Blade, impeller, centrifugal fan and vehicle

Abstract

The invention relates to a blade, an impeller, a centrifugal fan and a vehicle, the blade comprises a blade body, and the blade body comprises a suction surface, a front edge and an overflowing flow path; wherein the overflowing flow path is configured to be communicated with the front edge and the suction surface so as to reduce the impact of airflow on the front edge. The beneficial effects of the present application are that by arranging the overflowing flow path communicating the front edge and the suction surface, the airflow near the front edge is guided to the suction surface through the overflowing flow path, so that the impact of the airflow on the front edge is reduced, and the pneumatic noise is effectively reduced.

Description

Technical Field

[0001] This application relates to the field of wind turbine technology, and more particularly to a blade, impeller, centrifugal fan and vehicle. Background Technology

[0002] Multi-blade centrifugal fans are a common type of airflow device. Due to their unique structure, the air intake conditions of the impeller vary at different circumferential positions. The uneven flow at different circumferential positions and the large angle of attack of the airflow at the inlet of the inter-blade channel cause a strong impact on the leading edge of the blades, resulting in significant noise. Summary of the Invention

[0003] This application provides a blade that effectively reduces noise, thereby at least partially solving the above-mentioned technical problems.

[0004] To achieve the above objectives, according to a first aspect of this application, a blade is provided, comprising:

[0005] The blade body includes the suction surface, the leading edge, and the flow path.

[0006] The flow path is configured to connect the leading edge and the suction surface to reduce the impact of airflow on the leading edge.

[0007] Optionally, the blade body further includes a pressure surface and a trailing edge;

[0008] The leading edge is connected between the front end of the suction surface and the front end of the pressure surface;

[0009] The trailing edge is connected between the rear end of the suction surface and the rear end of the pressure surface.

[0010] Optionally, the flow path has:

[0011] The flow inlet is located at the leading edge;

[0012] An outlet is located at the suction surface;

[0013] A flow channel connects the flow inlet and the flow outlet.

[0014] Optionally, in the first direction of the blade body, the blade body is provided with a plurality of flow paths.

[0015] Optionally, the overall outline of the flow path is arc-shaped.

[0016] Optionally, the blade further includes:

[0017] The turbulent fluid is used to disturb the airflow flowing out of the flow path and generate eddies;

[0018] The turbulent fluid is disposed on the suction surface, and is located near the outlet of the flow path, between the outlet and the trailing edge.

[0019] Optionally, the overall profile of the turbulent fluid is triangular in shape.

[0020] Optionally, the turbulent fluid includes a turbulent surface, and the turbulent surface and the direction of the outflow of the airflow in the flow path have a first angle α, where the first angle α is an acute angle.

[0021] Optionally, the turbulent fluid includes a guide surface, and each of the two sides of the turbulent fluid is independently provided with a guide surface.

[0022] Optionally, the guide surface has an overall arc-shaped profile.

[0023] Optionally, the blade further includes:

[0024] Two turbulent fluids are used to agitate the airflow exiting the flow path to generate eddies;

[0025] The two turbulent fluids are disposed on the suction surface, and the turbulent fluids are disposed near the outlet of the flow path and located between the outlet and the tail edge.

[0026] The two turbulent fluids are arranged opposite each other.

[0027] Optionally, the two disturbing fluids are arranged opposite each other such that they have a first distance D1 and a second distance D2, wherein the first distance D1 is smaller than the second distance D2; the closer the distance between the two disturbing fluids is to the outlet distance of the flow path, the smaller the value.

[0028] Optionally, the second included angle β formed by the two disturbing fluids can range from 10° to 150°.

[0029] Optionally, the ratio of the maximum width W2 between the two guiding surfaces of the turbulent fluid to the width W1 of the turbulent surface ranges from W2:W1 = 2-4:1.

[0030] Optionally, one flow path corresponds to multiple sets of correspondingly configured disturbance fluids.

[0031] Optionally, the blade body further comprises:

[0032] The mixing channel is configured to connect the pressure surface and the suction surface.

[0033] Optionally, the blade further includes:

[0034] A baffle assembly is used to open or close the flow path.

