Fan wheel and centrifugal fan

Abstract

The invention relates to a fan wheel and a centrifugal fan. The fan wheel comprises a hub and a plurality of blades which are formed by outwards diverging and extending from the outer periphery of the hub. And each blade comprises a first section blade, a second section blade and a third section blade. And the first-section blade is connected to the hub. The second-section blade is positioned between the first-section blade and the third-section blade; and the second-section blade is connected with the first-section blade and the third-section blade. Along the outer periphery of the hub outwards, the first section of blade is bent and extends to form a circular arc section, and the third section of blade is bent and extends to form a circular arc section. And the bending directions of the first section blade and the third section blade are opposite. And the circle where the first-section blade is located is not overlapped with the second-section blade. The circle where the third-section leaf is located is not overlapped with the second-section leaf. According to the fan wheel, the wind driving performance can be effectively improved, and the overall performance of the centrifugal fan using the fan wheel is improved.

Description

Technical Field

[0001] The present application relates to a fan wheel and a centrifugal fan. Background Art

[0002] With the development of science and technology, computers are updated and replaced more and more quickly, and the heat generated by computer heat sources is also increasing, which makes the requirements for the cooling fans inside the computer higher and higher.

[0003] Existing heat dissipation devices usually use centrifugal fans, and the blades of existing centrifugal fans are usually made of metal or plastic. However, metal blades are heavy and difficult to shape, while plastic blades are light. In addition, the blades are generally composed of straight blades or curved blades, which makes it difficult to further reduce the noise of the centrifugal fan, further increase the output air volume of the centrifugal fan using the blades, etc., and therefore it is difficult to improve the wind driving performance of the centrifugal fan. Therefore, how to design and optimize a blade to improve the wind driving performance of the centrifugal fan is a difficult problem that plagues the industry. Summary of the invention

[0004] The purpose of the present application is to provide a fan wheel and a centrifugal fan for improving the performance of the heat dissipation fan.

[0005] The technical solutions provided by this application to solve its technical problems are as follows: A fan wheel comprises a hub and a plurality of blades extending outward from the outer periphery of the hub: Each of the blades comprises a first blade section, a second blade section and a third blade section, wherein the first blade section is connected to the hub, the second blade section is located between the first blade section and the third blade section, and the second blade section connects the first blade section and the third blade section; Wherein, along the outer periphery of the hub outward, the first blade section is bent and extended into a circular arc section, and the third blade section is bent and extended into a circular arc section; The bending directions of the first leaf segment and the third leaf segment are opposite; The circle where the first leaf segment is located does not overlap with the circle where the second leaf segment is located; The circle where the third leaf segment is located does not overlap with the circle where the second leaf segment is located.

[0006] Furthermore, the wind entry angle α of the blade is not greater than 90 degrees; The wind entry angle α of the blade is the angle between the direction of the tangent along the inner end of the first blade segment pointing to the outer side of the impeller and the direction opposite to the linear velocity direction of the inner end of the first blade segment when the impeller rotates.

[0007] Furthermore, on any one of the blades, along the rotation direction of the impeller, the inner end A of the first blade segment is located in front of the outer end C of the second blade segment.

[0008] Furthermore, on any one of the blades, along the rotation direction of the impeller, the outer end C of the second blade segment is located in front of the outer end D of the third blade segment.

[0009] Furthermore, the maximum outer diameter of the impeller is defined as OD; The maximum outer diameter of the hub of the fan wheel is defined as D0; The maximum outer diameter of the impeller at the outer end of the first blade segment is defined as D1; The maximum outer diameter of the impeller at the outer end of the second blade segment is defined as D2; Satisfy: D1≧OD*50%; Satisfy: OD*60%≦D2≦OD*90%; Satisfies: D0 <OD*50%。

[0010] Furthermore, the wind outlet angle β of the blade is not less than 75 degrees and not more than 125 degrees; The wind outlet angle β of the blade is the angle between the direction of the tangent along the outer end of the third blade segment pointing to the outer side of the impeller and the direction opposite to the linear velocity direction of the outer end of the third blade segment when the impeller rotates.

[0011] Furthermore, along the outer periphery of the hub outward, the second blade section is in a straight plate shape; A tangent line of the first leaf segment at the outer end portion overlaps with the second leaf segment; A tangent line of the third leaf segment at the inner end portion overlaps with the second leaf segment.

