Tip-Bed Velocity and Scour Depth of Horizontal-Axis Tidal Turbine with Consideration of Tip Clearance

: The scouring by a tidal turbine is investigated by using a joint theoretical and experimental approach in this work. The existence of a turbine obstructs a tidal ﬂow to divert the ﬂow passing through the narrow channel in between the blades and seabed. Flow suppression is the main cause behind inducing tidal turbine scouring, and its accelerated velocity is being termed as tip-bed velocity ( V tb ). A theoretical equation is currently proposed to predict the tip-bed velocity based on the axial momentum theory and the conservation of mass. The proposed tip-bed velocity equation is a function of four variables of rotor radius ( r ), tip-bed clearance ( C ), e ﬄ ux velocity ( V 0 ) and free ﬂow velocity ( V ∞ ), and a constant of mass ﬂow coe ﬃ cient ( C m ) of 0.25. An experimental apparatus was built to conduct the scour experiments. The results provide a better understanding of the scour mechanism of the horizontal axis tidal turbine-induced scour. The experimental results show that the scour depth is inversely proportional to tip-bed clearance. Turbine coe ﬃ cient ( K t ) is proposed based on the relationship between the tip-bed velocity and the experimental tidal turbine scour depth. Inclusion of turbine coe ﬃ cient ( K t ) into the existing pier scour equations can predict the maximum scour depth of a tidal turbine with an error range of 5–24%.


Introduction
Tidal current energy is predictable compared to other renewable resources, which makes it a reliable source of such energy [1]. Tidal turbines are the main energy generating devices used to harness tidal power in various countries [2]. Scientists and engineers have conducted various investigations to push for tidal power to be available for mass utilization with cheaper electricity prices [3]. The seabed scouring of turbines is an important consideration for their design and application. The maximum scour depth is one of the main interests of engineers, and scour depth can be related to water depth, turbine blade numbers, and blade area ratios [4]. The existence of a turbine obstructs flow with its blockage effects, and turbine scouring is influenced by the tip clearance between blades and the seabed [5].
The understanding of tidal turbine scouring is limited for scientists and engineers. SeaGen in Strangford Loch, Belfast, is an important case of using a quad pile structure fixed on the seabed to support a tidal power system. Early researchers presumed that tidal turbine-induced scouring is analogous to bridge pier-induced scouring when a monopile support is used [4]. A tidal turbine scour is dominated by its monopile support interacting with the seabed. This scouring is caused by a horseshoe vortex at the upstream pile as well as the vortex shedding within the downstream wake [6]. Neill [7] proposed that the ratio of scour depth to the diameter of a pile is a constant value, and maximum scour depth is proportional to the pile diameter. Breusers et al. [8], Sumer et al. [9], and Richardson et al. [10] suggested that more parameters should be considered, including free flow velocity, water depth, bed condition, and the size of sediment, for the proposal of their enhanced equations based on Neill's proposal.
Propeller scouring is different than the scouring caused by a single cylinder. The rotating propeller produces a high velocity jet, and this jet is the main factor of active seabed scouring. Albertson et al. [11], Hamill [12], and Lam et al. [13] investigated velocity distribution within propeller wake and proposed wake distribution equations. Jiang et al. [14] proposed a theoretical model for a ship twin-propeller jet. The scour pattern induced by a propeller was attributed mainly due to the expansion of a propeller wake. Hamill et al. [15,16] studied propeller seabed scouring under various seabed conditions, as well as a scouring pattern with the existence of a quay wall to propose equations for estimating the maximum depth of a scouring with a quay wall. Cui et al. [17] proposed an empirical 2D scour model to predict the scour profile of a propeller.
A tidal turbine and propeller are both the rotating devices submerged underwater. The rotating propeller releases energy into the water through the production of forward thrust, and a turbine extracts energy from the water through rotations. Lam et al. and Ma et al [18,19] found that strong shadowing effects appeared on the turbine through the analysis of experimental and numerical results. Chen and Lam [5] studied the shadowing effect of a turbine rotor and showed that the velocity of a slipstream is accelerated by about 105%. Previous studies have suggested the presence of tidal turbine effects on seabed scouring [20][21][22][23]. Giles et al. [24] showed that flow is suppressed due to blockage and accelerates to balance mass flow and velocity. Wang et al. [25] proposed efflux velocity equations by fitting an energy coefficient equation with a tip speed ratio.
This study was aimed to determine the effects of a rotating turbine on seabed scouring. A tip-bed velocity equation is proposed to predict the accelerated velocity in between the blades and seabed, with a consideration of the mass flow coefficient (C m ) based on the axial momentum theory and the conservation of mass. Experiments were conducted to investigate tidal turbine scouring with a consideration of tip clearances. An empirical equation is proposed to estimate the maximum scour depth.

