WO2025218488A1 - 波浪能转换装置及其评价方法 - Google Patents

波浪能转换装置及其评价方法

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Publication number
WO2025218488A1
WO2025218488A1 PCT/CN2025/086582 CN2025086582W WO2025218488A1 WO 2025218488 A1 WO2025218488 A1 WO 2025218488A1 CN 2025086582 W CN2025086582 W CN 2025086582W WO 2025218488 A1 WO2025218488 A1 WO 2025218488A1
Authority
WO
WIPO (PCT)
Prior art keywords
energy conversion
flow channel
wave energy
conversion device
wave
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/CN2025/086582
Other languages
English (en)
French (fr)
Inventor
张永良
郭鹏
杨焕彬
徐浩淳
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Tsinghua University
Original Assignee
Tsinghua University
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Tsinghua University filed Critical Tsinghua University
Publication of WO2025218488A1 publication Critical patent/WO2025218488A1/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B13/00—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates
    • F03B13/12—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy
    • F03B13/14—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy
    • F03B13/24—Adaptations of machines or engines for special use; Combinations of machines or engines with driving or driven apparatus; Power stations or aggregates characterised by using wave or tide energy using wave energy to produce a flow of air, e.g. to drive an air turbine
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F03—MACHINES OR ENGINES FOR LIQUIDS; WIND, SPRING, OR WEIGHT MOTORS; PRODUCING MECHANICAL POWER OR A REACTIVE PROPULSIVE THRUST, NOT OTHERWISE PROVIDED FOR
    • F03B—MACHINES OR ENGINES FOR LIQUIDS
    • F03B15/00—Controlling
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/0413—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded in the form of closure plates
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/044—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with more than one spring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/04—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded
    • F16K17/06—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side spring-loaded with special arrangements for adjusting the opening pressure
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16K—VALVES; TAPS; COCKS; ACTUATING-FLOATS; DEVICES FOR VENTING OR AERATING
    • F16K17/00—Safety valves; Equalising valves, e.g. pressure relief valves
    • F16K17/02—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side
    • F16K17/164—Safety valves; Equalising valves, e.g. pressure relief valves opening on surplus pressure on one side; closing on insufficient pressure on one side and remaining closed after return of the normal pressure
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • G06F30/28—Design optimisation, verification or simulation using fluid dynamics, e.g. using Navier-Stokes equations or computational fluid dynamics [CFD]
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06Q—INFORMATION AND COMMUNICATION TECHNOLOGY [ICT] SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES; SYSTEMS OR METHODS SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES, NOT OTHERWISE PROVIDED FOR
    • G06Q10/00—Administration; Management
    • G06Q10/06—Resources, workflows, human or project management; Enterprise or organisation planning; Enterprise or organisation modelling
    • G06Q10/063—Operations research, analysis or management
    • G06Q10/0639—Performance analysis of employees; Performance analysis of enterprise or organisation operations
    • G06Q10/06393—Score-carding, benchmarking or key performance indicator [KPI] analysis
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06Q—INFORMATION AND COMMUNICATION TECHNOLOGY [ICT] SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES; SYSTEMS OR METHODS SPECIALLY ADAPTED FOR ADMINISTRATIVE, COMMERCIAL, FINANCIAL, MANAGERIAL OR SUPERVISORY PURPOSES, NOT OTHERWISE PROVIDED FOR
    • G06Q50/00—Information and communication technology [ICT] specially adapted for implementation of business processes of specific business sectors, e.g. utilities or tourism
    • G06Q50/06—Energy or water supply
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2111/00—Details relating to CAD techniques
    • G06F2111/10—Numerical modelling
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2113/00—Details relating to the application field
    • G06F2113/08—Fluids
    • G—PHYSICS
    • G06—COMPUTING OR CALCULATING; COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
    • G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/30—Energy from the sea, e.g. using wave energy or salinity gradient

Definitions

  • the present application relates to the technical field of ocean wave energy utilization, and in particular to a wave energy conversion device and an evaluation method thereof.
  • Wave energy for example.
  • Wave energy boasts high energy density, wide distribution, and renewable potential.
  • Related technologies utilize wave energy conversion devices to convert wave energy into electricity through a series of energy conversions.
  • excessively high waves in the environment surrounding a wave energy conversion device can threaten its safety.
  • the present application provides a wave energy conversion device, comprising a fluid flow channel, an energy conversion system and a pressure relief system.
  • the fluid flow channel is used to convert the wave energy transmitted to the fluid flow channel into aerokinetic energy.
  • the energy conversion system is connected to the fluid flow channel and is used to convert the aerokinetic energy converted by the fluid flow channel into electrical energy; it comprises an air turbine, which comprises a flow channel wall, two groups of guide blades and a group of rotor blades; the contour line of the cross section of each guide blade comprises an elliptical arc segment and a straight line segment, and the straight line segment is arranged along the tangent direction of the circle around the main axis of rotation at one end point of the straight line segment; the contour line of the cross section of each rotor blade in the axial direction comprises an elliptical arc segment on the suction side and a circular arc segment on the pressure side; the number of guide blades in each group is 14-24.
  • the pressure relief system is connected to the fluid flow channel and is used to control the air chamber pressure in the fluid flow channel; it includes a valve flap, a valve seat, an elastic unit, a control rod and a connecting pipe, the valve flap is connected to the valve seat via the elastic unit; the valve flap is also connected to the air chamber via the connecting pipe; the control rod is fixedly connected to the valve seat, and the control rod is movably connected to the valve flap and the control component respectively; the control rod is a telescopic rod; the valve flap has multiple corresponding opening thresholds.
  • the control component is deployed on the surface of the connecting pipe and is used to dynamically adjust the initial length of the elastic unit through the control rod according to the sea conditions of the wave energy conversion device to control the corresponding opening threshold of the valve flap; the control component has multiple adjustment lengths for adjusting the initial length of the elastic unit.
  • valve flap when the pressure of the air chamber exceeds the opening threshold, the valve flap is in an open state, and when the pressure of the air chamber does not exceed the opening threshold, the valve flap is in a closed state.
  • the energy conversion system includes an air turbine and a power generation assembly, wherein the air turbine is connected to the power generation assembly.
  • the air turbine is configured to convert the pneumatic energy converted by the fluid flow path into mechanical energy.
  • the power generation assembly is configured to convert the mechanical energy converted by the air turbine into electrical energy.
  • the rotor speed of the air turbine is the same as the rotor speed of the generator.
  • the air turbine further includes a rotating main shaft and a rotor portion; one group of guide blades of the two groups of guide blades are evenly distributed at the flow channel inlet of the flow channel wall, and the other group of guide blades are evenly distributed at the flow channel outlet of the flow channel wall; the group of rotor blades are evenly distributed on the rotor portion in the central area of the flow channel of the air turbine along the circumference around the rotating main shaft.
  • a contour line of a cross section of the flow channel wall between the rotor blades and the guide vanes in the axial direction includes a 90° arc segment and straight line segments on both sides of the arc segment.
  • the device further comprises one or more mooring systems; the one or more mooring systems are connected to the wave-facing side of the wave energy conversion device.
  • each mooring system comprises a buoy, and the buoy is connected to the wave-facing side of the wave energy conversion device via at least one elastic component.
  • the fluid flow channel includes a horizontal flow channel and a vertical flow channel that are interconnected.
  • the vertical flow channel is arranged near the wave-facing side of the wave energy conversion device, and the mouth of the horizontal flow channel is arranged near the wave-receiving side of the wave energy conversion device.
  • the cross-sectional area of the horizontal flow channel is equal to the cross-sectional area of the vertical flow channel; the horizontal flow channel and the vertical flow channel are connected by a streamlined flow channel.
  • the fluid flow channel further includes a plurality of partitions; each partition is vertically fixed to the flow channel walls of the horizontal flow channel and the vertical flow channel.
  • the present application also provides a method for evaluating a wave energy conversion device, which includes the following steps.
  • a mathematical model is constructed for the wave energy conversion device according to any one of the first aspects.
  • the mathematical model is a simulation equation for simulating the motion characteristics of the wave energy conversion device.
  • the mathematical model is solved and the evaluation index value of the wave energy conversion device is obtained.
  • solving a mathematical model to obtain an evaluation index value of a wave energy conversion device includes the following steps.
  • the mathematical model is discretized to obtain a numerical model.
  • Discretization includes spatial discretization and temporal discretization.
  • the time history curve of the wave energy conversion device is solved.
  • the time history curve includes the corresponding relationship between the motion response and dynamic characteristics of the wave energy conversion device and time.
  • the evaluation index value of the wave energy conversion device is obtained.
  • solving a time history curve of a wave energy conversion device based on a numerical model includes the following steps.
  • the simulation time period is divided according to the preset time step to determine multiple moments.
  • a time course curve is constructed based on each moment and the motion response value corresponding to each moment.
  • obtaining the motion response value corresponding to the numerical model at each moment includes: for each moment, iteratively solving the numerical model according to a preset iterative strategy until the numerical model meets a preset convergence condition, thereby obtaining the motion response value at each moment.
  • the evaluation index value includes a power generation capacity index value and a reliability index value of the wave energy conversion device.
  • the present application also provides an evaluation device, which includes: a construction module and a calculation module.
  • a construction module is used to construct a mathematical model for the wave energy conversion device of any one of the first aspects, where the mathematical model is a simulation equation for simulating the motion characteristics of the wave energy conversion device.
  • the calculation module is used to solve the mathematical model and obtain the evaluation index value of the wave energy conversion device.
  • the present application further provides a computer device comprising a memory and a processor, wherein the memory stores a computer program, and when the processor executes the computer program, the steps of the wave energy conversion device evaluation method in any one of the embodiments of the second aspect are implemented.
  • the present application also provides a non-volatile computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the steps of the wave energy conversion device evaluation method in any one of the embodiments of the second aspect above.
  • the present application further provides a computer program product comprising computer executable instructions, which, when executed by a processor, implement the steps of the wave energy conversion device evaluation method in any one of the embodiments of the second aspect above.
  • the wave energy conversion device includes: a fluid flow channel, an energy conversion system, a pressure relief system and a control component.
  • the fluid flow channel is used to convert the wave energy transmitted to the fluid flow channel into aerokinetic energy.
  • the energy conversion system is connected to the fluid flow channel and is used to convert the aerokinetic energy converted by the fluid flow channel into electrical energy.
  • the air turbine includes a flow channel wall, two groups of guide blades and a group of rotor blades;
  • the contour line of the cross section of each guide blade includes an elliptical arc segment and a straight line segment, and the straight line segment is arranged along the tangent direction of the circle around the rotating main axis at one end point of the straight line segment;
  • the contour line of the cross section of each rotor blade in the axial direction includes an elliptical arc segment on the suction side and a circular arc segment on the pressure side; the number of guide blades in each group is 14-24.
  • the pressure relief system is connected to the fluid flow channel and is used to control the air chamber pressure in the fluid flow channel; it includes a valve flap, a valve seat, an elastic unit, a control rod and a connecting pipe, the valve flap is connected to the valve seat through the elastic unit; the valve flap is also connected to the air chamber through the connecting pipe; the control rod is fixedly connected to the valve seat, and the control rod is movably connected to the valve flap and the control component respectively; the control rod is a telescopic rod; the valve flap has multiple opening thresholds.
  • the control component is deployed on the surface of the connecting pipe and is used to dynamically adjust the initial length of the elastic unit through the control rod according to the sea conditions of the wave energy conversion device to control the opening threshold corresponding to the valve flap; the control component has multiple adjustment lengths for adjusting the initial length of the elastic unit.
  • the fluid flow channel converts wave energy into aerokinetic energy
  • the energy conversion system converts the aerokinetic energy converted by the fluid flow channel into electrical energy, that is, wave energy is converted into electrical energy through the fluid flow channel and the energy conversion system.
  • the pressure relief system controls the pressure of the air chamber in the fluid flow channel. This is equivalent to taking into account the factor that excessive waves affect the stability of the wave energy conversion device.
  • the pressure of the air chamber in the fluid flow channel is adjusted to a normal pressure range through the pressure relief system to ensure the safety of the wave energy conversion device.
  • FIG1 is a schematic structural diagram of a wave energy conversion device according to an embodiment of the present application.
  • FIG2 is a schematic structural diagram of a pressure relief system according to an embodiment of the present application.
  • FIG3 is a schematic structural diagram of a pressure relief system in another embodiment of the present application.
  • FIG4 is a front view of an air turbine according to one embodiment of the present application.
  • FIG5 is a top view of an air turbine according to one embodiment of the present application.
  • FIG6 is a schematic structural diagram of a wave energy conversion device according to another embodiment of the present application.
  • FIG7 is a schematic structural diagram of a mooring system according to an embodiment of the present application.
  • FIG8 is a schematic structural diagram of a wave energy conversion device in another embodiment of the present application.
  • FIG9 is a schematic flow chart of an evaluation method in one embodiment of the present application.
  • FIG10 is a flow chart of an indicator acquisition step in one embodiment of the present application.
  • FIG11 is a schematic diagram of a flow chart of a curve construction step in one embodiment of the present application.
  • FIG12 is a schematic flow chart of an evaluation method in another embodiment of the present application.
  • FIG13 is a schematic flow chart of an evaluation method in another embodiment of the present application.
  • FIG14 is a curve comparison diagram of the steady-state efficiency of turbines in one embodiment of the present application.
  • FIG15 is a schematic diagram of a curve of device performance parameters in one embodiment of the present application.
  • FIG16 is a structural block diagram of an evaluation device in one embodiment of the present application.
  • FIG17 is a diagram showing the internal structure of a computer device in one embodiment of the present application.
  • Wave energy conversion device 11. Fluid flow channel; 12 Energy conversion system; 121 Air turbine; 1211 guide vane; 1212 rotor blade; 13 pressure relief system; 1311 valve disc; 1312 elastic unit; 1313 valve seat; 1314 control rod; 1315 connecting pipe; 14 mooring system; 141 anchor; 142 chain segment; 143 float; 144 elastic components; 15 main buoyancy compartments; 16 secondary buoyancy tanks.
  • Wave energy is the highest-quality and most widely distributed marine renewable energy source that humans have yet to commercially develop. It is considered to be civilization's hope for future energy.
  • how to achieve efficient and reliable wave energy conversion is a major scientific issue in the global renewable energy field.
  • pneumatic wave energy conversion devices have the advantages of being relatively more efficient and more reliable.
  • pneumatic wave energy conversion devices still have shortcomings and challenges in improving efficiency, reliability, and design optimization theory, resulting in slow industrial development.
  • High reliability is the first indicator of a pneumatic wave energy conversion device.
  • the overall movement of the device and the oscillation of the water inside the air chamber are violent, the pressure on the flow channel wall of the device is too high, and at the same time, the pressure inside the air chamber of the device is too high, and the pneumatic energy input to the impulse air turbine is excessive, which seriously affects the reliability of the flow channel, turbine rotor, generator and the entire device. Therefore, a corresponding pressure relief and load reduction system must be adopted to protect the safety of the device; on the other hand, the violent and large movement of the device causes excessive force on the mooring system, which seriously affects the reliability and survivability of the mooring system and the entire device.
  • the energy conversion efficiency of the pneumatic wave energy conversion device is still low, and the wave frequency range that meets the requirements for efficient energy capture is still narrow.
  • the energy conversion process of the pneumatic wave energy conversion device includes the following three stages: the hull converts wave energy into aerodynamic energy, the air turbine converts aerodynamic energy into the rotational kinetic energy of the turbine rotor, and the generator converts the rotational kinetic energy into electrical energy.
  • the improvement of the energy conversion efficiency of any of the above stages affects the overall energy conversion efficiency of the pneumatic wave energy conversion device to varying degrees.
  • the air turbines currently used in aerodynamic wave energy conversion devices are mostly Wells turbines, axial-flow impulse turbines with fixed and symmetrically distributed guide vanes, and radial-inflow impulse turbines.
  • Wells turbines have high peak efficiency, but they suffer from stalling and are unsuitable for waters with low wave energy density, such as the west coast of the Pacific.
  • Axial-flow impulse turbines with fixed and symmetrically distributed guide vanes have a maximum average efficiency of no more than 48% under reciprocating airflow, severely limiting the overall performance of the device.
  • Existing radial-inflow impulse turbines often have large radial dimensions, making them difficult to install in aerodynamic wave energy conversion devices. Furthermore, their efficiency could be further improved.
  • the pneumatic wave energy conversion devices in the related art have the problems of low reliability and low energy conversion efficiency, and there is also a lack of theoretical optimization methods for wave energy conversion devices.
  • the present application provides an automatic pressure relief and load reduction system with adjustable thresholds to protect the reliability of the wave energy conversion device in real time; constructs a mooring system for the wave energy conversion device based on high-strength elastic components to reduce the maximum force of the mooring system and further improve the safety performance of the wave energy conversion device; and proposes a radial inflow impact air turbine, which improves the conversion efficiency of the wave energy conversion device due to its high reliability, high efficiency, and relatively compact axially and radially.
  • the embodiment of the present application also provides a simulation method for the full system coupling from wave to electricity for a pneumatic wave energy conversion device, filling the gap in the design optimization theory of wave energy conversion devices.
  • a wave energy conversion device 10 comprising a fluid flow channel 11, an energy conversion system 12, and a pressure relief system 13, wherein the fluid flow channel 11 is connected to the pressure relief system 13, and the fluid flow channel 11 is connected to the energy conversion system 12;
  • the fluid flow channel 11 is used to convert the wave energy transmitted to the fluid flow channel 11 into aerodynamic energy.
  • the energy conversion system 12 is used to convert the pneumatic energy converted by the fluid flow channel 11 into electrical energy.
  • the pressure relief system 13 is used to control the pressure of the air chamber in the fluid flow channel 11 .
  • the wave energy conversion device 10 shown in Figure 1 comprises a fluid flow channel 11, an energy conversion system 12, and a pressure relief system 13. As can be seen from Figure 1, the fluid flow channel 11 is connected to the energy conversion system 12 and the pressure relief system 13 respectively.
  • the fluid channel 11 includes a liquid channel and a gas channel.
  • One end of the fluid channel 11 (the inlet of the liquid channel) is connected to the water body to convert wave energy into aerodynamic energy.
  • the other end of the fluid channel 11 (the outlet of the gas channel) is connected to an energy conversion system 12, which converts the aerodynamic energy generated by the fluid channel 11 into electrical energy, for example, converting aerodynamic energy into rotational kinetic energy and then converting rotational kinetic energy into electrical energy.
  • the fluid flow channel 11 is also connected to the pressure relief system 13, so that the pressure relief system 13 automatically opens or closes the valve flap in the pressure relief system 13 according to the air chamber pressure of the gas flow channel in the fluid flow channel 11, thereby controlling the connection or closure between the fluid flow channel 11 and the atmosphere to control the air chamber pressure in the fluid flow channel 11.
  • the fluid flow channel 11 in the wave energy conversion device 10 is too high, considering that the aerokinetic energy input to the energy conversion system 12 is excessive, affecting the reliability of the wave energy conversion device 10, it is necessary to control the fluid flow channel 11 to be connected to the atmosphere to reduce the pressure of the air chamber in the fluid flow channel 11; if the pressure of the fluid flow channel 11 in the wave energy conversion device 10 is within the preset threshold range, it means that the aerokinetic energy of the energy conversion system 12 is not sufficient to affect the reliability of the wave energy conversion device 10. At this time, the fluid flow channel 11 can be controlled to be disconnected from the outside atmosphere, and no longer plays a role in reducing the pressure of the air chamber in the fluid flow channel 11.
  • the wave energy conversion device 10 also has a mooring function. Based on this, please continue to refer to Figure 1.
  • the wave energy conversion device 10 in the embodiment of the present application also includes a mooring system 14, which is used to fix the wave energy conversion device 10.
  • the mooring system 14 in the embodiment of the present application can be arranged on the wave-facing side or the wave-repelling side of the wave energy conversion device 10.
  • the present application takes the mooring system 14 arranged on the wave-facing side of the wave energy conversion device 10 in FIG1 as an example.
  • the wave energy conversion device 10 includes a fluid flow channel 11, an energy conversion system 12, and a pressure relief system 13.
  • the fluid flow channel 11 is connected to the pressure relief system 13, and the fluid flow channel 11 is connected to the energy conversion system 12.
  • the fluid flow channel 11 is used to convert the wave energy transmitted to the fluid flow channel 11 into aerokinetic energy.
  • the energy conversion system 12 is used to convert the aerokinetic energy converted by the fluid flow channel 11 into electrical energy.
  • the pressure relief system 13 is used to control the pressure of the air chamber in the fluid flow channel 11.
  • the fluid flow channel 11 converts wave energy into aerokinetic energy
  • the energy conversion system 12 converts the aerokinetic energy converted by the fluid flow channel 11 into electrical energy, that is, the wave energy is converted into electrical energy through the fluid flow channel 11 and the energy conversion system 12.
  • the pressure relief system 13 controls the pressure of the air chamber in the fluid flow channel 11. That is, taking into account the factor that excessive waves may affect the stability of the wave energy conversion device 10, the pressure relief system 13 is used to adjust the pressure of the air chamber in the fluid flow channel 11 to a normal pressure range, thereby ensuring the safety of the wave energy conversion device 10.
  • the fluid flow channel 11 includes a horizontal flow channel and a vertical flow channel that are interconnected.
  • the vertical flow channel is arranged close to the wave-facing side of the wave energy conversion device 10
  • the horizontal flow channel is arranged close to the wave-receiving side of the wave energy conversion device 10.
  • the cross-sectional area of the horizontal flow channel is equal to the cross-sectional area of the vertical flow channel, and the horizontal flow channel and the vertical flow channel are connected by a streamlined flow channel.
