JP7419282B2 - Damped power generation device, damped power generation system, and wind power generation system - Google Patents

Description

Embodiments of the present invention relate to a damped power generation device, a damped power generation system, and a wind power generation system.

Vibration damping technology that suppresses vibrations in structures is an important technology in terms of ensuring the reliability of structures. Active damping devices such as dynamic dampers or AMD (active mass dampers) are typical examples of damping techniques. Furthermore, a technique has also been developed in which a driving weight provided separately from the structures is interposed between the two structures as an inertial connection element to absorb the relative motion between the two structures. In this case, vibration transmission from one structure to the other structure can be suppressed.

On the other hand, technology has also been developed to convert vibrational energy into electrical energy by generating electricity using vibrational energy. A device that embodies this technology is called a vibration power generation device. The vibration power generation device absorbs vibration energy and generates power, thereby making it possible to simultaneously achieve vibration suppression and power generation. However, when vibration energy is converted into electrical energy and vibrations are suppressed, the energy allocated to power generation is reduced. As a result, the electric power that is the power generation output may decrease. That is, vibration energy and electrical energy converge at an equilibrium point, making it difficult to obtain sufficient power.

Additionally, wave power generation devices that utilize the rocking motion of ships have been developed. A wave power generation device is an example of a technology that uses a generator in combination with an AMD type active vibration damping device. More specifically, a generator is provided that converts the rocking motion of the driving weight of the AMD into generated energy, and the damping coefficient of the generator is adjusted so that the generated energy is greater than the control energy that drives the driving weight. is set. Therefore, power generation can be efficiently performed using the wave energy absorbed by driving the driving weight body. In this wave power generation device, the control energy required to drive the driving weight of the AMD is controlled to be 1/3 or less of the generated energy. In other words, control energy is suppressed in order to obtain power generation energy, and there is a trade-off relationship between power generation and damping.

In this way, both the vibration damping device and the vibration power generation device according to the prior art provide a driving weight body separately from the structure that receives vibration, and convert the kinetic energy of the driving weight body into vibration damping or electrical energy. The basic principle was to do so. This has made it difficult to achieve both vibration damping and vibration power generation.

Patent No. 4002899 Patent No. 5695991

The present invention has been made in consideration of these points, and provides a vibration-damped power generation device, a vibration-damped power generation system, and a wind power generation system that can suppress vibration and convert vibration energy into electrical energy. The purpose is to provide

The vibration damping power generation device according to the embodiment includes a first structure, a second structure, a conversion mechanism, and a device generator. The second structure is elastically supported by the first structure and is movable relative to the first structure. The conversion mechanism includes a conversion rotor and converts a relative displacement between the first structure and the second structure into a rotational displacement of the conversion rotor. The device generator generates electricity using the rotational displacement of the conversion rotor. The conversion rotor functions as an inertial mass element that reduces vibrations due to relative displacement between the first structure and the second structure.

The damped power generation system according to the embodiment includes the above-mentioned damped power generation device, a DC converter that converts the generated power of the device generator of the damped power generator into DC power and outputs it, and a DC power output from the DC power converter. It is equipped with a power storage device that stores electric power.

The wind power generation system according to the embodiment is a system that supplies power to auxiliary equipment that controls wind power generation equipment. The wind power generation system includes the above-mentioned vibration suppressed power generation device, an auxiliary power system that supplies power to the auxiliary devices, and a device power generation system that supplies the device generated power of the device generator of the vibration suppressed power generation device to the auxiliary power system. It is equipped with. The device power generation system includes a DC converter that converts device-generated power into DC power and outputs the DC power, and an AC converter that converts the DC power output from the DC converter into AC power and outputs the AC power.

According to the present invention, vibration can be suppressed and vibration energy can be converted into electrical energy.

FIG. 1 is a schematic cross-sectional view showing a vibration damping power generation device according to a first embodiment of the present invention. FIG. 2 is a schematic cross-sectional view showing a typical spar type offshore wind power generation facility. FIG. 3 is a diagram showing a dynamic model of the vibration damping power generation device of FIG. 1. FIG. 4 is a diagram showing the vibration transmissibility for comparing the effect of inertial mass in the vibration damping power generation device of FIG. FIG. 5 is a diagram showing the vibration transmissibility for comparing the effects of the damping ratio in the vibration damping power generation device of FIG. FIG. 6 is a schematic cross-sectional view showing a vibration damping power generation device according to a second embodiment of the present invention. FIG. 7 is a schematic cross-sectional view showing a vibration damping power generation device according to a third embodiment of the present invention. FIG. 8 is a schematic cross-sectional view showing a vibration damping power generation device according to a fourth embodiment of the present invention. FIG. 9 is a schematic cross-sectional view showing a vibration damping power generation device according to a fifth embodiment of the present invention. FIG. 10 is a diagram showing a dynamic model of the vibration damping power generation device of FIG. 9. FIG. 11 is a diagram showing the vibration transmissibility in the vibration damping power generation device of FIG. FIG. 12 is a schematic sectional view showing a vibration damping power generation device according to a sixth embodiment of the present invention. FIG. 13 is a schematic cross-sectional view showing a vibration damping power generation device according to a seventh embodiment of the present invention. FIG. 14 is a schematic cross-sectional view showing a vibration damping power generation device according to an eighth embodiment of the present invention. FIG. 15 is a schematic sectional view showing a vibration damping power generation device according to a ninth embodiment of the present invention. FIG. 16 is a schematic perspective view showing a modification of the conversion mechanism shown in FIG. 15. FIG. 17 is a schematic cross-sectional view showing a vibration damping power generation device according to a tenth embodiment of the present invention. FIG. 18 is a schematic perspective view showing a modification of the vibration damping power generation device of FIG. 17. FIG. 19 is a schematic sectional view showing a vibration damping power generation device according to an eleventh embodiment of the present invention. FIG. 20 is a schematic cross-sectional view showing a vibration damping power generation device according to a twelfth embodiment of the present invention. FIG. 21 is a schematic cross-sectional view showing a vibration damping power generation device according to a thirteenth embodiment of the present invention. FIG. 22 is a schematic cross-sectional view showing a vibration damping power generation device according to a fourteenth embodiment of the present invention. FIG. 23 is a schematic cross-sectional view showing a vibration damping power generation device according to a fifteenth embodiment of the present invention. FIG. 24 is a schematic cross-sectional view showing a vibration damping power generation device according to a sixteenth embodiment of the present invention. FIG. 25 is a diagram showing a vibration damping power generation system according to the seventeenth embodiment of the present invention. FIG. 26 is a diagram showing a wind power generation system according to the eighteenth embodiment of the present invention. FIG. 27 is a diagram showing a wind power generation system according to the nineteenth embodiment of the present invention. FIG. 28 is a diagram showing a wind power generation system according to the twentieth embodiment of the present invention. FIG. 29 is a diagram showing a wind power generation system according to the twenty-first embodiment of the present invention. FIG. 30 is a diagram showing a modification of FIG. 29.

EMBODIMENT OF THE INVENTION Hereinafter, with reference to drawings, a vibration damping power generation device, a vibration damping power generation system, and a wind power generation system according to embodiments of the present invention will be described.

(First embodiment)
First, the vibration damping power generation device according to the present embodiment will be explained using FIGS. 1 to 5. Here, an example of a vibration damping power generation device applied to an offshore wind power generation facility will be described. However, the application example of the damped power generation device is not limited to this.

Before explaining the damped power generation device 20 according to the present embodiment, a general offshore wind power generation facility 1 will be explained using FIG. 2. FIG. 2 shows an example of a spar type offshore wind power generation facility.

The offshore wind power generation facility 1 shown in FIG. 2 includes a floating body 2 floating on the ocean, a tower structure 3, and a wind power generator main body 4.

The floating body 2 is elongated in the vertical direction. A part of the floating body 2 is located below the water surface and is immersed. The water surface is indicated by the symbol W in FIG. 2 and the like. The floating body 2 is formed in a cylindrical shape and is configured to withstand water pressure. A weight portion 2a filled with a heavy object such as concrete or ballast water is provided at the lower part of the floating body 2. This lowers the center of gravity of the floating body 2 and increases the stability of the floating body 2 floating on the ocean. The buoyancy of the floating body 2 and the gravity of the entire offshore wind power generation facility 1 are balanced, and the stability of the offshore wind power generation facility 1 as a whole is improved.

A support frame 2b is provided at the upper end of the floating body 2. The support frame 2b extends horizontally and is located above the water surface.

The tower structure 3 is located above the floating body 2 and extends upward from the support pedestal 2b. The tower structure 3 is formed into a columnar shape so as to extend vertically.

The wind power generator main body 4 is provided at the upper end of the tower structure 3. The wind power generator main body 4 is rotatable within a horizontal plane with respect to the tower structure 3 depending on the wind direction and the like. The wind power generator main body 4 includes a nacelle 4a supported by the tower structure 3, and a power generation rotor 4b rotatably provided on the nacelle 4a. A wind power generator 4c that generates power by rotating a power generation rotor 4b is built into the nacelle 4a. The power generation rotor 4b includes a plurality of blades 4d.

In this way, the floating body 2 and tower structure 3 of the offshore wind power generation facility 1 vibrate in the vertical direction under the vibration force of the waves. This vibration is also called heave.

Since the floating body 2 is floating on the ocean as described above, it can be considered to be elastically supported with respect to the stationary system. To illustrate this, in FIG. 2, the floating body 2 is elastically supported with respect to the stationary system by a virtual elastic body 5 having a spring constant _k0 . The virtual elastic body 5 is used not to indicate the presence of a spring member, but to schematically indicate that the floating body 2 moves in the vertical direction due to the buoyant force received from the surrounding water.

The cross-sectional area of the floating body 2 on the water surface is small compared to the mass of the entire offshore wind power generation facility 1. Therefore, the natural frequency of the floating body 2 is on the order of 10 ⁻³ Hz, which is extremely low. The period of waves on the ocean is generally about 2 seconds to 20 seconds, and the frequency of waves is about 0.05 Hz to 0.5 Hz. Therefore, the natural frequency of the offshore wind power generation facility 1 is sufficiently detuned from the frequency of waves, and the offshore wind power generation facility 1 is prevented from resonating with the waves. In this way, the offshore wind power generation facility 1 is designed so that waves do not generate large amplitudes. Therefore, the amplitude of the offshore wind power generation facility 1 is suppressed in proportion to the response magnification determined from the detuning rate of the wave frequency. However, since the spring constant k ₀ of the virtual elastic body 5 due to buoyancy is extremely small, it is expected that an amplitude exceeding several tens of centimeters will occur in the floating body 2 even in good weather. Therefore, the amplitude of the offshore wind power generation facility 1 can become large even if it is suppressed by detuning as described above. This amplitude is large compared to the amplitude of unbalanced vibration of a rotating electric machine such as an electric motor, which is on the order of micrometers. When the height of waves increases, such as during bad weather, the amplitude of the floating body 21 may increase in proportion to the height of the waves.

The offshore wind power generation facility 1 includes an auxiliary machine 6 (see FIG. 26) that controls the wind power generator main body 4. The auxiliary machine 6 uses external power to control the direction of the wind power generator main body 4, the pitch (deflection angle) of the blades 4d, and the floating body according to wind conditions such as wind direction and wind speed. For this reason, it is preferable that the vibrations of the wind power generator main body 4 be reduced as much as possible. For example, when vibration increases during bad weather, the vibration acts as a mechanical load on the blade 4d and the like. For this reason, it is preferable that the vibrations transmitted to the wind power generator main body 4 be reduced.

In the offshore wind power generation facility 1, external power is supplied from an external power source to the auxiliary equipment 6 in order to control the direction of the wind power generator main body 4, etc., as described above. However, since the offshore wind power generation facility 1 is isolated, it becomes difficult to control it if the power supply system is lost during bad weather or the like. In some cases, the blade 4d may be damaged by the force of the wind. For this reason, the offshore wind power generation facility 1 is equipped with an emergency power source such as a storage battery or an emergency diesel generator. This prevents loss of control even if external power is lost. However, if the loss of external power continues for a long period of time, there is a possibility that the power supply from the emergency power source will reach its limit.

Considering this situation, the damped power generation device 20 that can suppress vibrations caused by waves and obtain electric power is beneficial from the viewpoint of stable operation of the offshore wind power generation facility 1 and maintenance of power supply in an emergency. .

Next, a vibration damping power generation device 20 according to the present embodiment will be described using FIG. 1. In this embodiment, an example in which a damped power generation device 20 is applied to an offshore wind power generation facility 10 shown in FIG. 1 will be described. Here, a spar-type offshore wind power generation facility will be explained as an example of the offshore wind power generation facility 10, but the offshore wind power generation facility is not limited to the spar type offshore wind power generation facility, and may be any type of offshore wind power generation facility.

The damped power generation device 20 shown in FIG. 1 includes a support structure 30, a tower structure 40, a first elastic body 50, a conversion mechanism 70, and a device generator 80. The offshore wind power generation facility 10 is comprised of this vibration damping power generation device 20 and the wind power generator main body 4 described above.

The support structure 30 is an example of a first structure. The support structure 30 includes a floating body 31. The floating body 31 is formed to extend along the central axis L1. That is, the floating body 31 is elongated along the central axis L1 and is formed in a cylindrical shape. When the floating body 31 is not rolling, the central axis L1 is along the vertical direction. A part of the floating body 31 is located below the water surface and immersed in the surrounding seawater. The floating body 31 is configured to withstand water pressure.

A weight section 32 filled with a heavy object such as concrete or ballast water is provided at the lower part of the floating body 31. This lowers the center of gravity of the floating body 31 and increases the stability of the floating body 31 floating on the ocean. The buoyancy of the floating body 31 and the gravity of the entire offshore wind power generation facility 10 are balanced, and the stability of the offshore wind power generation facility 10 as a whole is improved.

The floating body 31 includes a first cavity 33 that accommodates a lower portion 40a (an example of a portion) of the tower structure 40. The first cavity portion 33 extends in the axial direction d along the central axis L1. The diameter of the first cavity 33 is larger than the outer diameter of the tower structure 40.

A guide rail (not shown) extending in the axial direction d may be provided on the inner peripheral surface of the floating body 31. In this case, the relative displacement of the tower structure 40 with respect to the floating body 31 can be guided in the axial direction d. Further, a plurality of rollers 34 may be provided on the inner peripheral surface of the floating body 31. The roller 34 can roll against the outer peripheral surface of the tower structure 40. Thereby, relative displacement of the tower structure 40 with respect to the floating body 31 can be performed smoothly.

The floating body 31 is elastically supported with respect to the stationary system by a virtual elastic body 60 having a spring constant k ₀ , similar to the virtual elastic body 5 of the floating body 2 shown in FIG.

A generator support pedestal 35 is provided at the upper end of the floating body 31. The generator support pedestal 35 extends horizontally and is located above the water surface. The generator support pedestal 35 is fixed to the floating body 31 and supports the device generator 80. The generator support frame 35 includes a through hole 36 through which the tower structure 40 passes.

The tower structure 40 is an example of a second structure. The tower structure 40 extends in the axial direction d. That is, the tower structure 40 is elongated in the axial direction d and is formed in a cylindrical shape. The lower portion 40a of the tower structure 40 is accommodated in the first cavity 33 of the floating body 31, and extends upward from the first cavity 33 beyond the generator support frame 35. The tower structure 40 may be positioned concentrically with the floating body 31.

Tower structure 40 is resiliently connected to support structure 30. In this embodiment, the tower structure 40 is elastically supported by the floating body 31. The tower structure 40 is configured to be movable relative to the floating body 31. In this embodiment, the floating body 31 and the tower structure 40 are capable of translational displacement in the axial direction d. The above-mentioned wind power generator main body 4 is provided at the upper end of the tower structure 40.

The first elastic body 50 according to this embodiment elastically connects the tower structure 40 to the floating body 31. The first elastic body 50 has a spring constant _k1 . The first elastic body 50 may be constituted by a spring member such as a coil spring, for example.

