JP2000142125A - Flywheel battery supporting device having multifold elastic supporting structure - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a flywheel battery supporting device having multifold elastic supporting structure capable of reducing the swinging angle of flywheel and the bearing load. SOLUTION: Rotatably round the Y-axis a flywheel support 18 is supported by a gimbal rotatable round the X-axis and is arranged swingable in any direction on the Z-axis as the rotary shaft of a flywheel 36 while their rotations are suppressed by resilient force. The resilient force is set so as to reduce the swinging angle of the flywheel for low frequency vibration. The arrangement further includes a bearing part 38 to support the flywheel 36 rotatably round the Z-axis and a shock absorbing structural member 44 to function as a spring provided in the area to the flywheel support 18, and the bearing part 38 is made rotatable relative to the flywheel support 18. The spring hardness of the structural member 44 is set so as to reduce the bearing load of the bearing part 38 for high frequency vibrations.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a flywheel battery support device, and more particularly to an improved flywheel battery support device having a multiple elastic support structure.

[0002]

2. Description of the Related Art Heretofore, there has been proposed a technique in which a flywheel battery having a flywheel rotating at a high speed is installed in a moving body, for example, an automobile, and its kinetic energy is used in the form of a storage battery.

[0003] In the case of a moving body equipped with such a flywheel battery, when a disturbance occurs when the moving body moves, for example, a road surface vibration acts on the moving body, a moment generally called a gyro effect is generated. Acts on the wheel. Therefore, depending on the method of supporting the flywheel, an excessive load may act on the bearing supporting the flywheel, or the flywheel may vibrate significantly.

[0004] In order to reduce the influence of such a gyro effect, a technique has been proposed in which the relative movement between the vehicle and the spin axis of the flywheel is suppressed by, for example, a highly rigid bearing (prior art 1). An example of such an example is “Development of an Energy Storage Device Using a Flywheel for Electric Vehicles, Katsutaka Tanabe et al., Materials of the 2nd Research Conference for Electric Vehicles, p. 31”.

There is also known a structure in which a free gimbal is used as a support mechanism and only translational force is suppressed by a flywheel bearing (prior art 2). Examples of this include the “flywheel power storage system, Tetsushi Ikeda,
Proceedings of the 73rd Ordinary General Meeting of the Japan Society of Mechanical Engineers (II
I) pp-471-472 ".

A flywheel support for rotatably supporting a flywheel around its rotation axis is supported by a spring and a damper on a housing, and a relative movement between the housing and the flywheel support is allowed to some extent. Known (prior art 3). An example of this is “Gyrodynamics and its engeneering applicatio
n, Ronald N. Arnold (1961).

Further, an actuator is used to control the relative rotation of the gimbal rotatably mounted on the housing and the flywheel support rotatably mounted on the gimbal about an axis orthogonal to the rotation axis of the gimbal. Methods have also been proposed. This is the vehicle operation amount, which is the operation amount of the steering, accelerator, brake, etc. of the vehicle,
It detects vehicle behavior such as vehicle body acceleration and vehicle body attitude angular velocity, and flywheel behavior such as flywheel attitude angular velocity and bearing load, etc., and uses actuators to achieve the target flywheel swing angle and bearing load. The control torque is calculated, and the actuator is controlled based on the calculated torque (prior art 4).

[0008]

However, in the prior art 1, in order to withstand the gyro moment described above,
A high-capacity bearing mechanism is required, resulting in problems such as an increase in cost, an increase in weight and an increase in loss. In addition, there has been a problem that unexpected disturbance occurs due to the gyro moment, and the operation stability of the vehicle is deteriorated.

Further, in the above prior art 2, since the flywheel support is supported by the free gimbal, the relative angle between the vehicle body and the flywheel support becomes too large, so that the flywheel battery device itself becomes large. At the same time, there is a problem that wiring inside the device becomes complicated to allow a large relative angle.

Further, in the above-mentioned prior art 3, when the spring constant of the spring supporting the flywheel bearing is increased, the bearing load against high frequency vibration increases. Conversely, when the spring constant is decreased, the flywheel against low frequency vibration increases. The swing angle increases. For this reason, there is a problem that it is difficult to set the characteristics of the spring and the damper.

