# Conceptual Study of a Real-Time Hybrid Simulation Framework for Monopile Offshore Wind Turbines Under Wind and Wave Loads

^{1}Department of Civil, Construction and Environmental Engineering, University of Alabama, Tuscaloosa, AL, United States^{2}Department of Civil and Environmental Engineering, Louisiana State University, Baton Rouge, LA, United States^{3}School of Civil Engineering, Tianjin University, Tianjin, China

As an attractive renewable energy source, offshore wind plants are becoming increasingly popular for energy production. However, the performance assessment of offshore wind turbine (OWT) structure is a challenging task due to the combined wind-wave loading and difficulties in reproducing such loading conditions in laboratory. Real-time hybrid simulation (RTHS), combining physical testing and numerical simulation in real-time, offers a new venue to study the structural behavior of OWTs. It overcomes the scaling incompatibilities in OWT scaled model testing by replacing the rotor components with an actuation system, driven by an aerodynamic simulation tool running in real-time. In this study, a RTHS framework for monopile OWTs is proposed. A set of sensitivity analyses is carried out to evaluate the feasibility of this RTHS framework and determine possible tolerances on its design. By simulating different scaling laws and possible error contributors (delays and noises) in the proposed framework, the sensitivity of the OWT responses to these parameters are quantified. An example using a National Renewable Energy Lab (NREL) 5-MW reference OWT system at 1:25 scale is simulated in this study to demonstrate the proposed RTHS framework and sensitivity analyses. Three different scaling laws are considered. The sensitivity results show that the delays in the RTHS framework significantly impact the performance on the response evaluation, higher than the impact of noises. The proposed framework and sensitivity analyses presented in this study provides important information for future implementation and further development of the RTHS technology for similar marine structures.

## Introduction

As an emerging field of wind power generation, offshore wind power is growing rapidly in recent years due to its vast potential in energy production capacity (Esteban et al., 2011; Musial et al., 2016; Keivanpour et al., 2017). With the development of offshore wind energy technology, the turbine capacity and the hub height are constantly climbing, and at the same time, these offshore wind turbines (OWTs) are facing a more complicated and extreme marine environment as their regions of deployment going to deeper ocean (Perveen et al., 2014; Anaya-Lara et al., 2018). To ensure the structural integrity and operation safety of these energy harnessing systems during their foreseen lifetime (20–25 years) (Dnvgl, 2016; Anaya-Lara et al., 2018), it is imperative to enhance our understanding on OWTs' structural behavior in the complex marine environment.

Due to their working environment at exposed sites, OWTs are subjected to combined actions of multiple loads during their normal operations. These loads include wind, wave, and underwater current. These different forms of environmental loads combined with turbine operation condition, soil-structure interaction and flexible member dynamics make it difficult to accurately quantify the complicated dynamics and predict the system behavior of OWT (Dnvgl, 2016; Aasen et al., 2017; Bhattacharya, 2019). Wind and wave-current loads are the main external loads applied on operational OWTs, which may lead to a great overturning moment and shear force at its foundation and supporting structure (Alagan Chella et al., 2012; Stansby et al., 2013; Morató et al., 2017). Because of its special structural configuration (slender high-rising structural system with a concentrated mass at its top), an OWT's fundamental frequency often lies between the dominant frequency ranges of offshore lateral loads (Arany et al., 2017; Bhattacharya, 2019), which implies that its response is sensitive to those lateral forces such as wind and wave-current excitations. In addition, the misalignment between wind and wave plays an important role in predicting the extreme and fatigue loads in OWT systems. In a sensitivity study carried out in Barj et al. (2014), it is shown that considering only aligned wind and waves leads to an underestimation of the tower base side-side bending moment by approximately 50% and an overestimation of the tower-base fore-aft bending moment by about 5%. To accurately characterize and capture the structural behavior of OWTs, it is of great importance to consider the combined wind and wave-current actions.

Numerical tools are available to calculate wind and wave-current loads acting on OWT. The blade element momentum theory (BEM) (Hansen, 2015) is the most widely used method to estimate the aerodynamic loads on rotor blades. In the BEM theory, time series of aerodynamic loading are computed based on the momentum theory, the blade characteristics and the operational conditions. To characterize hydrodynamic loads caused by wave and current, wave climate first needs to be defined, usually in the form of a variance density spectrum, called wave spectrum. Two often used standard wave spectra are the Pierson—Moskowitz wave spectrum (Pierson and Moskowitz, 1964) and the Joint North Sea Wave Project (JONSWAP) wave spectrum (Hasselmann et al., 1973). Characterizing current load is a more challenging task, because current velocities vary in space and time as wind velocities, but with much larger variations in both length and time scales than those of wind. Although the well-established linear wave theory has been applied in modeling ocean wave dispersions (Lamb, 1945; Newman, 1977), complex physical phenomena, such as wave-current interaction effects, viscous loads, or extreme wave loads, are still not fully understood, nor confidently modeled (Sauder et al., 2016). Despite the development of increasingly sophisticated numerical models and tools, physical hydrodynamic model testing in wave tank facilities is still required for calibrating parameters in numerical models, assessing performance of current designs, and verifying new designs of OWTs.

Model testing in wave tank facilities usually adopts Froude scaling law, i.e., the scaling between experimental model and full-scale prototype maintains constant Froude number. By preserving the ratio of gravitational and inertial forces, Froude scaling ensures the similitude of free surface hydrodynamics, but it cannot maintain the same viscous effect due to the reduced Reynolds number (Campagnolo, 2013; Canet et al., 2018). While the Reynolds number dependence of the hydrodynamic load is often neglected in marine structure tests, the associated change of aerodynamic Reynolds number poses a challenge for OWT tests, because wind turbine aerodynamics are very sensitive to the viscous forces which are dominating at small scales (Martin, 2011; Robertson et al., 2013). One solution to address the incompatibility between the Froude and Reynolds scaling laws is to modify the design of the rotor blades. By adjusting the chord length and twist angle of blades, low-Reynolds number airfoil designs are developed to achieve similar thrust coefficients as full-scale blade in Froude scaled wind (De Ridder et al., 2014; Kimball et al., 2014; Du et al., 2016). Although this approach can mitigate the Froude-Reynold scaling conflict, the distortion in geometry leads to limitations such as mismatch in aerodynamic torque, generator torque, and roll-forcing (Bredmose et al., 2012).

A promising alternative to address the above scaling incompatibility is real-time hybrid simulation (RTHS). RTHS is a powerful dynamic testing technique for large or complex structural systems, in particular of those systems with multiple components and complex interactions (Carrion and Spencer, 2007; Phillips and Spencer, 2012). It originates in the field of earthquake engineering (Nakashima et al., 1992). In RTHS, part of the structural system is simulated using numerical models with good accuracy and confidence, and the rest of the system requires physical testing under realistic operational conditions. By interfacing physical testing with numerical simulation in real-time via actuators and sensors, RTHS not only provides insights into detailed dynamic behavior of the physical subsystem, but also offers a better understanding of the entire complex structural system. Due to its closed-loop nature, a successful RTHS framework needs to control the delays and noises in the interfacing actuator and sensor systems, as they tend to bring destabilizing effect into RTHS, causing large experimental error or even failure (Christenson et al., 2014; Maghareh et al., 2014; Hayati and Song, 2017). Research studies have also been conducted to quantify uncertainties in RTHS due to experimental errors (Sauder et al., 2019) and modeling choices (Abbiati et al., 2021).

