Fan assembly

Abstract

Disclosed in the present application is a fan assembly, comprising: a fan housing; an assembly base arranged in the fan housing and connected to the fan housing by means of a plurality of stationary blades; an electric motor assembly assembled in the fan housing and connected to the assembly base; and a fan impeller connected to the electric motor assembly, wherein the end of each of the plurality of stationary blades facing the fan impeller is formed with flow-guiding serrations; or the assembly base is provided with a hollow tube, the electric motor assembly is connected to the hollow tube, a first bearing and a support member are provided in the hollow tube, one end of a rotating shaft of the electric motor assembly is sequentially inserted through and extended out of the support member and the first bearing, the other end of the rotating shaft extends out of the hollow tube, the fan impeller is connected to the end of the rotating shaft extending out of the hollow tube, and a first elastic member is compressed between the first bearing and the support member.

Description

Fan assembly

[0001] This application claims priority to Chinese Patent Applications Nos. 202411197336.1, 202422149432.0, 202422310550.5, 202422308137.5, 202422315345.8, 2024225079473, 202422511278.7, and 2024114542220, the entire contents of which are incorporated herein by reference. Technical Field

[0002] This application relates to the field of fans, and more particularly to a fan assembly. Background Technology

[0003] In the hot summer, fans have become an essential item for people to relieve the heat. With people's demand for convenient use, lighter and more portable fans are becoming increasingly popular.

[0004] In existing technology, a fan contains a fan motor and fan blades. The fan motor is fixed inside the fan housing and is connected to the fan blades via a shaft. The rotation of the fan blades drives airflow; however, the airflow is not straight forward but rotates under the push of the fan blades. To reduce the potential energy of the airflow's rotation and improve its directional movement, stationary blades are placed in front of the fan blades to physically eliminate the rotational potential energy of the airflow.

[0005] Application content

[0006] This application provides a fan assembly, including:

[0007] Fan housing; mounting base, the mounting base being disposed within the fan housing and connected to the fan housing via multiple stationary blades; motor assembly, the motor assembly being mounted within the fan housing and connected to the mounting base;

[0008] Fan blades, the fan blades being connected to the motor assembly; the ends of the plurality of stationary blades facing the fan blades having guide serrations; or...

[0009] The mounting base is provided with a hollow tube, and the motor assembly is connected to the hollow tube. A first bearing and a support member are disposed inside the hollow tube. One end of the motor assembly's shaft is inserted into and exits the support member and the first bearing in sequence, and the other end of the shaft extends out of the hollow tube. The fan blade is connected to the end of the shaft extending out of the hollow tube. A first elastic member is compressed and disposed between the first bearing and the support member. One end of the first elastic member is connected to the support member, and the other end of the first elastic member is connected to the first inner ring or the first outer ring of the first bearing; or...

[0010] A fan blade is connected to the motor assembly; one end of the motor assembly is inserted into the mounting base; there is an air inlet gap between the fan blade and the mounting base; there is a first assembly gap between the motor assembly and the mounting base; a first air outlet is provided on the mounting base; the air inlet gap, the first assembly gap, and the first air outlet form a first heat dissipation path; or...

[0011] The fan blades, with the other end of the motor assembly inserted into and connected to the fan blades; or...

[0012] A sleeve, which is fitted onto the fan housing; shock-absorbing protrusions, which are distributed on the surface and / or at both ends of the sleeve; a first interference zone, which is distributed on the surface and / or at both ends of the sleeve, having a thickness difference between the first interference zone and its surrounding environment, and located on the circumferential path of the sleeve and / or the shock-absorbing protrusions, for blocking the circumferential extension trend of the sleeve and / or the shock-absorbing protrusions. Attached Figure Description

[0013] The above and / or additional aspects and advantages of this application will become apparent and readily understood from the following description of the embodiments taken in conjunction with the accompanying drawings, wherein:

[0014] Figure 1 is a schematic diagram of the overall structure of a fan assembly according to a specific embodiment 1 of this application;

[0015] Figure 2 is a cross-sectional view of a fan assembly according to a specific embodiment 1 of this application;

[0016] Figure 3 is a schematic diagram of the structure of a fan housing according to a specific embodiment 1 of this application;

[0017] Figure 4 is an exploded structural diagram of a fan assembly according to a specific embodiment 1 of this application;

[0018] Figure 5 is a schematic diagram of the overall structure of the fan assembly in a specific embodiment 2 of this application;

[0019] Figure 6 is a structural schematic diagram of the fan housing from a first perspective of a specific embodiment 2 of this application;

[0020] Figure 7 is an exploded structural diagram of a fan assembly according to a specific embodiment 2 of this application;

[0021] Figure 8 is a schematic diagram of the overall structure of the fan assembly in a specific embodiment 3 of this application;

[0022] Figure 9 is a cross-sectional schematic diagram of a fan assembly according to a specific embodiment 3 of this application;

[0023] Figure 10 is a structural schematic diagram of the fan housing from a first perspective of a specific embodiment 3 of this application;

[0024] Figure 11 is an exploded structural diagram of a fan assembly according to a specific embodiment 3 of this application;

[0025] Figure 12 is a three-dimensional structural diagram of the support member according to a specific embodiment 3 of this application;

[0026] Figure 13 is a cross-sectional view of the support member according to a specific embodiment 3 of this application;

[0027] Figure 14 is a schematic diagram of the overall structure of the fan assembly in a specific embodiment 4 of this application;

[0028] Figure 15 is a cross-sectional schematic diagram of a fan assembly according to a specific embodiment 4 of this application;

[0029] Figure 16 is a schematic diagram of the fan housing structure of a specific embodiment 4 of this application;

[0030] Figure 17 is an exploded view of a fan assembly according to a specific embodiment 4 of this application;

[0031] Figure 18 is a schematic diagram of the airflow path of the first heat dissipation passage in a specific embodiment 4 of this application;

[0032] Figure 19 is a schematic diagram of the airflow path of the second heat dissipation passage in a specific embodiment 4 of this application;

[0033] Figure 20 is a cross-sectional view and clearance indication schematic diagram of a fan assembly according to a specific embodiment 4 of this application;

[0034] Figure 21 is a schematic diagram of the structure of the motor housing in a specific embodiment 4 of this application;

[0035] Figure 22 is a schematic diagram of the coil structure and gap indicator of a specific embodiment 4 of this application;

[0036] Figure 23 is a schematic diagram of the overall structure of a fan assembly according to a specific embodiment 5 of this application;

[0037] Figure 24 is a cross-sectional schematic diagram of a fan assembly according to a specific embodiment 5 of this application;

[0038] Figure 25 is an exploded view of a fan assembly according to a specific embodiment 5 of this application;

[0039] Figure 26 is a schematic diagram of the structure of a motor housing according to a specific embodiment 5 of this application;

[0040] Figure 27 is a schematic diagram of the overall structure of a fan assembly according to a specific embodiment 6 of this application;

[0041] Figure 28 is a cross-sectional schematic diagram of a fan assembly according to a specific embodiment 6 of this application;

[0042] Figure 29 is an exploded view of a fan assembly according to a specific embodiment 6 of this application;

[0043] Figure 30 is a schematic diagram of the structure of a fan housing according to a specific embodiment 6 of this application;

[0044] Figure 31 is a schematic diagram of the airflow path of the first heat dissipation passage in a specific embodiment 6 of this application;

[0045] Figure 32 is a schematic diagram of the airflow path of the second heat dissipation passage in a specific embodiment 6 of this application;

[0046] Figure 33 is a schematic diagram of the support structure of a specific embodiment 6 of this application;

[0047] Figure 34 is a cross-sectional schematic diagram of a support member according to a specific embodiment 6 of this application;

[0048] Figure 35 is a schematic diagram of the structure of a motor housing according to a specific embodiment 6 of this application;

[0049] Figure 36 is a schematic diagram of the coil structure and gap indicator of a specific embodiment 6 of this application;

[0050] Figure 37 is a cross-sectional view and clearance indication schematic diagram of a fan assembly according to a specific embodiment 6 of this application;

[0051] Figure 38 is a schematic diagram of the hollow tube structure of a specific embodiment 6 of this application;

[0052] Figure 39 is a first-view structural schematic diagram of the shock-absorbing sleeve of a specific embodiment 7 of this application;

[0053] Figure 40 is a second-view structural schematic diagram of the shock-absorbing sleeve of a specific embodiment 7 of this application;

[0054] Figure 41 is a third-view structural schematic diagram of the shock-absorbing sleeve of a specific embodiment 7 of this application;

[0055] Figure 42 is a fourth-view structural schematic diagram of the shock-absorbing sleeve of a specific embodiment 7 of this application;

[0056] Figure 43 is a cross-sectional view of the shock-absorbing sleeve AA surface of a specific embodiment 7 of this application. Detailed Implementation

[0057] To facilitate understanding of this application, a more detailed description is provided below with reference to the accompanying drawings and specific embodiments. It should be noted that when an element is described as "fixed to" another element, it can be directly on the other element, or one or more intermediate elements may exist between them. When an element is described as "connected to" another element, it can be directly connected to the other element, or one or more intermediate elements may exist between them. The terms "vertical," "horizontal," "left," "right," and similar expressions used in this specification are for illustrative purposes only.

[0058] Unless otherwise defined, all technical and scientific terms used in this specification have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of this application. The term "and / or" as used in this specification includes any and all combinations of one or more of the associated listed items.

[0059] Example 1

[0060] Please refer to Figures 1 and 2. Figure 1 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 2 is a schematic diagram of the exploded structure of the fan assembly in this embodiment.

[0061] Please refer to Figures 1 and 2. Figure 1 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 2 is a schematic diagram of the exploded structure of the fan assembly in this embodiment.

[0062] As shown in Figures 1 and 2, a fan assembly includes: a fan housing 1, a motor assembly 3, a mounting base 2, and fan blades 4. The motor assembly 3 is assembled inside the fan housing 1; the mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11, and the motor assembly 3 is connected to the mounting base 2; the fan blades 4 are connected to the motor assembly 3; the ends of the multiple stationary blades 11 facing the fan blades 4 have guide serrations 111.

[0063] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0064] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0065] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0066] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor. Structurally, the motor assembly 3 can be (but is not limited to): an internal rotor motor or an external rotor motor.

[0067] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0068] The guide sawtooth 111 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide sawtooth 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0069] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out from the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0070] In some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0071] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0072] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0073] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0074] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0075] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0076] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0077] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0078] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0079] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0080] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0081] In some embodiments, the tooth marks of the guide serration 111 are aligned with the inclination direction of the tooth marks of the trailing edge serration 421.

[0082] When the inclination direction of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 is consistent, the guide sawtooth 111 and the trailing sawtooth 421 can perform secondary dispersion and decomposition on the airflow with the same flow direction, making the vortex decomposition effect of the inclination direction more obvious.

[0083] In some embodiments, the tooth marks of the guide serration 111 are tilted in the opposite direction to the tooth marks of the trailing edge serration 421.

[0084] When the inclination directions of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 are opposite, the guide sawtooth 111 and the trailing sawtooth 421 can break down the vortices that their inclination directions point to, so that the vortex area broken down by the guide sawtooth 111 and the trailing sawtooth 421 is wider.

[0085] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the direction of the fan housing 1, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the direction of the fan housing 1.

[0086] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The tooth marks of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Similarly, the tooth marks of the trailing edge serrations 421 are also inclined towards the fan housing 1, again aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, further enhancing their efficiency in dispersing and decomposing the airflow. Furthermore, since both tooth marks are inclined in the same direction as the airflow, the wind resistance of the guide serrations 111 and trailing edge serrations 421 is reduced, improving the airflow efficiency. The tooth marks of the guide sawtooth 111 and the trailing edge sawtooth 421 are both inclined toward the fan housing 1, which can further disperse and decompose the airflow with the same flow direction, making the vortex decomposition effect in the inclined direction more obvious.

[0087] In some embodiments, the tooth marks of the guide serration 111 are inclined toward the fan housing 1, and the tooth marks of the trailing edge serration 421 are inclined toward the mounting base 2.

[0088] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The serrations of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the serrations and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Meanwhile, the serrations of the trailing edge serrations 421 are inclined towards the mounting base 2, opposite to the airflow direction. This reverse-direction arrangement allows for multiple decompositions of the laterally moving airflow, resulting in more thorough dispersal of vortices. Furthermore, both the guide serrations 111 and 421 can disperse and decompose vortices in their respective inclination directions, expanding the vortex area dispersed by the guide serrations 111 and 421.

[0089] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the mounting base 2, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the fan housing 1. The guide saw teeth 111 and the trailing edge saw teeth 421 can break down and decompose the vortices in their respective inclined directions, so that the vortex areas broken down and decomposed by the guide saw teeth 111 and the trailing edge saw teeth 421 are larger.

[0090] In some embodiments, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 are both inclined toward the mounting base 2.

[0091] In some embodiments, the tooth marks of the guide serration 111 correspond to and engage with the tooth marks of the trailing edge serration 421.

[0092] In this embodiment, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 correspond to each other, meaning that the tooth marks of the trailing edge saw teeth 421 are provided at the position where the extension line of the tooth marks of the guide saw teeth 111 intersects with the position of the trailing edge saw teeth 421; conversely, the tooth marks of the guide saw teeth 111 are provided at the position where the extension line of the tooth marks of the trailing edge saw teeth 421 intersects with the position of the guide saw teeth 111.

[0093] The serrations of the guide serration 111 and the trailing edge serration 421 correspond and cooperate with each other, and the serrations of the trailing edge serration 421 have the function of dividing the airflow. The divided airflow will reconverge at the guide serration 111, and the converged airflow will be dispersed and divided again by the serrations of the guide serration 111, preventing the vortex from reconverging and improving the vortex division effect.

[0094] In some embodiments, the tooth marks of the guide serration 111 and the tooth marks of the trailing edge serration 421 are misaligned and matched.

[0095] In this embodiment, the misalignment of the tooth marks of the guide sawtooth 111 and the tooth marks of the trailing sawtooth 421 means that: a notch of the trailing sawtooth 421 is provided at the position where the extension line of the tooth mark of the guide sawtooth 111 intersects with the trailing sawtooth 421; conversely, a notch of the guide sawtooth 111 is provided at the position where the extension line of the tooth mark of the trailing sawtooth 421 intersects with the guide sawtooth 111.

[0096] The tooth marks of the guide sawtooth 111 and the tooth marks of the trailing edge sawtooth 421 are staggered and matched. Both the tooth marks of the trailing edge sawtooth 421 and the tooth marks of the guide sawtooth 111 have the function of dividing the airflow. The two are staggered and can separate the vortices at different positions, increase the vortex division area, and further reduce aerodynamic noise.

[0097] In some embodiments, the length ratio of the stationary blade 11 to the moving blade 42 is 1.1-2.8. The length of the stationary blade 11 refers to the length between the end of the stationary blade 11 with the guide serrations 111 and the opposite end. The length of the moving blade 42 refers to the length between the end of the moving blade 42 with the trailing edge serrations 421 and the opposite end.

[0098] At the aforementioned length ratio, the length of the stationary blade 11 is greater than the length of the moving blade 42. When the fan blade 4 rotates, the moving blade 42 restrains and guides the airflow. If the moving blade 42 is too long, the rotational potential energy of the airflow will be too high. The main function of the stationary blade 11 is to counteract and convert the rotational potential energy of the airflow, causing it to move horizontally in a directional direction along the stationary blade 11. If the length of the stationary blade 11 is too short, the rotational potential energy of the airflow exiting the fan assembly will be too high, resulting in poor directional movement capability and a short directional air delivery distance.

[0099] Setting the length ratio of the stationary blade 11 to the moving blade 42 between 1.1 and 2.8 allows the rotational potential energy of the airflow exiting the fan blade 4 to be fully canceled and converted when passing through the moving blade 42, improving the overall airflow efficiency and directional air delivery capability of the fan assembly. Simultaneously, the airflow is blown out from the fan blade 4, guided by the stationary blade 11, and then blown out. During this process, due to the mounting base 2, the airflow space is compressed, resulting in a pressurized and accelerated airflow process. The relatively large length of the stationary blade 11 corresponds to the path length required for acceleration, thus improving the airflow acceleration efficiency.

[0100] When the ratio of the two is less than 1.1, the rotational potential energy of the airflow blown out by the fan assembly is too large, the diffusion surface of the airflow after it is blown out is too large, and the directional air delivery capability decreases. When the ratio of the two is greater than 2.8, the energy loss of the fan assembly within the fan housing 1 is too large, the initial kinetic energy of the airflow at the air outlet of the fan assembly decreases, which also reduces the directional air delivery capability of the fan assembly.

[0101] In some embodiments, the ratio of the number of stationary blades 11 to the number of moving blades 42 is 0.5-1.

[0102] When the ratio of stationary blades 11 to moving blades 42 is within a certain range, it can increase the airflow and air pressure of the fan assembly, resulting in a higher airflow speed. When the ratio of stationary blades 11 to moving blades 42 is less than 0.5, the number of stationary blades 11 is too small, and the stationary blades 11 are not sufficient to offset and convert the rotational potential energy of the airflow, reducing the directional airflow capability of the fan assembly. When the ratio of stationary blades 11 to moving blades 42 is greater than 1, the number of stationary blades 11 is too large, increasing the airflow resistance and reducing the airflow conversion efficiency.

[0103] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0104] A fan assembly includes: a fan housing 1, a mounting base 2, and a motor assembly 3. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11. The motor assembly 3 is assembled inside the fan housing 1. The mounting base 2 is provided with a hollow tube 23, and the motor assembly 3 is connected to the hollow tube 23. A first bearing 33 and a support member 35 are disposed inside the hollow tube 23. One end of the rotating shaft 313 of the motor assembly 3 is inserted into and passes through the support member 35 and the first bearing 33 in sequence, and the other end of the rotating shaft 313 extends out of the hollow tube 23. Fan blades 4 are connected to the end of the rotating shaft 313 that extends out of the hollow tube 23. A first elastic member 34 is compressed and disposed between the first bearing 33 and the support member 35. One end of the first elastic member 34 is connected to the support member 35, and the other end of the first elastic member 34 is connected to the first inner ring or the first outer ring of the first bearing 33.

[0105] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0106] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0107] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0108] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0109] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0110] In some embodiments, the mounting base 2 includes only a hollow tube 23. One end of a plurality of stationary blades 11 is wrapped around the hollow tube 23, and the other end of the plurality of stationary blades 11 is radially distributed and connected to the fan housing 1.

[0111] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0112] In some embodiments, the mounting base 2 includes a connecting ring 22 and a hollow tube 23. The connecting ring 22 is connected to the fan housing 1 through a plurality of stationary blades 11, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0113] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0114] In this embodiment, the first elastic element 34 is (but is not limited to): a helical spring and a rubber spring. The material and structure of the first elastic element 34 can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0115] The first elastic element 34 is sleeved on the rotating shaft 313. However, the arrangement of the first elastic element 34 is not limited to this. Depending on the specific application scenario, in some embodiments, multiple first elastic elements 34 are provided, and multiple first elastic elements 34 are arranged around the rotating shaft 313 and are respectively connected to the support member 35 and the first bearing 33.