[0035] Optionally, the baffle assembly includes a front baffle mechanism, which includes a front baffle and a front drive structure. The front baffle is disposed at the leading edge, and the front drive structure is used to drive the front baffle to open or close the flow path.

[0036] Optionally, the baffle assembly includes a rear baffle mechanism, which includes a rear baffle and a rear drive structure. The rear baffle is disposed on the suction surface, and the rear drive structure is used to drive the rear baffle to open or close the flow path.

[0037] According to a second aspect of this application, an impeller, an impeller cover, and blades as described above are provided, with a plurality of said blades disposed on the impeller cover.

[0038] According to a third aspect of this application, a centrifugal fan is also provided, including the impeller as described above.

[0039] According to a fourth aspect of this application, a vehicle is also provided, including the centrifugal fan as described above.

[0040] The beneficial effects of this application are as follows: by setting a flow path that connects the leading edge and the suction surface, the airflow near the leading edge is guided to the suction surface through the flow path, thereby reducing the impact of the airflow on the leading edge and effectively reducing aerodynamic noise.

[0041] Other features and advantages of this application will be described in detail in the following detailed description section. Attached Figure Description

[0042] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0043] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings, wherein the same reference numerals in the following description denote the same parts.

[0044] Figure 1 This is a schematic diagram of the overall structure of the impeller provided in an exemplary embodiment of this application;

[0045] Figure 2 This is a schematic diagram of the blade structure provided in an exemplary embodiment of this application;

[0046] Figure 3 yes Figure 2 An enlarged schematic diagram of a portion;

[0047] Figure 4 This is a bottom view of the impeller provided in an exemplary embodiment of this application;

[0048] Figure 5 This is a cross-sectional view of the first type of blade provided in an exemplary embodiment of this application;

[0049] Figure 6 This is a cross-sectional view of the second type of blade provided in an exemplary embodiment of this application;

[0050] Figure 7 This is a cross-sectional view of the third type of blade provided in an exemplary embodiment of this application;

[0051] Figure 8 This is a schematic diagram of the structure of the turbulent fluid in the blade provided in an exemplary embodiment of this application;

[0052] Figure 9 This is a schematic diagram of the structure of the turbulent fluid in the blade provided in an exemplary embodiment of this application;

[0053] Figure 10 This is a schematic diagram of the flow field between adjacent blades in an impeller provided in an exemplary embodiment of this application;

[0054] Figure 11 This is a schematic diagram of the flow field at locations where no flow path or turbulent fluid is provided in this application;

[0055] Figure 12 It is the fluid simulation result of the impeller in the existing technology;

[0056] Figure 13 The fluid simulation results of the impeller provided in the exemplary embodiments of this application are as follows;

[0057] Figure 14 This is a schematic diagram of the overall structure of the vehicle provided in an exemplary embodiment of this application.

[0058] Explanation of reference numerals in the attached figures:

[0059] 100. Leaf blade;

[0060] 110. Blade body;

[0061] 111. Suction surface; 112. Pressure surface; 113. Leading edge; 114. Trailing edge;

[0062] 115. Flow path; 115a. Flow inlet; 115b. Flow outlet; 115c. Flow channel; 115d. Mixing channel;

[0063] 120. Turbulent fluid; 121. Turbulent surface; 122. Guide surface;

[0064] 131. Front fender; 132. Rear fender;

[0065] 10. Impeller; 200. Impeller cover plate;

[0066] C1, First Direction;

[0067] D1, first distance; D2, second distance;

[0068] α, the first included angle; β, the second included angle;

[0069] H, the height of the turbulent fluid; L, the length of the turbulent fluid;

[0070] W1, width of the turbulence surface; W2, maximum width between the two guide surfaces;

[0071] 1. Vehicles. Detailed Implementation

[0072] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of them. All other embodiments obtained by those skilled in the art based on the embodiments of this application without creative effort are within the protection scope of this application.

