JP6581035B2 - Rotating electric machine - Google Patents

Description

  The present invention relates to a rotating electrical machine including a hood damper and a plurality of support legs.

  As a typical structure of a rotating electrical machine including an electric motor and a generator, a fixed support member including a cylindrical stator fixedly supported, and a rotor supported rotatably in the fixed support member Is widely known. In a rotating electrical machine, resonance occurs when the electromagnetic force frequency acting between the fixed support member and the rotor matches the natural frequency of the fixed support member, and the fixed support member vibrates to generate electromagnetic noise. There are things to do.

  As a countermeasure for suppressing such vibration of the rotating electrical machine, particularly vibration in the annular vibration mode, a technique of attaching a dynamic vibration absorber to the rotating electrical machine is known (Patent Document 1).

  In addition, a technique for suppressing vibration in consideration of the position of the support leg of the rotating electrical machine is known (Patent Document 2).

  Furthermore, a technique for suppressing the vibration of a motor by a vibration damping member using a granular material is known (Patent Document 3).

JP 2014-57406 A JP 2013-150383 A JP 2000-46103 A

  In the said patent document 1, it is necessary to attach a dynamic vibration absorber, and it is not considered about the support leg of a rotary electric machine. In Patent Document 2, although consideration is given to the support leg of the rotating electrical machine, the support leg is handled as a mere fixed support and is not considered as an elastic support element.

  Further, Patent Document 3 does not disclose anything about which position on the outer periphery of the motor is effective when the damping member using the powder particles is attached.

  The present invention has been made in view of the above circumstances, and in a rotating electrical machine having a plurality of support legs, a vibration damper is not used, but a hood damper is used and vibrations are considered in consideration of elastic deformation of the support legs. The purpose is to control.

In order to achieve the above object, one aspect of a rotating electrical machine according to the present invention includes a cylindrical fixed support member, a rotor that is rotatably supported in the fixed support member, and a periphery of the fixed support member. first and second supporting legs for supporting the fixed support member are disposed with a predetermined first opening angle of the direction, spacing in the circumferential direction of the fixed support member relative to the second support leg A rotating electric machine having a hood damper that is disposed on the fixed support member and generates a resistance force against a radial movement of the fixed support member, and takes an angular coordinate in a rotation direction of the rotor When the coordinate positions of the first and second support legs are α ₁ and α ₂ , the coordinate position of the hood damper is θ _1, and α ₁ <α ₂ , (α ₂ −α ₁ ) is 70 to 110 degrees, 160 to 200 degrees, 2 0-290 degrees, 340 to 380 degrees, is either, and, (θ ₁ -α ₂₎ is 60 to 80 degrees, 150 to 170 degrees, 240-260 degrees, 330-350 degrees, either It is characterized by.

Further, another aspect of the rotating electrical machine according to the present invention includes a cylindrical fixed support member, a rotor supported rotatably in the fixed support member, and a predetermined direction in a circumferential direction of the fixed support member . first and second support legs are arranged with a first opening angle to support the fixed support member, said circumferentially spaced stationary support member relative to said first and second support legs And a first hood damper and a second hood damper which are arranged apart from each other in the circumferential direction of the fixed support member, and which are attached to the fixed support member and generate a resistance force against the radial movement of the fixed support member; , Wherein angle coordinates are taken in the rotation direction of the rotor, and the coordinate positions of the first and second support legs are respectively α ₁ and α _2, and the first and second each coordinate position of the hood damper theta ₁ When the preliminary _{θ 2, (α 2 -α 1} ) is 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, 340 to 380 degrees, it is either, and, (θ ₁ -α ₂ ) Is any of 65 to 80 degrees, 155 to 170 degrees, 245 to 260 degrees, and 335 to 350 degrees.