[0116] In this embodiment, the first bearing 33 is disposed at the first hollow end of the hollow tube 23. However, the placement of the first bearing 33 is not limited to this. In some embodiments, the first bearing 33 is disposed at the second hollow end of the hollow tube 23.

[0117] In this embodiment, the connection method between the first elastic member 34 and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0118] In this embodiment, the connection method between the first elastic element 34 and the first bearing 33 includes (but is not limited to): abutment, welding or adhesive connection.

[0119] In the above embodiment, the first elastic element 34 is disposed between the support 35 and the first bearing 33, with one end of the elastic element connected to the support 35 and the other end connected to the first inner ring or the first outer ring of the first bearing 33. The first elastic element 34 is compressed between the first bearing 33 and the support 35, so that the first inner ring or the first outer ring of the first bearing 33 is always subjected to elastic force. After the first inner ring or the first outer ring is subjected to force, the first bearing 33 is always in a state of bridging the axial gap between the first inner ring and the first outer ring, that is, the balls between the first inner ring and the first outer ring are always clamped, and the axial gap between the first inner ring and the first outer ring is minimized. In the above state, the problem of vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates can be reduced, the vibration frequency of the fan blade 4 is greatly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. At the same time, the wear of the first bearing 33 can also be reduced, and the service life of the first bearing 33 can be extended.

[0120] In some embodiments, the fan assembly further includes: a second bearing 36, a first bearing 33 and a second bearing 36 respectively disposed at both ends of the hollow tube 23, a support member 35 disposed between the first bearing 33 and the second bearing 36, and one end of the rotating shaft 313 sequentially inserted into and through the second bearing 36, the support member 35 and the first bearing 33.

[0121] The arrangement of the first bearing 33 and the second bearing 36 enables the rotating shaft 313 to rotate more smoothly. At the same time, the arrangement of two rotating shafts 313 makes the linear rotation of the rotating shaft 313 more stable, enabling the fan motor to rotate at a faster speed.

[0122] In some embodiments, the first support end of the support member 35 abuts against the second inner ring or the second outer ring of the second bearing 36, and the second support end of the support member 35 is connected to the first elastic member 34.

[0123] To prevent axial displacement between the inner and outer rings of the second bearing 36, the first support end of the support member 35 abuts against the second inner or outer ring of the second bearing 36. The abutment of the second outer or inner ring of the second bearing 36 by the support member 35 ensures that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the second inner and outer rings, meaning the balls between them are always tightly clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it also reduces wear on the second bearing 36 and extends its service life.

[0124] In some embodiments, a second elastic member is compressed between the support member 35 and the second bearing 36. One end of the second elastic member is connected to the first support end of the support member 35, and the other end of the second elastic member is connected to the second inner ring and the second outer ring of the second bearing 36.

[0125] In this embodiment, the second elastic element is (but is not limited to): a helical spring and a rubber spring. The material and structure of the second elastic element can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0126] The second elastic element is sleeved on the rotating shaft 313. However, the arrangement of the second elastic element is not limited to this. Depending on the specific application scenario, in some embodiments, multiple second elastic elements are provided, which are arranged around the rotating shaft 313 and respectively connected to the support member 35 and the second bearing 36.

[0127] In this embodiment, the second bearing 36 is disposed at the second hollow end of the hollow tube 23. However, the placement of the second bearing 36 is not limited to this. In some embodiments, the second bearing 36 is disposed at the first hollow end of the hollow tube 23.

[0128] To prevent axial displacement between the inner and outer rings of the second bearing 36, a second elastic element is provided between the support member 35 and the second bearing 36. One end of the second elastic element is connected to the second support end of the support member 35, and the other end is connected to the second inner or outer ring of the second bearing 36. The second elastic element, when compressed, connects the second outer or inner ring of the second bearing 36, ensuring that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the inner and outer rings, meaning the balls between them are always tightly clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it also reduces wear on the second bearing 36 and extends its service life.

[0129] In this embodiment, the connection method between the second elastic member and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0130] In this embodiment, the connection method between the second elastic element and the second bearing 36 includes (but is not limited to): abutment, welding or adhesive connection.

[0131] In some embodiments, the support member 35 is interference-fitted with the hollow tube 23. The relative position between the support member 35 and the hollow tube 23 is fixed, keeping the first elastic member 34 and the second elastic member in a compressed state.

[0132] In this embodiment, the support member 35 is an independent ring structure disposed inside the hollow tube 23, and the support member 35 is sleeved on the rotating shaft 313. However, the arrangement of the support member 35 is not limited to this. Depending on the specific application scenario, in some embodiments, the support member 35 is a protrusion or a protruding ring formed by the protrusion inside the hollow tube 23.

[0133] In some embodiments, the thickness of the first support end of the support member 35 gradually decreases along the direction from the second support end to the first support end.

[0134] When the support member 35 is an independently constructed annular structure, it needs to be assembled into the hollow tube 23 through either the first or second hollow end, and pushed to a fixed position to form an interference fit with the hollow tube 23 at that position. To facilitate assembly, the first support end, as the head structure of the support member 35, needs to have a certain deformation capacity to adapt to assembly even when there are errors in the inner diameter of the hollow tube 23. The thickness of the first support end of the support member 35 gradually decreases along the direction from the second support end to the first support end. This allows the first support end to be easily inserted into the assembly process, and the gradual decrease in thickness also makes the first support end more easily deformable under pressure, maximizing its adaptability to assembly apertures with errors within the hollow tube 23. This improves the assembly efficiency of the support member 35.

[0135] In some embodiments, the support member 35 has a first deformation notch at its second support end. The first deformation notch allows the second support end of the support member 35 to deform under pressure, facilitating easy assembly. This maximizes adaptability to assembly apertures with varying tolerances within the hollow tube 23, improving the assembly efficiency of the support member 35. Furthermore, when the support member 35 with the first deformation notch is subjected to an external force from the first support end towards the second support end, the connection point between the second support end and the hollow tube 23 will flare outwards towards the hollow tube 23, forming a trumpet-shaped structure to resist external forces, thus improving the assembly stability and resistance to external forces of the support member 35.

[0136] In some embodiments, the support member 35 has a second deformation notch at the second support end. The second deformation notch has the same function as the first deformation notch, and will not be described again here.

[0137] In some embodiments, the outer surface of the support member 35 is raised to form ridges. The ridges reduce the contact area between the support member 35 and the hollow tube 23, and the space between the ridges can serve as space for the ridges to deform under force, reducing assembly resistance and improving assembly efficiency. At the same time, it can also reduce the risk of the support member 35 bursting through the hollow tube 23 during assembly.

[0138] In some embodiments, the first deformation notch and the second deformation notch are arranged opposite to each other. The arrangement of the first deformation notch and the second deformation notch opposite to each other maximizes the deformable range of the second support end.

[0139] In some embodiments, the protrusion height of the ridge gradually decreases along the direction from the second support end to the first support end.

[0140] Because the support member 35 is assembled with the second support end facing the first support end, the protrusion height of the rib gradually decreases along the direction from the second support end to the first support end. That is, the position with the lowest protrusion height in the rib makes contact with the hollow tube 23 first during assembly. This reduces the assembly difficulty and makes the assembly resistance gradually increase with the depth of assembly, reducing the risk of the hollow tube 23 being burst during assembly.

[0141] In some embodiments, the end of the protruding ridge facing the first support end smoothly transitions with the surface of the support member 35. Since the support member 35 is assembled with the second support end facing the first support end, the smooth transition between the end of the protruding ridge facing the first support end and the surface of the support member 35 effectively reduces assembly resistance and improves assembly efficiency. Simultaneously, it also prevents protruding foreign objects from scratching the inner wall of the hollow tube 23 during assembly.

[0142] In some embodiments, the motor assembly 3 includes a coil 321, which is sleeved on the hollow tube 23, and the support 35 and the second bearing 36 are located at the connection between the coil 321 and the hollow tube 23.

[0143] The coil 321 is fitted onto the hollow tube 23, and the connection between the two is an interference fit. Because the hollow tube 23 is hollow inside, its strength under stress is relatively lower compared to a solid structure of the same material, and it is at risk of local collapse under significant external forces. The support member 35 and the second bearing 36 are located at the connection point between the coil 321 and the hollow tube 23, providing support for the hollow tube 23, increasing its strength, and reducing the risk of collapse under stress.

[0144] In some embodiments, the support member 35 is assembled from the second hollow end of the hollow tube 23 toward the first hollow end. Since the assembly direction is opposite, the support member 35 is assembled after being reversed.

[0145] A fan assembly includes: a fan housing 1, a mounting base 2, a motor assembly 3, and fan blades 4. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11; the motor assembly 3 is assembled inside the fan housing 1; the fan blades 4 are connected to the motor assembly 3; one end of the motor assembly 3 is inserted into the mounting base 2; there is an air inlet gap between the fan blades 4 and the mounting base 2; there is a first assembly gap between the motor assembly 3 and the mounting base 2; and a first air outlet 24 is provided on the mounting base 2. The air inlet gap, the first assembly gap, and the first air outlet 24 form a first heat dissipation passage.

[0146] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0147] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0148] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0149] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0150] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0151] In some embodiments, the first air outlet 24 has a multiple function. For example, the first air outlet 24 can serve as a wiring hole for the motor assembly 3. Depending on the specific application scenario, other functions of the first air outlet 24 will not be listed here. However, it should be noted that any openings, holes, or gaps on the mounting base 2, regardless of their different uses, as long as they also serve the function of facilitating ventilation and airflow, fall under the category of the first air outlet 24 in this embodiment.

[0152] In some implementations, the first air outlet 24 has two or more outlets.

[0153] In this embodiment, the width of the air inlet gap is determined based on the end-to-end distance between the fan blade 4 and the mounting base 2. In some embodiments, the air inlet gap is a narrow slit with a relatively short distance between them. In other embodiments, the air inlet gap is a wide slit with a relatively long distance between them.

[0154] In this embodiment, the first assembly gap refers to the distance between the inner surface of the mounting base 2 and the outer surface of the end where the motor assembly 3 is inserted into the mounting base 2.

[0155] In the above embodiment, the fan blades 4 rotate under the drive of the motor assembly 3, and the rotation of the fan blades 4 drives the airflow inside the fan housing 1 to move in a specific direction. Airflow is a fluid, and the inherent flow characteristics of fluids cause the airflow to flow into any airflow channel connected to the external environment. There is an air inlet gap between the fan blades 4 and the mounting base 2, and a first assembly gap between the motor assembly 3 and the mounting base 2. The mounting base 2 has a first air outlet 24. The air inlet gap, the first assembly gap, and the first air outlet 24 form a complete airflow channel to the external environment. When the motor assembly 3 is working, it generates heat. If this heat is not dissipated in time, it will affect the normal operation of the motor assembly 3, and in severe cases, it may cause damage or burnout of the fan assembly. The airflow, flowing along the first heat dissipation path formed by the air inlet gap, the first assembly gap, and the first air outlet 24, carries away the heat generated by the motor assembly 3, cooling the motor assembly 3 and achieving a cooling effect.

[0156] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is connected to the fan housing 1 via multiple stationary blades 11. One end of the motor assembly 3 is inserted into the connecting cylinder 21, and a first assembly gap exists between the connecting cylinder 21 and the motor assembly 3. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0157] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0158] In some embodiments, the motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, the motor rotor 31 is sleeved on the motor stator 32, one end of the motor rotor 31 is inserted into the mounting base 2, and there is a first assembly gap between the motor rotor 31 and the mounting base 2.

[0159] The motor stator 32 includes an iron core and multiple coils 321 wound on the iron core. Since each coil 321 is wound independently on the iron core, the coils 321 cannot be completely filled with each other or with the iron core. Therefore, gaps will appear between the coils 321 on the motor stator 32.

[0160] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 36. The other end of the shaft 313 is connected to the fan blade 4. The motor stator 32 is fitted onto the hollow tube 23 with an interference fit. The magnetic ring 312 is fitted onto the motor stator 32, and the motor housing 311 is fitted onto the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0161] In some embodiments, there is a first assembly gap between the motor housing 311 and the mounting base 2, one end of the motor housing 311 is inserted into the mounting base 2, and an air inlet is provided at the end of the motor housing 311 facing the fan blade 4.

[0162] In some embodiments, the magnetic ring 312 is composed of multiple independent magnetic strips spaced apart. The multiple magnetic strips are connected to the motor housing by means of adhesive bonding, welding, snap-fitting, etc.

[0163] In some embodiments, the motor rotor 31 has an air inlet opening, and the motor stators 32 have a coil 321 gap. The air inlet opening, the coil 321 gap, and the first air outlet 24 form a second heat dissipation passage.

[0164] In this embodiment, there are four air inlets. However, the number of air inlets is not limited to this. Depending on the specific application scenario, in some embodiments, the number of air inlets can be (but is not limited to): one, two, three, five, or more.

[0165] The air inlet, the gap in coil 321, and the first air outlet 24 form a complete airflow channel to the external environment. The airflow, following the second heat dissipation path formed by the air inlet, the gap in coil 321, and the first air outlet 24, carries away the heat generated by the motor assembly 3, cooling it and achieving a cooling effect. Since the second heat dissipation path exits after passing through the motor stator 32, it effectively cools the inside of the motor assembly 3. Under the same airflow, the internal temperature of the motor assembly 3 is higher, resulting in more heat being carried away by the internal cooling, and a more significant heat dissipation effect. The first and second heat dissipation paths, located outside and inside the fan assembly respectively, dissipate heat from the motor assembly 3, improving the effectiveness of air cooling. This allows the motor assembly 3 to operate in a stable and suitable temperature environment, ensuring its efficiency and stability, and extending the service life of both the motor assembly 3 and the fan assembly.

[0166] In some embodiments, a coupling gap also exists between the motor stator 32 and the magnetic ring 312. The air inlet, coupling gap, and first air outlet 24 form a third heat dissipation path, which also carries away the heat generated by the motor assembly 3 during operation, thus cooling the motor assembly 3 and achieving a cooling effect. The third heat dissipation path also flows out after passing through the inside of the motor assembly 3, removing more heat from the interior and resulting in a more significant heat dissipation effect. The first, second, and third heat dissipation paths are located outside and inside the fan assembly, respectively, dissipating heat from the motor assembly 3 and further improving the air cooling effect, enabling the motor assembly 3 to operate in a stable and suitable temperature environment.

[0167] In some embodiments, when the magnetic ring 312 is composed of multiple independent magnetic strip intervals, the magnetic ring 312 forms a separation gap. The separation gap spatially expands the coupling gap, making the coupling gap larger and increasing the contact area between the third heat dissipation path and the motor assembly 3, resulting in better heat dissipation.

[0168] In some implementations, since both the coil 321 gap and the coupling gap are located inside the motor assembly 3, the second heat dissipation path and the third heat dissipation path are interconnected, further improving the heat dissipation effect.

[0169] When the motor assembly 3 is in operation, the motor rotor 31 rotates around the motor stator 32. The rotation of the motor rotor 31 will drive the airflow in the second heat dissipation passage and the third heat dissipation passage to rotate. The airflow in the second heat dissipation passage and the third heat dissipation passage moves in a spiral shape. This movement mode makes the contact area between the airflow and the internal structure of the motor assembly 3 larger, and removes more heat, further improving the cooling effect.

[0170] In some embodiments, the end of the motor rotor 31 facing the fan blade 4 is inserted into the fan blade 4, and there is a second assembly gap between the fan blade 4 and the motor rotor 31. The second assembly gap, the air inlet opening, the coil 321 gap and the first air outlet 24 form a second heat dissipation passage.

[0171] The end of the motor housing 311 facing the fan blade 4 is inserted into the fan blade 4, which reduces the exposed area of ​​the motor housing 311 and lowers the wind resistance inside the fan housing 1. At the same time, because the internal space of the fan blade 4 is reused, the axial length of the fan assembly is reduced, making the spatial structure of the fan assembly more compact and smaller.

[0172] In some embodiments, the fan assembly further includes: a PCB circuit board 5, which is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2, and the first air outlet 24 and the second air outlet 51 are connected.

[0173] The PCB circuit board 5 is connected to the connecting cylinder 21 of the mounting base 2. The connection between the PCB circuit board 5 and the connecting cylinder 21 is a screw connection. However, the connection method between the PCB circuit board 5 and the connecting cylinder 21 is not limited to this. Depending on the specific application scenario, in some embodiments, the connection method between the PCB circuit board 5 and the connecting cylinder 21 includes (but is not limited to): snap-fit, soldering, riveting, adhesive fixing, etc. The connection method between the PCB circuit board 5 and the connecting cylinder 21 can be determined according to the needs of the specific implementation method and is not limited to specific examples.

[0174] In some embodiments, when the PCB circuit board 5 has the same or larger cross-sectional dimensions as the mounting base 2, the PCB circuit board 5 covers the mounting base 2. To prevent the PCB circuit board 5 from blocking the first, second, and third heat dissipation paths, a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2.

[0175] In some embodiments, the second air outlet 51 on the PCB circuit board 5 has a multiple function. For example, the second air outlet 51 can serve as a wiring hole on the PCB circuit board 5. Depending on the specific application scenario, other functions of the second air outlet 51 will not be listed here. However, it should be noted that: regardless of the different uses of holes and gaps on the PCB circuit board 5, as long as they also have the function of facilitating ventilation and airflow, they belong to the category of the second air outlet 51 referred to in this embodiment.

[0176] In some embodiments, the second air outlet 51 is formed on the side wall of the connecting cylinder 21.

[0177] In some implementations, a second air outlet 51 is provided on both the PCB circuit board 5 and the mounting base 2.

[0178] In some embodiments, when the size of the PCB circuit board 5 is smaller than the cross-sectional size of the mounting base 2, or when the PCB circuit board 5 is mounted above the mounting base 2, the second air outlet 51 is the gap between the PCB circuit board 5 and the mounting base 2.

[0179] The PCB circuit board 5 also generates heat during operation. Accumulated heat can lead to a decrease in the performance of the PCB circuit board 5 and even cause a fire. The PCB circuit board 5 is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2. The first air outlet 24 and the second air outlet 51 are connected, and the airflow from the first, second, and third heat dissipation paths flows out through the second air outlet 51. During this flow, the airflow carries away the heat generated by the PCB circuit board 5, providing air cooling and ensuring a stable operating environment for the PCB circuit board 5, thus extending its service life.

[0180] In some embodiments, the mounting base 2 is provided with a plurality of connecting flanges at one end connected to the PCB circuit board 5, and there are flange gaps between adjacent connecting flanges. The PCB circuit board 5 is covered on the plurality of connecting flanges, and the PCB circuit board 5 and the flange gaps enclose and form a second air outlet 51.

[0181] The second air outlet 51 is formed by the gap between the PCB circuit board 5 and the baffle. The airflow blown out from the first air outlet 24 first contacts the PCB circuit board 5, and then blows out from the second air outlet 51 along the PCB circuit board 5. In this process, the contact area and time between the airflow and the PCB circuit board 5 are increased, thereby improving the heat dissipation efficiency and making the cooling effect more significant.

[0182] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0183] A fan assembly includes: a fan housing 1, a mounting base 2, a motor assembly 3, and fan blades 4. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via a plurality of stationary blades 11; one end of the motor assembly 3 is inserted into and connected to the mounting base 2; the other end of the motor assembly 3 is inserted into and connected to the fan blades 4.