RTHS has been applied in scaled wave tank tests for floating wind turbines (FWTs) to resolve the Froude-Reynold scaling conflict. Chabaud et al. (2013) proposed a RTHS set up for a conceptual FWT, simplified as a single degree-of-freedom (DOF) mass-spring system, and conducted a case study to identify potential challenges and corresponding solutions. Hall et al. (2014) used a set of wind turbine simulations to determine the performance specifications for a RTHS system. Later, Hall et al. (2018) applied a similar approach to study RTHS strategies with two different coupling locations. Sauder et al. (2016) presented a RTHS testing method (ReaTHM) of a FWT and discussed possible error sources and their quantification. The same RTHS method later was applied in testing a 10-MW FWT (Thys et al., 2018). In these wave basin RTHS tests, the numerical component is the aerodynamic portion of the FWT simulated by a computer model, and the physical component is the Froude scaled floating structure including the tower. An interfacing system including both sensors and actuators provides the coupling between the two components. Because the scaling can be set arbitrarily in a simulation, the Froude-Reynold scaling conflict is therefore eliminated. In addition, by simulating the aerodynamic loading numerically, the RTHS testing method offers a convenient way to consider different rotor blade designs with fine controlled wind field and avoids geometry distortion in blade and the demand of wind production during tests. The above developments demonstrated the great potential of RTHS in studying structural behavior of OWT under combined actions of wind and wave, especially took a solid step toward the RTHS implementation. However, they were mostly studied only in one scale (either reduced scale for RTHS or full-scale for prototype) to examine the performance of interfacing system or conduced in an open loop setting without fully exploring the coupled dynamics between numerical and physical components. None of them have provided a systematic investigation on the errors between the scaled RTHS and the matching full-scale prototype or discussed how the delays and noises in RTHS and different scaling laws will impact these errors. In addition, these above studies are mostly focused on FWTs, and have not covered the OWTs with fixed foundation, such as monopile OWTs.

In this study, a RTHS framework for monopile OWTs is proposed. A series of sensitivity analyses are conducted by comparing the responses of the proposed RTHS framework in reduced scale and those of the matching full-scale prototype under the influence of a variety of factors, including scaling laws, delays, noises, and wind-wave loading characteristics. Among these factors, the experimental errors (e.g., noise and delay) can provide information on RTHS compensation designs, and the modeling choices (e.g., scaling laws, wave heights, and misalignment angles) can guide specimen designs. Both the RTHS and the prototype are simulated numerically under controlled condition to isolate the influencing factors. The obtained results can help to better understand if the proposed RTHS framework can achieve desired accuracy and robustness in capturing the behavior of a full-scale OWT design. They also offer insights to guide the future RTHS implementation by identifying possible contributors that may impact the RTHS performance and quantifying the associated specification tolerance.

## Preliminaries

To facilitate the numerical simulation, a fully coupled three-dimensional (3D) dynamic model for monopile OWT is established using Euler-Lagrange equation and finite element (FE) method. The modeling details are descried in Section Preliminaries.

### Description of OWT Model

A typical monopile OWT subjected to the combined action of wind and wave is shown in Figure 1A. A cartesian coordinate system originating at the intersection of the tower center line and the mean sea level (MSL) is defined in the same graph. The wind-wave misalignment angle is denoted as β. The turbine blades are modeled by considering the major bending modes in the edgewise and flapwise directions of the blade, with the corresponding mode shapes denoted as ϕ_{1e} and ϕ_{1f}, respectively. The DOFs of the blades are illustrated in Figure 2: *u*_{1}~*u*_{3} denotes the modal coordinates in edgewise direction, *u*_{4}~*u*_{6} denotes the modal coordinates in flapwise direction, and *u*_{7} and *u*_{8} denotes the movements of the nacelle (and the hub) in the fore-aft (*x*) and side-side (*y*) directions at the top of the tower, respectively. The blades rotating speed is denoted as Ω (rad/sec) and the azimuthal angle ψ_{j}(*t*) of the *j*th blade can be expressed as:

Simplified foundation models are shown in Figure 3. Soil effects are considered by translational springs with coefficients *k*_{x} and *k*_{y} and rotational springs with coefficients *k*_{xϕ} and *k*_{yϕ}. Similarly, the damping properties of the soil are considered by introducing translational and rotational dashpots with coefficients *c*_{x}, *c*_{y}, *c*_{xϕ}, and *c*_{yϕ}. In Section FE Model for Tower Including Foundation, these stiffness and damping parameters are included in the FE model of the tower.

**Figure 1**. Monopile offshore wind turbine and its FE model. **(A)** Overview of the monopile offshore wind turbine. **(B)** FE model of the tower.

**Figure 2**. Degrees-of-freedom of the rotor blades. **(A)** Blade in-plane movement. **(B)** Blade out-of-plane movement.

**Figure 3**. Simplified foundation model of the offshore wind turbine. **(A)** Foundation model in *xz* plane. **(B)** Foundation model in *yz* plane.

In this study, the modeling of the aerodynamic and hydrodynamic components of OWT follows the procedure described in Sun and Jahangiri (2018); Sun (2018a); Sun (2018b). The tower, however, is modeled by FE method with physical movements as the DOFs instead of modal coordinates—the major bending modes in *x* and *y* directions adopted in Sun and Jahangiri (2018); Sun (2018a); Sun (2018b). The equations of motion of the OWT are established accordingly. The derivation details are shown in the Sections FE Model for Tower Including Foundation, Kinetic Energy, Potential Energy, Loads on OWT.

### FE Model for Tower Including Foundation

In actual RTHS implementation, usually the tower structure of the OWT is built in wave tank facility in reduced scale. In this concept study, all the components of the RTHS, including the experimental component (tower structure), are simulated numerically. As shown in Figure 1B, the entire tower of the OWT, including the tower structure above the MSL and below until seabed (also called the wet section), is modeled together as one tower model using two-node 3D elastic beam elements. Each node contains four DOFs: two translations (*u*_{x}, *u*_{y}) and two rotations (θ_{x}, θ_{y}) with respect to the *x* and *y* axis. The torsional behavior and axial deformation of the tower are ignored in this study. Assuming modal damping, the formulation of the mass **M**_{tow}, stiffness **K**_{tow}, and damping **C**_{tow} matrices can be found in standard texts (Przemieniecki, 1968; Craig and Kurdila, 2006) and hence are not repeated here. The pile is modeled as part of the tower structure extended to the seabed. Once the global mass, stiffness, and damping matrices of the tower are assembled, they are further modified by adding the stiffness (*k*_{x}, *k*_{y}, *k*_{xϕ}, and *k*_{yϕ}) and damping (*c*_{x}, *c*_{y}, *c*_{xϕ}, and *c*_{yϕ}) terms from the foundation model shown in Figure 3 to the corresponding DOFs. With the FE model of the tower established, the kinetic energy *T*_{tow} and potential energy *V*_{tow} of the tower can be expressed as

and

where **M**_{tow} and **K**_{tow} are the mass matrix and stiffness matrix; **u**_{tow} and **v**_{tow} are the displacement and velocity response vectors of the DOFs of the tower; Superscript “*T*” indicates transpose operation. It is noted that *u*_{7} and *u*_{8} are included in the vector **u**_{tow} too.

