JP2005264729A - Sound insulating structure and turbine equipped with the sound insulating structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a sound insulating structure in which fluid noise generated by pressure fluctuations of a fluid can be insulated in a simple configuration. <P>SOLUTION: An acoustic liner 31 comprises an outer peripheral wall 32 of a steam inlet pipe 30 and an annular covered part 33 for covering the outer peripheral wall 32. The outer peripheral wall 32 covered by the annular covered part 33 has a porous structure including a plurality of through holes 34 and a dimple structure containing ruggedness on the surface. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

  The present invention relates to a sound insulation structure for reducing fluid noise caused by fluid pressure fluctuations caused by turbulence or separation caused by changes in fluid flow velocity and the like, and a turbine equipped with the sound insulation structure.

  In the steam turbine, the steam flow is disturbed or separated due to the structure in the vicinity of the steam inlet to which steam (fluid) is supplied from the outside or the steam supply pipe for supplying steam. That is, in the vicinity of the steam inlet portion, sheet metal is applied and the steam supply pipe etc. are connected so that the gradient is not smooth, and the steam supply pipe has a bent portion in its structure. The flow velocity changes in the part, and a separation flow and a vortex flow are generated. This turbulence and separation of the steam flow cause pressure fluctuations inside the steam turbine, and this pressure fluctuation propagates to the steam turbine cabin, so that sound is emitted outside from the cabin wall and fluid noise is generated. Occur.

As a steam turbine piping device for preventing fluid noise generated by the propagation of such pressure fluctuation, a pressure fluctuation propagation preventing pipe having a higher-order acoustic mode different from that of the steam turbine piping is provided downstream of the flow control valve. An arranged steam turbine piping device is disclosed (see Patent Document 1). In this steam turbine piping device, the inner diameter of the pressure fluctuation propagation preventing pipe is different from the inner diameter of the pipe, and the axial length of the pressure fluctuation propagation preventing pipe is longer than the axial wavelength of the coupled vibration with the pipe wall. By setting the length, it is possible to suppress vibrations in the pipe wall coupled to the pressure vibration.
JP-A-7-332576

  However, merely installing the pressure fluctuation propagation prevention pipe in the steam turbine pipe does not contribute to the reduction of fluid noise generated due to the structure near the steam inlet portion. Therefore, it is necessary to take measures for reducing fluid noise caused by the structure near the steam inlet including the steam supply pipe. In addition, it is conceivable that the entire apparatus is sound-insulated by covering it with a soundproofing material, but if the object is large, the structure becomes large and inefficient.

  In view of such a problem, an object of the present invention is to provide a sound insulation structure including a structure capable of insulating a fluid noise due to a fluid pressure fluctuation with a simple configuration. It is another object of the present invention to provide a turbine capable of insulating noise caused by an inlet structure to which a fluid is supplied with simple equipment.

  In order to achieve the above object, the sound insulation structure of the present invention is a sound insulation structure constituted by a housing through which a fluid flows, and partially covers the outer peripheral surface of the housing in the circumferential direction, and the surface thereof has an uneven shape. And a plurality of through holes that are formed in the wall of the housing covered with the covering portion and penetrate from the inside of the housing to the space between the covering portion and the wall of the housing. It is characterized by.

  Further, the turbine of the present invention includes a rotor that rotates when a supplied fluid collides with a moving blade, a rotor that supports the rotor as a center, and includes a stationary blade between the moving blades in the axial direction of the rotor. A turbine comprising a vehicle compartment, wherein the above-described sound insulation structure is provided at a fluid inlet of the vehicle compartment to which the fluid is supplied.

  Further, the turbine of the present invention includes a rotor that rotates when a supplied fluid collides with a moving blade, a rotor that supports the rotor as a center, and includes a stationary blade between the moving blades in the axial direction of the rotor. A turbine comprising a vehicle compartment, wherein the above-described sound insulation structure is provided in a fluid supply pipe that supplies the fluid to the vehicle compartment.

