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MARE-WINT pp 309-334 | Cite as

CFD Study of DTU 10 MW RWT Aeroelasticity and Rotor-Tower Interactions

  • Sergio González HorcasEmail author
  • François Debrabandere
  • Benoît Tartinville
  • Charles Hirsch
  • Grégory Coussement
Open Access
Chapter

Abstract

A numerical analysis of the DTU 10 MW RWT wind turbine aerodynamics is presented in this work. The development of an innovative methodology based on three-dimensional computational fluid dynamics allowed to tackle two challenging problems related to this application. On one hand, the impact of blade deflections on rotor performance was assessed in a rotor-only context. Different blade configurations were studied, including the installation of Gurney flaps and the consideration of prebending and preconing. On the other hand, flow unsteadiness of the full machine (i.e. including the tower) was modeled by means of the Non-Linear Harmonic method. This approach allowed to characterize local aspects of the flow and the impact of rotor-tower interactions on the computed loads.

Keywords

Computational Fluid Dynamics Wind Turbine Reynolds Average Navier Stokes Reynolds Average Navier Stokes Offshore Wind Turbine 
These keywords were added by machine and not by the authors. This process is experimental and the keywords may be updated as the learning algorithm improves.

18.1 Introduction

Industry standards for the aeroelastic simulations of horizontal axis wind turbines are based on the Blade Element Momentum (BEM) theory. For classical machine designs, such a method offers a very good computational efficiency and an acceptable flow response. BEM base formulation has been improved along with onshore wind turbines evolution, thanks to the introduction of additional sub-models (Jonkman and Buhl 2007; Heege et al. 2013). The accuracy of this approach is however limited when dealing with large Offshore Wind Turbine (OWT) rotors due to the existence of highly skewed flows and heavy detachments. Hence, the use of more sophisticated Computational Fluid Dynamics (CFD) techniques is justified.

Due to the continuous upscaling of modern OWTs, important aeroelastic effects are also expected. Traditional CFD approaches do not consider the flexibility of the rotor. However, blade deflections can have a non negligible impact on the machine performance, and a possible blade-tower impact should be considered at the design stage. This requires the consideration of rotor structural models in CFD computations. Due to the lack of publicly available industrial configurations, previous studies concerning wind turbines aeroelasticity are based on the so-called academic or reference designs. In this group we find the works of Corson et al. (2012) for the SNL-100-00 blade and the studies of the NREL 5 MW performed by Hsu and Bazilevs (2012) and Yu and Kwon (2014). In all these publications, blade deflections were found to have a direct impact on the final rotor performance.

Previous CFD studies of wind turbine rotors are based on steady flow rotor-only simulations (where only blades, hub and nacelle geometries are considered). Thanks to the problem periodicity when assuming an incoming wind aligned with the rotor axis, a single blade passage is normally meshed. These simulations allow to characterize the local flow behaviour around the wind turbine and its impact on global rotor performance with a reduced computational effort. However, by omitting the tower geometry the main source of flow unsteadiness is also neglected. Indeed, due to the proximity of the rotor to the tower, the generation of complex unsteady flow phenomena is expected. This mechanism is often referred as rotor-tower interactions. First NREL Phase VI publications assessing this topic revealed the existence of both blade and tower shedding phenomena and fluctuating loads generation related to the blade-tower alignment event (Zahle et al. 2009; Lynch 2011; Wang et al. 2012; Hsu et al. 2014; Li 2014). Similar unsteady effects were computed for the NREL 5 MW studies of Hsu and Bazilevs (2012) and Yu and Kwon (2014), and in the industrial wind turbines publications of Zahle and Sørensen (20082011).

In this chapter high fidelity CFD models were used in order to characterize the rotor aerodynamics of the DTU 10 MW RWT reference wind turbine (Bak et al. 2013), whose main parameters are summarized in Table 18.1. Aeroelasticity and rotor-tower interactions problems were assessed in two independent numerical studies. In Sect. 18.2, rotor-only simulations were performed based on the computational framework for OWT rotors static aeroelasticity analysis developed by Horcas et al. (2014). In particular, the impact of Gurney flaps installation and the effect of prebending and preconing on rotor performance were evaluated. This work can be understood as a continuation of previous DTU 10 MW RWT studies (Horcas et al. 2015a,b). In Sect. 18.3, the flow unsteadiness related to rotor-tower interactions was characterized by means of the Non Linear Harmonics (NLH) method presented by Vilmin et al. (2006).