### Kinetic Energy

Based on Figures 1, 2, the absolute velocity of the nacelle (and the hub) *v*_{nac} is expressed as

Consider an infinitesimal unit *dr* of the *j*th blade in Figure 2, its movements (*x*_{r,j}, *y*_{r,j}, *z*_{r,j}) in the *xyz* coordinate system can be expressed as (*j* = 1, 2, 3)

Taking the derivative with respect to time, the magnitude of the absolute velocity of the unit *dr* of the *j*th blade *v*_{b,j} in Figure 2 is

Therefore, the total kinetic energy *T* of the OWT is given as

where *R* denotes the length of the blade; *M*_{nac} and *M*_{hub} are the mass for the nacelle and hub, respectively; $\overline{m}$ is the mass density per length of the blade.

### Potential Energy

The total potential energy of the blades *V*_{b} is calculated considering the strain energy due to bending and the stiffening effects due to centrifugal force and gravity. It is expressed as Sun and Jahangiri (2018).

where the bending stiffness in edge and flap direction, *k*_{eg} and *k*_{fp}, are expressed as,

the tension stiffening geometric stiffness in edge and flap direction due to centrifugal force, *k*_{ge,eg} and *k*_{ge,fp}, are expressed as,

the tension stiffening geometric stiffness in edge and flap direction due to gravity, *k*_{gr,eg} and *k*_{gr,fp}, are expressed as,

where *I*_{eg} and *I*_{fp} are the moment of inertia in the edgewise and flapwise direction, *g* is the gravitational acceleration; the superscripts “′” and “″” denote the first and second order derivatives with respect to the blade length *R*. Therefore, the total potential energy *V* of the OWT is.

### Loads on OWT

This section presents the derivation of wind, wave, and damping forces based on the principle of virtual work and FE method.

#### Wind Loading

The generation of the wind field follows IEC 61400-1 standard (Iec, 2005) using the Kaimal spectral model, with the length of roughness is set equal to 0.03. The associated coherence function is defined as,

where *a* = 12, *L*_{c} = 340.2 *m* are adopted in this study. During implementation, a three dimensional wind field profile covering the domain of the rotor disk is generated using the TurbSim program (Jonkman and Kilcher, 2012). A MATLAB code is developed to map the generated wind field onto each spanwise elements of the rotating blades to apply the BEM theory.

In this study, the BEM theory (Hansen, 2015) is applied to calculate the aerodynamic loads on the rotor blades. Figure 4 shows a blade element with the velocities and angles that determine the aerodynamic loads on the element. The angle of attack is denoted as α; *c* is the local chord length; θ is the sum of the local pitch angle and the twist of the blade element, which are determined by the blade profile; the relative velocity *V*_{rel} is a combination of the axial velocity *V*_{∞}(1 − *a*) and the tangential velocity Ω*r*(1 + *a*′) at the rotor plane, where *V*_{∞} is the flow velocity; *r* is the radial distance from the blade element to the rotor center; *a* and *a*′ are the axial and tangential induction factors, respectively. The lift and drag forces are projected to the directions normal to and tangential to the rotor plane to obtain the aerodynamic forces (per length) normal to the rotor plane *p*_{N} and tangential to the rotor plane *p*_{T}, as shown in the Equation (13),

where ρ_{A} is the air density; the lift and drag coefficients *C*_{l} and *C*_{d} can be determined from a given blade profile.

In practice, because the induction factors *a* and *a*′ are not known, an iterative procedure is required to implement the BEM theory. In this study, a MATLAB code is developed to calculate the time series of *p*_{N} and *p*_{T} based on an algorithm proposed in Sun (2018a). Prandtl's model and Glauert correction are considered in the MATLAB code to account for tip- and hub-loss. After the aerodynamic forces are determined, the principle of virtual work is applied to calculate the generalized aerodynamic loads on the OWT model.

Under *p*_{N} and *p*_{T}, the virtual work δ*W*_{wind} done by external wind load is expressed as,

where *p*_{Nj} and *p*_{Tj} denote the normal and tangential aerodynamic forces (per length) *p*_{N} and *p*_{T} acting on the *j*th blade. It is noted that the work done by the aerodynamic load acting on the DOFs of the tower is shown to be zero, except at the tip of the tower where the nacelle (and the hub) is located, i.e., *u*_{7} and *u*_{8}.

#### Wave and Current Loading

In this study, the JONSWAP wave spectrum is adopted to characterize wave climate. Based on the spectral representation method and linear wave theory, the random wave surface elevation η_{w}, current velocity ${\stackrel{\bullet}{u}}_{w}$, and acceleration ü_{w} can be generated as,

where Δ*f* = *f*_{cut}/*N* denotes the resolution of the frequency domain; *N*, usually a large number, indicates the number of segments that the frequency domain is divided into; and *f*_{cut} is the upper cut-off frequency for wave spectrum *S*; ${A}_{j}=2\sqrt{S({f}_{j})\Delta f}$ and *f*_{j} = *j*·Δ*f*, *j* = 1, …, *N*; *S* is the JONSWAP wave spectrum (Dnvgl, 2010); ϕ_{j} is the generated random phase angle uniformly distributed from 0 to 2π; *H*_{w} denotes water depth; *k*_{j} represents wave number, which is related to *f*_{j} by the dispersion equation (Faltinsen, 1990)

In Figure 5, the time history (for 200 s) and the spectrum of a generated random wave with the setting of wave peak period *T*_{p} = 10 *s*, significant wave height *H*_{s} = 3*m*, water depth *H*_{w} = 17.5*m*, number of segments *N* = 2, 000 are generated and compared with the target JONSWAP spectrum. The close match indicates the generated wave achieves the desired wave climate and can be used for load evaluation.

**Figure 5**. Generated wave (*T*_{p} = 10 *s*, *H*_{s} = 3*m*, *H*_{w} = 17.5*m*, *N* = 2000). **(A)** Time history of the generated wave elevation. **(B)** Spectrum of the generated wave.

With the current velocity ${\stackrel{\bullet}{u}}_{w}$ and acceleration ü_{w} obtained from Equations (16) and (17), the hydrodynamic forces exerted on a unit length of a pile can be evaluated using Morison's equation (Morison et al., 1950).

Where ${F}_{d}=\frac{1}{2}{\rho}_{w}D{C}_{d}{\stackrel{\bullet}{u}}_{w}\left|{\stackrel{\bullet}{u}}_{w}\right|$ denotes the drag orce (per length) and ${F}_{a}=\frac{1}{4}{\rho}_{w}\pi {D}^{2}{C}_{m}{\ddot{u}}_{w}$ denotes the inertia force (per length); ρ_{w} is the density of the fluid (${\rho}_{w}=1,025\text{}kg/{m}^{3}$ is adopted in this study); *D* is the diameter of the pile section; *C*_{d} and *C*_{m} are the drag and inertial coefficients (*C*_{d} = 1.2, *C*_{m} = 2.0 are adopted in this study). The virtual work δ*W*_{wave} done by the hydrodynamic forces along the tower including the monopile under MSL can be expressed as,

where δ*u*_{x} and δ*u*_{y} indicate the virtual displacement along *x* and *y* directions, respectively. The last approximation in Equation (20) is based on work-equivalent nodal force using the FE model established in Section FE Model for Tower Including Foundation. *N*_{w} indicates the total number of elements that are below MSL; **F**_{wave, i} and δ**u**_{tow, i} are the work-equivalent nodal force vector and virtual displacement vector of the *i*th element of the tower FE model, respectively. It is noted that δ*W*_{wave} does not involve the DOFs above the MSL.