[0073] like Figure 11 As shown, due to the uneven inflow at different circumferential positions and the large angle of attack of the airflow at the blade inlet of the multi-blade centrifugal fan, a large impact is often generated on the leading edge region of the blades. At the same time, flow separation is very likely to occur on the suction surface, reducing the fan efficiency and increasing the fan noise. In addition, the airflow exiting the impeller has serious unevenness, specifically manifested as excessively high local flow velocity at the impeller outlet, forming a high-speed region at the trailing edge, and excessively low flow velocity in the region near the trailing edge of the blades on the suction surface. The high-speed fluid exiting the impeller constantly beats and impacts the volute tongue, ultimately leading to serious aerodynamic noise.

[0074] According to the first aspect of this application, referring to Figure 2 and Figure 5 The blade 100 of this application includes a blade body 110. The blade body includes a suction surface 111, a leading edge 113, and a flow path 115. The flow path 115 is configured to connect the leading edge 113 and the suction surface 111 to reduce the impact of airflow on the leading edge 113.

[0075] By using the above technical solution, by setting a flow path 115 that connects the leading edge 113 and the suction surface 111, the airflow near the leading edge 113 is guided to the suction surface 111 through the flow path 115, thereby reducing the impact of the airflow on the leading edge 113 and effectively reducing aerodynamic noise.

[0076] In some embodiments, refer to Figure 2 and Figure 5 The blade body also includes a pressure surface 112 and a trailing edge 114.

[0077] The leading edge 113 is connected between the front end of the suction surface 111 and the front end of the pressure surface 112; the trailing edge 114 is connected between the rear end of the suction surface 111 and the rear end of the pressure surface 112.

[0078] In some embodiments, refer to Figure 2 and Figure 5 In this application, the pressure surface 112 of the blade body 110 is concave, while the suction surface 111 is convex. The leading edge 113 and the trailing edge 114 are disposed between the suction surface 111 and the pressure surface 112.

[0079] In some embodiments, the flow path includes: a flow inlet 115a, a flow outlet 115b, and a flow channel 115c.

[0080] In some embodiments, refer to Figure 2 and Figure 5 The inlet 115a is located at the leading edge 113, and the outlet 115b is located at the suction surface 111; the flow channel 115c connects the inlet 115a and the outlet 115b.

[0081] For example, the overflow outlet 115b is located at the middle section of the suction surface 111.

[0082] In some embodiments, refer to Figure 2 and Figure 5 The overall outline of the flow path 115 is arc-shaped.

[0083] More specifically, the flow path 115 extends along a curve, and at least a portion of the flow path 115 extends at an angle tangent to the suction surface 111 to the flow outlet 115b at the suction surface 111, so that the airflow from the flow outlet 115b flows in a direction approximately tangent to the suction surface 111.

[0084] With this approach, under the Coanda effect, the high-speed airflow adheres to the suction surface 111, increasing the energy of the fluid near the suction surface 111, delaying and improving the flow separation phenomenon near the suction surface 111 in the blade passage, which can effectively reduce the vortex noise generated in the blade passage and improve the aerodynamic efficiency of the multi-blade centrifugal fan.

[0085] In some embodiments, refer to Figures 1 to 5In the first direction C1 (which may be the axial direction of the impeller), the blade body 110 is provided with multiple flow paths 115. The suction surface 111, pressure surface 112, leading edge 113 and trailing edge 114 all have smooth curves in their cross-sectional profiles.

[0086] In some embodiments, refer to Figures 1 to 3 , Figure 5 and Figure 9 As shown, the blade body 110 also includes a turbulent fluid 120. The turbulent fluid 120 is used to turbulent the airflow exiting through the flow path 115 to generate vortices. The turbulent fluid 120 is disposed on the suction surface 111, and is located near the flow outlet 115b of the flow path 115, between the flow outlet 115b and the trailing edge 114. The flow path 115 can provide a better forward flow field for the turbulent fluid 120, and the combined noise reduction of the flow path 115 and the turbulent fluid 120 improves the internal airflow of the impeller.

[0087] By employing this scheme, a turbulent fluid 120 is arranged downstream of the overflow outlet 115b. The vortex generated by the turbulent fluid 120 mixes the low-energy airflow near the suction surface 111 with the high-energy airflow in the trailing edge high-speed region. This improves the uneven distribution of flow velocity at the impeller outlet and the phenomenon of excessive local flow velocity, thereby reducing the interference between the impeller and the vortex tongue, reducing the intensity of the noise source, and ultimately reducing the aerodynamic noise of the centrifugal fan.

