JP2024033634A - Vibration control power generation device - Google Patents

Abstract

An object of the present invention is to provide a vibration damping power generation device that can suppress vibration and generate power. A vibration damping power generation device according to an embodiment includes a floating body including an internal space and a movable body disposed within the internal space, the movable body being elastically coupled to the floating body and capable of relative translation in a first direction with respect to the floating body. It includes a movable body that can move, a conversion mechanism that converts relative translational motion between the floating body and the movable body into rotational motion, and a device generator that generates electricity. The device generator includes a rotor that rotates with a rotational motion converted by a conversion mechanism. [Selection diagram] Figure 1

Description

This embodiment relates to a vibration damping power generation device.

Offshore wind power generation, in which wind power is generated offshore, has the advantage of being able to generate electricity using stable offshore wind. In deep waters, it is difficult to establish foundations on the seabed and secure wind turbine facilities for wind power generation, so floating offshore wind power generation is considered to be an effective implementation method.

In a floating offshore wind power generation facility, a floating structure is provided on a floating body floating on the ocean, and a tower is erected on top of this floating structure. A wind generator is mounted on the top of the tower. The floating structure is moored to the seabed with an anchor chain to maintain its position. Floating structures mainly perform vertical vibration (heave vibration) due to waves. As a result, in order to suppress damage to power generation equipment due to vibrations, countermeasures have been taken, such as detuning the natural frequency of floating structures from the natural period of waves. Further suppression of vibration is important for equipment maintenance during times of high waves such as when a typhoon approaches.

On the other hand, a wind power generation device is a device that generates electricity using wind power, but the power source for controlling the angle and direction of the wind turbine, the attitude of the floating body, etc., and the control power source for operating the auxiliary equipment are dependent on external sources. . External power supply networks may be cut off in the event of a disaster such as a typhoon. If the external power source is lost, the wind power generator cannot be controlled. For example, if it becomes difficult to control the attitude of a floating body, there may be a risk that the floating body may collapse. As the control power source, it is possible to use a battery that can store electricity. However, the power storage method has a limited battery capacity, and if the external power supply is lost for a long period of time, time constraints may become a problem.

Patent No. 3718683 Patent No. 5627527

The embodiments have been made with these points in mind, and an object thereof is to provide a vibration-damping power generation device that can suppress vibration and generate power.

A vibration damping power generation device according to an embodiment includes a floating body including an internal space, and a movable body disposed within the internal space, the movable body being elastically coupled to the floating body and capable of translational movement relative to the floating body in a first direction. It includes a body, a conversion mechanism that converts relative translational motion between the floating body and the movable body into rotational motion, and a device generator that generates electricity. The device generator includes a rotor that rotates with a rotational motion converted by a conversion mechanism.

A floating platform apparatus according to an embodiment is located on water. The floating platform device includes a platform and the plurality of vibration damping power generation devices described above that support the platform. When viewed in at least one direction perpendicular to the first direction, vibration damping power generation devices are arranged on both sides of the platform in a lateral direction with respect to the center of gravity.

According to the embodiment, vibration can be suppressed and power generation can be performed.

FIG. 1 is a diagram showing an example of an offshore wind power generation facility to which a vibration-damped power generation device according to the first embodiment is applied. FIG. 2 is a diagram showing a dynamic model of the vibration damping power generation device of FIG. 1. FIG. 3 is a response diagram showing the vibration transmissibility of heave vibration of the damped power generator shown in FIG. FIG. 4 is a schematic vertical cross-sectional view showing a vibration damping power generation device in a second embodiment. FIG. 5 is a schematic longitudinal sectional view showing a vibration damping power generation device in a third embodiment. FIG. 6 is a schematic vertical cross-sectional view showing a vibration damping power generation device in a fourth embodiment. FIG. 7 is a schematic vertical sectional view showing a vibration damping power generation device in a fifth embodiment. FIG. 8A is a schematic vertical cross-sectional view showing a vibration damping power generation device in a sixth embodiment. FIG. 8B is a schematic diagram showing the main rope as viewed along arrow P1 in FIG. 8A. FIG. 9A is a schematic vertical cross-sectional view showing a vibration damping power generation device in a seventh embodiment. FIG. 9B is a schematic diagram showing the main rope as viewed along arrow P2 in FIG. 9A. FIG. 10A is a schematic vertical cross-sectional view showing a vibration damping power generation device in an eighth embodiment. FIG. 10B is a schematic diagram showing the main rope as viewed along arrow P3 in FIG. 10A. FIG. 11 is a schematic vertical cross-sectional view showing a vibration damping power generation device in a ninth embodiment. FIG. 12 is a schematic sectional view showing a floating platform device equipped with a vibration damping power generation device according to a tenth embodiment. FIG. 13 is a diagram showing a dynamic model of the floating platform device of FIG. 12. FIG. 14 is a response diagram showing the vibration transmissibility of heave vibration of the floating platform device of FIG. 12. FIG. 15 is a response diagram showing the vibration transmissibility of pitching vibration of the floating platform device of FIG. 12. FIG. 16 is a plan view showing an example of the floating platform device of FIG. 12. FIG. 17 is a plan view showing another example of the floating platform device of FIG. 12.

DESCRIPTION OF THE PREFERRED EMBODIMENTS A vibration damping power generation device and a floating platform device according to embodiments of the present invention will be described below with reference to the drawings.

(First embodiment)
A vibration damping power generation device according to this embodiment will be explained using FIGS. 1 to 3. Here, an example of a vibration damping power generation device applied to a spar type offshore wind power generation facility will be described. However, the application example of the damped power generation device is not limited to this.

First, an offshore wind power generation facility 1 to which a damped power generation device 10 according to the present embodiment is applied will be described using FIG. 1. FIG. 1 shows a schematic cross-sectional structure of a damped power generation device 10 according to the present embodiment, and shows an example in which the damped power generation device 10 shown here is applied to an offshore wind power generation facility 1.

The offshore wind power generation facility 1 shown in FIG. 1 includes a wind power generation device 2, a tower 3 that supports the wind power generation device 2, and a vibration damping power generation device 10 that is located below the tower 3 and supports the tower 3. ing. The vibration damping power generation device 10 is located on the water.

The tower 3 extends vertically upward from the vibration damping power generation device 10 and is formed in a columnar shape. The wind power generator 2 is attached to the upper end of the tower 3. The wind power generation device 2 is supported by a vibration damping power generation device 10 with a tower 3 interposed therebetween.

The wind power generator 2 includes a nacelle 2a and a power generation rotor 2b. The nacelle 2a is rotatably supported around an axis extending perpendicularly to the tower 3 depending on the wind direction and the like. The power generation rotor 2b is rotatably provided in the nacelle 2a. A wind power generator 2c that generates power by rotating a power generation rotor 2b is built into the nacelle 2a. The power generation rotor 2b includes a plurality of blades 2d.

Although not shown, the offshore wind power generation facility 1 further includes electrical equipment for supplying power generated by the wind power generator 2c to the outside, a control device for controlling the wind power generation device 2, and a mooring device for mooring a floating body 20, which will be described later. We are prepared.

Such an offshore wind power generation facility 1 vibrates in the vertical direction in response to the excitation force of waves. This vibration is also called heave vibration. A vibration suppressed power generation device 10 according to the present embodiment is a device for suppressing this heave vibration and generating power using this heave vibration.

Next, the vibration damping power generation device 10 according to the present embodiment will be described using FIG. 1.

In the following explanation, an XYZ three-dimensional orthogonal coordinate system will be defined and explained as shown in FIG. The X axis extends in the vertical direction, and the X direction is an example of a first direction. The Y axis extends horizontally and is an example of the second direction. The Y direction corresponds to a direction perpendicular to the paper plane of FIG. The Z axis extends horizontally and is an example of a third direction. The Z-axis is perpendicular to the X-axis and perpendicular to the Y-axis. The Z direction corresponds to the lateral direction of the paper in FIG.

As shown in FIG. 1, the vibration damping power generation device 10 according to the present embodiment includes a floating body 20, a movable body 30, a conversion mechanism 40, and a device generator 50. In this embodiment, an example in which the tower 3 is supported by one vibration-damping power generation device 10 will be described.

The floating body 20 is configured to float on water (or seawater). The floating body 20 may be formed in a cylindrical shape so as to extend in the X direction. A portion of the floating body 20 is located below the water surface and is immersed in the surrounding water. The water surface is indicated by the symbol W in FIG. 1 etc. The floating body 20 is configured to withstand water pressure.

A weight section (not shown) filled with a heavy object such as concrete or ballast water is provided at the lower part of the floating body 20. This lowers the center of gravity of the floating body 20 and balances the buoyancy of the floating body 20 with the gravity of the offshore wind power generation facility 1. In this way, the stability of the floating body 20 floating on water is increased.

The floating body 20 is floating on water as described above. Therefore, the floating body 20 vibrates under the excitation force of the waves, and a restoring force due to the buoyancy is acting on the floating body 20. This allows the floating body 20 to be considered to be elastically coupled to the stationary system by water. To illustrate this, in FIG. 1, the floating body 20 is elastically coupled to the stationary system by a virtual elastic body 60 having a spring constant _k1 . The restoring force acting on the floating body 20 is represented by the product k ₁ ×x ₁ of k ₁ and the displacement x ₁ of the floating body 20. The virtual elastic body 60 is composed of a buoyancy spring. The virtual elastic body 60 is used not to indicate the presence of a spring member, but to schematically indicate that the floating body 20 is supported in the X direction by the buoyant force received from the surrounding water. The natural frequency of the floating body 20 may be designed to be sufficiently detuned from the frequency of the waves.

