CN106677979B - A kind of pneumatic equipment bladess aerodynamic configuration couples optimization method with main frame operation characteristic - Google Patents
A kind of pneumatic equipment bladess aerodynamic configuration couples optimization method with main frame operation characteristic Download PDFInfo
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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
- F03D—WIND MOTORS
- F03D1/00—Wind motors with rotation axis substantially parallel to the air flow entering the rotor
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- F03D1/0608—Rotors characterised by their aerodynamic shape
- F03D1/0633—Rotors characterised by their aerodynamic shape of the blades
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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
- F03D—WIND MOTORS
- F03D3/00—Wind motors with rotation axis substantially perpendicular to the air flow entering the rotor
- F03D3/06—Rotors
- F03D3/061—Rotors characterised by their aerodynamic shape, e.g. aerofoil profiles
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- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
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- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
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- Y02E10/72—Wind turbines with rotation axis in wind direction
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- 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
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- Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
- Y02E10/00—Energy generation through renewable energy sources
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- Y02E10/74—Wind turbines with rotation axis perpendicular to the wind direction
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Abstract
The invention discloses a kind of pneumatic equipment bladess aerodynamic configuration to couple optimization method with main frame operation characteristic, and step is as follows：Step S1, construct the global chord length distribution model of pneumatic equipment bladess；Step S2, construct the global torsional angle distributed model of pneumatic equipment bladess；Step S3, construction control variable X；Step S4, the constraints of construction leaf chord length C, blade bending moment M and wind wheel to the thrust T of tower；S5, construction object function F (X)；S6, the population containing several particles is constructed, and optimization processing is iterated to each population, obtain optimal blade profile.The present invention characterizes blade using Bezier, realizes the global parameterized expression of blade aerodynamic profile；When choosing optimal blade, the calculating of blade annual electricity generating capacity takes into full account actual power generation under different wind conditions, the design of blade profile and main frame operation characteristic is realized in optimization design simultaneously, the best match of design blade and destination host can be achieved, blade is improved in the aeroperformance in low wind speed region, avoids the generation of blade early stage stall.
Description
Technical Field
The invention belongs to the technical field of wind power generation equipment, and particularly relates to a method for optimizing coupling of aerodynamic shape of a wind turbine blade and operating characteristics of a main engine.
Background
The steady-state operation characteristic of the wind turbine refers to a steady-state control strategy of the wind turbine, and comprises a steady-state change curve of a blade pitch angle, a wind wheel rotating speed, a blade tip speed ratio, a power coefficient and the like of the wind turbine along with the incoming wind speed in an ideal working state, so that the steady-state operation characteristic is a basis for accurately calculating the annual energy generation of the wind turbine and designing a dynamic control strategy and a controller of a unit and is an essential design characteristic of the wind turbine. In the optimization design of the blade, the shape of the blade and the steady-state operation characteristic of the wind turbine are mutually influenced and constrained, and on one hand, the shape parameter of the blade is the premise of designing the steady-state operation characteristic of the wind turbine; on the other hand, parameters such as annual energy production, load and the like of the blade can be accurately calculated only after the steady-state operation control strategy of the wind turbine is determined. In the existing research, some researchers set the optimal tip speed ratio to a fixed value in the optimization design of the blade, and perform the optimization design of the aerodynamic profile (mainly the chord length and the torsional angle distribution) of the blade with the target of the maximum aerodynamic power coefficient or the maximum annual energy production of the blade at the optimal tip speed ratio. However, the blades do not always work at the optimal tip speed ratio in actual operation, and the basic control strategy of the wind turbine should set the corresponding tip speed ratio to maximize the aerodynamic power of the wind turbine as much as possible by changing the rotation speed of the wind turbine under the limiting condition of satisfying the rotation speed of the generator and the rated torque for different incoming wind speeds. The method for optimally designing the blade under the constant optimal tip speed ratio only considers the optimal working state of the blade and cannot ensure the global optimality of the designed blade, particularly the power generation performance of the blade under the low wind speed working condition. Some papers propose that the shape of the blade is optimally designed with the aim of minimizing the incoming flow wind speed under the rated power coefficient, and then the steady-state operation characteristic of the wind turbine is designed according to the optimized blade shape.
Disclosure of Invention
The invention aims to solve the technical problems that the overall parametric expression of a blade and the integrated optimization design of the aerodynamic shape and the host operating characteristics of the blade cannot be realized in the conventional optimization design method of the blade shape, so that the coupling optimization method of the aerodynamic shape and the host operating characteristics of the wind turbine blade for performing the overall parametric expression of the chord length and the torsion angle of the blade by adopting a multi-order Bessel curve is provided.
In order to solve the technical problems, the technical scheme adopted by the invention is as follows:
a method for optimizing coupling of aerodynamic shape of wind turbine blade and operation characteristic of host computer comprises the following steps: s1, constructing a global chord length distribution model of the wind turbine blade.
The method comprises the following specific steps: s1.1, constructing n control points, wherein the abscissa of each control point is a fixed value, and a first control point c 1 A second control point c 2 And nth control point c n Is a fixed control point; first control point c 1 Ordinate and second control point c 2 Is set as the diameter of the blade root, the n-1 th control point c n-1 Has the ordinate of the (n-2) th control point c n-2 1.5 times of ordinate of the control point c n Has a vertical coordinate of 0, and a third control point c 3 To the n-2 control point c n-2 The ordinate of (a) is a design variable.