[0088] Meanwhile, the composite noise reduction scheme of combining the flow path and the turbulent fluid adopted in this application still keeps the blade as a whole, avoiding the introduction of complex structural modifications (such as multi-blade combination or blade deformation), which would increase the risk of failure of the blade during long-term operation and ensure the reliability of the blade.

[0089] In some embodiments, refer to Figure 2 , Figure 3 , Figure 5 and Figure 9 As shown, the overall outline of the turbulent fluid 120 is triangular in shape.

[0090] Understandable, refer to Figure 8 The cross-sectional profile obtained by cutting the disturbing fluid 120 along the section indicator line AA is triangular in shape.

[0091] In some embodiments, the turbulent fluid 120 includes a turbulent surface 121, and the turbulent surface 121 and the direction of airflow out of the flow path 115 are at a first angle α, where the first angle α is an acute angle.

[0092] In some embodiments, refer to Figure 9As shown, the turbulent fluid 120 includes a guide surface 122, with each of the two sides of the turbulent fluid 121 having its own guide surface 122. The guide surfaces 122 guide the airflow to reduce its impact on the turbulent fluid 120.

[0093] In some embodiments, refer to Figure 9 As shown, the guide surface 122 has an overall arc-shaped outline.

[0094] In some embodiments, the blade 100 further includes two turbulence streams 120. The two turbulence streams 120 are used to turbulent the airflow exiting the flow path 115 to generate eddies; the two turbulence streams 120 are disposed on the suction surface 111, the turbulence streams 120 are disposed near the flow outlet 115b of the flow path, and are located between the flow outlet 115b and the trailing edge 114; the two turbulence streams 120 are disposed opposite to each other.

[0095] It is understood that the disturbance fluids 120 in this application are generally set in pairs.

[0096] In some embodiments, refer to Figure 2 , Figure 3 , Figure 5 and Figure 8 As shown, the two turbulent fluids 120 are arranged opposite each other so that they have a first distance D1 and a second distance D2, where the first distance D1 is smaller than the second distance D2; the closer the distance between the two turbulent fluids 120 is to the flow outlet 115b of the flow path 115, the smaller the distance value.

[0097] It is understandable that the two paired turbulence fluids 120 are arranged at a certain angle to each other. Moreover, the distance between the two turbulence fluids gradually increases in the direction away from the flow outlet.

[0098] Specifically, refer to Figure 2 , Figure 3 , Figure 5 and Figure 9 As shown, two turbulent fluids 120 are vertically mounted in pairs at a certain second included angle β on the suction surface 111 of the blade body 110 and located between the overflow outlet 115b and the trailing edge 114.

[0099] Here, the second included angle β of the turbulent fluid 120 refers to the included angle formed by the extension direction of the turbulent surface 121, or it can be the included angle formed by a plane perpendicular to the turbulent surface 121.

[0100] The vertical installation of the turbulent fluid 120 means that the turbulent fluid 120 is approximately perpendicular to the turbulent surface 121. Alternatively, the generatrix of the turbulent surface 121 of the turbulent fluid 120 may be parallel to the generatrix of the blade body 110, or parallel to the central axis of the multi-blade centrifugal fan.

[0101] After the airflow exits the outlet, it is affected by the Coanda effect and will flow along the suction surface, so that there should be a good incoming flow state in front of the turbulent fluid 120, ensuring that the turbulent fluid 120 can play its role.

[0102] exist Figure 9 The key parameters of the turbulent fluid 120 can be seen, such as the second included angle β of the turbulent fluid 120, the height H of the turbulent fluid 120, the width W1 and the length L.

[0103] Because the flow state within the blade passages of a multi-blade centrifugal fan changes significantly with varying operating conditions, the determination of the above key parameters should be based on the specific design conditions and dimensions of the multi-blade centrifugal fan.