The floating body 20 includes an internal space 20S. The internal space 20S is a space surrounded by the inner wall surface 21 of the floating body 20, and the movable body 30 described above is accommodated in the internal space 20S. The diameter of the internal space 20S is larger than the outer diameter of the movable body 30. The internal space 20S may be arranged above the weight section described above.

Floating body 20 includes an upper plate 22 disposed above internal space 20S. The upper plate 22 is formed to cover the internal space 20S from above. The internal space 20S is sealed to prevent water from entering the internal space 20S from the outside. The upper plate 22 may be formed into a plate shape along the Y direction and the Z direction. The tower 3 mentioned above may be supported by the upper plate 22.

The movable body 30 is arranged within the internal space 20S. The movable body 30 is configured to be able to move in translation relative to the floating body 20 in the X direction. The movable body 30 may include a movable cylindrical body 31 and an upper flange 32.

The movable cylinder 31 is formed into a cylindrical shape extending in the X direction. A plurality of rollers 33 may be attached to the outer peripheral surface of the movable cylinder 31. The plurality of rollers 33 may be spaced apart in the X direction, or may be spaced apart in the circumferential direction. The roller 33 can roll against the inner wall surface 21 that defines the inner space 20S of the floating body 20. Thereby, relative translation between the floating body 20 and the movable body 30 can be performed smoothly. A guide rail (not shown) extending in the X direction may be attached to the inner wall surface 21 of the floating body 20. This makes it possible to suppress the movable body 30 from performing rotational movement about the axis along the X direction with respect to the floating body 20. Further, relative translational movement between the floating body 20 and the movable body 30 can be guided in the X direction. The roller 33 may be configured to roll relative to the guide rail.

The movable body 30 is elastically coupled to the floating body 20. More specifically, the movable body 30 may be connected to the floating body 20 with an elastic body 70 interposed therebetween. The elastic body 70 is disposed within the internal space 20S, and is connected to the lower end of the movable cylinder 31 and the bottom surface 23 of the internal space 20S. The elastic body 70 has a spring constant _k2 . The elastic body 70 may be configured by a spring member such as a coil spring, for example. The number of elastic bodies 70 is arbitrary. In the example shown in FIG. 1, the floating body 20 and the movable cylinder 31 are connected by two elastic bodies 70.

The upper flange 32 is provided on the upper part of the movable cylinder 31. The upper flange 32 is formed to cover the movable cylinder 31 from above. The movable cylinder 31 may be formed into a plate shape along the Y direction and the Z direction.

An adjustment weight 34 may be provided on the upper surface of the upper flange 32. The adjustment weight 34 may be configured to be able to adjust its mass. For example, the adjustment weight 34 may have a structure in which a plurality of weight plates formed in a plate shape are stacked, and the mass may be adjustable by changing the number of weight plates. Although the planar shape of the adjustment weight 34 is arbitrary, it may be ring-shaped so as to surround a block 35, which will be described later.

The conversion mechanism 40 is configured to convert relative translational motion between the floating body 20 and the movable body 30 into rotational motion. The conversion mechanism 40 according to this embodiment includes a female threaded hole 41 and a conversion rotation shaft 43 including a male threaded portion 42 . The conversion mechanism 40 is arranged in the internal space 20S of the floating body 20.

The female screw hole 41 has a central axis extending in the X direction. The female screw hole 41 is formed in the upper flange 32 mentioned above. The female screw hole 41 may be formed in the block 35 provided on the upper flange 32. The block 35 may be formed thicker than the upper flange 32. The female screw hole 41 penetrates the block 35. The male threaded portion 42 is configured to be screwed into the female threaded hole 41. The male threaded portion 42 is provided on the conversion rotation shaft 43. The conversion rotation shaft 43 extends in the X direction and is connected to a rotor 56, which will be described later. With such a configuration, the relative translational movement between the floating body 20 and the movable body 30 is converted into a rotational movement of the male threaded portion 42, and this rotational movement is transmitted to the device generator 50 by the conversion rotation shaft 43.

The conversion rotation shaft 43 may pass through the female screw hole 41. In this case, the upper end of the conversion rotation shaft 43 is located above the female screw hole 41. A flywheel 44 may be provided at the upper end of the conversion rotation shaft 43. The flywheel 44 may be configured to be able to adjust the moment of inertia of the rotor 56. For example, the flywheel 44 has a structure in which a plurality of weight plates formed in a plate shape are stacked, and by changing the number of weight plates, the moment of inertia of a rotor 56 of the device generator 50, which will be described later, can be adjusted. It may be possible.

The device generator 50 is supported by the floating body 20. As a result, the device generator 50 performs a translational movement in synchronization with the floating body 20, together with the above-mentioned male threaded portion 42, conversion rotation shaft 43, and the like. The device generator 50 may be fixed to the bottom surface 23 of the internal space 20S. The device generator 50 is arranged in the internal space 20S of the floating body 20. The device generator 50 is arranged inside the movable cylinder 31 and below the upper flange 32. The device generator 50 includes a stator 51 and a rotor 56.

Stator 51 includes a stator cylinder body 52, a stator upper flange 53, a stator lower flange 54, and a stator coil 55. The stator cylinder body 52 is formed in a cylindrical shape so as to extend in the X direction. The stator cylinder body 52 may be fixed to the bottom surface 23 of the internal space 20S. The stator upper flange 53 is provided on the upper part of the stator cylinder body 52. The stator upper flange 53 is formed to cover the stator cylinder body 52 from above. The stator upper flange 53 may be formed into a plate shape along the Y direction and the Z direction. The stator lower flange 54 is provided at the lower part of the stator cylinder body 52. The stator lower flange 54 may be formed into a plate shape along the Y direction and the Z direction. The stator coil 55 is attached to the inner surface of the stator cylinder body 52.

The rotor 56 is configured to rotate with the rotational movement converted by the conversion mechanism 40 described above. The rotor 56 is connected to the above-mentioned conversion rotation shaft 43, and the rotor 56 rotates by transmitting the rotational motion of the conversion rotation shaft 43.

More specifically, rotor 56 is arranged inside stator coil 55. Rotor 56 includes a generator rotation shaft 57. The generator rotating shaft 57 extends in the X direction and is rotatably supported by a bearing 58a provided on the stator lower flange 54 and a bearing 58b provided on the stator upper flange 53. The bearing 58a is configured as a thrust bearing and receives the thrust load of the generator rotating shaft 57. The rotor 56 includes a plurality of magnets (not shown) facing the stator coil 55. N poles and S poles are alternately arranged to form a magnetic field around the outer periphery of the rotor 56.

The power generated by the device generator 50 may be supplied to the control device described above. In this case, the control power of the wind power generator 2 can be covered by the power generated by the device generator 50. Therefore, dependence of the control power of the wind power generator 2 on supply from an external power source can be suppressed.

As shown in FIG. 1, the conversion mechanism 40 may include a transmission 45 interposed between the conversion rotation shaft 43 and the rotor 56. The transmission device 45 is interposed between the conversion rotation shaft 43 and the generator rotation shaft 57 and is configured to convert the rotation speed of the conversion rotation shaft 43 and transmit it to the generator rotation shaft 57. The transmission 45 may be, for example, a planetary gear transmission. The transmission 45 may be supported by the stator upper flange 53.

The vibration damping power generation device 10 according to the present embodiment configured as described above is schematically represented by a dynamic model shown in FIG. 2. FIG. 2 is a diagram showing a dynamic model of the vibration damping power generation device of FIG. 1.

The displacement X shown in FIG. 2 represents the displacement of the water surface W in the x direction, the displacement x ₁ represents the displacement of the floating body 20 in the x direction, and the displacement x ₂ represents the displacement of the movable body 30 in the x direction. The total mass of the floating body 20 is represented by m ₁ . _m1 includes the mass of equipment supported by the floating body 20, such as the wind power generation device 2, the tower house 3, and the device generator 50. The mass of the movable body 30 including the adjustment weight 34 is expressed in _m2 .

The combination of the female threaded hole 41 and the male threaded portion 42 converts the relative translational displacement between the floating body 20 and the movable body 30 into rotational displacement of the male threaded portion 42 . In this process, the relative translational acceleration between the floating body 20 and the movable body 30 is expressed as follows.

An inertial force proportional to this relative translational acceleration acts on the floating body 20 and the movable body 30. If the proportional coefficient of this inertial force is the inertial mass m _s2 , the pitch p between the female threaded hole 41 and the male threaded portion 42, the speed increase rate ε of the planetary gear transmission 14, and the moment of inertia I of the rotor 56 of the device generator 50, then It is expressed as below.

The equation of motion for the model in FIG. 2 is derived as follows.

Here, the displacement X of the water surface W is expressed as a function of the angular frequency Ω [rad/s] as follows.

Assume that the responses of x ₁ and x ₂ to equation (4) are as follows.

By substituting equations (4) to (6) into equation (3) and rearranging, the following equation (7) can be obtained.
is obtained.

When equation (7) is solved to determine the transfer functions χ ₁ and χ ₂ of the floating body 20 and the movable body 30, the following equation (8) is obtained.

However, D is expressed as follows.

By setting c ₁ =c ₂ =0, ignoring attenuation, and calculating Ω _s1 such that χ ₁ =0 from equation (8), the following equation (10) is obtained.

If equation (10) is solved for Ω _s1 , the following equation (11) is derived.

Equation (11) means that when the angular frequency of the displacement of the water surface W, that is, the excitation angular frequency for the floating body 20 takes the value of Equation (11), the response transfer function χ ₁ of the floating body 20 becomes 0. are doing. The following equation (12), which is obtained by rewriting equation (11) as a frequency, is called the cutoff frequency of the floating body 20.