The conversion mechanism 70 includes a conversion rotor 71 and is a mechanism that converts the relative displacement between the floating body 31 and the tower structure 40 into a rotational displacement of the conversion rotor 71. The conversion mechanism 70 includes a rack rail 72 and a pinion gear 73.

The rack rail 72 is an example of a rack, and is provided on the outer peripheral surface of the tower structure 40. The rack rail 72 extends in the axial direction d. The rack rail 72 can be inserted into the first cavity 33 of the floating body 31.

The pinion gear 73 is rotatably supported by the generator support frame 35. The pinion gear 73 constitutes the conversion rotor 71 described above. The pinion gear 73 meshes with the teeth of the rack rail 72, and converts a relative translational displacement in the axial direction d between the tower structure 40 and the floating body 31 into a rotational displacement. In this embodiment, pinion gear 73 is coaxially connected to generator rotor 81. In FIG. 1, the pitch radius of the pinion gear 73 is indicated by r.

The device generator 80 is fixedly supported by the generator support pedestal 35. The device generator 80 is configured to generate power by bidirectional rotational displacement of the conversion rotor 71. The device generator 80 includes a generator rotor 81 and is configured as a rotating electric machine. In this embodiment, generator rotor 81 has a rotation axis along the horizontal direction. In FIG. 1, the rotational axis of the generator rotor 81 is along a direction perpendicular to the plane of the paper. Further, in FIG. 1, one device generator 80 is installed on the generator support pedestal 35. The rotational displacement converted from the relative displacement of the tower structure 40 by one conversion mechanism 70 is transmitted to the generator rotor 81 of the device generator 80.

The vibration damping power generation device 20 according to this embodiment configured as described above is schematically represented by a dynamic model shown in FIG. M shown in FIG. 3 is the mass of the floating body 31, m is the mass of the tower structure 40, _k0 is the spring constant of the virtual elastic body 60, and _k1 is the spring constant of the first elastic body 50. . m _S is the inertial mass and c _S is the damping coefficient. The displacement of the floating body 31 is represented by X, and the displacement of the tower structure 40 is represented by x.

More specifically, the mass M of the floating body 31 is the mass of the floating body 31 plus the mass of the generator support frame 35, the mass of the stator of the device generator 80, and the incidental mass due to waves. be. The mass m of the tower structure 40 is the mass of the tower structure 40 plus the mass of the wind power generator main body 4. The damping coefficient c _S is determined by the specifications of the device generator 80 .

なお、慣性モーメントＩ_１、Ｉ_２は、ピニオン歯車７３または発電機回転子８１にフライホイールを取り付けて調整することができる。このように、変換回転子７１および発電機回転子８１は、浮体３１と塔構造体４０との間の相対変位による振動を低減する慣性質量要素として機能している。 _The inertial mass m _S can be calculated using the following formula ( ₁ ).

Note that the moments of inertia I ₁ and I ₂ can be adjusted by attaching a flywheel to the pinion gear 73 or the generator rotor 81. In this way, the conversion rotor 71 and the generator rotor 81 function as inertial mass elements that reduce vibrations due to relative displacement between the floating body 31 and the tower structure 40.

を作用させる。慣性質量ｍ_Ｓは、浮体３１と塔構造体４０との相対運動によって慣性力

を浮体３１および塔構造体４０に作用させる。図３においては、慣性質量ｍ_Ｓによる慣性力の作用を、２つの“／”で“○”を挟んだ記号で表しており、一般の質量と区別した記号を用いている。 The mass M is caused by the inertial force due to the movement of the floating body 31.

to act. The inertial mass m _S is caused by the inertial force due to the relative movement between the floating body 31 and the tower structure 40

is applied to the floating body 31 and the tower structure 40. In FIG. 3, the action of the inertial force due to the inertial mass _mS is represented by a symbol with an "o" sandwiched between two "/", and the symbol is used to distinguish it from a general mass.

ここで、Ｆは波の加振力である。一般的な構造物では、左辺の質量行列は、対角行列となる。本実施の形態においては、非対角項に、“－ｍ_Ｓ”が入っている。 The equation of motion of the dynamic model shown in FIG. 3 is an equation of motion of a two-degree-of-freedom system, as shown in equation (2) below.

Here, F is the wave excitation force. In a typical structure, the mass matrix on the left side is a diagonal matrix. In this embodiment, "-m _S " is included in the off-diagonal term.

で表される。図４および図５に示すνは加振角振動数比であり、

で表される。このうちωは加振角振動数である。ωｎは角固有振動数であり、

で表される。ξは質量比であり、

で表される。ζは減衰比であり、

で表される。なお、式（２）において、質量Ｍが十分に大きく、かつばね定数ｋ_０が十分に小さいため、浮体３１の固有振動数が、加振振動数である波の振動数よりも十分に低くなる。このため、簡易的に式（２）を１自由度系として取り扱い、図４および図５に示す振動伝達率関数Ｔ（ν）を得た。 When the vibration transmissibility function of the displacement x of the tower structure 40 with respect to the displacement X of the floating body 31 is determined from equation (2), FIGS. 4 and 5 are obtained. Here, the vibration transmissibility function T(ν) is

It is expressed as ν shown in FIGS. 4 and 5 is the excitation angular frequency ratio,

It is expressed as Among these, ω is the excitation angular frequency. ωn is the angular natural frequency,

It is expressed as ξ is the mass ratio,

It is expressed as ζ is the damping ratio,

It is expressed as In addition, in equation (2), since the mass M is sufficiently large and the spring constant _k0 is sufficiently small, the natural frequency of the floating body 31 is sufficiently lower than the frequency of the wave which is the excitation frequency. . For this reason, equation (2) was simply treated as a one-degree-of-freedom system, and the vibration transfer rate function T(ν) shown in FIGS. 4 and 5 was obtained.

のときに、Ｔ＝１に達する。更に振動数比νが増加すると、振動伝達率Ｔは更に減少するが、減少は緩やかで、広い範囲でＴ＝１よりも低い状態が維持される。 FIG. 4 shows the vibration transmissibility T when the damping ratio ζ is 0.01 and the mass ratio ξ is changed. The broken line shows the vibration transmissibility T when ξ=0, in which case the inertial mass m _S =0. That is, the broken line indicates the vibration transmissibility T when the device generator 80 and the conversion mechanism 70 are not present. When ν=0, T=1, and as the frequency ratio ν increases, the vibration transmissibility T also increases, and when ν=1, the vibration transmissibility T becomes maximum. That is, when ν=1, the excitation angular frequency ω and the angular natural frequency ω _n are equal, and a resonance point appears at this time. As the frequency ratio ν increases from the resonance point, the vibration transmissibility T decreases,

T=1 is reached when . As the frequency ratio ν further increases, the vibration transmissibility T further decreases, but the decrease is gradual and remains lower than T=1 over a wide range.

On the other hand, as shown in FIG. 3, when an inertial mass m _S is added between masses M and m, the frequency ratio ν at the resonance point becomes smaller and the frequency ratio ν is larger than the resonance point. The vibration transmissibility T tends to decrease.

程度に低下する。そして、振動数比νが、

において、実質的にＴ＝０となる。ここから振動数比νが増加すると、振動伝達率Ｔは緩やかに増加するが、増加は緩やかで、広い範囲でＴ＝１よりも低い状態が維持される。 For example, when ξ=0.5, the frequency ratio ν at the resonance point is

decreases to a certain degree. And the frequency ratio ν is

, substantially T=0. As the frequency ratio ν increases from here, the vibration transmissibility T gradually increases, but the increase is gradual and remains lower than T=1 over a wide range.

となる。そして、ν＝１で、実質的にＴ＝０となる。ここから振動数比νが増加すると、振動伝達率Ｔは増加するが、振動伝達率Ｔの増加は緩やかで、広い範囲でＴ＝１よりも低い状態が維持される。 Moreover, when ξ=1.0, the frequency ratio ν at the resonance point is

becomes. Then, when ν=1, T=0 essentially. As the frequency ratio ν increases from here, the vibration transmissibility T increases, but the increase in the vibration transmissibility T is gradual and remains lower than T=1 over a wide range.

By adding the inertial mass m _S in this way, it is possible to expand the range in which the vibration transmissibility T is lower than 1. In this case, the range of frequency ratios ν in which the displacement of the tower structure 40 can be reduced can be expanded, and the displacement of the tower structure 40 can be reduced in a wider range of frequency ratios ν.

で表される。例えば、遮断振動数は、

で表されるが、この遮断振動数を、加振振動数である波の振動数ｆｗに一致させるまたは近づける場合には、振動伝達率Ｔは小さくなり、０（ゼロ）または０に近い値になる。このことにより、塔構造体４０の振動を抑制し、塔構造体４０を実質的に静止させることができる。 Here, the frequency ratio at which T=0 is called the cut-off frequency ratio ν _S ,

It is expressed as For example, the cutoff frequency is

However, when this cutoff frequency is made to match or approach the wave frequency fw, which is the excitation frequency, the vibration transmissibility T becomes smaller and becomes 0 (zero) or a value close to 0. Become. Thereby, vibration of the tower structure 40 can be suppressed and the tower structure 40 can be made substantially stationary.

FIG. 5 shows the vibration transmissibility T when the damping ratio ζ is changed with the mass ratio ξ=1.0. The current generated in the generator rotor 81 is proportional to the rotation speed of the generator rotor 81. That is, as the amount of power generated by the device generator 80 increases, the damping coefficient c _S increases, and the damping ratio ζ also increases. As shown in FIG. 5, when the damping ratio ζ is increased from 0.01 to 0.1, the maximum amplitude at the resonance point becomes smaller. On the other hand, in the cut-off frequency ratio ν _S , there is a tendency for the vibration transmissibility T to increase as the damping ratio ζ increases, but the amount of increase is small. That is, even if the damping ratio ζ increases tenfold by increasing the amount of power generation, the vibration transmissibility T is sufficiently smaller than 1. Therefore, it can be seen that both vibration suppression of the tower structure 40 and conversion into electrical energy can be achieved.

The electric power obtained by the power generation in the device generator 80 as described above may be used for the auxiliary machine 6 that controls the direction of the wind power generator main body 4 and the like. In this case, even if the external power source is lost, the power source for the auxiliary equipment 6 in an emergency can be maintained, and a situation in which the wind power generator main body 4 becomes uncontrollable can be avoided.

As described above, according to the present embodiment, the relative displacement between the floating body 31 and the tower structure 40 is converted into the rotational displacement of the conversion rotor 71, and the rotational displacement of the conversion rotor 71 causes the device generator 80 to be activated. Generate electricity. The conversion rotor 71 functions as an inertial mass element that reduces vibrations due to relative displacement between the floating body 31 and the tower structure 40. Thereby, relative displacements between the floating body 31 and the tower structure 40 are transmitted via the inertial mass element, which is acted upon by the conversion rotor 71 and the generator rotor 81. Therefore, vibrations imparted to the floating body 31 by receiving waves can be suppressed from being transmitted to the tower structure 40. Further, the device generator 80 can generate electricity by rotational displacement of the conversion rotor 71. As a result, vibration of the tower structure 40 can be suppressed, and vibration energy can be converted into electrical energy. That is, it is possible to both suppress vibrations of the tower structure 40 and convert it into electrical energy.

Further, according to this embodiment, the device generator 80 includes a generator rotor 81, and the generator rotor 81 functions as an inertial mass element together with the conversion rotor 71. By this, the inertial mass can be increased, and the vibration of the floating body 31 can be further suppressed from being transmitted to the tower structure 40. Therefore, vibration of the tower structure 40 can be further suppressed.

Further, according to this embodiment, the floating body 31 includes the first cavity portion 33 that accommodates the lower portion 40a of the tower structure 40. This allows the floating body 31 to be placed outside the lower portion 40a of the tower structure 40. Therefore, the strength of the vibration damping power generation device 20 against the shear load (load acting in the horizontal direction) on the tower structure 40 can be improved.

Further, according to the present embodiment, the floating body 31 and the tower structure 40 are capable of relative displacement in the axial direction d along the central axis L1, and the conversion mechanism 70 is provided in the tower structure 40. It includes a rack rail 72 extending in the axial direction d, and a pinion gear 73 that meshes with the teeth of the rack rail 72. The pinion gear 73 and the device generator 80 are supported by a generator support pedestal 35 provided on the floating body 31. Thereby, the relative displacement in the axial direction d between the floating body 31 and the tower structure 40 can be converted into rotational displacement, and the device generator 80 can generate electricity. Therefore, vibration of the tower structure 40 can be suppressed and vibration energy can be converted into electrical energy.

In addition, in this embodiment mentioned above, the example in which the apparatus generator 80 contains the generator rotor 81 and was comprised as a rotating electric machine was demonstrated. However, the present invention is not limited to this, and the device generator 80 may be a linear generator. In this case, the rotational displacement of the pinion gear 73 may be converted into a translational displacement, and the device generator 80 may generate power using this translational displacement.

Furthermore, in the present embodiment described above, an example has been described in which the generator rotor 81 of the device generator 80 has a rotation axis along the horizontal direction. However, the invention is not limited to this, and if power can be generated by the rotational displacement of the pinion gear 73, the rotational axis of the generator rotor 81 may be set in a direction other than the horizontal direction (for example, in the axial direction d of the floating body 31, etc.). ).

(Second embodiment)
Next, a vibration damping power generation device according to a second embodiment will be described using FIG. 6.

The second embodiment shown in FIG. 6 differs mainly in that the tower structure is floating on liquid stored in the cavity of the floating body, and the other configuration is similar to the second embodiment shown in FIGS. This embodiment is substantially the same as the first embodiment. Note that in FIG. 6, the same parts as those in the first embodiment shown in FIGS. 1 to 5 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 6, in this embodiment, a liquid 37 is stored in the first cavity 33 of the floating body 31, and the lower part of the tower structure 40 may be immersed in this liquid 37. In this case, the tower structure 40 can receive buoyancy from the liquid 37 and is elastically supported by the floating body 31. Therefore, the tower structure 40 according to the present embodiment can be considered to be elastically supported by the floating body 31 by the virtual elastic body 65 having a spring constant _k1 , similar to the virtual elastic body 60 shown in FIG. I can do it. The spring constant k ₁ of this virtual elastic body 65 can be set to be approximately the same as the spring constant k ₀ of the virtual elastic body 60 of the floating body 31 . Therefore, the spring constant _k1 of the virtual elastic body 65 can be made small.

Here, the range of frequency ratios in which the vibration transmissibility T shown in FIGS. 4 and 5 can be most suppressed is near the cut-off frequency ratio _νS . As mentioned above, the frequency fw of the wave is 0.05Hz to 0.5Hz, which is relatively low. If an attempt is made to bring the above-mentioned cutoff frequency closer to the frequency fw of this wave, the angular natural frequency ω _n will become lower. In this case, depending on the mass of the tower structure 40, it is required to reduce the spring constant _k1 .

In contrast, in the example shown in FIG. 6, the tower structure 40 is elastically supported by the floating body 31 by the buoyancy of the liquid 37, as described above. Therefore, the spring constant _k1 of the virtual elastic body 65 due to the buoyancy of the liquid 37 can be reduced.

In addition, in FIG. 6, the tower structure 40 is elastically supported by the floating body 31 by a virtual elastic body 65 having a spring constant _k1 . The virtual elastic body 65 does not indicate the presence of a spring member, but rather the tower structure 40 is moved in the axial direction d due to the buoyant force that the tower structure 40 receives from the liquid 37 stored in the first cavity 33. It is used to schematically show movement. However, in order to adjust the spring constant k ₁ , the tower structure 40 is operated not only by the liquid 37 stored in the first cavity 33 but also by a spring member or the like elastically connecting the tower structure 40 to the floating body 31 . An elastic body may additionally be used.

As described above, according to the present embodiment, the tower structure 40 is floating on the liquid 37 stored in the first cavity 33 of the floating body 31. This allows the spring constant k ₁ of the virtual elastic body 65 that elastically supports the tower structure 40 on the floating body 31 to be small. Therefore, even if the mass of the tower structure 40 is small, the angular natural frequency ω _n can be made low, and the cut-off frequency can be easily brought close to the wave frequency.