[0104] It should be noted that, in order to avoid the turbulent fluid 120 generating a large intensity and a large-sized wingtip vortex that completely fills the flow field in the inter-blade channel, causing a sharp deterioration in the aerodynamic performance and noise level of the fan, the size of the turbulent fluid 120 should not be too large.

[0105] As a preferred embodiment, two pairs of disturbance fluids 120 are arranged symmetrically relative to a symmetrical plane, and the vertex of the second included angle β formed by the two disturbance fluids 120 is on the symmetrical plane.

[0106] In some embodiments, refer to Figure 5 and Figure 9 As shown, the second included angle β formed by the two turbulent fluids 120 ranges from 10° to 150°; the ratio of the maximum width W2 between the two guide surfaces 122 of the turbulent fluid 120 to the width W1 of the turbulent surface ranges from W2:W1 = 2-4:1; the ratio of the width W1 of the turbulent surface to the thickness T of the blade body ranges from W1:T = 0.1-0.5.

[0107] By selecting the above parameters, the turbulent fluid can generate a worm tip with strength and size that matches the blade, effectively improving the uneven distribution of flow velocity at the impeller outlet and the phenomenon of excessive local flow velocity.

[0108] Figure 10 The flow field between two adjacent blades is shown. (Refer to...) Figure 10 As shown, the flow inlet 115a of the flow path 115 of this application is located at the leading edge 113 of the blade body 110. It can reduce the inflow impact near the leading edge 113 and introduce the high-speed airflow near the leading edge 113 into the suction surface 111 through the flow path 115. Under the action of the Coanda effect, the airflow flows along the wall, increasing the energy of the fluid near the suction surface 111 to improve the flow separation at that point, reduce the vortex noise in the inter-blade channel, and at the same time provide a better forward flow field for the rear turbulence component.

[0109] A turbulent fluid 120 is installed downstream of the flow outlet 115b near the suction surface 111, i.e., downstream of the airflow. The vortex generated by the turbulent fluid 120 mixes the low-energy airflow near the wall of the blade body 110 with the high-energy airflow in the high-speed region of the trailing edge. This improves the uneven velocity distribution and excessive uniform velocity at the outlet of the centrifugal fan impeller 10, thereby reducing the interference between the impeller 10 and the volute tongue, reducing the intensity of the noise source, and ultimately reducing the aerodynamic noise of the multi-blade centrifugal fan.

[0110] In some embodiments, refer to Figure 2 and Figure 3 As shown, one flow path 115 corresponds to multiple sets of correspondingly arranged disturbance fluids 120.

[0111] For example, one flow path 115 corresponds to multiple sets of two correspondingly configured disturbance fluids 120.

[0112] In some embodiments, refer to Figure 6 As shown, the blade 100 also includes a baffle assembly. The baffle assembly is used to open or close the flow path 115.

[0113] By adopting this scheme, the flow path 115 can be opened at high speeds to reduce noise, while the flow path 115 can be closed at low speeds to improve the work capacity of the impeller 10.

[0114] As a specific plan, refer to Figure 6 As shown, the baffle assembly includes a front baffle mechanism, which includes a front baffle 131 and a front drive structure. The front baffle 131 is disposed at the leading edge 113, and the front drive structure is used to drive the front baffle 131 to open or close the flow path.

[0115] It is understood that the front baffle 131 is located at the flow inlet 115a of the flow path 115. The flow path 115 is opened or closed by the movement of the front baffle 131 relative to the blade body 110, such as rotation.

[0116] For example, the front drive structure can be a torsion spring, which is disposed between the front baffle 131 and the blade body 110. The front baffle 131 and the blade body 110 are rotatably connected, and the rotation axis is parallel to the first direction C1 of the blade body 110. The front baffle 131 is disposed at the flow inlet of the flow path 115, that is, at the leading edge. When the rotation speed is high enough, the front baffle 131 overcomes the force of the torsion spring under the action of centrifugal force, thereby opening the flow path 115. When the rotation speed is low, the torsion spring causes the front baffle 131 to close the flow inlet 115a under the action of elasticity.

