CN112963293A - Wave energy device of oscillating floater swing wing turbine and design method thereof - Google Patents

Wave energy device of oscillating floater swing wing turbine and design method thereof Download PDF

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Publication number
CN112963293A
CN112963293A CN202110299473.6A CN202110299473A CN112963293A CN 112963293 A CN112963293 A CN 112963293A CN 202110299473 A CN202110299473 A CN 202110299473A CN 112963293 A CN112963293 A CN 112963293A
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swing wing
floater
wing turbine
turbine
blade
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CN112963293B (en
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周军伟
闫文辉
梅蕾
于东
郭彬
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Harbin Institute of Technology Weihai
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Harbin Institute of Technology Weihai
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    • 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
    • F03B13/16—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 using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem"
    • F03B13/20—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 using the relative movement between a wave-operated member, i.e. a "wom" and another member, i.e. a reaction member or "rem" wherein both members, i.e. wom and rem are movable relative to the sea bed or shore
    • 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
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • 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
    • F03B11/00—Parts or details not provided for in, or of interest apart from, the preceding groups, e.g. wear-protection couplings, between turbine and generator
    • F03B11/008—Measuring or testing arrangements
    • 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
    • F03B13/22—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 using the flow of water resulting from wave movements to drive a motor or turbine
    • 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
    • Y02E10/20—Hydro energy
    • 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

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  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Abstract

The invention relates to the technical field of wave energy acquisition and power generation devices, in particular to a wave energy device of an oscillating floater/oscillating wing turbine and a design method thereof The method can adapt to complex sea conditions, and has the advantages of high reliability, high energy conversion efficiency, high application value and the like.

Description

Wave energy device of oscillating floater swing wing turbine and design method thereof
Technical Field
The invention relates to the technical field of wave energy acquisition and power generation devices, in particular to a wave energy device of an oscillating floater/oscillating wing turbine, which has a simple structure, high reliability, high energy conversion efficiency and high application value, can adapt to complex sea conditions and is provided with a design method.
Background
As is well known, the world energy crisis is becoming more severe, and people have seen great attention in the ocean. Ocean accounts for 71 percent of the global surface area, and huge energy is stored, wherein wave energy is one of the main existing forms of ocean energy, has the advantages of huge reserves, cleanness, renewability and the like, and is considered as a new direction for solving the energy problem. The wave energy resources in China are considerable, the energy content of the wave energy is about 1.5 hundred million kW, the exploitable and utilizable amount is about 2300 to 3500 ten thousand kW, and the wave energy resources have very wide development prospects.
At present, the existing wave energy power generation devices are roughly of the types of oscillating float type, oscillating water column type, push pendulum type, nodding duck type, type, wave type and the like. Because the power part of wave energy power generation facility is by wave drive, therefore most have reciprocating motion's characteristic, be difficult to directly be connected with traditional generator, and reciprocating motion makes most power generation facility be in intermittent type operating condition, in addition, because the wave cycle is longer, the operating frequency of these devices is generally on the low side.
In view of the utilization of wave energy, the power generation by the wave energy is not needed to supply power for offshore land, and the power supply of an open sea ocean detection device is urgent at present. In order to ensure the reliability of the detection device, an oscillating float type wave energy power generation device is generally adopted. At present, a linear motor or a hydraulic device is generally adopted as an oscillating float type energy conversion mechanism, and the problems of poor sealing performance, low efficiency, difficulty in realization, poor reliability, low working frequency and the like exist.
Disclosure of Invention
The invention aims to solve the defects of the prior art and provide the wave energy device of the oscillating floater/swing wing turbine, which has the advantages of simple structure, high reliability, high energy conversion efficiency and high application value, can adapt to complex sea conditions and is provided, and the design method thereof.
The technical scheme adopted by the invention for solving the technical problems is as follows:
the wave energy device is characterized by comprising a floater, a long shaft, a universal coupling and a swing wing turbine assembly, wherein a power generation device is arranged in the floater, an input shaft of the power generation device extends out of the lower portion of the floater and is connected with the upper end of the long shaft through the universal coupling, the lower end of the long shaft is connected with the swing wing turbine assembly, at least one group of swing wing turbine assemblies is arranged, each swing wing turbine assembly comprises a main shaft, a hub and blades, the middle of the hub is fixedly connected with the main shaft, at least three connectors are arranged on the side face of the hub, the connectors are annularly distributed on the circumference of the hub and are elastically and rotatably connected with the hub through elastic pieces, the blades are fixedly connected with the connectors, and adjacent swing wing turbine assemblies are connected through the main shaft.