  Further, the sound insulation structure of the present invention is a sound insulation structure constituted by a pipe through which a fluid flows, wherein the pipe serves as a first flow path that is a main flow path of the fluid and a second flow of the fluid. A first pipe that joins the first flow path and the second flow path and joins the second flow path to the first flow path; At a branch point with the second pipe, a perforated plate having a plurality of through holes covering a connection portion of the second pipe in the first pipe is installed.

  In such a sound insulation structure, the first tube includes a bent portion, and the branch point between the first tube and the second tube is more in the fluid flow direction than the bent portion in the vicinity of the bent portion. It may be installed on the same surface as the inner side of the inner peripheral surface of the bent portion of the first pipe on the downstream side. In addition, the inner peripheral surface of the first tube and the surface of the porous plate constitute the same curved surface, and the curved surface formed by the inner peripheral surface of the first tube and the surface of the porous plate includes the fluid. The flow resistance may be reduced in shape.

  Further, the sound insulation structure of the present invention is a sound insulation structure constituted by a pipe through which a fluid flows, wherein the pipe is a first flow path that is a main flow path of the fluid. A second pipe serving as two flow paths is inserted and connected, and a pipe wall on the downstream side in the fluid flow direction in the portion of the second pipe inserted into the first pipe is inserted into the second pipe from the inside of the second pipe. By providing a plurality of through holes penetrating to the inside of the first pipe, the first flow path and the second flow path are merged.

  Further, the turbine of the present invention includes a rotor that rotates when a supplied fluid collides with a moving blade, a rotor that supports the rotor as a center, and includes a stationary blade between the moving blades in the axial direction of the rotor. In a turbine including a vehicle compartment and a fluid supply pipe that supplies fluid from a plurality of flow paths to the vehicle compartment, in each of the portions where the plurality of flow paths of the fluid supply pipe meet, A sound insulation structure is provided.

  Further, the turbine of the present invention includes a rotor that rotates when a supplied fluid collides with a moving blade, a rotor that supports the rotor as a center, and includes a stationary blade between the moving blades in the axial direction of the rotor. A turbine comprising: a vehicle compartment; and a plurality of support rods installed in a circumferential direction of the rotor at an inlet portion to which the fluid in the vehicle compartment is supplied. It is characterized by having a shape in which the flow resistance is small.

  In such a turbine, the angle formed by the flow direction of the fluid on the upstream side and the slope formed by the outer peripheral surface of the support rod is increased, and the flow direction of the fluid on the downstream side and the slope formed by the outer peripheral surface of the support rod are It is also possible to reduce the angle formed by the above-mentioned, and the outer peripheral surface of the support rod may be uneven.

  According to the present invention, a through-hole is provided in a pipe wall of a portion that reduces noise, and a covering portion that covers the pipe wall provided with the through-hole is installed to absorb vibration caused by fluid pressure fluctuation. , Fluid noise can be reduced. Further, by making the surface of the covering portion uneven, it is possible to further suppress the propagation of noise to the outside and to improve the strength of the covering portion against external force. By installing the sound insulation structure having such a configuration at the fluid inlet portion of the turbine, it is possible to prevent noise caused by pressure fluctuation caused by the shape of the fluid inlet portion. In addition, by installing a sound insulation structure with such a configuration in the fluid supply pipe of the turbine, noise caused by pressure fluctuations caused by the shape of the fluid supply pipe or the confluence of fluid from another branched supply pipe can be reduced. Can be prevented.

  In addition, by providing a perforated plate at the confluence of different flow paths, the flow of fluid in another flow path to be merged is dispersed. Further, by being installed downstream of the bent portion of the tube, fluid separation can be compensated. Therefore, pressure fluctuation in the pipe can be suppressed, and generation of noise can be prevented. Furthermore, by making the curved surface formed by the inner peripheral surface of the bent portion and the surface of the perforated plate into a shape that reduces the flow resistance with respect to the fluid, fluid separation at the bent portion can be suppressed. Therefore, pressure fluctuation in the pipe can be suppressed, and generation of noise can be prevented. Further, by providing the turbine with the fluid supply pipe having such a configuration, it is possible to prevent noise caused by pressure fluctuations caused by the shape of the fluid supply pipe or the confluence of fluid from another branched supply pipe. it can. Furthermore, the disturbance of the flow of the fluid generated by the support rod can be suppressed by making the shape of the support rod installed in the turbine casing of the turbine into a shape that reduces the flow resistance with the fluid. Therefore, the pressure fluctuation around the support rod can be suppressed, and the generation of noise can be prevented.