Further, in the above prior art 4, since there is a delay time in the control system of the actuator, it has little effect on vibrations higher in frequency than the control frequency band, and the resolution of the sensor or the actuator for detecting the control amount is reduced. Due to the limitations of the above, there is a problem that it is impossible to cope with minute vibration.

SUMMARY OF THE INVENTION The present invention has been made in view of the above-mentioned conventional problems, and has as its object to reduce the swing angle of a flywheel against low-frequency vibrations and reduce the bearing load against high-frequency vibrations. An object of the present invention is to provide a flywheel battery support device having a support structure.

[0013]

SUMMARY OF THE INVENTION In order to achieve the above object, the present invention is directed to a fixing member provided for fixing a position to a vehicle, and a fixed member provided with a spring or a damper. A gimbal rotatably supported around the first support axis by an elastic mounting portion that exerts a restraining force, and an elastic mounting portion formed of a spring or a damper on the gimbal and configured to exert a predetermined restraining force in the rotational direction. A flywheel support rotatably supported around a second support axis orthogonal to the first support axis, a flywheel held inside the flywheel support, and a flywheel Inside, a bearing portion rotatably supported around a rotation axis orthogonal to both the first and second support shafts, and provided between the bearing portion and the flywheel support, A flywheel battery support device having a multiple elastic support structure comprising a cushioning member functioning as a spring, wherein the spring hardness of the elastic mounting portion reduces the swing angle of the flywheel with respect to low frequency vibration. The spring hardness of the buffer structure member is softer than the spring hardness of the spring element present in the bearing portion, and the resonance frequency of the mass and the buffer structure member combining the flywheel and the bearing portion is a flywheel. The resonance frequency of the gimbal is set to be higher than the resonance frequency of the gimbal and the mass of the bearing and the flywheel support.

According to the above configuration, a double elastic support structure is provided by the elastic mounting portion for supporting the gimbal and the flywheel support, and the interference structure provided between the bearing portion and the flywheel support. Be composed. With the gimbal alone, the increase in the swing angle of the flywheel for low-frequency vibration and the increase in the bearing load for high-frequency vibration are contradictory, and it is difficult to reduce both of them. Any of these can be reduced by adopting the elastic support structure described above. That is, by adjusting the setting of the elastic mounting portion for rotatably supporting the gimbal and the flywheel support around their respective support axes, the swing angle of the flywheel with respect to low-frequency vibration is reduced, and the spring structure of the cushioning structure is reduced. By setting the height as described above, it is possible to reduce the bearing load for high-frequency vibration.

[0015]

Embodiments of the present invention (hereinafter referred to as embodiments) will be described below with reference to the drawings.

Embodiment 1 FIG. 1 is a perspective view of a flywheel battery support device having a multiple elastic support structure according to the present invention. In FIG. 1, a fixing member 12 is attached to a housing 10 fixed to a vehicle, and a gimbal 14 is attached to the fixing member 12 so as to be rotatable around an X axis as a first support axis. The gimbal 14 is rotatably mounted on the fixed member 12 with an elastic mounting portion 16 formed of a spring or a damper with a predetermined spring constant or damping coefficient.

The gimbal 14 is provided with a flywheel support 18 holding a flywheel therein so as to be rotatable around a Y axis as a second support axis orthogonal to the X axis. This flywheel support 18 also
Similar to the gimbal 14, it is rotatably mounted with a predetermined spring constant or damping coefficient by an elastic mounting portion 20 constituted by a spring or a damper.

The flywheel held by the flywheel support 18 is supported by a bearing (not shown) so as to be rotatable around the Z axis orthogonal to the X axis and the Y axis.

The structure of the elastic mounting portions 16 and 20 described above is as follows.
For example, any configuration may be used as long as one or both of the torsion spring and the damper can apply a predetermined elastic force as a repulsive force to the relative rotation of the gimbal 14 and the flywheel support 18.

FIGS. 2 and 3 show a simplified example of the elastic mounting portion 16. In both figures, the fixing member 12 is omitted.

