Magnus turbine wind generator and design method thereof

Abstract

This invention relates to the field of wind power generation technology, specifically a Magnus turbine wind turbine and its design method. It includes a tower, characterized by a turbine annular sleeve fixed on the tower. The inner wall of the turbine annular sleeve has an annular sliding ring hole, at which an annular gear ring is fixed. Multiple generator carriages are evenly distributed within the turbine annular sleeve. The carriage body of each generator carriage is rotatably connected to the outer end of a cylinder via an outer bearing. A drive gear meshing with the annular gear ring is located on the outer end of the cylinder. The inner end of the cylinder is rotatably connected to a central shaft via an inner bearing. A generator is fixed to the carriage body of each generator carriage. The generator's input end is connected to a generator gear, which meshes with the annular gear ring. The generator's output end is connected to a conductive brush, which contacts a conductive slip ring fixed to the inner wall of the turbine annular sleeve for electrical conduction. This design features a simple structure, excellent performance, reduced generator gear size, and compatibility with high-speed generators.

Description

Technical Field

[0001] This invention relates to the field of wind power generation technology, specifically a Magnus turbine wind turbine and its design method. Background Technology

[0002] When a fluid flows around a rotating cylindrical or spherical obstacle, the rotating object experiences a lateral force. This lateral force is actually a lift phenomenon caused by the difference in fluid velocity on both sides of the cylinder—the Magnus effect. The resulting lateral force is called the Magnus effect force or Magnus (lift) force. Currently, many devices generate electricity using the Magnus principle. For example, patent publication number CN103717884A, patent name: Vertical Axis Magnus Wind Turbine, has a complex mechanism, requires an independent drive motor, needs a control baffle during operation, and lacks relevant theoretical support. There is also patent publication number CN104500346A, patent name: A Combined Magnus Wind Turbine, which includes a three-bladed Magnus wind turbine. It replaces the turbine blades with cylinders, and drives the blades to rotate around their own axis through the contact between the wind turbine key limit roller and the main shaft. This method has certain structural advantages, but the transmission ratio of this structure is limited and cannot meet the high speed requirements of the Magnus cylinder. Summary of the Invention

[0003] The purpose of this invention is to overcome the shortcomings of the prior art and provide a Magnus turbine wind turbine and its design method that are simple in structure, have excellent performance, reduce the number of gears in the generator, and can be adapted to high-speed generators.

[0004] The technical solution adopted by this invention to solve its technical problem is:

[0005] A Magnus turbine wind turbine generator includes a tower. The tower is characterized by a turbine annular sleeve with an annular sliding ring hole on its inner wall. An annular gear ring is fixed at the position of the sliding ring hole. Multiple generator carriages are evenly distributed within the turbine annular sleeve. Each generator carriage's body is rotatably connected to the outer end of a cylinder via an outer bearing. The outer end of the cylinder has a drive gear that meshes with the annular gear ring. The inner end of the cylinder is rotatably connected to a central shaft via an inner bearing. A generator is fixed to the body of each generator carriage. The generator's input end is connected to a generator gear, which meshes with the annular gear ring. The generator's output end is connected to a conductive brush, which contacts a conductive slip ring fixed to the inner wall of the turbine annular sleeve for electrical conduction.

[0006] The turbine annular sleeve of the present invention has a front guide shield and a rear guide shield connected to its front and rear sides, respectively, to facilitate the straightening of the wind direction.

[0007] The turbine annular sleeve of the present invention includes a front U-shaped sleeve and a rear U-shaped sleeve. The front U-shaped sleeve and the rear U-shaped sleeve are laid flat and connected with an opening. The upper arm end of the front U-shaped sleeve is connected to the front flange, and the upper arm end of the rear U-shaped sleeve is connected to the rear flange. The front U-shaped sleeve and the rear U-shaped sleeve are locked together by bolts and nuts passing through the front flange and the rear flange. The lower arm end of the front U-shaped sleeve and the lower wall end of the rear U-shaped sleeve are not connected to form an annular sliding ring hole.