[0012] Furthermore, along the outer periphery of the hub outward, the second blade section is bent and extended into a circular arc segment; The tangent line of the first leaf segment at the outer end portion overlaps with the tangent line of the second leaf segment at the inner end portion; The tangent line of the second leaf segment at the outer end portion overlaps with the tangent line of the third leaf segment at the inner end portion; The bending radius of the second leaf segment is not equal to the bending radius of the first leaf segment; The bending radius of the second leaf segment is not equal to the bending radius of the third leaf segment.

[0013] Furthermore, the bending radius of the second leaf segment is greater than the bending radius of the first leaf segment; The bending radius of the second leaf segment is greater than the bending radius of the third leaf segment.

[0014] Furthermore, the bending radius of the first leaf segment is not equal to the bending radius of the third leaf segment.

[0015] Furthermore, the bending radius of the first leaf segment is smaller than the bending radius of the third leaf segment.

[0016] Furthermore, along the outer periphery of the hub outward, the second blade section bends and extends into a cloud gauge line.

[0017] Furthermore, the thicknesses of the first leaf section, the second leaf section and the third leaf section are the same.

[0018] Furthermore, it also includes a silent ring, which connects a plurality of the third-section leaves as a whole.

[0019] Furthermore, along the outer periphery of the hub outward, at least half of the extension length of the second blade segment is exposed upward to the outside of the air inlet in the up-down direction; Along the outer periphery of the hub outward, at least half of the extension length of the third blade section is not exposed upward to the outside of the air inlet in the up-down direction.

[0020] This application also discloses the following technical solutions: A centrifugal fan, comprising the fan wheel as described in any one of the above items, further comprising: A shell body is formed with a hollow cavity and an air inlet and an air outlet for connecting the cavity with the outside; The fan wheel is rotatably assembled in the cavity of the shell and is located directly below the air inlet; A stator assembly is installed in the cavity of the housing and forms a magnetic induction gap with the impeller; An air flow channel is formed between the outer periphery of the impeller and the inner wall surface of the cavity of the shell.

[0021] The beneficial effects of the present application are as follows: a three-section blade impeller is designed to improve the wind driving performance of the impeller, thereby improving the overall performance of the centrifugal fan. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] The present application will be further described below in conjunction with drawings and embodiments.

[0023] Figure 1 It is a three-dimensional schematic diagram of the centrifugal fan of the present application.

[0024] Figure 2 It is a top view of the centrifugal fan of the present application.

[0025] Figure 3 yes Figure 1 A partial exploded view of the centrifugal fan, showing the three-dimensional schematic diagram when the upper cover is separated.

[0026] Figure 4 It is a top view of the centrifugal fan of the present application, mainly showing the positional relationship between the fan wheel and the air inlet on the upper cover plate.

[0027] Figure 5 yes Figure 4 A magnified view of the structure within the dashed box.

[0028] Figure 6 It is a top view of the first embodiment of the impeller of the present application.

[0029] Figure 7 yes Figure 6 A magnified view of the structure within the dashed box.

[0030] Figure 8 It is a top view of the second embodiment of the impeller of the present application.

[0031] Fig. 9 yes Figure 8 A magnified view of the structure within the dashed box.

[0032] Fig.10 It is a comparison chart of the P / Q performance curves of the centrifugal fan using the fan wheel of the first embodiment of the present application and the centrifugal fan using the traditional fan wheel of two-stage S-shaped blades. DETAILED DESCRIPTION

[0033] In order to make the purpose, technical solution and advantages of this application more clear, the following will be combined with the drawings and specific embodiments to further describe this application in detail. It should be understood that the specific embodiments described here are only used to explain this application and are not used to limit this application.