<First Embodiment>
A first embodiment of the present invention will be described with reference to the drawings. FIG. 1 is a schematic sectional view in the axial direction showing the configuration of the steam turbine in the present embodiment, and FIG. 2 is a schematic sectional view in the same direction as the circumferential section of the rotor showing the configuration of the steam turbine in the present embodiment. It is.

  The steam turbine of FIG. 1 includes a steam supply pipe (crossover pipe) 10 that supplies steam to the steam turbine, an outer casing 20 that is connected to the steam supply pipe 10 and covers the entire steam turbine, and a chamber wall of the outer casing 20. The inner wall includes a steam inlet pipe 30 connected to the steam supply pipe 10 and a stationary blade 41 connected to the steam inlet pipe 30 and the turbine inlet chamber 60 and rectifying the steam supplied from the steam inlet pipe 30 on the inner wall. A casing 40 and a rotor 70 that is inserted into the center position of the inner casing 40 and supported by the inner casing 40 and includes a rotor blade 71 that receives steam rectified by the stationary blade 41 are provided.

  A turbine inlet chamber 60 is provided in an annular shape in the central portion of the inner casing 40 and is connected to the steam inlet pipe 30 on the upper side, and a plurality of stages of stationary blades 41 and the center of the turbine inlet chamber 60 are provided. The moving blades 71 are installed so as to be symmetrical in the axial direction of the rotor 70. A plurality of stationary blades 41 and moving blades 71 at each stage are installed in the circumferential direction on the inner wall of the inner casing 40 and the peripheral surface of the rotor 70, respectively. Further, the steam inlet pipe 30 connected to the steam supply pipe 10 is inserted into the inner casing 40 and also connected to the turbine inlet chamber 60. The insertion position into the inner casing 40 and the connection to the turbine inlet chamber 60 are also included. A support bar (stay bar) 50 for supporting the steam inlet pipe 30 and the inner casing 40 is installed at the position. Further, as shown in FIG. 2, the support rod 50 is installed at a plurality of circumferential positions having the same diameter around the rotor 70 and in the vicinity of a connection position between the steam inlet pipe 30 and the inner casing 40.

  Further, as shown in FIG. 1, the stationary blade 41 and the moving blade 71 are arranged along the axial direction of the rotor 70 in order from the first-stage stationary blade 41 so as to be symmetrical about the turbine inlet chamber 60. Alternatingly arranged. Further, as shown in FIG. 1 and FIG. 2, the sound that reduces the fluid noise transmitted to the outer peripheral wall of the steam inlet pipe 30 by reducing the pressure fluctuation generated in the inner casing 40 including the steam inlet pipe 30. A liner 31 is installed. The acoustic liner 31 is installed so as to cover a part or the whole of the steam inlet pipe 30 with respect to the flow direction of the steam in the steam inlet pipe 30 and covers the entire outer peripheral surface of the steam inlet pipe 30 at the installation position. Installed.

  The steam turbine configured as above is supplied to the inner casing 40 including the steam inlet pipe 30 by supplying the steam supplied from the outside through the steam supply pipe 10 to the steam inlet pipe 30 inside the outer casing 20. Is done. When steam is supplied to the turbine inlet chamber 60 located immediately below the steam inlet pipe 30, the supplied steam branches and flows along the circumferential direction of the rotor 70 in the turbine inlet chamber 60 as shown in FIG. 2. Is spread. At this time, as shown in FIG. 1, the steam flowing into the turbine inlet chamber 60 also diffuses in the direction along the axial direction of the rotor 70. That is, the inflowing steam diffuses symmetrically about the turbine inlet chamber 60 in FIG. The steam diffused in this manner is rectified by the stationary blade 41 and collides with the moving blade 71, whereby the rotor 70 rotates and is rotationally driven as a steam turbine.