FIG. 3 is a response diagram showing the vibration transmissibility of the heave vibration of the damped power generator 10 of FIG. 1, and is an example of calculation of the transfer functions χ ₁ and χ ₂ of the floating body 20 and the movable body 30. The solid line indicates the transfer function χ ₁ of the floating body 20, and the dashed line indicates the transfer function χ ₂ of the movable body 30. It can be seen that 0.47 Hz is the cutoff frequency f _s1 of the floating body 20, and the transfer function χ ₁ of the floating body 20 becomes small in the vicinity thereof. As a comparative example, FIG. 3 shows a transfer function χ of a floating body 20 of a general spar-type offshore wind power generation facility that does not have a damping power generation structure composed of a movable body 30, a conversion mechanism 40, and a device generator 50. ₁ is indicated by a two-dot chain line. In the range of 0.05 Hz to 0.5 Hz, which is the frequency range of waves in the natural world, the transfer function χ ₁ of the floating body 20 by the vibration damping power generation device 10 according to the present embodiment is similar to that of a general spar type offshore wind power generation facility. The transfer function χ ₁ of the floating body 20 is suppressed to be smaller than 1. In addition, since the difference between the transfer functions χ ₁ and χ ₂ between the floating body 20 and the movable body 30 is maintained in this frequency range, it can be seen that power generation by 50 is possible for the device power generation. In particular, a large amount of power generation can be obtained at the cutoff frequency _fs1 .

Further, the broken lines indicate transfer functions χ ₁ and χ ₂ in the case where the damped power generation device 10 according to the present embodiment does not have an inertial mass. In this case, the cutoff frequency f _s1 is expressed as the following equation (13) since the inertial mass m _s2 is 0 in equation (12).

Equation (13) means an inverse resonance point of a two-degree-of-freedom system, and indicates that the movable body 30 acts as a dynamic vibration absorber. From this, it can be interpreted that the inertial mass m _s2 has a function of adjusting the frequency of the anti-resonance point. As expressed by equation (2), the inertial mass m _s2 is the speed increase rate ε of the planetary gear transmission 14, the pitch between the female screw hole 41 and the male screw portion 42 as p, and the moment of inertia I of the rotor 56 of the device generator 50. is expressed as a function of Therefore, by adjusting the cut-off frequency f _s1 , the inertial mass m _s2 , the speed increase rate ε, and the moment of inertia I, it is possible to suppress the vibration of the floating body 20 and adjust the power generation amount in accordance with the wave frequency. In order to perform such adjustment, the conversion mechanism 40 according to this embodiment includes the flywheel 44 and transmission 45 described above. If the transmission 45 is a transmission with a variable speed increase rate, such as a CVT, it is also possible to flexibly adjust the cutoff frequency f _s1 in response to the frequency of waves.

As described above, according to the present embodiment, the movable body 30 arranged in the internal space 20S of the floating body 20 performs a relative translational movement in the X direction with respect to the floating body 20. This allows the conversion mechanism 40 to convert this relative translational movement into rotational movement. Therefore, the rotor 56 of the device generator 50 can rotate, and the device generator 50 can generate electricity. As a result, vibration of the floating body 20 can be suppressed, and the device generator 50 can generate electricity.

Also, according to this embodiment, device generator 50 includes a rotor 56 . Thereby, the vibration damping power generation device 10 can have an inertial mass element that reduces vibrations of the floating body 20. Therefore, the heave vibration applied to the floating body 20 can be suppressed, and damage to the wind power generation device 2 mounted on the floating body 20 can be suppressed. Further, the relative displacement between the floating body 20 and the movable body 30 can be increased, and the amount of power generated by the device generator 50 can be increased.

Moreover, according to this embodiment, the movable body 30, the conversion mechanism 40, and the device generator 50 can be arranged in the internal space 20S of the floating body 20. This makes it possible to install it on the floating body 20 of an existing offshore wind power generation facility that does not have a vibration damping power generation structure, and it can be easily retrofitted to a facility that has a vibration damping power generation structure. Moreover, the movable body 30, the conversion mechanism 40, and the device generator 50 can be protected from seawater existing outside the floating body 20, and reliability can be improved.

Further, according to the present embodiment, the conversion mechanism 40 includes a female threaded hole 41 having a central axis extending in the X direction, and a conversion rotation shaft 43 including a male threaded portion 42 that is screwed into the female threaded hole 41. . Thereby, the relative translational motion between the floating body 20 and the movable body 30 can be converted into a rotational motion of the male threaded portion 42 and the conversion rotation shaft 43. Therefore, the conversion mechanism 40 that converts relative translational movement into rotational movement can be easily configured.

Further, according to this embodiment, the conversion mechanism 40 includes a transmission 45 interposed between the conversion rotation shaft 43 and the rotor 56 of the device generator 50. Thereby, the rotational speed of the rotor 56 can be adjusted by the transmission 45, and the amount of power generated by the device generator 50 can be adjusted. Further, when the transmission 45 includes a gear, the speed increase rate, which is the rotational speed ratio of the conversion rotation shaft 43 and the rotor 56, can be adjusted by adjusting the number of teeth of the gear. Therefore, the vibration of the floating body 20 can be effectively suppressed, and the amount of power generated by the device generator 50 can be effectively increased.

Further, according to this embodiment, the device generator 50 is supported by the floating body 20. This allows the device generator 50 to perform translational movement in synchronization with the floating body 20. The relative translational motion between the device generator 50 and the floating body 20 and the movable body 30 is converted into a rotational motion by the conversion mechanism 40, so that the device generator 50 can generate electricity.

(Second embodiment)
Next, a vibration damping power generation device according to a second embodiment will be described using FIG. 4.

The second embodiment shown in FIG. 4 differs mainly from the first embodiment shown in FIGS. 1 to 3 in that the device generator is supported by a movable body. are the same. Note that in FIG. 4, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 4 is a schematic cross-sectional view showing a vibration damping power generation device according to a second embodiment.

As shown in FIG. 4, in this embodiment, the device generator 50 is supported by the movable body 30.

As shown in FIG. 4, floating body 20 includes an internal flange 24. As shown in FIG. Internal flange 24 is arranged within internal space 20S. Internal flange 24 is arranged between upper plate 22 and movable body 30. The internal flange 24 may be formed into a plate shape along the Y direction and the Z direction.

The movable body 30 is arranged within the internal space 20S. Movable body 30 includes a support flange 36. The support flange 36 according to this embodiment is provided at the lower part of the movable cylinder 31. The support flange 36 may be formed into a plate shape along the Y direction and the Z direction. The elastic body 70 may be connected to the bottom surface 23 of the internal space 20S and the support flange 36.

The female screw hole 41 of the conversion mechanism 40 according to this embodiment is formed in the internal flange 24. The female threaded hole 41 may be formed in the block 25 provided on the internal flange 24. The block 25 may be formed thicker than the internal flange 24. The female screw hole 41 passes through the block 25.

As mentioned above, the device generator 50 is supported by the movable body 30. As a result, the device generator 50 performs a translational movement in synchronization with the movable body 30, together with the above-mentioned male threaded portion 42, conversion rotation shaft 43, and the like.

The stator cylinder body 52 of the stator 51 is fixed to the support flange 36 of the movable body 30. In the example shown in FIG. 4, the stator cylindrical body 52 is not provided with the stator lower flange 54 shown in FIG. The support flange 36 of the movable body 30 also serves as the stator lower flange 54 shown in FIG. For this reason, a bearing 58a that supports the lower part of the generator rotating shaft 57 is provided on the support flange 36. A bearing 58b that supports the upper part of the generator rotating shaft 57 is provided on the internal flange 24 of the floating body 20. The transmission 45 may be supported by the upper flange 32 of the movable body 30. The generator rotating shaft 57 passes through the upper flange 32 and is connected to the transmission 45 .

As described above, according to the present embodiment, the device generator 50 is supported by the movable body 30. This allows the device generator 50 to perform translational movement in synchronization with the movable body 30. The relative translational motion between the floating body 20, the device generator 50, and the movable body 30 is converted into a rotational motion by the conversion mechanism 40, so that the device generator 50 can generate electricity. The dynamic model according to this embodiment is equivalent to the dynamic model according to the first embodiment shown in FIG. Therefore, vibration of the floating body 20 due to vibration of the water surface W can be suppressed, and the device generator 50 can be driven to generate electricity.

(Third embodiment)
Next, a vibration damping power generation device according to a third embodiment will be described using FIG. 5.

The third embodiment shown in FIG. 5 differs mainly in that the movable body floats on liquid stored in the internal space and is elastically coupled to the floating body by the liquid. This is substantially the same as the second embodiment shown. Note that in FIG. 5, the same parts as those in the second embodiment shown in FIG. 4 are given the same reference numerals, and detailed explanations will be omitted. FIG. 5 is a schematic cross-sectional view showing a vibration damping power generation device according to a third embodiment.

As shown in FIG. 5, in this embodiment, water (or seawater) as an example of liquid is stored in the internal space 20S of the floating body 20. The stored water will be referred to as a water seal 26 and will be described below.

Movable body 30 includes a bottom flange 37 . The bottom flange 37 is provided at the bottom of the movable cylinder 31. The interior space 30S of the movable body 30 is sealed to prevent water or the like from entering the interior space 30S from the outside. The internal space 30S is surrounded by the movable cylinder 31. The bottom flange 37 may be formed into a plate shape along the Y direction and the Z direction.

The device generator 50 according to this embodiment is supported by the support flange 36 of the movable body 30. The support flange 36 according to this embodiment is arranged above the bottom flange 37.

