JP5259350B2 - Rotating electric machine - Google Patents

Description

  The present invention relates to a rotating electrical machine that vibrates due to a magnetic attractive force generated when a rotor rotates.

  A rotating electrical machine such as a generator or an electric motor usually has a rotor having a rotating shaft and a stator. The stator includes a cylindrical stator core formed so as to surround the rotor, and a stator frame that covers the stator core with a cylindrical outer peripheral plate from the radial direction.

  Magnetic vibration is generated in the stator by the magnetic attractive force generated by the rotation of the rotor. It is necessary to prevent this magnetic vibration from propagating to the foundation on which the rotating electrical machine is installed. A general stator of a rotating electrical machine suppresses propagation of magnetic vibration to the outside of the stator by supporting the stator core via an elastic body between the stator core and the stator frame. ing.

  For example, in a two-pole turbine generator, the magnetic attractive force acting on the rotor vibrates in an annular vibration mode having vibration nodes along the circumferential direction. The two-pole turbine generator has four nodes. This annular vibration mode moves along the circumferential direction at the rotational frequency of the rotor.

  On the other hand, the stator vibrates in a four-node annular natural vibration mode, similarly to the magnetic attractive force. Since the vibration mode of the stator is almost the same as the vibration mode of the magnetic attraction force of the rotor, it receives strong excitation. That is, as the vibration mode of the magnetic attractive force (excitation force) increases, the natural vibration mode of the stator also increases.

The circumferential distribution of the excitation force mode is expressed by the equation (1) because there are four nodes. Here, θ is the angle in the circumferential direction, and F ₀ is the magnitude of the magnetic attraction force of the rotor.
F (θ) = F ₀ cos (4θ) (1)

On the other hand, the distribution in the circumferential direction of the ring natural vibration mode of the stator core is expressed by Equation (2), where n is the number of nodes. Where x is the circumferential displacement, x ₀ is its amplitude.
x (θ) = x ₀ · cos (n · θ) (2)

Accordingly, the mode excitation force _{F n} can be expressed by Equation (3).

  That is, since the orthogonality is established except for n = 4, the mode excitation force becomes 0, so that mode responses other than n = 4 can be ignored.

  This four-node natural ring vibration mode has two modes. In one mode, for example, a vibration antinode (a portion with a large amplitude) is formed on the vertical central axis of the cross section in the rotation axis direction of the stator core, whereas the other mode is from the vertical central axis described above. An antinode of vibration is formed on an axis having an inclination of 45 degrees.

  In the distribution of both vibration modes, a vibration node (a position where the amplitude becomes 0) and a vibration antinode are interchanged. That is, the position that becomes the antinode of one mode becomes the node of the other mode. Moreover, the natural frequency of each mode is substantially equal.

  In a two-pole turbine generator, the above four-node natural ring vibration mode is excited by the excitation force of a rotor having substantially the same four-node ring vibration mode. The position is constant. Therefore, the position of the node does not change in each mode response, and the other portions perform harmonic vibration in time in proportion to the shape of the mode. Such a form of vibration is called a standing wave.

  However, the stator has two natural annular vibration modes, such as the magnetic attraction force of the rotor described above, and the nodes and antinodes of these vibration modes are generated in a mutually reversed manner. The vibration mode generated in the actual stator obtained by superimposing the responses of these two vibration modes has the same shape as the four-node ring vibration mode, similarly to the excitation force.

  When this rotates at the angular velocity of the rotor, the amplitude of the stator shows a constant value over the entire circumference. In other words, there is a vibration node in the response of each natural vibration mode, but no node is generated in the actual response obtained by superimposing the responses of the two modes.

  In this case, since the stator has the same amplitude in the entire circumference in the circumferential direction, it is difficult to suppress propagation of the magnetic vibration generated in the stator to the foundation on which the rotating electrical machine is installed.

As a method for suppressing the vibration of the rotating electric machine stator due to the magnetic attraction force of the rotor, for example, as disclosed in Patent Document 1, the cross-sectional shape of the stator core is made polygonal so that the structure of the stator There is known a technique for reducing vibration by breaking the symmetry.
JP 2003-088008 A

  However, the stator iron core of a rotating electrical machine is manufactured by stacking punched plates in the axial direction. However, in a large rotating electrical machine such as a turbine generator, the shape of the stator core is large. It is difficult to mold with one sheet. Therefore, the stator core is manufactured by forming the punched plate into a sector shape divided in a small angle in the circumferential direction, and laminating it in the axial direction by shifting half the inner angle of the sector shape.

  In this case, forming a polygon requires a plurality of types of punched plate shapes, which complicates the manufacturing process. In addition, the outer shape of the stator core is larger than that of the circular cross section, which increases the size and weight of the generator body. Therefore, it may be difficult to apply the vibration countermeasure by making the stator core polygonal to a large machine.

  The present invention has been made to solve the above-described problems, and an object thereof is to suppress electromagnetic vibration of the stator frame that is generated by rotation of the rotor.

In order to achieve the above object, a rotating electrical machine according to the present invention includes a rotor having a rotating shaft and a plurality of substantially disk-shaped iron plates stacked in the direction of the rotating shaft so as to surround the outer periphery of the rotor. and arranged substantially hollow cylindrical laminated core has a stator frame which is configured to cover a substantially cylindrical outer circumferential frame of the laminated core from semi-radially outward, said radially disposed on a side surface of the laminated core A damping part comprising: a weight configured to be able to swing; and an elastic member that is arranged between the weight and the laminated core and is elastically deformable in the radial direction, and is arranged so as to connect them, A stator frame connecting means for connecting the stator frame and the laminated iron core, and the stator frame connecting means includes a vibration antinode and a vibration anti-vibrator along a circumferential direction when the damping part is disposed on a side surface of the laminated iron core. Knots Provided in the section in the vicinity of the circular mode of vibration occurring in the laminated core, when the vibration damping unit is not installed, the rotating magnetic force the rotor is excited, the circumferentially rotor Corresponding to the first natural ring vibration mode in which the amplitude is distributed in the circumferential direction so that vibration antinodes and nodes can be alternately arranged at almost equal intervals by twice the number of poles. A position corresponding to the antinode of the first natural annular vibration mode having a natural frequency substantially the same as the natural frequency of the first natural ring vibration mode, and a position corresponding to the node of the first natural annular vibration mode being antinode. A second natural annular vibration mode in which the amplitude is distributed in the circumferential direction, and the damping part is attached in the vicinity of the abdomen of the first natural annular vibration mode, Third natural ring with antinode vibrations distributed in the opposite direction to the mode And the dynamic mode is generated, it is configured the response of the first natural circular mode of vibration to cancel the response of the third natural circular mode of vibration, characterized by.

The rotating electrical machine according to the present invention is arranged such that a rotor having a rotating shaft and a plurality of substantially disk-shaped iron plates are stacked in the rotating shaft direction so as to surround the outer periphery of the rotor, and the rotating A substantially hollow cylindrical laminated core that vibrates in the radial direction by a rotating magnetic force generated when the child rotates, and a stator frame configured to cover the laminated core with a substantially cylindrical outer peripheral plate from the radially outer side; A stator frame connecting means for connecting the stator frame and the laminated iron core, an elastic member disposed in at least one of the stator frame and the stator frame connecting means and elastically deformable in the radial direction, and connected to the elastic member. A damping part comprising a weight configured to be able to swing in the radial direction, and the stator frame connecting means has the damping part in the step. It provided in the section in the vicinity of the circular mode of vibration that antinodes and nodes are generated alternately vibration in the circumferential direction by being arranged in data frames, wherein the stator frame, the damping unit is not attached Sometimes, the rotational magnetic force excited by the rotor causes the amplitude to be distributed in the circumferential direction so that vibration antinodes and nodes can be alternately arranged at equal intervals along the circumferential direction by twice the number of poles of the rotor. A position corresponding to the antinode of the first natural annular vibration mode has a natural frequency substantially the same as the natural frequency corresponding to the first natural annular vibration mode and the natural frequency corresponding to the first natural annular vibration mode. A second natural annular vibration mode in which an amplitude is distributed in a circumferential direction so that a position corresponding to a node of the first natural annular vibration mode becomes an antinode. Installed near the outside of the abdomen in annular vibration mode Generating a third natural annular vibration mode in which antinode vibrations are distributed in the opposite direction with respect to the first natural annular vibration mode, and changing the response of the first natural annular vibration mode to the third natural annular vibration mode. It is comprised so that it may cancel in response to.

