An Inverse Method for Wind Turbine Blade Design with Given Distributions of Load Coefficients

Abstract

It is shown in the literature that wind turbine designs with different load distributions have different wake features. To systematically study how different load distributions affect turbine wakes, a method for designing variants of blades with different radial load distributions, but with approximately the same power ($C_P$) or thrust coefficient ($C_T$), is needed. In this work, an inverse design method based on the blade element momentum method and the multi-dimensional Newton’s method, with the normal and tangential force coefficients as the design objective and iterations for satisfying the $C_P$ or $C_T$ constraint, is developed. The proposed method is validated using the two-bladed small-scale NREL phase VI S809 wind turbine blade design and the three-bladed utility-scale NREL 5 MW wind turbine blade design. Four variants of the NREL 5 MW wind turbine, i.e., the Root-CP, Tip-CP, Root-CT, and Tip-CT designs, which represent the variants of the original design (NREL-Ori) with a higher load near the blade root and tip regions with approximately the same power coefficient ($C_P$) or thrust coefficient ($C_T$) as that of the NREL-Ori design, respectively, are then designed using the proposed method. At last, the flapwise blade bending moment and the power coefficients from different variants of the NREL 5 MW turbine are compared for different tip speed ratios, showing that the “Root” designs are featured by a wider chord near the root, lower blade bending moment, and higher power coefficients for tip-speed ratios greater than nine.

1. Introduction

Driven by the increasing demand for energy systems with low or net-zero carbon emission to slow climate change, wind energy is becoming one of the fastest growing renewable energies [1,2,3,4]. Innovative designs of blades can increase the performance of wind turbines and decrease the wind energy capital expenditures. Moreover, recent studies show that the blade design can also affect the dynamics of wind turbine wakes [5,6]. This work is devoted to develop a blade design method for designing blades with certain radial distributions of load coefficients.

The methods for designing wind turbine blades can be classified into two categories: (i) the direct approach which is also called the design-by-analysis approach, and (ii) the inverse design approach. To design a blade, a wind turbine performance solver is required, such as the blade element momentum (BEM) method [7,8,9,10], the vortex line method (VLM) [11,12,13,14], and the computational fluid dynamic method [15,16,17,18,19]. The BEM method [7,9] is the one routinely used because of its reasonable accuracy and low computational cost. In the BEM method, the performance of the rotor is computed using the one-dimensional momentum method with aerodynamics forces at each radial location computed using the blade element approach with tables of blade twist and chord distributions, airfoil type distribution, and lift and drag coefficients for different angles of attack and Reynolds numbers. The VLM represents the wind turbine blade as a series of bound vortex and trailing vortices, which can model the blade aerodynamics more accurately, but is more computationally expensive when compared with the BEM method. The CFD method, including large eddy simulation (LES) and Reynolds-averaged Navier Stokes (RANS) approaches, especially when coupled with the non-boundary conforming method [20,21,22,23], can simulate the blade aerodynamics in a more accurate and efficient way, however requires significantly high computational cost especially for the DNS and LES approaches, which are not yet feasible for blade design in engineering applications.

In the aforementioned blade design approaches, the direct approach, which prescribes and adjusts the blade geometry, and then determines the performance through analysis [24,25], is easy to implement, however its performance depends on the experience of the user and may become time consuming. In practice, an optimization method is often employed with a specific objective function when designing a wind turbine blade [26]. Chattot [11] used the Lagrange multiplier technique to determine distributions of blade twist and chord. Juan Méndez and David Greiner [27] adopted the genetic algorithms to optimize the wind blade chord and twist distributions with the objective of maximizing the power output. Since the direct approach is time consuming with no guarantee of achieving the desired optimum values, an inverse design approach was developed by Selig and Tangler [24]. They combined the multi-dimensional Newton’s iteration method with the BEM method to design the blade twist and chord distributions with the desired distributions of the lift coefficient and the axial induction factor along the blade radial directions. To account for the three-dimensional blade features, Lee [28] combined the multi-dimensional Newton’s iteration method with a vortex line method to design the blade geometry. Wind turbine wakes are closely related with the force distribution along the blade. Instead of using the lift coefficient and the axial induction factor as the input in the inverse design method [24,28], in this work, we employ the normal and tangential force coefficients as the input, which are more convenient for designing blades with different load distributions.