The movable body 30 is floating on sealed water 26 stored in the internal space 20S. The sealed water 26 stored in the internal space 20S is prevented from entering the internal space 30S of the movable body 30, as described above. The movable body 30 receives buoyancy from the water seal 26 in the internal space 20S.

The movable body 30 is elastically coupled to the floating body 20 by a water seal 26. To illustrate this, in FIG. 5, it can be assumed that the movable body 30 is elastically coupled to the floating body 20 by the elastic body 70 having a spring constant _k2 . Like the virtual elastic body 60, the elastic body 70 is composed of a buoyancy spring. The elastic body 70 according to the present embodiment does not indicate the presence of a spring member, but rather the movable body 30 is moved in the X direction by the buoyant force received from the sealed water 26 stored in the internal space 20S of the floating body 20. Supported.

The virtual elastic body 60 described above is configured by the buoyancy force that the floating body 20 receives. As a result, the spring constant k ₁ of the virtual elastic body 60 is smaller than that of a general coil spring, and the virtual elastic body 60 can tolerate a large displacement. When the spring constant _k2 of the elastic body 70 is large, it becomes difficult for the movable body 30 to perform relative translational motion with respect to the floating body 20, and the translational motion of the movable body 30 is integrated with the translational motion of the floating body 20. Cheap. In order to cause the movable body 30 to perform a relative translational movement with respect to the floating body 20, it is preferable that the spring constant k ₂ of the elastic body 70 is made as small as the spring constant k ₁ of the virtual elastic body 60. In this case, it is preferable that the elastic body 70 can tolerate large displacement.

In this embodiment, as described above, the movable body 30 is floating on the water seal 26 stored in the internal space 20S of the floating body 20, and the movable body 30 is elastically coupled to the floating body 20 by the water seal 26. ing. As a result, the elastic body 70 can be configured by the buoyant force that the movable body 30 receives from the water seal 26, and the spring constant _k2 of the elastic body 70 can be made small. Further, the elastic body 70 can tolerate large displacement.

Generally, when a rod-like structure with a cross-sectional area S [m ² ] is floating in a fluid with a density ρ [kg・m ² /s ² ], the spring constant k [N/m] acting on the rod-like structure by the fluid is is expressed as the following equation (14), where the gravitational acceleration is g [m/s ² ].

Since the floating body 20 is floating on water (or seawater), the density of the water seal 26 is approximately equal to the density of the water surrounding the floating body 20. Since the cross-sectional areas of the floating body 20 and the movable body 30 are similar, the spring constants k ₁ and k ₂ are set to approximately the same value. On the other hand, the spring constant _k2 can be adjusted to a desired value by adjusting the cross-sectional area of the movable body 30 (the part submerged in the water seal 26) or by adjusting the density of the water seal 26. can.

As described above, according to the present embodiment, the movable body 30 floats on the water seal 26 stored in the internal space 20S, and is elastically coupled to the floating body 20 by the water seal 26. Thereby, the spring constant _k2 of the elastic body 70 that elastically couples the floating body 20 and the movable body 30 can be easily reduced. Therefore, the movable body 30 can be easily translated relative to the floating body 20. As a result, the conversion mechanism 40 can suppress vibrations of the floating body 20 while converting relative translational motion into rotational motion, and the device generator 50 can generate power.

In addition, in this embodiment mentioned above, the example in which the device generator 50 was instructed to the movable body 30 was explained. However, the present embodiment is not limited to this, and the device generator 50 may be supported by the floating body 20. In this case, the female screw hole 41 is provided in the movable body 30.

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

In the fourth embodiment shown in FIG. 6, a gas chamber for storing gas is provided at the lower part of the movable body, and the movable body uses the liquid stored in the internal space and the gas stored in the gas chamber. The main difference is that the third embodiment is elastically connected to the floating body, and the other configurations are substantially the same as the third embodiment shown in FIG. Note that in FIG. 6, the same parts as those in the third embodiment shown in FIG. 5 are given the same reference numerals, and detailed explanations will be omitted. FIG. 6 is a schematic cross-sectional view showing a vibration damping power generation device according to a fourth embodiment.

As shown in FIG. 5, in this embodiment, a gas chamber 38 filled with gas is provided at the bottom of the movable body 30. The gas sealed in the gas chamber 38 is in contact with the sealed water 26 stored in the internal space 20S. More specifically, the bottom flange 37 of the movable body 30 is located above the lower end of the movable cylinder 31. The movable cylinder 31 protrudes below the bottom flange 37. This protruding portion and the bottom flange 37 define a movable body recess 39 that opens downward. The water seal 26 may enter the lower part of the movable body recess 39 . Gas is sealed in a portion of the movable body recess 39 above the water seal 26, and the water seal 26 and the gas are in contact with each other. The gas may be air.

The movable body 30 is elastically coupled to the floating body 20 by sealed water 26 stored in the internal space 20S of the floating body 20 and gas sealed in the gas chamber 38. In this case, the elastic body 70 can be configured as a spring in which a buoyancy spring that the movable body 30 receives from the water seal 26 and an air spring formed by the gas sealed in the gas chamber 38 are connected in series. By including the spring constant of the air spring in the spring constant of the elastic body 70, the spring constant of the elastic body 70 can be made even smaller.

As described above, according to the present embodiment, the gas chamber 38 filled with gas is provided at the lower part of the movable body 30. The movable body 30 is elastically coupled to the floating body 20 by sealed water 26 stored in the internal space 20S of the floating body 20 and gas sealed in the gas chamber 38. Thereby, the spring constant _k2 of the elastic body 70 that elastically couples the floating body 20 and the movable body 30 can be further reduced. Therefore, the movable body 30 can be easily translated relative to the floating body 20. As a result, the conversion mechanism 40 can convert relative translational motion into rotational motion, suppress vibration of the floating body 20, and allow the device generator 50 to generate electricity.

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

The fifth embodiment shown in FIG. 7 differs mainly in that the conversion mechanism includes a rack and a generator gear that interlocks with the rack and is connected to the rotor. This embodiment is substantially the same as the second embodiment shown in FIG. Note that in FIG. 7, the same parts as those in the second embodiment shown in FIG. 4 are designated by the same reference numerals, and detailed description thereof will be omitted. FIG. 7 is a schematic cross-sectional view showing a vibration damping power generation device according to a fifth embodiment.

As shown in FIG. 5, in this embodiment, the conversion mechanism 40 includes a rack rail 80 and a generator gear 81. The conversion mechanism 40 is arranged in the internal space 20S of the floating body 20.

Rack rail 80 is an example of a rack. The rack rail 80 is provided on the inner wall surface 21 of the floating body 20. The rack rail 80 is arranged at a position where it does not interfere with the roller 33 described above. Rack rail 80 extends in the X direction. Since the movable body 30 is prevented from rotating around the axis along the X direction by the guide rail described above, the rack rail 80 can mesh with the generator gear 81 .

The generator gear 81 may be supported by the upper flange 32 of the movable body 30. The generator gear 81 is rotatably attached to the upper flange 32 via a bearing (not shown). The generator gear 81 meshes with the rack rail 80 via a speed change gear 83, which will be described later, and is interlocked with the rack rail 80. Relative translational motion between the rack rail 80 and the generator gear 81 in the X direction is converted into rotational motion of the generator gear 81. Generator gear 81 may be coaxially connected to rotor 56 of device generator 50 .

The device generator 50 is supported by the movable body 30. As a result, the device generator 50 performs a translational movement in synchronization with the movable body 30 together with the above-mentioned generator gear 81 and the like. The device generator 50 may be supported on the upper flange 32 of the movable body 30. The device generator 50 is arranged in the internal space 20S of the floating body 20 and above the movable body 30. In the example shown in FIG. 7, the generator rotating shaft of device generator 50 extends in the Y direction. The apparatus generator 50 is different from the apparatus generator 50 shown in FIG. may have been done.

As shown in FIG. 7, conversion mechanism 40 according to this embodiment may include a transmission 82 interposed between rack rail 80 and generator gear 81. As shown in FIG. The transmission device 82 according to this embodiment may include a transmission gear 83. The generator gear 81 may interlock with the rack rail 80 with a speed change gear 83 interposed therebetween. The teeth of the speed change gear 83 mesh with the teeth of the rack rail 80 and also mesh with the teeth of the generator gear 81. The transmission 82 may be supported by the upper flange 32 of the movable body 30. The speed change gear 83 may be rotatably attached to the upper flange 32 via a bearing (not shown).

The number of teeth of the speed change gear 83 is different from the number of teeth of the generator gear 81. Due to this, the rotational speed of the speed change gear 83 and the rotational speed of the generator gear 81 are different. In the example shown in FIG. 7, the pitch circle radius of the speed change gear 83 is larger than the pitch circle radius of the generator gear 81. As a result, the number of teeth of the speed change gear 83 is greater than the number of teeth of the generator gear 81, and the speed change gear 83 can increase the rotation speed of the generator gear 81.

The damped power generation device 10 according to this embodiment may include a plurality of conversion mechanisms 40 and a plurality of device generators 50. The conversion mechanism 40 and the device generator 50 that correspond to each other may be arranged in pairs on the upper flange 32 of the movable body 30. One set of conversion mechanism 40 and device generator 50 and another set of conversion mechanism 40 and device generator 50 may be arranged apart from each other in the circumferential direction of interior space 20S, and may be placed along the central axis of interior space 20S. They may be arranged rotationally symmetrically with respect to each other. The central axis of the internal space 20S is an axis extending in the X direction, and may coincide with the central axis of the movable body 30. For example, when two sets of conversion mechanism 40 and device generator 50 are arranged on upper flange 32, each set may be arranged at 180° different positions when viewed in the X direction.

