Water platform equipment

Abstract

To provide a sea-based platform device which can restrain vibration and can generate electric power by converting vibration energy into electric energy.SOLUTION: A sea-based platform device according to an embodiment includes a platform, and a plurality of vibration cut-off mechanisms supporting the platform. The vibration cut-off mechanism includes a floating body floating on water, and a first power generation mechanism. The floating body is elastically connected to the platform so as to perform a relative translational motion in a first direction with respect to the platform. The first power generation mechanism generates electric power by converting the relative translational motion between the platform and the floating body into rotational motion. When viewed in at least one direction of directions orthogonal to the first direction, the vibration cut-off mechanism is disposed in lateral direction both sides with respect to a center of gravity of the platform.SELECTED DRAWING: Figure 1

Description

[Technical Field]

[0001] This embodiment relates to a floating platform device. [Background technology]

[0002] Offshore wind power generation, which involves generating electricity at sea, has the advantage of being able to generate power using the stable winds at sea. In deep waters, it is difficult to fix wind turbine facilities to the seabed by constructing foundations, so floating offshore wind power generation is considered one of the effective implementation methods.

[0003] In floating offshore wind power facilities, a floating structure is erected on a floating platform on the ocean, and a tower is built on top of this floating structure. Wind turbines are mounted at the top of the tower. The floating structure is subjected to rocking motion by waves, imposing significant vibrational loads on the tower and wind turbines. These vibrational loads can cause damage to the system's equipment.

[0004] Vibration control technology, which suppresses vibrations in structures, is an important technology in ensuring the reliability of structures. Dynamic vibration absorbers or active mass dampers (AMDs) are typical examples of vibration control technology. In addition, a technology has been developed in which a separately installed drive weight is interposed between two structures as an inertial connection element to absorb the relative motion between them. In this case, vibration propagation from one structure to the other can be suppressed.

[0005] Incidentally, a technology has also been developed that converts vibration energy into electrical energy by generating electricity from vibration energy. Devices that embody this technology are sometimes called vibration power generation devices. In vibration power generation devices, vibration damping and power generation can be achieved simultaneously by absorbing vibration energy and generating electricity. However, because vibration energy is converted into electrical energy and vibration is suppressed, the amount of energy allocated to power generation may decrease. As a result, the power output may decrease. In other words, vibration energy and electrical energy converge at an equilibrium point, making it difficult to obtain sufficient power.

[0006] Wave power generation devices that utilize the oscillation of ships have been developed as vibration power generation devices. Wave power generation devices are an example of technology that uses a generator in combination with an active vibration damping device of the AMD type. More specifically, wave power generation devices are equipped with a generator that converts the oscillation motion of the AMD's drive weight into power generation energy. The damping constant of the generator is set so that the power generation energy is greater than the control energy required to drive the drive weight. Therefore, power generation can be efficiently performed using the wave energy absorbed by driving the drive weight. For example, the damping constant of the generator is set so that the control energy is 1 / 3 of the power generation energy. In other words, the control energy is suppressed in order to obtain power generation energy, and there is a trade-off relationship between power generation and vibration damping.

[0007] Thus, conventional vibration damping devices and vibration power generation devices both have a drive weight separate from the structure receiving the vibration, and their basic principle is to convert the kinetic energy of the drive weight into vibration damping or electrical energy. For this reason, it has been difficult to achieve both vibration damping and vibration power generation simultaneously. [Prior art documents] [Patent Documents]

[0008] [Patent Document 1] Patent No. 4002899 [Patent Document 2] Patent No. 5695991 [Overview of the project] [Problems that the invention aims to solve]

[0009] The embodiment was made with these points in mind, and aims to provide a floating platform device that can suppress vibrations and convert vibration energy into electrical energy to generate electricity. [Means for solving the problem]

[0010] The floating platform device according to this embodiment is a device located on the water. The floating platform device comprises a platform and a plurality of vibration isolation mechanisms that support the platform. The vibration isolation mechanism includes a floating body that floats on the water and a first power generation mechanism. The floating body is elastically coupled to the platform and is capable of relative translational motion with respect to the platform in a first direction. The first power generation mechanism generates electricity by converting the relative translational motion between the platform and the floating body into rotational motion. The vibration isolation mechanisms are arranged on both sides of the platform's center of gravity in the lateral direction when viewed in at least one direction perpendicular to the first direction.

[0011] The floating platform device according to this embodiment is a device located on the water. The floating platform device comprises a platform and a plurality of vibration isolation mechanisms that support the platform. The vibration isolation mechanism comprises an intermediate structure, a floating body that floats on the water, and a second power generation mechanism. The intermediate structure is elastically coupled to the platform and is capable of relative translational motion with respect to the platform in a first direction. The floating body is elastically coupled to the intermediate structure and is capable of relative translational motion with respect to the intermediate structure in a first direction. The second power generation mechanism generates electricity by converting the relative translational motion between the platform and the intermediate structure into rotational motion. The vibration isolation mechanisms are arranged on both sides of the platform's center of gravity in the lateral direction when viewed in at least one direction perpendicular to the first direction. [Effects of the Invention]

[0012] According to this embodiment, vibrations can be suppressed, and vibration energy can be converted into electrical energy to generate electricity. [Brief explanation of the drawing]

[0013] [Figure 1] Figure 1 shows an example of an offshore wind power generation facility to which the floating platform device according to the first embodiment is applied. [Figure 2] Figure 2 is a schematic longitudinal cross-sectional view showing the floating platform device in the first embodiment, and is a cross-sectional view along line BB in Figure 3, which will be described later. [Figure 3] Figure 3 is a cross-sectional view along line AA showing the floating platform device in Figure 2. [Figure 4] Figure 4 shows the dynamic model of the floating platform device shown in Figure 2. [Figure 5] Figure 5 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 2. [Figure 6] Figure 6 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 2. [Figure 7] Figure 7 is a schematic vertical outline view showing a typical floating platform device as a comparative example, and is a cross-sectional view along the DD line in Figure 8, which will be described later. [Figure 8] Figure 8 is a cross-sectional view along line CC showing the floating platform device in Figure 7. [Figure 9] Figure 9 shows the dynamic model of the floating platform device shown in Figure 7. [Figure 10] Figure 10 is a schematic longitudinal cross-sectional view showing a floating platform device in a second embodiment. [Figure 11] Figure 11 is a cross-section along the EE line showing the floating platform device in Figure 10. [Figure 12] Figure 12 is a schematic longitudinal cross-sectional view showing a floating platform device in a third embodiment. [Figure 13]Figure 13 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 12. [Figure 14] Figure 14 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 12. [Figure 15] Figure 15 is a schematic longitudinal cross-sectional view showing a floating platform device in the fourth embodiment. [Figure 16] Figure 16 is a schematic longitudinal cross-sectional view showing a floating platform device in the fifth embodiment. [Figure 17] Figure 17 is a schematic longitudinal cross-sectional view showing a floating platform device in the sixth embodiment, and is a cross-sectional view along the GG line shown in Figure 18, which will be described later. [Figure 18] Figure 18 is a cross-sectional view along the FF line showing the floating platform device in Figure 17. [Figure 19] Figure 19 shows the dynamic model of the floating platform device shown in Figure 17. [Figure 20] Figure 20 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 17. [Figure 21] Figure 21 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 17. [Figure 22] Figure 22 is a schematic longitudinal cross-sectional view showing a floating platform device in the seventh embodiment. [Figure 23] Figure 23 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 22. [Figure 24] Figure 24 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 22. [Figure 25] Figure 25 is a schematic longitudinal cross-sectional view showing a floating platform device in the eighth embodiment. [Figure 26] Figure 26 shows the dynamic model of the floating platform device shown in Figure 25. [Figure 27]Figure 27 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 25. [Figure 28] Figure 28 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 25. [Figure 29] Figure 29 is a schematic vertical outline view showing a floating platform device in the ninth embodiment. [Figure 30] Figure 30 is a schematic plan view showing the floating platform device shown in Figure 29. [Figure 31] Figure 31 is a cross-sectional view along the HH line showing the vibration isolation mechanism of Figure 30. [Figure 32] Figure 32 is a schematic longitudinal cross-sectional view showing a floating platform device in the tenth embodiment. [Figure 33] Figure 33 shows the dynamic model of the floating platform device shown in Figure 32. [Figure 34] Figure 34 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 32. [Figure 35] Figure 35 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 32. [Figure 36] Figure 36 is a schematic longitudinal cross-sectional view showing a floating platform device in the eleventh embodiment. [Figure 37] Figure 37 is a response diagram showing the vibration transmission coefficient of the heave vibration of the floating platform device shown in Figure 36. [Figure 38] Figure 38 is a response diagram showing the vibration transmission coefficient of the pitching vibration of the floating platform device shown in Figure 36. [Modes for carrying out the invention]

[0014] The floating platform device according to an embodiment of the present invention will be described below with reference to the drawings.

[0015] (First Embodiment) The floating platform device according to this embodiment will be explained using Figures 1 to 9. Here, an example of a floating platform device applied to a spar-type offshore wind power generation facility will be described. However, the application examples of the floating platform device are not limited to this.

[0016] First, an offshore wind power generation facility 1 to which the floating platform device according to this embodiment is applied will be described using Figure 1. Figure 1 shows an example of an offshore wind power generation facility to which the floating platform device according to this embodiment is applied.

[0017] The offshore wind power generation facility 1 shown in Figure 1 comprises a wind turbine 2, a tower 3 supporting the wind turbine 2, and a floating platform device 10 located below the tower 3 and supporting the tower 3. The floating platform device 10 is located on the water.

[0018] The tower structure 3 extends vertically upward from the floating platform device 10 and is formed in a columnar shape. The wind turbine 2 is attached to the upper end of the tower structure 3. The wind turbine 2 is supported by the floating platform device 10 via the tower structure 3.

[0019] The wind power generation device 2 includes a nacelle 2a and a power generation rotor 2b. The nacelle 2a is supported so as to be rotatable around an axis that extends perpendicularly to the tower 3 according to the wind direction, etc. The power generation rotor 2b is rotatably mounted on the nacelle 2a. A wind turbine generator 2c, which generates electricity by the rotation of the power generation rotor 2b, is built into the nacelle 2a. The power generation rotor 2b includes a plurality of blades 2d.

[0020] Such an offshore wind power facility 1 vibrates vertically in response to the excitation force of waves. This vibration is also called heave vibration. In addition, the offshore wind power facility 1 vibrates by oscillating around a horizontally extending axis in response to the excitation force of waves. This vibration is also called pitching vibration.

[0021] Next, the floating platform device 10 according to this embodiment will be described with reference to Figures 2 and 3. Figure 2 is a longitudinal cross-sectional view showing the floating platform device 10 in this embodiment. Figure 3 is a cross-sectional view along line AA in Figure 2, which is a schematic plan cross-sectional view of the floating platform device 10.

[0022] In the following explanation, we define and describe the XYZ three-dimensional Cartesian coordinate system as shown in Figures 2 and 3. The X-axis extends vertically, and the X-direction is an example of the first direction. The Y-axis extends horizontally, and is an example of the second direction. The Y-direction corresponds to the direction perpendicular to the plane of the paper in Figure 2. The Z-axis extends horizontally, and is an example of the third direction. The Z-axis is perpendicular to both the X-axis and the Y-axis. The Z-direction corresponds to the horizontal direction of the paper in Figure 2.

[0023] As shown in Figures 2 and 3, the floating platform device 10 according to this embodiment comprises a platform 20 and a plurality of vibration isolation mechanisms. In this embodiment, an example in which the platform 20 is supported by four vibration isolation mechanisms 30A to 30D will be described.

[0024] As shown in Figure 2, the platform 20 includes a platform body 21 and a first columnar body 22. In the example shown in Figures 2 and 3, for simplification, the planar shape of the platform body 21 is square and the height of the platform body 21 is uniform. The first columnar body 22 extends downward in the X direction from the platform body 21. The first columnar body 22 may be formed in a cylindrical shape so as to extend in the X direction. The first columnar body 22 is inserted into a first cavity 41, which will be described later. The platform 20 according to this embodiment includes four first columnar bodies 22. For convenience, as shown in Figure 3, the four first columnar bodies 22 are arranged so as to be at the vertices of a square when viewed in the X direction.

[0025] Similar to the first columnar body 22, the four vibration isolation mechanisms 30A to 30D are arranged at the vertices of a square when viewed in the X direction. The vibration isolation mechanisms 30A to 30D are arranged along the Y and Z directions. Each of the vibration isolation mechanisms 30A to 30D in this embodiment includes a floating body 40 and a plurality of first power generation mechanisms 50A and 50B. In this embodiment, an example in which each vibration isolation mechanism 30A to 30D includes two first power generation mechanisms 50A and 50B will be described. However, this is not the only example, and the number of first power generation mechanisms included in each vibration isolation mechanism 30A to 30D may be one, three or more, or any other number.

[0026] The floating body 40 is configured to float on water. The floating body 40 is elastically coupled to the platform 20 and is configured to be able to move relative to the platform 20 in the X direction. The floating body 40 may be able to move relative to the platform 20 in the vertical direction and in a direction perpendicular to the water surface. As shown in Figures 2 and 3, the floating body 40 may be formed in a cylindrical shape so as to extend in the X direction. A portion of the floating body 40 is located below the water surface and is immersed in the surrounding water. The water surface is indicated by the symbol W in Figure 2, etc. The floating body 40 is configured to withstand water pressure.