The present computational analysis was performed using the commercial CFD package FINETM/Turbo (NUMECA International 2013b). This tool was previously validated in the framework of NREL Phase VI rotor-only simulations by other authors (Fan and Kang 2009; Elfarra et al. 2014; Suárez et al. 2015a,b). The FINETM/Turbo solver is a three-dimensional, density-based, structured, multi-block finite volume code. A central-difference scheme is employed for the spatial discretization with Jameson type artificial dissipation. A four-stage explicit Runge-Kutta scheme is applied for the temporal discretization. Multi-grid method, local time-stepping and implicit residual smoothing are used in order to speed-up the convergence.

Table 18.1

DTU 10 MW RWT main parameters

Parameter description

Parameter value

 

Cut in wind speed

4 m s−1

 

Cut out wind speed

25 m s−1

 

Rated wind speed

11.4 m s−1

 

Rated power

10 MW

 

Number of blades

3

 

Rotor diameter

178.3 m

 

Min. rotor speed

6 RPM

 

Max. rotor speed

9.6 RPM

 

Hub height

119 m

 

Tower diameter top

5.5 m

 

Tower diameter base

8.3 m

 

Tower clearance

18.26 m

 

18.2 DTU 10 MW RWT Rotor-Only Analysis

In this section, a complete characterization of DTU 10 MW RWT aeroelasticity in a rotor-only framework is presented. A Reynolds Averaged Navier Stokes (RANS) approach was used in order to perform steady flow simulations of this OWT. Turbulence was considered by means of the Spalart–Allmaras model (Spalart and Allmaras 1992). Rotor was considered either as rigid or flexible. For the latter case, the consideration of a blade structure sub-model was necessary. Mesh deformation was carried out by the 3-steps hybrid method described in Horcas et al. (2015a).

First computations included in Sect. 18.2.1 were based on the standard DTU 10 MW RWT rotor, assuming a rigid configuration. Straight blades were considered, equipped with the so-called Gurney flaps devices at low span range [20 %, 30 %] (see Fig. 18.1). Obtained results were compared with three-dimensional CFD simulations performed by other authors. The same methodology was used in Sect. 18.2.2 to compare the performance of this standard blade with a clean variant, where the Gurney flaps were removed. Both rigid and flexible rotor configurations were studied. Finally, in Sect. 18.2.3 the impact of of prebending and preconing on DTU 10 MW RWT aeroelastic behaviour is assessed.

Fig. 18.1

DTU 10 MW RWT straight blade geometry equipped with Gurney flaps. (a ) Low span zoom. (b ) Global view

18.2.1 Steady Aerodynamics, Standard Geometry

In this section, the DTU 10 MW RWT standard rotor was studied for the 0 pitch operating range compiled in Table 18.2. The hypothesis of rigid blades was made.

Table 18.2

DTU 10 MW RWT aerodynamic load cases definition

DLC Identifier

Wind speed [ms−1]

RPM

 

FT_WSP07

7

6.000

 

FT_WSP08

8

6.426

 

FT_WSP09

9

7.229

 

FT_WSP10

10

8.032

 

FT_WSP11a

11

8.836

 

a FT_WSP11 being very close to the wind turbine design point, it is referred in this document as rated speed

Autogrid5TM structured grids generator was used in order to perform a three-dimensional mesh of the DTU 10 MW RWT rotor (NUMECA International 2013a). Blade surfaces as well as original nacelle and hub geometries were included in this process. A blocking topology was established around the blade, putting special attention in the local mesh around the blunt edge and blade tip. A single blade passage was meshed, accounting for 7. 2 × 106 nodes and 24 blocks. A first cell size of 3. 0 × 10−5 m was imposed around the considered geometry, in order to properly describe the boundary layer for the studied wind speed range. Flow inlet and outlet were located at 2.2 and 3.2 blade radius from the nacelle respectively. Figure 18.2 shows a global overview of the mesh. For clarity purposes the three blades are displayed, and 1 out of 2 grid lines are skipped. In Fig. 18.3a, the cross-section mesh at mid-span is illustrated. The geometry of Gurney flaps at 20 % of span together with the surrounding cross-section mesh are shown in Fig. 18.3b.