  • the fluid flow channel 11 can be an L-shaped flow channel, specifically including a horizontal section and a vertical section that are interconnected.
  • the end of the horizontal section away from the vertical section is the mouth of the fluid flow channel 11 and is completely immersed in the water body.
  • the mouth of the fluid flow channel 11 is located on the back-wave side, and the upper half of the vertical section is an air chamber.
  • the horizontal cross-section can be rectangular, pentagonal or other streamlined shapes
  • the vertical cross-section of the fluid flow channel 11 can be rectangular.
  • the upper and lower corners inside the fluid flow channel 11 may be chamfered or rounded.
  • the fluid flow channel 11 further includes a plurality of partitions, each of which is vertically fixed to the channel walls of the horizontal flow channel and the vertical flow channel.
  • a plurality of vertical partitions are arranged perpendicular to the channel wall at predetermined intervals.
  • Each partition is fixedly connected to the inner and outer walls of the channel, for example, by welding.
  • the number of vertical partitions is set to 1 to 3.
  • one end of the partition extends to the mouth of the horizontal section of the fluid flow channel 11 , and the other end extends to the free water surface position of the vertical section of the fluid flow channel 11 .
  • the vertical baffles help guide the water in the fluid flow channel 11 to flow smoothly in the vertical direction, thereby improving the energy capture efficiency of the wave energy conversion device 10; at the same time, the vertical baffles strengthen the structural strength of the fluid flow channel of the device, and can also improve the safety of the wave energy conversion device 10 in complex sea conditions to a certain extent.
  • the pressure relief system 13 includes a valve flap 1311, a valve seat 1313, an elastic unit 1312, a control rod 1314, and a connecting pipe 1315.
  • the valve flap 1311 is connected to the valve seat 1313 via the elastic unit 1312, and the valve flap 1311 is further connected to the air chamber via the connecting pipe 1315.
  • the control rod 1314 is fixedly connected to the valve seat 1313, and the control rod 1314 is movably connected to the valve flap 1311 and the control assembly, respectively.
  • the control component is used to dynamically adjust the initial length of the elastic unit 1312 through the control rod 1314 to control the corresponding opening threshold of the valve disc 1311.
  • the control rod 1314 may be a telescopic rod
  • the elastic unit 1312 may be a spring or other elastic system
  • the initial state of the elastic unit 1312 is a compressed state
  • the initial length is the compressed length of the elastic unit 1312 in the compressed state.
  • the dotted line on the inner wall of the connecting tube 1315 in Figure 2 represents a plane with a gap, on which a control component can be installed.
  • the control component deployed on the surface of the connecting tube 1315 can be connected to the control rod 1314 to flexibly adjust the upward/downward movement of the control rod 1314, thereby controlling the initial length of the elastic unit 1312 to shorten/lengthen, and further controlling the corresponding opening threshold of the valve flap 1311 to increase/decrease.
  • control component when the control component detects that the wave energy conversion device 10 is in or about to be in severe sea conditions, it can control the control rod 1314 in the pressure relief system 13 to move downward, so that the initial length of the elastic unit 1312 becomes longer, thereby lowering the opening threshold of the valve flap 1311.
  • control component monitors that the wave energy conversion device 10 is converted from severe sea conditions to normal sea conditions, it controls the control rod 1314 in the pressure relief system 13 to move upward, so that the initial length of the elastic unit 1312 becomes shorter, or returns to the initial compressed length, so as to increase the opening threshold of the valve flap 1311.
  • control component can also be connected to the elastic unit 1312 to directly adjust the initial length of the elastic unit 1312.
  • control component can have multiple adjustment lengths for adjusting the initial length of the elastic unit through the control rod 1314, that is, the valve flap 1311 can have multiple opening thresholds, and the embodiment of the present application does not limit this.
  • valve flap 1311 when the pressure of the air chamber exceeds the opening threshold, the valve flap 1311 is in an open state to perform a pressure relief and load unloading action.
  • valve flap 1311 When the pressure of the air chamber does not exceed the opening threshold, the valve flap 1311 is in a closed state to stop performing the pressure relief and load reduction action.
  • valve flap 1311 Under normal conditions, as shown in Figure 2 , valve flap 1311 is closed due to the force of gravity and elastic pressure. When the pressure within the air chamber reaches a threshold, the gas pressure acting on valve flap 1311 becomes greater than the sum of its own gravity and elastic pressure, causing valve flap 1311 to move upward (toward the valve seat) and open, as shown in Figure 3 . At this point, the air chamber is connected to the atmosphere, relieving pressure and load, and protecting the various components of energy conversion system 12.
  • the energy conversion system 12 includes an air turbine 121 and a power generation assembly, wherein the air turbine is connected to the power generation assembly.
  • the air turbine 121 is used to convert the pneumatic energy converted by the fluid flow channel 11 into mechanical energy.
  • the power generation component is used to convert the mechanical energy converted by the air turbine 121 into electrical energy.
  • the rotor speed of the air turbine 121 is the same as the rotor speed of the power generation assembly.
  • Air turbine 121 can be an impulse-type air turbine with self-rectifying characteristics.
  • Figure 4 is a schematic structural diagram of air turbine 121.
  • air turbine 121 includes guide vanes 1211 and rotor blades 1212.
  • the air torque acting on rotor blades 1212 of air turbine 121 is always in the same direction.
  • rotor blades 1212 of air turbine 121 always maintain unidirectional rotation, so that air turbine 121 can fully convert aerokinetic energy into mechanical energy, thereby improving the overall energy conversion efficiency of wave energy conversion device 10.
  • the height between the flow channel inlet of the air turbine 121 and the free water surface in the air chamber meets a certain vertical distance requirement, that is, under the operating conditions of the wave energy conversion device 10, the water in the fluid flow channel 11 will not flow back into the turbine flow channel.
  • the impact air turbine and the air chamber are connected by a flow channel with a streamlined profile, or the upper side wall of the flow channel inlet below the turbine coincides with the top side wall of the air chamber, thereby achieving a fixed connection between the hull part of the device and the impact air turbine.
  • the power generation component can be a direct-drive generator, which causes the rotor to rotate through the rotating magnetic field formed by permanent magnets, thereby generating induced electromotive force, which is processed by electrical equipment such as rectifiers and ultimately converts mechanical energy into electrical energy.
  • the power generation component is coaxially connected to the turbine rotor 121 and has the same rotation speed, so that the power generation component can fully utilize the mechanical energy converted by the air turbine 121 and improve the conversion efficiency of mechanical energy into electrical energy.
  • the air turbine 121 includes a flow channel wall, two groups of guide vanes 1211 and rotor blades 1212 .
  • One set of guide blades of the two sets of guide blades 1211 is evenly distributed at the flow channel inlet of the flow channel wall, and the other set of guide blades is evenly distributed at the flow channel outlet of the flow channel wall.
  • the rotor blades 1212 are evenly distributed in the axial direction in the central area of the flow passage of the air turbine 121 .
  • the air turbine 121 is an impact air turbine, which consists of a flow channel wall, two sets of guide blades 1211, a turbine rotor part (including a hub), rotor blades 1212 fixed on the rotor part (hub), and a rotating main shaft.
  • the flow channel of air turbine 121 is shaped like the area formed by rotating a letter U of a certain thickness. It can be divided into guide vanes 1211, the flow channel wall (transition section), and rotor blades 1212. Further, referring to Figure 5, which is a top view of air turbine 121, it can be seen that the guide vanes 1211 of air turbine 121 are evenly distributed at the flow channel inlet of the flow channel wall. It should be noted that air turbine 121 has a symmetrical structure. That is, the top view and bottom view of air turbine 121 arranged vertically in the axial direction (i.e., the direction of the main axis of rotation) are the same. Therefore, in the embodiment of the present application, another set of guide vanes 1211 of air turbine 121 is evenly distributed near the flow channel outlet of the flow channel wall.
  • the two groups of guide vanes 1211 are fixedly connected to the flow channel wall of the air turbine 121 and are evenly and symmetrically distributed along the circumference at positions close to the flow channel inlet and the flow channel outlet.
  • the cross-sections of the guide vanes 1211 are of equal thickness.
  • the contour line of the cross section of each guide blade 1211 in the air turbine 121 is composed of an elliptical arc segment and a shorter straight line segment, and the straight line segment is arranged along the tangent direction of the circle around the rotating main axis at one end point of the straight line segment.
  • the turbine rotor portion is axially arranged in a cylindrical region at the center of the flow channel, and the rotor blades 1212 are evenly arranged on the rotor portion along the circumferential direction.
  • the contour line of the cross section of each rotor blade 1212 in the air turbine 121 in the axial direction is an elliptical arc segment on the suction side and a circular arc segment on the pressure side, that is, the contour line of the cross section of each rotor blade 1212 in the air turbine 121 along the axial direction is crescent-shaped.
  • a contour line of a cross section in the axial direction of a transition section between a rotor blade 1212 and a guide vane 1211 in the air turbine 121 includes a 90° arc segment and straight line segments on both sides of the arc segment.
  • the airflow is radially incident from the inlet of the U-shaped flow channel turbine, and after passing through a set of guide blades 1211 and the flow channel wall, it flows into the rotor blades 1212 at a certain angle and drives the rotor blades 1212 in the air turbine 121 to rotate. Then the airflow passes through another set of guide blades 1211 and flows out from the turbine outlet.
  • the number of rotor blades 1212 on the turbine rotor portion of the air turbine 121 is 26 to 34, and the hub ratio is 0.60 to 0.75.
  • the radius corresponding to the outer wall of the flow channel where the rotor blades 1212 of the air turbine 121 are located is R
  • the semi-major axis of the elliptical arc of the guide vane 1211 is 0.40R ⁇ 0.65R, and the semi-minor axis is 0.26R ⁇ 0.34R
  • the length of the straight section of the guide vane 1211 is 0.03R ⁇ 0.06R
  • the number of guide vanes 1211 is 14 ⁇ 24
  • the radius of the inner wall of the arc portion of the transition section is 0.45R ⁇ 0.55R
  • the length of the straight portion is 0.20R ⁇ 0.30R.
  • the impingement-type air turbine 121 has fixed guide vanes 1211 and no moving parts other than the rotor blades 1212, resulting in a simple structure and high reliability.
  • the flow passage cross-section between the rotor blades 1212 of the air turbine 121 and the downstream guide vanes 1211 continuously increases, gradually decreasing the airflow velocity. This reduces aerodynamic losses at the downstream guide vanes 1211, thereby improving turbine efficiency and achieving high efficiency.
  • the transition section of the air turbine 121 is relatively small in both radial and axial dimensions.
  • the air turbine 121 is compact in both axial and radial directions, resulting in a cost-effective design and further facilitating the secure connection between the air turbine 121 and the fluid flow passage 11 of the wave energy conversion device 10. Furthermore, the air turbine 121 is relatively lightweight, which improves the stability of the wave energy conversion device 10.
  • the mooring system 14 is used to fix the wave energy conversion device 10 in a specific position, such as a device at a mooring position such as the seabed and the coast. Normally, in order to maintain the balance of the wave energy conversion device 10, the mooring system 14 is set on the wave-facing side of the wave energy conversion device 10, and the counterweight system is fixed on the back-wave side of the wave energy conversion device 10. Of course, the mooring system 14 can also be fixed at other positions on the back-wave side of the wave energy conversion device 10, and this embodiment of the present application does not limit this.
  • the wave energy conversion device further includes one or more mooring systems 14 ; each mooring system 14 is connected to the wave-facing side of the wave energy conversion device 10 .
  • the mooring system 14 is used to fix the wave energy conversion device 10 at a designated location.
  • a wave energy conversion device 10 includes three mooring systems 14. Each mooring system 14 can be fixed to a vertical section of the fluid flow channel 11 in the wave energy conversion device 10, and each mooring system 14 is fixed at a different location. In this embodiment, one end of the mooring system 14 is fixed to the wave energy conversion device 10, and the other end can be fixed to the seabed, meaning that the wave energy conversion device 10 can be moored on the sea surface.
  • one or more mooring systems 14 can also be deployed on the wave-drifting side of the wave energy conversion device 10.
  • the mooring system 14 can be a single anchor and chain, or a new type of mooring system 14 including elastic components, to improve the reliability and survivability of the wave energy conversion device 10. Based on this, the structure and function of the mooring system 14 are further described below.
  • FIG. 7 is a top view of a mooring system 14 .
  • the mooring system 14 includes an anchor 141 , a chain 142 , a buoy 143 and two elastic components 144 .
  • the buoy 143 of the mooring system 14 is connected to the wave-facing side of the wave energy conversion device 10 via at least one elastic component 144 .
  • FIG7 takes the mooring system 14 including two elastic components 144 as an example, which is only a schematic diagram of the mooring system 14 .
  • the mooring system 14 may also include one, three, or the like elastic components 144 .
  • the chain 142 includes a catenary segment and a lying segment, and the total length of the chain 142 may be 1.5 to 8.0 times the depth of the water.
  • one end of the chain 142 is connected to the anchor 141 and fixed to the seabed, and the other end of the chain 142 is fixed to the buoy 143.
  • the buoy 143 is respectively connected to two elastic components 144, and the other ends of the two elastic components 144 are respectively fixed at different positions of the wave energy conversion device 10.
  • each elastic segment in the elastic component 144 can be a combination of a chain and a spring/other elastic system, or a high-strength elastic rope.
  • a single mooring system 14 may include one elastic component, two elastic components arranged in a V-shape, or more elastic components arranged in a dispersed manner.
  • each elastic component 144 is 2 to 3 times the length of the wave energy conversion device 10 (ie, the distance from the buoy 143 to the wave energy conversion device 10 ).
  • the mooring system 14 utilizes an anchor 141, a chain segment 142, a buoy 143, and an elastic component 144.
  • the combination of the buoy 143 and the elastic component 144 reduces the maximum force in the mooring system 14 to a certain extent, improving the reliability of the mooring system 14 and, to a certain extent, enhancing the overall reliability and survivability of the wave energy conversion device 10.
  • the wave energy conversion device 10 can also include multiple other components to further improve the wave energy conversion device 10 and adapt to actual needs, such as sensors for monitoring the status of the device, energy storage systems, monitoring systems, etc.
  • the wave energy conversion device 10 may further include a buoyancy tank, an energy storage system, a power output system, a monitoring system, a counterweight, a sensor, and the like.
  • FIG8 is a schematic diagram of the structure of a wave energy conversion device 10.
  • the buoyancy compartments include a main buoyancy compartment 15 and a secondary buoyancy compartment 16.
  • the main buoyancy compartment 15 can be positioned above the horizontal section of the L-shaped channel, partially submerged in water, while the secondary buoyancy compartment 16 can be positioned outside the vertical section of the L-shaped channel, partially or fully submerged in water.
  • the mooring system 14 in the wave energy conversion device 10 can also be secured to the secondary buoyancy compartment 16.
  • the wave energy conversion device 10 includes the main buoyancy compartment 15, the auxiliary buoyancy compartment 16 may not be provided. This embodiment of the present application does not limit this.
  • the monitoring system includes information collection equipment (such as sensors, cameras, etc.), information transmission equipment, back-end control equipment, storage equipment and display equipment.
  • the energy storage system, the back-end control and display equipment of the monitoring system, the counterweight, etc. are all arranged inside the main buoyancy compartment 15.
  • the sensors include but are not limited to the following sensors: (1) a liquid level sensor, which can be installed inside the air chamber to monitor the water level oscillation elevation in the L-shaped flow channel; (2) a vibration sensor, which can be installed on the base of the power generation component to monitor the water level vibration of the power generation component; (3) a temperature sensor, which can be installed on the surface of the generator and inside the main buoyancy chamber 15 to monitor the temperature of the power generation component and the temperature inside the main buoyancy chamber 15; (4) a flow sensor, which can be installed inside the flow channel of the air turbine 121 to monitor the gas volume flow rate; (5) a speed sensor, which can be installed on the connecting shaft between the rotor part of the air turbine 121 and the power generation component to monitor the turbine rotor speed and the power generation component speed; (6) a torque sensor, which can be installed on the connecting shaft between the rotor part of the air turbine 121 and the power generation component to monitor the main torque provided by the turbine rotor to the power generation component.
  • a liquid level sensor which can be installed
  • the data obtained by the above sensors and the monitoring data obtained by the monitoring system can be uploaded to the cloud for remote viewing by staff.
  • the working principle of the wave energy conversion device 10 can be summarized as follows: under the action of waves, currents, wind, etc., the wave energy conversion device 10 undergoes six degrees of freedom motion, namely, longitudinal sway, transverse sway, heave sway, roll, pitch, and bow sway, causing the water body in the fluid flow channel 11 of the wave energy conversion device 10 to couple with the device to oscillate, causing the water column in the liquid flow channel of the fluid flow channel 11 to oscillate up and down, and the air pressure in the air chamber to alternate between positive and negative; the top or side wall of the air chamber is connected to the atmosphere through the air flow channel in the fluid flow channel 11.
  • the air flow passage 11 is connected, and a reciprocating air flow is formed in the air flow passage under the action of the pressure difference, driving the impact-type air turbine 121 installed in the air flow passage to rotate in one direction, thereby driving the power generation component coaxially connected to the air turbine 121 to generate electricity, realizing the conversion of wave energy into aerokinetic energy, aerokinetic energy into rotational mechanical energy, and rotational mechanical energy to electrical energy; at the same time, when the pressure of the air chamber in the fluid flow passage 11 is higher than the pressure threshold, the threshold-adjustable pressure relief system 13 installed above the air chamber opens, which plays a role in relieving pressure and reducing load, and protecting the air turbine 121 and the power generation component.
  • the wave energy conversion device 10 in the embodiment of the present application can also be expanded into a multi-chamber pneumatic type, that is, a plurality of the above-mentioned hull parts are connected in parallel to form a wave energy primary energy conversion system, a secondary energy conversion system and a tertiary energy conversion system.
  • the layout scheme can adopt a multi-turbine multi-generator mode, a multi-turbine single generator mode or a single turbine single generator mode.
  • the multi-chamber pneumatic wave energy conversion device 10 has been greatly expanded in the width direction. A single set of devices can capture wave energy in a larger range, greatly increasing the power output of a single set of devices.
  • the multi-chamber pneumatic wave energy conversion device 10 has N+6 degrees of freedom of movement, where N represents the oscillation freedom of the water column of the N air chambers, and 6 represents the longitudinal, transverse, vertical, roll, pitch, and bow swing of the device itself, a total of 6 degrees of freedom.
  • each degree of freedom of the device Since each degree of freedom of the device generates oscillation waves in the flow channel with different frequencies, these oscillation waves of different frequencies are superimposed on the oscillation of the water column itself in the flow channel, so that when wave energy is converted into aerokinetic energy, the aerokinetic energy shows a multi-peak characteristic with the periodic change curve, and the device responds to the increase in the width of the wave period, the efficiency of converting wave energy into aerokinetic energy increases, thereby producing an efficiency-enhancing broadband effect.
  • the unit kilowatt cost of the multi-chamber pneumatic wave energy conversion device 10 is greatly reduced, which is specifically reflected in the reduction of the device transportation cost (i.e., transportation from the shipyard to the working sea area), mooring system cost, power output system cost, turbine cost and generator cost (when using a multi-turbine single generator mode or a single turbine single generator mode).
  • the device transportation cost i.e., transportation from the shipyard to the working sea area
  • mooring system cost i.e., transportation from the shipyard to the working sea area
  • power output system cost i.e., power output system cost
  • turbine cost and generator cost when using a multi-turbine single generator mode or a single turbine single generator mode.
  • the embodiment of the present application also provides a wave energy conversion device evaluation method, which provides a reliability analysis basis for the system design and optimization of the wave energy conversion device.
  • a wave energy conversion device evaluation method including the following steps S901 and S902 .
  • the wave energy conversion device is divided into the hull system (fluid flow channel and buoyancy chamber), air turbine system, power generation component system (generator), pressure relief system and mooring system; then, according to the motion characteristics of each system, the control equations of each system are constructed respectively. Finally, the above-constructed equations are coupled to the entire system to obtain the mathematical model of the wave energy conversion device.
  • the mathematical model specifically includes the fluid motion equation, the hull motion equation, the turbine rotor motion equation, the pressure relief system control equation, the generator model control equation, the mooring system control equation, and the determination of the mathematical model boundary conditions and the mathematical model initial conditions.
  • the fluid motion equations are the continuity equation considering the compressibility of the fluid, the Reynolds-averaged Navier-Stokes equations, the turbulence model equations and the gas state equations; the hull motion equations, the turbine rotor motion equations and the pressure relief system control equations are Newton's second law equations.
  • a Cartesian coordinate system Ox 1 x 2 x 3 is defined, where the origin O coincides with the still water surface, the x 1 axis is oriented in the direction of wave propagation, the x 2 axis is oriented in the direction of the wave crest line, and the x 3 axis is oriented vertically upward. Furthermore, a local coordinate system O′-x 1 ′x 2 ′x 3 ′ is established at the center of mass of the pneumatic wave energy converter, moving with the device.
  • the fluid part includes water and gas. Its governing equations are the continuity equation and the Reynolds-averaged Navier-Stokes equations.
  • the turbulence model equations are introduced and expressed as:
  • ⁇ is the fluid density
  • t time
  • u i is the fluid velocity along the x i direction
  • fi is the volume force acting on the fluid cluster in the x i direction
  • p is the fluid relative pressure
  • ⁇ and ⁇ t are the fluid dynamic viscosity and turbulent viscosity, respectively
  • ⁇ ij is the Kronecker function
  • K is the turbulent kinetic energy.