(Third embodiment)
Next, a vibration damping power generation device according to a third embodiment will be described using FIG. 7.

The third embodiment shown in FIG. 7 is mainly different from the first embodiment shown in FIGS. 1 to 5 in that it includes a plurality of conversion mechanisms and a plurality of device generators. The form is almost the same as that of . In FIG. 7, the same parts as those in the first embodiment shown in FIGS. 1 to 5 are denoted by the same reference numerals, and detailed explanations will be omitted.

As shown in FIG. 7, the vibration damping power generation device 20 in this embodiment includes a plurality of conversion mechanisms 70 and a plurality of device generators 80. The damped power generation device 20 shown in FIG. 7 includes two conversion mechanisms 70 and two device generators 80. Each of the device generators 80 is provided corresponding to each of the conversion mechanisms 70, and generates power by rotational displacement of the corresponding conversion mechanism 70.

As shown in FIG. 7, one conversion mechanism 70 is located on one side (for example, the left side in FIG. 7) of the tower structure 40 when viewed horizontally (or when viewed from above). One device generator 80 corresponding to the conversion mechanism 70 is located. Then, on the other side (for example, the right side in FIG. 7) with respect to the tower structure 40, another conversion mechanism 70 and another device generator 80 corresponding to the conversion mechanism 70 are located. There is. For example, when viewed from above, the conversion mechanism 70 and the device generator 80 may be located at positions that are point symmetrical about the central axis L1 of the floating body 31, respectively.

The force couples generated in the generator rotors 81 of both device generators 80 have the same magnitude and opposite directions of action. This makes it possible to suppress rolling (rotational vibration centered on the rotational axis of the generator rotor 81) occurring in the floating body 31. That is, the rotational directions of the rotational forces generated by the couple generated in each generator rotor 81 are opposite to each other. Therefore, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited.

As described above, according to the present embodiment, the conversion mechanism 70 and the device generator 80 corresponding to the conversion mechanism 70 are located on both sides of the tower structure 40, respectively. The rotational forces generated by the couple generated in the generator rotor 81 of each device generator 80 can cancel each other out. This can suppress rolling in the support structure 30. Therefore, occurrence of rolling in the floating body 31 can be suppressed, and control of the wind power generator main body 4 can be suppressed from being adversely affected.

Further, according to the present embodiment, since two conversion mechanisms 70 and two device generators 80 are installed, vibration of the tower structure 40 can be further suppressed, and the amount of power generation can be increased. can be increased.

In addition, in this embodiment mentioned above, the example in which the vibration damping power generation device 20 was provided with two conversion mechanisms 70 and two device generators 80 was explained. In this example, when one conversion mechanism 70 and one device generator 80 are combined as one set, the vibration damping power generation device 20 includes two sets of the conversion mechanism 70 and the device generator 80. There is. However, the number of combinations of the conversion mechanism 70 and the device generator 80 is not limited to this, and the number of combinations is arbitrary as long as the rotational force generated by the couple generated in each generator rotor 81 can be canceled out. It may be an even number.

(Fourth embodiment)
Next, a vibration damping power generation device according to a fourth embodiment will be described using FIG. 8.

The fourth embodiment shown in FIG. 8 is mainly different from the third embodiment shown in FIG. 7 in that the conversion mechanism includes a transmission section that can change the rotation speed of the pinion gear. is almost the same as Note that in FIG. 8, the same parts as those in the third embodiment shown in FIG. 7 are given the same reference numerals, and detailed explanations will be omitted.

As shown in FIG. 8, in this embodiment, the conversion mechanism 70 includes a transmission section 74 that can change the rotation speed of the pinion gear 73. In this embodiment as well, an example will be described in which two device generators 80 are supported by the generator support pedestal 35 in the same manner as in the third embodiment described above. A conversion mechanism 70 is provided corresponding to each device generator 80, but the two conversion mechanisms 70 are configured in the same way.

The transmission section 74 includes a plurality of transmission gears 75 capable of converting a relative displacement of the tower structure 40 in the axial direction d into a rotational displacement and transmitting the rotational displacement to the pinion gear 73. The number of teeth of the plurality of speed change gears 75 is different from each other. One of the plurality of speed change gears 75 is selected and meshes with the teeth of the rack rail 72 and the teeth of the pinion gear 73, respectively. The speed change gear 75 converts the relative displacement of the tower structure 40 in the axial direction d into a rotational displacement and transmits the rotational displacement to the pinion gear 73 . Such a speed change gear 75 constitutes the conversion rotor 71 together with the pinion gear 73. As a result, the moment of inertia _I1 of the conversion rotor 71 becomes the sum of the moment of inertia of the pinion gear 73 and the moment of inertia of the speed change gear 75.

The number of teeth of each speed change gear 75 is different from the number of teeth of the pinion gear 73. As a result, the rotational speed of each transmission gear 75 and the rotational speed of the pinion gear 73 are different. In this embodiment, the number of teeth of each speed change gear 75 is greater than the number of teeth of pinion gear 73, and each speed change gear 75 speeds up the rotation of pinion gear 73.

The transmission section 74 includes a switching section (not shown) that switches the transmission gear 75. This switching portion is configured to switch the speed change gear 75 that meshes with the teeth of the rack rail 72 and the teeth of the pinion gear 73, respectively. The plurality of speed change gears 75 may be arranged in parallel in a direction along the rotational axis of the generator rotor 81 (a direction perpendicular to the paper surface of FIG. 8). The transmission section 74 may include a cover 76 that covers the transmission gear 75.

Here, as shown in FIG. 8, an example will be described in which one of the plurality of speed change gears 75 is selected. The pitch circle radius r1 of this speed change gear 75 is larger than the pitch circle radius r of the pinion gear 73. The pitch circle radius r of the pinion gear 73 shown in FIG. 8 is smaller than the pitch circle radius r of the pinion gear 73 shown in FIG.

で表される。Ｉ_１は、２つの変換回転子７１の慣性モーメントの合計値であり、Ｉ_２は、２つの発電機回転子８１の慣性モーメントの合計値である。εは１よりも大きくなるため、変速歯車７５が設けられていない場合の式（１）と比較すると、慣性質量ｍ_Ｓは、増速率の二乗倍になり、大幅に増大する。 If the speed increase rate, which is the ratio of the number of teeth of the speed change gear 75 to the number of teeth of the pinion gear 73, is ε, then the inertial mass m _S of each device generator 80 is:

It is expressed as I ₁ is the sum of the moments of inertia of the two conversion rotors 71 , and I ₂ is the sum of the moments of inertia of the two generator rotors 81 . Since ε becomes larger than 1, the inertial mass m _S becomes the square of the speed increase rate and increases significantly compared to equation (1) when the speed change gear 75 is not provided.

Similarly, the number of teeth of the other transmission gears 75 is larger than the number of teeth of the pinion gear 73, and the number of teeth of each transmission gear 75 is different from each other. Thereby, by switching the speed change gear 75 using the switching section, the speed increase rate of the speed change section 74 can be changed.

で表されるため、慣性質量ｍ_Ｓを調整することにより、遮断振動数比ν_Ｓを調整することができる。このため、遮断振動数比ν_Ｓを所望の値に調整することができる。例えば、上述の遮断振動数を波の振動数ｆｗに一致させるまたは近づけるように、遮断振動数比ν_Ｓを調整することができる。この場合、振動伝達率Ｔを低減させることができる。 In this way, by adjusting the speed increase rate of the transmission section 74, the inertial mass _mS can be adjusted. That is, the cutoff frequency ratio ν _S is

Therefore, by adjusting the inertial mass m _S , the cutoff frequency ratio ν _S can be adjusted. Therefore, the cutoff frequency ratio ν _S can be adjusted to a desired value. For example, the cut-off frequency ratio ν _S can be adjusted so that the above-mentioned cut-off frequency matches or approaches the wave frequency fw. In this case, the vibration transmissibility T can be reduced.

Note that an acceleration sensor (not shown) may be provided on the floating body 31 to measure the frequency fw of the waves, and the speed increase rate of the speed change section 74 may be adjusted based on the measured value of the frequency fw. For example, a speed change gear 75 whose cut-off frequency can be brought close to the measured value of the wave frequency fw may be selected, and the switching unit may switch to the speed change gear 75.

As described above, according to the present embodiment, the conversion mechanism 70 includes the transmission section 74 that can change the speed of the rotation of the pinion gear 73. As a result, the speed increase rate of the transmission section 74 can be adjusted, and the cut-off frequency ratio ν _S can be adjusted to match or be close to the wave frequency f _w . Therefore, the vibration transmissibility T can be effectively reduced according to the wave frequency _fw , and the vibrations of the tower structure 40 can be effectively suppressed.

In addition, in this embodiment mentioned above, the example where the transmission part 74 speeds up the rotation of the pinion gear 73 was demonstrated. However, the invention is not limited to this, and the transmission section 74 may reduce the rotation of the pinion gear 73. In this case, the number of teeth of each speed change gear 75 may be smaller than the number of teeth of the pinion gear 73. Further, the transmission section 74 may be configured to be able to both speed up and slow down the rotation of the pinion gear 73. In this case, the number of teeth of some of the speed change gears 75 may be larger than the number of teeth of the pinion gear 73, and the number of teeth of the other speed change gears 75 may be smaller than the number of teeth of the pinion gear 73.

Further, in the present embodiment described above, the two device generators 80 are supported by the generator support pedestal 35, and the conversion mechanism 70 including the speed change section 74 is provided corresponding to each device generator 80. An example was explained. In this case, as described above, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited. However, the invention is not limited to this, and the number of device generators 80 supported by the generator support frame 35 is arbitrary. For example, as shown in FIG. 1, the number of device generators 80 is one. It may be. In this case, there is only one conversion mechanism 70 including the transmission section 74.

(Fifth embodiment)
Next, a vibration damping power generation device according to a fifth embodiment will be described using FIGS. 9 to 11.

In the fifth embodiment shown in FIGS. 9 to 11, the support structure includes a floating body and a connecting structure that is elastically supported by the floating body and elastically supports the tower structure. The main difference is that the other configurations are substantially the same as the fourth embodiment shown in FIG. Note that in FIGS. 9 to 11, the same parts as those in the fourth embodiment shown in FIG. 8 are denoted by the same reference numerals, and detailed explanations will be omitted.

As shown in FIG. 9, in this embodiment, the support structure 30 includes a floating body 31 floating on the ocean and a connecting structure 100. The floating body 31 is an example of a first support structure, and the connection structure 100 is an example of a second support structure. The connecting structure 100 is elastically supported by the floating body 31 from below, and also elastically supports the tower structure 40 from below. In this way, the tower structure 40 is elastically supported by the floating body 31 via the connection structure 100.

The connecting structure 100 extends in the axial direction d and is formed in a cylindrical shape. The connecting structure 100 includes a second cavity 101. The second cavity 101 is defined by a cylindrical inner peripheral surface extending in the axial direction d. The upper portion 31a (an example of a portion) of the floating body 31 can pass through the second cavity portion 101. The diameter of the second cavity 101 is larger than the outer diameter of the floating body 31.

A guide rail (not shown) extending in the axial direction d may be provided on the inner peripheral surface of the connecting structure 100. In this case, relative displacement of the connecting structure 100 with respect to the floating body 31 can be guided in the axial direction d. Furthermore, a plurality of rollers 102 may be provided on the inner peripheral surface of the connected structure 100. The roller 102 can roll against the outer peripheral surface of the floating body 31. Thereby, relative displacement of the connecting structure 100 with respect to the floating body 31 can be performed smoothly. The connecting structure 100 may be positioned concentrically with the floating body 31 and the tower structure 40.

The first elastic body 110 according to this embodiment elastically connects the connecting structure 100 to the floating body 31. More specifically, the first elastic body 110 connects the support pedestal 38 provided on the floating body 31 and the support pedestal 103 provided at the lower end of the connection structure 100. The first elastic body 110 may be constituted by a spring member such as a coil spring, for example. The floating body 31 and the connecting structure 100 may be connected by a plurality of first elastic bodies 110. In this case, the first elastic bodies 110 may be arranged evenly in the circumferential direction around the central axis L1 of the floating body 31 when viewed from above. FIG. 9 shows an example in which the floating body 31 and the connecting structure 100 are connected by two first elastic bodies 110. The composite value of the spring constants of the two first elastic bodies 110 is defined as _k1 . Note that the support frame 38 extends in the horizontal direction and is located above the water surface. Further, the support frame 103 also extends in the horizontal direction.

The connecting structure 100 and the tower structure 40 are elastically connected by a second elastic body 120. More specifically, the second elastic body 120 connects the generator support pedestal 104 provided at the upper end of the connection structure 100 and the support pedestal 41 provided in the tower structure 40. The second elastic body 120 may be constituted by a spring member such as a coil spring, for example. The spring constant of the second elastic body 120 is k2. Note that the connecting structure 100 and the tower structure 40 may be connected by a plurality of second elastic bodies 120. In this case, the second elastic bodies 120 may be arranged evenly in the circumferential direction around the central axis L1 of the floating body 31 when viewed from above. Note that the generator support pedestal 104 and the support pedestal 41 extend in the horizontal direction.

In this way, the floating body 31 and the connecting structure 100 can be translated in the axial direction d, and the connecting structure 100 and the tower structure 40 can be translated in the axial direction d.

In this embodiment, two device generators 80 similar to those in the fourth embodiment described above are fixedly supported on a generator support pedestal 104. Two conversion mechanisms 70 are provided corresponding to each device generator 80. The conversion mechanism 70 and the device generator 80 may be positioned symmetrically about the central axis L1 of the floating body 31 when viewed from above. In FIG. 9, for convenience, the conversion mechanism 70 and the device generator 80 are shown on the right side of the tower structure 40, and the second elastic body 120 is shown on the left side.

Conversion mechanism 70 according to this embodiment converts the relative displacement between coupling structure 100 and tower structure 40 into rotational displacement of conversion rotor 71. The rack rail 72 is provided on the outer peripheral surface of the tower structure 40. The transmission section 74 and the pinion gear 73 are supported by a generator support pedestal 104 provided on the connection structure 100. The device generator 80 is also supported by a generator support pedestal 104 . Conversion rotor 71 and generator rotor 81 according to this embodiment function as inertial mass elements that reduce vibrations due to relative displacement between coupling structure 100 and tower structure 40.

The vibration damping power generation device 20 according to the present embodiment configured as described above is schematically illustrated as a dynamic model shown in FIG. M shown in FIG. 10 is the mass of the floating body 31, m' is the mass of the connecting structure 100, and m is the mass of the tower structure 40. k ₀ is the spring constant of the virtual elastic body 60 , k ₁ is the spring constant of the first elastic body 110 , and k 2 is the spring constant of the second elastic body 120 . m _S is the inertial mass and c _S is the damping coefficient. The displacement of the floating body 31 is represented by X, the displacement of the connected structure 100 is represented by y, and the displacement of the tower structure 40 is represented by x. Note that the dynamic model shown in FIG. 10 differs from the dynamic model shown in FIG. The difference is that it is performed by the relative displacement of.

More specifically, the mass M of the support structure 30 is the mass of the floating body 31, the mass of the support pedestal 38, and the incidental mass due to waves. The mass m' of the connected structure 100 is the mass of the connected structure 100 plus the mass of the stators of the two device generators 80. The mass m of the tower structure 40 is the mass of the tower structure 40 plus the mass of the wind power generator main body 4. The damping coefficient c _S is determined by the specifications of the device generator 80 . The inertial mass m _S is determined by the above-mentioned formula (3).

The equation of motion of the dynamic model shown in FIG. 10 is an equation of motion of a three-degree-of-freedom system, as shown in equation (4) below.