[0034] Please refer to Figures 1 to 7As shown, it is a schematic diagram of a first embodiment of a fan wheel disclosed in the present application and a schematic diagram of a cooling fan assembled with the fan wheel. Specifically, the cooling fan includes a housing 30, a fan wheel (not numbered) installed in the housing 30, and a stator assembly (not shown). Among them, the housing 30 is formed with a hollow cavity 31 and an air inlet 301 and an air outlet 302 that connect the cavity 31 with the outside. The fan wheel is rotatably assembled in the cavity 31 of the housing 30 and is located directly below the air inlet 301. The fan wheel includes a hub 10 and a plurality of blades 20, and the plurality of blades 20 are formed by extending outward from the outer periphery of the hub 10 and are arranged at intervals along the circumference of the hub 10. The stator assembly is installed in the cavity 31 of the housing 30. In a specific embodiment, the stator assembly is located directly below the hub 10. A magnetic induction gap is formed between the stator assembly and the fan wheel. An air flow channel 303 is formed between the outer periphery of the impeller and the inner wall surface of the cavity 31 of the housing 30. The heat dissipation fan of the present application is preferably a centrifugal heat dissipation fan. When in use, the stator assembly is energized to generate a magnetic field and generate magnetic coupling with the impeller to drive the impeller to rotate. After the impeller rotates, the air is driven to be sucked in through the air inlet 301 and centrifuged through the air channel (unnumbered) formed between adjacent blades 20, and then accelerated in the air flow channel 303 and finally blown out through the air outlet 302 to achieve the function of driving wind and heat dissipation.

[0035] The centrifugal fan of the present application can be used in an electronic device, including but not limited to mobile phones, tablet computers (portable android device, PAD), laptop computers, personal digital assistants (personal digital assistants, PDA), servers, switches, computing devices, vehicle-mounted devices, wearable devices, virtual reality (virtual reality, VR) terminal devices, augmented reality (augmented reality, AR) terminal devices, wireless terminals in industrial control (industrial control), wireless terminals in self driving, wireless terminals in remote medical, wireless terminals in smart grids (smart grid), wireless terminals in transportation safety (transportation safety), wireless terminals in smart cities (smart cities), wireless terminals in smart homes (smart homes), etc.

[0036] Please refer to Figures 3 to 7As shown, in the present application, each blade 20 includes a first blade segment 21, a second blade segment 22 and a third blade segment 23. The first blade segment 21 is connected to the hub 10, the second blade segment 22 is located between the first blade segment 21 and the third blade segment 23, and the second blade segment 22 connects the first blade segment 21 and the third blade segment 23. Preferably, a silent ring 30 is further included, and the silent ring 30 connects a plurality of the third blade segments 23 as a whole.

[0037] Each of the blades 20 is formed with an inlet angle α and an outlet angle β. Specifically, the inlet angle α of the blade 20 is the angle between the direction of the tangent along the inner end of the first segment blade 21 pointing to the outer side of the fan wheel and the opposite direction of the linear velocity direction of the inner end of the first segment blade 21 when the fan wheel rotates. The outlet angle β of the blade 20 is the angle between the direction of the tangent along the outer end of the third segment blade 23 pointing to the outer side of the fan wheel and the opposite direction of the linear velocity direction of the outer end of the third segment blade 23 when the fan wheel rotates. In a preferred embodiment, the inlet angle α of the blade 20 is not greater than 90 degrees. In a preferred embodiment, the outlet angle β of the blade 20 is not less than 75 degrees and not greater than 125 degrees (may include but are not limited to 75 degrees, 76 degrees, 77 degrees...123 degrees, 124 degrees, 125 degrees, etc.).

[0038] Please refer to Figures 5 to 7 As shown, in the present application, preferably, along the outer periphery of the hub 10 outward, the first segment leaf 21 is bent and extended into a circular arc segment. The third segment leaf 23 is bent and extended into a circular arc segment. The second segment leaf 22 is in the shape of a straight plate. Preferably, the bending radius of the first segment leaf 21 is smaller than the bending radius of the third segment leaf 23. The bending directions of the first segment leaf 21 and the third segment leaf 23 are opposite. The tangent of the first segment leaf 21 at the outer end B overlaps with the second segment leaf 22. The tangent of the third segment leaf 23 at the inner end (that is, the outer end B of the first segment leaf 21) overlaps with the second segment leaf 22. Preferably, along the rotation direction of the impeller, the inner end A of the first segment leaf 21 is located in front of the outer end C of the second segment leaf 22. Preferably, along the rotation direction of the impeller, the outer end C of the second segment leaf 22 is located in front of the outer end D of the third segment leaf 23.