[0008] The turbine annular sleeve of the present invention is connected to a wing plate on its outer wall, and the turbine annular sleeve is fixedly connected to the tower via the wing plate.

[0009] The cylinder of the present invention is connected to an upper connecting shaft and a lower connecting shaft at both ends. The upper end of the cylinder is rotatably connected to the body of the generator trolley via the upper connecting shaft passing through the outer bearing, and the lower end of the cylinder is rotatably connected to the central shaft via the lower connecting shaft passing through the inner bearing.

[0010] The turbine annular sleeve of the present invention has an annular dustproof plate on the sliding ring hole on the inner wall. The annular dustproof plate has a through hole for the cylinder to pass through. The annular dustproof plate is slidably connected to the inner wall of the turbine annular sleeve. The cylinder drives the annular dustproof plate to rotate as it rotates along the circumference of the turbine annular sleeve.

[0011] The turbine annular sleeves on both sides below the sliding ring hole of the present invention are respectively connected to the guards, and the annular dustproof sheet is supported by the guards.

[0012] The power generation trolley of the present invention includes a vehicle body, vertical wheels, and horizontal wheels. The vertical wheels are rotatably connected to eight positions on the vehicle body (upper, lower, front, rear, left, and right) that contact the inner wall of the turbine annular sleeve. The vertical wheels serve as vertical supports for the vehicle body within the turbine annular sleeve. Horizontal wheels are rotatably connected to the upper and lower positions between the left and right vertical wheels of the vehicle body. The horizontal wheels serve as lateral supports for the vehicle body within the turbine annular sleeve.

[0013] The central shaft described in this invention is a hollow shaft, which reduces the overall size and weight, alleviates flow blockage, and reduces the overall wind resistance of the turbine.

[0014] A design method for a Magnus turbine wind turbine, characterized by a cylindrical diameter... d At different radii r The iterative design process for the distribution at a given location consists of the following steps:

[0015] Step 1: Select a design tip velocity ratio λ The angle can be obtained according to the following formula (2). θ At different radii r Distribution curve at location;

[0016] (2);

[0017] θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in radians (rad). v ∞ The velocity of the incoming flow from a distance is expressed in m / s. ω Turbine speed, in rad / s. R λ represents the turbine radius in meters (m), r represents different radius positions of the turbine in meters (m), and λ is a dimensionless value.

[0018] Step 2: Select a number of leaves N and lift coefficient C L According to the following formula (1), the diameter of the cylinder can be obtained. d At different radii r Distribution curve at location;

[0019] (1);

[0020] d is the diameter of the cylinder at radius r, in meters. C L Let be the lift coefficient of the rotating cylinder, and be a dimensionless value. N The number of cylinders arranged circumferentially, θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in rad. R Turbine radius, in meters;

[0021] Step 3: Select a ratio of cylinder spin speed to turbine speed. ω 2 / ω The tangential velocity ratio can be obtained according to the following formula (3). a At different radii r Distribution curve at location;

[0022] (3);

[0023] ω 2 represents the rotational speed of the cylinder, in rad / s. W for r The relative incoming flow velocity at the radius position, in m / s. d for r The diameter of the cylinder at the radius position, in meters (m). ω Turbine speed, in rad / s. θ The angle between the relative flow velocity and the direction of rotation is expressed in radians (rad), and r represents different radial positions of the turbine, expressed in meters (m). ，a The ratio of tangential velocities is a dimensionless value.

[0024] Step 4: Based on the tangential velocity ratio aThe lift coefficient is calculated using the distribution of the following formula (4). C L At different radii r Distribution at location;

[0025] (4);

[0026] In the above formula (4), ;

[0027] ; C L (a) is the lift coefficient function for a rotating cylinder under different tangential velocity ratios a. a The ratio is the tangential velocity, and e is the natural constant, which can be approximated as 2.718. d for r The diameter of the cylinder at the radius position, in meters (m); the minimum diameter of the d2 corrugated cylinder, in meters (m).