Tip-Bed Velocity Used for Seabed Scouring
The tip-bed velocity between a tidal turbine and the seabed is the main factor in seabed scouring around tidal turbine structures. Tip-bed flow is squeezed and accelerated due to the existence and blockage of a rotating turbine. Flow suppression increases the velocity within the channel and in between the blades and seabed. This accelerated velocity in the region between the blades and turbine is termed the tip-bed velocity, a concept which can lead to a more severe scour. We propose a tip-bed velocity equation to predict the velocity between the tidal turbine and seabed based on the axial momentum theory and conservation of mass.

Tip-Bed Velocity Equation
A minimum efflux velocity appears at the outflow plane of a tidal turbine due to the extraction of energy. Equations to predict efflux velocity were proposed by Albertson et al. [11], Hamill et al. [26], and Lam and Chen [27] based on the axial momentum theory. The turbine is considered an actuator disc under assumptions in axial momentum theory. Figure 1 shows the effect of an actuator disc model on the flow pattern in one direction. The axial momentum theory assumes no energy losses in fluid motion, and the Bernoulli equation can be applied to balance energy in the upstream regions (far upstream (location 1) and immediately upstream (location 2)) and downstream regions (immediately downstream (location 3) and far downstream (location 4)), as shown in Figure 1. Equation (1) shows the relationship between the pressure potential energy and kinetic energy upstream of the actual disc (locations 1 and 2).
Equation (2) shows the relationship between the pressure potential energy and kinetic energy downstream of the actuator disc (locations 3 and 4).
where ρ is the density of fluid (kg/m 3 ); P 1 , P 2 , P 3 , and P 4 are the pressure (Pa); and U 1 , U 2 , U 3 , and U 4 are the axial velocity (m/s). The thrust acted at the actuator disc is produced due to the pressure difference (P 2 , P 3 ) between front and back surfaces in Equation (3). The free flow has energy losses when passing through the actuator disc.
where T is the thrust force (N), A is the area of the actuator disc (m 2 ), and P 2 and P 3 are the pressures located at the immediate upstream and immediate downstream (Pa). Pressure is assumed to be equal (P 1 = P 4 ) far upstream and far downstream, and fluid velocity is equal (U 2 = U 3 ) when immediately passing through the actuator disc due to continuity. Equation (4) can be obtained by solving (P 2 -P 3 ) using Equations (1)-(3).
The thrust function (T) with thrust coefficient (C T ) of tidal turbine in Lam et al. [18] is presented in Equation (5) as an alternative to balance Equation (6).
The efflux velocity equation in Lam et al. [18] is obtained through the rearrangement of Equation (6) to predict the efflux velocity (V 0 ), as shown in Equation (7).
where V 0 is efflux velocity (m/s), which is equal to U 4 in the Equation (6). V ∞ is the free flow velocity (m/s) which is equal to U 1 in Equation (6) A narrow region is formed between the turbine and seabed when the turbine is close to the seabed. The existence of rotating turbine disturbs the natural water flow by blocking partial water and extracting energy with velocity reduction with a complicated wake downstream and accelerated tip-bed velocity, which is generally called as shadowing effect. The shadowing effect of a tidal turbine is the main influencing factor on tidal turbine scouring. The squeezing process of tip-bed velocity is shown in Figure 2. The tip-bed velocity of this squeezed flow is accelerated by the shadowing effect of tidal turbines [5]. The aforementioned axial momentum theory is combined with the conservation of mass to estimate the tip-bed velocity. Partial free flow passes through the actuator disc, and the other flow spreads around due to the shadowing effect of rotating turbines. Equation (8) shows the mass flow pass through a turbine in a unit time.