#### Damping Load

Modal damping is assumed for both the blades and the tower. The virtual work done by the damping force is given as,

where *c*_{bj, eg} and *c*_{bj, fp} are the edgewise and flapwise modal damping coefficients of the *j*th blade; *c*_{aero, x} and *c*_{aero, y} are the aerodynamic damping coefficients of the nacelle in *x* and *y* directions, respectively; **C**_{tow} is the modal damping matrix of the FE model of the tower.

#### Equations of Motion of OWT

With the kinetic energy, potential energy, and the forces obtained, the equations of motion of the monopile OWT can be obtained using the Euler-Lagrange equation as follows,

where the kinetic energy *T* and potential energy *V* can be obtained from Equation (9) and Equation (11), respectively; *u*_{i} indicates each DOF of the FE model of the tower; the corresponding forcing term *F*_{i} can be obtained by,

with δ*W*_{wind}, δ*W*_{wave}, and δ*W*_{damping} obtained from Equations (14), (20), and (21).

After collecting the terms in Equation (22), the following equations of motion can be obtained,

where ${u}_{\text{N}}={\left[\begin{array}{c}{u}_{1}\text{}{u}_{2}\text{}{u}_{3}\text{}{u}_{4}\text{}{u}_{5}\text{}{u}_{6}{u}_{tow}^{T}\end{array}\right]}^{T}$; the corresponding mass matrix **M**, damping matrix **C**, stiffness matrix**K**, and force vector **F** are listed in the Appendix.

## Proposed Real-Time Hybrid Simulation Framework

A RTHS framework is proposed in this section to study the structural behavior of the monopile OWT shown in Figure 1A. Its details, including the framework descript, possible scaling laws applied, and error contributors are explained in Section. Proposed Real-Time Hybrid Simulation Framework.

### Framework Description

The proposed RTHS platform is shown in Figure 6. In this RTHS platform, the numerical component contains the rotor blades and aerodynamic loads; the experimental component contains the tower structure (including the nacelle, hub, and foundation) along with the hydrodynamic loading effects provided by wave tank and necessary hardware (actuators and sensors). It is noted that, the numerical component is simulated under full-scale, and the experimental component is tested in reduced scale. The two components are interfaced through the displacement DOFs (*u*_{7} and *u*_{8}) at the top of the tower. This RTHS framework directly resolves the Froude-Reynold scaling conflict by applying full-scale aerodynamic simulation in the numerical component, and meanwhile it can preserve the complex hydrodynamic behaviors in the wave tank facility at a reduced scale, including soil-structure interaction and wave-current interaction. In this concept study, to assess the feasibility of the proposed RTHS framework and identify possible contributors that may impact the RTHS performance, a “virtual” RTHS is established through numerical simulation of both the numerical and experimental components.

To explain, the displacement vector of the entire OWT, **u**, defined in Equation (24) is partitioned based on the proposed RTHS framework as,

where ${\text{u}}_{\text{N}}={\left[\begin{array}{c}{u}_{1}\text{}{u}_{2}\text{}{u}_{3}\text{}{u}_{4}\text{}{u}_{5}\text{}{u}_{6}\end{array}\right]}^{T}$, ${\text{u}}_{\text{I}}={\left[\begin{array}{c}{u}_{7}\text{}{u}_{8}\end{array}\right]}^{T}$, and **u**_{E} is the tower displacement vector **u**_{tow} excluding the DOFs of **u**_{I}. The subscripts “*I*”, “*N*”, and “*E*” indicate the DOFs are related to the interfacing system, numerical component, and experimental component of the proposed RTHS framework, respectively. Based on the partition shown in Equation (25), the equations of motion, Equation (24), can be written into the partitioned formulation as,

The subscripts are defined in the same manner as in Equation (25). The superscripts “*E*” and “*N*” indicate the term originates from the experimental component or from the numerical component. The detailed expressions for each term are listed in the Appendix.

Based on Equation (26), the equation of motion for the numerical component [1^{st} block row in Equation (26)] of the RTHS framework can be determined as

where ${\text{f}}_{\text{I}}^{\text{N}}$ indicates the interface force acting on the numerical component. It can be computed as

The last equality in Equation (28) holds because **C**_{NI}** = 0** and **K**_{NI}** = 0** (see Appendix).

Similarly, the equation of motion for the experimental component [2^{nd} and 3^{rd} block rows in Equation (26)] of the RTHS framework can be determined as

where ${\text{f}}_{\text{I}}^{\text{E}}$ indicates the interface force acting on the experimental component. It can be computed as

The last equality in Equation (30) holds because ${\text{K}}_{\text{II}}^{\text{N}}=0$ (see Appendix). In addition, if sufficient amount of mass can be added to the experimental component to include the mass effect from the nacelle and rotor systems, i.e., ${\text{M}}_{\text{II}}^{\text{N}}$, then ${\text{M}}_{\text{II}}^{\text{N}}{\ddot{\text{u}}}_{\text{I}}$ can be removed from Equation (30) as it will be naturally considered during the testing of experimental component.

Based on the numerical and experimental components defined in Figure 6, the procedure for RTHS using wave tank facility can be extracted from Equations (27)~(30). To summarize, the numerical component takes the measurement of ${\ddot{\text{u}}}_{\text{I}}$ during the test to compute ${\text{f}}_{\text{I}}^{\text{N}}$ [Equation. (28)]. The response of numerical component, **u**_{N}, under the combined action of aerodynamic load **F**_{N} and ${\text{f}}_{\text{I}}^{\text{N}}$, is determined through numerical integration by solving Equation (27). The solved responses (**u**_{N}, ${\stackrel{\bullet}{\text{u}}}_{\text{N}}$, and ${\ddot{\text{u}}}_{\text{N}}$) are used to compute ${\text{f}}_{\text{I}}^{\text{E}}$ (Equation 30). In wave tank facility, ${\text{f}}_{\text{I}}^{\text{E}}$ combined with the aerodynamic force ${\text{F}}_{\text{I}}^{\text{N}}$ are applied to the OWT specimen via actuators, while the force vector ${\left[\begin{array}{c}{({\text{F}}_{\text{I}}^{\text{E}})}^{T}\text{}{({\text{F}}_{E})}^{T}\end{array}\right]}^{T}$is generated via wavemaker. Then, the induced response (${\ddot{\text{u}}}_{\text{I}}$) is measured through sensors and fed to the numerical component to close the loop. A block diagram describing this process is provide in Figure 7.

