Semi-cylindrical shell floating breakwater with multi-stage energy dissipation and flexible mooring system

Abstract

The application discloses a semi-cylindrical shell floating breakwater with multi-stage energy dissipation and flexible mooring system, and belongs to the technical field of ocean engineering. The breakwater aims to solve the technical problems of limited energy dissipation efficiency, violent overall motion response and excessive stress on the mooring system of the existing floating breakwater under complex sea conditions. The breakwater comprises a floating unit, a semi-cylindrical shell and a floating box, and a plurality of rows of wave dissipation holes are arranged on the wave-encountering side of the shell; an energy dissipation and vibration reduction system arranged below the floating box, comprising a vertical connecting rod, a horizontal perforated vibration reduction heaving plate, a first vibration reduction damper arranged on the vertical connecting rod segment and a vertical perforated wave dissipation plate; and a flexible mooring system, comprising an anchor block arranged on the seabed, an anchor chain connecting the anchor block and the floating box and a second vibration reduction damper arranged on the anchor chain. The breakwater is mainly used for wave protection and energy dissipation in the port, coastal and offshore engineering areas.

Description

Technical Field

[0001] This invention relates to the field of marine engineering technology. More specifically, this invention relates to a semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system. Background Technology

[0002] Floating breakwaters, as marine engineering structures adapted to deep-water environments and designed to reduce their impact on seabed ecology, have gradually gained attention in recent years. Their basic working principle involves using floating bodies to impede wave propagation and disrupting the movement of water particles through the motion of these floating bodies, thereby dissipating wave energy and achieving wave dissipation. Compared to traditional bottom-mounted breakwaters, floating structures offer advantages such as strong adaptability to changes in water depth, lower requirements for seabed geological conditions, convenient construction and relocation, and relatively smaller impact on the marine hydrodynamic environment and ecology. However, in practical engineering applications and long-term operation, existing conventional floating breakwaters still generally face several unresolved technical challenges, restricting their full performance and reliability improvement.

[0003] Firstly, regarding wave dissipation performance, traditional floating breakwaters primarily rely on the reflection of the floating body above the water surface and the rigid body motion (such as heave and pitch) of the floating body under wave action to dissipate energy. This energy dissipation mechanism is relatively simple and effective for short-period waves, but its efficiency drops significantly for swells with concentrated energy and longer periods. The fundamental reason is that wave energy is not uniformly distributed in water, but rather decays exponentially from the surface to depth. Traditional floating structures are unable to effectively intervene in and dissipate the wave kinetic energy of the middle and lower water layers. Therefore, existing designs often suffer from narrow wave dissipation bandwidths and limited energy dissipation effects on long waves, making it difficult to meet the engineering requirements of open sea areas or environments with complex wave spectra.

[0004] Secondly, controlling the dynamic response of the structure under wave action is another prominent challenge. Under continuous wave load excitation, the floating body will exhibit multi-degree-of-freedom motion, including heave (vertical movement), pitch (forward and backward tilting), and roll (left and right swaying). Excessive amplitude of motion not only reduces the stability of the water area behind it, affecting mooring stability, but also leads to stress concentration and fatigue at structural connections, potentially causing long-term structural damage or even failure. Existing technologies typically focus on inertial suppression of motion by increasing the size or mass of the floating body, but this significantly increases material usage and cost, and is ineffective in suppressing high-frequency vibrations. How to effectively attenuate wave-induced vibrations in multiple directions without significantly increasing weight and cost remains a persistent technical challenge.

[0005] Furthermore, the long-term reliability and survivability of the mooring system face severe challenges. As a key subsystem for fixing the position of a floating breakwater, the mooring system directly bears the dynamic environmental loads transmitted from the floating body. Under the alternating effects of wind, waves, currents, and especially extreme sea states, the anchor chain is subjected to significant cyclic tensile forces and impact loads, making it highly susceptible to fatigue damage and even breakage, leading to the drift failure of the entire breakwater structure. Traditional mooring designs often focus on providing sufficient static mooring force, lacking a systematic solution for effectively buffering and dissipating the dynamic impact loads acting on the anchor chain. This makes the anchor chain a weak link in the floating breakwater system, and its fatigue life directly affects the operational safety and maintenance cycle of the overall structure.

[0006] Furthermore, the aforementioned problems are interconnected, increasing the difficulty of comprehensive solutions. For example, insufficient wave-damping efficiency means that more wave energy must be borne by the structure itself and its mooring system, exacerbating structural vibration and anchor chain loads; while excessive structural movement can, in turn, affect the stability of the wave-damping effect. Attempts to improve only one aspect (such as simply increasing the stiffness of the buoy or simply increasing the size of the anchor chain) often yield limited results and may lead to a surge in costs or other side effects.

[0007] Therefore, given the shortcomings of existing floating breakwaters in terms of efficient three-dimensional energy dissipation, multi-directional structural vibration suppression, and dynamic load buffering of mooring systems, there is an urgent need to explore new technological approaches. This requires developing integrated solutions that can synergistically improve wave dissipation performance, structural dynamic stability, and anchoring reliability, based on a deep understanding of the interaction mechanism between waves and structures, in order to meet the increasingly stringent requirements of marine engineering environments. Summary of the Invention

[0008] One object of the present invention is to solve at least the above-mentioned problems and to provide at least the advantages that will be described later.

[0009] Another objective of this invention is to provide a semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system. This solves the technical problem that traditional floating breakwaters have a single wave dissipation mechanism, which makes it difficult to efficiently dissipate wave energy at different water depths, especially with limited effectiveness in reducing long-period waves. It also solves the technical problem that the floating body's motion response under wave action is too large, affecting the stability of the sheltered water area and aggravating structural fatigue damage.

[0010] To achieve these objectives and other advantages of the present invention, a semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system is provided, comprising:

[0011] The floating unit includes a semi-cylindrical hull (specifically, a semi-cylindrical hull with an open structure at both ends) and a buoy connected to the bottom of the semi-cylindrical hull; the semi-cylindrical hull is provided with multiple wave-damping holes on the wave-facing side.

[0012] The energy dissipation and vibration reduction system, located below the pontoon, includes:

[0013] Multiple vertical connecting rods are arranged in a matrix, with the top of each vertical connecting rod connected to the bottom of the pontoon and the bottom extending downwards;

[0014] At least two layers of horizontally perforated vibration damping sway plates are fixedly sleeved on multiple vertical connecting rods at intervals along the vertical direction, and the at least two layers of horizontally perforated vibration damping sway plates divide each vertical connecting rod into multiple segments;

[0015] Multiple first vibration dampers are respectively installed on the segments of the vertical connecting rod, and are located between two adjacent layers of horizontal through-hole vibration damping sway plates, and between the pontoon and the uppermost horizontal through-hole vibration damping sway plate;

[0016] At least one vertical perforated wave-damping plate, the plate surface of which is arranged parallel to the wave incident direction, and the two ends of the vertical perforated wave-damping plate are respectively connected to the shells of two first vibration dampers located at the same height;

[0017] A flexible mooring system includes an anchor block on the seabed, an anchor chain connecting the anchor block to the bottom of the buoy, and a second vibration damper on the anchor chain.

[0018] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction and flexible mooring system has connectors on both sides of the buoy for connecting adjacent floating units, and a rotation damper is provided between the connectors.

[0019] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system has a vertical connecting rod comprising an inner column and an outer sleeve arranged coaxially, forming an annular cavity filled with magnetorheological fluid; a piezoelectric sensing layer is provided on the outer wall of the inner column, and a first electrode layer is covered on the outer surface of the piezoelectric sensing layer; a second electrode layer is correspondingly provided on the inner wall of the outer sleeve;

[0020] The inner column and the outer sleeve are connected by flexible pleated membranes at multiple axial intervals. The flexible pleated membranes seal the annular cavity and divide the annular cavity into multiple independent damping adjustment segments along the axial direction.

[0021] The vertical connecting rod is equipped with a controller. The signal input end of the controller is connected to the piezoelectric sensing layer, and the output end is connected to the first electrode layer and the second electrode layer of each damping adjustment segment.

[0022] The controller is configured to receive real-time electrical signals generated by the piezoelectric sensing layer due to the vibration or deformation of the rod, process the electrical signals into feedback values ​​characterizing the relative velocity or displacement between the inner column and the outer sleeve, and use the feedback values ​​as control variables. The controller is programmed to apply a regulating voltage to the electrode layer of each damping adjustment segment in a positive correlation with the absolute value of the control variable, and the polarity of the regulating voltage is configured such that the direction of the magnetorheological damping force generated by it is opposite to the direction of the relative velocity.

[0023] Preferably, the semi-cylindrical shell floating breakwater with multi-stage energy dissipation and vibration reduction and flexible mooring system has each layer of horizontal perforated vibration reduction heave plate as a detachable modular energy dissipation cylinder; each energy dissipation cylinder consists of an outer frame and multiple layers of staggered metal mesh grids inside the outer frame, the surface of the metal mesh grids is coated with a catalytic coating, and the porous elastic damping material blocks are located between the staggered gaps of the metal mesh grids;

[0024] The outer frame is connected to the vertical connecting rod through a quick-locking mechanism. The quick-locking mechanism consists of multiple eccentric cam locks evenly distributed around the circumference. The rotating shaft of each lock passes through the wall panel of the outer frame and is connected to the pre-tightening pressure plate at its inner end. When the lock is closed, the rotating shaft drives the pre-tightening pressure plate to press axially onto the vertical connecting rod.

[0025] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system includes a gravity anchoring platform on the seabed. Anchor blocks are distributed on the upper surface of the gravity anchoring platform via universal hinges. The anchor chain is divided into an upper chain segment and a lower chain segment, and a second vibration damper is connected between the upper and lower chain segments. The lower end of the lower chain segment is connected to the center of the gravity anchoring platform via a spherical bearing hinge.

