JP2013148186A - Torsional dynamic vibration absorber and rotary electric machine - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress a plurality of torsional natural frequencies by changing vibration characteristics of a torsional dynamic vibration absorber.SOLUTION: A torsional dynamic vibration absorber 1 includes: a first flange that is attached to an axis member 2 and where a first axial hole 22 is formed along in a circumferential direction; a second flange that is disposed to form an axial gap in the first flange and where a second axial hole is formed in a position facing the first axial hole 22; a magnetic member 14 that is disposed to forme a specific radial direction gap in the axis member 2 so that one end is in the first axial hole 22 and the other end is in the second axial hole; an elastic member 10 that is deformable in a circumferential direction and supports the magnetic member 14; a coil 41 that is disposed outside in a radial direction of the magnetic member 14 in the axial direction gap; and a power supply device 45 for supplying current to the coil 41.

Description

  Embodiments described herein relate generally to a torsional vibration absorber and a rotating electrical machine using the torsional vibration absorber.

  In a steam turbine generator, a steam turbine rotor and a generator rotor are coupled by a coupling. Each rotor is supported by a journal bearing with low friction loss using the load capacity of the lubricating oil film.

  Since the shaft system of large rotating machinery such as steam turbine generators is heavy and heavy, there are many torsional natural vibrations of the rotor within the operating speed or operating frequency range (both are collectively referred to as the operating frequency range). There are many cases. For example, in the primary torsional vibration mode, each rotor is in a torsional vibration mode (vibration form) in which a large torsional angle deformation occurs in the journal portion that supports both rotors without undergoing torsional deformation. In the second-order or higher-order torsional vibration mode, a torsional vibration mode having a node at the center of each rotor appears.

  As described above, the large rotating body is levitated and supported by the journal bearing, so the resistance to the rotational tangential direction of the shaft is small, the damping of the torsional vibration mode of the shaft is small, and when vibration starts, the vibration will continue for a long time. Persists.

  When the natural frequency and the frequency of forced external force (generator frequency disturbance, motor torque ripple, etc.) match, a resonance state is reached. In this case, the damping is very small, resulting in a large vibration, which may damage the shaft.

  A dynamic vibration absorber is used as a means for reducing the vibration of the structure. A generally used dynamic vibration absorber is composed of a vibration system including a mass and an elastic body. By making the natural frequency of the vibration system coincide with the basic natural frequency (lowest natural frequency) of the target structure, resonance between the excitation force and the basic natural frequency can be avoided. Basically, a vibration system with one degree of freedom is targeted for vibration suppression.

  However, in a complex structure such as a rotating machine in which the vibration frequency changes, it is necessary to reduce vibrations generated at a plurality of natural frequencies. Development of a dynamic vibration absorber corresponding to a plurality of natural frequencies existing in a wide frequency range, that is, a dynamic vibration absorber considering a multi-degree-of-freedom system is demanded.

JP-A-10-19088

  A dynamic vibration absorber that reduces torsional vibrations of a rotating shaft has already been generally applied, and a dynamic vibration absorber or device constituted by a vibration system is added to a shaft joint or the like. Normally, the optimum design of the torsional vibration absorber is made to act as a dynamic vibration absorber by attaching a vibration system having the same frequency as the natural frequency of the main system (in the case of a rotating shaft, the torsional natural frequency of the rotating body). Therefore, a single dynamic vibration absorber can effectively work in only one vibration mode, and a rotating body that has multiple torsional natural vibration modes within the operating frequency, such as a large rotating machine, has those vibration modes. It is necessary to install multiple torsional vibration absorbers.

  Therefore, when a plurality of dynamic vibration absorbers cannot be attached to the rotating shaft, means for avoiding operation near the torsional natural frequency is taken, which hinders efficient operation of the rotating machine.

  In addition, by attaching a plurality of dynamic vibration absorbers, it is necessary to make the rotating shaft more complicated and further extend the shaft length, which may impair reliability.

  An embodiment of the present invention is to solve the above-described problems, and an object thereof is to enable suppression of vibrations having a plurality of torsional natural frequencies by changing vibration characteristics of the torsional vibration absorber. .

  To achieve the above object, a torsional vibration absorber according to the present invention is attached to the shaft member so as to surround a shaft member rotating around a shaft extending in a predetermined direction from the outside in the radial direction, and rotates together with the shaft member. A first flange having a plurality of first axial holes each having a predetermined axial depth at a first axial end face facing in an axial direction and spaced apart from each other in the circumferential direction. And a plate-like shape that is arranged to form a predetermined axial gap in the first flange, is attached to the shaft member so as to surround the shaft member from the outside in the radial direction, and rotates together with the shaft member, A second flange in which a second axial hole is formed at each of the positions facing the first axial hole on the second axial end surface on the side facing the first axial end surface; The axial end of the first axial direction A magnetic member disposed so that an opposite axial end portion is in the second axial hole and forming a predetermined radial gap in the shaft member, and the first shaft An elastic member attached to the directional hole, elastically deformable in the circumferential direction and configured to support the magnetic member, and a coil disposed radially outward of the magnetic member in the axial gap; And a power supply device that is electrically connected to the coil and allows a current to flow through the coil.