FIG. 2 shows a spring 22 as the elastic mounting portion 16.
An example is shown in which the gimbal 14 is attached to the housing 10 using. The elastic mounting portion 20 for mounting the flywheel support 18 to the gimbal 14 can be similarly configured. In FIG. 2, when the gimbal 14 is about to rotate around the X axis, an elastic force corresponding to the spring hardness (spring constant) of the spring 22 acts, and the rotational movement thereof is suppressed to a predetermined extent. In general, when the spring hardness of the spring 22 is increased (the spring constant is increased), the swing angle of the flywheel with respect to low-frequency vibration applied to the vehicle, that is, the swing angle of the gimbal 14 and the flywheel support 18 is reduced. The load applied to the bearing portion of the flywheel due to the high frequency vibration applied to the flywheel increases. Conversely, if the spring hardness of the spring 22 is softened, the bearing load against high-frequency vibrations is reduced, but the swing angle of the flywheel against low-frequency vibrations is increased. In the present invention, the spring hardness of the spring 22 serving as the elastic mounting portion 16 is set to a certain level, and the elastic mounting portion 16 is configured to reduce the swing angle of the flywheel with respect to low-frequency vibration.

FIG. 3 schematically shows an example of the elastic mounting portion 16 using a damper 24 instead of the spring 22 of FIG. The damper 24 is also configured to exert a predetermined suppressing force according to the amount of rotation of the gimbal 14. FIG. 4 shows an example of the structure of such a damper 24. FIG.
In the liquid chamber 28 formed by the fixed wall 26 having a shape as shown in FIG.
The movable orifice 30 has a movable portion 3
2 are installed. When the area movable orifice 30 moves in the liquid chamber 28, a predetermined stress is generated by the interaction between the liquid in the liquid chamber 28 and the accumulator 34,
Thus, a predetermined damping ratio can be obtained with respect to the displacement of the movable part 32. Regarding the shape of this damper 24,
The spring 22 is not limited to the one shown in FIG. 4, but can generate a stress high enough to reduce the swing angle of the gimbal 14 and the flywheel support 18 against low-frequency vibration, similarly to the spring 22 described above. I just need.

It is preferable that the elastic mounting portion 16 has a configuration in which the above-described spring 22 and damper 24 are combined.

FIG. 5 shows the Z of the flywheel support 18.
An axial sectional view is shown. FIG. 6 shows the VI of FIG.
A VI sectional view is shown.

Referring to FIGS. 5 and 6, a flywheel 36 is held inside the flywheel support 18. The flywheel 36 is a flywheel support 1
Inside 8, a Z-axis orthogonal to the X-axis and the Y-axis is used as a rotation axis, and is supported by a bearing 38 so as to be rotatable therearound. The bearing section 38 is provided with a radial bearing 40 and a thrust bearing 42. The radial bearing 40 also serves as a motor generator that generates electric power by rotation of the flywheel 36.

As shown in FIGS. 5 and 6, the bearing 38 is attached to the flywheel support 18 by a plate-shaped buffer structure 44. The cushioning structural member 44 is constituted by a leaf spring or a coil spring, rubber, or the like in its structure, and functions as a spring when the bearing 38 is attached to the flywheel support 18.
Therefore, the spring hardness (spring constant) of the buffer structure member 44
Is adjusted to an appropriate value, the effect of high frequency vibration applied to the vehicle body can be reduced.

FIGS. 7 (a), 7 (b) and 7 (c) show a mechanism for reducing high-frequency vibrations by the buffer structure member 44. FIG. FIGS. 7A, 7B, and 7C schematically show the flywheel support 18, the bearing 38, and the cushioning structural member 44. FIG. When vibration is generated in the vehicle from a state where there is no vibration shown in FIG.
As shown in (c), the cushioning structure member 44 bends according to its spring constant, and the bearing portion 38 supporting the flywheel 36 makes a rotational movement with respect to the flywheel support 18. In this manner, by attaching the bearing 38 to the flywheel support 18 by the cushioning member 44, a gimbal-like movement between the flywheel support 18 and the bearing 38 located inside is enabled. 7 (b) and 7 (c), the buffer structure member 4
Although the deflection method of No. 4 is drawn larger than the actual one, the actual rotation angle of the bearing portion 38 is not large enough to be visually confirmed.

As a result, the high-frequency vibration which cannot be reduced by the spring hardness of the elastic mounting portion 16 absorbs the high-frequency vibration.
4, and the bearing load due to high-frequency vibration can be reduced.