で表される。振動伝達率Ｔ’（ν）は、

で表される。図１１では、Ｔ（ν）を実線で示し、Ｔ’（ν）を破線で示している。図１１では、質量比ξを０．１とし、減衰比ζを０．０１としている。 From equation (4), the vibration transmissibility function T(ν) of the displacement x of the tower structure 40 with respect to the displacement X of the floating body 31, and the vibration transmissibility function T' of the displacement y of the connecting structure 100 with respect to the displacement When (v) is determined, FIG. 11 is obtained. Here, the vibration transmissibility function T(ν) is

It is expressed as The vibration transmissibility T'(ν) is

It is expressed as In FIG. 11, T(v) is shown by a solid line, and T'(v) is shown by a broken line. In FIG. 11, the mass ratio ξ is 0.1 and the damping ratio ζ is 0.01.

As shown in FIG. 11, due to the existence of the connected structure 100, the natural frequencies exist at two frequency ratios ν. One natural frequency exists in the vicinity of ν=0.1 as a natural frequency related to the vibration transmissibility T(ν). The other natural frequency exists in the vicinity of ν=1.0 as a natural frequency related to the vibration transmissibility T'(ν). In the vicinity of ν=1.0, the vibration transmissibility T(ν) is small. It can be seen from this that the vibration of the tower structure 40 is attenuated, and almost no amplitude occurs in the tower structure 40. On the other hand, it can be seen that in the vicinity of ν=1.0, the vibration transmissibility T'(ν) becomes large, and the amplitude of the connected structure 100 becomes large. That is, in the vicinity of ν=1.0, the displacement x of the tower structure 40 is suppressed, whereas the displacement y of the connected structure 100 becomes large. Therefore, the relative displacement between the connecting structure 100 and the tower structure 40 is large.

である場合、またはこの近傍である場合、装置発電機８０の発電には有利である。遮断振動数を波の振動数ｆｗに一致させるまたは近づけるように高次固有振動数

を設定してもよい。この場合、装置発電機８０の発電量を増加させることができるとともに、塔構造体４０の振動を抑制できる。 Since such vibration characteristics are exhibited, when the frequency ratio ν is the cut-off frequency ratio ν _S described above, that is,

If this is the case, or if it is near this, it is advantageous for the device generator 80 to generate electricity. Higher natural frequencies to make the cut-off frequency match or approach the wave frequency fw

may be set. In this case, the amount of power generated by the device generator 80 can be increased, and vibrations of the tower structure 40 can be suppressed.

As described above, according to the present embodiment, the connecting structure 100 is elastically supported by the floating body 31 from below, and the tower structure 40 is elastically supported by the connecting structure 100 from below. Then, the relative displacement between the connecting structure 100 and the tower structure 40 is converted into a rotational displacement of the conversion rotor 71, and the device generator 80 generates power by the rotational displacement of the conversion rotor 71. The conversion rotor 71 functions as an inertial mass element that reduces vibrations due to relative displacement between the coupling structure 100 and the tower structure 40. Thereby, relative displacements between the coupling structure 100 and the tower structure 40 are transmitted via the inertial mass element, which is acted upon by the conversion rotor 71 and the generator rotor 81. Therefore, vibrations imparted to the floating body 31 by receiving waves can be suppressed from being transmitted to the tower structure 40. Further, the device generator 80 can generate electricity by rotational displacement of the conversion rotor 71. As a result, vibration of the tower structure 40 can be suppressed, and vibration energy can be converted into electrical energy. That is, it is possible to both suppress vibrations of the tower structure 40 and convert it into electrical energy.

Further, according to this embodiment, the connecting structure 100 of the support structure 30 includes the second cavity 101 through which the upper portion 31a of the floating body 31 can pass. This allows the connecting structure 100 to be placed outside the upper portion 31a of the floating body 31. Therefore, the strength of the vibration damping power generation device 20 against the shear load (load acting in the horizontal direction) on the tower structure 40 can be improved.

Further, according to the present embodiment, the connecting structure 100 and the tower structure 40 can be relatively displaced in the axial direction d along the central axis L1, and the rack rail 72 of the conversion mechanism 70 is connected to the tower structure. 40 , and the pinion gear 73 and device generator 80 are supported by a generator support pedestal 104 provided in the connection structure 100 . Thereby, the relative displacement in the axial direction d between the connecting structure 100 and the tower structure 40 can be converted into a rotational displacement, and the device generator 80 can generate electricity. Therefore, vibration of the tower structure 40 can be suppressed and vibration energy can be converted into electrical energy.

Note that in the present embodiment described above, two device generators 80 are supported by the generator support pedestal 35, and a conversion mechanism 70 including a transmission section 74 is provided corresponding to each device generator 80. An example was explained. In this case, as described above, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited. However, the invention is not limited to this, and the number of device generators 80 supported by the generator support frame 35 is arbitrary. For example, as shown in FIG. 1, the number of device generators 80 is one. It may be. In this case, there is only one conversion mechanism 70 including the transmission section 74. Furthermore, the conversion mechanism 70 may or may not include the transmission section 74.

(Sixth embodiment)
Next, a vibration damping power generation device according to a sixth embodiment will be described using FIG. 12.

In a sixth embodiment shown in FIG. 12, the connecting structure includes a cavity through which the lower part of the tower structure can pass, and in the direction of relative displacement between the floating body and the connecting structure, the connecting structure The main difference is that the structure is located at a different position from the floating body, and the other configurations are substantially the same as the fifth embodiment shown in FIGS. 9 to 11. Note that in FIG. 12, the same parts as in the fifth embodiment shown in FIGS. 9 to 11 are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 12, in this embodiment, the connecting structure 100 includes a second cavity 101 through which the tower structure 40 can pass. The diameter of the second cavity 101 is larger than the diameter of the tower structure 40. Further, the diameter of the second cavity 101 may be equal to the diameter of the first cavity 33 of the floating body 31. A rack rail 72 can be inserted into the second cavity 101.

In the direction of relative displacement between the floating body 31 and the connecting structure 100, the connecting structure 100 is located at a different position from the floating body 31. In this embodiment, the floating body 31 and the connecting structure 100 are capable of translation in the axial direction d. Due to this, the connecting structure 100 is located at a different position from the floating body 31 in the axial direction d. In FIG. 12, the lower end of the connecting structure 100 is located above the upper end of the floating body 31. The upper end of the floating body 31 and the lower end of the connecting structure 100 are spaced apart from each other in the vertical direction. The support frame 38 to which the first elastic body 110 is connected is provided at the upper end of the floating body 31.

A guide rail (not shown) extending in the axial direction d may be provided on the inner peripheral surface of the connecting structure 100. In this case, the relative displacement of the tower structure 40 with respect to the connection structure 100 can be guided in the axial direction d. Further, a plurality of rollers 102 may be provided on the inner peripheral surface of the connected structure 100. The roller 102 can roll against the outer peripheral surface of the tower structure 40. Thereby, relative displacement of the tower structure 40 with respect to the connection structure 100 can be performed smoothly. The connecting structure 100 may be positioned concentrically with the floating body 31 and the tower structure 40.

As described above, according to the present embodiment, the connecting structure 100 includes the second cavity 101 through which the tower structure 40 can pass, and in the direction of relative displacement between the floating body 31 and the connecting structure 100, The connecting structure 100 is located at a different position from the floating body 31. This makes it possible to avoid placing the connecting structure 100 outside the floating body 31. In this case, the structure of the vibration damping power generation device 20 can be simplified, and ease of assembly can be improved.

Note that in the present embodiment described above, two device generators 80 are supported by the generator support pedestal 35, and a conversion mechanism 70 including a transmission section 74 is provided corresponding to each device generator 80. An example was explained. In this case, as described above, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited. However, the invention is not limited to this, and the number of device generators 80 supported by the generator support frame 35 is arbitrary. For example, as shown in FIG. 1, the number of device generators 80 is one. It may be. In this case, there is only one conversion mechanism 70 including the transmission section 74. Further, the conversion mechanism 70 does not need to include the transmission section 74.

(Seventh embodiment)
Next, a vibration damping power generation device according to a seventh embodiment will be described using FIG. 13.

The seventh embodiment shown in FIG. 13 differs mainly in that the rack rail of the conversion mechanism is provided on the connection structure, and the pinion gear and the device generator are supported on the tower structure. The configuration is substantially the same as that of the sixth embodiment shown in FIG. Note that in FIG. 13, the same parts as those in the sixth embodiment shown in FIG. 12 are given the same reference numerals, and detailed explanations will be omitted.

As shown in FIG. 13, in this embodiment, the rack rail 72 of the conversion mechanism 70 is provided on the connection structure 100. More specifically, an extension 105 extends upward from the upper end of the connection structure 100. A rack rail 72 is provided on this extension portion 105. A plurality of extensions 105 may extend from the upper end of the coupling structure 100 in correspondence with the conversion mechanism 70 and the device generator 80. In FIG. 13, for convenience, an extension 105 corresponding to the conversion mechanism 70 and device generator 80 shown on the right side of the tower structure 40 is shown.

In this embodiment, the first elastic body 110 connects the support pedestal 38 provided at the upper end of the floating body 31 and the support pedestal 103 provided at the lower end of the connection structure 100. The second elastic body 120 connects the support pedestal 106 provided on the connection structure 100 and the generator support pedestal 42 provided on the tower structure 40. Note that the support pedestal 106 and the generator support pedestal 42 extend in the horizontal direction. Further, the generator support frame 42 includes a through hole 43 through which the extension portion 105 and the rack rail 72 pass.

In this embodiment, two device generators 80 similar to those in the sixth embodiment described above are supported by a generator support frame 42.

The conversion mechanism 70 according to this embodiment converts the relative displacement between the connecting structure 100 of the support structure 30 and the tower structure 40 into a rotational displacement of the conversion rotor 71. The rack rail 72 is provided on the connecting structure 100 and the extension portion 105. That is, the rack rail 72 extends from the connecting structure 100 to the extension portion 105. The transmission section 74 and the pinion gear 73 are supported by a generator support frame 42 provided in the tower structure 40. The device generator 80 is also supported by the generator support pedestal 42 . Conversion rotor 71 and generator rotor 81 according to this embodiment function as inertial mass elements that reduce vibrations due to relative displacement between coupling structure 100 and tower structure 40.

As described above, according to the present embodiment, the rack rail 72 of the conversion mechanism 70 is provided on the connecting structure 100 and the extension part 105, and the pinion gear 73 and the device generator 80 are provided on the generator support of the tower structure 40. It is supported by a pedestal 42. This allows the device generator 80 to be supported by the tower structure 40 with suppressed vibrations. Therefore, the reliability of the device generator 80 can be improved.

Note that in the present embodiment described above, two device generators 80 are supported by the generator support pedestal 42, and a conversion mechanism 70 including a transmission section 74 is provided corresponding to each device generator 80. An example was explained. In this case, as described above, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited. However, the invention is not limited to this, and the number of device generators 80 supported by the generator support frame 42 is arbitrary. For example, as shown in FIG. 1, the number of device generators 80 is one. It may be. In this case, there is only one conversion mechanism 70 including the transmission section 74. Further, the conversion mechanism 70 does not need to include the transmission section 74.

(Eighth embodiment)
Next, a vibration damping power generation device according to an eighth embodiment will be described using FIG. 14.

The eighth embodiment shown in FIG. 14 is mainly different from the first embodiment shown in FIGS. 1 to 5 in that the support structure and the displacement structure are movable relative to each other. The form is almost the same as that of . Note that in FIG. 14, the same parts as those in the first embodiment shown in FIGS. 1 to 5 are designated by the same reference numerals, and detailed description thereof will be omitted.

In this embodiment, an example of a vibration damping power generation device 20 applied to a ship 200 will be described.

As shown in FIG. 14, the vibration damping power generation device 20 according to the present embodiment includes a hull structure 210, a cabin structure 220, a first elastic body 230, a conversion mechanism 70, and a device generator 80. We are prepared. The hull structure 210 is an example of a support structure, and the cabin structure 220 is an example of a displacement structure. The hull structure 210 and the cabin structure 220 are capable of relative rotational displacement about the rotation center axis L2. The rotational center axis L2 has a rotational center axis L2 that extends horizontally from the bow of the hull 211 toward the stern (in a direction perpendicular to the paper surface of FIG. 14). In FIG. 14, the rotation center axis L2 extends perpendicularly to the plane of the paper, and is therefore represented by a dot.

The hull structure 210 includes a hull 211 floating on the ocean. A portion of the hull 211 is located below the water surface and is submerged. A weight section 213 filled with a heavy object such as concrete or ballast water is provided at the lower part of the hull 211. This lowers the center of gravity of the hull 211 and increases the stability of the hull 211 floating on the ocean. The buoyancy of the hull 211 and the gravity of the entire ship 200 are balanced, and the stability of the ship 200 as a whole is improved.

The hull 211 includes a hull cavity 214 that accommodates a lower portion (an example of a portion) of the cabin structure 220. The hull cavity 214 may be provided with a guide rail (not shown) that guides relative rotational displacement of the hull structure 210 about the rotation center axis L2. Further, a plurality of rollers 215 may be provided in the hull cavity 214. The roller 215 can roll on the outer circumferential surface 223 of the rotation support base 222 of the hull structure 210. This allows the cabin structure 220 to be smoothly rotated relative to the hull 211. The hull 211, like the floating body 31 shown in FIG. 1 and the like, is elastically supported in a stationary system by a virtual elastic body 60 having a spring constant _k0 . Here, in the above-described first to seventh embodiments, an example in which the floating body 31 and the tower structure 40 are relatively translated in the axial direction d has been described, but in this embodiment, the ship body 211 and the cabin structure 220 undergo relative rotational displacement. For this reason, FIG. 14 shows an example in which the hull 211 is supported in a stationary system by two virtual elastic bodies 60. These two virtual elastic bodies 60 allow the hull 211 and the cabin structure 220 to rotate relative to each other. The composite value of the spring constants of the two virtual elastic bodies 60 is defined as _k0 . The generator support pedestal 212 is fixed to the hull 211 and supports the device generator 80.

A generator support pedestal 212 is provided inside the hull 211 . Generator support pedestal 212 supports device generator 80 .

The cabin structure 220 is an example of a displacement structure. The cabin structure 220 is elastically supported by the hull 211. The cabin structure 220 is configured to be rotatable relative to the hull 211. The cabin structure 220 is rotatable relative to the hull 211 about the rotation center axis L2 described above.

The cabin structure 220 includes a cabin body 221 and a rotation support base 222 provided at the bottom of the cabin body 221. The rotation support base 222 includes an outer circumferential surface 223 and an inner circumferential surface 224, each of which is formed in an arc shape about the rotation center axis L2. The outer circumferential surface 223 and the inner circumferential surface 224 are each an example of a circular arc surface. The above-mentioned roller 215 rolls on this outer peripheral surface 223.

The first elastic body 230 according to this embodiment elastically connects the cabin structure 220 to the hull 211. The first elastic body 230 may be constituted by a spring member such as a coil spring, for example. In FIG. 14, the first elastic bodies 230 are arranged on both left and right sides of the rotation support base 222 when viewed along the rotation center axis L2. That is, one first elastic body 230 connects one end of the rotation support base 222 to the wall surface of the hull 211 facing the end when viewed along the rotation center axis L2. . The other support spring connects the other end of the rotation support base 222 to the wall surface of the hull 211 facing the end. FIG. 9 shows an example in which the hull 211 and the cabin structure 220 are connected by two first elastic bodies 230. The composite value of the spring constants of the two first elastic bodies 230 is defined as _k1 .

In this way, the hull 211 and the cabin structure 220 can be rotated relative to each other.

Conversion mechanism 70 in this embodiment converts the relative rotational displacement between hull 211 and cabin structure 220 into rotational displacement of conversion rotor 71. More specifically, the conversion mechanism 70 in this embodiment includes a rack rail 72 and a pinion gear 73 that constitutes the conversion rotor 71. The rack rail 72 is an example of a rack, and is provided on the inner peripheral surface 224 of the rotation support base 222. In this case, the teeth of the rack rails 72 are directed inward. The rack rail 72 is formed to extend in an arc shape along the inner circumferential surface 224, and extends in the circumferential direction about the rotation center axis L2.

The pinion gear 73 is supported by the generator support frame 212 of the hull 211, and constitutes the conversion rotor 71 described above. The pinion gear 73 meshes with the teeth of the rack rail 72 and converts rotational displacement of the hull structure 210 into rotational displacement of the conversion rotor 71.