  • ⁇ t can be solved using the SST K- ⁇ model or the KE model, expressed as:
  • Equation (4) ⁇ represents K and ⁇ , or K and E, depending on the selected turbulence model; ⁇ is the model coefficient; G ⁇ is the generator of ⁇ ; and Y ⁇ is the dissipator of ⁇ . ⁇ , G ⁇ , and Y ⁇ have different expressions in different models.
  • the water phase is considered incompressible, and the compressibility of the gas phase can be ignored in small-scale models or rough calculations.
  • the above formulas (1) to (4) are closed.
  • the compressibility of the gas phase must be considered in large-scale or full-scale models.
  • Ta is the absolute temperature of the gas phase
  • ⁇ a is the density of the air phase.
  • formula (5) is a general form of the gas phase state equation, and an ideal gas state, a real gas state equation, a thermodynamic equation, etc. can be selected according to specific circumstances.
  • the real gas state equation includes but is not limited to the van der Waals equation, the R-K equation, the S-R-K equation, the Virial equation, etc.
  • M is the generalized mass matrix in the form of a 6-order diagonal matrix, corresponding to the 6 degrees of freedom of the hull; and F are the generalized acceleration vector and generalized force vector, respectively.
  • F m (- cm ,0, -cm sinh( um2 ))
  • F m (-k s ⁇ x cos ⁇ s ,0,-(am s g+k s ⁇ x sin ⁇ s ))
  • m h is the mass of the hull section; g is the gravitational acceleration vector; S d is the wall surface of the hull section; n is the unit normal vector of the hull wall area unit; I is the third-order unit tensor; ⁇ represents the shear stress tensor acting on the hull wall area unit; represents the acceleration vector of the rotor.
  • cm and um2 are the catenary model parameters of the mooring system; ks , ms , and ⁇ s are the stiffness coefficient, mass, and angle between the axis and the horizontal direction of the taut mooring system component, respectively; ⁇ x is the deformation of the mooring system component after tensioning; a is the proportional coefficient, which is related to the mass distribution of the mooring system itself; and g is the acceleration of gravity.
  • the expression of the mooring force Fm is not only applicable to the mooring system in the embodiment of the present application, but also applicable to the traditional anchor chain mooring method and the mooring system using anchor chain, buoy and chain.
  • the above expression of the mooring force Fm only considers that a single mooring system component is directly connected to the wave energy conversion device, and the layout direction of the mooring system component coincides with the x1 direction.
  • the mooring forces generated by each mooring system component need to be calculated separately according to the expression of Fm and superimposed. If other layout directions of the mooring system components are considered, the mooring forces obtained from the expression of Fm need to be decomposed in the Cartesian coordinate system Ox1x2x3 .
  • T h r p ⁇ F p +r ⁇ ⁇ F ⁇ +r r ⁇ F r +r m ⁇ F m formula (13)
  • r p , r ⁇ , r r and r m are the distance vectors from the fluid pressure, fluid shear force, rotor reaction force and mooring force to the center of mass of the hull part, respectively.
  • the turbine is fixed to the hull and moves with it in six degrees of freedom, its equation of motion being Newton's second law. Simultaneously, the turbine rotor rotates unidirectionally relative to the hull about the rotor's axis of rotation. Its motion is described in the local coordinate system O′-x 1 ′x 2 ′x 3 ′ as:
  • n′ d is the driving torque along the x 3 ′ direction caused by the pressure difference between the suction side and the pressure side of the rotor blade
  • n′ g is the damping torque along the x 3 ′ direction applied by the generator to the turbine rotor
  • n f ′ is the bearing friction torque and other resistance torque along the x 3 ′ direction applied to the turbine rotor when it rotates.
  • the pressure relief system is an automatic pressure relief system with an adjustable threshold. It is installed above the air chamber of the hull.
  • the motion equation of its valve disc is Newton's second law.
  • the valve disc of the automatic pressure relief system with an adjustable threshold moves with a single degree of freedom along the x 3 ′ direction relative to the hull, which can be expressed as:
  • m v is the mass of the valve disc of the automatic pressure relief system with adjustable threshold; is the acceleration of the valve disc along the x 3 ′ direction; F p ′ is the lifting force exerted on the valve disc by the gas in the air chamber (along the x 3 ′ direction); G v ′ is the component of the valve disc's own gravity along the x 3 ′ direction; k v is the elastic coefficient of the spring or other elastic system between the valve disc and the valve seat; and are the initial length of the spring or other elastic system and the actual length at the current moment, and they must satisfy F f ′ is the damping force along the x 3 ′ direction received by the valve disc during movement. It should be noted that F f ′>0 during the opening process of the valve disc and F f ′ ⁇ 0 during the closing process of the valve disc. F N ′ is the supporting force along the x 3 ′ direction received by the valve disc.
  • H is the wave height; They are There are m selectable adjustment values.
  • m in formula (16) is not restricted here, and even It can be expressed as a continuous function of H.
  • k v in formula (15) can also be adjusted.
  • the corresponding automatic pressure relief system can be an automatic pressure relief system with a fixed threshold.
  • the power generation component can be a direct-drive generator, with the generator rotor coaxially connected to the turbine rotor and having the same rotational angular velocity.
  • the main torque of the generator is provided by the turbine rotor, while the generator's resistance torque includes air resistance, mechanical friction, and electromagnetic resistance during the operation of the generator rotor.
  • the generator applies a damping torque n'g to the turbine rotor.
  • the governing equation of the mooring system is the catenary equation or Hooke's law, which corresponds to the chain segment and elastic segment of the mooring system being in a relaxed and taut state respectively.
  • x1m is the x1 coordinate of the catenary element
  • x3m is the x3 coordinate of the catenary element
  • ⁇ m and ⁇ m are integration constants that depend on the positions of the two end points of the catenary and the mass of the catenary
  • um is the catenary curve parameter
  • am and bm are model parameters.
  • ⁇ 0m and Leq are the mass per unit length and the relaxation length of the catenary under the condition of no force, respectively; Km is the stiffness of the catenary; um1 and um2 are the um values of the connection points between the catenary and the seabed and the connection point with the pneumatic wave energy conversion device, respectively; ⁇ m is the inclination angle of the catenary curve.
  • the buoy's motion equation also needs to be considered.
  • the governing equation for the buoy's motion is Newton's second law, and the forces acting on the buoy include its own gravity, fluid pressure, fluid shear force, and mooring forces on both sides.
  • the mathematical model boundaries include the inlet boundary, outlet boundary, bottom boundary, top boundary, side wall boundary, fluid-solid interface (between the fluid and the hull, turbine and float) and gas-liquid interface (between the water phase and the gas phase) of the overall calculation domain.
  • the boundary condition of the inlet boundary is set as velocity inlet.
  • the velocity of the water phase at the inlet boundary takes into account the wave velocity and water flow velocity
  • the velocity of the gas phase at the inlet boundary takes into account the wind speed, which can be expressed as:
  • u w1 and u w3 are the wave velocities along the x 1 direction and x 3 direction obtained according to wave theory; u c is the water flow velocity; u wind is the wind speed; and ⁇ is the x 3 coordinate of the interface between the water phase and the air phase.
  • the spatiotemporal distribution of the wave velocity at the inlet can be calculated based on micro-wave theory, high-order Stokes wave theory, irregular wave theory, or other wave theories.
  • the boundary condition of the outlet boundary is set to pressure outlet, and the specific pressure distribution is not restricted.
  • the pressure distribution of the water phase at the outlet boundary satisfies the static pressure distribution of the water phase, and the pressure of the gas phase at the outlet boundary is 0, which is expressed as:
  • ⁇ w is the density of the water phase.
  • the boundary condition of the bottom boundary is set to a no-slip wall.
  • the no-slip wall means that the force and velocity values of the fluid unit and the structural unit on the boundary are equal, which is expressed as:
  • the boundary condition at the top boundary is set to a pressure outlet.
  • the overall computational domain is high enough that the water phase cannot splash onto the top boundary, so only the gas phase traverses the top boundary.
  • the pressure distribution at the top boundary is zero, indicating free outflow.
  • the boundary condition of the fluid-solid interface is set as a no-slip wall, which is expressed as formula (28).
  • the water phase and gas phase at the gas-liquid interface are immiscible.
  • the water phase and gas phase share the same velocity field and pressure field.
  • the equivalent fluid density and dynamic viscosity are expressed as:
  • ⁇ is the volume fraction of water, and its value range is 0 ⁇ 1; ⁇ w and ⁇ a are the dynamic viscosities of the water phase and the gas phase, respectively.
  • the six-degree-of-freedom displacements and velocities of the hull, turbine rotor, and buoy of the PWEC are all zero, and waves, currents, and wind propagate to a location just before the PWEC's wavefront.
  • the initial conditions can be set to that the wind, waves and currents just propagate to the front of the wave-facing side of the pneumatic wave energy conversion device.
  • S902 Solve the mathematical model to obtain an evaluation index value of the wave energy conversion device.
  • the mathematical model is solved according to a preset solution algorithm to obtain the calculation results of the mathematical model.
  • the calculation results are then used as the actual operating results of the wave energy conversion device under the initial conditions, and the power generation capacity index value and reliability index value of the wave energy conversion device are evaluated based on this, which are used as the evaluation index value of the wave energy conversion device.
  • the evaluation index value includes not only the power generation capacity index value and the reliability index value of the wave energy conversion device, but also other evaluation parameters to characterize the performance of the wave energy conversion device in multiple dimensions. This embodiment of the present application does not limit this.
  • a mathematical model is constructed for a wave energy conversion device.
  • the mathematical model is an equation that simulates the kinetic characteristics of the wave energy conversion device.
  • This mathematical model is then solved to obtain evaluation indicators for the wave energy conversion device.
  • This method simulates the kinetic characteristics of the wave energy conversion device and comprehensively considers the various energy conversion stages of the device and the interactions between them. This method improves the accuracy of the wave energy conversion device's power generation capacity and reliability, providing optimization strategies for the device in multiple dimensions, such as conversion efficiency and reliability.
  • the simulation equations in mathematical models are typically continuous in both time and space.
  • the entire computational domain of the mathematical model can be divided into a finite number of grid cells.
  • the governing equations in the mathematical model are transformed into discrete equations representing the relationships between the function values at the nodes of the continuous grid cells.
  • the conservation equations for mass, momentum, and energy are then solved for each grid cell.
  • solving a mathematical model to obtain an evaluation index value of a wave energy conversion device includes steps S1001 , S1002 and S1003 .
  • the steps of obtaining a numerical model can be broken down into three steps: establishing a high-quality mesh, determining a numerical solution method, and establishing reasonable and feasible interface conditions.
  • the purpose of establishing a high-quality mesh is to discretize the mathematical model in space; the purpose of determining the numerical solution method is to discretize the discretized mathematical model in time; and considering that the mesh sizes of the two sub-regions connected by the interface near the interface remain basically consistent during the mesh establishment process, it is also necessary to establish reasonable and feasible interface conditions.
  • establishing a high-quality grid includes six parts: determining the numerical solution area, determining the grid type, determining the grid refinement criterion, determining the grid transition criterion, controlling the grid quality and determining the number of grids.
  • step a determine the numerical solution area.
  • the numerical solution region is determined to be a numerical wave tank of size 12 ⁇ 8b ⁇ 2hw , where ⁇ is the wavelength, b is the width of the wave energy conversion device, and hw is the water depth.
  • the distance from the wave-facing wall of the wave energy conversion device to the inlet boundary of the numerical wave tank is 5 ⁇ .
  • the size of the numerical solution area and the position of the device in the numerical solution area can be adjusted appropriately according to actual conditions.
  • Step b Determine the grid type.
  • the grid structure is determined to be a hexahedral grid, but one or more corners of the hexahedral grid are cut at the boundary position to form a polyhedral grid.
  • the grid structure can also adopt tetrahedral grids or a combination of hexahedral grids and tetrahedral grids.
  • the cost of numerical solution is higher and the solution accuracy is relatively lower, it is difficult to effectively adapt to the solution of the complex full-system coupling model of the pneumatic wave energy conversion device.
  • Step c Determine the mesh refinement criteria.
  • mesh encryption is performed including but not limited to the model boundary (including the inlet boundary, outlet boundary, bottom boundary, top boundary, side wall boundary, fluid-solid interface and gas-liquid interface of the numerical wave tank), the L-shaped flow channel area of the hull part, the turbine flow channel area, the area involved in the movement of the hull part, the area involved in the movement of the float of the mooring system, and the area involved in the movement of the valve flap of the automatic pressure relief system with adjustable threshold.
  • model boundary including the inlet boundary, outlet boundary, bottom boundary, top boundary, side wall boundary, fluid-solid interface and gas-liquid interface of the numerical wave tank
  • the height of the gas-liquid interface encryption area is 1.5H ⁇ 2.0H, where H is the wave height, and the mesh size of this area meets
  • the mesh in the turbine flow passage area needs to be refined, especially in the area where the rotor blades and guide vanes are located. At least six mesh layers should be distributed between the rotor blades. In particular, there is a very thin gap between the rotor blade tip and the inner wall of the turbine flow passage. The leakage effect of this gap has a significant impact on turbine performance. Therefore, to ensure a relatively accurate depiction of the flow characteristics of the blade tip clearance, at least two to three mesh layers should be distributed through the thickness of this area.
  • Step d Determine the grid transition criterion.
  • the numerical solution area is distributed with grids of different sizes, and the transition layers between grids of adjacent sizes are at least 2 to 3 layers.
  • Step e Control mesh quality.
  • the mesh quality should be strictly controlled to ensure that the mesh quality of all meshes in the numerical solution area is higher than the preset minimum mesh quality.
  • the preset minimum mesh quality may be selected as 0.05.
  • Step f Determine the number of grids.
  • a set of high-quality meshes is established according to steps a to e. Furthermore, the final number of meshes is determined by mesh convergence analysis.
  • the grid convergence criterion is selected to be 0.5% to 1.0%. That is, as the number of grids continues to increase, the changes in physical quantities such as the hull movement, air chamber pressure, impulse air turbine rotor speed, and anchor chain force obtained by the wave-to-electric system coupling simulation method of the device do not exceed 0.5% to 1.0%. At this time, it is considered that the grid convergence requirement is met.
  • the final number of meshes determined can vary significantly depending on the hydrodynamic conditions, mesh refinement criteria, mesh transition criteria, and mesh convergence criteria. Research has shown that when the requirements of steps a through f are strictly met, the number of meshes established is no less than 4.5 million.
  • determining the numerical solution method includes determining the numerical method and determining the solution algorithm.
  • the corresponding discretization method is determined to be the finite volume method.
  • the finite volume method refers to integrating the fluid control equation in space and time within each grid control volume and a certain time interval to obtain a set of discrete equations.
  • the discrete forms of formula (1) and formula (2) are expressed as:
  • V is the control volume
  • A is the surface of the control volume
  • ni is the component of the unit normal vector n of the control volume surface in the xi direction
  • Su and su are source terms.
  • the SIMPLE algorithm When numerically solving the discrete equations of fluid motion, the SIMPLE algorithm is used to couple pressure and velocity.
  • a second-order implicit scheme is used to handle the time term
  • a Gaussian least squares method is used to handle the gradient term
  • a second-order upwind scheme is used to handle the convection term
  • the HRIC algorithm is used to capture the free surface
  • a full y + wall treatment is used to predict the flow and turbulence of the wall boundary layer.
  • This full y + wall treatment is a hybrid method that uses a low y + wall treatment for fine meshes and a high y + wall treatment for coarse meshes.
  • control equations for the hull, the rotor of the impulse air turbine, the valve disc of the automatic pressure relief system with adjustable threshold, and the float of the mooring system are discretely solved using the time-domain step-by-step integration method.
  • the trapezoidal format with good stability and second-order accuracy is expressed as:
  • M -1 is the inverse matrix of the generalized mass matrix M;
  • v(t- ⁇ t), x(t- ⁇ t) and x(t- ⁇ t) are the generalized velocity, generalized acceleration, and generalized displacement vectors of the hull, the rotor of the impulse air turbine, the valve disc of the automatic pressure relief system with adjustable threshold, or the float of the mooring system at the time (t- ⁇ t), respectively;
  • ⁇ t is the time step.
  • the time step size is primarily related to the grid size and the turbine rotor speed. Generally, the higher the turbine rotor speed, the smaller the selected time step. Furthermore, the final time step size is determined through time step convergence analysis.
  • Establishing reasonable and feasible interface conditions includes dividing the calculation area and setting the interface between the areas.
  • the overall numerical solution area is divided into five sub-areas, namely, the background area representing the entire numerical wave tank, the overlapping area 1 including the hull part of the pneumatic wave energy conversion device and the impulse air turbine but excluding the turbine rotor area, the overlapping area 2 including the automatic pressure relief system with adjustable threshold, the overlapping area 3 including the float, and the rotor area where the turbine rotor is located.
  • the background area is a static area
  • the overlapping area 1, overlapping area 2, overlapping area 3 and the rotor area are all moving areas.
  • the device is not equipped with an automatic pressure relief system or the valve flap of the automatic pressure relief system with adjustable threshold is always in a closed state, there is no need to set the overlapping area 2; if the device is equipped with multiple automatic pressure relief systems, there will be multiple independent overlapping areas 2 (which can be recorded as overlapping area 2-1, overlapping area 2-2, ).
  • the mooring system of the device adopts a traditional anchor chain mooring method, that is, one end of the chain is connected to the anchor and fixed to the seabed, and the other end is fixed to the hull part of the device, then there is no need to set the overlapping area 3; if the mooring system of the device includes multiple buoys, then there are multiple independent overlapping areas 3 (which can be recorded as overlapping area 3-1, overlapping area 3-2, ).
  • the interface between the above-mentioned background area and the overlapping area 1 adopts an overlapping grid interface; the interface between the above-mentioned background area and the overlapping area 3 adopts an overlapping grid interface; the interface between the above-mentioned overlapping area 1 and the overlapping area 2 adopts an overlapping grid interface; the interface between the above-mentioned overlapping area 1 and the rotor area adopts an internal in-situ interface; there is no direct data interaction between the other sub-areas, and there is no need to set interface conditions.
  • the above-mentioned overlapping grid interface and the internal in-situ interface realize data interaction between two physically connected sub-areas.
  • the grid sizes of the two sub-areas connected by the above-mentioned interface near the interface remain basically consistent.
  • the step of solving the time history curve of the wave energy conversion device based on the numerical model includes steps S1101 , S1102 and S1103 .
  • the 0.001 second, 0.002 second, 0.003 second, ..., 180,000 moments in the preset time period are determined, for a total of 3 minutes.
  • the numerical model is iteratively solved according to a preset iterative strategy until the numerical model meets the preset convergence condition, and the motion response value at each moment is obtained.
  • FIG12 is an iterative solution process of a wave-to-electricity full system coupling simulation method for a wave energy conversion device provided by an embodiment of the present application, including the following steps S1201 to S1209 .
  • the fluid pressure and shear stress on the surfaces of components such as the hull, impulse air turbine, automatic pressure relief system with adjustable threshold, and float of the mooring system of the pneumatic wave energy conversion device are integrated to obtain the forces and moments acting on each part of the device.
  • S1204 Determine whether the velocity field, pressure field, and density field of the fluid region have all met convergence conditions.
  • the fluid motion equation is solved iteratively, and the process returns to S1002 until the convergence condition is met.
  • the positions of the overlapping area 1, overlapping area 2, overlapping area 3 and the rotor area are updated according to the solution results.
  • the motion response and dynamic characteristics of the pneumatic wave energy conversion device at the current moment are obtained.
  • the motion response and dynamic characteristics include, but are not limited to, the force, acceleration, velocity, and displacement of the hull portion and the buoy of the mooring system in the six degrees of freedom of motion directions in the Cartesian coordinates Ox 1 x 2 x 3 ; the force of the mooring system; the opening and closing state of the valve flap of the automatic pressure relief system with adjustable threshold; the force and rotation of the impulse air turbine rotor in the local coordinate system O′-x 1 ′x 2 ′x 3 ′ (which is also the rotation of the direct-drive generator rotor); the free liquid surface distribution, in particular, the spatial distribution of the water column elevation in the L-shaped flow channel in the local coordinate system O′-x 1 ′x 2 ′x 3 ′; and the pressure, velocity, and density distribution of the water phase and gas phase in the fluid domain, in particular, the pressure distribution of the air chamber in the L-shaped flow channel and the flow velocity distribution in the impulse air
  • the hydrodynamic input power P in,t S ⁇ b Formula (35)
  • P pt ⁇ p t Q t Formula (36)
  • P rt n′ dt ⁇ ′ Rt Formula (37)
  • P out,t n′ gt ⁇ ′ Rt Formula (38)
  • S ⁇ is the single-width energy flux density under the superposition of incident waves and water flow
  • ⁇ pt is the air chamber pressure at the current moment
  • Qt is the air chamber volume flow rate at the current moment
  • n′ dt and n′ gt are the driving torque on the turbine rotor and the damping torque applied to the turbine rotor by the generator in the local coordinate system O′-x 1 ′x 2 ′x 3 ′ at the current moment
  • ⁇ ′ Rt is the speed of the turbine rotor (and the generator rotor) in the local coordinate system O′-x 1 ′x 2 ′x 3 ′ at the current moment.
  • the incident wave may be a regular wave (including a micro-amplitude wave, a high-order Stokes wave), an irregular wave, etc., and the corresponding expressions of S ⁇ are also different.
  • S1103 Construct a time history curve according to each moment and the motion response value corresponding to each moment.
  • evaluation index values such as power generation capacity index value and reliability index value are calculated.
