JP6595926B2 - Rotating machine - Google Patents

Description

  The present disclosure relates to rotating machinery.

A rotating machine such as a steam turbine or a gas turbine usually has a gap between a stationary part and a rotating part, for example, a gap between a moving blade and a member surrounding the moving blade, or between a stationary blade and a rotor shaft. A sealing device capable of restricting the flow of fluid in the gap is provided.
For example, a sealing device for a rotating machine disclosed in Patent Document 1 has a deformed portion, and is configured to be able to automatically adjust the width of a seal gap according to a pressure difference between a first range and a second range. .
Moreover, the automatic adjustment seal of the turbo rotating machine disclosed in Patent Document 2 has a movable seal ring, and the movable seal ring is pressed radially inward by the working fluid during rated operation to automatically increase the width of the seal gap. It is configured to be adjustable.

Japanese translation of PCT publication No. 2002-520562 JP 2000-97352 A

According to the sealing device for a rotary machine disclosed in Patent Document 1 and the self-adjusting seal of a turbo rotating machine disclosed in Patent Document 2, the width of the seal gap can be passively adjusted, but the width of the seal gap is active. Cannot be adjusted.
Moreover, although patent document 1 and patent document 2 are disclosing adjusting the width | variety of the sealing clearance gap formed by the sealing device arrange | positioned in the clearance gap between a rotation part and a stationary part, a rotation part and stationary It does not disclose until the width of the gap between the parts is adjusted.

  In view of the circumstances described above, the object of at least one embodiment of the present invention is to determine the size of the blade tip clearance between the rotating part and the stationary part formed outside the rotor blade in the radial direction of the rotor shaft. An object of the present invention is to provide a rotating machine that is variable by actively changing the outer diameter of the rotating machine.

(1) A rotating machine according to at least one embodiment of the present invention includes:
A housing;
A rotor shaft extending through the housing;
A plurality of stationary blades fixed to the housing;
A plurality of blades fixed to the rotor shaft;
A gap adjusting device capable of adjusting the size of a blade tip gap existing between the moving blade and the housing;
The gap adjusting device includes:
A plurality of electromagnets fixed to the housing and arranged in a circumferential direction of the rotor shaft;
The blades are attached to the tip portions of the plurality of rotor blades so as to be displaceable in the radial direction of the rotor shaft by the electromagnetic force generated by the electromagnet. A plurality of movable parts adjustable in size;
including.

  According to the above configuration (1), the movable part is displaced in the radial direction of the rotor shaft by the electromagnetic force generated by the electromagnet, thereby actively increasing the size of the blade tip gap between the moving blade and the housing. It can be adjusted. For this reason, the magnitude | size of a blade tip clearance gap can be adjusted according to the driving | running state of a rotary machine.

(2) In some embodiments, in the configuration (1),
Each of the plurality of movable parts is
A radially outer wall facing the tip of the rotor blade and the radial direction of the rotor shaft;
A pair of side walls that are continuous with the radially outer wall and are opposed to the tip of the rotor blade in the axial direction of the rotor shaft;
Have
According to the configuration (2), the radial outer wall can face each of the plurality of electromagnets in the radial direction of the rotor shaft, and the movable part can be attracted radially outward by the electromagnetic force generated by the electromagnet. It is. When the radial outer wall is sucked, the pair of side walls are also displaced outward in the radial direction, and the size of the blade tip gap can be reduced by the radial outer wall and the pair of side walls.

(3) In some embodiments, in the configuration (2),
The gap adjusting device further includes at least one elastic member disposed between each of the plurality of movable parts and each of the tip parts of the plurality of moving blades.
According to the configuration (3), the position of the movable part when the electromagnetic force of the electromagnet is not generated can be determined by the elastic member disposed between the movable part and the tip of the moving blade. Depending on the magnitude of the electromagnetic force generated by the electromagnet, the size of the blade tip gap can be determined.