In this case, the spring hardness of the buffer structure member 44 is determined as follows. That is, the radial bearing 40 and the thrust bearing 42 that support the flywheel 36 in the bearing portion 38 include spring elements generated by the material composition and shape. Therefore, the spring hardness of the buffer structure member 44 is set to be softer than the spring hardness of the bearing portion 38. Furthermore, the spring hardness of the buffer structure member 44 is determined by the resonance frequency of the inside of the buffer structure member 44, that is, the mass of the flywheel 36 and the bearing 38 and the buffer structure member 44, within the gimbal 14, ie, the flywheel 36. Mass and gimbal 14 in which the bearing 38 and the flywheel support 18 are combined
Is set so as to be higher than the resonance frequency. By setting the spring hardness of the buffer structure member 44 as described above, the high-frequency vibration applied to the vehicle is absorbed as a deflection of the buffer structure member 44 without acting on the bearing portion 38 as a bearing load. Therefore, even if high-frequency vibration is applied to the vehicle, an increase in the bearing load of the bearing portion 38 can be suppressed.

As described above, the elastic mounting portions 16 and 20 and the buffer structure member 44 form the multiple elastic support structure according to the present embodiment, and the swing angle of the flywheel due to low frequency vibration and the bearing due to high frequency vibration. And the load can be reduced.

FIG. 8 shows the measurement results of the vibration damping effect when the flywheel battery support device having the multiple elastic support structure according to the present embodiment is used. In FIG.
The horizontal axis indicates the frequency of the vibration acting on the vehicle. On the vertical axis, when this vibration acts, the transmission characteristic from the vibration to the bearing load applied to the bearing portion 38 and the swing angle of the gimbal 14 and the flywheel support 18, that is, the rotation axis of the flywheel 36, Z The transmission characteristics up to the pivot angle of the shaft are shown. ω _X is the vibration represented by the angular velocity, and G _x is the bearing load in the X-axis direction. The G _y is the bearing load of the Y-axis direction. Further, theta _x is swinging angle of the X-axis direction, theta _y is swinging angle of the Y-axis direction.
The rotation speed of the flywheel 36 at the time of performing this measurement was 30,000 rpm.

FIG. 8 shows four types of measurement results. That is, the spring hardness of the cushioning structure member 44 is adjusted by adjusting the resonance frequency of the mass obtained by combining the flywheel 36 and the bearing portion 38 with the cushioning member 44 by the flywheel 36, the bearing portion 38, and the flywheel support 18. The case where the resonance frequency of the mass and the gimbal 14 is set to be substantially the same is indicated by the line (1). Further, the result when the spring hardness of the buffer structure member 44 according to the present embodiment is adopted is shown by the line (2). Further, the case where the spring hardness of the buffer structure member 44 is set equal to the spring hardness of the spring element existing in the bearing portion 38 is expressed as (3), and the result without the buffer structure member 44 is expressed as (4). In this case, the results of (3) and (4) completely overlap. Therefore, when the spring hardness of the buffer structure member 44 is set to be equal to the spring hardness of the spring element in the bearing portion 38, it is understood that there is no improvement in the bearing load and the swing angle of the flywheel 36.

Under the condition shown in (1),
In comparison with (4) in the case where the buffer structure member 44 is not provided, the difference between 0.
At a frequency of 005 Hz or higher, the transmission gain decreases for both the swing angle and the bearing load. Conversely, at a low frequency range of 0.005 Hz or lower, these transmission gains greatly increase. Therefore, under the condition shown in (1), at a low frequency,
Very produce large swing ((approximately 1 in 4) and compared the theta _y
00 times), which is not a form suitable for practical use.

On the other hand, in the case of (2), which is the condition according to the present embodiment, the bearing load and the swing angle in the low frequency region are lower than in (4) where the buffer structure member 44 is not provided. The transmission gain has almost the same characteristics, and in the high frequency region around 100 Hz, the transmission gain of the peak existing in (4) can be reduced. That is, improvement is recognized in both the bearing load against the high frequency vibration applied to the vehicle and the swing angle of the flywheel 36.

