JP2015233369A - Vibration power generator - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a vibration power generator capable of more effectively and efficiently performing power generation by utilizing vibration energy of non-utilized energy.SOLUTION: The vibration power generator includes: a rotational inertial mass mechanism 1 which is provided while being connected to a vibrating structure 10 and generates rotational inertial mass effects by rotating a weight when the structure 10 is displaced; a power generation mechanism 2 which is provided while being connected to the rotational inertial mass mechanism 1 and driven by rotating the rotational inertial mass mechanism 1 to generate power; and an additional spring 3 which is connected in series to the rotational inertial mass mechanism 1 and the power generation mechanism 2. A vibration frequency that is determined by the rotational inertial mass mechanism 1 and the additional spring 3, is tuned to a dominant vibration frequency of the structure 10.

Description

  The present invention relates to a vibration power generator.

  Conventionally, it has been proposed and put into practical use that a damping device called TMD (Tuned Mass Damper) is installed on the top side of a building (such as a rooftop) to reduce the earthquake response of the building (for example, Patent Document 1, Patent Document 2).

  This TMD is configured, for example, as a one-degree-of-freedom vibration system in which a pendulum (weight (weight)) is attached to an accompanying frame and the weight reciprocates. And by synchronizing the primary natural period of the building and vibrating the weight in the opposite direction to the vibration of the building, that is, by utilizing the inertial resistance force (inertial mass effect) due to the vibration of the weight It can attenuate the seismic energy acting on the building and reduce the response of the building.

  On the other hand, Non-Patent Document 1 discloses a system (vibration power generator) that increases the amount of power generated by a vibration generator by amplifying small vibrations generated inside and outside a building, such as a TMD weight body, by a vibration amplifier. Yes.

JP 2000-18323 A JP 2011-220511 A

Takenaka Corporation: September 16, 2010, Takenaka Corporation homepage release, “http://www.takenaka.co.jp/news/2010/09/02/index.html”

  However, the vibration power generator described above is intended for micro vibrations, and the frequency at which efficient power generation can be performed is 25 to 30 Hz. That is, there is a problem that power cannot be generated by effectively using vibration energy in a wide frequency band.

  In view of the above circumstances, an object of the present invention is to provide a vibration power generation apparatus that can generate power more effectively and efficiently by using vibration energy of unused energy.

  In order to achieve the above object, the present invention provides the following means.

  The vibration power generation apparatus of the present invention is connected to a vibrating structure, and when the structure is displaced, a weight rotates to generate a rotating inertial mass effect, and the rotating inertial mass mechanism is connected to the rotating inertial mass mechanism. A power generation mechanism that is driven by the rotation of the rotary inertial mass mechanism to generate power, and the rotary inertial mass mechanism and an additional spring connected in series to the power generation mechanism, the rotary inertial mass mechanism and the The frequency determined by the additional spring is tuned to the dominant frequency of the structure.

  In the vibration power generator of the present invention, it is desirable that a load resistance defined by the following formula (1) is connected to the power generation mechanism.

ここで、Ｒ：回路抵抗、Ｌ_ｄ：ボールねじのリード、Ｋ_Ｅ：起電力定数、Ｋ_Ｔ：トルク係数、ｍ：構造物の質量、ｋ：構造ばね（剛性）、μ：慣性質量と構造物の質量の比（Ψ／ｍ）である。

Here, R: circuit resistance, L _d : ball screw lead, K _E : electromotive force constant, K _T : torque coefficient, m: mass of structure, k: structural spring (rigidity), μ: inertia mass and structure This is the mass ratio (Ψ / m) of the object.

  In the vibration power generation device of the present invention, the vibration energy transmitted from the structure is converted into rotational kinetic energy by the rotating inertial mass mechanism by being connected to the structure, and the power generation mechanism can generate power.

  Moreover, it can synchronize with a structure by providing an additional spring, and it becomes possible to amplify the amplitude of a power generator from the amplitude of a structure, and to improve electric power generation efficiency.

  Furthermore, it can be applied not only to fine vibrations but also to large amplitude vibrations with a relatively simple device configuration. In addition, a tuning effect can be obtained at a low frequency, and a vibration power generator having excellent power generation efficiency and high reliability can be manufactured at low cost. Furthermore, since the vibration applied to the structure can be converted into electric energy, a secondary effect of reducing the vibration of the structure such as a building can be expected.