[0184] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0185] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0186] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0187] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0188] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0189] In the above embodiment, one end of the motor assembly 3 is inserted into the mounting base 2, and the other end of the motor assembly 3 is inserted into the fan blade 4. This structure results in a smaller portion of the fan blade 4 covering the motor assembly 3 compared to a design where the motor assembly 3 is completely inserted into the fan blade 4, thus reducing the axial length of the fan blade 4. This reduction in axial length shortens the overall rotational arm of the fan blade 4, thereby reducing its rotational torque. With reduced rotational torque, the fan blade 4 rotates faster under the same output conditions as the motor assembly 3. The reduced rotational torque also decreases the abnormal centrifugal force caused by imbalance in the fan blade 4, leading to more stable rotation, reducing the probability of abnormal vibration, and lowering rotational noise.

[0190] In some embodiments, the fan blade 4 is provided with a connecting shaft post 43 and a plurality of reinforcing ribs 411. The plurality of reinforcing ribs 411 are arranged around the connecting shaft post 43. The motor assembly 3 abuts against the connecting shaft post 43 and / or the plurality of reinforcing ribs 411 to reduce the rotational torque of the fan blade 4.

[0191] The fan blade 4 includes a hub 41 and multiple moving blades 42. The multiple moving blades 42 are spaced apart on the surface of the hub 41. The hub 41 is hollow inside, and the connecting shaft 43 is located at the center of the hub 41.

[0192] The motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, and the motor rotor 31 is sleeved on the motor stator 32, with one end of the motor rotor 31 inserted into the mounting base 2. The motor stator 32 includes an iron core and a plurality of coils 321 wound on the iron core.

[0193] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 36. The other end of the shaft 313 is connected to the connecting shaft 43 of the fan blade 4. The motor stator 32 is sleeved on the hollow tube 23 and is interference-fitted with the hollow tube 23. The magnetic ring 312 is sleeved on the motor stator 32, and the motor housing 311 is sleeved on the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0194] One end of the motor housing 311 in the motor assembly 3 is inserted into the mounting base 2, and the other end is inserted into the hub 41 of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411.

[0195] In this embodiment, when the motor assembly 3 is working, the motor stator 32 first performs electromagnetic conversion, driving the motor housing 311, which is fitted with a magnetic ring 312, to rotate; then the motor housing 311 drives the rotating shaft 313 to rotate; finally, the rotating shaft 313 drives the fan blades 4 to rotate. One end of the motor housing 311 inserted into the fan blades 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411. This creates friction between the motor housing 311 and the connecting shaft 43 and / or multiple reinforcing ribs 411 during rotation. When the motor housing 311 and the fan blades 4 rotate at the same frequency, this friction is converted into the rotational driving force of the fan blades 4, which is equivalent to increasing the radial contact area between the rotating shaft 313 and the fan blades 4, making the rotation of the fan blades 4 more stable.

[0196] In some embodiments, the hub 41 of the fan blade 4 is constructed in a conical, frustum-shaped, hemispherical, or bullet-shaped configuration. This structure results in varying lever arms between different parts of the hub 41 and the shaft 313 when the fan blade 4 rotates. The lever arm is largest at the end of the hub 41 where the motor housing 311 is inserted, resulting in a larger torque. Excessive torque differences at different positions of the hub 41 can lead to unstable rotation of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411, effectively reducing the torque at the end of the hub 41 and decreasing the torque difference at different positions, thus making the fan blade 4 rotate more stably.

[0197] In some embodiments, when the motor housing 311 abuts against the reinforcing rib 411, the motor housing 311 abuts against only a portion of the structure of the reinforcing rib 411.

[0198] In some embodiments, the length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4.

[0199] The length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4. This structure keeps the axial length of the fan blade 4 within an optimal range. This maximizes the speed of the fan blade 4 under the same output environment, making the rotation of the fan blade 4 more stable and the noise lower.

[0200] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0201] In some embodiments, a plurality of stationary blades 11 have guide serrations 111 formed at the end facing the fan blade 4.

[0202] In some embodiments, the guide serrations 111 are composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide serrations 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0203] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out of the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0204] In some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0205] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0206] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0207] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0208] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0209] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0210] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0211] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0212] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0213] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0214] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0215] In some embodiments, there is a gap between the inner wall of the fan blade 4 and the portion of the motor rotor 31 inserted into the fan blade.

[0216] In some embodiments, the motor rotor 31 includes a magnetic ring 312 and a motor housing 311. The magnetic ring 312 is sleeved on the motor stator 32, and the motor housing 311 is sleeved on the magnetic ring 312. The motor housing 311 has multiple air inlet openings at the end facing the fan blades 4, and the multiple air inlet openings are arranged in pairs symmetrically.

[0217] Specifically, there is a gap between the motor housing 311 and the side wall of the fan blade 4. This gap allows airflow from the fan housing 1 to enter the motor assembly 3 through multiple air inlets, cooling the motor assembly 3 and maintaining its internal temperature at a suitable level, thus extending its service life. The multiple air inlets are arranged in pairs and symmetrically, ensuring a uniform mass distribution within the motor housing 311 and improving its rotational stability.

[0218] Example 2

[0219] Please refer to Figures 5 and 6. Figure 5 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 6 is a schematic diagram of the exploded structure of the fan assembly in this embodiment.

[0220] As shown in Figures 5 and 6, a fan assembly includes: a fan housing 1, a motor assembly 3, a mounting base 2, and fan blades 4. The motor assembly 3 is assembled inside the fan housing 1; the mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11, and the motor assembly 3 is connected to the mounting base 2; the fan blades 4 are connected to the motor assembly 3; the ends of the multiple stationary blades 11 facing the fan blades 4 have guide serrations 111.

[0221] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0222] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0223] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0224] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor. Structurally, the motor assembly 3 can be (but is not limited to): an internal rotor motor or an external rotor motor.

[0225] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0226] The guide sawtooth 111 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide sawtooth 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0227] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out of the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0228] Please refer to Figure 7, which is an exploded structural diagram of the fan assembly in this embodiment.

[0229] As shown in Figure 7, in some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0230] The fan blades 4 also include a hub 41, with multiple moving blades 42 arranged around the hub 41.

[0231] The guide serrations 111 are disposed on the stationary blade 11, while the trailing edge serrations 421 are disposed on the moving blade 42. Since the airflow possesses rotational potential energy during flow, and the rotation direction of this potential energy is the same as the rotation direction of the moving blade 42, the trailing edge serrations 421 of the moving blade 42 perform co-directional cutting of the vortex. However, the guide serrations 111 disposed on the stationary blade 11 perform static blocking cutting of the vortex, resulting in higher cutting efficiency and a more pronounced vortex-breaking effect.

[0232] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0233] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0234] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0235] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0236] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0237] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0238] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0239] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0240] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0241] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0242] In some embodiments, the tooth marks of the guide serration 111 are aligned with the inclination direction of the tooth marks of the trailing edge serration 421.

[0243] When the inclination direction of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 is consistent, the guide sawtooth 111 and the trailing sawtooth 421 can perform secondary dispersion and decomposition on the airflow with the same flow direction, making the vortex decomposition effect of the inclination direction more obvious.

[0244] In some embodiments, the tooth marks of the guide serration 111 are tilted in the opposite direction to the tooth marks of the trailing edge serration 421.

[0245] When the inclination directions of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 are opposite, the guide sawtooth 111 and the trailing sawtooth 421 can break down the vortices that their inclination directions point to, so that the vortex area broken down by the guide sawtooth 111 and the trailing sawtooth 421 is wider.

[0246] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the direction of the fan housing 1, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the direction of the fan housing 1.

[0247] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The tooth marks of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Similarly, the tooth marks of the trailing edge serrations 421 are also inclined towards the fan housing 1, again aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, further enhancing their efficiency in dispersing and decomposing the airflow. Furthermore, since both tooth marks are inclined in the same direction as the airflow, the wind resistance of the guide serrations 111 and trailing edge serrations 421 is reduced, improving the airflow efficiency. The tooth marks of the guide sawtooth 111 and the trailing edge sawtooth 421 are both inclined toward the fan housing 1, which can further disperse and decompose the airflow with the same flow direction, making the vortex decomposition effect in the inclined direction more obvious.

[0248] In some embodiments, the tooth marks of the guide serration 111 are inclined toward the fan housing 1, and the tooth marks of the trailing edge serration 421 are inclined toward the mounting base 2.

[0249] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The serrations of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the serrations and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Meanwhile, the serrations of the trailing edge serrations 421 are inclined towards the mounting base 2, opposite to the airflow direction. This reverse-direction arrangement allows for multiple decompositions of the laterally moving airflow, resulting in more thorough dispersal of vortices. Furthermore, both the guide serrations 111 and 421 can disperse and decompose vortices in their respective inclination directions, expanding the vortex area dispersed by the guide serrations 111 and 421.

[0250] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the mounting base 2, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the fan housing 1. The guide saw teeth 111 and the trailing edge saw teeth 421 can break down and decompose the vortices in their respective inclined directions, so that the vortex areas broken down and decomposed by the guide saw teeth 111 and the trailing edge saw teeth 421 are larger.

[0251] In some embodiments, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 are both inclined toward the mounting base 2.

[0252] In some embodiments, the tooth marks of the guide serration 111 correspond to and engage with the tooth marks of the trailing edge serration 421.

[0253] In this embodiment, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 correspond to each other, meaning that the tooth marks of the trailing edge saw teeth 421 are provided at the position where the extension line of the tooth marks of the guide saw teeth 111 intersects with the position of the trailing edge saw teeth 421; conversely, the tooth marks of the guide saw teeth 111 are provided at the position where the extension line of the tooth marks of the trailing edge saw teeth 421 intersects with the position of the guide saw teeth 111.

[0254] The serrations of the guide serration 111 and the trailing edge serration 421 correspond and cooperate with each other, and the serrations of the trailing edge serration 421 have the function of dividing the airflow. The divided airflow will reconverge at the guide serration 111, and the converged airflow will be dispersed and divided again by the serrations of the guide serration 111, preventing the vortex from reconverging and improving the vortex division effect.

[0255] In some embodiments, the tooth marks of the guide serration 111 and the tooth marks of the trailing edge serration 421 are misaligned and matched.

[0256] In this embodiment, the misalignment of the tooth marks of the guide sawtooth 111 and the tooth marks of the trailing sawtooth 421 means that: a notch of the trailing sawtooth 421 is provided at the position where the extension line of the tooth mark of the guide sawtooth 111 intersects with the trailing sawtooth 421; conversely, a notch of the guide sawtooth 111 is provided at the position where the extension line of the tooth mark of the trailing sawtooth 421 intersects with the guide sawtooth 111.

[0257] The tooth marks of the guide sawtooth 111 and the tooth marks of the trailing edge sawtooth 421 are staggered and matched. Both the tooth marks of the trailing edge sawtooth 421 and the tooth marks of the guide sawtooth 111 have the function of dividing the airflow. The two are staggered and can separate the vortices at different positions, increase the vortex division area, and further reduce aerodynamic noise.

[0258] In some embodiments, the length ratio of the stationary blade 11 to the moving blade 42 is 1.1-2.8. The length of the stationary blade 11 refers to the length between the end of the stationary blade 11 with the guide serrations 111 and the opposite end. The length of the moving blade 42 refers to the length between the end of the moving blade 42 with the trailing edge serrations 421 and the opposite end.

[0259] At the aforementioned length ratio, the length of the stationary blade 11 is greater than the length of the moving blade 42. When the fan blade 4 rotates, the moving blade 42 restrains and guides the airflow. If the moving blade 42 is too long, the rotational potential energy of the airflow will be too high. The main function of the stationary blade 11 is to counteract and convert the rotational potential energy of the airflow, causing it to move horizontally in a directional direction along the stationary blade 11. If the length of the stationary blade 11 is too short, the rotational potential energy of the airflow exiting the fan assembly will be too high, resulting in poor directional movement capability and a short directional air delivery distance.

[0260] Setting the length ratio of the stationary blade 11 to the moving blade 42 between 1.1 and 2.8 allows the rotational potential energy of the airflow exiting the fan blade 4 to be fully canceled and converted when passing through the moving blade 42, improving the overall airflow efficiency and directional air delivery capability of the fan assembly. Simultaneously, the airflow is blown out from the fan blade 4, guided by the stationary blade 11, and then blown out. During this process, due to the mounting base 2, the airflow space is compressed, resulting in a pressurized and accelerated airflow process. The relatively large length of the stationary blade 11 corresponds to the path length required for acceleration, thus improving the airflow acceleration efficiency.

[0261] When the ratio of the two is less than 1.1, the rotational potential energy of the airflow blown out by the fan assembly is too large, the diffusion surface of the airflow after it is blown out is too large, and the directional air delivery capability decreases. When the ratio of the two is greater than 2.8, the energy loss of the fan assembly within the fan housing 1 is too large, the initial kinetic energy of the airflow at the air outlet of the fan assembly decreases, which also reduces the directional air delivery capability of the fan assembly.

[0262] In some embodiments, the ratio of the number of stationary blades 11 to the number of moving blades 42 is 0.5-1.

[0263] When the ratio of stationary blades 11 to moving blades 42 is within a certain range, it can increase the airflow and air pressure of the fan assembly, resulting in a higher airflow speed. When the ratio of stationary blades 11 to moving blades 42 is less than 0.5, the number of stationary blades 11 is too small, and the stationary blades 11 are not sufficient to offset and convert the rotational potential energy of the airflow, reducing the directional airflow capability of the fan assembly. When the ratio of stationary blades 11 to moving blades 42 is greater than 1, the number of stationary blades 11 is too large, increasing the airflow resistance and reducing the airflow conversion efficiency.

[0264] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0265] Please refer to Figures 5 and 6. Figure 5 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 6 is a schematic diagram of the exploded structure of the fan assembly in this embodiment.

[0266] As shown in Figures 5 and 6, a fan assembly includes: a fan housing 1, a motor assembly 3, a mounting base 2, and fan blades 4. The motor assembly 3 is assembled inside the fan housing 1; the mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11, and the motor assembly 3 is connected to the mounting base 2; the fan blades 4 are connected to the motor assembly 3; the ends of the multiple stationary blades 11 facing the fan blades 4 have guide serrations 111.

[0267] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0268] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0269] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0270] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor. Structurally, the motor assembly 3 can be (but is not limited to): an internal rotor motor or an external rotor motor.

[0271] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0272] The guide sawtooth 111 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide sawtooth 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0273] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out from the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0274] Please refer to Figure 7, which is an exploded structural diagram of the fan assembly in this embodiment.

[0275] As shown in Figure 7, in some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0276] The fan blades 4 also include a hub 41, with multiple moving blades 42 arranged around the hub 41.

[0277] The guide serrations 111 are disposed on the stationary blade 11, while the trailing edge serrations 421 are disposed on the moving blade 42. Since the airflow possesses rotational potential energy during flow, and the rotation direction of this potential energy is the same as the rotation direction of the moving blade 42, the trailing edge serrations 421 of the moving blade 42 perform co-directional cutting of the vortex. However, the guide serrations 111 disposed on the stationary blade 11 perform static blocking cutting of the vortex, resulting in higher cutting efficiency and a more pronounced vortex-breaking effect.

[0278] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0279] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0280] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0281] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0282] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0283] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0284] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0285] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0286] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0287] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0288] In some embodiments, the tooth marks of the guide serration 111 are in the same direction of inclination as the tooth marks of the trailing edge serration 421.

[0289] When the inclination direction of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 is consistent, the guide sawtooth 111 and the trailing sawtooth 421 can perform secondary dispersion and decomposition on the airflow with the same flow direction, making the vortex decomposition effect of the inclination direction more obvious.

[0290] In some embodiments, the tooth marks of the guide serration 111 are tilted in the opposite direction to the tooth marks of the trailing edge serration 421.

[0291] When the inclination directions of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 are opposite, the guide sawtooth 111 and the trailing sawtooth 421 can break down the vortices that their inclination directions point to, so that the vortex area broken down by the guide sawtooth 111 and the trailing sawtooth 421 is wider.

[0292] In some embodiments, the tooth marks of the guide serration 111 are inclined toward the fan housing 1, and the tooth marks of the trailing edge serration 421 are inclined toward the fan housing 1.

[0293] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The tooth marks of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Similarly, the tooth marks of the trailing edge serrations 421 are also inclined towards the fan housing 1, again aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, further enhancing their efficiency in dispersing and decomposing the airflow. Furthermore, since both tooth marks are inclined in the same direction as the airflow, the wind resistance of the guide serrations 111 and trailing edge serrations 421 is reduced, improving the airflow efficiency. The tooth marks of the guide sawtooth 111 and the trailing edge sawtooth 421 are both inclined toward the fan housing 1, which can further disperse and decompose the airflow with the same flow direction, making the vortex decomposition effect in the inclined direction more obvious.

[0294] In some embodiments, the tooth marks of the guide serration 111 are inclined toward the fan housing 1, and the tooth marks of the trailing edge serration 421 are inclined toward the mounting base 2.

[0295] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The serrations of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the serrations and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Meanwhile, the serrations of the trailing edge serrations 421 are inclined towards the mounting base 2, opposite to the airflow direction. This reverse-direction arrangement allows for multiple decompositions of the laterally moving airflow, resulting in more thorough dispersal of vortices. Furthermore, both the guide serrations 111 and 421 can disperse and decompose vortices in their respective inclination directions, expanding the vortex area dispersed by the guide serrations 111 and 421.

[0296] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the mounting base 2, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the fan housing 1. The guide saw teeth 111 and the trailing edge saw teeth 421 can break down and decompose the vortices in their respective inclined directions, so that the vortex areas broken down and decomposed by the guide saw teeth 111 and the trailing edge saw teeth 421 are larger.

[0297] In some embodiments, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 are both inclined toward the mounting base 2.

[0298] In some embodiments, the tooth marks of the guide serration 111 correspond to and engage with the tooth marks of the trailing edge serration 421.

[0299] In this embodiment, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 correspond to each other, meaning that the tooth marks of the trailing edge saw teeth 421 are provided at the position where the extension line of the tooth marks of the guide saw teeth 111 intersects with the position of the trailing edge saw teeth 421; conversely, the tooth marks of the guide saw teeth 111 are provided at the position where the extension line of the tooth marks of the trailing edge saw teeth 421 intersects with the position of the guide saw teeth 111.

[0300] The serrations of the guide serration 111 and the trailing edge serration 421 correspond and cooperate with each other, and the serrations of the trailing edge serration 421 have the function of dividing the airflow. The divided airflow will reconverge at the guide serration 111, and the converged airflow will be dispersed and divided again by the serrations of the guide serration 111, preventing the vortex from reconverging and improving the vortex division effect.

[0301] In some embodiments, the tooth marks of the guide serration 111 and the tooth marks of the trailing edge serration 421 are misaligned and matched.

[0302] In this embodiment, the misalignment of the tooth marks of the guide sawtooth 111 and the tooth marks of the trailing sawtooth 421 means that: a notch of the trailing sawtooth 421 is provided at the position where the extension line of the tooth mark of the guide sawtooth 111 intersects with the trailing sawtooth 421; conversely, a notch of the guide sawtooth 111 is provided at the position where the extension line of the tooth mark of the trailing sawtooth 421 intersects with the guide sawtooth 111.