Furthermore, another aspect of the rotating electrical machine according to the present invention includes a cylindrical fixed support member, a rotor rotatably supported in the fixed support member, and a predetermined direction in a circumferential direction of the fixed support member . first and second support legs are arranged with a first opening angle to support the fixed support member, said fixed support member circumferentially predetermined with respect to said first and second support legs A first opening having a second opening angle and spaced apart from each other in the circumferential direction of the fixed support member, and is attached to the fixed support member to generate a resistance force against a radial movement of the fixed support member. And a second hood damper, wherein angle coordinates are taken in the rotation direction of the rotor, and the coordinate positions of the first and second support legs are α ₁ and α ₂ , respectively. Seats for the first and second hood dampers When position and theta ₁ and theta _2, respectively, is (α ₂ -α _1), 70~110 degrees, 160-200 degrees, 250-290 degrees, is any of 340 to 380 degrees, and, (theta _1- α ₂ ) is any of 0 to 60 degrees, 90 to 150 degrees, 180 to 240 degrees, 270 to 330 degrees, and (θ ₂ −θ ₁ ) is 25 to 70 degrees, 115 to It is any one of 160 degrees, 205-250 degrees, and 295-340 degrees.

  According to the present invention, in a rotating electrical machine including a plurality of support legs, vibration suppression can be achieved in consideration of elastic deformation of the support legs using a hood damper without using a dynamic vibration absorber.

It is typical sectional drawing perpendicular | vertical to the rotating shaft of the rotary electric machine which concerns on embodiment of this invention. It is a figure which shows the example of distribution of the circumferential direction in sectional drawing perpendicular | vertical to the axis | shaft of a rotary electric machine of the electromagnetic force concerning the fixing support member of a rotary electric machine. In the rotating electrical machine according to the embodiment of the present invention, the amplitude of the damper / spring opening angle φ and the dimensionless spring constant κ in the case where two spring supports and one hood damper are provided (one damper case). It is a graph which shows an influence. It is a graph which shows the influence which the spring opening angle (DELTA) (alpha) and dimensionless spring constant (kappa) have on an amplitude in the rotary electric machine (case with one damper) which concerns on embodiment of this invention. 4 is a graph showing an example of a resonance curve in which the dimensionless frequency is taken on the horizontal axis and the dimensionless amplitude is taken on the vertical axis in the rotating electrical machine (case with one damper) according to the embodiment of the present invention. Effect of Damper Opening Angle Δθ and Damper / Spring Opening Angle φ on Amplitude When Rotating Electric Machine According to Embodiment of the Present Invention is Provided with Two Spring Supports and Two Hood Dampers (Two Damper Cases) Is a graph showing a case where the influence of the damper opening angle Δθ is small (first group). FIG. 6 is a graph showing the influence of the damper opening angle Δθ and the damper / spring opening angle φ on the amplitude in the rotating electrical machine (two damper cases) according to the embodiment of the present invention, where the influence of the damper opening angle Δθ is large. It is a graph shown about (2nd group). It is a graph which shows the influence which damper opening angle (DELTA) (theta) and dimensionless spring constant (kappa) exert on an amplitude in the 2nd group of the rotary electric machine (case with two dampers) which concerns on embodiment of this invention. It is a graph which shows the influence which the spring opening angle (DELTA) (alpha) and dimensionless spring constant (kappa) have on an amplitude in the 2nd group of the rotary electric machine (case with two dampers) which concerns on embodiment of this invention. 5 is a graph showing an example of a resonance curve in which a dimensionless frequency is taken on the horizontal axis and a dimensionless amplitude is taken on the vertical axis in the first group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention. 6 is a graph showing an example of a resonance curve in which a dimensionless frequency is taken on the horizontal axis and a dimensionless amplitude is taken on the vertical axis in the second group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention.

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

  First, an analysis method related to vibration suppression of an embodiment of a rotating electrical machine according to the present invention will be described.

  FIG. 1 is a schematic cross-sectional view perpendicular to the rotation axis of the rotating electrical machine according to the embodiment of the present invention. FIG. 2 is a diagram showing an example of the distribution in the circumferential direction in a cross-sectional view perpendicular to the axis of the rotating electrical machine, of the electromagnetic force applied to the fixed support member of the rotating electrical machine.

  In a hammering test, it is known that a mode having nodes in the axial direction cannot be obtained in a frequency range of several thousand Hz or less where electromagnetic vibration is a problem. Therefore, for the sake of simplicity, the stationary support member 10 including the stator of the rotating electrical machine and the outer stator frame is approximated by a uniform ring as shown in FIG. 1 that does not consider the axial distribution of displacement. I decided to. Here, the name of the “fixed support member” is “fixed” in the sense that the rotor 50 is supported without rotating, and when considering the vibration of the fixed support member 10, It is not fixed and vibrates.

