JP2012122545A - Torsional vibration control device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a torsional vibration control device which changes liquid loads without special electric control and effectively controls the torsional vibration by automatically changing the state under the load from the liquid when the rotational direction of a disk is forward/backward.SOLUTION: The torsional vibration control device for attenuating the torsional vibration of a rotary shaft from which the torsional vibration occurs, includes: a disk 11 fixed to the rotary shaft; a casing which covers the entire disk and in which a fluid R is sealed; a movable body 13 stored in a recess 14 formed in an end face of the disk 11 in a projecting/retracting manner; and an urging member 16 for urging the movable body 13 to the outside of the recess 14. The movable body 13 has a first pressure-receiving surface 13a for receiving the pressure from the fluid R so that the movable body 13 is absorbed in the recess 14 against the urging force of the urging member 16 when the rotary shaft is rotated to one side, and a second pressure-receiving surface 13b for receiving the pressure in the tangential direction of the rotary shaft from the fluid R when the rotary shaft is rotated to the other side.

Description

  The present invention includes, for example, a driving-side rotating body and a driven-side rotating body on the same rotating shaft, and is caused by a load from the driven-side rotating body between the driving-side rotating body and the driven-side rotating body. The present invention relates to a torsional vibration damping device that suppresses torsional vibration when torsional vibration occurs.

Conventionally, for example, in an apparatus including a turbine as a driving-side rotating body and a generator as a driven-side rotating body arranged on the same rotating shaft, the rotating shaft between the turbine and the generator is connected to the rotating shaft from the generator. Torsional vibration may occur due to the load.
In Patent Document 1, in a device in which such torsional vibration is generated, a direct current component of back electromotive force and an alternating current waveform component due to torsional vibration are separated by a control device, and an alternating current waveform component due to this separated torsional vibration is extracted. A technique is disclosed in which a torsional vibration component is controlled to be canceled by inputting a signal pressure whose phase is inverted by 180 °, that is, whose sign is inverted, to an electric motor.

JP 09-329191 A

However, the conventional techniques for controlling torsional vibrations have the following problems.
That is, it is effective for relatively small rotating shafts such as a crankshaft and a camshaft that perform reciprocating motions, such as a two-cycle engine, but for example, torsional vibration generated between a turbine and a generator. There was a problem of being unsuitable.
More specifically, when a turbine and a generator are provided on the same rotating shaft, and when generating power on the generator side by applying rotational torque on the turbine side, a load for power generation is applied on the generator side. The rotating shaft is in a state where a force in the direction opposite to the rotating direction is applied. Here, the generator may momentarily remove this load, and the torsional vibration is generated on the rotating shaft at the moment when this load is removed.
Therefore, there is a problem that it is very difficult to specifically control the direct current component and the alternating current component caused by torsional vibration.
Furthermore, recent turbines tend to be larger, and the portion connecting the turbine and the generator is relatively thin, so the load due to torsional vibration tends to concentrate on the narrow portion, so it is simply 180 ° inverted. There is a problem that the torsional vibration cannot be effectively canceled by the control in which the received signal pressure is input to the generator side.

  The present invention has been made in view of the above-described problems, and is a torsional vibration capable of effectively suppressing a torsional vibration that occurs instantaneously on a rotating shaft while having a simple and inexpensive configuration. An object is to provide a vibration damping device.

  In order to achieve the above object, a torsional vibration damping device according to the present invention is a torsional vibration damping device that attenuates torsional vibration of a rotating shaft, and includes a disk fixed to the rotating shaft and the entire disk. A casing that covers and encloses a fluid; a movable body that is retractably housed in a recess formed in an end surface of the disk; and a biasing member that biases the movable body toward the outside of the recess. The movable body has a first pressure receiving surface that receives pressure from the fluid so as to be immersed in the recess against the urging force of the urging member when the rotating shaft rotates to one side. And a second pressure receiving surface that receives pressure from the fluid in a tangential direction of the rotating shaft when the rotating shaft rotates to the other side.

  In the present invention, by automatically switching the state in response to the load from the fluid depending on the rotation direction of the disk, the fluid load can be switched without special electrical control, and the torsional vibration is effectively suppressed. be able to.

  Further, in the torsional vibration damping device according to the present invention, the first pressure receiving surface has a fluid flow direction when the rotating shaft rotates to one side with the movable body protruding from the recess. The torsional vibration damping device according to claim 1, further comprising an inclined surface that gradually separates from an end surface of the disk.

