Wind wheel speed reducing device for vertical shaft fan

Abstract

The wind wheel speed reducing device comprises two spoilers and a transmission mechanism, the spoilers are symmetrically arranged on a cylindrical cross beam of a fan blade, the two spoilers are spliced and fixed together, the spoilers are rotationally arranged on the cross beam, and the transmission mechanism is arranged on the cross beam. The transmission mechanism is mounted on the inner walls of the two spoilers, is in transmission fit with the cross beam and is used for driving the spoilers to rotate on the cross beam; the speed reduction device is installed on the supporting cross beam of the vertical shaft fan blade and located at the end, close to the blade, of the cross beam, when the fan needs to be braked, the speed reduction device can rotate around the cross beam, the windward area of the spoiler is increased, air resistance is provided for rotation of the fan, and the purpose of rapid speed reduction of the fan is achieved.

Description

Technical Field

[0001] The present invention relates to the field of wind turbines, and particularly to a wind wheel speed reduction device for a vertical axis wind turbine. Background Art

[0002] When a vertical axis wind turbine operates in a harsh environment, it may cause damage to the wind turbine blades, damage to the overall structure, failure of the control system, etc. Therefore, how to ensure the safety of the wind turbine when encountering some special situations during the operation of the wind turbine has become an important research issue, and braking the vertical axis wind turbine is a protection measure taken for this problem.

[0003] The braking of a vertical axis wind turbine plays a crucial role in the overall safety and stability of the wind turbine. Its purpose is to quickly reduce the rotational speed of the wind turbine through certain devices in harsh environments and other situations, thereby achieving shutdown and protecting the wind turbine equipment from damage.

[0004] The requirement for the braking effect is timely and rapid. For the braking of a 250KW vertical axis wind turbine, if a mechanical braking system is used alone to achieve the braking of the wind turbine, it cannot quickly reduce the rotational speed of the wind wheel to achieve shutdown, the braking effect is not good, and the mechanical braking device is prone to overheating during the working process, affecting its service life. Summary of the Invention

[0005] In view of this, the purpose of the present invention is to provide a wind wheel speed reduction device for a vertical axis wind turbine. The present invention provides a wind wheel speed reduction device for a vertical axis wind turbine adopting the following technical solutions:

[0006] A wind wheel speed reduction device for a vertical axis wind turbine includes two baffle plates symmetrically arranged on the cylindrical cross beam of the wind turbine blade and a transmission mechanism. The two baffle plates are spliced and fixed together. The baffle plates are rotatably arranged on the cross beam. The transmission mechanism is installed on the inner walls of the two baffle plates and is in transmission cooperation with the cross beam for driving the baffle plates to rotate on the cross beam.

[0007] Further, the transmission mechanism includes a driving motor installed in the two baffle plates, a worm in transmission cooperation with the output end of the driving motor, and a worm gear section arranged on the side wall of the cross beam and in transmission cooperation with the worm. A fixed seat for installing the worm gear section is arranged on the cross beam. The driving motor drives the worm to rotate, causing the worm to rotate around the worm gear and driving the baffle plates to rotate.

[0008] Further, a box body is installed between the two baffle plates. The worm is rotatably arranged in the box body. A bevel gear set is arranged in the box body. The bevel gear set includes a bevel gear Ⅰ arranged on the output shaft of the driving motor and a bevel gear Ⅱ coaxially arranged on the worm. The bevel gear Ⅰ and the bevel gear Ⅱ are meshed.

[0009] Further, arc-shaped sliders are provided at the tops of the side plates on both sides of the box body, arc-shaped sliding rails are provided on both sides of the worm gear section of the fixed seat, and the arc-shaped sliders can slide on the arc-shaped sliding rails.

[0010] Further, the tops of the side plates on both sides of the box body for installing the arc-shaped sliders are arc-shaped and provided with a cross beam for cooperation.

[0011] Further, a mounting seat for installing the arc-shaped sliding rail is provided on the fixed seat, and the mounting seat is arc-shaped.

[0012] Further, bearing bush assemblies are provided on both sides of the cross beam where the transmission mechanism is located. The bearing bush assemblies include bearing bush I fixedly sleeved on the cross beam and bearing bush II rotatably sleeved on bearing bush I, and bearing bush II is connected to the inner walls of the two baffle plates.

[0013] Further, limit retaining rings are provided at both ends of the cross beam where bearing bush I is located.

[0014] Further, the baffle plate is arranged in an airfoil structure.

