JP2011196280A - Flow regulating device of rotary machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flow regulating device of a rotary machine, improving the performance by inhibiting fluid leakage at a fluid inlet.SOLUTION: An air passage 43 is formed between inner and outer casings having cylindrical shapes. A rotor 32 is supported rotatably on the inner casing, stator blades 23 are fixed to the casings, and rotor blades 24 are fixed to the rotor 32. An inlet guide vane 22 is provided on an air inlet 20 side of the air passage 43. As the inlet guide vane 22, a plurality of vane bodies 51 are provided to be arranged in a radial manner along the circumferential direction with ends in the radial direction rotatably supported on the respective casings, and at the ends in the radial direction of each vane body 51, close members 54, 55, 56, 57 are provided for closing gaps by displacing or deforming, for instance extending and contracting, to the respective casing sides.

Description

  The present invention relates to a flow rate adjusting device for a rotary machine that can adjust a flow rate of a fluid taken into the interior using a variable guide vane provided at a fluid inlet of the rotary machine.

  For example, a gas turbine for power generation, which is a kind of rotating machine, includes a compressor, a combustor, and a turbine. The air taken in from the air intake port is compressed by the compressor to become high-temperature and high-pressure compressed air. In the combustor, the fuel is supplied to the compressed air and burned, so that the high-temperature and high-pressure is burned. The combustion gas (working fluid) is obtained, the turbine is driven by the combustion gas, and the generator connected to the turbine is driven.

  In such a gas turbine compressor, a plurality of rotor blades are mounted on a rotating shaft in a plurality of stages, a plurality of stator blades are mounted on a casing in a plurality of stages, and an inlet guide blade is provided in an air intake. Is provided. In this inlet guide vane, a plurality of blade main bodies are arranged side by side along the circumferential direction, and the angle of each blade main body can be changed by a driving device. Therefore, by changing the angle of each blade body by the drive device according to the amount of power generated by the gas turbine, the amount of air taken into the interior can be adjusted by changing the flow passage area of the air intake.

  The air intake port of the compressor is constituted by a circular casing. On the other hand, each blade main body constituting the inlet guide vane is rotatably supported by the casing in the longitudinal direction. In this case, by rotating each blade body and changing its angle, the flow passage area of the air intake port is changed, and at this time, a gap is formed between the end of each blade body and the casing. End up. Then, since the air leakage flow acts in the gap between the blade body and the casing, there is a possibility that vortex is generated here or flow separation occurs and the performance of the compressor is deteriorated. is there.

  Therefore, as a solution to such a problem, for example, there is one described in Patent Document 1 below. In the air volume adjustment device for a blower described in Patent Document 1, a plurality of vane shafts are rotatably supported in a radial manner on a vane casing, and a vane blade is fixed to the vane shaft, and the vane casing, the vane shaft, A seal member is attached to the gap with the vane blade.

JP 58-205000 A

  However, in the above-described conventional air volume adjusting device for a blower, the seal member is provided on the casing side and is in contact only when the vane blade is closed to seal air leakage. Therefore, in a state where the vane blade is opened and the flow passage area of the air intake port is adjusted to a predetermined size, air leakage cannot be sealed by the sealing member, and vortex generation or separation flow still remains. Occurrence cannot be suppressed, and there is a problem that performance is degraded.

  The present invention solves the above-described problems, and an object of the present invention is to provide a rotary machine flow rate adjusting device that can improve performance by suppressing fluid leakage at a fluid inlet.

  In order to achieve the above-described object, a flow rate adjusting device for a rotary machine according to the present invention comprises an annular flow path constituted by an outer wall and an inner wall, and a rotary blade is rotatably supported in the annular flow path. In a flow control device for a rotary machine, in which an inlet guide vane capable of adjusting a flow rate of fluid is provided at a fluid inlet portion of a passage, the inlet guide vanes are arranged along a circumferential direction so as to form a radial shape in the annular flow path. And a plurality of wing bodies that are rotatably supported by at least one of the outer wall and the inner wall in a radial direction, and the outer walls and the inner walls of the wing body have radial ends. A closing member capable of closing a gap with at least one of the two is provided.