  It is assumed that the fixed support member 10 is cylindrical and has a uniform thickness in the circumferential direction. Inside the fixed support member 10, a rotor 50 that rotates around an axis common to the axis of the fixed support member 10 is disposed. A gap 51 is formed between the fixed support member 10 and the rotor 50.

On the outside of the fixed support member 10, L spring supports (support legs) 111 and 112 are installed at positions of an angle α = α _n (n = 1,..., L) in the circumferential direction. FIG. 1 shows a case where L = 2.

Here, since the fixed support member 10 is assumed to be the radial vibration, the spring support 111 and 112, the elastic fixing support member 10 in the radial direction with respect to the fixed position via a spring of spring constant k _n It shall be supported.

Further, N hood dampers 301 and 302 are installed on the outer side of the fixed support member 10 at positions of circumferential angles θ = θ _j (j = 1,..., N). The hood damper generally refers to a vibration damping device including a resistance element 13 (damping coefficient: c _Hj ) and a damper mass body 14 (mass: m _Hj ) attached to the end of the resistance element 13. Here, since it is assumed that the fixed support member 10 performs an annular vibration, the damper mass body 14 is assumed to be movable at least in the radial direction. FIG. 1 shows a case where N = 2.

  The radial displacement u of the fixed support member 10 is expressed by the following equation (1) when considering M vibration modes.

here,
θ: Coordinates in the circumferential direction (rad) (counterclockwise is positive)
i: an integer representing a vibration mode in the circumferential direction a _i : displacement of a cosine type i having a belly at θ = 0 b _i : displacement of a sine type mode i having a belly at θ = π / (2i) Rotation As a general external force acting on the electric machine, a force acting in the radial direction is an electromagnetic force that is distributed in the circumferential direction and rotates in the circumferential direction, and is expressed by the following equation (2).

Where s: integer representing the mode of electromagnetic force Ω _s : angular frequency of electromagnetic force having mode s F _s : amplitude of electromagnetic force of mode s Although the actual electromagnetic force contains many frequency components, Therefore, consider the case where only the component of F _s cos (−Ωst + sθ) acts. Further, _assuming that the spring constant kn is not so large and only the i-th mode is adopted and the case of i = s is handled, the equations of motion are as shown in the following equations (3) to (5).

Where r: radius of the ring E: longitudinal elastic modulus of the ring support member A: cross-sectional area (in the case of a rectangular cross-section, the product of the thickness H of the ring and the length W in the axial (width) direction, A = H × W)
I: circular face second moment about the vertical main shaft (in the case of rectangular cross-section, ^{I =} WH 3/12)
ρ: Density of annulus L: Number of spring supports k _n : Spring constant of a spring support installed at θ = θ _n (n = 1,..., L)
c _0i : viscosity damping coefficient of main system (i = 1,..., M)
x _j : Displacement of the hood damper installed at θ = θ _j (j = 1,..., N)
m _Hj : mass of the hood damper installed at θ = θ _j μ _Hj : mass ratio of the hood damper installed at θ = θ _j μ _Hj = m _Hj / {(5/4) πrρA}
c _Hj : Viscous damping coefficient of the hood damper installed at θ = θ _j γ _Hj : Damping ratio of the hood damper installed at θ = θ _j γ _Hj = c _Hj / (2m _Hj ω ₀₂ )
N: Number of hood dampers Here, i = 2 mode is taken as an example. For example, the steady solutions of the equations (3) to (5) are set as the following equations (6) to (9).
a ₂ = A ₁ cosΩ ₂ t + B ₁ sinΩ ₂ t (6)
b ₂ = A ₂ cosΩ ₂ t + B ₂ sinΩ ₂ t (7)
x ₁ = A ₃ cosΩ ₂ t + B ₃ sinΩ ₂ t (8)
x ₂ = A ₄ cosΩ ₂ t + B ₄ sinΩ ₂ t (9)

  When i is 0, the vibration of the circular ring becomes larger or smaller as it is. When i is 1, the shape and size of the circular ring remains unchanged, and the vibration is alternately displaced to one circumferential position and the opposite side.