  • the power generation capacity index value The expression is:
  • t0 is the time when the numerical simulation reaches the dynamic equilibrium stage, and its value varies in different examples
  • n is the number of wave periods corresponding to the data length selected during data averaging, and is usually an integer between 4 and 8.
  • the average hydrodynamic performance It can also be characterized as the capture width ratio of the wave energy conversion device, and The calculated result can exceed 100%.
  • the reliability index is a parameter used to evaluate the wave energy conversion device's ability to continue operating normally in a specific marine environment. If one or more of these parameters, such as the turbine rotor speed, the mooring forces in the mooring system's chain segments and/or elastic segments, or the pressure differential force on the walls of the hull's liquid flow passages (i.e., the difference in pressure between the inside and outside of the wall), exceed their rated upper limits for an extended period during the simulation period, the reliability index of the wave energy conversion device will be severely affected.
  • a larger power generation capacity index value indicates a higher energy conversion efficiency of the wave energy conversion device; a larger reliability index value indicates a more reliable wave energy conversion device.
  • the power generation capacity index and reliability index values of a wave energy conversion device are calculated simultaneously. If the reliability index value meets actual requirements, the power generation capacity index value is maximized.
  • the reliability index value may be one of two discrete values, for example, 0 or 1. In this case, a reliability index value of 0 indicates that the wave energy conversion device is unreliable, and a reliability index value of 1 indicates that the wave energy conversion device is reliable.
  • the reliability index value can be determined based on whether the physical parameters (including but not limited to the rotational speed, mooring force and pressure differential force) exceed the rated upper limit of the corresponding parameters: if one of the physical parameters exceeds the rated upper limit of the corresponding parameter, it means that the wave energy conversion device is in an unsafe operating state, and the reliability index value is determined to be 0; if all physical parameters do not exceed the rated upper limit of the corresponding parameters, it means that the wave energy conversion device is in a safe and reliable operating state, and the reliability index value is determined to be 1.
  • the reliability index value is determined to be 0; if the rotational speed of the power generation component does not exceed 700 rpm during the simulation process, the reliability index value is determined to be 1.
  • the reliability index value may be any value in the interval [0, 1], such as 0.1, 0.5, 0.9, etc. In this case, the closer the reliability index value is to 0, the less reliable the wave energy conversion device is, and the closer the reliability index value is to 1, the more reliable the wave energy conversion device is.
  • the reliability index value can be determined based on the duration that the physical parameters (including but not limited to rotational speed, mooring force, and pressure differential force) exceed the rated upper limit of the corresponding parameters, and the duration is negatively correlated with the reliability index value, that is, the longer the duration that the physical parameters exceed the rated upper limit of the corresponding parameters, the lower the reliability index value; the shorter the duration, the higher the reliability index value.
  • the purpose of this setting is that in actual operation scenarios, some hardware in the wave energy conversion device has a certain degree of pressure resistance.
  • the power generation component can allow short-term overload operation.
  • f(t beyond ) represents a function that is positively correlated with the duration t beyond , and its value range is [0, 1].
  • the simplest example is that f(t beyond ) and t beyond are linearly related within a certain range, that is,
  • T 0 represents the maximum duration that the rotation speed of the power generation component is allowed to exceed its rated upper limit.
  • the steps of the evaluation method shown in Figures 8 to 10 can be repeated to obtain evaluation indicators of the power generation capacity, reliability, etc. of the pneumatic wave energy conversion device under different conditions as the above-mentioned hydrodynamic incident conditions, generator characteristics, the threshold of the automatic pressure relief system with an adjustable threshold, and the mooring system parameters change, thereby deeply revealing the energy conversion mechanism of the pneumatic wave energy conversion device.
  • a numerical model that is easy to calculate is obtained. Then, a time curve is constructed based on the numerical model to visualize the dynamic characteristics of the wave energy conversion device, so that the evaluation index value determined based on the time curve is more in line with the actual operating status of the wave energy conversion device.
  • a method for simulating a wave energy conversion device including the following steps S1301 to S1305.
  • the above S1301 to S1305 are repeatedly executed to obtain evaluation indicators of the wave energy conversion device under different conditions.
  • the energy conversion mechanism of the wave energy conversion device is revealed, providing an optimization direction for improving the power generation capacity and reliability of the wave energy conversion device.
  • a comprehensive and complete simulation method for the full system coupling of wave-to-electricity of a wave energy conversion device is provided to fill the gap in the lack of reliable design optimization theory for pneumatic wave energy conversion devices.
  • a method for evaluating a wave energy conversion device comprising the following steps:
  • the mathematical model is a simulation equation that simulates the motion characteristics of the wave energy conversion device.
  • the discretization process includes spatial discretization and temporal discretization.
  • the numerical model is iteratively solved according to the preset iterative strategy until the numerical model meets the preset convergence conditions and the motion response value at each moment is obtained.
  • the time history curve is used to characterize the corresponding relationship between the motion response and dynamic characteristics of the wave energy conversion device and time.
  • the evaluation index values include the power generation capacity index value and the reliability index value of the wave energy conversion device.
  • a mathematical model is constructed for a wave energy conversion device.
  • the mathematical model is an equation that simulates the kinetic characteristics of the wave energy conversion device.
  • This mathematical model is then solved to obtain evaluation indicators for the wave energy conversion device.
  • This method simulates the kinetic characteristics of the wave energy conversion device and comprehensively considers the various energy conversion stages of the device and the interactions between them. This method improves the accuracy of the wave energy conversion device's power generation capacity and reliability, providing optimization strategies for the device in multiple dimensions, such as conversion efficiency and reliability.
  • the optimization method provided in the embodiment of the present application is universal and applicable not only to the performance prediction of the wave energy conversion device proposed in the embodiment of the present application, but also to the performance prediction of all other types of pneumatic wave energy conversion devices.
  • wave energy power generation devices with hull sections of the rear-bend pipe type, front-bend pipe type, and center-tube type; wave energy power generation devices with air turbines of the radial impulse type, axial-flow impulse type, Wells turbine type, and other types; wave energy power generation devices with mooring methods using a single anchor chain mooring method, anchor chain + buoy + chain; wave energy power generation devices with a fixed threshold pressure relief system; and wave energy power generation devices with generators having a wide range of torque-speed relationships.
  • the pneumatic wave energy conversion device in this simulation method uses an impulse air turbine with fixed guide vanes.
  • impulse air turbines with guide vanes that can actively/passively rotate or slide have been proven to have very low reliability in actual marine environments and will be destroyed after a very short period of operation. Therefore, they are not considered here.
  • the maximum steady-state efficiency of the air turbine (radial-inflow impulse air turbine) proposed in the embodiment of the present application is 68%, and the maximum cycle-average efficiency is 63%, which are 35.8% and 31.5% higher than the maximum steady-state efficiency and maximum cycle-average efficiency of the axial-flow impulse air turbine with fixed guide vanes, respectively.
  • Figure 14 is a comparison of turbine steady-state efficiency curves obtained using the simulation method of an embodiment of the present application.
  • S1 is the steady-state efficiency curve of the radial impulse air turbine provided by the embodiment of the present application
  • S2 is the steady-state efficiency curve of the axial impulse air turbine.
  • the steady-state efficiency of the radial impulse air turbine provided by the present application is greater than that of the axial impulse air turbine.
  • the average overall performance of the pneumatic wave energy conversion device using the new impulse air turbine proposed in the embodiment of the present application is as high as 62%, which is 20.6% higher than the highest average overall performance of the pneumatic wave energy conversion device using the axial flow impulse air turbine with fixed guide blades, proving the applicability and high efficiency of the new impulse air turbine proposed in the embodiment of the present application.
  • Figure 15 shows the average power generation performance of the wave energy conversion device under regular wave conditions.
  • the average overall performance of the pneumatic wave energy conversion device using the new impulse air turbine proposed in the present invention is up to 35%, which is 19.8% higher than the highest average overall performance of the pneumatic wave energy conversion device using the axial flow impulse air turbine with fixed guide blades, once again proving the applicability and high efficiency of the new impulse air turbine proposed in the embodiments of the present application.
  • the average overall performance of the wave energy conversion device using the new mooring system proposed in the embodiment of the present application is improved, with the maximum improvement of 12.5% and 3.2% respectively;
  • the high-efficiency energy capture range of the pneumatic wave energy conversion device using the new mooring system proposed in the embodiment of the present application is widened by 46.8% and 10.5% respectively compared with the high-efficiency energy capture range of the pneumatic wave energy conversion device using a single anchor chain mooring method and a mooring method using an anchor chain + buoy + chain, which proves the effectiveness of the new mooring system proposed in the embodiment of the present application in enhancing broadband efficiency and improving the overall power generation capacity of the device.
  • the maximum mooring force of the pneumatic wave energy conversion device using the new mooring system proposed in the embodiment of the present application is reduced compared with the maximum mooring force of the pneumatic wave energy conversion device using a single anchor chain mooring method and a mooring method using an anchor chain + buoy + chain, with the maximum reduction being 212% and 156% respectively, which proves the effectiveness of the new mooring system proposed in the embodiment of the present application in improving the reliability of the device.
  • the incident wave energy increased by more than 20 times, while the maximum pressure difference force on the wall of the L-shaped flow channel of the hull increased by only 3.05 times; in extreme sea conditions, compared with normal sea conditions, the incident wave energy increased by more than 300 times, while the maximum pressure difference force on the wall of the L-shaped flow channel of the hull increased by only 2.1 times, which proves the reliability of the pneumatic wave energy conversion device itself and the effectiveness of the threshold-adjustable automatic pressure relief system proposed by the present invention in improving the reliability of the device.
  • the research results show that the natural frequencies of the six degrees of freedom of the wave energy conversion device provided in the embodiment of the present application are different, so that each degree of freedom movement generates a water column oscillation wave in the flow channel. These water column oscillation waves produce a superposition effect, thereby widening the frequency response width of the device and increasing the capture width ratio.
  • the longitudinal oscillation motion of the device moored by the anchor chain buoy mooring system contributes the most to the capture width ratio of the device. Under different sea conditions, the contribution of the longitudinal oscillation motion to the capture width ratio accounts for 50% to 95% of the total capture width ratio.
  • the pneumatic wave energy conversion device provided in the embodiments of the present application includes a hull portion, an impact air turbine, an automatic pressure relief and load reduction system, a generator, a mooring system, and other systems/equipment/components.
  • the radial inflow impact air turbine of the pneumatic wave energy conversion device has the advantages of high reliability, high efficiency, and relatively compactness in both the axial and radial directions.
  • the automatic pressure relief system with adjustable thresholds can be remotely manually or automatically controlled according to actual sea conditions, improving the reliability of the device in high sea conditions.
  • the high-efficiency broadband mooring system of the anchor chain, buoy, and elastic energy absorption component has the advantages of broadband efficiency and reduced maximum force in the mooring system.
  • the present application also provides an evaluation device for implementing the aforementioned evaluation method.
  • the solution provided by this device is similar to the solution described in the aforementioned method. Therefore, the specific limitations of one or more evaluation device embodiments provided below can be found in the above-mentioned limitations of the evaluation method and will not be repeated here.
  • a wave energy conversion device evaluation device including: a construction module 1601 and a calculation module 1602 .
  • the construction module 1601 is used to construct a mathematical model for the wave energy conversion device.
  • the mathematical model is a simulation equation for simulating the motion characteristics of the wave energy conversion device.
  • the calculation module 1602 is used to solve the mathematical model and obtain the evaluation index value of the wave energy conversion device.
  • the operation module 1602 includes a discrete processing unit, a curve construction unit, and an indicator acquisition unit.
  • the discrete processing unit is used to discretize the mathematical model to obtain a numerical model; the discretization processing includes spatial discretization processing and temporal discretization processing.
  • the curve construction unit is used to solve the time history curve of the wave energy conversion device based on the numerical model.
  • the time history curve includes the corresponding relationship between the motion response and dynamic characteristics of the wave energy conversion device and time.
  • the index acquisition unit is used to obtain the evaluation index value of the wave energy conversion device according to the time history curve.
  • the curve construction unit includes a time division subunit, a response acquisition subunit, and a time course construction subunit.
  • the time division subunit is used to divide the simulation time period according to the preset time step and determine multiple moments.
  • the response acquisition subunit is used to obtain the motion response value corresponding to the numerical model at each moment.
  • the time history construction subunit is used to construct a time history curve according to each moment and the motion response value corresponding to each moment.
  • the response acquisition subunit is specifically used to iteratively solve the numerical model at any moment in multiple moments according to a preset iterative strategy until the numerical model meets the preset convergence conditions, thereby obtaining the motion response value at the moment.
  • the evaluation index value includes a power generation capability index value and a reliability index value of the wave energy conversion device.
  • Each module in the above-mentioned evaluation device can be implemented in whole or in part through software, hardware, or a combination thereof.
  • Each module can be embedded in or independent of the processor of the computer device in hardware form, or can be stored in the memory of the computer device in software form, so that the processor can call and execute the corresponding operations of each module.
  • a computer device which may be a terminal. Its internal structure diagram may be shown in Figure 17.
  • the computer device includes a processor, memory, an input/output interface, a communication interface, a display unit, and an input device.
  • the processor, memory, and input/output interface are connected via a system bus, and the communication interface, display unit, and input device are connected to the system bus via the input/output interface.
  • the processor of the computer device provides computing and control capabilities.
  • the memory of the computer device includes a non-volatile storage medium and internal memory.
  • the non-volatile storage medium stores an operating system and a computer program.
  • the internal memory provides an environment for the operating system and computer program stored in the non-volatile storage medium.
  • the input/output interface of the computer device is used to exchange information between the processor and external devices.
  • the communication interface of the computer device is used to communicate with external terminals via wired or wireless communication, which may be achieved via Wi-Fi, a mobile cellular network, NFC (near-field communication), or other technologies.
  • the computer program When executed by the processor, the computer program implements a method for evaluating a wave energy conversion device.
  • the display unit of the computer device is used to produce a visually visible image and may be a display screen, a projection device, or a virtual reality imaging device.
  • the display screen can be a liquid crystal display screen or an electronic ink display screen
  • the input device of the computer device can be a touch layer covering the display screen, or a button, trackball or touchpad set on the computer device casing, or an external keyboard, touchpad or mouse.
  • FIG. 17 is merely a block diagram of a portion of the structure related to the solution of the present application, and does not constitute a limitation on the computer device to which the solution of the present application is applied.
  • the specific computer device may include more or fewer components than shown in the figure, or combine certain components, or have a different component arrangement.
  • a computer device including a memory and a processor.
  • the memory stores a computer program
  • the processor implements the steps in the above-mentioned wave energy conversion device evaluation method embodiments when executing the computer program.
  • a non-volatile computer-readable storage medium on which a computer program is stored.
  • the computer program is executed by a processor, the steps in the above-mentioned wave energy conversion device evaluation method embodiments are implemented.
  • a computer program product comprising computer executable instructions, which, when executed by a processor, implement the steps in the above-mentioned wave energy conversion device evaluation method embodiments.
  • user information including but not limited to user device information, user personal information, etc.
  • data including but not limited to data used for analysis, stored data, displayed data, etc.
  • any reference to memory, database or other media used in the embodiments provided in this application can include at least one of non-volatile and volatile memory.
  • Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetic random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc.
  • Volatile memory can include random access memory (RAM) or external cache memory, etc.
  • RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM).
  • the database involved in the various embodiments provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include, but are not limited to, distributed databases based on blockchains.
  • the processors involved in the various embodiments provided in this application may be, but are not limited to, general-purpose processors, central processing units, graphics processors, digital signal processors, programmable logic devices, data processing logic devices based on quantum computing, etc.