(4) In some embodiments, in the configuration (2) or (3),
The gap adjusting device further includes at least one permanent magnet attached to each radially outer wall of the plurality of movable parts.
According to the configuration (4), the attraction force acting on the movable portion by the electromagnetic force of the electromagnet can be increased by the at least one permanent magnet attached to the radially outer wall of the movable portion. When a permanent magnet is used, the size of the blade tip gap can be adjusted using not only the attractive force between the permanent magnet and the electromagnet but also the repulsive force.

(5) In some embodiments, in any one of the configurations (1) to (4),
The gap adjusting device includes:
At least one sensor attached to the housing and capable of measuring the size of the tip clearance;
A control device capable of adjusting an electromagnetic force generated by the plurality of electromagnets based on a measurement result of the at least one sensor;
Is further included.
According to the configuration (5), since the control device can adjust the electromagnetic force generated by the electromagnet based on the measurement result of the sensor, the size of the blade tip clearance is determined according to, for example, the operating state of the rotating machine. Can be adjusted.

(6) In some embodiments, in the configuration (5),
The plurality of electromagnets are arranged in the circumferential direction of the rotor shaft in two rows spaced apart from each other in the axial direction of the rotor shaft,
The at least one sensor is disposed between the two rows in the axial direction of the rotor shaft.
According to the configuration (6), since the plurality of electromagnets are arranged in two rows and the sensor is arranged between the two rows, the movable portion is balanced radially outward by the plurality of electromagnets. The suction can be performed well, and the size of the blade tip gap can be reliably measured by the sensor.

(7) In some embodiments, in the configuration (5) or (6),
The at least one sensor includes a plurality of sensors arranged in a circumferential direction of the rotor shaft.
According to the configuration (7), by adjusting the electromagnetic force of each electromagnet according to the measurement results of the plurality of sensors, the size of the blade tip gap can be adjusted according to the circumferential position of the rotor shaft. As a result, for example, the size of the blade tip gap can be made uniform in the circumferential direction of the rotor shaft, and vibration of the rotor shaft can be suppressed. For example, when vibration of the rotor shaft is detected based on the measurement results of a plurality of sensors, the electromagnetic force of each electromagnet can be adjusted so as to suppress the vibration. Furthermore, for example, the rotor shaft may be bent by its own weight, but when detecting the bending of the rotor shaft based on the measurement results of a plurality of sensors, the electromagnetic force of each electromagnet may be adjusted so as to suppress the bending. it can.

  According to at least one embodiment of the present invention, the size of the blade tip gap between the rotating part and the stationary part formed on the outer side of the rotor blade in the radial direction of the rotor shaft is set to the active diameter of the rotating part. A rotating machine is provided that is variable by changing to.

It is a longitudinal section showing a schematic structure of a turbine concerning one embodiment of the present invention. It is a longitudinal cross-sectional view which expands and schematically shows a part of turbine of FIG. FIG. 3 is a schematic sectional view taken along line III-III in FIG. 2. It is a schematic longitudinal cross-sectional view of the area | region IV in FIG. 2, Comprising: It is a figure which shows a state when the electromagnet is generating the electromagnetic force. It is a schematic longitudinal cross-sectional view of the area | region IV in FIG. 2, Comprising: It is a figure which shows a state when an electromagnet is not generating the electromagnetic force. FIG. 4 is a schematic cross-sectional view of a region VI in FIG. 3. It is a longitudinal cross-sectional view equivalent to FIG. 4 of the turbine which concerns on other one Embodiment. It is a longitudinal cross-sectional view equivalent to FIG. 4 of the turbine which concerns on other one Embodiment. It is a longitudinal cross-sectional view equivalent to FIG. 4 of the turbine which concerns on other one Embodiment. FIG. 10 is a diagram illustrating a radially outer wall of a movable part in the turbine of FIG. It is a figure which expand | deploys and shows the radial direction outer wall of the movable part in the turbine which concerns on other one Embodiment. It is a figure for demonstrating the example of control of an electromagnet when using the arrangement | sequence of the permanent magnet shown in FIG.

Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of the components described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples. Absent.
For example, expressions expressing relative or absolute arrangements such as “in a certain direction”, “along a certain direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” are strictly In addition to such an arrangement, it is also possible to represent a state of relative displacement with an angle or a distance such that tolerance or the same function can be obtained.
For example, an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
For example, expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
On the other hand, the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of the other constituent elements.