where m is the mass flow rate (kg/s), ρ is the density of fluid (kg/m 3 ), U 2/3 is the axial velocity immediate upstream or immediate downstream (m/s), A is the area of the actuator disc (m 2 ), U 1 is the axial velocities far upstream (m/s), and A 1 is the area of water flowing through the actuator disc at location 1 (m 2 ). Equation (9) shows the total mass flow rate far upstream in area A, which is same as the area of the actuator disc, as shown in Figure 2 where m 1 is the total mass flow rate in area A at location 1 (kg/s). Free flow diffusion occurs due to the shadowing effect of the actuator disc within area A, as shown in Figure 3, which leads to the acceleration of the surrounding flow. Equation (10) shows the mass flow that does not pass through the actuator disc.
where ∆m is the mass flow rate that does not pass through the actuator disc (kg/s). The fluid that does not pass through the actuator disc can be represented by U 1 and U 4 through energy analysis in order to rearrange and simplify Equation (10). Equation (11) shows the extracted energy by a tidal turbine.
where ∆P is the extracted energy of tidal turbine and m is the mass flow rate through a turbine (kg/s). Energy changes after the flow passes through a turbine. The change of energy can be regarded as the energy extracted by the turbine, as shown in Equation (12).
The mass flow rate that does not pass through the tidal current turbine (Equation (10)) can be represented by inserting U 2/3 of Equation (13), as shown in Equation (14).
The flow that does not pass through the tidal turbine is spread around due to the shadowing effect of tidal current turbines, as shown in Figure 3. Downward flow is mixed with free flow in the tip-bed region, which leads to an increase in tip-bed velocity compared to the undisturbed free flow. The mass flow coefficient C m is proposed to present the ratio of ∆m 1 (flow mass passing through the mixing area) to ∆m (the total mass that does not pass through the tidal turbine), as shown in Equation (15). The mixing area is shown in Figure 4. The mass flow coefficient C m is related to turbine parameters, tip clearance, water depth, turbulence intensity, and seabed conditions. This assumes that the water can flow downward, upward, leftward, and rightward, and 25% of the water is flowing downward into the mixing area. A mass flow coefficient C m of 0.25 is taken to represent the downward water.
where C m is the mass flow coefficient and ∆m 1 is the downward mass flow (kg/s). Equation (16) shows the mass flow passing through the mixing area. The left hand side is the mass flow passing through the mixing area upstream. The right hand side is the mass flow which represents the tip-bed velocity. A tip-bed velocity equation is proposed by rearranging Equation (16), as shown in Equation (17).
where r is the radius of the actuator disc (m), C m is mass flow coefficient, C is the tip clearance between the turbine and seabed (m), V tb is the tip-bed velocity (m/s), V 0 is the efflux velocity (m/s), and V ∞ is the free flow velocity (m/s).