  Further, the torsional vibration absorber according to the present invention is a plate-like shape that is attached to the shaft member so as to surround the shaft member rotating around the shaft extending in a predetermined direction from the outside in the radial direction and rotates together with the shaft member, A plurality of axial holes are formed in the axial end surface facing the axial direction at intervals in the circumferential direction along the circumferential direction, and a notch is formed in the circumferential interval, and in the axial hole An arranged magnetic member, an elastic member attached to the axial hole, elastically deformable in the circumferential direction and configured to support the magnetic member, and arranged radially outside each magnetic member And a coil wound around the iron core, and a power supply device that is electrically connected to the coil and allows a current to flow through the coil.

  A rotating electrical machine according to an embodiment of the present invention surrounds a shaft member rotating around a shaft extending in a predetermined direction, a torsional vibration absorber attached to the shaft member, and the shaft member from the outside in the radial direction. In a rotating electrical machine comprising: a rotor configured to be coaxially rotated with the shaft member; and a stator that surrounds the rotor while forming a predetermined gap in a circumferential surface of the rotor. The torsional vibration absorber is a plate-like shape that is attached to the shaft member so as to surround the shaft member from the outside in the radial direction and rotates together with the shaft member, and has a predetermined axial direction on each first axial end surface facing the axial direction. A plurality of first axial holes having a depth are arranged so as to form a predetermined axial gap in the first flange, the first flange having a circumferential interval along the circumferential direction, The shaft member A plate that is attached to the shaft member so as to surround from the outer side in the radial direction and rotates together with the shaft member. The second axial end surface on the side facing the first axial end surface faces the first axial hole. A second flange having a second axial hole formed at each of the positions, and extending in the axial direction, with one axial end in the first axial hole and the opposite axial end in the second A magnetic member arranged to be in the axial hole, an elastic member attached to the first axial hole, elastically deformable in a circumferential direction, and configured to support the axial member; It has a coil which is arranged on the outside in the radial direction of the magnetic member in the axial gap and through which a predetermined current flows, and a power supply device for flowing a current through the coil.

  According to the embodiment of the present invention, it is possible to suppress vibrations at a plurality of torsional natural frequencies by changing the vibration characteristics of the torsional vibration absorber.

1 is a schematic side view of a rotating electrical machine according to a first embodiment of the present invention. It is a front view of the torsional vibration damper of FIG. It is a side view of the torsional vibration absorber of FIG. FIG. 4 is a partial front view showing the vicinity of the vibrator of FIG. 3 partially enlarged. It is a schematic perspective view of a general dynamic vibration absorber or the like. 5 is a graph showing the vibration response of the dynamic vibration absorber of FIG. 5 when the rotational speed of the rotating body of FIG. 5 is changed, with the horizontal axis representing frequency and the vertical axis representing vibration intensity. 5 is a graph showing the natural frequency such as ω1 in FIG. It is a schematic side view of the torsional vibration damper of the second embodiment according to the present invention. It is a schematic front view of the torsional vibration damper of 3rd Embodiment which concerns on this invention. FIG. 10 is a schematic top view showing the vibrator, the leaf spring, and the like of FIG. It is a graph which shows the strength of the magnetic field which generate | occur | produces in the torsional vibration damper of 4th Embodiment which concerns on this invention. It is a partial front view which shows the vibrator | oscillator vicinity of the torsional vibration damper of 5th Embodiment which concerns on this invention. It is a partial front view which shows the airtight container of the torsional vibration damper of 6th Embodiment which concerns on this invention, its periphery, etc. It is a graph which shows the relationship between the attenuation coefficient of the magnetic fluid of FIG. 13, and the magnetic force of the surrounding magnetic field. The horizontal axis represents the frequency, and the vertical axis represents the vibration intensity. When there is no torsional vibration absorber, FIG. 2 shows the torsional vibration absorber, and FIG. 13 shows the torsional vibration absorber. It is a schematic front view of the torsional vibration damper of the seventh embodiment according to the present invention. It is a schematic side view of the XVII-XVII arrow of FIG. It is a schematic front view of the torsional vibration damper of 8th Embodiment which concerns on this invention. It is a schematic front view of the torsional vibration damper of the ninth embodiment according to the present invention. 20 is a graph showing a current waveform when the vibrator of FIG. 19 is not vibrating and a current waveform when the vibrator is vibrating. It is a graph which shows the difference of the waveform when the vibrator | oscillator of FIG. 20 is vibrating, and the waveform when not vibrating.

  Embodiments of a torsional vibration absorber 1 and a rotating electrical machine using the torsional vibration absorber 1 according to the present invention will be described below with reference to the drawings.

[First Embodiment]
1st Embodiment is described using drawing (FIGS. 1-7).

  First, the structure of the rotary electric machine which attaches the torsional vibration damper 1 of this embodiment is demonstrated using FIGS.

  FIG. 1 is a schematic side view schematically showing the rotating electrical machine of the present embodiment. FIG. 2 is a front view of the torsional vibration absorber 1 of FIG. FIG. 3 is a side view of the torsional vibration damper 1 of FIG. FIG. 4 is a partial front view showing the vicinity of the vibrator 14 in FIG. 3 partially enlarged. FIG. 5 is a schematic perspective view of a general dynamic vibration absorber or the like.

  As shown in FIG. 1, the rotating electrical machine includes a shaft member 2, a rotor 3, a stator 4, a stator frame 5, and a torsional vibration absorber 1. The stator frame 5 is virtually indicated by a two-dot chain line. The torsional vibration absorber 1 is not shown in detail.

  The shaft member 2 is a member that rotates around a horizontally extending shaft, and is rotatably supported by a bearing (not shown). The rotor 3 is rotatably fixed so as to surround the shaft member 2 from the outside in the radial direction, and is configured to rotate coaxially with the shaft member 2.