S1.2, obtaining an n-1 order Bezier curve C (u) of the global chord length distribution of the wind turbine blade according to the n control points in the step S1.1:
wherein n is the number of control points; p i The abscissa and the ordinate of the ith control point are represented; u is a scaling factor and u is ∈ [0,1 ]](ii) a If a plurality of equally dividing points are inserted on the Bezier curve to equally divide the Bezier curve into a plurality of equally dividing points, the ratio of the curve length from the starting point to the jth point of the Bezier curve to the total length of the curve is u.
B i,n (u) is a Bernstein polynomial, and the specific formula is as follows:
and S2, constructing a global torsion angle distribution model of the wind turbine blade.
The method comprises the following specific steps: s2.1, constructing m control points, wherein the abscissa of each control point is a fixed value, and the first control point t 1 A second control point t 2 A third control point t 3 M-1 th control point t m-1 And the mth control point t m Is a fixed control point; first control point t 1 A second control point t 2 And a third control point t 3 Are equal in ordinate; fourth control point t 4 And a sixth control point t 6 Are equal in ordinate; m-1 th control point t m-1 And the mth control point t m The ordinate of (a) is 0; fifth control point t 5 To the m-2 control point t m-2 The ordinate of (c) is the design variable.
S2.2, obtaining an m-1 order Bezier curve C (u) of the torsion angle of the wind turbine blade according to the m control points in the step S2.1;
wherein m is the number of control points; p i The abscissa and the ordinate of the ith control point are represented; u is a scaling factor and u is ∈ [0,1 ]](ii) a If a plurality of equally dividing points are inserted on the Bezier curve to equally divide the Bezier curve into a plurality of equally dividing points, the ratio of the curve length from the starting point to the jth point of the Bezier curve to the total length of the curve is u.
B i,m (u) is Bernstein polynomial, and the specific formula is as follows:
in order to prevent the blade tip from stalling in advance under the condition of large aeroelastic torsional deformation, the torsional angle distribution of the blade tip is not optimally designed, but a certain amount of reverse torsional angle distribution is given in advance.
S3, selecting a variable construction control variable X from the global chord length model in the S1 and the torsion angle model in the S2;
selecting a third control point c in the global chord length model 3 To the (n-2) th control point c n-2 And the fifth control point t in the torsional angle model 5 To the m-2 control point t m-2 The ordinate of (a) constitutes the control variable X; the control variable X is:
X＝(c 3 ,c 4 ,c 5 ,c 6 ,.....,c n-3 ,c n-2 ,t 4 ,t 5 ,t 6 ,......,t m-3 ,t m-2 ) (5)；
s4, constructing constraint conditions of blade chord length C, blade bending moment M and thrust T of a wind wheel to a tower drum;
s4.1, constructing the constraint condition of the chord length C of the blade,
C≤C max (6)；
wherein, C max Is a constant value;
s4.2, constructing a constraint condition of the bending moment M of the blade,
M≤M max (7)；
wherein M is max Is a constant value;
s4.3, constructing a constraint condition of the thrust T of the wind wheel to the tower drum,
T≤T max (8)；
wherein, T max Is a constant value.
S5, constructing an objective function F (X);
the specific formula is as follows:
F(X)＝AEP*p1*p2*p3 (9)；
wherein AEP is the annual energy production of the blades, and the calculation formula is as follows:
wherein, f (v) i ＜v 0 ＜v i+1 ) The wind speed is located at v in one year i And v i+1 The probability of (d) in (d); p (v) i ) For wind speed at v i The generated power of the wind turbine.
p1, p2 and p3 are penalty factors.
The penalty factor p1 is related to the chord length C of the blade, and when C is less than or equal to C max When p1=1, otherwise, p1= (C) max /C)^2。
The penalty factor p2 is related to the blade root bending moment M, when M is less than or equal to M max When p2=1, otherwise, p2= (M) max /M)^2。
The calculation formula of the blade root bending moment M is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed.
The penalty factor p3 is related to the wind wheel thrust T, and when T is less than or equal to T max When p3=1, otherwise, p3= (T) max [ solution ]/T) ^2; the calculation formula of the wind wheel thrust T is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed.
S6, constructing particle swarms containing a plurality of particles by taking the design variable X as the particles, and performing iterative optimization processing on each particle swarms to obtain the optimal blade shape.
The method comprises the following specific steps: s6.1, initializing each particle in the particle swarm.
Velocity, position, and individual optimum P for each particle i And performing value assignment.
S6.2, calculating the annual power generation AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle in the current generation to obtain an objective function value F (X) of each particle.
S6.3, mixing the particlesThe objective function values F (X) of each particle in the group are compared, and the value with the largest value is selected as the global optimum P in the contemporary particle group g 。
S6.4, iterating each particle to obtain a next-generation particle;
the iterative formula is
Wherein, w, c 1 ,c 2 ,r 1 ,r 2 Are weight coefficients respectively; x is a radical of a fluorine atom i k Is the position of the ith particle in the kth generation; v. of i k The velocity of the ith particle in the kth generation; x is the number of i k+1 The position of the ith particle in the k +1 th generation; v. of i k+1 The velocity of the ith particle in the k +1 th generation; p is a radical of formula i k Optimal for the ith particle in the kth generation; p is a radical of g k Is global optimum of the k-th generation particle swarm.
S6.5, repeating the step S6.2 to calculate the annual energy production AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle of the current generation particle swarm, and obtaining the objective function value F (X) of each particle.