In this embodiment, the conversion mechanism 70 may include a transmission section 74. The transmission section 74 can be configured similarly to the fourth embodiment described above.

The device generator 80 is fixedly supported by a generator support frame 212 of the hull 211. Note that FIG. 14 shows an example in which one device generator 80 is installed on the generator support pedestal 212. However, a plurality of device generators 80 may be installed on the generator support pedestal 212.

The conversion rotor 71 and the generator rotor 81 according to the present embodiment function as inertial mass elements that reduce vibrations caused by rolling (also referred to as rolling) caused by relative rotational displacement between the hull 211 and the cabin structure 220. are doing. In other words, the vibration damping power generation device 20 according to the present embodiment can suppress vibrations caused by rolling of the ship 200 and generate power.

As described above, according to the present embodiment, the relative rotational displacement between the hull 211 and the cabin structure 220 is converted into the rotational displacement of the conversion rotor 71, and the rotational displacement of the conversion rotor 71 is used to generate the device generator. 80 generates electricity. The conversion rotor 71 functions as an inertial mass element that reduces vibrations caused by relative rotational displacement between the hull 211 and the cabin structure 220. Thereby, the relative rotational displacement between the hull 211 and the cabin structure 220 is transmitted via the inertial mass element, which is operated by the conversion rotor 71 and the generator rotor 81. Therefore, vibrations imparted to the hull 211 by receiving transverse waves can be suppressed from being transmitted to the cabin structure 220. Further, the device generator 80 can generate electricity by rotational displacement of the conversion rotor 71. As a result, vibrations of the cabin structure 220 can be suppressed and vibration energy can be converted into electrical energy. That is, it is possible to simultaneously suppress vibrations of the cabin structure 220 and convert it into electrical energy.

In addition, in this embodiment mentioned above, the example where the rack rail 72 was provided in the inner peripheral surface 224 of the rotation support stand 222 was demonstrated. However, the present invention is not limited to this, and the rack rail 72 may be provided on the outer circumferential surface 223 of the rotation support base 222, and the teeth of the rack rail 72 may be directed outward. In this case, the conversion mechanism 70 and the device generator 80 are arranged at positions corresponding to the rack rails 72 provided on the outer peripheral surface 223.

Moreover, in the present embodiment described above, an example has been described in which the vibration damping power generation device 20 is applied to the ship 200 as an example of a moving object. However, the invention is not limited to this, and may be applied to moving objects other than the ship 200. For example, the vibration damping power generation device 20 described above may be applied to a railway vehicle as another example of a moving body. In this case, the chassis of the railway vehicle may be used as the support structure, and the body of the railway vehicle may be used as the displacement structure. This makes it possible to suppress vibrations caused by rolling (or rolling) acting on the railway vehicle and to generate electricity. Furthermore, the above-described vibration-damping power generation device 20 may be applied to an automobile as another example of a moving object. In this case, the chassis of the motor vehicle may serve as the support structure, and the body of the motor vehicle may serve as the displacement structure. This makes it possible to suppress vibrations caused by rolling (or rolling) that acts on the vehicle, and to generate electricity.

(Ninth embodiment)
Next, a vibration damping power generation device according to a ninth embodiment will be described using FIGS. 15 and 16.

In the ninth embodiment shown in FIGS. 15 and 16, the first structure includes a first floating body floating on the ocean, and the second structure includes a second floating body floating on the ocean at a different position from the first floating body. The main difference is that a floating body is included, and the other configurations are substantially the same as the first embodiment shown in FIGS. 1 to 5. Note that in FIGS. 15 and 16, the same parts as those in the first embodiment shown in FIGS. 1 to 5 are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 15, in this embodiment, the vibration damping power generation device 320 includes a first structure 330, a second structure 340, a conversion mechanism 70, and a device generator 80. . The offshore wind power generation facility 10 shown in FIG. 15 includes a vibration damping power generation device 320 and the wind power generator main body 4 described above.

The first structure 330 includes a main floating body 331 , a first generator support pedestal 332 , and a tower structure 333 . The first structure 330 is generally formed to extend along the central axis L3.

The main floating body 331 is configured to float on the ocean. The main floating body 331 is an example of a first floating body. The main floating body 331 is formed to extend along the central axis L3. The main floating body 331 is formed into a cylindrical shape centered on the central axis L3. When the main floating body 331 is not rolling, the central axis L3 is along the vertical direction. A portion of the main floating body 331 is located below the water surface and immersed in the surrounding seawater. The main floating body 331 is configured to withstand water pressure.

A weight section 32 (see FIG. 1, etc.) filled with a heavy object such as concrete or ballast water is provided at the lower part of the main floating body 331. This lowers the center of gravity of the main floating body 331 and increases the stability of the main floating body 331 floating on the ocean.

The main floating body 331 is elastically supported with respect to the stationary system by a virtual elastic body 361 having a spring constant k1, similar to the virtual elastic body 5 of the floating body 2 shown in FIG. Further, the natural frequency of the main floating body 331 may be designed to be sufficiently detuned from the frequency of waves.

The first generator support pedestal 332 is provided at the upper end of the main floating body 331. The first generator support pedestal 332 extends in the horizontal direction (direction perpendicular to the axial direction d along the central axis L3) and is located above the power generation floating body 341, which will be described later. The first generator support pedestal 332 is fixed to the main floating body 331. The first generator support pedestal 332 may be formed into a disk shape centered on the central axis L3. The first generator support pedestal 332 includes a through hole 332a. The through hole 332a extends in the axial direction d and penetrates the first generator support frame 332. The through hole 332a includes a cylindrical wall surface centered on the central axis L4 of the second structure 340.

The tower structure 333 is located above the main floating body 331 and extends upward from the first generator support pedestal 332. The tower structure 333 is formed into a columnar shape so as to extend vertically. The above-mentioned wind power generator main body 4 is provided at the upper end of the tower structure 333.

The second structure 340 includes a power generation floating body 341 and a second rod 342. The second structure 340 is generally formed to extend along the central axis L4. The central axis L4 is along the axial direction d, and may be parallel to the central axis L3 described above.

The power generation floating body 341 is configured to float on the ocean at a different position from the main floating body 331 described above. The power generation floating body 341 is an example of a second floating body. The power generation floating body 341 is formed to extend along the central axis L4. The power generation floating body 341 is formed into a cylindrical shape centered on the central axis L4. When the floating body 341 for power generation is not horizontally swaying, the central axis L4 is along the vertical direction. A part of the power generation floating body 341 is located below the water surface and immersed in the surrounding seawater. The power generation floating body 341 is configured to withstand water pressure.

A weight part (not shown) filled with a heavy material such as concrete or ballast water may be provided at the lower part of the power generation floating body 341. This lowers the center of gravity of the power generation floating body 341 and increases the stability of the power generation floating body 341 floating on the ocean. The buoyancy of the power generation floating body 341, the buoyancy of the main floating body 331 mentioned above, and the gravity of the entire offshore wind power generation facility 10 are balanced, and the stability of the offshore wind power generation facility 10 as a whole is improved.

Similar to the virtual elastic body 5 of the floating body 2 shown in FIG. 2, the power generation floating body 341 is elastically supported with respect to the stationary system by a virtual elastic body 362 having a spring constant k2.

The second rod 342 extends upward from the power generation floating body 341 along the central axis L4. The second rod 342 passes through the through hole 332a of the first generator support pedestal 332 and extends in the axial direction d so as to exceed the first generator support pedestal 332. The second rod 342 is formed into a cylindrical shape centered on the central axis L4. The power generation floating body 341 and the second rod 342 may be positioned concentrically with the through hole 332a.

A plurality of rollers 343 may be provided on the outer peripheral surface of the second rod 342. The roller 343 can roll against the wall surface of the through hole 332a described above. This allows the first structure 330 and the second structure 340 to be smoothly displaced relative to each other. A guide rail (not shown) extending in the axial direction d may be provided on the wall surface of the through hole 332a. In this case, the relative displacement of the second structure 340 with respect to the first structure 330 can be guided in the axial direction d.

The second structure 340 is elastically connected to the first structure 330. The second structure 340 is configured to be movable relative to the first structure 330. In this embodiment, the first structure 330 and the second structure 340 are capable of translational displacement in the axial direction d.

The first elastic body 350 according to this embodiment elastically connects the second structure 340 to the first structure 330. More specifically, the first elastic body 350 is connected to the first generator support pedestal 332 and the floating body 341 for power generation. Although FIG. 15 shows an example in which two first elastic bodies 350 are connected to the first generator support pedestal 332 and the power generation floating body 341, the number of first elastic bodies 350 is arbitrary. . The first elastic body 350 has a spring constant _k12 . The first elastic body 350 may be configured by a spring member such as a coil spring, for example.

The conversion mechanism 70 includes a conversion rotor 71 and is a mechanism that converts the relative displacement between the first structure 330 and the second structure 340 into a rotational displacement of the conversion rotor 71. The conversion mechanism 70 includes a rack rail 72 and a pinion gear 73.

The rack rail 72 is provided on the outer peripheral surface of the second rod 342. The rack rail 72 extends in the axial direction d. This suppresses the second structure 340 from rotating relative to the first structure 330. The rack rail 72 can be inserted into the through hole 332a of the first generator support frame 332.

The pinion gear 73 is rotatably supported by the first generator support frame 332. The pinion gear constitutes the conversion rotor 71 described above. The pinion gear 73 meshes with the teeth of the rack rail 72, and converts a relative translational displacement in the axial direction d between the first structure 330 and the second structure 340 into a rotational displacement. In this embodiment, pinion gear 73 is coaxially connected to generator rotor 81.

The device generator 80 is supported by the first generator support pedestal 332 . In this embodiment, generator rotor 81 has a rotation axis along the horizontal direction. Further, in FIG. 15, one device generator 80 is installed on the first generator support pedestal 332. The rotational displacement converted from the relative displacement between the first structure 330 and the second structure 340 by one conversion mechanism 70 is transmitted to the generator rotor 81 of the device generator 80.

The dynamic model of the damped power generation device 320 according to the present embodiment configured as described above can be expressed by a two-degree-of-freedom system of motion equations shown in Equation (5) below.

Here, m ₁ is the mass of the main floating body 331, which is the mass of the first generator support pedestal 332, the mass of the stator of the device generator 80, the mass of the wind power generator main body 4, and the accompanying mass due to waves. The mass includes the mass and the mass. m ₂ is the mass of the power generation floating body 341, which includes the mass of the second rod 342 and the accompanying mass due to waves. m _s is the inertial mass. x ₁ is the displacement of the first structure 330 and x ₂ is the displacement of the second structure 340. c ₁ is the attenuation coefficient of the main floating body 331 against waves, and c ₂ is the attenuation coefficient of the power generation floating body 341 against waves. _c12 is a damping coefficient for relative displacement between the main floating body 331 and the power generation floating body 341. k ₁ is the spring constant of the first virtual elastic body 361 , and k ₂ is the spring constant of the second virtual elastic body 362 . k ₁₂ is a spring constant of the first elastic body 350. f ₁ is the wave excitation force on the main floating body 331, and f ₂ is the wave excitation force on the power generation floating body 341. In a typical structure, the mass matrix on the left side is a diagonal matrix. In this embodiment, since the generator rotor 81 of the device generator 80 functions as an inertial mass element, "-m _S " is included in the off-diagonal term.

Here, the offshore wind power generation facility 10 as shown in FIG. 15 has the advantage of being able to generate electricity using stable offshore wind. Furthermore, when the water depth suddenly increases from land to offshore, it is difficult to install wind power generation equipment with a foundation on the seabed. In this case, the floating offshore wind power generation facility 10 can be an effective facility. Each piece of equipment in the offshore wind power generation facility 10 can be damaged by the vibrations applied by the waves. To prevent such damage, the offshore wind power generation facility 10 is designed to be detuned from the natural period of the waves. It is desirable to sufficiently suppress vibrations even when a typhoon approaches or when waves are high.

Further, the wind power generator 4c (see FIG. 2) can generate electricity by rotating the blades 4d by the wind. On the other hand, the offshore wind power generation facility 10 includes an auxiliary machine 6 (see FIG. 26) that controls the wind power generator main body 4. The auxiliary machine 6 uses external power to control the direction of the wind power generator main body 4, the pitch (deflection angle) of the blades 4d, and the floating body according to wind conditions such as wind direction and wind speed. The system for supplying this external power to the offshore wind power generation facility 1 may be cut off in the event of a disaster such as a typhoon. If it is blocked, for example, the floating body may become uncontrollable, and in some cases, the floating body may collapse.

In contrast, in the present embodiment, the first structure 330 includes a main floating body 331 floating on the ocean, and the second structure 340 includes a power generation floating body 341 floating on the ocean. This allows the first structure 330 and the second structure 340 to be relatively displaced in the axial direction d. Then, this relative displacement is converted into a rotational displacement, and the device generator 80 can generate electricity. In this way, the vibrational energy of the waves can be converted into electrical energy to obtain electric power. The power generated by the device generator 80 can also be used to control the offshore wind power generation facility 1, as shown in FIG. 25, etc., which will be described later. Therefore, it is possible to maintain the power supply in an emergency, and it is possible to avoid a situation where the wind power generator main body 4 becomes uncontrollable.

As described above, according to the present embodiment, the first structure 330 includes the main floating body 331 floating on the ocean, and the second structure 340 includes the power generation floating body 341 floating on the ocean at a different position from the main floating body 331. Contains. This allows the first structure 330 and the second structure 340 to be relatively displaced by the force received from the waves. Therefore, the relative displacement between the first structure 330 and the second structure 340 is converted into a rotational displacement of the conversion rotor 71, and the device generator 80 generates power using the rotational displacement of the conversion rotor 71. I can do it. The conversion rotor 71 functions as an inertial mass element that reduces vibrations due to relative displacement between the first structure 330 and the second structure 340. This makes it possible to reduce vibrations imparted to the first structure 330 by receiving waves. Further, the device generator 80 can generate electricity by rotational displacement of the conversion rotor 71. As a result, vibration of the first structure 330 can be suppressed, and vibration energy can be converted into electrical energy. That is, it is possible to simultaneously suppress vibrations of the first structure 330 and convert it into electrical energy.

Further, according to this embodiment, the device generator 80 includes a generator rotor 81, and the generator rotor 81 functions as an inertial mass element together with the conversion rotor 71. With this, the inertial mass can be increased, and the vibration of the first structure 330 can be further reduced. Therefore, vibration of the first structure 330 can be further suppressed.

Further, according to the present embodiment, the first structure 330 and the second structure 340 can be relatively displaced in the axial direction d along the central axis L3, and the conversion mechanism 70 The rack rail 72 includes a rack rail 72 provided in the rack rail 72 and extending in the axial direction d, and a pinion gear 73 that meshes with the teeth of the rack rail 72. The pinion gear 73 and the device generator 80 are supported by a first generator support frame 332 of the first structure 330. Thereby, the relative displacement in the axial direction d between the first structure body 330 and the second structure body 340 can be converted into rotational displacement, and the device generator 80 can generate electricity. Therefore, vibration of the first structure 330 can be suppressed and vibration energy can be converted into electrical energy.

Further, according to the present embodiment, the first structure 330 includes the first generator support pedestal 332 located above the power generation floating body 341, and the second structure 340 includes the first generator support pedestal 332 located above the power generation floating body 341. 1 includes a second rod 342 extending beyond the generator support pedestal 332 . A rack rail 72 is provided on this second rod 342. Thereby, the translational relative displacement in the axial direction d between the first structure 330 and the second structure 340 can be easily converted into rotational displacement.

In addition, in this embodiment mentioned above, the conversion mechanism 70 demonstrated the example containing the rack rail 72 provided in the outer peripheral surface of the 2nd rod 342 of the 2nd structure 340. However, it is not limited to this. For example, as shown in FIG. 16, the conversion mechanism 70 may include a gear groove 77 provided on the outer peripheral surface of the second rod 342. The gear groove 77 may be formed all around the outer peripheral surface of the second rod 342. A plurality of gear grooves 77 are formed at different positions in the axial direction d. In this case as well, the pinion gear 73 can mesh with the gear groove 77 and convert the translational relative displacement in the axial direction d between the first structure 330 and the second structure 340 into rotational displacement. can. Note that, in order to simplify the drawing, FIG. 16 shows the wall surface of the through hole 332a in a planar shape.