The adjustment weight 34 of the movable body 30 may be provided on the upper surface of the bottom flange 37. Although the planar shape of the adjustment weight 34 is arbitrary, it may be circular.

Here, using the module radius r of the transmission gear 83, the speed increase rate ε of the transmission 82, and the moment of inertia I of the rotor 56 of the device generator 50, the inertial mass m _s2 can be calculated using the following equation (15). It is expressed as follows.

The number “2” in the coefficient on the right side of equation (15) corresponds to the number of sets of conversion mechanism 40 and device generator 50. By replacing equation (2) above with equation (15), the dynamic handling is the same as in the first embodiment.

As described above, according to the present embodiment, the conversion mechanism 40 includes the rack rail 80 extending in the X direction, the generator gear 81 that is interlocked with the rack rail 80 and connected to the rotor 56 of the device generator 50, Contains. This allows the relative translational motion between the floating body 20 and the movable body 30 to be converted into rotational motion of the generator gear 81. Therefore, the conversion mechanism 40 that converts relative translational movement into rotational movement can be easily configured.

Further, according to this embodiment, the conversion mechanism 40 includes a transmission 82 interposed between the rack rail 80 and the generator gear 81. Thereby, the speed change device 82 can adjust the rotational speeds of the generator gear 81 and the rotor 56, and the amount of power generated by the device generator 50 can be adjusted. Further, when the transmission device 82 includes a speed change gear 83, by adjusting the number of teeth of the speed change gear 83, the speed increase rate, which is the rotational speed ratio of the speed change gear 83 and the generator gear 81, can be adjusted. Therefore, the vibration of the floating body 20 can be effectively suppressed, and the amount of power generated by the device generator 50 can be effectively increased.

(Sixth embodiment)
Next, a vibration damping power generation device according to a sixth embodiment will be described using FIGS. 8A and 8B.

In a sixth embodiment shown in FIGS. 8A and 8B, the device generator is supported on a floating body, the conversion mechanism includes a rope and a pulley connected to a rotor, and the rope is wound around the pulley. The main difference is that the second embodiment is configured differently, and the other configurations are substantially the same as the first embodiment shown in FIGS. 1 to 3. Note that in FIGS. 8A and 8B, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 8A is a schematic cross-sectional view showing the vibration damping power generation device according to the sixth embodiment, and FIG. 8B is a schematic view showing the main rope when viewed along arrow P1 in FIG. 8A.

As shown in FIG. 8A, the device generator 50 according to this embodiment is supported by the floating body 20. More specifically, the device generator 50 is arranged above the movable body 30 and above the internal space 20S of the floating body 20. The device generator 50 is supported by an internal flange 24 located in the internal space 20S. The movable body 30 is arranged below the internal flange 24.

As shown in FIGS. 8A and 8B, the conversion mechanism 40 includes a rope 90 and a pulley 91. The rope 90 is wound around a pulley 91 so as to make a U-turn in the X direction. Pulley 91 is connected to rotor 56 of device generator 50 .

On one side of the pulley 91, the rope 90 is supported by the movable body 30, and on the other side of the pulley 91, the rope 90 is supported by the floating body 20 with an elastic body 70 interposed therebetween. More specifically, the rope 90 includes a first end 90a and a second end 90b. The first end 90a is fixed to the upper surface of the upper flange 32 of the movable body 30. The second end portion 90b is fixed to the bottom surface 23 of the internal space 20S with the elastic body 70 interposed therebetween. That is, the elastic body 70 is connected to the second end 90b of the rope 90, and supports the movable body 30 with the rope 90 interposed therebetween. Tension based on the gravity of the movable body 30 and the elastic force of the elastic body 70 is loaded on the rope 90 .

As shown in FIG. 8B, the rope 90 extends upward from the first end 90a, passes through the through hole 24a provided in the internal flange 24, and reaches the pulley 91. The rope 90 is wrapped around the upper half of the pulley 91 and changes direction by 180 degrees (makes a U-turn). The rope 90 extends downward from the pulley 91, passes through the through hole 24b provided in the internal flange 24, and reaches the second end 90b.

Conversion mechanism 40 may include a transmission 45 interposed between pulley 91 and rotor 56 of device generator 50 . The transmission device 45 according to the present embodiment is interposed between the converting rotation shaft 43 to which a pulley 91 is connected and the rotor 56, and is configured to convert the rotational speed of the pulley 91 and transmit it to the rotor 56. It is configured. The transmission 45 may be, for example, a planetary gear transmission. The transmission 45 may be supported by a device generator 50.

The adjustment weight 34 of the movable body 30 may be provided on the upper surface of the bottom flange 37. Although the planar shape of the adjustment weight 34 is arbitrary, it may be circular.

As described above, since the rope 90 has tension, it can come into frictional contact with the pulley 91 and can rotate the pulley 91. Therefore, the relative translational motion between the floating body 20 and the movable body 30 is converted into a rotational motion of the pulley 91. The rotational motion of the pulley 91 is transmitted to the rotor 56 via the conversion rotation shaft 43 and the transmission 45, and the rotor 56 performs rotational motion. In this way, the device generator 50 generates electricity. In order to increase the frictional force of the rope 90 against the pulley 91, the rope 90 may be wound around the pulley 91 multiple times.

Here, using the radius r of the pulley 91, the speed increase rate ε of the transmission 45, and the moment of inertia I of the rotor 56 of the device generator 50, the inertial mass m _s2 is expressed as in the following equation (16). Ru.

By replacing equation (2) above with equation (16), the dynamic handling is the same as in the first embodiment.

As described above, according to the present embodiment, the device generator 50 is supported by the floating body 20, and the conversion mechanism 40 includes the rope 90 and the pulley 91 connected to the rotor 56 of the device generator 50. There is. The rope 90 is wound around a pulley 91 so as to make a U-turn in the X direction. The rope 90 is supported by the movable body 30 on one side with respect to the pulley 91, and the rope 90 is supported with the floating body 20 with the elastic body 70 interposed on the other side with respect to the pulley 91. This allows the relative translational motion between the floating body 20 and the movable body 30 to be converted into rotational motion of the pulley 91. Therefore, the conversion mechanism 40 that converts relative translational movement into rotational movement can be easily configured.

Further, according to this embodiment, the elastic body 70 is connected to the second end 90b of the rope 90. Thereby, an elastic force can be applied to the rope 90, and the floating body 20 and the movable body 30 can be elastically coupled.

Further, according to this embodiment, the conversion mechanism 40 includes a transmission 45 interposed between the pulley 91 and the rotor 56 of the device generator 50. Thereby, the rotational speed of the rotor 56 can be adjusted by the transmission 45, and the amount of power generated by the device generator 50 can be adjusted. Furthermore, when the transmission 45 includes a gear, the speed increase rate, which is the rotational speed ratio of the pulley 91 and the rotor 56, can be adjusted by adjusting the number of teeth of the gear. Therefore, the vibration of the floating body 20 can be effectively suppressed, and the amount of power generated by the device generator 50 can be effectively increased.

(Seventh embodiment)
Next, a vibration damping power generation device according to a seventh embodiment will be described using FIGS. 9A and 9B.

In the seventh embodiment shown in FIGS. 9A and 9B, the main point is that the conversion mechanism includes a movable pulley around which a rope is wound, and the movable pulley is connected to the floating body through an elastic body. However, the other configurations are substantially the same as the sixth embodiment shown in FIGS. 8A and 8B. Note that in FIGS. 9A and 9B, the same parts as those in the sixth embodiment shown in FIGS. 8A and 8B are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 9A is a schematic cross-sectional view showing the vibration damping power generation device according to the seventh embodiment, and FIG. 9B is a schematic view showing the main rope when viewed along arrow P2 in FIG. 9A.

As shown in FIG. 9A, conversion mechanism 40 according to this embodiment includes a movable pulley 92. As shown in FIG. The rope 90 is wound around a movable pulley 92 so as to make a U-turn in the X direction.

The movable pulley 92 is fixed to the bottom surface 23 of the internal space 20S with an elastic body 70 interposed therebetween. That is, the elastic body 70 is interposed between the movable pulley 92 and the floating body 20. The movable pulley 92 is movable in the X direction and can be translated relative to the floating body 20 and the movable body 30. In this way, the rope 90 is loaded with tension based on the gravity of the movable body 30 and the elastic force of the elastic body 70. In order to increase the frictional force of the rope 90 with respect to the movable pulley 92, the rope 90 may be wound around the movable pulley 92 multiple times. The movable pulley 92 may be connected to the elastic body 70 with a support member 93 interposed therebetween. The movable pulley 92 may be rotatably attached to the support member 93.

The second end 90b of the rope 90 according to this embodiment is fixed to the lower surface of the internal flange 24.

As shown in FIGS. 9A and 9B, the rope 90 extends upward from a first end 90a located on the upper surface of the movable body 30, passes through the through hole 24a provided in the internal flange 24, and reaches the pulley 91. There is. The rope 90 is wrapped around the upper half of the pulley 91 and makes a U-turn. The rope 90 extends downward from the pulley 91, passes through the through hole 24b provided in the internal flange 24, and reaches the movable pulley 92. The rope 90 is wrapped around the lower half of the movable pulley 92 and makes a U-turn. The rope 90 extends upward from the movable pulley 92 to reach a second end 90b located on the lower surface of the internal flange 24.