  When i is 2, the displacement in the radial direction is at an intermediate position between the belly where the amplitude is maximum and between the belly and the belly every 90 degrees in the circumferential direction, similarly to the force distribution shown in FIG. The node with the smallest is formed. When i is 3 or more, belly and nodes are alternately formed at equal intervals in the circumferential direction. In a vibration phenomenon in an actual rotating electrical machine, the case where i = s is 2 is usually most important. Therefore, in the following, the case of i = s = 2 will be studied. Therefore, each phenomenon at each angular position in the circumferential direction described below is the same at 180 degrees from the angle, and the displacement, speed, acceleration, etc. at each time are the same, and 90 degrees and 270 degrees are shifted from the angle. In terms of position, this means that a phenomenon occurs in which the absolute values of displacement, speed, acceleration, etc. at each time are the same and the signs are reversed.

[Numerical analysis results]
Here, the results of numerical analysis of the state of annular vibration of the fixed support member when the spring support is disposed at two places in the circumferential direction of the fixed support member and one or two hood dampers are further disposed will be described. .

  The embodiment of the present invention satisfies the condition that the amplitude obtained by the analysis is as small as possible.

In FIGS. 3 to 11, the vertical axis represents the average of the square of the radial displacement u represented by the equation (1) in space and time as represented by the following equation (10) (F ₂ π / k ₀₂ ) ² divided by ² and defined as non-dimensional.

However, k ₀₂ = 9EIπ / r ³ and T = 2π / Ω ₂ .

The horizontal axis of the resonance curves shown in FIGS. 5, 10, and 11 is ν = Ω ₂ / ω ₀₂ , and the angular frequency of the electromagnetic force is made non-dimensional with the natural angular frequency of the secondary mode. However, ω ₀₂ ² = 36EI / (5ρAr ⁴ ). Therefore, ν = 1 on the horizontal axis in FIGS. 5, 10, and 11 is the dimensionless natural angular frequency of the secondary mode of the main system, that is, the resonance point.

  Further, the maximum dimensionless amplitude value of the resonance curve obtained from the calculation using the set parameter values is adopted as the dimensionless amplitude value on the vertical axis in FIGS. 3, 4, and 6 to 9. ing.

[With two spring supports and one hood damper]
First, calculation results in the case where two spring supports and one hood damper are provided (hereinafter, also simply referred to as “one damper case”) will be described. As shown in FIG. 1, the first spring support 111 is disposed in the angular coordinate position alpha _1, second spring support 112 is disposed in the angular coordinate position alpha _2. The spring opening angle Δα between the spring supports 111 and 112 is defined as Δα = α ₂ −α ₁ .

Also, one of the hood damper 301 is disposed in the angular coordinate position theta _1. In this case, the hood damper 302 shown in FIG. 1 does not exist. A damper / spring opening angle φ between the hood damper 301 and the second spring support 112 is defined as φ = θ ₁ −α ₂ .

FIG. 3 shows a damper / spring opening angle φ and a dimensionless spring constant κ in the case where the rotating electrical machine according to the embodiment of the present invention includes two spring supports and one hood damper (one damper case). It is a graph which shows the influence which acts on an amplitude. Here, α ₁ = 135 degrees, α ₂ = 225 degrees, and Δα = α ₂ −α ₁ = 90 degrees. Further, it is assumed that the mass ratio μ _{H1 of} the hood damper is 0.1 and the damping ratio γ _H1 of the hood damper is 0.5.

Assuming that the dimensionless spring constants κ ₁ and κ ₂ of the first and second spring supports 111 and 112 are equal to each other, these values are 0.032, 0.048, 0.064, and 0.096. Calculated.

  FIG. 3 also shows a case where neither a spring support nor a hood damper is provided for comparison.

From FIG. 3, it can be seen that due to the presence of the spring supports 111 and 112 and the hood damper 301, the amplitude is significantly reduced as compared to the case without them. The amplitude is dimensionless spring constant kappa _1, although depending on the size of the kappa _2, dimensionless spring constant kappa _1, when the damper spring opening angle φ is 60 to 80 degrees regardless of the size of the kappa ₂ It can be seen that the amplitude is minimized. For example, in the case of κ ₁ = κ ₂ = 0.064, the amplitude is minimized when φ = 72 degrees.

FIG. 4 is a graph showing the influence of the spring opening angle Δα and the dimensionless spring constants κ ₁ and κ ₂ on the amplitude in the rotating electrical machine (case with one damper) according to the embodiment of the present invention. Here, as in the case of FIG. 3, it is assumed that the mass ratio μ _{H1 of} the hood damper is 0.1 and the damping ratio γ _H1 of the hood damper is 0.5. The damper / spring opening angle φ is φ = θ ₁ −α ₂ = 72 degrees. The value of φ corresponds to the case where the amplitude in the case of κ ₁ = κ ₂ = 0.064 in FIG. 3 is minimized.