[0039] In addition, it should be noted that, in the embodiment of the present application, preferably, the thicknesses of the first blade section 21, the second blade section 22 and the third blade section 23 are the same. In addition, preferably, along the outer periphery of the hub (10) outward, at least half of the area of ​​the extension length of the second blade section 22 along the radial direction of the impeller is exposed upward to the outside of the air inlet 301 in the vertical direction. At least half of the area of ​​the extension length of the third blade section 23 along the radial direction of the impeller is not exposed upward to the outside of the air inlet 301 in the vertical direction.

[0040] Through the attached Figures 1 to 7 The first embodiment of the impeller of the present application shown in the figure designs the blade 20 into a swept structure (understood as the blade 20 extending outward from the inner end A and being located as a whole behind the impeller at the radius of the inner end A along the direction of rotation of the impeller), and forms a three-section structure formed by the first section of the blade 21, the second section of the blade 22 and the third section of the blade 23. It can realize that the blade 20 has a larger wind-driving area. At the same time, during the entire wind-driving action process, the blade 20 can realize that the wind resistance at one end of the rotating shaft close to the hub is small and it is not easy to form vortices, which can make the air flow formed between the two adjacent blades 20 smoother, and can reduce the noise when the impeller rotates and the air flow loss, which is beneficial to increase the air volume, reduce the noise and improve the static pressure when the centrifugal fan is running, and further help to improve the overall performance of the cooling fan.

[0041] Furthermore, in a preferred embodiment, the wind inlet angle α of the blade 20 is not greater than 65 degrees and not less than 25 degrees (may include but are not limited to 25 degrees, 26 degrees, 27 degrees, 28 degrees, 29 degrees... 64 degrees, 65 degrees, etc.). This can increase the layout density of the blades 20 at the periphery of the hub 10, while ensuring the effective width of the flow channel between two adjacent blades 20 at the first segment 21; in other words, a better balance can be achieved between the layout density of the blades 20 and the effective width of the flow channel between two adjacent blades 20 at the first segment 21. This helps to improve the wind inlet effect of the impeller at the first segment 21 and reduce noise.

[0042] Furthermore, in the embodiment of the present application, by setting the second blade 22 (in some examples: compared with the first blade 21 and the third blade 23, the second blade 22 has the smallest curvature and the largest inclination (compared with the radius direction of the corresponding position)), the blade 20 has a longer centrifugal acceleration distance for the inhaled air at the second blade 22 position, has a better centrifugal acceleration effect, and has a positive effect on the increase of air volume and static pressure value. At the same time, the relatively flat second blade 22 is also conducive to reducing wind resistance, is not easy to form vortices, and has a positive effect on noise reduction.

[0043] Furthermore, in the embodiment of the present application, by providing the third blade 23, it is possible to guide the air accelerated by the second blade 22 so that the air tends to be blown out along the diameter direction of the impeller, and the air driven by the impeller and flowing out from the air outlet 302 has better aggregation (stronger consistency), thereby improving the overall performance of the centrifugal fan.

[0044] In a preferred embodiment, the maximum outer diameter of the fan wheel is defined as OD. The maximum outer diameter of the hub 10 of the fan wheel is defined as D0. The maximum outer diameter of the fan wheel at the outer end of the first-stage blade 21 is defined as D1. The maximum outer diameter of the fan wheel at the outer end of the second-stage blade 22 is defined as D2. Preferably, it satisfies: D1 > 50% * OD. It satisfies: 60% * OD < D2 < 90% * OD. It satisfies: D0 < 50% * OD. By optimizing the length ratios of the respective segments (the first-stage blade 21, the second-stage blade 22, and the third-stage blade 23) of the blade 20. In this way, the air volume and static pressure value can be further improved and the noise can be effectively reduced.

[0045] The following is a performance comparison (P / Q characteristic curve trend diagram) of a centrifugal fan with the fan wheel designed in this application and a centrifugal fan with an old fan wheel through actual measurement of samples. Among them, the old fan wheel adopts an S-shaped two-stage blade structure (such as the fan wheel shown in the prior art patent CN216407281U), and the P-Q characteristic curve trend diagram measured under the same test conditions. Where the abscissa Q represents the air volume (unit: CFM), and the ordinate P represents the static pressure value (unit: mm-Aq). It can be seen that compared with the old fan wheel, the air volume and static pressure of the fan wheel in this application have been significantly improved. In addition, through actual measurement of samples, under the condition of the same noise requirement, the rotational speed of the fan wheel designed in this application has also been significantly improved compared with the old fan wheel (not shown). It can be seen that the overall performance of the fan wheel with the three-stage blade 20 designed in this application is superior to the traditional old fan wheel.