  According to the present invention, it is possible to suppress the electromagnetic vibration of the stator frame generated by the rotation of the rotor.

  Hereinafter, embodiments of a rotating electrical machine according to the present invention will be described with reference to the drawings.

[First Embodiment]
1st Embodiment which concerns on the rotary electric machine of this invention is described using FIGS. First, the configuration of the rotating electrical machine of the present embodiment will be described. FIG. 1 is a schematic longitudinal sectional view showing a configuration of an example of a rotating electrical machine according to this embodiment, which is applied to a two-pole turbine generator. FIG. 2 is a schematic cross-sectional view taken along the line II-II in FIG.

  The rotating electrical machine according to the present embodiment includes a rotor 1 having a horizontal rotating shaft and a stator. The stator includes a stator core 5 that is configured to surround the outer periphery of the rotor 1, and a stator frame 7 that covers the stator core 5.

  The stator core 5 includes a laminated core 9, a rib bar 11 attached to a side surface of the laminated core 9, and iron core support plates 13a and 13b for fixing the rib bar 11 from the outside.

  The laminated iron core 9 has a substantially cylindrical shape in which a plurality of substantially disk-shaped iron plates having an opening at the center are laminated in the direction of the rotation axis of the rotor 1. The rotor 1 is inserted into the hollow portion 9 a formed inside the laminated core 9. Further, a coil 10 is wound around the laminated iron core 9.

  The rib bars 11 are a plurality of bars extending in the rotation axis direction, arranged on the side surfaces of the laminated core 9 at intervals in the circumferential direction, and fix the laminated core 9 in the radial direction from the outside to the inside. ing. The rib bars 11 are often arranged at equal intervals in the circumferential direction, but are not necessarily equal intervals. The iron core support plates 13a and 13b are ring-shaped plates whose end surfaces are flat in a direction perpendicular to the rotation axis, are arranged so as to surround the laminated iron core 9, and are attached so as to fix the rib bar 11 from the outside. It has been. A plurality of the iron core support plates 13a and 13b are arranged at intervals in the rotation axis direction. Further, a ring-shaped rib plate 12 having an end surface extending in a direction perpendicular to the rotation axis and a side surface formed along the circumferential direction is provided on a radially outer side surface of the stator iron core 5 from the outer side. Multiple surroundings are fixed. These rib plates 12 are arranged at intervals in the rotation axis direction.

  Furthermore, core holding plates 14 that hold down the stator core 5 by attaching tension to the rib rod 11 from both ends in the rotation axis direction toward the center are attached to both end faces of the stator core 5 perpendicular to the rotation axis direction. ing. The iron core retainer plate 14 has an end surface perpendicular to the rotation axis direction and a side surface formed along the circumferential direction.

  The stator frame 7 includes a substantially cylindrical outer peripheral plate 15 that covers the stator core 5 from the outside in the radial direction, and a plurality of partition plates welded to the inner surface of the outer peripheral plate 15. In the present embodiment, there are three partition plates, which are the first partition plate 17a, the second partition plate 17b, and the third partition plate 17c. On the outside of the outer peripheral plate 15, leg plates 19 that support the stator frame 7 on the foundation on which the rotating electrical machine is installed are arranged at least at two places. In the present embodiment, the two leg plates 19 are arranged on the outer peripheral side surface of the stator frame 7 so as to support a position that is horizontal and vertical to the rotation axis, that is, a position slightly below the side of the rotation axis.

  The first to third partition plates 17a, 17b, and 17c are ring-shaped plates having end faces that extend in a direction perpendicular to the rotation axis, and their radially outer side surfaces are fixed to the inner side surface of the outer peripheral plate 15 by welding. ing. The first to third partition plates 17a, 17b, and 17c are alternately (alternately) arranged in the rotation axis direction with respect to the iron core support plates 13a and 13b. In the example of FIG. 1, the first and second partition plates 17a and 17b are disposed at both ends of the outer periphery of the stator core 5 in the rotation axis direction, and the first partition plate 17a is disposed at the left end portion of FIG. The second partition plate 17b is disposed at the right end. The third partition plate 17c is disposed substantially at the center of the first and second partition plates 17a and 17b. The iron core support plate 13a is arranged in the middle of the first and third diaphragms 17a and 17c, and the iron core support plate 13b is arranged in the middle of the second and third diaphragms 17b and 17c. The number of the partition plates 17a, 17b, 17c, or the iron core support plates 13a, 13b may be further increased at intervals from each other along the rotation axis direction.

  A plurality of spring bars 18 extending in the rotation axis direction are fixed to the first to third partition plates 17a, 17b, and 17c. Both ends of the spring bar 18 are fixed by the first partition plate 17a and the second partition plate 17b, and the approximate center of the spring bar 18 is fixed by the third partition plate 17c. Further, these spring bars 18 are fixed to the iron core support plates 13a and 13b through the iron core support plates 13a and 13b from the rotation axis direction. Thereby, the stator core 5 is connected to the outer peripheral plate 15 via the plurality of spring bars 18. Since the spring bar 18 is connected to the iron core support plate 13a between the first and third partition plates 17a and 17c, the spring bar 18 is displaced with respect to the displacement perpendicular to the rotation axis of the iron core support plate 13b. Is elastically deformed and has a function of absorbing relative deformation between the first partition plate 17a, the third partition plate 17c and the iron core support plate 13a. Similarly, the spring bar 18 absorbs relative deformation between the second partition plate 17b, the third partition plate 17c, and the iron core support plate 13b. As a result, the laminated iron core 9 and the stator frame 7 are elastically connected, so that these spring bars 18 also have a function of suppressing the vibration generated in the stator iron core 5 from propagating to the stator frame 7. .

  A vibration damping mechanism 21 is disposed on the outer peripheral surface of the stator core 5 directly above the central portion in the rotation axis direction. The vibration control mechanism 21 has a weight 23 and an elastic member 25. The weight 23 is configured to be swingable in the radial direction. The elastic member 25 is configured to be elastically deformable in the radial direction, and the weight 23 and the stator core 5 are connected by the elastic member 25. In the example of FIGS. 1 and 2, the detailed structure of the damping mechanism 21 is not shown, and the weight 23 and the elastic member 25 are schematically shown as a vibration system having a mass and a spring element.

  The arrangement of the leg plate 19 is a position moved approximately 90 degrees in the circumferential direction counterclockwise and clockwise with respect to the position where the vibration control mechanism 21 is arranged.

  Further, as shown in FIG. 2, a plurality of spring bars 18 are arranged at four locations at intervals of 90 degrees in the circumferential direction with reference to the position where the vibration damping mechanism 21 is arranged. In the example of FIG. 2, four spring bars 18 are arranged at one place. In the present embodiment, the four spring bars 18 arranged at one place are arranged at substantially equal intervals along the circumferential direction. In the other three locations, four spring bars 18 are similarly arranged.

  When the rotor 1 rotates, a magnetic attractive force acts on the stator core 5 and the stator core 5 vibrates. In the present embodiment, this vibration forms an annular vibration mode having four nodes that occur every 90 degrees in the circumferential direction. A broken line C shown in FIG. 2 shows an amplitude distribution of an annular vibration mode having four nodes. These four nodes are generated in the vicinity of the installation positions of the vibration control mechanism 21 and the spring bar 18.

  The vibration control mechanism 21 has a function of suppressing a part of vibration generated in the stator core 5. Below, the effect | action of the rotary electric machine of this embodiment is demonstrated.

  When the rotor 1 rotates, a magnetic attraction force acts on the stator core 5 as described above, and this magnetic attraction force becomes an excitation force to generate magnetic vibration in the stator core 5. This magnetic vibration is a vibration that is displaced in the radial direction, and an amplitude distribution C of an annular natural vibration mode is formed along the circumferential direction of the stator core 5.