It is a figure which shows the vibration electric power generating apparatus which concerns on one Embodiment of this invention. It is a model figure of the vibration electric power generating apparatus which concerns on one Embodiment of this invention. It is a model figure of the vibration electric power generating apparatus which concerns on one Embodiment of this invention. It is a figure which shows the relationship between the inertial mass ratio of the vibration electric power generating apparatus which concerns on one Embodiment of this invention, and generated electric power. It is a figure which shows the relationship between the inertial mass ratio of the vibration electric power generating apparatus which concerns on one Embodiment of this invention, and a displacement response magnification. It is a figure which shows the relationship between the inertial mass ratio and damping coefficient ratio of the vibration electric power generating apparatus which concerns on one Embodiment of this invention. It is a figure which shows the relationship between the inertial mass ratio and absorption energy ratio of the vibration electric power generating apparatus which concern on one Embodiment of this invention.

  Hereinafter, a vibration power generation apparatus according to an embodiment of the present invention will be described with reference to FIGS. 1 to 7.

  As shown in FIG. 1, the vibration power generation apparatus A of the present embodiment is configured by integrating a rotary inertia mass mechanism (rotational inertia mass) 1 and a power generation mechanism 2 of a power generation motor. Further, in the present embodiment, as shown in FIG. 2, the vibration power generation apparatus A is configured by connecting the rotary inertia mass mechanism 1 and the power generation mechanism 2 and the additional spring 3 in series.

  Specifically, as shown in FIG. 1, the rotary inertia mass mechanism 1 of the vibration power generator A of the present embodiment mainly includes a ball screw mechanism (a ball screw 4 and a ball nut 5 screwed to the ball screw 4). The axial O1 displacement is converted into rotation by a mechanism as an element) and the weight 6 is rotated to generate an inertial mass effect that is several thousand times as large as the weight.

  Furthermore, in the vibration power generation apparatus A of the present embodiment, a rotating shaft is connected to the ball screw 4, and the power generation mechanism 2 is integrally coupled to the rotating inertial mass mechanism 1 so that the rotating shaft rotates by the rotation of the rotating inertial mass mechanism 1. Has been. Thus, the power generation mechanism 2 is configured to rotate in proportion to the axial O1 displacement.

  The vibration power generator A of the present embodiment is configured such that one end portion (one end portion side to which the bearing 7 is fixed) 8 of the rotary inertia mass mechanism 1 is connected to the power generation mechanism 2 and the other end portion (the ball nut 5 is fixed). (End side) 9 is connected to a structure (vibrating structure) 10 and the one end 8 side and the other end 9 side of the rotary inertia mass mechanism 1 are rotationally restrained. As a result, when vibration occurs in the structure 10, the vibration causes an axial O1 displacement to rotate the rotary inertia mass mechanism 1, and the rotary inertia mass mechanism 1 rotates and the power generation mechanism 2 drives to generate power.

Therefore, by installing this vibration power generation apparatus A connected to the structure 10, the vibration energy transmitted from the structure 10 is amplified by the rotary inertia mass mechanism 1, and the generator motor generates power using the vibration energy that is the unused energy. The mechanism 2 can be rotated to generate power.
Further, when the rotary inertia mass mechanism 1 is handled as a rotary inertia mass damper, the rotational resistance force of the power generation mechanism 2 can be used as attenuation of the rotary inertia mass damper.

Here, the electromotive force E of the power generation mechanism 2 is expressed by the following equation (2), assuming that the displacement x, the rotation amount θ = 2πx / L _d , and the electromotive force constant K _E (unit: V · s / rad). The

The load circuit current I is I = E / R, where R is the circuit resistance, and the resistance F of the vibration exciter (rotational inertial mass mechanism 1) is the torque coefficient K _T (unit) of the power generation mechanism 2 by this current. : N · m / A) and the rotational moment of inertia I _θ of the weight 6 are expressed by the following equation (3).

  On the other hand, it is known that a resistance (such as an illumination lamp as a load) is connected to a coil (power generation mechanism), such as a handwheel generator for disaster prevention or a dynamo generator for bicycles, and it rotates when the lamp is turned on. Resistance increases (heavy). A device that exhibits a damping force based on this principle is shown in, for example, “Sagoda, Otake, Matsuoka: Research on Power Generation Type Vibration Suppressor, Transactions of the Japan Society of Mechanical Engineers, August 2005” and a damping force proportional to speed. Has been shown to be demonstrated.