S6.5, the objective function values F (X) of the current generation particles are compared with the objective function values F (X) of the previous generation particles, and the individual optimum Pi of each particle in the current generation is selected as the value having the larger objective function value F (X).
And S6.6, comparing the objective function values F (X) of each particle in the current-generation particle swarm, and selecting the maximum objective function value F (X) as the global optimal Pg in the current-generation particle swarm.
S6.7, calculating the difference value between the current generation global optimal Pg and the previous generation global optimal Pg, and comparing the difference value with 1; stopping the iteration if the variation of the global optimal Pg in the iteration continuously exceeds 10 times is less than or equal to 1, and enabling the particles corresponding to the current global optimal Pg to be in the optimal blade shape; otherwise, steps S6.3-S6.6 are repeated.
P (v) at different wind speeds in the annual energy production AEP i ) The solution of (a) is divided into three cases: first, when the real-time wind speed v is i Rated wind speed V Forehead (D) Time, generator speed omega g At maximum speed of rotation omega g max Power generated by a wind turbine p (v) i ) Is rated power P of generator Forehead (forehead) 。
Second case, when v i min ≤v i ≤V Forehead (D) The pitch angle beta of the blade is 0 DEG, and the tip speed ratio is the optimum tip speed ratio lambda opt 。
According to the optimum tip speed ratio lambda opt Calculating the generated power p (v) of the wind turbine i ) (ii) a The specific formula is as follows:
λ opt ＝Rω r (v i )/v i (16)；
ω r (v i )＝ω g (v i )/G (17)；
p(v i )＝T(v i )ω g (v i ) (18)；
wherein, ω is r (v i ) The rotational speed of the wind wheel; omega g (v i ) Is the generator speed; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed.
In the third case, when v i ≤v i min When the pitch angle beta of the blade is 0 DEG, the wind wheel rotating speed omega r Constant at omega r ＝ω g min /G。
According to the rotational speed omega of the wind wheel r Calculating the generated power p (v) of the wind turbine i )；
The specific calculation formula is as follows:
λ(v i )＝Rω g,min /(Gv i ) (19)；
p(v i )＝T(v i )ω g min (21)；
wherein, λ (v) i ) Is the tip speed ratio; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is the air density.
The rated wind speed v Forehead (D) The calculation process of (2) is as follows: when the wind speed reaches the rated wind speed v Forehead (D) Time, generator speed omega g Is the maximum rotation speed omega g max The pitch angle beta =0 DEG according to the generator speed omega g max Determining the rated wind speed v Forehead (D) ，
The specific formula is as follows:
T(v i )＝p forehead (forehead) /ω g max (22)；
λ(v i )＝Rω g,max /(Gv i ) (24)；
Wherein, λ (v) i ) Is tip speed ratio; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is the air density; a' is a tangential induction factor; r is the length of the blade.
Said optimum tip speed ratio λ opt The calculation process of (c) is as follows:
firstly, according to the power coefficient of the bladeC P Obtaining C under the condition of 0-degree pitch angle by a relational expression of tip speed ratio lambda P -a λ -curve;
power coefficient of blade C P The relationship to tip speed ratio λ is as follows:
wherein a' is a tangential induction factor; r is the length of the blade, and λ is the tip speed ratio.
Then, according to C P Obtaining optimum tip speed ratio lambda of blade by lambda curve opt ；
According to the maximum power coefficient C of the blade Pmax Size of (1), C P Flatness of the top of the lambda curve and lambda opt Three criteria of size of (2) select λ opt 。
The blade operating at optimum tip speed ratio lambda opt Minimum wind speed v of min The calculation process of (2) is as follows:
when real-time wind speed v i Up to v min While, the rotational speed omega of the generator g Is omega g min 。
According to the optimum tip speed ratio lambda opt And the rotational speed omega of the generator g min Calculating a minimum wind speed value v min； The specific formula is as follows:
λ opt ＝Rω g min /Gv i (26)；
wherein R is the length of the blade; g is the transmission ratio of the gear box; v. of i Is the real-time wind speed.
According to the invention, the Bezier curve is used for representing the overall chord length and torsional angle distribution of the blade, so that the chord length and torsional angle distribution of the blade can be more effectively controlled, and the overall parametric expression of the aerodynamic shape of the blade is realized; when the optimal blade is selected, the annual power generation amount of the blade is calculated by fully considering the actual power generation amount under different wind speeds, the design of the blade appearance and the host operation characteristic is realized simultaneously in the optimization design, the optimal matching of the designed blade and a target host can be realized, the aerodynamic performance of the blade in a low wind speed area is improved, and the early stall of the blade is avoided.
Drawings
FIG. 1 is a flow chart of the system of the present invention.
FIG. 2 is a Bessel plot of the blade global chord length of the present invention.
FIG. 3 is a Bessel plot of blade twist angle according to the present invention.
FIG. 4 is a comparison distribution diagram of the chord length of the optimized blade and the chord length of the original blade.
FIG. 5 is a graph showing the comparison of the twist angle of the optimized blade of the present invention with the twist angle of the original blade.
FIG. 6 is a power comparison distribution diagram of the optimized blade and the original blade under different incoming flow wind speeds.
FIG. 7 is a graph of tip speed ratio versus incoming wind speed for the present invention.
FIG. 8 is a graph of rotor speed versus incoming wind speed for the present invention.
FIG. 9 is a graph of the operating characteristics of a host machine to which the optimized blades of the present invention are matched.