  Here, the effect | action of the vibration system of the rotary electric machine in this embodiment is demonstrated using FIGS. 3-5 using a 1 degree-of-freedom vibration model as an example.

  FIG. 3 is a diagram in which the rotating electrical machine in the example of FIG. 1 is modeled as a vibration system with one degree of freedom (radial direction of the rotating electrical machine). 3A is a vibration model of the entire system 31 showing a radial vibration system of the entire rotating electrical machine, and FIG. 3B shows a low-order mode in FIG. 3A, and FIG. ) Shows a higher-order mode in FIG.

  3A, 3 </ b> B, and 3 </ b> C, the first mass 37 indicates the mass of the stator core 5 and has a degree of freedom in the radial direction. The first spring element 39 indicates the rigidity of the stator core 5 in the radial direction. The second mass 41 indicates the mass of the weight 23 of the damping mechanism 21, and the second spring element 43 indicates the radial rigidity of the elastic member 25 of the damping mechanism 21. Here, the arrow 70 indicates the direction and amount in which the first mass 37 is displaced, and the arrow 71 indicates the direction and amount in which the second mass 41 is displaced. Here, the vibration model of the whole system 31 is a first vibration system 33 composed of a first mass 37 and a first spring element 39, and a second vibration system composed of a second mass 41 and a second spring element 43. This is the sum of 35.

When the value of the first mass 37 is m1 and the elastic coefficient of the first spring element 39 is k1, the natural frequency of the first vibration system 33 composed of the first mass 37 and the first spring element 39 is expressed by the formula ( 4).
f ₁ = 1 / (2π) · √ (k ₁ / m ₁ ) (4)

A second vibration system 35 having a second mass 41 having a mass m2 and a second spring element 43 having an elastic coefficient k2 is attached to the first mass 37, that is, the damping mechanism 21. In the second spring element 43, the natural frequency of the second vibration system 35 when the contact point of the first mass 37 is fixed is expressed by Expression (5).
f ₂ = 1 / (2π) · √ (k ₂ / m ₂ ) (5)

At this time, the natural frequency f of the entire system 31 including the first vibration system 33 and the second vibration system 35 can be obtained by solving the equation (6).
λ ⁴ − (1 + ν ² + ν ² · R) · λ ² + ν ² = 0 (6)

Here, if f is the natural frequency of the entire system 31, R, ν, and λ are expressed by the following equations (7), (8), and (9), respectively.
R = m ₂ / m ₁ (mass ratio of weight 23 of damping mechanism 21 and stator core 5) (7)
ν = f ₂ / f ₁ (ratio of natural frequencies of vibration control mechanism 21 and stator core 5) (8)
λ = f / f ₁ (ratio of natural frequencies of the entire system 31 and the stator core 5) (9)

  FIG. 4 shows the natural vibration of the entire system 31 with respect to the ratio ν of the natural frequencies of the second vibration system 35 (damping mechanism 21) and the first vibration system 33 (stator core 5) when R = 0.05. It is the graph which showed the relationship of number ratio (lambda). A curve L indicates a low-order mode, and a curve H indicates a high-order mode.

The natural frequency f of the entire system 31 to which the vibration damping mechanism 21 is attached has two natural frequencies f _{1, that} is, a low-order natural frequency f _L and a high-order natural frequency f _H. Separated.

As ν increases, the natural frequency ratio of the low-order mode L asymptotically approaches λ = 1, and the natural frequency ratio of the high-order mode H approaches asymptotically λ = ν. As described above, the natural frequency f _L and f _H of the entire system 31 can be changed by adjusting the mass ratio R and the natural frequency ratio ν of the stator core 5 and the vibration control mechanism 21.

In the present embodiment, by adjusting the mass ratio R and the natural frequency ratio ν, the low-order natural frequency f _L is lower than the excitation frequency f _Mg due to the magnetic attractive force (excitation force) of the rotor 1. set to be, the natural frequency f _H of the higher order is set to be higher than the vibration frequency f _Mg.

At this time, as shown in FIG. 3B, the natural vibration mode corresponding to the low-order natural frequency f _L is the first mass 37, that is, the radial displacement of the mass of the stator core 5 is the first. The two masses 41, that is, the weights 23 are in a common mode that is displaced in the same direction. On the other hand, as shown in FIG. 3C, the natural vibration mode corresponding to the higher order natural frequency f _H is the second mass 41, that is, the weight with respect to the first mass 37, that is, the radial displacement of the stator core 5. 23 becomes a reverse phase mode in which they are displaced in directions opposite to each other.

  As described above, when the natural frequency and the natural vibration mode corresponding to the natural frequency are known in advance, the vibration that is actually generated overlaps (adds) the response for each natural vibration mode. Can be determined by

  FIG. 5A is a graph showing the responses of the low-order mode and the high-order mode as a function of frequency. A curve L in the figure indicates a low-order mode, and a curve H indicates a high-order mode. FIG. 5B is a graph showing the phase of FIG. Similar to FIG. 5A, the curve L indicates the low-order mode, and the curve H indicates the high-order mode. FIG. 5C is a graph showing the response obtained by superimposing the responses of the low-order mode and the high-order mode as a function of frequency.

As shown in FIG. 5A, the amplitude of the low-order mode L increases as the frequency increases and becomes maximum at f _L , and when it becomes larger than f _L , the amplitude decreases and gradually approaches 0. Similarly, the amplitude of the higher order mode H is maximized by increased with increasing frequency f _H, the amplitude becomes larger than f _H is asymptotic to 0 decreases. In between the two natural frequencies f _L and f _H amplitudes of the two modes are approximately equal.

As shown in FIG. 5 (b), the phase response of the low-order mode L and higher mode H is, between f _L and f _H, a difference of approximately 180 degrees. That is, the responses of the low-order mode L and the high-order mode H between f _L and f _H indicate that the amplitudes are substantially equal to each other and the displacement directions vibrate in reverse.

When determining the actual amplitude by superimposing responses of the low-order mode L and higher mode H, as shown in FIG. 5 (c), in between f _L and f _H, the amplitude decreases. In the frequency band where the responses of the low-order mode L and the high-order mode H are equal, the actual amplitude approaches almost zero.

The mass of the weight 23 of the vibration control mechanism 21 and the elastic coefficient of the elastic member 25 are adjusted so that the excitation frequency by the rotor 1 is substantially the same as this frequency band. As a result, the actual amplitude of vibration can be suppressed. In other words, by installing the vibration damping mechanism 21, between f _L and f _H, it can respond lower order mode L and higher mode H is offset, to minimize the amplitude of the stator core 5 .

  As for the natural annular vibration mode of the stator core 5, as in the example of the one-degree-of-freedom vibration model, separation of natural frequencies and superposition of mode responses are established. Hereinafter, the operation of the example in which the vibration control mechanism 21 is attached to the two-pole turbine generator will be described with reference to FIGS. 2, 6, and 7.

  FIG. 6 is a model diagram showing the first natural annular vibration mode when the damping mechanism 21 is not attached to the stator core 5, and the curve A shows the first natural annular vibration mode. FIG. 7 is a model diagram showing the second natural annular vibration mode, and a curve B shows the second natural annular vibration mode.

  As shown in FIGS. 6 and 7, when the damping mechanism 21 is not attached to the stator core 5, the stator core 5 has two natural annular vibration modes, that is, the first natural annular vibration. It vibrates in a mode in which the mode responses of mode A and second natural annular vibration mode B are superimposed. The first natural annular vibration mode A includes four nodes having amplitudes of 0 as indicated by four points a1, a2, a3, and a4 shown on the first natural annular vibration mode A in FIG. Have. The amplitude distribution in the circumferential direction in the electromagnetic vibration that vibrates in the radial direction is formed so that the nodes and the abdomen are alternately generated along the circumferential direction, thereby forming a substantially elliptical shape. The second natural annular vibration mode B has substantially the same natural frequency as that of the first natural vibration mode, and the four points b1, b2, shown on the second natural annular vibration mode B in FIG. As shown in b3 and b4, it has four nodes having an amplitude of 0, and has the same shape as the first natural annular vibration mode A, and the major axes are formed at an angle of 45 degrees with each other. .