  In the present invention, the protrusion of the movable body to the outside of the recess when the rotation direction of the disk is switched is promoted by the second pressure receiving surface. In addition, since the fluid load can be increased in a wide range from the second pressure receiving surface to the inside of the recess, the torsional vibration can be easily controlled even when the torsional vibration load is large.

  Further, in the torsional vibration damping device according to the present invention, the second pressure receiving surface is perpendicular to the end surface of the disk or the rotation shaft rotates to the other side with the movable body protruding from the recess. And a primary surface gradually approaching the end surface of the disk along the fluid flow direction.

  According to such a configuration, the force that the primary surface of the second pressure receiving surface receives from the fluid has a component component in the direction of the urging force that the movable body receives from the urging member. Thereby, the protrusion operation | movement outside the recessed part of a movable body is accelerated | stimulated.

  In the torsional vibration damping device according to the present invention, the second pressure-receiving surface may be along a fluid flow direction when the rotating shaft rotates to the other side on the projecting side of the movable body on the primary surface. And a secondary surface that is gently inclined from the primary surface.

  According to such a configuration, the force received from the fluid by the secondary surface provided on the projecting side of the movable body from the primary surface also has a component component in the direction of the urging force that the movable body receives from the urging member. The magnitude is larger than the force that the primary surface receives from the fluid. Accordingly, the protruding operation of the movable body out of the recess is further promoted.

  According to the torsional vibration damping device of the present invention, the immersion of the movable body into the concave portion or the protrusion outside the concave portion is automatically switched by using the load from the fluid depending on the rotation direction of the disk. The fluid load can be switched without electrical control, and the torsional vibration can be effectively suppressed.

1 shows an example of a torsional vibration damping device according to the present invention, (A) is a schematic diagram showing a turbine generator plant equipped with the torsional vibration damping device of the present invention, and (B) shows a load change when torsional vibration occurs. FIG. 1 shows a torsional vibration damping device according to a first embodiment of the present invention, in which (A) is a longitudinal sectional view of the torsional vibration damping device during normal disk rotation, and (B) is a torsional vibration damping during disk reverse rotation. It is a longitudinal cross-sectional view of an apparatus. 1 shows a torsional vibration damping device according to a first embodiment of the present invention and is a front view of a disk. FIG. 1 shows a torsional vibration damping device according to a first embodiment of the present invention, (A) is an explanatory view of a main part showing a state of a movable body during normal rotation of the disk, and (B) is a movable body during reverse rotation of the disk. It is explanatory drawing of the principal part which shows the state. FIG. 2 shows a torsional vibration damping device according to a second embodiment of the present invention, in which (A) is an explanatory view of the main part showing the state of the movable body during normal rotation of the disk, and (B) is the movable body during reverse rotation of the disk It is explanatory drawing of the principal part which shows the state. FIG. 6 shows a torsional vibration damping device according to a third embodiment of the present invention, where (A) is an explanatory view of the main part showing the state of the movable body during normal rotation of the disk, and (B) is the movable body during reverse rotation of the disk. It is explanatory drawing of the principal part which shows the state.

  Hereinafter, a torsional vibration damping device according to an embodiment of the present invention is applied to a turbine generator plant and described with reference to the drawings. The following embodiments are preferred specific examples of the torsional vibration damping device of the present invention, and may have various technically preferable limitations, but the technical scope of the present invention is particularly limited. As long as there is no description which limits this invention, it is not limited to these aspects. In addition, the constituent elements in the embodiments shown below can be appropriately replaced with existing constituent elements and the like, and various variations including combinations with other existing constituent elements are possible. Therefore, the description of the embodiment described below does not limit the contents of the invention described in the claims.

As shown in FIG. 1 (A), the torsional vibration damping device 10 of the present invention enables, for example, a high-pressure steam turbine 20 and a generator 21 to rotate coaxially via a turbine shaft 22 and a generator shaft 23. It is provided and applied to a turbine generator plant 24 in which the rotational force of the steam turbine 20 is transmitted to the generator 21 by a clutch mechanism (not shown).
In the present embodiment, the torsional vibration damping device 10 is the turbine 20 side where a load that causes torsional vibration is likely to occur among the generator shafts 23 (rotating shafts) extending on both sides of the generator 21. Although the torsional vibration damping device 10 is provided on the generator shaft 23, the installation position is not limited.