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Abstract

一种波浪能转换装置，包括：流体流道，用于将传递至所述流体流道的波浪能转换为气动能；能量转换系统，与所述流体流道连接，用于将所述流体流道转换得到的气动能转换为电能；包括空气透平，所述空气透平包括流道壁、两组导流叶片和一组转子叶片；泄压系统，与所述流体流道连接，用于控制所述流体流道中的气室的压强；包括阀瓣、阀座、弹性单元、控制杆和连接管；所述控制杆与所述阀座固定连接，且所述控制杆分别与所述阀瓣和控制组件活动连接；其中所述控制组件，部署在所述连接管表面，用于根据所述波浪能转换装置的海况，通过所述控制杆动态调整所述弹性单元的初始长度，以控制所述阀瓣对应的开启阈值。

Description

波浪能转换装置及其评价方法
相关申请
本申请要求2024年4月19日申请的，申请号为202410475117.9，名称为“波浪能转换装置和评价方法”的中国专利申请的优先权，在此将其全文引入作为参考。
技术领域
本申请涉及海洋波浪能利用技术领域，特别是涉及一种波浪能转换装置及其评价方法。
背景技术
随着科技的发展，能源的需求量越来越大。在此情况下，新能源的开发以及利用备受关注，比如太阳能、潮汐能、地热能、波浪能等。
以波浪能为例，波浪能具有能量密度高、分布广、可再生等特点，相关技术中，通过波浪能转换装置将波浪能进行一系列能量转换，最终生成电能，以实现波浪能的转换。但一旦波浪能转换装置所处环境的波浪过大，可能会威胁到波浪能转换装置的安全性。
发明内容
基于此，有必要针对上述技术问题，提供一种波浪能转换装置和一种波浪能转换装置评价方法，以提升波浪能转换装置的安全性。
第一方面，本申请提供了一种波浪能转换装置，包括流体流道、能量转换系统和泄压系统。流体流道用于将传递至流体流道的波浪能转换为气动能。能量转换系统与所述流体流道连接，用于将流体流道转换得到的气动能转换为电能；包括空气透平，所述空气透平包括流道壁、两组导流叶片和一组转子叶片；各所述导流叶片的横截面的轮廓线包括一条椭圆弧段和一条直线段，且所述直线段沿所述直线段一端点处围绕所述旋转主轴的圆的切线方向布置；各所述转子叶片的轴向方向的截面的轮廓线，包括吸力侧为椭圆弧段，压强侧为圆弧段；每组导流叶片的数量为14-24。泄压系统与所述流体流道连接，用于控制流体流道中的气室压强；包括阀瓣、阀座、弹性单元、控制杆和连接管，所述阀瓣通过所述弹性单元与所述阀座连接；所述阀瓣还通过所述连接管与所述气室连接；所述控制杆与所述阀座固定连接，且所述控制杆分别与所述阀瓣和控制组件活动连接；所述控制杆为伸缩杆；所述阀瓣对应的开启阈值有多个。所述控制组件，部署在所述连接管表面，用于根据所述波浪能转换装置的海况，通过所述控制杆动态调整所述弹性单元的初始长度，以控制所述阀瓣对应的开启阈值；所述控制组件调整所述弹性单元的初始长度的调整长度有多个。
在其中一个实施例中，对应于气室的压强超过开启阈值的情况，阀瓣处于开启状态。对应于气室的压强未超过开启阈值的情况，阀瓣处于关闭状态。
在其中一个实施例中，能量转换系统包括空气透平和发电组件，空气透平与发电组件连接。空气透平，用于将流体流道转换得到的气动能转换为机械能。发电组件，用于将空气透平转换得到的机械能转换为电能。
在其中一个实施例中，空气透平的转子转速与发电机的转子转速相同。
在其中一个实施例中，空气透平还包括旋转主轴和转子部；两组导流叶片的一组导流叶片均匀分布在流道壁的流道入口，且另一组导流叶片均匀分布在流道壁的流道出口；所述一组转子叶片沿围绕所述旋转主轴的周向均匀分布在空气透平的流道的中心区域的转子部上。
在其中一个实施例中，所述转子叶片与所述导流叶片之间的流道壁的轴向方向的截面的轮廓线，包括一条90°的圆弧段和所述圆弧段两侧的直线段。
在其中一个实施例中，装置还包括一个或多个系泊系统；所述一个或多个系泊系统与所述波浪能转换装置的迎波侧连接。
在其中一个实施例中，每一系泊系统包括一浮球，所述浮球通过至少一个弹性组件与所述波浪能转换装置的迎波侧连接。
在其中一个实施例中，流体流道包括互相连通的水平流道和垂直流道，垂直流道靠近波浪能转换装置的迎波侧设置，且水平流道的口门靠近波浪能转换装置的背波侧设置，水平流道的横截面面积与垂直流道的横截面面积相等；水平流道和垂直流道之间采用流线型流道连通。
在其中一个实施例中，流体流道还包括多个隔板；各隔板垂直固定在水平流道和垂直流道的流道壁。
第二方面，本申请还提供了一种波浪能转换装置评价方法，该方法包括以下步骤。
针对第一方面任一项的波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程。
对数学模型进行求解运算，得到波浪能转换装置的评价指标值。
在其中一个实施例中，对数学模型进行求解运算，得到波浪能转换装置的评价指标值，包括以下步骤。
对数学模型进行离散化处理，得到数值模型。离散化处理包括空间离散化处理和时间离散化处理。
基于数值模型，求解波浪能转换装置的时程曲线。时程曲线包括波浪能转换装置运动响应和动力特性与时间的对应关系。
根据时程曲线，获取波浪能转换装置的评价指标值。
在其中一个实施例中，基于数值模型，求解波浪能转换装置的时程曲线，包括以下步骤。
根据预设时间步对模拟时间段进行划分，确定多个时刻。
获取数值模型在每一时刻对应的运动响应值。
根据每一时刻以及每一时刻对应的运动响应值，构建时程曲线。
在其中一个实施例中，获取数值模型与每一时刻对应的运动响应值，包括：对于每一时刻，按照预设的迭代策略，对数值模型进行迭代求解，直至数值模型满足预设的收敛条件，得到每一时刻的运动响应值。
在其中一个实施例中，评价指标值包括波浪能转换装置中的发电能力指标值和可靠性指标值。
第三方面，本申请还提供了一种评价装置，该装置包括：构建模块和运算模块。
构建模块，用于针对第一方面任一项的波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程。
运算模块，用于对数学模型进行求解运算，得到波浪能转换装置的评价指标值。
第四方面，本申请还提供了一种计算机设备，包括存储器和处理器，存储器存储有计算机程序，处理器执行计算机程序时实现上述第二方面中任一项实施例中的波浪能转换装置评价方法的步骤。
第五方面，本申请还提供了一种非易失计算机可读存储介质，其上存储有计算机程序，计算机程序被处理器执行时实现上述第二方面中任一项实施例中的波浪能转换装置评价方法的步骤。
第六方面，本申请还提供了一种计算机程序产品，包括计算机可执行指令，该计算机可执行指令被处理器执行时实现上述第二方面中任一项实施例中的波浪能转换装置评价方法的步骤。
上述波浪能转换装置及其评价方法，波浪能转换装置包括：流体流道、能量转换系统、泄压系统和控制组件。流体流道用于将传递至流体流道的波浪能转换为气动能。能量转换系统与所述流体流道连接，用于将流体流道转换得到的气动能转换为电能包括空气透平，所述空气透平包括流道壁、两组导流叶片和一组转子叶片；各所述导流叶片的横截面的轮廓线包括一条椭圆弧段和一条直线段，且所述直线段沿所述直线段一端点处围绕所述旋转主轴的圆的切线方向布置；各所述转子叶片的轴向方向的截面的轮廓线，包括吸力侧为椭圆弧段，压强侧为圆弧段；每组导流叶片的数量为14-24。泄压系统与所述流体流道连接，用于控制流体流道中的气室压强；包括阀瓣、阀座、弹性单元、控制杆和连接管，所述阀瓣通过所述弹性单元与所述阀座连接；所述阀瓣还通过所述连接管与所述气室连接；所述控制杆与所述阀座固定连接，且所述控制杆分别与所述阀瓣和控制组件活动连接；所述控制杆为伸缩杆；所述阀瓣对应的开启阈值有多个。所述控制组件，部署在所述连接管表面，用于根据所述波浪能转换装置的海况，通过所述控制杆动态调整所述弹性单元的初始长度，以控制所述阀瓣对应的开启阈值；所述控制组件调整所述弹性单元的初始长度的调整长度有多个。该装置中，流体流道将波浪能转换为气动能，能量转换系统将流体流道转换得到的气动能转换为电能，即通过流体流道和能量转换系统，将波浪能转换为电能。并且，在波浪能转换为电能的过程中，泄压系统控制流体流道中的气室的压强，相当于考虑到波浪过大影响波浪能转换装置稳定性的因素，通过泄压系统将流体流道中的气室的压强调整在正常的压强范围内，保障波浪能转换装置的安全性。
附图说明
为了更清楚地说明本申请实施例或相关技术中的技术方案，下面将对实施例或相关技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1为本申请一个实施例中波浪能转换装置的结构示意图；
图2为本申请一个实施例中泄压系统的结构示意图；
图3为本申请另一个实施例中泄压系统的结构示意图；
图4为本申请一个实施例中空气透平的正视图；
图5为本申请一个实施例中空气透平的俯视图；
图6为本申请另一个实施例中波浪能转换装置的结构示意图；
图7为本申请一个实施例中系泊系统的结构示意图；
图8为本申请又一个实施例中波浪能转换装置的结构示意图；
图9为本申请一个实施例中评价方法的流程示意图；
图10为本申请一个实施例中指标获取步骤的流程示意图；
图11为本申请一个实施例中曲线构建步骤的流程示意图；
图12为本申请另一个实施例中评价方法的流程示意图；
图13为本申请又一个实施例中评价方法的流程示意图；
图14为本申请一个实施例中透平稳态效率的曲线对比图；
图15为本申请一个实施例中装置性能参数的曲线示意图；
图16为本申请一个实施例中评价装置的结构框图；
图17为本申请一个实施例中计算机设备的内部结构图。
附图标记说明：
10          波浪能转换装置；11                 流体流道；
12            能量转换系统；121                空气透平；
1211              导流叶片；1212               转子叶片；
13                泄压系统；1311                   阀瓣；
1312              弹性单元；1313                   阀座；
1314                控制杆；1315                 连接管；
14                系泊系统；141                      锚；
142                 链条段；143                    浮球；
144                弹性组件；15                 主浮力舱；
16                 副浮力舱。
具体实施方式
为了使本申请的目的、技术方案及优点更加清楚明白，以下结合附图及实施例，对本申请进行进一步详细说明。应当理解，此处描述的具体实施例仅仅用以解释本申请，并不用于限定本申请。基于本申请中的实施例，本领域普通技术人员在没有做出创造性劳动前提下所获得的所有其他实施例，都应当属于本申请保护的范围。
在此使用的术语仅仅是为了描述本发明具体实施例，而并非在于限制本申请。在此使用的术语“包括”、“包含”等表明了所述特征、步骤、部件和/或操作的存在，但并不排除存在或添加一个或多个其他特征、步骤、部件或操作。
在本申请中，除非另有明确的规定和限定，术语“安装”、“固定”等应做广义理解。对于本领域的普通技术人员而言，应根据具体情况理解上述术语在本申请中的具体含义。
在此使用的所有术语(包括技术术语和科学术语)具有本领域技术人员通常所理解的含义，除非另有定义。应注意，此处使用的术语具有与本申请权利要求书、说明书中对应术语上下文相一致的含义，而不应该以理想化或过于刻板的方式进行理解。
波浪能是人类至今尚未具备商业化开发能力的品位最高、分布最广的海洋可再生能源，被认为是人类未来能源的希望，而如何实现高效可靠波浪能转换是全球可再生能源领域中的重大科学问题。气动式波浪能转换装置相较于现有的其他类型的波浪能转换装置，具备相对更高效、更可靠等优点。然而，气动式波浪能转换装置在提高效率、提高可靠性、设计优化理论等方面依然存在不足与挑战，致使其产业化发展缓慢。这些不足与挑战主要包括：
(1)高可靠性是气动式波浪能转换装置的第一指标要素。在高海况条件下，一方面，装置整体运动以及气室内部水体振荡剧烈，装置流道壁受到的压强过大，同时装置气室内的压强过大，输入给冲击式空气透平的气动能过剩，严重影响流道、透平转子、发电机以及装置整体的可靠性，因此必须采用相应的泄压减荷系统以保护装置安全；另一方面，装置的剧烈的、大幅的运动导致系泊系统的受力过大，严重影响系泊系统以及装置整体的可靠性和生存性。
(2)气动式波浪能转换装置的能量转换效率仍然较低，且符合高效俘能的波浪频率范围依然较窄。气动式波浪能转换装置的能量转换过程依次包括以下三个阶段：船体部分将波浪能转换为气动能，空气透平将气动能转换为透平转子的旋转动能，以及发电机将旋转动能转换为电能，上述任一阶段能量转换效率的提高都在不同程度上影响着气动式波浪能转换装置的整体能量转换效率。另外，经过大量研究与实验，发现引入一些共振机制，也有可能拓宽波浪能转换装置高效俘能的频率范围。
基于此，在考虑气动式波浪能转换装置可靠性的前提下，目前气动式波浪能转换装置采用的空气透平多为威尔斯透平、导流叶片固定且对称分布的轴流冲击式空气透平以及径向入流的冲击式空气透平。威尔斯透平峰值效率较高，但存在失速现象，且不适合于如太平洋西岸等波浪能流密度较低的海域。导流叶片固定且对称分布的轴流冲击式空气透平在往复气流下，平均效率的最高值不超过48％，严重制约了装置的整体性能。已有的径向入流的冲击式空气透平往往径向尺寸庞大，不利于其与气动式波浪能转换装置的安装，且其效率还有望进一步提高。因此，有必要提供一种兼具高可靠、高效、轴向和径向都比较紧凑等优点的空气透平。同时，系泊系统也会影响到装置的整体性能，在此基础上，提供一种适用于气动式波浪能转换装置的增效宽频系泊系统，对保障系泊系统的可靠性也十分必要。
(3)气动式波浪能转换装置的高可靠性和高效性之间可能存在矛盾关系。若泄压减荷系统的阈值较大，提高了装置的发电量，但装置的发电机在大海况条件下长时间处于高功率发电状态且有可能长时间超过额定功率，影响发电机的可靠性。若泄压减荷系统的阈值较小，更好地保护了透平、发电机的安全性，但影响装置的发电功率，况且泄压减荷系统的频繁开启/关闭也会影响泄压减荷系统以及装置整体的可靠性。
在实际海洋环境下，浪、流、风条件时空分布不规则，偶尔的大波引起气室内压强过大，但由于时间短暂并不会影响发电机的可靠性(即发电机允许短时间超过额定功率运行)，此时可以不需要泄压减荷系统发挥作用，这样不仅有利于提高发电量，也提高了泄压减荷系统的可靠性。
(4)气动式波浪能转换装置的设计优化理论欠缺。气动式波浪能转换装置的海试试验时间代价和人力物力成本都相当巨大。在此情况下，数值模拟结果方法是研究气动式波浪能转换装置性能以及优化的最主要手段。然而，由于气动式波浪能转换装置模拟的极度复杂性，需要考虑多运动体、多物理场、多相流、强非线性等高难度问题，准确预测装置性能还需要考虑各级能量转化阶段之间的相互作用。目前为止，尽管许多专家学者都认识到气动式波浪能转换装置从浪至电全系统耦合模拟的重要性，但仍然尚未建立起相应的理论模型，气动式波浪能转换装置的设计优化理论欠缺。
现有气动式波浪能转换装置的数值模拟均只专注于装置某一级能量转换阶段，或采用简化模型描述各级能量转换阶段之间的相互作用，针对气动式波浪能转换装置整体性能的预测模型基本上采用线性叠加的方法(参见“An integrated numerical model for the chamber-turbine system of an oscillating water column wave energy converter(Liu et.Al，2021)”)。在装置共振点及其附近，装置响应幅值模拟误差高达100％，能量转换效率模拟误差高达30％。由此可见，现有模拟方法无法准确预测气动式波浪能转换装置各级能量转化效率和装置整体性能，也难以提供可靠的，优化装置性能的分析工具。
综上，相关技术中的气动式波浪能转换装置存在可靠性较低、能量转换效率较低的问题，同时缺少波浪能转换装置的理论优化方法。基于此，本申请提供了阈值可调的自动泄压减荷系统，实时保护波浪能转换装置的可靠性；根据高强度的弹性部件构建波浪能转换装置的系泊系统，降低系泊系统的最大受力，进一步提升波浪能转换装置的安全性能；以及提出径向入流的冲击式空气透平，以其兼具高可靠、高效、轴向和径向都比较紧凑的特性，提升波浪能转换装置的转换效率。另外，本申请实施例还提供了气动式波浪能转换装置从浪至电全系统耦合模拟方法，填补了波浪能转换装置的设计优化理论的空白。
下面以具体的实施例对本申请的技术方案以及本申请的技术方案如何解决上述技术问题进行详细说明。下面这几个具体的实施例可以相互结合，对于相同或相似的概念或过程可能在某些实施例中不再赘述。下面将结合附图，对本申请的实施例进行描述。
在一个示例性的实施例中，如图1所示，提供了一种波浪能转换装置10，该装置包括流体流道11、能量转换系统12和泄压系统13，流体流道11与泄压系统13连接，且流体流道11与能量转换系统12连接；
流体流道11，用于将传递至流体流道11的波浪能转换为气动能。
能量转换系统12，用于将流体流道11转换得到的气动能转换为电能。
泄压系统13，用于控制流体流道11中的气室压强。
图1所示的波浪能转换装置10中，包括：流体流道11、能量转换系统12、和泄压系统13。由图1可以看出，流体流道11分别与能量转换系统12和泄压系统13连接。
其中，流体流道11包括液体流道和气体流道，流体流道11的一端(液体流道的入口)与水体连接，用于将波浪能转换为气动能。流体流道11的另一端(气体流道的出口)与能量转换系统12连接，能量转换系统12将流体流道11转换生成的气动能转换为电能，比如将气动能转换为旋转动能、再将旋转动能转换为电能。
另外，在波浪能转换装置10的能量转换过程中，流体流道11还与泄压系统13连接，以便于泄压系统13根据流体流道11中气体流道的气室压强，自动实现泄压系统13中阀瓣的开启或者闭合，从而控制流体流道11与大气之间连通或者闭合，以控制流体流道11中的气室压强。
在实际应用场景中，若波浪能转换装置10中流体流道11的压强过大，考虑到输入给能量转换系统12的气动能过剩，影响波浪能转换装置10的可靠性，则需要控制流体流道11与大气连通，以降低流体流道11内的气室压强；若波浪能转换装置10中流体流道11的压强处于预设阈值范围内，意味着能量转换系统12的气动能不足以影响波浪能转换装置10的可靠性，此时则可以控制流体流道11与外界大气断开连接，不再起到降低流体流道11内的气室压强的作用。
需要强调的是，波浪能转换装置10还具备停泊功能，基于此，请继续参见图1，本申请实施例中的波浪能转换装置10还包括系泊系统14，该系泊系统14用于固定所述波浪能转换装置10。
本申请实施例中的系泊系统14可以设置在波浪能转换装置10的迎波侧，也可以设置在波浪能转换装置10的背波侧。本申请以图1中的系泊系统14设置在波浪能转换装置10的迎波侧为例进行说明。
本申请实施例中，波浪能转换装置10包括流体流道11、能量转换系统12、和泄压系统13，流体流道11与泄压系统13连接，且流体流道11与能量转换系统12连接。其中，流体流道11，用于将传递至流体流道11的波浪能转换为气动能。能量转换系统12，用于将流体流道11转换得到的气动能转换为电能。泄压系统13，用于控制流体流道11中的气室压强。该装置中，流体流道11将波浪能转换为气动能，能量转换系统12将流体流道11转换得到的气动能转换为电能，即通过流体流道11和能量转换系统12，将波浪能转换为电能。并且，在波浪能转换为电能的过程中，泄压系统13控制流体流道11中的气室压强，也就是说，考虑到波浪过大影响波浪能转换装置10稳定性的因素，通过泄压系统13将流体流道11中的气室压强调整在正常的压强范围内，保障波浪能转换装置10的安全性。
接下来，分别对波浪能转换装置10中的流体流道11、能量转换系统12、泄压系统13以及系泊系统14的结构以及功能进行说明。
在一个示例性的实施例中，流体流道11包括互相连通的水平流道和垂直流道，垂直流道靠近波浪能转换装置10的迎波侧设置，且水平流道靠近波浪能转换装置10的背波侧设置，水平流道的横截面面积与垂直流道的横截面面积相等，水平流道和垂直流道之间采用流线型流道连通。
请继续参见图1，流体流道11可以是L型流道，具体包括互相连通的水平段和垂直段，水平段远离垂直段的一端为流体流道11的口门，并完全浸没在水体中，且流体流道11口门位于背波向一侧，垂直段的上半部分为气室。
本申请实施例在流体流道11的水平段横截面的面积与垂直段横截面的面积相等的情况下，对流体流道11的水平段横截面以及垂直段横截面的形状均不作限制，比如水平段横截面可以为矩形、五边形或其他流线形等，流体流道11垂直段横截面可以为矩形。
请继续参见图1，为改善流体流道11中的流场，还可以在流体流道11内部上、下拐角处(即水平流道和垂直流道的交接处)设置为倒角或圆角。
在一个示例性的实施例中，流体流道11还包括多个隔板。各隔板垂直固定在水平流道和垂直流道的流道壁。
在流体流道11内部，按照预设的间隔设置有多个垂直于流道壁的垂直隔板，各隔板与流道内壁、外壁固定连接，比如通过焊接连接。在一实施例中，垂直隔板的数量设置为1～3个。
进一步地，隔板的一端延伸至流体流道11水平段的口门处，另一端延伸至流体流道11垂直段自由水面位置处。
本申请实施例中，垂直隔板有助于引导流体流道11内水体在垂直方向上平顺流动，提高波浪能转换装置10的俘能效率；同时，垂直隔板加强了装置流体流道的结构强度，还可以在一定程度上提高波浪能转换装置10在复杂海况下的安全性。
下面，对波浪能转换装置10中的泄压系统13的结构以及功能进行说明。
在一个示例性的实施例中，请参见图2，泄压系统13包括阀瓣1311、阀座1313、弹性单元1312、控制杆1314和连接管1315，阀瓣1311通过弹性单元1312与阀座1313连接，阀瓣1311还通过连接管1315与气室连接；控制杆1314与阀座1313固定连接，且控制杆1314分别与阀瓣1311和控制组件活动连接；