  In the first and second natural annular vibration modes A and B, if the structure of the stator core 5 is symmetrical with respect to the rotational axis, the natural frequencies corresponding to the structures are equal.

  The position corresponding to the abdomen of the first natural ring vibration mode A is the node of the second natural ring vibration mode B. The position corresponding to the node portion of the first natural annular vibration mode A is the abdomen of the second natural annular vibration mode B.

  As shown in FIG. 2, the damping mechanism 21 is attached to a portion corresponding to the abdomen of the first natural vibration mode A on the outer peripheral surface of the stator core 5.

  By attaching the damping mechanism 21, the first natural ring vibration mode A has two natural vibration frequencies corresponding to this mode. And higher order modes appear. The radial displacement of the weight 23 of the damping mechanism 21 is the same phase in the low-order mode and the opposite phase in the higher-order mode with respect to the radial displacement of the stator core 5 at the mounting position of the damping mechanism 21. Become.

As in the example of the one-degree-of-freedom vibration model, the natural frequency f _L in the low-order mode is set to be lower than the excitation frequency f _Mg due to the magnetic attractive force (excitation force) of the rotor 1. and, natural frequency f _H in higher order modes is set to be higher than the vibration frequency f _Mg. At this time, the mass of the weight 23 is preferably about 5% (R = 0.05) of the mass of the stator core 5.

Thereby, the mode responses of the low-order mode and the high-order mode are approximately equal in amplitude and opposite in phase between f _L and f _H. Therefore, it is possible to suppress actual vibration in the frequency band near f _Mg . That is, by attaching the vibration control mechanism 21, the amplitude of the abdomen of the first natural annular vibration mode A can be reduced.

  On the other hand, in the second natural ring vibration mode, since the vibration suppression mechanism 21 is attached to a portion corresponding to the node of this mode, the natural vibration corresponding to this mode is provided even if the vibration suppression mechanism 21 is installed. The number does not change.

  That is, since the second natural annular vibration mode B is not affected by the vibration control mechanism 21, the mode response to the excitation force is maintained.

  The fixed obtained by superimposing the response of the first natural annular vibration mode A whose abdominal amplitude is reduced by the vibration suppression mechanism 21 and the response of the second natural annular vibration mode B not affected by the vibration suppression mechanism 21. The amplitude distribution C (absolute value) of the annular vibration mode of the core 5 is such that the abdomen and nodes of vibration alternately occur at equal intervals along the circumferential direction as shown by the curve C in FIG. Become. In this case, since the response of the first natural ring vibration mode A hardly appears in the response due to the four-node ring natural vibration mode which is a multiple root, the amplitude distribution of the stator core 5 is not rotationally moved. Standing.

  As a result, the curve C, that is, the shape of the amplitude distribution C in the circumferential direction of the stator core 5 has nodes at the mounting position of the vibration damping mechanism 21, and the nodes are spaced at 90 ° intervals in the circumferential direction with reference to this node. It is formed. Further, the amplitude distribution C of the annular vibration mode becomes a standing wave having an abdomen at a position moved 45 degrees along the circumferential direction from each of the four nodes. Note that the above 90 degrees corresponds to a value obtained by dividing 360 degrees by the number of nodal parts in the ring vibration mode, that is, four.

  In the two-pole turbine generator, the circumferential distribution of the magnetic attractive force of the rotor 1 is an annular vibration mode having four nodes that are twice the number of poles. This annular vibration mode has the same shape as the annular vibration mode C generated in the stator core 5.

  As can be understood from the above description, by arranging the vibration control mechanism 21, it is possible to generate a node portion in the amplitude distribution C of vibration generated in the stator core 5.

  The stator core 5 and the stator frame 7 are connected to each other through spring bars 18 and the like at four nodes where the circumferential amplitude distribution in the radial vibration of the stator core 5 becomes small. For this reason, it is possible to suppress the magnetic vibration of the stator core 5 caused by the magnetic attractive force of the rotor 1 from propagating to the stator frame 7.

  Furthermore, since the leg plate 19 is attached in the vicinity of the node portion, it is also possible to suppress propagation through the stator frame 7 and the leg plate 19 to the foundation on which the rotating electrical machine is installed.

[Second Embodiment]
A second embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 8 and 9. FIG. 8 is a schematic longitudinal sectional view of the rotating electrical machine of the present embodiment, and FIG. 9 is a schematic transverse sectional view taken along arrow IX-IX in FIG. In addition, this embodiment is a modification of 1st Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, the iron core support plates 13 a and 13 b are directly attached to the inner surface of the outer peripheral plate 15 without using the spring bar 18 used in the first embodiment. At this time, a notch 51 is formed on a side surface other than the contact portion with the outer peripheral plate 15 on the side surfaces on the outer peripheral side in the radial direction of the iron core support plates 13a and 13b, that is, on the side surface other than the position facing the node portion of the annular vibration mode. It is formed so as not to contact the outer peripheral plate 15.

  According to this embodiment, if the rotating electrical machine has a smaller magnetic attraction force of the rotor 1 than the first embodiment, in addition to the effects of the first embodiment, the stator can be made more compact. become.

[Third Embodiment]
A third embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 10 and 11. FIG. 10 is a schematic vertical cross-sectional view of the rotating electrical machine of the present embodiment, and FIG. 11 is a schematic cross-sectional view taken along the line XI-XI in FIG. In addition, this embodiment is a modification of 1st Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, the leg plate 19 that supports the stator frame 7 is disposed outside the abdomen of the stator core 5 in the annular vibration mode.

  The vibration control mechanism 21 is arranged so as to reduce the amplitude of the abdomen in the second natural annular vibration mode. Thereby, the vibration damping mechanism 21 is attached to the position moved 45 degrees along the circumferential direction with respect to the vibration damping mechanism 21 arranged right above the rotation axis shown in the first embodiment. In addition, you may fix to the leg board 19 in the state which rotated the whole stator of 1st Embodiment 45 degree | times along the circumferential direction.

  In the first embodiment, since the stator core 5 is connected to the stator frame 7 at the node of the annular vibration mode C of the stator core 5, vibration propagation to the stator frame 7 is suppressed, but vibration propagation is completely performed. In some cases, it cannot be suppressed. For this reason, it is desirable that the connecting portion between the stator frame 7 and the stator core 5 and the position where the stator frame 7 is in contact with the foundation are located at separate positions.

  According to the present embodiment, the leg plate 19 is disposed at a position farthest from the connection position between the stator core 5 and the stator frame 7. Thereby, since the vibration transmitted to the leg plate 19 from the connection position of the stator core 5 and the stator frame 7 is suppressed, the vibration transmitted from the leg plate 19 to the foundation on which the rotating electrical machine is installed is suppressed.

[Fourth Embodiment]
A fourth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 12 is a schematic cross-sectional view of the rotating electrical machine of the present embodiment. In addition, this embodiment is a modification of 1st Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, there are two vibration damping mechanisms 21, that is, a first vibration damping mechanism 21a and a second vibration damping mechanism 21b. The first vibration control mechanism 21a is located at the position corresponding to the abdomen of the first natural ring mode, and is disposed at a position directly above the rotation axis in the example of FIG. 12, and the second vibration control mechanism 21b is the second natural circle mode. It is arranged at a position corresponding to the abdomen of the ring vibration mode. The first and second vibration damping mechanisms 21a and 21b are disposed on the cross section perpendicular to the rotation axis direction of the stator core 5 at an angle of 45 degrees along the circumferential direction. The spring bars 18 are arranged at regular intervals at intervals along the circumferential direction.

  The natural frequency of the first natural ring vibration mode is separated into two by the first damping mechanism 21a as in the first embodiment, and the low-order mode and the high frequency corresponding to each of these natural frequencies are separated. The next mode occurs. This reduces the amplitude at the excitation frequency. Similarly, the second vibration control mechanism 21b also reduces the amplitude of the abdomen in the second natural annular vibration mode.

