Blade, impeller, centrifugal fan and vehicle

Abstract

A vehicle, comprising a blade, an impeller, and a centrifugal fan. The blade comprises: a blade body, the blade body comprising a suction surface, a leading edge, and a through-flow path, wherein the through-flow path is configured to communicate the leading edge with the suction surface so as to reduce the impact of an airflow on the leading edge.

Description

Blade, impeller, centrifugal fan and vehicle

[0001] The present application claims priority to the Chinese patent publication with the publication number 202411392484.9, the title of "Blade, impeller, centrifugal fan and vehicle", which was filed on September 30, 2024, in the China Patent Office, the whole content of which is incorporated herein by reference. TECHNICAL FIELD

[0002] The present application relates to, but is not limited to, the fan technical field, in particular to a blade, an impeller, a centrifugal fan and a vehicle. BACKGROUND

[0003] The multi-wing centrifugal fan is a common air flow device.

[0004] In the related art, due to the unique structure of the multi-wing centrifugal fan, the inlet conditions of the impeller at different circumferential positions are different, the inlet flow at different circumferential positions is uneven, and the inlet flow of the inter-blade passage has a large angle of attack, which will produce a strong impact on the leading edge of the blade, thereby generating a large noise. SUMMARY

[0005] The embodiments of the present application provide a blade, which effectively reduces noise to at least partially solve the above technical problems.

[0006] According to a first aspect of the present application, a blade is provided, comprising:

[0007] a blade body, the blade body comprising a suction surface, a leading edge and a flow passage;

[0008] wherein the flow passage is configured to connect the leading edge and the suction surface to reduce the impact of the airflow on the leading edge.

[0009] In some embodiments of the present application, the blade body further comprises a pressure surface and a trailing edge;

[0010] wherein the leading edge is connected between the front end of the suction surface and the front end of the pressure surface;

[0011] wherein the trailing edge is connected between the rear end of the suction surface and the rear end of the pressure surface.

[0012] In some embodiments of the present application, the flow passage has:

[0013] a flow inlet provided at the leading edge;

[0014] a flow outlet provided at the suction surface;

[0015] a flow channel connecting the flow inlet and the flow outlet.

[0016] In some embodiments of the present application, the vane body is provided with a plurality of the flow passage in the first direction of the vane body.

[0017] In some embodiments of the present application, the overall profile of the flow passage is arc-shaped.

[0018] In some embodiments of the present application, the vane further comprises:

[0019] a spoiler for disturbing the airflow flowing out of the flow passage to generate vortex flow;

[0020] The spoiler is arranged on the suction surface, and is arranged adjacent to the flow outlet of the flow passage and between the flow outlet and the trailing edge.

[0021] In some embodiments of the present application, the overall profile of the spoiler is triangular.

[0022] In some embodiments of the present application, the spoiler comprises a spoiler surface, and the spoiler surface has a first included angle with the direction of the airflow flowing out of the flow passage, and the first included angle is an acute angle.

[0023] In some embodiments of the present application, the spoiler comprises a spoiler surface, and the spoiler surface has a first included angle with the direction of the airflow flowing out of the flow passage, and the first included angle is an acute angle.

[0024] In some embodiments of the present application, the overall profile of the spoiler surface is arc-shaped.

[0025] In some embodiments of the present application, the vane further comprises:

[0026] two spoilers for disturbing the airflow flowing out of the flow passage to generate vortex flow;

[0027] The two spoilers are arranged on the suction surface, and are arranged adjacent to the flow outlet of the flow passage and between the flow outlet and the trailing edge.

[0028] The two spoilers are oppositely arranged.

[0029] In some embodiments of the present application, the two spoilers are oppositely arranged to have a first distance and a second distance therebetween, and the first distance is smaller than the second distance; the distance between the two spoilers is closer to the flow outlet of the flow passage.

[0030] In some embodiments of the present application, the second included angle between the two spoilers ranges from 10° to 150°.

[0031] In some embodiments of the present application, the maximum width between the two guide surfaces of the spoiler is W2, the width of the spoiler is W1, and the ratio of W2 to W1 is in the range of 2-4:1.

[0032] In some embodiments of the present application, one of the flow paths corresponds to a plurality of groups of the spoilers.

[0033] In some embodiments of the present application, the blade body further comprises:

[0034] The mixed flow passage is configured to communicate the pressure surface and the suction surface.