[0028] Step 5: Repeat steps 2 through 4 until the cylinder diameter is reached. d At different radii r The distribution at point i is convergent; to ensure convergence, the diameter at step i+1 is... d The calculation formula can be written as:

[0029] (5);

[0030] ,

[0031] x is the relaxation factor, which is a dimensionless value;

[0032] d for r The diameter of the cylinder at the radius position, in meters (m). R Turbine radius, in meters. N The number of cylinders arranged circumferentially. C L (a) represents the lift coefficient of the rotating cylinder under different tangential velocity ratios, which is a dimensionless value. θ The angle between the relative incoming flow velocity and the direction of rotation is expressed in rad.

[0033] Step 6: Input the actual design dimensions and wind speed to obtain the specific cylinder diameter, rotational speed, and turbine rotational speed.

[0034] The tip velocity ratio λ of the present invention is 1 to 5, the number of blades N is 2 to 7, and the ratio of cylinder spin speed to turbine speed ω2 / ω is 20 to 80.

[0035] Due to the adoption of the above-mentioned structure and design method, the present invention has the advantages of simple structure, excellent performance, reduced generator gears, and compatibility with high-speed generators. Attached Figure Description

[0036] Figure 1 This is a schematic diagram of the structure of the present invention.

[0037] Figure 2 yes Figure 1 Enlarged cross-sectional view of the annular sleeve of the fixed turbine.

[0038] Figure 3 yes Figure 1 Diagram showing the connection between the internal structure of the fixed turbine annular sleeve and the generator trolley.

[0039] Figure 4 yes Figure 3 Enlarged view of the connection between the generator trolley and the cylinder.

[0040] Figure 5 It is a diagram showing the relationship between the height of the cylinder (dr) on the annular surface and various parameters of the cylinder's rotation and circumferential rotation. 5-1 is the side view and 5-2 is the front view.

[0041] Figure 6 This is a graph showing the velocity relationship of the cylinder at a radius of r when viewed from the top down.

[0042] Figure 7 This is a graph showing the distribution of angle θ at different radii r.

[0043] Figure 8 It is a distribution curve of the cylinder diameter d at different radii r.

[0044] Figure 9 It is a graph showing the distribution of the tangential velocity ratio 'a' at different radii 'r'.

[0045] Figure 10 This is a graph showing the distribution of the cylinder diameter d at different radii r after the first iteration.

[0046] Figure 11 This is a graph showing the distribution of the cylinder diameter d at different radii r after the second iteration.

[0047] Figure 12 This is a graph showing the distribution of the cylinder diameter d at different radii r after the third iteration.

[0048] Figure 13 This is a tangential velocity ratio distribution diagram of the final calculation results of the embodiment.

[0049] Figure 14 These are schematic diagrams of a cylinder, where 14-1 is a schematic diagram of a smooth cylinder and 14-2 is a schematic diagram of a corrugated cylinder.

[0050] Reference numerals: 1. Tower; 2. Turbine annular sleeve; 3. Sliding ring hole; 4. Annular gear ring; 5. Generator trolley; 6. Cylinder; 601. Smooth cylinder; 602. Corrugated cylinder; 7. Drive gear; 8. Central shaft; 9. Generator; 10. Conductive brush; 11. Conductive slip ring; 12. Front fairing; 13. Rear fairing; 14. Front U-shaped sleeve; 15. Rear U-shaped sleeve; 16. Front flange; 17. Rear flange; 18. Wing plate; 19. Upper connecting shaft; 20. Lower connecting shaft; 21. Annular dustproof sheet; 22. Edge protector; 23. Car body; 24. Vertical wheel; 25. Lateral wheel; 26. Conductive wire; 27. Detailed Implementation

[0051] The present invention will be further described below with reference to the accompanying drawings:

[0052] As shown in the attached figure, a Magnus turbine wind turbine generator includes a tower 1. The tower 1 is characterized by a turbine annular sleeve 2 fixed on it. The inner wall of the turbine annular sleeve 2 has an annular sliding ring hole 3. An annular gear ring 4 is fixed at the position of the sliding ring hole 3. Multiple generator carriages 5 are evenly distributed inside the turbine annular sleeve 2. The carriage body of each generator carriage 5 is rotatably connected to the outer end of a cylinder 6 via an outer bearing. The outer end of the cylinder 6 has a drive gear 7 that meshes with the annular gear ring 4. The inner end of the cylinder 6 is rotatably connected to a central shaft 8 via an inner bearing. A generator 9 is fixed to the carriage body of the generator carriage 5. The generator input end of the generator 9 is connected to a generator gear 10, which meshes with the annular gear ring 4. The output end of the generator 9 is connected to a conductive brush 11, which contacts and conducts electricity with a conductive slip ring 12 fixed to the inner wall of the turbine annular sleeve 2.