[0027] The lower part of the floating body 40 is provided with a weight section (not shown) filled with a heavy object such as concrete or ballast water. This lowers the center of gravity of the floating body 40 and balances the buoyancy of the floating body 40 with the gravity of the offshore wind power generation facility 1. In this way, the stability of the floating body 40 floating on the water is enhanced.

[0028] As described above, the floating body 40 floats on water. Therefore, since the floating body 40 vibrates under the excitation force of the waves, it can be considered to be elastically coupled to the stationary frame. To illustrate this, in Figure 2, the floating body 40 is elastically coupled to the stationary frame by a first virtual elastic body 60 having a spring constant k2. The first virtual elastic body 60 is composed of a buoyancy spring. In Figure 2, the spring constant of the first virtual elastic body 60 corresponding to the vibration isolation mechanism 30A is k 2a As shown, the spring constant of the first virtual elastic body 60 corresponding to the vibration isolation mechanism 30B is k 2b This is shown. The first virtual elastic body 60 is not used to indicate the presence of a spring member, but rather to schematically show that the floating body 40 is supported in the X direction by a force from the surrounding water. The natural frequency of the floating body 40 may be designed to be sufficiently detuned with respect to the frequency of the wave.

[0029] The floating body 40 includes a first cavity 41 extending in the X direction. The first columnar body 22 described above is inserted into the first cavity 41. The diameter of the first cavity 41 is larger than the outer diameter of the first columnar body 22. In this embodiment, the first cavity 41 does not penetrate the floating body 40.

[0030] Multiple rollers 42 may be attached to the wall surface of the first cavity 41. The multiple rollers 42 may be spaced apart in the X direction or spaced apart in the circumferential direction. The rollers 42 are capable of rolling against the outer circumferential surface of the first columnar body 22. This allows for smooth relative translational motion between the floating body 40 and the first columnar body 22. Guide rails (not shown) extending in the X direction may be attached to the outer circumferential surface of the first columnar body 22. This prevents the first columnar body 22 from performing rotational motion about an axis along the X direction relative to the floating body 40. It also allows for guidance of the relative translational motion between the floating body 40 and the first columnar body 22 in the X direction.

[0031] The floating body 40 is connected to the platform 20 via a first elastic body 70. The first elastic body 70 is located within the first cavity 41 and is connected to the lower end of the first columnar body 22 and the bottom surface of the first cavity 41. In this way, the floating body 40 is elastically coupled to the platform 20. The first elastic body 70 has a spring constant k3. The first elastic body 70 may be composed of a spring member such as a coil spring. In Figure 2, the spring constant of the first elastic body 70 corresponding to the vibration isolation mechanism 30A is k 3a As shown, the spring constant of the first elastic body 70 corresponding to the vibration isolation mechanism 30B is k 3b This is shown in Figure 2. The number of first elastic bodies 70 for one floating body 40 is arbitrary. In the example shown in Figure 2, one floating body 40 and the first columnar body 22 are connected by one first elastic body 70. Alternatively, the first elastic body 70 may be composed of a buoyancy spring. In this case, a fluid such as water may be injected into the first cavity 41, and the buoyancy force acting on the first columnar body 22 may be used to constitute the buoyancy spring.

[0032] As described above, in this embodiment, the platform 20 is supported by four vibration isolation mechanisms 30A to 30D. Each first columnar body 22 of the platform 20 is inserted into the first cavity 41 of the corresponding floating body 40. When viewed in the X direction, each first columnar body 22 is arranged concentrically with the corresponding first cavity 41.

[0033] Each of the first power generation mechanisms 50A and 50B is configured to generate electricity by converting the relative translational motion between the platform 20 and the floating body 40 into rotational motion.

[0034] More specifically, the first power generation mechanisms 50A and 50B each include a first rack rail 51, a first generator gear 52, and a first device generator 53.

[0035] The first rack rail 51 is an example of the first rack. The first rack rail 51 is provided on the first columnar body 22. More specifically, the first rack rail 51 is attached to the outer circumferential surface of the first columnar body 22. The first rack rail 51 is positioned so as not to interfere with the roller 42 described above. The first rack rail 51 extends in the X direction and is insertable into the first cavity 41. Because the rotational motion of the first columnar body 22 about an axis along the X direction is suppressed by the guide rail described above, the first rack rail 51 can mesh with the first generator gear 52.

[0036] The first generator gear 52 is supported by the floating body 40. The first generator gear 52 is rotatably mounted to the floating body 40 via bearings (not shown). The first generator gear 52 meshes with the first rack rail 51 and operates in conjunction with the first rack rail 51. The relative translational motion between the first rack rail 51 and the first generator gear 52 is converted into rotational motion of the first generator gear 52. The first generator gear 52 may be coaxially connected to the first device generator 53.

[0037] The first generator 53 is supported by a floating body 40. The first generator 53 includes a first generator rotor 54. The first generator 53 is configured to generate electricity by the rotational motion of the first generator gear 52, which causes the first generator rotor 54 to rotate. The electricity generated is supplied to a load (not shown). The first generator rotor 54 has a rotation axis along the horizontal direction. As shown in Figures 2 and 3, the rotation axis of the first generator rotor 54 may be along the Y or Z direction. The first generator rotor 54 may include a flywheel (not shown). In this case, the moment of inertia of the first generator rotor 54 can be adjusted.

[0038] The first generator rotor 54 described above functions as an inertial mass element that reduces vibration transmission from the floating body 40 to the platform 20. The moment of inertia of the first generator rotor 54 of the vibration isolation mechanism 30A is J a The module radius of the first generator gear 52 is r a Therefore, the inertial mass msa This is expressed by the following equation (1). This inertial mass m sa However, it acts on the relative motion in the X direction that occurs between the first columnar body 22 and the floating body 40.

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[0039] When viewed in the X direction, the multiple first power generation mechanisms 50A, 50B may be arranged around the first columnar body 22, or they may be arranged rotationally symmetrically with respect to the first columnar body 22. In this embodiment, each vibration isolation mechanism 30A to 30D includes two first power generation mechanisms 50A, 50B. As shown in Figure 2, the two first power generation mechanisms 50A, 50B are arranged on both sides of the first columnar body 22 in the Z direction when viewed in the Y direction. As shown in Figure 3, the two first power generation mechanisms 50A, 50B are arranged rotationally symmetrically with respect to the first columnar body 22 when viewed in the X direction. In the example shown in Figure 3, the two first power generation mechanisms 50A, 50B are positioned 180° apart from each other. In other words, the first generator gear 52 of one first power generation mechanism 50A and the first generator gear 52 of the other first power generation mechanism 50A are aligned in a straight line when viewed in the X direction. In the example shown in Figure 3, the first device generator 53 of the first power generation mechanism 50A of the vibration isolation mechanism 30A is located below the first generator gear 52. The first device generator 53 of the first power generation mechanism 50B of the vibration isolation mechanism 30A is located above the first generator gear 52. The first device generator 53 of the first power generation mechanism 50A of the vibration isolation mechanism 30B is located to the left of the first generator gear 52. The first device generator 53 of the first power generation mechanism 50B of the vibration isolation mechanism 30B is located to the right of the first generator gear 52. The first device generator 53 of the first power generation mechanism 50A of the vibration isolation mechanism 30C is located to the left of the first generator gear 52. The first device generator 53 of the first power generation mechanism 50B of the vibration isolation mechanism 30C is located to the right of the first generator gear 52. The first device generator 53 of the first power generation mechanism 50A of the vibration isolation mechanism 30D is located below the first generator gear 52. The first generator 53 of the first power generation mechanism 50B of the vibration isolation mechanism 30D is positioned above the first generator gear 52.

[0040] As shown in Figure 3, when viewed in the X direction, the four vibration isolation mechanisms 30A to 30D are arranged to surround the center of gravity G of the platform 20. In the example shown in Figure 3, the center of gravity G of the platform 20 is located at the center of the square formed by connecting the centers of the four vibration isolation mechanisms 30A to 30D. Vibration isolation mechanisms 30A and 30C are aligned along the Y direction, as are vibration isolation mechanisms 30B and 30D. Vibration isolation mechanisms 30A and 30B are aligned along the Z direction, as are vibration isolation mechanisms 30C and 30D.

[0041] When the floating platform device 10 configured in this way is viewed in the Y direction, vibration isolation mechanisms 30A to 30D are positioned on both sides of the platform 20 in the lateral direction relative to the center of gravity G. In other words, as shown in Figure 2, vibration isolation mechanisms 30A and 30B are positioned on both sides of the Z direction when viewed in the Y direction. When viewed at arrow P in Figure 3, vibration isolation mechanism 30A is positioned to the left of the center of gravity G, and vibration isolation mechanism 30B is positioned to the right of the center of gravity G. Behind vibration isolation mechanism 30A shown in Figure 2, vibration isolation mechanism 30C is positioned, and behind vibration isolation mechanism 30B, vibration isolation mechanism 30D is positioned. Alternatively, for example, two vibration isolation mechanisms 30A and 30D are positioned on both sides of the Y direction when viewed in the Z direction. When viewed at arrow Q in Figure 3, vibration isolation mechanism 30D is positioned to the left of the center of gravity G, and vibration isolation mechanism 30A is positioned to the right of the center of gravity G. Thus, when viewed from at least one direction perpendicular to the X direction, one or more vibration isolation mechanisms 30A to 30D may be arranged on each of the lateral sides with respect to the center of gravity G. When viewed from all directions perpendicular to the X direction, vibration isolation mechanisms may be arranged on both lateral sides with respect to the center of gravity G.

[0042] The floating platform device 10 configured in this embodiment is schematically represented by the dynamic model shown in Figure 4. Figure 4 is a diagram showing the dynamic model of the floating platform device shown in Figure 2.

[0043] Here, the dynamic model of the water platform device 10 is treated as a two-dimensional model in the XZ plane. That is, considering only the displacement in the X direction, the first columnar body 22 is regarded as being rotatably connected to the platform main body 21 around the Y axis. The platform main body 21 is structurally uniform, and it is assumed that all the vibration isolation mechanisms 30A to 30D have the same structure. As a result, in this embodiment, since the target structure is mechanically formed with respect to the XZ plane and the YZ plane respectively, only the platform 20 and the two vibration isolation mechanisms 30A and 30B need to be considered as a two-dimensional problem in the XZ plane. Hereinafter, the dynamic model is treated as a two-dimensional model in the XZ plane. In the following description, the reference numerals related to the vibration isolation mechanism 30A are suffixed with the subscript "a", and the reference numerals related to the vibration isolation mechanism 30B are suffixed with the subscript "b".

[0044] The vibration isolation mechanisms 30A and 30B are arranged at positions at a distance b in the Z direction from the origin O. The platform 20 is regarded as a rigid body, and the center of gravity G is located on the X axis extending from the origin O. Let the mass of the platform 20 be M and the moment of inertia about the Y axis at the center of gravity G be I. The mass M and the moment of inertia I include the inertial masses of each first columnar body 22 and each first rack rail 51. Let the mass of the floating body 40 of the vibration isolation mechanism 30A be m 1a and the mass of the vibration isolation mechanism 30B be m 1b Let the mass m<00000​​​​​​​​​​​​​​​​​2b It is expressed as follows. On the other hand, mass m 1a , m 1b The spring constant k of the first elastic body 70 is 3a , k 3b The mass and total moment of inertia M and I of platform 20 are connected via c. 3a , c 3b m represents damping. s3a , m s3b This represents the inertial mass. Since the two vibration isolation mechanisms 30A and 30B have the same structure, m 1a =m 1b =m1, m s3a =m s3b =m s , k 2a =k 2b =k², c 2a =c 2b =c², k 3a =k 3b =k3, c 3a =c 3b = c3.

[0045] Assuming the wave wavelength is sufficiently long compared to the length of platform 20, the water surface w a , w b The plane is maintained, and the translational displacement in the X direction is represented by X0, and the rotational displacement around the Y axis is represented by Θ0. If Θ0 is small, the water surface w a , w b Translational displacement X a , X b It can be expressed using X0 and Θ0 as follows:

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[0046] Let x0 be the translational displacement in the X direction at the center of gravity G of platform 20. If the rotational displacement Θ0 around the Y axis is small, then the translational displacement in the X direction at the connection point between platform 20 and vibration isolation mechanisms 30A and 30B is x 2a , x 2b This can be expressed as follows:

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[0047] The relationship between the moment of inertia I and the mass M of the platform 20 is expressed in the form of equation (6) using an equivalent dimension d.

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[0048] mass m 1a , m 1b The translational displacement in the X direction is x 1a , x 2b Therefore, the equations of motion for the dynamic model shown in Figure 4 can be expressed as follows:

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[0049] To perform the response calculation, equation (7) is modified into the following matrix format.

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[0050] The mass matrix [M], damping matrix [C], and stiffness matrix [K] in equation (9) are expressed as follows:

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[0051] The displacement vector x in equation (9) is expressed as shown in equation (13), and the external force vector F is expressed as shown in equation (14).

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[0052] Here, in order to determine the frequency response, the external force vector F in equation (16) is used.

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[0053] Corresponding to equation (14), the response x is,

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[0054] By solving equation (18), the response x can be found using equation (17).

[0055] For simplicity, let's set β as follows.

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[0056] Comparing equation (7) and equation (22), in equation (7) x 1a , x 2a , x 1b , x 2b Although they are coupled, in equation (22) x 1a , x 2a and x 1b , x 2b These two pairs are coupled, x 1a , x 2a The pair and x 1b , x 2b The pairs are not coupled. Therefore, the 4-degree-of-freedom system in Figure 4 is x 1a , x 2a and x 1b , x 2b It can be considered as two separate systems of two degrees of freedom. That is, vibration isolation mechanism 30A and vibration isolation mechanism 30B each independently generate wavefront w a , w b Displacement X a , X b Displacement x of platform 20 2a , x 2b This means blocking vibration propagation to the pitting vibration. This condition not only simplifies the equations but also offers design advantages because it allows for the independent treatment of heave vibration and pitting vibration.