In FIG. 4, as in the case of FIG. 3, the dimensionless spring constants κ ₁ and κ ₂ are assumed to be equal to each other, and these values are 0.032, 0.048, 0.064, and 0.096. Calculated. In FIG. 4, the spring opening angle Δα = α ₂ −α ₁ is calculated in the range of 0 to 180 degrees, but the phenomenon of 0 to 90 degrees at the angle coordinate position is the same as the phenomenon of 90 to 180 degrees.

From the calculation results shown in FIG. 4, it can be seen that the amplitude is particularly small when the spring opening angle Δα is 70 to 110 degrees or 160 to 200 degrees, regardless of the magnitude of the dimensionless spring constants κ ₁ and κ ₂ .

FIG. 5 is a graph showing an example of a resonance curve in which the dimensionless frequency is plotted on the horizontal axis and the dimensionless amplitude is plotted on the vertical axis in the rotating electrical machine (case with one damper) according to the embodiment of the present invention. The calculation conditions of FIG. 5 are selected from a range where the amplitude obtained by FIGS. 3 and 4 is particularly small. That is, α ₁ = 135 degrees, α ₂ = 225 degrees, Δα = α ₂ −α ₁ = 90 degrees, θ ₁ = 297 degrees, and φ = θ ₁ −α ₂ = 72 degrees. Furthermore, the dimensionless spring constant κ ₁ = κ ₂ = 0.064 of the spring support, the hood damper mass ratio μ _H1 = 0.1, and the hood damper damping ratio γ _H1 = 0.5.

  FIG. 5 also shows a resonance curve C1 when there is no spring support and no hood damper for comparison. In the resonance curve C1, since the natural frequencies of the sine mode and the cosine mode are the same, the dimensionless angular frequency ν = 1 has only one peak. On the other hand, in the case of two spring supports and one damper, the natural frequencies of the sine mode curve and the cosine mode curve are shifted, and the peak value of each mode is low. It has become. Therefore, the peak value of the actual resonance curve (sin mode + cos mode) which is the sum of the sine mode and the cosine mode is significantly lower than the peak value of the resonance curve C1.

  Further, not only the amplitude when the dimensionless frequency ν = 1.0 is reduced, but also the amplitude is suppressed even when ν changes. A great vibration damping effect can be obtained in the electric motor.

As described above, when two spring supports and one hood damper are provided, the spring opening angle Δα = α ₂ −α ₁ is set to 70 to 110 degrees, and the damper / spring opening angle φ = θ ₁ −. by setting alpha ₂ to 60 to 80 degrees, it can be seen that small amplitude. However, the effect is the same even if an angle obtained by adding any of 90 degrees, 180 degrees, and 270 degrees to these angles. Therefore, the condition for reducing the amplitude is that the spring opening angle Δα = α ₂ −α ₁ is 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, 340 to 380 degrees, and the damper spring The opening angle φ = θ ₁ −α ₂ is 60 to 80 degrees, 150 to 170 degrees, 240 to 260 degrees, or 330 to 350 degrees.

[When equipped with two spring supports and two hood dampers]
Next, calculation results in the case where two spring supports and two hood dampers are provided (hereinafter also simply referred to as “two damper cases”) will be described. As in the case of the damper 1 of the case, as shown in FIG. 1, the first spring support 111 is disposed in the angular coordinate position alpha _1, second spring support 112 is disposed in angular coordinate position alpha ₂ Yes. The spring opening angle Δα between the spring supports 111 and 112 is Δα = α ₂ −α ₁ . Furthermore, the first hood damper 301 is disposed in the angular coordinate position theta _1, second hood damper 302 is disposed in the angular coordinate position theta _2. A damper opening angle Δθ between the hood dampers 301 and 302 is defined as Δθ = θ ₂ −θ ₁ . A damper / spring opening angle φ between the first hood damper 301 and the second spring support 112 is defined as φ = θ ₁ −α ₂ .