[0026] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system has a sealed air chamber inside the semi-cylindrical hull that communicates with the pontoon (the air chamber forms a partially sealed space in the middle region of the hull, and the open structure at both ends does not affect its aerodynamic energy dissipation function); the air chamber is connected to an air storage tank located in the pontoon through a first pipe, and the air storage tank is connected to an air compressor located in the pontoon through a second pipe; the inner end of the wave-dissipating hole communicates with the air chamber; the wave-dissipating hole communicates with the air chamber (to interfere with and break the wave surface structure of the oncoming waves).

[0027] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring systems features horizontally perforated vibration-damping heave plates with their opening design parametrically adapted to the characteristic wave height H and average wave period T of the target sea area; wherein:

[0028] The aperture diameter d satisfies: H / 15≤d≤H / 8, and the aperture diameter on the same layer plate increases gradually from the center to the edge, with the aperture diameter in the edge region being 1.2 to 1.5 times that in the center region;

[0029] The overall permeability η of the plate is optimized based on the wave period T and satisfies the relationship: η=k×ln(T)+b, where k and b are coefficients related to the energy dissipation cylinder level, and the permeability of each layer of the plate decreases sequentially from top to bottom, with a permeability gradient difference of 5~10%.

[0030] Preferably, the semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system also includes a structurally optimized configuration of the system based on water depth and geological conditions.

[0031] When the deployment area is a shallow water area with a water depth of less than 20m, a simplified two-stage energy dissipation configuration is adopted, namely, two layers of horizontal perforated vibration damping heave plates and one layer of vertical perforated wave damping plate; and the foundation thickness t of the horizontal perforated vibration damping heave plates increases with the increase of water depth h, satisfying: t=t0+0.5×(h-10), where t0 is the base thickness in mm;

[0032] When the deployment area is a deep water area with a depth greater than 30m, an enhanced three-stage energy dissipation configuration is adopted, with the addition of a third layer of horizontal perforated vibration damping heave plate, and the lowest vertical perforated wave-dissipating plate extending downward to 3-5m above the seabed surface.

[0033] The design weight W of the anchor block is optimized for different seabed geological types: in silty soft soil foundations, W ≥ 1.5 × F max / μ s In sandy foundations, W ≥ F max / μ s Among them, F max To design the maximum anchor chain tension, μ s This represents the friction coefficient of the anchor block in the corresponding foundation.

[0034] Preferably, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system has a rated damping force F of the first and second vibration damping devices. d Must satisfy: 0.3 × F w ≤F d ≤0.7×F w F w This refers to the design wave impact force acting at the corresponding component connection location, calculated based on the Morrison equation.

[0035] Rotational damper, its torsional stiffness K t It matches the dimensions of the connected floating body unit, satisfying the empirical formula: K t =C×ρ×g×B 2×L×D, where ρ is the density of seawater, g is the gravitational acceleration, B is the width of a single floating unit, L is the length, C is the correlation coefficient ranging from 0.05 to 0.15, and D is the draft of the floating unit.

[0036] The present invention has at least the following beneficial effects:

[0037] 1. This invention constructs a three-dimensional energy dissipation system by setting up multiple layers of horizontal and vertical perforated plates. This structure guides water flow through the holes at different depths, generating continuous vortices and friction, thereby achieving layer-by-layer dissipation of wave energy along the water depth direction, significantly enhancing the ability to reduce long-period waves and broadening the effective wave dissipation frequency band. By setting multiple stages of first-stage vibration dampers on the vertical connecting rods, a series damping energy dissipation mechanism is formed. This design can effectively absorb and dissipate the heave motion energy caused by waves, suppress excessive movement of the floating body, help improve the stability of the water behind, and reduce the risk of fatigue damage to the structure itself. By integrating a second vibration damper into the anchor chain, a flexible buffer force transmission path is constructed. The second vibration damper can actively absorb and dissipate the dynamic impact load transmitted to the anchor chain, smoothing the load peak, thereby significantly reducing the stress amplitude and fatigue effect of the anchor chain, and improving the reliability and durability of the mooring system under long-term alternating loads.

[0038] 2. This invention adds connecting components with rotational dampers to both sides of the pontoon to connect multiple floating units in series. This structure significantly improves the overall integrity and motion coordination of the breakwater. The rotational dampers effectively limit the relative rotation between adjacent units, suppressing torsional deformation caused by wave phase differences, thereby reducing stress peaks and the risk of fatigue damage at the connection points. Furthermore, the dampers dissipate the relative motion energy between units, allowing the multi-unit breakwater to maintain a stable overall alignment even under the action of long waves, improving its protection of the waters behind and its survivability in complex sea conditions.

[0039] 3. This invention designs an intelligent adaptive vertical connecting rod based on magnetorheological fluid. A piezoelectric sensing layer detects the vibration deformation of the rod in real time, and the controller dynamically adjusts the damping characteristics of the magnetorheological fluid in each independent segment accordingly. This structure achieves real-time, active, and segmented control of the damping force of the energy dissipation and vibration reduction system, enabling it to accurately match the structural response caused by wave loads of different water depths and frequencies. This adaptive mechanism significantly improves the suppression effect on broadband wave excitation, avoiding the limitations of fixed parameters in traditional passive dampers. While enhancing vibration reduction performance, it also optimizes the energy consumption and applicability of the damping system.

[0040] 4. This invention designs the horizontally perforated vibration damping heave plate as a modular, detachable energy dissipation cylinder, and employs a quick-locking mechanism for installation. The modular design greatly facilitates transportation, installation, and subsequent maintenance and replacement, reducing the total life-cycle cost. The multi-layered interlaced metal mesh and porous elastic damping material inside the energy dissipation cylinder constitute a composite energy-dissipating structure, which efficiently dissipates water kinetic energy through multiple mechanisms such as vortex generation, friction, and material internal friction. The quick-locking mechanism (such as an eccentric cam lock) ensures a secure connection and convenient assembly / disassembly, allowing the energy dissipation components to be quickly adjusted and updated according to marine conditions or damage, improving the system's maintainability and adaptability to different operating conditions.

[0041] 5. This invention introduces a gravity anchorage platform, universally hinged anchor blocks arranged in a distributed manner, and spherical bearing hinge connections into a flexible mooring system. The gravity anchorage platform provides a stable foundation and distributes the load through large-area contact. The universally hinged arrangement of the anchor blocks allows them to adaptively adjust their direction, evenly distributing the anchor chain tension from different directions and avoiding single-point stress concentration. The spherical bearing hinge allows the lower chain segment to swing in multiple directions, effectively releasing the bending stress of the anchor chain. This combined design significantly enhances the mooring system's ability to bear and adapt to dynamic alternating loads, significantly reduces the risk of anchor chain fatigue, and improves overall anchoring reliability, making it particularly suitable for seabed conditions with uneven bearing capacity or bottom current scouring.

[0042] 6. This invention incorporates a connected air chamber and a matching inflation / deflation system (air tank, air compressor) within a semi-cylindrical shell. This design constitutes an active aerodynamic energy dissipation mechanism. When waves impact the wave-damping holes, the gas inside the air chamber is compressed or expanded, consuming wave energy; simultaneously, the air pressure within the air chamber can be actively adjusted through the piping system, altering its stiffness and response characteristics. This allows the breakwater to not only passively dissipate energy but also actively interfere with waves through a "breathing" effect, particularly effectively reducing breaking waves. The combination of aerodynamic energy dissipation with the semi-cylindrical shell's reflection and permeability mechanisms broadens the effective wave-damping frequency band, especially enhancing the energy dissipation efficiency for water layers with concentrated wave energy (near the water surface).

[0043] 7. This invention proposes a parameterized method for the design of openings in a horizontally perforated vibration-damping heave plate, optimized based on characteristic wave height and wave period. The aperture gradually increases along the plate surface towards the edge, conforming to the lateral distribution of wave particle velocity, which is beneficial for uniform flow guidance and reducing local impact pressure. The logarithmic relationship between perforation rate and wave period ensures that the plate's drag characteristics match the main energy cycle of the wave, optimizing the ratio of inertial drag to form drag. This refined design based on the target sea state parameters enables the energy dissipation system to dissipate the energy of specific waves more effectively, avoiding the performance deficiencies or redundancy of a "one-size-fits-all" design, and achieving an optimal balance between energy dissipation efficiency and structural load.

[0044] 8. This invention provides a structural optimization configuration strategy for different water depths and seabed geological conditions. For shallow water areas, a simplified two-stage energy dissipation configuration is adopted, saving materials and construction costs while ensuring basic performance. Furthermore, the plate thickness increases with water depth, adapting to the significant wave bottom effect in shallow water. For deep water areas, a reinforced three-stage configuration with extended vertical plates is employed, aiming to control water movement at greater depths and achieve more comprehensive intervention in the wave energy of the entire water column. The anchor block weight is differentiated according to the foundation type (silt or sand), ensuring sufficient and economical pull-out resistance under different geological conditions. This hierarchical optimization strategy demonstrates good engineering economy and environmental adaptability.

[0045] 9. This invention further provides a clear method for determining the design parameters of the first and second vibration dampers and the rotary damper. By linking the rated damping force of the damper with the design wave impact force calculated by the Morrison equation, it ensures that the damper has sufficient energy dissipation capacity while avoiding excessive constraint on structural motion or the transfer of excessive loads to the foundation due to excessive damping. The empirical formula for the torsional stiffness of the rotary damper matches its stiffness with the geometry of the floating unit (related to the drainage volume), effectively controlling the amplitude and speed of relative rotation between units. These quantitative design principles provide a direct basis for the selection and design of damping elements, ensuring the effectiveness and reliability of the multi-stage energy dissipation and vibration reduction system and the flexible mooring system working together, and avoiding the blindness of parameter design.

[0046] Other advantages, objectives and features of the present invention will become apparent in part from the following description, and in part from those skilled in the art through study and practice of the invention. Attached Figure Description

[0047] Figure 1 This is a schematic diagram of a semi-cylindrical shell floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system, as described in one technical solution of the present invention.

[0048] Figure 2 This is a schematic diagram of the structure of the semi-cylindrical shell floating breakwater with a multi-stage energy dissipation and vibration reduction and flexible mooring system described in another technical solution of the present invention.