  Since the generator 21 is loaded for power generation, a load in the direction opposite to the forward rotation direction of the turbine 20 is generated. The torsion is generated particularly on the generator shaft 23 side due to the load in the reverse rotation direction of the generator 21 during the forward rotation of the turbine 20. Further, the generator 21 may momentarily remove the load for power generation.

  As a result, as shown in FIG. 1B, the generator shaft 23 instantaneously has a no-load state, and then a load due to power generation is applied again. In the graph of FIG. 1B, the load before and after the no-load state is at the same level, but strictly speaking, the load applied to the generator shaft 23 is the no load on the generator shaft 23 in the twisted state. Therefore, when a reverse force is applied to the generator shaft 23 again from the no-load state, the load increases in a counter manner. As a result, the generator shaft 23 is easily damaged.

  Therefore, the torsional vibration damping device 10 of the present invention attenuates the rotational force when a force in the reverse rotation direction is applied to the generator shaft 23 after this no-load state is reached, and thereby suppresses the torsional vibration. .

(First embodiment)
As shown in FIG. 2, the torsional vibration damping device according to the first embodiment (hereinafter referred to as “torsional vibration damping device 10 </ b> A”) is arranged in the middle of the generator shaft 23, and the generator 21 is arranged. A disk-shaped disk 11 fixed to a generator shaft 23 that is a rotating shaft on the side (left side in the figure), a casing 12 that covers the entire disk 11 in a hermetically sealed manner and encloses a fluid R therein, and a disk 11 is provided with a movable body 13 provided on the end face of 11.

  The disk 11 is made of a metal that is not easily corroded and has high rigidity, and a generator shaft 23 is inserted and fixed at the center thereof. Further, as shown in FIG. 3, a plurality of recesses 14 are formed on the end surface of the disk 11 at predetermined intervals in the circumferential direction.

  The casing 12 is made of a metal that is not easily corroded and has high rigidity, and the generator shaft 23 passes through the center of the casing 12. By sealing this through portion with a seal or the like, the internal sealing performance is secured. ing. In addition, as the fluid R enclosed in the casing 12, oil with high viscosity (for example, so-called machine oil) that prevents corrosion of the disk 11 and the casing 12 is used.

  As shown in FIGS. 3 and 4, the movable body 13 is a columnar member having a square cross section, and the length thereof is slightly shorter than the radial width of the recess. The movable body 13 is surrounded by a first pressure receiving surface 13a, a second pressure receiving surface 13b, and a mounting surface 13c. Here, the first pressure receiving surface 13a and the second pressure receiving surface 13b form an acute angle with each other. Further, the second pressure receiving surface 13b and the mounting surface 13c form an obtuse angle. The first pressure receiving surface 13a and the mounting surface 13c form an acute angle with each other.

  Further, as shown in FIG. 4, the second pressure receiving surface 13b has a primary surface 13d that forms an obtuse angle with the mounting surface 13c, and a secondary surface 13e that forms an acute angle with the first pressure receiving surface 13a. Yes. The primary surface 13d and the secondary surface 13e form an obtuse angle.

  The movable body 13 configured as described above is rotatably supported by the rotation shaft 15. Specifically, as shown in FIG. 3, a rotation shaft 15 is provided inside the recess 14 so as to extend in the radial direction of the disk 11, and both end portions thereof are fixed to the inner wall surface of the recess 14. As shown in FIG. 4, the movable body 13 has the rotating shaft 15 inserted through the corner formed by the first pressure receiving surface 13 a and the mounting surface 13 c with the mounting surface 13 c facing the concave portion 14. Has been. As a result, the movable body 13 is rotatable about the rotating shaft 15 so as to be immersed in the recess 14 or projecting out of the recess 14.

  Further, as shown in FIG. 4, the movable body 13 is urged toward the outside of the recess 14 by the urging member 16. Specifically, one end of the biasing member 16 that is a coil spring is fixed to the bottom of the recess 14, and the other end is fixed to a position on the second pressure receiving surface 13 b side of the mounting surface 13 c of the movable body 13. As a result, as shown in FIG. 4B, in a state where no external force is applied, the movable body 13 protrudes out of the recess 14 by rotating around the rotating shaft 15 by the urging force received from the urging member 16. It has become a state.