To systematically study how the blade design affects the wake evolution, blade designs with different load distributions have to be developed. It will be convenient if one can obtain such blade designs from the existing wind turbine blade design. To achieve this objective, in this paper, we develop an inverse method based on the multi-dimensional Newton’s iteration method and the BEM method, and design four variants of the NREL 5 MW wind turbines [29,30], i.e., (i) the Root-CP, (ii) the Tip-CP, (iii) the Root-CT, and (iv) the Tip-CT wind turbines, which represent the designs with a higher load near the blade root and tip with approximately the same power coefficient ($C_P$) or the thrust coefficient ($C_T$), respectively.

The novelty of the proposed method underpins on the design objectives, i.e., variants of blade designs with different radial distributions of normal and tangential load coefficients with approximately the same power or thrust coefficient, which are the radial distributions of the lift coefficient and axial induction factor in the methods developed by Selig and Tangler [24] and Lee [28]. The axial induction factor, a quantity describing the momentum loss as the air flows through the rotor, is not directly related with the forces exerted on the blade. For the simulations with the rotor parameterized using the actuator disk [15], which employs the axial induction factor as the input, therefore using the axial induction factor as the design objective is a right choice. For the actuator line/surface simulations [17,31], where each blade is modeled using distributed forces, directly using the load coefficients as the design objectives is obviously better suited. One drawback of the method developed in this work is the low fidelity of the employed blade element momentum method for modeling the aerodynamics of wind turbines, which depends on the quality of the lift and drag coefficients as well as the corrections for the three-dimensional effect and the tip loss correction [9].

The rest of the paper is structured as follows. The inverse design method is introduced in Section 2. In Section 3, the inverse method is validated for the two-bladed NREL phase VI S809 wind turbine and the three-blade NREL 5 MW wind turbine. Then, four variants of the NREL 5 MW turbine are designed and presented in Section 4. At last, conclusions are drawn in Section 5.

2. The Inverse Method for Blade Design

In this section, the inverse method for designing blades with given distributions of force coefficients is described. The present inverse design method employs the desired normal force coefficient $C_{n_d}\left(r\right)$ and tangential force coefficient $C_{t_d}\left(r\right)$ as the input, and gives the radial distributions of the chord $c\left(r\right)$ and twist $\theta \left(r\right)$ as the output. Using the multi-dimensional Newton’s method, the radial distributions of $c\left(r\right)$ and $\theta \left(r\right)$ are computed as follows:

$${\mathbf{X}}^{k+1}={\mathbf{X}}^k-\mathbf{J}{\left({\mathbf{X}}^k\right)}^{-1}\mathbf{F}\left({\mathbf{X}}^k\right),$$

(1)

where:

$$\begin{array}{c}\hfill \mathbf{X}=\left[\begin{array}{c}\theta \left(r_1\right)\\ ⋮\\ \theta \left(r_n\right)\\ c\left(r_1\right)\\ ⋮\\ c\left(r_n\right)\end{array}\right],\mathbf{F}\left(\mathbf{X}\right)=\left[\begin{array}{c}\delta {\left(C_n\right)}^1\\ ⋮\\ \delta {\left(C_n\right)}^n\\ \delta {\left(C_t\right)}^1\\ ⋮\\ \delta {\left(C_t\right)}^n\end{array}\right],\end{array}$$