[0046] Please refer to Figure 8 and Fig. 9 As shown, the second embodiment of the fan wheel disclosed in this application, the difference from the first embodiment shown in Figures 1 to 7 is only in the structure of the second-stage blade 22. In the second embodiment, the second-stage blade 22 is bent and extended into an arc segment, and the tangent of the first-stage blade 21 at the outer end B overlaps with the tangent of the second-stage blade 22 at the inner end (which is actually the outer end B of the first-stage blade 21). The tangent of the second-stage blade 22 at the outer end C overlaps with the tangent of the third-stage blade 23 at the inner end (which is actually the outer end C of the second-stage blade 22). Preferably, the bending radius of the second-stage blade 22 is not equal to the bending radius of the first-stage blade 21, and the bending radius of the second-stage blade 22 is not equal to the bending radius of the third-stage blade 23. Preferably, the bending radius of the second-stage blade 21 is greater than the bending radius of the first-stage blade 21, and the bending radius of the second-stage blade 21 is greater than the bending radius of the third-stage blade 23.

[0047] In addition, the fan wheel disclosed in this application can also have a third embodiment (not shown), which is different from Figures 1 to 7The difference between the first embodiment shown in FIG. 1 and FIG. 2 is only the structure of the second leaf segment 22. In the third embodiment, the second leaf segment 22 is bent and extended to form a cloud gauge line, and the cloud gauge line needs to meet the following requirements: The tangent line of the first leaf segment 21 at the outer end B overlaps with the tangent line of the second leaf segment 22 at the inner end (actually, the outer end B of the first leaf segment 21); The tangent line of the second leaf segment 22 at the outer end C overlaps with the tangent line of the third leaf segment 23 at the inner end (actually, the outer end C of the second leaf segment 22); The second leaf section 22 is bent from the inner end portion to the outer end portion C to form a curve with a continuously changing curvature.

[0048] Among them, the impellers of the above-mentioned second and third embodiments disclosed in the present application were also tested for samples, and the conclusions were similar to those of the first embodiment. Compared with the above-mentioned old impellers, the performance of the above-mentioned three embodiments of the present application are improved.

[0049] It is obvious to those skilled in the art that the present application is not limited to the details of the above exemplary embodiments, and that the present application can be implemented in other specific forms without departing from the spirit or essential features of the present application. Therefore, no matter from which point of view, the embodiments should be regarded as exemplary and non-restrictive, and the scope of the present application is defined by the appended claims rather than the above description, and it is intended that all changes falling within the meaning and scope of the equivalent elements of the claims are included in the present application.

[0050] In addition, it should be understood that although the present specification is described according to embodiments, not every embodiment contains only one independent technical solution. This narrative method of the specification is only for the sake of clarity. Those skilled in the art should regard the specification as a whole. The technical solutions in each embodiment may also be appropriately combined to form other implementation methods that those skilled in the art can understand.

Claims

1. A fan wheel, comprising a hub (10) and a plurality of blades (20) extending outward from the outer periphery of the hub (10), characterized in that: Each blade (20) comprises a first blade section (21), a second blade section (22) and a third blade section (23), wherein the first blade section (21) is connected to the hub (10), the second blade section (22) is located between the first blade section (21) and the third blade section (23), and the second blade section (22) connects the first blade section (21) and the third blade section (23); Wherein, along the outer periphery of the hub (10) outwards, the first blade section (21) is bent and extended into a circular arc section, and the third blade section (23) is bent and extended into a circular arc section; The bending directions of the first leaf segment (21) and the third leaf segment (23) are opposite; The circle where the first leaf segment (21) is located does not overlap with the circle where the second leaf segment (22) is located; The circle where the third leaf segment (23) is located does not overlap with the circle where the second leaf segment (22) is located.

2. The impeller according to claim 1, characterized in that: The wind entry angle α of the blade (20) is no greater than 90 degrees; The wind entry angle α of the blade (20) is the angle between a direction along a tangent line of the inner end of the first blade segment (21) pointing to the outer side of the impeller and a direction opposite to a linear velocity direction of the inner end of the first blade segment (21) when the impeller rotates.