  The stator 4 surrounds the rotor 3 while forming a predetermined gap on the circumferential surface of the rotor 3. The stator 4 is housed and fixed in a stator frame 5. A bearing housing (not shown) for attaching a bearing that supports the shaft member 2 is also fixed to the stator frame 5.

  The torsional vibration absorber 1 is attached to a shaft member 2 on the outer side in the axial direction of the rotor 3. Hereinafter, the configuration of the dynamic vibration absorber attached to the shaft member 2 of the rotating electrical machine will be described. As shown in FIGS. 2 and 3, the torsional vibration absorber 1 includes two flanges, that is, a first flange 20 and a second flange 25, four vibrators 14, and an elastic member 10 (in this example, a coil). A spring 10), a coil 41, a yoke 42, and a power supply device 45.

  The first flange 20 has a disk shape attached to the shaft member 2 so as to surround the shaft member 2 from the outside in the radial direction, and rotates coaxially with the shaft member 2. Four first axial holes 22 are formed in the first flange 20. These first axial holes 22 are formed on the right side surface (first axial end surface 21) of the first flange 20 in FIG. 3 on one surface facing in the axial direction. In this case, each first axial hole 22 opens on the right side of FIG. 3 and is formed with a predetermined axial depth on the left side. Further, the first axial holes 22 are formed at equal intervals in the circumferential direction along the circumferential direction, that is, every 90 degrees in the circumferential direction.

  Further, circumferential holes 24 are formed at two locations on the inner wall surface of the first axial hole 22. The circumferential holes 24 are formed to face each other with a predetermined circumferential depth.

  Similar to the first flange 20, the second flange 25 is attached to the shaft member 2 so as to surround the shaft member 2 from the outside in the radial direction, and has a disk shape that rotates coaxially with the shaft member 2. The second flange 25 is attached to the shaft member 2 so as to form a predetermined axial gap 35 in the first flange 20.

  The second flange 25 has a second axial hole at a position facing the first axial hole 22 on a surface (second axial end surface 26) on the side facing the first axial end surface 21 of the first flange 20. 27 is formed. These second axial holes 27 open on the left side of FIG. 3 and are formed with a predetermined axial depth on the right side. The second axial holes 27 are formed at intervals in the circumferential direction along the circumferential direction. That is, it is formed every 90 degrees in the circumferential direction.

  Further, circumferential holes 24 are formed at two locations on the inner wall surface of the second axial hole 27. The circumferential holes 24 are formed to face each other with a predetermined circumferential depth.

  Each vibrator 14 is made of a magnetic member and extends in the axial direction so that one axial end is in the first axial hole 22 and the opposite axial end is in the second axial hole 27. Placed in. At this time, the vibrator 14 is formed so as to maintain the axial gap 35 from the outer peripheral surface of the shaft member 2.

  As shown in FIG. 4, the vibrator 14 has a recess 15 formed on the circumferential surface of the portion in the first axial hole 22 of the vibrator 14. Although omitted in FIG. 4, the recess 15 is similarly formed on the circumferential surface of the portion in the second axial hole 27.

  As shown in FIG. 4, the coil spring 10 has one end attached to the bottom of the circumferential hole 24 and the opposite end attached to the recess 15. The coil spring 10 is elastically deformable in the circumferential direction and elastically supports the vibrator 14. When the coil spring 10 supports the vibrator 14, a circumferential gap 33 is formed between the circumferential end of the vibrator 14 and the circumferential wall surface in the first axial hole 22. These coil springs 10 and the vibrator 14 form a vibration system supported by a spring having a mass m of a predetermined spring constant k. The vibration system vibrates in a tangential direction with respect to the outer peripheral surface of the shaft member 2.

  The coil 41 is wound so as to surround the vibrator 14 at the axial position of the axial gap 35 from the outside in the radial direction. The coil 41 is configured such that a current flows through the power supply device 45. The yoke 42 is an annular metal member formed so as to surround the first flange 20, the second flange 25, and the coil 41 from the outside in the radial direction.

  Although details about the fixing of the coil 41 and the yoke 42 are omitted, for example, they are indirectly fixed to the stator frame 5 or the like.

  When the current of the coil 41 flows, a magnetic field is generated in the vibrator 14 and the first flange 20 and the second flange 25. This magnetic field is generated as indicated by a broken line X shown in FIGS. The generation of the magnetic field will be described later.

  As shown in FIG. 5, a general dynamic vibration absorber 91 corresponding to torsional vibration has a vibration system attached to a rotating shaft 90. This vibration system includes a spring member 93 having a predetermined spring constant and a member having a predetermined mass 94. As described above, the dynamic vibration absorber 91 works effectively only at a predetermined frequency, and does not work effectively at frequencies other than the predetermined frequency.

  Here, the operation of the torsional vibration absorber 1 of the present embodiment will be described below with reference to FIGS. 6 and 7 in addition to FIGS.

  Here, FIG. 6 is a graph showing the vibration response of the dynamic vibration absorber and the like of FIG. 5 when the operating rotational speed of the rotating body of FIG. 5 is changed, and the horizontal axis indicates the frequency and the vertical axis indicates the vibration intensity. FIG. 7 is a graph showing the natural frequency such as ω1 in FIG. 6 and shows the natural vibration with respect to the current intensity and the like.