Detailed Description
As shown in the figure 1, the method for optimizing the coupling of the aerodynamic profile of the wind turbine blade and the operating characteristics of the main engine comprises the following steps: s1, constructing a global chord length model of the wind turbine blade.
The method comprises the following specific steps: s1.1, constructing n control points, wherein the abscissa of each control point is a fixed value, and a first control point c 1 A second control point c 2 And nth control point c n Is a fixed control point; first control point c 1 And a second control point c 2 Is set as the diameter of the blade root, the n-1 th control point c n-1 Has the ordinate of the (n-2) th control point c n-2 1.5 times the ordinate of the control point c n Has a vertical coordinate of 0, and a third control point c 3 To the (n-2) th control point c n-2 The ordinate of (c) is the design variable.
S1.2, obtaining an n-1 order Bezier curve C (u) of the global chord length of the wind turbine blade according to the n control points in the step S1.1,
wherein n is the number of control points; p is i Represents the abscissa and ordinate of the ith control point; u is a scaling factor and u is ∈ [0,1 ]](ii) a If a plurality of equally dividing points are inserted on the Bezier curve to equally divide the Bezier curve into a plurality of equally dividing points, the ratio of the curve length from the starting point to the jth point of the Bezier curve to the total length of the curve is u.
B i,n (u) is Bernstein polynomial, and the specific formula is as follows:
and S2, constructing a global torsion angle model of the wind turbine blade.
The method comprises the following specific steps: s2.1, constructing m control points, wherein the abscissa of each control point is a fixed value, and the first control point t 1 A second control point t 2 A third control point t 3 M-1 th control point t m-1 And the mth control point t m Is a fixed control point; first control point t 1 A second control point t 2 And a third control point t 3 Are equal in ordinate; fourth control point t 4 And a sixth control point t 6 Are equal in ordinate; m-1 th control point t m-1 And the mth control point t m The ordinate of (a) is 0; fifth control point t 5 To m-2 control point t m-2 The ordinate of (a) is a design variable.
S2.2, obtaining an m-1 order Bezier curve C (u) of the torsion angle of the wind turbine blade according to the m control points in the step S2.1,
wherein m is the number of control points; p i The abscissa and the ordinate of the ith control point are represented; u is a scaling factor and u is ∈ [0,1 ]](ii) a If a plurality of equal division points are inserted into the Bezier curve to equally divide the Bezier curve into a plurality of equal division points, the ratio of the curve length from the starting point to the jth point of the Bezier curve to the total length of the curve is u.
B i,m (u) is a Bernstein polynomial, and the specific formula is as follows:
in order to prevent the blade tip from stalling in advance under the condition of large aeroelastic torsional deformation, the torsional angle distribution of the blade tip is not optimally designed, and a certain amount of reverse torsional angle distribution is given in advance.
S3, selecting a variable construction control variable X from the global chord length model in the S1 and the torsion angle model in the S2;
selecting a third control point c in the global chord length model 3 To the (n-2) th control point c n-2 Of the ordinate and the fifth control point t in the torsion angle model 5 To the m-2 control point t m-2 The ordinate of (a) constitutes the control variable X; the control variable X is:
X＝(c 3 ,c 4 ,c 5 ,c 6 ,.....,c n-3 ,c n-2 ,t 4 ,t 5 ,t 6 ,......,t m-3 ,t m-2 ) (5)。
s4, constructing constraint conditions of blade chord length C, blade bending moment M and thrust T of a wind wheel to a tower;
s4.1, constructing the constraint condition of the chord length C of the blade,
C≤C max (6)；
wherein, C max Is a constant value.
S4.2, constructing a constraint condition of a blade root bending moment M,
M≤M max (7)；
wherein M is max Is a constant value.
S4.3, constructing a constraint condition of the thrust T of the wind wheel to the tower drum,
T≤T max (8)；
wherein, T max Is a constant value.
S5, constructing an objective function F (X);
the concrete formula is as follows:
F(X)＝AEP*p1*p2*p3 (9)。
wherein, AEP is the annual energy production of the blades, and the calculation formula is as follows:
wherein, f (v) i ＜v 0 ＜v i+1 ) The wind speed is located at v in one year i And v i+1 The probability of (d) in (d); p (v) i ) For wind speed at v i The generated power of the wind turbine.
p1, p2 and p3 are penalty factors.
The penalty factor p1 is related to the chord length C of the blade, and when C is less than or equal to C max When p1=1, otherwise, p1= (C) max /C)^2。
The penalty factor p2 is related to the blade root bending moment M, and when M is less than or equal to M max When p2=1, otherwise, p2= (M) max /M)^2。
The calculation formula of the blade root bending moment M is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed.
The penalty factor p3 is related to the thrust T of the wind wheel, when T is less than or equal to T max When p3=1, otherwise p3= (T) max /T) ^2; the calculation formula of the wind wheel thrust T is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed.
S6, constructing particle swarms containing a plurality of particles by taking the design variable X as the particles, and performing iterative optimization processing on each particle swarms to obtain the optimal blade shape.
The method comprises the following specific steps: s6.1, initializing each particle in the particle swarm.
The velocity, position, and individual optimal Pi of each particle are assigned.
S6.2, calculating the annual energy production AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle in the current generation to obtain an objective function value F (X) of each particle.
S6.3, comparing the objective function values F (X) of all the particles in the particle swarm, and selecting the value with the maximum value as the global optimal Pg in the contemporary particle swarm.