Comparison
Chen and Lam [5] investigated the slipstream between the seabed and the marine current turbine via OpenFOAM. Figure 5 shows the comparison between the proposed tip-bed velocity equation and the previous works. The mass flow coefficient C m is theoretically taken as 0.25. The tip-bed velocity is 1.46 V ∞ in theory when the tip clearance is zero. Theoretical work shows the maximum increment of the tip-bed velocity is 46% of the free flow velocity due to blockage effects. The application range of the tip-bed velocity equation is for a tip clearance of more than 0.4 D t . The maximum variation of 3.06% occurred at 0.4 D t for the tip clearance in the range 0.4-1.0 D t , as shown in Table 1.
The proposed equation fits better in bigger tip-bed clearance areas compared to previous works. The variation increases in smaller tip-bed clearance. The discrepancy may be due to the influence of mass flow coefficient C m in the calculation of tip-bed velocity. It is assumed that 25% of water flows downward into the mixing area. Actually, C m depends on many turbine parameters, and various values of C m at different tip-bed clearances should be proposed in future.

Purposed-Built Apparatus
A series of scour experiments were carried out in the Marine Renewable Energy Laboratory at Tianjin University, P.R. China. The experimental flume was a purpose-built horizontal recirculating flume used to model the tidal flow in the actual conditions. This flume was 1.8 m in length, 0.8 m in width, and 0.6 m in height, as shown in Figure 6. An inner separator was used to produce a recirculating channel with a 0.25 m width. The flume was a patented invention of a horizontal recirculating flume for a tidal-current-turbine by Lam et al. [28], with an application number of 2016107047703CN. Perspex panels were used for both sides of the recirculating flume to allow for transparent observations from the side view during experiments. The flow recirculation was driven by a propeller submerged into the water channel (as shown in label 2 in Figure 6). The turbine model was positioned at opposite sides of the flume to investigate its induced scouring. A pitot tube was used to measure the mean velocity to determine the incoming flow speed in the recirculating flow. The free flow velocity in the water channel could be adjusted by controlling the rotational speed of a propeller. The turbine was made via 3D-printing, using a polylactic acid (PLA) material with an accurate curvature blade, as shown in   Sediment was filled into a sand box, which was 0.25 m in width, 1 m in length, and 0.1 m in depth, to model the seabed (located at label 9 in Figure 6). The sand box was used to locate the sand at the designated location in the flume bed and was easy to remove after experiments. The upstream and downstream areas of the sandbox had slopes to ensure that the flow passed through the measurement area smoothly. A flat plate was fixed on the head of the sand box. The combination of a slope plate and a flat plate made the flow pass through the test section smoothly in the scouring process. The sand was filled in the box and was levelled by using a sand leveller before the scour experiments. A monopile support structure was embedded into the middle of the sandbed during the tests. Sands with a median particle size of d 50 = 1 mm were used in the experiments to keep the scouring condition of clear water, as shown in Figure 8, which ensured that the incoming flow velocity near the seabed (u* ≈ 0.013 m/s) was below the incipient velocity of sediment (u c * ≈ 0.023 m/s for the sediment with a diameter d 50 = 1.0 mm. The critical Shields parameter was 0.034).
The turbine used in the experiment was a three-bladed horizontal-axis turbine. The rotor diameter was 0.08 m, and the pitch angle was 15 • . These parameters of the blades were obtained from the performance test of a tidal turbine based on Bahaj et al. [29], which was a 1:10th geometric scaling model. In this paper, the free flow velocity applying Froude similitude was 0.22 m/s. Four types of Reynolds number were provided on the basis of facility, the tidal turbine, and the cylinder structure [30][31][32]. Detailed flow parameters of the flume and tidal turbine are shown in Table 2.  Four groups of experiments were conducted at various tip clearances to investigate the seabed scouring of a tidal turbine, as listed in Table 3. The seabed scour depth was measured at time = 2 min, 15 min, 30 min, 60 min, and 120 min. Water recirculation in the flume was stopped during the scour depth measurement. The seabed scour depth was measured by using a laser range finder. The propeller continued to drive the water circulation after the completion of each measurement. According to the work of Whelan et al, the blockage ratio (B = A/bh) was 0.04 in the recirculating flume, which was effectively unblocked [33]. The diameter of the turbine was much smaller than the width of the water channel with 1 D t space to the edges of flume. The tidal turbine was submerged at 2 D t underwater. Thus, the impacts of boundary effects and water free surface were assumed insignificant during seabed scour experiments.