  Thereby, the vibration of the stator core 5 is suppressed in all circumferential directions.

[Fifth Embodiment]
5th Embodiment of the rotary electric machine which concerns on this invention is described using FIGS. 13-15. FIG. 13 is a schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. 14 is a schematic cross-sectional view taken along the arrow XIV-XIV in FIG. FIG. 15 is a schematic cross-sectional view taken along arrow XV-XV in FIG. In addition, this embodiment is a modification of 4th Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 4th Embodiment, and duplication description is abbreviate | omitted.

  In this embodiment, as shown in these FIGS. 13-15, it has the two damping mechanisms 21, ie, the 1st damping mechanism 21a, and the 2nd damping mechanism 21b. These first and second damping mechanisms 21a and 21b are respectively arranged on the outer peripheral surfaces of the stator core 5 in the vicinity of both ends in the rotation axis direction, and the first damping mechanism 21a is arranged on the left side in FIG. The second vibration damping mechanism 21b is disposed on the right side.

  As shown in FIGS. 13 and 14, the first and second vibration control mechanisms 21a and 21b are attached at an angle of 45 degrees to each other along the circumferential direction.

  As shown in FIG. 13, the four spring bars 18 arranged in the vicinity of the first damping mechanism 21a are arranged between the first and third diaphragms 17a and 17c, and the first and third It is fixed by third partition plates 17a and 17c. Further, as shown in FIG. 14, four spring bars 18 are arranged every 90 degrees along the circumferential direction with reference to the position where the first vibration control mechanism 21a is arranged.

  Further, as shown in FIG. 15, the four spring bars 18 arranged in the vicinity of the second vibration damping mechanism 21b are arranged between the second diaphragm 17b and the third diaphragm 17c, and the second 2 and the third partition plates 17b and 17c. Further, four spring bars 18 are arranged every 90 degrees along the circumferential direction with reference to the position where the second vibration control mechanism 21b is arranged.

  Therefore, in FIG. 13, the arrangement of the left spring bars 18 of the third partition plate 17c shown in FIG. 14 and the arrangement of the right spring bars 18 shown in FIG.

  In a large-capacity turbine generator, the stator core 5 is lengthened. Therefore, when the vibration damping mechanism 21 is attached only to the central portion in the rotation axis direction of the stator core 5 as in the first embodiment, the weight 23 is increased. There is a need to.

  Since the amplitude of the stator core 5 is substantially uniform in the rotation axis direction, the same effect as in the first embodiment can be obtained even if the damping mechanism 21 is attached in the vicinity of the end of the stator core 5 in the rotation axis direction. It is done.

  According to this embodiment, by attaching two damping mechanisms 21, that is, the first damping mechanism 21a and the second damping mechanism 21b, the weights arranged on the first and second damping mechanisms 21a and 21b, respectively. The mass of 23 can be reduced, and the stator can be made more compact.

  Further, by arranging the first vibration control mechanism 21a and the second vibration control mechanism 21b at an interval of 45 degrees along the circumferential direction, the same effect as that of the fourth embodiment can be obtained.

[Sixth Embodiment]
A sixth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 16 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. This embodiment shows a more specific arrangement example of the weight 23 and the elastic member 25 of the vibration damping mechanism 21 in the first to fifth embodiments, and is the same as the first embodiment or Similar parts are denoted by the same reference numerals, and redundant description is omitted.

  Both end support beams 55 extending in the direction of the rotation axis are supported and fixed to the side surfaces of the adjacent rib plates 12 on the radially outer side surface of the stator core 5 of the present embodiment. The both end support beams 55 have the same function as the elastic member 25 of the vibration damping mechanism 21.

  A weight 23 is disposed at substantially the center of the both end support beams 55. The weight 23 is configured such that a plurality of, for example, metallic rectangular flat plates are stacked in the radial direction, and the number of stacked layers can be adjusted. The mass of the weight 23 can be adjusted by the number of stacked flat plates.

  The vibration control mechanism 21 includes the support beams 55 at both ends, a laminated flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position, mass adjustment, and the like are facilitated on the radially outer side surface of the stator core 5.

[Seventh Embodiment]
A seventh embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 17 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. The present embodiment is a modification of the sixth embodiment, and the same or similar parts as those of the sixth embodiment are denoted by the same reference numerals, and redundant description is omitted.

  In the stator core 5 of the present embodiment, both-end support beams 55 are fixed to the core presser plate 14 and the rib plate 12 adjacent thereto. The both end support beams 55 are supported at both ends by the side surface in the radial direction of the iron core retainer plate 14 and the side surface of the rib plate 12 adjacent to the iron core retainer plate 14. The both end support beams 55 have the same function as the elastic member 25 of the vibration damping mechanism 21.

  As in the sixth embodiment, a weight 23 is disposed at substantially the center of the both end support beams 55. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated.

  The vibration control mechanism 21 includes the support beams 55 at both ends, a laminated flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position, mass adjustment, and the like are facilitated on the radially outer side surface of the stator core 5.

[Eighth Embodiment]
An eighth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 18 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. In addition, this embodiment is a modification of 7th Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 7th Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, a cantilever beam 53 extending from the end face of the iron core holding plate 14 not holding the stator iron core 5 toward the opposite side of the spring bar 18 in the rotation axis direction is attached. This cantilever beam 53 has the same function as the elastic member 25 of the vibration damping mechanism 21.

  A weight 23 is disposed at the tip of the cantilever 53. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated.

  The vibration damping mechanism 21 includes these cantilever beams 53 and laminated flat plate weights 23 and the like. According to this configuration, the vibration damping mechanism 21 is attached to the vicinity of the outer peripheral portion of the stator core 5 and to the end portion in the rotation axis direction. For this reason, the outer diameter of the outer peripheral plate 15 can be reduced so that the inner surface of the outer peripheral plate 15 is brought closer to the outer surface of the stator core 5.

  As a result, the rotating electrical machine can be configured more compactly.

[Ninth Embodiment]
A ninth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 19 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. In addition, this embodiment is a modification of 6th Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 6th Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, a cantilever beam 53 extending in the rotation axis direction is attached from one end face of the rib plate 12. This cantilever beam 53 has the same function as the elastic member 25 of the vibration damping mechanism 21.

  A weight 23 is disposed at the tip of the cantilever 53. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated.

  The vibration control mechanism 21 includes the support beams 55 at both ends, a laminated flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position, mass adjustment, and the like are facilitated on the radially outer side surface of the stator core 5.

[Tenth embodiment]
A tenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 20 is a partial schematic longitudinal cross-sectional view of the rotating electrical machine of the present embodiment, and FIG. 21 is a schematic cross-sectional view taken along arrow XXI-XXI in FIG. In addition, this embodiment is a modification of 6th Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 6th Embodiment, and duplication description is abbreviate | omitted. In this embodiment, an example in which the spring bar 18 is not arranged as in the second embodiment will be described.

  In this embodiment, two substantially parallelepiped seat plates 57 extending in the rotation axis direction between the iron core support plate 14 and the rib plate 12 adjacent thereto are arranged in the circumferential direction on the outer peripheral side surface of the stator iron core 5. It is attached.

  Both end support beams 55 extending along the circumferential direction are attached so that both ends are supported by the radially outer side surfaces of the two seat plates 57. The both end support beams 55 have the same function as the elastic member 25 of the vibration damping mechanism 21.

  As in the sixth embodiment, a weight 23 is disposed at substantially the center of the both end support beams 55. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated. The seat plate 57 can also be disposed between adjacent rib plates.

  The vibration control mechanism 21 includes the seat plate 57, the both end support beams 55, the stacked flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position and mass adjustment are facilitated on the radially outer side surface of the stator core 5.