  The acoustic liner 31 installed as a sound insulation structure in this steam turbine will be described below with reference to FIG. FIG. 3 is a cross-sectional perspective view for explaining the structure of the acoustic liner 31. The acoustic liner 31 includes an outer peripheral wall portion 32 of the steam inlet pipe 30 and an annular covering portion 33 that covers the outer peripheral wall portion 32. The outer peripheral wall portion 32 covered with the covering portion 33 has a porous structure in which a plurality of through holes 34 are provided, and the covering portion 33 has a dimple structure having irregularities on the surface.

  When the acoustic liner 31 is configured in this way, in the viscoelastic model damping system as shown in FIG. 4, the thickness d of the air layer in which the spring K representing elasticity is constituted by the outer peripheral wall portion 32 and the covering portion 33. The object M representing the mass corresponds to the mass of the vapor (fluid) passing through the through hole 34, and the dash port C representing the viscosity corresponds to the resistance when the vapor (fluid) passes through the through hole 34. . As described above, since each part of the acoustic liner 31 corresponds to the damping system of FIG. 4, propagation of pressure fluctuations in the inner casing 40 including the steam inlet pipe 30 can be suppressed. Further, by forming the covering portion 33 located on the outer portion of the acoustic liner 31 with a dimple structure, the vibration propagated from the inner casing 40 including the steam inlet pipe 30 is canceled to prevent the propagation of the vibration to the outside. be able to.

  As described above, the space between the outer peripheral wall portion 32 and the covering portion 33 and the damping system structure constituted by the through hole 34 provided in the outer peripheral wall portion 32 and the dimple structure constituted on the surface of the covering portion 33, Since propagation of vibration caused by pressure fluctuation in the inner casing 40 including the steam inlet pipe 30 can be prevented, fluid noise generated due to the propagation of this vibration can be insulated. Furthermore, the intensity | strength with respect to the external force of the coating | coated part 33 can be improved by making the surface of the coating | coated part 33 into a dimple structure.

<Second Embodiment>
A second embodiment of the present invention will be described with reference to the drawings. FIG.5 and FIG.6 is the external view and sectional drawing which show the structure of the steam supply pipe | tube 10 provided in the steam turbine in this embodiment.

  The steam turbine of the present embodiment is used as a low pressure turbine T1, and as shown in FIG. 5, steam exhausted from a high pressure turbine T2 and an intermediate pressure turbine T3, which are other steam turbines, is supplied via a steam supply pipe 10. Is done. At this time, the steam supply pipe 10 includes a steam supply pipe 10a formed in a U shape from the high pressure turbine T2 toward the low pressure turbine T1, and a bent portion 11 on the high pressure turbine T2 side with respect to the steam supply pipe 10a. A branch point 12 is provided at a position closer to the high-pressure turbine T2 (upstream side from the bent portion 11). Further, the steam supply pipe 10 includes a steam supply pipe 10b formed from the intermediate pressure turbine T3 toward the branch point 12, so that the steam exhausted from the intermediate pressure turbine T3 at the branch point 12 is output from the high pressure turbine T2. Merges with the exhausted steam. Further, the steam turbine used as the low-pressure turbine T1 is configured as shown in FIGS. 1 and 2 as in the first embodiment.

  In the steam supply pipe 10, an acoustic liner 13 that covers the outer peripheral surface of the steam supply pipe 10 a is installed between the bent portion 11 and the branch point 12 in the steam supply pipe 10 a. This acoustic liner 13 is configured as shown in FIG. 3, similarly to the acoustic liner 31 installed in the steam turbine in the first embodiment. That is, as shown in the cross-sectional view of FIG. 6, a covering portion 15 (corresponding to the covering portion 33 of FIG. 3) covering the outer peripheral surface of the steam supply pipe 10 shown in FIG. The acoustic liner 13 is constituted by the tube wall portion 14 (peripheral wall portion 32 in FIG. 3) having a porous structure including a plurality of 16 (through holes 34 in FIG. 3).