[0053] Furthermore, the front and rear sides of the turbine annular sleeve 2 are respectively connected to the front guide shroud 13 and the rear guide shroud 14 to facilitate the straightening of the wind direction.

[0054] Furthermore, the turbine annular sleeve 2 includes a front U-shaped sleeve 15 and a rear U-shaped sleeve 16. The front U-shaped sleeve 15 and the rear U-shaped sleeve 16 are laid flat and connected with an opening. The upper arm end of the front U-shaped sleeve 15 is connected to the front flange 17, and the upper arm end of the rear U-shaped sleeve 16 is connected to the rear flange 18. The front U-shaped sleeve 15 and the rear U-shaped sleeve 16 are locked together by bolts and nuts passing through the front flange 17 and the rear flange 18. The lower arm end of the front U-shaped sleeve 15 is not connected to the lower wall end of the rear U-shaped sleeve 16 to form an annular sliding ring hole 3.

[0055] Furthermore, a wing plate 19 is connected to the outer wall of the turbine annular sleeve 2, and the turbine annular sleeve 2 is fixedly connected to the tower 1 via the wing plate 19.

[0056] Furthermore, the two ends of the cylinder 6 are respectively connected to the upper connecting shaft 20 and the lower connecting shaft 21. The upper end of the cylinder 6 is rotatably connected to the body of the generator trolley 5 via the upper connecting shaft 20 passing through the outer bearing, and the lower end of the cylinder 6 is rotatably connected to the central shaft 8 via the lower connecting shaft 21 passing through the inner bearing.

[0057] Furthermore, an annular dustproof plate 22 is provided on the sliding ring hole 3 on the inner wall of the turbine annular sleeve 2. The annular dustproof plate 22 is provided with a through hole for the cylinder 6 to pass through. The annular dustproof plate 22 is slidably connected to the inner wall of the turbine annular sleeve 2. The cylinder 6 drives the annular dustproof plate 22 to rotate as it rotates along the circumference of the turbine annular sleeve 2.

[0058] Furthermore, protective edges 23 are connected to the turbine annular sleeves 2 on both sides below the sliding ring hole 3, and the annular dustproof sheet 22 is supported by the protective edges 23.

[0059] Furthermore, the power generation trolley 5 includes a body 24, vertical wheels 25, and horizontal wheels 26. The eight positions of the body 24 that contact the inner wall of the turbine annular sleeve 2 are rotatably connected to the vertical wheels 25. The vertical wheels 25 serve as vertical supports for the body 24 within the turbine annular sleeve 2. The horizontal wheels 26 are rotatably connected to the vertical positions between the left and right vertical wheels 25 of the body 24. The horizontal wheels 26 serve as lateral supports for the body 24 within the turbine annular sleeve 2.

[0060] Furthermore, the central shaft 8 is a hollow shaft, which reduces the overall size and weight, alleviates flow blockage, and reduces the overall wind resistance of the turbine.

[0061] The generator 9 fixed on the aforementioned generator trolley is selected as a generator 9 with motor function. When starting, the generator is turned by external power supply, which in turn drives the turbine to rotate. Once the turbine is formed, it can enter the power generation state.

[0062] The outer side of the aforementioned turbine annular sleeve 2 is connected to a conductive wire 27, which is connected to the inner conductive slip ring 12. The outer side of the conductive wire 27 is connected to a battery that stores electrical energy.