  FIG. 6 shows a rotary electric machine according to an embodiment of the present invention, in which a damper opening angle Δθ and a damper / spring opening angle φ in a case where two spring supports and two hood dampers are provided (case of two dampers). It is a graph which shows the influence which acts on an amplitude, Comprising: It is a graph shown about the case where the influence of damper opening angle (DELTA) (theta) is small (1st group). FIG. 7 is a graph showing the influence of the damper opening angle Δθ and the damper / spring opening angle φ on the amplitude in the case of two dampers similar to the case of FIG. 6, where the influence of the damper opening angle Δθ is large. It is a graph shown about (2nd group).

6 and 7, the spring opening angle Δα = α ₂ −α ₁ = 90 degrees, the dimensionless spring constant κ ₁ = κ ₂ = 0.064 of the spring support, and the mass ratio of the hood damper μ _H1 = μ _H2 = The damping ratio of the food damper was γ _H1 = γ _H2 = 0.5. 6 and 7 also show a case where neither a spring support nor a hood damper is provided for comparison.

The influence of the damper opening angle Δθ = θ ₂ −θ ₁ on the amplitude was examined by changing the damper / spring opening angle φ = θ ₁ −α ₂ as a parameter and changing the value to 0 to 90 degrees. The calculation results (FIG. 7) are the same when the damper / spring opening angle φ = 0 ° and φ = 90 °. As a result, as shown in FIG. 6, when the damper / spring opening angle φ is in the range of 65 to 80 degrees (in the specific calculation example, 65 degrees, 70 degrees, 75 degrees, and 80 degrees), the influence of the damper opening angle Δθ. As shown in FIG. 7, the damper / spring opening angle φ ranges from 0 to 60 degrees (in the specific calculation example, 0 degrees, 10 degrees, 20 degrees, 30 degrees, 40 degrees, 50 degrees, 60 degrees ) Shows that the influence of the damper opening angle Δθ is large. In the range where the damper / spring opening angle φ is 0 to 60 degrees (FIG. 7), the amplitude is small when the damper opening angle Δθ is in the range of 25 to 70 degrees.

FIG. 8 is a graph showing the influence of the damper opening angle Δθ and the dimensionless spring constant κ on the amplitude in the second group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention. Similar to FIGS. 6 and 7, the spring opening angle Δα = α ₂ −α ₁ = 90 degrees, the mass ratio μ _H1 = μ _H2 = 0.05 of the hood damper, and the damping ratio γ _H1 = γ _H2 = of the hood damper. 0.5.

Assuming that the dimensionless spring constants κ ₁ and κ ₂ of the first and second spring supports 111 and 112 are equal to each other, these values are 0.032, 0.048, 0.064, and 0.096. Calculated.

  For comparison, the case where there is no spring support and no hood damper is also shown.

From FIG. 8, it can be seen that due to the presence of the spring supports 111 and 112 and the hood dampers 301 and 302, the amplitude is significantly reduced as compared to the case without them. The amplitude is dimensionless spring constant kappa _1, although depending on the size of the kappa _2, the amplitude when the damper opening angle Δθ is 25 to 70 degrees regardless of the dimensionless spring constant kappa _1, the kappa ₂ size It can be seen that is minimized.

  FIG. 9 is a graph showing the influence of the spring opening angle Δα and the dimensionless spring constant κ on the amplitude in the second group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention.

The damper / spring opening angle φ = θ ₁ −α ₂ was set to 90 degrees, and the damper opening angle Δθ = θ ₂ −θ ₁ was set to 45 degrees as a preferable value for reducing the amplitude in FIG. Similarly to FIG. 8, the mass ratio μ _H1 = μ _H2 = 0.05 of the hood damper and the damping ratio γ _H1 = γ _H2 = 0.5 of the hood damper were set.

As in FIG. 8, assuming that the dimensionless spring constants κ ₁ , κ ₂ of the first and second spring supports 111, 112 are equal to each other, these values are 0.032, 0.048, 0.064 and Calculation was made for the case of 0.096. In FIG. 9, the spring opening angle Δα = α ₂ −α ₁ is calculated in the range of 0 to 180 degrees, but the phenomenon of 0 to 90 degrees at the angle coordinate position is the same as the phenomenon of 90 to 180 degrees.

  For comparison, the case where there is no spring support and no hood damper is also shown.