  At this time, the first pressure receiving surface 13a is inclined so as to be gradually separated from the end surface of the disk 11 from the mounting surface 13c side toward the second pressure receiving surface 13b side. At this time, the primary surface 13d of the second pressure receiving surface 13b is inclined so as to gradually approach the end surface of the disk 11 from the mounting surface 13c side toward the first pressure receiving surface 13a side. Further, at this time, the secondary surface 13e of the second pressure receiving surface 13b is gradually closer to the end surface of the disk from the primary surface 13d side toward the first pressure receiving surface 13a side, and more gently than the primary surface 13d. It is in an inclined state.

  In the above configuration, when the disk 11 rotates in the normal rotation direction S shown in FIG. 4A, that is, when the generator shaft 23 rotates in the normal direction, the first pressure receiving surface 13a receives pressure from the fluid R. As a result, the movable body 13 rotates counterclockwise in FIG. 4A with the rotating shaft 15 as a fulcrum, and the first pressure receiving surface 13a and the end surface of the disk 11 are substantially flush with each other in the recess 14. Immerse yourself in. Accordingly, the disk 11 rotates in the forward rotation direction in a low load state.

On the other hand, when the disk 11 rotates in the reverse rotation direction G shown in FIG. 4B, the second pressure receiving surface 13b receives pressure from the fluid R. As a result, the movable body 13 pivots clockwise in FIG. 4B with the rotating shaft 15 as a fulcrum, and protrudes out of the recess 14 so as to receive the pressure from the fluid R over substantially the entire second pressure receiving surface 13b. To do.
At this time, the force received from the fluid R by the second pressure receiving surface 13 b of the movable body 13 has a component component in the direction of the urging force received from the urging member 16. Therefore, the protrusion of the movable body 13 to the outside of the concave portion 14 is promoted.
Further, the second pressure receiving surface 13b is provided with a secondary surface 13e, and the force received by the secondary surface 13e from the fluid R is larger than the force received by the primary surface 13d from the fluid R. The component component in the direction of the urging force received from 16 increases. Thereby, the protrusion of the movable body 13 to the outside of the concave portion 14 is further promoted.

As described above, in the present invention, the movable body 13 that receives the pressure from the fluid is switched from the state of being immersed in the concave portion 14 to the state of protruding out of the concave portion 14 depending on the rotation direction of the disk 11. Without changing the fluid load state.
Further, since the movable body 13 is buried in the recess 14 against the urging of the urging member 16 by the pressure from the fluid received by the first pressure receiving surface 13a during the normal rotation of the disk 11, the fluid load is low. The disk 11 can be rotated. On the other hand, when the disk 11 is rotated in the reverse direction, the movable body 13 instantaneously protrudes from the recess 14 due to the urging of the urging member 16 in addition to the pressure from the fluid received by the second pressure receiving surface 13b, and the disk is in a state where the fluid load is large. 11 can be rotated, and torsional vibration can be effectively suppressed.

  Next, another embodiment of the torsional vibration damping device of the present invention will be described with reference to the accompanying drawings. The same reference numerals are used for members and parts that are the same as or similar to those in the first embodiment. A description will be omitted, and a configuration different from that of the first embodiment will be described.

(Second Embodiment)
As shown in FIG. 5, in the torsional vibration damping device (torsional vibration damping device 10B) according to the second embodiment, the shaft 15 shown in the first embodiment is abolished, and the movable body 13 is moved into the recess 14. To project in a direction substantially perpendicular to the end surface of the disk 11.

Specifically, a plurality of guide grooves 14 a extending linearly from the bottom surface toward the open end side are formed on the side wall of the recess 14, and the movable body 13 is engaged with the guide grooves 14 a. A protrusion 13c is formed.
As a result, when the disk 11 rotates in the forward rotation direction S, that is, when the generator shaft 23 rotates forward, the first pressure receiving surface 13a receives pressure from the fluid as shown in FIG. Is immersed in the recess 14. Accordingly, the disk 11 rotates in the forward rotation direction in a low load state.

  On the other hand, when the disk 11 rotates in the reverse rotation direction G, as shown in FIG. 5 (B), the second pressure receiving surface 13b receives pressure from the fluid so that substantially the entire second pressure receiving surface 13b receives a fluid load. Furthermore, the movable body 13 protrudes out of the recess 14. At this time, since the fluid load on the first pressure receiving surface 13a is reduced and the urging force of the urging member 16 is superior, the state change in which the movable body 13 protrudes from the recess 14 is promoted. Therefore, the disk 11 rotates in the reverse rotation direction under a high load state.