S6.4, iterating each particle to obtain a next-generation particle;
the iterative formula is
Wherein, w, c 1 ,c 2 ,r 1 ,r 2 Are weight coefficients respectively; x is the number of i k Is the position of the ith particle in the kth generation; v. of i k Velocity of the ith particle in the kth generation; x is a radical of a fluorine atom i k+1 The position of the ith particle in the k +1 th generation; v. of i k+1 The velocity of the ith particle in the k +1 th generation;p i k optimal for the ith particle in the kth generation; p is a radical of formula g k Is the global optimum of the k-th generation particle swarm.
S6.5, repeating the step S6.2 to calculate the annual energy production AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle of the current generation particle swarm to obtain an objective function value F (X) of each particle.
S6.5, the objective function values F (X) of the current generation particles are compared with the objective function values F (X) of the previous generation particles, and the individual optimal Pi of each particle in the current generation is selected as the one having the larger objective function value F (X).
And S6.6, comparing the objective function values F (X) of each particle in the current-generation particle swarm, and selecting the maximum objective function value F (X) as the global optimal Pg in the current-generation particle swarm.
S6.7, calculating the difference between the current generation global optimal Pg and the previous generation global optimal Pg, and comparing the difference with 1; stopping the iteration if the variation of the global optimal Pg in the iteration continuously exceeds 10 times is less than or equal to 1, and enabling the particles corresponding to the current global optimal Pg to be in the optimal blade shape; otherwise, steps S6.3-S6.6 are repeated.
In the invention, the wind wheel rotating speed omega r The graph with wind speed is shown in FIG. 8, and it can be seen from FIG. 8 that p (v) is shown at different wind speeds in the annual energy production AEP i ) The calculation of (b) should be divided into three cases: first, when the real-time wind speed v is i Rated wind speed V Forehead (D) Time, generator speed omega g Is the maximum rotation speed omega g max Generated power p (v) of a wind turbine i ) Is rated power P of generator Forehead (D) 。
In the second case, when v i min ≤v i ≤V Forehead (forehead) The pitch angle beta of the blade is 0 DEG, and the tip speed ratio is the optimum tip speed ratio lambda opt 。
According to the optimum tip speed ratio lambda opt Calculating the generated power p (v) of the wind turbine i ) The concrete formula is as follows:
λ opt ＝Rω r (v i )/v i (16)；
ω r (v i )＝ω g (v i )/G (17)；
p(v i )＝T(v i )ω g (v i ) (18)；
wherein, ω is r (v i ) The rotational speed of the wind wheel; omega g (v i ) Is the generator speed; g is the gear ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed.
In the third case, when v i ≤v i min When the pitch angle beta of the blade is 0 degree, the rotating speed omega of the wind wheel r Constant at omega r ＝ω g min /G。
According to the rotational speed omega of the wind wheel r Calculating the generated power p (v) of the wind turbine i )；
The specific calculation formula is as follows:
λ(v i )＝Rω g,min /(Gv i ) (19)；
p(v i )＝T(v i )ω g min (21)；
wherein, λ (v) i ) Is the tip speed ratio; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is the air density.
The rated wind speed v Forehead (D) The calculation process of (2) is as follows: when the wind speed reaches the rated wind speed v Forehead (D) Time, generator speed omega g Is the maximum rotation speed omega g max The pitch angle beta =0 DEG according to the rotation speed omega of the generator g max Calculating the rated wind speed v Forehead (D) In particularThe formula is as follows:
T(v i )＝p forehead (forehead) /ω g max (22)；
λ(v i )＝Rω g,max /(Gv i ) (24)；
Wherein, λ (v) i ) Is the tip speed ratio; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is the air density; a' is a tangential induction factor; r is the length of the blade.
Said optimum tip speed ratio λ opt The calculation process of (c) is as follows:
firstly, according to the power coefficient C of the blade P Obtaining C under the condition of 0-degree pitch angle by a relational expression of tip speed ratio lambda P -a curve of λ, as shown in FIG. 7,
coefficient of power of blade C P The relationship with tip speed ratio λ is as follows:
wherein a' is a tangential induction factor; r is the length of the blade, and λ is the tip speed ratio.
Then, according to C P Obtaining optimum tip speed ratio lambda of blade by lambda curve opt ；
According to the maximum power coefficient C of the blade Pmax The larger the better, C P The flatter the top of the lambda curve, the better the sum lambda opt Three criteria selection λ are better the smaller opt 。
The blade works at the optimum tip speed ratio lambda opt Minimum wind speed v of min The calculation process of (2) is as follows:
when the real-time wind speed v i Reaches v min While, the rotational speed omega of the generator g Is omega g min 。
According to optimum tip speed ratio lambda opt And the rotational speed omega of the generator g min Calculating a minimum wind speed value v min (ii) a The specific formula is as follows:
λ opt ＝Rω g min /Gv i (26)；
wherein R is the length of the blade; g is the transmission ratio of the gear box; v. of i Is the real-time wind speed.
The invention is further illustrated in the following by an optimized design example of a 1.5MW blade.
1) The bezier curves characterize the chord length and twist angle of the blade.
For the wind turbine blade, the chord length and the torsion angle distribution of the wind turbine blade vary greatly from the blade root to the blade tip, and the existing method is difficult to realize the global parameterized expression of the aerodynamic shape of the blade. Therefore, the profile curve of the blade is designed by the multi-step bezier curve.