Flow Disturbance and Perturbation
Flow disturbance and perturbation were mainly caused by the water circulation in the channel. The bend of the water channel caused the outer flow (flow close to the outer section) to move faster than the inner flow (flow close to the inner section) due to centrifugal forces. Before the seabed scouring experiment, velocity measurements were carried out at four transverse sections upstream of the turbine (Figure 9), and these were used to investigate the incoming flow structure and its turbulent level.
The distribution of axial velocity was complicated at Section 1 of Figure 9a due to the combined effects of water motion in the bending region and the propeller wake as shown in Figure 10a. A perforated distribution plate ( Figure 6, label 8) with square grids was fitted to break the turbulence structures and to remove the large scale eddies caused by the flow direction change in the bending region. This produced a continuous flow with uniform velocity distribution at the inlet of the test section. The size of the square grids is generally calculated using the empirical Equation (18) [34].
where M is the width of the water channel (m) and d is the width of the square grids on the perforated distribution plate (m). The velocity distributions at the horizontal and vertical sections in the water channel are presented in Figure 10a,b. The velocities in the x-axis are non-dimensionalised by the free flow velocity (V ∞ ). The y-axis in Figure 10a,b represent the distances along the horizontal and vertical sections, respectively, and are non-dimensionalised by the channel depth (L d ) and the channel width (L w ). The axial velocity profile at Section 1 shows that the turbulent level was significant in the turning point, and the velocity distribution was non-uniform compared to the following downstream Sections 2-4, as shown in Figure 10a. The flow was smoothened to be more uniform after passing through the perforated distribution plate at Section 2. The mean velocity was slightly increased at Section 3 compared to Section 2 due to the existence of the sand box. The sand box reduced the water height to accelerate the flow in the channel due to continuity effects. The velocity difference between the outer flow and inter flow at Sections 2 and 3 was much greater than Section 4. It can be seen that the velocity difference between the inner and outer flows decreased downstream and reached a close to uniform flow at 1 D t upstream. The maximum difference of velocity was insignificant, with only 0.01 m/s for the inner and outer flows at Section 4. A vertical velocity distribution in the z direction was located at Section 4, as shown in Figure 10b. Vertical lines 1 and 3 were located at the left/outer side and right/inner side of the cross section respectively and the vertical line 2 was located at the middle, as shown in Figure 9b. It should be noted that the zero point in z direction was located at seabed.
The influence of water depth was insignificant, with a maximum velocity difference of only 0.02 m/s due to seabed effects. The flume was presumed to provide uniform flow for the experimental investigation.

Results and Discussion
Seabed scouring experiments for turbines were conducted to better understand the influences of the shadowing effect on seabed scouring at different tip clearances. The experiment results were recorded at the times of 2 min, 15 min, 30 min, 60 min, and 120 min. The heights of the turbine position were set at the tip clearances of 0.25 D t , 0.50 D t , 0.75 D t , and 1.00 D t .

Seabed Scour Profile
Tidal turbine scouring has an analogous profile and moving trend compared to cylinder scouring, as shown in Figure 11. The maximum scour depth for a tidal turbine with clearances C/D t = 0.5 and 1.0 was compared to the cylinder scouring experiments by Zhao et al. [35], Kitsikoudis et al. [36], and Yao et al. [37], as listed in Table 4. The monopile-supported tidal turbine scouring was analogous to the single monopile when its turbine was placed at a position with sufficient height. The influence of the rotating turbine was significant to the seabed at a low clearance condition, but it was insignificant for a high clearance. The maximum scour depth for a tidal turbine with a tip clearance of 1.0 D t was 0.9 D s , which is close to the cylinder scour depth of 1.11 D s , 1.0 D s , and 1.0 D s found by Zhao et al. [35], Kitsikoudis et al. [36], and Yao et al. [37], respectively. The tidal turbine had a deeper scour pit compared to the cylinder monopile when the tip clearance of the tidal turbine was small, which was 0.5 D t in the current work. The scouring range of the sand pit caused by the tidal turbine with a tip clearance of 1.0 D t was almost the same as the cylinder scour. However, the sand dune profile was different for various cases. The tidal turbine-induced sand dune was higher compared to the cylinder due to the participation of turbine wake. The free flow velocity and scouring time also had significant impacts on the height of the sand dunes.  Lam et al. [18], Chen [38], and Hill et al. [22] analysed the shadowing effect of tidal turbines on seabed scouring. Figure 12 shows a comparison between the current experimental results and those of Chen  The maximum scour depth in the recirculating flume (S = 0.177 D t ) was only 8% deeper than the seabed scour depth found by Chen (S = 0.165 D t ) [38]. The rear boundary of the scour pit was moved backward compared that found by Chen [38], which may be due to the effects of a higher turbulence intensity at the rear of the tidal turbine. Chen [38] used a tip speed ratio (TSR) = 3.67 for all cases, and the current works used TSR = 5. Turbulence intensity may cause excessive vortex shedding at the rear of a tidal turbine with the higher TSR, leading to seabed scour pit was more expansive than Chen [38] Our tidal turbine-induced scour profile is slightly different than that of Hill et al. [22] in both clear water and live bed sediment transport experiments. It should be noted that the turbine was only submerged at 0.5 D t in the Hill et al. [22], and the tidal turbine was submerged at 2 D t in this work. The difference in position of the submerged turbine caused the different scour depths due to the influence of the free water surface. Hill et al. [22] indicated that their mean water surface elevations indicated a maximum peak-to-trough oscillation at the rotor location of approximately 2-3% of the flow depth with the turbine effect on the free surface. The oscillation of the free surface led to the length extension of the seabed scour pit. The maximum seabed scour depth in live-bed conditions (Hill et al. [22] had a scour depth of S = 0.24 D t ) is usually deeper than that of clear water scouring (novel recirculating flume scour depth, S = 0.177 D t ).