[0035] In some embodiments of the present application, the blade further comprises:

[0036] The baffle assembly is configured to open or close the flow path.

[0037] In some embodiments of the present application, 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 at the leading edge, and the front driving structure is configured to drive the front baffle to open or close the flow path.

[0038] In some embodiments of the present application, 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 at the suction surface, and the rear driving structure is configured to drive the rear baffle to open or close the flow path.

[0039] According to a second aspect of the present application, a blade wheel, a blade wheel cover plate, and the blade as described in the first aspect are provided, and a plurality of the blades are arranged on the blade wheel cover plate.

[0040] According to a third aspect of the present application, a centrifugal fan is further provided, comprising the blade wheel as described in the second aspect.

[0041] According to a fourth aspect of the present application, a vehicle is further provided, comprising the centrifugal fan as described in the third aspect.

[0042] The present application has the beneficial effect that by arranging the flow path communicating 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 the aerodynamic noise.

[0043] Other features and advantages of the present application will be described in detail in the following specific embodiments. BRIEF DESCRIPTION OF DRAWINGS

[0044] In order to more clearly illustrate the technical solutions in the embodiments of the present application, the following will briefly introduce the drawings needed in the embodiment description. Obviously, the drawings in the following description only show some embodiments of the present application, and other drawings can be obtained by those skilled in the art without any creative effort on the basis of these drawings.

[0045] In order to more completely understand the present application and its beneficial effects, the following will be described in conjunction with the drawings, wherein the same reference numerals in the following description represent the same parts.

[0046] Fig. 1 is a schematic diagram of the overall structure of an impeller provided in an exemplary embodiment of the present application;

[0047] Fig. 2 is a schematic diagram of the structure of a blade provided in an exemplary embodiment of the present application;

[0048] Fig. 3 is an enlarged schematic diagram of a portion of Fig. 2;

[0049] Fig. 4 is a bottom view of the impeller provided in an exemplary embodiment of the present application;

[0050] Fig. 5 is a sectional view of a first blade provided in an exemplary embodiment of the present application;

[0051] Fig. 6 is a sectional view of a second blade provided in an exemplary embodiment of the present application;

[0052] Fig. 7 is a sectional view of a third blade provided in an exemplary embodiment of the present application;

[0053] Fig. 8 is a schematic diagram of the structure of a spoiler in a blade provided in an exemplary embodiment of the present application;

[0054] Fig. 9 is a schematic diagram of the structure of a spoiler in a blade provided in an exemplary embodiment of the present application;

[0055] Fig. 10 is a schematic diagram of the flow field between adjacent blades in an impeller provided in an exemplary embodiment of the present application;

[0056] Fig. 11 is a schematic diagram of the flow field at a location where no overflow flow path and spoiler are provided;

[0057] Fig. 12 is a fluid simulation result of an impeller in the prior art;

[0058] Fig. 13 is a fluid simulation result of an impeller provided in an exemplary embodiment of the present application;

[0059] Fig. 14 is a schematic diagram of the overall structure of a vehicle provided in an exemplary embodiment of the present application.

[0060] Explanation of reference signs: 100, blade; 110, blade body; 111, suction surface; 112, pressure surface; 113, leading edge; 114, trailing edge; 115, flow passage; 115a, flow inlet; 115b, flow outlet; 115c, flow channel; 115d, mixing channel; 120, spoiler; 121, spoiler surface; 122, guide surface; 131, front baffle; 132, rear baffle; 10, impeller; 200, impeller cover plate; C1, first direction; D1, first distance; D2, second distance; a, first included angle; b, second included angle; H, height of spoiler; L, length of spoiler; W1, width of spoiler surface; W2, maximum width between two guide surfaces; 1, vehicle. DETAILED DESCRIPTION

[0061] The technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, rather than all the embodiments. Based on the embodiments in the present application, all other embodiments obtained by a person skilled in the art without creative labor fall within the protection scope of the present application.

[0062] As shown in FIG. 11, due to the uneven inflow at different circumferential positions of the multi-blade centrifugal fan and the large flow angle of the air flow at the inlet of the blade channel, a large impact on the leading edge region of the blade is often generated, and flow separation is also prone to occurring on the suction surface, thereby reducing the efficiency of the fan and increasing the noise of the fan. In addition, the air flow out of the impeller has serious unevenness, specifically, the local flow velocity at the outlet of the impeller is too large to form a high-speed region at the trailing edge, and the flow velocity near the trailing edge region of the blade on the suction surface is too small, and the high-speed fluid out of the impeller constantly hits and impacts the volute tongue, which eventually leads to serious aerodynamic noise.