  From the above, the vibration power generation apparatus A of the present embodiment, in which the power generation mechanism 2 and the rotary inertia mass mechanism 1 are integrated, has the relative speed x (above) at both ends of the rotary inertia mass mechanism 1 by the power generation mechanism 2. It has a proportional damping force and a resistance force proportional to the relative acceleration x (above). And when satisfy | filling the relationship of following Formula (4) and Formula (5), it will be comprised as the vibration electric power generating apparatus A which made the damping coefficient c and the inertial force Ψ parallel.

  More specifically, the vibration power generation apparatus A according to the present embodiment in which the power generation mechanism 2, the rotary inertia mass mechanism 1, and the additional spring 3 are connected in series is structured as shown in FIGS. Will be described in connection with the structural spring (rigidity) k. In this case, the rotation of the power generation mechanism 2 and the rotation of the weight 6 are the same (or the speed increasing ratio β times), and the power generation mechanism 2 and the rotary inertia mass mechanism 1 are in parallel, and this vibration power generation device is on the vibration model. A is equivalent to the parallel arrangement of the damping coefficient c and the rotational inertial mass Ψ in the equations (4) and (5).

  In the above model, when the damping effect is exerted by the rotary inertial mass mechanism 1, the optimum values of each specification are expressed as “Kenji Saito, Satoru Kurita, Norio Inoue: Linear viscous damper using inertial connection elements” The following may be set with reference to “Study on Optimal Response Control and Kelvin Modeling Method for One-mass Structure by Mathematical Structure, Vol. 53B, pp. 53-66, March 2007”.

First, the inertial mass Ψ is obtained from the rotational inertia moment I _θ of the rotary weight 6 and the lead (screw thread interval) L _{d of the} ball screw 4 by Expression (6).

If the ratio of the structure 10 to the mass m is μ = Ψ / m and the structural rigidity is k, the optimum value k _d of the additional spring 3 is the expression (7), and the optimum value c of the damping parallel to the inertia mass Ψ is the expression (8)

  Next, from the equations (6), (7), (8), and (4), the optimum load resistance (impedance) R connected to the power generation mechanism 2 is represented by equation (9).

And if comprised in this way, near the natural frequency of the structure 10, the amplitude of the vibration electric power generating apparatus A will become larger than the amplitude of the structure 10 by a tuning effect. For this reason, the power generation efficiency can be improved by providing the power generation mechanism 2 at a location where the amplitude is enlarged. Further, if the load resistance to the power generation mechanism 2 is the same, if the amplitude (speed amplitude) of the power generation mechanism 2 is increased n times, the voltage (electromotive force) and current generated in the power generation mechanism 2 are also increased n times. The power generated by mechanism 2 is n ² times. This generated power can be used for the illumination 11 of the structure 10 or can be stored and combined with other power (buying, solar power, wind power, etc.).

More detailed description is as follows.
In the model shown in FIG. 2, the electric power generated by the power generation mechanism 2 can be obtained as follows.

  As shown in the following formula (10), the excitation force f acting on the structure 10 is a sine wave having an angular frequency ω.

ここで、ｉ＝√（−１）、ｔは時間である。また、構造物１０の固有角振動数をω_０＝√（ｋ／ｍ）とし、構造減衰は無視する。

Here, i = √ (−1), t is time. Further, the natural angular frequency of the structure 10 is set to ω ₀ = √ (k / m), and the structure damping is ignored.

In the optimum design expressed by the equations (6) to (9), the maximum value of the frequency transfer function is optimized at the time of tuning, and the larger angular frequency of the two maximum values. Ω _Q , the ratio ν _Q to the natural angular frequency ω ₀ of the structure 10 ν _Q = ω _Q / ω ₀ , and the natural angular frequency ω _d = √ (k _d / by the additional spring k _d and the inertial mass Ψ. When the ratio γ of Ψ) to ω ₀ is γ = ω _d / ω ₀ , the amplitude X _d of the vibration power generator A with respect to the amplitude X of the structure 10 is expressed by the following equation (11).

ここで、ｈ_ｄは慣性質量Ψに並列する減衰係数の最適値ｃから慣性質量比μ＝Ψ／ｍ（最適値に対しμ＝（γ^２−１）／γ^２）を用い、次の式（１２）で定められる。

Here, h _d is using the optimum value inertial mass ratio from c μ = Ψ / m of attenuation coefficients in parallel to the inertial mass [psi (relative optimum ^{μ = (γ 2 -1) /} γ 2), the following equation (12).