In FIG. 9A, the spring constant of the elastic body 70 is shown as 4k ₂ (=4×k ₂ ). _k2 is equivalent to the spring constant of the elastic body 70 shown in FIG. 1 and the like. That is, if the tension applied to the rope 90 is T, then the tension applied to the elastic body 70 from the rope 90 is 2T. Since the displacement of the movable pulley 92 is half of the relative displacement (=x ₁ - x ₂ ) between the floating body 20 and the movable body 30, considering the balance of forces acting on the movable pulley 92, the elastic body shown in FIG. 9A A spring constant of 70 can be expressed as _4k2 . As described in the third embodiment, the spring constant of the elastic body 70 is preferably a small value, and the elastic body 70 is preferably capable of allowing large displacement. The elastic body 70 according to this embodiment may have a larger spring constant than the elastic body 70 shown in FIG. 1, and may have a smaller displacement tolerance.

As described above, according to the present embodiment, the conversion mechanism 40 includes a movable pulley 92, and the rope 90 is wound around the movable pulley 92 so as to make a U-turn in the X direction. The movable pulley 92 is connected to the floating body 20 with an elastic body 70 interposed therebetween. As a result, even if the elastic body 70 has a relatively large spring constant, the floating body 20 and the movable body 30 can be moved in relative translation to suppress the vibration of the floating body 20, and the device generator 50 can generate electricity. be able to. Therefore, restrictions on the spring constant of the elastic body 70 can be reduced, and the elastic body 70 can be designed easily.

(Eighth embodiment)
Next, a vibration damping power generation device according to an eighth embodiment will be described using FIGS. 10A and 10B.

In the eighth embodiment shown in FIGS. 10A and 10B, the conversion mechanism includes a fixed pulley around which a rope is wound, the movable pulley includes a plurality of grooves around which the rope is wound, and the rope is movable. The main difference is that the seventh embodiment is wound around a pulley, a fixed pulley, and a movable pulley in this order, and the other configurations are substantially the same as the seventh embodiment shown in FIGS. 9A and 9B. Note that in FIGS. 10A and 10B, the same parts as those in the seventh embodiment shown in FIGS. 9A and 9B are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 10A is a schematic cross-sectional view showing the vibration damping power generation device according to the eighth embodiment, and FIG. 10B is a schematic view showing the main rope when viewed along arrow P3 in FIG. 10A.

As shown in FIG. 10A, conversion mechanism 40 according to this embodiment includes a fixed pulley 94. As shown in FIG. The rope 90 is wound around a fixed pulley 94 so as to make a U-turn in the X direction. The fixed pulley 94 is fixed to the lower surface of the internal flange 24 of the floating body 20 with a support member 95 interposed therebetween. The fixed pulley 94 may be rotatably attached to the support member 95. The support member 95 does not need to have a substantially elastic function. No elastic body is interposed between the fixed pulley 94 and the upper plate 22, and the fixed pulley 94 may translate in synchronization with the floating body 20.

As shown in FIGS. 10A and 10B, the rope 90 is wound around a movable pulley 92, a fixed pulley 94, and a movable pulley 92 in this order. The movable pulley 92 includes a plurality of grooves around which the rope 90 is wound. In this embodiment, movable pulley 92 includes two grooves, namely, a first groove 92a and a second groove 92b.

More specifically, the rope 90 that reaches the movable pulley 92 from the pulley 91 is wrapped around the lower half of the movable pulley 92 and makes a U-turn. At this time, the rope 90 is wound around the first groove 92a of the movable pulley 92. The rope 90 extends upward from the first groove 92a of the movable pulley 92 to reach the fixed pulley 94, and is wrapped around the upper half of the fixed pulley 94. The rope 90 extends downward from the fixed pulley 94 to the movable pulley 92 and is wrapped around the lower half of the movable pulley 92 again. At this time, the rope 90 is wound around the second groove 92b of the movable pulley 92. The rope 90 extends upward from the second groove 92b of the movable pulley 92 and reaches a second end 90b located on the lower surface of the internal flange 24. In this way, the rope 90 is wrapped around the movable pulley 92 twice. In order to increase the frictional force of the rope 90 with respect to the movable pulley 92, the rope 90 may be wound around the movable pulley 92 three or more times. In this case, the movable pulley 92 may include a number of grooves corresponding to the number of windings. In this way, the rope 90 can be wrapped around the movable pulley 92 multiple times.

In FIG. 10A, the spring constant of the elastic body 70 is shown as 16k ₂ (=16×k ₂ ). _k2 is equivalent to the spring constant of the elastic body 70 shown in FIG. 1 and the like. That is, if the tension applied to the rope 90 is T, then the tension applied to the elastic body 70 from the rope 90 is 4T. Since the displacement of the movable pulley 92 is 1/4 of the relative displacement between the floating body 20 and the movable body 30, considering the balance of forces acting on the movable pulley 92, the spring constant of the elastic body 70 shown in FIG. 10A is as follows. It can be expressed as 16k ₂ . Therefore, the elastic body 70 according to the present embodiment may have a larger spring constant than the elastic body 70 shown in FIG. 1, and may have a smaller displacement tolerance. Here, to generalize, if the number of times the rope 90 is wound around the movable pulley 92 is n times, the spring constant of the elastic body 70 is (2n) ² ×k ₂ .

As described above, according to the present embodiment, the conversion mechanism 40 includes a fixed pulley 94, and the rope 90 is wound around the fixed pulley 94 so as to make a U-turn in the X direction. The movable pulley 92 includes a plurality of grooves 92a and 92b, and the rope 90 is wound around the movable pulley 92, the fixed pulley 94, and the movable pulley 92 in this order. As a result, even if the elastic body 70 has a relatively large spring constant, the floating body 20 and the movable body 30 can be moved in relative translation to suppress the vibration of the floating body 20, and the device generator 50 can generate electricity. be able to. Therefore, restrictions on the spring constant of the elastic body 70 can be further reduced, and the elastic body 70 can be designed even more easily.

(Ninth embodiment)
Next, a vibration damping power generation device according to a ninth embodiment will be described using FIG. 11.

In a ninth embodiment shown in FIG. 11, the device generator is supported on a movable body, on one side relative to the pulley the rope is supported on the floating body, and on the other side relative to the pulley the rope The main difference is that the seventh embodiment is supported by a floating body with an elastic body interposed therebetween, and the other configurations are substantially the same as the seventh embodiment shown in FIGS. 9A and 9B. Note that in FIG. 11, the same parts as those in the seventh embodiment shown in FIGS. 9A and 9B are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 11 is a schematic cross-sectional view showing a vibration damping power generation device according to a ninth embodiment.

As shown in FIG. 11, a device generator 50 according to this embodiment is supported by a movable body 30. As shown in FIG. More specifically, the device generator 50 is disposed in the internal space 30S of the movable body 30 and supported by the bottom flange 37.

On one side of the pulley 91, the rope 90 is supported by the floating body 20, and on the other side of the pulley 91, the rope 90 is supported by the floating body 20 with an elastic body 70 interposed therebetween. More specifically, the first end 90a of the rope 90 is fixed to the lower surface of the upper plate 22 of the floating body 20. The second end portion 90b is fixed to the bottom surface 23 of the internal space 20S.

The movable pulley 92 is fixed to the lower surface of the upper plate 22 of the floating body 20 with an elastic body 70 interposed therebetween. In this way, the rope 90 is loaded with tension based on the gravity of the movable body 30 and the elastic force of the elastic body 70. In order to increase the frictional force of the rope 90 with respect to the movable pulley 92, the rope 90 may be wound around the movable pulley 92 multiple times. In this case, a fixed pulley 94 shown in FIG. 10A may be used.

The rope 90 extends downward from the first end 90a and reaches the pulley 91 through a through hole (not shown) provided in the upper flange 32. The rope 90 is wrapped around the lower half of the pulley 91 and makes a U-turn. The rope 90 extends upward from the pulley 91, passes through a through hole (not shown) provided in the upper flange 32, and reaches the movable pulley 92. The rope 90 is wrapped around the upper half of the movable pulley 92 and makes a U-turn. The rope 90 extends downward from the movable pulley 92 and reaches a second end 90b located on the bottom surface 23 of the internal space 20S.

As described above, according to the present embodiment, the device generator 50 is supported by the movable body 30, and the conversion mechanism 40 includes the rope 90 and the pulley 91 connected to the rotor 56 of the device generator 50. I'm here. The rope 90 is wound around a pulley 91 so as to make a U-turn in the X direction. A rope 90 is supported by the floating body 20 on one side with respect to the pulley 91, and on the other side with respect to the pulley 91, the rope 90 is supported by the floating body 20 with an elastic body 70 interposed therebetween. This allows the relative translational motion between the floating body 20 and the movable body 30 to be converted into rotational motion of the pulley 91. Therefore, the conversion mechanism 40 that converts relative translational movement into rotational movement can be easily configured.

In addition, in this embodiment mentioned above, the example where the rope 90 was wound around the movable pulley 92 was demonstrated. However, the present embodiment is not limited to this, and similarly to FIGS. 8A and 8B, one end of the rope 90 (for example, the The two ends 90b) may be connected to the elastic body 70.

(Tenth embodiment)
Next, a vibration damping power generation device and a floating platform device according to a tenth embodiment will be described using FIGS. 12 to 17.

The tenth embodiment shown in FIGS. 12 to 17 is mainly different in that the platform is supported by a plurality of vibration damping power generation devices, and the vibration damping power generation devices are arranged on both sides of the platform in the lateral direction with respect to the center of gravity. , the other configurations are substantially the same as the first embodiment shown in FIGS. 1 to 3. Note that in FIGS. 12 to 17, the same parts as those in the first embodiment shown in FIGS. 1 to 3 are denoted by the same reference numerals, and detailed description thereof will be omitted. FIG. 12 is a schematic cross-sectional view showing a floating platform device equipped with a vibration damping power generation device according to a tenth embodiment.