Fig. 18.2

DTU 10 MW RWT surface mesh overview (displayed 1 every 2 grid lines). (a ) Global view. (b ) Detail of nacelle and low blade span range

Fig. 18.3

DTU 10 MW RWT cross-section meshes, 20 and 50 % span. (a ) 50 % span. (b ) 20 % span

A good agreement in terms of loads prediction with respect to the three-dimensional RANS computations described in Bak et al. (2013) and performed with EllipSys3D (Sørensen 1995) was observed. A global loads comparison for all the studied operating points is included in Fig. 18.4.

Fig. 18.4

DTU 10 MW RWT total rotor thrust and mechanical power versus wind speed. (a ) Total thrust. (b ) Mechanical power

Recirculations were observed near blade trailing edges at low span range. To illustrate this issue, Fig. 18.5 shows the friction streamlines around the DTU 10 MW RWT for the rated speed operating point. This observation is in-line with EllipSys3D computations performed by Zahle et al. (2014), where an important 3D flow behaviour was found up to an approximated radius of 30 m.

Fig. 18.5

Friction streamlines at rated speed. (a ) Suction surface. (b ) Pressure surface

18.2.2 Static Aeroelasticity, Impact of Gurney Flaps

Original DTU 10 MW RWT blade geometry is equipped with the so-called Gurney flaps at low span range [20 %, 30 %]. This device, originally developed for race car applications, consists on a small plate located at the trailing edge. It is used to increase the lift produced by the airfoil when operating in separated flow conditions. A low drag penalty is expected. First studies characterizing the performance of this passive device were performed by Liebeck (1978). Figure 18.6 reproduces the conclusions of this work. The beneficial effects of the Gurney flaps installation are explained by the re-attachment of suction side flow close to the trailing edge. In order to evaluate the behaviour of the DTU 10 MW RWT Gurney flaps the load cases of Table 18.2 were studied again in a mesh with clean trailing edges, and compared with previous results. This comparison was performed not only under the hypothesis of rigid blades, but also by considering a flexible rotor.

Fig. 18.6

Expected effects on trailing edge flow due to Gurney flaps installation. (a ) Clean trailing edge. (b ) Trailing edge accounting for a Gurney flap

A new mesh was generated with the same set-up described in Sect. 18.2.1, but based on a variant geometry of the DTU 10 MW RWT where the Gurney flaps were replaced by the unmodified blade profiles definition. This new mesh is referred in this section as no-Gurney, or NG. For clarity purposes, the one initially created in Sect. 18.2.1 is referred as Gurney or G. In order to illustrate the differences between G and NG configurations, Fig. 18.7 displays a cross-section of the mesh corresponding to a 25 % of blade span.

Fig. 18.7

Cross-section meshes at 25 % span for G (Gurney) and NG (no-Gurney) configurations. (a ) G cross-section mesh. (b ) G trailing edge. (c ) NG cross-section mesh. (d ) NG trailing edge

For the considered aeroelastic simulations, the blade structure was linearized by means of the Reduced-Order Model (ROM) developed by Debrabandere (2014). A modal analysis was performed within the commercial package Abaqus (Simulia 2008) based on the model provided by Bak et al. (2013). Obtained natural frequencies were compared against the results of the aeroelastic computations of HAWC2 (Larsen and Hansen 2007), a third party software based on blade element momentum (BEM) theory. Computed frequencies for each identified mode are compiled in Table 18.3. To reduce the computational cost attached to aeroelastic simulations, only the first six frequencies of the obtained modal basis were used to model blade flexibility. A mixed mode was found between first torsion and fourth flap. No pure third edge mode was identified within the considered frequency range. These differences could be explained by the complexity of the astructural models used for natural frequencies extraction.

Table 18.3

DTU 10 MW RWT blade modes, comparison in the absence of rotation

Natural frequency [Hz]

Isolated blade modes

 

Abaqus

Bak et al. (2013)

Identifier

Description

 

0.61

0.61

1

1st flap

 

0.96

0.93

2

1st edge

 

1.75

1.74

3

2nd flap

 

2.88

2.76

4

2nd edge

 

3.58

3.57

5

3rd flap

 

5.71

5.69

6

1st torsion

 

5.75

7

Mixed flap/torsion

 

6.16

6.11

8

4th flap

 

6.66

9

3rd edge

 
Fig. 18.8

Evolution of DTU 10 MW RWT blade frequencies in function of rotational speed (first six modes plotted)

Additional modal analysis were performed taking into account the centrifugal effects of each one of the analyzed rotor RPMs. This allowed to include the initial blade deformation due to the rotation. In addition, a slight structural frequencies shift was observed. This effect is illustrated in Fig. 18.8, where the variations of blade frequencies against non-rotating frequency are plotted at every RPM. Even if this frequency shifting is not as important as in other rotatory applications including large blade deformations (such as helicopters), a non-negligible value is observed for the first modes. As an example a difference up to 6.12 % was found for the first mode at 9.6 RPM.