Further, from the calculation of the optimum value, ν _Q is expressed by the following equation (13).

  Then, when these formulas (12) and (13) are substituted into formula (11), formula (14) is obtained.

Since | X _d / X | is the ratio of the displacement of the vibration power generator A and the displacement of the structure 10, when the power generation mechanism 2 is provided in the vibration power generator A (FIG. 3B: damping coefficient c + inertial mass Ψ (+ Additional spring kd)) and the ratio of the electromotive force (voltage) when the power generation mechanism 2 is provided between the structure 10 and the fixed end (FIG. 3 (a): only the damping coefficient c) Yes, if the load resistance is the same, the current ratio will be the same. In addition, the electric power generated by the power generation mechanism 2 is “electromotive force (voltage) × current, and | X _d / X | ² is between the case where the vibration power generation apparatus A includes the power generation mechanism 2 and the structure 10 and the fixed end. It can be regarded as the ratio of power when provided.

Substituting the relationship of γ ² = 1 / (1-μ) with respect to the optimum value into the equation (14), the inertial mass ratio μ and the generated power E (the power generation mechanism 2 is provided between the structure 10 and the fixed end) The comparison with the power in the case is as shown in FIG.
That is, the smaller the inertial mass ratio, the higher the power amplification factor. From the above equation (8), the attenuation coefficient c becomes smaller, so that the generated power is small, but it can be seen that power can be generated efficiently.

On the other hand, it is necessary to consider the vibration of the structure 10 with respect to the excitation force. The displacement amplitude X of the structure 10 is obtained by the response magnification with respect to the static displacement (f ₀ / k) with respect to the excitation force, and is expressed by the following equation (15).
FIG. 5 shows the relationship of the equation (15).

Here, for example, in the case of “vibration power generation apparatus A in which the power generation mechanism 2 and the rotary inertia mass mechanism 1 are integrated”, the inertia mass Ψ is set to 5% of the structure 10 (μ = 0.05). The displacement response of 10 is 6 times the “static displacement when the excitation force f _{0 is applied} to the structural rigidity k”, and the power of the power generation mechanism 2 at this time is provided between the structure 10 and the fixed end. 12.5 times greater than

In addition, when the inertial mass Ψ is set to 15% of the structure 10 (μ = 0.15), the displacement response magnification of the structure 10 is reduced to three times this half, and the response suppression effect is improved. The power of the power generation mechanism 2 at that time is five times that provided between the structure 10 and the fixed end, and the amplification efficiency decreases.
However, since the amplification factor is always larger than 1, it can be said that the power generation efficiency can be improved much more than the case where the power generation mechanism 2 is integrated with the rotary inertial mass mechanism 1 as compared with other places.

On the other hand, when the power generation mechanism 2 is provided between the structure 10 and the fixed end and the load resistance is provided so as to achieve the optimum attenuation that minimizes the displacement response magnification, the mechanism in which the load resistance is added to the power generation mechanism 2 the equivalent damping constant When h ₁ by a maximum displacement response magnification is expressed by the following equation (16).

ここで、ｈ_１は振動発電装置Ａの減衰係数をｃ_１としたとき、ｈ_１＝ｃ_１／（２ｍω_０）で表される。

Here, h ₁ is represented by h ₁ = c ₁ / (2 mω ₀ ), where c ₁ is the damping coefficient of the vibration power generator A.

  Next, when the response magnifications are made uniform from the equations (15) and (16), the following equations (17), (18), and (19) are obtained.

  Therefore, the ratio R (the same as the ratio of the power to be generated) of the absorbed energy in the vibration power generator A of the present embodiment to the absorbed energy when the power generation mechanism 2 is provided between the structure 10 and the fixed end is: From the equation (8), it is expressed by the following equation (20).

Then, the relationship of Expression (20) is illustrated in FIGS. 6 and 7.
Thus, for example, in the vibration power generation apparatus A integrally including the rotary inertia mass mechanism 1 and the power generation mechanism 2, when the inertia mass Ψ is 5% of the structure 10 (μ = 0.05), the structure 10 The absorption energy of 1.07 times, that is, the generated electric power of 1.07 times can be obtained with the attenuation coefficient of 0.1 times when the displacement response is made the same by providing between the first and the fixed ends.

  Further, when the inertial mass Ψ is set to 15% of the structure 10 (μ = 0.15), the absorption energy / generated power of 1.25 times can be obtained with the attenuation factor of 0.25.