[0049] Figure 3 This is a schematic diagram of the structure of a semi-cylindrical shell floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system, as described in another technical solution of the present invention.

[0050] Explanation of reference numerals in the attached drawings: 1-shell, 11-wave-damping hole, 12-reinforcing rib, 2-floating box, 3-vertical connecting rod, 4-horizontal through-hole vibration-damping heave plate, 5-first vibration-damping damper, 6-vertical through-hole wave-damping plate, 71-anchor block, 72-anchor chain, 73-second vibration-damping damper, 74-anchor ring; 8-connector, 81-rotation damper. Detailed Implementation

[0051] The present invention will now be described in further detail with reference to the accompanying drawings and embodiments, so that those skilled in the art can implement it based on the description.

[0052] It should be understood that terms such as “having,” “comprising,” and “including” as used herein do not exclude the presence or addition of one or more other elements or combinations thereof.

[0053] It should be noted that, unless otherwise specified, the experimental methods described in the following implementation plan are all conventional methods, and the reagents and materials described are all commercially available unless otherwise specified.

[0054] In the description of this invention, the terms "lateral", "longitudinal", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", and "outer" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this invention.

[0055] like Figure 1-3 As shown, the present invention provides a semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system, comprising:

[0056] The floating unit includes a semi-cylindrical hull (which is an open structure with open ends) and a buoy connected to the bottom of the semi-cylindrical hull; the semi-cylindrical hull is provided with multiple wave-damping holes on the wave-facing side.

[0057] The energy dissipation and vibration reduction system, located below the pontoon, includes:

[0058] Multiple vertical connecting rods are arranged in a matrix, with the top of each vertical connecting rod connected to the bottom of the pontoon and the bottom extending downwards;

[0059] At least two layers of horizontally perforated vibration damping sway plates are fixedly sleeved on multiple vertical connecting rods at intervals along the vertical direction, and the at least two layers of horizontally perforated vibration damping sway plates divide each vertical connecting rod into multiple segments;

[0060] Multiple first vibration dampers are respectively installed on the segments of the vertical connecting rod, and are located between two adjacent layers of horizontal through-hole vibration damping sway plates, and between the pontoon and the uppermost horizontal through-hole vibration damping sway plate;

[0061] At least one vertical perforated wave-damping plate, the plate surface of which is arranged parallel to the wave incident direction, and the two ends of the vertical perforated wave-damping plate are respectively connected to the shells of two first vibration dampers located at the same height;

[0062] A flexible mooring system includes an anchor block on the seabed, an anchor chain connecting the anchor block to the bottom of the buoy, and a second vibration damper on the anchor chain.

[0063] The above-mentioned technical solutions mainly address the problems of traditional floating breakwaters having a single wave dissipation mechanism under complex sea conditions, insufficient dissipation of wave energy in the middle and lower water layers, and limited effectiveness in reducing long-period waves. At the same time, the floating body's heave and other motion responses under wave action are too large, affecting the stability of the sheltered water area and aggravating structural fatigue. In addition, the anchoring system lacks effective buffering against dynamic impact loads, and the anchor chain is prone to fatigue damage.

[0064] The core of this invention, a semi-cylindrical hull floating breakwater with a multi-stage energy dissipation, vibration reduction, and flexible mooring system, lies in constructing a three-dimensional system extending from the water surface to underwater, combining energy dissipation and vibration reduction functions. The floating unit in this system is a combination of a semi-cylindrical hull 1 and a bottom pontoon 2. The semi-cylindrical hull 1 is a hollow structure, with open ends and an open bottom facing the pontoon 2. Multiple vertically arranged reinforcing ribs 12 are firmly connected to the top of the pontoon 2 on the inner wall of the convex surface (i.e., the arc-shaped surfaces facing and away from the waves), forming a robust frame-like structure. Multiple rows of wave-dissipating holes 11 are opened on the arc-shaped surface facing the waves of the hull 1, allowing some wave water to penetrate, and the wave energy is initially dissipated through vortices and friction within the holes. Compared to traditional floating breakwaters that rely solely on floating body reflection and overall motion for energy dissipation, this invention adds an energy dissipation and vibration reduction system that extends deep into the water below the pontoon 2. The system comprises a matrix of vertically connected rods 3, which connect the pontoon 2 to the underwater structure. Multi-layered horizontally perforated vibration-damping heave plates 4, arranged at vertical intervals, are fixedly fitted onto these connecting rods, dividing the rods into segments. A first vibration damper 5 is installed on each segment, between adjacent horizontal plates and between the pontoon and the uppermost horizontal plate. Additionally, there is at least one vertically perforated wave-dissipating plate 6 with its surface parallel to the wave incidence direction, its ends connected to the outer shells of two first vibration-damping dampers 5 at the same height. Here, the "horizontally perforated vibration-damping heave plate" refers to a horizontally placed plate-like component with numerous holes. Its function is twofold: first, to utilize the turbulence and form resistance generated when water flows through the holes to dissipate the kinetic energy of the water; and second, to use its mass and area to suppress the vertical movement of the pontoon. The "vertically perforated wave-dissipating plate" is a vertically placed plate with similar holes, primarily used to cut and disrupt the trajectory of wave particles along the water depth direction, thus damaging the wave structure. The first vibration damper 5 is a device capable of absorbing and dissipating mechanical vibration energy, used in this structure to attenuate wave dynamic loads transmitted through the connecting rod. The flexible mooring system includes an anchor block 71 disposed on the seabed, an anchor chain 72 connecting the anchor block and the buoy, and a second vibration damper 73 integrated on the anchor chain, which is specifically designed to buffer and dissipate dynamic impact tension borne by the anchor chain.

[0065] When waves arrive, the energy transfer process is decomposed and dissipated in multiple stages. First, some wave energy is consumed through the wave-dissipating holes 11 on the semi-cylindrical shell 1 in the form of vortices and friction. The remaining wave energy drives the floating unit to move and acts on the energy dissipation and vibration reduction system below it. The multi-layered horizontal perforated vibration-damping heave plate 4 is like a series of deep-water grids, forcing water flows of different depths to pass through its holes. In this process, the kinetic energy of the water flow is consumed layer by layer through continuous vortex generation, friction between the fluid and the hole walls, and the additional mass effect caused by the movement of the plate itself. Especially for long-period waves, whose energy distribution is deep, traditional floating bodies are difficult to effectively intervene. However, this invention can directly act on these middle and lower water layers through the deep-placed horizontal plates, significantly improving the energy dissipation efficiency. At the same time, the vertical perforated wave-dissipating plate 6 further disrupts the vertical motion structure of the water flow, forming a three-dimensional energy-dissipating grid in conjunction with the horizontal plates. The kinetic energy, such as the heave of the buoy 2, is transmitted through the vertical connecting rod 3 to the multi-stage first vibration damping dampers 5 arranged in series. These dampers, like "shock absorbers," convert kinetic energy into heat energy and dissipate it, thereby effectively suppressing the excessive movement amplitude of the buoy. For the mooring system, when the dynamic load of the buoy caused by waves is transmitted through the anchor chain 72, it first passes through the second vibration damping damper 73. This damper absorbs and smooths the load peak, significantly reducing the impact force directly acting on the anchor block 71 and the end of the anchor chain 72, thereby greatly alleviating the fatigue problem of the anchor chain.

[0066] In terms of wave-damping performance, the above-mentioned technical solution achieves "full-section" intervention of wave energy along the water depth direction through the three-dimensional combination of surface shell openings and underwater multi-layer perforated plates, significantly broadening the effective wave-damping frequency band, especially enhancing the attenuation capability for long-period swells. Regarding structural dynamic stability, the rigid frame formed by the reinforcing ribs 12 and the buoy 2 improves the overall integrity of the superstructure, while the multi-level horizontal plates increase the system's heave mass and damping. The first vibration damper 5, connected in series, actively dissipates kinetic energy. Under these multiple effects, the motion response of the buoy in waves is effectively controlled, improving the stability of the rear shelter area and reducing the dynamic stress and fatigue risk at structural connection points. In terms of mooring reliability, the second vibration damper 73 integrated into the anchor chain 72 constitutes a crucial flexible buffer link, transforming the traditional rigid or weakly damped force transmission path into a flexible path that can actively dissipate energy, thereby significantly improving the survivability and service life of the mooring system under long-term alternating loads. Through the synergistic effect of the above-mentioned multi-level and multi-mechanism systems, the entire system comprehensively improves the working efficiency and durability of floating breakwaters in complex sea conditions without significantly increasing the self-weight and size of the floating body.

[0067] In another technical solution, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction and flexible mooring system has connectors on both sides of the buoy for connecting adjacent floating units, and a rotation damper is provided between the connectors.

[0068] In the above technical solution, connectors 8 for connecting adjacent floating body units are provided on both sides of the float box 2, and rotational dampers 81 are provided between adjacent connectors 8. Here, "connector 8" refers to a rigid connection structure fixed to the side of the float box 2, such as a lug or flange, whose function is to mechanically connect multiple floating body units in series to form a continuous breakwater. The rotational damper 81 is a device that provides a resistance torque in the direction of rotation. It typically contains a viscous fluid or a highly damped elastic element. Its core function is to generate a damping torque proportional to the rotational angular velocity when adjacent units rotate relative to each other, thereby consuming rotational kinetic energy and suppressing the rotational amplitude. Compared with the rigid hinges or simple pin connections commonly used in existing technologies, although the existing technical solutions are structurally simple, they are essentially a "hard connection," directly and without buffering the movement (including harmful torsional deformation) of adjacent units. When waves propagate along the breakwater, the alternating action of wave crests and troughs causes adjacent units to be subjected to different forces at different times. This rigid connection cannot dissipate the torsional energy generated by asynchronous motion, resulting in repeated alternating stress at the connection points, which can easily lead to fatigue cracks. At the same time, the entire breakwater line may exhibit irregular wave-like deformation, resulting in unstable wave-damping effect.

