In typical VAWT, the blades are arranged vertically and rotate around the vertical axis. Some of the niche advantages of Savonius turbines are insensitive to the wind direction, ease of maintenance by placing the drive train components on the ground [8] , lo manufacturing cost of blades and reduced tower height. For urban applications, Savonius turbines are preferred than the Darrieus turbines despite its lower efficiency (~15%) [9] . Savonius turbines are drag based and can generate power in turbulent and low wind speed prevalent in the built-up area. Myriad studies are carried out in the past unfolding the flow pattern around the Savonius buckets and its blade wake interactions. Numerous experimental studies [10] established the critical parameters of the turbine such as effect of end plates, optimum end plate diameters, effect of aspect ratio, influence of bucket spacing, bucket overlap, number of buckets, number of stages, interference of shat, effect of deflecting plate, helical and straight blades as shown in Figure 1. The aspect ratio can be defined as the ratio between the height to the diameter of the rotor. It was concluded through experimental results that the efficiency increases with the aspect ratio [11] . The past research shows that the end plate significantly improves the power performance by preventing the fluid flowing over the blades and thus maintaining the pressure difference between the concave and the convex side over the height of the rotor [12] . Sivasegaram [13] conducted an experimental investigation on the effect of the end plate and found that optimum end plate diameters are 1.1 times the rotor diameter. According to Kamoji [14] , the maximum power coefficient decreases with increase in overlap ratio, whereas the experimental study by Alexander [15] reveals that, the efficiency increases with the overlap ratio for the tested values of −0.07 to 0.22 [16] . Helical Savonius rotor reduces the peak torque [17] by spreading over wide azimuthal angle substantially reducing the peak alternating stress on buckets. Despite these efforts, the maximum efficiency of the Savonius turbines hovers around 18%. The maximum commercially available Savonius turbine has the power capacity of 10 kW manufactured by Wind Side [18] . Compared to HAWT, Savonius turbines have much better prospects in terms of return on investment in low wind.

Savonius turbines operate by drag force, through diminutive lift force also contributes to the torque. Increase in wind speed invariably increases the drag force. The drag force, if not converted to torque will result in higher wind load. The obstacle plate used to reduce the negative moment on the convex side [21] of the

blade by directing the wind towards the concave side tends to increase the wind load, though the deflecting plate increases the efficiency to 27% [22] . As per IEC61400-2, for small wind turbines, the wind load is calculated based on the frontal area [23] . The frontal area of the Savonius rotor does not change in the event of high winds. This is not the case with HAWT as they are equipped with furling mechanism, in which the rotor plane orients to the wind direction exposing the minimal frontal area to the wind. The aligning force is generated through the difference in the aerodynamic thrust between the tail and the rotor. Researchers have attempted to introduce such a mechanism to Savonius turbine to reduce the wind load and have achieved notable success. As the concave shape of the Savonius buckets has the drag coefficient of ~2.2, whereas the cylinder has the drag coefficient of ~0.47, converting the semicircular buckets to cylindrical shape was proposed as a solution by Patrick-Leroy [24] . The linkages attached to the centershaft rotate the semicircular buckets to one cylinder. Though the experimental studies reveal that the wind loads are reduced by 20% - 30%, the cylinder at high winds will induce von Karman vortices [25] which will compound the wind loading with alternating moment and vibrations. Telescopic Savonius Turbine (TST) was proposed as a potential solution to curtail the wind load as shown in Figure 2. The telescopic turbine is able to expand and retract based on wind conditions. The ability of the turbine to modify its frontal area in accordance with the wind speed helps the wind turbine to maintain its power and wind loads within the acceptable limits. Numerical simulation shows that the wind load of TST can be reduced by ~60% [26] compared to conventional Savonius turbine. Savonius turbines are not preferred for the power capacity more than 10 kW due to the higher wind loads which demand heavier support structures.