The wave energy devices are provided with two buoys, the two buoys in the two wave energy devices are connected through the connecting rod and the hinge, two ends of the connecting rod are respectively connected with the hinge, and the hinge is connected with the buoys to avoid the rotation of the buoys.
The side surface of the floater is connected with the platform through the connecting frame, one end of the connecting frame is connected with the platform through the hinge, and the other end of the connecting piece is connected with the floater through the hinge, so that the floater is prevented from rotating.
The main shafts between the adjacent swing wing turbine assemblies are connected through the universal coupling, and the swing wing turbine assembly at the lowest part is connected with the balancing weight, so that the swing wing turbine assemblies connected in series are in a tensioned state.
The floater adopts a spherical vertical cylinder with a frustum at the bottom or a hemispherical vertical cylinder at the bottom.
The blade adopts a straight wing, a wing shape or an inverted wing shape which is formed by directly stacking wing shapes, wherein the wing shapes are symmetrical wing shapes, thin wings, flat plates with inverted front and back radiuses and sharp rear edges, or wing shapes which are independently constructed by smooth curves.
A design method of a wave energy device of an oscillating floater/swing wing turbine is characterized by comprising the following steps:
sea state determination: determining the main wave period T and the wave height H of the local sea area, or estimating the main wave period T according to the wave height H, wherein the estimation method comprises the following steps: t =0.8 × 2 × π × sqrt (h), the wavelength λ is obtained from the wave period T, expressed as: λ = gT2/(2 π). g is the gravity acceleration, and g =9.8m/s is taken;
(II) determining a floater: the diameter D of the floater is related to the energy conversion efficiency of the floater, and can be 0.2 lambda-0.05 lambda, the draft depth D of the floater is also related to the energy conversion efficiency of the floater, and can be 0.2 lambda-0.05 lambda, under the design parameters, verification is carried out, the energy conversion efficiency eta of the floater can be guaranteed to reach 20%, eta =20% is obtained, and then the absorption power P of the floater can be calculated and obtained by matching with a proper swing wing turbineF=ηρg2H2DT/(32 pi), rho is the density of water;
(III) designing a main shaft and a hub in the swing wing turbine assembly: overall diameter D of the swing wing turbine assemblyTShould be as consistent as possible with float diameter, can be 0.5D ~2D, main shaft length L should be no less than wave height H, hub diameter D among swing wing turbine subassemblyhAnd the overall diameter DTThe ratio of (A) to (B) is 0.2-0.5;
(IV) designing blades in the swing wing turbine assembly: number of blades N in a swing wing turbine assemblyh2-10, according to the blade extension formula h = (D) of swing wing turbineT-Dh) 2, obtaining the blade extension, wherein the chord length c of the middle part of the blade is the intersection of the following two ranges, which are respectively limited by the blade extension and the wave height, and the two ranges are respectively (0.1H-0.5H) and (0.12H-0.3H); chord length c of blade roothLimited by the diameter of the hub, and has a value range of (pi D)h/Nh/8~πDh/Nh) The distance between the position of the blade mounting shaft and the front edge of the blade is less than 0.1 time of chord length, namely 0.1 c;
(V) working condition design of the swing wing turbine assembly: the angular velocity of the swing wing turbine is designed to be ω = JX 1.3H/T/(D)T+Dh) The unit rad/s and J are advancing speed coefficients, the value range is 5-15, and the pendulum is controlled according to the number of opposite pendulumHydrodynamic analysis of airfoil turbine blades to obtain a torque of a single swing airfoil turbine of M =0.069KTNhρH3(DT 2-Dh 2)/T2Designing a generator according to the above, wherein KT is the stress coefficient of the blade and is a function of a speed advance coefficient J, and is represented as KT (J) = -0.0068J2+0.269J-0.337, the power of a single oscillating wing turbine is PT= M ω, the power absorbed by the floats is partially lost when converted into the power of the oscillating-wing turbines, the conversion efficiency is about 80%, and the number of the oscillating-wing turbines N is then countedTIs 0.8PF/PTAnd (6) taking the whole. If the number of the tandem turbines is too large, so that the practical engineering is difficult to realize, the number of the tandem turbines can be reduced by increasing the diameter of the swing wing turbines and increasing the number of blades of each turbine;
(VI) designing a connecting head between the blade and the hub: the torsional spring stiffness coefficient of the connecting head between the blade and the hub can be designed to be K = 0.275K' rho H3hc/T2And k' is a dimensionless spring stiffness ratio, the value of which is related to the advance rate coefficient and is expressed as LOG10[k’(J)]=0.25J-1.0, and the torsional spring stiffness coefficient K of the connector is finally obtained;
(seventhly) debugging the system: design errors of all parameters can cause the final system to deviate from the original design working condition point, and the system has certain self-adaptive capacity, so that the system can be simply debugged to achieve the optimal working condition, and a simple and convenient debugging method comprises the following steps: and the load of the generator is adjusted, so that the rotating speed and the torque of the generator are finely adjusted, and the working point with the highest power can be found.