(2)

and J is the Jacobian matrix formed as follows:

$$\begin{array}{c}\hfill {\mathbf{J}}_{ij}=\left[\begin{array}{ccc}\frac{\partial F_1}{\partial x_1}& \cdots & \frac{\partial F_1}{\partial x_N}\\ ⋮& \ddots & ⋮\\ \frac{\partial F_N}{\partial x_1}& \cdots & \frac{\partial F_m}{\partial x_N}\end{array}\right]=\left[\begin{array}{cccccc}\frac{\partial \delta {\left(C_n\right)}_{\theta \left(r_1\right)}^1}{\partial \theta \left(r_1\right)}& \cdots & \frac{\partial \delta {\left(C_n\right)}_{\theta \left(r_n\right)}^1}{\partial \theta \left(r_n\right)}& \frac{\partial \delta {\left(C_n\right)}_{c\left(r_1\right)}^1}{\partial c\left(r_1\right)}& \cdots & \frac{\partial \delta {\left(C_n\right)}_{c\left(r_n\right)}^1}{\partial c\left(r_n\right)}\\ ⋮& \ddots & ⋮& ⋮& \ddots & ⋮\\ \frac{\partial \delta {\left(C_n\right)}_{\theta \left(r_1\right)}^n}{\partial \theta \left(r_1\right)}& \cdots & \frac{\partial \delta {\left(C_n\right)}_{\theta \left(r_n\right)}^n}{\partial \theta \left(r_n\right)}& \frac{\partial \delta {\left(C_n\right)}_{c\left(r_1\right)}^n}{\partial c\left(r_1\right)}& \cdots & \frac{\partial \delta {\left(C_n\right)}_{c\left(r_n\right)}^n}{\partial c\left(r_n\right)}\\ \frac{\partial {\left(C_t\right)}_{\theta \left(r_1\right)}^1}{\partial \theta \left(r_1\right)}& \cdots & \frac{\partial {\left(C_t\right)}_{\theta \left(r_n\right)}^1}{\partial \theta \left(r_n\right)}& \frac{\partial {\left(C_t\right)}_{c\left(r_1\right)}^1}{\partial c\left(r_1\right)}& \cdots & \frac{\partial {\left(C_t\right)}_{c\left(r_n\right)}^1}{\partial c\left(r_n\right)}\\ ⋮& \ddots & ⋮& ⋮& \ddots & ⋮\\ \frac{\partial {\left(C_t\right)}_{\theta \left(r_1\right)}^n}{\partial \theta \left(r_1\right)}& \cdots & \frac{\partial {\left(C_t\right)}_{\theta \left(r_n\right)}^n}{\partial \theta \left(r_n\right)}& \frac{\partial {\left(C_t\right)}_{c\left(r_1\right)}^n}{\partial c\left(r_1\right)}& \cdots & \frac{\partial {\left(C_t\right)}_{c\left(r_n\right)}^n}{\partial c\left(r_n\right)}\end{array}\right].\end{array}$$

(3)

In the above equations, n denotes the number of elements along the blade in the radial direction, and $\delta \left(C_{n,t}\right)$ represents the difference between the computed value and the desired value. To get a better idea on the structure of the Jacobian matrix, a schematic is shown in Figure 1. As seen, in the first row, the first (I) and second quadrants (II) describe the rate of change of the normal force coefficient ($C_n$) to the change of the twist angle ($\theta$) and the change of the blade chord (c) at each element, respectively. Meanwhile, in the second row, the third (III) and fourth quadrants (IV) describe the rate of change of the tangential force coefficient ($C_t$) to the change of the twist angle ($\theta$) and the change of the blade chord (c) at each radial element, respectively.