[0057] If we ignore damping and determine the frequency response, the cutoff frequency can be expressed as follows:

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[0058] For a typical example of this embodiment, the frequency response was determined using the frequency response solution method described above. The calculation results are shown in Figures 5 and 6. Figure 5 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device in Figure 2, and Figure 6 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device in Figure 2.

[0059] Looking at equation (15), we can see that the external force vector F is the sum of the component due to the translational displacement X0 in the X direction of the wavefront and the component due to the rotational displacement Θ0 around the Y axis. The former is the heave (translational displacement in the X direction) component, and the latter is the pitching (rotational displacement around the Y axis) component. In equation (15)

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[0060] As a comparative example, the response of a floating platform device 10 without a vibration isolation mechanism, as shown in Figures 7 and 8, was calculated and is shown in Figures 5 and 6 with a dashed line. As shown in Figure 7, the floating platform device 10 shown in Figures 7 and 8 has the same shape and dimensions as the floating platform device 10 shown in Figures 2 and 3, but differs in that each first columnar body 22 and each floating body 40 are directly connected and rigidly connected.

[0061] The comparative example, the floating platform device 10, is schematically represented by the dynamic model shown in Figure 9.

[0062] The amplitude of the heave oscillation shown in Figure 4 exhibits the following relationship.

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[0063] The phase of the heave oscillation shown in Figure 4 exhibits the following relationship.

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[0064] Regarding the comparative example, the floating platform device 10, the following relationship can be observed due to its symmetry.

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[0065] The amplitude response curve of the comparative example has a sharp peak (natural frequency) near 0.020 Hz.

[0066] In contrast, the amplitude response curve of the floating body 40 according to this embodiment |x 1a / X0|, |x 1b / X0| has one sharp peak (natural frequency) near 0.015 Hz. Compared with the case without the vibration blocking mechanism, the natural frequency of the floating platform device 10 according to the present embodiment is slightly lowered. Also, only one natural frequency appears for the floating platform device 10 according to the present embodiment. Further, compared with the case without the vibration blocking mechanism, the amplitude value of the floating platform device 10 according to the present embodiment is lower in the frequency region higher than the natural frequency. In particular, the fact that there is only one peak of the natural frequency is a characteristic phenomenon. Since the mechanical model in FIG. 4 has four degrees of freedom, usually, two natural frequencies exist in the heave response. Since two natural frequencies exist in the pitching vibration described later, as a whole, it has four natural frequencies equal to the number of degrees of freedom. The fact that there is only one peak of the natural frequency as described above is due to the fact that the secondary natural frequency is set to the cutoff frequency by the inertial mass, resulting in the suppression of the response of the secondary natural frequency. The amplitude response curve of the floating body 40 |x 1a / X0|, |x 1b / X0| shows a sharp peak near 0.015 Hz and a broad peak near 0.1 Hz, indicating that it has two natural frequencies. That is, it can be seen that the cutoff frequency of the inertial mass is set near 0.1 Hz. The width response curve |x 2a / X0|, |x 2b / X0| has a high amplitude in the frequency region higher than the primary natural frequency. Since the peak of the secondary natural frequency exists near 0.1 Hz and the wave frequency is generally 0.05 - 0.2 Hz, in this region, the relative displacement |(x 2a -x 1a ) / X0|, |(x 2b -x 1b ) / X0| becomes large. Since the first device generators 53 of the respective vibration blocking mechanisms 30A and 30B are driven by this relative displacement |(x 2a -x 1a ) / X0|, |(x 2b -x 1b ) / X0|, efficient power generation can be realized in the present embodiment. Particularly in the frequency region of vibration frequencies above the secondary natural frequency, the phase relationship between x 2a and x 1a , x2b and x 1b Since the phase relationship with x is the opposite phase, a relative displacement twice as large can be obtained, which is even more advantageous.

[0067] Figure 6 shows the pitching response. When compared with the amplitude in Figure 5, they are quite similar. This is because d is close to b, so as described above, x 1a , x 2a The combination with x 1b , x 2b is in a state where the concatenation of the combination with x is weak. The following relationship is observed for the amplitude.

Number

Number

Number

Number

Number

[0068] In pitching vibration, in the frequency region between the first and second natural frequencies, x 1a and x 1b between and x 2a and x 2b The phases are reversed between them. As a result, twice the relative displacement can be obtained, leading to more efficient power generation.

[0069] The actual wavefront is the sum of the translational displacement X0 and the rotational displacement bΘ0, as expressed by equations (1) and (2). However, since the dynamic model shown in Figure 4 is a linear system, the responses of both can be superimposed. Therefore, the characteristics described in Figures 5 and 6 hold true even when heave vibration and pitching vibration occur simultaneously.

[0070] If the Z-axis in Figure 4 is replaced with the Y-axis, the above theory also holds true in the XY plane. Therefore, in this embodiment, the relative motion between the floating body 40 and the first columnar body 22 can be converted into rotational motion of the first generator rotor 54 of the first generator 53, thereby acting as inertial mass for waves coming from both the Y and Z directions. This makes it possible to block vibrations from propagating from the floating body 40 to the floating platform device 10, while simultaneously generating electricity with the first generator 53.

[0071] As described above, according to this embodiment, the inertial mass of the first device generator 53 causes the water surface w a , w b The vibrations transmitted from the translational displacements X1 and X2 to the floating platform device 10 can be blocked. This allows for the simultaneous reduction of both heave vibration and pitching vibration responses of the floating platform device 10. Furthermore, a large relative displacement can be generated between the floating platform device 10 and the floating body 40 in the region of 0.05 Hz to 0.2 Hz, which is the typical frequency range of waves. This allows the first device generator 53 to be driven, enabling wave power generation. By suppressing vibrations of the floating platform device 10 caused by waves, the wave loads acting on structures, equipment, and devices attached to the floating platform device 10 can be reduced, improving reliability and stability. In addition, the comfort of the occupants on the floating platform device 10 can be improved.

[0072] As described above, according to this embodiment, the vibration isolation mechanisms 30A to 30D include a floating body 40 elastically coupled to the platform 20, and first power generation mechanisms 50A and 50B that convert the relative translational motion between the platform 20 and the floating body 40 into rotational motion to generate electricity. As a result, the first power generation mechanisms 50A and 50B can suppress vibrations of the platform 20 and convert vibration energy into electrical energy to generate electricity.

[0073] Furthermore, according to this embodiment, the first power generation mechanisms 50A and 50B can have inertial mass elements that reduce vibration transmission from the floating body 40 to the platform 20. This suppresses heave vibrations applied to the platform 20 and reduces damage to the wind turbine 2 mounted on the platform 20. In addition, the relative displacement between the floating body 40 and the platform 20 can be increased, thereby increasing the amount of power generated by the first power generation mechanisms 50A and 50B.

[0074] Furthermore, according to this embodiment, vibration isolation mechanisms 30A to 30D are arranged on both sides in the Z direction with respect to the center of gravity G of the platform 20 when viewed in at least one direction (for example, the Y direction) perpendicular to the X direction. As a result, the vibration isolation mechanisms can suppress oscillations (pitching vibrations) caused by rotational displacement around an axis extending in the Y direction, thereby preventing damage to the wind turbine 2 mounted on the platform 20. Here, pitching vibrations can generate large stresses in the tall tower 3 and excite the wind turbine 2 with a large amplitude. Generally, even when the waves are small, the tilt of the pitching vibration can exceed 5°, and the impact on the tower 3 and the wind turbine 2 cannot be said to be small. In contrast, according to this embodiment, as described above, pitching vibrations can be effectively suppressed, and therefore the propagation of pitching vibrations to the wind turbine 2 can be effectively suppressed. Therefore, damage to the wind turbine 2 can be prevented. In particular, according to this embodiment, both the heave vibration and pitching vibration responses of the platform 20 described above can be suppressed simultaneously.

[0075] Furthermore, according to this embodiment, a first columnar body 22 extending downward from the platform 20 is inserted into the first cavity 41 of the floating body 40. The first power generation mechanisms 50A and 50B include a first rack rail 51 provided on the first columnar body 22, a first generator gear 52 that is interlocked with the first rack rail 51, and a first device generator 53 connected to the first generator gear 52. This allows for the conversion of the relative translational motion between the first columnar body 22 and the floating body 40 into rotational motion to generate electricity, and also suppresses vibrations of the platform 20. For this reason, the first power generation mechanisms 50A and 50B can be easily constructed.

[0076] Furthermore, according to this embodiment, the vibration isolation mechanisms 30A to 30D include a plurality of first power generation mechanisms 50A and 50B, and when viewed in the X direction, the plurality of first power generation mechanisms 50A and 50B are arranged rotationally symmetrically with respect to the first columnar body 22. As a result, the first power generation mechanisms 50A and 50B can rotate in opposite directions to each other. Therefore, the moment generated by the rotational motion of the first power generation mechanism 50A and the moment generated by the rotational motion of the first power generation mechanism 50B can be canceled out.

[0077] In the embodiment described above, an example was described in which the platform 20 is supported by four vibration isolation mechanisms 30A to 30D. However, the invention is not limited to this, and the number of vibration isolation mechanisms supporting the platform 20 can be any number of two or more. For example, if the platform 20 is supported by two vibration isolation mechanisms, and the two vibration isolation mechanisms are arranged in one direction along the horizontal direction, both heave vibration and pitching vibration responses around a specific rotation axis can be suppressed simultaneously. For example, as in the second embodiment described later, the platform 20 may be supported by three vibration isolation mechanisms 30A to 30C, or by four or more vibration isolation mechanisms, and in any case, both heave vibration and pitching vibration responses around two or more specific rotation axes can be suppressed simultaneously.

[0078] In addition, in the above-described embodiment, an example in which the floating platform device 10 is applied to an offshore wind power generation facility has been described. However, the present invention is not limited to this, and the floating platform device 10 can be applied to any facility as long as it is a facility located on water. For example, it may be a power supply facility as described in the fourth embodiment described later.

[0079] (Second Embodiment) Next, a floating platform device according to the second embodiment will be described with reference to FIGS. 10 and 11.

[0080] In the second embodiment shown in FIGS. 10 and 11, the main difference is that the platform is supported by three vibration isolation mechanisms, and the other configurations are substantially the same as those of the first embodiment shown in FIGS. 1 to 6. In FIGS. 10 and 11, the same parts as those of the first embodiment shown in FIGS. 1 to 6 are denoted by the same reference numerals, and detailed description thereof is omitted. FIG. 10 is a schematic cross-sectional view showing a floating platform device according to the second embodiment, and FIG. 11 is a cross-sectional view taken along line E-E of FIG. 10.

[0081] As shown in FIGS. 10 and 11, in the present embodiment, the platform 20 is supported by three vibration isolation mechanisms 30A to 30C.

[0082] As shown in FIG. 11, the planar shape of the platform body 21 is generally a regular triangle. More specifically, each vertex of the triangle is cut off. Three first columnar bodies 22 extend downward from the platform body 21. As shown in FIG. 11, the three first columnar bodies 22 are arranged so as to be located at the vertices of a regular triangle when viewed in the X direction.

[0083] As shown in FIG. 11, when viewed in the X direction, the three vibration isolation mechanisms 30A to 30C are arranged so as to surround the center of gravity G of the platform 20. In the example shown in FIG. 11, the center of gravity G of the platform 20 is arranged at the center of the equilateral triangle formed by connecting the centers of the three vibration isolation mechanisms 30A to 30C.

[0084] When the floating platform device 10 configured as described above is viewed in the Y direction, the vibration isolation mechanisms 30A to 30C are arranged on both lateral sides in the horizontal direction with respect to the center of gravity G of the platform 20. In other words, in the example shown in FIG. 10, the vibration isolation mechanisms 30A and 30B are arranged on both sides in the Z direction when viewed in the Y direction. The vibration isolation mechanism 30A is arranged on the left side of the center of gravity G, and the vibration isolation mechanism 30B is arranged on the right side of the center of gravity G. In the example shown in FIG. 10, the vibration isolation mechanism 30C is arranged at a position between the vibration isolation mechanism 30A and the vibration isolation mechanism 30B.

[0085] According to this embodiment as described above, the platform 20 is supported by the three vibration isolation mechanisms 30A to 30C. And when viewed in at least one direction (for example, the Y direction) orthogonal to the X direction, the vibration isolation mechanisms 30A and 30B are arranged on both sides in the Z direction with respect to the center of gravity G of the platform 20. Thus, the vibration isolation mechanism can suppress the rocking (pitching vibration) due to the rotational displacement around the axis extending in the Y direction, and can suppress damage to the wind power generation device 2 mounted on the platform 20. Also, similar to the first embodiment, heave vibration can be suppressed, and vibration energy can be converted into electric energy to generate power.

[0086] (Third Embodiment) Next, a floating platform device according to the third embodiment will be described with reference to FIGS. 12 to 14.

[0087] In the third embodiment shown in Figures 12 to 14, the main difference is that a first transmission is interposed between the rack rail and the first generator gear; other configurations are substantially the same as those of the first embodiment shown in Figures 1 to 6. In Figures 12 to 14, the same reference numerals are used for parts identical to those in the first embodiment shown in Figures 1 to 6, and detailed descriptions are omitted. Figure 12 is a schematic cross-sectional view showing a floating platform device according to the third embodiment.