In the step (one), when the wave is irregular, the wave height H is approximately taken as the average value of the wave height of a certain point in the sea area in a period of time, and the average value is calculated by the following method: and observing the wave surface curve of the point, counting the wave height count and size, and selecting the largest 1/3 calculated average values.
Due to the adoption of the structure, the invention has the advantages of simple structure, high reliability, high energy conversion efficiency, high application value and the like, and can adapt to complex sea conditions.
Drawings
Fig. 1 is a schematic structural view of the present invention.
Fig. 2 is a connection relation diagram of two wave energy devices.
Fig. 3 is a diagram of the connection between the wave energy device and the platform.
FIG. 4 is a diagram of a swing wing turbine assembly interconnection.
Fig. 5 is a schematic structural view of the float, wherein 5-1 is a sphere, 5-2 is an upright cylinder, fig. 5-3 is an upright cylinder with a frustum at the bottom, and fig. 5-4 is an upright cylinder with a hemisphere at the bottom.
FIG. 6 is a schematic structural view of a swing wing turbine assembly.
FIG. 7 is a schematic structural view of a blade, wherein 7-1 is an airfoil shape, 7-2 is a straight airfoil shape, and 7-3 is an inverted airfoil shape.
Detailed Description
The invention is further described below with reference to the accompanying drawings:
as shown in the attached drawing, the wave energy device of the oscillating floater/swing wing turbine is characterized by comprising a floater 1, a long shaft 2, a universal coupling 3 and swing wing turbine components, wherein a power generation device is arranged in the floater 1, an input shaft of the power generation device extends out of the lower part of the floater 1 and is connected with the upper end of the long shaft 2 through the universal coupling 3, the lower end of the long shaft 2 is connected with the swing wing turbine components, at least one group of swing wing turbine components are arranged, each swing wing turbine component comprises a main shaft 4, a hub 5 and blades 6, the middle part of the hub 5 is fixedly connected with the main shaft 4, at least three connectors are arranged on the side surface of the hub 5, the connectors are annularly distributed on the circumference of the hub 5 and are elastically and rotatably connected with the hub 5 through elastic pieces, the blades 6 are fixedly connected with the connectors, and adjacent swing wing turbine components are connected through, the wave energy devices are two, floats 1 in the two wave energy devices are connected through a connecting rod 9 and a hinge 10, two ends of the connecting rod 9 are respectively connected with the hinge 10, the hinge 10 is connected with the floats 1 to avoid the floats 1 from rotating, the side surfaces of the floats 1 are connected with a platform 8 through a connecting frame 7, one end of the connecting frame 7 is connected with the platform 8 through the hinge 10, the other end of the connecting piece is connected with the floats 1 through the hinge 10 to avoid the floats 1 from rotating, a main shaft 4 between the adjacent swing wing turbine assemblies is connected through a universal coupling 3, the swing wing turbine assembly at the lowest part is connected with a balancing weight to ensure that the swing wing turbine assemblies connected in series are in a tensioning state, the floats 1 are spherical, vertical cylindrical and vertical cylinders with frustum bottoms or vertical cylinders with hemispheres at the bottoms, and the blades 6 are in the shape of straight wings directly stacked by wing profiles, The wing profile is a symmetrical wing profile, a thin wing profile or a flat plate with a round front and back profile, or a flat plate with a round front edge and a sharp rear edge, or a wing profile which is automatically constructed by a smooth curve.