[0069] In another technical solution, the semi-cylindrical shell floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system has a vertical connecting rod comprising an inner column and an outer sleeve arranged coaxially, forming an annular cavity filled with magnetorheological fluid; a piezoelectric sensing layer is provided on the outer wall of the inner column, and a first electrode layer is covered on the outer surface of the piezoelectric sensing layer; a second electrode layer is correspondingly provided on the inner wall of the outer sleeve;

[0070] The inner column and the outer sleeve are connected by a flexible pleated membrane at multiple axial intervals. The flexible pleated membrane seals the annular cavity and divides the annular cavity into multiple independent damping adjustment segments along the axial direction.

[0071] The vertical connecting rod is equipped with a controller. The signal input end of the controller is connected to the piezoelectric sensing layer, and the output end is connected to the first electrode layer and the second electrode layer of each damping adjustment segment.

[0072] The controller is configured to receive real-time electrical signals generated by the piezoelectric sensing layer due to the vibration or deformation of the rod, process the electrical signals into feedback values ​​characterizing the relative velocity or displacement between the inner column and the outer sleeve, and use the feedback values ​​as control variables. The controller is programmed to apply a regulating voltage to the electrode layer of each damping adjustment segment in a positive correlation with the absolute value of the control variable, and the polarity of the regulating voltage is configured such that the direction of the magnetorheological damping force generated by it is opposite to the direction of the relative velocity.

[0073] In the above technical solution, the vertical connecting rod 3 adopts an intelligent adaptive structure based on magnetorheological fluid. Specifically, the vertical connecting rod 3 consists of an inner column and an outer sleeve arranged coaxially, forming an annular sealed cavity filled with magnetorheological fluid. Considering the high-pressure environment of the deep sea, the outer sleeve adopts a thick-walled design, and a pressure compensation membrane is set inside the annular cavity to balance the internal and external pressures and prevent magnetorheological fluid leakage. The magnetorheological fluid uses a special formula that is resistant to high pressure and corrosion to ensure long-term stability in the deep-sea environment. The controller dynamically adjusts the damping force of each segment based on the signal from the piezoelectric sensing layer and the data from the depth sensor to ensure stable operation even under high pressure. The outer wall of the inner column is sequentially provided with a piezoelectric sensing layer and a first electrode layer covering it; the inner wall of the outer sleeve is correspondingly provided with a second electrode layer. The inner column and outer sleeve are connected axially by multiple flexible pleated membranes. These pleated membranes not only serve as a connection but, more importantly, divide the annular cavity axially into multiple independent damping adjustment segments. The entire vertical connecting rod 3 is equipped with a controller. The controller's signal input is connected to the piezoelectric sensing layer, and its output is connected to the first and second electrode layers of each damping adjustment segment, respectively. The "magnetorheological fluid" here is a smart material whose rheological properties (such as shear yield stress) change significantly, rapidly, and reversibly with the strength of the applied magnetic field. The "piezoelectric sensing layer" is a sensitive material layer that can directly convert mechanical deformation or vibration into electrical signals. The "flexible pleated membrane" is a flexible sealing diaphragm that can expand axially and has high radial stiffness, allowing limited relative axial displacement between adjacent segments while maintaining the independent sealing of the magnetorheological fluid within each segment. The "controller" is a microprocessor system responsible for signal acquisition, processing, and issuing control commands. Compared to the solid steel rods or passive damping rods filled with a fluid of fixed viscosity commonly used in existing technologies, the connecting rods of existing technologies can only provide fixed stiffness and extremely limited passive damping. Their mechanical parameters cannot be changed once they are manufactured. When the wave load frequency changes or when impact waves occur, these passive rods cannot adjust their own characteristics to adapt to the changes. They either resonate with the structure and aggravate the vibration, or become the direct force transmission path of the impact load due to their excessive rigidity.

[0074] When waves act on the breakwater, causing the buoy 2 to move and transmit the load to the underwater energy dissipation system through the vertical connecting rod 3, the connecting rod itself will vibrate and deform. At this time, the piezoelectric sensing layer attached to the inner column will sense the strain or vibration acceleration of the rod in real time and convert it into a corresponding electrical signal. This electrical signal is transmitted to the controller. The controller's internal preset algorithm will process the signal, for example, through integration or differentiation, to convert it into a feedback value that can characterize the relative velocity or displacement between the inner column and the outer sleeve at the current moment. This feedback value is used as the core control variable. Based on the magnitude and sign (direction) of this control variable, the controller calculates in real time the control voltage value that needs to be applied to each independent damping adjustment segment. The control logic is as follows: the magnitude of the DC or pulse voltage applied to the first and second electrode layers of a certain segment is positively correlated with the absolute value of the relative velocity monitored at that segment; simultaneously, the controller adjusts the polarity of the applied voltage so that the direction of the magnetic field generated between the two electrode layers can excite the magnetorheological fluid to produce a damping force opposite to the current relative velocity direction. The physical process is that the voltage generates an electric field between the two electrode layers, which in turn generates a magnetic field in a coil (if present) or directly through electromagnetic induction. This magnetic field acts on the magnetorheological fluid in the segment, causing it to instantly transform from a Newtonian fluid-like state to a solid-like state with a certain yield strength, thereby generating a huge, controllable Coulomb damping force during the relative shear motion of the inner and outer cylinders. Because each segment is independently controllable, segmented and differentiated adjustment of the damping force along the length of the rod can be achieved.

[0075] In the aforementioned technical solution, the vertical connecting rod 3 is transformed from a passive force-transmitting component into an active and intelligent vibration damping organ. Firstly, its adaptive capability significantly enhances its vibration damping performance against broadband wave excitation. Whether it's high-frequency breaking waves or low-frequency swells, the controller can rapidly adjust the damping force through real-time feedback, ensuring that the dynamic characteristics of the connecting rod always approach the optimal energy dissipation state under the current primary wave load. This maximizes the suppression of heave and other movements of the pontoon 2, improving the stability of the waters behind it. Secondly, this real-time controllable damping mechanism provides excellent impact load buffering capability. When encountering extreme large wave impacts, the controller can instantly apply maximum voltage, causing the magnetorheological fluid to reach maximum yield stress, providing extremely high instantaneous damping force to absorb and dissipate impact energy, protecting the energy dissipation system and mooring system below from excessive peak loads. Under normal sea conditions, the damping is reduced to minimize unnecessary structural internal forces and energy consumption, achieving a balance between safety and economy. Furthermore, segmented independent control allows for targeted suppression of vibration modes at different parts of the connecting rod, such as focusing on suppressing relative motion at specific inflection points, making vibration control more precise and efficient. In addition, the integrated design of the piezoelectric sensing layer enables the rod to possess both "sensing" and "acting" functions, resulting in a highly integrated structure and high reliability. This technical solution, by integrating magnetorheological fluid smart materials, sensing technology, and control algorithms into the vertical connecting rod 3, creatively solves the inherent problem of non-adjustable damping in traditional connecting rods, achieving an active and adaptive response to wave loads, and greatly enhancing the intelligence level and environmental adaptability of the overall energy dissipation and vibration reduction system of the floating breakwater.

[0076] In another technical solution, the semi-cylindrical shell floating breakwater with multi-stage energy dissipation and vibration reduction and flexible mooring system has a detachable modular energy dissipation cylinder for each layer of horizontal perforated vibration reduction heave plate; each energy dissipation cylinder consists of an outer frame and multiple layers of staggered metal mesh inside the outer frame, the surface of the metal mesh is coated with a catalytic coating, and the porous elastic damping material blocks are located between the staggered gaps of the metal mesh.

[0077] The outer frame is connected to the vertical connecting rod through a quick-locking mechanism. The quick-locking mechanism consists of multiple eccentric cam locks evenly distributed around the circumference. The rotating shaft of each lock passes through the wall panel of the outer frame and is connected to the pre-tightening pressure plate at its inner end. When the lock is closed, the rotating shaft drives the pre-tightening pressure plate to press axially onto the vertical connecting rod.

[0078] In the above technical solution, the horizontal perforated vibration damping heave plate 4 is designed as a detachable modular energy dissipation cylinder. Each energy dissipation cylinder consists of an outer frame and a composite energy dissipation structure located inside the outer frame. This composite energy dissipation structure includes multiple layers of staggered metal mesh, with a catalytic coating attached to the surface of the mesh wires, and porous elastic damping material blocks filling the interlacing gaps between the metal mesh. The outer frame is detachably connected to the vertical connecting rod 3 via a quick-locking mechanism. Here, "modular energy dissipation cylinder" refers to designing the horizontal energy dissipation plate as an independent, fully functional cylindrical or flat box-shaped prefabricated module. "Multi-layered staggered metal mesh" refers to a mesh structure woven or welded from metal wires, stacked at a certain angle to form a complex three-dimensional flow channel. "Catalytic coating" is a functional material coated on the surface of the mesh wires, such as a photocatalyst like titanium dioxide, or a coating that promotes cavitation and generates micro-nano bubbles under the shearing action of seawater flow. "Porous elastic damping material block" refers to a high-damping elastic material with a continuous open structure, such as polyurethane foam or rubber sponge, which fills the gaps in the grid. "Quick locking mechanism" is a mechanical connection device that allows for rapid locking and releasing without complex tools; in this solution, it specifically refers to multiple circumferentially distributed eccentric cam locks. Compared with traditional perforated plates that are directly welded to the support structure or fixed with multiple bolts, existing technologies have significant shortcomings: First, large-sized steel plates are difficult to install with precision at sea, the welding workload is large, and the quality is greatly affected by the environment; second, once the plate is damaged during service due to corrosion, impact, or fatigue, local repairs are difficult, often requiring complete replacement at a high cost; third, its energy dissipation mechanism is relatively simple, mainly generating vortices through the interaction between water flow and the edge of the holes, and it does not fully utilize changes in water flow direction and multi-level energy dissipation.