[0063] According to a first aspect of the present application, with reference to FIGS. 2 and 5, the blade 100 of the present application comprises a blade body 110. The blade body comprises a suction surface 111, a leading edge 113 and a flow passage 115. The flow passage 115 is configured to communicate the leading edge 113 and the suction surface 111 to reduce the impact of the air flow on the leading edge 113.

[0064] Through the above technical solution, by setting the flow passage 115 communicating the leading edge 113 and the suction surface 111, the air flow near the leading edge 113 is guided to the suction surface 111 through the flow passage 115, thereby reducing the impact of the air flow on the leading edge 113 and effectively reducing the aerodynamic noise.

[0065] In some embodiments, with reference to FIGS. 2 and 5, the blade body further comprises a pressure surface 112 and a trailing edge 114.

[0066] The leading edge 113 is connected between the front end of the suction surface 111 and the front end of the pressure surface 112; and the trailing edge 114 is connected between the rear end of the suction surface 111 and the rear end of the pressure surface 112.

[0067] In some embodiments, referring to Figs. 2 and 5, the pressure surface 112 of the blade body 110 of the present application is concave inwardly, while the suction surface 111 is convex outwardly. The leading edge 113 and the trailing edge 114 are arranged between the suction surface 111 and the pressure surface 112.

[0068] In some embodiments, referring to Fig. 5, the through-flow flow path has a through-flow inlet 115a, a through-flow outlet 115b and a through-flow channel 115c.

[0069] In some embodiments, referring to Figs. 2 and 5, the through-flow inlet 115a is arranged at the leading edge 113, and the through-flow outlet 115b is arranged at the suction surface 111; and the through-flow channel 115c connects the through-flow inlet 115a and the through-flow outlet 115b.

[0070] Exemplarily, the through-flow outlet 115b is arranged at a middle section of the suction surface 111.

[0071] In some embodiments, referring to Figs. 2 and 5, the through-flow flow path 115 has an arc-shaped overall profile.

[0072] More specifically, the through-flow flow path 115 extends along a curve, and at least a portion of the through-flow flow path 115 extends to the through-flow outlet 115b at the suction surface 111 along an angle tangent to the suction surface 111, so that the airflow flowing out of the through-flow outlet 115b flows in a direction substantially tangent to the suction surface 111.

[0073] With such a scheme, under the action of the Coanda effect, the high-speed airflow flows along 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 channel, effectively reducing the vortex noise generated in the blade channel, and improving the aerodynamic efficiency of the multi-blade centrifugal fan.

[0074] In some embodiments, referring to Figs. 1 to 5, in the first direction C1 (which can be the axial direction of the impeller) of the blade body 110, the blade body 110 is provided with a plurality of through-flow flow paths 115. The suction surface 111, the pressure surface 112, the leading edge 113 and the trailing edge 114 all have a smooth curve in cross-sectional profile.

[0075] In some embodiments, referring to FIGS. 1-3, 5 and 9, the blade body 110 further comprises a spoiler 120. The spoiler 120 is used to disturb the airflow flowing out of the through-flow flow path 115 to generate vortex. The spoiler 120 is arranged on the suction surface 111 and is arranged adjacent to the through-flow outlet 115b of the through-flow flow path 115 and between the through-flow outlet 115b and the trailing edge 114. The through-flow flow path 115 can provide a better front flow field for the spoiler 120, and the combined noise reduction mode of the through-flow flow path 115 and the spoiler 120 improves the internal airflow flow of the impeller.

[0076] With such a scheme, by arranging the spoiler 120 downstream of the through-flow outlet 115b, the wing tip vortex generated by the spoiler 120 is used to mix the low-energy airflow near the suction surface 111 with the high-energy airflow in the high-speed area of the trailing edge, so as to improve the uneven outlet flow velocity distribution and the local flow velocity too large phenomenon of the impeller, thereby reducing the interference between the impeller and the volute tongue, reducing the strength of the noise source, and finally achieving the weakening of the aerodynamic noise of the centrifugal fan.