  By supplying a current from the power supply device 45 to the coil 41, the vibrator 14 made of a magnetic member is magnetized, and an N pole and an S pole are generated on both sides in the axial direction as shown in FIGS.

  The first flange 20 and the second flange 25 are made of a magnetic material as described above. For this reason, when the vibrator 14 is magnetized, an attractive force is generated between the vibrator 14 and the first flange 20 and the second flange 25. This suction force acts between the vibrator 14 and the first flange 20 and the second flange 25 as a non-linear spring that increases the suction force when approaching each other.

When the vibrator 14 is not magnetized, the natural frequency ω of the vibrator 14 is determined by the following equation (1) by the mass m of the vibrator 14 and the spring constant k of the coil spring 10.

When the power supply device 45 is operated and a current is passed through the coil 41, the vibrator 14 is magnetized. In this case, as shown in FIGS. 2 and 3, a suction force is generated between the vibrator 14 and the first flange 20 and the second flange 25. When the electromagnetic force, which is an attractive force, is F, and the circumferential width of the circumferential gap 33 that changes due to vibration is δ (FIG. 4), it is expressed as shown in Equation (2).

H is the strength of the magnetic field and is proportional to the strength of the current. Here, when δ is small, it can be shown as follows, and it can be seen that it acts on the vibrator 14 as a negative spring constant (−k ′).

Therefore, when the electromagnetic force F is applied to the vibrator 14, the natural frequency of the vibrator 14 is expressed by the following equation, and the natural frequency can be lowered.

  As shown in FIG. 6, when there are three torsional natural frequencies in the operating frequency range, the vibrations increase when the operating frequencies coincide with the respective torsional natural frequencies, resulting in a resonance state.

  The optimum torsional vibration absorber 1 that effectively acts on the three vibration modes is obtained by adjusting the natural frequency of the dynamic vibration absorber to the same natural frequency as the torsional natural frequency at each vibration peak. According to this, it is possible to reduce the peak amplitude of vibration as indicated by a dotted line.

  The action of reducing the peak amplitude (adjustment work) will be described with reference to FIG. In order to perform this adjustment during operation, the natural frequency before the current is passed through the coil 41 is given by Equation (1), and therefore the mass of the vibrator 14 and the spring constant K of the coil spring 10 are adjusted. . The natural frequency at this time is ω1.

  When the operating frequency is ω1, it is possible to effectively act as the torsional vibration absorber 1 without passing a current through the coil 41, and to reduce vibration.

  When the operating frequency becomes ω2, the current I2 is supplied to the coil 41, the electromagnetic force is applied as an attractive force, and the spring constant is lowered so that the natural frequency becomes ω2. As a result, even when the torsional vibration mode resonates, the vibration amplitude can be lowered as shown by the broken line in FIG.

  Further, when the operating frequency changes to ω3, the current I3 is passed through the coil 41, and the natural frequency of the torsional vibration absorber 1 is adjusted to be ω3. As a result, even when the torsional vibration mode resonates, the vibration amplitude can be lowered as shown by the dotted line. By performing this current adjustment, the peak of torsional vibration can be lowered over the entire operating range.

  As can be seen from the above description, according to the present embodiment, the natural frequency of the torsional vibration absorber 1 attached to the outer peripheral portion of the rotating shaft can be adjusted during operation, and the natural frequency mode with different rotational speeds can be adjusted. However, the single torsional vibration absorber 1 can efficiently reduce vibration, avoid resonance of torsional vibration, and realize a stable and reliable operating range of a wide range of devices.

  Note that the first axial hole 22 and the second axial hole 27 of the present embodiment may be notches that open in the radial direction. Further, the first axial hole 22 and the second axial hole 27 may penetrate in the axial direction.

[Second Embodiment]
A second embodiment will be described with reference to FIG. FIG. 8 is a schematic side view of the torsional vibration absorber 1 of the present embodiment. In addition, this embodiment is a modification of 1st Embodiment (FIGS. 1-7), Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is carried out. Omitted.

  As shown in FIG. 8, the yoke 42 of the present embodiment is formed with a first inner protrusion 23 and a second inner protrusion 28 having the same shape. The first inner protrusion 23 is formed to protrude radially inward from the axial end of the yoke 42 closer to the first flange 20. The first inner protrusion 23 is formed on the entire circumference of the yoke 42, and the inner surface of the first inner protrusion 23 faces the radially outer surface of the first flange 20.

  The second inner protruding portion 28 is formed so as to protrude radially inward from the axial end portion of the yoke 42 closer to the second flange 25. The second inner protruding portion 28 is formed on the entire circumference of the yoke 42, and the inner surface of the second inner protruding portion 28 faces the radially outer surface of the second flange 25. The first inner protrusion 23 and the second inner protrusion 28 are formed of the same material as the yoke 42.

  When a current is passed through the coil 41, a magnetic field is generated, the vibrator 14 is magnetized, and the natural frequency of the torsional vibration absorber 1 can be adjusted from the outside.

  By forming the first inner protrusion 23 and the second inner protrusion 28 on the yoke 42, the distance between the radially outer surface of the first flange 20 and the yoke 42 is smaller than that in the first embodiment. . Thereby, the flow of magnetic flux can be smoothly passed through the vibrator 14, and a stronger magnetic field is formed.

  As can be seen from the above description, according to the present embodiment, the same effects as those of the first embodiment can be obtained, the magnetization of the vibrator 14 can be strengthened, and the torsional natural frequency can be adjusted more efficiently. .