[0079] The modular energy dissipation cylinder is prefabricated and assembled in an onshore factory, including welding of the outer frame, positioning and installation of the internal multi-layer metal mesh, injection and curing of porous elastic damping material, and spraying of a catalytic coating. After being transported to the site, it is connected to corresponding components pre-installed on vertical connecting rod 3 via a quick-locking mechanism integrated into its outer frame. Taking the eccentric cam lock as an example, during operation, the lock's shaft is rotated, passing through the outer frame wall panel. The pre-tightening pressure plate connected to its inner end moves axially under the action of the cam, ultimately pressing against the wall of the vertical connecting rod 3, achieving a secure lock through friction. Disassembly is achieved by reversing the operation. When waves cause water flow through the energy dissipation cylinder, the water first passes through large holes in the outer frame and then enters the complex internal multi-layered interlaced metal mesh system. The multi-layered interlaced layout of the mesh forces the water flow to constantly change direction, split, and merge, generating numerous vortices of varying sizes and high intensity, greatly increasing the shear and friction within the fluid, thereby efficiently dissipating kinetic energy. The porous elastic damping material filling the gaps in the mesh further enhances energy dissipation: on the one hand, water is forced to flow through its tortuous microporous channels, resulting in a sharp increase in flow resistance; on the other hand, the viscoelasticity of the material itself deforms and generates internal friction under the periodic water flow pressure, converting some of the water's kinetic energy into heat energy. The catalytic coating on the surface of the metal mesh may promote the generation of micro- and nano-bubbles through cavitation as seawater continuously flows over it. The collapse of these bubbles generates localized high pressure and micro-jet streams, disturbing the water flow and consuming additional energy. Simultaneously, some coatings can also catalytically decompose organic pollutants in seawater, providing a certain degree of auxiliary environmental purification function.

[0080] Modular design and quick-locking mechanism greatly enhance the convenience and economy of engineering implementation. Energy dissipation cylinders can be prefabricated in well-equipped factories with controllable quality, and then installed on-site via standardized quick-locking mechanisms in a "plug-and-play" manner. This significantly reduces high-altitude operations and welding work at sea, shortens the construction period, and lowers construction risks and costs. Secondly, this design endows the system with unprecedented maintainability and upgradeability. When an energy dissipation cylinder is damaged or needs to be adapted to new sea conditions, it can be quickly disassembled and replaced with a new module without large-scale modifications to the main support structure (vertical connecting rod 3), making maintenance convenient and reducing lifecycle costs. Furthermore, the internal composite energy dissipation structure (interlaced grid + porous damping material) creates multiple, synergistic energy dissipation mechanisms. Compared to a single perforated plate, it significantly improves energy dissipation efficiency per unit volume or unit projected area through the combined effects of multiple physical processes such as flow channel segmentation, vortex generation, porous medium flow resistance, and internal material friction. It is particularly adaptable to unsteady, multi-directional complex flows and has a wider energy dissipation bandwidth. Furthermore, the introduction of the catalytic coating adds environmental functionality to the structure, embodying the concept of green marine engineering. The aforementioned technical solution innovatively designs the horizontal perforated vibration-damping heave plate 4 as a modular energy dissipation cylinder with an internal composite energy dissipation structure and an external quick-locking mechanism. This effectively solves the prominent problems of difficult installation and maintenance, and the single and unadjustable energy dissipation mode of traditional underwater energy dissipation components. It achieves high efficiency, convenience, and maintainability of the energy dissipation system, significantly improving the engineering practicality and long-term economic efficiency of the entire floating breakwater.

[0081] In another technical solution, the semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction and flexible mooring system includes a gravity anchoring platform on the seabed. Anchor blocks are distributed on the upper surface of the gravity anchoring platform via universal hinges. The anchor chain is divided into an upper chain segment and a lower chain segment, and a second vibration damper is connected between the upper and lower chain segments. The lower end of the lower chain segment is connected to the center of the gravity anchoring platform via a spherical bearing hinge.

[0082] The above technical solution adds a gravity anchoring platform on the seabed. Multiple anchor blocks 71 are distributed on the upper surface of the gravity anchoring platform via universal joints. Anchor rings 74 are provided on the anchor blocks 71 and on the bottom or sides of the pontoon 2 for connecting the anchor chain 72. The anchor chain 72 connects the anchor rings 74 of the pontoon 2 and the anchor rings 74 of the anchor blocks 71. To optimize the force transmission path and buffer dynamic loads, the anchor chain 72 is structurally divided into an upper chain segment and a lower chain segment, with a second vibration damper 73 connecting the upper and lower chain segments. The lower end of the lower chain segment is connected to the center of the gravity anchoring platform via a spherical bearing hinge. Here, the "gravity anchoring platform" is a rigid seabed foundation structure with a large bottom area and self-weight. Its core function is to provide overall stability and disperse base pressure through its own weight and bottom area. The anchor rings 74 are standard, high-strength metal connecting rings, fixed to the anchor blocks 71 and the pontoon 2 respectively, serving as reliable mooring points for the anchor chain 72. The universal joint is a hinge mechanism connecting the anchor block 71 to the gravity anchorage platform, allowing the anchor block to rotate in multiple directions to a limited extent, thus enabling it to adaptively adjust its attitude to more effectively provide pull-out resistance. A spherical bearing hinge is a hinge with a spherical contact pair, allowing the connected components (such as the chain segment below) to swing in multiple directions. Compared to the traditional method of directly connecting the two ends of the anchor chain 72 to the independently distributed anchor blocks 71 and the pontoon 2 via shackles or simple hinges, the existing technology has significant shortcomings: First, the distributed anchor blocks 71, on soft mud or uneven seabeds, are prone to independent slippage or overturning due to uneven stress, leading to gradual loosening or failure of the system. Second, the connection points at both ends of the anchor chain 72 (at the anchor ring 74) and the contact points between the anchor chain and the seabed, due to the lack of sufficient release for multi-dimensional swinging, bear complex bending, torsional, and tensile-compressive combined stresses, making them highly susceptible to fatigue cracks and wear, which are the most common failure points in mooring systems.

[0083] The gravity anchorage platform, serving as a stable integral foundation, is pre-placed and anchored firmly to the seabed. Its large bottom area design significantly reduces pressure on the ground, enhancing its anti-slip and anti-overturning stability on soft seabeds. Multiple anchor blocks 71, distributed across the platform via universal joints, share the tension of the anchor chain 72 through their anchor rings 74. This design allows each anchor block 71 to finely adjust its attitude according to the actual direction of the tension, optimizing the anti-slip force component provided by gravity and achieving efficient synergy of anchoring forces. The upper end of the anchor chain 72 is connected to the anchor rings 74 on the buoy 2 via standard shackles or connectors. A second vibration damper 73, located in the middle of the anchor chain 72, is specifically designed to absorb and dissipate longitudinal impact and vibration energy transmitted by the movement of the floating body. The lower end of the lower chain segment is connected to the center of the gravity anchorage platform via a spherical bearing hinge, rather than being directly fixed to any anchor block 71. One of the core innovations of this design is that the spherical bearing hinge allows the lower chain segment and its connected anchor chain portion to swing freely within a certain range in three-dimensional space relative to the seabed platform. This greatly relieves the constraints on the anchor chain 72 at the "contact point" or "connection point," where bending stress and wear are most likely to occur near the seabed, allowing this segment of the anchor chain to primarily bear tensile loads, thus significantly improving its stress state. Simultaneously, the anchor rings 74 on the pontoon 2 and the anchor blocks 71, as standardized high-strength connection interfaces, ensure the reliability and replaceability of the connection.

[0084] In another technical solution, the semi-cylindrical hull floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system has a sealed air chamber inside the semi-cylindrical hull that communicates with the pontoon (the air chamber forms a partially sealed space in the middle region of the hull, and the open structure at both ends does not affect its aerodynamic energy dissipation function); the air chamber is connected to an air storage tank located in the pontoon through a first pipe, and the air storage tank is connected to an air compressor located in the pontoon through a second pipe; the inner end of the wave-damping hole communicates with the air chamber.

[0085] In the above technical solution, to ensure the sealing reliability and pressure balance of the air chamber under wave impact, a high-pressure sealing flange is used at the connection between the first pipeline and the air chamber and the air storage tank, and a pressure safety valve is installed. A one-way valve and a pressure sensor are installed between the air storage tank and the air compressor. The controller automatically adjusts the inflation and deflation of air according to the pressure changes inside the air chamber to maintain the air pressure inside the air chamber within the set range. The inner wall of the air chamber is coated with an anti-corrosion coating and is equipped with a drain outlet to prevent water accumulation from affecting aerodynamic performance.

[0086] The semi-cylindrical hull 1 has a sealed air chamber inside its cavity that communicates with the interior of the pontoon 2. This air chamber is connected to an air storage tank located inside the pontoon 2 via a first pipe, and the air storage tank is connected to an air compressor also located inside the pontoon 2 via a second pipe. The wave-damping hole 11 on the wave-facing side of the hull 1 has its inner end directly connected to the air chamber. The sealed air chamber refers to a closed or semi-closed gas space formed in the upper or middle region of the hull 1, isolated from the open seawater. The air storage tank is a pressure vessel used to store compressed air. The air compressor is a power device used to compress air and pump it into the air storage tank. The connection between the wave-damping hole 11 and the air chamber forms a "gas-liquid" interface, allowing wave pressure and the air pressure inside the air chamber to be mutually transmitted and converted. Compared with the hull cavities commonly found in the prior art, which only serve as permeable or counterweight spaces and are directly connected to the atmosphere or completely closed, the cavities in the prior art basically do not have active energy regulation functions. Its internal air pressure is roughly the same as the ambient atmospheric pressure or passively varies with the waves. Energy dissipation mainly relies on the friction and vortex of water entering and exiting the cavities, which is a purely passive dissipation. When encountering extremely large waves, water may rush into the cavity at high speed, generating a powerful "water hammer" impact force that threatens the structure; while for long-period swells, its passive dissipation efficiency is relatively low.