In order to check if the Gurney flaps flow control mechanism illustrated in Fig. 18.6 was reproduced in the DTU 10 MW RWT geometry, a detailed analysis of the rigid configuration at rated speed was performed. Figure 18.9 shows a comparison of the cross-section streamlines at r = 23 m. The generation of the pressure surface separation bubble was visible for the G configuration. A detailed view of this phenomenon is included in Fig. 18.9b. The suppression of the suction surface recirculation, expected after the installation of the Gurney flaps, was not observed. This behaviour was found for the whole low span range, as it can be deduced from the comparison of blade surface streamlines of Fig. 18.10a and b. Indeed, the removal of the Gurney flaps led to a slight decrease of the maximum radius of the suction surface separation (passing from 39.7 m for G to 38.1 m for NG). In addition, the flow around the pressure surface of NG remained attached for the whole blade span, except for a small recirculation bubble located at r = [14. 9, 20. 3] m (see Fig. 18.10d). A similar flow pattern was observed for all the operating points of Table 18.2.

Fig. 18.9

Cross-section streamlines for r = 23 m at rated speed. Rigid simulations. (a ) G (Gurney), global view. (b ) G (Gurney), pressure side zoom. (c ) NG (no-Gurney), global view. (d ) NG (no-Gurney), pressure side zoom

Fig. 18.10

Friction streamlines at rated speed for suction and pressure surfaces (referred as SS and PS respectively). Rigid simulations of G (Gurney) and NG (no-Gurney) configurations. (a ) SS-G. (b ) SS-NG. (c ) PS-G. (d ) PS-NG

The benefits of the no-Gurney N G configuration on flow behavior had a direct impact on global rotor performance. Figure 18.11a and b show the global thrust and mechanical power coefficients, computed for both G and NG configurations. The results for rigid and flexible blade models are included. Global load coefficients were computed based on the following equations:
$$\displaystyle{ C_{t,global} = \frac{BT} {0.5\rho U_{\infty }^{2}\pi R^{2}}\;,C_{p,global} = \frac{B\tau \varOmega } {0.5\rho U_{\infty }^{3}\pi R^{2}}\;, }$$
(18.1)
Where T stands for the thrust force generated per blade, τ is the torque per blade, B stands for the number of blades, \(U_{\infty }\) is the incoming fluid speed, ρ is the fluid density, R is the total blade span and Ω is the rotating speed.
Fig. 18.11

Global load coefficients in function of wind speed for G (Gurney) and NG (no-Gurney) configurations. (a ) Global thrust coefficient. (b ) Global mechanical power coefficient

Fig. 18.12

DTU 10 MW RWT blade deformation in function of normalized radius. G (Gurney) and NG (no-Gurney) configurations. (a ) Blade axis displacement parallel to rotor axis. (b ) Blade axis displacement normal to rotor axis

At rated speed and for the rigid blade model, the installation of Gurney flaps decreased the mechanical power of 1.4 %, while the thrust was increased of 0.8 %. A similar trend was observed for lower wind speeds. Same remarks concerning the efficiency of Gurney flaps could be made when considering blade elasticity.

A global thrust and mechanical power decrease was observed for both G and NG configurations when considering aeroelasticity. This is related to the important blade deflections experienced by the blade. Figure 18.12 displays the computed displacements parallel and normal to the rotor axis (often referred as out-of-rotor plane and in-rotor plane respectively). No significant differences were observed between the deflections corresponding to G and NG geometries. For both configurations, deformation parallel to rotor axis reached the 44 % of the blade tip/tower distance (18.26 m) at the rated speed operating point.

Based on the presented results, a decrease of the performance of the DTU 10 MW RWT rotor is expected after the integration of the Gurney flaps. Other alternatives in order to avoid the observed flow separation can be found in the literature. In Gaunaa et al. (2013), the use of leading edge slats at low span regions rR = [0. 8, 0. 32] was studied. Troldborg et al. (2015) considered the installation of vortex generators in order to control flow separation.