[0015] In summary, the present invention includes at least one of the following beneficial effects: The speed reduction device is installed on the support cross beam of the vertical axis fan blade, and its position is at one end of the cross beam close to the blade. When the fan needs to be braked, the speed reduction device will rotate around the cross beam, increasing the windward area of the baffle plate, providing air resistance to the rotation of the fan, and achieving the purpose of quickly decelerating the fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] Figure 1 is a schematic structural diagram of an embodiment of the present invention;

[0017] Figure 2 is an installation schematic diagram of the cross beam and the baffle plate of an embodiment of the present invention;

[0018] Figure 3 is Figure 2 an enlarged view of part A in

[0019] Figure 4 is an installation schematic diagram of the transmission mechanism and the cross beam of an embodiment of the present invention;

[0020] Figure 5 is a force analysis diagram for preventing the occurrence of friction self-locking phenomenon when the acting point of the concentrated force of the worm gear on the worm deviates in an embodiment of the present invention;

[0021] Figure 6 is an analysis diagram of gravity and acting force for preventing the occurrence of friction self-locking phenomenon when the acting point of the concentrated force of the worm gear on the worm deviates in an embodiment of the present invention;

[0022] Figure 7This is a force analysis diagram for preventing the phenomenon of friction self-locking when the force exerted by the bolt group on the arc-shaped slider is offset in the embodiment of the present invention.

[0023] Explanation of reference numerals:

[0024] 1. Baffle plate; 2. Transmission mechanism; 21. Driving motor; 22. Worm; 23. Worm gear section; 24. Coupling; 3. Box body; 31. Arc-shaped slider; 32. Bearing seat; 4. Bevel gear set; 41. Bevel gear I; 42. Bevel gear II; 5. Fixed seat; 51. Arc-shaped slide rail; 52. Mounting seat; 6. Bearing bush I; 62. Bearing bush II; 7. Cross beam; 71. Limit retaining ring. Specific implementation manners

[0025] The following uses specific specific examples to illustrate the implementation manners of the present invention. Those skilled in the art can easily understand other advantages and effects of the present invention from the content disclosed in this specification. The present invention can also be implemented or applied through other different specific implementation manners. Various details in this specification can also be modified or changed based on different viewpoints and applications without departing from the spirit of the present invention.

[0026] The following Figure 1-7 Further detailed description of the present invention is made in conjunction with the attached

[0027] The embodiment of the present invention discloses a wind wheel speed reduction device for a vertical axis fan. Referring to Figures 1-7 , the wind wheel speed reduction device for a vertical axis fan includes two baffle plates 1 symmetrically arranged on the cylindrical cross beam 7 of the fan blade and a transmission mechanism 2. The two baffle plates 1 are spliced and fixed together, and both baffle plates 1 are airfoil structures. The baffle plate 1 is rotatably arranged on the cross beam 7, and its position is at one end of the cross beam 7 close to the blade. The transmission mechanism 2 is installed on the inner walls of the two baffle plates 1 and is in transmission cooperation with the cross beam 7 for driving the baffle plate 1 to rotate on the cross beam 7; when it is necessary to brake the fan, the transmission mechanism 2 is controlled to drive the baffle plate 1 to rotate on the cross beam 7, increasing its windward area, providing air resistance to the rotation of the fan, and achieving the purpose of quickly decelerating the fan.

[0028] In this embodiment, the transmission mechanism 2 includes a drive motor 21 installed inside two baffle plates 1, a worm 22 in transmission cooperation with the output end of the drive motor 21, and a worm gear section 23 arranged on the side wall of the cross beam 7 and in transmission cooperation with the worm 22. A fixed seat 5 for installing the worm gear section 23 is arranged on the cross beam 7. The fixed seat 5 is arc-shaped and fixed on the outer side wall of the cross beam 7. The worm gear section 23 is arranged in an arc shape on the cross beam 7. The drive motor 21 drives the worm 22 to rotate, causing the worm 22 to rotate around the worm gear 23 and drive the airfoil structure to rotate. The drive motor 21 drives the worm 22 to rotate. During the rotation of the worm 22, it rotates around the worm gear section 23, driving the baffle plate 1 to rotate and changing the windward surface of the baffle plate 1. The rotation direction of the baffle plate 1 can be controlled by controlling the forward and reverse rotation of the drive motor 21.