[0063] A design method for a Magnus turbine wind turbine, characterized by a cylindrical diameter... d At different radii r The iterative design process for the distribution at a given location consists of the following steps:

[0064] Step 1: Select a design tip velocity ratio λ The angle can be obtained according to the following formula (2). θ At different radii r Distribution curve at location;

[0065] (2);

[0066] θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in radians (rad). v ∞ The velocity of the incoming flow from a distance is expressed in m / s. ω Turbine speed, in rad / s. R λ represents the turbine radius in meters (m), r represents different radius positions of the turbine in meters (m), and λ is a dimensionless value.

[0067] Step 2: Select a number of leaves N and lift coefficient C L According to the following formula (1), the diameter of the cylinder can be obtained. d At different radii r Distribution curve at location;

[0068] (1);

[0069] d is the diameter of the cylinder at radius r, in meters. C L Let be the lift coefficient of the rotating cylinder, and be a dimensionless value. N The number of cylinders arranged circumferentially. θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in rad. R The radius of the turbine is in meters (m).

[0070] Step 3: Select a ratio of cylinder spin speed to turbine speed. ω 2 / ω The tangential velocity ratio can be obtained according to the following formula (3). a At different radii r Distribution curve at location;

[0071] (3);

[0072] ω 2 represents the rotational speed of the cylinder, in rad / s. W for r The relative incoming flow velocity at the radius position, in m / s. d for r The diameter of the cylinder at the radius position, in meters (m). ω Turbine speed, in rad / s. θ The angle between the relative flow velocity and the direction of rotation is expressed in radians (rad), and r represents different radial positions of the turbine, expressed in meters (m). ，a The ratio of tangential velocities is a dimensionless value.

[0073] Step 4: Based on the tangential velocity ratio a The lift coefficient is calculated using the distribution of the following formula (4). C L At different radii r Distribution at location;

[0074] (4);

[0075] In the above formula (4), ;

[0076] ; C L (a) is the lift coefficient function for a rotating cylinder under different tangential velocity ratios a. a The ratio is the tangential velocity, and e is the natural constant, which can be approximated as 2.718. d for r The diameter of the cylinder at the radius position, in meters (m); the minimum diameter of the d2 corrugated cylinder, in meters (m).

[0077] Step 5: Repeat steps 2 through 4 until the cylinder diameter is reached. d At different radii r The distribution at point i is convergent; to ensure convergence, the diameter at step i+1 is... d The calculation formula can be written as:

[0078] (5);

[0079] ,

[0080] x is the relaxation factor, which is a dimensionless value;

[0081] d for r The diameter of the cylinder at the radius position, in meters (m). R Turbine radius, in meters. N The number of cylinders arranged circumferentially. C L (a) represents the lift coefficient of the rotating cylinder under different tangential velocity ratios, which is a dimensionless value. θ The angle between the relative incoming flow velocity and the direction of rotation is expressed in rad.

[0082] Step 6: Input the actual design dimensions and wind speed to obtain the specific cylinder diameter, rotational speed, and turbine rotational speed.

[0083] The tip velocity ratio λ of the present invention is 1 to 5, the number of blades N is 2 to 7, and the ratio of cylinder spin speed to turbine speed ω2 / ω is 20 to 80.

[0084] The cylinder 6 described in this invention is a smooth cylinder 601 or a corrugated cylinder 602 with a corrugated outer wall. Figure 14 (As shown).

[0085] The present invention has the following beneficial effects:

[0086] 1. The present invention can achieve self-driving of the cylinder rotating around the axis without the need for a separate cylinder spin drive motor;

[0087] 2. The present invention adopts an outer ring drive scheme, which, according to calculations, can better adapt to the high speed requirements of the Magnus cylinder;

[0088] 3. The present invention places the generator inside the outer ring, thus providing high-speed operating conditions and significantly reducing the required motor size;

[0089] 4. This invention provides a basis for the design of the dimensions of the rotating cylinder.

[0090] 5. Due to the adoption of the above-mentioned structure and design method, the present invention has the advantages of simple structure, excellent performance, reduced gears in generator 9, and compatibility with high-speed generator 9.