The straight bladed Darrieus turbine is the simplest of the type as they are easier to manufacture, transport and assemble on the turbine. Numbers of blades for a given power capacity are based on the average wind speed on the installation site, rpm of the machine and starting characteristics. A two-straight bladed Darrieus rotor is commonly referred as H-Rotor [27] and more than two-bladed turbines are referred as Giromill [28] as shown in Figure 3. Though in most cases the blades are parallel to the axis of rotation, delta rotor, diamond rotor, V or Y rotor was reported to have their blades inclined to the axis of rotation. The maximum coefficient of performance (Cp) of a straight bladed turbine is in the range of 0.25 - 0.35. The Cp of the turbine is highly influenced by the solidity of the turbine defined by the ratio between the blade area to the swept area. Solidity can be increased by increasing the number of blades or increasing the chord length of the blades. The solidity of a straight bladed Darrieus rotor has a major impact on the starting characteristics of the turbine. The experimental study by Baker [29] shows that the static torque coefficient is higher for three bladed turbines compared to a two-bladed turbine. The blade mounting struts can be steel tubes which reduces the manufacturing cost and available in a wide range of diameters with various wall thicknesses. Straight bladed Darrieus turbines are not preferred for urban applications due to its lower performance in low and turbulent winds. Unable to self-start at wind speeds below 4 m/s [30] is a major drawback hindering these turbine installations on rooftop. The past studies on self-starting reveal that the flow detachment from the blades at low Reynolds number (Re) and high Angle of Attack (AoA) results in the generation of low lift significantly reducing the net torque [31] . Another shortcoming of smaller Darrieus turbines is the rotational speed. Darrieus turbines are comparatively slow rpm machines than HAWT. The increased generator size for the same power capacity leads to an increase in cogging torque [32] , offering higher resistive

torque against rotation. In spite of these drawbacks, aesthetically pleasing and simple construction led to the development of innovative small-scale Darrieus wind turbines. The straight bladed Darrieus turbines are commercially available in power capacities from 500 W to 1.5 MW.

The helical turbine was proposed by Gorlov in 1995 [37] . Compared to the straight bladed turbine, helical bladed turbine offers noteworthy advantages such as enhanced self-starting capability, low noise, increased blade life, low vibrations and reduced peak stress in the blades [38] . The self-starting capability is improved by the reduction of AoA and the ability of the blades to accelerate beyond the dead band [39] . It is also evident from the past studies that the stall angle is increased due to the boundary layer attachment by the introduction of spanwise flow by the helical blades. Tailored airfoils are proposed to delay stall [40] . The helical angle of the blades also has a significant impact on the stall angle. The experimental comparison between straight bladed Darrieus turbine and the helical turbine reveals that the peak Cp of the helical turbine is, in fact, lower than the straight bladed turbine. The vibrations are reduced due to continuous wake rather than vortices in the case of straight bladed Darrieus turbine [41] . On the negative note, the helical blade manufacturing cost is higher compared to straight blades. The only choice of manufacturing the helical blade is through the mould, whereas the straight blades can be manufactured by aluminium extrusion. Though most of the helical turbines are three-bladed, turbines with two bladed and five-bladed are reported. Increase in the number of blades tends to reduce the operating Tip Speed Ratio (TSR). Blade tip loss and blade wake interactions are highly pronounced for turbines of three-bladed or more. Commercial helical turbines are prevalent in the power capacity of 2 - 10 kW. 7.5 kW model was manufactured by VWT power as qr6 [42] , the current generation turbines. The three-bladed turbines have the swept area of 16 m² and survival wind speed of 52.5 m/s with maximum rpm of 260. The blade fixing arms are made of carbon fibre, which reduces the weight of the rotor and thereby aids in self-starting by reducing the inertia [43] . Another similar manufacturer of the helical turbine is Turby, which is a research outcome from the Delft University of Technology. The 2.5 kW turbine reaches its output at 14 m/s. The turbine is optimized for rooftop installation reaching an efficiency of 40% even at skewed flow. The qr6 turbine and the Turby are shown in Figure 4.