  Therefore, by providing a closing member capable of closing a gap between at least one of the outer wall and the inner wall on a plurality of blade bodies constituting the inlet guide blade, each blade body is adjusted to adjust the flow rate of the fluid taken into the interior. When rotating, the distance between the outer wall and / or the inner wall and the end of the blade body changes, but the closing member is displaced or deformed from the blade body side to the outer wall side and / or the inner wall side, for example, expands and contracts to close the gap. Thus, fluid leakage at the inlet guide vanes can be suppressed at the fluid inlet, and the performance of the rotating machine can be improved.

  In the rotary machine flow control device according to the present invention, the outer wall and the inner wall are formed by inner and outer casings having a cylindrical shape, and the blocking member extends from the radial end of the blade body to the inner periphery of the outer casing. It is characterized by being displaceable or deformable with respect to at least one of the surface and the outer peripheral surface of the inner casing, for example, extendable and contractible.

  Therefore, the closing member is displaced or deformed from the blade body side to the outer casing and / or the inner casing, for example, expands and contracts to close the gap, and fluid leakage at the inlet guide blade can be appropriately suppressed.

  The flow rate adjusting device for a rotary machine according to the present invention is characterized in that a biasing member for biasing the closing member from the blade main body side to at least one of the outer wall side and the inner wall side is provided.

  Therefore, the closing member on the blade body side is constantly pressed against the outer wall and / or inner wall by the biasing member to close the gap, and the clearance between the blade body and the outer wall and / or inner wall can be easily reduced with a simple configuration. can do.

  In the rotary machine flow rate adjusting device of the present invention, the wing body has a radial end portion rotatably supported by at least one of the outer casing and the inner casing by a support shaft, and has a diameter at the support shaft. The blocking member is mounted on both sides in the direction.

  Therefore, the closing member is attached while avoiding the support shaft, and the gap between the wing body and the casing can be reduced without affecting the rotation of the wing body.

  In the flow rate adjusting device for a rotary machine according to the present invention, the blade main body is characterized in that a housing recess is formed at an end in the radial direction, and the closing member is supported movably in the housing recess.

  Therefore, the closing member does not fall off or scatter, can be smoothly moved while being guided by the inner wall of the housing recess, can improve followability, and can be easily disassembled and assembled. Can do.

  In the flow control device for a rotary machine according to the present invention, the blocking member is divided into a plurality of parts in the width direction and / or the thickness direction of the blade body.

  Therefore, by dividing the blocking member, the divided portion of the blocking member is individually displaced or deformed according to the shape of the casing, for example, expands and contracts to close the gap between the wing body and the casing. The followability to fluctuations in the gap amount during movement is also improved, and this gap can be effectively reduced.

  In the flow control device for a rotary machine according to the present invention, the closing member is formed of an elastic body.

  Therefore, the closing member made of an elastic body is pressed against the casing while being elastically deformed to close the gap, and the gap between the blade body and the casing can be easily reduced with a simple configuration.

  According to the flow control device for a rotary machine of the present invention, a plurality of blade main bodies are arranged radially and end portions are rotatably supported on the outer wall and / or the inner wall to form inlet guide blades. Since a closing member that can expand and contract toward the outer wall side and / or the inner wall side to close the gap is provided at the end in the radial direction, the closing member is displaced or deformed to the outer wall side and / or the inner wall side when each blade body is rotated. For example, since the gap is closed by expanding and contracting, even when the inlet guide vane rotates at the fluid inlet portion, fluid leakage can always be suppressed, and the performance of the rotating machine can be improved.

FIG. 1 is a schematic diagram illustrating a flow rate adjusting device for a rotary machine according to a first embodiment of the present invention. FIG. 2 is a schematic diagram illustrating an inlet guide blade in the flow rate adjusting device for the rotary machine according to the first embodiment. FIG. 3 is a top view or a bottom view of the inlet guide vane of the first embodiment. FIG. 4 is a cross-sectional view illustrating a closing member in the inlet guide vane of the first embodiment. FIG. 5 is a schematic diagram illustrating a gas turbine to which the flow rate adjusting device for a rotary machine according to the first embodiment is applied. FIG. 6 is a cross-sectional view illustrating a closing member in an inlet guide blade representing a flow rate adjusting device for a rotary machine according to a second embodiment of the present invention. FIG. 7 is a schematic diagram illustrating a closing member in an inlet guide blade that represents a modification of the second embodiment. FIG. 8 is a schematic diagram illustrating a closing member in an inlet guide vane that represents a flow rate adjusting device for a rotary machine according to a third embodiment of the present invention. FIG. 9 is a schematic diagram illustrating a closing member in an inlet guide blade that represents a modification of the third embodiment.