[Eleventh embodiment]
An eleventh embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 22 and 23. 22 is a schematic longitudinal sectional view of the rotor 1 of the rotating electrical machine according to the present embodiment, and FIG. 23 is a schematic transverse sectional view taken along the line XXIII-XXIII in FIG. A broken line C1 in FIG. 23 is a schematic curve showing the natural annular vibration mode when the vibration suppression mechanism 21 is not provided, and a broken line C2 is a schematic curve showing the natural circular vibration mode when the vibration suppression mechanism 21 is attached. .

  In addition, this embodiment is a modification of 1st Embodiment, Comprising: The same code | symbol is attached | subjected to the same part or similar part as 1st Embodiment, and duplication description is abbreviate | omitted.

  In the present embodiment, the vibration damping mechanism 21 is disposed on the radially outer side surface of the outer peripheral plate 15 of the stator frame 7 just above the substantially central portion in the rotation axis direction.

  If the vibration damping mechanism 21 is not provided, the stator core 5 vibrates in the first natural ring vibration mode and the second natural ring vibration mode as described in the first embodiment. This vibration is propagated to the stator frame 7 via the spring bar 18 and the like, and the stator frame 7 vibrates in the same manner as the stator core 5.

  At this time, the stator frame 7 vibrates in two natural ring vibration modes, that is, a first natural ring vibration mode and a second natural ring vibration mode. These first and second natural annular vibration modes have a substantially elliptical shape having four nodes, and the major axes of the ellipses form an angle of 45 degrees with each other.

  Further, the natural frequency of each of the first and second natural annular vibration modes is substantially equal since the stator frame 7 is a substantially rotationally symmetric structure. Since the leg plate 19 and the like are attached to the stator frame 7, it is not a completely rotationally symmetric structure, but these influences are small and can be ignored.

  In the design of the stator frame 7, the thickness of the outer peripheral plate 15 and the partition plate 17a are set to be sufficiently higher than the excitation frequency so as not to resonate with the excitation frequency (twice the rotation frequency) due to the magnetic attraction force of the rotor 1. , 17b, 17c and the thickness thereof may be set in advance.

  In the present embodiment, as in the first embodiment, the stator core 5 and the stator frame 7 are constituted by the first to third partition plates 17a, 17b, 17c, the spring bar 18, the core support plates 13a, 13b, and the like. They are connected to each other via connecting means configured.

  The vibration damping mechanism 21 of the present embodiment is located outside the position corresponding to the abdomen of the first natural ring vibration mode of the stator core 5 and at the radially outer position of the connecting means such as the spring bar 18. is set up.

  The vibration damping mechanism 21 acts in the same manner as in the first embodiment so as to suppress magnetic vibration that propagates to the stator frame 7 via connecting means such as the spring bar 18. For this reason, the amplitude of the vibration propagated to the stator frame 7 becomes small.

  Note that, as shown by broken lines C1 and C2 in FIG. 23, the vibration propagating to the stator frame 7 is suppressed by the damping mechanism 21, but is slightly propagated. In the vibration mode (broken line C2) of the propagated vibration, nodes appear at four locations every 90 degrees in the circumferential direction with reference to the position where the vibration damping mechanism 21 is attached, as in the first embodiment.

  By attaching the leg plate 19 to a position corresponding to this node, it is possible to suppress the vibration of the stator frame 7 from being propagated to the foundation on which the rotating electrical machine is installed.

  The mass of the weight 23 of the vibration control mechanism 21 is desirably about 5% of the mass of the structure that suppresses vibration. In the first embodiment, the mass of about 5% of the mass of the stator core 5 is required, but the weight 23 of the present embodiment may be about 5% of the mass of the stator frame 7. Since the stator frame 7 has a smaller mass than the stator core 5, the vibration damping mechanism 21 can be made smaller than that of the first embodiment.

  Therefore, the rotating electrical machine can be made more compact.

[Twelfth embodiment]
A twelfth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 24 is a schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. Note that this embodiment is a modification of the eleventh embodiment, and the same reference numerals are given to the same or similar parts as those of the eleventh embodiment, and the duplicated description is omitted.

  In the present embodiment, two vibration damping mechanisms 21, that is, a first vibration damping mechanism 21 a and a second vibration damping mechanism 21 b are arranged on the outer side of the outer peripheral plate 15 at intervals from each other along the rotation axis direction. The first damping mechanism 21a is disposed outside the left end portion of the stator core 5 in FIG. 24, and the second damping mechanism 21b is disposed outside the right end portion.

  In a large-capacity turbine generator, the stator core 5 becomes long. Therefore, if the vibration damping mechanism 21 is attached only to the center portion of the stator core 5 as in the eleventh embodiment, it is necessary to enlarge the weight 23. is there.

  Since the amplitude of the stator core 5 is substantially uniform in the rotation axis direction, the same effect as in the eleventh embodiment can be obtained even if the damping mechanism 21 is attached in the vicinity of the end of the stator core 5 in the rotation axis direction. It is done.

  According to the present embodiment, two vibration damping mechanisms 21, that is, a first vibration damping mechanism 21a and a second vibration damping mechanism 21b, are attached to the first and second vibration damping mechanisms 21a and 21b, respectively. The mass of the weight 23 can be reduced, and the stator can be made more compact.

[Thirteenth embodiment]
A thirteenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 25 and 26. 25 is a schematic longitudinal sectional view of the rotating electrical machine according to the present embodiment, and FIG. 26 is a schematic transverse sectional view taken along the line XXVI-XXVI in FIG. Note that this embodiment is a modification of the eleventh embodiment, and the same reference numerals are given to the same or similar parts as those of the eleventh embodiment, and the duplicated description is omitted.

  In the present embodiment, the iron core support plates 13 a and 13 b are directly attached to the inner surface of the outer peripheral plate 15 without using the spring bar 18 used in the eleventh embodiment. At this time, a notch 51 is formed on a side surface other than the contact portion with the outer peripheral plate 15 on the side surfaces on the outer peripheral side in the radial direction of the iron core support plates 13a and 13b, that is, on the side surface other than the position facing the node portion of the annular vibration mode. It is formed so as not to contact the outer peripheral plate 15.

  According to this embodiment, if the rotating electrical machine has a smaller magnetic attraction force of the rotor 1 than the eleventh embodiment, in addition to the effects of the eleventh embodiment, the stator can be made more compact. become.

[Fourteenth embodiment]
A fourteenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 27 and 28. 27 is a schematic longitudinal sectional view of the rotating electrical machine of the present embodiment, and FIG. 28 is a schematic transverse sectional view taken along the line XXVIII-XXVIII in FIG. Note that this embodiment is a modification of the eleventh embodiment, and the same reference numerals are given to the same or similar parts as those of the eleventh embodiment, and the duplicated description is omitted.

  In the present embodiment, as shown in FIGS. 27 and 28, there are two vibration damping mechanisms 21, that is, a first vibration damping mechanism 21a and a second vibration damping mechanism 21b. The first vibration control mechanism 21 a is disposed outside the position corresponding to the abdomen of the first natural ring mode of the stator core 5, and the second vibration control mechanism 21 b is the second natural ring of the stator core 5. It is arranged outside the position corresponding to the abdomen in the vibration mode. The first and second vibration damping mechanisms 21a and 21b are disposed on the cross section perpendicular to the rotation axis direction of the stator core 5 at an angle of 45 degrees along the circumferential direction. The spring bars 18 are arranged at regular intervals at intervals along the circumferential direction.

  The natural frequency of the first natural ring vibration mode is separated into two by the first damping mechanism 21a as in the eleventh embodiment, and the low-order mode and the high frequency corresponding to each of these natural frequencies are separated. The next mode occurs. This reduces the amplitude at the excitation frequency. Similarly, the second vibration control mechanism 21b also reduces the amplitude of the abdomen in the second natural annular vibration mode.

  Thereby, the vibration of the stator core 5 is suppressed in all circumferential directions.

[Fifteenth embodiment]
A fifteenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 29 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. The present embodiment shows a more specific arrangement example of the weight 23 and the elastic member 25 of the vibration damping mechanism 21 in the 11th to 14th embodiments, and is the same as or similar to the 11th embodiment. Parts are denoted by the same reference numerals, and redundant description is omitted.