[0029] In this embodiment, a box body 3 is installed between the two baffle plates 1. The worm 22 is rotatably arranged inside the box body 3. A bearing seat 32 is installed inside the box body 3, and the worm 22 is installed on the bearing seat 32. A bevel gear set 4 is arranged inside the box body 3. The bevel gear set 4 includes a bevel gear I 41 arranged on the output shaft of the drive motor 21 and a bevel gear II 42 arranged coaxially on the worm 22. A coupling 24 is installed on the output shaft of the drive motor 21, and the coupling 24 is connected to the bevel gear I 41. The bevel gear I 41 and the bevel gear II 42 are meshed. Through the cooperation of the bevel gear I 41 and the bevel gear II 42, the drive motor 21 drives the worm 22 to rotate.

[0030] In this embodiment, arc-shaped sliders 31 are arranged at the tops of the side plates on both sides of the box body 3, and arc-shaped slide rails 51 are arranged on both sides of the worm gear section 23 on the fixed seat 5. The arc-shaped sliders 31 can slide on the arc-shaped slide rails 51. The cooperation between the arc-shaped sliders 31 and the arc-shaped slide rails 51 can guide the rotation of the box body 3 and also support the entire reduction device, reducing the load force received by the transmission mechanism 2.

[0031] In this embodiment, the tops of the two side plates of the box body 3 for installing the arc-shaped sliders 31 are arc-shaped and are used to cooperate with the cross beam 7. The cross beam 7 passes through the top of the box body 3. The arc-shaped setting of the top of the side plate of the box body 3 facilitates the cross beam 7 to pass through and can save space occupancy.

[0032] In this embodiment, a mounting seat 52 for installing the arc-shaped slide rail 51 is arranged on the fixed seat 5. The mounting seat 52 is arc-shaped and can support the arc-shaped slide rail 51.

[0033] In this embodiment, bearing bush assemblies 6 are arranged on both sides of the transmission mechanism 2 on the cross beam 7. The bearing bush assembly 6 includes a bearing bush I 61 fixedly sleeved on the cross beam 7 and a bearing bush II 62 rotatably sleeved on the bearing bush I 61. The bearing bush II 62 is connected to the inner walls of the two baffle plates 1. The bearing bush II 62 can rotate relative to the bearing bush I 61, and the bearing bush I 61 also restricts the axial movement of the bearing bush II 62. There are threaded holes on both of the two baffle plates 1 of the bearing bush II 62, and they can be rotated together by screw connection.

[0034] In this embodiment, limit retaining rings 71 are arranged at both ends of the bearing bush I 61 on the cross beam 7. The limit retaining rings 71 are fixed on the cross beam 7 by screws. The limit retaining rings 71 can fix the bearing bush I 61 on the cross beam 7 and restrict the axial movement of the bearing bush I 61 along the cross beam 7.

[0035] In this embodiment, referring to Figures 5-7 , during the installation process, installation errors such as position deviation and angle deviation may occur, resulting in additional lateral forces or torques generated during the operation of the components, thereby increasing the risk of jamming. The following two anti-jamming situations need to be considered in the specific implementation of the device;

[0036] When the box body 3 rotates around the cross beam 7 along the arc-shaped slide rail 51, the acting force generated by the meshing of the tooth surface of the turbine section 23 and the helical surface of the dividing cylinder of the worm 22 can be approximately equivalent to a pair of mutual acting forces acting at the midpoint of the contact line between the turbine and the worm. When the acting point of the concentrated acting force of the turbine section 23 on the worm 22 is offset, a friction self-locking phenomenon, that is, jamming, may occur. Assuming that the acting force F is offset by a millimeters, the included angle between the gravity P and the acting force F along the direction of the force F is α, the length of the arc-shaped slider 31 is b, and the distance between the two arc-shaped sliders 31 is h. At this time, a force analysis is performed on this simplified model, and the following equilibrium equations are listed:

[0037] (1) F - F SA - F SB + P·cosα = 0

[0038] (2) F NA - F NB = 0

[0039] (3) F·(h / 2 + a)+ P·cosα·h / 2 - F SA ·h - F NA ·b

[0040] And there is F SA = F NA ·f s , F SB = F NB ·f s , f s is the friction coefficient;

[0041] By solving the simultaneous equations (1), (2), and (3), the maximum value of the offset a is obtained as a max = b / 2f s ·(1 + P·cosα). That is, when a is less than this value, this friction self-locking phenomenon will not occur in the device. Refer to Figures 5-6 .