  Exemplary embodiments of a flow control device for a rotary machine according to the present invention will be described below in detail with reference to the accompanying drawings. In addition, this invention is not limited by this Example.

  1 is a schematic diagram illustrating a flow rate adjusting device for a rotary machine according to a first embodiment of the present invention, FIG. 2 is a schematic diagram illustrating an inlet guide vane in the flow rate adjusting device for the rotary machine according to the first embodiment, and FIG. FIG. 4 is a cross-sectional view showing a closing member in the inlet guide vane of the first embodiment, and FIG. 5 is a flow control device for a rotary machine of the first embodiment. It is the schematic showing a gas turbine.

  As shown in FIG. 5, the gas turbine of the first embodiment includes a compressor 11, a combustor 12, and a turbine 13. A generator (not shown) is connected to the gas turbine and can generate power.

  The compressor 11 has an air intake 20 for taking in air, an inlet guide vane (IGV) 22 is disposed in the compressor casing 21, and a plurality of stationary blades 23 and moving blades 24 are provided. Arranged alternately in the front-rear direction (the axial direction of the rotor 32 to be described later), the bleed chamber 25 is provided on the outside thereof. The combustor 12 is combustible by supplying fuel to the compressed air compressed by the compressor 11 and igniting it. In the turbine 13, a plurality of stationary blades 27 and moving blades 28 are alternately disposed in a turbine casing 26 in the front-rear direction (the axial direction of a rotor 32 described later). An exhaust chamber 30 is disposed downstream of the turbine casing 26 via an exhaust casing 29, and the exhaust chamber 30 has an exhaust diffuser 31 that is continuous with the turbine 13.

  Further, a rotor (rotating shaft) 32 is positioned so as to penetrate the compressor 11, the combustor 12, the turbine 13, and the central portion of the exhaust chamber 30. The end of the rotor 32 on the compressor 11 side is rotatably supported by the bearing portion 33, while the end of the exhaust chamber 30 side is rotatably supported by the bearing portion 34. The rotor 32 is fixed by stacking a plurality of disks with each blade 24 mounted thereon by the compressor 11 and fixed by a plurality of disks having each blade 28 mounted by the turbine 13. A generator drive shaft (not shown) is connected to the end on the exhaust chamber 30 side.

  In this gas turbine, the compressor casing 21 of the compressor 11 is supported by the legs 35, the turbine casing 26 of the turbine 13 is supported by the legs 36, and the exhaust chamber 30 is supported by the legs 37. .

  Therefore, the air taken in from the air intake port 20 of the compressor 11 passes through the inlet guide vane 22, the plurality of stationary vanes 23, and the moving blades 24 and is compressed to become high-temperature and high-pressure compressed air. A predetermined fuel is supplied to the compressed air in the combustor 12 and burned. Then, the high-temperature and high-pressure combustion gas (working fluid) that is the working fluid generated by the combustor 12 passes through the plurality of stationary blades 27 and the moving blades 28 that constitute the turbine 13 to drive and rotate the rotor 32. Then, the generator connected to the rotor 32 is driven. On the other hand, the energy of the exhaust gas (combustion gas) is converted into pressure by the exhaust diffuser 31 in the exhaust chamber 30 and decelerated before being released to the atmosphere.

  In the compressor 11 of the first embodiment described above, as shown in FIG. 1, the compressor casing 21 is composed of an outer casing (outer wall) 41 having a cylindrical shape and an inner casing (inner wall) 42 having a similar cylindrical shape. An air passage (annular passage) 43 is formed between the outer casing 41 and the inner casing 42. The rotor 32 is disposed concentrically with the casings 41 and 42 inside the inner casing 42, and is rotatably supported by the inner casing 42 by bearing portions 33 and 34 (see FIG. 5). The stationary blades 23 as fixed blades are arranged radially in the air passage 43 and are arranged in the circumferential direction, and each end is fixed to each casing 41, 42. Further, the moving blades 24 as the rotating blades are arranged radially in the air passage 43 and are arranged in the circumferential direction, and the base end portion is fixed to the rotor 32 via the disk 44. Yes.