(Tenth embodiment)
Next, a vibration damping power generation device according to a tenth embodiment will be described using FIGS. 17 and 18.

The tenth embodiment shown in FIGS. 17 and 18 mainly differs in that it includes a plurality of second structures, a plurality of conversion mechanisms, and a plurality of device generators, and other configurations include: This embodiment is substantially the same as the ninth embodiment shown in FIGS. 15 and 16. Note that in FIGS. 17 and 18, the same parts as those in the ninth embodiment shown in FIGS. 15 and 16 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 17, the vibration damping power generation device 320 in this embodiment includes a plurality of second structures 340, a plurality of conversion mechanisms 70, and a plurality of device generators 80. The vibration damping power generation device 320 shown in FIG. 17 includes two second structures 340. Each of the conversion mechanisms 70 is provided corresponding to each of the second structures 340, and converts the relative displacement of the corresponding second structure 340 in the axial direction d into rotational displacement. Each of the device generators 80 is provided corresponding to each of the conversion mechanisms 70, and generates power by rotational displacement of the corresponding conversion mechanism 70. Each second structure 340 is not integrated. Therefore, each of the second structures 340 is configured to vibrate independently of each other and to be displaced relative to the first structure 330 independently of each other.

As shown in FIG. 17, when viewed in the horizontal direction (or when viewed from above), one second structure is located on one side (for example, the left side in FIG. 17) with respect to the first structure 330. The conversion mechanism 70 and the device generator 80 corresponding to the body 340 and the second structure 340 are located. Then, on the other side of the first structure 330 (for example, on the right side in FIG. 17), another second structure 340 and the conversion mechanism 70 and device generator 80 corresponding to the second structure 340 are installed. positioned. For example, when viewed from above, the second structure 340 may be located at a point symmetrical position with respect to the central axis L3 of the first structure 330.

Device generators 80 are provided corresponding to both second structures 340, and the force couples generated in the generator rotors 81 of each device generator 80 have the same magnitude and opposite directions of action. As a result, rolling (rotational vibration centered on the rotational axis of the generator rotor 81) occurring in the second structure 340 can be suppressed. That is, the rotational directions of the rotational forces generated by the couple generated in each generator rotor 81 are opposite to each other. Therefore, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited.

Furthermore, in this embodiment, two conversion mechanisms 70 and two device generators 80 are provided for one second structure 340. Each of the device generators 80 is provided corresponding to each of the conversion mechanisms 70, and generates power by rotational displacement of the corresponding conversion mechanism 70.

The second structure 340 shown on the left side in FIG. 17 will be explained.

As shown in FIG. 17, when viewed in the horizontal direction (or when viewed from above), on one side (for example, the left side in FIG. 17) with respect to the second rod 342 of the second structure 340, One conversion mechanism 70 and one device generator 80 corresponding to the conversion mechanism 70 are located. Then, on the other side (for example, the right side in FIG. 17) with respect to the second rod 342, another conversion mechanism 70 and another device generator 80 corresponding to the conversion mechanism 70 are located. There is. For example, when viewed from above, the conversion mechanism 70 and the device generator 80 may be located at positions that are point symmetrical about the central axis L1 of the second rod 342, respectively.

The force couples generated in the generator rotors 81 of both device generators 80 have the same magnitude and opposite directions of action. Thereby, rolling occurring in the second structure 340 can be suppressed. That is, the rotational directions of the rotational forces generated by the couple generated in each generator rotor 81 are opposite to each other. Therefore, the rotational force generated by the couple generated in each generator rotor 81 can be canceled out, and rolling can be suppressed from being excited.

The second structure 340 shown on the right side in FIG. 17 can be configured in a similar manner, and rolling can be suppressed from occurring in the second structure 340.

As described above, according to the present embodiment, the second structures 340 are provided on both sides of the first structure 330, and the conversion mechanism 70 and the device generator 80 correspond to each second structure 340. is located. The rotational forces generated by the couple generated in the generator rotor 81 of each device generator 80 can cancel each other out. This makes it possible to prevent rolling from being excited in the second structure 340. Therefore, occurrence of rolling in the second structure 340 can be suppressed, and control of the wind power generator main body 4 can be suppressed from being adversely affected.

Further, according to the present embodiment, since the conversion mechanism 70 and the device generator 80 are mounted in correspondence with the two second structures 340, the number of conversion mechanisms 70 and the number of device generators 80 can be reduced. can be increased. Therefore, vibration of the first structure 330 can be further suppressed, and the amount of power generation can be increased.

Further, according to the present embodiment, the conversion mechanism 70 and the device generator 80 corresponding to the conversion mechanism 70 are located on both sides of the second structure 340, respectively. The rotational forces generated by the couple generated in the generator rotor 81 of each device generator 80 can cancel each other out. This makes it possible to prevent rolling from being excited in the second structure 340. Therefore, occurrence of rolling in the second structure 340 can be suppressed, and control of the wind power generator main body 4 can be suppressed from being adversely affected.

Further, according to the present embodiment, since two conversion mechanisms 70 and two device generators 80 are mounted on one second structure 340, the vibration of the first structure 330 is reduced. This can be further suppressed and the amount of power generation can be increased.

In addition, in this embodiment mentioned above, the example where the 2nd structure 340 is not integrated was demonstrated. However, it is not limited to this. For example, as shown in FIG. 18, the plurality of second structures 340 may be connected to each other. In this case, each of the second structures 340 vibrates integrally and is integrally displaced relative to the first structure 330. Therefore, the vibration that the second structure 340 receives from the waves can be increased, and the relative displacement between the first structure 330 and the second structure 340 can be increased. For example, as shown in FIG. 18, each of the second structures 340 may be directly connected by a connecting body 334 formed in a ring shape so as to surround the first structure 330. In addition, in FIG. 18, in order to make the drawing clear, illustration of the first generator support pedestal 332 is omitted, and the conversion mechanism 70 and the device generator 80 are simplified.

Further, in the present embodiment described above, an example in which the vibration damping power generation device 320 includes two second structures 340 has been described. However, the number of second structures 340 is not limited to this, and may be any even number as long as the rotational force generated by the couple generated in each generator rotor 81 can be canceled out. .

Furthermore, in the present embodiment described above, an example has been described in which the vibration damping power generation device 320 includes four conversion mechanisms 70 and four device generators 80. In this example, when one conversion mechanism 70 and one device generator 80 are combined as one set, the vibration damping power generation device 320 is configured to provide two sets for one second structure 340. A conversion mechanism 70 and a device generator 80 are provided. However, the invention is not limited to this, and the number of combinations of the conversion mechanism 70 and the device generator 80 for one second structure 340 is limited to the rotation caused by the couple generated in each generator rotor 81. Any even number may be used as long as the forces can be canceled out.

(Eleventh embodiment)
Next, a vibration damping power generation device according to an eleventh embodiment will be described using FIG. 19.

The eleventh embodiment shown in FIG. 19 differs mainly in that the conversion mechanism includes a transmission section that can change the speed of the rotation of the pinion gear. This embodiment is substantially the same as the embodiment No. 9. Note that in FIG. 19, the same parts as those in the ninth embodiment shown in FIGS. 15 and 16 are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 19, in this embodiment, the conversion mechanism 70 includes a transmission section 74 that can change the speed of the rotation of the pinion gear 73.

The transmission section 74 includes a plurality of transmission gears 75 that can convert the relative displacement of the first structure 330 in the axial direction d into a rotational displacement and transmit the rotational displacement to the pinion gear 73. The number of teeth of the plurality of speed change gears 75 is different from each other. One of the plurality of speed change gears 75 is selected and meshes with the teeth of the rack rail 72 and the teeth of the pinion gear 73, respectively. The speed change gear 75 converts the relative displacement of the first structure 330 in the axial direction d into a rotational displacement and transmits the rotational displacement to the pinion gear 73 . Such a speed change gear 75 constitutes the conversion rotor 71 together with the pinion gear 73. As a result, the moment of inertia _I1 of the conversion rotor 71 becomes the sum of the moment of inertia of the pinion gear 73 and the moment of inertia of the speed change gear 75.

The number of teeth of each speed change gear 75 is different from the number of teeth of the pinion gear 73. As a result, the rotational speed of each transmission gear 75 and the rotational speed of the pinion gear 73 are different. In this embodiment, the number of teeth of each speed change gear 75 is greater than the number of teeth of pinion gear 73, and each speed change gear 75 speeds up the rotation of pinion gear 73.

The transmission section 74 includes a switching section (not shown) that switches the transmission gear 75. This switching portion is configured to switch the speed change gear 75 that meshes with the teeth of the rack rail 72 and the teeth of the pinion gear 73, respectively. The plurality of speed change gears 75 may be arranged in parallel in a direction along the rotational axis of the generator rotor 81 (a direction perpendicular to the paper surface of FIG. 19). The transmission section 74 may include a cover 76 that covers the transmission gear 75.

As described above, according to the present embodiment, the conversion mechanism 70 includes the transmission section 74 that can change the speed of the rotation of the pinion gear 73. Thereby, the speed increase rate of the speed change section 74 can be adjusted. Therefore, the speed increase rate of the transmission section 74 can be adjusted according to the frequency of the waves, and the vibration of the first structure 330 can be effectively suppressed.

In addition, in the transmission section 74 according to the present embodiment described above, for example, as shown in FIG. The present invention can also be applied to a configuration including a machine 80.

(Twelfth embodiment)
Next, a vibration damping power generation device according to a twelfth embodiment will be described using FIG. 20.

The twelfth embodiment shown in FIG. 20 differs mainly in that the second floating body extends higher than the first floating body, and the pinion gear and device generator are supported by the first floating body. The configuration is substantially the same as that of the ninth embodiment shown in FIGS. 15 and 16. Note that in FIG. 20, the same parts as in the ninth embodiment shown in FIGS. 15 and 16 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 20, in this embodiment, the first structure 330 does not include the first generator support pedestal 332 as shown in FIG. 15 and the like. Tower structure 333 extends upward from main floating body 331 .

The second structure 340 does not include the second rod 342 as shown in FIG. 15 and the like. The power generation floating body 341 extends upward from the main floating body 331 along the axial direction d.

A rack rail 72 may be provided at a position above the main floating body 331 in the power generation floating body 341. The lower part of the rack rail 72 may be located below the upper surface 331a of the main floating body 331.

In this embodiment, pinion gear 73 and device generator 80 are supported by main floating body 331. The pinion gear 73 and the device generator 80 are installed on the upper surface 331a of the main floating body 331.

The power generation floating body 341 is provided with a guide rail 345 extending in the axial direction d. The guide rail 345 is located below the rack rail 72 described above. The main floating body 331 is provided with a guide portion 335a that is slidable on the guide rail. Thereby, the relative displacement of the second structure 340 with respect to the first structure 330 can be guided in the axial direction d.

The first elastic body 350 according to the present embodiment includes a first elastic body 350a provided above the guide section 335 and a first elastic body 350b provided below the guide section 335. The first elastic body 350a is attached to the power generation floating body 341 via the attachment part 335b. The first elastic body 350b is attached to the power generation floating body 341 via the attachment portion 335c. The first structure 330 and the second structure 340 are elastically connected by the first elastic body 350a and the first elastic body 350b.

As described above, according to the present embodiment, the power generation floating body 341 extends above the main floating body 331 in the axial direction d, and the pinion gear 73 and the device generator 80 are supported by the main floating body 331. This makes it possible to eliminate the need for the first generator support pedestal 332 shown in FIG. I can do it. Therefore, even if the displacement of the second structure 340 with respect to the first structure 330 becomes large, interference or collision between the first structure 330 and the second structure 340 can be prevented. .

Note that in the present embodiment described above, for example, as shown in FIG. 17, the vibration damping power generation device 320 includes a plurality of second structures 340, a plurality of conversion mechanisms 70, a plurality of device generators 80, It can also be applied to a form provided with.

(13th embodiment)
Next, a vibration damping power generation device according to a thirteenth embodiment will be described using FIG. 21.

The thirteenth embodiment shown in FIG. 21 differs mainly in that the rack rail of the conversion mechanism is provided on the first structure, and the pinion gear and the device generator are supported on the second structure. , and other configurations are substantially the same as the ninth embodiment shown in FIGS. 15 and 16. Note that in FIG. 21, the same parts as in the ninth embodiment shown in FIGS. 15 and 16 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 21, in this embodiment, the first structure 330 includes a main floating body 331, a first rod 336, and a connecting body 337 that connects the first rod 336 to the main floating body 331. I'm here. Tower structure 333 extends upward from main floating body 331 .

The first rod 336 is formed to extend along the central axis L4 of the second structure 340. That is, the first rod 336 is elongated in the axial direction d and has a cylindrical shape. The lower portion 336a of the first rod 336 is accommodated in a second cavity 344 of the power generation floating body 341, which will be described later, and extends upward from the second cavity 344 beyond the second generator support frame 346. . The first rod 336 may be positioned coaxially with the power generation floating body 341.

The power generation floating body 341 according to the present embodiment is elongated along the central axis L4 and is formed in a cylindrical shape. The power generation floating body 341 includes a second cavity 344 that accommodates the lower portion 336a of the first rod 336 of the first structure 330. The second cavity 344 extends in the axial direction d. The diameter of the second cavity 344 is larger than the outer diameter of the first rod 336.

A guide rail (not shown) extending in the axial direction d may be provided on the inner peripheral surface of the power generation floating body 341. In this case, the relative displacement of the first rod 336 with respect to the power generation floating body 341 can be guided in the axial direction d. Further, a plurality of rollers 343 may be provided on the inner peripheral surface of the floating body 341 for power generation. The roller 343 can roll against the outer peripheral surface of the first rod 336. This allows the first rod 336 to be smoothly displaced relative to the power generation floating body 341.

A second generator support pedestal 346 is provided at the upper end of the power generation floating body 341. The second generator support pedestal 346 extends horizontally and is located above the water surface. The second generator support pedestal 346 is fixed to the power generation floating body 341. The second generator support pedestal 346 includes a through hole 347 through which the first rod 336 passes.

In this embodiment, the rack rail 72 of the conversion mechanism 70 is provided on the first rod 336. The pinion gear 73 and the device generator 80 are supported by a second generator support pedestal 346. The first elastic body 350 connects the first rod 336 of the first structure 330 and the power generation floating body 341 of the second structure 340.

As described above, according to the present embodiment, the rack rail 72 of the conversion mechanism 70 is provided on the first rod 336, and the pinion gear 73 and the device generator 80 are supported on the second generator support frame 346. . Thereby, the translational relative displacement in the axial direction d between the first structure 330 and the second structure 340 can be easily converted into rotational displacement.

Note that in the present embodiment described above, for example, as shown in FIG. 17, the vibration damping power generation device 320 includes a plurality of second structures 340, a plurality of conversion mechanisms 70, a plurality of device generators 80, It can also be applied to a form provided with.

(Fourteenth embodiment)
Next, a vibration damping power generation device according to a fourteenth embodiment will be described using FIG. 22.

In the fourteenth embodiment shown in FIG. 22, the conversion rotor includes a screw bearing provided on the generator rotating shaft, and the second floating body is provided with a second holder that holds the screw bearing. The main difference is that the other configurations are substantially the same as the ninth embodiment shown in FIGS. 15 and 16. Note that in FIG. 22, the same parts as in the ninth embodiment shown in FIGS. 15 and 16 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 22, in this embodiment, the device generator 80 includes a generator rotation shaft 82 that extends in the axial direction d so as to exceed the first generator support frame 332. may be formed to extend along the central axis L4 of the second holder 348, which will be described later. The generator rotating shaft 82 passes through the rotor 83, and a stator 84 is provided around the rotor 83. The generator rotation shaft 82 and the rotor 83 constitute the above-mentioned generator rotor 81 and function as an inertial mass element. The generator rotating shaft 82 is rotatably supported by a bearing 86 provided in the generator casing 85. The generator casing 85 is fixed to the first generator support frame 332.