As self-starting and the low-speed behaviour are crucial for a small wind turbine, Darrieus community is in constant search for a solution that can address the above said challenges. J-profile was conceived by researchers and later adopted by manufacturers around the world. The J-Profile on the blade is formed by removing a portion on the pressure side of the airfoil [45] . The choice of the airfoil is mostly symmetric NACA series though the use of cambered airfoil is reported. The opening length and position along the chord is a parameter for optimization based on the prevailing wind speed [46] . Different opening ratio (Chord length/Opening length) has been adopted by manufacturers to circumvent the patents on J-Blade. The opening on the blades can be continuous or it can be intermittent. For a smaller blade length (~4 m) the opening can be continuous, for the higher blade length of ~8 m, the blade opening can be intermittent as shown in Figure 5. A continuous opening for a longer blade will result in bending along the length due to centrifugal forces that are not supported by arms. Poring over the numerical simulation reveals that, the J-blade turbine operates both in lift and drag mode dictated by the opening ratio [47] . The cavity in the blade acts as a drag bucket, smaller opening manifests the turbine more like a conventional Darrieus rotor, whereas larger opening results in the turbine operating g more mon drag force similar to a Savonius rotor. Cost of blade manufacturing can be substantially reduced for J-blade, as the blades can be manufactured by extrusion for smaller length and bending the low carbon sheets with sufficient ribs welded. Employing aluminium material for blade manufacturing paves the way for recycling of blades after the lifetime of the turbine. The study performed by Yusaku [48] shows that the turbine has higher Cp in the low Reynolds number region and as the TSR increases, the conventional Darrieus rotor outperforms. This can be attributed to the loss of lift due to the flow detachment in low Re. The peak torque amplitude is found to be lower and widespread over larger azimuthal angles. The efficiency of the J-bladed turbine lies in between Savonius-Darrieus hybrid rotor and conventional Darrieus rotor.

The curved bladed rotor was derived from the phi rotor [52] developed during the earlier days of VAWT. The primary difference between the curved bladed rotor and the phi rotor is that the ends of blades are attached to the tower in the case of phi rotor, whereas in the curved bladed rotor it is free. The curved blades are attached to the tower through struts [53] . Presence of struts has a greater influence on the torque generation due to the resistive torque by parasitic drag. In large turbines, struts are made of symmetrical airfoils to reduce the parasitic drag. In both cases, the tower can be rotating or non-rotating. Phi rotor design is prevalent for turbines of capacity more than 50 kW, the curved rotor designs are suitable for small turbines of capacity ~10 kW. The struts are directly attached to the top flange of the axial flux generator as shown in Figure 6. The ring bearing in the generator can sustain greater moment load than deep groove ball bearings of similar size. From the aerodynamics perspective, curved rotor and the H-rotor has notable differentiation. The Re of the H-rotor blades is uniform along the length of the blades, whereas in the curved blades the Re is higher at the center of the blade length [54] . The changes in Re results in an earlier dynamic stall close to the root. This, in turn, induces more blade tip vortices resulting in lower Cp. Curved bladed rotor is aesthetically pleasing than H-rotor and hence a suitable candidate for rooftop installations. Blade manufacturing is a comparatively complex than straight blades. Smaller curved blades are manufactured by using glass fibre through moulding process [55] . Larger curved blades are manufactured through extrusion process followed by bending by a skilled worker. Since the larger curved blades are manufactured in sections, there is a possibility of using different airfoils for different sections [56] . Small scale curved blades are manufactured by Greef up to 2 kW as seen in Figure 6. The 2-kW turbine has a maximum rpm of 160 with the blades manufactured by using Fiber Reinforced Plastic (FRP). The rated wind speed and the startup wind speed are 11 m/s and 2.8 m/s respectively. The startup torque required to accelerate the rotor was claimed to be less than 0.3 Nm.