[0077] At the same time, the combined noise reduction scheme of the through-flow flow path and the spoiler adopted in the present application still maintains that the blade is an integral whole, avoids introducing complex structural modifications (such as multi-blade combination or blade deformation, etc.), and increases the failure risk of the blade during long-term work, thereby ensuring the reliability of the blade.

[0078] In some embodiments, referring to FIGS. 2, 3, 5 and 9, the overall profile shape of the spoiler 120 is triangular.

[0079] It can be understood that, referring to FIG. 8, the cross-sectional profile obtained by cutting the spoiler 120 along the section indication line A-A is triangular.

[0080] In some embodiments, the spoiler 120 comprises a spoiler surface 121, and the spoiler surface 121 has a first included angle a with the direction of the airflow flowing out of the through-flow flow path 115, and the first included angle a is an acute angle.

[0081] In some embodiments, referring to FIG. 9, the spoiler 120 comprises a flow guide surface 122, and each of the two sides of the spoiler surface 121 is independently provided with a flow guide surface 122. The flow guide surface 122 is arranged to guide the airflow passing through to reduce the impact of the airflow on the spoiler 120.

[0082] In some embodiments, referring to FIG. 9, the flow guide surface 122 has an overall profile shape in the form of an arc.

[0083] In some embodiments, the blade 100 further comprises two spoiler 120. The two spoiler 120 is used to disturb the air flow out of the through-flow flow path 115 to generate vortex; the two spoiler 120 is arranged on the suction surface 111, and is arranged near the through-flow outlet 115b of the through-flow flow path and between the through-flow outlet 115b and the trailing edge 114; the two spoiler 120 is oppositely arranged.

[0084] It can be understood that the spoiler 120 of the present application is generally arranged in pairs.

[0085] In some embodiments, referring to FIG. 2, FIG. 3, FIG. 5 and FIG. 8, the two spoilers 120 are oppositely arranged so that they have a first distance D1 and a second distance D2 therebetween, the first distance D1 is smaller than the second distance D2; the distance between the two spoilers 120 is smaller when it is closer to the through-flow outlet 115b of the through-flow flow path 115.

[0086] It can be understood that the two spoilers 120 arranged in pairs are arranged at a certain angle with each other. The distance between the two spoilers gradually increases in the direction away from the through-flow outlet.

[0087] Specifically, referring to FIG. 2, FIG. 3, FIG. 5 and FIG. 9, the two spoilers 120 are vertically arranged in pairs at the suction surface 111 of the blade body 110 and between the through-flow outlet 115b and the trailing edge 114 at a certain second angle β.

[0088] Here, the second angle β of the spoiler 120 refers to the angle formed by the extension direction of the spoiler surface 121, or the angle formed by the plane perpendicular to the spoiler surface 121.

[0089] The vertical installation of the spoiler 120 refers to that the spoiler 120 is generally perpendicular to the spoiler surface 121, or the generatrix of the spoiler surface 121 of the spoiler 120 is parallel to the generatrix of the blade body 110, or is parallel to the central axis of the multi-wing centrifugal fan.

[0090] After the air flow out of the through-flow outlet, the air flow will be attached to the suction surface due to the Coanda effect, so that the spoiler 120 in front of the air flow has a good incoming flow state, which ensures that the spoiler 120 can play a role.

[0091] In FIG. 9, the key parameters of a set of spoilers 120 such as the second angle β of the spoiler 120, the height H, the width W1 and the length L of the spoiler 120 can be seen.

[0092] Since the flow state in the inter-blade channel of the multi-wing centrifugal fan will change greatly with the change of the working condition, the above key parameters should be determined according to the specific design working condition, size, etc. of the multi-wing centrifugal fan.

[0093] It should be noted that, in order to avoid the large intensity of the disturbance fluid 120, the full filling of the large size wing tip vortex in the flow field in the inter-blade passage leads to the sharp deterioration of the aerodynamic performance and noise level of the fan, and the size of the disturbance fluid 120 should not be too large.

[0094] As a preferred solution, the two pairs of disturbance fluids 120 are symmetrically arranged relative to a pair of symmetry planes, and the vertexes of the second included angle β formed by the two disturbance fluids 120 are on the symmetry planes.