The power generation device in the floater 1 is a rotary power generation device, and has the same power generation form as a fan, so that the power generation device is the prior art and is not described herein.
The working principle of the invention is as follows:
the swing wing turbine is suspended in deep water below the floater 1, and the swing wing turbine and the floater 1 are connected through a long shaft 2 and a universal coupling 3 to form an oscillating floater 1/swing wing turbine system. The length of the long shaft 2 is more than half of the wave wavelength, and as shown in the figure, only the heave motion can act on the swing wing turbine when the floater 1 does complex motion in sea waves, so that the stable working environment of the swing wing turbine is ensured.
When the floater 1 vertically swings under the action of waves, the swing wing turbine is driven to vertically reciprocate, and the swing wing turbine converts the vertical reciprocating motion into rotary motion to drive the generator in the floater 1 to work. The swing wing turbine has better mechanical performance because the rotary motion of the swing wing turbine is continuous motion, and the motion of most wave energy devices is reciprocating motion. And because the rotating speed of the swing wing turbine can be designed, the swing wing turbine is not limited by the wave period, the design is more flexible, and the adaptability to the working condition is stronger.
When the swing wing turbine continuously rotates and drives the generator in the floater 1 to work, the floater 1 is driven to rotate, which is not beneficial to the work of the generator. To avoid this, two schemes may be employed. Firstly, an oscillating floater 1/swing wing turbine system with a duplex structure is adopted, namely two oscillating floater 1/swing wing turbine systems are linked together, and the specific method comprises the following steps: the two floats 1 are linked through a connecting rod 9 and a hinge 10, and the designed rotating directions of the two groups of swing wing turbines are opposite, so that most of the moment is counteracted. The action of the link 9 and the hinge 10 allows the heaving motion of each float 1 to be unrestricted, allowing the two to be restrained from colliding with each other, as shown in fig. 2. Secondly, the float 1 may be attached to the edge of the platform 8 by the link 7 and the hinge 10, and the link 7 and the hinge 10 may restrict the collision of the float 1 with the platform 8 without restricting the heave motion of the float, as shown in fig. 3.
When one of the oscillating wing turbines is not sufficient to absorb the energy of the heaving motion of the float 1, it may take the form of a plurality of sets of oscillating wing turbines in series, which may be rigidly linked, or linked by a universal joint 3, as shown in fig. 4. The weight of the swing wing turbine at the middle position is reduced as much as possible, and the balance weight is applied to the swing wing turbine at the lowest position, so that the tandem swing wing turbine is ensured to be in a tensioned state.
The float 1 may be in the form of a sphere, an upright cylinder with a truncated cone at the bottom, or an upright cylinder with a hemisphere at the bottom, as shown in fig. 5.
Sea state determination: determining the main wave period T and the wave height H of the local sea area, or estimating the main wave period T according to the wave height H, wherein the estimation method comprises the following steps: t =0.8 × 2 × pi × sqrt (H), when the wave is irregular, the wave height H can be approximated as the average value of the wave heights of a certain point in the sea area in a period of time, and the average value is calculated by: and observing the wave surface curve of the point, counting the wave height count and size, and selecting the largest 1/3 calculated average values.
From the wave period T, the wavelength λ can be obtained, expressed as: λ = gT2/(2 π). g is the gravity acceleration, and g =9.8m/s is taken.
(II) the floater 1 determines: the diameter D of the floater 1 is related to the energy conversion efficiency of the floater 1, and can be 0.2 lambda-0.05 lambda.
The draft d of the float 1 is also related to the energy conversion efficiency of the float 1, and may be 0.2 λ to 0.05 λ.
Under the design parameters, verification proves that the energy conversion efficiency eta of the floater 1 can reach the energy conversion efficiency eta of the floater by matching with a proper swing wing turbine20 percent. In design, η =20% may be taken. The absorbed power P of the float 1 can be calculatedF=ηρg2H2DT/(32 π). ρ is the density of water.
And (III) designing a main shaft 4 and a hub 5 in the swing wing turbine assembly: the swing wing turbine is mainly composed of a main shaft 4, a hub 5 and blades 6, as shown in fig. 6. Overall diameter D of the oscillating-wing turbineTThe diameter of the float 1 is consistent as much as possible, and the diameter can be 0.5D-2D.
The length L of the main shaft 4 should be no less than the wave height H to avoid hydrodynamic interference between adjacent turbines.