18.2.3 Static Aeroelasticity, Impact of Prebending and Preconing

The distance between the blade tip and the tower is often referred in the wind energy context as the tower clearance. In order to increase this gap (especially when dealing with large rotors), wind turbine designers use to introduce three geometrical considerations on the assembly:
  • Tilt angle: Angle between rotor axis and tower

  • Precone angle: Angle between blade axis and rotor axis

  • Prebending: Blade deflection towards the incoming wind direction imposed during the blade design stage

The DTU 10 MW RWT accounts for all of them, as shown in Fig. 18.13a, where a sketch from the definition document of Bak et al. (2013) is reproduced. The geometrical effects of prebending, tilt and preconing are highlighted. In an operating wind turbine, the combination of all these modifications will try to align the deformed blade with the tower, as shown in Fig. 18.13b.

Fig. 18.13

Examples of whole wind turbine assemblies. (a ) Sketch of the DTU 10 MW RWT assembly. (b ) Representative sketch of a working wind turbine

The aim of this section is to analyze how these geometrical considerations will impact rotor performance. The results of the already studied straight configuration were compared against a new and more realistic variant, accounting for tower clearance increase devices. Based on the conclusions of Sect. 18.2.2, new simulations were based on a blade geometry without Gurney flaps. In order to explore the whole 0 operating range of the machine, the load cases from Table 18.2 were analyzed again and compared with the straight-NG configuration results. Both rigid and flexible blades were analyzed.

A new mesh was generated with the same characteristics as the one described in Sect. 18.2.1. Since the introduction of the tilt angle was not compatible with the angular periodicity hypothesis, only the prebending and the preconing were considered. Based on the design specifications from Bak et al. (2013), the new considered geometry was generated by the application of the following geometrical operators on the standard DTU 10 MW RWT configuration:
  1. 1.

    Application of the prebending law definition on the straight blade (see Fig. 18.14)

     
  2. 2.

    Application of the 2.5 precone angle to the already prebent blade

     
Fig. 18.14

DTU 10 MW RWT axis prebending definition, (reproduced from Bak et al. 2013)

Due to the significant geometrical modifications performed on the new prebent-precone blade, a new set of natural structural frequencies and mode shapes was required. The methodology described in Sect. 18.2.2 was used in order to perform modal analysis for each one of the considered RPM. The same blade modes identified for the straight blade were observed for the new geometry. As previously shown in Fig. 18.8 for the straight configuration, a small RPM dependency was observed. In Fig. 18.15, the relative variations of natural frequencies corresponding to both configurations are compared. They are normalized by the frequency of the non-rotating straight blade. The evolutions of the frequencies with the rotation speed were very similar. Only a constant shift between straight and prebent-precone configuration was observed. This shift tended to increase with the mode number.

Fig. 18.15

Evolution of DTU 10 MW RWT blade frequencies in function of rotational speed, straight and prebent-precone blades (first six modes plotted)

Fig. 18.16

DTU 10 MW RWT modal analysis initial deformation (blue-yellow), superposed to the blade geometry reference (red) at rated speed. (a ) Straight blade. (b ) Prebent-precone blade

A more significant difference was related to the centrifugal effects included in the performed modal analysis. Indeed, an important initial deformation was observed for the prebent-precone configuration, due to offset of the blade geometry. In Fig. 18.16, the initial deformation (in blue-yellow) is superposed to the corresponding blade geometries (in red) for the rated speed operating point. While no difference was visible for the straight configuration (Fig. 18.16a), the centrifugal effects tended to straighten up the blade (Fig. 18.16b). As performed in the previous section, only the first six frequencies of the computed modal basis were used to model blade flexibility in the simulations.

Figure 18.17 shows the blade deformations for the flexible simulations of the prebent-precone rotor. Computed deformations were slightly higher than the ones corresponding to the straight rotor and previously displayed in Fig. 18.12. However, higher deformed blade tip/tower distances were observed for the prebent-precone configuration, due to its more conservative initial tower clearance. In order to illustrate this fact, Fig. 18.18 shows the reference (i.e. undeformed) and deformed blade axis coordinates for each of the presented aeroelastic computations. A global view is provided as well as a close zoom in order to properly contextualize the magnitude of the deformations. For the prebent-precone configuration, a blade tip/blade root alignment was observed for for the 10 m s−1 simulation. This operating point is indeed very close to the rated speed of the machine, verifying the prebending law defined at the design stage.