The values of Jacobian J are calculated using a second-order finite difference scheme. In the Jacobian J, $F_i$ is the difference between the values of $C_n$ and $C_t$ calculated by the BEM method and the desired values of $C_{n_d}$ and $C_{t_d}$, respectively. Details on the implementation of the BEM method can be found in Appendix A. For example, $F_1$ is computed as follows:

$$\begin{array}{c}\hfill F_1=\delta {\left(C_n\right)}_{\theta \left(r_1\right)}={\left(C_n\right)}_{\theta \left(r_1\right)}-{\left(C_{n_d}\right)}_{r_1}\end{array}$$

(4)

where ${\left(C_n\right)}_{\theta \left(r_1\right)}$ is the $C_n$ at the first element when $\theta$ is the variable. A second-order, finite central difference scheme is used to compute the Jacobian matrix. For example, $J_{11}$ is computed by:

$$\begin{array}{cc}\hfill J_{11}& =\frac{\delta {\left(C_n\right)}_{\theta \left(r_1\right)+\delta \theta }-\delta {\left(C_n\right)}_{\theta \left(r_1\right)-\delta \theta }}{2\delta \theta }\hfill \\ \hfill & =\frac{[{\left(C_n\right)}_{\theta \left(r_1\right)+\delta \theta }-{\left(C_{n_d}\right)}_{r_1}]-[{\left(C_n\right)}_{\theta \left(r_1\right)-\delta \theta }-{\left(C_{n_d}\right)}_{r_1}]}{2\delta \theta }\hfill \\ \hfill & =\frac{[{\left(C_n\right)}_{\theta \left(r_1\right)+\delta \theta }-{\left(C_n\right)}_{\theta \left(r_1\right)-\delta \theta }]}{2\delta \theta }\hfill \end{array}.$$

(5)

A flowchart for the inverse design method is shown in Figure 2. At first, the desired wind turbine performance $C_{n_d}$ and $C_{t_d}$ are read from the input files, meanwhile the initial values of the blade geometrical parameters ($\theta \left(r\right)$ and $c\left(r\right)$) are assigned to $\mathbf{X}$. Then the BEM code (shown in blue in Figure 2) is performed to provide the computed aerodynamic behavior ($C_n$ and $C_t$). Once $\mathbf{J}$ and $\mathbf{F}$ are obtained, the linear algebraic equation in Equation (1) is solved to obtain new values of X. At this step, the $l^2$-norm is used to check the convergence of the solutions, which is defined as:

$$l^2=\sqrt{\sum _{i=1}^n{|\theta \left(i\right)}^{k+1}-\theta {\left(i\right)}^k{|}^2+\sum _{i=1}^n{|c{\left(i\right)}^{k+1}-c{\left(i\right)}^k|}^2},$$

(6)

where i denotes the index of the blade element at each radial position and k is the number of Newton’s iteration. In our study, ${10}^{-3}$ is set as the convergence criteria of the $l^2$-norm, which is found to be sufficient to guarantee the accuracy and computational efficiency.

Having approximately the same $C_P$ or $C_T$ will enable a fair comparison among the blade designs with different force distributions. However, this cannot be directly satisfied when we design the blade with the given normal and tangential force coefficients as $C_P$ and $C_T$ being dependent on the chord at different radial locations as well, which is the output when designing a blade. In this work, we solve this problem via an iterative way. Specifically, we multiply the load distribution with a coefficient and manually tune its value based on the $C_P$ and $C_T$ of the obtained blade design.

3. Validations

In this section, the proposed method is validated with the two-bladed NREL phase VI S809 [32,33,34] wind turbine and three-bladed NREL 5 MW [29,30] wind turbine. The parameters of the two turbines are shown in

Table 1. Wind turbine parameters.

Turbines	Number of Blades	TSR	Pitch (deg)	R (m)	Rb (m)
NREL S809	2	8	0	5.029	1.51
NREL 5 MW	3	8	0	63.0	9.7

, the tip speed ratio ($\lambda =\frac{\omega R}{V_0}$, TSR) is set to be 8, which is defined as the ratio between the tangential speed at the blade tip ($\omega R$) and the incoming wind speed $V_0$. For both cases, 200 elements are used for discretizing the blade. Note that the blade root region of the cylinder shape is not designed with starting position at 1.51 m and 9.7 m along the blade radial directions for NREL S809 and NREL 5 MW wind turbines, respectively. In the case of the two-bladed S809 wind turbine, the 2D polar data of this airfoil at $Re=5\times {10}^5$ were obtained from XFOIL [35].