[0303] The tooth marks of the guide sawtooth 111 and the tooth marks of the trailing edge sawtooth 421 are staggered and matched. Both the tooth marks of the trailing edge sawtooth 421 and the tooth marks of the guide sawtooth 111 have the function of dividing the airflow. The two are staggered and can separate the vortices at different positions, increase the vortex division area, and further reduce aerodynamic noise.

[0304] In some embodiments, the length ratio of the stationary blade 11 to the moving blade 42 is 1.1-2.8. The length of the stationary blade 11 refers to the length between the end of the stationary blade 11 with the guide serrations 111 and the opposite end. The length of the moving blade 42 refers to the length between the end of the moving blade 42 with the trailing edge serrations 421 and the opposite end.

[0305] At the aforementioned length ratio, the length of the stationary blade 11 is greater than the length of the moving blade 42. When the fan blade 4 rotates, the moving blade 42 restrains and guides the airflow. If the moving blade 42 is too long, the rotational potential energy of the airflow will be too high. The main function of the stationary blade 11 is to counteract and convert the rotational potential energy of the airflow, causing it to move horizontally in a directional direction along the stationary blade 11. If the length of the stationary blade 11 is too short, the rotational potential energy of the airflow exiting the fan assembly will be too high, resulting in poor directional movement capability and a short directional air delivery distance.

[0306] Setting the length ratio of the stationary blade 11 to the moving blade 42 between 1.1 and 2.8 allows the rotational potential energy of the airflow exiting the fan blade 4 to be fully canceled and converted when passing through the moving blade 42, improving the overall airflow efficiency and directional air delivery capability of the fan assembly. Simultaneously, the airflow is blown out from the fan blade 4, guided by the stationary blade 11, and then blown out. During this process, due to the mounting base 2, the airflow space is compressed, resulting in a pressurized and accelerated airflow process. The relatively large length of the stationary blade 11 corresponds to the path length required for acceleration, thus improving the airflow acceleration efficiency.

[0307] When the ratio of the two is less than 1.1, the rotational potential energy of the airflow blown out by the fan assembly is too large, the diffusion surface of the airflow after it is blown out is too large, and the directional air delivery capability decreases. When the ratio of the two is greater than 2.8, the energy loss of the fan assembly within the fan housing 1 is too large, the initial kinetic energy of the airflow at the air outlet of the fan assembly decreases, which also reduces the directional air delivery capability of the fan assembly.

[0308] In some embodiments, the ratio of the number of stationary blades 11 to the number of moving blades 42 is 0.5-1.

[0309] When the ratio of stationary blades 11 to moving blades 42 is within a certain range, it can increase the airflow and air pressure of the fan assembly, resulting in a higher airflow speed. When the ratio of stationary blades 11 to moving blades 42 is less than 0.5, the number of stationary blades 11 is too small, and the stationary blades 11 are not sufficient to offset and convert the rotational potential energy of the airflow, reducing the directional airflow capability of the fan assembly. When the ratio of stationary blades 11 to moving blades 42 is greater than 1, the number of stationary blades 11 is too large, increasing the airflow resistance and reducing the airflow conversion efficiency.

[0310] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0311] Example 3

[0312] Please refer to Figures 8 and 9. Figure 8 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 9 is a cross-sectional schematic diagram of the fan assembly in this embodiment.

[0313] As shown in Figures 8 and 9, a fan assembly includes: a fan housing 1, a mounting base 2, and a motor assembly 3. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11. The motor assembly 3 is assembled inside the fan housing 1. The mounting base 2 is provided with a hollow tube 23, and the motor assembly 3 is connected to the hollow tube 23. A first bearing 33 and a support member 35 are disposed inside the hollow tube 23. One end of the rotating shaft 313 of the motor assembly 3 is inserted into and passes through the support member 35 and the first bearing 33 in sequence, and the other end of the rotating shaft 313 extends out of the hollow tube 23. The fan blades 4 are connected to the end of the rotating shaft 313 that extends out of the hollow tube 23. A first elastic member 34 is compressed and disposed between the first bearing 33 and the support member 35. One end of the first elastic member 34 is connected to the support member 35, and the other end of the first elastic member 34 is connected to the first inner ring or the first outer ring of the first bearing 33.

[0314] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0315] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0316] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0317] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0318] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0319] In some embodiments, the mounting base 2 includes only a hollow tube 23. One end of a plurality of stationary blades 11 is wrapped around the hollow tube 23, and the other end of the plurality of stationary blades 11 is radially distributed and connected to the fan housing 1.

[0320] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0321] In some embodiments, the mounting base 2 includes a connecting ring 22 and a hollow tube 23. The connecting ring 22 is connected to the fan housing 1 through a plurality of stationary blades 11, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0322] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0323] In this embodiment, the first elastic element 34 is (but is not limited to): a helical spring and a rubber spring. The material and structure of the first elastic element 34 can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0324] The first elastic element 34 is sleeved on the rotating shaft 313. However, the arrangement of the first elastic element 34 is not limited to this. Depending on the specific application scenario, in some embodiments, multiple first elastic elements 34 are provided, and multiple first elastic elements 34 are arranged around the rotating shaft 313 and are respectively connected to the support member 35 and the first bearing 33.

[0325] In this embodiment, the first bearing 33 is disposed at the first hollow end 231 of the hollow tube 23. However, the location of the first bearing 33 is not limited to this. In some embodiments, the first bearing 33 is disposed at the second hollow end 232 of the hollow tube 23.

[0326] In this embodiment, the connection method between the first elastic member 34 and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0327] In this embodiment, the connection method between the first elastic element 34 and the first bearing 33 includes (but is not limited to): abutment, welding or adhesive connection.

[0328] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0329] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0330] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0331] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0332] When the motor assembly 3 is a three-phase motor powered by a battery, the high-speed rotating motor assembly 3 is easily affected by minor vibrations, leading to significant aerodynamic noise and abnormal vibration in the fan assembly. By setting the first elastic element 34 to abut against the first bearing 33, abnormal vibrations caused by bearing structural design defects or errors are reduced, greatly lowering the aerodynamic noise of the fan assembly and improving the rotational stability of the fan assembly.

[0333] Please refer to Figures 10 and 11. Figure 10 is a structural schematic diagram of the fan housing from a first perspective in this embodiment; Figure 11 is an exploded structural schematic diagram of the fan assembly in this embodiment.

[0334] As shown in Figures 10 and 11, in some embodiments, the motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, the motor rotor 31 is sleeved on the motor stator 32, one end of the motor rotor 31 is inserted into the mounting base 2, and there is a first assembly gap between the motor rotor 31 and the mounting base 2.

[0335] The motor stator 32 includes an iron core and multiple coils 321 wound on the iron core. Since each coil 321 is wound independently on the iron core, the coils 321 cannot be completely filled with each other or with the iron core. Therefore, gaps will appear between the coils 321 on the motor stator 32.

[0336] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 36. The other end of the shaft 313 is connected to the fan blade 4. The motor stator 32 is fitted onto the hollow tube 23 with an interference fit. The magnetic ring 312 is fitted onto the motor stator 32, and the motor housing 311 is fitted onto the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0337] In the above embodiment, the first elastic element 34 is disposed between the support 35 and the first bearing 33, with one end of the elastic element connected to the support 35 and the other end connected to the first inner ring or the first outer ring of the first bearing 33. The first elastic element 34 is compressed between the first bearing 33 and the support 35, so that the first inner ring or the first outer ring of the first bearing 33 is always subjected to elastic force. After the first inner ring or the first outer ring is subjected to force, the first bearing 33 is always in a state of bridging the axial gap between the first inner ring and the first outer ring, that is, the balls between the first inner ring and the first outer ring are always clamped, and the axial gap between the first inner ring and the first outer ring is minimized. In the above state, the problem of vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates can be reduced, the vibration frequency of the fan blade 4 is greatly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. At the same time, the wear of the first bearing 33 can also be reduced, and the service life of the first bearing 33 can be extended.

[0338] In some embodiments, the fan assembly further includes: a second bearing 36, a first bearing 33 and a second bearing 36 respectively disposed at both ends of the hollow tube 23, a support member 35 disposed between the first bearing 33 and the second bearing 36, and one end of the rotating shaft 313 sequentially inserted into and through the second bearing 36, the support member 35 and the first bearing 33.

[0339] The arrangement of the first bearing 33 and the second bearing 36 enables the rotating shaft 313 to rotate more smoothly. At the same time, the arrangement of two rotating shafts 313 makes the linear rotation of the rotating shaft 313 more stable, enabling the fan motor to rotate at a faster speed.

[0340] In some embodiments, the first support end 351 of the support member 35 abuts against the second inner ring or the second outer ring of the second bearing 36, and the second support end 352 of the support member 35 is connected to the first elastic member 34.

[0341] To prevent axial displacement between the inner and outer rings of the second bearing 36, the first support end 351 of the support member 35 abuts against the second inner or outer ring of the second bearing 36. The abutment of the second outer or inner ring of the second bearing 36 by the support member 35 ensures that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the second inner and outer rings, meaning the balls between them are always tightly clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it also reduces wear on the second bearing 36 and extends its service life.

[0342] In some embodiments, a second elastic member (not shown) is compressed between the support member 35 and the second bearing 36. One end of the second elastic member is connected to the first support end 351 of the support member 35, and the other end of the second elastic member is connected to the second inner ring and the second outer ring of the second bearing 36.

[0343] In this embodiment, the second elastic element is (but is not limited to): a helical spring and a rubber spring. The material and structure of the second elastic element can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0344] The second elastic element is sleeved on the rotating shaft 313. However, the arrangement of the second elastic element is not limited to this. Depending on the specific application scenario, in some embodiments, multiple second elastic elements are provided, which are arranged around the rotating shaft 313 and respectively connected to the support member 35 and the second bearing 36.

[0345] In this embodiment, the second bearing 36 is disposed at the second hollow end 232 of the hollow tube 23. However, the placement of the second bearing 36 is not limited to this. In some embodiments, the positions of the first bearing 33 and the second bearing 36 can be interchanged, and the second bearing 36 is disposed at the first hollow end 231 of the hollow tube 23.

[0346] In some embodiments, the second elastic element can be disposed between the second bearing and the motor housing 311, with one end of the second elastic element abutting against the inner or outer ring of the second bearing and the other end connected to the motor housing 311.

[0347] To prevent axial displacement between the inner and outer rings of the second bearing 36, a second elastic element is provided between the support member 35 and the second bearing 36. One end of the second elastic element is connected to the second support end 352 of the support member 35, and the other end is connected to the second inner or outer ring of the second bearing 36. The second elastic element, when compressed, connects the second outer or inner ring of the second bearing 36, ensuring that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the inner and outer rings, meaning the balls between them are always clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it reduces wear on the second bearing 36 and extends its service life.

[0348] By placing the second elastic element between the second bearing and the motor housing 311, the axial clearance between the second inner ring and the second outer ring can be minimized.

[0349] In this embodiment, the connection method between the second elastic member and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0350] In this embodiment, the connection method between the second elastic element and the second bearing 36 includes (but is not limited to): abutment, welding or adhesive connection.

[0351] In some embodiments, the support member 35 is interference-fitted with the hollow tube 23. The relative position between the support member 35 and the hollow tube 23 is fixed, keeping the first elastic member 34 and the second elastic member in a compressed state.

[0352] In this embodiment, the support member 35 is an independent ring structure disposed inside the hollow tube 23, and the support member 35 is sleeved on the rotating shaft 313. However, the arrangement of the support member 35 is not limited to this. Depending on the specific application scenario, in some embodiments, the support member 35 is a protrusion or a protruding ring formed by the protrusion inside the hollow tube 23.

[0353] Please refer to Figures 12 and 13. Figure 12 is a three-dimensional structural schematic diagram of the support member in this embodiment; Figure 13 is a cross-sectional view of the support member in this embodiment.

[0354] As shown in Figures 12 and 13, in some embodiments, the thickness of the first support end 351 of the support member 35 gradually decreases along the direction from the second support end 352 to the first support end 351.

[0355] When the support member 35 is an independently constructed annular structure, it needs to be assembled into the hollow tube 23 via the first hollow end 231 or the second hollow end 232, and pushed to a fixed position to form an interference fit with the hollow tube 23 at that position. To facilitate assembly, the first support end 351, as the head structure of the support member 35, needs to have a certain deformation capacity to adapt to assembly even when there are errors in the inner diameter of the hollow tube 23. The thickness of the first support end 351 gradually decreases along the direction from the second support end 352 to the first support end 351. This allows the first support end 351 to be easily inserted into the assembly, and the gradual decrease in thickness also makes it more easily deformable under pressure, maximizing its adaptability to assembly apertures with errors within the hollow tube 23. This improves the assembly efficiency of the support member 35.

[0356] In some embodiments, the support member 35 has a first deformation notch 353 at its second support end 352. The first deformation notch allows the second support end 352 of the support member 35 to deform under pressure, facilitating easy assembly. This maximizes adaptability to assembly apertures with varying tolerances within the hollow tube 23, improving the assembly efficiency of the support member 35. Furthermore, when the support member 35 with the first deformation notch 353 is subjected to an external force from the first support end 351 towards the second support end 352, the connection point between the second support end 352 and the hollow tube 23 will flare outwards towards the hollow tube 23, forming a trumpet-shaped structure to resist external forces, thus improving the assembly stability and resistance to external forces of the support member 35.

[0357] In some embodiments, the support member 35 has a second deformation notch 354 at the second support end 352. The second deformation notch 354 has the same function as the first deformation notch 353, and will not be described again here.

[0358] In some embodiments, the outer surface of the support member 35 is raised to form a ridge 355. The ridge 355 reduces the contact area between the support member 35 and the hollow tube 23, and the space between the ridges 355 can serve as a space for the ridges 355 to deform under force, thereby reducing assembly resistance, improving assembly efficiency, and also reducing the risk of the support member 35 bursting through the hollow tube 23 during assembly.

[0359] In some embodiments, the first deformation notch 353 and the second deformation notch 354 are arranged opposite to each other. The arrangement of the first deformation notch 353 and the second deformation notch 354 opposite to each other maximizes the deformable range of the second support end 352.

[0360] In some embodiments, the protrusion height of the ridge 355 gradually decreases along the direction from the second support end 352 toward the first support end 351.

[0361] Because the support member 35 is assembled with the second support end 352 moving towards the first support end 351, the protrusion height of the ridge 355 gradually decreases along the direction from the second support end 352 to the first support end 351. That is, the position with the lowest protrusion height in the ridge 355 contacts the hollow tube 23 first during assembly. This reduces the assembly difficulty and makes the assembly resistance gradually increase with the depth of assembly, reducing the risk of the hollow tube 23 bursting during assembly.

[0362] In some embodiments, the end of the protruding ridge 355 facing the first support end 351 smoothly transitions with the surface of the support member 35. Since the support member 35 is assembled with the second support end 352 facing the first support end 351, the smooth transition between the end of the protruding ridge 355 facing the first support end 351 and the surface of the support member 35 effectively reduces assembly resistance and improves assembly efficiency. Simultaneously, it also prevents protruding foreign objects from scratching the inner wall of the hollow tube 23 during assembly.

[0363] In some embodiments, the motor assembly 3 includes a coil 321, which is sleeved on the hollow tube 23, and the support 35 and the second bearing 36 are located at the connection between the coil 321 and the hollow tube 23.

[0364] The coil 321 is fitted onto the hollow tube 23, and the connection between the two is an interference fit. Because the hollow tube 23 is hollow inside, its strength under stress is relatively lower compared to a solid structure of the same material, and it is at risk of local collapse under significant external forces. The support member 35 and the second bearing 36 are located at the connection point between the coil 321 and the hollow tube 23, providing support for the hollow tube 23, increasing its strength, and reducing the risk of collapse under stress.

[0365] In some embodiments, the support member 35 is assembled from the second hollow end 232 of the hollow tube 23 toward the first hollow end 231. Since the assembly directions are opposite, the support member 35 is assembled after being reversed.

[0366] Example 4

[0367] Please refer to Figures 14, 15 and 18. Figure 14 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 15 is a cross-sectional schematic diagram of the fan assembly in this embodiment; and Figure 18 is a schematic diagram of the airflow path of the first heat dissipation passage in this embodiment.

[0368] As shown in Figures 14, 15, and 18, a fan assembly includes: a fan housing 1, a mounting base 2, a motor assembly 3, and fan blades 4. The mounting base 2 is disposed within the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11. The motor assembly 3 is assembled within the fan housing 1. The fan blades 4 are connected to the motor assembly 3. One end of the motor assembly 3 is inserted into the mounting base 2. An air inlet gap H1 exists between the fan blades 4 and the mounting base 2. A first assembly gap exists between the motor assembly 3 and the mounting base 2. A first air outlet hole 24 is provided on the mounting base 2. The air inlet gap H1, the first assembly gap H2, and the first air outlet hole 24 form a first heat dissipation passage.

[0369] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0370] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0371] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0372] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0373] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0374] Please refer to Figures 16 and 20. Figure 16 is a structural schematic diagram of the fan housing in this embodiment; Figure 20 is a cross-sectional view and clearance indication schematic diagram of the fan assembly in this embodiment.

[0375] As shown in Figures 16 and 20, in some embodiments, the first air outlet 24 has a multiple function. For example, the first air outlet 24 can serve as a wiring hole for the motor assembly 3. Depending on the specific application scenario, other functions of the first air outlet 24 will not be listed here. However, it should be noted that any openings, holes, or gaps on the mounting base 2, regardless of their different uses, as long as they also serve the function of facilitating ventilation and airflow, fall under the category of the first air outlet 24 referred to in this embodiment.

[0376] In some implementations, the first air outlet 24 has two or more outlets.

[0377] In this embodiment, the width of the air inlet gap H1 is determined based on the end-to-end distance between the fan blade 4 and the mounting base 2. In some embodiments, the air inlet gap H1 is a narrow slit with a relatively short distance. In other embodiments, the air inlet gap H1 is a wide slit with a relatively long distance.

[0378] In this embodiment, the first assembly gap H2 refers to the distance between the inner surface of the mounting base 2 and the outer surface of the end where the motor assembly 3 is inserted into the mounting base 2.

[0379] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0380] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0381] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0382] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0383] When the motor assembly 3 is a three-phase motor and is powered by a battery, the high-speed rotating motor assembly 3 is prone to generating a large amount of heat in the motor assembly 3 and the mounting base 2. By guiding part of the high-pressure airflow generated by the fan blades into the first heat dissipation passage, the motor assembly 3 and the mounting base 2 are cooled, making the working state of the three-phase motor more stable.

[0384] In the above embodiment, the fan blades 4 rotate under the drive of the motor assembly 3, and the rotation of the fan blades 4 drives the airflow inside the fan housing 1 to move in a specific direction. Airflow is a fluid, and the inherent flow characteristics of fluids cause the airflow to flow into any airflow channel connected to the external environment. There is an air inlet gap H1 between the fan blades 4 and the mounting base 2, and a first assembly gap H2 between the motor assembly 3 and the mounting base 2. A first air outlet 24 is provided on the mounting base 2. The air inlet gap H1, the first assembly gap H2, and the first air outlet 24 form a complete airflow channel to the external environment. When the motor assembly 3 is working, it generates heat. If this heat is not dissipated in time, it will affect the normal operation of the motor assembly 3, and in severe cases, it may cause damage or burnout of the fan assembly. The airflow, flowing through the first heat dissipation path formed by the air inlet gap H1, the first assembly gap H2, and the first air outlet 24, carries away the heat generated by the motor assembly 3, cooling the motor assembly 3 and achieving a cooling effect.