Scouring Process
Seabed scouring is mainly caused by the obstruction of a support structure and the shadowing effect of a rotating tidal turbine. Figure 13 shows the evolution of the scouring process of tidal turbines with support structures. The vortex scale is small in the initial stage, but its effect on local scouring is obvious. This indicates that the scouring process was strong at the initial stage, and a scour pit was quickly formed around the cylinder. The sand dune was deposited at the rear of the cylinder. The experiment showed that the depth of the scour reached about 60% of the stabilisation stage in the first 15 minutes. During the development stage, the depth of the seabed scour consistently increased with time, and the width of the pit was expanded. A sharp edge was formed at the tail of sand dunes, and the height of sand dunes kept increasing. During the stabilisation stage, the depth of the sand pit was no longer changed. The shear stresses and turbulence disturbance were no longer significant to the motion of sediment particles in the scour pit. The scour depth tended to reach the limit. Though the scour pit was balanced, the sand dunes continued to move downstream. The sand dunes were continuously scoured and gradually approached the seabed as the scouring proceeded.   Figure 14 shows the maximum scour depth of the tidal turbine under different tip clearances. Tidal turbine scour depth is inversely proportional to tip clearance. Larger scour depths occur with the smaller clearances. The increase of scour depth occurred obviously in between 0.50 D t and 0.80 D t with the decrease of tip clearance, while the scour depth maintained for the further reduction of clearance. When the tip clearance was shorter than 0.50 D t , the flow in the gap between the turbine and seabed no longer need to be accelerated intensely. Less blocked water was diverted into the narrow region when tip clearance was shorter than 0.50 D t . The same shadowing effect occurred when the clearance was smaller than 0.50 D t . The scour depth kept constant at various lower tip clearances. Meanwhile, the shadowing effect had less influence on the tidal turbine scouring when the turbine position was sufficiently higher than 1.00 D t . The sand dune had a reverse trend compared to the sand pit, as shown in Figure 15. The sand pit depth increased with the decreasing of the tip clearance, but the sand dune height decreased with the decreasing of the tip clearance. The decrease of sand dune height was due to the vortex formed at a lower turbine position. For the lower turbine position, a large amount of sediment was scoured from the sand pit and deposited to form sand dunes. The sediment deposited at the sand dune was further scoured downstream due to the effect of the turbine position. The upstream edge of the scour pits occurred at x/D t = 0.35. The position of upstream edge had an insignificant difference for various tip clearances. The downstream edge of the scour pits moved further downstream with smaller tip clearances.

Equation Used to Predict Maximum Scour Depth for Tidal Turbine
The seabed scour of the horizontal-axis tidal turbine was more severe than the cylinder scour mainly due to the shadowing effect of a rotating turbine. Neil [7], Breusers et al. [8], Richardson et al. [10], and Raaijmakers and Rudolph [39] proposed numerous equations to estimate the scour depth of a pier or pile, as shown in Table 5 and Appendix A. In this paper, the equations were based on the development of a pier or pile to predict the maximum scour depth for a tidal turbine. Table 5. Equations used to predict the pile or pier scour.

Previous Works Pile or Pier Scour Equation Proposed Turbine Scour Equation
Neil (1973) [7] S D = K s S D = K s K t Breusers et al. (1977)