  One end portion of the air passage 43 communicates with an air intake port 20 as a fluid inlet portion, and an inlet guide vane 22 capable of adjusting the flow rate of air (fluid) is disposed therein. Although the inlet guide vanes 22 are arranged radially in the air passage 43 and are arranged in the circumferential direction of the rotor 32 as in the case of the stationary vanes 23, the radial direction of the rotor 32 (radial direction). ) Are rotatably supported by the casings 41 and 42, respectively.

  That is, the inlet guide vanes 22 are arranged along the circumferential direction of the rotor 32 so as to form a radial shape, and a plurality of blade bodies 51 whose radial ends are rotatably supported by the casings 41 and 42 are provided. Have. As shown in FIGS. 1 to 4, the wing body 51 has a support shaft 52 fixed to one end portion (outer end portion) in the longitudinal direction, which is a radial direction, and the support shaft 52 is rotatable to the outer casing 41. It is supported by. The blade body 51 has a support shaft 53 fixed to the other end portion (inner end portion) in the longitudinal direction, and the support shaft 53 is rotatably supported by the inner casing 42. The support shaft 52 on the outer casing 41 side is connected to a drive device (not shown), and the blade body 51 can be rotated over a predetermined angle range via the support shaft 52 by the drive device.

  In this embodiment, the blade main body 51 expands and contracts toward the casings 41 and 42 to close the gaps between the radial ends of the blade main body 51 and the casings 41 and 42 in the radial direction of the rotor 32. Possible closing members 54, 55, 56, 57 are provided. The closing members 54, 55, 56, 57 are urged and supported from the blade body 51 side to the casings 41, 42 side by compression springs 58, 59 as urging members.

  The wing body 51 is at the outer end on both sides of the support shaft 52, that is, on both sides in the width direction (see FIG. 3) of the wing body 51, in other words, on both ends in the radial direction of the support shaft 52. Opening storage recesses 61, 62 are formed, and the closing members 54, 55 are stored in the storage recesses 61, 62 and are movable in the longitudinal direction of the wing body 51 (see FIG. 2). Compression springs 58 and 59 are interposed between the closing members 54 and 55 and the bottom surfaces of the recesses 61 and 62. The end portions of the closing members 54 and 55 are pressed against the inner peripheral surface of the outer casing 41 by the urging force of the compression springs 58 and 59 accommodated in the recesses 61 and 62.

  The wing body 51 has end portions on both sides of the support shaft 53 at the inner end, that is, on both sides in the width direction (see FIG. 3) of the wing body 51, in other words, on both sides in the radial direction of the support shaft 52. Storage recesses 63 and 64 that are open to the side are formed. Closure members 56 and 57 are stored in the storage recesses 63 and 64 and are movable in the longitudinal direction of the wing body 51 (see FIG. 2). A compression spring (not shown) is interposed between the closing members 56 and 57 and the bottom surfaces of the recesses 63 and 64. The end portions of the closing members 56 and 57 are pressed against the outer peripheral surface of the inner casing 42 by the urging force of the compression springs housed in the recesses 63 and 64.

  Therefore, when the wing body 51 rotates around the support shafts 52 and 53 as shown in FIG. 3, the widthwise ends of the wing body 51 (left and right ends in FIG. 3) Moves in the direction of the axis B, which is the circumferential direction of the rotor 32, with respect to the axis A along the air flow direction (the axial direction of the rotor 32). At this time, since the inner wall surface of the outer casing 41 has an arc shape at the outer end portion of the wing body 51, when the end portion in the width direction of the wing body 51 is separated from the axis A, the outer casing 41 The distance from the inner wall surface is shortened. Therefore, the closing members 54 and 55 are pressed against the inner wall surface of the outer casing 41 to compress the compression springs 58 and 59 and enter the recesses 61 and 62. On the other hand, when the end of the wing body 51 in the width direction approaches the axis A, the distance from the inner wall surface of the outer casing 41 becomes longer. Therefore, the closing members 54 and 55 protrude from the recesses 61 and 62 while pressing the inner wall surface of the outer casing 41 by the urging force of the compression springs 58 and 59.