[0088] As shown in Figure 12, the first power generation mechanisms 50A and 50B according to this embodiment each include a first transmission device 55 interposed between the first rack rail 51 and the first generator gear 52. The first transmission device 55 includes a first transmission gear 56. The first generator gear 52 is interlocked with the first rack rail 51 via the first transmission gear 56. The teeth of the first transmission gear 56 mesh with the teeth of the first rack rail 51 and also with the teeth of the first generator gear 52.

[0089] The number of teeth of the first transmission gear 56 is different from the number of teeth of the first generator gear 52. As a result, the rotational speed of the first transmission gear 56 and the rotational speed of the first generator gear 52 are different. In the example shown in Figure 12, the pitch circle radius of the first transmission gear 56 is larger than that of the first generator gear 52. As a result, the number of teeth of the first transmission gear 56 is greater than that of the first generator gear 52, and the first transmission gear 56 can increase the rotational speed of the first generator gear 52.

[0090] The number of teeth of the first gear 56 of the vibration isolation mechanism 30A is Z 1a The number of teeth of the first generator gear 52 is set to Z 2a In this case, the rotational speed ratio of the first generator gear 52 and the first transmission gear 56, i.e., the speed increase rate ε, is... a This can be expressed as follows:

number

[0091] The moment of inertia of the rotor 54 of the first generator 53 is J. aThe module radius of the first transmission gear 56 is r a Therefore, the inertial mass m sa This is expressed as follows: This inertial mass m sa This acts on the relative translational motion in the X direction that occurs between the first columnar body 22 and the floating body 40.

number

[0092] Each vibration isolation mechanism 30A to 30D includes a first power generation mechanism 50A, 50B which includes a first speed gear 56, and has a similar configuration. Thus, in this embodiment, the speed increase rate of the first transmission 55 of the vibration isolation mechanism 30A is ε a The speed increase rate of the first transmission 55 of the vibration isolation mechanism 30B is ε b The speed increase rate of the first transmission 55 of the vibration isolation mechanism 30C is ε c The speed increase rate of the first transmission 55 of the vibration isolation mechanism 30D is ε d Therefore, by changing these acceleration rates, the inertial mass m sa , m sb , m sc , m sd It can be changed.

[0093] Figures 13 and 14 show the inertia mass ratio μ, focusing on amplitude in the analysis of Figures 5 and 6. s This is a response diagram when μ is changed as a parameter. s is the inertial mass m s This is a value normalized by the inertial mass value used in the calculations in Figures 5 and 6. μ s When μ = 1, the response diagrams in Figures 13 and 14 coincide with the response diagrams in Figures 5 and 6, respectively. s When μ = 0, i.e., when there is no inertial mass (more precisely, when the first transmission gear 56 is not meshed with the first rack rail 51), two peaks of natural frequencies appear in the responses of heave vibration and pitching vibration, respectively. The first natural frequency is located near 0.015 Hz, and the second natural frequency is located near 0.15 Hz. sWhen set to =0.1, there is almost no change in the first natural frequency, but the second natural frequency decreases slightly. Furthermore, due to the effect of the cutoff frequency, x 2a , x 1a A minimum point appears near 0.35 Hz in the transfer coefficient response diagram of μ. s As the value of increases, the second natural frequency and cutoff frequency decrease. The decrease is more pronounced in the cutoff frequency, therefore μ s When =1, the second natural frequency and the cutoff frequency coincide, x 2a , x 2b The peak of the second natural frequency disappears from the transmission coefficient. The first embodiment is μ s With x = 1, 2a , x 2b The design suppresses the peak of the second natural frequency of the response and blocks vibration propagation to the platform 20. In this way, to reduce vibration of the platform 20, the inertial mass m sa , m sb It is preferable to set it appropriately. In the first embodiment, as shown in formula (1), the moment of inertia J of the first generator 53 and the first generator 54 is a , J b It is conceivable to adjust this using a flywheel or the like, but there are limitations due to the dimensional constraints of the first device generator 53. In contrast, in this embodiment, as shown in equation (24), the square of the speed increase rate ε a 2 , ε b 2 This allows for significant changes, thus enabling a wide range of inertial mass m sa , m sb This makes x adjustable. 2a , x 2b This makes it easier to design the system to suppress the peak of the second natural frequency of the response, thereby blocking vibration propagation to the platform 20.

[0094] The first embodiment employs a strategy that achieves both vibration damping and power generation by suppressing vibration propagation to the platform 20 in the range of wave frequencies distributed from 0.05 Hz to 0.2 Hz, while increasing the relative displacement between the platform 20 and the floating body 40. On the other hand, since wave frequencies are constantly changing in nature, a strategy to further increase power generation can also be considered by adjusting the second natural frequency to match the wave frequency, as shown in Figures 13 and 14. In response to this approach, the first transmission 55 of each vibration isolation mechanism 30A to 30D has a speed increase rate ε similar to that of a CVT. a , ε b , ε c , ε d However, by using a variable transmission, it becomes possible to adjust the secondary natural frequency and cutoff frequency in accordance with the changing wave frequency, thereby achieving both vibration damping of the platform structure 1 and securing power generation capacity.

[0095] As described above, according to this embodiment, the first power generation mechanisms 50A and 50B include a first transmission 55 interposed between the first rack rail 51 and the first generator gear 52. This allows the rotational speed of the first generator gear 52 to be adjusted by the first transmission 55, thereby adjusting the amount of power generated by the first generator 53. Furthermore, if the first transmission 55 includes a first transmission gear 56, the speed increase rate, which is the rotational speed ratio between the first transmission gear 56 and the first generator gear 52, can be adjusted by adjusting the number of teeth of the first transmission gear 56. As a result, vibrations of the platform 20 can be effectively suppressed, and the amount of power generated by the first generator 53 can be effectively increased.

[0096] (Fourth embodiment) Next, a floating platform device according to the fourth embodiment will be described using Figure 15.

[0097] In the fourth embodiment shown in Figure 15, the main difference is that the floating platform device is applied to uses other than offshore wind power generation facilities; other configurations are substantially the same as those of the third embodiment shown in Figures 12 to 14. In Figure 15, the same reference numerals are used for parts identical to those of the third embodiment shown in Figures 12 to 14, and detailed descriptions are omitted. Figure 15 is a schematic cross-sectional view showing the floating platform device according to the fourth embodiment.

[0098] In the example shown in Figure 15, the floating platform device 10 according to this embodiment is used as a power supply facility for an electric flying object 80 (such as an electric drone) that performs offshore surveillance.

[0099] More specifically, as shown in Figure 15, the power obtained by the first device generator 53 of each vibration isolation mechanism 30A to 30D is supplied to the rectifier 82 via the output cable 81. Since the output of the first device generator 53 is an alternating current, it is rectified by the rectifier 82 and converted into DC power. The DC power is charged to the storage battery 84 via the charging cable 83. The power charged to the storage battery 84 can be used to charge various electric devices via the connector 85. In the example shown in Figure 15, it is used to charge a rechargeable electric flying vehicle 80.

[0100] Even when the floating platform device 10 shown in Figure 15 is applied to the offshore wind power generation facility 1, the power stored in the battery 84 can be used as a backup power source. Even in the event of a loss of external power due to severe weather, power can be reliably used as a backup power source. If the battery 84 alone is used, the usable time may be limited if there is a failure such as the interruption of external power supply or fuel supply for power generation. However, even if the external power supply or fuel supply is interrupted, the battery 84 can be continuously charged by wave power. Therefore, stable operation as a power supply facility for the electric flying vehicle 80 becomes possible. In addition, since the first power generation mechanisms 50A and 50B can simultaneously suppress both heave vibration and pitching vibration responses of the platform 20, stable takeoff and landing of flying vehicles 80 such as drones on the platform 20 is possible even in severe weather.

[0101] (Fifth Embodiment) Next, a water platform device according to the fifth embodiment will be described using FIG. 16.

[0102] In the fifth embodiment shown in FIG. 16, the main difference is that the water platform device includes propulsion devices. Other configurations are substantially the same as those of the third embodiment shown in FIGS. 12 to 14. In FIG. 16, the same parts as those of the third embodiment shown in FIGS. 12 to 14 are denoted by the same reference numerals, and detailed descriptions thereof are omitted. FIG. 16 is a schematic cross-sectional view showing the water platform device according to the fifth embodiment.

[0103] As shown in FIG. 16, the water platform device 10 according to the present embodiment includes propulsion devices 90 and 91. The propulsion devices 90 and 91 are attached to the lower part of the floating body 40 of each vibration isolation mechanism 30A to 30D. The propulsion devices 90 and 91 may be side thruster - type propulsion devices. Each floating body 40 is provided with a propulsion device 90 for propulsion in the Z direction and a propulsion device 91 for propulsion in the Y direction. Thus, the water platform device 10 can move in the Y direction and the Z direction.

[0104] The propulsion devices 90 and 91 are not limited to being side thruster - type propulsion devices, and may be screw - type propulsion devices such as those used in general ships. Also, a steering device (not shown) for changing the propulsion direction may be combined with the propulsion devices 90 and 91.

[0105] (Sixth Embodiment) Next, a water platform device according to the sixth embodiment will be described using FIGS. 17 to 21.

[0106] In the sixth embodiment shown in Figures 17 to 21, the floating body is elastically coupled to the platform via an intermediate structure, and the relative translational motion between the platform and the intermediate structure is converted into rotational motion to generate electricity. The other configurations are substantially the same as those of the third embodiment shown in Figures 12 to 14. In Figures 17 to 21, the same reference numerals are used for parts identical to those in the third embodiment shown in Figures 12 to 14, and detailed descriptions are omitted. Figure 17 is a schematic cross-sectional view showing the floating platform device according to the sixth embodiment. Figure 18 is a cross-sectional view of Figure 17 along the FF line.

[0107] As shown in Figure 17, each vibration isolation mechanism 30A to 30D according to this embodiment includes an intermediate structure 100, a floating body 40, and second power generation mechanisms 120A and 120B. The intermediate structure 100 is elastically coupled to the platform 20 and is capable of relative translational movement in the X direction relative to the platform 20. The intermediate structure 100 may also be capable of relative translational movement in the vertical direction relative to the platform 20 and in a direction perpendicular to the water surface relative to the platform 20. Each floating body 40 is elastically coupled to the corresponding intermediate structure 100 and is capable of relative translational movement in the X direction relative to the corresponding intermediate structure 100. The floating body 40 may also be capable of relative translational movement in the vertical direction relative to the intermediate structure 100 and in a direction perpendicular to the water surface relative to the intermediate structure 100. Each floating body 40 is connected to the platform 20 via the corresponding intermediate structure 100. The intermediate structure 100 is positioned above the floating body 40 and below the platform body 21. The intermediate structure 100 may be formed in a cylindrical shape so as to extend in the X direction.

[0108] The platform 20 includes a second columnar body 23 as a replacement for the first columnar body 22. The second columnar body 23 extends downward in the X direction from the platform body 21. The second columnar body 23 may be formed in a cylindrical shape so as to extend in the X direction, as will be described later. The second columnar body 23 is inserted into the second cavity 101, as will be described later, and penetrates the second cavity 101. The platform 20 according to this embodiment includes four second columnar bodies 23. The four second columnar bodies 23 are arranged so as to be at the vertices of a square when viewed in the X direction, as shown in Figure 18.

[0109] The second columnar body 23 may penetrate the second cavity 101 and be inserted into the first cavity 41 of the floating body 40. A roller 42 attached to the wall surface of the first cavity 41 is capable of rolling against the outer circumferential surface of the second columnar body 23. This allows for smooth relative translational motion between the floating body 40 and the second columnar body 23. A guide rail (not shown) extending in the X direction may be attached to the outer circumferential surface of the second columnar body 23. This prevents the second columnar body 23 from performing rotational motion about an axis along the X direction relative to the floating body 40. It also allows for guidance of the relative translational motion between the floating body 40 and the second columnar body 23 in the X direction.

[0110] As shown in Figure 17, an elastic body connecting portion 24, to which a second elastic body 110 (described later) is connected, is fixed to the second columnar body 23. As shown in Figure 18, two elastic body connecting portions 24 may be fixed to the second columnar body 23. In this case, the two elastic body connecting portions 24 may be arranged symmetrically with respect to the second columnar body 23.

[0111] The intermediate structure 100 includes a second cavity 101 extending in the X direction. The second columnar body 23 described above is inserted into the second cavity 101. The diameter of the second cavity 101 is larger than the outer diameter of the second columnar body 23. In this embodiment, the second cavity 101 penetrates the intermediate structure 100.

[0112] Multiple rollers 102 may be attached to the wall surface of the second cavity 101. The multiple rollers 102 may be spaced apart in the X direction or spaced apart in the circumferential direction. The rollers 102 are capable of rolling against the outer circumferential surface of the second columnar body 23. This allows for smooth relative translational motion between the intermediate structure 100 and the second columnar body 23. Guide rails (not shown) extending in the X direction may be attached to the outer circumferential surface of the second columnar body 23. This prevents the second columnar body 23 from performing rotational motion about an axis along the X direction relative to the intermediate structure 100. It also allows for guidance of the relative translational motion between the intermediate structure 100 and the second columnar body 23 in the X direction.