  When comprised in this way, a pressure fluctuation generate | occur | produces because the steam from the intermediate pressure turbine T3 which flows through the steam supply pipe | tube 10b joins the steam from the high pressure turbine T2 which flows through the steam supply pipe | tube 10a at the branch point 12. FIG. At this time, the acoustic liner 13 is installed closer to the low-pressure turbine T1 than the branch point 12, so that the space between the tube wall portion 14 and the covering portion 15 and the size of the through hole 16 are attenuated. The dimple structure formed on the surface of the covering portion 15 can prevent propagation of vibration due to pressure fluctuation. Therefore, it is possible to prevent the fluid noise caused by the confluence of the steam from the steam supply pipe 10b at the branching point 12 from propagating to the outside and to insulate the sound.

<Third Embodiment>
A third embodiment of the present invention will be described with reference to the drawings. FIG. 7 is a cross-sectional view showing a configuration of the steam supply pipe 10 provided in the steam turbine in the present embodiment. In the present embodiment, parts used for the same purpose as those in the second embodiment (FIGS. 5 and 6) are denoted by the same reference numerals, and detailed description thereof is omitted.

  As in the second embodiment, the steam supply pipe 10 shown in FIG. 7 includes a U-shaped steam supply pipe 10a through which steam from the high-pressure turbine T2 flows, and a steam supply pipe 10b through which steam from the intermediate-pressure turbine T3 flows. . In the steam supply pipe 10, unlike the second embodiment, a branching point 12a between the steam supply pipe 10a and the steam supply pipe 10b is in the vicinity of the bent portion 11 on the high pressure turbine T2 side of the steam supply pipe 10a and the bent portion. 11 is installed at a portion located on the low-pressure turbine T1 side (downstream side from the bent portion 11). Further, at this branching point 12a, the steam supply pipe 10b is connected on the inner peripheral surface that continues to the inside of the bent portion 11 of the steam supply pipe 10a.

  And the perforated plate 100 provided with the through-hole 101 which covers the connection part with the steam supply pipe | tube 10b is installed in the inside of the branch point 12a of the steam supply pipe | tube 10a. The perforated plate 100 is shaped so that its surface forms a smooth surface with respect to the inner peripheral surface of the steam supply pipe 10a. Furthermore, an acoustic liner 13 that covers the outer peripheral surface of the steam supply pipe 10a is located at a position on the low-pressure turbine T1 side (downstream side from the branch point 12a) of the steam supply pipe 10a as in the second embodiment. Is installed.

  When configured in this manner, for example, in the case of the configuration as in the second embodiment, in the vicinity of the downstream side of the bent portion 11, steam is peeled off on the inner inner peripheral surface, and a vortex is caused, and pressure loss occurs. Increases, causing fluid noise. On the other hand, as in this embodiment, the position where the vortex is caused to rise by connecting the steam supply pipe 10b whose connecting portion is covered with the perforated plate 100 to the inner peripheral surface near the downstream side of the bent portion 11. Since steam can be poured into the vortex, generation of vortices can be suppressed and an increase in pressure loss can be prevented. Further, since the connection portion is covered with the perforated plate 100, the steam from the steam supply pipe 10b can be dispersed and merged, so that the turbulence generated when merging with the steam flowing through the steam supply pipe 10a is suppressed. be able to.

  As described above, since the turbulence of the steam generated in the vicinity of the bent portion 11 and the connection portion of the steam supply pipes 10a and 10b can be reduced, the fluid noise generated along with this can be suppressed. Further, the acoustic liner 13 is installed on the downstream side of the branch point 12a, so that the generated fluid noise can be prevented from propagating to the outside.