  Further, when the wing body 51 rotates about the support shafts 52 and 53, the outer wall surface of the inner casing 42 has an arc shape at the inner end of the wing body 51. When the end portion is separated from the axis A, the distance from the outer wall surface of the inner casing 42 is increased. Therefore, the closing members 56 and 57 protrude from the recesses 63 and 64 while pressing the outer wall surface of the inner casing 42 by the urging force of the compression spring. On the other hand, when the end of the blade body 51 in the width direction approaches the axis A, the distance from the outer wall surface of the inner casing 42 is shortened. Therefore, each closing member 56, 57 is pressed against the outer wall surface of the inner casing 42 to compress the compression spring and enter the recesses 63, 64.

  When the inlet guide vanes 22 are operated and the blade main bodies 51 are rotated about the support shafts 52 and 53, the sizes of the gaps between the end portions in the longitudinal direction of the blade main bodies 51 and the casings 41 and 42 are changed. To do. However, as the length (distance) of the gap changes, the closing members 54, 55, 56, and 57 appear and disappear by the urging force of the compression springs 58 and 59, and the closing members 54, 55, 56, and 57 The tip portion always follows and contacts the wall surface of each casing 41, 42, and the gap between the blade body 51 and each casing 41, 42 is reduced to a minimum.

  As described above, in the flow rate adjusting device for a rotary machine according to the first embodiment, the air passage 43 is formed between the cylindrical inner and outer casings 41 and 42, and the rotor 32 is rotatably supported by the inner casing 42. The stationary blade 23 is fixed to the casings 41, 42, while the moving blade 24 is fixed to the rotor 32, and the inlet guide blade 22 is provided on the air intake port 20 side of the air passage 43. As the inlet guide blade 22, A plurality of wing bodies 51 arranged in the circumferential direction so as to form a radial shape and whose radial ends are rotatably supported by the casings 41 and 42 are provided, and the radial ends of the wing main bodies 51 are provided. The part is provided with closing members 54, 55, 56, and 57 that can be expanded and contracted (deformed) toward the casings 41 and 42 to close the gaps.

  Accordingly, when each blade body 51 constituting the inlet guide blade 22 is rotated in order to adjust the flow rate of air taken into the compressor 11, the distance between each casing 41, 42 and the end of each blade body 51. However, the closing members 54, 55, 56, 57 are displaced or deformed from the blade body 51 side to the casings 41, 42 side, and are expanded or contracted here to close the fluctuating gap. Thus, fluid leakage at the inlet guide vane 22 can be suppressed. In addition, since the generation of vortices and flow separation caused by the gap can be suppressed by this, the flow of air flowing from the air intake port 20 through the air passage 43 to the blades 23 and 24 becomes smooth, and the work load of the moving blade 24 is increased. Increases, the amount of air sucked in and the heat insulation efficiency are improved, and the performance of the compressor 11 and the gas turbine can be improved.

  In this case, an inner casing 42 is provided inside the outer casing 41, one end of each wing body 51 is rotatably supported by the outer casing 41 with a support shaft 52, and the other end of each wing body 51 is connected to the inner casing 42. And a support member 53 that is pivotally supported and is displaced or deformed toward the casings 41 and 42 at both radial ends of each wing body 51. 55, 56, 57 are provided. Therefore, when each blade body 51 is supported by both inner and outer casings 41, 42, the gaps on both end portions of each blade body 51 may be blocked by the blocking members 54, 55, 56, 57. it can.

  Further, in the flow rate adjusting device for a rotary machine according to the present embodiment, compression springs 58 and 59 for urging the closing members 54, 55, 56, and 57 from the blade body 51 side to the casings 41 and 42 side are provided. Therefore, the closing members 54, 55, 56, 57 mounted on the blade bodies 51 are always pressed against the casings 41, 42 by the compression springs 58, 59 to close the gaps. Thus, the gap between the blade body 51 and the casings 41 and 42 can be easily reduced.

  In this case, storage recesses 61, 62, 63, 64 are formed at each end of the blade body 51, and the closing members 54, 55, 56, 57 are stored in the storage recesses 61, 62, 63, 64 in a movable manner. The compression springs 58 and 59 are interposed between the closing members 54, 55, 56 and 57 and the bottom surfaces of the recesses 61, 62, 63 and 64. Therefore, the closing members 54, 55, 56, and 57 do not fall off, can move smoothly while being guided by the inner walls of the storage recesses 61, 62, 63, and 64, and the followability can be improved. Further, the disassembling and assembling of the closing members 54, 55, 56, and 57 can be easily performed.