[0087] When waves crash against the breakwater, some seawater enters or compresses the air chamber through the wave-dissipating holes 11. If the wave pressure is higher than the air chamber pressure, the water will partially compress the gas inside the chamber, converting the kinetic and potential energy of the wave into the internal energy (pressure energy) of the gas. Conversely, when the wave recedes, the compressed gas expands, pushing the water out of the wave-dissipating holes 11. This "breathing" process itself consumes a large amount of wave energy through the compression and expansion of the gas, and its principle is similar to a gas spring damper, with an efficiency far higher than simple water friction. More importantly, the integrated air compressor and air tank system gives the air chamber an active adjustment capability. Through preset programs or sensor feedback, the air compressor can be controlled to inject or extract air into the air chamber, thereby actively changing the initial air pressure of the air chamber and the stiffness of the "air cushion". For example, when large waves or storms are forecast, the air pressure in the air chamber can be increased in advance to enhance its "rigidity" against wave impact, reduce water intrusion, and lower structural load. Under normal wave conditions, the air pressure can be reduced to make the air chamber more "flexible," allowing it to efficiently dissipate conventional wave energy through greater "breathing" movements. The air compressor and air tank serve as power sources and energy storage units, enabling this regulation to continue without relying on external energy sources, or to achieve self-sustaining operation using the solar and wave energy power generation systems mounted inside the floating tank 2.

[0088] The aforementioned technical solution represents a leap in energy dissipation modes, from passive to a combination of active and passive, and from fixed to adjustable. First, it introduces and strengthens an aerodynamic energy dissipation mechanism. The compressibility of gas allows the air chamber to absorb and store a large amount of impact energy, which is then released smoothly through expansion, transforming the intense impact load of waves into a gently changing air pressure load. This provides excellent buffering and protection for the structure, making it particularly suitable for dealing with impact loads such as breaking waves. Second, active adjustability greatly broadens the structure's environmental adaptability and wave dissipation frequency band. By adjusting the air pressure, the natural frequency of the air chamber-water column system can be changed, thereby specifically optimizing the response and energy dissipation efficiency to waves of different periods, achieving targeted wave dissipation. For example, for long-period swells, lower air pressure can be used to induce system resonance, efficiently dissipating energy through significant gas volume changes; for short-period waves, higher air pressure can be used primarily for reflection. This capability is unavailable in passive structures. Third, the system enhances its protection against extreme events. The active pressurization mode is equivalent to putting an "inflatable armor" on the breakwater before a storm, effectively resisting the impact of abnormally high waves and improving the system's survivability. Finally, this solution, together with the original reflection, diffraction, and energy dissipation mechanisms of the semi-cylindrical shell 1 and the perforated plate system below, forms a multi-mechanism, three-dimensional synergy. From the water surface to underwater, from solid structures to fluids and then to gases, it constructs a more layered and adaptable comprehensive energy dissipation system, thereby significantly improving the breakwater's wave dissipation efficiency, reliability, and intelligence level.

[0089] In another technical solution, the semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system features a horizontally perforated vibration-damping heave plate with an opening design that is parametrically adapted to the characteristic wave height H and average wave period T of the target sea area; wherein:

[0090] The aperture diameter d satisfies: H / 15≤d≤H / 8, and the aperture diameter on the same layer plate increases gradually from the center to the edge, with the aperture diameter in the edge region being 1.2 to 1.5 times that in the center region;

[0091] The overall permeability η of the plate is optimized based on the wave period T and satisfies the relationship: η=k×ln(T)+b, where k and b are coefficients related to the energy dissipation cylinder level, and the permeability of each layer of the plate decreases sequentially from top to bottom, with a permeability gradient difference of 5~10%.

[0092] In the above technical solution, the perforation design of the horizontal perforated vibration damping heave plate 4 is explicitly required to be parametrically adapted according to the characteristic wave height H and average wave period T of the target sea area. Specifically, the perforation diameter d needs to satisfy a range related to the characteristic wave height H: H / 15≤d≤H / 8. Furthermore, on the same layer plate, the perforation diameter is not uniform, but increases gradually from the center of the plate to the edge, with the perforation diameter in the edge area designed to be 1.2 to 1.5 times that in the center area. The overall permeability η of the plate is determined based on the average wave period T and is optimized to satisfy the relationship η=k×ln(T)+b, where k and b are specific coefficients related to the layer of the energy dissipation cylinder (i.e., the horizontal perforated vibration damping heave plate 4), and k and b are coefficients related to the layer of the energy dissipation cylinder, which are determined through wave spectrum analysis of the target sea area combined with flume model tests. For example, for the uppermost plate, k can be 0.12 and b can be 0.08; for the middle plates, k can be 0.10 and b can be 0.05; and for the lowermost plate, k can be 0.08 and b can be 0.03. The porosity of each plate decreases sequentially from top to bottom, with a porosity gradient difference of 5-10% to accommodate the distribution of wave energy attenuation with water depth. Furthermore, the porosity of each plate decreases sequentially from top to bottom, with the porosity gradient difference between adjacent plates controlled between 5% and 10%. Here, "characteristic wave height H" usually refers to the significant wave height or a certain cumulative wave height, representing the typical wave energy intensity of the sea area. "Mean wave period T" represents the time scale of wave energy concentration. "Porosity η" refers to the percentage of the total area of ​​all openings on the plate to the total projected area of ​​the plate. "Gradient increase" refers to the continuous or stepwise increase in aperture from the center to the edge of the plate. Compared to existing technologies that typically use empirical values ​​or fixed specifications (such as uniform aperture, uniform distribution, and constant permeability) to determine perforated plate parameters, current technologies neglect the non-uniformity of wave field spatial distribution and the differences in wave spectra across different sea areas. The actual horizontal velocity of wave particles is greatest below the wave crest and decreases towards the sides and depth; uniform perforation cannot accommodate this velocity field distribution. Simultaneously, wave energy distribution varies across different periodic components, and a fixed permeability cannot achieve optimal impedance matching with the dominant wave period.

[0093] First, it is necessary to obtain the characteristic wave height H and average wave period T design values ​​obtained from long-term observation or numerical simulation of the target sea area. The design is then based on these core sea state parameters: the range of the aperture d is determined to ensure a reasonable ratio between the aperture size and the common local wave height. An aperture that is too small (less than H / 15) is prone to blockage by debris or excessive local velocity when the wave height is high, while an aperture that is too large (greater than H / 8) weakens the turbulence and shearing effects when water flows through the aperture. The design of increasing aperture gradient from the center to the edge is to match the distribution of water particle horizontal velocity in the lateral direction (perpendicular to the wave direction) under wave action. Typically, the horizontal velocity of water particles is greatest at the center of the plate, corresponding to the wave crest, and a relatively smaller aperture can generate stronger jets and vortices; while in the edge region, the water particle motion weakens, and increasing the aperture ensures sufficient water flow, avoiding excessive pressure drag and structural load, thus achieving a relative balance and optimization of energy dissipation efficiency across the entire plate surface. The logarithmic relationship between porosity η and wave period T reflects the need for the overall resistance characteristics of the energy dissipation plate to match the main vibration period of the waves. A longer period T typically corresponds to a larger displacement of water particles, requiring a higher porosity to reduce rigid resistance and allow more water to pass through, preventing the structure from bearing excessive inertial forces. A shorter period T requires a lower porosity to increase form drag and friction, rapidly dissipating energy. The coefficients k and b are adjusted according to the energy dissipation layer (e.g., first layer, second layer), reflecting the different emphases on wave energy dissipation methods at different water depth levels. The gradient design with decreasing porosity from top to bottom considers the exponential decay of wave energy with water depth. The upper plate needs to handle the strongest water movement, so the porosity setting focuses more on passage to reduce direct impact; at the lower plate, wave energy weakens, and a lower porosity enhances the disturbance and dissipation of residual water flow.

[0094] The aforementioned technical solution transforms the energy dissipation system from a "general design" to a "tailor-made" approach, thereby achieving an optimized balance between performance and cost in engineering practice. Firstly, the aperture design and gradient distribution based on wave height H significantly improve the adaptability and energy dissipation efficiency of a single energy dissipation plate to typical local waves. This makes the water flow through the plate holes closer to the design expectation, forming effective vortex energy dissipation in different areas of the plate surface, while avoiding additional loads caused by local flow separation or excessive resistance due to unreasonable design, resulting in a more rational structural stress. Secondly, the core innovation lies in linking the porosity η with the wave period T through a mathematical model. This ensures that the overall impedance characteristics of the energy dissipation plate system can be "tuned" to the dominant wave period of the sea area, allowing wave energy to be more effectively converted into turbulent kinetic energy and thermal energy through the plate holes, rather than being simply reflected or causing excessive structural movement. This broadens the effective wave dissipation frequency band, particularly improving the reduction effect on long-period swells. Furthermore, the gradient design of the multi-layered plate with decreasing porosity from top to bottom constitutes a "three-dimensional filtering" system that matches the attenuation law of wave energy at deep water. The upper plate is more like a "coarse filter," mainly for the initial attenuation and diversion of high-energy surface water; the lower plate is like a "fine filter," further disturbing and dissipating the infiltrated mid-to-low-level water flow. This synergistic design achieves stratified and efficient intervention of wave energy across the entire water column.

[0095] The aforementioned technical solution introduces a parametric design method based on characteristic wave height H and average wave period T, transforming the horizontally perforated vibration-damping heave plate 4 from an isolated, fixed-parameter component into a system closely coupled with the specific marine environment, with predictable and optimizable performance. This not only significantly improves energy dissipation efficiency but also enhances the scientific and economic feasibility of the design, enabling the breakwater to better adapt to the wave characteristics of specific sea areas and achieve optimal protective performance.

[0096] In another technical solution, the semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system also includes a structurally optimized configuration of the system based on water depth and geological conditions.

[0097] When the deployment area is a shallow water area with a water depth of less than 20m, a simplified two-stage energy dissipation configuration is adopted, namely, two layers of horizontal perforated vibration damping heave plates and one layer of vertical perforated wave damping plate; and the foundation thickness t of the horizontal perforated vibration damping heave plates increases with the increase of water depth h, satisfying: t=t0+0.5×(h-10), where t0 is the base thickness in mm;

[0098] When the deployment area is a deep water area with a depth greater than 30m, an enhanced three-stage energy dissipation configuration is adopted, with the addition of a third layer of horizontal perforated vibration damping heave plate, and the lowest vertical perforated wave-dissipating plate extending downward to 3-5m above the seabed surface.