[0385] Please refer to Figure 17, which is an exploded view of the fan assembly in this embodiment.

[0386] As shown in Figure 17, in some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is connected to the fan housing 1 through multiple stationary blades 11. One end of the motor assembly 3 is inserted into the connecting cylinder 21, and a first assembly gap H2 exists between the connecting cylinder 21 and the motor assembly 3. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0387] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0388] In some embodiments, the motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, the motor rotor 31 is sleeved on the motor stator 32, one end of the motor rotor 31 is inserted into the mounting base 2, and a first assembly gap H2 exists between the motor rotor 31 and the mounting base 2.

[0389] The motor stator 32 includes an iron core and multiple coils 321 wound on the iron core. Since each coil 321 is wound independently on the iron core, the coils 321 cannot be completely filled with each other or with the iron core, resulting in coil gaps on the motor stator 32.

[0390] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 36. The other end of the shaft 313 is connected to the fan blade 4. The motor stator 32 is fitted onto the hollow tube 23 with an interference fit. The magnetic ring 312 is fitted onto the motor stator 32, and the motor housing 311 is fitted onto the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0391] In some embodiments, there is a first assembly gap H2 between the motor housing 311 and the mounting base 2, one end of the motor housing 311 is inserted into the mounting base 2, and an air inlet 314 is provided at the end of the motor housing 311 facing the fan blade 4.

[0392] In some embodiments, the magnetic ring 312 is composed of multiple independent magnetic strips spaced apart. The multiple magnetic strips are connected to the motor housing by means of adhesive bonding, welding, snap-fitting, etc.

[0393] Please refer to Figures 19, 21 and 22. Figure 19 is a schematic diagram of the airflow path of the second heat dissipation channel in this embodiment; Figure 21 is a schematic diagram of the structure of the motor housing in this embodiment; Figure 22 is a schematic diagram of the coil structure and gap indication in this embodiment.

[0394] As shown in Figures 19, 21 and 22, in some embodiments, the motor rotor 31 has an air inlet 314, and the motor stators 32 have a coil gap H5. The air inlet 314, the coil gap H5 and the first air outlet 24 form a second heat dissipation passage.

[0395] In this embodiment, there are four air inlet openings 314. However, the number of air inlet openings 314 is not limited to this. Depending on the specific application scenario, in some embodiments, the number of air inlet openings 314 can be (not limited to): 1, 2, 3, 5 or more.

[0396] The air inlet 314, coil gap H5, and first air outlet 24 form a complete airflow channel to the external environment. The airflow, following the second heat dissipation path formed by the air inlet 314, coil gap H5, and first air outlet 24, carries away the heat generated by the motor assembly 3, cooling it and achieving a cooling effect. Since the second heat dissipation path exits after passing through the motor stator 32, it effectively cools the inside of the motor assembly 3. Under the same airflow, the internal temperature of the motor assembly 3 is higher, resulting in more heat being carried away by the internal cooling, and a more significant heat dissipation effect. The first and second heat dissipation paths, located outside and inside the fan assembly respectively, dissipate heat from the motor assembly 3, improving the effectiveness of air cooling. This allows the motor assembly 3 to operate in a stable and suitable temperature environment, ensuring its efficiency and stability, and extending the service life of both the motor assembly 3 and the fan assembly.

[0397] In some embodiments, a coupling gap also exists between the motor stator 32 and the magnetic ring 312. The air inlet 314, the coupling gap H3, and the first air outlet 24 form a third heat dissipation path, which also carries away the heat generated by the motor assembly 3 during operation, thus cooling the motor assembly 3 and achieving a cooling effect. The third heat dissipation path also flows out after passing through the inside of the motor assembly 3, so it carries away more heat from the inside, resulting in a more significant heat dissipation effect. The first, second, and third heat dissipation paths are located outside and inside the fan assembly, respectively, dissipating heat from the motor assembly 3, further improving the air cooling effect and enabling the motor assembly 3 to operate in a stable and suitable temperature environment.

[0398] In some embodiments, when the magnetic ring 312 is composed of multiple independent magnetic strip intervals, the magnetic ring 312 forms a separation gap. The separation gap spatially expands the coupling gap H3, making the coupling gap H3 larger and increasing the contact area between the third heat dissipation path and the motor assembly 3, resulting in better heat dissipation.

[0399] In some implementations, since both the coil gap H5 and the coupling gap H3 are located inside the motor assembly 3, the second heat dissipation path and the third heat dissipation path are interconnected, further improving the heat dissipation effect.

[0400] When the motor assembly 3 is in operation, the motor rotor 31 rotates around the motor stator 32. The rotation of the motor rotor 31 will drive the airflow in the second heat dissipation passage and the third heat dissipation passage to rotate. The airflow in the second heat dissipation passage and the third heat dissipation passage moves in a spiral shape. This movement mode makes the contact area between the airflow and the internal structure of the motor assembly 3 larger, and removes more heat, further improving the cooling effect.

[0401] In some embodiments, the end of the motor rotor 31 facing the fan blade 4 is inserted into the fan blade 4, and there is a second assembly gap H4 between the fan blade 4 and the motor rotor 31. The second assembly gap H4, the air inlet opening 314, the coil gap H5 and the first air outlet 24 form a second heat dissipation passage.

[0402] The end of the motor housing 311 facing the fan blade 4 is inserted into the fan blade 4, which reduces the exposed area of ​​the motor housing 311 and lowers the wind resistance inside the fan housing 1. At the same time, because the internal space of the fan blade 4 is reused, the axial length of the fan assembly is reduced, making the spatial structure of the fan assembly more compact and smaller.

[0403] In some embodiments, the fan assembly further includes: a PCB circuit board 5, which is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2, and the first air outlet 24 and the second air outlet 51 are connected.

[0404] The PCB circuit board 5 is connected to the connecting cylinder 21 of the mounting base 2. The connection between the PCB circuit board 5 and the connecting cylinder 21 is a screw connection. However, the connection method between the PCB circuit board 5 and the connecting cylinder 21 is not limited to this. Depending on the specific application scenario, in some embodiments, the connection method between the PCB circuit board 5 and the connecting cylinder 21 includes (but is not limited to): snap-fit, soldering, riveting, adhesive fixing, etc. The connection method between the PCB circuit board 5 and the connecting cylinder 21 can be determined according to the needs of the specific implementation method and is not limited to specific examples.

[0405] In some embodiments, when the PCB circuit board 5 has the same or larger cross-sectional dimensions as the mounting base 2, the PCB circuit board 5 covers the mounting base 2. To prevent the PCB circuit board 5 from blocking the first, second, and third heat dissipation paths, a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2.

[0406] In some embodiments, the second air outlet 51 on the PCB circuit board 5 has a multiple function. For example, the second air outlet 51 can serve as a wiring hole on the PCB circuit board 5. Depending on the specific application scenario, other functions of the second air outlet 51 will not be listed here. However, it should be noted that: regardless of the different uses of holes and gaps on the PCB circuit board 5, as long as they also have the function of facilitating ventilation and airflow, they belong to the category of the second air outlet 51 referred to in this embodiment.

[0407] In some embodiments, the second air outlet 51 is formed on the side wall of the connecting cylinder 21.

[0408] In some implementations, a second air outlet 51 is provided on both the PCB circuit board 5 and the mounting base 2.

[0409] In some embodiments, when the size of the PCB circuit board 5 is smaller than the cross-sectional size of the mounting base 2, or when the PCB circuit board 5 is mounted above the mounting base 2, the second air outlet 51 is the gap between the PCB circuit board 5 and the mounting base 2.

[0410] The PCB circuit board 5 also generates heat during operation. Accumulated heat can lead to a decrease in the performance of the PCB circuit board 5 and even cause a fire. The PCB circuit board 5 is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2. The first air outlet 24 and the second air outlet 51 are connected, and the airflow from the first, second, and third heat dissipation paths flows out through the second air outlet 51. During this flow, the airflow carries away the heat generated by the PCB circuit board 5, providing air cooling and ensuring a stable operating environment for the PCB circuit board 5, thus extending its service life.

[0411] In some embodiments, the mounting base 2 is provided with a plurality of connecting flanges at one end connected to the PCB circuit board 5, and there are flange gaps between adjacent connecting flanges. The PCB circuit board 5 is covered on the plurality of connecting flanges, and the PCB circuit board 5 and the flange gaps enclose and form a second air outlet 51.

[0412] The second air outlet 51 is formed by the gap between the PCB circuit board 5 and the baffle. The airflow blown out from the first air outlet 24 first contacts the PCB circuit board 5, and then blows out from the second air outlet 51 along the PCB circuit board 5. In this process, the contact area and time between the airflow and the PCB circuit board 5 are increased, thereby improving the heat dissipation efficiency and making the cooling effect more significant.

[0413] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0414] Example 5

[0415] Please refer to Figures 23 and 24. Figure 23 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 24 is a cross-sectional schematic diagram of the fan assembly in this embodiment.

[0416] As shown in Figures 23 and 24, a fan assembly includes: a fan housing 1, a mounting base 2, a motor assembly 3, and fan blades 4. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11; one end of the motor assembly 3 is inserted into and connected to the mounting base 2; the other end of the motor assembly 3 is inserted into and connected to the fan blades 4.

[0417] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0418] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0419] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0420] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0421] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0422] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0423] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0424] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0425] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0426] When motor assembly 3 is a three-phase motor powered by a battery, the fan assembly not only has speed requirements but also energy consumption needs to be considered. By improving the assembly structure of motor assembly 3 and fan blades 4, the torque required for fan blades 4 to rotate is reduced, thus lowering the kinetic energy required for fan blades 4 to rotate. This reduces the energy consumption of the fan assembly, giving it a longer operating range. Simultaneously, the reduced torque allows for greater stability of the fan blades 4's rotational posture at high speeds, reducing the probability of abnormal fan vibration.

[0427] The high-speed rotating motor assembly 3 easily generates a lot of heat in the motor assembly 3 and the mounting base 2. By guiding part of the high-pressure airflow generated by the fan blades into the first heat dissipation passage, the motor assembly 3 and the mounting base 2 are cooled, making the working state of the three-phase motor more stable.

[0428] In the above embodiment, one end of the motor assembly 3 is inserted into the mounting base 2, and the other end of the motor assembly 3 is inserted into the fan blade 4. This structure results in a smaller portion of the fan blade 4 covering the motor assembly 3 compared to a design where the motor assembly 3 is completely inserted into the fan blade 4, thus reducing the axial length of the fan blade 4. This reduction in axial length shortens the overall rotational arm of the fan blade 4, thereby reducing its rotational torque. The reduced rotational torque allows the fan blade 4 to rotate faster under the same output conditions of the motor assembly 3. The reduced rotational torque also decreases the abnormal centrifugal force caused by imbalance in the fan blade 4, making its rotation more stable, reducing the probability of abnormal vibration, and lowering the rotational noise of the fan blade 4.

[0429] In some embodiments, the fan blade 4 is provided with a connecting shaft post 43 and a plurality of reinforcing ribs 411. The plurality of reinforcing ribs 411 are arranged around the connecting shaft post 43. The motor assembly 3 abuts against the connecting shaft post 43 and / or the plurality of reinforcing ribs 411 to reduce the rotational torque of the fan blade 4.

[0430] The fan blade 4 includes a hub 41 and multiple moving blades 42. The multiple moving blades 42 are spaced apart on the surface of the hub 41. The hub 41 is hollow inside, and the connecting shaft 43 is located at the center of the hub 41.

[0431] Please refer to Figure 25, which is an exploded view of the fan assembly in this embodiment.

[0432] As shown in Figure 25, in some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is connected to the fan housing 1 through multiple stationary blades 11. One end of the motor assembly 3 is inserted into the connecting cylinder 21, and a first assembly gap exists between the connecting cylinder 21 and the motor assembly 3. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0433] The motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, and the motor rotor 31 is sleeved on the motor stator 32, with one end of the motor rotor 31 inserted into the mounting base 2. The motor stator 32 includes an iron core 322 and a plurality of coils 321 wound on the iron core 322.

[0434] The motor stator 32 includes an iron core 322 and multiple coils 321 wound on the iron core 322. The iron core 322 is fitted onto a hollow tube 23.

[0435] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 34. The other end of the shaft 313 is connected to the connecting shaft 43 of the fan blade 4. The motor stator 32 is sleeved on the hollow tube 23 and is interference-fitted with the hollow tube 23. The magnetic ring 312 is sleeved on the motor stator 32, and the motor housing 311 is sleeved on the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0436] One end of the motor housing 311 in the motor assembly 3 is inserted into the mounting base 2, and the other end is inserted into the hub 41 of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411.

[0437] In this embodiment, when the motor assembly 3 is working, the motor stator 32 first performs electromagnetic conversion, driving the motor housing 311, which is fitted with a magnetic ring 312, to rotate; then the motor housing 311 drives the rotating shaft 313 to rotate; finally, the rotating shaft 313 drives the fan blades 4 to rotate. One end of the motor housing 311 inserted into the fan blades 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411. This creates friction between the motor housing 311 and the connecting shaft 43 and / or multiple reinforcing ribs 411 during rotation. When the motor housing 311 and the fan blades 4 rotate at the same frequency, this friction is converted into the rotational driving force of the fan blades 4, which is equivalent to increasing the radial contact area between the rotating shaft 313 and the fan blades 4, making the rotation of the fan blades 4 more stable.

[0438] In some embodiments, the hub 41 of the fan blade 4 is constructed in a conical, frustum-shaped, hemispherical, or bullet-shaped configuration. This structure results in varying lever arms between different parts of the hub 41 and the shaft 313 when the fan blade 4 rotates. The lever arm is largest at the end of the hub 41 where the motor housing 311 is inserted, resulting in a larger torque. Excessive torque differences at different positions of the hub 41 can lead to unstable rotation of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411, effectively reducing the torque at the end of the hub 41 and decreasing the torque difference at different positions, thus making the fan blade 4 rotate more stably.

[0439] In some embodiments, when the motor housing 311 abuts against the reinforcing rib 411, the motor housing 311 abuts against only a portion of the structure of the reinforcing rib 411.

[0440] In some embodiments, the length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4.

[0441] The length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4. This structure keeps the axial length of the fan blade 4 within an optimal range. This maximizes the speed of the fan blade 4 under the same output environment, making the rotation of the fan blade 4 more stable and the noise lower.

[0442] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0443] Please refer to Figure 26, which is a schematic diagram of the structure of the motor housing in this embodiment.

[0444] As shown in Figure 26, in some embodiments, a plurality of stationary blades 11 have guide serrations 111 formed on the end facing the fan blade 4.

[0445] In some embodiments, the guide serrations 111 are composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide serrations 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0446] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out from the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0447] In some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0448] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0449] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0450] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0451] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0452] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0453] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0454] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0455] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0456] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0457] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0458] In some embodiments, there is a gap between the inner wall of the fan blade 4 and the portion of the motor rotor 31 inserted into the fan blade.

[0459] In some embodiments, the motor rotor 31 includes a magnetic ring 312 and a motor housing 311. The magnetic ring 312 is sleeved on the motor stator 32, and the motor housing 311 is sleeved on the magnetic ring 312. The motor housing 311 has multiple air inlet openings at the end facing the fan blades 4, and the multiple air inlet openings are arranged in pairs symmetrically.

[0460] Specifically, there is a gap between the motor housing 311 and the side wall of the fan blade 4. This gap allows airflow from the fan housing 1 to enter the motor assembly 3 through multiple air inlets, cooling the motor assembly 3 and maintaining its internal temperature at a suitable level, thus extending its service life. The multiple air inlets are arranged in pairs and symmetrically, ensuring a uniform mass distribution within the motor housing 311 and improving its rotational stability.

[0461] Example 6

[0462] Please refer to Figures 27, 28 and 31. Figure 27 is a schematic diagram of the overall structure of the fan assembly in this embodiment; Figure 28 is a cross-sectional schematic diagram of the fan assembly in this embodiment; and Figure 31 is a schematic diagram of the airflow path of the first heat dissipation passage in this embodiment.

[0463] As shown in Figures 27, 28, and 31, a fan assembly includes: a fan housing 1; a mounting base 2 disposed inside the fan housing 1 and connected to the fan housing 1 via multiple stationary blades 11; a motor assembly 3 assembled inside the fan housing 1; fan blades 4 connected to the motor assembly 3; an air inlet 314 on the motor assembly 3 communicating with the interior of the fan housing 1 and the interior of the motor assembly 3; an internal assembly gap (not shown) for airflow inside the motor assembly 3; and a first air outlet 24 on the mounting base 2. The air inlet 314, the internal assembly gap, and the first air outlet 24 form a first heat dissipation passage.

[0464] In this embodiment, the fan housing 1 is constructed in a cylindrical shape, and a cylindrical air cavity is formed inside the cylinder. However, the shape of the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the fan housing 1 can be: triangular, quadrilateral, pentagonal, other polygonal or other regular shapes. The external structure of the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0465] One end of the mounting base 2 is disposed inside the fan housing 1, and the other end of the mounting base 2 extends outside the fan housing 1. However, the positional relationship between the mounting base 2 and the fan housing 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the entire mounting base 2 is disposed inside the fan housing 1. The positional relationship between the mounting base 2 and the fan housing 1 can be determined according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0466] In this embodiment, the number of stationary blades 11 is 7. However, the number of stationary blades 11 is not limited to this. Depending on the specific application scenario, the number of stationary blades 11 can be 2, 3, 4, 5, 6, 8, or more. The number of stationary blades 11 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0467] In this embodiment, the motor assembly 3 can be (but is not limited to): a single-phase motor, a two-phase motor, or a three-phase motor.

[0468] Structurally, the fan blade 4 can be (but is not limited to): axial flow fan or diagonal flow fan. In specific applications, the required fan blade 4 can be selected according to the needs of the specific application scenario, and no limitation is imposed here.

[0469] In some embodiments, the first air outlet 24 has a multiple function. For example, the first air outlet 24 can serve as a wiring hole for the motor assembly 3. Depending on the specific application scenario, other functions of the first air outlet 24 will not be listed here. However, it should be noted that any openings, holes, or gaps on the mounting base 2, regardless of their different uses, as long as they also serve the function of facilitating ventilation and airflow, fall under the category of the first air outlet 24 in this embodiment.

[0470] In some implementations, the first air outlet 24 has two or more outlets.

[0471] In this embodiment, the internal assembly gap refers to the total space within the motor assembly that allows airflow. This includes (but is not limited to): coupling gap H3, coil gap H5, or the separation gap between bar magnetic rings (not shown in the figure).