  Further, in the flow rate adjusting device for a rotary machine according to the present embodiment, each blade main body 51 rotatably supports each end portion in the radial direction on each casing 41, 42 by the support shafts 52, 53, and each support shaft. Closing members 54, 55, 56, 57 are mounted on both sides in the radial direction of 52, 53. Accordingly, the blocking members 54, 55, 56, and 57 are attached while avoiding the support shafts 52 and 53, and without adversely affecting the rotation of each blade body 51, that is, the operation of the inlet guide blade 22. The gap between each wing body 51 and each casing 41, 42 can be reduced.

  FIG. 6 is a cross-sectional view showing a closing member in an inlet guide blade representing a flow rate adjusting device for a rotary machine according to a second embodiment of the present invention, and FIG. 7 shows the closing member in the inlet guide blade representing a modification of the second embodiment. FIG. Note that members having the same functions as those of the above-described embodiments are denoted by the same symbols, and detailed description thereof is omitted.

  In the flow rate adjusting device for a rotary machine according to the second embodiment, as shown in FIG. 6, a blade body 51 constituting an inlet guide blade is rotatably supported at one end in the longitudinal direction by an outer casing 41 by a support shaft 52. In addition, closing members 71 and 72 that can close the gap between the blade body 51 and the outer casing 41 by extending and contracting to the outer casing 41 side are provided at one end portion. In this embodiment, the closing members 71 and 72 are divided into a plurality (two in this embodiment) in the width direction of the wing body 51 (left and right in FIG. 6).

  That is, the blade main body 51 is formed with storage recesses 73 and 74 that open to the end side, adjacent to the support shaft 52 at the outer end, that is, on the lateral side of the blade main body 51. The closing members 71 and 72 are accommodated in the accommodating recesses 73 and 74 and are movable in the longitudinal direction of the wing body 51. Compression springs 75 and 76 are interposed between the closing members 71 and 72 and the bottom surfaces of the recesses 73 and 74. The end portions of the closing members 71 and 72 are pressed against the inner peripheral surface of the outer casing 41 by the urging force of the compression springs 75 and 76 accommodated in the recesses 73 and 74.

  Therefore, when the blade body 51 rotates about the support shaft 52, the end in the width direction of the blade body 51 moves in a direction intersecting the air flow direction in the air passage 43, and the inner wall surface of the outer casing 41 The distance of fluctuates. At this time, the closing members 71 and 72 are displaced or deformed, for example, expanded and contracted, with the elastic force of the compression springs 75 and 76 while the tip portion presses the inner wall surface of the outer casing 41. Therefore, the end portions of the closing members 71 and 72 are always in contact with the outer casing 41, and the gap between the blade body 51 and the outer casing 41 is reduced to the minimum. In this case, since the closing members 71 and 72 are divided into two parts, the closing members 71 and 72 individually follow in accordance with the shape of the inner wall surface of the outer casing 41 to close the gap. The gap between 51 and the outer casing 41 is efficiently reduced.

  In the second embodiment, the blocking members 71 and 72 are divided into two in the width direction of the blade body 51. However, the dividing direction and the number of divisions are not limited to this embodiment.

  That is, as shown in FIG. 7, the blade body 51 constituting the inlet guide blade is provided with a support shaft 52 at one end in the longitudinal direction, and is displaced or deformed toward the outer casing at one end, for example, expands and contracts. Thus, closing members 77 and 78 that can close the gap between the blade body 51 and the outer casing are provided. In this modification, a plurality of closing members 77 and 78 are provided in the width direction (left and right direction in FIG. 7) and the thickness direction (see FIG. 3; up and down direction in FIG. 7) of the wing body 51 (this embodiment). In the example, each of the four divided bodies 77a, 77b, 77c, 77d, 78a, 78b, 78c, and 78d is divided. In this case, although not shown, the closing members 77 and 78 (divided bodies 77 a, 77 b, 77 c, 77 d, 78 a, 78 b, 78 c and 78 d) are compressed in a recess formed at one end of the blade body 51. The tip portion is pressed against the outer casing by the biasing force of the spring.