  By adjusting the length and shape of the guide groove 14a and the urging position (and urging force) of the urging member 15, the displacement amount on the apex side of the movable body 13 and the displacement amount on the second pressure receiving surface 13b side are obtained. In this second embodiment as well, as shown in FIG. 4A of the first embodiment, the first pressure receiving surface 13a is substantially flush with the end surface of the disk 11. It becomes possible.

(Third embodiment)
As shown in FIG. 6, the torsional vibration damping device (torsional vibration damping device 10 </ b> C) according to the third embodiment is obtained by eliminating the recess 14 shown in the first and second embodiments. .

  Specifically, the disk 31 is a simple flat disk. A flat plate-like movable body 33 is rotatably provided on the end surface of the disk 31 via a pair of leg portions 32.

The movable body 33 is rotatably supported by the leg portion 32 via a shaft 34 on one end side that is in the forward direction with the forward rotation direction S of the disk 11.
As a result, in this embodiment, the movable body 33, as shown in FIG. 6 (A), has one surface of the disk 31 that is difficult to receive a load from the fluid R when the disk 31 rotates in the forward direction. As shown in FIG. 6B, the substantially parallel first state and the load from the fluid R when the disk 31 rotates in the opposite direction are more affected by the load from the fluid R than in the first state. The structure which switches to the 2nd state which stood up easily which is easy to receive is employ | adopted.
In the second state of the movable body 33, it is possible to set an upright angle formed by one surface by bringing the end of the disk 31 in the forward rotation direction and the forward direction into contact with one surface of the disk 31. .

  According to such a configuration, it is possible to realize a change in the state of the fluid load of the movable body 33 when the disk 31 rotates forward and backward with a simpler and less expensive configuration.

The embodiment of the torsional vibration damping device 10 according to the present invention has been described above. However, the present invention is not limited to the above-described embodiment, and can be appropriately changed without departing from the spirit of the present invention.
For example, in the above embodiment, the turbine generator plant 24 in which one turbine 21 is arranged is disclosed. However, in a large power generation system, in many cases, two or more steam turbines are arranged in series or in parallel to generate power. Since the machine is often driven to generate electric power, it can be applied to a type in which a plurality of steam turbines (high pressure, low pressure, etc.) are connected to drive a generator.
Of course, the present invention can be applied to all rotating shafts that generate torsional vibration other than the turbine generator plant 24.

DESCRIPTION OF SYMBOLS 10 Torsional vibration damping device 11 Disk 12 Casing 13 Movable body 13a 1st pressure receiving surface 13b 2nd pressure receiving surface 13c Mounting surface 13d Primary surface 13e Secondary surface 14 Recessed part 15 Rotating shaft 16 Energizing member 23 Generator shaft (Rotating shaft)

Claims (4)

A torsional vibration damping device that attenuates torsional vibration of a rotating shaft,
A disk fixed to the rotating shaft;
A casing covering the entire disk and enclosing a fluid therein;
A movable body slidably housed in a recess formed on the end surface of the disk;
A biasing member that biases the movable body toward the outside of the recess,
The movable body has a first pressure receiving surface that receives pressure from the fluid so as to be immersed in the recess against the urging force of the urging member when the rotating shaft rotates to one side, A torsional vibration damping device having a second pressure receiving surface that receives pressure from the fluid in a tangential direction of the rotating shaft when the rotating shaft rotates to the other side.   The first pressure receiving surface has an inclined surface that gradually separates from the end surface of the disk along the fluid flow direction when the rotating shaft rotates to one side with the movable body protruding from the recess. The torsional vibration damping device according to claim 1, wherein:   The second pressure-receiving surface is perpendicular to the end surface of the disc or the end surface of the disc along the fluid flow direction when the rotating shaft rotates to the other side with the movable body protruding from the recess. The torsional vibration damping device according to claim 1, further comprising a primary surface that gradually approaches.   The second pressure receiving surface is a secondary surface that is gently inclined from the primary surface along the fluid flow direction when the rotating shaft rotates to the other side on the projecting side of the movable body on the primary surface. The torsional vibration damping device according to claim 3.

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