[0091] The design principles described above are as follows: The relationship between the design parameters is as follows:

[0092] According to Bates's Law, in a cylinder dr The relationship between the height on the toroidal surface and the various parameters of the cylinder's rotation and circumferential rotation is as follows: Figure 5 As shown, Figure 5 This diagram shows the relationship between the height of the cylinder (dr) on the annular surface and various parameters of the cylinder's rotation and circumferential rotation. 5-1 is a side view, and 5-2 is a front view. (It is assumed that the diameter of the cylinder is different at different radii of the turbine, and the duct is not shown.) The power loss due to wind energy is:

[0093] ;

[0094] ∆p The pressure difference is expressed in Pa. dQ cylindrical dr The flow rate generated on the height torus, in m³ / s, is as follows:

[0095] ;

[0096] ;

[0097] ρ Fluid density, in kg / m³. v ∞ Let the velocity of the incoming flow from a distance be m / s. Simplifying, we get:

[0098] ;

[0099] According to Magnus's principle of work done by a rotating cylinder, neglecting the cylinder's resistance, the cylinder... dr The power absorbed at altitude is:

[0100] ;

[0101] N The number of cylinders arranged circumferentially. W for r The relative incoming flow velocity at the radius position is expressed in m / s; CL is the lift coefficient of the rotating cylinder, a dimensionless value; and d is the cylinder diameter at the radius position r, expressed in meters. θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in radians (rad). ω This refers to the turbine speed, expressed in rad / s. Figure 6 As shown, the velocity relationship of the cylinder at a position with radius r is viewed from top to bottom.

[0102] ;

[0103] λ The tip velocity ratio is the ratio of the tangential velocity at the blade tip to the velocity of the incoming flow from a distance; it is a dimensionless value. R Let the turbine radius be in meters. dr The power of work done by a highly rotating cylinder can be written as:

[0104] ;

[0105] Sorted as:

[0106] ;

[0107] According to the law of conservation of energy, dr On the toroidal surface at a certain height, the wind energy loss is the same as the power absorbed by the cylinder, that is:

[0108] ;

[0109] Then we have:

[0110] ;

[0111] (1);

[0112] in,

[0113] (2);

[0114] The ratio of the tangential velocity on the surface of the rotating cylinder to the relative velocity of the incoming flow is called the tangential velocity ratio, which can be expressed as follows based on the velocity relationship:

[0115] (3);

[0116] ω 2 represents the rotational speed of the cylinder, in rad / s.

[0117] Example: Take a smooth cylinder as an example.

[0118] Step 1: Select a design tip velocity ratio λ =2.5, according to formula (2), the angle can be obtained. θ At different radii r Distribution curve at such location, such as Figure 7 As shown;

[0119] (2);

[0120] In the formula, r / R represents different percentage radius positions and is a dimensionless value;

[0121] Step 2: Select a number of leaves N =5, and lift coefficient C L =8, according to formula (1), the diameter of the cylinder can be obtained. d At different radii r Distribution curve at such location, such as Figure 8 As shown;

[0122] (1);

[0123] d / r can be obtained by dividing d / R by r / R;

[0124] Step 3: Select a ratio of cylinder spin speed to turbine speed. ω 2 / ω =50, according to formula (3), the tangential velocity ratio can be obtained. a At different radii r Distribution curve at such location, such as Figure 9 As shown;

[0125] (3);

[0126] Step 4: Based on the tangential velocity ratio a Based on the distribution and formula (4), the lift coefficient is calculated. C L At different radii r Distribution at location;

[0127] (4);

[0128] In the above formula (4), ;

[0129] ;

[0130] In this example, we take d2=d, i.e., δ=0, and C1=2.5, C2=50, C3=2.

[0131] Step 5: First iteration, select the relaxation factor. x =0.5, repeat steps 2 to 4, and obtain the cylinder diameter according to formula (5). d At different radii r Distribution curve at such location, such as Figure 10 As shown;

[0132] (5);

[0133] ,

[0134] x It is a relaxation factor;

[0135] The second iteration yields the cylinder diameter. d At different radii r Distribution curve at such location, such as Figure 11 As shown;

[0136] The third iteration yielded the cylinder diameter. d At different radii r Distribution curve at such location, such as Figure 12 As shown;

[0137] Compared to the second iteration, it can be seen that d The change is already very small, and it can be considered converged. And from... d From the distribution, the results are almost all of equal diameter. Based on the values ​​obtained from the results... d / R =0.0535.