3. The impeller according to claim 1, characterized in that: On any one of the blades (20), along the rotation direction of the impeller, the inner end A of the first blade section (21) is located in front of the outer end C of the second blade section (22).

4. The impeller according to claim 3, characterized in that: On any one of the blades (20), along the rotation direction of the impeller, the outer end C of the second blade section (22) is located in front of the outer end D of the third blade section (23).

5. The impeller according to claim 1, characterized in that: The maximum outer diameter of the impeller is defined as OD; The maximum outer diameter of the hub (10) of the fan wheel is defined as D0; The maximum outer diameter of the impeller at the outer end of the first blade segment (21) is defined as D1; The maximum outer diameter of the impeller at the outer end of the second blade section (22) is defined as D2; Satisfy: D1≧OD*50%; Satisfy: OD*60%≦D2≦OD*90%; Satisfies: D0 <OD*50%。 6. The impeller according to claim 1, characterized in that: The wind outlet angle β of the blade (20) is not less than 75 degrees and not more than 125 degrees; The outlet angle β of the blade (20) is the angle between the direction of the tangent along the outer end of the third blade (23) pointing to the outer side of the impeller and the direction opposite to the linear velocity direction of the outer end of the third blade (23) when the impeller rotates.

7. The impeller according to any one of claims 1 to 6, characterized in that: Along the outer periphery of the hub (10) outwards, the second blade section (22) is in a straight plate shape; A tangent line of the first leaf segment (21) at an outer end portion overlaps with the second leaf segment (22); The tangent line of the third leaf segment (23) at the inner end portion overlaps with the second leaf segment (22).

8. The impeller according to any one of claims 1 to 6, characterized in that: Along the outer periphery of the hub (10) outwards, the second blade section (22) is bent and extended into a circular arc section; The tangent line of the first leaf segment (21) at the outer end portion overlaps with the tangent line of the second leaf segment (22) at the inner end portion; The tangent line of the second leaf segment (22) at the outer end portion overlaps with the tangent line of the third leaf segment (23) at the inner end portion; The bending radius of the second leaf segment (22) is not equal to the bending radius of the first leaf segment (21); The bending radius of the second leaf segment (22) is not equal to the bending radius of the third leaf segment (23).

9. The impeller according to claim 8, characterized in that: The bending radius of the second leaf segment (22) is greater than the bending radius of the first leaf segment (21); The bending radius of the second leaf segment (22) is greater than the bending radius of the third leaf segment (23).

10. The impeller according to claim 1, characterized in that: The bending radius of the first leaf segment (21) is not equal to the bending radius of the third leaf segment (23).

11. The impeller according to claim 10, characterized in that: The bending radius of the first leaf segment (21) is smaller than the bending radius of the third leaf segment (23).

12. The impeller according to claim 10 or 11, characterized in that: Along the outer periphery of the hub (10) outwards, the second blade section (22) bends and extends to form a cloud gauge line.

13. The impeller according to any one of claims 1 to 6, characterized in that: The first leaf section (21), the second leaf section (22) and the third leaf section (23) have the same thickness.

14. The impeller according to any one of claims 1 to 6, characterized in that: Also includes: A silent ring (30), wherein the silent ring (30) integrally connects a plurality of the third segment leaves (23).

15. The impeller according to any one of claims 1 to 6, characterized in that: Along the outer periphery of the hub (10) outwards, at least half of the extension length of the second blade (22) is exposed upwards to the outside of the air inlet (301) in the up-down direction; Along the outer periphery of the hub (10) outwards, at least half of the extension length of the third blade section (23) is not exposed upwards to the outside of the air inlet (301) in the up-down direction.

16. A centrifugal fan, comprising the impeller according to any one of claims 1 to 15, characterized in that: Also includes: A shell (30) is formed with a hollow cavity (31) and an air inlet (301) and an air outlet (302) for connecting the cavity (31) with the outside; The impeller is rotatably assembled in the cavity (31) of the housing (30) and is located directly below the air inlet (301); A stator assembly is installed in the cavity (31) of the housing (30) and forms a magnetic induction gap with the impeller; An air flow channel (303) is formed between the outer periphery of the impeller and the inner wall surface of the cavity (31) of the housing (30).

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