### Scaling Laws

In the proposed RTHS framework (Figure 6), the scaling conflict is avoided because the aerodynamic effects are simulated in full-scale, which is separated from the hydrodynamic effects produced in wave tank facility in reduced scale. So far, most of the existing scaled wave tank tests adopts Froude scaling, because the Froude number, *Fr*, defined in Equation (31) below, characterizes the gravitational effect which is dominating in problems with free surface waves.

where *V* is the wave celerity or propagation speed, *g* is the gravitational acceleration, and *L* is the characteristic length. However, hydrodynamic effects due to water waves are not the only dynamic effects need to be considered in the RTHS tests. The elastic effect due to slender specimen deformation also needs to be considered. Following the Froude scaling, it can be shown that the consistent scaling to preserve the similitude in structural modal information (natural frequencies and mode shapes) is (Martin, 2011; Bredmose et al., 2012)

where λ_{EI}, λ_{ρ}, and λ_{L} are the scaling factor of bending stiffness (*EI*), density (ρ), and length (*L*), between the model and the prototype. It is noted that (Equation 32) implies that if the density of the material stays unchanged (λ_{ρ} = 1), the elastic modulus *E* needs to be modified. This requirement is usually difficult to achieve directly. Often for the OWT tower, it is sufficient that the bending stiffness *EI* scales correctly, which provides some freedom in the model design. Therefore, the combination of material density, stiffness, and geometry are usually tuned together to achieve the scaling goal. This method, although challenging, has been applied in OWT wave tank studies (Martin, 2011; Martin et al., 2014).

In this study, several alternatives have been considered in addition to the above Froude scaling law. In earthquake engineering, Cauchy scaling combined with Froude scaling are often considered in designing scaled models for dynamic testing. Cauchy scaling preserves the Cauchy number, *Ca*, defined in Equation (33), which is important in characterizing the deformation of the specimen.

With the condition λ_{E} = λ_{ρ}λ_{L}, Froude and Cauchy similitudes are simultaneous. It implies that if the same material is used for both prototype and model with λ_{E} = 1, the density of the specimen needs to be increased. Usually added artificial masses are distributed to the model specimen to achieve that and minimize the change in mass distribution. However, when applying this simultaneous Fr-Ca scaling law, the hydrodynamic effects are distorted, because water usually is the only liquid considered in wave tank facilities. Under the Fr-Ca similitude, the proper scaling factor for force acting on the OWT ${\lambda}_{tf}={\lambda}_{L}^{2}$. But with water used as the testing fluid, the scaling factor for hydrodynamic force induced by wave and current is, ${\lambda}_{hf}={\lambda}_{L}^{3}\ne {\lambda}_{tf}$, which causes distortion in hydrodynamic force scaling. To consider the impacts of possible scaling laws on the proposed RTHS, a total of three scaling laws are considered in this study:

• Froude scaling with λ_{ρ} = 1. In this case, all terms are properly scaled but it poses a challenge to the model construction in preserving the similitude in bending stiffness;

• Conventional Fr-Ca scaling, which induces distorted hydrodynamic force induced from the wave tank;

• Fr-Ca scaling with increased wave amplitude. By increasing the amplitude of the generated wave by a factor of $\sqrt{1/{\lambda}_{L}}$, the drag force *F*_{d} in Equation (19) can be properly scaled with a factor of ${\lambda}_{L}^{2}$, matching the requirement from the OWT. However, the inertia force *F*_{a} is still distorted under this scaling law.

The last two of the scaling laws both are derived from Fr-Ca scaling. A systematic way of model construction is the advantage in them, comparing to the Froude scaling. The trade-off is they both suffer from distorted hydrodynamic effects. One of the goals in this study is to examine how these scaling laws impact the error in the proposed RTHS framework. Other options have also been considered in the early stage of this study:

• Fr-Ca scaling with increased depth by a factor of 1/λ_{L}. In this case, the wet section of the tower (*z* ∈ [−*H*_{w}, 0]) is effectively unscaled, then the similitude of hydrodynamic forces generated on the specimen are preserved. But it is infeasible for wave tank facility to offer such a depth to study OWT. In addition, the design of the unscaled section needs to be adjusted to preserve the similitude in bending stiffness and mass.

• Fr-Ca scaling with increased wave amplitude by a factor of 1/λ_{L}. In this case, the amplitude of the generated wave is effectively unscaled. The inertia force *F*_{a} is properly scaled with a factor of ${\lambda}_{L}^{2}$, but the drag force *F*_{d} is distorted. This option is infeasible due to its high demand in the wavemaker.

• Froude scaling with λ_{ρ} = 1 and no further adjustment for the tower geometry, i.e., no added mass nor a matching bending stiffness *EI*. In this case, the hydrodynamic effects from the wave tank are properly scaled, but the modal properties of the OWT is distorted which causes significant response error.

These three options all have been rejected due to issues in their feasibility or accuracy.

### Error Contributors

In RTHS, experimental errors accumulate in real-time closed loop through the numerical integration scheme due to control and measurement discrepancies. It is known that delays and noises in the interfacing actuator and sensor systems are the main contributors to the above errors, as they tend to bring destabilizing effect into RTHS, causing large experimental error or even failure (Christenson et al., 2014; Maghareh et al., 2014; Hayati and Song, 2017). Such destabilizing effect is more pronounced in reduced scaled model testing than in full-scale, because the frequency of interest is amplified according to scaling process (Hayati and Song, 2018; Wu and Song, 2019). In addition, the impact of modeling choices (e.g., scaling laws, wave heights, and misalignment angles) on errors are also studied to guide future specimen designs.

In this study, to evaluate the feasibility and assess the performance of the proposed RTHS framework, noises, and delays are considered as the primary error contributors and modeled into the RTHS. As a concept study, the hardware implementation issues of sensors and actuators are out of the current scope. In Figure 7, a block diagram is provided to illustrate the general RTHS process described in Section. Framework Description. The noises and delays considered are the actuator noise, actuator delay, sensor noise, and sensor delay, which are also shown in Figure 7. The details of how the delays and noises are generated can be found in Section. Case I: Delay and Section. Case II: Noise, respectively. In addition, the other possible error contributors considered in this study are the scaling laws, misalignment angle β and the significant wave height *H*_{s}.

## Numerical Study

A concept study is carried out to assess the feasibility and identify the impact of the selected contributors on the performance of the proposed RTHS. The details and results for the study are described in Section. Numerical Study.

### System Parameters

The National Renewable Energy Lab (NREL) 5-MW reference wind turbine (Jonkman et al., 2009) is used in this study. Details of the modeling parameters are presented in Table 1.

As indicated in Figure 3, soil effects are considered using linear springs and dashpots. According to Carswell et al. (2015); Sun and Jahangiri (2018), the values for the spring stiffness are chosen as ${k}_{x}={k}_{y}=3.89\times 1{0}^{9}\text{}N/m$ and ${k}_{x\varphi}={k}_{y\varphi}=1.14\times 1{0}^{11}\text{}Nm/rad$ to represent clay soil condition. Soil damping coefficients *c*_{x}, *c*_{y}, *c*_{xϕ}, and *c*_{yϕ} are selected such that the corresponding damping ratios are ζ_{x} = ζ_{y} = ζ_{xϕ} = ζ_{yϕ} = 0.6%. Based on the FE model, the natural frequencies of the major bending mode with and without soil effects are 0.315 Hz and 0.335 Hz, respectively. Comparing to the natural frequency listed in Table 1, both values are close to the original natural frequency of 0.324 Hz, although the soil effects reduce the fundamental frequency by ~6%. The natural frequencies of the blade are obtained as 1.09 Hz (edgewise) and 0.68 Hz (flapwise), also match the values listed in Table 1.