For maximum energy output, it is necessary for the turbine to accelerate to the rated rpm in a shortest possible time. Wind turbines are either connected to the electrical grid or to an energy storage system such as battery and in either case, it is possible to use the energy to accelerate the rotor to the rated rpm. Since most of the turbines use direct drive permanent magnet generator [PMG], Liu [58] proposed a solution in which the generator can operate as a motor during starting and low wind. As the rotor accelerates beyond the dead band and gains sufficient rpm, it can operate as a generator producing power [59] . The proposed solution can reduce the cost involved in high voltage components as the windings demand only low voltage components. The concept of active motoring was simulated on a 5 kW HAWT by Aner [60] with two blades accelerated typically in 12 s to the rated rpm at 10 m/s wind speed. Though the motoring start has negligible impact on the peak power coefficient of a turbine, the significant startup time reduction aids in maximizing the energy extraction. Cogging torque [32] is an inherent characteristic of any PMGs arises from cogging between magnets and the armature windings and can be measured by the torque required to rotate the shaft under no load. The electric start can provide an initial acceleration, but may not able to sustain the low wind speed rotation and hence will not be suitable for Darrieus turbines operating at low wind speed sites. A frequent start and acceleration may consume a considerable amount of power, which will decrease the annual energy production. One such electrical start turbine was commercially manufactured by Cleanfield Energy. V3.5 model offered by the firm is 3.5 kW three-bladed turbine, reaching its rated power at 12.5 m/s. The turbine has a maximum rpm of 190 with a blade length of 3 m. The turbine was developed and tested extensively by National Research Council (NRC) of Canada. Another innovative turbine was developed by Apple Wind. The turbine has lower strut of airfoil shape, while the upper strut has been replaced by the bar. The bar will be subjected to tensile force due to centrifugal force of the blades. The current arrangement will reduce the parasitic drag due to struts as seen in Figure 7. The lack of endplates on the top end of blades will generate blade vortices decreasing the net torque.

The continuous research on the Darrieus turbine has yielded many innovative designs, yet a very few concepts have the potential to be scaled up for commercial purpose. These turbines are optimized for low wind speed and are economical. An airfoil that is capable of maintaining the lift over high AoA without significant increase in drag will be an apt choice for Darrieus turbines [63] . Airfoils are modified such as trailing edge cavity modification [64] was found to enhance energy yield. Kline [65] (KF) conceived airfoils with abrupt discontinuity claiming to have enhanced lift. Though the airfoil doesn’t outperform in the pre-stall region, it demands attention for its aerodynamic behaviours in the post-stall region when the step is located on the suction side of the airfoil as reported by Mishriky [66] . The new airfoil KF-N-21 was created by introducing the step discontinuity borrowed from the KF airfoil on the suction side of the NACA 0021 airfoil. In order to create maximum drag during the reverse flow to aid in the startup, the depth of step is located at 18%c, while the maximum thickness of airfoil is 21%c [67] . The step length is 50%c and originates at 30%c from the leading edge, though location near to the trailing edge is favourable for high lift coefficient. The experimental comparison with conventional turbines reveals that the turbine Cp has been increased by 13% at low Re. Another innovative turbine is Double Darrieus (DD) rotor. The proposed DD rotor comprises two sets of blades sharing a common shaft [68] . The outer rotor hereafter referred as the primary rotor (PR) has three straight blades of NACA 0018 and inner rotor hereafter referred as the secondary rotor (SR) has three blades of NACA0018. Experimental comparison with conventional Darrieus shows that starting torque is significantly higher and the turbine is able to generate substantial power even at low wind speed. Characteristics of this turbine at high wind speed are not assessed yet. The third innovative design is the Adaptive Hybrid Darrieus Turbine (AHDT), which combines both the advantages of Darrieus and Savonius, yet overcoming the issues of Hybrid Savonius Darrieus design. The Savonius buckets can slide on the Darrieus rotor strut to form a cylinder thereby eliminating the turbulent wake flow affecting the Darrieus rotor performance. The three primary types of Darrieus rotors discussed above are shown in Figure 8.