[0113] The intermediate structure 100 is connected to the platform 20 via a second elastic body 110. The second elastic body 110 connects the elastic body connecting portion 24, which is fixed to the second columnar body 23, to the intermediate structure 100. In the example shown in Figure 17, one second elastic body 110 connects the elastic body connecting portion 24 to the intermediate structure 100, but the number of second elastic bodies 110 is arbitrary. The second elastic body 110 has a spring constant k4. The second elastic body 110 may be composed of a spring member such as a coil spring. In Figure 2, the spring constant of the second elastic body 110 corresponding to the vibration isolation mechanism 30A is k 4a As shown, the spring constant of the second elastic body 110 corresponding to the vibration isolation mechanism 30B is k 4b This is shown.

[0114] In this embodiment, the floating body 40 is connected to the intermediate structure 100 via the first elastic body 70. The first elastic body 70 connects the intermediate structure 100 and the floating body 40. In the example shown in Figure 17, two first elastic bodies 70 connect the intermediate structure 100 and the floating body 40, but the number of first elastic bodies 70 is arbitrary.

[0115] The second power generation mechanisms 120A and 120B are configured to generate electricity by converting the relative translational motion between the platform 20 and the intermediate structure 100 into rotational motion.

[0116] More specifically, the second power generation mechanisms 120A and 120B each include a second rack rail 121, a second generator gear 122, and a second device generator 123.

[0117] The second rack rail 121 is an example of a second rack. The second rack rail 121 is provided on the second columnar body 23. More specifically, the second rack rail 121 is attached to the outer circumferential surface of the second columnar body 23. The second rack rail 121 is positioned so as not to interfere with the roller 102 described above. The second rack rail 121 extends in the X direction and is insertable into the second cavity 101. Because the rotational motion of the second columnar body 23 about an axis along the X direction is suppressed by the guide rail described above, the second rack rail 121 can mesh with the second generator gear 122.

[0118] The second generator gear 122 is supported by the intermediate structure 100. The second generator gear 122 is rotatably mounted to the intermediate structure 100 via a bearing (not shown). The second generator gear 122 meshes with the second rack rail 121 and operates in conjunction with the second rack rail 121. In this way, the relative translational motion between the second rack rail 121 and the second generator gear 122 is converted into rotational motion of the second generator gear 122. The second generator gear 122 may also be coaxially connected to the second device generator 123.

[0119] The second generator 123 is supported by the intermediate structure 100. The second generator 123 includes a second generator rotor 124. The second generator 123 is configured such that the rotational motion of the second generator gear 122 causes the second generator rotor 124 to rotate and generate electricity. The electricity generated is supplied to a load (not shown). The second generator rotor 124 has a rotation axis along the horizontal direction. As shown in Figures 17 and 18, the rotation axis of the second generator rotor 124 may be along the Y or Z direction. The second generator rotor 124 may include a flywheel (not shown). In this case, the moment of inertia of the second generator rotor 124 can be adjusted.

[0120] As shown in Figures 17 and 18, the second power generation mechanisms 120A and 120B according to this embodiment each include a second transmission device 125 interposed between the second rack rail 121 and the second generator gear 122. The second transmission device 125 includes a second transmission gear 126. The second generator gear 122 is interlocked with the second rack rail 121 via the second transmission gear 126. The teeth of the second transmission gear 126 mesh with the second rack rail 121 and also mesh with the teeth of the second generator gear 122. The second transmission gear 126 can be configured similarly to the first transmission gear 56, so a detailed explanation is omitted here. Each vibration isolation mechanism 30A to 30D includes a second power generation mechanism 120A and 120B including a second transmission gear 126, and has a similar configuration.

[0121] The second generator rotor 124 described above functions as an inertial mass element that reduces vibration transmission from the intermediate structure 100 to the platform 20. The moment of inertia of the second generator rotor 124 of the vibration isolation mechanism 30A is J 1a The module radius of the second generator gear 122 is r 1a The speed increase rate of the second generator gear 122 and the second transmission gear 126 is set to ε 1a Therefore, the inertial mass m s4a This can be expressed by the following equation (25).

number

[0122] Each vibration isolation mechanism 30A to 30D may include a plurality of second power generation mechanisms 120A and 120B. When viewed in the X direction, the plurality of second power generation mechanisms 120A and 120B may be arranged around the second columnar body 23, or they may be arranged rotationally symmetrically with respect to the second columnar body 23. In this embodiment, each vibration isolation mechanism 30A to 30D includes two second power generation mechanisms 120A and 120B. As shown in Figure 18, when viewed in the Y direction, the two second power generation mechanisms 120A and 120B are arranged on both sides of the second columnar body 23 in the Z direction. As shown in Figure 18, when viewed in the X direction, the two second power generation mechanisms 120A and 120B are arranged rotationally symmetrically with respect to the second columnar body 23. In the example shown in Figure 18, the two second power generation mechanisms 120A and 120B are arranged at positions 180° apart from each other. In other words, the second generator gear 122 of one second power generation mechanism 120A and the second generator gear 122 of the other second power generation mechanism 120A are aligned in a straight line when viewed in the X direction. In the example shown in Figure 18, the second device generator 123 of the second power generation mechanism 120A of the vibration isolation mechanism 30A is located below the second generator gear 122. The second device generator 123 of the second power generation mechanism 120B of the vibration isolation mechanism 30A is located above the second generator gear 122. The second device generator 123 of the second power generation mechanism 120A of the vibration isolation mechanism 30B is located to the left of the second generator gear 122. The second device generator 123 of the second power generation mechanism 120B of the vibration isolation mechanism 30B is located to the right of the second generator gear 122. The second device generator 123 of the second power generation mechanism 120A of the vibration isolation mechanism 30C is located to the left of the second generator gear 122. The second generator 123 of the second power generation mechanism 120B of the vibration isolation mechanism 30C is located to the right of the second generator gear 122. The second generator 123 of the second power generation mechanism 120A of the vibration isolation mechanism 30D is located below the second generator gear 122. The second generator 123 of the second power generation mechanism 120B of the vibration isolation mechanism 30D is located above the second generator gear 122. In Figure 17, for convenience, one of the two second power generation mechanisms 120A and 120B is shown, while the other is omitted to show the second elastic body 110.

[0123] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the dynamic model shown in Figure 19. Figure 19 is a diagram showing the dynamic model of the floating platform device shown in Figure 17.

[0124] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the mechanical model shown in Figure 19. Similar to the explanation in Figure 4, it is treated as a two-dimensional problem in the XZ plane. That is, displacement is considered only in the X direction, and the second columnar body 23 is assumed to be freely rotatable to the platform body 21 around the Y axis. The platform body 21 is assumed to be structurally uniform, and all vibration isolation mechanisms 30A to 30D are assumed to have the same structure. As a result, this embodiment has a mechanically symmetrical structure with respect to the XZ and YZ planes, respectively, so only the platform 20 and the two vibration isolation mechanisms 30A and 30B need to be considered as a two-dimensional problem in the XZ plane.

[0125] The main difference between the mechanical model shown in Figure 19 and the mechanical model shown in Figure 4 is the mass m of the intermediate structure 100. 2a =m 2b =m2 is the point inserted between platform 20 and floating body 40. The spring constant k is between platform 20 and intermediate structure 100. 4a =k 4b =k4 and damping constant c 4a =c 4b =c4, inertial mass m s4a =m s4b =m s4 They are connected by a spring constant k. 3a =k 3b =k3, damping constant c 3a =c 3b =c3, inertial mass m s3a =m s3b =m s3 They are connected by [this]. Note that the model shown in Figure 19 has an inertial mass m s3a =m s3b =m s3 Although it is described, in this embodiment m s3Treat it as =0. The degrees of freedom of the dynamic model in Figure 19 are 6, and the equations of motion are expressed in matrix form as follows.

number

[0126] The mass matrix [M], damping matrix [C], and stiffness matrix [K] in equation (9) are expressed as follows:

number

number

number

[0127] The displacement vector x in equation (26) is expressed as shown in equation (30), and the external force vector F is expressed as shown in equation (31).

number

number

[0128] Here, in order to determine the frequency response, the external force vector F in equation (31) is used.

number

number

number

number

[0129] The frequency characteristics of this embodiment are shown in Figures 20 and 21. Figure 20 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device 10 in Figure 17. Figure 21 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device 10 in Figure 17.

[0130] The fact that the amplitude of the heave vibration and the amplitude of the pitting vibration are approximate is, as in the first embodiment,

number

[0131] As described above, according to this embodiment, the vibration isolation mechanisms 30A to 30D include an intermediate structure 100 elastically coupled to the platform 20 and the floating body 40, and second power generation mechanisms 120A and 120B that convert the relative translational motion between the platform 20 and the intermediate structure 100 into rotational motion to generate electricity. As a result, the second power generation mechanisms 120A and 120B can suppress vibrations and convert vibration energy into electrical energy to generate electricity.

[0132] Furthermore, according to this embodiment, the second power generation mechanisms 120A and 120B can have inertial mass elements that reduce vibration transmission from the intermediate structure 100 to the platform 20. This suppresses heave vibrations applied to the platform 20, thereby preventing damage to the wind turbine 2 mounted on the platform 20. In addition, the relative displacement between the intermediate structure 100 and the platform 20 can be increased, thereby increasing the amount of power generated by the second power generation mechanisms 120A and 120B.

[0133] Furthermore, according to this embodiment, a second columnar body 23 extending downward from the platform 20 is inserted into the second cavity 101 of the intermediate structure 100. The second power generation mechanisms 120A and 120B include a second rack rail 121 provided on the second columnar body 23, a second generator gear 122 that is interlocked with the second rack rail 121, and a second device generator 123 connected to the second generator gear 122. This allows power generation to be performed by converting the relative translational motion between the second columnar body 23 and the intermediate structure 100 into rotational motion. For this reason, the second power generation mechanisms 120A and 120B can be easily constructed.

[0134] Furthermore, according to this embodiment, the second power generation mechanisms 120A and 120B include a second transmission 125 interposed between the second rack rail 121 and the second generator gear 122. This allows the rotational speed of the second generator gear 122 to be adjusted by the second transmission 125, thereby adjusting the power output of the second generator 123. Also, if the second transmission 125 includes a second transmission gear 126, the speed increase rate, which is the rotational speed ratio between the second transmission gear 126 and the second generator gear 122, can be adjusted by adjusting the number of teeth of the second transmission gear 126. As a result, vibrations of the platform 20 can be effectively suppressed, and the power output of the second generator 123 can be effectively increased.

[0135] (Seventh Embodiment) Next, a floating platform device according to the seventh embodiment will be described using Figures 22 to 24.

[0136] In the seventh embodiment shown in Figures 22 to 24, the main difference is that the vibration isolation mechanism includes a first power generation mechanism and a second power generation mechanism; other configurations are substantially the same as those of the sixth embodiment shown in Figures 17 to 21. In Figures 22 to 24, the same reference numerals are used for parts identical to those in the sixth embodiment shown in Figures 17 to 21, and detailed descriptions are omitted. Figure 22 is a schematic cross-sectional view showing a floating platform device according to the seventh embodiment.

[0137] As shown in Figure 22, the second columnar body 23 of the platform 20 according to this embodiment is inserted into the second cavity 101 of the intermediate structure 100.

[0138] The intermediate structure 100 includes an intermediate structure body 104 and a first columnar body 103. The planar shape of the intermediate structure body 104 may be the same as that of the platform body 21. The height of the intermediate structure body 104 may be uniform. The first columnar body 103 extends downward in the X direction from the intermediate structure body 104. The first columnar body 103 may be formed in a cylindrical shape so as to extend in the X direction. The first columnar body 103 is inserted into the first cavity 41 of the floating body 40. The intermediate structure 100 according to this embodiment includes four first columnar bodies 103. The outer diameter of the first columnar body 103 is smaller than the diameter of the first cavity 41. The second cavity 101 may penetrate the intermediate structure body 104 and extend into the first columnar body 103. The second cavity 101 does not penetrate the intermediate structure 100. The first columnar body 103 may be formed in a sleeve shape.

[0139] The roller 42 attached to the wall surface of the first cavity 41 is capable of rolling relative to the outer surface of the first columnar body 103. This allows for smooth relative translational motion between the floating body 40 and the first columnar body 103. A guide rail (not shown) extending in the X direction may be attached to the outer surface of the first columnar body 103. This prevents the first columnar body 103 from performing rotational motion about an axis along the X direction relative to the floating body 40. It also guides the relative translational motion between the floating body 40 and the first columnar body 103 in the X direction.

[0140] The first elastic body 70 is connected to the lower end of the first columnar body 103 and to the bottom surface of the first cavity 41.

[0141] Each vibration isolation mechanism 30A to 30D includes a first power generation mechanism 50A, 50B and a second power generation mechanism 120A, 120B. The first power generation mechanisms 50A, 50B are supported by the floating body 40 and are configured to convert the relative translational motion between the first columnar body 103 of the intermediate structure 100 and the floating body 40 into rotational motion.

[0142] More specifically, the first power generation mechanisms 50A and 50B each include a first rack rail 51, a first generator gear 52, and a first device generator 53.

[0143] The first rack rail 51 is provided on the first columnar body 103. More specifically, the first rack rail 51 is attached to the outer circumferential surface of the first columnar body 103. The first rack rail 51 is positioned so as not to interfere with the roller 42 described above. The first rack rail 51 extends in the X direction and is insertable into the first cavity 41. Because the rotational motion of the first columnar body 103 about an axis along the X direction is suppressed by the guide rail described above, the first rack rail 51 can mesh with the first generator gear 52.

[0144] The first generator gear 52 and the first device generator 53 are supported by the floating body 40.