[0042] When the arc-shaped slider 31 slides along the arc-shaped slide rail 51, the force exerted by the bolt group on the arc-shaped slider 31 can be approximately equivalent to a concentrated force acting on the middle bolt. Assume that the acting force F is offset by d millimeters, the angle between the gravity G and the acting force F along the direction of the force F is β, R is the distance from the upper contact surface of the arc-shaped slider 31 to the center of the crossbeam 7, r is the distance from the bottom of the arc-shaped slider 31 to the center of the crossbeam 7. The extension line of the center of gravity of the arc-shaped slider 31 along the F direction intersects with the side of the arc-shaped slider 31, and the upper contact surface of the arc-shaped slider 31 intersects with the side of the arc-shaped slider 31. The distance between these two intersection points is c. At this time, a force analysis is carried out on the simplified model, and the following equilibrium equations are listed:

[0043] (4) F + F NC ·sinθ + F ND ·sinθ - F SC ·cosθ - G·sinβ = 0

[0044] (5) F NC ·cosθ + F SC ·sinθ - F ND ·cosθ - F SD ·sinθ - G·cosβ = 0

[0045] (6) F·(R - Rsinθ + d) - (F NC ·cosθ + F SC ·sinθ)·(R + r)·sinθ - (F SD ·cosθ - F ND ·sinθ)·(R - r)G·cosθ + G·sinβ + G·cosβ·R·sinθ = 0

[0046] And there is F SF = F NF ·f s , F SG = F NG ·f s ;

[0047] By solving the simultaneous equations (4), (5), and (6), the maximum value of the offset d can be obtained. That is, when d is less than this value, this friction self-locking phenomenon will not occur in the device. Refer to Figure 7 .

[0048] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention and not to limit them. Although the present invention has been described in detail with reference to the preferred embodiments, those of ordinary skill in the art should understand that the technical solutions of the present invention can be modified or equivalently replaced without departing from the purpose and scope of the technical solutions of the present invention, and they should all be covered within the scope of the claims of the present invention.

Claims

1. A wind wheel speed reduction device for a vertical axis wind turbine, characterized in that: It includes two flow restrictors (1) and a transmission mechanism (2) symmetrically arranged on the cylindrical cross beam (7) of the fan blade. The two flow restrictors (1) are spliced and fixed together. The flow restrictor (1) is rotatably arranged on the cross beam (7), and the transmission mechanism (2) is installed on the inner walls of the two flow restrictors (1) and is in transmission cooperation with the cross beam (7) to drive the flow restrictor (1) to rotate on the cross beam (7).

2. The wind turbine speed reduction device for a vertical axis wind turbine according to claim 1, wherein: The transmission mechanism (2) includes a driving motor (21) installed in the two flow restrictors (1), a worm (22) in transmission cooperation with the output end of the driving motor (21), and a worm gear section (23) arranged on the side wall of the cross beam (7) and in transmission cooperation with the worm (22). A fixing seat (5) for installing the worm gear section (23) is arranged on the cross beam (7). The driving motor (21) drives the worm (22) to rotate, so that the worm (22) rotates around the worm gear (23) to drive the flow restrictor (1) to rotate.

3. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 2, characterized in that: A box body (3) is installed between the two flow restrictors (1). The worm (22) is rotatably arranged in the box body (3). A bevel gear set (4) is arranged in the box body (3). The bevel gear set (4) includes a bevel gear I (41) arranged on the output shaft of the driving motor (21) and a bevel gear II (42) coaxially arranged on the worm (22). The bevel gear I (41) and the bevel gear II (42) are meshed.

4. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 3, characterized in that: Arc-shaped sliders (31) are arranged at the tops of the side plates on both sides of the box body (3). Arc-shaped slide rails (51) are arranged on both sides of the worm gear section (23) on the fixing seat (5). The arc-shaped sliders (31) can slide on the arc-shaped slide rails (51).

5. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 4, characterized in that: The tops of the two side plates of the box body (3) for installing the arc-shaped sliders (31) are arc-shaped and are used to cooperate with the cross beam (7).

6. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 5, characterized in that: An installation seat (52) for installing the arc-shaped slide rails (51) is arranged on the fixing seat (5). The installation seat (52) is arc-shaped.

7. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 1, characterized in that: Bearing bush assemblies (6) are arranged on both sides of the cross beam (7) where the transmission mechanism (2) is located. The bearing bush assemblies (6) include a bearing bush I (61) fixedly sleeved on the cross beam (7) and a bearing bush II (62) rotatably sleeved on the bearing bush I (61). The bearing bush II (62) is connected to the inner walls of the two flow restrictors (1).

8. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 7, characterized in that: Limit retaining rings (71) are arranged at both ends of the cross beam (7) where the bearing bush I (61) is located.

9. The wind wheel speed reduction device for a vertical axis wind turbine according to claim 1, characterized in that: The two flow restrictors (1) are arranged in an airfoil structure.

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