### Simulated Loads

According to the procedure in Section. Wind Loading and the parameters in Table 1, the aerodynamic loading corresponding to a rotor speed of *V*_{r} = 12.1 *rpm*, an average wind speed of ${V}_{\infty}=12\frac{m}{s}$ at the hub height 90*m*, and a turbulence intensity of *TI* = 10%, is generated. According to the procedure in Section. Wave and Current Loading, a random wave corresponding to with the setting of *T*_{p} = 10 *s*, *H*_{s} = 3*m*, *H*_{w} = 17.5*m* (same as shown in Figure 5), is generated. Then, the nodal forces and moments, **F**_{wave}, at a misalignment angle β = 30° are computed accordingly. It is noted that the selected parameters in Section. System parameters and in generating these structural loads constitute a representative case of typical OWT behavior to investigate the proposed RTHS framework. Complex OWT behavior under specific site conditions will be investigated in future study.

### Numerical Models

In this study, the prototype and the RTHS models are simulated using MATLAB (MathWorks, 2020). The prototype is modeled using the parameters provided in Section. System parameters and the loads generated in Section. Simulated loads. The RTHS models are modeled in a similar way. The scaling laws described in Section. Error contributors are applied in creating experimental component in the corresponding RTHS models. Therefore, three RTHS models are created with one for each scaling law. The details about the scaling relations are shown in Table 2.

In all RTHS models, a length scale λ_{L} = 1/25 is used for the experimental component (the tower structure) and the water is considered as the fluid for the wave tank (hence λ_{ρw} = 1). Based on Table 2, it is noted that

*i)* The only scaling law completely preserves the similitude is the “Fr” model. The wave force generated in “Fr-Ca” and “Fr-Ca-dg” models does not match the force similitude of the tower structure. But it is noted that the specimen design is more challenging for the “Fr” model than the other two models as described in Section. Error contributors.

*ii)* The difference between “Fr-Ca” and “Fr-Ca-dg” models is that the wave spectrum is adjusted by a factor of 1/λ_{L}, or wave amplitude by a factor of $\sqrt{1/{\lambda}_{L}}$. As pointed out in Section. Error contributors, although such an adjustment preserves the similitude of drag force *F*_{d}, but the overall wave force scale is still distorted.

### Study Cases

A total of five cases are considered in this study to evaluate the feasibility and identify error contributors of the proposed RTHS framework. In each case, sensitivity analysis is performed to determine the influence of the error contributors and their tolerances for a feasible RTHS design. The relative root-mean-square error (RMSE) between the responses obtained from RTHS and the prototype model is used to measure the performance. Prior to the RMSE calculation, the responses obtained from the RTHS models are scaled back to full-scale using the corresponding scale factors listed in Table 2. Each numerical simulation runs with a time step of 1/1,024 s and a duration of 120 s.

#### Case I: Delay

In this case, both the actuator delay and the sensor delay shown in Figure 7 are considered in the RTHS simulations. Seven different delayed time steps are considered, which are 0, 2, 3, 4, 6, 8, and 10, for both delays. Therefore, a total of 49 simulations are performed for each RTHS model. To focus on the impact from delay, noises are set as zero in all the simulations.

The RMSE for the responses *u*_{7} and *u*_{8} are summarized in Figure 8. The responses of these two DOFs are chosen because they are the interfacing DOFs whose accuracy directly impacts the accuracy of both numerical and experimental components, and hence the overall performance. Abbreviations “Fr,” “Fr-Ca,” and “Fr-Ca-dg” indicate RTHS models obtained using Froude scaling, Froude-Cauchy scaling, and Froude-Cauchy scaling with drag force correction, respectively. The axes “*delay*_{A}” and “*delay*_{M}” indicate the number of delayed time steps in actuator and sensor (measurement) systems, respectively.

**Figure 8**. Case I: RMSE comparison. **(A)** RMSE of *u*_{7}, from left to right: Fr, Fr-Ca, Fr-Ca-dg. **(B)** RMSE of *u*_{8}, from left to right: Fr, Fr-Ca, Fr-Ca-dg.

From Figure 8, the RMSE error quickly increases as the delays increase. For the response in *u*_{7} the performance of the three RTHS models are similar. But, for the response in *u*_{8}, the error in Fr model is much smaller than the other two, indicating a better performance due to its preserved similitude. The contrast between *u*_{7} and *u*_{8} is because most of the response in *u*_{7} is induced by wind load, and most of the response in *u*_{8} is induced by the hydrodynamic forces. The error in *u*_{8} serves as a better indicator for scaling distortion in hydrodynamic force. For the RTHS models “Fr-Ca” and “Fr-Ca-dg,” where the hydrodynamic forces are distorted, their *u*_{8} responses are expected with higher errors than the “Fr” model.

To determine the tolerance on delays, a closer view on the RMSE results indicates, when both delays are 3 steps, the RMSEs for the Fr, Fr-Ca, Fr-Ca-dg are 5.5, 9.3, 5.3% for *u*_{7}, and 3.4, 86.5, 87.0% for *u*_{8}. These results indicate that the drag force correction improves the accuracy of *u*_{7} in the Fr-Ca-dg model comparing to the Fr-Ca model. But clearly, Fr model is the one that can provide accurate response estimation for both *u*_{7} and *u*_{8}. When inspecting Figure 9, the time histories in the Fr-Ca-dg model indicates that, although the comparison between the “INTG” (prototype) and the “RTHS” in *u*_{8} show obvious discrepancies, the amplitude of *u*_{8} is much smaller (almost negligible) than *u*_{7}. Actually, the root-mean-square (RMS) value of *u*_{8} is only 5% of that of *u*_{7}. Therefore, if only the significant fore-aft response is of concern, the Fr-Ca-dg RTHS model can also be considered as a viable alternative when both delays are 3 steps. For the Fr-Ca model, even when both delays are zero, the RMSE is still around 7%, which is the worst among all three RTHS models.

**Figure 9**. Case I: time history comparison in Fr-Ca-dg model (INTG—prototype; RTHS—RTHS model). **(A)** Time history of *u*_{7}. **(B)** Time history of *u*_{8}.

#### Case II: Noise

To determine the influence of noise on the performance of the proposed RTHS framework, both the actuator noise and the sensor noise shown in Figure 7 are considered in the RTHS simulations. The noises are generated as normally distributed random numbers with a zero mean and a standard deviation equal to a ratio of the standard deviation of the corresponding signal. *r*_{A} and *r*_{M} denote such ratios for the actuator noise and the sensor noise, respectively. Seven values for both ratios are chosen as 0, 1, 2, 5, 10, 15, and 20%. Therefore, a total of 49 simulations are performed for each RTHS model. To focus on the impact from noise, delays are set as zero in all the simulations.

From Figure 10, it is shown that, for *u*_{7}, both the Fr and the Fr-Ca-dg models produce smaller errors than the Fr-Ca model; for *u*_{8}, the Fr model yields the smallest error, and both the Fr-Ca and the Fr-Ca-dg models produce similar levels of error, due to their distorted hydrodynamic effects. The contour lines in parallel to *r*_{M} axis in all the graphs indicate that the RMSEs are more sensitive to the noise levels in the actuator system than in the sensor system. The reason is that the numerical component simulated in full-scale has lower natural frequencies than the experimental component. The sensor noises fed into the numerical system is effectively “filtered” by the numerical system and impose little influence on the system responses. While most of the RMSE results demonstrate an increasing trend with respect to the noise level, the RMSE of *u*_{8} in the Fr-Ca-dg model shows a decreasing phase before the increasing trend. The exact reason to this observation is unknown, but it may be related to the drag force correction. The RMSEs of the blade responses (*u*_{1}~*u*_{6}) are also examined, but only small changes are shown with the considered noise range, and therefore are not shown in this study.