Raaijmakers and Rudolph (2008) [39]
proposed a simple equation with the ratio of scour depth to the pile diameter as a constant K s . K s is correction factor for a pier nose shape. In this work, a turbine coefficient (K t ) in Equation (19) is proposed to predict the maximum tidal turbine scour depth. K t is considered as the effect of a tidal turbine on scouring, which is related to the tip-bed velocity due to the existence of a rotating turbine.
where S is the scour depth for turbine (m), D is the diameter of the support structure (m), K s is the correction factor of the pier shape, and K t is correction factor of turbine. In this study, the seabed scouring of the tidal turbine was under the clear water condition. The tip-bed velocity was the main factor affecting the turbine coefficient K t . Figure 16 shows the relationship between the tidal turbine scouring and tip-bed velocity. Two linear relationships were formed between the scour depth and tip-bed velocity. It can be seen that the scour depth was linear with the increase of velocity, and it no longer increased when the tip clearance was less than 0.50 D t . The turbine coefficient K t is related to tip-bed velocity and free flow velocity in the tip clearance range between 0.50 D t and 1.00 D t . K t was obtained by the regression analysis from the experimental measurements, as shown in Equation (20) where V tb is the tip-bed velocity (m/s) and V ∞ is the free flow velocity (m/s). The tidal turbine scour depth no longer increased when tip clearance was less than 0.50 D t . K t was considered a constant to produce Equation (21) when dimensionless the tip-bed velocity V tb /V ∞ was larger than 1.14: The predicted tidal turbine scour depth was compared to the experimental measurement at various tip-bed clearances, as listed in Table 6. The predicted scour and the experimental measurements show good agreement, as shown in Figure 17. The maximum variation of 24.72% occurred in results from Chen [38]'s 0.50 D t clearance case, which may be related to the influence of the tip speed ratio (TSR) of the tidal turbine. Generally, the empirical equation could estimate the seabed scour of a tidal turbine within a 30% error range. Based on Hill et al. [22], and Chen [38] results, the statistical functions using correlation coefficient (R), mean absolute error (MAE), root mean squared error (RSME), and scatter index (SI) in Equations (22)-(25) [40][41][42] were calculated to evaluate the performance and accuracy of Equation (19).
where O i is the experimental value, P i is the predicted value from the equation, O is the average of the experimental value, P is the average of the predicted value, and M is the number of experimental points. The predicted scour from the proposed equation fits well with the experimental data from the results of the statistical functions in Table 7. Berusers et al. [8], Richardson et al. [10], and Raaijmakers and Rudolph [39] improved Neil's cylindrical scour equation [7] with a consideration of water depth, flow angle, seabed conditions, and the size of bed material. The turbine coefficient K t can also be included in other cylinder scour equations (Berusers et al. [8], Richardson et al. [10], and Raaijmakers and Rudolph [39]) to estimate turbine scour.

Conclusions
This research demonstrates the scour profile for horizontal-axis tidal turbines using theoretical and experimental investigations. An experimental apparatus was built to investigate tidal turbine scouring at various clearances in between the blades and seabed. The maximum scour depth, length of scour pit, and height of the deposited dune are presented through experimental measurements at different times. Tip-bed velocity, the accelerated velocity in between the blades and turbine, was studied in this research. The existence of a turbine leads to the flow acceleration of the tip-bed velocity and intensifies the seabed scour. Scouring experiments were conducted around a horizontal-axis tidal turbine with different tip clearances in a steady current. The conclusions are: (1) A tip-bed velocity equation is proposed to estimate the seabed scour of a tidal turbine.
The derivation of the equation is based on the axial momentum theory and conservation of mass. In the calculation of a single case (Chen and Lam [5]), the proposed equation showed the variation was less than 4% for various tip clearances.
(2) A turbine significantly impacts its seabed scour due to shadowing effects. The influence of a turbine on scouring depends on the tip-bed clearance in between the blades and seabed. Scour depth is inversely proportional to tip clearance. The influence of a turbine is less significant when the clearance is excessively high (C > 1.00 D t ) due to less significant shadowing effects. The influence of a turbine is the same even with smaller clearance after C < 0.50 D t due to less blocked water diverting into the narrow region. (3) An empirical equation is proposed to estimate the maximum tidal turbine scour depth. The turbine coefficient (K t ) is proposed to estimate the seabed scour depth of a tidal turbine with a consideration of the tip-bed velocity. The predicted data are well correlated with measured scour depth within a 5-24% error range. The correlation coefficient (R), mean absolute error (MAE), root mean squared error (RSME), and scatter index (SI) are 0.944, 0.085, 0.142, and 0.081, respectively. Mean sediment grain diameter in mm D pile diameter in m h pile height in m S scour depth for turbine K s correction factor of pier shape K t correction factor of turbine