FIG. 1 is a longitudinal sectional view showing a schematic configuration of a turbine 1A according to an embodiment of the present invention. FIG. 2 is an enlarged longitudinal sectional view schematically showing a part of the turbine 1A. FIG. 3 is a schematic cross-sectional view taken along line III-III in FIG. FIG. 4 is a schematic longitudinal sectional view of region IV in FIG. 2 and shows a state when the electromagnet does not generate electromagnetic force. FIG. 5 is a schematic longitudinal sectional view of a region IV in FIG. 2 and shows a state when the electromagnet generates an electromagnetic force. FIG. 6 is a schematic cross-sectional view of region VI in FIG. FIG. 7 is a longitudinal sectional view corresponding to FIG. 4 of a turbine 1B according to another embodiment. FIG. 8 is a longitudinal sectional view corresponding to FIG. 4 of a turbine 1C according to another embodiment. FIG. 9 is a longitudinal sectional view corresponding to FIG. 4 of a turbine 1D according to another embodiment. FIG. 10 is a developed view of the radially outer wall of the movable part in the turbine 1D of FIG. FIG. 11 is a developed view of the radially outer wall of the movable part in the turbine 1E according to another embodiment. FIG. 12 is a diagram for explaining an example of control of an electromagnet in the turbine 1E.
In the following description, the turbines 1A to 1E are also collectively referred to as the turbine 1.

  As shown in FIG. 1, the turbine 1 is a steam turbine applicable to, for example, combined cycle power generation, and is connected to a generator 3. The turbine 1 generates torque using steam, and the generator 3 generates power using the torque output from the turbine 1.

  The turbine 1 has a housing (cabinet) 5, a rotor shaft 7, a stationary blade row fixed to the housing 5, and a plurality of blade rows fixed to the rotor shaft 7. The rotor shaft 7 is supported by the journal bearing devices 9 and 10 and the thrust bearing device 11 so as to be rotatable around a horizontal axis, and at least a part of the rotor shaft 7 extends in the cylindrical housing 5, for example. The generator 3 is connected to one end side of the rotor shaft 7.

  A cylindrical internal flow path 12 is formed between the housing 5 and the rotor shaft 7, and a plurality of stationary blade rows and moving blade rows are arranged in the internal flow channel 12. Each stationary blade row includes a plurality of stationary blades 14 arranged in the circumferential direction of the rotor shaft 7, and each stationary blade 14 is fixed to the housing 5. Each moving blade row includes a plurality of moving blades 15 arranged in the circumferential direction of the rotor shaft 7, and each moving blade 15 is fixed to the rotor shaft 7. In each stationary blade row, the flow of steam is accelerated, and in each blade row, steam energy is converted into rotational energy of the rotor shaft 7.

In other words, the turbine 1 roughly includes a stationary part 17 and a rotating part 19 that can rotate relative to the stationary part 17, and the housing 5 and the stationary blade 14 constitute the stationary part 17, and the rotor shaft 7 and the rotor blade 15 constitute a rotating part 19.
The turbine 1 includes a high-pressure turbine 20, an intermediate-pressure turbine 22, and a low-pressure turbine 24, but all of the high-pressure turbine 20, the intermediate-pressure turbine 22, and the low-pressure turbine 24 are in relation to the stationary portion 17 and the stationary portion 17. And a rotating part 19 capable of relative rotation.

  As illustrated in FIGS. 2 to 9, the turbine 1 includes a gap adjusting device 26. The gap adjusting device 26 can adjust the size of a gap (blade end gap) EG existing between the moving blade 15 and the housing 5. The blade tip gap EG is a gap formed between the moving blade 15 and the housing 5 in the radial direction of the rotor shaft 7.

The gap adjusting device 26 has a plurality of electromagnets 28 and a plurality of movable parts 30.
The plurality of electromagnets 28 are each fixed to the housing 5 and arranged in the circumferential direction of the rotor shaft 7. The electromagnet 28 includes, for example, a core 32 and a coil 34 wound around the core 32, and can generate an electromagnetic force (magnetic flux) by energizing the coil 34.