Firstly, with the reference data of the twist and chord for both turbines, the BEM simulations are carried out to obtain the $C_n$ and $C_t$, which are used as the input data for the validation of the proposed method. By prescribing the distributions of $C_n$ and $C_t$, the distributions of the blade twist ($\theta$) and chord (c) are designed using the proposed method with the initial distributions of $\theta$ and c off the actual data. The $\theta$ and c designed using the proposed method are then compared with the reference data of the two-bladed NREL phase VI S809 and three-bladed NREL 5 MW wind turbines.

The convergence history for the NREL phase VI turbine is shown in Figure 3, and the black-dashed line shows the convergence threshold. As seen, it takes 5 steps for the multi-dimensional Newton’s iterations to converge.

The twist ($\theta$) and chord (c) distributions designed by the proposed method (blue dots) are compared with the published data (red lines) for the NREL phase VI wind turbine in Figure 4. As seen, the design of the proposed method agrees well with the actual design of the blade.

Figure 5 shows the comparison of the $C_n$ and $C_t$ from the design using the proposed method (blue dots) with the reference data (red lines), with the black-dashed lines showing the $C_n$ and $C_t$ of the initial design. As seen, the $C_n$ and $C_t$ obtained by the proposed method converge to the desired values.

In the following, the validation results for the NREL 5 MW wind turbine are presented. Figure 6 shows the convergence history with the residual $l^2$-norm of ${10}^{-3}$ is used. It is seen that the solutions converge after four Newton’s iterations.

Figure 7 shows the twist and chord distributions of the NREL 5 MW turbine blade, in which the initial and converged distributions are shown with the black dashed lines and the blue dots, respectively, with the original distributions shown by the red solid lines. It is found that the design of the proposed method matches well with the original data of the NREL 5 MW turbine blade.

Figure 8 shows the distributions of the thrust and tangential force coefficients. As seen, an excellent agreement between the converged values and the desired values is achieved over the entire blade radial locations. It is noticed that step-like changes are observed on these curves especially for $C_n$ for both the design from the present work that is referenced. This is caused by the change of the airfoil type at those locations instead of any convergence issue with the proposed method.

4. Four Variants of the NREL 5 MW Wind Turbine

In this section, the proposed method is applied to design four variants of the NREL 5 MW wind turbine [29] with different radial load distributions, including (i) the Root-CP design, (ii) the Tip-CP design, (iii) the Root-CT design, and (iv) the Tip-CT design. Note that the original NREL 5 MW wind turbine is named as the NREL-Ori turbine in the following parts. Besides, the Root-CP and Tip-CP types of wind turbines are obtained by keeping approximately the same power coefficient as that of the NREL-Ori turbine, meanwhile the Root-CT and Tip-CT wind turbines are inversely designed with the constraints of keeping approximately the same thrust coefficient as that of the NREL-Ori turbine. The “Root” and “Tip” turbines represent the designs with higher normal loads near the blade root and tip regions, respectively, when compared with the original design. The tip speed ratio is kept at 8 in this work.

To design the variants of NREL 5 MW wind turbine, the radial distribution of the thrust coefficient ($C_n$) of the original design is modified. For the “Root” and “Tip” variants of design, the thrust coefficients are obtained by adding a linear function with zero mean to the original distribution. During the inverse design process, the distributions of $C_n$ were slightly modified by multiplying a value approximately one in an iterative way to keep approximately the same power coefficient or thrust coefficient as the original design. Figure 9 shows that the same initial twist and chord distributions are used in the inverse design of the (i) Root-CP, (ii) Tip-CP, (iii) Root-CT, and (iv) Tip-CT cases. The red lines represent the twist and chord distributions of the original NREL turbine, while the green lines represent the initial values used in the other four cases. As seen, the same initial values are used for all cases.