The hub 5 is fixedly arranged on the main shaft 4, a plurality of joints are arranged on the hub 5, the joints are uniformly distributed in an annular shape, and the hub 5 can rotate relative to the hub 5 along the span direction of the blades 6. There is also a resilient connection between the joint and the hub 5, which enables the joint to withstand a certain torque. The elastic joint is not limited in implementation, but should be designed to have a certain design torsion spring rate. The joint is automatically returned to the neutral position when no torque is applied. Number of joints N on hub 5hPreferably 2 to 10. The shape of the hub 5 should be streamlined as much as possible to reduce hydrodynamic damping during heave motion.
The blade 6 and the hub 5 are fixedly connected, but the connection method is not limited, such as welding, bonding, flange connection, etc.
Hub 5 diameter DhAnd diameter D of turbineTThe ratio of (a) to (b) can be 0.2-0.5, and the diameter of the hub 5 should be as small as possible to reduce hydrodynamic damping.
The overall weight of the swing wing turbine should be controlled. Especially in the case of a tandem turbine, it should be adapted to the displacement of the float 1.
(IV) blade 6 design in the swing wing turbine assembly: the shape of the blade 6 can adopt a straight wing formed by directly stacking wing profiles, a wing profile or an inverted wing profile, as shown in fig. 7.
The wing shape is adopted, namely the chord length of the root part is larger, and the chord length of the tip part is smaller, so that the design has better strength performance;
the design of the inverted wing is adopted, namely the chord length of the root part is smaller, and the chord length of the tip part is larger, so that the design is beneficial to energy conversion, and a framework can be implanted into the blade 6 to improve the strength;
the design of the straight wing is adopted, namely the chord length of the blade 6 is unchanged along the spanwise direction, the processing is convenient, and the strength performance and the energy conversion capability are more centered.
The material design principle is as follows: the blades 6 should be made of light materials as much as possible to reduce the moment of inertia thereof, thereby facilitating the improvement of performance.
The wing section design principle is as follows: the airfoil profile is symmetrical and as thin as possible, such as NACA0009, NACA0012, NACA0015 and NACA0018 airfoil profiles, or flat plates with rounded front and back edges, or flat plates with rounded front edges and sharpened back edges, or other airfoil profiles which are independently constructed by smooth curves.
Diameter D of the turbine with the pendulum wingTAnd hub 5 diameter DhIt was determined that the available spanwise length h = (D) of the blade 6T-Dh)/2。
The chord length c of the middle part of the blade 6 can be the intersection of the following two ranges, which are respectively limited by the expansion length and the wave height of the blade 6, and the two ranges are respectively (0.1H-0.5H) and (0.12H-0.3H). The former ensures that the aspect ratio of the blade 6 is not too large or too small, the too large aspect ratio causes the strength and rigidity of the blade 6 to be insufficient, the requirement on the joint of the hub 5 is higher, and the too small aspect ratio causes the hydrodynamic performance of the blade 6 to be reduced; the latter ensures that the blade 6 has a certain oscillation amplitude, which is too small and leads to a decrease in the hydrodynamic performance of the blade 6, whereas at a certain wave height, if too large an oscillation amplitude ratio is required, the chord length of the blade 6 must be too small, which is also detrimental to the strength and stiffness of the blade 6. If there is no intersection between the two, the diameter of the hub 5 should be adjusted to cause the two ranges to intersect.
Chord length c of root of blade 6hLimited by the diameter of the hub 5, and has a value range of (pi D)h/Nh/8~πDh/Nh) I.e. to maximize the root chord length while mitigating the disturbance of the attached blades 6. If the root chord length chIs obviously unreasonable in design, the number of joints N can be adjustedhTo meet the requirements.
The blade 6 mounting axis is located less than 0.1 chord length, i.e. 0.1c, from the leading edge of the blade 6.
(V) working condition design of the swing wing turbine assembly: the angular speed of the swing wing turbine can be designed to be omega = J × 1.3H/T/(D)T+Dh) Unit rad/s. J is a speed coefficient, and the value range is 5-15. It is verified that at this rotation speed, the turbine is easy to achieve higher energy conversion efficiency.