  In the present embodiment, a cantilever beam 53 extending from the end face of the second partition plate 17b that is not in contact with the spring bar 18 toward the opposite side of the spring bar 18 in the rotation axis direction is disposed. This cantilever beam 53 has the same function as the elastic member 25 of the vibration damping mechanism 21.

  For example, a weight 23 is disposed at the tip of the cantilever 53. The weight 23 is configured such that a plurality of, for example, metallic rectangular flat plates are stacked in the radial direction, and the number of stacked layers can be adjusted. The mass can be adjusted by the number of stacked flat plates.

  The vibration damping mechanism 21 includes these cantilever beams 53 and laminated flat plate weights 23 and the like. According to this configuration, the vibration control mechanism 21 is attached to the outer side in the rotation axis direction than the end portion in the rotation axis direction of the stator core 5. For this reason, the outer diameter of the outer peripheral plate 15 can be reduced so that the inner surface of the outer peripheral plate 15 is brought closer to the outer surface of the stator core 5.

  As a result, the rotating electrical machine can be configured more compactly.

[Sixteenth Embodiment]
A sixteenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIG. FIG. 30 is a partial schematic longitudinal sectional view of the rotating electrical machine of the present embodiment. The present embodiment is a modification of the fifteenth embodiment, and the same or similar parts as those of the fifteenth embodiment are denoted by the same reference numerals, and redundant description is omitted.

  In this embodiment, two substantially rectangular parallelepiped seat plates 57 extending in the circumferential direction are attached to the outer surface of the outer peripheral plate 15 side by side in the rotation axis direction.

  Both-end support beams 55 extending in the direction of the rotation axis are attached so that both ends are supported on the radially outer side surfaces of the two seat plates 57. The both end support beams 55 have the same function as the elastic member 25 of the vibration damping mechanism 21.

  As in the fifteenth embodiment, a weight 23 is disposed at substantially the center of the both end support beams 55. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated.

  The vibration control mechanism 21 includes the seat plate 57, the both end support beams 55, the stacked flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position, mass adjustment, and the like are facilitated on the outer side surface of the outer peripheral plate 15.

[Seventeenth embodiment]
A seventeenth embodiment of the rotating electrical machine according to the present invention will be described with reference to FIGS. 31 and 32. FIG. 31 is a schematic vertical cross-sectional view of the rotating electrical machine of the present embodiment, and FIG. 32 is a schematic cross-sectional view taken along the arrow XXXII-XXXII in FIG. Note that this embodiment is a modification of the fifteenth embodiment, and the same or similar parts as those of the fifteenth embodiment are denoted by the same reference numerals, and redundant description is omitted.

  In the present embodiment, two substantially cubic seats 59 arranged in the circumferential direction on the outer surface of the outer peripheral plate 15 are installed, and beams 63 are bridged and fixed to these seats 59. A fixing member 61 is provided. Two fixing members 61 are arranged side by side in the direction of the rotation axis and spaced from each other. Further, both end support beams 55 extending in the rotation axis direction are attached to the beams 63 of the fixing member 61, respectively. Both ends of the both-end support beam 55 are fixed to the fixing member 61, respectively. The both end support beams 55 have the same function as the elastic member 25 of the vibration damping mechanism 21.

  As in the sixth embodiment, a weight 23 is disposed at the approximate center of the both end support beams 55. As in the sixth embodiment, the weight 23 can be adjusted by the number of flat plates on which the mass is laminated.

  The vibration damping mechanism 21 includes the fixing member 61, the both end support beams 55, the laminated flat plate weight 23, and the like. By configuring the vibration damping mechanism 21 as described above, adjustment of the attachment position, mass adjustment, and the like are facilitated on the outer side surface of the outer peripheral plate 15.

[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 above-described embodiment, an example in which one or two vibration control mechanisms 21 are attached has been described, but the present invention is not limited to this. Three or more may be arranged in the direction of the rotation axis, and the mass of the weight 23 of each vibration control mechanism 21 may be reduced.

It is a schematic longitudinal cross-sectional view of the rotary electric machine of 1st Embodiment which concerns on this invention. FIG. 2 is a schematic cross-sectional view taken along the line II-II in FIG. 1. (A) is a vibration model of the vibration damping mechanism and laminated core of FIG. 1, (b) is a model diagram showing a lower order mode of (a), and (c) is a model diagram showing a higher order mode of (a). . 7 is a graph showing the relationship of the natural frequency ratio λ of the entire system to the natural frequency ratio ν of the second vibration system and the first vibration system when R = 0.05. (A) is a graph showing the response of each of the low-order mode and the high-order mode as a function of frequency, (b) is a graph showing the phase of (a), and (c) is the response of the low-order mode and the high-order mode. It is the graph which expressed the superimposed response as a function of frequency. It is a model figure which shows the 1st natural ring vibration mode of the stator core of embodiment of FIG. It is a model figure which shows the 2nd natural ring vibration mode of the stator core of embodiment of FIG. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 2nd Embodiment which concerns on this invention. FIG. 9 is a schematic cross-sectional view taken along arrow IX-IX in FIG. 8. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 3rd Embodiment which concerns on this invention. It is a XI-XI arrow schematic cross-sectional view of FIG. It is a schematic cross-sectional view of the rotating electrical machine of the fourth embodiment according to the present invention. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 5th Embodiment which concerns on this invention. FIG. 14 is a schematic cross-sectional view taken along arrow XIV-XIV in FIG. 13. FIG. 14 is a schematic cross-sectional view taken along arrow XV-XV in FIG. 13. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 6th Embodiment which concerns on this invention. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 7th Embodiment which concerns on this invention. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 8th Embodiment which concerns on this invention. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 9th Embodiment which concerns on this invention. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 10th Embodiment which concerns on this invention. FIG. 21 is a schematic cross-sectional view taken along the arrow XXI-XXI in FIG. 20. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 11th Embodiment based on this invention. FIG. 23 is a schematic cross-sectional view taken along the line XXIII-XXIII in FIG. 22. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 12th Embodiment based on this invention. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 13th Embodiment based on this invention. FIG. 26 is a schematic cross-sectional view taken along arrow XXVI-XXVI in FIG. 25. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 14th Embodiment which concerns on this invention. FIG. 28 is a schematic cross-sectional view taken along arrow XXVIII-XXVIII in FIG. 27. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 15th Embodiment based on this invention. It is a partial schematic longitudinal cross-sectional view of the rotary electric machine of 16th Embodiment which concerns on this invention. It is a schematic longitudinal cross-sectional view of the rotary electric machine of 17th Embodiment based on this invention. FIG. 32 is a schematic cross-sectional view taken along arrow XXXII-XXXII in FIG. 31.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 ... Rotor, 5 ... Stator iron core, 7 ... Stator frame, 9 ... Laminated iron core, 9a ... Hollow part, 10 ... Coil, 11 ... Rib bar, 12 ... Rib plate, 13a, 13b ... Iron core support plate, 14 ... Iron core retainer plate, 15 ... outer peripheral plate, 17a ... first partition plate, 17b ... second partition plate, 17c ... third partition plate, 18 ... spring bar, 19 ... leg plate, 21 ... damping mechanism, 21a ... first control Vibration mechanism, 21b ... second vibration control mechanism, 23 ... weight, 25 ... elastic member, 31 ... overall system, 33 ... first vibration system, 35 ... second vibration system, 37 ... first mass, 39 ... first spring Element, 41 ... second mass, 43 ... second spring element, 51 ... notch, 53 ... cantilever, 55 ... both ends supporting beam, 57 ... seat plate, 59 ... seat, 61 ... fixing member, 63 ... beam

Claims (18)