The Bezier curve of the chord length of the blade and the arrangement of the control points are shown in FIG. 2, the distribution of the chord length of the blade is expressed by adopting a 13 th-order Bezier curve, c 1 And c 2 The control point is fixed and is determined according to the diameter of the blade root; c. C 13 And c 14 To fix the control point, c 13 Has a ordinate of c 12 1.5 times of ordinate, c 14 The coordinate value is 0; c. C 3 ～c 12 The ordinate of (a) is a design variable; c. C 1 ～c 14 The abscissa of (a) is empirically set to a fixed value.
The Bezier curve of the torsional angle of the blade and the arrangement of the control points are shown in FIG. 3. In FIG. 3, the distribution of the torsional angle of the blade is expressed by adopting 13 th-order Bezier curve, and t is 1 、t 2 、t 3 、t 13 And t 14 The control point is fixed and is determined according to experience; t is t 5 ～t 12 Is a design variable, where t 4 And t 6 Value of (a)Etc.; t is t 1 ～t 14 The abscissa of (a) is empirically set to a fixed value. In order to prevent the blade tip from stalling under low wind speed due to torsional deformation, the torsional angle distribution of the blade tip is not optimally designed, but is designed into a fixed curve.
2) And a control variable X.
Taking the ordinate of the control points from 3 rd to 12 th of the chord length distribution of the blade as the variable of the optimized design of the chord length distribution, taking the ordinate of the control points from 5 th to 12 th of the twist angle distribution of the blade as the variable of the optimized design of the chord length distribution, and taking 18 design variables in total;
X＝(c 3 ,c 4 ,c 5 ,c 6 ,.....,c 11 ,c 12 ,t 5 ,t 6 ,......,t 11 ,t 12 )。
3) And an objective function F (x).
The wind speed probability density distribution of a wind field is reflected by adopting Weibull distribution, the shape coefficient k is 2.26, the annual average wind speed is 7m/s, and the maximum annual power generation amount of the blade under the given wind field condition is taken as an objective function:
F(x)＝max(AEP*p1*p2*p3)；
in the formula, AEP is the annual energy production of the blade, and p1, p2 and p3 are penalty factors.
4) And constraint conditions.
For convenience of transportation and manufacturing, the maximum chord length C of the blade is constrained:
C≤3；
and (3) restraining the bending moment M of the root part of the blade and the high thrust T of the wind wheel to the tower drum:
M≤2452.2kN·m；
T≤251.6kN；
5) Optimization algorithm
The particle swarm algorithm has the characteristics of high precision, high convergence speed and the like, so the particle swarm algorithm is adopted for optimizing and designing the blades. The flow of blade optimization design is shown in fig. 1. p is a radical of formula i ,p g Respectively adopting penalty function for the position of the current individual optimal solution and the position of the global optimal solution in the optimization design of the bladeThe method processes the constraint condition, and when the current and the latter target values are smaller than the minimum allowable value, the iteration is finished.
6) Optimizing results
Fig. 4 is a distribution comparison diagram of chord lengths of the optimized blades and chord lengths of the original blades, and fig. 5 is a distribution comparison diagram of twist angles of the optimized blades and twist angles of the original blades. From fig. 4 and 5, it can be seen that the maximum chord length of the optimized blade is 2.95m, and the chord length distribution from the maximum chord length to the middle section of the blade is reduced compared with that of the original blade, but is obviously increased compared with the original blade in the rear half part of the blade. The smaller average chord length of the front half section of the blade is beneficial to reducing the wind wheel thrust of the wind turbine, and the increased average chord length of the rear half section is beneficial to improving the aerodynamic performance of the blade. Through the optimized design of the torsional angle distribution of the blades, the annual generated energy of the optimized blades can be greatly improved on the premise that the bending moment of the blade root and the thrust of the wind wheel are not increased. The comparison of the performance parameters of the optimized and raw blades is shown in table 1.
TABLE 1
FIG. 6 is a graph showing power distribution of the optimized blade and the original blade at different incoming wind speeds and a comparison, and it is obvious from the graph that the optimized blade has better aerodynamic performance than the original blade under the condition of lower than rated wind speed. The Weibull distribution is adopted to reflect the wind speed probability density distribution of a wind field, the shape coefficient k is 2.26, the annual average wind speed is 7m/s, and the combination of the table 1 can obtain that the annual power generation amount of the wind turbine under the original blade is 4.32e + 06kW.h, the annual power generation amount of the optimized blade is 4.67e + 06kW.h, and the annual power generation amount is increased by 8.2%. FIG. 9 is a graph of the operating characteristics of the main machine for optimizing blade matching.