[0472] In the above embodiment, the fan blades 4 rotate under the drive of the motor assembly 3, and the rotation of the fan blades 4 in turn drives the airflow inside the fan housing 1 to move in a specific direction. Airflow is a fluid, and the inherent flow characteristics of fluids cause the airflow to flow into any airflow channel connected to the external environment. Under the action of wind pressure, the airflow enters the interior of the motor assembly 3 through the air inlet opening and flows out of the motor assembly 3 through the internal assembly gap and the first air outlet 24. This airflow carries away the heat generated by the operation of the motor assembly 3, cooling the motor assembly 3 and achieving a cooling effect. Since the first heat dissipation path cools the interior of the motor assembly 3, under the same airflow conditions, because the internal temperature of the motor assembly 3 is higher, more heat is carried away by the internal cooling, resulting in a more significant heat dissipation effect.

[0473] Please refer to Figure 37, which is a cross-sectional view and clearance indication diagram of the fan assembly in this embodiment.

[0474] As shown in Figure 37, in some embodiments, there is an air inlet gap H1 between the fan blade 4 and the mounting base 2, and a second assembly gap H4 between the motor assembly 3 and the mounting base 2. A first air outlet hole 24 is provided on the mounting base 2. The air inlet gap H1, the second assembly gap H4 and the first air outlet hole 24 form a second heat dissipation passage.

[0475] In some embodiments, the mounting base 2 is shorter and is not fitted onto the motor assembly 3. That is, the motor housing 311 of the motor assembly 3 is exposed, and the mounting base 2 is located on one side of the motor assembly 3. In this case, the second assembly gap H4 between the motor assembly 3 and the mounting base 2 is similar to the air inlet gap H1 between the motor assembly 3 and the fan blade 4. In this situation, the second assembly gap H4 can act as the air outlet of the motor assembly 3, allowing airflow from the internal assembly gap to exit through the second assembly gap H4 and the first air outlet 24.

[0476] In this embodiment, the width of the air inlet gap H1 is determined based on the end-to-end distance between the fan blade 4 and the mounting base 2. In some embodiments, the air inlet gap H1 is a narrow slit with a relatively short distance. In other embodiments, the air inlet gap H1 is a wide slit with a relatively long distance.

[0477] In this embodiment, the second assembly gap H4 refers to the distance between the inner surface of the mounting base 2 and the outer surface of the end where the motor assembly 3 is inserted into the mounting base 2.

[0478] Please refer to Figure 32, which is a schematic diagram of the airflow path of the second heat dissipation channel in this embodiment.

[0479] As shown in Figure 32, the fan blades 4 rotate under the drive of the motor assembly 3. The rotation of the fan blades 4, in turn, propels the airflow within the fan housing 1 to move in a specific direction. Airflow is a fluid, and the inherent flow characteristics of fluids cause it to flow into any airflow channel connected to the external environment. There is an air inlet gap H1 between the fan blades 4 and the mounting base 2, and a second assembly gap H4 between the motor assembly 3 and the mounting base 2. The mounting base 2 has a first air outlet 24. The air inlet gap H1, the second assembly gap H4, and the first air outlet 24 form a complete airflow channel to the external environment. When the motor assembly 3 is working, it generates heat. If this heat is not dissipated in time, it will affect the normal operation of the motor assembly 3, and in severe cases, it may cause damage or burnout of the fan assembly. The airflow, flowing through the second heat dissipation path formed by the air inlet gap H1, the second assembly gap H4, and the first air outlet 24, carries away the heat generated by the motor assembly 3, cooling the motor assembly 3 and providing a cooling effect.

[0480] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0481] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0482] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0483] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0484] When the motor assembly 3 is a three-phase motor and is powered by a battery, the high-speed rotating motor assembly 3 is prone to generating a large amount of heat in the motor assembly 3 and the mounting base 2. By guiding part of the high-pressure airflow generated by the fan blades into the second heat dissipation passage, the motor assembly 3 and the mounting base 2 are cooled, making the working state of the three-phase motor more stable.

[0485] Please refer to Figure 29, which is an exploded view of the fan assembly in this embodiment.

[0486] As shown in Figure 29, in some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is connected to the fan housing 1 through multiple stationary blades 11. One end of the motor assembly 3 is inserted into the connecting cylinder 21, and a second assembly gap H4 exists between the connecting cylinder 21 and the motor assembly 3. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0487] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0488] In some embodiments, the motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, the motor rotor 31 is sleeved on the motor stator 32, one end of the motor rotor 31 is inserted into the mounting base 2, and a second assembly gap H4 is provided between the motor rotor 31 and the mounting base 2.

[0489] The motor stator 32 includes an iron core 322 and multiple coils 321 wound on the iron core 322. Since each coil 321 is independently wound on the iron core 322, the coils 321 cannot be completely filled with each other or with the iron core 322, resulting in coil gaps on the motor stator 32.

[0490] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 36. The other end of the shaft 313 is connected to the fan blade 4. The motor stator 32 is fitted onto the hollow tube 23 with an interference fit. The magnetic ring 312 is fitted onto the motor stator 32, and the motor housing 311 is fitted onto the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0491] Please refer to Figure 35, which is a structural schematic diagram of the motor housing in this embodiment.

[0492] As shown in Figure 35, in some embodiments, there is a second assembly gap H4 between the motor housing 311 and the mounting base 2, one end of the motor housing 311 is inserted into the mounting base 2, and an air inlet 314 is provided at the end of the motor housing 311 facing the fan blade 4.

[0493] In some embodiments, the magnetic ring 312 is composed of multiple independent magnetic strips spaced apart. The multiple magnetic strips are connected to the motor housing by means of adhesive bonding, welding, snap-fitting, etc.

[0494] Please refer to Figure 36, which is a schematic diagram of the coil structure and gap indication in this embodiment.

[0495] As shown in Figure 36, in some embodiments, the motor rotor 31 has an air inlet 314, and the motor stators 32 have a coil gap H5. The air inlet 314, the coil gap H5, and the first air outlet 24 form a first heat dissipation passage.

[0496] In this embodiment, there are four air inlet openings 314. However, the number of air inlet openings 314 is not limited to this. Depending on the specific application scenario, in some embodiments, the number of air inlet openings 314 can be (not limited to): 1, 2, 3, 5 or more.

[0497] The air inlet 314, coil gap H5, and first air outlet 24 form a complete airflow channel to the external environment. The airflow, following the first heat dissipation path formed by the air inlet 314, coil gap H5, and first air outlet 24, carries away the heat generated by the motor assembly 3, cooling it and achieving a cooling effect. Since the first heat dissipation path exits after passing through the motor stator 32, it effectively cools the inside of the motor assembly 3. Under the same airflow, the internal temperature of the motor assembly 3 is higher, resulting in more heat being carried away by the internal cooling, and a more significant heat dissipation effect. The second and first heat dissipation paths, located outside and inside the fan assembly respectively, further dissipate heat from the motor assembly 3, improving the cooling effect and enabling the motor assembly 3 to operate in a stable and suitable temperature environment. This ensures the efficiency and stability of the motor assembly 3 and extends the service life of both the motor assembly 3 and the fan assembly.

[0498] In some embodiments, a coupling gap H3 is also provided between the motor stator 32 and the magnetic ring 312. The coupling gap H3 is interconnected with the coil gap H5, which expands the space of the internal assembly gap, making the airflow space inside the motor assembly larger, the airflow smoother, and the heat dissipation effect better.

[0499] In some embodiments, when the magnetic ring 312 is composed of multiple independent magnetic strip intervals, the magnetic ring 312 forms a separation gap. The separation gap spatially expands the coupling gap H3 and the coil gap H5, making the space of the coupling gap H3 and the coil gap H5 larger, and making the contact area between the first heat dissipation path and the motor assembly 3 larger, resulting in better heat dissipation.

[0500] When the motor assembly 3 is in operation, the motor rotor 31 rotates around the motor stator 32. The rotation of the motor rotor 31 will drive the airflow flowing through the first heat dissipation passage to rotate. The airflow movement path of the first heat dissipation passage is spiral. This movement mode makes the contact area between the airflow and the internal structure of the motor assembly 3 larger, and removes more heat, further improving the cooling effect.

[0501] In some embodiments, the end of the motor rotor 31 facing the fan blade 4 is inserted into the fan blade 4, and there is a first assembly gap H2 between the fan blade 4 and the motor rotor 31. The first assembly gap H2, the air inlet opening 314, the coil gap H5 and the first air outlet 24 form a first heat dissipation passage.

[0502] The end of the motor housing 311 facing the fan blade 4 is inserted into the fan blade 4, which reduces the exposed area of ​​the motor housing 311 and lowers the wind resistance inside the fan housing 1. At the same time, because the internal space of the fan blade 4 is reused, the axial length of the fan assembly is reduced, making the spatial structure of the fan assembly more compact and smaller.

[0503] In some embodiments, the fan assembly further includes: a PCB circuit board 5, which is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2, and the first air outlet 24 and the second air outlet 51 are connected.

[0504] The PCB circuit board 5 is connected to the connecting cylinder 21 of the mounting base 2. The connection between the PCB circuit board 5 and the connecting cylinder 21 is a screw connection. However, the connection method between the PCB circuit board 5 and the connecting cylinder 21 is not limited to this. Depending on the specific application scenario, in some embodiments, the connection method between the PCB circuit board 5 and the connecting cylinder 21 includes (but is not limited to): snap-fit, soldering, riveting, adhesive fixing, etc. The connection method between the PCB circuit board 5 and the connecting cylinder 21 can be determined according to the needs of the specific implementation method and is not limited to specific examples.

[0505] In some embodiments, when the PCB circuit board 5 has the same or larger cross-sectional dimensions as the mounting base 2, the PCB circuit board 5 covers the mounting base 2. To prevent the PCB circuit board 5 from blocking the second, first, and third heat dissipation paths, a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2.

[0506] In some embodiments, the second air outlet 51 on the PCB circuit board 5 has a multiple function. For example, the second air outlet 51 can serve as a wiring hole on the PCB circuit board 5. Depending on the specific application scenario, other functions of the second air outlet 51 will not be listed here. However, it should be noted that: regardless of the different uses of holes and gaps on the PCB circuit board 5, as long as they also have the function of facilitating ventilation and airflow, they belong to the category of the second air outlet 51 referred to in this embodiment.

[0507] In some embodiments, the second air outlet 51 is formed on the side wall of the connecting cylinder 21.

[0508] In some implementations, a second air outlet 51 is provided on both the PCB circuit board 5 and the mounting base 2.

[0509] In some embodiments, when the size of the PCB circuit board 5 is smaller than the cross-sectional size of the mounting base 2, or when the PCB circuit board 5 is mounted above the mounting base 2, the second air outlet 51 is the gap between the PCB circuit board 5 and the mounting base 2.

[0510] The PCB circuit board 5 also generates heat during operation. Accumulated heat can lead to a decrease in the performance of the PCB circuit board 5 and even cause a fire. The PCB circuit board 5 is connected to the end of the mounting base 2 facing away from the fan blades 4, and a second air outlet 51 is provided on the PCB circuit board 5 and / or the mounting base 2. The first air outlet 24 and the second air outlet 51 are connected, and the airflow from the second, first, and third heat dissipation paths flows out through the second air outlet 51. During this flow, the airflow carries away the heat generated by the PCB circuit board 5, providing air cooling and ensuring a stable operating environment for the PCB circuit board 5, thus extending its service life.

[0511] In some embodiments, the mounting base 2 is provided with a plurality of connecting flanges at one end connected to the PCB circuit board 5, and there are flange gaps between adjacent connecting flanges. The PCB circuit board 5 is covered on the plurality of connecting flanges, and the PCB circuit board 5 and the flange gaps enclose and form a second air outlet 51.

[0512] The second air outlet 51 is formed by the gap between the PCB circuit board 5 and the baffle. The airflow blown out from the first air outlet 24 first contacts the PCB circuit board 5, and then blows out from the second air outlet 51 along the PCB circuit board 5. In this process, the contact area and time between the airflow and the PCB circuit board 5 are increased, thereby improving the heat dissipation efficiency and making the cooling effect more significant.

[0513] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0514] Please refer to Figure 30, which is a schematic diagram of the fan housing structure in this embodiment.

[0515] As shown in Figure 30, a fan assembly includes: a fan housing 1, a motor assembly 3, a mounting base 2, and fan blades 4. The motor assembly 3 is assembled inside the fan housing 1; the mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11, and the motor assembly 3 is connected to the mounting base 2; the fan blades 4 are connected to the motor assembly 3; the ends of the multiple stationary blades 11 facing the fan blades 4 have guide serrations 111.

[0516] The guide sawtooth 111 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the guide sawtooth 111, the intersection of the "V" shaped notches is smoothed, and the apex of the "V" shaped tooth marks is also smoothed.

[0517] In the above embodiment, multiple stationary blades 11 are arranged between the fan housing 1 and the mounting base 2, and each stationary blade 11 has a guide serration 111 at the end facing the fan blade 4. The airflow flowing out from the fan blade 4 has rotational potential energy, which will form a vortex. The guide serration 111 on the stationary blade 11 breaks the large vortex into multiple smaller vortices when it comes into contact with the vortex. When the smaller vortices collide with the stationary blade 11, they have less rotational potential energy, and the aerodynamic noise generated by the collision is greatly reduced. At the same time, the stationary blades 11 are statically arranged and serve to intercept and guide. When the airflow comes into contact with the guide serration 111, the airflow is intercepted and guided, while part of the airflow flows to the next stationary blade 11 through the gap in the guide serration 111. This part of the airflow has a longer movement space, and the position where it contacts and collides with the next stationary blade 11 is behind the guide serration 111 of that stationary blade 11. The guide serrations 111 can shift part of the collision position between the airflow and the stationary blades 11 to the rear, dispersing the total potential energy of the collision at the same position, and further reducing the aerodynamic noise of the fan assembly.

[0518] In some embodiments, the fan blade 4 is provided with a plurality of moving blades 42, and the end of the plurality of moving blades 42 facing the mounting base 2 is provided with a trailing edge serration 421.

[0519] The fan blades 4 also include a hub 41, with multiple moving blades 42 arranged around the hub 41.

[0520] The guide serrations 111 are disposed on the stationary blade 11, while the trailing edge serrations 421 are disposed on the moving blade 42. Since the airflow possesses rotational potential energy during flow, and the rotation direction of this potential energy is the same as the rotation direction of the moving blade 42, the trailing edge serrations 421 of the moving blade 42 perform co-directional cutting of the vortex. However, the guide serrations 111 disposed on the stationary blade 11 perform static blocking cutting of the vortex, resulting in higher cutting efficiency and a more pronounced vortex-breaking effect.

[0521] In this embodiment, the number of moving blades 42 is 9. However, the number of moving blades 42 is not limited to this. Depending on the specific application scenario, the number of moving blades 42 can be 2, 3, 4, 5, 6, 8, or more. The number of moving blades 42 can be determined according to the needs of the specific application scenario and is not limited to this specific embodiment.

[0522] The trailing edge serration 421 is composed of alternating "V" shaped notches and "V" shaped tooth marks. In some embodiments, in order to reduce the aerodynamic noise of the trailing edge serration 421, the intersection of the "V" shaped notches and the apex of the "V" shaped tooth marks are smoothed.

[0523] When the fan blade 4 rotates, it generates a vortex at the trailing edge of the blade. A trailing edge serration 421 is provided on the moving blade 42. When the trailing edge serration 421 comes into contact with the vortex, it breaks the large vortex into multiple smaller vortices, and the aerodynamic noise generated by the smaller vortices is greatly reduced.

[0524] When trailing edge serrations 421 are provided on the moving blade 42 and guide serrations 111 are provided on the stationary blade 11, the guide serrations 111 can break up and decompose the outflowing vortex, while the guide serrations 111 on the stationary blade 11 further decompose the broken up and decomposed vortex. The two processes of breaking up and decomposing the vortex inside the fan assembly are miniaturized, which reduces the aerodynamic noise of the fan assembly to the greatest extent.

[0525] In some embodiments, each of the plurality of stationary blades 11 extends curvedly along the inner surface of the fan housing 1, and the plurality of moving blades 42 extend curvedly along the surface of the hub 41 of the fan blades 4, and the bending direction of the plurality of stationary blades 11 is opposite to the rotation direction of the plurality of moving blades 42.

[0526] In this embodiment, the bending direction of the stationary blade 11 being opposite to the rotation direction of the moving blade 42 means that the bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42, and is not limited to the specific embodiment where the bending direction of the stationary blade 11 is 180° to the rotation direction of the moving blade 42. In some embodiments, when the extension line of the bending of the stationary blade 11 forms an obtuse angle with the rotation direction of the moving blade 42, it is also within the scope of the opposite definition in this embodiment.

[0527] The bending direction of the stationary blade 11 is opposite to the rotation direction of the moving blade 42. When the moving blade 42 rotates, it will drive the airflow to rotate in the same direction. At this time, the bending direction of the stationary blade 11 is opposite to the rotation direction of the airflow. When the airflow rotates, it comes into contact with the curved part of the stationary blade 11. Since the directions are opposite, the angle between the airflow and the curved part of the stationary blade 11 is greater than 90 degrees. The airflow comes into contact with the stationary blade 11 at a larger angle, which can reduce the kinetic energy loss of the airflow when contacting the stationary blade 11. During the larger angle contact process, the guiding effect of the stationary blade 11 on the airflow is obvious, the energy loss is small, and the air outlet efficiency is greatly improved.

[0528] In some embodiments, the tooth marks of the guide serration 111 are inclined. The guide serration 111 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the guide serration 111 can be inclined from the fan housing 1 towards the mounting base 2, or from the mounting base 2 towards the fan housing 1.

[0529] In some embodiments, the tooth marks of the trailing edge serration 421 are inclined. The trailing edge serration 421 is disposed between the fan housing 1 and the mounting base 2, so the tooth marks of the trailing edge serration 421 can be inclined from the fan housing 1 toward the mounting base 2, or from the mounting base 2 toward the fan housing 1.

[0530] In some embodiments, the tooth marks of the guide serration 111 are inclined, and the tooth marks of the trailing edge serration 421 are also inclined.

[0531] In some embodiments, the tooth marks of the guide serration 111 are aligned with the inclination direction of the tooth marks of the trailing edge serration 421.

[0532] When the inclination direction of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 is consistent, the guide sawtooth 111 and the trailing sawtooth 421 can perform secondary dispersion and decomposition on the airflow with the same flow direction, making the vortex decomposition effect of the inclination direction more obvious.

[0533] In some embodiments, the tooth marks of the guide serration 111 are tilted in the opposite direction to the tooth marks of the trailing edge serration 421.

[0534] When the inclination directions of the tooth marks of the guide sawtooth 111 and the trailing sawtooth 421 are opposite, the guide sawtooth 111 and the trailing sawtooth 421 can break down the vortices that their inclination directions point to, so that the vortex area broken down by the guide sawtooth 111 and the trailing sawtooth 421 is wider.

[0535] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the direction of the fan housing 1, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the direction of the fan housing 1.

[0536] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The tooth marks of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Similarly, the tooth marks of the trailing edge serrations 421 are also inclined towards the fan housing 1, again aligning their inclination with the airflow direction. This increases the contact area between the tooth marks and the airflow, further enhancing their efficiency in dispersing and decomposing the airflow. Furthermore, since both tooth marks are inclined in the same direction as the airflow, the wind resistance of the guide serrations 111 and trailing edge serrations 421 is reduced, improving the airflow efficiency. The tooth marks of the guide sawtooth 111 and the trailing edge sawtooth 421 are both inclined toward the fan housing 1, which can further disperse and decompose the airflow with the same flow direction, making the vortex decomposition effect in the inclined direction more obvious.