As described above, by using the cushioning structure member 44 according to the present embodiment, the effect of high frequency vibration can be suppressed.
The swing angle of the flywheel 36 for low frequency vibration can be reduced, and the bearing load of the bearing portion 38 for high frequency vibration can be suppressed.

Embodiment 2 FIG. FIG. 9 shows a gimbal 14 and a flywheel support 1 used in a flywheel battery support device having a multiple elastic support structure according to the present invention.
An actuator 46 that rotatably supports 8 is shown. The actuator 46 includes a motor 48 and a motor shaft 50 to which a rotational torque is given by the motor 48. The motor 48 is fixed to the fixing member 12 and the gimbal 14 shown in FIG. 1 and is used instead of the elastic mounting portions 16 and 20 shown in FIG. A torsion spring 52 is also used in case the motor 48 of the actuator 46 fails. The ends of the motor shaft 50 and the torsion spring 52 are connected to the gimbal 14 and the flywheel support 18, respectively.
The gimbal 14 and the flywheel support 18 are rotatably supported around the X axis and the Y axis, respectively.

As described above, the actuator 46 determines a vehicle operation amount such as steering, accelerator, and brake, a vehicle behavior such as vehicle body acceleration, a vehicle body posture angular velocity, a flywheel posture angular velocity, a flywheel behavior such as a bearing load, and the like. , And is controlled by a control mechanism (not shown) to exert a predetermined suppressing force on the rotational force of the gimbal 14 and the flywheel support 18. As a result, both the bearing load and the swing angle of the flywheel 36 can be reduced with respect to the low frequency vibration acting on the vehicle. However, the actuator 46 cannot exhibit the vibration damping function with respect to vibration having a vibration component higher than the control frequency band, or minute vibration near or below the resolution of the sensor or the actuator. Therefore, as in the first embodiment, the cushioning member 44 is provided between the flywheel support 18 and the bearing portion 38, and the spring hardness is set to an appropriate value, whereby the above-described minute vibration and actuator The effect of high-frequency vibration equal to or higher than the response frequency of 46 is reduced. Thus, the bearing load can be reduced.

In this case, the spring hardness of the buffer structure member 44 is made softer than the spring hardness of the spring element in the bearing portion 38, and the mass of the flywheel 36 and the bearing portion 38 and the buffer structure member 44 are combined. And the resonance frequency is
The mass of the mass of the flywheel 36, the bearing portion 38, and the flywheel support 18 and the resonance frequency of the gimbal 14 are set to be sufficiently higher, and the mass of the flywheel 36 and the bearing portion 38 is combined with the buffer structure. The resonance frequency with the member 44 is set to be higher than the response frequency of the actuator 46. As a result, as described above, high-frequency vibrations and minute vibrations that cannot be damped by the actuator 46 are absorbed by the buffer structure member 44, and the bearing load of the bearing portion 38 can be suppressed.

The bearing load used when controlling the actuator 46 can be measured by attaching a strain gauge 54 to the cushioning structural member 44 as shown in FIG.

FIG. 10 shows the actuator 46 described above.
The result of the measurement of the effect is shown. 10 (a), (b),
The horizontal axis and vertical axis of (c) and (d) are the same as those in FIG. The rotation speed of the flywheel 36 is also 30,000 rpm as in the case of FIG.

As shown in FIGS. 10 (a), 10 (b), 10 (c) and 10 (d), when the actuator 46 is used, as compared with the case where the actuator 46 is not used.
A difference occurs in the peak height of the transmission gain existing at 0.003 Hz. That is, when the actuator 46 is used, the height of the peak gain is reduced by about 10 dB, and the amplitude generated when the same vibration is applied to the vehicle is reduced by about one third by the control of the actuator 46.
It can be seen that it is suppressed.

FIG. 11 shows the vibration damping action of the case where the rotation of the gimbal 14 and the flywheel support 18 is controlled only by the actuator 46 and the case where the buffer structure member 44 according to the present embodiment is used together. The measurement results are shown. 11 (a), (b), (c), and (d), the horizontal axis and vertical axis and the rotation speed of the flywheel 36 are the same as those in FIGS.