As shown in FIG. 12, the damped power generation device 10 applied to the floating platform device 100 according to the present embodiment is configured similarly to the damped power generation device 10 according to the first embodiment shown in FIG. Good too. However, the present invention is not limited to this, and vibration-damping power generation devices 10 according to other embodiments may be applied to the floating platform device 100 according to this embodiment.

Floating platform device 100 according to this embodiment includes a platform 110 and a plurality of vibration damping power generation devices 10 that support platform 110. The floating platform device 100 is located on the water, and the tower 3 of the offshore wind power generation facility 1 shown in FIG. 1 may be installed on the platform 110, for example. However, the present invention is not limited to this, and any equipment can be installed on the platform 110 as long as it is located on water.

The platform 110 may be supported by two damped power generation devices 10. The platform 110 may cover the two damped power generation devices 10 when viewed in the X direction. In the following, two damped power generation devices 10 will be referred to as a damped power generation device 10A and a damped power generation device 10B. Platform 110 may be formed into a plate shape along the Y direction and the Z direction.

Each floating body 20 is fixed to a platform 110. Each floating body 20 is configured to be able to translate in synchronization with the platform 110. Each floating body 20 may not include the top plate 22 shown in FIG. In this case, each internal space 20S may be covered with the platform 110 from above and sealed.

In FIG. 12, the spring constant of the virtual elastic body 60 corresponding to the vibration damping power generation device 10A is indicated by k _1a , and the spring constant of the virtual elastic body 60 corresponding to the vibration damping power generation device 10B is indicated by k _1b . ing. The spring constant of the elastic body 70 corresponding to the vibration damping power generation device 10A is indicated by k _2a , and the spring constant of the elastic body 70 corresponding to the vibration damping power generation device 10B is indicated by k _2b .

When the floating platform device 100 is viewed in the Y direction, the vibration damping power generation devices 10A and 10B may be arranged on both sides of the platform 110 in the lateral direction with respect to the center of gravity G. In other words, as shown in FIG. 12, the vibration damping power generation devices 10A and 10B are arranged on both sides of the center of gravity G in the Z direction when viewed in the Y direction. In the example shown in FIG. 12, the vibration damping power generation device 10A is arranged on the left side of the center of gravity G, and the vibration damping power generation device 10B is arranged on the right side of the center of gravity G. In this way, the two vibration damping power generation devices 10A and 10B may be arranged to sandwich the center of gravity G of the platform 110. The distance in the Z direction from the center of gravity G to each vibration damping power generation device 10A, 10B is indicated by b.

The floating platform device 100 according to this embodiment configured as described above is schematically represented by a dynamic model shown in FIG. 13. FIG. 13 is a diagram showing a dynamic model of the floating platform device 100 of FIG. 12.

Here, the dynamic model of the water platform device 100 is handled as a two-dimensional model in the XZ plane. That is, displacement is considered only in the X direction. It is assumed that the platform 110 is uniform in structure, and the two vibration damping power generation devices 10A and 10B have the same structure. As a result, the dynamic model according to this embodiment is treated as a two-dimensional problem within the XZ plane. In the following description, the suffix "a" is added to the reference numerals related to the damped power generator 10A, and the suffix "b" is added to the reference numerals related to the damped power generator 10B.

The vibration damping power generation devices 10A and 10B are each placed at a distance b from the origin O in the Z direction. The platform 110 is a rigid body, and the center of gravity G is located on the X axis extending from the origin O. Let M be the mass of the platform 110, and let J be the moment of inertia around the Y axis at the center of gravity G. Let m _1a be the mass of the floating body 20 of the vibration damping power generation device 10A, and let m _1b be the mass of the floating body 20 of the vibration damping power generation device 10B. The mass m _1a includes the mass of the members supported by the floating body 20 (conversion rotation shaft 43, transmission 45, etc.) among the conversion mechanism 40 corresponding to the vibration damping power generation device 10A, and the mass of the device generator 50, Also includes fluid effects such as added mass of water. Similarly, the mass m _1b includes the mass of the member supported by the floating body 20 and the mass of the device generator 50 in the conversion mechanism 40 corresponding to the vibration damping power generation device 10B, as well as fluid effects such as the additional mass of water. Also includes. The masses m _1a and m _1b are connected to the water surfaces W _a and W _b , respectively, via a virtual elastic body 60 due to buoyancy. The spring constants of the virtual elastic body 60 are expressed by k _1a and k _1b . Attenuation due to buoyancy is represented by c _1a and c _1b . On the other hand, the masses m _1a and m _1b are connected to the mass M and the moment of inertia J of the platform 110 via spring constants k _2a and k _2b of the elastic body 70. c _2a and c _2b represent attenuation. m _s2a and m _s2b represent inertial masses. Since the two damping power generation devices 10A and 10B have the same structure, m _1a = m _1b = m, k _1a = k _1b = k ₁ , c _1a = c _1b = c ₁ , m _s2a = m _s2b = m _s2. , k _2a = k _2b = k ₂ , and c _2a = c _2b = c ₂ .

Assuming that the wavelength of the wave is sufficiently long compared to the length of the platform 110, the water surfaces W _a and W _b maintain a plane, and the translational displacement in the X direction is expressed as X ₀ and the rotational displacement around the Y axis is expressed as Θ ₀ . . If Θ ₀ is minute, the translational displacements X _a and X _b of the water surfaces W _a and W _b can be expressed as follows using X ₀ and Θ ₀ .

Let x ₀ be the translational displacement in the X direction at the center of gravity G of the platform 110 . Let the rotational displacement around the Y-axis be θ ₀ . If θ ₀ is minute, the translational displacements x _2a and x _2b of the platform 110 in the X direction are expressed as follows.

The translational displacements of the masses m _1a and m _1b of the movable body 30 in the X direction are respectively x _1a and x _1b , the mass of the platform 110 is M, and the polar moment of inertia around the center of gravity G is J. It is assumed that the relationship between the polar moment of inertia J and the mass M is expressed in the form of equation (21) using an equivalent dimension d.

The equation of motion of the dynamic model shown in FIG. 13 is expressed as the following equation.
However, β is expressed as follows.

In order to calculate the response, equation (22) is changed to the following matrix format.

The mass matrix [M], damping matrix [C], and stiffness matrix [K] in Equation (24) are each expressed as follows.

The displacement vector x in equation (24) is expressed as in equation (28) below, and the external force vector F is expressed as in equation (29) below.

Here, in order to obtain the frequency response, the external force vector F in equation (29) is
Assume that However, t is time and Ω is the angular frequency. The external force vector F in equation (30) is expressed as follows.

Corresponding to equation (29), the response x is
By substituting into equation (24) and rearranging, the following equation is obtained.

By solving equation (33), response x can be obtained from equation (32).

Here, for simplicity, β is set as follows.
That is,
Considering the case where the equation (22) is rewritten as the equation (37).

Comparing equation (22) and equation (37), in equation (22) x _1a , x _2a , x _1b , x _2b are coupled, but in equation (37) x _1a , x _2a and x _1b , x _2b are each coupled, and the set of x _1a , x _2a and the set of x _1b , x _2b are not coupled. Therefore, the four-degree-of-freedom system in FIG. 13 can be considered as being separated into two sets of two-degree-of-freedom systems: x _1a , x _2a and x _1b , x _2b . This is equivalent to the fact that the system shown by the dynamical model in FIG. 13 can be separated into two systems shown by the dynamical model in FIG. 2. It should also be noted that the two sets of equations (37) are identical in form to equation (3). In equation (37), M/2 can be replaced with m _2a for the set x _1a , x _2a , and m _2b for the set x _1b , x _2b , and each set can have the same form as equation (3). It can be understood. That is, the damped power generation device 10A and the damped power generation device 10B independently block vibration propagation from the displacements X _a and X _b of the water surfaces W _a and W _b to the displacements x _{2 a} and x _{2 b} of the platform 110, respectively. means. Making the assumption of Equation (36) not only simplifies the mathematical expression, but also allows heave vibration and pitching vibration to be treated independently, which has a great advantage in terms of design.

When damping is ignored, the cut-off frequency of the floating body 20 is expressed as follows from the frequency response in the same way as Equation (12).

In equation (38), the frequency response at x _2a and x _2b can be theoretically zero. From this, it was analytically confirmed that the vibration damping power generation devices 10A and 10B block the vibration propagation from the translational displacements X ₁ and X ₂ of the water surfaces W _a and W _b to the translational displacements x _2a and x _2b of the platform 110. can do.

The response calculation results are shown in FIGS. 14 and 15. FIG. 14 is a response diagram showing the vibration transmission rate of heave vibration, and FIG. 15 is a response diagram showing the vibration transmission rate of pitching vibration. In FIGS. 14 and 15, the left side shows the response of the damped power generator 10A, and the right side shows the response of the damped power generator 10B. Both amplitudes are designed to be the same as in FIG. 3. The solid lines are the responses of the transfer functions χ _1a and χ _1b of the floating body 20, and the dash-dotted lines are the responses of the transfer functions χ _2a and χ _2b of the movable body 30, respectively. It can be seen that 0.47 Hz is the cutoff frequency f _s1 of the floating body 20, and the transfer functions χ _1a and χ _1b of the floating body 20 become small in the vicinity thereof. For comparison, the transfer functions χ _1a and χ _1b of the floating body 20 without the vibration-damping power generation structure are shown by two-dot chain lines. In the present embodiment, the transfer functions χ _1a and χ _1b of the floating body 20 according to the present embodiment do not have a vibration damping power generation structure in the frequency range of 0.05 Hz to 0.5 Hz, which is the frequency range of waves in the natural world. It is designed to be suppressed to a level smaller than the actual case.