  The plurality of movable portions 30 are respectively attached to the tip portions 31 of the plurality of moving blades 15 so as to be displaceable in the radial direction of the rotor shaft 7 by the electromagnetic force generated by the electromagnet 28. Specifically, a plurality of electromagnets 28 are attached to the region of the housing 5 that faces the movable portion 30. The plurality of movable parts 30 can adjust the size of the blade tip gap EG in accordance with the amount of displacement of each movable part 30 in the radial direction of the rotor shaft 7.

According to the above configuration, the size of the blade tip clearance EG existing between the moving blade 15 and the housing 5 is obtained by displacing the movable portion 30 in the radial direction of the rotor shaft 7 by the electromagnetic force generated by the electromagnet 28. Can be actively adjusted. For this reason, the size of the blade tip gap EG can be adjusted according to the operating state of the turbine 1.
The movable part 30 constitutes a part of the rotating part 19, and the outer diameter of the rotating part 19 can be changed by actively displacing the movable part 30 in the radial direction of the rotor shaft 7. Thus, the size of the blade tip gap EG can be adjusted.

  In some embodiments, as shown in FIGS. 4 to 9, each of the plurality of movable portions 30 has a radially outer wall 36 that faces the tip portion 31 of the rotor blade 15 and the rotor shaft 7 in the radial direction. . As shown in FIGS. 4, 5, and 7 to 9, each of the plurality of movable portions 30 is connected to the radial outer wall 36, so A pair of side walls (axial side walls) 38 facing each other are provided.

  According to the above configuration, the radial outer wall 36 can be opposed to each of the plurality of electromagnets 28 in the radial direction of the rotor shaft 7, and the movable portion 30 is moved radially outward by the electromagnetic force generated by the electromagnet 28. Suction is possible. When the radial outer wall 36 is sucked, the pair of side walls 38 are also displaced outward in the radial direction, and the size of the blade tip gap EG can be reduced by the radial outer wall 36 and the pair of side walls 38. .

For example, the tip 31 of the moving blade 15 is constituted by a shroud ring 40 formed integrally with the blade body of the moving blade 15. In a state where the plurality of moving blades 15 are arranged in the circumferential direction of the rotor shaft 7, the plurality of shroud rings 40 are arranged in the circumferential direction of the rotor shaft 7 corresponding to the arrangement of the moving blades 15.
Further, for example, the radial outer wall 36 has a plate shape curved along the circumferential direction of the rotor shaft 7, and the outer surface of the radial outer wall 36 defines the inner circumferential side of the blade tip gap EG.
Further, for example, each of the pair of side walls 38 has a fan-shaped plate shape, and is slidable in the radial direction of the rotor shaft 7 with respect to the side surface of the tip 31 of the opposed moving blade 15.

  In some embodiments, as shown in FIG. 6, each of the movable parts 30 is connected to the radial outer wall 36 and the side wall 38 and is opposed to the tip part 31 of the rotor blade 15 and the circumferential direction of the rotor shaft 7. Side wall (circumferential side wall) 42. For example, the pair of side walls 42 are disposed so as to be slidable in the radial direction of the rotor shaft 7 with respect to the side surface of the tip portion 31 of the opposed moving blade 15. In this case, the movable portion 30 has a cup shape that is slidably fitted in the radial direction of the rotor shaft 7 with respect to the tip portion 31 of the rotor blade 15.

In some embodiments, as illustrated in FIGS. 4 to 9, the gap adjusting device 26 is disposed between each of the plurality of movable portions 30 and each of the tip portions 31 of the plurality of moving blades 15. At least one elastic member 44 is further included. The elastic member 44 is disposed so as to allow the movable portion 30 to be displaced in the radial direction of the rotor shaft 7 in accordance with the magnitude of the electromagnetic force generated by the electromagnet 28.
According to the above configuration, the position of the movable portion 30 when the electromagnetic force of the electromagnet 28 is not generated is determined by the elastic member 44 disposed between the movable portion 30 and the tip portion 31 of the rotor blade 15. In addition, the size of the blade tip gap EG can be determined according to the magnitude of the electromagnetic force generated by the electromagnet 28.