  As described above, in the flow rate adjusting device for a rotary machine according to the second embodiment, the inlet guide vanes are arranged along the circumferential direction so as to form a radial shape, and the end portions in the radial direction are rotatably supported by the casing. A plurality of blade main bodies 51 are provided, and at the radial end portions of the blade main bodies 51, displacement members or displacement, for example, closing members 71, 72, 77, and 78 that can be expanded and contracted to close the gaps are provided. Yes.

  Therefore, even if the wing body 51 rotates and the distance between the casing and the end of the wing body 51 changes, the closing members 71, 72, 77, 78 are displaced or deformed from the wing body 51 side to the casing side, for example, The expansion and contraction closes the fluctuating gap, so that fluid leakage at the inlet guide vane can be suppressed and the performance of the compressor can be improved.

  In this case, the closing members 71 and 72 are divided in the width direction of the wing body 51, and the closing members 77 and 78 are divided in the width direction and the thickness direction of the wing body 51. Accordingly, by forming the closing members 71, 72, 77, 78 separately, the divided portions of the closing members 71, 72, 77, 78 are individually displaced or changed according to the shape of the inner wall surface or the outer wall surface of the casing. Deformation, for example, expansion and contraction closes the gap between the wing body 51 and the casing, and this gap can be effectively reduced.

  In each of the above-described embodiments, the biasing member of the present invention is configured by the compression springs 58, 59, 75, and 76, but is not limited to this configuration, and is blocked by an elastic body such as rubber or synthetic resin. The member may be biased and supported on the casing side.

  FIG. 8 is a schematic diagram showing a closing member in an inlet guide vane representing a flow rate adjusting device for a rotary machine according to a third embodiment of the present invention, and FIG. 9 shows a closing member in the inlet guide vane representing a modified example in the third embodiment. FIG. Note that members having the same functions as those of the above-described embodiments are denoted by the same symbols, and detailed description thereof is omitted.

  In the rotary machine flow rate adjusting apparatus according to the third embodiment, as shown in FIG. 8, the blade body 51 constituting the inlet guide blade is provided with a support shaft 52 at one end in the longitudinal direction, and the blade body 51 rotates. It is formed of an elastic body so that the gap between the wing body 51 and the outer casing can be closed by following the displacement or deformation following the fluctuation of the gap amount with the outer casing side that occurs at this time. Flexible closing members 81 and 82 are provided at one end of the wing body 51. In this embodiment, the closing members 81 and 82 are constituted by brush seals. In a modification, as shown in FIG. 9, the closing members 83 and 84 are constituted by leaf seals in which a plurality of thin plates are stacked.

  That is, the closing members 81 and 82 constituted by brush seals can be elastically deformed three-dimensionally to close the gap in response to the change in the gap between the blade body 51 and the outer casing. In addition, the closing members 83 and 84 configured by leaf seals can be elastically deformed two-dimensionally to close the gaps against fluctuations in the gaps between the blade body 51 and the outer casing. In this case, the closing members 81, 82, 83, 84 themselves function as urging members.

  As described above, in the flow rate adjusting device for the rotary machine according to the third embodiment, the closing members 81 and 82 are formed of an elastic body to form a brush seal. Further, the closing members 83 and 84 are formed of an elastic body to form a leaf seal. Therefore, the closing members 81, 82, 83, 84 made of an elastic body press the casing while elastically deforming to close the gap, and easily reduce the gap between the blade body 51 and the casing with a simple configuration. be able to.

  In the third embodiment, the closing members 81, 82, 83, and 84 are formed of an elastic body to form a brush seal or a leaf seal. However, the present invention is not limited to this configuration. For example, a spring seal as an elastic body in which a plurality of comb-like thin plates are stacked as the closing member may be used.

  Moreover, in each Example mentioned above, although the obstruction | occlusion member of this invention was provided in the both ends in the longitudinal direction of the blade | wing main body 51 which comprises the inlet guide blade 22, you may provide in only one side. Further, the blade main body 51 has been described as a double-sided support structure, but the present invention can also be applied to a case where the blade main body constituting the inlet guide blade has a cantilever support structure in which only one end portion in the longitudinal direction is supported by the casing. In this case, the gap amount can be further reduced by providing a closing member on substantially the entire end portion of the end portion without the support shaft. It is supported when the blade body is cantilevered by the casing at the outer end in the longitudinal direction and there is no casing inside, and the outer peripheral surface of the rotor (rotating shaft) directly faces the inner end of the blade body. A closing member may be provided at the outer end of the formed side, and a closing member may be provided at the inner end of the blade body to close the gap between the outer peripheral surface of the rotary shaft serving as the inner wall.