  In addition, as shown in FIG. 8A, the perforated plate 100 installed at the connection portion of the steam supply pipes 10a and 10b in the present embodiment is a fan-shaped one protruding inside the steam supply pipe 10a. The generation of fluid noise may be suppressed by reducing the opening area of the road. Further, as shown in FIG. 8 (b), the perforated plate 100 is projected on the inner side of the steam supply pipe 10a and is gently inclined toward the inner peripheral surface of the steam supply pipe 10a from the apex to the downstream side. As a thing of shape, it is good also as what can reduce peeling of the flow of a vapor | steam more.

<Fourth Embodiment>
A fourth embodiment of the present invention will be described with reference to the drawings. FIG. 9 is a cross-sectional view showing the configuration of the steam supply pipe 10 provided in the steam turbine in the present embodiment. In the present embodiment, parts used for the same purpose as those in the second embodiment (FIGS. 5 and 6) are denoted by the same reference numerals, and detailed description thereof is omitted.

  As in the second embodiment, the steam supply pipe 10 shown in FIG. 9 includes a U-shaped steam supply pipe 10a through which steam from the high-pressure turbine T2 flows, and a steam supply pipe 10b through which steam from the intermediate-pressure turbine T3 flows. . The steam supply pipe 10 is different from the second embodiment in that the steam supply pipe 10b is inserted into the steam supply pipe 10a at a branching point 12 of the steam supply pipe 10a. And in this steam supply pipe 10b, it is in the surface (surface seen from the bending part 11 side) which becomes a downstream with respect to the flow direction of the steam in the steam supply pipe 10a among the parts inserted inside the steam supply pipe 10a. As shown in FIG. 9, a plurality of holes 150 are provided. Furthermore, an acoustic liner 13 that covers the outer peripheral surface of the steam supply pipe 10a is installed at a position closer to the low-pressure turbine T1 than the branch point 12 of the steam supply pipe 10a, as in the second embodiment.

  When configured in this way, for example, in the case of the configuration as in the second embodiment, the flow direction of the steam flowing from the steam supply pipe 10b at the junction of the connecting portion 12 is the flow of steam in the steam supply pipe 10a. Since the directions intersect, the steam flow is disturbed at the junction of the connecting portions 12. As a result, pressure fluctuations occur at the junction of the connecting portion 12, causing fluid noise. On the other hand, as in this embodiment, the steam flowing through the steam supply pipe 10b flows into the steam supply pipe 10a through a plurality of holes 150 provided on the downstream surface of the steam supply pipe 10b, and the steam supply pipe Combined with the steam flowing through 10a.

  Therefore, the steam is discharged from the plurality of holes 150 of the steam supply pipe 10b along the flow of the steam flowing through the steam supply pipe 10a and merged. Variations can be reduced. Therefore, it is possible to suppress the fluid noise generated with this pressure fluctuation. Furthermore, since the acoustic liner 13 is installed on the downstream side of the branch point 12, it is possible to prevent propagation of the generated fluid noise to the outside.

  Further, in this embodiment, the shape of the steam supply pipe 10b inserted into the steam supply pipe 10a may be a streamlined shape (blade shape) with respect to the flow direction of the steam in the steam supply pipe 10a as shown in FIG. . That is, the angle formed between the flow direction of the upstream steam and the slope formed by the outer peripheral surface of the steam supply pipe 10b is increased, and the angle formed between the flow direction of the downstream steam and the slope formed by the outer peripheral surface of the steam supply pipe 10b is increased. By reducing the size, it is possible to reduce the fluid noise by suppressing the separation of the steam generated on the outer peripheral surface on the downstream side of the steam supply pipe 10b due to the influence of the inserted steam supply pipe 10b. FIG. 10 is a view showing a cross section of the steam supply pipe 10b perpendicular to the flow direction of the steam in the steam supply pipe 10b.

<Fifth Embodiment>
A fifth embodiment of the present invention will be described with reference to the drawings. FIG. 11 is a cross-sectional view in the axial direction showing the configuration of the support rod 50 provided in the steam turbine in the present embodiment. In addition, the structure of the steam turbine in this embodiment is made into the structure as FIG.1 and FIG.2 similarly to 1st Embodiment.