控制组件，用于通过控制杆1314动态调整弹性单元1312的初始长度，以控制阀瓣1311对应的开启阈值。
其中，控制杆1314可以是伸缩杆，弹性单元1312可以是弹簧或其他弹性系统，且弹性单元1312的初始状态为压缩状态，初始长度也就是弹性单元1312在压缩状态下的压缩长度。
请继续参见图2，图2中连接管1315内壁虚线所表示的是一个具有缝隙的平面，该平面上可以安装控制组件，如此设置，部署在连接管1315表面的控制组件就可以与控制杆1314连接，以灵活调整控制杆1314向上/向下运动，进而控制弹性单元1312的初始长度变短/变长，进一步控制阀瓣1311对应的开启阈值增大/减小。
在实际场景中，控制组件可以在监测到波浪能转换装置10处于或者即将处于恶劣海况的情况下，控制泄压系统13中的控制杆1314向下运动，使得弹性单元1312的初始长度变长，以降低阀瓣1311的开启阈值。
进一步地，控制组件在监测到波浪能转换装置10从恶劣海况转换为正常海况的情况下，控制泄压系统13中的控制杆1314向上运动，使得弹性单元1312的初始长度变短，或者回归至初始的压缩长度，以提升阀瓣1311的开启阈值。
需要说明的是，控制组件还可以与弹性单元1312相连接，以直接调整弹性单元1312的初始长度。
另外，本申请实施例中，控制组件通过控制杆1314调整弹性单元的初始长度的调整长度可以有多个，也就是阀瓣1311的开启阈值可以有多个，对此，本申请实施例不作限制。
在一个示例性的实施例中，在气室的压强超过开启阈值的情况下，阀瓣1311处于开启状态，以执行泄压减荷动作。
在气室的压强未超过开启阈值的情况下，阀瓣1311处于关闭状态，以停止执行泄压减荷动作。
对泄压系统13中的泄压原理作进一步说明。：正常条件下，如图2所示，在阀瓣1311的重力和弹性压强的作用下，阀瓣1311关闭。当气室内压强达到阈值时，阀瓣1311受到的气体压强大于其自身重力和弹性压强之和，阀瓣1311向上(阀座方向)运动并打开，如图3所示，此时气室与大气连通，起到泄压减荷、保护能量转换系统12中各部件的作用。
需要说明的是，结合图2和图3，在连接管1315固定在特定位置的情况下，随着控制杆1314的伸缩，阀座1313与连接管1315的上表面之间的距离也会随之变化。例如，控制杆1314缩短，弹性单元1312的长度缩短，阀座1313与连接管1315的距离增加。并且，阀瓣1311上升的高度，为阀瓣1311与连接管1315上表面之间的距离(即气流运动的间隙)相同。
下面，对波浪能转换装置10中的能量转换系统12的结构以及功能进行说明。
在一个示例性的实施例中，能量转换系统12包括空气透平121和发电组件，空气透平与发电组件连接。
空气透平121，用于将流体流道11转换得到的气动能转换为机械能。
发电组件，用于将空气透平121转换得到的机械能转换为电能。
在一个示例性的实施例中，空气透平121的转子转速与发电组件的转子转速相同。
空气透平121可以是冲击式空气透平，具有自整流特点。图4为空气透平121的结构示意图，如图4所示，空气透平121包括导流叶片1211和转子叶片1212。在实际应用中，无论空气透平121流道内的气流方向是流入还是流出，空气透平121的转子叶片1212受到的空气作用力矩始终沿同一方向，即空气透平121的转子叶片1212始终保持单向转动，以便于空气透平121将气动能充分转换为机械能，进而提升波浪能转换装置10的整体能量转换效率。
另外，空气透平121的流道入口与气室内自由水面的高度满足一定的垂直距离要求，即在波浪能转换装置10运行条件下，流体流道11内的水体不会倒灌入透平流道。
可选的，冲击式空气透平与气室之间通过轮廓为流线形的流道连接，或者透平下方流道入口的上边壁与气室顶部边壁重合，实现装置船体部分与冲击式空气透平的固定连接。
发电组件可以为直驱发电机，通过永磁体形成的旋转磁场，引起转子旋转，进而产生感应电动势，通过整流器等电气设备处理，最终将机械能转化为电能。
在波浪能转换装置10中，发电组件与透平转子121同轴连接并且具有相同的转速，以便于发电组件充分利用空气透平121转换得到的机械能，提升机械能转换为电能的转换效率。
在一个示例性的实施例中，请继续参见图4，空气透平121包括流道壁、两组导流叶片1211和转子叶片1212。
两组导流叶片1211的一组导流叶片均匀分布在流道壁的流道入口，且另一组导流叶片均匀分布在流道壁的流道出口。
转子叶片1212沿轴向均匀分布在空气透平121的流道的中心区域。
其中，空气透平121为冲击式空气透平，由流道壁、两组导流叶片1211、透平转子部(包括轮毂)和固定于转子部(轮毂)之上的转子叶片1212)以及旋转主轴组成。
空气透平121流道形如具有一定厚度的字母U旋转一周而形成的区域，可以分为导流叶片1211、流道壁(过渡段)和转子叶片1212。进一步地，请参见图5，图5为空气透平121的俯视图，由图5可以看出，空气透平121的导流叶片1211均匀分布在流道壁的流道入口。需要说明的是，空气透平121为对称结构，也就是说，轴向(即旋转主轴方向)垂直布置的空气透平121的俯视图和仰视图是一样的，因此，本申请实施例中空气透平121的另一组导流叶片1211均匀分布在流道壁的流道出口附近。
其中，两组导流叶片1211与空气透平121的流道壁固定连接，且沿周向均匀对称地分布于靠近流道入口和流道出口的位置，且各导流叶片1211横截面等厚度。
在一个实施例中，请继续参见图4或者图5，空气透平121中的各导流叶片1211的横截面的轮廓线由一条椭圆弧段和一条较短的直线段组成，直线段沿所述直线段一端点处围绕所述旋转主轴的圆的切线方向布置。
其中，透平转子部沿轴向布置于流道中心位置处的柱形区域内，转子叶片1212沿周向均匀布置于转子部上。
在一个实施例中，空气透平121中的各转子叶片1212的轴向方向(即旋转主轴方向)的截面的轮廓线，在吸力侧是一条椭圆弧段，压强侧是一条圆弧段，即空气透平121中的各转子叶片1212的沿轴向方向的截面的轮廓线呈现新月形。
在一个实施例中，空气透平121中的转子叶片1212和导流叶片1211之间的过渡段的轴向方向的截面的轮廓线，包括一条90°的圆弧段和圆弧段两侧的直线段。
正常工作条件下，气流从U型流道透平的入口径向入射，经由一组导流叶片1211和流道壁的导流作用后，以一定角度流入转子叶片1212并驱动空气透平121中的转子叶片1212旋转，之后气流经由另一组导流叶片1211再从透平的出口流出。
在一实施例中，空气透平121的透平转子部上的转子叶片1212数量为26～34，轮毂比为0.60～0.75。
在一实施例中，若空气透平121的转子叶片1212所在位置处的流道外壁对应的半径为R，导流叶片1211椭圆弧的半长轴为0.40R～0.65R，半短轴为0.26R～0.34R；导流叶片1211直线段的长度为0.03R～0.06R；导流叶片1211的数量为14～24；过渡段的圆弧部分内壁的半径为0.45R～0.55R，直线部分的长度为0.20R～0.30R。
本申请实施例中，冲击式的空气透平121中导流叶片1211固定，除了转子叶片1212外不再有活动部件，结构简单，可靠性高。空气透平121的转子叶片1212与下游的导流叶片1211之间的流道过流断面不断增大，气流速度逐渐降低，因此发生在下游的导流叶片1211处的气动损失减小，从而提高了透平效率，具有高效特点。同时，空气透平121的过渡段沿径向和轴向的尺寸都比较小，一方面，空气透平121整体在轴向和径向上都比较紧凑，性价比高，也更有助于空气透平121与波浪能转换装置10的流体流道11之间的固定连接；另一方面，空气透平121的重量比较小，有利于提高波浪能转换装置10的稳定性。
在波浪能转换装置10的实际应用场景中，尤其是风浪较大的时候，波浪能转换装置10的停泊能力也至关重要。本申请实施例中，系泊系统14用于固定波浪能转换装置10在特定位置，比如海床、海岸等停泊位置的设备。通常情况下，为保持波浪能转换装置10的平衡性，系泊系统14设置在波浪能转换装置10的迎波侧，配重系统固定在波浪能转换装置10的背波侧。当然，系泊系统14也可以固定在波浪能转换装置10背波侧的其他位置，对此，本申请实施例不作限制。
在一个示例性的实施例中，波浪能转换装置还包括一个或多个系泊系统14；各系泊系统14于波浪能转换装置10的迎波侧连接。
其中，系泊系统14，用于固定波浪能转换装置10在指定位置。
以波浪能转换装置10包括三个系泊系统14为例，请参见图6，图6为波浪能转换装置10的俯视图，各系泊系统14可以固定在波浪能转换装置10中流体流道11的竖直段，且不同系泊系统14的固定位置不同。本申请实施例中，系泊系统14的一端固定在波浪能转换装置10，另一端可以固定在海床上，这意味着，波浪能转换装置10可以在海面上停泊。
在实际场景中，波浪能转换装置10背波向一侧同样可以布置一个或多个系泊系统14，此处的系泊系统14可以是单独的锚和链条，也可以是包括弹性组件的新型的系泊系统14，以提高波浪能转换装置10的可靠性和生存性。基于此，下面对系泊系统14的结构功能作进一步说明。
在一个示例性的实施例中，如图7所示，图7为一系泊系统14的俯视图，系泊系统14包括锚141、链条142、浮球143和两个弹性组件144。
其中，系泊系统14的浮球143通过至少一个弹性组件144与波浪能转换装置10的迎波侧连接。
需要说明的是，图7以系泊系统14中包括两个弹性组件144为例，仅仅是系泊系统14的一种示意图，在实际应用中，系泊系统14中的弹性组件144还可以是1条、3条等等。
可选的，链条142包括悬链段和躺链段，且链条142的总长度可以为水的深度的1.5～8.0倍。
在实际停泊场景中，链条142的一端与锚141连接并固定在海床上，链条142的另一端固定在浮球143上，浮球143分别与两个弹性组件144连接，两个弹性组件144的另一端分别固定在波浪能转换装置10的不同位置。
在材质方面，弹性组件144中的各弹性段可以是根据链条和弹簧/其他弹性系统构建的组合件，也可以是高强度的弹性绳。
在数量方面，单套系泊系统14的弹性组件可以为一条，可以为两条呈V型布置，也可以为更多条呈分散状布置。
在长度方面，各条弹性组件144的水平长度为波浪能转换装置10长度(即浮球143到波浪能转换装置10的距离)的2～3倍。
本申请实施例中，系泊系统14采用锚141、链条段142、浮球143、弹性组件144的系泊方式，平缓了系泊系统14对波浪能转换装置10船体部分的系泊力，增大了波浪能转换装置10在波浪条件下的纵荡响应，从而达到宽频增效的效果，进而提高波浪能转换装置10的整体发电性能。另外，浮球143和弹性组件144(或弹性吸能部件)的组合方式在一定程度上降低了系泊系统14中的最大受力，提高了系泊系统14的可靠性，也在一定程度上提升了波浪能转换装置10整体的可靠性与生存性。
在实际应用场景中，波浪能转换装置10除了包括上述泄压系统13、流体流道11、发电组件和空气透平121之外，还可以包括多个其他组件，以进一步完善波浪能转换装置10，适应实际需求，比如监测装置状态的传感器、能量储备系统、监控系统等等。
在一个示例性的实施例中，波浪能转换装置10中还可以包括浮力舱、储能系统、电力输出系统、监控系统、配重、传感器等。
在其中一实施例中，请参见图8，图8为波浪能转换装置10的架构示意图，图8中，浮力舱包括主浮力舱15和副浮力舱16，以流体流道11为L型流道为例，主浮力舱15可以设置在L型流道的水平段上方，半淹在水里，副浮力舱16可以设置在L型流道的竖直段的外侧，半淹或全淹在水里。此时，波浪能转换装置10中的系泊系统14也可以固定在副浮力舱16上。
在实际应用中，若波浪能转换装置10包括主浮力舱15，也可以不设置副浮力舱16。对此，本申请实施例不作限制。
监控系统包括信息采集设备(比如传感器、摄像机等)、信息传输设备、后端控制设备、存储设备和显示设备。
储能系统、监控系统的后端控制及显示设备、配重等均布置于主浮力舱15内部。
传感器包括但不限于以下传感器：(1)液位传感器，可以安装在气室内部，用于监测L型流道内的水位振荡高程；(2)振动传感器，可以安装在发电组件的底座上，用于监测发电组件的水位振动情况；(3)温度传感器，可以安装在发电机表面以及主浮力舱15内部，用于监测发电组件温度以及主浮力舱15内部温度；(4)流量传感器，可以安装在空气透平121的流道内部，用于监测气体体积流量；(5)转速传感器，可以安装在空气透平121的转子部与发电组件之间的连接轴上，用于监测透平转子转速和发电组件转速；(6)扭矩传感器，可以安装在空气透平121的转子部与发电组件之间的连接轴上，用于监测透平转子提供给发电组件的主力矩。
在其中一实施例中，为实时监测波浪能转换装置10的运行状态，上述传感器获取的数据，监控系统监测得到的监测数据，均可以上传至云端，以便于工作人员远程查看。
结合上述对波浪能转换装置10的结构说明，可以将波浪能转换装置10的工作原理归纳如下：在浪、流、风等作用下，波浪能转换装置10发生纵荡、横荡、垂荡、横摇、纵摇、艏摇共六自由度运动，引起波浪能转换装置10流体流道11内的水体与装置耦合振荡，致使流体流道11中的液体流道内水柱上下振荡、气室内空气压强正负交替；气室顶部或者侧壁通过流体流道11中的空气流道与大气连通，在压差作用下空气流道内形成往复气流并驱动安装在空气流道内的冲击式的空气透平121单向旋转，进而带动与空气透平121同轴连接的发电组件发电，实现了波浪能到气动能、气动能到旋转机械能、旋转机械能再到电能的转换；同时，当流体流道11内气室的压强高于压强阈值时，安装于气室上方的阈值可调的泄压系统13打开，起到泄压减荷、保护空气透平121和发电组件的作用。
需要强调的是，本申请实施例中的波浪能转换装置10还可以拓展成多气室气动式，即由多个上述的船体部分并联而共同组成波浪能一级能量转换系统，二级能量转换系统和三级能量转换系统的布置方案，可以采用多透平多发电机模式、多透平单发电机模式或者单透平单发电机模式。
多气室气动式的波浪能转换装置10在宽度方向上得到了极大的扩展。单套装置可以俘获更大范围内的波浪能，极大地增加了单套装置的电能输出。多气室气动式的波浪能转换装置10具有N+6个运动自由度，其中N表示N个气室的水柱振荡自由度，6表示装置本身的纵荡、横荡、垂荡、横摇、纵摇、艏摇共6个自由度运动，由于装置各自由度运动在流道内分别产生振荡波且频率各异，这些不同频率振荡波与流道内水柱自身振荡产生叠加现象，使得波能转换成气动能时，气动能随周期变化曲线展现多峰特点，并且装置响应波周期宽度增宽，波能转换成气动能的效率增大，从而产生增效宽频效果。多气室气动式的波浪能转换装置10的单位千瓦成本大幅缩减，具体体现在装置运输成本(即从船厂运输到工作海域)、系泊系统成本、电力输出系统成本、透平成本和发电机成本(采用多透平单发电机模式或者单透平单发电机模式时)的缩减，这是因为在总装机容量相同的情况下，多台单气室装置相较于单台多气室装置而言，多台单气室装置运输费用比单台多气室的要高、多台单气室装置所配置的锚泊系统和输电电缆更多、海上施工和日后运维工作量更大，每千瓦装机容量的成本和运维成本更高。
上述是对波浪能转换装置结构的说明，考虑到波浪能转换装置整体性能预测和结构优化缺乏可靠分析模型和理论依据，本申请实施例还提供了一种波浪能转换装置评价方法，为波浪能转换装置的系统设计及优化提供了可靠性分析依据。
在一个示例性的实施例中，如图9所示，提供了一种波浪能转换装置评价方法，包括以下步骤S901和S902。
S901，针对波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程。
按照功能类型，将波浪能转换装置划分为船体系统(流体流道和浮力舱)、空气透平系统、发电组件系统(发电机)、泄压系统和系泊系统；接着，根据各系统的运动特性，分别构建各系统的控制方程，最后，将上述构建的方程进行全系统耦合，得到波浪能转换装置的数学模型。
本申请实施例中，数学模型具体包括流体运动方程、船体部分运动方程、透平转子运动方程、泄压系统控制方程、发电机模型控制方程、系泊系统控制方程、以及确定数学模型边界条件和数学模型初始条件。
其中，流体运动方程为考虑流体压缩性的连续方程、雷诺时均纳维-斯托克斯方程组、湍流模型方程组以及气体状态方程；船体部分运动方程、透平转子运动方程、泄压系统控制方程为牛顿第二定律方程。
下面，对数学模型的具体构建过程进行说明。
规定笛卡尔坐标系O-x1x2x3，其中原点O与静止水面重合，x1轴方向为波浪传播方向，x2轴方向为波峰线方向，x3轴方向为竖直向上。另外，在气动式波浪能转换装置质心位置处建立随装置一起运动的局部坐标系O′-x1′x2′x3′。
流体部分包括水体和气体，其控制方程为连续方程和雷诺时均纳维-斯托克斯方程组，并引入湍流模型方程组，表示为：

上述公式中，ρ是流体密度；t是时间；下标i，j和k是哑标，且i＝1，j＝2，k＝3；ui是流体沿xi方向上的速度；fi是作用在流体微团在xi方向上的体积力；p是流体相对压强；μ和μt分别是流体动力粘性系数和湍流粘度；δij是克罗内克函数；K是湍流动能。其中，μt可以采用SST K-Ω模型或者K-E模型进行求解，表示为：
上述公式(4)中，Ψ根据选择的湍流模型的不同分别代表K和Ω，或者K和E；σΨ是模型系数；GΨ是Ψ的生成项；YΨ是Ψ的耗散项。σΨ、GΨ和YΨ在不同模型中的表达式不同。
可选地，水相认为是不可压缩的，气相的可压缩性在小尺度模型或者在粗略计算中可以忽略不计，此时所述公式(1)～公式(4)闭合。但在大尺度或全尺度模型中必须考虑气相的可压缩性，此时补充气相状态方程用于求解气相密度变化，表示为：
F(p,Ta,ρa)＝0                                      公式(5)
上述公式(5)中，Ta为气相绝对温度；ρa是空气相的密度。
可选地，公式(5)为气相状态方程的一般形式，根据具体情况可选择理想气体状态、实际气体状态方程、热力学方程等。所述实际气体状态方程包括但不限于范德华方程、R-K方程、S-R-K方程、维里方程等。
上述公式(1)～(5)形成闭合，构建得到的流体运动方程，可用于求解流体区域的流速场、压强分布和密度分布。
其中，船体部分运动方程为牛顿第二定律，表示为：
上述公式(6)中，M是广义质量矩阵，形式为6阶对角矩阵，对应船体部分的6个运动自由度；和F分别是广义加速度矢量和广义力矢量。其中，作用在船体部分的力包括重力Gh、流体压力Fp、流体剪切力Fτ、转子反作用力Fr和系泊力Fm，分别表示为：
Gh＝mhg                             公式(7)

Fm＝(-cm,0,-cmsinh(um2))            公式(11)
Fm＝(-ksΔx cosφs,0,-(amsg+ksΔx sinφs))         公式(12)
上述公式中，mh是船体部分质量；g是重力加速度矢量；Sd是船体部分壁面；n是船体壁面面积单元的单位法向量；I是三阶单位张量；τ表示作用于船体壁面面积单元的剪切应力张量；表示转子的加速度矢量。
需要说明的是，系泊力Fm的表达式有两种，对应了系泊系统所处的不同状态：当与气动式波浪能转换装置直接相连的系泊系统部件(如系泊系统的弹性段)处于松弛状态时采用公式(11)，与气动式波浪能转换装置直接相连的系泊系统部件(如系泊系统的弹性段)处于拉紧并产生弹性形变的状态时采用公式(12)。
在Fm的表达式中，即公式(11)和公式(12)中，cm、um2是系泊系统悬链线模型参数；ks、ms和φs分别是拉紧的系泊系统部件的刚度系数、质量和其轴线与水平向的夹角；Δx是拉紧后的系泊系统部件的形变量；a是比例系数，与系泊系统自身的质量分布相关；g是重力加速度。
需要强调的是，系泊力Fm的表达式不仅适用于本申请实施例中的系泊系统，同样适用于传统的锚链系泊方式、以及采用锚链、浮球和链条进行系统的的系泊系统。
另外，上述系泊力Fm的表达式中只考虑了单条系泊系统部件与波浪能转换装置直接相连，且该系泊系统部件布置方向与x1方向重合。
若考虑多条系泊系统部件与装置直接相连时，需要根据Fm的表达式分别计算各条系泊系统部件产生的系泊力并叠加；若考虑系泊系统部件的其他布置方向时，需要将Fm的表达式得到的系泊力在笛卡尔坐标系O-x1x2x3中进行分解。
船体部分所受力矩是流体压力Fp、流体剪切力Fτ和转子反作用力Fr和系泊力Fm与各个力向量到船体部分质心的距离向量做叉积运算后相加得到，表示为：
Th＝rp×Fp+rτ×Fτ+rr×Fr+rm×Fm                    公式(13)
上述公式(13)中，rp、rτ、rr和rm分别是流体压力、流体剪切力、转子的反作用力和系泊力到船体部分质心的距离向量。
透平流道的一端开口与船体部分的气室连通，另一端开口与大气联通。透平整体固定在船体部分之上且跟随船体部分做6自由度运动，其运动方程为牛顿第二定律。同时，透平转子相对于船体部分绕转子的旋转轴单向转动，在局部坐标系O′-x1′x2′x3′下描述其运动，表示为：
上述公式(14)中，是透平转子沿x3′方向的转动惯量；是透平转子沿x3′方向的角加速度；n′d是由于转子叶片吸力侧与压力侧的压差而产生的沿x3′方向的驱动扭矩；n′g是发电机施加给透平转子的沿x3′方向的阻尼扭矩；nf′是透平转子转动时受到的沿x3′方向的轴承摩擦力矩以及其他阻力矩。
泄压系统为阈值可调的自动泄压系统，安装于船体部分的气室上方，其阀瓣的运动方程为牛顿第二定律。同时，阈值可调的自动泄压系统的阀瓣相对于船体部分沿x3′方向单自由度运动，表示为：
上述公式(15)中，mv是阈值可调的自动泄压系统的阀瓣的质量；是阀瓣沿x3′方向的加速度；Fp′是阀瓣受到的气室内气体的顶托力(沿x3′方向)；Gv′是阀瓣自身重力沿x3′方向的分量；kv是阀瓣与阀座之间的弹簧或其他弹性系统的弹性系数；和分别是弹簧或其他弹性系统的初始长度和当前时刻的实际长度，且一定满足Ff′是阀瓣运动时受到的沿x3′方向的阻尼力，需要说明的是，在阀瓣打开的过程中Ff′>0，在阀瓣关闭的过程中Ff′<0；FN′是阀瓣受到的沿x3′方向的支持力。