[0537] In some embodiments, the tooth marks of the guide serration 111 are inclined toward the fan housing 1, and the tooth marks of the trailing edge serration 421 are inclined toward the mounting base 2.

[0538] The airflow exiting the fan blades 4 rotates in a spiral motion from the fan blades 4 towards the fan housing 1. The serrations of the guide serrations 111 are inclined towards the fan housing 1, aligning their inclination with the airflow direction. This increases the contact area between the serrations and the airflow, resulting in higher efficiency in dispersing and decomposing the airflow. Meanwhile, the serrations of the trailing edge serrations 421 are inclined towards the mounting base 2, opposite to the airflow direction. This reverse-direction arrangement allows for multiple decompositions of the laterally moving airflow, resulting in more thorough dispersal of vortices. Furthermore, both the guide serrations 111 and 421 can disperse and decompose vortices in their respective inclination directions, expanding the vortex area dispersed by the guide serrations 111 and 421.

[0539] In some embodiments, the tooth marks of the guide saw teeth 111 are inclined toward the mounting base 2, and the tooth marks of the trailing edge saw teeth 421 are inclined toward the fan housing 1. The guide saw teeth 111 and the trailing edge saw teeth 421 can break down and decompose the vortices in their respective inclined directions, so that the vortex areas broken down and decomposed by the guide saw teeth 111 and the trailing edge saw teeth 421 are larger.

[0540] In some embodiments, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 are both inclined toward the mounting base 2.

[0541] In some embodiments, the tooth marks of the guide serration 111 correspond to and engage with the tooth marks of the trailing edge serration 421.

[0542] In this embodiment, the tooth marks of the guide saw teeth 111 and the tooth marks of the trailing edge saw teeth 421 correspond to each other, meaning that the tooth marks of the trailing edge saw teeth 421 are provided at the position where the extension line of the tooth marks of the guide saw teeth 111 intersects with the position of the trailing edge saw teeth 421; conversely, the tooth marks of the guide saw teeth 111 are provided at the position where the extension line of the tooth marks of the trailing edge saw teeth 421 intersects with the position of the guide saw teeth 111.

[0543] The serrations of the guide serration 111 and the trailing edge serration 421 correspond and cooperate with each other, and the serrations of the trailing edge serration 421 have the function of dividing the airflow. The divided airflow will reconverge at the guide serration 111, and the converged airflow will be dispersed and divided again by the serrations of the guide serration 111, preventing the vortex from reconverging and improving the vortex division effect.

[0544] In some embodiments, the tooth marks of the guide serration 111 and the tooth marks of the trailing edge serration 421 are misaligned and matched.

[0545] In this embodiment, the misalignment of the tooth marks of the guide sawtooth 111 and the tooth marks of the trailing sawtooth 421 means that: a notch of the trailing sawtooth 421 is provided at the position where the extension line of the tooth mark of the guide sawtooth 111 intersects with the trailing sawtooth 421; conversely, a notch of the guide sawtooth 111 is provided at the position where the extension line of the tooth mark of the trailing sawtooth 421 intersects with the guide sawtooth 111.

[0546] The tooth marks of the guide sawtooth 111 and the tooth marks of the trailing edge sawtooth 421 are staggered and matched. Both the tooth marks of the trailing edge sawtooth 421 and the tooth marks of the guide sawtooth 111 have the function of dividing the airflow. The two are staggered and can separate the vortices at different positions, increase the vortex division area, and further reduce aerodynamic noise.

[0547] In some embodiments, the length ratio of the stationary blade 11 to the moving blade 42 is 1.1-2.8. The length of the stationary blade 11 refers to the length between the end of the stationary blade 11 with the guide serrations 111 and the opposite end. The length of the moving blade 42 refers to the length between the end of the moving blade 42 with the trailing edge serrations 421 and the opposite end.

[0548] At the aforementioned length ratio, the length of the stationary blade 11 is greater than the length of the moving blade 42. When the fan blade 4 rotates, the moving blade 42 restrains and guides the airflow. If the moving blade 42 is too long, the rotational potential energy of the airflow will be too high. The main function of the stationary blade 11 is to counteract and convert the rotational potential energy of the airflow, causing it to move horizontally in a directional direction along the stationary blade 11. If the length of the stationary blade 11 is too short, the rotational potential energy of the airflow exiting the fan assembly will be too high, resulting in poor directional movement capability and a short directional air delivery distance.

[0549] Setting the length ratio of the stationary blade 11 to the moving blade 42 between 1.1 and 2.8 allows the rotational potential energy of the airflow exiting the fan blade 4 to be fully canceled and converted when passing through the moving blade 42, improving the overall airflow efficiency and directional air delivery capability of the fan assembly. Simultaneously, the airflow is blown out from the fan blade 4, guided by the stationary blade 11, and then blown out. During this process, due to the mounting base 2, the airflow space is compressed, resulting in a pressurized and accelerated airflow process. The relatively large length of the stationary blade 11 corresponds to the path length required for acceleration, thus improving the airflow acceleration efficiency.

[0550] When the ratio of the two is less than 1.1, the rotational potential energy of the airflow blown out by the fan assembly is too large, the diffusion surface of the airflow after it is blown out is too large, and the directional air delivery capability decreases. When the ratio of the two is greater than 2.8, the energy loss of the fan assembly within the fan housing 1 is too large, the initial kinetic energy of the airflow at the air outlet of the fan assembly decreases, which also reduces the directional air delivery capability of the fan assembly.

[0551] In some embodiments, the ratio of the number of stationary blades 11 to the number of moving blades 42 is 0.5-1.

[0552] When the ratio of stationary blades 11 to moving blades 42 is within a certain range, it can increase the airflow and air pressure of the fan assembly, resulting in a higher airflow speed. When the ratio of stationary blades 11 to moving blades 42 is less than 0.5, the number of stationary blades 11 is too small, and the stationary blades 11 are not sufficient to offset and convert the rotational potential energy of the airflow, reducing the directional airflow capability of the fan assembly. When the ratio of stationary blades 11 to moving blades 42 is greater than 1, the number of stationary blades 11 is too large, increasing the airflow resistance and reducing the airflow conversion efficiency.

[0553] Please refer to Figure 38, which is a schematic diagram of the hollow tube structure in this embodiment.

[0554] As shown in Figure 38, a fan assembly includes: a fan housing 1, a mounting base 2, and a motor assembly 3. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 via multiple stationary blades 11. The motor assembly 3 is assembled inside the fan housing 1. The mounting base 2 is provided with a hollow tube 23, and the motor assembly 3 is connected to the hollow tube 23. A first bearing 33 and a support member 35 are disposed inside the hollow tube 23. One end of the rotating shaft 313 of the motor assembly 3 is inserted into and passes through the support member 35 and the first bearing 33 in sequence, and the other end of the rotating shaft 313 extends out of the hollow tube 23. The fan blades 4 are connected to the end of the rotating shaft 313 that extends out of the hollow tube 23. A first elastic member 34 is compressed and disposed between the first bearing 33 and the support member 35. One end of the first elastic member 34 is connected to the support member 35, and the other end of the first elastic member 34 is connected to the first inner ring or the first outer ring of the first bearing 33.

[0555] In some embodiments, the mounting base 2 includes only a hollow tube 23. One end of a plurality of stationary blades 11 is wrapped around the hollow tube 23, and the other end of the plurality of stationary blades 11 is radially distributed and connected to the fan housing 1.

[0556] In some embodiments, the mounting base 2 includes a connecting cylinder 21, a connecting ring 22, and a hollow tube 23. The connecting cylinder 21 is disposed inside the fan housing 1 and is connected to the fan housing 1 through a plurality of stationary blades 11. The connecting ring 22 is disposed inside the connecting cylinder 21, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0557] In some embodiments, the mounting base 2 includes a connecting ring 22 and a hollow tube 23. The connecting ring 22 is connected to the fan housing 1 through a plurality of stationary blades 11, the hollow tube 23 is connected to the connecting ring 22, and the motor assembly 3 is connected to the hollow tube 23.

[0558] The connection methods between the hollow tube 23 and the connecting ring 22 include (but are not limited to): integral molding, plug-in, snap-fit, interference fit, welding, screw connection, adhesive connection, etc.

[0559] In this embodiment, the first elastic element 34 is (but is not limited to): a helical spring and a rubber spring. The material and structure of the first elastic element 34 can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0560] The first elastic element 34 is sleeved on the rotating shaft 313. However, the arrangement of the first elastic element 34 is not limited to this. Depending on the specific application scenario, in some embodiments, multiple first elastic elements 34 are provided, and multiple first elastic elements 34 are arranged around the rotating shaft 313 and are respectively connected to the support member 35 and the first bearing 33.

[0561] In this embodiment, the first bearing 33 is disposed at the first hollow end 231 of the hollow tube 23. However, the location of the first bearing 33 is not limited to this. In some embodiments, the first bearing 33 is disposed at the second hollow end 232 of the hollow tube 23.

[0562] In this embodiment, the connection method between the first elastic member 34 and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0563] In this embodiment, the connection method between the first elastic element 34 and the first bearing 33 includes (but is not limited to): abutment, welding or adhesive connection.

[0564] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0565] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0566] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0567] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0568] When the motor assembly 3 is a three-phase motor powered by a battery, the high-speed rotating motor assembly 3 is easily affected by minor vibrations, leading to significant aerodynamic noise and abnormal vibration in the fan assembly. By setting the first elastic element 34 to abut against the first bearing 33, abnormal vibrations caused by bearing structural design defects or errors are reduced, greatly lowering the aerodynamic noise of the fan assembly and improving the rotational stability of the fan assembly.

[0569] In the above embodiment, the first elastic element 34 is disposed between the support 35 and the first bearing 33, with one end of the elastic element connected to the support 35 and the other end connected to the first inner ring or the first outer ring of the first bearing 33. The first elastic element 34 is compressed between the first bearing 33 and the support 35, so that the first inner ring or the first outer ring of the first bearing 33 is always subjected to elastic force. After the first inner ring or the first outer ring is subjected to force, the first bearing 33 is always in a state of bridging the axial gap between the first inner ring and the first outer ring, that is, the balls between the first inner ring and the first outer ring are always clamped, and the axial gap between the first inner ring and the first outer ring is minimized. In the above state, the problem of vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates can be reduced, the vibration frequency of the fan blade 4 is greatly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. At the same time, the wear of the first bearing 33 can also be reduced, and the service life of the first bearing 33 can be extended.

[0570] In some embodiments, the fan assembly further includes: a second bearing 36, a first bearing 33 and a second bearing 36 respectively disposed at both ends of the hollow tube 23, a support member 35 disposed between the first bearing 33 and the second bearing 36, and one end of the rotating shaft 313 sequentially inserted into and through the second bearing 36, the support member 35 and the first bearing 33.

[0571] The arrangement of the first bearing 33 and the second bearing 36 enables the rotating shaft 313 to rotate more smoothly. At the same time, the arrangement of two rotating shafts 313 makes the linear rotation of the rotating shaft 313 more stable, enabling the fan motor to rotate at a faster speed.

[0572] In some embodiments, the first support end 351 of the support member 35 abuts against the second inner ring or the second outer ring of the second bearing 36, and the second support end 352 of the support member 35 is connected to the first elastic member 34.

[0573] To prevent axial displacement between the inner and outer rings of the second bearing 36, the first support end 351 of the support member 35 abuts against the second inner or outer ring of the second bearing 36. The abutment of the second outer or inner ring of the second bearing 36 by the support member 35 ensures that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the second inner and outer rings, meaning the balls between them are always tightly clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it also reduces wear on the second bearing 36 and extends its service life.

[0574] In some embodiments, a second elastic member (not shown) is compressed between the support member 35 and the second bearing 36. One end of the second elastic member is connected to the first support end 351 of the support member 35, and the other end of the second elastic member is connected to the second inner ring and the second outer ring of the second bearing 36.

[0575] In this embodiment, the second elastic element is (but is not limited to): a helical spring and a rubber spring. The material and structure of the second elastic element can be determined according to the needs of specific application scenarios and are not limited to specific embodiments.

[0576] The second elastic element is sleeved on the rotating shaft 313. However, the arrangement of the second elastic element is not limited to this. Depending on the specific application scenario, in some embodiments, multiple second elastic elements are provided, which are arranged around the rotating shaft 313 and respectively connected to the support member 35 and the second bearing 36.

[0577] In this embodiment, the second bearing 36 is disposed at the second hollow end 232 of the hollow tube 23. However, the placement of the second bearing 36 is not limited to this. In some embodiments, the positions of the first bearing 33 and the second bearing 36 can be interchanged, and the second bearing 36 is disposed at the first hollow end 231 of the hollow tube 23.

[0578] In some embodiments, the second elastic element can be disposed between the second bearing and the motor housing 311, with one end of the second elastic element abutting against the inner or outer ring of the second bearing and the other end connected to the motor housing 311.

[0579] To prevent axial displacement between the inner and outer rings of the second bearing 36, a second elastic element is provided between the support member 35 and the second bearing 36. One end of the second elastic element is connected to the second support end 352 of the support member 35, and the other end is connected to the second inner or outer ring of the second bearing 36. The second elastic element, when compressed, connects the second outer or inner ring of the second bearing 36, ensuring that the second inner or outer ring is always subjected to an axial force that brings them closer together. Under this force, the second bearing 36 remains in a state of closing the axial gap between the inner and outer rings, meaning the balls between them are always clamped, minimizing the axial gap. In this state, the vertical displacement along the axial direction when the shaft 313 of the motor assembly 3 rotates is reduced, the vibration frequency of the fan blades 4 is significantly reduced, and the abnormal noise caused by the displacement of the inner and outer rings of the bearing in the fan assembly disappears. Simultaneously, it reduces wear on the second bearing 36 and extends its service life.

[0580] By placing the second elastic element between the second bearing and the motor housing 311, the axial clearance between the second inner ring and the second outer ring can be minimized.

[0581] In this embodiment, the connection method between the second elastic member and the support member 35 includes (but is not limited to): abutment, welding, adhesive connection or integral molding.

[0582] In this embodiment, the connection method between the second elastic element and the second bearing 36 includes (but is not limited to): abutment, welding or adhesive connection.

[0583] In some embodiments, the support member 35 is interference-fitted with the hollow tube 23. The relative position between the support member 35 and the hollow tube 23 is fixed, keeping the first elastic member 34 and the second elastic member in a compressed state.

[0584] In this embodiment, the support member 35 is an independent ring structure disposed inside the hollow tube 23, and the support member 35 is sleeved on the rotating shaft 313. However, the arrangement of the support member 35 is not limited to this. Depending on the specific application scenario, in some embodiments, the support member 35 is a protrusion or a protruding ring formed by the protrusion inside the hollow tube 23.

[0585] Please refer to Figures 33 and 34. Figure 33 is a schematic diagram of the support structure in this embodiment; Figure 34 is a cross-sectional schematic diagram of the support in this embodiment.

[0586] As shown in Figures 33 and 34, in some embodiments, the thickness of the first support end 351 of the support member 35 gradually decreases along the direction from the second support end 352 to the first support end 351.

[0587] When the support member 35 is an independently constructed annular structure, it needs to be assembled into the hollow tube 23 via the first hollow end 231 or the second hollow end 232, and pushed to a fixed position to form an interference fit with the hollow tube 23 at that position. To facilitate assembly, the first support end 351, as the head structure of the support member 35, needs to have a certain deformation capacity to adapt to assembly even when there are errors in the inner diameter of the hollow tube 23. The thickness of the first support end 351 gradually decreases along the direction from the second support end 352 to the first support end 351. This allows the first support end 351 to be easily inserted into the assembly, and the gradual decrease in thickness also makes it more easily deformable under pressure, maximizing its adaptability to assembly apertures with errors within the hollow tube 23. This improves the assembly efficiency of the support member 35.

[0588] In some embodiments, the support member 35 has a first deformation notch 353 at its second support end 352. The first deformation notch allows the second support end 352 of the support member 35 to deform under pressure, facilitating easy assembly. This maximizes adaptability to assembly apertures with varying tolerances within the hollow tube 23, improving the assembly efficiency of the support member 35. Furthermore, when the support member 35 with the first deformation notch 353 is subjected to an external force from the first support end 351 towards the second support end 352, the connection point between the second support end 352 and the hollow tube 23 will flare outwards towards the hollow tube 23, forming a trumpet-shaped structure to resist external forces, thus improving the assembly stability and resistance to external forces of the support member 35.

[0589] In some embodiments, the support member 35 has a second deformation notch 354 at the second support end 352. The second deformation notch 354 has the same function as the first deformation notch 353, and will not be described again here.

[0590] In some embodiments, the outer surface of the support member 35 is raised to form a ridge 355. The ridge 355 reduces the contact area between the support member 35 and the hollow tube 23, and the space between the ridges 355 can serve as a space for the ridges 355 to deform under force, thereby reducing assembly resistance, improving assembly efficiency, and also reducing the risk of the support member 35 bursting through the hollow tube 23 during assembly.

[0591] In some embodiments, the first deformation notch 353 and the second deformation notch 354 are arranged opposite to each other. The arrangement of the first deformation notch 353 and the second deformation notch 354 opposite to each other maximizes the deformable range of the second support end 352.

[0592] In some embodiments, the protrusion height of the ridge 355 gradually decreases along the direction from the second support end 352 toward the first support end 351.

[0593] Because the support member 35 is assembled with the second support end 352 moving towards the first support end 351, the protrusion height of the ridge 355 gradually decreases along the direction from the second support end 352 to the first support end 351. That is, the position with the lowest protrusion height in the ridge 355 contacts the hollow tube 23 first during assembly. This reduces the assembly difficulty and makes the assembly resistance gradually increase with the depth of assembly, reducing the risk of the hollow tube 23 bursting during assembly.

[0594] In some embodiments, the end of the protruding ridge 355 facing the first support end 351 smoothly transitions with the surface of the support member 35. Since the support member 35 is assembled with the second support end 352 facing the first support end 351, the smooth transition between the end of the protruding ridge 355 facing the first support end 351 and the surface of the support member 35 effectively reduces assembly resistance and improves assembly efficiency. Simultaneously, it also prevents protruding foreign objects from scratching the inner wall of the hollow tube 23 during assembly.

[0595] In some embodiments, the motor assembly 3 includes a coil 321, which is sleeved on the hollow tube 23, and the support 35 and the second bearing 36 are located at the connection between the coil 321 and the hollow tube 23.

[0596] The coil 321 is fitted onto the hollow tube 23, and the connection between the two is an interference fit. Because the hollow tube 23 is hollow inside, its strength under stress is relatively lower compared to a solid structure of the same material, and it is at risk of local collapse under significant external forces. The support member 35 and the second bearing 36 are located at the connection point between the coil 321 and the hollow tube 23, providing support for the hollow tube 23, increasing its strength, and reducing the risk of collapse under stress.

[0597] In some embodiments, the support member 35 is assembled from the second hollow end 232 of the hollow tube 23 toward the first hollow end 231. Since the assembly directions are opposite, the support member 35 is assembled after being reversed.