**Figure 10**. Case II: RMSE comparison. **(A)** RMSE of *u*_{7}, from left to right: Fr, Fr-Ca, Fr-Ca-dg. **(B)** RMSE of *u*_{8}, from left to right: Fr, Fr-Ca, Fr-Ca-dg.

Because the RMSEs show weak sensitivity with respect to the sensor noises, Table 3 is prepared by averaging all the RMSEs with the same actuator noise levels but different sensor noises.

Based on Table 3, it can be seen that the Fr-Ca-dg model yields the smallest error on *u*_{7}, and the next is the Fr model. Both of them yield around 4 − 5% error under 15% level of noise. The Fr-Ca model, however, produces more than 10% RMSE at 15% level of noise. For *u*_{8}, similar as Case I, only the Fr model can produce accurate tracking up to 5% level of noise. Again, if *u*_{8} is not of concern, then both the Fr and the Fr-Ca-dg models can be adopted for RTHS development.

#### Case III: Delay Combined With Noise

To examine the performance under combined effects of delay and noise, the actuator delay and the sensor delay are set to be equal to each other with the seven predetermined values, i.e., *delay*_{A} = *delay*_{M} = *delay* = 0, 2, 3, 4, 6, 8, and 10; and the noises are also set in a similar manner with *r*_{A} = *r*_{M} = *r* = 0, 1, 2, 5, 10, 15, and 20%. A total of 49 simulations are performed for each RTHS model.

In Figure 11, three RMSE plots are presented for the Fr model. The blade response *u*_{1} is selected to represent the blade edgewise responses, *u*_{1}~*u*_{3}, and *u*_{4} to represent the flapwise responses, *u*_{4}~*u*_{6}. All three plots indicate an increasing trend with response to the delays, and the contour lines show that RMSEs are more sensitive to the delays than to the noise levels. It is also noted that the blade flapwise response *u*_{4} has a much higher RMSE value than the others, which is inspected further when discussing the tolerance. It is observed that the RMSEs of *u*_{1}, *u*_{4}, and *u*_{7} in the Fr-Ca and Fr-Ca-dg models are similar as those in Figure 11, and therefore are not repeated here.

The RMSEs for *u*_{8} of the three RTHS models are compared in Figure 12. They all show sensitivities to both delay and noise levels to some extent. The Fr-Ca model shows higher sensitivity to noises than to delays, while the Fr model shows similar levels of sensitivities to both. The Fr-Ca-dg model provides a non-monotonic relation against noise, which matches the observation made in Case II. The RMSEs in the Fr-Ca and Fr-Ca-dg models are much higher than the Fr model, similar as observed from Cases I and II.

Because the RMSEs of *u*_{1}, *u*_{4}, and *u*_{7} show weak sensitivity to noise levels, Table 4 is prepared to demonstrate the delay impacts on error tolerance by averaging all the RMSEs with the same delays but different noise levels. Note that the delays applied in this section carry a doubled-effect because both actuator and sensor are specified with the same amount of delay. Based on the results in Table 4, all three models show similar performance for *u*_{1} and *u*_{4}. For *u*_{7}, both the Fr and Fr-Ca-dg models provide superior performance to the Fr-Ca model, and Fr-Ca-dg model is slightly better than the Fr model. It is noted that, even with very low delays, the RMSE for *u*_{4} is around 4% and increases rapidly as the delay increases. However, such a level of RMSEs in the blade responses do not induce a large error in the tower response, *u*_{7}, because tower is evaluated under a reduced scale and the errors in the full-scale blade responses are reduced accordingly before sending to the experimental component. Therefore, if the blade responses are of interest, the RTHS implementation needs to guarantee a well-compensated RTHS to address the delay issues. To further understand the behavior of the scaled RTHS model, 20 s of time histories of the actuator force (in *x* direction), ${\text{F}}_{\text{I}}^{\text{N}}-{\text{f}}_{\text{I}}^{\text{E}}$, the sensor measurement (in *x* direction), ${\ddot{\text{u}}}_{\text{I}}$, and the responses, *u*_{4} and *u*_{7}, are shown in Figure 13 for the Fr model with *delay* = 2 and *r* = 20%. In the plots, the “INTG” curve indicates the prototype behavior without delay and noise, and the “RTHS” curve indicates the behavior from the Fr model. It can be seen that although the actuator force and sensor measurement are contaminated by noises, the responses show fairly smooth behavior and follow the natural frequencies of the blade and the tower. The reason is the broadband noises are effectively filtered by the blade and tower which has low fundamental frequencies (see Table 1) even after the scaling.

**Figure 13**. Case III: time history comparison in Fr model for *delay* = 2 and *r* = 20% (INTG—prototype; RTHS—RTHS model). **(A)** Time history of actuator force. **(B)** Time history of sensor measurement. **(C)** Time history of *u*_{4}. **(D)** Time history of *u*_{7}.

#### Case IV: Misalignment Angle

The misalignment angle β = 30° is applied in Cases I, II, and III. Based on their results, the errors generated in RTHS models are closely related to the delays and noise levels. For the Fr-Ca and Fr-Ca-dg models, the errors are also attributed to the distorted hydrodynamic effects. Therefore, the hydrodynamic load generation is further examined. In this case, the impact of misalignment angle β on the RTHS performance is studied. For each RTHS model, three nominal delay-noise combinations are considered:

• Good condition: *delay*_{A} = *delay*_{M} = *delay* = 1, *r*_{A} = *r*_{M} = *r* = 1%;

• Medium condition: *delay*_{A} = *delay*_{M} = *delay* = 3, *r*_{A} = *r*_{M} = *r* = 5%;

• Bad condition: *delay*_{A} = *delay*_{M} = *delay* = 6, *r*_{A} = *r*_{M} = *r* = 10%.

These conditions correspond to the quality of the actuator compensation design and fidelity of the sensor signals. For each condition, the misalignment angles ranging from 0° to 360° are considered with an increment of 15°.

The RMSE results for *u*_{7} and *u*_{8} are shown in Figure 14. For *u*_{7}, the performances of the Fr and the Fr-Ca-dg model are similar and show no particular dependence on β. The Fr-Ca model, however, shows that the errors near β = 90° or 270° are lower than the other β values. For *u*_{8}, only the Fr model demonstrates RMSE values lower than 5% in all β values under the good condition. The Fr model also shows that higher RMSEs are expected when β is near 0° or 180° in all conditions. In contrast, for the Fr-Ca and the Fr-Ca-dg models, the RMSE is lower (around 5%) when β is near 0° or 180° (alongwind) under the good condition. This observation is expected because the distorted hydrodynamic effects only influence the fore-aft responses in this case and causes a lower impact in the side-side responses comparing to the wind load. High RMSEs are expected in other β values. Therefore, they can be considered for RTHS implementation for the alongwind cases. The RMSEs of the blade responses (*u*_{1}~*u*_{6}) for all three RTHS models are also examined. They show no particular dependence on β, and therefore, are not repeated here.