Fig. 18.17

DTU 10 MW RWT blade deformation in function of normalized radius for the prebent-precone configuration. (a ) Blade axis displacement parallel to rotor axis. (b ) Blade axis displacement normal to rotor axis

Fig. 18.18

Reference and deformed DTU 10 MW RWT blade axis coordinates with respect to closest tower edge. (a ) Straight rotor (global view). (b ) Prebent-precone rotor (global view). (c ) Straight rotor (zoom). (d ) Prebent-precone rotor (zoom)

Computed global mechanical power coefficients of straight and prebent-precone configurations are shown in Fig. 18.19, together with a diagram superposing reference and deformed rotor geometries at rated speed. When considering the blades as rigid, a decrease in power was observed when introducing blade prebending and preconing. For the straight rotor, accounting for blade flexibility led to a reduction of the total power. This trend was reversed for the prebent-precone configuration, since the effect of flexibility tended to deform the blade towards a more orthogonal geometry with respect to the incoming flow (Fig. 18.19b). At rated speed, the power produced by the flexible prebent-precone blade was very close to the one computed for the rigid straight blade. An analogous plot regarding rotor global thrust coefficient is included in Fig. 18.20. Lower thrust values were computed for the prebent-precone configuration with respect to the straight rotor. No significant differences between flexible and rigid simulations were observed for the prebent-precone configuration.

As a global conclusion, presented results show that aeroelastic analysis of DTU 10 MW RWT cannot be performed without considering the prebending and the preconing of the blades. Indeed, even if it does not largely affect the natural frequencies of the blade, its shape modification influences the performances of the wind turbine.

Fig. 18.19

Mechanical power coefficient of the DTU 10 MW RWT rotor, effects of prebending-preconing and flexibility. (a ) Global mechanical power coefficient. (b ) View of deformed blades at rated speed

Fig. 18.20

Global thrust coefficient of the DTU 10 MW RWT rotor, effects of prebending-preconing and flexibility. (a ) Global thrust coefficient. (b ) View of deformed blades at rated speed

Fig. 18.21

Sketch of the DTU 10 MW RWT assembly. (a ) Front view. (b ) Side view

18.3 DTU 10 MW RWT Rotor-Tower Interactions Analysis

In this section, flow complexity was increased by considering the DTU 10 MW RWT tower in the computational domain. This more realistic scenario introduced an important unsteadiness in the flow due to the so-called rotor-tower interactions. Hence, the use of more sophisticated numerical methods was required. In particular, the Non-linear Harmonic (NLH) approach presented by Vilmin et al. (2006) was used. In the NLH method, unsteady flow perturbations are Fourier decomposed. Navier-Stokes equations are then cast in the frequency domain, leading to the extraction of a set of transport equations for each harmonic. A single blade passage mesh is required. As a first approach and in order to keep the rotational periodicity of the problem, the incoming wind was assumed to be aligned with rotor axis. The hypothesis of rigid rotor blades was also made. The studied operating point was characterized by the following parameters:
  • Incoming wind speed: 10.5 m s−1

  • Rotor speed: 8.836 RPM

  • Blade pitch: 0

Figure 18.21 illustrates the main geometrical properties of the studied DTU 10 MW RWT assembly, based on its definition from Bak et al. (2013). The rotor axis was co-linear with Z axis. A tilt angle of 5 was considered between rotor and tower axes. Blades accounted for a precone angle of 2.5 as well as a distributed prebending. Based on the disadvantageous effects on rotor performance found in Sect. 18.2.2, Gurney flaps were removed from blade geometry. In order to present the unsteady results of this section, the normalized time tT was used. In this context, t is defined as the already lapsed time in the current revolution and T refers to the period of rotation. The DTU 10 MW RWT operates in clockwise rotation, and it was assumed that at tT = 0 one of the blades was aligned with the tower axis. This particular blade, displayed in red in Fig. 18.21, is referred in this document as the observed blade.

To generate a suitable mesh for NLH computations, DTU 10 MW RWT blade sections defined in Bak et al. (2013) were imported in Autogrid5TM structured grids generator (NUMECA International 2013a). Original nacelle, hub and tower geometries were also considered in the mesh generation process. To properly describe the boundary layer for the considered operating point, a first cell size of 3. 0 × 10−5 m was imposed around the blade. A rotor/stator interface crossing the DTU 10 MW RWT nacelle was defined in order to connect rotating and non-rotating computational domains. A single blade passage was meshed in the rotor side, while a 360 grid was generated for the tower (or stator) region. Flow inlet and outlet were located at 2.2 and 3.2 blade radius from the nacelle, respectively. Figure 18.22 shows the complete generated mesh, accounting for 13 millions of nodes. For clarity purposes, 1 out of 2 mesh lines were skipped.