From the hydrodynamic analysis of the swollen turbine blades 6, the torque of a single swollen turbine can be found to be M =0.069KTNhρH3(DT 2-Dh 2)/T2The generator design can be carried out accordingly. KT is the force coefficient of the blade 6, and is a function of the advancing speed coefficient J, and is expressed as KT (J) = -0.0068J2+0.269J-0.337。
The power of the single swing wing turbine is PT=Mω。
When the power absorbed by the floater 1 is converted into the power of the swing wing turbine, the partial loss exists, the conversion efficiency is about 80 percent, and the number N of the serial swing wing turbines isTIs 0.8PF/PTAnd (6) taking the whole. If the number of tandem turbines is too large, making the actual process difficult to implement, the number of tandem turbines can be reduced by increasing the diameter of the swing wing turbine and increasing the number of blades 6 per turbine. In general, the number of tandem turbines is inversely proportional to the turbine diameter and also inversely proportional to the number of turbine blades 6.
(sixth) design of the connection head between the blade 6 and the hub 5: the torsional spring rate of the joint between the blade 6 and the hub 5 can be designed to be K = 0.275K' ρ H3hc/T2And k' is a dimensionless spring stiffness ratio, the value of which is related to the advance rate coefficient and is expressed as LOG10[k’(J)]=0.25J-1.0；
(seventhly) debugging the system: design errors of all parameters can cause the final system to deviate from an original design working condition point, and the system has certain self-adaptive capacity, so that the system can be simply debugged to achieve the optimal working condition. A simple debugging method comprises the following steps: and the load of the generator is adjusted, so that the rotating speed and the torque of the generator are finely adjusted, and the working point with the highest power can be found.
Examples
Sea state determination: designed for the following sea conditions: observing to obtain the main wave height H =1 m of the sea area, directly substituting the main wave height H into a formula T =0.8 × 2 π × Sqrt (H), and estimating the wave period T =5 seconds; according to the wavelength formula λ = gT2/(2 pi), the available wavelength λ =39 m.
(II) the floater 1 determines:
the spherical floater 1 is selected.
The value range of the diameter D of the floater 1 is designed to be 0.2 lambda-0.05 lambda, namely 7.8 m-1.95 m, and D =4m is taken.
The value range of the draft d of the floater 1 is designed to be 0.2 lambda-0.05 lambda, namely 7.8 m-1.95 m, and d =2 m.
Designing the absorbed power P of the float 1F=ηρg2H2DT/(32 π), performing dry-bottom cultivation with η =20% and seawater density ρ =1025Kg/m to obtain the designed absorption power P of the floater 1F=3.9KW。
And (III) designing a main shaft 4 and a hub 5 in the swing wing turbine assembly:
design of the overall diameter D of the swing wing turbineTThe value range of (1) is 0.5D-2D, namely DT=4m。
Design hub 5 diameter DhRange of =0.2~0.5DTTaken as 0.25DTI.e. Dh=1m。
The number of blades 6 of a single swing wing turbine is preliminarily designed to be 3, namely Nh=3。
(IV) blade 6 design in the swing wing turbine assembly:
according to the length formula h = (D) of the swing wing turbine blade 6T-Dh) And 2, the available blade 6 has an expansion length h =1.5 m.
The swing wing turbine blades 6 are made of composite material or other lightweight material.
The shape of the swing wing turbine blade 6 adopts a straight wing shape.
The wing profile of the swing wing turbine blade 6 adopts a front and back inverted flat shape.
The value range of the chord length c in the middle of the swing wing turbine blade 6 is the intersection of (0.1H-0.5H) and (0.12H-0.3H), namely the intersection of (0.15 m-0.75 m) and (0.12 m-0.3 m), and c =0.3m is taken.
Chord length c of root of swing blade turbine blade 6hHas a value range of (pi D)h/Nh/8~πDh/Nh) I.e. (0.13 m-1.04 m), take chAnd the thickness is =0.3m, and the design requirement of the straight wing is met.
The installation shaft of the swing wing turbine blade 6 is designed at the front edge of the wing profile and is less than 0.1c, so that the requirement is met.
(V) working condition design of the swing wing turbine assembly:
the design formula of the angular speed of the swing wing turbine is omega = J multiplied by 1.3H/T/(D)T+Dh) Unit rad/s. The value range of the advancing speed coefficient J is 5-15. Taking J =10, the angular velocity ω =0.52rad/s, reduced to 29.8 °/s, is obtained.