For example, the elastic member 44 is configured by a metal spring. As the spring, a tension coil spring 44a as shown in FIGS. 4 to 6, 8, and 9, a compression coil spring 44b as shown in FIG. 7, or a leaf spring (not shown) can be used.
For example, when using the tension coil spring 44a, as shown in FIGS. 4 to 6, 8, and 9, the hollow portion 46 is formed over one or both of the tip portion 31 and the movable portion 30 of the moving blade 15. The distal end portion of the moving blade 15 and the movable portion 30 may be connected in the radial direction of the rotor shaft 7 by the tension coil spring 44 a provided and disposed in the cavity portion 46.
More specifically, as shown in FIGS. 4 to 6, 8, and 9, a recess 46 a is provided at the tip 31 of the moving blade 15, and the recess 46 a is formed by a tension coil spring 44 a disposed in the recess 46 a. The bottom and the radial outer wall 36 may be connected in the radial direction of the rotor shaft 7.

Further, for example, when the compression coil spring 44 b is used, as shown in FIG. 7, a cavity portion 48 is provided over one or both of the tip portion 31 and the movable portion 30 of the moving blade 15, and is arranged in the cavity portion 48. What is necessary is just to urge the movable part 30 toward the radial inside of the rotor shaft 7 by the compressed coil spring 44b.
More specifically, as shown in FIG. 7, an outward flange 50 may be provided at the tip portion 31 of the moving blade 15, and an inward flange 52 may be provided at the movable portion 30. The outward flange 50 and the inward flange 52 oppose each other in the radial direction of the rotor shaft 7, and the compression coil spring 44 b is disposed in a cavity 48 formed between the outward flange 50 and the inward flange 52. do it.

In some embodiments, the tension coil spring 44a is such that the amount of extension of the tension coil spring 44a is zero when the rotor shaft 7 is rated (for example, at 3600 rpm) compared to when the rotor shaft 7 is stopped. Is composed. That is, the tension coil spring 44 a is configured such that a tensile force that is about the same as the centrifugal force that acts on the movable portion 30 during the rated rotation of the rotor shaft 7 acts on the movable portion 30 when the rotor shaft 7 stops.
In some embodiments, the tension coil spring 44a is configured such that the extension amount of the tension coil spring 44a is larger at the rated rotation of the rotor shaft 7 than when the rotor shaft 7 is stopped.

In some embodiments, the gap adjusting device 26 further includes at least one permanent magnet 54 attached to each radial outer wall 36 of the plurality of movable parts 30 as shown in FIGS. 9 to 11. The permanent magnet 54 is attached to a region of the radial outer wall 36 that can face the electromagnet 28. For example, grooves or holes are formed in the radial outer wall 36 so that the outer surface of the permanent magnet 54 and the outer surface of the radial outer wall 36 are flush with each other, and the permanent magnet 54 is disposed in these grooves or holes.
According to the above configuration, the attraction force acting on the movable part 30 by the electromagnetic force of the electromagnet 28 can be increased by the at least one permanent magnet 54 attached to the radial outer wall 36 of the movable part 30. When the permanent magnet 54 is used, the size of the blade tip gap EG can be adjusted using not only the attractive force between the permanent magnet 54 and the electromagnet 28 but also the repulsive force.
The shape of the permanent magnet 54 is not particularly limited. For example, each permanent magnet 54 is configured such that its own N pole and S pole are arranged in the radial direction of the rotor shaft 7.

In some embodiments, the entire radial outer wall 36 of the movable part 30 is constituted by a permanent magnet.
Also with the above configuration, the entire radial outer wall 36 of the movable portion 30 is formed of a permanent magnet, so that the attractive force acting on the movable portion 30 by the electromagnetic force of the electromagnet 28 can be increased.