  The support rod 50 shown in FIG. 11 has a streamline shape (blade shape) with respect to the flow direction of steam in the turbine inlet chamber 60 (arrow A in FIG. 11). That is, the angle formed between the flow direction of the upstream steam and the slope formed by the outer peripheral surface of the support rod 50 is increased, and the angle formed between the flow direction of the downstream steam and the slope formed by the outer peripheral surface of the support rod 50 is decreased. . Thus, by making the support rod 50 into a streamline shape, it is possible to suppress the peeling of steam generated on the outer peripheral surface on the downstream side of the support rod 50 and reduce the pressure fluctuation. Therefore, fluid noise caused by this pressure fluctuation can be suppressed.

<Sixth Embodiment>
A sixth embodiment of the present invention will be described with reference to the drawings. FIG. 12 is an external view in the axial direction showing the configuration of the support rod 50 provided in the steam turbine in the present embodiment. In addition, the structure of the steam turbine in this embodiment is made into the structure as FIG.1 and FIG.2 similarly to 1st Embodiment.

  The support rod 50 shown in FIG. 12 has a dimple structure in which the outer peripheral surface has an uneven shape. In this way, by forming the outer peripheral surface in contact with the steam with a dimple structure, the turbulent flow is intentionally formed by the dimple and the turbulent flow is shifted to the downstream side, thereby preventing the steam from peeling off on the outer peripheral surface of the support rod 50. At the same time, the pressure recovery surface can be increased. Therefore, since resistance to steam is reduced, pressure fluctuation caused by the support rod 50 can be reduced, and fluid noise can be reduced.

  In this embodiment, the support rod 50 has a streamlined shape similar to that of the fifth embodiment, and further, separation on the downstream side of the support rod 50 is prevented, and pressure fluctuation is further reduced to reduce fluid noise. You may make it plan. In the second to fourth embodiments, the support bar 50 may be a support bar (FIGS. 11 and 12) having the shape described in the fifth or sixth embodiment. Further, in each of the above-described embodiments, a portion where noise is generated in the outer casing 20 of the steam turbine is a plate having the same shape as the covering portions 15 and 33 in which the surfaces of the acoustic liners 13 and 31 are dimple structure plates. The covering may prevent noise from being propagated to the outside.

These are schematic sectional drawings which show the structure of the steam turbine in 1st Embodiment. These are schematic sectional drawings which show the structure of the steam turbine in 1st Embodiment. FIG. 3 is a cross-sectional perspective view showing a configuration of an acoustic liner. These are the figures for demonstrating the viscoelastic model damping system in the acoustic liner of FIG. These are external views which show the structure of the steam supply pipe with which the steam turbine in 2nd Embodiment is equipped. These are sectional drawings which show the structure of the steam supply pipe with which the steam turbine in 2nd Embodiment is equipped. These are sectional drawings which show the structure of the steam supply pipe with which the steam turbine in 3rd Embodiment is equipped. These are sectional drawings which show another structure of the steam supply pipe with which the steam turbine in 3rd Embodiment is equipped. These are sectional drawings which show the structure of the steam supply pipe with which the steam turbine in 4th Embodiment is equipped. These are sectional drawings which show another structure of the steam supply pipe with which the steam turbine in 4th Embodiment is equipped. These are sectional drawings which show the structure of the support rod with which the steam turbine in 5th Embodiment is equipped. These are external views which show the structure of the support rod with which the steam turbine in 6th Embodiment is equipped.