[0095] In some embodiments, as shown in FIGS. 5 and 9, the second included angle β formed by the two disturbance fluids 120 ranges from 10° to 150°; the ratio of the maximum width W2 between the two guide surfaces 122 of the disturbance fluid 120 to the width W1 of the disturbance surface ranges from 2:1 to 4:1; and the ratio of the width W1 of the disturbance surface to the thickness T of the blade body ranges from 0.1 to 0.5.

[0096] The above parameter selection enables the disturbance fluid to generate a wing tip vortex with a strength and size matched with the blade, effectively improving the uneven flow velocity distribution and the excessively large local flow velocity at the outlet of the impeller.

[0097] FIG. 10 shows the flow field between two adjacent blades. As shown in FIG. 10, the flow inlet 115a of the flow passage 115 is arranged at the leading edge 113 of the blade body 110, which can introduce the high-speed airflow near the leading edge 113 into the suction surface 111 through the flow passage 115 while reducing the inflow impact near the leading edge 113. Under the action of the Coanda effect, the airflow flows along the wall surface, increases the energy of the fluid near the suction surface 111 to improve the flow separation, reduces the vortex noise in the inter-blade passage, and provides a better upstream flow field for the rear disturbance member.

[0098] The disturbance fluid 120 is arranged downstream of the flow outlet 115b near the suction surface 111, and the wing tip vortex generated by the disturbance fluid 120 mixes the low-energy airflow near the wall surface of the blade body 110 with the high-energy airflow in the high-speed region of the trailing edge, so as to improve the uneven flow velocity distribution and the excessively large uniform flow velocity at the outlet of the impeller 10 of the centrifugal fan, and further reduce the interference between the impeller 10 and the volute tongue, thereby reducing the strength of the noise source and finally achieving the weakening of the aerodynamic noise of the multi-blade centrifugal fan.

[0099] In some embodiments, as shown in FIGS. 2 and 3, one flow passage 115 corresponds to a plurality of groups of corresponding disturbance fluids 120.

[0100] For example, one flow passage 115 corresponds to a plurality of groups of two corresponding disturbance fluids 120.

[0101] In some embodiments, referring to Fig. 6, the blade 100 further comprises a baffle assembly. The baffle assembly is configured to open or close the through-flow passage 115.

[0102] With such a configuration, the through-flow passage 115 can be opened at high rotation speed to reduce noise, and closed at low rotation speed to improve the work capacity of the impeller 10.

[0103] As a specific configuration, referring to Fig. 6, the baffle assembly comprises a front baffle mechanism, which comprises a front baffle 131 and a front driving structure. The front baffle 131 is arranged at the leading edge 113. The front driving structure is configured to drive the front baffle 131 to open or close the through-flow passage.

[0104] It can be understood that the front baffle 131 is arranged at the through-flow inlet 115a of the through-flow passage 115. The through-flow passage 115 is opened or closed by the movement, such as rotation, of the front baffle 131 relative to the blade body 110.

[0105] Exemplarily, the front driving structure can be a torsion spring. The torsion spring is arranged between the front baffle 131 and the blade body 110. The front baffle 131 is rotationally connected to the blade body 110. The rotation axis is parallel to the first direction C1 of the blade body 110. The front baffle 131 is arranged at the through-flow inlet of the through-flow passage 115, i.e. at the leading edge. When the rotation speed is large enough, the front baffle 131 overcomes the force of the torsion spring under the action of centrifugal force to open the through-flow passage 115. When the rotation speed is small, the torsion spring elastically closes the through-flow inlet 115a.

[0106] As a specific configuration, referring to Fig. 6, the baffle assembly comprises a rear baffle mechanism, which comprises a rear baffle 132 and a rear driving structure. The rear baffle 132 is arranged at the suction surface 111. The rear driving structure is configured to drive the rear baffle 132 to open or close the through-flow passage.

[0107] It can be understood that the rear baffle 132 is arranged at the through-flow outlet 115b of the through-flow passage 115. The through-flow passage 115 is opened or closed by the movement, such as rotation, of the rear baffle 132 relative to the blade body 110.

[0108] As an optional solution, a torsion spring can be arranged between the back plate 132 and the blade body 110, the back plate 132 and the blade body 110 are rotationally connected, the rotation axis is parallel to the first direction C1 of the blade body 110, the back plate 132 is arranged at the through-flow outlet 115b of the through-flow flow path 115, i.e. at the suction surface 111, when the rotation speed is large enough, the back plate 132 overcomes the force of the torsion spring under the action of centrifugal force and thus opens the through-flow flow path 115, when the rotation speed is small, the torsion spring elastically closes the through-flow outlet 115b.