[0138] Step 6: Substitute the actual design diameter R = 1m and wind speed v ∞ = 2m / s, to obtain the specific cylinder diameter d = 0.0535 R =53.5mm, ω = λv ∞ / R = 5rad / s, cylinder rotation speed ω 2 = 50 ω = 250 rad / s.

[0139] The calculations show that the Magnus effect cylinder has a moderate diameter and a relatively high rotational speed, making it suitable for high-speed generators and thus significantly reducing the generator's size. Furthermore, when using a Magnus effect cylinder instead of traditional wind turbine blades, the lift-to-drag ratio must be considered; a higher lift-to-drag ratio ensures higher operating efficiency for the Magnus wind turbine. The optimal lift-to-drag ratio for the Magnus effect cylinder is within the range of a tangential velocity ratio α = 1.5 to 3. Figure 13 The tangential velocity ratio distribution of the final calculation results is given. Figure 13 The tangential velocity ratio distribution map of the final calculation results in the example is shown below. Figure 13 As can be seen, the Magnus wind turbine of this design operates within the range of the optimal tangential velocity ratio in most areas at different radii.

Claims

1. A Magnus turbine wind turbine generator, equipped with a tower, characterized in that... A turbine annular sleeve is fixed on the tower. An annular sliding ring hole is provided on the inner wall of the turbine annular sleeve. An annular gear ring is fixed at the position of the sliding ring hole. Multiple generator trolleys are evenly distributed inside the turbine annular sleeve. The body of each generator trolley is rotatably connected to the outer end of a cylinder via an outer bearing. A drive gear that meshes with the annular gear ring is provided on the outer end of the cylinder. The inner end of the cylinder is rotatably connected to a central shaft via an inner bearing. A generator is fixed on the body of each generator trolley. The generator's input end is connected to a generator gear, which meshes with the annular gear ring. The generator's output end is connected to a conductive brush. The conductive brush contacts a conductive slip ring fixed to the inner wall of the turbine annular sleeve for electrical conduction. The cylinder is connected to an upper connecting shaft and a lower connecting shaft at both ends. The upper end of the cylinder is rotatably connected to the body of the generator trolley via the upper connecting shaft passing through the outer bearing. The lower end of the cylinder is rotatably connected to the central shaft via the lower connecting shaft passing through the inner bearing. The generator trolley includes a body, vertical wheels, and horizontal wheels. The eight vertical wheels on the upper, lower, front, rear, left, and right sides of the body are rotatably connected to the inner wall of the turbine annular sleeve. The vertical wheels serve as vertical supports for the body within the turbine annular sleeve. Horizontal wheels are rotatably connected to the upper and lower positions between the left and right vertical wheels of the body. The horizontal wheels serve as lateral supports for the body within the turbine annular sleeve.

2. A Magnus turbine wind turbine generator according to claim 1, characterized in that... The front and rear sides of the turbine annular sleeve are respectively connected to the front and rear guide shields to facilitate the straightening of the wind direction.

3. A Magnus turbine wind turbine generator according to claim 1, characterized in that... The turbine annular sleeve includes a front U-shaped sleeve and a rear U-shaped sleeve. The front U-shaped sleeve and the rear U-shaped sleeve are laid flat and connected with an opening. The upper arm end of the front U-shaped sleeve is connected to the front flange, and the upper arm end of the rear U-shaped sleeve is connected to the rear flange. The front U-shaped sleeve and the rear U-shaped sleeve are locked together by bolts and nuts passing through the front flange and the rear flange. The lower arm end of the front U-shaped sleeve and the lower wall end of the rear U-shaped sleeve are not connected to form an annular sliding ring hole.

