region of the swirling flow generation chamber in the radial direction of the rotor; however, it is only necessary that the guiding member is positioned at least facing the gap of the sealing device in the axial direction and the outside or the inside in the radial direction at this position may be eliminated. That is to say, the guiding member may be fixed only to the first wall portion. 
     In the aforementioned embodiments, the sealing device is the labyrinth seal; however, another noncontact seal may be employed. 
     In the aforementioned embodiments, the rotating machine according to the present invention is used for the steam turbine  10 ; however, the rotating machine can be used not just for the steam turbine but also for other rotating machines in which the internal pressure becomes higher than the external pressure in the operation, such as a compressor or an exhaust turbine. 
     REFERENCE SIGNS LIST 
     
         
         
           
               10  steam turbine (rotating machine) 
               11  casing 
               11   a  inner circumferential surface 
               12  rotor 
               13  stator blade 
               14  rotor blade 
               15  sealing device 
               20  bearing 
               21  rotor disc 
               22  steam inlet 
               23  steam passage 
               24  blade cascade part 
               25  exhaust hood 
               26  steam discharge port 
               31  swirling flow generation chamber 
               32 ,  60 ,  70 ,  80 ,  90 ,  110 ,  120 ,  130 ,  140 ,  150 ,  160 ,  170  guiding member 
               33 ,  61 ,  71 ,  81 ,  91 ,  101 ,  111 ,  121 ,  131 ,  141 ,  151 ,  161 ,  171  first guiding surface 
               41  shroud 
               42  recessed portion 
               43 ,  44 ,  45  seal fin 
               46  inner circumferential surface 
               47  first wall surface 
               48  second wall surface 
               49  protrusion 
               51 ,  63 ,  73 ,  83 ,  93 ,  103 ,  113 ,  123 ,  133 ,  143 ,  153 ,  163 ,  173  extension portion 
               52 ,  62 ,  72 ,  82 ,  92 ,  102 ,  112 ,  122 ,  132 ,  142 ,  152 ,  162 ,  172  second guiding surface 
               94 ,  104 ,  164  curved portion 
             θ 1 , θ 2  inclination angle 
             A axial direction 
             A 1  steam flow direction 
             C circumferential direction 
             C 1  rotational direction 
             L 1 , L 2  length 
             R radial direction 
             S steam 
             S 1  mainstream steam 
             S 2  leakage steam 
             S 3  swirling flow steam 
             S 4  leakage steam