In some embodiments, the gap adjustment device 26 includes at least one sensor 56 and a control device 58 as shown in FIGS.
The sensor 56 is attached to the housing 5 and can measure the size of the blade tip gap EG. The sensor 56 is an optical sensor, for example, and can output a measurement result corresponding to the size of the blade tip gap EG.

  The control device 58 is configured by, for example, a computer and a power source, and can adjust the electromagnetic force generated by the plurality of electromagnets 28 based on the measurement result of the sensor 56. That is, the control device 58 adjusts the amount of current supplied to the electromagnet 28 and, if necessary, the direction of the current supplied to the electromagnet 28 so that the blade tip gap EG has a desired size. Is possible.

  According to the above configuration, since the control device 58 can adjust the electromagnetic force generated by the electromagnet 28 based on the measurement result of the sensor 56, the size of the blade tip clearance EG is determined according to, for example, the operation status of the turbine 1. Can be adjusted.

  In some embodiments, the plurality of electromagnets 28 are arranged in two rows spaced apart from one another in the axial direction of the rotor shaft 7, as shown in FIGS. 4, 5, and 7-9. They are arranged in the circumferential direction of the shaft 7. At least one sensor 56 is disposed between the two rows of electromagnets 28 in the axial direction of the rotor shaft 7.

  According to the above configuration, since the plurality of electromagnets 28 are arranged in two rows and the sensor 56 is disposed between the two rows, the movable portion 30 is moved radially outward by the plurality of electromagnets 28. The suction can be performed in a well-balanced manner, and the size of the blade tip gap EG can be reliably measured by the sensor 56.

  In some embodiments, corresponding to the plurality of electromagnets 28 being arranged in two rows, the plurality of permanent magnets 54 is formed on the rotor shaft 7 as shown in FIGS. They are arranged so as to form two rows spaced apart from each other in the axial direction. In this case, the positions of the two rows of the electromagnets 28 and the positions of the two rows of the permanent magnets 54 are matched in the axial direction of the rotor shaft 7.

In some embodiments, as shown in FIG. 10, the plurality of permanent magnets 54 are arranged such that the same pole faces the radially outer side of the rotor shaft 7.
In some embodiments, as shown in FIG. 11, the plurality of permanent magnets 54 are arranged in the circumferential direction of the rotor shaft 7 such that the poles facing radially outward are alternately opposite. .
According to the above configuration, as shown in FIG. 12, the direction of the current supplied to the electromagnet 28 is changed by alternating the magnetic poles of the electromagnet 28 according to the rotation angle of the rotor shaft 7. Thus, the movable portion 30 can be sucked forward in the rotational direction of the rotor shaft 7 while the movable portion 30 is sucked outward in the radial direction of the rotor shaft 7. For this reason, the moving blade 15 can be smoothly rotated by the electromagnetic force of the electromagnet 28.

In some embodiments, the at least one sensor 56 includes a plurality of sensors 56 arranged in the circumferential direction of the rotor shaft 7.
According to the above configuration, the size of the blade tip clearance EG can be adjusted according to the circumferential position of the rotor shaft 7 by adjusting the electromagnetic force of each electromagnet 28 according to the measurement results of the plurality of sensors 56. . As a result, for example, the size of the blade tip gap EG can be made uniform in the circumferential direction of the rotor shaft 7, and vibration of the rotor shaft 7 can be suppressed. For example, when the vibration of the rotor shaft 7 is detected based on the measurement results of the plurality of sensors 56, the electromagnetic force of each electromagnet 28 can be adjusted so as to suppress the vibration. Further, for example, the rotor shaft 7 may be bent by its own weight, but when detecting the bending of the rotor shaft 7 based on the measurement results of the plurality of sensors 56, the electromagnetic force of each electromagnet 28 is controlled so as to suppress the bending. Can be adjusted. In this case, the bending of the rotor shaft 7 is indirectly suppressed by applying a force that corrects the bending to the rotor shaft 7 via the movable portion 30 and the elastic member 44 by the electromagnetic force. it can.