[0109] In some embodiments, referring to FIG. 7, the blade body 110 is further provided with a mixed-flow channel 115d. The mixed-flow channel 115d is configured to communicate the outside space at the pressure surface 112 and the suction surface 111.

[0110] As an optional solution, a mixed-flow channel 115d can be arranged, which extends from the pressure surface 112 to the suction surface 111 to communicate the space outside the pressure surface 112 and the space outside the suction surface 111. That is, the pressure surface 112 and the suction surface 111 near the trailing edge 114 are communicated, which can to some extent 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 area of the trailing edge on the pressure surface side, which can replace or supplement the role of the turbulence generator 120, improve the uneven distribution of flow velocity at the outlet of the impeller 10, and reduce the noise of the multi-blade centrifugal fan.

[0111] According to a second aspect of the present application, referring to FIGS. 1 and 4, an impeller 10 is provided, which includes an impeller cover plate 200 and the above-mentioned blade 100, a plurality of blades 100 are arranged on the two impeller cover plates 200 and are respectively fixedly connected with the two impeller cover plates 200. The impeller 10 has all the beneficial effects of the above-mentioned blade 100, which will not be repeated here.

[0112] As a preferred solution, one of the impeller cover plates 200 can be configured as a motor cover plate.

[0113] Referring to FIGS. 12 and 13, FIG. 12 shows the fluid simulation results of the existing impeller 10, and FIG. 13 shows the fluid simulation results of the impeller 10 of the present application.

[0114] As can be seen from the comparison of FIG. 12 and FIG. 13, the composite noise reduction mode proposed in the present solution can effectively reduce the airflow impact at the leading edge 113, improve the problem of excessive local flow rate at the outlet of the blade passage, and also effectively suppress the flow separation occurring in the blade passage. It needs to be additionally supplemented that according to the simulation results, moving the overflow outlet 115b at the suction surface 111 to the direction of the leading edge 113 can further reduce the flow separation phenomenon at the suction surface 111 of the blade 100, and improve the flow field in the blade passage. That is, the overflow outlet 115b of the overflow flow path 115 should be closer to the leading edge 113 of the blade body 110.

[0115] According to a third aspect of the present application, a centrifugal fan is provided, which includes the above-mentioned impeller 10 and has all the beneficial effects of the above-mentioned impeller 10, which will not be repeated here.

[0116] According to a fourth aspect of the present application, with reference to FIG. 14, a vehicle 1 is provided, which includes the above-mentioned centrifugal fan and has all the beneficial effects of the above-mentioned centrifugal fan, which will not be repeated here.

[0117] The vehicle 1 can be a fuel automobile, a plug-in hybrid electric vehicle, or a new energy vehicle, etc., which is not specifically limited in the present application.

[0118] In the description of the present application, the terms "first" and "second" are only for descriptive purposes, and cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features. Therefore, the features defined as "first" and "second" can explicitly or implicitly include one or more features. In the description of the present application, the meaning of "multiple" is two or more, unless otherwise specifically limited.

[0119] In the above embodiments, the description of each embodiment has its own emphasis, and the parts not described in detail in a certain embodiment can be referred to the related description of other embodiments.

[0120] The embodiments, implementation manners and related technical features of the present application can be combined or replaced with each other without conflict.

[0121] The above is only the preferred embodiments of the present application, and does not limit the present application in any form, but any simple modification, equivalent change and modification made to the above embodiments according to the technical essence of the present application, without departing from the technical solution content of the present application, still belongs to the scope of the technical solution of the present application.

Claims

1. A blade (100), comprising: a blade body (110) comprising a suction surface (111), a leading edge (113), and a through-flow flow path (115); wherein the through-flow flow path (115) is configured to communicate the leading edge (113) and the suction surface (111) to reduce the impact of airflow on the leading edge (113).

2. The vane (100) according to claim 1, wherein the blade body (110) further comprises a pressure surface (112) and a trailing edge (114); wherein the leading edge (113) is connected between a front end of the suction surface (111) and a front end of the pressure surface (112); and the trailing edge (114) is connected between a rear end of the suction surface (111) and a rear end of the pressure surface (112).