As shown in FIGS. 11A, 11B, 11C, and 11D, the actuator 46 according to the present embodiment
About 100H in the case of using together with the buffer structure member 44
In the high frequency region exceeding z, the bearing load of the bearing portion 38 and the transmission gain to the swing angle of the rotating shaft (Z axis) of the flywheel 36 are all reduced. The control frequency band of the actuator 46 is 10 Hz in this experimental example.
Therefore, the effect of suppressing vibration exceeding the control frequency band of the actuator 46 is recognized by using the buffer structure member 44 together.

[0044]

As described above, according to the present invention,
Even when low frequency vibration acts on the vehicle, the swing angle of the rotary shaft of the flywheel does not increase, so that the device can be downsized and the degree of freedom in designing the vehicle can be improved.

Further, even when high-frequency vibration acts on the vehicle, the bearing load can be suppressed, so that the size of the bearing portion can be reduced and the energy loss can be reduced.

[Brief description of the drawings]

FIG. 1 is a perspective view of a first embodiment of a flywheel battery support device having a multiple elastic structure according to the present invention.

FIG. 2 is a view showing an example of an elastic mounting portion used in the embodiment shown in FIG. 1;

FIG. 3 is a view showing an example of an elastic mounting portion used in the embodiment shown in FIG. 1;

FIG. 4 is a sectional view showing an example of the damper shown in FIG. 3;

FIG. 5 is a sectional view showing the inside of a flywheel support in the embodiment shown in FIG. 1;

6 is a sectional view taken along line VI-VI in FIG.

FIG. 7 is an explanatory diagram of an operation of the buffer structure member shown in FIGS. 5 and 6;

FIG. 8 is a diagram showing a vibration damping action of the flywheel battery support device having the multiple elastic support structure according to the present embodiment.

FIG. 9 is a view showing an actuator used in a flywheel battery support device having a multiple elastic support structure according to a second embodiment of the present invention.

FIG. 10 is a diagram showing a vibration damping action when the actuator shown in FIG. 9 is used.

FIG. 11 is a diagram illustrating a vibration damping action of a flywheel battery support device having a multiple elastic support structure using both an actuator and a buffer structure member according to a second embodiment.

[Explanation of symbols]

10 housing, 12 fixing members, 14 gimbal,
16, 20 elastic mounting portion, 18 flywheel support, 22 spring, 24 damper, 26 fixed wall, 28
Liquid chamber, 30 area movable orifice, 32 movable section, 34
Accumulator, 36 flywheel, 38 bearing, 40 radial bearing, 42 thrust bearing, 44 cushioning structural member, 46 actuator, 48
Motor, 50 motor shaft, 52 torsion spring, 54
Strain gauge.

Continuing from the front page (72) Inventor Toshifumi Arakawa 41-cho, Chuchu-Yokomichi, Nagakute-cho, Aichi-gun, Aichi Prefecture Inside of Toyota Central R & D Laboratories Co., Ltd. No. 1 Inside Toyota Central Research Institute Co., Ltd. (72) Inventor Yukio Inaguma 41-Cho, Yokomichi, Oji, Nagakute-cho, Aichi-gun, Aichi Prefecture No. 1 Inside Toyota Central Research Laboratory Co., Ltd. 41, No. 41, Yokomichi, Chochu-machi

Claims (1)

[Claims] 1. A fixing member provided to fix a position to a vehicle, and an elastic mounting portion configured by a spring or a damper on the fixing member to apply a predetermined suppressing force in a rotation direction.
A gimbal rotatably supported around a first support shaft, and an elastic mounting portion configured by a spring or a damper on the gimbal and acting on a predetermined restraining force in a rotation direction.
A flywheel support rotatably supported around a second support axis orthogonal to the first support axis; a flywheel held inside the flywheel support; and the flywheel support as a flywheel support. And a bearing portion rotatably supported around a rotation axis orthogonal to both the first and second support shafts, and provided between the bearing portion and the flywheel support member, and functions as a spring. A flywheel battery support device having a multiple elastic support structure, comprising: a shock-absorbing structure member; The spring hardness of the shock-absorbing structural member is softer than the spring hardness of the spring element present in the bearing portion, and the flywheel and the bearing portion are in contact with each other. The resonance frequency of the mass and the buffer structure member is set to be higher than the resonance frequency of the gimbal and the mass of the flywheel, the bearing, and the flywheel support. Flywheel battery support device with multiple elastic support structures.