[0145] The first power generation mechanisms 50A and 50B according to this embodiment differ from the first power generation mechanisms 50A and 50B according to the first embodiment in that the columnar body performing relative translational motion is the first columnar body 103 of the intermediate structure 100, rather than the first columnar body 22 of the platform 20. Other than this, the first power generation mechanisms 50A and 50B according to this embodiment may have the same configuration as the first power generation mechanisms 50A and 50B according to the first embodiment.

[0146] The second power generation mechanisms 120A and 120B are configured to convert the relative translational motion between the second columnar body 23 of the platform 20 and the intermediate structure 100 into rotational motion. The second power generation mechanisms 120A and 120B according to this embodiment may have the same configuration as the second power generation mechanisms 120A and 120B according to the sixth embodiment.

[0147] As shown in Figure 22, the first power generation mechanisms 50A and 50B according to this embodiment each include a first transmission 55 interposed between a first rack rail 51 and a first generator gear 52. The first transmission 55 includes a first transmission gear 56. Similarly, the second power generation mechanisms 120A and 120B according to this embodiment each include a second transmission 125 interposed between a second rack rail 121 and a second generator gear 122. The second transmission 125 includes a second transmission gear 126.

[0148] The moment of inertia of the rotor 54 of the first generator 53 is J. 2a The module radius of the first transmission gear 56 is r a2 The speed increase rate of the first transmission gear 56 and the first generator gear 52 is set to ε 2a Therefore, the inertial mass m s3a This can be expressed by the following equation (36).

number

[0149] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the dynamic model shown in Figure 19 above. The formulation of the dynamic model is expressed by equations (26) to (35) as described above. Mathematically, the inertial mass m, which was ignored in the sixth embodiment, is represented. s3a The point of considering this is new.

[0150] The results of determining the frequency characteristics according to this embodiment are shown in Figures 23 and 24. Figure 23 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device 10 in Figure 22. Figure 24 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device 10 in Figure 22.

[0151] The difference between the response diagrams shown in Figures 23 and 24 according to this embodiment and the response diagrams shown in Figures 20 and 21 according to the sixth embodiment will be explained. The difference is that the response diagrams shown in Figures 20 and 21 show three natural frequency peaks, whereas the response diagrams shown in Figures 23 and 24 do not show a peak at the third natural frequency. This is due to the inertial mass m s3a This is because the cutoff frequency was set to the third natural frequency. As a result, compared to the case without a vibration damping mechanism, the displacement x of the platform 20 is reduced over a wide range of 0.02 Hz and above. 3a , x 3b This can be suppressed so that the amplitude becomes smaller. Also, the relative displacement |(x 2a -x 1a )|,|(x 2b -x 1b )| and simultaneously relative displacement|(x 3a -x 2a )|,|(x 3b -x 2b Because a )| occurs, in addition to the output of the second device generator 123, the output of the first device generator 53 is obtained.

[0152] As described above, according to this embodiment, each vibration isolation mechanism 30A to 30D includes a first power generation mechanism 50A, 50B and a second power generation mechanism 120A, 120B. The first power generation mechanisms 50A, 50B convert the relative translational motion between the first columnar body 103 of the intermediate structure 100 and the floating body 40 into rotational motion, and the second power generation mechanisms 120A, 120B convert the relative translational motion between the second columnar body 23 of the platform 20 and the intermediate structure 100 into rotational motion. This increases the power generation amount of each vibration isolation mechanism 30A to 30D. Furthermore, it is possible to suppress the propagation of vibrations from the floating body 40 to the platform 20 via the intermediate structure 100, thereby suppressing vibrations of the platform 20.

[0153] (Eighth embodiment) Next, a floating platform device according to the eighth embodiment will be described using Figures 25 to 28.

[0154] In the eighth embodiment shown in Figures 25 to 28, the main difference is that the first columnar body of the platform includes a first buoyancy-receiving section that is submerged and receives buoyancy; the other configurations are substantially the same as those of the third embodiment shown in Figures 12 to 14. In Figures 25 to 28, the same reference numerals are used for parts that are the same as those in the third embodiment shown in Figures 12 to 14, and detailed descriptions are omitted. Figure 25 is a schematic cross-sectional view showing a floating platform device according to the eighth embodiment.

[0155] As shown in Figure 25, the first cavity 41 of the floating body 40 in this embodiment penetrates the floating body 40. The first columnar body 22 of the platform 20 penetrates the first cavity 41.

[0156] The first columnar body 22 includes a first buoyancy-receiving portion 25. The first buoyancy-receiving portion 25 is the part that is submerged in water and receives buoyancy. As shown in Figure 25, the lower end of the first columnar body 22 may be located below the floating body 40. Water has entered the first cavity 41.

[0157] In this way, the first columnar body 22 floats on the water. Therefore, the first columnar body 22 vibrates under the excitation force of the wave and can be considered to be elastically coupled to the stationary frame. To illustrate this, in Figure 25, the first columnar body 22 is elastically coupled to the stationary frame by a second virtual elastic body 130 having a spring constant k1. The second virtual elastic body 130 is composed of a buoyancy spring. In Figure 25, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30A is k 1a As shown, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30B is k 1b This is shown. The second virtual elastic body 130 is not used to indicate the presence of a spring member, but rather to schematically show that the first columnar body 22 is supported in the X direction by a force from the surrounding water. The natural frequency of the first columnar body 22 may be designed to be sufficiently detuned with respect to the frequency of the wave.

[0158] As shown in Figure 25, an elastic body connecting portion 26 to which the first elastic body 70 is connected is fixed to the first columnar body 22. In the same manner as the elastic body connecting portion 24 shown in Figures 17 and 18 above, two elastic body connecting portions 26 may be fixed to the first columnar body 22. In this case, the two elastic body connecting portions 26 may be arranged symmetrically with respect to the first columnar body 22.

[0159] As shown in Figure 25, the first power generation mechanisms 50A and 50B according to this embodiment each include a first speed change gear 56 interposed between the first rack rail 51 and the first generator gear 52.

[0160] The number of teeth of the first gear 56 of the vibration isolation mechanism 30A is Z 1a The number of teeth of the first generator gear 52 is set to Z 2a In this case, the rotational speed ratio of the first generator gear 52 and the first transmission gear 56, i.e., the speed increase rate ε, is... a This can be expressed as follows:

number

[0161] The moment of inertia of the rotor 54 of the first generator 53 is J. a The module radius of the first transmission gear 56 is r a Therefore, the inertial mass m sa This is expressed as follows: This inertial mass m sa This acts on the relative translational motion in the X direction that occurs between the first columnar body 22 and the floating body 40.

number

[0162] Therefore, the speed increase rate ε of the first transmission 55 in equation (37) a By changing this, the inertial mass m can be calculated by equation (38). sa It can be changed.

[0163] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the dynamic model shown in Figure 26. As before, it is treated as a two-dimensional problem in the XZ plane.

[0164] As can be seen by comparing it with the mechanical model in Figure 4, the mechanical model in Figure 26 is the same as the mechanical model in Figure 4 but with a spring constant k. 1a , k 1b Along with the addition of the damping constant c, 1a , c 1b This is considered a model with added features.

[0165] The center of the first columnar body 22 is located at a distance a from the origin O in the X direction. The center of the floating body 40 is located at a distance b from the origin O in the X direction. In vibration isolation mechanisms 30A and 30B, the first columnar body 22 and the floating body 40 are arranged coaxially, so in reality a=b, but in the model diagram of Figure 26, the distances a and b are made different so that they do not overlap. The platform 20 is a rigid body, and its center of gravity G is located on the X axis extending from the origin O. Let M be the mass of the platform 20, and I be the moment of inertia around the Y axis at the center of gravity G. The mass M and moment of inertia I include the inertial mass of each first columnar body 22 and each first rack rail 51. The mass of the floating body 40 of vibration isolation mechanism 30A is m 1a The mass of the vibration isolation mechanism 30B is m 1b Let's assume the mass is m. 1a This includes not only the mass of the first generator gear 52 and the first device generator 53 supported by the floating body 40 of the vibration isolation mechanism 30A, but also fluid effects such as the load mass of water. Similarly, mass m 1b This includes not only the mass of the first generator gear 52 and the first device generator 53 supported by the floating body 40 of the vibration isolation mechanism 30B, but also fluid effects such as the added mass of water. 1a , m 1b Each of these flows through the first virtual elastic body 60 due to buoyancy to the water surface w a , w b It is connected. The spring constant of the first virtual elastic body 60 is k 2a , k 2b It is expressed as follows: Damping due to buoyancy is c 2a , c 2b It is expressed as follows. On the other hand, mass m 1a , m 1b The spring constant k of the first elastic body 70 is 3a , k 3b The mass and moment of inertia M and I of platform 20 are connected via c. 3a , c 3b m represents damping. s3a , m s3b k represents the inertial mass. The fluid force acting on the first columnar body 22 is equal to the spring constant k. 1a , k 1b and damping constant c 1a , c1b It is represented as follows.

[0166] Since the two vibration isolation mechanisms 30A and 30B have the same structure, m 1a =m 1b =m1, m sa =m sb =m s , k 1a =k 1b =k1, k 2a =k 2b =k², k 3a =k 3b =k3, c 1a =c 1b =c1, c 2a =c 2b =c2, c 3a =c 3b = c3.

[0167] Assuming the wave wavelength is sufficiently long compared to the length of platform 20, the water surface w a -w b Assume that the plane is maintained. Let X0 be the translational displacement of the wave in the X direction at the origin O, and Θ0 be the rotational displacement around the Y axis. If Θ0 is small, the water surface w a , w b Translational displacement X 1a , X 1a , X 3a , X 3b It can be expressed using X0 and Θ0 as follows:

number

number

number

number

[0168] Let x0 be the translational displacement in the X direction at the center of gravity G of platform 20, and Θ0 be the rotational displacement around the Y axis. If Θ0 is small, the translational displacement in the X direction of platform 20 and vibration isolation mechanisms 30A and 30B is x 2a , x 2b This can be expressed as follows:

number

number

[0169] x 3a , x 3b This can be expressed as follows:

number

number

[0170] The dynamic model in Figure 26 has 4 degrees of freedom, and the equations of motion are expressed in matrix form as follows:

number

[0171] The mass matrix [M], damping matrix [C], and stiffness matrix [K] in equation (47) are expressed as follows:

number

number

number

[0172] The displacement vector x and the external force vector F in equation (47) are expressed as follows:

number

number

[0173] However, α and β are expressed as follows:

number

number

[0174] Comparing the matrices in equations (48) to (50) with those in equations (13) to (15), in the dynamic model shown in Figure 26, the damping matrix [C] and stiffness matrix [K] are x 1a , x 2a The pair and x 1b , x 2b It can be seen that a coupling occurs between the pairs.

[0175] Here, in order to determine the frequency response, we assume the external force vector F in equation (16) is as follows.

number

number

[0176] Corresponding to equation (56), the response x is,

number

number

number

[0177] By solving equation (59), the response x can be found using equation (57).

[0178] The frequency characteristics of this embodiment were determined based on the analysis method described above. The calculation results are shown in Figures 27 and 28. Figure 27 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device in Figure 25, and Figure 28 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device in Figure 25.

[0179] The amplitude of heave vibration and the amplitude of pitting vibration are approximately the same because

number

[0180] Focusing on the amplitude, it can be seen that the amplitude of the displacement of platform 20 is significantly lower at the peak near 0.02 Hz, which corresponds to the first natural frequency, compared to the case without vibration isolation mechanisms 30A and 30B (shown by the dashed line). In the region above the first natural frequency, the two are almost the same, and even with vibration isolation mechanisms 30A and 30B installed, no peak at the second natural frequency occurs. This is because the cutoff frequencies of vibration isolation mechanisms 30A and 30B are set to match the second natural frequency. In contrast, the amplitude of the floating body 40 when vibration isolation mechanisms 30A and 30B are installed shows peaks near 0.02 Hz and near 0.1 Hz, the former being the first natural frequency and the latter the second natural frequency. The base of the second peak is broad, and in the region of 0.05 Hz to 0.2 Hz, which is the frequency of waves, the relative displacement |(x 2a -x 1a )|,|(x 2b -x 1b As the value of )| increases, the output of the first device generator 53 can be obtained.

[0181] According to this embodiment, heave vibration and pitching vibration of the platform 20 can be suppressed in the wave frequency region, and power can be extracted from the relative translational motion between the platform 20 and the floating body 40.

[0182] Thus, according to this embodiment, the first columnar body 22 of the platform 20 includes a first buoyancy receiving portion 25 that is submerged in water and receives buoyancy. In this case as well, the first power generation mechanisms 50A and 50B can convert vibration energy into electrical energy and generate electricity.

[0183] (Ninth Embodiment) Next, a floating platform device according to the ninth embodiment will be described using Figures 29 to 31.

[0184] In the ninth embodiment shown in Figures 29 to 31, the main difference is that relative translational motion is converted into rotational motion by screwing the male threaded portion of the generator's rotating shaft into the female threaded portion provided in the through-hole of the platform. Other configurations are substantially the same as those of the eighth embodiment shown in Figures 25 to 28. In Figures 29 to 31, the same reference numerals are used for parts identical to those of the eighth embodiment shown in Figures 25 to 28, and detailed descriptions are omitted. Figure 29 is a schematic vertical outer diameter view showing the floating platform device according to the ninth embodiment. Figure 30 is a schematic plan view showing the floating platform device of Figure 29. Figure 31 is a cross-sectional view along line HH showing the vibration isolation mechanism of Figure 30.

[0185] As shown in Figure 29, this embodiment describes a floating platform device 10 that is applied to a semi-submerged offshore wind power generation facility.