Claims (10)
1. A method for optimizing coupling of aerodynamic profile of wind turbine blade and operating characteristics of a host is characterized by comprising the following steps: s1, constructing a global chord length distribution model of a wind turbine blade;
s2, constructing a global torsion angle distribution model of the wind turbine blade;
s3, selecting a variable construction control variable X from the global chord length distribution model in the S1 and the global torsion angle distribution model in the S2;
s4, constructing constraint conditions of blade chord length C, blade bending moment M and thrust T of a wind wheel to a tower;
s5, constructing an objective function F (X);
the specific formula is as follows:
F(X)＝AEP*p1*p2*p3 (9)；
wherein, AEP is the annual energy production of the blades, and the calculation formula is as follows:
wherein, f (v) i <v 0 <v i+1 ) The wind speed is located at v in one year i And v i+1 A probability of therebetween; p (v) i ) For wind speed at v i The generated power of the wind turbine;
p1, p2 and p3 are penalty factors;
the penalty factor p1 is related to the chord length C of the blade, and when C is less than or equal to C max When p1=1, otherwise, p1= (C) max /C)^2；
The penalty factor p2 is related to the blade root bending moment M, and when M is less than or equal to M max When p2=1, otherwise, p2= (M) max /M)^2；
The calculation formula of the blade root bending moment M is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed;
the penalty factor p3 is related to the thrust T of the wind wheel, when T is less than or equal to T max When p3=1, otherwise, p3= (T) max [ solution ]/T) ^2; the calculation formula of the wind wheel thrust T is as follows:
wherein a is an axial induction factor, and F is a Plantt tip loss correction factor; r is the length of the blade, and rho is the air density; v is the wind speed;
and S6, constructing a particle swarm containing a plurality of particles by taking the design variable X as the particles, and performing iterative optimization processing on each particle swarm to obtain the optimal blade shape.
2. The method for optimizing the coupling between the aerodynamic profile of the wind turbine blade and the operational characteristics of the main engine according to claim 1, wherein in the step S1, the specific steps are as follows: s1.1, constructing n control points, wherein the abscissa of each control point is a fixed value, and a first control point c 1 A second control point c 2 And nth control point c n Is a fixed control point; first control point c 1 And a second control point c 2 Is set as the diameter of the blade root, the n-1 th control point c n-1 Has the ordinate of the (n-2) th control point c n-2 1.5 times ordinate, nth control point c n Has a vertical coordinate of 0, and a third control point c 3 To the n-2 control point c n-2 The ordinate of (a) is a design variable;
s1.2, obtaining an n-1 order Bezier curve C (u) of the wind turbine blade global chord length distribution according to the n control points in the step S1.1:
wherein n is the number of control points; p i The abscissa and the ordinate of the ith control point are represented; u is a scaling factor and u is ∈ [0,1 ]]；
B i,n (u) is Bernstein polynomial, and the specific formula is as follows:
3. the method for optimizing the coupling between the aerodynamic profile of the wind turbine blade and the operational characteristics of the main engine according to claim 1, wherein in the step S2, the specific steps are as follows: s2.1, constructing m control points, wherein the abscissa of each control point is a fixed value, and the first control point t 1 A second control point t 2 A third control point t 3 M-1 th control point t m-1 And the m-th control point t m Is a fixed control point; first control point t 1 A second control point t 2 And a third control point t 3 Are equal in ordinate; fourth control point t 4 And a sixth control point t 6 Are equal in ordinate; m-1 th control point t m-1 And the m-th control point t m The ordinate of (a) is 0; fifth control point t 5 To the m-2 control point t m-2 The ordinate of (a) is a design variable;
s2.2, obtaining an m-1 order Bezier curve C (u) of the wind turbine blade global torsion angle distribution according to the m control points in the step S2.1;
wherein m is the number of control points; p i The abscissa and the ordinate of the ith control point are represented; u is a scaling factor and u is ∈ [0,1 ]]；
B i,m (u) is a Bernstein polynomial, and the specific formula is as follows:
in order to prevent the blade tip from stalling in advance under the condition of large aeroelastic torsional deformation, the torsional angle distribution of the blade tip is not optimally designed, but a certain amount of reverse torsional angle distribution is given in advance.
4. The aerodynamic profile and main blade of a wind turbine as claimed in claim 1The machine operation characteristic coupling optimization method is characterized in that in step S3, a third control point c in a global chord length model is selected 3 To the n-2 control point c n-2 And the fifth control point t in the torsional angle model 5 To the m-2 control point t m-2 The ordinate of (a) constitutes the control variable X; the control variable X is:
X＝(c 3 ,c 4 ,c 5 ,c 6 ,.....,c n-3 ,c n-2 ,t 5 ,t 6 ,......,t m-3 ,t m-2 ) (5)；
5. the method for optimizing the coupling between the aerodynamic profile of the wind turbine blade and the operating characteristics of the main engine as claimed in claim 1, wherein in the step S4, the specific steps are as follows:
s4.1, constructing the constraint condition of the chord length C of the blade,
C≤C max (6)；
wherein, C max Is a constant value;
s4.2, constructing a constraint condition of the bending moment M of the blade,
M≤M max (7)；
wherein, M max Is a constant value;
s4.3, constructing a constraint condition of the thrust T of the wind wheel to the tower,
T≤T max (8)；
wherein, T max Is a constant value.