The first generator support pedestal 332 includes a through hole 332a through which the generator rotating shaft 82 passes. The generator rotation shaft 82 extends beyond the first generator support frame 332 and into a second holder 348 of the second structure 340, which will be described later. A ball bearing 338 is provided in the through hole 332a, and the generator rotating shaft 82 is rotatably supported by the first generator support frame 332.

In this embodiment, the power generation floating body 341 is formed in a ring shape so as to surround the main floating body 331. A second holder 348 is provided on the power generation floating body 341. The second holder 348 is positioned below the device generator 80. The second holder 348 may be formed in a cylindrical shape along the central axis L4.

Conversion rotor 71 includes a screw bearing 78 provided at the lower end of generator rotating shaft 82 . The moment of inertia _I1 of the conversion rotor 71 becomes the moment of inertia of the screw bearing 78. The screw bearing 78 may be a screw ball bearing. For example, a screw-shaped groove may be provided in the lower portion of the generator rotating shaft 82, and a screw-shaped groove may be provided in the inner peripheral surface of the second holder 348. A plurality of balls are inserted into the groove of the generator rotating shaft 82 and the groove of the second holder 348. The screw bearing 78 can be configured in this way.

In this embodiment, the first elastic body 350 connects the generator rotating shaft 82 and the second holder 348. As a result, the first structure 330 and the second structure 340 are elastically connected via the device generator 80.

As described above, according to the present embodiment, the device generator 80 is supported on the first generator support pedestal 332 and includes the generator rotating shaft 82 extending in the axial direction d. The conversion rotor 71 includes a screw bearing 78 provided on the generator rotating shaft 82, and the power generation floating body 341 is provided with a second holder 348 that holds the screw bearing 78. This allows the screw bearing 78 of the conversion rotor 71 to function as an inertial mass element that reduces vibrations due to relative displacement between the first structure 330 and the second structure 340. Therefore, vibrations caused by relative displacement between the first structure 330 and the second structure 340 can be reduced. Furthermore, vibrations of the power generation floating body 341 along the axial direction d are converted into rotational displacement of the generator rotating shaft 82 by the screw bearing 78 . Therefore, the relative displacement in the axial direction d between the first structure 330 and the second structure 340 can be converted into rotational displacement, and the device generator 80 can generate electricity. As a result, vibration of the first structure 330 can be suppressed and vibration energy can be converted into electrical energy.

Further, according to the present embodiment, the screw bearing 78 converts the relative displacement between the first structure 330 and the second structure 340 in the axial direction d into rotational displacement. Thereby, the mechanical resistance of the conversion rotor 71 can be reduced, and the relative displacement along the axial direction d can be efficiently converted into rotational displacement. Therefore, even if the force that the power generation floating body 341 receives from waves is small, the device generator 80 can generate power.

Note that the vibration damping power generation device 320 in this embodiment described above may include a plurality of conversion mechanisms 70 and a plurality of device generators 80. In this case, a second holder 348 may be provided below each device generator 80.

(15th embodiment)
Next, a vibration damping power generation device according to a fifteenth embodiment will be described using FIG. 23.

The fifteenth embodiment shown in FIG. 23 differs mainly in that the conversion mechanism includes a transmission section that can change the speed of the rotation of the generator rotating shaft, and the other configuration is different from that of the fourteenth embodiment shown in FIG. 22. The form is almost the same as that of . In FIG. 23, the same parts as those in the fourteenth embodiment shown in FIG. 22 are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 23, in this embodiment, the conversion mechanism 70 includes a transmission section 370 that can change the speed of the rotation of the generator rotating shaft 82. The transmission section 370 includes a transmission shaft 371 extending in the axial direction d so as to exceed the first generator support frame 332, a first transmission gear 372 provided on the generator rotating shaft 82, and a transmission shaft 371 provided at the upper end of the transmission shaft 371. and a second speed change gear 373. The speed change shaft 371 may be formed to extend along the central axis L4 of the second holder 348. The speed change shaft 371 may be parallel to the generator rotation axis 82. The first speed change gear 372 and the second speed change gear 373 mesh with each other.

A speed change shaft 371 passes through the through hole 332a of the first generator support frame 332. The speed change shaft 371 extends beyond the first generator support frame 332 and into the second holder 348 of the second structure 340 . The speed change shaft 371 is rotatably supported by the first generator support frame 332 by a ball bearing 338 provided in the through hole 332a. The screw bearing 78 is provided at the lower end of the speed change shaft 371 of the speed change section 370. The speed change shaft 371 is rotatably supported by a bearing 374 provided on the first generator support frame 332.

The rotation of the screw bearing 78 is changed in speed by the second speed change gear 373 and the first speed change gear 372, and is transmitted to the generator rotating shaft 82. The transmission shaft 371, the first transmission gear 372, and the second transmission gear 373 constitute the conversion rotor 71 together with the screw bearing 78. As a result, the moment of inertia _I1 of the conversion rotor 71 becomes the sum of the moment of inertia of the screw bearing 78, the moment of inertia of the first speed change gear 372, and the moment of inertia of the second speed change gear 373.

Note that a transmission (not shown) may be interposed between the first transmission gear 372 and the second transmission gear 373. The transmission includes a plurality of gears each having a different number of teeth, and a switching unit that switches the gears, and the first transmission gear 372 and the second transmission gear 373 are configured to mesh with each other through a selected gear. may have been done. The plurality of gears may be configured such that the switching portion switches the gears meshing with the first speed change gear 372 and the second speed change gear 373. In this case, the speed change rate (speed increase rate or deceleration rate) of the rotation of the generator rotating shaft 82 can be changed.

In this embodiment, the first elastic body 350 connects the speed change shaft 371 and the second holder 348. As a result, the first structure 330 and the second structure 340 are elastically connected via the device generator 80.

As described above, according to the present embodiment, the conversion mechanism 70 includes the transmission section 370 that can change the speed of the rotation of the generator rotating shaft 82. This allows the speed of rotation of the generator rotating shaft 82 to be changed. In this case, the cut-off frequency ratio ν _S can be adjusted to match or approach the frequency f _w of the wave. Therefore, the vibration transmissibility T can be effectively reduced according to the wave frequency _fw , and the vibration of the first structure 330 can be effectively suppressed.

Note that the vibration damping power generation device 320 in this embodiment described above may include a plurality of conversion mechanisms 70 and a plurality of device generators 80. In this case, a second holder 348 may be provided below each device generator 80.

(16th embodiment)
Next, a vibration damping power generation device according to a sixteenth embodiment will be described using FIG. 24.

In the 16th embodiment shown in FIG. 24, the main points are that the device generator is supported by a floating body for power generation, and the first generator support frame is provided with a first holder that holds a screw bearing. However, the other configurations are substantially the same as the fourteenth embodiment shown in FIG. 22. Note that in FIG. 24, the same parts as those in the fourteenth embodiment shown in FIG. 22 are designated by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 24, in this embodiment, the device generator 80 is supported by a floating body 341 for power generation. The power generation floating body 341 is formed in a ring shape so as to surround the main floating body 331. The power generation floating body 341 according to this embodiment includes a generator accommodating portion 341a formed in a concave shape. The upper end of the generator housing portion 341a may be open. The device generator 80 is housed in the generator housing section 341a. The generator rotation shaft 82 extends upward from the rotor 83 in the axial direction d. The generator casing 85 is fixed to the power generation floating body 341.

A plurality of rollers 343 may be provided on the inner peripheral surface of the power generation floating body 341. The roller 343 may be attached to the inner peripheral surface of the power generation floating body 341 via an adapter 349. The roller 343 can roll against the outer peripheral surface of a first holder 339, which will be described later. This allows the first structure 330 and the second structure 340 to be smoothly displaced relative to each other. A guide rail (not shown) extending in the axial direction d may be provided on the inner peripheral surface of the power generation floating body 341. In this case, the relative displacement of the second structure 340 with respect to the first structure 330 can be guided in the axial direction d.

The screw bearing 78 is provided at the upper end of the generator rotating shaft 82. A first holder 339 is provided on the lower surface of the first generator support pedestal 332 . A lower portion of the first holder 339 enters into the generator accommodating portion 341a. The screw bearing 78 is held by the first holder 339. The first holder 339 may be formed in a cylindrical shape along the central axis L4.

In this embodiment, the first elastic body 350 connects the generator rotating shaft 82 and the first holder 339. As a result, the first structure 330 and the second structure 340 are elastically connected via the device generator 80.

As described above, according to the present embodiment, the device generator 80 is supported on the first generator support pedestal 332 and includes the generator rotating shaft 82 extending in the axial direction d. The conversion rotor 71 includes a screw bearing 78 provided on the generator rotating shaft 82 , and a first holder 339 that holds the screw bearing 78 is provided on the first generator support pedestal 332 . This allows the screw bearing 78 of the conversion rotor 71 to function as an inertial mass element that reduces vibrations due to relative displacement between the first structure 330 and the second structure 340. Therefore, vibrations caused by relative displacement between the first structure 330 and the second structure 340 can be reduced. Furthermore, vibrations of the power generation floating body 341 along the axial direction d are converted into rotational displacement of the generator rotating shaft 82 by the screw bearing 78 . Therefore, the relative displacement in the axial direction d between the first structure 330 and the second structure 340 can be converted into rotational displacement, and the device generator 80 can generate electricity. As a result, vibration of the first structure 330 can be suppressed and vibration energy can be converted into electrical energy.

Further, according to the present embodiment, the screw bearing 78 converts the relative displacement between the first structure 330 and the second structure 340 in the axial direction d into rotational displacement. Thereby, the mechanical resistance of the conversion rotor 71 can be reduced, and the relative displacement along the axial direction d can be efficiently converted into rotational displacement. Therefore, even if the force that the power generation floating body 341 receives from waves is small, the device generator 80 can generate power.

Note that the vibration damping power generation device 320 in this embodiment described above may include a plurality of conversion mechanisms 70 and a plurality of device generators 80. In this case, a first holder 339 may be provided above each device generator 80.

Further, in the present embodiment described above, the conversion mechanism 70 may include the transmission section 370 shown in FIG. 23.

(Seventeenth embodiment)
Next, a vibration damping power generation system according to a seventeenth embodiment will be described using FIG. 25.

As shown in FIG. 25, a damped power generation system 400 in this embodiment includes the above-described damped power generation devices 20 and 320, a DC converter 401, and a power storage device 402. The damped power generation devices 20 and 320 in the first to sixteenth embodiments described above may be applied to the damped power generation devices 20 and 320 shown in FIG. 25.

The DC converter 401 is configured to convert the power generated by the device generator 80 of the damped power generator 20, 320 into DC power and output the DC power. The power generated by the vibration damping power generation devices 20 and 320 is AC power, and the DC converter 401 converts the AC power supplied from the device generator 80 into DC power. An example of the DC converter 401 is a diode rectifier or the like.

Power storage device 402 is configured to store DC power output from DC converter 401. Examples of the power storage device 402 include a storage battery, a large capacity capacitor, and the like. The DC converter 401 and the power storage device 402 may be installed on the generator support pedestal 35, the first generator support pedestal 332, or the second generator support pedestal 346. However, DC converter 401 and power storage device 402 may be installed on the ground.

One end of the first line 403 is connected to the device generator 80 of the vibration damping power generation device 20, 320. A DC converter 401 is provided in this first line 403 . The other end of the first line 403 may be connected to an AC converter 404 . An example of the AC converter 404 is an inverter. A load may be connected to the other end of the first line 403 instead of the AC converter. A second line 405 branches off from the first line 403, and the power storage device 402 is connected to the second line 405.

As described above, according to the present embodiment, the power generated by the device generator 80 of the vibration damping power generation device 20, 320 is rectified by the DC converter 401 and converted into DC power. As a result, generated power having an irregular AC waveform can be converted into DC power that can be used for general electrical products. Further, the DC power converted from the generated power can be stored in the power storage device 402. This allows the generated power to be stored as DC power that can be used for general electrical products. Further, the DC power can be converted to AC power by the AC converter 404. This allows the generated power to be converted into alternating current power that can be used for general electrical products. Therefore, the availability of generated power can be improved.

In addition, in this embodiment mentioned above, the example where the damping power generation device 20, 320 is a device applied to the offshore wind power generation facility 10 shown in FIG. 2 was explained. However, it is not limited to this. The damped power generation devices 20 and 320 may be applied to equipment other than the offshore wind power generation equipment 10. For example, the vibration damping power generation devices 20 and 320 according to the ninth to sixteenth embodiments may be applied to an offshore buoy (not shown).

(18th embodiment)
Next, a wind power generation system according to an eighteenth embodiment will be described using FIG. 26.

As shown in FIG. 26, a wind power generation system 500 according to the present embodiment is a system that supplies power to the auxiliary equipment 6 that controls the offshore wind power generation facility 10 described above. The wind power generation system 500 includes the above-described vibration-damped power generation devices 20 and 320, a wind power generation system 510, an auxiliary power system 520, and a device power generation system 530. The vibration damping power generation devices 20 and 320 are installed in the wind power generator main body 4. The damped power generation devices 20 and 320 in the first to sixteenth embodiments described above may be applied to the damped power generation devices 20 and 320 shown in FIG.

The wind power generation system 510 supplies wind power generated by the wind power generator 4c of the wind power generator main body 4 to an external power system 540. Wind power generation system 510 includes a controller 511 and a main transformer 512. The controller 511 converts the wind power generated by the wind power generator 4c into DC power, converts the converted DC current into AC power, and outputs the AC power. The output AC power is supplied to external power system 540 via main transformer 512. One end of a wind power generation line 513 is connected to the wind power generator 4c. The other end of the wind power generation line 513 is connected to an external power system 540. The wind power generation line 513 is provided with a controller 511 and a main transformer 512.

Auxiliary power system 520 supplies power to auxiliary equipment 6. Auxiliary power system 520 includes an auxiliary transformer 521. One end of an auxiliary machine line 522 is connected to the auxiliary machine 6. This auxiliary equipment line 522 is provided with an auxiliary transformer 521 . The other end of the auxiliary equipment line 522 is connected to the wind power generation line 513 of the wind power generation system 510. The auxiliary equipment line 522 is connected to the wind power generation line 513 at a position between the controller 511 and the main transformer 512.

The device power generation system 530 supplies the device generated power of the device generator 80 of the damped power generation device 20, 320 to the auxiliary power system 520. The device power generation system 530 includes a DC converter 531 and an AC converter 532.

The DC converter 531 is configured to convert device-generated power into DC power and output it. The DC converter 531 converts AC power supplied from the device generator 80 into DC power. An example of the DC converter 531 is a diode rectifier or the like.

The AC converter 532 is configured to convert the DC power output from the DC converter 531 into AC power and output the AC power. An example of the AC converter 532 is an inverter. One end of a device power generation line 533 is connected to the device generator 80 of the vibration damping power generation device 20, 320. This device power generation line 533 is provided with a DC converter 531 and an AC converter 532. The other end of the device power generation line 533 is connected to the auxiliary equipment line 522. The device power generation line 533 is connected to the auxiliary machine line 522 at a position between the auxiliary transformer 521 and the auxiliary machine 6.

As described above, according to the present embodiment, the power generated by the device generator 80 of the vibration damping power generation devices 20, 320 is converted into DC power by the DC converter 531, and the DC power is converted into AC converter. It is converted to AC power by device 532. Thereby, the generated power can be supplied to the auxiliary machine 6 via the auxiliary machine power system 520. Therefore, even if the power supply from the external power system 540 to the auxiliary machine 6 is cut off, the generated power obtained from the vibration energy can be supplied to the auxiliary machine 6, and the wind power generator main body 4 can be It is possible to control and continue operation. Note that if AC power can be supplied to the auxiliary machine 6 from the external power system 540, the AC power may be supplied to the auxiliary machine 6 via the main transformer 512 and the auxiliary transformer 521.