[0186] As shown in Figure 29, the platform 20 of the floating platform device 10 according to this embodiment includes a third columnar body 141 located in the center and a plurality of fourth columnar bodies 142 located around the third columnar body 141 when viewed in the X direction. The wind turbine 2 is supported on the third columnar body 141 via a tower 3 (see Figure 1). In Figure 29, an example is shown in which the platform 20 is composed of three fourth columnar bodies 142, but the number of fourth columnar bodies 142 can be any number of two or more.

[0187] The three fourth prisms 142 are arranged so that they form the vertices of an equilateral triangle when viewed in the X direction. The third prism 141 is positioned at the center of this equilateral triangle.

[0188] The third columnar body 141 and each of the fourth columnar bodies 142 are connected by an upper arm 143 and a lower arm 144. The upper arm 143 is positioned above the lower arm 144, and the lower arm 144 is positioned below the upper arm 143. The upper arm 143 and the lower arm 144 extend horizontally and are arranged radially when viewed in the X direction, as shown in Figure 30. The upper arm 143 connects the upper part of the third columnar body 141 to the upper part of the fourth columnar body 142. The lower arm 144 connects the lower part of the third columnar body 141 to the lower part of the fourth columnar body 142.

[0189] The inner end of each lower arm 144 and the outer end of the corresponding upper arm 143 are connected by an arm beam 145. More specifically, the inner end of a lower arm 144 connected to a fourth columnar body 142 and the outer end of an upper arm 143 located above this lower arm 144 are connected by an arm beam 145. The inner end of the lower arm 144 is the end connected to the third columnar body 141, and the outer end of the upper arm 143 is the end connected to the fourth columnar body 142. The arm beams 145 are arranged radially so as to overlap with the upper arm 143 and the lower arm 144 when viewed in the X direction.

[0190] Two adjacent fourth columnar bodies 142 are connected by connecting beams 146. The three connecting beams 146 are arranged in a ring around the third columnar body 141 when viewed in the X direction. The connecting beams 146 connect the upper parts of the two fourth columnar bodies 142. In the example shown in Figure 29, the connecting beams 146 are positioned at the same height as the upper arm 143.

[0191] A rod 147 extends upward from the upper surface of the fourth columnar body 142. The rod 147 extends in the X direction. A stay 148 is provided at the top of the rod 147. Multiple stays 148 extend radially from one rod 147. In the example shown in Figure 30, four stays 148 extend from one rod 147, but the four stays 148 are not evenly distributed around the rod 147. This is because a notch 43, which will be described later, is provided in the floating body 40. The stays 148 are positioned above the floating body 40. The stays 148 extend horizontally, and a hub 149 is provided at the outer end of the stay 148. The rod 147, stays 148, and hub 149 are components of the platform 20, fixed to the fourth columnar body 142, and perform translational motion together.

[0192] Each of the fourth columnar bodies 142 includes a first buoyancy receiving portion 142a. More specifically, the first buoyancy receiving portion 142a is provided at the lower part of the fourth columnar body 142. The lower end of the fourth columnar body 142 may be located below the floating body 40. Water has entered the first cavity 41 of the floating body 40.

[0193] In this way, the fourth columnar body 142 floats on the water. Therefore, since the fourth columnar body 142 vibrates under the excitation force of the wave, it can be considered to be elastically coupled to the stationary frame. To illustrate this, in Figure 29, the fourth columnar body 142 is elastically coupled to the stationary frame by a second virtual elastic body 130 having a spring constant k1.

[0194] The third columnar body 141 may also float in the water. However, the outer diameter of the third columnar body 141 is smaller than the outer diameter of the fourth columnar body 142. In this case, the buoyant force exerted on the third columnar body 141 by the water is small and can be ignored in the mechanical model.

[0195] As shown in Figure 31, the platform 20 includes a through hole 150. The through hole 150 is provided in the hub 149 described above.

[0196] As shown in Figures 29 and 30, the platform 20 according to this embodiment is supported by three vibration isolation mechanisms 30E to 30G. Each of the vibration isolation mechanisms 30E to 30G includes a floating body 40 and a plurality of first power generation mechanisms 160. In this embodiment, each vibration isolation mechanism 30E to 30G includes four first power generation mechanisms 160, but the number of first power generation mechanisms 160 is arbitrary as long as there are two or more.

[0197] The floating body 40 according to this embodiment includes a first cavity 41 extending in the X direction. The fourth columnar body 142 described above is inserted into the first cavity 41. The diameter of the first cavity 41 is larger than the outer diameter of the fourth columnar body 142. Multiple rollers 42 attached to the wall surface of the first cavity 41 are capable of rolling against the outer circumferential surface of the fourth columnar body 142. This allows for smooth relative translational motion between the floating body 40 and the fourth columnar body 142. Guide rails (not shown) extending in the X direction may be attached to the outer circumferential surface of the fourth columnar body 142. This prevents the fourth columnar body 142 from performing rotational motion about an axis along the X direction relative to the floating body 40. It also allows for guidance of the relative translational motion between the floating body 40 and the fourth columnar body 142 in the X direction.

[0198] The floating body 40 is connected to the platform 20 via the first elastic body 70. The first elastic body 70 may also be connected to the floating body 40 and the stay 148.

[0199] As shown in Figure 30, the floating body 40 is provided with a notch 43. The notch 43 is provided to prevent the upper arm 143 and arm beam 145 described above from interfering with the floating body 40.

[0200] The first power generation mechanism 160 is configured to generate electricity by converting the relative translational motion between the platform 20 and the floating body 40 into rotational motion.

[0201] The first power generation mechanism 160 includes a female screw portion 161, a generator rotating shaft 162, a male screw portion (screw portion 163), and a first device generator 164.

[0202] The female threaded portion 161 is provided in the through hole 150 described above. The generator rotating shaft 162 extends in the X direction and passes through the through hole 150. The generator rotating shaft 162 is supported by the floating body 40. The screw threaded portion 163 is formed on the generator rotating shaft 162 and is screwed into the female threaded portion 161.

[0203] The first generator 164 is supported by the floating body 40. The first generator 164 may also be embedded in the floating body 40. A generator rotating shaft 162 is connected to the first generator rotor of the first generator 164.

[0204] Since the screw thread portion 163 of the generator rotating shaft 162 is screwed into the female thread portion 161 provided in the through hole 150 of the hub 149, the generator rotating shaft 162 rotates when relative translational motion occurs between the platform 20 and the floating body 40. This rotation causes the first generator rotor of the first device generator 164 to rotate, and the first device generator 164 generates electricity.

[0205] The first power generation mechanism 160 may include a speed changer 165 interposed between the generator rotating shaft 162 and the first device generator 164. In this case, the rotational speed of the first generator rotor can be adjusted. For example, the rotational speed of the first generator rotor can be increased by adjusting the speed increase rate of the speed changer 165. The speed changer 165 may be, for example, a planetary gear type speed changer.

[0206] Moment of inertia J of the rotor of the first generator of the first device generator 164 a , acceleration rate ε a Using the lead l of the screw, the inertial mass m sa This is expressed as follows: This inertial mass m sa This acts on the relative translational motion in the X direction that occurs between the fourth columnar body 142 and the floating body 40.

number

[0207] This embodiment, configured in this way, is compared with the eighth embodiment. The changes are that the number of vibration isolation mechanisms has changed from four to three, and the mechanism for converting relative translational motion to rotational motion has changed from gears to screws. However, in the mechanical model according to this embodiment, the inertial mass represented by equation (61) is connected between the platform 20 and the floating body 40. Therefore, as with the eighth embodiment, heave vibration and pitching vibration of the platform 20 can be suppressed in the wave frequency domain, and power can be extracted from the relative translational motion between the platform 20 and the floating body 40. Furthermore, the structure allows for the addition of vibration isolation mechanisms 30E to 30G, including the floating body 40, to the platform 20. Therefore, it is possible to add vibration isolation mechanisms 30E to 30G to existing semi-submerged offshore wind power generation facilities to give them wave power generation capabilities. Adding wave power generation equipment not only increases electrical output but can also function as a backup power source in the event of a loss of external power, contributing to improved reliability of semi-submerged offshore wind power generation facilities.

[0208] When the floating platform device 10 configured in this way is viewed in the Y direction, vibration isolation mechanisms 30E to 30G are positioned on both sides of the platform 20 in the lateral direction relative to the center of gravity G, similar to the floating platform device 10 shown in Figures 10 and 11. In other words, in the example shown in Figure 29, vibration isolation mechanisms 30E and 30F are positioned on both sides of the Z direction when viewed in the Y direction. Vibration isolation mechanism 30E is positioned to the left of the center of gravity G, and vibration isolation mechanism 30F is positioned to the right of the center of gravity G. In the example shown in Figure 29, vibration isolation mechanism 30G is positioned between vibration isolation mechanism 30E and vibration isolation mechanism 30F.

[0209] As described above, according to this embodiment, the screw thread portion 163 of the generator rotating shaft 162 is screwed into the female thread portion 161 provided in the through hole 150 of the platform 20. The generator rotating shaft 162 is connected to the first device generator 164 supported by the floating body 40. This allows the relative translational motion between the platform 20 and the floating body 40 to be converted into rotational motion, enabling the first device generator 164 to generate electricity and suppressing vibrations of the platform 20. For this reason, the first power generation mechanism 160 can be easily constructed.

[0210] Furthermore, according to this embodiment, the first power generation mechanism 160 includes a transmission 165 interposed between the generator rotating shaft 162 and the first device generator 164. This allows the rotational speed of the first generator rotor to be adjusted by the transmission 165, thereby adjusting the power output of the first device generator 164. In addition, by adjusting the speed increase rate of the transmission 165, vibrations of the platform 20 can be effectively suppressed, and the power output of the first device generator 164 can be effectively increased.

[0211] In the above-described embodiment, an example was described in which the first power generation mechanism 160, including the screw portion 163, generates electricity by converting the relative translational motion between the platform 20 and the floating body 40 into rotational motion. However, the embodiment is not limited to this. For example, the second power generation mechanisms 120A and 120B (see Figure 6, etc.), which generate electricity by converting the relative translational motion between the platform 20 and the intermediate structure 100 into rotational motion, may have a mechanism using the screw portion 163 as shown in Figures 29 to 31, rather than a mechanism using the second generator gear 122. In this case as well, the relative translational motion between the platform 20 and the intermediate structure 100 can be converted into rotational motion, and the second device generator 123 can generate electricity. In this case, a similar speed change device may be interposed between the generator rotating shaft and the second device generator 123. Furthermore, the first device generator and the second device generator in the seventh embodiment described above or the eleventh embodiment described later may each have a mechanism using the screw portion 163.

[0212] (Tenth embodiment) Next, a floating platform device according to the tenth embodiment will be described using Figures 32 to 35.

[0213] In the tenth embodiment shown in Figures 32 to 35, the main difference is that the second columnar body of the platform includes a second buoyancy receiving section that is submerged and receives buoyancy. The other configurations are substantially the same as those of the sixth embodiment shown in Figures 17 to 21. In Figures 32 to 35, the same reference numerals are used for parts that are the same as those in the sixth embodiment shown in Figures 17 to 21, and detailed descriptions are omitted. Figure 32 is a schematic cross-sectional view showing a floating platform device according to the tenth embodiment.

[0214] As shown in Figure 32, the first cavity 41 of the floating body 40 in this embodiment penetrates the floating body 40. The second columnar body 23 of the platform 20 penetrates both the second cavity 101 and the first cavity 41.

[0215] The second columnar body 23 includes a second buoyancy-receiving portion 27. The second buoyancy-receiving portion 27 is the part that is submerged and receives buoyancy. As shown in Figure 32, the lower end of the second columnar body 23 may be located below the floating body 40. Water has entered the first cavity 41.

[0216] In this way, the second columnar body 23 floats on the water. Therefore, the second columnar body 23 vibrates under the excitation force of the wave and can be considered to be elastically coupled to the stationary frame. To illustrate this, in Figure 32, the second columnar body 23 is elastically coupled to the stationary frame by a second virtual elastic body 130 having a spring constant k1. The second virtual elastic body 130 is composed of a buoyancy spring. In Figure 32, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30A is k 1a As shown, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30B is k 1b This is shown. The second virtual elastic body 130 is not used to indicate the presence of a spring member, but rather to schematically show that the second columnar body 23 is supported in the X direction by a force from the surrounding water. The natural frequency of the second columnar body 23 may be designed to be sufficiently detuned with respect to the frequency of the wave.

[0217] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the dynamic model shown in Figure 33. The dynamic model shown in Figure 19 according to the sixth embodiment is compared with the dynamic model shown in Figure 33 according to this embodiment. Degrees of freedom x of platform 20 4a , x 4b , and the degrees of freedom of the water surface X 2a , X 2b It has been added. Also, degrees of freedom x 4a , X 2a The spring constant k 1a , damping constant c 1a It is inserted. Degrees of freedom x 4b , X 2b The spring constant k 1b , damping constant c 1bThese are inserted respectively. However, since the vibration isolation mechanism 30A and the vibration isolation mechanism 30B have the same structure, k 1a =k 1b =k1, c 1a =c 1b Let = c1. Note that in the dynamic model in Figure 33, the degrees of freedom x are set to allow for generality. 1a and degrees of freedom x 2a Between them is the inertial mass m s3a However, degrees of freedom x 1b and degrees of freedom x 2b During the interval, inertial mass m s3b Each of these is inserted. s3a =m s3b =m s This embodiment can be represented by treating it as =0. The degrees of freedom of the dynamic model in Figure 33 are 6, and the equations of motion are expressed in matrix form as follows.

number

[0218] The mass matrix [M], damping matrix [C], and stiffness matrix [K] in equation (62) are expressed as follows:

number

number

number

[0219] The displacement vector x and the external force vector F in equation (62) are expressed as follows:

number

number

[0220] In the dynamic model shown in Figure 33, the damping matrix [C] and the stiffness matrix [K] are x 1a, x 2a , x 3a The pair and x 1b , x 2b , x 3b It can be seen that a coupling occurs between the pair.