Fig. 18.22

DTU 10 MW RWT assembly mesh, 1 out of 2 mesh lines are skipped. (a ) Surface mesh, global view. (b ) Surface mesh, rotor detail. (c ) Half-span cross-section grid line

A total of nine harmonics were considered. The Spalart–Allmaras turbulence model (Spalart and Allmaras 1992) was used. A full non-matching non-reflecting approach was employed for the modeling of the rotor/stator interface (Vilmin et al. 2006). First resolved rotor harmonic was located at 0.15 Hz, corresponding to the rotational speed at the considered operating point. Since the DTU 10 MW RWT has a three-bladed rotor, a frequency of 0.45 Hz was observed for the first tower harmonic. Even if flow variables are solved in the frequency domain, NLH results can be easily reconstructed in time in order to perform a more comprehensive postprocessing. This process is referred in this document as the time solution reconstruction.

The complexity of this unsteady problem could be already pointed out with the visualization of the flow at a given time. Figure 18.23 illustrates the iso-surfaces of Q-criterion for a value of 0.5 of the time reconstructed solution at \(\frac{t} {T} = 0.50\). Important vortical structures could be observed downstream of the tower. These were present all along the tower height. High vorticity regions were identified at low blade span range (where the DTU 10 MW RWT is equipped with thicker airfoils). The generation of blade tip vortex was clearly visible. The collision of this structure with the tower led to an important increase of downstream vorticity.

The observed vorticity at low blade span can be related to the shedding phenomenon. Figure 18.24 shows the streamlines around the observed blade for a r = 20 m cross-section. Indeed, the low span suction side recirculation already identified for the rotor-only RANS computations was shed from the blade. This effect was especially visible when the blade approached the tower (i.e. for \(\frac{t} {T} = 0.00\) and \(\frac{t} {T} = 0.76\)). A similar vortex shedding phenomenon was identified downstream of the tower all along its height.

Fig. 18.23

Iso-surface of 0.5 Q-criterion at \(\frac{t} {T} = 0.50\)

Fig. 18.24

Relative velocity streamlines around the observed blade for a r = 20 m cross-section. (a ) \(\frac{t} {T} = 0.00\). (b ) \(\frac{t} {T} = 0.24\). (c ) \(\frac{t} {T} = 0.50\). (d ) \(\frac{t} {T} = 0.76\)

When characterizing the frequency content of the blade shedding, an important spanwise dependency was observed. Two sets of sensors were defined in order to have an overview of this relation: BLADE_DOWNSTR and TOWER_UPSTR, both installed all along a mesh line. While BLADE_DOWNSTR was positioned at the observed blade shedding location, TOWER_UPSTR intended to analyze the impact of the rotor perturbation on the tower (see Fig. 18.25).

Fig. 18.25

Location of BLADE_DOWNSTR and TOWER_UPSTR sets of sensors. (a ) DTU 10 MW RWT front view. (b ) Cut at r = 44. 5 m

Figure 18.26 illustrates the harmonic pressure amplitudes for every point included in BLADE_DOWNSTR and TOWER_UPSTR. The results are expressed as a function of the considered harmonic (referenced here as Harmonic order), and of the radial position of each point. The blade shedding phenomenon could be identified for BLADE_DOWNSTR at the vicinity of 20 m. In this region, important harmonic amplitudes corresponding to the fifth harmonic were observed. The influence of blade shedding on the tower was visible in TOWER_UPSTR, where a shifting of the harmonic content towards higher frequencies was observed at low span.

Fig. 18.26

Harmonic pressure amplitude [Pa] for the defined sets of sensors, as a function of r [m]. (a ) BLADE_DOWNSTR. (b ) TOWER_UPSTR

Fig. 18.27

DTU 10 MW RWT rotor loads as a function of normalized time. (a ) Thrust [kN]. (b ) Power [kW]

Figure 18.27 shows rotor loads time evolution, where the effects of the blade-tower alignment event are clearly visible at \(\frac{t} {T} = 0\), \(\frac{1} {3}\), \(\frac{2} {3}\). The corresponding result for a rotor-only RANS simulation based on the set-up of Sect. 18.2 is included for reference. Relative loads fluctuation amplitudes of 1 % for the rotor thrust and 2 % for the mechanical power were computed. The presence of the tower led to a time-averaged decrease of 5 % of rotor thrust and 8 % of mechanical power with respect to the corresponding rotor-only simulation. Therefore it can be concluded that the influence of the tower is not negligible when assessing the wind turbine performance.