4. A Magnus turbine wind turbine generator according to claim 1, characterized in that... The outer wall of the turbine annular sleeve is connected to a wing plate, and the turbine annular sleeve is fixedly connected to the tower via the wing plate.

5. A Magnus turbine wind turbine generator according to claim 1, characterized in that... The inner wall of the turbine annular sleeve is provided with an annular dustproof plate on the sliding ring hole. The annular dustproof plate is provided with a through hole for the cylinder to pass through. The annular dustproof plate is slidably connected to the inner wall of the turbine annular sleeve. As the cylinder rotates along the circumference of the turbine annular sleeve, it drives the annular dustproof plate to rotate.

6. A Magnus turbine wind turbine generator according to claim 1, characterized in that... The turbine annular sleeves on both sides below the sliding ring hole are respectively connected to the guards, which support the annular dustproof sheet. The central shaft is a hollow shaft, which reduces the overall size and weight, reduces flow blockage, and reduces the overall wind resistance of the turbine.

7. A design method for a Magnus turbine wind turbine generator as described in claim 1, characterized in that... The design method is based on the cylinder diameter. d At different radii r The iterative design process for the distribution at a given location consists of the following steps: Step 1: Select a design tip velocity ratio λ The angle can be obtained according to the following formula (2). θ At different radii r Distribution curve at location; （2）； θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in radians (rad). v ∞ The velocity of the incoming flow from a distance is expressed in m / s. ω Turbine speed, in rad / s. R λ represents the turbine radius in meters (m), r represents different radius positions of the turbine in meters (m), and λ is a dimensionless value. Step 2: Select a number of leaves N and lift coefficient C L According to the following formula (1), the diameter of the cylinder can be obtained. d At different radii r Distribution curve at location; （1）； d is the diameter of the cylinder at radius r, in meters. C L Let be the lift coefficient of the rotating cylinder, and be a dimensionless value. N The number of cylinders arranged circumferentially. θ The angle between the relative incoming flow velocity and the direction of rotation, expressed in rad. R The radius of the turbine is in meters (m). Step 3: Select a ratio of cylinder spin speed to turbine speed. ω 2 / ω The tangential velocity ratio can be obtained according to the following formula (3). a At different radii r Distribution curve at location; （3）； ω 2 represents the rotational speed of the cylinder, in rad / s. W for r The relative incoming flow velocity at the radius position, in m / s. d for r The diameter of the cylinder at the radius position, in meters (m). ω Turbine speed, in rad / s. θ The angle between the relative flow velocity and the direction of rotation is expressed in radians (rad), and r represents different radial positions of the turbine, expressed in meters (m). ，a The ratio of tangential velocities is a dimensionless value. Step 4: Based on the tangential velocity ratio a The lift coefficient is calculated using the distribution of the following formula (4). C L At different radii r Distribution at location; （4）； In the above formula (4), ; ; C L (a) is the lift coefficient function for a rotating cylinder under different tangential velocity ratios a. a The ratio is the tangential velocity, and e is the natural constant, which can be approximated as 2.

718. d for r The diameter of the cylinder at the radius position, in meters (m); the minimum diameter of the d2 corrugated cylinder, in meters (m). Step 5: Repeat steps 2 through 4 until the cylinder diameter is reached. d At different radii r The distribution at point i is convergent; to ensure convergence, the diameter at step i+1 is... d The calculation formula can be written as: （5）； ， x is the relaxation factor, which is a dimensionless value; d for r The diameter of the cylinder at the radius position, in meters (m). R Turbine radius, in meters. N The number of cylinders arranged circumferentially. C L (a) represents the lift coefficient of the rotating cylinder under different tangential velocity ratios, which is a dimensionless value. θ The angle between the relative incoming flow velocity and the direction of rotation is expressed in rad. Step 6: Input the actual design dimensions and wind speed to obtain the specific cylinder diameter, rotational speed, and turbine rotational speed.

8. The design method of a Magnus turbine wind turbine according to claim 7, characterized in that... The blade tip velocity ratio λ is 1~5, the number of blades N is 2~7, and the ratio of cylinder spin speed to turbine speed ω2 / ω is 20~80.

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