In practice, blade twist and chord distribution should be smooth enough for the manufacturing process. Therefore, in the present study, the twist and chord distributions designed by the proposed method are smoothed using the univariate spline method with the smoothing factor selected as 0.5 [36,37]. Figure 10 plots the obtained distributions of twist and chord. Meanwhile, the blade shapes from different variants of designs are shown in Figure 11 and Figure 12. In the middle part of the blade, it is seen that the chord lengths of the “Tip” type blades are narrower and wider in the near-root and near-tip regions, respectively, which are in the exact opposite way for the “Root” type blade designs, a result from the different distributions of the force coefficients for the two types of blade designs. The momentum mixing in wind turbine wakes happens at different scales. In the shear layer near the wake boundary in the radial direction, a larger gradient of the streamwise velocity in the radial direction can result in a higher mixing rate, which is the case for the “Tip”-type blades as shown in our recent work [38]. In a larger scale, the entertainment of the wake is affected by its large scale, low frequency motion in the crosswise direction, the so-called wake meandering. The literature has shown that the hub vortex plays an important role on the initiation and intensification of the wake meandering. It was shown in [38] that, compared with the “Tip” type blades, the turbulent mixing of the wake of the “Root” type blade is lower in the near wake but higher in the far wake, which is probably related to the onset of wake meandering being different for the two designs.

The performance of the variants of the NREL 5 MW turbine is shown in

Table 2. Performances of different variants of the NREL 5 MW wind turbine designs.

Constraints	Turbines	${\mathit{C}}_{\mathit{T}}$	${\mathit{C}}_{\mathit{P}}$	Differences	Differences
Same $C_P$	NREL-Ori	0.770	0.506	-	-
	Root-CP	0.791	0.506	+2.76%	-
	Tip-CP	0.835	0.506	+8.47%	-
Same $C_T$	Root-CT	0.770	0.50	-	−1.33%
	Tip-CT	0.770	0.483	-	−4.68%

. It is seen that when keeping the same power coefficients, the thrust coefficients of the Root-CP and Tip-CP turbines are slightly higher than the NREL-Ori turbine at −2.76% and 8.47%, respectively. While keeping the same thrust coefficients, compared with the NREL-Ori turbine, the power coefficients of the Root-CT and Tip-CT are somewhat less, at −1.33% and 4.68%, respectively.

The thrust coefficient and the tangential force coefficient of the designs of the variants of the NREL 5 MW turbine are plotted in Figure 13. Meanwhile, the thrust and tangential force are plotted in Figure 14. As seen, compared with the NREL-Ori turbine, the “Root” type designs (both Root-CP and Root-CT) have higher loads near the blade root and lower loads near the blade tip, while the loads of the “Tip” designs (both Tip-CP and Tip-CT) are distributed in an opposite way. It should be emphasized that the objective of this work is to design turbine blades with different force distributions in the radial direction, which has been shown to have significant effects on the evolution of wind turbine wakes [5,38]. The blade designs obtained here together with the original design provide a basis for a systematic study on how different blade designs affect the wake characteristics.

The blade bending moment plays an important role when carrying out fatigue analysis on turbine blades. In

Table 3. The coefficients of the blade flapwise bending moment for different turbine designs.