Explanation of symbols

10, 10a, 10b Steam supply pipe (crossover pipe)
DESCRIPTION OF SYMBOLS 11 Bending part 12, 12a Branch point 13 Acoustic liner 14 Tube wall part 15 Covering part 16 Through hole 20 Outer casing 30 Steam inlet pipe 31 Acoustic liner 32 Outer peripheral wall part 33 Covering part 34 Through hole 40 Inner casing 41 Stator blade 50 Support Stick
60 Turbine inlet chamber 70 Rotor 71 Rotor blade 100 Perforated plate 101 Through hole 150 hole

Claims (12)

In the sound insulation structure that is composed of a housing through which fluid flows,
The outer peripheral surface of a part of the housing is covered in the circumferential direction, and the surface of the cover has an uneven shape, and
A plurality of through holes formed in the wall of the casing covered with the covering portion and penetrating from the inside of the casing to a space between the covering portion and the wall of the casing;
A sound insulation structure comprising: When the housing includes a branch point where the fluids merge,
The sound insulation structure is installed downstream of the branch point in the fluid flow direction. In the sound insulation structure composed of a pipe through which fluid flows,
The pipe has a configuration in which a first pipe serving as a first flow path that is a main flow path of the fluid and a second pipe serving as a second flow path of the fluid are connected, and the first flow path and the second flow path While joining the flow path,
A plurality of through holes are provided to cover a connection portion of the second pipe in the first pipe at a branch point between the first pipe and the second pipe that joins the second flow path to the first flow path. A sound insulation structure in which a perforated plate is installed. The first tube includes a bent portion;
The branching point between the first pipe and the second pipe is located on the inner side of the inner peripheral surface of the bent portion of the first pipe at the downstream side of the bent portion near the bent portion in the fluid flow direction. The sound insulation structure according to claim 3, wherein the sound insulation structure is installed on the same surface. The inner peripheral surface of the first tube and the surface of the perforated plate constitute the same curved surface,
5. The sound insulation structure according to claim 4, wherein the curved surface formed by an inner peripheral surface of the first tube and a surface of the perforated plate has a shape in which a flow resistance to the fluid is reduced. In the sound insulation structure composed of a pipe through which fluid flows,
The pipe is connected by inserting a second pipe serving as a second flow path of the fluid into a first pipe serving as a first flow path that is the main flow path of the fluid,
By providing a plurality of through holes penetrating from the inside of the second pipe to the inside of the first pipe on the pipe wall on the downstream side in the fluid flow direction in the portion inserted into the first pipe of the second pipe,
A sound insulation structure characterized by joining the first flow path and the second flow path. In a turbine comprising: a rotor that rotates when a supplied fluid collides with a moving blade; and a casing that supports the rotor around the rotor and includes a stationary blade between the moving blades in the axial direction of the rotor. ,
A turbine comprising the sound insulation structure according to claim 1 at a fluid inlet of the vehicle compartment to which the fluid is supplied. In a turbine comprising: a rotor that rotates when a supplied fluid collides with a moving blade; and a casing that supports the rotor around the rotor and includes a stationary blade between the moving blades in the axial direction of the rotor. ,
A turbine comprising the sound insulation structure according to claim 1 in a fluid supply pipe that supplies the fluid to the vehicle compartment. A rotor that rotates when a supplied fluid collides with a moving blade, a casing that supports the rotor as a center and includes a stationary blade between the moving blades in the axial direction of the rotor, and a plurality of flow paths A turbine comprising: a fluid supply pipe for supplying fluid from
A turbine comprising the sound insulation structure according to any one of claims 2 to 6 in each portion where the plurality of flow paths of the fluid supply pipe merge. A rotor that rotates when the supplied fluid collides with the rotor blades, a vehicle casing that supports the rotor in the center and includes stationary blades between the rotor blades in the axial direction of the rotor; In a turbine comprising a plurality of support rods installed in a circumferential direction of the rotor at an inlet portion to which the fluid is supplied,
A turbine characterized in that a cross-sectional shape of the plurality of support rods is a shape that reduces a flow resistance with the fluid.   Increase the angle formed by the flow direction of the fluid on the upstream side and the slope formed by the outer peripheral surface of the support rod, and decrease the angle formed by the flow direction of the fluid on the downstream side and the slope formed by the outer peripheral surface of the support rod. The turbine according to claim 10.   The turbine according to any one of claims 10 and 11, wherein an outer peripheral surface of the support rod is formed into an uneven shape.

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