[Third Embodiment]
A third embodiment will be described with reference to FIGS. 9 and 10. FIG. 9 is a schematic front view of the torsional vibration absorber 1 of the present embodiment. FIG. 10 is a schematic top view showing the vibrator 14 and the leaf spring 12 of FIG. 9 as viewed in the direction of arrows XX.

  In addition, this embodiment is a modification of 1st Embodiment (FIGS. 1-7), Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is carried out. Omitted.

  In the present embodiment, a leaf spring 12 is used instead of the coil spring 10 (FIGS. 2 to 4) described in the first embodiment.

  The leaf springs 12 are respectively attached to both ends in the circumferential direction of the portion in the first axial hole 22 and are also attached to both sides in the circumferential direction of the portion in the second axial hole 27. The vibrator 14 is elastically supported by these leaf springs 12. Each leaf spring 12 is configured to elastically deform in the circumferential direction.

  In the vibrator 14 of this embodiment, the concave portion 15 (FIG. 4) described in the first embodiment is not formed. In addition, the circumferential hole 24 described in the first embodiment is not formed in each of the first axial hole 22 and the second axial hole 27.

  Each leaf spring 12 generates frictional damping at the contact surface between the vibrator 14 and the first flange 20 and the second flange 25. This friction damping effect can reduce the vibration response in the vicinity of the natural frequency. Thereby, the effect similar to 1st Embodiment can be acquired.

  In this embodiment, the space around the vibrator 14 can be further reduced. In addition, the shape of the vibrator 14, the first axial hole 22, and the like can be made simpler, which is effective in reducing the manufacturing process.

[Fourth Embodiment]
A fourth embodiment will be described with reference to FIG. FIG. 11 is a graph showing the strength of the magnetic field generated in the torsional vibration absorber 1 of the present embodiment. The configuration of the torsional vibration absorber 1 of this embodiment is the same as that of the torsional vibration absorber 1 (FIGS. 2 to 4) described in the first embodiment.

  The present embodiment is a modification of the first embodiment (FIGS. 1 to 7), and the same reference numerals are given to the same or similar parts as the first embodiment, and the duplicated description is omitted. .

  The vibrator 14 of this embodiment is formed of a variable magnet such as a samarium cobalt magnet. The power supply device 45 in this example is a device that can generate a high-voltage pulse current. As shown in FIG. 11, the variable magnet increases the magnetic force when a magnetic field is applied to the plus side in a pulsed manner. It is possible to reduce the magnetic force by applying a magnetic force to the negative side.

  In the present embodiment, the power supply device 45 (FIG. 2) described in the first embodiment can supply a pulse current as shown in FIG. By supplying the pulse current, the natural frequency of the vibrator 14 can be changed by adding the pulse current.

  Thereby, compared with 1st Embodiment, the natural frequency of the torsional vibration absorber 1 can be changed efficiently according to an operating frequency. In addition, since it is not necessary to supply a constant current, power is saved as compared with the first embodiment.

[Fifth Embodiment]
A fifth embodiment will be described with reference to FIG. FIG. 12 is a partial front view showing the vicinity of the vibrator 14 of the torsional vibration absorber 1 of the present embodiment. In addition, this embodiment is a modification of 1st Embodiment (FIGS. 1-7), Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is carried out. Omitted.

  Two permanent magnet members 16 are attached to the first axial hole 22 of the present embodiment so as to face each other on the circumferential surface of the inner periphery.

  Although not shown in detail, these permanent magnet members 16 are plate-like members in which through holes 17 are formed. The coil spring 10 passes through the through hole 17. The permanent magnet member 16 is formed to have a polarity opposite to that of the end of the vibrator 14. That is, the right end portion of the vibrator 14 in FIG. 12 is an S pole, and the permanent magnet member 16 facing the S pole is an N pole.

  By arranging the permanent magnet member 16 having the opposite polarity to the vibrator 14, the attractive force can be increased. As a result, adjustment of the natural frequency of the torsional vibration absorber 1 from the outside can be performed with a change in the magnetic force of the vibrator 14 that is smaller than that of the torsional vibration absorber 1 of the first embodiment. Further, by increasing the suction force, the natural frequency can be adjusted in a wider frequency range.

[Sixth Embodiment]
A sixth embodiment will be described with reference to FIGS. FIG. 13 is a partial front view showing the hermetic container 18 of the torsional vibration damper 1 of the present embodiment, its periphery, and the like. FIG. 14 is a graph showing the relationship between the attenuation coefficient of the magnetic fluid 19 in FIG. 13 and the magnetic force of the surrounding magnetic field.

  FIG. 15 is a graph showing the frequency on the horizontal axis and the vibration intensity on the vertical axis. The response (L3) when the torsional vibration absorber 1 is not provided, the torsional vibration absorber 1 described in the first embodiment (FIG. 2). A response (L4) in the case of being present and a response (L5) in the case of having the torsional vibration damper 1 of the present embodiment (FIG. 13) are shown.

  In addition, this embodiment is a modification of 1st Embodiment (FIGS. 1-7), Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is carried out. Omitted.

  As shown in FIG. 13, the vibrator 14 is accommodated in a sealed container 18 filled with a magnetic fluid 19. This sealed container 18 is a container extending in the axial direction, and one axial end is in the first axial hole 22, and the opposite axial end is in the second axial hole 27 (in FIG. 13, (Not shown). When the coil spring 10 supports the sealed container 18, a circumferential gap 33 is formed between the circumferential end of the sealed container 18 and the circumferential wall surface in the first axial hole 22.