(19th embodiment)
Next, a wind power generation system according to a nineteenth embodiment will be described using FIG. 27.

In the nineteenth embodiment shown in FIG. 27, the device power generation system includes a line that supplies DC power output from the DC converter to a DC auxiliary machine driven by DC power among the auxiliary machines. The main difference is that the other configurations are substantially the same as the eighteenth embodiment shown in FIG. Note that in FIG. 27, the same parts as in the eighteenth embodiment shown in FIG. 26 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 27, in this embodiment, the auxiliary machine 6 includes an AC auxiliary machine 6a driven by AC power, and a DC auxiliary machine 6b driven by DC power. The device power generation system 530 includes a DC line 534 that supplies DC power output from the DC converter 531 to the DC auxiliary machine 6b. One end of the DC line 534 is connected to a position of the device power generation line 533 between the DC converter 531 and the AC converter 532, and the other end of the DC line 534 is connected to the DC auxiliary machine 6b.

As described above, according to the present embodiment, the DC power output from the DC converter 531 can be directly supplied to the DC auxiliary machine 6b driven by DC power. This allows the power generated by the device generator 80 to be effectively used.

(Twentieth embodiment)
Next, a wind power generation system according to a twentieth embodiment will be described using FIG. 28.

The 20th embodiment shown in FIG. 28 differs mainly in that the device power generation system includes a power storage device that stores the DC power output from the DC converter, and the other configuration is the 20th embodiment shown in FIG. This is substantially the same as the 18th embodiment. Note that in FIG. 28, the same parts as in the eighteenth embodiment shown in FIG. 26 are denoted by the same reference numerals, and detailed description thereof will be omitted.

As shown in FIG. 28, in this embodiment, device power generation system 530 includes a power storage device 535 that stores DC power output from DC converter 531. Examples of the power storage device 535 include a storage battery, a large capacity capacitor, and the like. One end of the power storage line 536 is connected to a position of the device power generation line 533 between the DC converter 531 and the AC converter 532, and the other end of the power storage line 536 is connected to the power storage device 535.

As described above, according to the present embodiment, device power generation system 530 can supply DC power output from DC converter 531 to power storage device 535. Thereby, the power storage device 535 can store power using the power generated by the device generator 80. For example, if the power generated by the device generator 80 is surplus to the AC power required by the auxiliary device 6, the surplus may be stored in the power storage device 535. On the other hand, if the power generated by the device generator 80 is insufficient for the AC power required by the auxiliary machine 6, the power stored in the power storage device 535 is transferred to the auxiliary machine 6 via the AC converter 532. may be supplied to

(21st embodiment)
Next, a wind power generation system according to a twenty-first embodiment will be described using FIGS. 29 and 30.

In the twenty-first embodiment shown in FIGS. 29 and 30, the main difference is that the device power generation system is connected to supply the AC power output from the AC converter to the wind power generation system; The configuration is substantially the same as that of the 20th embodiment shown in FIG. Note that in FIGS. 29 and 30, the same parts as those in the twentieth embodiment shown in FIG. 28 are given the same reference numerals, and detailed explanations will be omitted.

As shown in FIG. 29, in this embodiment, device power generation system 530 is connected to supply AC power output from AC converter 532 to wind power generation system 510. In FIG. 29 , the device power generation line 533 is connected to the auxiliary equipment line 522 at a position between the wind power generation line 513 and the auxiliary transformer 521 . Electrically, the connection point between the wind power generation line 513 and the auxiliary equipment line 522 is the same as the connection point between the wind power generation line 513 and the device power generation line 533, and is the same as the AC connection point of the auxiliary power system 520. The AC connection points of the device power generation system 530 are the same.

As described above, according to the present embodiment, the device power generation system 530 can supply the AC power output from the AC converter 532 to the wind power generation system 510. Thereby, the power generated by the device generator 80 can be supplied to the external power system 540. Further, the AC power output from the AC converter 532 can also be supplied to the auxiliary machine 6.

In addition, in this embodiment mentioned above, the example in which the device power generation system 530 includes the DC converter 531 and the AC converter 532 was explained. However, it is not limited to this. For example, as shown in FIG. 29, device power generation system 530 may include power conversion control device 537. The power conversion control device 537 constitutes a DC converter 531 and an AC converter 532 shown in FIG. Power conversion control device 537 may include a switching element. In this case, the device generator 80 may have a function as an electric motor. The switching element is made of a semiconductor element, and may be configured not only to rectify the power generated by the device generator 80 but also to supply power supplied from the external power system 540 to the device generator 80. Power supplied via the switching elements from the external power system 540 allows the device generator 80 to function as an electric motor. In this case, the second structure 340 can be actively displaced with respect to the first structure 330, and the relative displacement between the first structure 330 and the second structure 340 can be effectively reduced. I can do it. Note that the power conversion control device 537 may be connected to a power storage line 536 and be capable of outputting DC power.

According to the embodiments described above, vibration can be suppressed and vibration energy can be converted into electrical energy.

Although several embodiments of the invention have been described, these embodiments are presented by way of example and are not intended to limit the scope of the invention. These novel embodiments can be implemented in various other forms, and various omissions, substitutions, and changes can be made without departing from the gist of the invention. These embodiments and their modifications are included within the scope and gist of the invention, as well as within the scope of the invention described in the claims and its equivalents. Furthermore, it is of course possible to combine these embodiments as appropriate within the scope of the invention.

6: Auxiliary equipment, 6b: DC auxiliary equipment, 10: Offshore wind power generation equipment, 20: Damping power generation device, 30: Support structure, 31a: Upper part, 33: First cavity, 40: Tower structure, 40a : Lower part, 70: Conversion mechanism, 71: Conversion rotor, 72: Rack rail, 73: Pinion gear, 78: Screw bearing, 80: Device generator, 81: Generator rotor, 82: Generator rotating shaft , 100: Connected structure, 101: Second cavity, 210: Hull structure, 220: Cabin structure, 320: Vibration damping power generation device, 330: First structure, 331: Main floating body, 332: First power generation Machine support frame, 339: first holder, 340: second structure, 341: floating body for power generation, 342: second rod, 348: second holder, 370: transmission section, 400: vibration suppression power generation system, 401: DC Conversion device, 402: Power storage device, 500: Wind power generation system, 510: Wind power generation system, 520: Auxiliary power system, 530: Device power generation system, 531: DC conversion device, 532: AC conversion device, 535: Power storage device, 537: Power conversion control device, d: Axial direction, L1: Center axis, L2: Rotation center axis, L4: Center axis

Claims (32)

a support structure;
a displacement structure that is elastically supported by the support structure and is movable relative to the support structure;
a conversion mechanism that includes a conversion rotor and converts a relative displacement between the support structure and the displacement structure into a rotational displacement of the conversion rotor;
A device generator that generates power by the rotational displacement of the conversion rotor,
the conversion rotor functions as an inertial mass element that reduces vibrations due to relative displacement between the support structure and the displacement structure ;
The support structure includes a floating body floating on the ocean.
Vibration control power generation device. the device generator includes a generator rotor;
The damped power generation device according to claim 1 , wherein the generator rotor functions as the inertial mass element. The vibration damping power generation device according to claim 1 or 2 , wherein the support structure includes a first cavity portion that accommodates a portion of the displacement structure. The support structure is formed to extend along a central axis,
The support structure and the displacement structure are capable of relative displacement in an axial direction along the central axis,
The conversion mechanism includes a rack provided on the displacement structure and extending in the axial direction, and a pinion gear that constitutes the conversion rotor and meshes with the rack,
The damped power generation device according to any one of claims 1 to 3 , wherein the pinion gear and the device generator are supported by the support structure. a plurality of the conversion mechanisms;
a plurality of the device generators provided corresponding to each of the conversion mechanisms,
On one side with respect to the displacement structure, one of the conversion mechanisms and one of the device generators corresponding to the conversion mechanism are located, and on the other side, another of the conversion mechanisms and the conversion mechanism. 5. The damped power generation device according to claim 4 , wherein a corresponding one of the device generators is located. The vibration damping power generation device according to claim 4 or 5 , wherein the conversion mechanism includes a transmission section capable of changing the rotation speed of the pinion gear. The support structure includes a first support structure and a second support structure that is elastically supported by the first support structure and elastically supports the displacement structure,
The conversion mechanism converts a relative displacement between the second support structure and the displacement structure into a rotational displacement of the conversion rotor,
The vibration damper according to any one of claims 1 to 3 , wherein the conversion rotor functions as an inertial mass element that reduces vibrations due to relative displacement between the second support structure and the displacement structure. Power generator. The vibration damping power generation device according to claim 7 , wherein the second support structure includes a second cavity through which a portion of the first support structure can pass. the second support structure includes a second cavity through which the displacement structure can pass;
8. The second support structure according to claim 7 , wherein the second support structure is located at a different position than the first support structure in the direction of relative displacement between the first support structure and the second support structure. The vibration damping power generation device described. The first support structure is formed to extend along the central axis,
The second support structure and the displacement structure are capable of relative displacement in an axial direction along the central axis,
The conversion mechanism includes a rack provided on the displacement structure and extending in the axial direction, and a pinion gear that constitutes the conversion rotor and meshes with the rack,
The damped power generation device according to any one of claims 7 to 9 , wherein the pinion gear and the device generator are supported by the second support structure. The first support structure is formed to extend along the central axis,
The second support structure and the displacement structure are capable of relative displacement in an axial direction along the central axis,
The conversion mechanism includes a rack provided on the second support structure and extending in the axial direction, and a pinion gear that constitutes the conversion rotor and meshes with the rack,
The damped power generation device according to any one of claims 7 to 9 , wherein the pinion gear and the device generator are supported by the displacement structure. The vibration damping power generation device according to claim 10 or 11 , wherein the conversion mechanism includes a transmission section capable of changing the rotation speed of the pinion gear. The support structure and the displacement structure are capable of relative rotational displacement about a rotation center axis,
The displacement structure includes a circular arc surface formed in an arc shape with the rotation center axis as the center, and the conversion mechanism is provided on the circular arc surface and has a circumferential surface formed in an arc shape with the rotation center axis as the center. a rack extending in the direction; and a pinion gear constituting the conversion rotor that meshes with the rack,
The damped power generation device according to any one of claims 1 to 3 , wherein the pinion gear and the device generator are supported by the support structure. a first structure;
a second structure that is elastically connected to the first structure and is movable relative to the first structure;
a conversion mechanism that includes a conversion rotor and converts a relative displacement between the first structure and the second structure into a rotational displacement of the conversion rotor;
A device generator that generates power by the rotational displacement of the conversion rotor,
The conversion rotor functions as an inertial mass element that reduces vibrations due to relative displacement between the first structure and the second structure,
The first structure includes a first floating body floating on the ocean,
The second structure is a vibration damping power generation device including a second floating body floating on the ocean at a different position from the first floating body. the device generator includes a generator rotor;
The damped power generation device according to claim 14 , wherein the generator rotor functions as the inertial mass element. The first structure is formed to extend along the central axis,
The first structure and the second structure are capable of relative displacement in an axial direction along the central axis,
The conversion mechanism includes a rack provided in the second structure and extending in the axial direction, and a pinion gear that constitutes the conversion rotor and meshes with the rack,
The damped power generation device according to claim 14 or 15 , wherein the pinion gear and the device generator are supported by the first structure. The first structure includes a pedestal located above the second floating body,
The second structure includes a rod extending from the second floating body in the axial direction beyond the pedestal,
The vibration damping power generation device according to claim 16 , wherein the rack is provided on the rod. multiple conversion mechanisms;
a plurality of the device generators provided corresponding to each of the conversion mechanisms,
One of the conversion mechanisms and one of the device generators corresponding to the conversion mechanism are located on one side with respect to the second structure, and one of the other conversion mechanisms and the device generator are located on the other side. The vibration damping power generation device according to claim 16 or 17 , wherein another one of the device generators corresponding to the conversion mechanism is located. a plurality of said second structures;
a plurality of conversion mechanisms provided corresponding to each of the second structures;
a plurality of the device generators provided corresponding to each of the conversion mechanisms,
One of the second structures, one of the conversion mechanisms and one of the device generators corresponding to the second structures are located on one side with respect to the first structure, and on the other side, The vibration damping power generation device according to claim 14 or 15 , wherein another one of the second structures, one of the conversion mechanisms, and one of the device generators corresponding to the second structures are located. The damping power generation device according to claim 19 , wherein the plurality of second structures are connected to each other. The first structure is formed to extend along the central axis,
The first structure and the second structure are capable of relative displacement in an axial direction along the central axis,
The conversion mechanism includes a rack provided in the first structure and extending in the axial direction, and a pinion gear that constitutes the conversion rotor and meshes with the rack,
The damped power generation device according to claim 14 or 15 , wherein the pinion gear and the device generator are supported by the second structure. The vibration-damping power generation device according to any one of claims 16 to 18 and 21 , wherein the conversion mechanism includes a transmission section capable of changing the speed of rotation of the pinion gear. the first floating body extends in the axial direction;
The second floating body extends higher than the first floating body in the axial direction,
the pinion gear and the device generator are supported by the first floating body;
The vibration damping power generation device according to claim 16 . The first structure is formed to extend along the central axis,
The first structure and the second structure are capable of relative displacement in an axial direction along the central axis,
The first structure includes a pedestal located above the second floating body,
the device generator is supported on the pedestal;
The device generator includes a generator rotation shaft extending in the axial direction beyond the mount, the conversion rotor includes a screw bearing provided on the generator rotation shaft,
The vibration damping power generation device according to claim 14 or 15 , wherein the second floating body is provided with a second holder that holds the screw bearing. The first structure is formed to extend along the central axis,
The first structure and the second structure are capable of relative displacement in an axial direction along the central axis,
The first structure includes a pedestal located above the second floating body,
the device generator is supported on the pedestal;
The device generator includes a generator rotation shaft extending in the axial direction so as to exceed the mount, and the conversion mechanism includes a speed change unit capable of changing the rotation speed of the generator rotation shaft,
The conversion rotor includes a screw bearing provided in the transmission section,
The vibration damping power generation device according to claim 14 or 15 , wherein the second floating body is provided with a second holder that holds the screw bearing. The first structure is formed to extend along the central axis,
The first structure and the second structure are capable of relative displacement in an axial direction along the central axis,
The first structure includes a pedestal located above the second floating body,
the device generator is supported by the second floating body;
The device generator includes a generator rotating shaft extending in the axial direction,
The conversion rotor includes a screw bearing provided on the generator rotation shaft,
The vibration damping power generation device according to claim 14 or 15 , wherein the pedestal is provided with a first holder that holds the screw bearing. The damping power generation device according to any one of claims 1 to 26 ,
a DC converter that converts the generated power of the device generator of the vibration suppressed power generation device into DC power and outputs the DC power;
A vibration-damping power generation system, comprising: a power storage device that stores DC power output from the DC converter. A wind power generation system that supplies power to auxiliary equipment that controls wind power generation equipment,
The damping power generation device according to any one of claims 1 to 26 ,
an auxiliary power system that supplies power to the auxiliary equipment;
a device power generation system that supplies the device generated power of the device generator of the vibration damping power generation device to the auxiliary power system;
The device power generation system includes a DC converter that converts the device generated power into DC power and outputs the DC power;
A wind power generation system comprising: an AC converter that converts DC power output from the DC converter into AC power and outputs the AC power. The wind power generation system according to claim 28 , wherein the device power generation system includes a line that supplies DC power output from the DC converter to a DC auxiliary machine driven by DC power among the auxiliary machines. The wind power generation system according to claim 28 or 29 , wherein the device power generation system includes a power storage device that stores DC power output from the DC converter. Further comprising a wind power generation system that supplies wind power generated by the wind power generation equipment to an external power system,
The wind power generation system according to any one of claims 28 to 30 , wherein the device power generation system is connected to supply the AC power output from the AC converter to the wind power generation system. The DC converter and the AC converter are configured by a power conversion control device,
32. The wind power generation system according to claim 31 , wherein the device generator of the vibration suppressed power generation device has a function as an electric motor driven by electric power supplied from the power conversion control device.

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