A rotor with a rotation axis;
A substantially hollow cylindrical laminated core in which a plurality of substantially disk-shaped iron plates are laminated in the direction of the rotation axis and arranged to surround the outer periphery of the rotor;
A stator frame that is configured to cover a substantially cylindrical outer circumferential frame of the laminated core from the half radial outside,
A weight arranged on a side surface of the laminated core and configured to be swingable in the radial direction, and an elastically arranged elastically deformable in the radial direction arranged so as to be connected between the weight and the laminated core. A vibration control unit comprising a member;
Stator frame connecting means for connecting the stator frame and the laminated iron core;
Have
The stator frame coupling means is provided in the vicinity of a node portion in an annular vibration mode in which vibration damping portions and nodes are alternately generated along a circumferential direction by arranging the damping portion on a side surface of the laminated core. ,
When the vibration damping portion is not attached, the laminated iron core has vibration antinodes that are approximately equally spaced by twice the number of poles of the rotor along the circumferential direction by the rotating magnetic force excited by the rotor. And the first natural ring vibration mode in which the amplitude is distributed in the circumferential direction so that the nodes can be alternated, and the first natural ring vibration mode has substantially the same natural frequency as the natural frequency corresponding to the first natural ring vibration mode. A second natural annular vibration mode in which the amplitude is distributed in the circumferential direction so that a position corresponding to the antinode of the natural annular vibration mode becomes a node and a position corresponding to the node of the first natural annular vibration mode becomes an antinode; Have
The vibration control unit is attached in the vicinity of the abdomen of the first natural annular vibration mode, and has a third natural annular vibration mode in which antinode vibrations are distributed in the opposite direction to the first natural annular vibration mode. Generating and canceling the response of the first natural ring vibration mode with the response of the third natural ring vibration mode;
Rotating electric machine. The third natural ring vibration mode is set such that the natural frequency of the first natural ring vibration mode when the vibration control unit is attached is lower than the vibration frequency by the magnetic attraction force of the rotor. 2. The mass of the weight and the elastic coefficient of the elastic member are set so that the natural frequency becomes higher than the excitation frequency due to the magnetic attractive force of the rotor. Rotating electric machine. The stator frame connecting means includes
A plurality of rib bars attached to the side surface of the laminated iron core extending in the direction of the rotation axis and arranged at intervals in the circumferential direction;
An iron core support plate, which is attached to the outside of the rib bar so as to surround the laminated iron core, and a plurality of iron core support plates arranged at intervals in the rotation axis direction;
A spring bar that is disposed outside the annular vibration mode node in the circumferential direction, extends in the direction of the rotation axis, and is fixed to the iron core support plate;
A plurality of the iron core support plates are arranged at positions separated in the rotation axis direction, and a partition plate that connects the inside of the stator frame and the spring bar,
The rotating electrical machine according to claim 1, wherein: A plurality of ring-shaped rib plates arranged so as to surround and fix the plurality of rib bars from the outside are arranged at intervals from each other in the rotation axis direction,
The elastic member is a both-end support beam that is supported at both ends by the adjacent rib plate and extends in the direction of the rotation axis, and the weight is disposed substantially at the center of the both-end support beam. The rotating electrical machine according to 3 . A plurality of ring-shaped rib plates arranged so as to surround and fix the plurality of rib bars from the outside are arranged at intervals from each other in the rotation axis direction,
4. The rotation according to claim 3, wherein the elastic member is a cantilever beam fixed to the rib plate and extending in the direction of the rotation axis, and the weight is disposed at a tip portion of the cantilever beam. Electric. A plurality of ring-shaped rib plates arranged so as to surround and fix the plurality of rib bars from the outside are arranged at intervals from each other in the rotation axis direction,
Two seat plates are provided that are fixed to at least one of the rib plates and extend in the direction of the rotation axis, and are arranged on the outer peripheral side surface of the laminated core at intervals in the circumferential direction.
The elastic member is a both-end support beam that is supported at both ends on the radially outer side surfaces of the two seat plates and extends along the circumferential direction, and the weight is disposed substantially at the center of the both-end support beams. The rotating electrical machine according to claim 3, wherein: A rotor with a rotation axis;
A substantially hollow cylinder in which a plurality of substantially disk-shaped iron plates are stacked in the direction of the rotation axis so as to surround the outer periphery of the rotor, and vibrates in a radial direction by a rotating magnetic force generated when the rotor rotates. A laminated iron core,
A stator frame configured to cover the laminated iron core with a substantially cylindrical outer peripheral plate from the radially outer side;
Stator frame connecting means for connecting the stator frame and the laminated iron core;
An elastic member disposed in at least one of the stator frame and the stator frame coupling means and elastically deformable in the radial direction; and a weight connected to the elastic member and configured to be swingable in the radial direction. A vibration control unit,
Have
The stator frame coupling means is provided in the vicinity of a node portion of an annular vibration mode in which vibration antinodes and nodes are alternately generated along the circumferential direction by arranging the damping unit on the stator frame,
When the vibration control portion is not attached, the stator frame has vibration antinodes at equal intervals by twice the number of poles of the rotor along the circumferential direction by the rotating magnetic force excited by the rotor. A first natural annular vibration mode in which amplitudes are distributed in the circumferential direction so that nodes can be alternated, and the first natural vibration frequency having substantially the same natural frequency as the natural frequency corresponding to the first natural annular vibration mode. A second natural annular vibration mode in which the amplitude is distributed in the circumferential direction so that a position corresponding to the antinode of the annular vibration mode becomes a node and a position corresponding to the node of the first natural annular vibration mode becomes an antinode; Have
The vibration damping unit is attached in the vicinity of the outer side of the abdomen of the first natural annular vibration mode, and a third natural annular vibration mode in which antinode vibrations are distributed in the opposite direction to the first natural annular vibration mode. To cancel the response of the first natural ring vibration mode with the response of the third natural ring vibration mode,
Rotating electric machine according to claim. The third natural ring vibration mode is set such that the natural frequency of the first natural ring vibration mode when the vibration control unit is attached is lower than the vibration frequency by the magnetic attraction force of the rotor. 8. The mass of the weight and the elastic coefficient of the elastic member are set so that the natural frequency of the weight is higher than the excitation frequency due to the magnetic attraction force of the rotor. rotary electric machine. The stator frame connecting means includes
A plurality of rib bars attached to the side surface of the laminated iron core extending in the direction of the rotation axis and arranged at intervals in the circumferential direction;
An iron core support plate, which is attached to the outside of the rib bar so as to surround the laminated iron core, and a plurality of iron core support plates arranged at intervals in the rotation axis direction;
A spring bar extending in the rotational axis direction and fixed to the iron core support plate;
A partition plate disposed at both ends of the spring bar and connecting the stator frame and the spring bar;
The rotating electrical machine according to claim 7 or 8, characterized by comprising: 10. The rotating electrical machine according to claim 9, wherein the elastic member is a cantilever beam extending in a rotation axis direction from the partition plate, and the weight is disposed at a tip portion of the cantilever beam . Two seat plates arranged at intervals in the rotation axis direction on the outer side of the outer peripheral plate,
The elastic member is a both-end support beam that is supported at both ends by the two seat plates and extends in the direction of the rotation axis, and the weight is disposed at substantially the center of the both-end support beam. 9. The rotating electrical machine according to 9 . Two seat plates arranged at intervals in the circumferential direction outside the outer peripheral plate,
The elastic member is a both-end support beam that is supported at both ends by the two seat plates and extends in the circumferential direction, and the weight is arranged at substantially the center of the both-end support beam. 9. The rotating electrical machine according to 9 . The rotating electrical machine according to any one of claims 1 to 12, wherein a plurality of the vibration damping units are arranged at intervals in the rotation axis direction . The rotating electrical machine according to claim 13, wherein the two adjacent damping parts are arranged such that the swing directions of the weights are at a predetermined angle with respect to each other . The rotating electrical machine according to claim 14, wherein the predetermined angle is a value obtained by dividing 180 degrees by the number of nodes generated in the annular vibration mode . The rotating electrical machine according to any one of claims 1 to 15, wherein a plurality of the vibration damping units are arranged at intervals along the circumferential direction . The two adjacent damping parts are characterized in that the angle between the swing directions of the respective weights is a value obtained by dividing 180 degrees by the number of node parts generated in the annular vibration mode. The rotating electrical machine according to claim 16 . The number of nodes in the ring vibration mode is the same as the number of nodes in the ring vibration mode formed by the magnetic attraction force of the rotor. The rotating electrical machine according to claim 1.

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