  As can be seen from the relationship between the attenuation coefficient of the magnetic fluid 19 in FIG. 14 and the magnetic force of the surrounding magnetic field, the attenuation coefficient increases as the magnetic force increases. The magnetic fluid 19 in the hermetic container 18 can add attenuation to the torsional vibration absorber 1 described in the first embodiment.

  In FIG. 15, the response (L3) without the torsional vibration absorber 1 is indicated by a solid line, and the response (L4) when the torsional vibration absorber 1 is installed is indicated by a broken line. Moreover, the response (L5) when the torsional vibration absorber 1 that is damped is installed is indicated by a thick broken line.

  Thus, it becomes possible to give an appropriate damping effect to each vibration peak (ω1, ω2, ω3), and vibration can be reduced more effectively.

  As can be seen from the above description, according to the present embodiment, the natural frequency of the torsional vibration absorber 1 can be adjusted over a wide range, and the vibration can be further reduced by the effect of damping. Stable operation is possible.

[Seventh Embodiment]
A seventh embodiment will be described with reference to FIGS. 16 and 17. FIG. 16 is a schematic front view of the torsional vibration absorber 1 of the present embodiment. 17 is a schematic side view taken along arrow XVII-XVII in FIG. The present embodiment is a modification of the first embodiment (FIGS. 1 to 7), and the same reference numerals are given to the same or similar parts as the first embodiment, and the duplicated description is omitted. .

  The torsional vibration absorber 1 of this embodiment includes a notched flange 50, a vibrator 14 made of a variable magnet member, a coil 41, an iron core 54, a rotational position sensor 60, and a control unit 61.

  The vibrator 14 has the same characteristics as those of the variable magnet member described in the fourth embodiment (FIG. 11), and can freely change the magnetic force. Thereby, the natural frequency of the vibrator 14 can be changed from the outside during operation.

  The notched flange 50 has a plate shape that is attached to the shaft member 2 so as to surround the shaft member 2 from the outside in the radial direction and rotates together with the shaft member 2. Two types of notches, a first notch 51 and a second notch 52, are formed at four locations on the outer periphery of the notch flange 50.

  The first notches 51 are formed at equal intervals in the circumferential direction at four locations on the outer periphery. The second notch 52 is formed between the first notches 51 adjacent to each other in the circumferential direction. The circumferential width of each second notch 52 is formed to be smaller than the circumferential width of the first notch 51, and the circumferential intervals between adjacent second notches 52 are formed to be equal. .

  A first notch 51 and a second notch 52 are formed on the outer periphery of the notch flange 50 so as to alternate in the circumferential direction, and the gap between the first notch 51 and the second notch 52 is radially outward. A protrusion 53 is formed so as to protrude to the front. That is, the protrusions 53 are formed on both sides in the circumferential direction such as the first notch 51.

  A circumferential hole 24 is formed in a portion of the protrusion 53 facing the first notch 51, and the coil spring 10 is attached. The vibrators 14 are inserted into the first notches 51 and supported by the coil springs 10.

  The iron core 54 is disposed on the outer side in the radial direction of each vibrator 14, and the coil 41 is wound around each iron core 54. A pulse current is supplied to each coil 41 by a power supply device 45. FIG. 16 shows a state where power is supplied only to the lower coil 41, and the remaining coils 41 are not shown. Although details of the fixed state of the iron core 54 are omitted, the iron core 54 may be attached indirectly to a stationary part, for example, inside a stator frame or the like.

  When a current flows through the coil 41, a magnetic field is generated by the vibrator 14, the coil 41, the iron core 54, and the like. In the present embodiment, by forming the second notch 52, the leakage magnetic flux can be suppressed, and the strength of the magnetic field can be further stabilized.

  A rotational position sensor 60 and a controller 61 are electrically connected to the power supply device 45 of the present embodiment.

  The rotational position sensor 60 has a function of detecting the rotational position of the vibrator 14. The control unit 61 can receive an electrical signal from the rotational position sensor 60 and has a function of controlling a current flowing from the power supply device 45 to the coil 41.

  The rotational position sensor 60 provides information on the position of the projection 53 when the circumferential position of the corner on the radially outer side of the projection 53 overlaps (matches) the circumferential position of the rotational position sensor 60. Send to.

  Based on the position information from the rotational position sensor 60, the control unit 61 generates a command for causing a pulse current to flow through the coil 41.

  As can be seen from the above description, according to the present embodiment, in addition to the effects of the first embodiment and the fourth embodiment, the natural frequency of the torsional vibration absorber 1 is simply changed corresponding to the operating frequency. Is possible. Moreover, since it is not necessary to always supply a current, power is saved.

  The first notch 51 into which the magnetic member 14 is inserted may be formed in the same manner as the first axial hole 22 described in the first embodiment. Moreover, it is good also as a through hole.

[Eighth Embodiment]
The eighth embodiment will be described with reference to FIG. FIG. 18 is a schematic front view of the torsional vibration absorber 1 of the present embodiment. Note that this embodiment is a modification of the seventh embodiment (FIGS. 16 and 17), and the same reference numerals are given to the same or similar parts as those in the seventh embodiment, and redundant description is given. Omitted.

  The torsional vibration absorber 1 of the present embodiment includes an annular member 29 made of a non-conductor. The annular member 29 is formed in an annular shape at a radial position corresponding to the radially inner bottoms of the first notch 51 and the second notch 52 of the notch flange 50.