According to the calculation result shown in FIG. 9, the amplitude is 70 to 110 degrees or 160 to 200 degrees in the spring opening angle Δα regardless of the magnitude of the dimensionless spring constants κ ₁ and κ ₂ (in FIG. 9, Δα is 160 to 180 degrees). It can be seen that it is particularly small when the angle is equivalent to 0 degree and 0 to 20 degrees.

FIG. 10 is a graph showing an example of a resonance curve in which the dimensionless frequency is plotted on the horizontal axis and the dimensionless amplitude is plotted on the vertical axis in the first group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention. It is. The calculation conditions in FIG. 10 are selected from a range in which the amplitude obtained in FIG. 6 is particularly small. That is, α ₁ = 135 degrees, α ₂ = 225 degrees, Δα = α ₂ −α ₁ = 90 degrees, θ ₁ = 295 degrees, θ ₂ = 344 degrees, Δθ = θ ₂ −θ ₁ = 49 degrees, φ = θ ₁ −α ₂ = 70 degrees. Furthermore, the dimensionless spring constant κ ₁ = κ ₂ = 0.064 of the spring support, the mass ratio of the hood damper μ _H1 = μ _H2 = 0.05, and the damping ratio of the hood damper γ _H1 = γ _H2 = 0.5 .

  FIG. 10 also shows the resonance curve C1 when there is no spring support and no hood damper, as in FIG. In the case of the two spring supports and the two dampers, as in FIG. 5, the natural frequencies of the sine mode curve and the cosine mode curve are shifted, and the peak value of each mode is It is low. Therefore, the peak value of the actual resonance curve (sin mode + cos mode) which is the sum of the sine mode and the cosine mode is significantly lower than the peak value of the resonance curve C1.

  Similarly to the case of one damper (FIG. 5), not only the amplitude when the dimensionless frequency ν = 1.0 is reduced, but also the amplitude can be suppressed even when ν is changed. A large damping effect can be obtained in a rotating electric machine that is operated by a number.

FIG. 11 is a graph showing an example of a resonance curve in which the dimensionless frequency is plotted on the horizontal axis and the dimensionless amplitude is plotted on the vertical axis in the second group of the rotating electrical machine (case with two dampers) according to the embodiment of the present invention. It is. The calculation conditions in FIG. 11 are selected from a range in which the amplitude obtained in FIG. 7 is particularly small. That is, α ₁ = 135 degrees, α ₂ = 225 degrees, Δα = α ₂ −α ₁ = 90 degrees, θ ₁ = 315 degrees, θ ₂ = 367 degrees, Δθ = θ ₂ −θ ₁ = 52 degrees, φ = θ ₁ −α ₂ = 90 degrees. Furthermore, the dimensionless spring constant κ ₁ = κ ₂ = 0.064 of the spring support, the mass ratio of the hood damper μ _H1 = μ _H2 = 0.05, and the damping ratio of the hood damper γ _H1 = γ _H2 = 0.5 .

  The calculation result shown in FIG. 11 is substantially the same as the calculation result of FIG. 10, and the peak value of the resonance curve (sin mode + cos mode) is significantly lower than the peak value of the resonance curve C1.

As described above, when two spring supports and two hood dampers are provided, when the damper / spring opening angle φ = θ ₁ −α ₂ is 65 to 80 degrees (first group), the spring It can be seen that by setting the opening angle Δα = α ₂ −α ₁ to 70 to 110 degrees, the amplitude can be reduced regardless of the damper opening angle Δθ = θ ₁ −θ ₂ .

When the damper / spring opening angle φ = θ ₁ −α ₂ is 0 to 60 degrees (second group), the spring opening angle Δα = α ₂ −α ₁ is set to 70 to 110 degrees, and the damper opening angle Δθ. It can be seen that the amplitude can be reduced by setting = θ ₂ -θ ₁ to 25 to 70 degrees.

  However, the effect is the same even if an angle obtained by adding any one of 90 degrees, 180 degrees, and 270 degrees to the above-described angle.

Accordingly, the condition for reducing the amplitude is that in the first group, the damper / spring opening angle φ = θ ₁ −α ₂ is 65 to 80 degrees, 155 to 170 degrees, 245 to 260 degrees, or 335 to 350 degrees. Yes, the spring opening angle Δα = α ₂ −α ₁ is any of 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, and 340 to 380 degrees.