[0099] The design weight W of the anchor block is optimized for different seabed geological types: in silty soft soil foundations, W ≥ 1.5 × F max / μ s In sandy foundations, W ≥ F max / μ s Among them, F max To design the maximum anchor chain tension, μ s This represents the friction coefficient of the anchor block in the corresponding foundation.

[0100] In the above technical solution, when the deployment area is a shallow water area with a depth of less than 20 meters, a simplified two-stage energy dissipation configuration is adopted, namely, setting two layers of horizontal perforated vibration damping heave plates 4 and one layer of vertical perforated wave-dissipating plates 6. Furthermore, for sections with a water depth h ≥ 10m, the foundation thickness t of the horizontal perforated vibration damping heave plates 4 increases with the water depth h, satisfying the relationship t = t0 + 0.5 × (h - 10), where t0 is the base thickness in mm; for sections with a water depth h < 10m, t = t0 can be taken, or determined according to the specific design. When the deployment area is a deep water area with a depth greater than 30 meters, an enhanced three-stage energy dissipation configuration is adopted, adding a third layer of horizontal perforated vibration damping heave plates 4, and the lowest vertical perforated wave-dissipating plate 6 extends downwards to 3 to 5 meters above the seabed surface. Simultaneously, the design weight W of the anchor block 71 needs to be optimized according to the seabed geological type: in silty soft soil foundations, W ≥ 1.5 × F is required. max / μ s In sandy foundations, W ≥ F is required. max / μ s Among them, F max To design the maximum anchor chain tension, μ s This refers to the friction coefficient of the anchor block under the corresponding foundation conditions. The "two-stage energy dissipation configuration" here refers to the basic energy dissipation unit consisting of two layers of horizontally perforated vibration-damping heave plates 4 and connected vertically perforated wave-damping plates 6. The "three-stage energy dissipation configuration" adds another layer of horizontally perforated vibration-damping heave plates 4 to the two-stage configuration, forming a deeper energy dissipation structure. "Foundation thickness t" refers to the basic thickness of the horizontally perforated vibration-damping heave plate 4 structure, excluding coatings, etc. "Reference thickness t0" is a pre-set design value based on material strength and conventional loads. "Design maximum anchor chain tension F" max "This is the maximum tensile force that the anchor chain can withstand, calculated based on the design sea conditions." "Anchor block friction coefficient μ" sThis reflects the anti-slip capability between the bottom surface of the anchor block and the specific seabed soil. Compared with the existing technology, which usually adopts a uniform specification and configuration for the entire breakwater system, ignoring the differences in the vertical distribution of wave energy at different water depths and the differences in the bearing capacity of different foundations, the existing technology is obviously unreasonable. In shallow water, wave energy is mainly concentrated in the entire water column, especially the movement of water particles at the bottom is still significant, and using the same number and size of energy dissipation plates as in deep water may be wasteful. In deep water, if the energy dissipation structure cannot effectively extend to a sufficient depth, it cannot fully dissipate the wave energy of the middle and lower water layers. For mooring systems, using the same weight of anchor blocks in different geological conditions may waste materials on hard foundations and result in insufficient anchoring force on soft foundations.

[0101] First, a detailed hydrogeological survey is required to determine the design water depth h and the geological type of the seabed surface in the target sea area. In shallow waters, wave motion is significant across the entire depth range, but the total water volume is relatively small. Two layers of horizontally perforated vibration-damping heave plates 4, combined with one layer of vertically perforated wave-dissipating plates 6, are sufficient to effectively cover the main energy range. The rule of linearly increasing plate thickness with water depth is based on the consideration that in slightly deeper shallow waters, although wave motion is weakened, water pressure increases, and there may be stronger bottom backflow. Appropriately increasing the plate thickness can enhance the structure's rigidity and resistance to impact fatigue. In deep waters, wave energy decreases with depth, but the impact depth is large. Adding a third layer of horizontally perforated vibration-damping heave plates 4 and significantly extending the bottommost vertically perforated wave-dissipating plate 6 downwards aims to expand the energy dissipation structure's range of action in the water depth direction, more effectively intervening in and dissipating the wave kinetic energy of the middle and lower water layers, forming a continuous energy dissipation barrier from the water surface to near the seabed. The design of anchor block 71 transforms the anchoring stability problem into a quantitative design based on soil mechanics principles. On silty soft soil, due to low soil cohesion and easy compressibility, the anti-sliding force provided solely by friction is unstable and the calculated value may be too high. Therefore, a safety factor of 1.5 is introduced to increase the required anchor block weight, ensuring no significant displacement occurs under soft soil creep or instantaneous impact. On sandy foundations, the friction coefficient is relatively stable and reliable, allowing the minimum required weight to be calculated directly based on the maximum tensile force and the friction coefficient. This differentiated design principle ensures that anchor block 71 provides sufficient safety reserve with the most economical weight under different geological conditions.

[0102] The aforementioned technical solution achieves refined, scenario-based, and economical design of floating breakwaters. Firstly, by differentiating between shallow and deep-water configurations, the complexity and scale of the energy dissipation system are precisely matched to the actual wave characteristics (vertical energy distribution) of the water area. In shallow water, excessive structural design and material waste are avoided, while in deep water, enhanced configuration ensures sufficient energy dissipation depth and effectiveness, realizing the design concept of "allocation on demand" and optimizing construction costs while ensuring performance. Secondly, the differentiated foundation design based on the weight of anchor block 71 is key to unifying the safety and economy of the mooring system. It abandons the previous crude approach of relying on experience or uniformly amplified safety factors, instead using targeted calculations based on soil mechanics principles and foundation characteristics. This prevents the risk of slippage failure due to insufficient weight of anchor block 71 on weak foundations, and also avoids material waste and increased construction difficulty caused by using excessively heavy anchor blocks 71 on good foundations. Furthermore, the rules governing the variation of slab thickness with water depth and the regulations on the vertical slab extension depth reflect a meticulous consideration of the differences in the local stress environment of the structure, enhancing the local strength and overall adaptability of the structure under different water depth conditions. In the above technical solution, by providing a clear and quantifiable set of rules for adapting to water depth and geological conditions, the design of the entire breakwater system (including energy dissipation structures and mooring foundations) moves from vague empirical judgments to scientific parametric decision-making. This not only improves the performance reliability and safety of the structure in various deployment environments but also significantly improves material utilization and engineering economy, making the technical solution of this invention more widely applicable and competitive in engineering.

[0103] In another technical solution, the semi-cylindrical hull floating breakwater with a multi-stage energy dissipation, vibration reduction, and flexible mooring system has a rated damping force F of the first and second vibration damping devices. d Must satisfy: 0.3 × F w ≤F d ≤0.7×F w F w This refers to the design wave impact force acting at the corresponding component connection location, calculated based on the Morrison equation.

[0104] Rotational damper, its torsional stiffness K t It matches the dimensions of the connected floating body unit, satisfying the empirical formula: K t =C×ρ×g×B 2 ×L×D, where ρ is the density of seawater (kg / m³) 3 g is the acceleration due to gravity (m / s²). 2Let B be the width (m) of a single floating body unit, L be the length (m), C be the correlation coefficient ranging from 0.05 to 0.15, and D be the draft (m) of the floating body unit. The value of coefficient C is determined through a combination of model tests and numerical simulations, depending on the width-to-length ratio of the floating body unit, the allowable relative rotation angle, and the wave characteristics of the target sea area. For example, for floating body units with a large width-to-length ratio, C can be taken as a higher value (e.g., 0.12 to 0.15) to provide stronger torsional constraints.

[0105] In the above technical solution, clear quantitative design criteria are provided for the first vibration damper 5, the second vibration damper 73, and the rotational damper 81. For the first vibration damper 5 and the second vibration damper 73, their rated damping force F... d Condition to be met: 0.3 × F w ≤F d ≤0.7×F w Among them, F w Let K be the design wave impact force acting at the corresponding damper installation location, calculated according to the Morrison equation. For the rotating damper 81, its torsional stiffness K... t It must match the dimensions of the connected floating body unit, satisfying the empirical formula: K t =C×ρ×g×B 2 ×L×D. Where ρ is the density of seawater (kg / m³). 3 g is the acceleration due to gravity (m / s²). 2 B is the width (m) of a single floating unit, L is the length (m), C is the correlation coefficient ranging from 0.05 to 0.15, and D is the draft (m) of the floating unit. Here, "rated damping force F" refers to... d "Refers to the maximum output damping force that the damper can stably provide." (Design wave impact force F) w "The load is calculated based on Morrison's equations in fluid mechanics, taking into account the drag force and inertial force generated by the velocity and acceleration of wave particles on the component." Torsional stiffness K t "The torque required for a rotational damper to generate a unit torsional angle reflects its ability to resist rotation." "Correlation coefficient C" is a dimensionless empirical coefficient that comprehensively reflects factors such as the motion characteristics of the floating body unit, wave conditions, and allowable relative rotation amplitude. Compared to existing technologies that typically select damper parameters based on analogy with similar engineering experience or deduce parameters through complex dynamic time-history analysis, but lack simple and universal design formulas, existing design processes are either too crude, potentially leading to substandard performance, or cumbersome, hindering preliminary design and standardization.