[0221] Here, in order to determine the frequency response, the external force vector F in equation (62) can be expressed as follows.

number

[0222] Corresponding to equation (68), the response x is,

number

number

number

[0223] By solving equation (70), the response x can be found using equation (69).

[0224] The frequency characteristics of this embodiment were determined based on the analysis method described above. The calculation results are shown in Figures 34 and 35. Figure 34 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device in Figure 32, and Figure 35 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device in Figure 32.

[0225] The amplitude of heave vibration and the amplitude of pitting vibration are approximately the same because

number

[0226] As shown in the amplitude of Figure 34, due to the increased degrees of freedom, in this embodiment there are three natural frequencies of 0.215Hz, 0.11Hz, and 0.38Hz near 0.02Hz, 0.1Hz, and 0.4Hz, but the displacement x of platform 20 3a , x 3b No peak in the second natural frequency near 0.1 Hz is observed. This is consistent with the amplitude shown in Figure 35. This is due to the inertial mass m s4 This indicates that the cutoff frequency coincides with the second natural frequency. Due to this effect, the displacement x of the platform 20 in the 0.02~0.25Hz range is reduced compared to the case without a vibration damping mechanism. 3a , x 3b It can be seen that the amplitude is small and suppressed. In the region above 0.25 Hz, there is a third natural frequency, so the displacement x of platform 20 3a , x 3b Although the frequency of the waves increases, the effect of the waves is small because the wave frequency is 0.05Hz to 0.2Hz. On the other hand, in this wave frequency range, there is a large relative displacement |(x 3a -x 2a ) / X0|, |(x 3b -x 2b ) / X0|, |(x 3a -x 2a ) / bΘ0|、|(x 3b -x 2b ) / bΘ0| occurs. The second device generator 123 has this relative displacement |(x 2a -x 1a )|,|(x 2b -x 1b Because it is driven by wave power, it can generate electricity using wave power.

[0227] According to this embodiment, vibration propagation from the floating body 40 can be suppressed for both heave vibration and pitching vibration of the platform 20 caused by waves, and power generation by wave power can be realized.

[0228] Thus, according to this embodiment, the second columnar body 23 of the platform 20 includes a second buoyancy receiving portion 27 that is submerged in water and receives buoyancy. In this case as well, the second power generation mechanisms 120A and 120B can convert vibration energy into electrical energy and generate electricity.

[0229] (Embodiment 11) Next, a floating platform device according to the eleventh embodiment will be described with reference to Figures 36 to 38.

[0230] In the 11th embodiment shown in Figures 36 to 38, the main difference is that the second columnar body of the platform includes a second buoyancy receiving section that is submerged and receives buoyancy; the other configurations are substantially the same as those of the 7th embodiment shown in Figures 22 to 24. In Figures 36 to 38, the same reference numerals are used for parts that are the same as those in the 7th embodiment shown in Figures 22 to 24, and detailed descriptions are omitted. Figure 36 is a schematic cross-sectional view showing a floating platform device according to the 11th embodiment.

[0231] As shown in Figure 36, the first cavity 41 of the floating body 40 in this embodiment penetrates the floating body 40. The second cavity 101 of the intermediate structure 100 penetrates the intermediate structure 100. The second columnar body 23 of the platform 20 penetrates both the second cavity 101 and the first cavity 41. The first columnar body 103 of the intermediate structure 100 is inserted into the first cavity 41 but does not penetrate the first cavity 41.

[0232] The second columnar body 23 includes a second buoyancy-receiving portion 27. The second buoyancy-receiving portion 27 is the part that is submerged and receives buoyancy. As shown in Figure 36, the lower end of the second columnar body 23 may be located below the floating body 40. Water has entered the first cavity 41. In the example shown in Figure 36, water has also entered the second cavity 101. The lower end of the first columnar body 103 is submerged, but the buoyancy force that the first columnar body 103 receives from the water is considered to be negligibly small.

[0233] In this way, the second columnar body 23 floats on the water. Therefore, the second columnar body 23 vibrates under the excitation force of the wave and can be considered to be elastically coupled to the stationary frame. To illustrate this, in Figure 36, the second columnar body 23 is elastically coupled to the stationary frame by a second virtual elastic body 130 having a spring constant k1. The second virtual elastic body 130 is composed of a buoyancy spring. In Figure 36, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30A is k 1a As shown, the spring constant of the second virtual elastic body 130 corresponding to the vibration isolation mechanism 30B is k 1b This is shown. The second virtual elastic body 130 is not used to indicate the presence of a spring member, but rather to schematically show that the second columnar body 23 is supported in the X direction by a force from the surrounding water. The natural frequency of the second columnar body 23 may be designed to be sufficiently detuned with respect to the frequency of the wave.

[0234] As shown in Figure 36, an elastic body connecting portion 26 to which the first elastic body 70 is connected is fixed to the first columnar body 103. In the same manner as the elastic body connecting portion 24 shown in Figures 17 and 18 described above, two elastic body connecting portions 26 may be fixed to the first columnar body 103. In this case, the two elastic body connecting portions 26 may be arranged symmetrically with respect to the first columnar body 103.

[0235] The floating platform device 10 according to this embodiment, configured in this way, is schematically represented by the dynamic model shown in Figure 33. The formulation of the dynamic model is expressed by equations (62) to (71) above. Here, the inertial mass m, which was not considered in the tenth embodiment, is also represented. s3 This is taken into consideration.

[0236] The frequency characteristics of this embodiment were determined. The results are shown in Figures 37 and 38. Figure 37 is a response diagram showing the vibration transmission rate of heave vibration of the floating platform device in Figure 36, and Figure 38 is a response diagram showing the vibration transmission rate of pitching vibration of the floating platform device in Figure 36.

[0237] The difference between the response diagrams shown in Figures 37 and 38 according to this embodiment and the response diagrams shown in Figures 34 and 35 according to the tenth embodiment will be explained. The difference is that while the response diagrams shown in Figures 34 and 35 show peaks of three natural frequencies, the response diagrams shown in Figures 36 and 37 do not show a peak of the third natural frequency. This is due to the inertial mass m s3a This is because the cutoff frequency was set to the third natural frequency. As a result, the displacement x of the platform 20 over a wide range of 0.02 Hz and above compared to the case without a vibration damping mechanism. 3a , x 3b This can be suppressed so that the amplitude becomes smaller. Also, the relative displacement |(x 2a -x 1a )|,|(x 2b -x 1b )| and simultaneously relative displacement|(x 3a -x 2a )|,|(x 3b -x 2b Because a )| occurs, in addition to the output of the second device generator 123, the output of the first device generator 53 is obtained. As described above, according to the embodiments of the present invention, heap vibration and pitching vibration of a floating platform structure can be suppressed simultaneously, and power generation can be performed using wave power.

[0238] Thus, according to this embodiment, the second columnar body 23 of the platform 20 includes a second buoyancy receiving portion 27 that is submerged in water and receives buoyancy. In this case as well, the second power generation mechanisms 120A and 120B can convert vibration energy into electrical energy and generate electricity.

[0239] According to the embodiments described above, vibrations can be suppressed, and vibration energy can be converted into electrical energy to generate electricity.

[0240] While several embodiments of the present invention have been described, these embodiments are presented as examples only and are not intended to limit the scope of the invention. These novel embodiments can be implemented in a variety of other forms, and various omissions, substitutions, and modifications can be made without departing from the spirit of the invention. These embodiments and their variations are included in the scope and spirit of the invention, as well as in the claims of the invention and its equivalents. Naturally, these embodiments can also be combined in part as appropriate within the scope of the spirit of the invention. [Explanation of symbols]

[0241] 10: Water platform device, 20: Platform, 22: First columnar body, 23: Second columnar body, 25: First buoyancy support section, 27: Second buoyancy support section, 30A~30G: Vibration isolation mechanism, 40: Floating body, 41: First cavity section, 50A, 50B: First power generation mechanism, 51: First rack rail, 52: First generator gear, 53: First device generator, 55: First transmission, 100: Intermediate Structure, 101: Second cavity, 103: First columnar body, 120A, 120B: Second power generation mechanism, 121: Second rack rail, 122: Second generator gear, 123: Second device generator, 125: Second transmission, 150: Through hole, 160: First power generation mechanism, 161: Female screw section, 162: Generator rotating shaft, 163: Screw thread section, 164: First device generator, 165: Transmission

Claims

1. A floating platform device located on the water, Platform and The platform comprises a plurality of vibration isolation mechanisms, The vibration isolation mechanism is, A floating body that floats on water, elastically coupled to the platform, and capable of relative translational motion in a first direction with respect to the platform, The system includes a first power generation mechanism that generates electricity by converting the relative translational motion between the platform and the floating body into rotational motion, When viewed in at least one of the directions perpendicular to the first direction, the vibration isolation mechanism is positioned on both sides of the platform's center of gravity in the lateral direction. The platform includes through holes, The first power generation mechanism is a floating platform device comprising: a female threaded portion provided in the through hole; a generator rotating shaft extending in the first direction and passing through the through hole; a male threaded portion provided on the generator rotating shaft that screws into the female threaded portion; and a first device generator supported by the floating body and connected to the generator rotating shaft.

2. The floating platform device according to claim 1, wherein the first power generation mechanism includes a speed change device interposed between the generator rotating shaft and the first device generator.

3. A floating platform device located on the water, Platform and The platform comprises a plurality of vibration isolation mechanisms, The vibration isolation mechanism is, An intermediate structure elastically coupled to the platform and capable of relative translational movement in a first direction with respect to the platform, A floating body that floats on water, elastically coupled to the intermediate structure, and capable of relative translational motion in the first direction with respect to the intermediate structure, The system includes a second power generation mechanism that generates electricity by converting the relative translational motion between the platform and the intermediate structure into rotational motion, A floating platform device wherein the vibration isolation mechanism is arranged on both sides of the platform's center of gravity in the lateral direction when viewed in at least one of the directions perpendicular to the first direction.

4. The intermediate structure includes a second cavity extending in the first direction, The platform includes a second columnar body extending in the first direction and inserted into the second cavity, The floating platform device according to claim 3, wherein the second power generation mechanism includes a second rack provided on the second columnar body, a second generator gear that is interlocked with the second rack, and a second device generator supported by the intermediate structure and connected to the second generator gear.

5. The floating platform device according to claim 4, wherein the second power generation mechanism includes a second transmission interposed between the second rack and the second generator gear.

6. The floating body includes a first cavity that penetrates the floating body, The second cavity penetrates the intermediate structure, The second columnar body penetrates the second cavity and the first cavity, The floating platform device according to claim 4 or 5, wherein the second columnar body includes a second buoyancy receiving portion that is submerged and receives buoyancy.

7. The vibration isolation mechanism includes a plurality of the second power generation mechanisms, The floating platform device according to claim 4 or 5, wherein, when viewed in the first direction, the plurality of second power generation mechanisms are arranged rotationally symmetrically with respect to the second columnar body.

8. The platform includes through holes, The floating platform device according to claim 3, wherein the second power generation mechanism includes a female screw portion provided in the through hole, a generator rotating shaft extending in the first direction and passing through the through hole, a male screw portion provided on the generator rotating shaft that screws into the female screw portion, and a second device generator supported by the intermediate structure.

9. The floating platform device according to claim 8, wherein the second power generation mechanism includes a speed change device interposed between the generator rotating shaft and the second device generator.

10. The floating platform device according to claim 3, wherein the vibration isolation mechanism includes a first power generation mechanism that converts the relative translational motion between the intermediate structure and the floating body into rotational motion to generate electricity.

11. The floating body includes a first cavity extending in the first direction, The intermediate structure includes a first columnar body extending in the first direction and inserted into the first cavity, The floating platform device according to claim 10, wherein the first power generation mechanism includes a first rack provided on the first columnar body, a first generator gear that is interlocked with the first rack, and a first device generator supported on the floating body and connected to the first generator gear.

12. The floating platform device according to claim 11, wherein the first power generation mechanism includes a first transmission interposed between the first rack and the first generator gear.

13. The intermediate structure includes a second cavity extending in the first direction, The platform includes a second columnar body extending in the first direction and inserted into the second cavity, The first cavity penetrates the floating body, The second cavity penetrates the intermediate structure, The second columnar body penetrates the second cavity and the first cavity, The floating platform device according to claim 11 or 12, wherein the second columnar body includes a second buoyancy receiving portion that is submerged and receives buoyancy.

14. The vibration isolation mechanism includes a plurality of the first power generation mechanisms, The floating platform device according to claim 11 or 12, wherein, when viewed in the first direction, the plurality of first power generation mechanisms are arranged rotationally symmetrically with respect to the first columnar body.

15. The platform includes through holes, The floating platform device according to claim 10, wherein the first power generation mechanism includes a female screw portion provided in the through hole, a generator rotating shaft extending in the first direction and passing through the through hole, a male screw portion provided on the generator rotating shaft that screws into the female screw portion, and a first device generator supported on the floating body and connected to the generator rotating shaft.

16. The floating platform device according to claim 15, wherein the first power generation mechanism includes a speed control device interposed between the generator rotating shaft and the first device generator.

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