  The annular member 29 can suppress the magnetic field from leaking to the notched flange 50 and weakening the magnetic field passing through the vibrator 14, and can increase the magnetic field generated in the vibrator 14. As a result, further power saving can be achieved.

[Ninth Embodiment]
The ninth embodiment will be described with reference to FIGS. First, the structure of the torsional vibration absorber of this embodiment will be described with reference to FIG. FIG. 19 is a schematic front view of the torsional vibration absorber 1 of the present embodiment.

  In addition, this embodiment is a modification of 1st Embodiment (FIGS. 1-7), Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is carried out. Omitted.

  The torsional vibration absorber 1 of the present embodiment includes an ammeter 71, a vibration detection device 72, a control device 70, in addition to the components of the torsional vibration absorber 1 (FIG. 2) described in the first embodiment. Have.

  The ammeter 71 is electrically connected to the coil 41 and measures the current flowing through the coil 41. The vibration detection device 72 is electrically connected to the ammeter 71 and detects vibration by determining whether the shaft member 2 is vibrating based on the current value measured by the ammeter 71.

  The control device 70 is electrically connected to the power supply device 45 and the vibration detection device 72, and can take in the determination result of the vibration detector. The control device 70 and the vibration detection device 72 are connected by a feedback circuit 73. The feedback circuit 73 is configured to be able to adjust the current that the power supply device 45 passes through the coil 41 based on the determination result.

  That is, the vibration detection device 72 and the control device 70 have both a signal detection function from the ammeter 71 and an instruction function for controlling the magnitude of the current flowing from the power supply device 45 to the coil 41.

  Here, the operation of the torsional vibration absorber 1 of the present embodiment will be described with reference to FIGS. 20 and 21 in addition to FIG. FIG. 20 is a graph showing a current waveform (L6) when the vibrator 14 of FIG. 19 is not oscillating and a current waveform (L7) when the vibrator 14 is oscillating. FIG. 21 is a graph showing the difference between the waveform when the vibrator 14 of FIG. 20 is oscillating and the waveform when it is not oscillating.

  When the torsional vibration is generated, the torsional vibration of the first flange 20 and the like is accompanied with the torsional vibration of the shaft member 2 that is a rotating body. When torsional vibration occurs in the first flange 20 or the like, the vibrator 14 vibrates. At resonance, this vibration becomes large.

  As described above, the vibrator 14 is magnetized by forming a magnetic field by the current flowing through the coil 41. When the vibrator 14 vibrates, the magnetic field changes. When the magnetic field changes, a current change that accompanies the vibration of the vibrator 14 occurs in the current flowing through the coil 41.

  The current flowing through the coil 41 can be detected and measured by an ammeter 71. As shown in FIG. 20, the current waveform varies depending on whether or not the vibration of the vibrator 14 is generated. This difference in current (difference in current waveform) increases the amplitude of the vibrator 14 at the time of resonance, so that the change in the magnetic field increases. Due to the change in the magnetic field, the change in the current also changes greatly.

  The current difference waveform (L8) in FIG. 21 indicates the vibration of the vibrator 14 itself.

  In the present embodiment, the ammeter 71 detects the difference between the current when vibration is generated and the current when there is no vibration, and the feedback circuit 73 sends the difference from the power supply device 45 so as to reduce the current component generated by the vibration. Control the current generated.

  At this time, it is possible to change the magnetic force generated in the vibrator 14 and adjust the natural frequency so that the torsional vibration absorber 1 can optimally reduce the vibration.

  As can be seen from the above description, after detecting torsional vibration and grasping its characteristics, the torsional vibration can be reduced, so that more efficient vibration suppression is possible, and the torsional vibration absorber 1 is reliable. Improves.

[Other Embodiments]
The description of the above embodiment is an example for explaining the present invention, and does not limit the invention described in the claims. Moreover, each part structure of this invention is not restricted to the said embodiment, A various deformation | transformation is possible within the technical scope as described in a claim.

  For example, in the first embodiment, the torsional vibration absorber 1 is arranged on the outer side in the one axial direction of the rotor 3, but the present invention is not limited to this, and it may be attached to both sides. Further, the annular member 29 described in the eighth embodiment may be provided with a non-conductive material only inside the protrusion 53.

DESCRIPTION OF SYMBOLS 1 ... Torsion dynamic vibration absorber, 2 ... Shaft member, 3 ... Rotor, 4 ... Stator, 5 ... Stator frame, 10 ... Elastic member (coil spring), 12 ... Leaf spring, 14 ... Vibrator (magnetic member) DESCRIPTION OF SYMBOLS 15 ... Recessed part 16 ... Permanent magnet member, 17 ... Through-hole, 18 ... Sealed container, 19 ... Magnetic fluid, 20 ... 1st flange, 21 ... 1st axial end surface, 22 ... 1st axial hole, 23 ... 1st inner protrusion, 24 ... circumferential hole, 25 ... second flange, 26 ... second axial end face, 27 ... second axial hole, 28 ... second inner protrusion, 29 ... annular member, 31 ... shaft Directional gap, 33 ... circumferential gap, 35 ... axial gap, 41 ... coil, 42 ... yoke, 45 ... power supply device, 50 ... notch flange, 51 ... first notch, 52 ... second notch, 53 ... Projection, 54 ... Iron core, 60 ... Rotational position sensor, 61 ... Control unit, 70 ... Control device, 71 ... Ammeter 72 ... vibration detector, 73 ... feedback circuit, 90 ... rotary shaft, 91 ... dynamic vibration absorber, 93 ... spring member 94 ... mass