In the second group, the damper / spring opening angle φ = θ ₁ −α ₂ is 0 to 60 degrees, 90 to 150 degrees, 180 to 240 degrees, 270 to 330 degrees, and the spring opening angle Δα = α ₂ −α ₁ is any of 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, and 340 to 380 degrees, and the damper opening angle Δθ = θ ₂ −θ ₁ is 25 to 70 degrees, 115 to One of 160 degrees, 205 to 250 degrees, and 295 to 340 degrees.

  In the above description, the number of spring supports to be attached is two, and the number of hood dampers is one or two. However, if each of these spring supports or hood dampers is divided into a plurality of parts and installed at positions apart from the basic position by 90 degrees, 180 degrees or 270 degrees, the basic and The same vibration control effect can be obtained as when one is attached at a certain position.

  As mentioned above, although some embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and their modifications are included in the scope and gist of the invention, and are also included in the invention described in the claims and the equivalents thereof.

10: Fixed support member (stator and stator frame)
111, 112 ... Spring support (support leg)
13 ... Resistance element 14 ... Damper mass body 301, 302 ... Hood damper 50 ... Rotor 51 ... Gap

Claims (4)

A cylindrical fixed support member;
A rotor rotatably supported in the fixed support member;
First and second support legs, wherein are arranged with a first opening angle in a predetermined circumferential direction of the fixed support member for supporting the fixed support member,
A hood damper that is disposed apart from the second support leg in the circumferential direction of the fixed support member and is attached to the fixed support member to generate a resistance force against a radial movement of the fixed support member;
A rotating electric machine having
Taking the angle coordinates in the rotation direction of the rotor, the coordinate positions of the first and second support legs are α ₁ and α ₂ , respectively, and the coordinate position of the hood damper is θ ₁ ,
When α ₁ <α ₂ ,
(Α ₂ −α ₁ ) is 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, 340 to 380 degrees, and
(Θ ₁ −α ₂ ) is any of 60 to 80 degrees, 150 to 170 degrees, 240 to 260 degrees, 330 to 350 degrees,
Rotating electric machine. A cylindrical fixed support member;
A rotor rotatably supported in the fixed support member;
First and second support legs, wherein are arranged with a first opening angle in a predetermined circumferential direction of the fixed support member for supporting the fixed support member,
The first and second support legs are spaced apart in the circumferential direction of the fixed support member and spaced apart from each other in the circumferential direction of the fixed support member, and are attached to the fixed support member and First and second hood dampers that produce resistance to radial movement of the fixed support member;
A rotating electric machine having
Taking the angle coordinates in the rotation direction of the rotor, the coordinate positions of the first and second support legs are α ₁ and α ₂ , respectively, and the coordinate positions of the first and second hood dampers are θ ₁ , respectively. And θ ₂ ,
(Α ₂ −α ₁ ) is 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, 340 to 380 degrees, and
(Θ ₁ −α ₂ ) is any of 65 to 80 degrees, 155 to 170 degrees, 245 to 260 degrees, and 335 to 350 degrees,
Rotating electric machine. A cylindrical fixed support member;
A rotor rotatably supported in the fixed support member;
First and second support legs, wherein are arranged with a first opening angle in a predetermined circumferential direction of the fixed support member for supporting the fixed support member,
The fixed support member is arranged with a predetermined second opening angle in the circumferential direction of the fixed support member with respect to the first and second support legs and spaced apart from each other in the circumferential direction of the fixed support member, and the fixed First and second hood dampers attached to a support member to produce a resistance to radial movement of the fixed support member;
A rotating electric machine having
Taking the angle coordinates in the rotation direction of the rotor, the coordinate positions of the first and second support legs are α ₁ and α ₂ , respectively, and the coordinate positions of the first and second hood dampers are θ ₁ , respectively. And θ ₂ ,
(Α ₂ −α ₁ ) is 70 to 110 degrees, 160 to 200 degrees, 250 to 290 degrees, 340 to 380 degrees, and
(Θ ₁ −α ₂ ) is 0 to 60 degrees, 90 to 150 degrees, 180 to 240 degrees, 270 to 330 degrees, and
(Θ ₂ −θ ₁ ) is any of 25 to 70 degrees, 115 to 160 degrees, 205 to 250 degrees, 295 to 340 degrees,
Rotating electric machine.   The rotating electrical machine according to any one of claims 1 to 3, wherein the rotational speed is variable.

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