The torque calculation formula of a single swing wing turbine is M =0.069KTNhρH3(DT 2-Dh 2)/T2Wherein, the stress coefficient KT is related to the advancing speed coefficient J, and the relational expression is KT (J) = -0.0068J2+ 0.269J-0.337. First, the force coefficient KT is calculated, and KT =1.66 and further the torque M =211n.m are obtained.
The power of the single swing wing turbine is PT=Mω=110W。
The number of the tandem swing wing turbines is NT=0.8PF/PTAnd is approximately equal to 28. Obviously, this number is too large and can be reduced by increasing the diameter of the oscillating-wing turbine and increasing the number of blades 6 per oscillating-wing turbine.
Designing again:
adjusting the diameter of the swing wing turbine to be 2D (8 m), adjusting the number of blades 6 of each swing wing turbine to be 6, keeping other selected parameters unchanged, and repeating the steps (4) to (6) to obtain the rotor blade of the rotor blade
Hub 5 diameter Dh=0.25DT=2m；
Span length h = (D) of blade 6T-Dh)/2=3m；
Oscillating-wing turbine angular velocity omega = JX 1.3H/T/(D)T+Dh)=0.26rad/s；
Torque M =0.069K of single swing wing turbineTNhρH3(DT 2-Dh 2)/T2=1.69KN.m；
Power P of single swing wing turbineT=Mω=440W；
The number of the tandem swing wing turbines is NT=0.8PF/P T7. It is acceptable.
And finally, selecting a secondary design scheme.
(sixth) design of the connection head between the blade 6 and the hub 5:
torsional spring rate K = 0.275K' ρ H of the joint between blade 6 and hub 53hc/T2Wherein k' can be according to the relational LOG10[k’(J)]And (d) = 0.25J-1.0. Calculated K' =32, and further K =325 n.m/rad.
(VII) System debugging
Design errors of all parameters can cause the final system to deviate from an original design working condition point, and the system has certain self-adaptive capacity, so that the system can be simply debugged to achieve the optimal working condition. A simple debugging method comprises the following steps: and the load of the generator is adjusted, so that the rotating speed and the torque of the generator are finely adjusted, and the working point with the highest power can be found.

Claims (8)

1. The wave energy device is characterized by comprising a floater, a long shaft, a universal coupling and a swing wing turbine assembly, wherein a power generation device is arranged in the floater, an input shaft of the power generation device extends out of the lower portion of the floater and is connected with the upper end of the long shaft through the universal coupling, the lower end of the long shaft is connected with the swing wing turbine assembly, at least one group of swing wing turbine assemblies is arranged, each swing wing turbine assembly comprises a main shaft, a hub and blades, the middle of the hub is fixedly connected with the main shaft, at least three connectors are arranged on the side face of the hub, the connectors are annularly distributed on the circumference of the hub and are elastically and rotatably connected with the hub through elastic pieces, the blades are fixedly connected with the connectors, and adjacent swing wing turbine assemblies are connected through the main shaft.
2. The wave energy device of an oscillating floater/swing wing turbine as claimed in claim 1, characterized in that the wave energy device is provided with two buoys, the two buoys are connected with each other through a connecting rod and a hinge, the two ends of the connecting rod are respectively connected with the hinge, and the hinge is connected with the buoys to prevent the buoys from rotating.
3. The wave energy device of an oscillating floater/swing wing turbine according to claim 1, characterized in that the side of the floater is connected with the platform through a connecting frame, one end of the connecting frame is connected with the platform through a hinge, and the other end of the connecting piece is connected with the floater through a hinge, so as to prevent the floater from rotating.
4. The wave energy device of an oscillating floater/swing wing turbine as claimed in claim 1, characterized in that the main shafts between adjacent swing wing turbine assemblies are connected through a universal coupling, and the lowest swing wing turbine assembly is connected with a balancing weight to ensure that the series-connected swing wing turbine assemblies are in a tensioned state.
5. An oscillating floater/swing wing turbine wave energy device according to claim 1, characterized in that the floater is a sphere, a vertical cylinder with a frustum of cone at the bottom or a vertical cylinder with a hemisphere at the bottom.
6. The wave energy device of the oscillating floater/swing wing turbine as claimed in claim 1, wherein the shape of the blade adopts a straight wing, a wing shape or an inverted wing shape which is formed by directly stacking wing shapes, and the wing shapes are symmetrical wing shapes, thin wings or flat plates with rounded front and back, or flat plates with rounded front edges and sharpened back edges, or wing shapes which are constructed by smooth curves.