[0117] As a specific plan, refer to Figure 6As shown, the baffle assembly includes a rear baffle mechanism, which includes a rear baffle 132 and a rear drive structure. The rear baffle 132 is disposed on the suction surface 111, and the rear drive structure is used to drive the rear baffle 132 to open or close the flow path.

[0118] It is understood that the rear baffle 132 is located at the flow outlet 115b of the flow path 115. The flow path 115 is opened or closed by the movement of the rear baffle 132 relative to the blade body 110, such as rotation.

[0119] As an optional solution, the rear drive structure can use a torsion spring disposed between the rear baffle 132 and the blade body 110. The rear baffle 132 and the blade body 110 are rotatably connected, and the rotation axis is parallel to the first direction C1 of the blade body 110. The rear baffle 132 is disposed at the flow outlet 115b of the flow path 115, that is, at the suction surface 111. When the rotation speed is high enough, the rear baffle 132 overcomes the force of the torsion spring under the action of centrifugal force, thereby opening the flow path 115. When the rotation speed is low, the torsion spring causes the rear baffle 132 to close the flow outlet 115b under the action of elasticity.

[0120] In some embodiments, refer to Figure 7 As shown, the blade body 110 also includes a mixing channel 115d. The mixing channel 115d is configured to connect the external space at the pressure surface 112 and the suction surface 111.

[0121] As an optional solution, a mixing channel 115d can be provided, which extends from the pressure surface 112 to the suction surface 111 so that the outer space of the pressure surface 112 and the outer space of the suction surface 111 are connected. That is, the pressure surface 112 and the suction surface 111 near the trailing edge 114 are connected. This arrangement can mix the low-energy fluid on the suction surface 111 side of the blade body 110 and the high-energy fluid in the high-speed region of the trailing edge on the pressure surface side to a certain extent, which can replace or supplement the effect of the turbulent fluid 120, improve the uneven velocity distribution at the impeller 10 outlet, and reduce the noise of the multi-blade centrifugal fan.

[0122] According to the second aspect of this application, referring to Figure 1 and Figure 4 As shown, an impeller 10 is provided, which includes an impeller cover plate 200 and the aforementioned blades 100. Multiple blades 100 are disposed on two impeller cover plates 200 and are fixedly connected to each of the two impeller cover plates 200. This impeller 10 possesses all the beneficial effects of the aforementioned blades 100, which will not be elaborated upon here.

[0123] As a preferred embodiment, one of the impeller covers 200 can be configured as a motor cover.

[0124] Reference Figure 12and Figure 13 As shown, Figure 12 The fluid simulation results of the existing impeller 10 are shown. Figure 13 The fluid simulation results of the impeller 10 of this application are shown.

[0125] Depend on Figure 12 and Figure 13 The comparison shows that the proposed composite noise reduction method can effectively reduce the airflow impact at the leading edge 113, improve the problem of excessive local flow velocity at the blade passage exit, and also effectively suppress the flow separation occurring within the blade passage. It should be added that, according to simulation results, moving the flow outlet 115b at the suction surface 111 towards the leading edge 113 can further reduce the flow separation phenomenon at the suction surface 111 of the blade 100, thereby improving the flow field within the blade passage. That is, the flow outlet 115b of the flow path 115 should be closer to the leading edge 113 of the blade body 110.

[0126] According to a third aspect of this application, a centrifugal fan is provided, which includes the impeller 10 described above. The centrifugal fan has all the beneficial effects of the impeller 10 described above, which will not be repeated here.

[0127] According to the fourth aspect of this application, referring to Figure 14 As shown, a vehicle 1 is provided, which includes the centrifugal fan described above. The vehicle 1 has all the beneficial effects of the centrifugal fan described above, which will not be repeated here.

[0128] The vehicle 1 can be a gasoline-powered vehicle, a plug-in hybrid electric vehicle, or a new energy vehicle, etc., and this application does not make any specific restrictions on it.

[0129] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined as "first" or "second" may explicitly or implicitly include one or more features. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0130] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0131] The embodiments, implementation methods, and related technical features of this application can be combined and substituted for each other without conflict.

[0132] The above are merely preferred embodiments of this application and are not intended to limit this application in any way. Any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this application without departing from the scope of the technical solution of this application shall still fall within the scope of the technical solution of this application.