当阀瓣关闭且气室内压强小于等于自动泄压系统的阈值时，气室压强不足以驱动阀瓣运动，此时阀瓣相对于局部坐标系O′-x1′x2′x3′静止，其加速度为0，公式(15)中的Ff′＝0，而Fp′、Gv′和FN′达到平衡；一旦当气室内压强大于自动泄压系统的阈值时，阀瓣开始打开，此时公式(15)中FN′＝0；之后随着的增大和/或Fp′的减小，阀瓣开始关闭，直至
需要说明的是，上述公式(15)中的可以根据实际海况进行调整，达到阈值可调的自动泄压的效果，表示为：
上述公式(16)中，H是波高；分别为的m个可选择的调整值。
优选地，考虑到在实际的气动式波浪能转换装置的设计过程中可靠性往往是最重要的，频繁调整自动泄压系统的阀瓣与阀座之间的弹簧或其他弹性系统的初始长度不利于装置整体的可靠性，因此公式(16)中m的取值建议为m＝2，或m＝3，即在装置面临可靠性挑战最严重的海况时，适当调整泄压系统的阈值以保证整体装置的安全运行；在其他较安全工况时，自动泄压系统的阈值保持不变。但若只是考虑阈值可调的自动泄压系统的数学模型，此处不对公式(16)中的m进行限制，甚至可表示为H的连续函数。
可选地，若是从数学模型的角度实现阈值可调的自动泄压系统的功能，也可以通过调整公式(15)中的kv。
可选地，当公式(15)中所述的和kv固定不变时，对应的自动泄压系统可以是阈值固定的自动泄压系统。
发电组件可以为直驱发电机，发电机转子与透平转子同轴相连且具有完全相同的旋转角速度。发电机的主力矩由透平转子提供，发电机的阻力矩包括发电机转子运行时的空气阻力、机械摩擦和电磁阻力。同时，发电机将施加给透平转子一个阻尼力矩n′g。n′g与发电机转子的转速有关，即与透平转子的转速有关，表示为：
n′g＝F(ω′R)                                     公式(17)
系泊系统的控制方程为悬链线方程或者胡克定律，分别对应了系泊系统的链条段和弹性段处于松弛状态和处于拉紧状态。悬链线方程表示为：
x1m＝amum+bmsinh(um)+αm                      公式(18)
上述公式(18)和公式(19)中，x1m是悬链线线单元的x1方向坐标；x3m是悬链线线单元的x3方向坐标；αm和βm是积分常量，取决于悬链线两个端点的位置和悬链线质量；um是悬链线曲线参数；am和bm是模型参数。
其中，am、bm和um的表达式分别为：

sinh(um)＝tan(φm)                                 公式(23)
上述公式(20)-公式(23)中，λ0m和Leq分别是无作用力条件下悬链线的单位长度质量和松弛长度；Km是悬链线刚度；um1和um2分别是悬链线与海床连接点、与气动式波浪能转换装置连接点的um值；φm是悬链线曲线倾角。
当系泊系统的链条段或弹性段处于松弛状态时，悬链线对装置的系泊力表示为：
Fm＝(-cm,0,-cmsinh(um2))                       公式(24)
当系泊系统的链条段或弹性段处于拉紧状态时，其对装置的系泊力根据胡克定律求解，表示为：
Fm＝(-ksΔx cosφs,0,-(amsg+ksΔx sinφs))         公式(25)
需要说明的是，当所述的系泊系统包括浮球时，还需要考虑浮球的运动方程。浮球运动的控制方程为牛顿第二定律，作用在浮球上作用力包括自身重力、流体压力、流体剪切力以及两侧的系泊力。
数学模型边界包括整体计算域的入口边界、出口边界、底部边界、顶部边界、侧壁边界、流固交界面(流体与船体部分、透平以及浮球之间)以及气液交界面(水相和气相之间)。
入口边界的边界条件设置为速度入口，入口边界处水相的速度考虑波速和水流流速，入口边界处气相的速度考虑为风速，表示为：
上述公式(26)中，uw1和uw3是根据波浪理论求解得到的波浪沿x1方向和x3方向的速度；uc是水流流速；uwind是风速；ζ是水相和气相交界面的x3坐标。
可选地，入口处的波速的时空分布可以根据微幅波理论理论求解，也可以根据高阶斯托克斯波理论、不规则波理论或其他波浪理论求解。水流流速和风速可以考虑其空间分布以及时间变化，即uc＝uc(x1,x2,x3,t)，uwind＝uwind(x1,x2,x3,t)。
出口边界的边界条件设置为压力出口，具体压力分布不作限制，比如出口边界处水相的压力分布满足水相静压分布，出口边界处气相的压力为0，表示为：
上述公式(27)中，ρw是水相密度。
底部边界的边界条件设置为无滑移壁面。所述无滑移壁面指边界上的流体单元和结构单元所受作用力和速度的值相等，表示为：
上述公式(28)中，us是边界上结构单元的速度矢量；u是边界上流体单元的速度矢量；ps边界上结构单元受到的流体作用力矢量；p是边界上流体单元受到的结构反作用力矢量。需要特别说明的是，对于底部边界，us＝u＝0。
顶部边界的边界条件设置为压力出口。所述整体计算域高度足够高，水相无法溅射到顶部边界，因此顶部边界只有气相穿越。顶部边界处的压力分布为0，即自由出流。
侧壁边界的边界条件设置为无滑移壁面，表示为公式(28)。需要特别说明的是，对于侧壁边界，us＝u＝0。
流固交界面的边界条件设置为无滑移壁面，表示为公式(28)。
气液交界面处水相和气相互不相溶，气液交界面所在区域的流体控制体积中，水相和气相共享速度场和压力场，其等效流体密度和动力粘度表示为：
上述公式(29)中，γ是水的体积分数，取值范围是0≤γ≤1；μw和μa分别是水相和气相的动力粘度。
所述数学模型初始条件是指时间t＝0时计算域内流体、船体部分、透平转子、系泊系统的浮球的运动情况。初始时刻气动式波浪能转换装置的船体部分、透平转子和浮球的六自由度位移和速度均为0，波、流、风传播至气动式波浪能转换装置的迎浪面之前的某一位置处。
可选地，为节省计算时间，初始条件可以设置为风、浪、流刚好传播至气动式波浪能转换装置的迎波侧前方。
S902，对数学模型进行求解运算，得到波浪能转换装置的评价指标值。
按照预设的求解算法对数学模型进行求解运算，获取数学模型的运算结果，接着将运算结果作为波浪能转换装置在初始条件下的真实运行结果，并以此评估波浪能转换装置的发电能力指标值和可靠性指标值，作为波浪能转换装置的评价指标值。
需要说明的，评价指标值除了包括波浪能转换装置中的发电能力指标值和可靠性指标值以外，还可以包括其他评价参数，以表征波浪能转换装置在多个维度的性能，对此，本申请实施例不作限制。
本申请实施例中，针对波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程，接着对数学模型进行求解运算，得到波浪能转换装置的评价指标值。该方法中，通过模拟波浪能转换装置中的运动特性，综合考虑了装置各级能量转换阶段以及各级能量转换阶段之间的相互作用，以提升波浪能转换装置较为准确的发电能力、可靠性等方面的评估，为波浪能转换装置在转换效率、可靠性等多个维度提供了优化方向。
为尽可能模拟真实场景下波浪能转换装置的运动特性，数学模型中的模拟方程在时间和空间上通常都是连续的。在此情况下，可以将数学模型的整体计算域划分成有限多个网格单元，通过数学原理将数学模型中的控制方程转化为连续网格单元节点上待求函数值之间关系的离散方程，然后对每个网格单元进行质量、动量和能量守恒方程的求解。
在一个示例性的实施例中，如图10所示，对数学模型进行求解运算，得到波浪能转换装置的评价指标值，包括步骤S1001，S1002和S1003。
S1001，对数学模型进行离散化处理，得到数值模型，其中离散化处理包括空间离散化处理和时间离散化处理。
对获取数值模型的步骤进行细分，可以包括：建立一套高质量网格、确定数值求解方式以及建立合理可行的交界面条件三个步骤。本申请实施例中，建立一套高质量网格的目的在于将数学模型在空间上作离散化处理；确定数值求解方式的目的在于将离散化后的数学模型在时间上作离散化处理；并且考虑到网格建立过程中交界面连接的两个子区域在交界面附近的网格大小保持基本一致，还需要建立合理可行的交界面条件。
首先，建立高质量网格包括：确定数值求解区域、确定网格类型、确定网格加密准则、确定网格过渡准则、控制网格质量和确定网格数量六部分内容。
具体地，步骤a：确定数值求解区域。
本申请实施例中，数值求解区域确定为大小为12λ×8b×2hw的数值波浪水槽。其中，λ是波长，b是波浪能转换装置的宽度，hw是水深。
在其中一实施例中，波浪能转换装置迎浪壁面到数值波浪水槽入口边界的距离为5λ。
可选的，数值求解区域的大小以及装置在数值求解区域中所处的位置可以根据实际情况适当调整。
步骤b：确定网格类型。
本申请实施例中，网格结构确定为六面体网格，但在边界位置处六面体网格的一个或多个角被切割从而形成了多面体网格。
可选的，网格结构也可以采用四面体网格或者六面体网格与四面体网格的组合，但由于采用四面体网格结构时对应的网格数量更加庞大，数值求解成本更高，而且求解精度相对更低，因此难以有效适应复杂的气动式波浪能转换装置全系统耦合模型的求解。
步骤c：确定网格加密准则。
本申请实施例中，包括但不限于在模型边界(包括数值波浪水槽的入口边界、出口边界、底部边界、顶部边界、侧壁边界以及流固交界面和气液交界面)、船体部分的L型流道区域、透平流道区域、船体部分运动涉及的区域、系泊系统的浮球运动涉及的区域、阈值可调的自动泄压系统的阀瓣运动涉及的区域进行网格加密。具体地，为保证波序列在数值波浪水槽中传播的可靠性，气液交界面加密区域的高度为1.5H～2.0H，其中H是波高，该区域网格尺寸满足透平流道区域的网格需要更加精细化，尤其是转子叶片和导流叶片所分布的区域，应保证转子叶片之间至少分布有6层网格。特别地，转子叶片顶端与透平流道内壁之间存在一个厚度很小的间隙，该间隙的泄流效应对透平特性有着重要影响，因此为保证比较准确地刻画叶端间隙的流动特性，在该区域的厚度方向上应至少分布有2～3层网格。
需要说明的是，为保证数值求解结果的可靠性，上述气液交界面加密区域、透平流道区域和叶端间隙的网格加密准则应严格执行。
步骤d：确定网格过渡准则。
在其中一实施例中，本申请实施例中，数值求解区域分布有不同尺寸的网格，相邻尺寸的网格间的过渡层至少为2～3层。
步骤e：控制网格质量。
本申请实施例中，应严格控制网格质量，确保数值求解区域所有网格质量高于预设最小网格质量。
可选地，预设最小网格质量可选取为0.05。
步骤f：确定网格数量。
本申请实施例中，根据所述步骤a～步骤e建立了一套高质量网格。进一步地，通过网格收敛性分析确定最终的网格数量。
在其中一实施例中，网格收敛性准则选择为0.5％～1.0％，即随着网格数量的继续增加，采用所述装置从浪至电全系统耦合模拟方法得到的船体部分运动、气室压强、冲击式空气透平转子转速、锚链力等物理量的变化均不超过0.5％～1.0％，此时认为满足网格收敛性要求。
需要说明的是，考虑不同的水动力条件、网格加密准则、网格过渡准则以及网格收敛性准则，最终确定的网格数量也会存在较大的差异。研究表明，严格满足所述步骤a～步骤f的要求时所建立网格数量不少于450万。
在构建好网格的情况下，确定数值求解方式包括确定数值方法和确定求解算法。
本申请实施例中，对于数学模型中的流体控制方程，确定对应的离散方式为有限体积法。具体的，有限体积法是指将流体控制方程在每一个网格控制体积和一定的时间区间内对空间和时间作积分，从而得出一组离散方程。基于有限体积法，公式(1)和公式(2)的离散形式表示为：
上述公式(30)和公式(31)中，V是控制体积；A是控制体积的表面；ni是控制体积表面单位法向量n在xi方向的分量；Su和su是源项。
数值求解流体运动的离散方程时，采用SIMPLE算法耦合压强和流速，采用二阶隐式格式处理时间项，采用高斯最小二乘法处理梯度项，采用二阶迎风格式处理对流项，采用HRIC算法捕捉自由液面，采用全y+壁面处理法来预测壁面边界层的流动和湍流问题。所述全y+壁面处理法是一种混合处理方法，即对精细网格采用低y+壁面处理，对粗糙网格采用高y+壁面处理。
对于船体部分、冲击式空气透平的转子、阈值可调的自动泄压系统的阀瓣以及系泊系统的浮球的控制方程，采用时域逐步积分法离散求解，比如稳定性较好的二阶精度的梯形格式，表示为：
上述公式(32)-公式(34)中，M-1是广义质量矩阵M的逆矩阵；v(t-Δt)，和x(t-Δt)分别是(t-Δt)时刻船体部分、冲击式空气透平的转子、阈值可调的自动泄压系统的阀瓣或者系泊系统的浮球的广义速度、广义加速度和广义位移矢量；Δt是时间步。
在其中一实施例中，所述时间步选择为Δt＝(1/2000)T～(1/10000)T，其中T是波浪周期。时间步的大小主要与网格尺寸与透平转子转速有关，一般地，透平转子转速越高，所选择的时间步越小。进一步地，通过时间步收敛性分析确定最终的时间步大小。
建立合理可行的交界面条件包括计算区域划分以及各区域之间交界面设置。
本实施例中，整体数值求解区域划分为五个子区域，分别为代表整个数值波浪水槽的背景区域、包含气动式波浪能转换装置船体部分和冲击式空气透平但不包括透平转子区域的重叠区域1、包含阈值可调的自动泄压系统的重叠区域2、包含浮球的重叠区域3和透平转子所在的转子区域，其中背景区域为静止区域，重叠区域1、重叠区域2、重叠区域3和转子区域均为运动区域。
可选的，若装置没有安装自动泄压系统或者阈值可调的自动泄压系统的阀瓣始终处于关闭状态，此时不需要设置重叠区域2；若装置安装多个自动泄压系统，此时对应多个独立的重叠区域2(可以记为重叠区域2-1，重叠区域2-2，……)。
可选的，若装置的系泊系统采用传统的锚链系泊方式，即链条一端与锚连接并固定在海床上，另一端固定在装置的船体部分上，此时不需要设置重叠区域3；若装置的系泊系统包含多个浮球，此时对应多个独立的重叠区域3(可以记为重叠区域3-1，重叠区域3-2，……)。
本申请实施例中，上述背景区域与重叠区域1之间的交界面采用重叠网格交界面；上述背景区域与重叠区域3之间的交界面采用重叠网格交界面；上述重叠区域1与重叠区域2之间的交界面采用重叠网格交界面；上述重叠区域1与转子区域之间的交界面采用内部原位交界面；其他各子区域之间不存在直接的数据交互，也不需要设置交界面条件。
需要说明的是，上述重叠网格交界面和内部原位交界面实现了物理上连通的两个子区域之间的数据交互，在建立网格的过程中应考虑上述交界面连接的两个子区域在交界面附近的网格大小保持基本一致。
S1002，基于数值模型，求解波浪能转换装置的时程曲线，时程曲线包括波浪能转换装置运动响应和动力特性与时间的对应关系。
在一个示例性的实施例中，如图10所示，基于数值模型，求解波浪能转换装置的时程曲线的步骤，包括步骤S1101，S1102和S1103。
S1101，根据预设时间步对模拟时间段进行划分，确定多个时刻。
其中，时间步Δt的大小主要与网格尺寸与透平转子转速有关，一般地，透平转子转速越高，所选择的时间步越小。进一步地，通过时间步收敛性分析确定最终的时间步大小。通常情况下，Δt＝(1/2000)T～(1/10000)T，其中T是波浪周期。
以模拟时间段为3min、预设时间步为0.001s为例，确定预设时间段的第0.001s、0.002s、0.003s、...，3min共180000个时刻。
S1102，获取数值模型在每一时刻对应的运动响应值。
对于多个时刻中的任一时刻，即对于每一时刻，按照预设的迭代策略，对数值模型进行迭代求解，直至数值模型满足预设的收敛条件，得到每一时刻的运动响应值。
请参见图12，图12为一个本申请实施例提供的波浪能转换装置从浪至电全系统耦合模拟方法的迭代求解流程，包括以下步骤S1201至S1209。
S1201，获取重叠网格交界面和内部原位交界面处的信息。
S1202，迭代求解流体运动方程。
S1203，获取流体区域的速度场、压强场、密度场信息。
对气动式波浪能转换装置的船体部分、冲击式空气透平、阈值可调的自动泄压系统、系泊系统的浮球等部件表面受到的流体压力和切应力进行积分得到装置各部分受到的作用力和力矩。
S1204，判断流体区域的速度场、压强场和密度场是否均达到收敛条件。
若未达到收敛条件则继续迭代求解流体运动方程，则返回S1002，直至达到收敛条件。
S1205，若是，则采用二阶精度的梯形格式求解船体部分、冲击式空气透平的转子、阈值可调的自动泄压系统的阀瓣、系泊系统的浮球的运动状态。
S1206，更新重叠网络。
具体的，根据求解结果更新重叠区域1、重叠区域2、重叠区域3和转子区域位置。
S1207，获取当前时间步的运动响应值。
S1208，判断是否完成所有时间步的计算。
S1209，若是，则获取当前时间步的运动响应值。
若否，则继续进行下一个时间步的迭代计算，直至获取所有时刻的运动响应值。
进一步地，获取当前时刻气动式波浪能转换装置的运动响应和动力特性。所述运动响应和动力特性包括但不限于船体部分、系泊系统的浮球在笛卡尔坐标O-x1x2x3下6个运动自由度方向上的受力情况、加速度、速度和位移情况；包括系泊系统受力情况；包括阈值可调的自动泄压系统的阀瓣的启闭状态；包括冲击式空气透平转子在局部坐标系O′-x1′x2′x3′下的受力情况和转动情况(也是直驱发电机转子的转动情况)；包括自由液面分布情况，尤其是L型流道内水柱高程在局部坐标系O′-x1′x2′x3′下的空间分布情况；包括流体域水相和气相的压强、速度、密度分布情况，尤其是L型流道内的气室压强分布情况、冲击式空气透平流道内的流速分布情况。
进一步地，获取当前时刻气动式波浪能转换装置的水动力输入功率、气动功率、透平转子机械功率以及装置最终的输出功率。所述水动力输入功率Pin,t、气动功率Ppt、透平转子机械功率Prt以及装置最终的输出功率Pout,t表示为：
Pin,t＝Sωb                                               公式(35)
Ppt＝ΔptQt                                               公式(36)
Prt＝n′dtω′Rt                                               公式(37)
Pout,t＝n′gtω′Rt                                             公式(38)
上述公式中，Sω是入射波和水流叠加作用下的单宽能流密度；Δpt是当前时刻的气室压强；Qt是当前时刻的气室体积流量；n′dt和n′gt是当前时刻局部坐标系O′-x1′x2′x3′下透平转子受到的驱动力矩和发电机施加给透平转子的阻尼力矩；ω′Rt是当前时刻在局部坐标系O′-x1′x2′x3′下透平转子(以及发电机转子)的转速。
可选地，所述入射波可以考虑规则波(包括微幅波、高阶斯托克斯波)、不规则波等，对应的Sω的表达式也不相同。
S1103，根据每一时刻以及每一时刻对应的运动响应值，构建时程曲线。
以各时刻为横轴，各时刻对应的运动响应值为纵轴，构建波浪能转换装置在预设时间段的时程曲线。
S1003，根据时程曲线，获取波浪能转换装置的评价指标值。
根据波浪能转换装置的的运动响应和动力特性的时程曲线，计算发电能力指标值和可靠性指标值等方面的评价指标值。
其中，发电能力指标值的表达式为：
上述公式(39)中，和分别是装置的平均水动力性能、平均透平性能、平均发电机性能以及平均整体性能，对应的表达式如下：
上述公式中，和分别是平均入射波功率、平均气动功率、平均转子机械功率和平均输出功率(即平均发电功率)；t0是数值模拟达到动态平衡阶段的时间，在不同的算例中取值有所不同；n是数据平均化时选定的数据长度对应的波周期个数，通常取4-8之间的整数。
需要说明的是，平均水动力性能也可以表征为波浪能转换装置的俘获宽度比，且的计算结果可以超过100％。
其中，可靠性指标值是用于评价波浪能转化装置在特定海洋环境下具备持续正常工作能力的指标参数。当模拟时间段内透平转子的转速、系泊系统的链条段和/或弹性段中的系泊力、船体部分液体流道的壁面受到的压差力(即壁面内外侧受到的压力之差)等参数中的一个或多个长时间超过对应参数的额定上限时，将严重影响波浪能转化装置的可靠性指标值。
本申请实施例中，发电能力指标值越大，表征波浪能转换装置的能量转换效率越高；可靠性指标值越大，表征波浪能转换装置就越可靠。在实际场景中，同时计算波浪能转化装置的发电能力指标值和可靠性指标值，并在可靠性指标值满足实际需求的情况下，尽量提高发电能力指标值。
在一种场景中，可靠性指标值可以是两个离散的数值中的其中一个，例如0和1中的0或者1。在此情况下，可靠性指标值为0表征波浪能转化装置不可靠，可靠性指标值为1表征波浪能转换装置可靠。
本申请实施例中，可以根据物理参数(包括但不限于转速、系泊力和压差力)是否超过对应参数的额定上限确定可靠性指标值：若其中一个物理参数超过对应参数的额定上限，意味着波浪能转换装置处于不安全的运行状态，此时则确定可靠性指标值为0；若所有物理参数均未超过对应参数的额定上限，意味着波浪能转换装置处于安全可靠的运行状态，则确定可靠性指标值为1。
以物理参数为发电组件的转速，且转速的额定上限是700转/分钟为例，若波浪能转化装置中的发电组件在模拟过程中的转速超过700转/分钟，则确定可靠性指标值为0；若该发电组件在模拟过程中的转速均未超过700转/分钟，则确定可靠性指标值为1。
在一种场景中，可靠性指标值可以是[0，1]区间内的任一数值，例如0.1、0.5、0.9等。在此情况下，可靠性指标值越接近0，表征波浪能转化装置越不可靠，可靠性指标值越接近1，表征波浪能转换装置越可靠。
本申请实施例中，可以根据物理参数(包括但不限于转速、系泊力和压差力)超过对应参数额定上限的持续时间确定可靠性指标值，且持续时间与可靠性指标值呈负相关，即物理参数超过对应参数额定上限的持续时间越长，可靠性指标值越低；持续时间越短，可靠性指标值越高。这样设置的目的在于，在实际运行场景中，波浪能转换装置中的部分硬件具备一定的抗压性，例如，发电组件允许短时间的超负载运行。