Constraints	Turbines	${\mathit{C}}_{{\mathit{M}}_{\mathit{b}}}$	Differences
Same $C_P$	NREL-Ori	0.525	-
	Root-CP	0.508	−3.24%
	Tip-CP	0.604	15.1%
Same $C_T$	Root-CT	0.491	−6.48%
	Tip-CT	0.563	7.24%

, the coefficient of the flapwise bending moment about the hub is examined for different turbine designs, which is defined as,

$$\begin{array}{c}\hfill C_{M_b}=\frac{M_b}{0.5B\rho \pi R^3{V_0}^2}\end{array}$$

(7)

where $M_b$ is the flapwise bending moment, which can be calculated using Equation (8). As seen, when compared with the original design (NREL-Ori), the $C_{M_b}$ from the Root-CP and Root-CT turbine designs is reduced by 3.24% and 6.48%, respectively, which, on the other hand, is increased by $15.1\%$ and $7.24\%$ for the Tip-CP and Tip-CT designs, respectively.

$$\begin{array}{c}\hfill M_b={\int }_0^{R}rd{F}_n\end{array}$$

(8)

The power coefficient ($C_P$) and the thrust coefficient ($C_T$) as a function of the tip speed ratio are plotted in Figure 15 for the variants of the NREL 5 MW wind turbine. As seen, the power coefficients ($C_P$) of the (i) Root-CP, (ii) Tip-CP, and (iii) Root-CT designs are almost the same with that of the NREL-Ori design when $\lambda$ is less than nine. When $\lambda$ is greater than nine, the (i) Root-CP and (ii) Root-CT designs have a higher power coefficient than the NREL-Ori design. Considering that the “Root” type designs have lower loads near the tip and thus lower bending moments and tip-induced noise, we argue that the NREL-Root design is more robust when compared with the original design. As for their effects on wind turbine wakes, more efforts are needed in the future work.

5. Conclusions

Radial distributions of blade loads affect the streamwise evolution of wind turbine wakes [5,38]. In this work, we developed an inverse method for blade designs with given distributions of normal and tangential force coefficients, and designed four variants of the NREL 5 MW wind turbine. The proposed method employs the multi-dimensional Newton’s method to design the chord and twist distributions with the normal and tangential force coefficients as the design objective, in which the blade element momentum method is employed for modeling the aerodynamics of the wind turbine. To ensure different variants of the blade designs giving the same power or thrust coefficients, the given normal force coefficients are multiplied by a coefficient, which is determined in an iterative way. The proposed method is validated using the two-bladed NREL phase VI S809 wind turbine and the three-bladed NREL 5 MW wind turbine. It is observed that the distributions of blade twist and chord designed using the proposed method agree well with the corresponding published data.

The proposed method is then applied to design four variants of the NREL 5 MW (NREL-Ori) wind turbine design, i.e., the Root-CP, Tip-CP, Root-CT, and Tip-CT designs, which have a higher load near the blade root or tip (as indicated by the left part of the name) with approximately the same power or thrust coefficients (as indicated by the right part of the name) as the original turbine design. It is observed that “Root” designs have a wider chord in the near-root region, where the chord of the “Tip” designs are relatively narrow when compared with the original NREL-Ori design. The blade flapwise bending moment about the hub is also compared for different designs, with less load observed for the “Root” (both Root-CP and Root-CT) designs. As for the power coefficients of the new designs, it is observed that the power coefficients of the Root-CP and Root-CT designs are almost the same with the original design for a TSR ($\lambda$) less than nine. When the $\lambda$ is larger than nine, the power coefficients of the “Root” designs are larger than the original design.

Note that the BEM method, as a low-fidelity method, cannot accurately take into account the three-dimensional effect. Although the power and force coefficients of the same blade design cannot be exactly the same with those shown in Table 2 when they are computed using a high-fidelity method, we believe that they will be close to each other and the major goal of having variants of designs with different distributions of load coefficients can still be achieved.

The present work has focused only on the load distributions without considering the structure of the blade, cost of the materials, etc. Future work shall be carried out to include more objectives in the design of the blade. To re-emphasize: The purpose of designing variants of blades is to examine how different designs affect the dynamics of wind turbine wakes. Studies on the wake dynamics of the four variants of NREL 5 MW turbine will be carried out in our future work.