Claims (14)

A plate member that is attached to the shaft member so as to surround the shaft member that rotates around the shaft extending in a predetermined direction from the outside in the radial direction and rotates together with the shaft member, and a plurality of shaft members that face the axial direction are arranged on the first axial end surface. A first flange in which the first axial holes are formed at circumferential intervals along the circumferential direction;
The first flange is arranged to form a predetermined axial gap, is attached to the shaft member so as to surround the shaft member from the outside in the radial direction, and rotates with the shaft member. A second flange in which a second axial hole is formed at each of the positions facing the first axial hole on the second axial end surface on the side facing the axial end surface;
An axial end is disposed such that one axial end is in the first axial hole and the opposite axial end is in the second axial hole, and the shaft member has a predetermined radius. A magnetic member arranged to form a directional gap;
An elastic member attached to the first axial hole, elastically deformable in a circumferential direction, and configured to support the magnetic member;
A coil disposed radially outside the magnetic member in the axial gap;
A power supply device that is electrically connected to the coil and causes a current to flow through the coil;
A torsional vibration absorber characterized by comprising:   The torsional vibration absorber according to claim 1, wherein the elastic member is a coil spring. The inner wall surface of the first axial hole is formed with at least two circumferential holes having a predetermined circumferential depth so as to face each other,
The inner wall surface of the second axial hole is formed with at least two circumferential holes having a predetermined circumferential depth so as to face each other,
One end of the coil spring is attached to the bottom of the circumferential hole,
The torsional vibration absorber according to claim 2.   The torsional vibration absorber according to claim 1, wherein the elastic member is a leaf spring. A first inner projecting portion projecting so as to face a radially outer surface of the first flange is formed at an axial end portion of the yoke closer to the first flange,
A second inner projecting portion projecting so as to face a radially outer surface of the second flange is formed at an axial end of the yoke closer to the second flange;
The torsional vibration damper according to any one of claims 1 to 4, wherein   The torsional vibration damper according to any one of claims 1 to 5, wherein the magnetic member is a magnet having a characteristic that a magnetic force changes when a magnetic field is applied in a pulsed manner.   The torsional vibration damper according to any one of claims 1 to 6, wherein permanent magnets are attached to portions on both sides in the circumferential direction of the axial hole. The magnetic member is housed in a sealed container filled with a magnetic fluid,
The elastic member is configured to support the sealed container and indirectly support the magnetic member;
The torsional vibration damper according to claim 1, wherein:   The torsion according to any one of claims 1 to 8, further comprising an annular yoke formed so as to surround the first flange, the second flange, and the coil from a radially outer side. Dynamic vibration absorber. An ammeter for measuring the current flowing through the coil;
A vibration detector for detecting vibration by determining whether or not the shaft member is vibrating based on a current value measured by the ammeter;
It is electrically connected to the power supply device and the vibration detector, can take the determination result of the vibration detector, and can adjust the current that the power supply device flows to the coil based on the determination result A configured control device; and
The torsional vibration absorber according to claim 1, wherein the torsional vibration absorber is provided. A plate that is attached to the shaft member and rotates together with the shaft member so as to surround the shaft member rotating around the shaft extending in a predetermined direction from the outside in the radial direction, and a plurality of shafts on the axial end surface facing the axial direction. A flange in which directional holes are formed at circumferential intervals along the circumferential direction, and notches are formed in the circumferential intervals;
A magnetic member disposed in the axial hole;
An elastic member attached to the axial hole, elastically deformable in a circumferential direction, and configured to support the magnetic member;
An iron core disposed on the radially outer side of each of the magnetic members;
A coil wound around the iron core;
A power supply device that is electrically connected to the coil and causes a current to flow through the coil;
A torsional vibration absorber characterized by comprising:   A non-conductive member is disposed at a position where a radial position includes a radially inner portion of the axial hole and a bottom portion of the notch and a circumferential position is at least between the axial hole and the notch. The torsional vibration absorber according to claim 11.   The torsional vibration absorber according to claim 12, wherein the non-conductive member is an annular shape surrounding the shaft member at the radial position. A shaft member rotating around an axis extending in a predetermined direction;
A torsional vibration absorber attached to the shaft member;
A rotor arranged to surround the shaft member from outside in the radial direction and configured to rotate coaxially with the shaft member;
A stator that surrounds the rotor in a circumferential direction while forming a predetermined gap;
In a rotating electrical machine having
The torsional vibration absorber is
The shaft member is attached to the shaft member so as to surround the shaft member from the outside in the radial direction and rotates together with the shaft member. The first end surface facing the axial direction has a plurality of first axial depths. A first flange in which one axial hole is formed at a circumferential interval along the circumferential direction;
The first flange is arranged to form a predetermined axial gap, is attached to the shaft member so as to surround the shaft member from the outside in the radial direction, and rotates with the shaft member. A second flange in which a second axial hole is formed at each of the positions facing the first axial hole on the second axial end surface on the side facing the axial end surface;
A magnetic member extending in the axial direction and disposed such that one axial end is in the first axial hole and the opposite axial end is in the second axial hole;
An elastic member attached to the first axial hole, elastically deformable in a circumferential direction, and configured to support the axial member;
A coil that is disposed radially outside the magnetic member in the axial gap and through which a predetermined current flows;
A power supply device for passing a current through the coil;
A rotating electric machine comprising:

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