6. The method for optimizing the coupling between the aerodynamic profile of the wind turbine blade and the operational characteristics of the main engine according to claim 1, wherein in the step S6, the specific steps are as follows:
s6.1, initializing each particle in the particle swarm;
for each particle's velocity, position and individual optimum P i Carrying out assignment;
s6.2, calculating the annual energy production AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle in the current generation to obtain an objective function value F (X) of each particle;
s6.3, comparing the objective function values F (X) of each particle in the particle swarm, and selecting the value with the maximum value as the global optimum P in the contemporary particle swarm g ；
S6.4, iterating each particle to obtain a next-generation particle;
the iterative formula is
Wherein, w, c 1 ,c 2 ,r 1 ,r 2 Are weight coefficients respectively; x is the number of i k Is the position of the ith particle in the kth generation; v. of i k Velocity of the ith particle in the kth generation; x is a radical of a fluorine atom i k+1 The position of the ith particle in the k +1 generation; v. of i k+1 The velocity of the ith particle in the k +1 th generation; p is a radical of i k Optimal for the ith particle in the kth generation; p is a radical of g k The global optimization is the global optimization of the kth generation of particle swarm;
s6.5, repeating the step S6.2 to calculate the annual energy production AEP, the blade root bending moment M, the wind wheel thrust T and the blade chord length C of each particle of the current generation particle swarm to obtain an objective function value F (X) of each particle;
s6.6, comparing the objective function value F (X) of each particle in the current generation with the objective function value F (X) of each particle in the previous generation, and selecting the individual optimal Pi of each particle in the current generation with the larger objective function value F (X);
s6.7, comparing the objective function values F (X) of each particle in the current-generation particle swarm, and selecting the maximum objective function value F (X) as the global optimal Pg in the current-generation particle swarm;
s6.8, calculating the difference value between the current generation global optimal Pg and the previous generation global optimal Pg, and comparing the difference value with 1; stopping iteration if the variation of the global optimal Pg in the iteration continuously exceeds 10 times is less than or equal to 1, and enabling the particles corresponding to the current global optimal Pg to be in an optimal blade shape; otherwise, steps S6.3-S6.7 are repeated.
7. The method as claimed in claim 1 or 6, wherein the AEP is a mean value of the power p (v) generated in the AEP calculation i ) The calculation of (b) is divided into three cases according to the difference of wind speed: first, when the real-time wind speed v is i Rated wind speed V Forehead (forehead) Time, generator speed omega g Is the maximum rotation speed omega gmax Power generated by a wind turbine p (v) i ) Is rated power P of generator Forehead (forehead) ；
Second case, when v imin ≤v i ≤V Forehead (D) The pitch angle beta of the blade is 0 DEG, and the tip speed ratio is the optimum tip speed ratio lambda opt ；
According to the optimum tip speed ratio lambda opt Calculating the generated power p (v) of the wind turbine i )；
The specific formula is as follows:
λ opt ＝Rω r (v i )/v i (16)；
ω r (v i )＝ω g (v i )/G (17)；
p(v i )＝T(v i )ω g (v i ) (18)；
wherein, ω is r (v i ) The rotational speed of the wind wheel; omega g (v i ) Is the generator speed; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed;
in the third case, when v i ≤v imin When the pitch angle beta of the blade is 0 DEG, the wind wheel rotating speed omega r Constant is omega r ＝ω gmin /G；
According to the rotational speed omega of the wind wheel r Calculating the generated power p (v) of the wind turbine i )；
The specific calculation formula is as follows:
λ(v i )＝Rω g,min /(Gv i ) (19)；
p(v i )＝T(v i )ω gmin (21)；
wherein, λ (v) i ) Is tip speed ratio; g is the transmission ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is the air density.
8. The method as claimed in claim 7, wherein the rated wind speed v is a rated wind speed Forehead (D) The calculation process of (c) is as follows: when the wind speed reaches the rated wind speed v Forehead (D) Time, generator speed omega g At maximum speed of rotation omega gmax The pitch angle beta =0 DEG according to the rotation speed omega of the generator gmax Determining the rated wind speed v Forehead (forehead) The concrete formula is as follows:
T(v i )＝p forehead (forehead) /ω gmax (22)；
λ(v i )＝Rω g,max /(Gv i ) (24)；
Wherein, λ (v) i ) Is tip speed ratio; g is the gear ratio of the gear box; t (v) i ) Is the torque of the generator; r is the length of the blade; v. of i Is the wind speed; ρ is nullThe air tightness; a' is a tangential induction factor; r is the length of the blade.
9. The method as claimed in claim 7, wherein the optimum tip speed ratio λ is a value obtained by optimizing the coupling between the aerodynamic profile of the wind turbine blade and the operational characteristics of the main engine opt The calculation process of (c) is as follows:
firstly, according to the power coefficient C of the blade P Obtaining C under a 0-degree pitch angle by a relational expression of tip speed ratio lambda P -a λ -curve;
coefficient of power of blade C P The relationship to tip speed ratio λ is as follows:
wherein a' is a tangential induction factor; r is the length of the blade, and lambda is the tip speed ratio;
then, according to C P Obtaining optimum tip speed ratio lambda of blade by lambda curve opt ；
According to the maximum power coefficient C of the blade Pmax Size of (1), C P Flatness of the top of the lambda curve and lambda opt Three criteria of size of (2) select λ opt 。
10. The method as claimed in claim 9, wherein the blade is operated at an optimum tip speed ratio λ opt Minimum wind speed v of min The calculation process of (2) is as follows:
when real-time wind speed v i Decrease to v min While, the rotational speed omega of the generator g Is omega gmin ；
According to the optimum tip speed ratio lambda opt And the rotational speed omega of the generator gmin Calculating a minimum wind speed value v min (ii) a The specific formula is as follows:
λ opt ＝Rω gmin /Gv i (26)；
wherein R is the length of the blade; g is the transmission ratio of the gear box; v. of i Is the real-time wind speed.
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Address after: 451191 No. 1 Huaihe Road, Shuang Hu Economic and Technological Development Zone, Xinzheng, Zhengzhou, Henan Patentee after: ZHONGYUAN University OF TECHNOLOGY Address before: 451191 No. 1 Huaihe Road, Shuanghu Town Economic and Technological Development Zone, Zhengzhou City, Henan Province Patentee before: Zhongyuan University of Technology |
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Granted publication date: 20180216 Termination date: 20211228 |