Thus, in the vibration power generator A of the present embodiment, even if the attenuation coefficient is reduced by α _c times, more power than the conventional power can be obtained. This equation (4), which means that only a small electromotive force constant K _E and torque coefficient K _T of the formula (5), thereby, in the vibration generator unit A of this embodiment, a small Large electric power can be obtained efficiently with an inexpensive generator (power generation mechanism 2).
6 and 7, if μ ≧ 0.25, R> 1, and it can be seen that the vibration power generation apparatus A of the present embodiment can obtain more electric power. And the additional spring 3 are connected in series to make them tuned so that they are in opposite phases during resonance and the amplitude of the power generation mechanism 2 integrated with the rotary inertial mass mechanism 1 is increased.

  Therefore, in the vibration power generation apparatus A of the present embodiment, the rotary inertia mass mechanism 1 and the power generation mechanism 2 are integrally configured, and the additional spring 3 is provided to be synchronized with the structure 10. Thus, it is possible to increase the amplitude of the power generation mechanism 2 and achieve power generation efficiency superior to the conventional one.

  Therefore, in the vibration power generation apparatus A of the present embodiment, the vibration energy transmitted from the structure 10 is converted into rotational kinetic energy by the rotary inertia mass mechanism 1 by installing the power generation mechanism 2 by connecting to the structure 10. It can be rotated to generate electricity.

  Moreover, it can synchronize with the structure 10 by providing the additional spring 3, and it becomes possible to amplify the amplitude of the electric power generation mechanism 2 from the amplitude of the structure 10, and to improve electric power generation efficiency here.

  Furthermore, it can be applied not only to fine vibrations but also to large amplitude vibrations with a relatively simple device configuration. Further, a tuning effect at a low frequency of 10 Hz or less with respect to the rotary inertia mass mechanism 1 has been confirmed, and the vibration power generator A having high reliability can be manufactured at low cost. Furthermore, since the vibration applied to the structure 10 can be converted into electric energy, a secondary effect of reducing the vibration of the structure 10 such as a building can be expected.

  The embodiment of the vibration power generation apparatus according to the present invention has been described above, but the present invention is not limited to the above-described embodiment, and can be changed as appropriate without departing from the spirit of the present invention.

For example, the vibration power generation apparatus A of the present embodiment may be used by replacing the inertial mass damper disclosed in Japanese Patent No. 5146757, for example. That is, the vibration power generation apparatus A may be configured by providing diagonal members like a stringed beam from both ends of an H-shaped beam of a large span structure and joining the rotary inertia mass mechanism 1 and the power generation mechanism 2 at the center thereof. In this case, the slant member is equivalent to the additional spring 3, to evaluate the vertical stiffness k _d. The vibration power generator A (the rotary inertia mass mechanism 1 and the power generation mechanism 2) has the inertia mass Ψ and the damping coefficient c in parallel, and evaluates the damping coefficient c by the resistance force of the power generation mechanism 2.

  The vibration power generation apparatus A of the present embodiment is installed on a bridge or the like, and is used to efficiently generate power using unused energy (vibration energy) such as traffic vibration, walking vibration, and vibration caused by wind load. May be.

1 Rotational inertial mass mechanism (rotational inertial mass)
2 Power generation mechanism 3 Additional spring 4 Ball screw 5 Ball nut 6 Rotary weight 7 Bearing 8 One end 9 Other end 10 Structure 11 Illumination A Vibration power generation device O1 Axial direction

Claims (2)

A rotary inertial mass mechanism that is connected to a vibrating structure and rotates when a displacement of the structure causes a rotational inertial mass effect;
A power generation mechanism that is connected to the rotary inertial mass mechanism and that generates power by being driven by the rotation of the rotary inertial mass mechanism;
An additional spring connected in series with the rotary inertia mass mechanism and the power generation mechanism,
A vibration power generator characterized in that a frequency determined by the rotary inertia mass mechanism and the additional spring is synchronized with an excellent frequency of the structure. The vibration power generator according to claim 1,
A vibration power generation apparatus, wherein a load resistance defined by the following formula (1) is connected to the power generation mechanism.

Here, R: circuit resistance, L _d : ball screw lead, K _E : electromotive force constant, K _T : torque coefficient, m: mass of structure, k: structural spring (rigidity), μ: inertia mass and structure This is the mass ratio (Ψ / m) of the object.

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