7. A design method of a wave energy device of an oscillating floater/swing wing turbine is characterized by comprising the following steps:
sea state determination: determining the main wave period T and the wave height H of the local sea area, or estimating the main wave period T according to the wave height H, wherein the estimation method comprises the following steps: t =0.8 × 2 × π × sqrt (h), the wavelength λ is obtained from the wave period T, expressed as: λ = gT2/(2 π). g is the gravity acceleration, and g =9.8m/s is taken;
(II) determining a floater: the diameter D of the floater is related to the energy conversion efficiency of the floater, and can be 0.2 lambda-0.05 lambda, the draft depth D of the floater is also related to the energy conversion efficiency of the floater, and can be 0.2 lambda-0.05 lambda, under the design parameters, verification is carried out, the energy conversion efficiency eta of the floater can be guaranteed to reach 20%, eta =20% is obtained, and then the absorption power P of the floater can be calculated and obtained by matching with a proper swing wing turbineF=ηρg2H2DT/(32 pi), rho is the density of water;
(III) designing a main shaft and a hub in the swing wing turbine assembly: overall diameter D of the swing wing turbine assemblyTShould be as consistent as possible with float diameter, can be 0.5D ~2D, main shaft length L should be no less than wave height H, hub diameter D among swing wing turbine subassemblyhAnd the overall diameter DTThe ratio of (A) to (B) is 0.2-0.5;
(IV) designing blades in the swing wing turbine assembly: number of blades N in a swing wing turbine assemblyh2-10, according to the blade extension formula h = (D) of swing wing turbineT-Dh) 2, obtaining the blade extension, wherein the chord length c of the middle part of the blade is the intersection of the following two ranges, which are respectively limited by the blade extension and the wave height, and the two ranges are respectively (0.1H-0.5H) and (0.12H-0.3H); chord length c of blade roothLimited by the diameter of the hub, and has a value range of (pi D)h/Nh/8~πDh/Nh) The distance between the position of the blade mounting shaft and the front edge of the blade is less than 0.1 time of chord length, namely 0.1 c;
(V) working condition design of the swing wing turbine assembly: the angular velocity of the swing wing turbine is designed to be ω = JX 1.3H/T/(D)T+Dh) And the unit rad/s and J are advancing speed coefficients, the value range is 5-15, and the torque of a single swing wing turbine is M =0.069K according to hydrodynamic analysis of the swing wing turbine bladeTNhρH3(DT 2-Dh 2)/T2Designing a generator according to the above, wherein KT is the stress coefficient of the blade and is a function of a speed advance coefficient J, and is represented as KT (J) = -0.0068J2+0.269J-0.337, the power of a single oscillating wing turbine is PT= M ω, the power absorbed by the float is partially lost when converted into power in a swing wing turbine, with a conversion efficiency of the order of magnitude of80% of the number of tandem pendulum wing turbines NTIs 0.8PF/PTAnd (6) taking the whole. If the number of the tandem turbines is too large, so that the practical engineering is difficult to realize, the number of the tandem turbines can be reduced by increasing the diameter of the swing wing turbines and increasing the number of blades of each turbine;
(VI) designing a connecting head between the blade and the hub: the torsional spring stiffness coefficient of the connecting head between the blade and the hub can be designed to be K = 0.275K' rho H3hc/T2And k' is a dimensionless spring stiffness ratio, the value of which is related to the advance rate coefficient and is expressed as LOG10[k’(J)]=0.25J-1.0, and the torsional spring stiffness coefficient K of the connector is finally obtained;
(seventhly) debugging the system: design errors of all parameters can cause the final system to deviate from the original design working condition point, and the system has certain self-adaptive capacity, so that the system can be simply debugged to achieve the optimal working condition, and a simple and convenient debugging method comprises the following steps: and the load of the generator is adjusted, so that the rotating speed and the torque of the generator are finely adjusted, and the working point with the highest power can be found.
8. An oscillating floater/swing wing turbine wave energy device according to claim 7, characterized in that, in the step (one), when the wave is irregular, the wave height H is approximately the average value of the wave height at a certain point in the sea area in a period of time, and the average value is calculated by: and observing the wave surface curve of the point, counting the wave height count and size, and selecting the largest 1/3 calculated average values.
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