仍以物理参数为发电组件的转速，且转速的额定上限是700转/分钟为例，设置初始可靠性指标值为1，在波浪能转化装置中的发电组件的转速超过700转/分钟的基础上，进一步监测转速超过700转/分钟的持续时间tbeyond，则可靠性指标值nR表示为：
nR＝1-f(tbeyond)                                          公式(43)
上述公式(43)中，f(tbeyond)表示与持续时间tbeyond呈正相关的函数，且其取值范围是[0，1]。最简单的一个例子，f(tbeyond)与tbeyond在一定范围内呈线性关系，即
上述公式(44)中，T0表示发电组件的转速允许超过其额定上限的最大持续时间。
进一步地，还可以通过改变水动力入射条件、发电机特性、阈值可调的自动泄压系统的阈值、系泊方式等参数，重复上述图8-图10所示的评价方法的步骤，以获取不同条件下气动式波浪能转换装置的发电能力、可靠性等方面的评价指标随上述水动力入射条件、发电机特性、阈值可调的自动泄压系统的阈值、系泊系统等参数的变化情况，深度揭示气动式波浪能转换装置的能量转换机理。
本申请实施例中，通过对数学模型进行离散化处理，得到易于计算的数值模型，接着根据数值模型构建时程曲线，对波浪能转换装置的动力特性进行可视化，使得基于时程曲线确定的评价指标值更贴切波浪能转换装置的实际运行状态。
在一个示例性的实施例中，提供了一种波浪能转换装置的模拟方法，包括以下步骤S1301至S1305。
S1301，建立波浪能转换装置的全系统耦合的数学模型。
S1302，建立波浪能转换装置的全系统耦合的数值模型。
S1303，基于数值迭代求解，获取波浪能转换装置的运动响应和动力特性。
S1304，构建运动响应和动力特性的时程曲线。
S1305，根据时程曲线，获取波浪能转换装置的评价指标值。
可选的，优化波浪能转换装置的结构参数等其他细节设计，重复执行上述S1301～S1305，以获取不同条件下波浪能转换装置的评价指标，并根据各结构参数和各结构参数对应的评价指标值，揭示波浪能转换装置的能量转换机理，为提升波浪能转换装置的发电能力、可靠性等提供优化方向。
本申请实施例中，提供了一种全面完整的波浪能转换装置从浪至电全系统耦合的模拟方法，以填补气动式波浪能转换装置缺乏可靠的设计优化理论的空白。
在一个示例性的实施例中，提供了一种波浪能转换装置的评价方法，包括以下步骤：
(1)针对波浪能转换装置构建数学模型。
其中，数学模型为模拟波浪能转换装置运动特性的模拟方程。
(2)对数学模型进行离散化处理，得到数值模型。
其中，离散化处理包括空间离散化处理和时间离散化处理。
(3)根据预设时间步对模拟时间段进行划分，确定多个时刻。
(4)对于多个时刻中的任一时刻，按照预设的迭代策略，对数值模型进行迭代求解，直至数值模型满足预设的收敛条件，得到各时刻下的运动响应值。
(5)根据各时刻以及各时刻对应的运动响应值，构建时程曲线。
其中，时程曲线用于表征波浪能转换装置运动响应和动力特性与时间的对应关系。
(6)根据时程曲线，获取波浪能转换装置的评价指标值。
其中，评价指标值包括波浪能转换装置中的发电能力指标值和可靠性指标值。
本申请实施例中，针对波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程，接着对数学模型进行求解运算，得到波浪能转换装置的评价指标值。该方法中，通过模拟波浪能转换装置中的运动特性，综合考虑了装置各级能量转换阶段以及各级能量转换阶段之间的相互作用，以提升波浪能转换装置较为准确的发电能力、可靠性等方面的评估，为波浪能转换装置在转换效率、可靠性等多个维度提供了优化方向。
另外，需要强调的是，本申请实施例所提供包括构建控制方程、数值求解等步骤在内的的优化方法具有普适性，不仅适用于本申请实施例提出的波浪能转换装置的性能预测，同样适用于其他所有形式的气动式波浪能转换装置的性能预测。例如没有安装自动减压系统的装置、运动自由度受限的装置、包括多个气动式波浪能转换装置之间固定连接形成整体的波浪能发电装置，除此之外，还适用于船体部分为后弯管式、前弯管式、中心管式的波浪能发电装置；空气透平为径向冲击式空气透平、轴流冲击式空气透平、Wells透平等其他类型的波浪能发电装置；系泊方式采用单独的锚链系泊方式、锚链+浮球+链条的波浪能发电装置；泄压系统为阈值固定的波浪能发电装置；包括较宽范围的扭矩-转速关系的发电机的波浪能发电装置。唯一需要注意的是，该模拟方法中气动式波浪能转换装置采用导流叶片固定的冲击式空气透平，而对于导流叶片可以主动/被动转动或滑动的冲击式空气透平已被证明在实际海洋环境中可靠性非常低，运行极其短暂的时间就会遭到破坏，因此此处不做考虑。
应该理解的是，虽然如上所述的各实施例所涉及的流程图中的各个步骤按照箭头的指示依次显示，但是这些步骤并不是必然按照箭头指示的顺序依次执行。除非本文中有明确的说明，这些步骤的执行并没有严格的顺序限制，这些步骤可以以其它的顺序执行。而且，如上所述的各实施例所涉及的流程图中的至少一部分步骤可以包括多个步骤或者多个阶段，这些步骤或者阶段并不必然是在同一时刻执行完成，而是可以在不同的时刻执行，这些步骤或者阶段的执行顺序也不必然是依次进行，而是可以与其它步骤或者其它步骤中的步骤或者阶段的至少一部分轮流或者交替地执行。
为进一步验证本申请实施例提供的波浪能转换装置的性能参数，本申请还进行了多组对比实验，研究表明：
(1)本申请实施例提出的空气透平(径向入流的冲击式空气透平)的稳态效率最高值为68％，周期平均效率最高值为63％，相较于导流叶片固定的轴流冲击式空气透平的稳态效率最高值和周期平均效率最高值分别提高了35.8％和31.5％。
具体结果参见图14，图14为采用本申请实施例的模拟方法获取的透平稳态效率的曲线对比图。图14中，S1为本申请实施例提供的径向冲击式空气透平的稳态效率曲线，S2为轴向冲击式空气透平的稳态效率曲线，由图13可知，在流动系数相同的情况下，本申请所提供的径向冲击式空气透平的稳态效率大于轴向冲击式空气透平的稳态效率。
(2)在规则波条件下，采用本申请实施例提出的新型冲击式空气透平的气动式波浪能转换装置的平均整体性能最高为62％，相较于采用导流叶片固定的轴流冲击式空气透平的气动式波浪能转换装置的最高平均整体性能提高了20.6％，证明了本申请实施例所提出的新型冲击式空气透平的适用性和高效性。
请参见图15，图15为波浪能转换装置在规则波条件下平均发电性能的情况下，波浪能转换装置的平均水动力性能平均透平性能以及平均整体性能的曲线示意图。
(3)在不规则波条件下，采用本发明提出的新型冲击式空气透平的气动式波浪能转换装置的平均整体性能最高为35％，相较于采用导流叶片固定的轴流冲击式空气透平的气动式波浪能转换装置的最高平均整体性能提高了19.8％，再次证明了本申请实施例提出的新型冲击式空气透平的适用性和高效性。
(4)在相同水动力条件下，相较于采用单独的锚链系泊方式、采用锚链+浮球+链条的系泊方式的气动式波浪能转换装置，采用本申请实施例提出的新型系泊系统(一种适用于气动式波浪能转换装置的锚链-浮球-弹性部件的增效宽频系泊系统)的波浪能转换装置的平均整体性能均有所提高，最大分别提高了12.5％和3.2％；同时，采用本申请实施例提出的新型系泊系统的气动式波浪能转换装置的高效俘能区间相较于采用单独的锚链系泊方式、采用锚链+浮球+链条的系泊方式的气动式波浪能转换装置的高效俘能区间分别拓宽了46.8％和10.5％，证明了本申请实施例提出的新型系泊系统在增效宽频和提高装置的整体发电能力方面的有效性。需要说明的是，此处规定水动力性能大于80％时对应的波浪频率范围为高效俘能区间。
(5)相同水动力条件下(高海况条件下)，采用本申请实施例提出的新型系泊系统的气动式波浪能转换装置的最大系泊力相较于采用单独的锚链系泊方式、采用锚链+浮球+链条的系泊方式的气动式波浪能转换装置的最大系泊力均有所降低，最大分别降低了212％和156％，证明了本申请实施例提出的新型系泊系统在提高装置的可靠性方面的有效性。
(6)在常规海况(本申请实施例中取波高1m，对应3级海况)、高海况(本申请实施例中取波高4m，对应5～6级海况)和极端海况(本申请实施例中取波高12m，对应8级海况)条件下，安装本发明新提出的阈值可调的自动泄压系统的气动式波浪能转换装置的气室压强、透平转子转速的最大值均得到了良好的控制。而且，高海况相较于常规海况，入射波能量提高了20余倍，船体部分L型流道的壁面受到的最大压差力最高只增加了3.05倍；极端海况相较于常规海况，入射波能量提高了300余倍，船体部分L型流道的壁面受到的最大压差力只增加了2.1倍，证明了气动式波浪能转换装置本身的可靠性以及本发明提出的阈值可调的自动泄压系统在提高装置的可靠性方面的有效性。
(7)进一步地，研究结果表明，本申请实施例提供的波浪能转换装置六个自由度运动的固有频率各不相同，使得各自由度运动在流道内各自产生一个水柱振荡波，这些水柱振荡波产生叠加效应，从而拓宽装置频率响应宽度并增大了俘获宽度比，锚链浮球系泊系统系泊的装置纵荡运动对装置俘获宽度比的贡献最大，在不同海况下纵荡运动对俘获宽度比的贡献在总俘获宽度比占50％～95％。
综合上述实验研究表明，与现有技术提供的能量转换装置相比，本申请实施例提供的气动式波浪能转换装置，包括船体部分、冲击式空气透平、自动泄压减荷系统、发电机、系泊系统和其他系统/设备/部件。其中，气动式波浪能转换装置的径向入流的冲击式空气透平，兼具高可靠、高效、轴向和径向都比较紧凑的优点；阈值可调的自动泄压系统，可以根据实际海况远程手动调控或者自动调控，提高装置在高海况下的可靠性；锚链-浮球-弹性吸能部件的增效宽频系泊系统，兼具宽频增效、降低系泊系统中的最大受力的优点。
基于同样的发明构思，本申请实施例还提供了一种用于实现上述所涉及的评价方法的评价装置。该装置所提供的解决问题的实现方案与上述方法中所记载的实现方案相似，故下面所提供的一个或多个评价装置实施例中的具体限定可以参见上文中对于评价方法的限定，在此不再赘述。
在一个示例性的实施例中，如图16所示，提供了一种波浪能转换装置评价装置，包括：构建模块1601和运算模块1602。
构建模块1601，用于针对波浪能转换装置构建数学模型，数学模型为模拟波浪能转换装置运动特性的模拟方程。
运算模块1602，用于对数学模型进行求解运算，得到波浪能转换装置的评价指标值。
在一个示例性的实施例中，运算模块1602，包括离散处理单元、曲线构建单元和指标获取单元。
离散处理单元，用于对数学模型进行离散化处理，得到数值模型；离散化处理包括空间离散化处理和时间离散化处理。
曲线构建单元，用于基于数值模型，求解波浪能转换装置的时程曲线，时程曲线包括波浪能转换装置运动响应和动力特性与时间的对应关系。
指标获取单元，用于根据时程曲线，获取波浪能转换装置的评价指标值。
在一个示例性的实施例中，曲线构建单元，包括时刻划分子单元、响应获取子单元和时程构建子单元。
时刻划分子单元，用于根据预设时间步对模拟时间段进行划分，确定多个时刻。
响应获取子单元，用于获取数值模型在各时刻对应的运动响应值。
时程构建子单元，用于根据各时刻以及各时刻对应的运动响应值，构建时程曲线。
在一个示例性的实施例中，响应获取子单元，具体用于对于多个时刻中的任一时刻，按照预设的迭代策略，对数值模型进行迭代求解，直至数值模型满足预设的收敛条件，得到时刻下的运动响应值。
在一个示例性的实施例中，评价指标值包括波浪能转换装置中的发电能力指标值和可靠性指标值。
上述评价装置中的各个模块可全部或部分通过软件、硬件及其组合来实现。上述各模块可以硬件形式内嵌于或独立于计算机设备中的处理器中，也可以以软件形式存储于计算机设备中的存储器中，以便于处理器调用执行以上各个模块对应的操作。
在一个示例性的实施例中，提供了一种计算机设备，该计算机设备可以是终端，其内部结构图可以如图17所示。该计算机设备包括处理器、存储器、输入/输出接口、通信接口、显示单元和输入装置。其中，处理器、存储器和输入/输出接口通过系统总线连接，通信接口、显示单元和输入装置通过输入/输出接口连接到系统总线。其中，该计算机设备的处理器用于提供计算和控制能力。该计算机设备的存储器包括非易失性存储介质和内存储器。该非易失性存储介质存储有操作系统和计算机程序。该内存储器为非易失性存储介质中的操作系统和计算机程序的运行提供环境。该计算机设备的输入/输出接口用于处理器与外部设备之间交换信息。该计算机设备的通信接口用于与外部的终端进行有线或无线方式的通信，无线方式可通过WIFI、移动蜂窝网络、NFC(近场通信)或其他技术实现。该计算机程序被处理器执行时以实现一种波浪能转换装置评价方法。该计算机设备的显示单元用于形成视觉可见的画面，可以是显示屏、投影装置或虚拟现实成像装置。显示屏可以是液晶显示屏或者电子墨水显示屏，该计算机设备的输入装置可以是显示屏上覆盖的触摸层，也可以是计算机设备外壳上设置的按键、轨迹球或触控板，还可以是外接的键盘、触控板或鼠标等。
本领域技术人员可以理解，图17中示出的结构，仅仅是与本申请方案相关的部分结构的框图，并不构成对本申请方案所应用于其上的计算机设备的限定，具体的计算机设备可以包括比图中所示更多或更少的部件，或者组合某些部件，或者具有不同的部件布置。
在一个示例性的实施例中，提供了一种计算机设备，包括存储器和处理器，存储器中存储有计算机程序，该处理器执行计算机程序时实现上述各波浪能转换装置评价方法实施例中的步骤。
在一个实施例中，提供了一种非易失计算机可读存储介质，其上存储有计算机程序，计算机程序被处理器执行时实现上述各波浪能转换装置评价方法实施例中的步骤。
在一个实施例中，提供了一种计算机程序产品，包括计算机可执行指令，该计算机可执行指令被处理器执行时实现上述各波浪能转换装置评价方法实施例中的步骤。
需要说明的是，本申请所涉及的用户信息(包括但不限于用户设备信息、用户个人信息等)和数据(包括但不限于用于分析的数据、存储的数据、展示的数据等)，均为经用户授权或者经过各方充分授权的信息和数据，且相关数据的收集、使用和处理需要符合相关规定。
本领域普通技术人员可以理解实现上述实施例方法中的全部或部分流程，是可以通过计算机程序来指令相关的硬件来完成，所述的计算机程序可存储于一非易失性计算机可读取存储介质中，该计算机程序在执行时，可包括如上述各方法的实施例的流程。其中，本申请所提供的各实施例中所使用的对存储器、数据库或其它介质的任何引用，均可包括非易失性和易失性存储器中的至少一种。非易失性存储器可包括只读存储器(Read-Only Memory，ROM)、磁带、软盘、闪存、光存储器、高密度嵌入式非易失性存储器、阻变存储器(ReRAM)、磁变存储器(Magnetoresistive Random Access Memory，MRAM)、铁电存储器(Ferroelectric Random Access Memory，FRAM)、相变存储器(Phase Change Memory，PCM)、石墨烯存储器等。易失性存储器可包括随机存取存储器(Random Access Memory，RAM)或外部高速缓冲存储器等。作为说明而非局限，RAM可以是多种形式，比如静态随机存取存储器(Static Random Access Memory，SRAM)或动态随机存取存储器(Dynamic Random Access Memory，DRAM)等。本申请所提供的各实施例中所涉及的数据库可包括关系型数据库和非关系型数据库中至少一种。非关系型数据库可包括基于区块链的分布式数据库等，不限于此。本申请所提供的各实施例中所涉及的处理器可为通用处理器、中央处理器、图形处理器、数字信号处理器、可编程逻辑器、基于量子计算的数据处理逻辑器等，不限于此。
以上实施例的各技术特征可以进行任意的组合，为使描述简洁，未对上述实施例中的各个技术特征所有可能的组合都进行描述，然而，只要这些技术特征的组合不存在矛盾，都应当认为是本说明书记载的范围。
以上所述实施例仅表达了本申请的几种实施方式，其描述较为具体和详细，但并不能因此而理解为对本申请专利范围的限制。应当指出的是，对于本领域的普通技术人员来说，在不脱离本申请构思的前提下，还可以做出若干变形和改进，这些都属于本申请的保护范围。因此，本申请的保护范围应以所附权利要求为准。

Claims (19)

  1. 一种波浪能转换装置，包括：
    流体流道，用于将传递至所述流体流道的波浪能转换为气动能；
    能量转换系统，与所述流体流道连接，用于将所述流体流道转换得到的气动能转换为电能；包括空气透平，所述空气透平包括流道壁、两组导流叶片和一组转子叶片；各所述导流叶片的横截面的轮廓线包括一条椭圆弧段和一条直线段，且所述直线段沿所述直线段一端点处围绕所述旋转主轴的圆的切线方向布置；各所述转子叶片的轴向方向的截面的轮廓线，包括吸力侧为椭圆弧段，压强侧为圆弧段；每组导流叶片的数量为14-24；
    泄压系统，与所述流体流道连接，用于控制所述流体流道中的气室的压强；包括阀瓣、阀座、弹性单元、控制杆和连接管，所述阀瓣通过所述弹性单元与所述阀座连接；所述阀瓣还通过所述连接管与所述气室连接；所述控制杆与所述阀座固定连接，且所述控制杆分别与所述阀瓣和控制组件活动连接；所述控制杆为伸缩杆；所述阀瓣对应的开启阈值有多个，其中所述控制组件，部署在所述连接管表面，用于根据所述波浪能转换装置的海况，通过所述控制杆动态调整所述弹性单元的初始长度，以控制所述阀瓣对应的开启阈值；所述控制组件调整所述弹性单元的初始长度的调整长度有多个。
  2. 根据权利要求1所述的装置，其特征在于，对应于所述气室的压强超过所述开启阈值的情况，所述阀瓣处于开启状态；对应于所述气室的压强未超过所述开启阈值的情况，所述阀瓣处于关闭状态。
  3. 根据权利要求1或2所述的装置，其特征在于，所述能量转换系统包括空气透平和发电组件，所述空气透平与所述发电组件连接；
    所述空气透平，用于将所述流体流道转换得到的气动能转换为机械能；
    所述发电组件，用于将所述空气透平转换得到的机械能转换为所述电能。
  4. 根据权利要求3所述的装置，其特征在于，所述空气透平的转子转速与所述发电组件的转子转速相同。
  5. 根据权利要求3或4所述的装置，其特征在于，所述空气透平还包括旋转主轴和转子部；
    所述两组导流叶片的一组导流叶片均匀分布在所述流道壁的流道入口，且另一组导流叶片均匀分布在所述流道壁的流道出口；
    所述一组转子叶片沿围绕所述旋转主轴的周向均匀分布在所述空气透平的流道的中心区域的转子部上。
  6. 根据权利要求5所述的装置，其特征在于，所述转子叶片与所述导流叶片之间的流道壁的轴向方向的截面的轮廓线，包括一条90°的圆弧段和所述圆弧段两侧的直线段。
  7. 根据权利要求1-6任一项所述的装置，还包括一个或多个系泊系统；所述一个或多个系泊系统与所述波浪能转换装置的迎波侧连接。
  8. 根据权利要求7所述的装置，其特征在于，每一系泊系统包括一浮球，所述浮球通过至少一个弹性组件与所述波浪能转换装置的迎波侧连接。
  9. 根据权利要求1-8任一项所述的装置，其特征在于，所述流体流道包括互相连通的水平流道和垂直流道；所述垂直流道靠近所述波浪能转换装置的迎波侧设置，且所述水平流道的口门靠近所述波浪能转换装置的背波侧设置；所述水平流道的横截面面积与所述垂直流道的横截面面积相等；所述水平流道和所述垂直流道之间采用流线型流道连通。
  10. 根据权利要求9所述的装置，其特征在于，所述流体流道还包括多个隔板；各所述隔板垂直固定在所述水平流道和所述垂直流道的流道壁。
  11. 一种波浪能转换装置评价方法，包括：
    针对权利要求1-10中任一项所述的波浪能转换装置构建数学模型，所述数学模型为模拟所述波浪能转换装置运动特性的模拟方程；
    对所述数学模型进行求解运算，得到所述波浪能转换装置的评价指标值。
  12. 根据权利要求11所述的方法，其特征在于，所述对所述数学模型进行求解运算，得到所述波浪能转换装置的评价指标值，包括：
    对所述数学模型进行离散化处理，得到数值模型，其中所述离散化处理包括空间离散化处理和时间离散化处理；
    基于所述数值模型，求解所述波浪能转换装置的时程曲线，其中所述时程曲线包括所述波浪能转换装置运动响应和动力特性与时间的对应关系；
    根据所述时程曲线，获取所述波浪能转换装置的评价指标值。
  13. 根据权利要求12所述的方法，其特征在于，所述基于所述数值模型，求解所述波浪能转换装置的时程曲线，包括：
    根据预设时间步对模拟时间段进行划分，确定多个时刻；
    获取所述数值模型在每一时刻对应的运动响应值；
    根据每一时刻以及每一时刻对应的运动响应值，构建所述时程曲线。
  14. 根据权利要求13所述的方法，其特征在于，所述获取所述数值模型与每一时刻对应的运动响应值，包括：
    对于每一时刻，按照预设的迭代策略，对所述数值模型进行迭代求解，直至所述数值模型满足预设的收敛条件，得到每一时刻的运动响应值。
  15. 根据权利要求11-14任一项所述的方法，其特征在于，所述评价指标值包括所述波浪能转换装置中的发电能力指标值和可靠性指标值。
  16. 一种波浪能转换装置评价装置，包括：
    构建模块，用于针对权利要求1-10中任一项所述的波浪能转换装置构建数学模型，所述数学模型为模拟所述波浪能转换装置运动特性的模拟方程；
    运算模块，用于对所述数学模型进行求解运算，得到所述波浪能转换装置的评价指标值。
  17. 一种计算机设备，包括存储器和处理器，所述存储器存储有计算机程序，其特征在于，所述处理器执行所述计算机程序时实现权利要求11-15中任一项所述的方法的步骤。
  18. 一种非易失计算机可读存储介质，其上存储有计算机程序，其特征在于，所述计算机程序被处理器执行时实现权利要求11-15中任一项所述的方法的步骤。
  19. 一种计算机程序产品，包括计算机可执行指令，其特征在于，所述计算机可执行指令被处理器执行时实现权利要求11-15中任一项所述的方法的步骤。
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