  In addition, the closing members 54 to 57, 71, 72, 77, 78 in the first and second embodiments described above may be rigid bodies, but the closing members themselves may be elastic bodies such as rubber and synthetic resin. In this case, the gap may be closed by pressing toward the casing using only the urging force of the closing member formed of an elastic body without using the urging members 58, 59, 75, and 76. .

  In each of the above-described embodiments, the blocking member of the present invention is divided into two in the width direction at both ends in the longitudinal direction of the blade body 51 constituting the inlet guide blade 22. It may be provided.

  In each of the above-described embodiments, a multistage compressor in which a plurality of rows of stationary blades and moving blades are alternately arranged has been described. However, the present invention is not limited to this, and only one row of stationary blades and moving blades is provided. The present invention can also be applied to a single-stage compressor.

  In each of the above-described embodiments, the flow rate adjusting device for a rotary machine according to the present invention has been described as applied to a compressor of a gas turbine, but the application field is not limited to a gas turbine, but as a rotary machine, For example, the present invention can be applied to a blower or a pump. In this case, the type is not limited to an axial flow type, a diagonal flow type, a centrifugal type, or the like.

  The flow control device for a rotary machine according to the present invention is provided with a closing member that can be displaced or deformed on the outer wall side and / or the inner wall side at the end of the blade body constituting the inlet guide blade, for example, can be closed by closing the gap. Thus, it is possible to improve the performance by suppressing the fluid leakage at the fluid inlet, and it can be applied to any kind of rotating machine.

11 Compressor 12 Combustor 13 Turbine 20 Air intake (fluid inlet)
21 Compressor compartment 22 Inlet guide vane 23 Stator vane 24 Rotor vane (rotary vane)
32 Rotor (Rotating shaft)
41 Outer casing (outer wall)
42 Inner casing (inner wall)
43 Air passage (annular passage)
51 Blade body 52, 53 Support shaft 54, 55, 56, 57, 71, 72, 77, 78, 81, 82, 83, 84 Closure member 58, 59, 75, 76 Compression spring (biasing member)
61, 62, 63, 64, 73, 74 Storage recess

Claims (7)

An annular channel is constituted by the outer wall and the inner wall, and the rotor blade is rotatably supported in the annular channel, and an inlet guide vane capable of adjusting the flow rate of the fluid is provided at the fluid inlet of the annular channel. In the flow control device of a rotating machine,
The inlet guide vanes are arranged along the circumferential direction so as to form a radial shape in the annular flow path, and a plurality of radial end portions are rotatably supported on at least one of the outer wall and the inner wall. Having a wing body
A closing member capable of closing a gap between at least one of the outer wall and the inner wall is provided at a radial end of the wing body.
A flow rate adjusting device for a rotating machine.   The outer wall and the inner wall are formed by inner and outer casings having a cylindrical shape, and the blocking member is at least one of an inner peripheral surface of the outer casing and an outer peripheral surface of the inner casing from a radial end of the wing body. The flow rate adjusting device for a rotary machine according to claim 1, wherein the flow rate adjusting device can be displaced or deformed with respect to one of the two.   In the rotary machine flow rate adjusting device of the present invention, a biasing member for biasing the closing member from the blade body side to at least one of the outer wall side and the inner wall side is provided. 2. A flow rate adjusting device for a rotary machine according to 2.   In the rotary machine flow rate adjusting device of the present invention, the wing body has a radial end portion rotatably supported by at least one of the outer casing and the inner casing by a support shaft, and has a diameter at the support shaft. 4. The flow rate adjusting device for a rotary machine according to claim 2, wherein the closing member is mounted on both sides in the direction. 5.   5. The wing body according to claim 1, wherein a storage recess is formed at an end portion in a radial direction, and the closing member is movably supported in the storage recess. Flow control device for rotating machinery.   The flow rate adjusting device for a rotary machine according to any one of claims 1 to 5, wherein the closing member is divided into a plurality of parts in a width direction and / or a thickness direction of the blade main body. The flow rate adjusting device for a rotary machine according to claim 1, wherein the closing member is formed of an elastic body.

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