Claims

1. A vane, characterized in that The blade body comprises a suction surface, a leading edge and a through-flow flow path; The through-flow flow path is configured to connect the leading edge and the suction surface to reduce the impact of airflow on the leading edge. The blade body further comprises a pressure surface and a trailing edge; 2. The blade of claim 1, wherein The leading edge is connected between the front end of the suction surface and the front end of the pressure surface; The trailing edge is connected between the rear end of the suction surface and the rear end of the pressure surface. The through-flow flow path has:

3. The blade of claim 2, wherein A through-flow inlet provided at the leading edge; A through-flow outlet provided at the suction surface; A through-flow channel connecting the through-flow inlet and the through-flow outlet. In the first direction of the blade body, the blade body is provided with a plurality of through-flow flow paths.

4. The blade of claim 1, wherein The overall contour shape of the through-flow flow path is arc-shaped.

5. The blade of claim 1, wherein The blade further comprises:

6. The blade of claim 3, wherein A spoiler for disturbing the airflow flowing out of the through-flow flow path to generate vortex flow; The spoiler is provided on the suction surface, and is arranged adjacent to the through-flow outlet of the through-flow flow path and between the through-flow outlet and the trailing edge. The overall contour shape of the spoiler is triangular.

7. The blade of claim 6, wherein The spoiler comprises a spoiler surface, and the spoiler surface has a first included angle a with the direction of airflow flowing out of the through-flow flow path, and the first included angle a is an acute angle.

8. The blade of claim 6, wherein The spoiler surface comprises a guide surface, and each of the two side surfaces of the spoiler surface is independently provided with a guide surface.

9. The blade of claim 8, wherein, The overall contour shape of the guide surface is arc-shaped.

10. The blade of claim 9, wherein The blade further comprises:

11. The blade of claim 6, wherein Two spoilers for disturbing the airflow flowing out of the through-flow flow path to generate vortex flow; The two spoilers are provided on the suction surface, and are arranged adjacent to the through-flow outlet of the through-flow flow path and between the through-flow outlet and the trailing edge. The two spoilers are oppositely arranged. The two spoilers are oppositely arranged to have a first distance D1 and a second distance D2 therebetween, and the first distance D1 is smaller than the second distance D2.

12. The blade of claim 11, wherein, The closer the distance between the two spoilers is to the through-flow outlet of the through-flow flow path, the smaller the distance value is.

13. The blade of claim 11, wherein, The second included angle β between the two spoilers ranges from 10° to 150°.

14. The blade of claim 9, wherein, The ratio of the maximum width W2 between the two guide surfaces of the spoiler to the width W1 of the spoiler surface ranges from 2:1 to 4:

1.

15. The blade of claim 6, wherein, One through-flow flow path corresponds to a plurality of groups of correspondingly arranged spoilers.

16. The blade according to any one of claims 1 to 5, characterized in that The blade body further comprises: A mixed-flow channel configured to connect the pressure surface and the suction surface.

17. The blade of any one of claims 1 to 5, wherein The blade further comprises: A baffle assembly for opening or closing the through-flow flow path.

18. The blade of claim 17, wherein, The baffle assembly comprises a front baffle mechanism, the front baffle mechanism comprises a front baffle and a front driving structure, the front baffle is arranged on the leading edge, and the front driving structure is used to drive the front baffle to open or close the through-flow flow path.

19. The blade of claim 17, wherein, The baffle assembly comprises a rear baffle mechanism, the rear baffle mechanism comprises a rear baffle and a rear driving structure, the rear baffle is arranged on the suction surface, and the rear driving structure is used to drive the rear baffle to open or close the through-flow flow path.

20. An impeller characterized by, The blade body comprises a suction surface, a leading edge and a through-flow flow path; Impeller cover plate and blade as claimed in claims 1 to 19, a plurality of said blades being arranged on the impeller cover plate.

21. A centrifugal fan characterized by Comprising: Impeller as claimed in claim 20.

22. A vehicle characterized by Centrifugal fan comprising a blade as claimed in claim 21.

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