In some embodiments, as shown in FIG. 8, at least one seal fin 60 may be disposed in the blade tip gap EG.
The seal fin 60 has an annular plate shape, and the inner peripheral edge of the seal fin 60 faces the movable portion 30 in the radial direction of the rotor shaft 7 with a seal gap SG.
According to the above configuration, the size of the seal gap SG can be adjusted by adjusting the electromagnetic force of the electromagnet 28.
In the case where the seal fin 60 is disposed in the blade tip gap EG, the seal fin 60 can be fixed to the housing 5 via a pedestal 62, for example. In this case, if necessary, the sensor 56 may be arranged so as to be able to measure the size of the blade tip gap EG through the pedestal 62. Or you may arrange | position the electromagnet 28 so that the base 62 may be penetrated and the movable part 30 may be opposed.

  The present invention is not limited to the above-described embodiments, and includes forms obtained by changing the above-described embodiments and forms obtained by combining these forms.

For example, the turbine to which the present invention is applied is not limited to a turbine applicable to combined cycle power generation. Moreover, the turbine to which the present invention is applied is not limited to a steam turbine, and may be a gas turbine. Furthermore, the present invention is applicable to rotating machines other than turbines. Therefore, the working fluid is not limited to steam.
Further, for example, the gap adjusting device 26 can be applied to any of the plurality of moving blade rows, but is applied to the moving blade row in the last paragraph in which the moving amount of the moving blade 15 is relatively large. Is preferred.

1,1A-1E Turbine 3 Generator 5 Housing (cabinet)
7 Rotor shafts 9 and 10 Journal bearing device 11 Thrust bearing device 12 Internal flow path 14 Stator blade 15 Rotor blade 17 Static portion 19 Rotating portion 20 High-pressure turbine 22 Medium-pressure turbine 24 Low-pressure turbine 26 Gap adjusting device 28 Electromagnet 30 Movable portion 31 Blade tip 32 Core 34 Coil 36 Radial outer wall 38 Side wall (Axial side wall)
40 shroud ring 42 side wall (circumferential side wall)
44 elastic member 44a tension coil spring 44b compression coil spring 46 cavity 46a recess 48 cavity 50 outward flange 52 inward flange 54 permanent magnet 56 sensor 58 controller 60 seal fin 62 base EG blade tip clearance SG seal clearance

Claims (7)

A housing;
A rotor shaft extending through the housing;
A plurality of stationary blades fixed to the housing;
A plurality of blades fixed to the rotor shaft;
A gap adjusting device capable of adjusting the size of a blade tip gap existing between the moving blade and the housing;
The gap adjusting device includes:
A plurality of electromagnets fixed to the housing and arranged in a circumferential direction of the rotor shaft;
The blades are attached to the tip portions of the plurality of rotor blades so as to be displaceable in the radial direction of the rotor shaft by the electromagnetic force generated by the electromagnet. A plurality of movable parts adjustable in size;
A rotating machine comprising: Each of the plurality of movable parts is
A radially outer wall facing the tip of the rotor blade and the radial direction of the rotor shaft;
A pair of side walls that are continuous with the radially outer wall and are opposed to the tip of the rotor blade in the axial direction of the rotor shaft;
The rotating machine according to claim 1, comprising:   The said clearance gap adjustment apparatus further contains at least 1 elastic member arrange | positioned between each of these movable parts, and each of the front-end | tip part of these moving blades. Rotating machine.   The rotating machine according to claim 2, wherein the gap adjusting device further includes at least one permanent magnet attached to each radially outer wall of the plurality of movable parts. The gap adjusting device includes:
At least one sensor attached to the housing and capable of measuring the size of the tip clearance;
A control device capable of adjusting an electromagnetic force generated by the plurality of electromagnets based on a measurement result of the at least one sensor;
The rotating machine according to claim 1, further comprising: The plurality of electromagnets are arranged in the circumferential direction of the rotor shaft in two rows spaced apart from each other in the axial direction of the rotor shaft,
The rotating machine according to claim 5, wherein the at least one sensor is disposed between the two rows in an axial direction of the rotor shaft.   The rotating machine according to claim 5 or 6, wherein the at least one sensor includes a plurality of sensors arranged in a circumferential direction of the rotor shaft.

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