[0106] First, based on the design sea state (such as design wave height and period) and the dimensions of the components at the specific installation location (such as the diameter of the vertical connecting rod 3, the diameter of the anchor chain 72, or the dimensions of the connection point of the pontoon 2), the Morrison equation is applied to calculate the maximum wave load F acting at that location. w This F w The value represents the maximum environmental excitation force that the damper needs to withstand. Subsequently, based on 0.3F... w up to 0.7F w The range is used to determine the rated damping force F of the first damper 5 and the second damper 73. d This range was established based on engineering practice and theoretical analysis: If the damping force is too small (below 0.3F),... w If the damping force is too large (above 0.7F), it will be insufficient to effectively dissipate energy and control motion; if the damping force is too large (above 0.7F), it will be insufficient to effectively dissipate energy and control motion. w If the damper itself becomes too rigid, it may directly transfer excessive dynamic loads to the supporting structure or foundation, losing its buffering function and even becoming a new load transfer bottleneck. For the rotational damper 81, its design is directly related to the geometry of the floating body unit. Formula K t =C×ρ×g×B 2 The physical meaning of ×L×D is that the torsional stiffness is related to the displacement volume of the floating body unit (and B). 2 The pitch restoring moment of the floating body unit in waves is directly proportional to the product of its displacement volume (ρ × g) and seawater specific gravity (ρ × g). The pitch restoring moment depends primarily on its displacement volume and metacentric height, with draft D being a key parameter affecting the metacentric height. The torsional stiffness required by the rotation damper 81 must match the magnitude of this restoring moment to effectively suppress relative rotation caused by waves. The coefficient C ranges from 0.05 to 0.15, allowing designers to fine-tune it based on requirements for strict motion control and expected wave steepness. Higher C values ​​can be used for designs with stricter requirements and less permissible rotation.

[0107] The above technical solution ensures the effectiveness and reliability of the coordinated operation of the multi-stage energy dissipation and vibration reduction system and the flexible mooring system. First, the rated damping force F of the damper... d With wave impact force F w By establishing a reasonable proportional range (0.3~0.7), a direct scientific basis is provided for damper selection. This avoids blind selection, ensuring that the damper has sufficient capacity to dissipate the main wave energy while maintaining a certain degree of flexibility to avoid becoming a rigid connection point, thus achieving an optimal balance between energy dissipation and buffering. This principle is crucial for the first damping damper 5 and the second damping damper 73 installed on the critical force transmission path. Secondly, the torsional stiffness K provided for the rotational damper 81... tThe empirical formula cleverly links the damper parameters with the basic dimensions of the floating body unit and the properties of seawater. This allows designers to quickly estimate the required stiffness value without complex dynamic analysis, greatly simplifying the design process and promoting standardization. The formula ensures that the "strength" of the rotating damper 81 matches the "scale" of the floating body unit, effectively limiting harmful relative rotation between adjacent units and maintaining the overall shape of the breakwater, while preventing excessive stiffness from completely locking the connection and affecting the system's adaptability to wave fluctuations. In the above technical solution, the quantitative design criteria solve the problem of the disconnect between damper element parameter design and overall system performance requirements. This makes the damper no longer an isolated component, but a system integration element deeply integrated with wave loads and structural characteristics, with predictable and optimizable parameters. This not only improves the working efficiency and reliability of each damper element itself, but more importantly, ensures that the entire energy dissipation and vibration reduction chain and flexible mooring chain, formed by their series or parallel connection, can work collaboratively and efficiently, thereby stably achieving the comprehensive technical effects expected by this invention.

[0108] The number of devices and processing scale described herein are for the purpose of simplifying the description of the invention. Applications, modifications, and variations of the invention will be readily apparent to those skilled in the art.

[0109] Although embodiments of the present invention have been disclosed above, they are not limited to the applications listed in the specification and embodiments. They can be applied to various fields suitable for the present invention. For those skilled in the art, other modifications can be easily made. Therefore, without departing from the general concept defined by the claims and their equivalents, the present invention is not limited to the specific details and illustrations shown and described herein.

Claims

1. A semi-cylindrical shell floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system, characterized in that, include: A floating unit, comprising a semi-cylindrical hull and a pontoon connected to the bottom of the semi-cylindrical hull; The semi-cylindrical shell has multiple wave-damping holes on its wave-facing side; The energy dissipation and vibration reduction system, located below the pontoon, includes: Multiple vertical connecting rods are arranged in a matrix, with the top of each vertical connecting rod connected to the bottom of the pontoon and the bottom extending downwards; At least two layers of horizontally perforated vibration damping sway plates are fixedly sleeved on multiple vertical connecting rods at intervals along the vertical direction, and the at least two layers of horizontally perforated vibration damping sway plates divide each vertical connecting rod into multiple segments; Multiple first vibration dampers are respectively installed on the segments of the vertical connecting rod, and are located between two adjacent layers of horizontal through-hole vibration damping sway plates, and between the pontoon and the uppermost horizontal through-hole vibration damping sway plate; At least one vertical perforated wave-damping plate, the plate surface of which is arranged parallel to the wave incident direction, and the two ends of the vertical perforated wave-damping plate are respectively connected to the shells of two first vibration dampers located at the same height; A flexible mooring system includes an anchor block on the seabed, an anchor chain connecting the anchor block to the bottom of the pontoon, and a second vibration damper on the anchor chain. The vertical connecting rod includes an inner column and an outer sleeve arranged coaxially, forming an annular cavity filled with magnetorheological fluid; a piezoelectric sensing layer is provided on the outer wall of the inner column, and a first electrode layer is covered on the outer surface of the piezoelectric sensing layer; a second electrode layer is correspondingly provided on the inner wall of the outer sleeve. The inner column and the outer sleeve are connected by flexible pleated membranes at multiple axial intervals. The flexible pleated membranes seal the annular cavity and divide the annular cavity into multiple independent damping adjustment segments along the axial direction. The vertical connecting rod is equipped with a controller. The signal input end of the controller is connected to the piezoelectric sensing layer, and the output end is connected to the first electrode layer and the second electrode layer of each damping adjustment segment. Each layer of horizontal perforated vibration damping heave plate is a detachable modular energy dissipation cylinder; each energy dissipation cylinder consists of an outer frame and multiple layers of staggered metal mesh grids inside the outer frame. The surface of the metal mesh grids is coated with a catalytic coating, and the staggered gaps of the metal mesh grids are filled with porous elastic damping material blocks. The outer frame is connected to the vertical connecting rod through a quick-locking mechanism. The quick-locking mechanism consists of multiple eccentric cam locks evenly distributed around the circumference. The rotating shaft of each lock passes through the wall panel of the outer frame and is connected to the pre-tightening pressure plate at its inner end. When the lock is closed, the rotating shaft drives the pre-tightening pressure plate to press axially onto the vertical connecting rod.

2. The semi-cylindrical shell floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system as described in claim 1, characterized in that, The two sides of the pontoon are provided with connectors for connecting adjacent pontoon units, and rotation dampers are provided between the connectors.

3. The semi-cylindrical shell floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system as described in claim 1, characterized in that, The flexible mooring system also includes a gravity anchoring platform set on the seabed, with anchor blocks distributed on the upper surface of the gravity anchoring platform via universal joints; the anchor chain is divided into an upper chain segment and a lower chain segment, with a second vibration damper connected between the upper and lower chain segments; the lower end of the lower chain segment is connected to the center of the gravity anchoring platform via a spherical bearing hinge.

4. The semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system as described in claim 1, characterized in that, The inner cavity of the semi-cylindrical hull is equipped with a sealed air chamber that communicates with the pontoon; the air chamber is connected to an air storage tank located in the pontoon through a first pipe, and the air storage tank is connected to an air compressor located in the pontoon through a second pipe; the inner end of the wave-damping hole is connected to the air chamber; the wave-damping hole is connected to the air chamber.

5. The semi-cylindrical hull floating breakwater with a multi-stage energy dissipation, vibration reduction, and flexible mooring system as described in claim 1, characterized in that, The opening design of the horizontal perforated vibration damping plate is parametrically adapted based on the characteristic wave height H and average wave period T of the target sea area; wherein: The aperture diameter d satisfies: H / 15≤d≤H / 8, and the aperture diameter on the same layer plate increases gradually from the center to the edge, with the aperture diameter in the edge region being 1.2 to 1.5 times that in the center region; The overall permeability η of the plate is optimized based on the wave period T and satisfies the relationship: η=k×ln(T)+b, where k and b are coefficients related to the energy dissipation cylinder level, and the permeability of each layer of the plate decreases sequentially from top to bottom, with a permeability gradient difference of 5~10%.

6. The semi-cylindrical shell floating breakwater with multi-stage energy dissipation, vibration reduction, and flexible mooring system as described in claim 1, characterized in that, It also includes structural optimization of the system based on water depth and geological conditions: When the deployment area is a shallow water area with a water depth of less than 20m, a simplified two-stage energy dissipation configuration is adopted, namely, two layers of horizontal perforated vibration damping heave plates and one layer of vertical perforated wave damping plate; and the foundation thickness t of the horizontal perforated vibration damping heave plates increases with the increase of water depth h, satisfying: t=t0+0.5×(h-10), where t0 is the base thickness in mm; When the deployment area is a deep water area with a depth greater than 30m, an enhanced three-stage energy dissipation configuration is adopted, with the addition of a third layer of horizontal perforated vibration damping heave plate, and the lowest vertical perforated wave-dissipating plate extending downward to 3-5m above the seabed surface. The design weight W of the anchor block is optimized for seabed geological types: in silty soft soil foundations, W ≥ 1.5 × Fmax / μ s In sandy foundations, W ≥ F max / μ s Among them, F max To design the maximum anchor chain tension, μ s This represents the friction coefficient of the anchor block in the corresponding foundation.

7. The semi-cylindrical hull floating breakwater with a multi-stage energy dissipation and vibration reduction system and a flexible mooring system as described in claim 2, characterized in that: The rated damping force F of the first and second vibration dampers d Must satisfy: 0.3 × F w ≤F d ≤0.7×F w , where F w This refers to the design wave impact force acting at the corresponding component connection location, calculated based on the Morrison equation. Rotational damper, its torsional stiffness K t It matches the dimensions of the connected floating body unit, satisfying the empirical formula: K t =C×ρ×g×B 2 ×L×D, where ρ is the density of seawater, g is the gravitational acceleration, B is the width of a single floating unit, L is the length, C is the correlation coefficient ranging from 0.05 to 0.15, and D is the draft of the floating unit.

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