18.4 Conclusions and Future Work

A numerical analysis of the DTU 10 MW RWT reference wind turbine aerodynamics was presented and discussed. A three-dimensional CFD-based methodology was developed in order to tackle two challenging problems. On one hand, the impact of large OWT blade deflections on rotor performance (the so-called aeroelastic effects). On the other hand, the modeling of flow unsteadiness coming from the consideration of the tower in the CFD set-up (also referred as rotor-tower interactions).

The issue of aeroelasticity was studied in a rotor-only framework. First simulations aimed to verify the obtained results for a straight and rigid configuration regarding to CFD simulations performed by other authors. For both methodologies, computed flow separation and rotor loads were in good agreement. After this initial comparison the developed tool was extended by including a structural model of the blade, represented by its natural frequencies and deformed shapes. This enhanced numerical approach was used in order to study the influence of two different geometrical modifications of the blade on final rotor performance and aeroelastic response. First, the impact of Gurney flaps installation was discussed. No re-attachment of the suction surface separation bubble was observed after the introduction of these devices, and a wider pressure surface recirculation zone was identified. The evaluation of the total mechanical power and thrust showed that Gurney flaps reduced the global performance of the DTU 10 MW RWT rotor for the considered operating points. This remark could be made for both rigid and flexible configurations. For the latter case blade tip deformations of 8 m were computed at rated speed, leading to a power production decrease of 1.4 %. It can be concluded that the consideration of blade flexibility is necessary in order to properly estimate the final rotor performance. Secondly, the results of a prebent-precone rotor were compared with the standard straight configuration. When considering the blades as rigid, the combination of both geometrical modifications led to a decrease of the computed rotor loads. At rated speed, reductions of 1 % of thrust and 2 % of mechanical power were observed. When analyzing the corresponding flexible blade configurations, the effect of aeroelasticity on rotor performance was reversed. Indeed, while a reduction in the generated power was observed for the deformed straight rotor, an increase was found for the prebent-precone configuration. This inversion was explained by the deformed rotor geometries, since for the prebent-precone simulations the blade flexibility tended to recover the orthogonality with respect to the incoming flow. These results show that aeroelastic analysis of DTU 10 MW RWT cannot be performed without considering the prebending and the preconing of the blades.

Finally, the NLH method was applied in order to study the whole DTU 10 MW RWT assembly (including the tower). This approach was able to capture the complex unsteady aerodynamics related to rotor-tower interactions. The presence of the tower had a direct impact on rotor performance, justifying the numerical analysis of the full machine. Decreases of around 5 % of time-averaged rotor thrust and 8 % of power were computed. These reductions are in line with previous studies based on other wind turbines (Hsu and Bazilevs 2012; Hsu et al. 2014; Carrión 2014; Li 2014). Local unsteady flow patterns around the whole DTU 10 MW RWT assembly were also characterized. In particular, both tower and blade shedding phenomena were identified. The latter effect was found to be related to high frequencies. In particular, the considered operating point revealed a blade shedding frequency corresponding to the fifth harmonic. This harmonic order is coherent with the results of previous CFD computations of the NREL Phase VI (Le Pape and Lecanu 2004; Li 2014). Regarding the blade-tower alignment event, loads fluctuation relative amplitudes of 1 % for the rotor thrust and 2 % for the mechanical power were computed.

Future work will be devoted to extend the capabilities of the NLH method to account for a structural model of the blades, in order to assess the combined impact of rotor flexibility and flow unsteadiness on rotor performance. Additionally, the studied DTU 10 MW RWT operating range will be extended to higher wind speeds to evaluate the performance of the presented methodology when considering more important angles of attack.

Notes

Acknowledgements

The authors acknowledge the European Commission for their research grant under the project FP7-PEOPLE-2012-ITN 309395 MAREWINT (new MAterials and REliability in offshore WINd Turbines technology), as well as all the members from FINETM/Turbo team of NUMECA International for their valuable and active contribution.

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Authors and Affiliations

  • Sergio González Horcas
    • 1
    Email author
  • François Debrabandere
    • 1
  • Benoît Tartinville
    • 1
  • Charles Hirsch
    • 1
  • Grégory Coussement
    • 2
  1. 1.NUMECA InternationalBruxellesBelgium
  2. 2.Faculty of Engineering, Fluids-Machines DepartmentUniversity of MonsMonsBelgium

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