3. The vane (100) according to claim 2, wherein the through-flow flow path (115) has: a through-flow inlet (115a) disposed at the leading edge (113); a through-flow outlet (115b) disposed at the suction surface (111); a through-flow channel (115c) communicating the through-flow inlet (115a) and the through-flow outlet (115b).

4. The blade (100) according to any one of claims 1 to 3, wherein In a first direction (C1) of the blade body (110), the blade body (110) is provided with a plurality of through-flow flow paths (115).

5. The blade (100) according to any one of claims 1 to 4, wherein The through-flow flow path (115) has an overall profile shape that is arc-shaped.

6. The vane (100) according to claim 3, wherein The blade (100) further comprises: a spoiler (120) for disturbing the airflow flowing out of the through-flow flow path (115) to generate vortex flow; wherein the spoiler (120) is disposed on the suction surface (111), the spoiler (120) is disposed adjacent to the through-flow outlet (115b) of the through-flow flow path (115) and is located between the through-flow outlet (115b) and the trailing edge (114).

7. The vane (100) according to claim 6, wherein The spoiler (120) has an overall profile shape that is triangular.

8. The vane (100) according to claim 6 or 7, wherein The spoiler (120) comprises a spoiler surface (121), the spoiler surface (121) has a first included angle (a) with the direction of airflow flowing out of the through-flow flow path (115), the first included angle (a) is an acute angle.

9. The vane (100) according to claim 8, wherein The spoiler (120) comprises a flow guide surface (122), each of the two side surfaces of the spoiler surface (121) is independently provided with one flow guide surface (122).

10. The vane (100) according to claim 9, wherein The flow guide surface (122) has an overall profile shape that is arc-shaped.

11. The blade (100) according to any one of claims 6 to 10, wherein The blade (100) further comprises: two spoilers (120) for disturbing the airflow flowing out of the through-flow flow path (115) to generate vortex flow; wherein the two spoilers (120) are disposed on the suction surface (111), the spoiler (120) is disposed adjacent to the through-flow outlet (115b) of the through-flow flow path (115) and is located between the through-flow outlet (115b) and the trailing edge (114). The two spoilers (120) are oppositely disposed.

12. The vane (100) according to claim 11, wherein The two disturbance bodies (120) are oppositely arranged to have a first distance (D1) and a second distance (D2) therebetween, the first distance (D1) being smaller than the second distance (D2); the distance between the two disturbance bodies (120) is closer to the outflow outlet (115b) of the outflow flow path (115) and has a smaller distance value.

13. The vane (100) according to claim 11 or 12, wherein The second included angle (β) between the two disturbance bodies (120) ranges from 10° to 150°.

14. The blade (100) according to claim 9 or 10, wherein The maximum width between the two guide surfaces (122) of the disturbance body (120) is W2, the width of the disturbance surface (121) is W1, and the ratio of W2 to W1 ranges from 2-4:

1.

15. The blade (100) according to any one of claims 6 to 14, wherein One outflow flow path (115) corresponds to multiple groups of multiple disturbance bodies (120) arranged correspondingly.

16. The blade (100) according to any one of claims 2 or 6 to 15, wherein The blade body (110) is further provided with: A mixed flow channel (115d) configured to communicate the pressure surface (112) and the suction surface (111).

17. The blade (100) according to any one of claims 1 to 16, wherein The blade (100) further comprises: A baffle assembly for opening or closing the outflow flow path (115).

18. The vane (100) according to claim 17, wherein The baffle assembly comprises a front baffle mechanism, the front baffle mechanism comprises a front baffle (131) and a front driving structure, the front baffle (131) is arranged on the front edge (113), and the front driving structure is used to drive the front baffle (131) to open or close the outflow flow path (115).

19. The vane (100) according to claim 17 or 18, wherein The baffle assembly comprises a rear baffle mechanism, the rear baffle mechanism comprises a rear baffle (132) and a rear driving structure, the rear baffle (132) is arranged on the suction surface (111), and the rear driving structure is used to drive the rear baffle (132) to open or close the outflow flow path (115).

20. An impeller (10) comprising: A blade (100) according to any one of claims 1 to 19, a plurality of the blades (100) are arranged on the impeller cover plate (200).

21. A centrifugal fan comprising: An impeller (10) according to claim 20.

22. A vehicle (1) comprising a centrifugal fan according to claim 21.

22. A vehicle (1) comprising a centrifugal fan according to claim 21.

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