On the other hand, focusing on the phase, in the heave vibration of FIG. 14, the damped power generators 10A and 10B are in the same phase, whereas in the pitching vibration of FIG. 15, the damped power generator 10A is in the same phase as the damped power generator 10A. , the phase is shifted by 180°. That is, the phase relationship between the vibration damping power generation devices 10A and 10B is reversed. This is because the translational displacements X ₁ and X ₂ of the water surfaces W _a and W _b are in opposite phases in pitching vibration (X ₀ =0).

With such a configuration, the vibrations of the displacements x _1a and x _1b are suppressed, and at the same time, the heave vibration of the platform 110 and the pitching vibration, which is rotational vibration around the Y axis (the axis perpendicular to the plane of the paper in FIG. 12), are suppressed. can do.

As described above, according to the present embodiment, when viewed in at least one direction (for example, the Y direction) perpendicular to the X direction, vibration damping power generation is provided on both sides of the center of gravity G of the platform 110 in the Z direction. Devices 10A and 10B are arranged. As a result, pitching vibration, which is rotational vibration around the Y-axis, can be suppressed, and damage to the wind power generation device 2 mounted on the platform 110 can be suppressed. Here, the pitching vibration can generate a large stress in the tall tower building 3 and vibrate the wind power generator 2 with a large amplitude. Generally, even when the waves are small, the pitching vibration may have an inclination of more than 5 degrees, and the influence on the tower 3 and the wind power generator 2 cannot be said to be small. On the other hand, according to the present embodiment, as described above, pitching vibration can be effectively suppressed, and thus propagation of pitching vibration to wind power generator 2 can be effectively suppressed. Therefore, damage to the wind power generator 2 can be suppressed. In particular, according to this embodiment, both the above-described heave vibration and pitching vibration responses of platform 110 can be suppressed at the same time.

In addition, in the present embodiment described above, for the sake of simplicity, the dynamic model of the floating platform device 100 is treated as a two-dimensional problem within the XZ plane. However, the present embodiment is not limited to this.

For example, on water, in addition to pitching vibration, rolling vibration, which is rotational vibration around the Z-axis, also occurs, so this rolling vibration may be suppressed. For this reason, as shown in FIG. 16, when viewed in the X direction, the damping power generation devices 10C and 10D may be arranged symmetrically with respect to the damping power generation devices 10A and 10B, respectively, with the center of gravity G between them. In this case, platform 110 is supported by four vibration damping power generation devices 10A to 10D.

More specifically, as shown in FIG. 16, the four vibration damping power generation devices 10A to 10D are arranged so as to surround the center of gravity G of the platform 110 when viewed in the X direction. In the example shown in FIG. 16, the center of gravity G of the platform 110 is located at the center of a square formed by connecting the centers of the four vibration damping power generation devices 10A to 10D. The damped power generation device 10A and the damped power generation device 10C are lined up along the Y direction, and the damped power generation device 10B and the damped power generation device 10D are lined up along the Y direction. The damped power generation device 10A and the damped power generation device 10B are lined up along the Z direction, and the damped power generation device 10C and the damped power generation device 10D are lined up along the Z direction.

When the floating platform device 100 configured as described above is viewed in the Y direction, the vibration damping power generation devices 10A to 10D are arranged on both sides of the platform 110 in the lateral direction with respect to the center of gravity G. In other words, as shown in FIG. 12, the vibration damping power generation devices 10A and 10B are arranged on both sides in the Z direction when viewed in the Y direction. When viewed from arrow P4 in FIG. 16, the vibration damping power generation device 10A is arranged on the left side of the center of gravity G, and the vibration damping power generation device 10B is arranged on the right side of the center of gravity G. A damped power generator 10C is arranged behind the damped power generator 10A shown in FIG. 12, and a damped power generator 10D is arranged behind the damped power generator 10B. Alternatively, for example, two vibration damping power generation devices 10A and 10D are arranged on both sides in the Y direction when viewed in the Z direction. When viewed from arrow P5 in FIG. 16, the vibration damping power generation device 10D is arranged on the left side of the center of gravity G, and the vibration damping power generation device 10A is arranged on the right side of the center of gravity G. In this way, when viewed from at least one of the directions orthogonal to the X direction, even if one or more vibration damping power generation devices 10A to 10D are arranged on each side of the center of gravity G in the lateral direction, good. When viewed from all directions perpendicular to the X direction, the vibration damping power generation device may be arranged on both sides of the center of gravity G in the lateral direction.

Alternatively, for example, as shown in FIG. 17, the three vibration damping power generation devices 10A, 10B, and 10C may be arranged at the vertices of an equilateral triangle when viewed in the X direction. In this case, platform 110 is supported by three vibration damping power generation devices 10A to 10C. The center of gravity G of the platform 110 may be located at the center of this equilateral triangle.

In the example shown in FIG. 17, vibration damping power generation devices 10A and 10B are arranged on both sides in the Z direction when viewed along arrow P6 (corresponding to the Y direction). The vibration damping power generation device 10A is arranged on the left side of the center of gravity G, and the vibration damping power generation device 10B is arranged on the right side of the center of gravity G. In the example shown in FIG. 17, the damped power generator 10C is arranged at a position between the damped power generator 10A and the damped power generator 10B.

When the platform 110 is supported by three or more vibration-damping power generation devices, the heave vibration, pitching vibration, and rolling vibration of the platform 110 can be simultaneously suppressed by arranging them in a planar manner as described above.

According to the embodiments described above, vibration can be suppressed and power generation can be performed.

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 partially combine these embodiments as appropriate within the scope of the gist of the present invention.

10: Vibration control power generation device, 20: Floating body, 20S: Internal space, 26: Water seal, 30: Movable body, 38: Gas chamber, 40: Conversion mechanism, 41: Female threaded hole, 42: Male threaded part, 43: Conversion rotation shaft, 45: transmission, 50: device generator, 56: rotor, 70: elastic body, 80: rack rail, 81: generator gear, 82: transmission, 90: rope, 90a: first end, 90b: second end, 91: pulley, 92: movable pulley, 92a: first groove, 92b: second groove, 94: fixed pulley, 100: floating platform device, 110: platform

Claims (16)

a floating body including an internal space;
a movable body disposed in the internal space, the movable body being elastically coupled to the floating body and capable of relative translational movement in a first direction with respect to the floating body;
a conversion mechanism that converts relative translational motion between the floating body and the movable body into rotational motion;
A device generator for generating electricity, including a rotor that rotates with the rotational motion converted by the conversion mechanism;
A vibration-damping power generation device equipped with The conversion mechanism is a conversion rotation shaft including a female threaded hole having a central axis extending in the first direction and a male threaded part screwed into the female threaded hole, the conversion rotating shaft extending in the first direction and connected to the rotor. The vibration damping power generation device according to claim 1, further comprising: a converting rotation shaft having a vibration damping function. The vibration damping power generation device according to claim 2, wherein the conversion mechanism includes a transmission interposed between the conversion rotation shaft and the rotor. The damped power generation device according to any one of claims 1 to 3, wherein the device generator is supported by the floating body. The vibration damping power generation device according to any one of claims 1 to 3, wherein the device generator is supported by the movable body. The movable body floats on a liquid stored in the internal space,
the movable body is elastically coupled to the floating body by the liquid;
The vibration damping power generation device according to any one of claims 1 to 3. A gas chamber is provided at a lower part of the movable body, and the gas chamber is filled with gas that comes into contact with the liquid stored in the internal space.
the movable body is elastically coupled to the floating body by the liquid and the gas;
The vibration damping power generation device according to claim 6. The vibration damping power generation device according to claim 1, wherein the conversion mechanism includes a rack extending in the first direction, and a generator gear interlocking with the rack and connected to the rotor. The conversion mechanism includes a transmission interposed between the rack and the generator gear.
The vibration damping power generation device according to claim 8. the device generator is supported on the floating body;
The conversion mechanism includes a rope and a pulley connected to the rotor,
The rope is wound around the pulley so as to make a U-turn in the first direction,
The rope is supported by the movable body on one side with respect to the pulley, and the rope is supported with the floating body with an elastic body interposed on the other side with respect to the pulley.
The vibration damping power generation device according to claim 1. The device generator is supported by the movable body,
The conversion mechanism includes a rope and a pulley connected to the rotor,
The rope is wound around the pulley so as to make a U-turn in the first direction,
The rope is supported by the floating body on one side with respect to the pulley, and the rope is supported by the floating body with an elastic body interposed on the other side with respect to the pulley.
The vibration damping power generation device according to claim 1. the elastic body is connected to one end of the rope;
The vibration damping power generation device according to claim 10 or 11. The conversion mechanism includes a movable pulley around which the rope is wound so as to make a U-turn in the first direction;
The movable pulley is connected to the floating body with the elastic body interposed therebetween.
The vibration damping power generation device according to claim 10 or 11. The conversion mechanism includes a fixed pulley connected to the floating body and around which the rope is wound so as to make a U-turn in the first direction,
The movable pulley includes a plurality of grooves around which the rope is wound,
The rope is wound around the movable pulley, the fixed pulley, and the movable pulley in this order.
The vibration damping power generation device according to claim 13. The vibration damping power generation device according to claim 10 or 11, wherein the conversion mechanism includes a transmission interposed between the pulley and the rotor. A floating platform device located on water,
platform and
A plurality of vibration damping power generation devices according to any one of claims 1, 8, 10 and 11 supporting the platform,
A floating platform device, wherein the vibration damping power generation device is disposed on both sides of the platform in a lateral direction with respect to the center of gravity when viewed in at least one direction perpendicular to the first direction.

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