The Savonius turbines are known for its higher starting torque, while the Darrieus turbines are notorious for poor starting torque. Obviously, the curious idea is to combine both the rotor to supplement each other [72] . At low wind speeds (<3 m/s) combined machine demonstrates the characteristics of Savonius rotor, while on high winds (>4 m/s) the combined machine will behave as conventional Darrieus rotor. Two configurations are practically feasible to combine a Savonius and Darrieus rotor. The Savonius rotor can be placed either above or below the Darrieus rotor or the Savonius rotor can be nested inside the Darrieus rotor. The placement of the Savonius rotor outside the Darrieus rotor tends to increase the length of the rotating shaft, which in turn will lead to vibrations. Hence pragmatic way is to place the Savonius rotor nested with Darrieus rotor. Based on the above idea, a number of past studies are conducted both experimentally and computationally. The objective of all these studies is to optimize the Savonius rotor diameter for maximum low wind performance and to maintain the Cp of the Darrieus rotor at high winds by minimizing the effect of Savonius rotor. The results show that the starting torque of the combined machine is much higher than the Darrieus rotor, while the peak Cp is attained at lower TSR [48] . The maximum operating TSR for the combined machine is 1 - 1.2. It has to be noted that the maximum TSR for a Savonius rotor is 1, and any attempt to operate beyond TSR 1 will generate negative torque. While the Darrieus rotor operates at TSR 3 - 6 [73] . This mismatch between the peak performance of two rotors is a crucial problem limiting the further development of these hybrid turbines. Potential solutions have been proposed to address the above problems associated with Darrieus Savonius rotor integration as shown in Figure 9. Mousavi [74] proposed to disengage the rotors when the Darrieus rotor, accelerates beyond the TSR 1. Though the solution is technically feasible, the energy captured by Savonius rotor after disengagement will not contribute to the total energy output and the wake generated by Savonius rotor still exist [75] . A promising strategy to eliminate the wake of Savonius rotor will brand this hybrid rotor as a potential solution for low wind speed operation.

Blade pitching was once proposed for large wind turbines, as integrating the system in small wind turbine is costly and complex. Due to the advent of actuation systems [78] and reduced cost of the associated electronics, pitching system can be implemented in small Darrieus turbines of capacity as low as 10 kW. Though the Darrieus rotor may look simple, the aerodynamics associated with it is much more complex than HAWT. The fixed blades encounter a wide range of AoA from 0˚ - 360˚ due to change in the relative velocity. Such a wide AoA constantly push the blades to stall. Due to hysteresis inflow, the flow may be detached even the AoA reduces. To keep the blades at optimum AoA, the blade pitching is a viable solution. Effect of blade pitching is well studied through Double Multiple StreamTube (DMST) [79] . The blades can be pitched either actively or passively. The active pitching is achieved by using closed-loop system actuated by motor for small wind turbines. Considerable amount of power is needed to actuate the motor. The advantage of active pitching compared to passive pitching is that the blades can be pitched individually [80] . The closed-loop system monitors the wind speed and wind direction and pitches the blade accordingly. This generates higher starting torque as all the blades take part in torque generation [81] . A closer investigation of the torque generated by the single blade for one complete revolution reveals that the peak positive torque is generated at upwind half, and smaller negative torque is generated in downwind half. Active individual blade pitching helps to reduce the negative torque which is not possible with passive pitching [82] . The passive pitching relies on the centrifugal force of the blades, in which the hinged blade is allowed to offset at a controlled manner. The passive pitching will increase the negative torque but the positive torque will increase comparatively more [83] . Hence active pitching is effective in increasing the overall performance of the turbine as shown in Figure 10. The past study by Paraschivoiu [84] shows that effective pitching can increase the annual energy yield by 30%. The future large Darrieus turbines will be equipped with blade pitching system for its advantages.