**Figure 14**. Case IV: RMSE comparison. **(A)** RMSE of *u*_{7}, from left to right: Fr, Fr-Ca, Fr-Ca-dg. **(B)** RMSE of *u*_{8}, from left to right: Fr, Fr-Ca, Fr-Ca-dg.

#### Case V: Wave Height

Another parameter related to the hydrodynamic load generation is the significant wave height *H*_{s}. In all previous cases, a significant wave height *H*_{s} = 3*m* is used. To study the impact of different wave heights on the RTHS performance, *H*_{s} values equal to 0.5, 1.5, 3, and 4.5 *m*, are considered. For each *H*_{s} value, the misalignment angles ranging from 0° to 360° are considered with an increment of 15°. In all simulations, only the “good condition” delay-noise combination is applied, i.e., *delay*_{A} = *delay*_{M} = *delay* = 1, *r*_{A} = *r*_{M} = *r* = 1%.

The RMSE results for *u*_{7} and *u*_{8} are shown in Figure 15. For *u*_{7}, the Fr model shows no particular dependence on *H*_{s}. The Fr-Ca-dg model provides similar RMSEs as the Fr model, except near the region β = 120° ~ 240°, where the error increases as *H*_{s} increases. The RMSEs in Fr-Ca-dg model increase as *H*_{s} increases, except near β = 90° or 270°, where the errors are lower and insensitive to the change in *H*_{s}. For *u*_{8}, only the Fr model provides RMSE values lower than 5% in all β values. The RMSE in the Fr model demonstrates a deceasing trend as *H*_{s} increases and reaches the highest values when β is near 0° or 180°. Both the Fr-Ca and the Fr-Ca-dg models show an RMSE increasing trend as *H*_{s} increases. In contrast to the Fr model, their RMSEs reaches the lowest values (around 5%) when β is near 0° or 180° (alongwind), and the highest when β is near 90° or 270° (crosswind). This observation is consistent with Case IV. The RMSEs of the blade responses (*u*_{1}~*u*_{6}) for all three RTHS models are also examined. They show no particular dependence on *H*_{s}, and therefore are not repeated here.

**Figure 15**. Case V: RMSE comparison. **(A)** RMSE of *u*_{7}, from left to right: Fr, Fr-Ca, Fr-Ca-dg. **(B)** RMSE of *u*_{8}, from left to right: Fr, Fr-Ca, Fr-Ca-dg.

## Conclusions

In this study, a RTHS framework for monopile OWT is proposed. Three RTHS models, representing three different scaling laws, are modeled and simulated. By comparing their responses with those of the prototype in a set of sensitivity analyses, the performance and the possible error contributors of the proposed RTHS are evaluated. The findings provide important insights for future RTHS implementations. These findings include:

• RTHS using Froude scaling (the Fr RTHS) can provide the best overall performance in capturing the responses in both the numerical (blades) and the experiment (tower) components. It can achieve <5% RMSE for all responses with all misalignment angles and wave heights under the “good condition,” i.e., *delay*_{A} = *delay*_{M} = *delay* = 1, *r*_{A} = *r*_{M} = *r* = 1%. Its specimen design and construction are more challenging than the other two scaling laws considered. But if the difficulty in specimen design can be overcome, the Froude scaling RTHS is the preferred method for RTHS implementation.

• RTHS using Froude-Cauchy scaling with drag force correction (the Fr-Ca-dg RTHS) is a viable alternative to the one with Froude scaling. It offers similar performance as the Fr model in almost all responses, except the ones in side-side direction (*u*_{8}), due to the distorted hydrodynamic effects. However, if the responses in side-side direction is not of concern or when they are in much lower amplitude than the wind-induced responses, for example, when the wave is aligned with the wind direction (β is near 0° and 180°), the Fr-Ca-dg RTHS can also be considered for RTHS implementation. Its advantage over the Froude scaling is in the specimen design—it provides a systematic way to construct the scaled specimen (using added artificial mass).

• RTHS using the conventional Froude-Cauchy scaling (the Fr-Ca RTHS) is the least attractive one in this study. It offers the same advantage in specimen design and construction like the Fr-Ca-dg model, and it has the same issue on capturing the side-side responses. But even for the fore-aft response (e.g., *u*_{7}), it demonstrates lower robustness against noise and delay comparing to the Fr-Ca-dg RTHS (see Tables 3, 4). It does have an advantage over the Fr-Ca-dg RTHS in that it is less demanding in the wave generation, as it does not require the drag force correction.

• Even with the Froude scaling, it is observed that, the proposed RTHS framework is more sensitive to the delays than to the noises, and it is more sensitive to the actuator noises than to the sensor noises.

• To accurately capture the responses in blades, a small (around 1~2 steps) delay needs to be specified. If only the responses in tower is of concern, the delay requirement can be relaxed to 4~6 steps (see Table 4).

As a concept study, only numerical simulations are considered herein, and the modeling parameters are selected to represent typical OWT behavior to investigate the proposed RTHS framework. Experimental implementations of the proposed RTHS framework will be carried out in the future. In addition, torsional DOFs of the tower are not considered at the current stage. As the study further develops, more complex modeling techniques, and loading cases will be considered in implementing the proposed RTHS framework with specific OWT designs and site conditions.

## Data Availability Statement

The datasets generated for this study are available on request to the corresponding author.

## Author Contributions

WS completed the main writing task of the paper and the main coding. Oversee the development of the study presented in the paper. CS completed part of the coding (on wave load generation) used in the analysis. YZ completed part of the literature review and the writing of the paper. VJ completed part of the coding (on wind load generation) used in the analysis. YL contribute to the review, editing, and assist the development of the study presented in the paper. QH contribute to the review, editing, and assist the development of the study presented in the paper. All authors contributed to the article and approved the submitted version.

## Conflict of Interest

The authors declare that the research was conducted in the absence of any commercial or financial relationships that could be construed as a potential conflict of interest.

## Supplementary Material

The Supplementary Material for this article can be found online at: https://www.frontiersin.org/articles/10.3389/fbuil.2020.00129/full#supplementary-material

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Keywords: monopile, offshore wind turbine, real-time hybrid simulation, wind load, wave load, froude scale, cauchy scale

Citation: Song W, Sun C, Zuo Y, Jahangiri V, Lu Y and Han Q (2020) Conceptual Study of a Real-Time Hybrid Simulation Framework for Monopile Offshore Wind Turbines Under Wind and Wave Loads. *Front. Built Environ.* 6:129. doi: 10.3389/fbuil.2020.00129

Received: 02 June 2020; Accepted: 15 July 2020;

Published: 26 August 2020.

Edited by:

Eleni N. Chatzi, ETH Zürich, SwitzerlandReviewed by:

Giuseppe Abbiati, Aarhus University, DenmarkFrancesco Tornabene, University of Salento, Italy

Imad Abdallah, ETH Zürich, Switzerland

Copyright © 2020 Song, Sun, Zuo, Jahangiri, Lu and Han. This is an open-access article distributed under the terms of the Creative Commons Attribution License (CC BY). The use, distribution or reproduction in other forums is permitted, provided the original author(s) and the copyright owner(s) are credited and that the original publication in this journal is cited, in accordance with accepted academic practice. No use, distribution or reproduction is permitted which does not comply with these terms.

*Correspondence: Wei Song, wsong@eng.ua.edu