[0598] As shown in Figure 28, a fan assembly includes: a fan housing 1, a mounting base 2, a motor assembly 3, and fan blades 4. The mounting base 2 is disposed inside the fan housing 1 and is connected to the fan housing 1 through multiple stationary blades 11; one end of the motor assembly 3 is inserted into and connected to the mounting base 2; the other end of the motor assembly 3 is inserted into and connected to the fan blades 4.

[0599] In some implementations, the motor assembly 3 is a three-phase motor, which has a higher rotational speed, thereby increasing the airflow rate and volume of the fan assembly.

[0600] In some implementations, the motor assembly 3 is powered by a battery, which can power two, three, four or more batteries in series.

[0601] In some embodiments, the rated operating voltage of the motor assembly 3 is 6-8.4V or 9-12.6V. When the rated operating voltage of the motor assembly 3 is 6-8.4V, the motor assembly 3 is powered by two batteries connected in series. Within this rated operating voltage range, the rated operating current of the motor assembly 3 is 0.1-2.9A, the rated power of the motor assembly 3 is 0.6-25W, and the speed of the motor assembly 3 is 14000-46000 rpm.

[0602] When the rated operating voltage of motor assembly 3 is 9-12.6V, motor assembly 3 is powered by three batteries connected in series. Under this rated operating voltage range, the rated operating current of motor assembly 3 is 0.08-2.7A, the rated power of motor assembly 3 is 0.7-33W, and the speed of motor assembly 3 is 14000-48000 rpm.

[0603] When motor assembly 3 is a three-phase motor powered by a battery, the fan assembly not only has requirements for speed but also for energy consumption. By improving the assembly structure of motor assembly 3 and fan blades 4, the torque required for fan blades 4 to rotate is reduced, thus lowering the kinetic energy required for their rotation. This reduces the energy consumption of the fan assembly, giving it a longer operating range. Simultaneously, the reduced torque improves the stability of fan blades 4's rotational posture at high speeds, reducing the probability of abnormal fan vibration.

[0604] The high-speed rotating motor assembly 3 easily generates a lot of heat in the motor assembly 3 and the mounting base 2. By guiding part of the high-pressure airflow generated by the fan blades into the first heat dissipation passage, the motor assembly 3 and the mounting base 2 are cooled, making the working state of the three-phase motor more stable.

[0605] In the above embodiment, one end of the motor assembly 3 is inserted into the mounting base 2, and the other end of the motor assembly 3 is inserted into the fan blade 4. This structure results in a smaller portion of the fan blade 4 covering the motor assembly 3 compared to a design where the motor assembly 3 is completely inserted into the fan blade 4, thus reducing the axial length of the fan blade 4. This reduction in axial length shortens the overall rotational arm of the fan blade 4, thereby reducing its rotational torque. The reduced rotational torque allows the fan blade 4 to rotate faster under the same output conditions of the motor assembly 3. The reduced rotational torque also decreases the abnormal centrifugal force caused by imbalance in the fan blade 4, making its rotation more stable, reducing the probability of abnormal vibration, and lowering the rotational noise of the fan blade 4.

[0606] In some embodiments, the fan blade 4 is provided with a connecting shaft post 43 and a plurality of reinforcing ribs 411. The plurality of reinforcing ribs 411 are arranged around the connecting shaft post 43. The motor assembly 3 abuts against the connecting shaft post 43 and / or the plurality of reinforcing ribs 411 to reduce the rotational torque of the fan blade 4.

[0607] The fan blade 4 includes a hub 41 and multiple moving blades 42. The multiple moving blades 42 are spaced apart on the surface of the hub 41. The hub 41 is hollow inside, and the connecting shaft 43 is located at the center of the hub 41.

[0608] The motor assembly 3 includes a motor stator 32 and a motor rotor 31. The motor stator 32 is connected to the mounting base 2, and the motor rotor 31 is sleeved on the motor stator 32, with one end of the motor rotor 31 inserted into the mounting base 2. The motor stator 32 includes an iron core 322 and a plurality of coils 321 wound on the iron core 322.

[0609] The motor stator 32 includes an iron core 322 and multiple coils 321 wound on the iron core 322. The iron core 322 is fitted onto a hollow tube 23.

[0610] The motor rotor 31 includes a shaft 313, a magnetic ring 312, and a motor housing 311. One end of the shaft 313 is inserted into the hollow tube 23 and fixed by connection with the first bearing 33 and the second bearing 34. The other end of the shaft 313 is connected to the connecting shaft 43 of the fan blade 4. The motor stator 32 is sleeved on the hollow tube 23 and is interference-fitted with the hollow tube 23. The magnetic ring 312 is sleeved on the motor stator 32, and the motor housing 311 is sleeved on the magnetic ring 312. The magnetic ring 312 and the motor stator 32 are magnetically coupled together, and the motor housing 311 is interference-fitted with the magnetic ring 312. The end of the motor housing 311 facing the fan blade 4 is interference-fitted with the shaft 313.

[0611] One end of the motor housing 311 in the motor assembly 3 is inserted into the mounting base 2, and the other end is inserted into the hub 41 of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411.

[0612] In this embodiment, when the motor assembly 3 is working, the motor stator 32 first performs electromagnetic conversion, driving the motor housing 311, which is fitted with a magnetic ring 312, to rotate; then the motor housing 311 drives the rotating shaft 313 to rotate; finally, the rotating shaft 313 drives the fan blades 4 to rotate. One end of the motor housing 311 inserted into the fan blades 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411. This creates friction between the motor housing 311 and the connecting shaft 43 and / or multiple reinforcing ribs 411 during rotation. When the motor housing 311 and the fan blades 4 rotate at the same frequency, this friction is converted into the rotational driving force of the fan blades 4, which is equivalent to increasing the radial contact area between the rotating shaft 313 and the fan blades 4, making the rotation of the fan blades 4 more stable.

[0613] In some embodiments, the hub 41 of the fan blade 4 is constructed in a conical, frustum-shaped, hemispherical, or bullet-shaped configuration. This structure results in varying lever arms between different parts of the hub 41 and the shaft 313 when the fan blade 4 rotates. The lever arm is largest at the end of the hub 41 where the motor housing 311 is inserted, resulting in a larger torque. Excessive torque differences at different positions of the hub 41 can lead to unstable rotation of the fan blade 4. The end of the motor housing 311 inserted into the fan blade 4 abuts against the connecting shaft 43 and / or multiple reinforcing ribs 411, effectively reducing the torque at the end of the hub 41 and decreasing the torque difference at different positions, thus making the fan blade 4 rotate more stably.

[0614] In some embodiments, when the motor housing 311 abuts against the reinforcing rib 411, the motor housing 311 abuts against only a portion of the structure of the reinforcing rib 411.

[0615] In some embodiments, the length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4.

[0616] The length of the motor assembly 3 inserted into the mounting base 2 is greater than the length of the motor assembly 3 inserted into the fan blade 4. This structure keeps the axial length of the fan blade 4 within an optimal range. This maximizes the speed of the fan blade 4 under the same output environment, making the rotation of the fan blade 4 more stable and the noise lower.

[0617] In some embodiments, the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 of the fan blade 4. The maximum outer diameter of the hub 41 is usually located at the end of the hub 41 near the connecting cylinder 21. The fact that the outer diameter of the mounting base 2 is the same as the maximum outer diameter of the hub 41 can minimize the wind resistance coefficient inside the fan housing 1 and improve the air output efficiency of the fan assembly.

[0618] Example 7

[0619] Please refer to Figures 39 and 40. Figure 39 is a schematic diagram of the shock-absorbing sleeve from a first perspective in this embodiment; Figure 40 is a schematic diagram of the shock-absorbing sleeve from a second perspective in this embodiment.

[0620] As shown in Figures 39 and 40, a shock-absorbing sleeve includes: a sleeve 1, shock-absorbing protrusions 2, and a first interference zone 3. The shock-absorbing protrusions 2 are distributed on the surface and / or both ends of the sleeve 1; the first interference zone 3 is distributed on the surface and / or both ends of the sleeve 1, and there is a thickness difference between the first interference zone 3 and its surrounding environment. The first interference zone 3 is located on the circumferential path of the sleeve 1 and / or the shock-absorbing protrusions 2, serving to block the circumferential extension trend of the sleeve 1 and / or the shock-absorbing protrusions 2.

[0621] In this embodiment, the sleeve 1 is constructed in a cylindrical shape. However, the shape of the sleeve 1 is not limited to this. Depending on the specific application scenario, the shape of the sleeve 1 can be adapted to the shape of the motor it is fitted with. For example, when the shape of the motor housing is prismatic, the shape of the sleeve 1 is correspondingly set to prismatic. Therefore, the shape of the sleeve 1 is not limited to the specific embodiment.

[0622] In this embodiment, the shock-absorbing protrusion 2 is a strip-shaped protrusion and / or a dot-shaped protrusion.

[0623] When the damping protrusion 2 is a strip-shaped protrusion, it can extend straight, obliquely, or curvedly along the first end 11 to the second end 12 of the damping sleeve. In some embodiments, the strip-shaped protrusion can also be arranged around the outer circumference of the sleeve 1, and the arrangement of the strip-shaped protrusion can be (but is not limited to): annular arrangement, spiral arrangement, bending arrangement, etc. The damping protrusion 2 can be a single, continuous strip-shaped protrusion, or it can be composed of two or more strip-shaped protrusions spaced apart. The cross-section of the strip-shaped protrusion can be (but is not limited to): semi-circular, elliptical, prismatic, etc. Depending on the specific application scenario, the arrangement direction, extension form, and cross-sectional shape of the strip-shaped protrusion can be combined to meet the needs of the scenario, and are not limited to the schemes listed in the specific embodiments.

[0624] When the damping protrusion 2 is a dot-shaped protrusion, the cross-sectional shape of the dot-shaped protrusion can be (but is not limited to): hemispherical, conical, frustum-shaped, triangular, quadrilateral, or other polygonal. The dot-shaped protrusions can be randomly distributed on the surface of the sleeve 1, or they can be arranged in a certain regular and orderly manner on the surface of the sleeve 1. Depending on the needs of the specific application scenario, the shape and arrangement of the dot-shaped protrusions can be configured to meet the requirements of the scenario, and are not limited to the schemes listed in the specific embodiments.

[0625] In some embodiments, the damping protrusion 2 includes strip-shaped protrusions and dot-shaped protrusions. The strip-shaped protrusions and dot-shaped protrusions can be alternately arranged or can be located in two separate areas.

[0626] In this embodiment, the first interference zone 3 is a groove or a protrusion on the surface of the sleeve 1. When the first interference zone 3 is a groove, its thickness is less than the thickness of the sleeve 1 at that location. When the first interference zone 3 is a protrusion, its thickness is greater than the thickness of the sleeve 1 at that location or the thickness of the damping protrusion 2 on the sleeve 1.

[0627] In some embodiments, the first interference zone 3 includes a groove and a protrusion, which are respectively disposed at different positions on the surface of the sleeve 1.

[0628] The first interference zone 3 is disposed on the outer surface of the sleeve 1 to block the extension trend of the sleeve 1 and / or the damping protrusion 2 in the circumferential direction. The first interference zone 3 can extend from the first end 11 of the sleeve 1 to the second end 12 opposite to the first end 11, or it can be disposed at a local position between the first end 11 and the second end 12. The first interference zone 3 can laterally block the extension trend of the entire sleeve 1 and all the damping protrusions 2, or it can only block the extension trend of a part of the sleeve 1 or a single damping protrusion 2.

[0629] In this embodiment, the obstruction refers to the fact that the groove formed by the protrusions or concave sections hinders the extension trend of the sleeve 1 or the damping protrusion 2 in the circumferential direction of the sleeve 1, thus interrupting or partially interrupting the original extension trend of the sleeve 1 or the damping protrusion 2. Since the sleeve 1 itself needs to maintain the closure of its surface, the first interference area 3 cannot completely disconnect the sleeve 1. Therefore, the obstruction does not mean isolation, but rather hindrance or partial interruption.

[0630] In this embodiment, "delay" refers to both extension and transmission. In the circumferential direction of the sleeve 1, the sleeve 1 is designed to have a tendency to circumferentially close with a constant thickness, and the damping protrusion 2 also has a tendency to circumferentially close with a constant thickness or to intermittently encircle. Regarding the transmission of mechanical waves, the sleeve 1 and the damping protrusion 2 also have a tendency to transmit the mechanical wave with a constant thickness. The first interference zone 3 is disposed on the circumferential path of the sleeve 1 and / or the damping protrusion 2, serving to block the tendency of the sleeve 1 and / or the damping protrusion 2 to extend with the same thickness, and to block the transmission of mechanical waves in a medium of the same thickness.

[0631] In the above embodiment, the main body of the shock-absorbing sleeve is constructed as a sleeve 1. The surface of the sleeve 1 is provided with shock-absorbing protrusions 2, and a first interference zone 3 is also provided on the outer surface of the shock-absorbing sleeve. The first interference zone 3 has a thickness difference with its surrounding environment. Specifically, a first interference zone 3 is formed on the surface of the sleeve 1 with a thickness greater than the thickness of the sleeve 1 or the thickness of the sleeve 1 plus the shock-absorbing protrusions 2, or a thickness less than the thickness of the sleeve 1 or the thickness of the sleeve 1 plus the shock-absorbing protrusions 2. The thickness of the first interference zone 3 differs from the thickness of the surrounding environment, and the first interference zone 3 is located on the circumferential path of the sleeve 1 and / or the shock-absorbing protrusions 2. When mechanical waves propagate circumferentially through the shock-absorbing sleeve, the thickness of the medium along the transmission path of the mechanical waves changes. At the interface between thick and thin media, mechanical waves undergo refraction, interference, diffraction, divergence, and dispersion. These phenomena accelerate the attenuation of the mechanical waves, enhance the shock-absorbing effect of the shock-absorbing sleeve, and thus make the noise reduction effect of the shock-absorbing sleeve more significant. At the same time, the attenuation speed of mechanical waves increases, reducing the probability of mechanical waves superimposing with other mechanical waves, thereby further enhancing the shock absorption and noise reduction effects of the damping sleeve.

[0632] Please refer to Figures 41 and 42. Figure 41 is a schematic diagram of the shock-absorbing sleeve from the third perspective of this embodiment; Figure 42 is a schematic diagram of the shock-absorbing sleeve from the fourth perspective of this embodiment.

[0633] As shown in Figures 41 and 42, in some embodiments, the shock-absorbing protrusion 2 includes at least one first protrusion 21, which is continuously arranged circumferentially along the outer wall of the sleeve 1 and forms a closed-loop structure.

[0634] The number of first protrusions 21 can be 1, 2, 3 or more. The number of first protrusions 21 can be set according to the needs of specific application scenarios and is not limited to the number specified in the specific embodiment.

[0635] The first protrusion 21 is continuously arranged along the circumferential direction of the outer wall of the sleeve 1, forming a closed-loop structure. When the first protrusion 21 extends along the circumferential direction of the outer wall of the sleeve 1, the extension method of the first protrusion 21 can be smooth extension or curved extension. The extension method of the first protrusion 21 can be flexibly selected according to the needs of specific application scenarios, and is not limited to specific embodiments.

[0636] In some embodiments, the shock-absorbing sleeve is provided with two first protrusions 21, which are respectively located near the first end 11 and the second end 12 of the sleeve 1.

[0637] The first protrusion 21 reduces the resistance between the damping sleeve and the outer housing (not shown), facilitating their assembly. The protruding structure of the first protrusion 21 provides greater deformation space under external force, resulting in better buffering and noise reduction. Furthermore, since the first protrusion 21 is continuously arranged, it can transfer force to other locations after localized stress, thus distributing the load.

[0638] In some embodiments, the damping protrusion 2 includes at least one second protrusion 22, which is circumferentially spaced along the outer wall of the sleeve 1.

[0639] The number of second protrusions 22 can be 1, 2, 3 or more. The number of second protrusions 22 can be set according to the needs of specific application scenarios and is not limited to the number specified in the specific embodiment.

[0640] The second protrusion 22 is a strip-shaped protrusion. However, the shape of the second protrusion 22 is not limited to this. Depending on the specific application scenario, in some embodiments, the shape of the second protrusion 22 can be a dot-shaped protrusion. Therefore, the shape of the second protrusion 22 can be selected according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0641] The second protrusions 22 are evenly spaced. However, the arrangement of the second protrusions 22 is not limited to this. Depending on the specific application scenario, in some embodiments, the second protrusions 22 are irregularly spaced. Therefore, the arrangement of the second protrusions 22 can be selected according to the needs of the specific application scenario and is not limited to the specific embodiment.

[0642] In some embodiments, the shock-absorbing sleeve is provided with two first protrusions 21 and one second protrusion 22, with the second protrusion 22 positioned between the two first protrusions 21. However, the number and relative positional relationship of the first protrusions 21 and the second protrusion 22 are not limited thereto, and can be set according to the needs of specific application scenarios, and are not limited to specific embodiments.

[0643] In some embodiments, the second protrusion 22 includes a plurality of protrusion segments 221, which are spaced apart circumferentially along the outer wall of the sleeve 1.

[0644] The second protrusion 22 includes two, three, four, or more protrusion segments 221. The number of protrusion segments 221 can be set according to the needs of specific application scenarios and is not limited to specific embodiments.

[0645] The second protrusion 22 reduces the resistance between the damping sleeve and the outer housing (not shown), facilitating their assembly. The protruding structure of the second protrusion 22 provides greater deformation space under external force, resulting in better cushioning and noise reduction. Furthermore, because the second protrusion 22 is spaced apart, its overall structure exhibits varying thickness; this thickness variation accelerates the attenuation of mechanical waves, further enhancing the damping and noise reduction effects of the damping sleeve.

[0646] In some embodiments, the first interference zone 3 includes at least one first groove 31 extending from the first end 11 of the sleeve 1 to the second end 12 of the sleeve 1.

[0647] The number of first slots 31 can be 1, 2, 3 or more. The number of first slots 31 can be set according to the needs of specific application scenarios and is not limited to the number specified in the specific embodiment.

[0648] The first groove 31 extends from the first end 11 to the second end 12, penetrating the surface area of ​​the sleeve 1. However, the positional relationship of the first groove 31 relative to the sleeve 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the first groove 31 is only disposed between the first end 11 and the first protrusion 21, or at a partial location between the first end 11 and the extended first protrusion 21. Therefore, the length and position of the first groove 31 on the sleeve 1 can be set according to the needs of the specific application scenario, and are not limited to the specific embodiments exemplified.

[0649] In some embodiments, the first interference zone 3 includes at least one second groove 32 extending from the first end 11 of the sleeve 1 to the second end 12 of the sleeve 1.

[0650] The number of second slots 32 can be 1, 2, 3 or more. The number of second slots 32 can be set according to the needs of specific application scenarios and is not limited to the number specified in the specific embodiment.

[0651] The second groove 32 extends from the first end 11 to the second end 12, penetrating the surface area of ​​the sleeve 1. However, the positional relationship of the second groove 32 relative to the sleeve 1 is not limited to this. Depending on the specific application scenario, in some embodiments, the second groove 32 is only disposed between the first end 11 and the first protrusion 21, or at a partial location between the first end 11 and the protrusion 21 extending outward. Therefore, the length and position of the second groove 32 on the sleeve 1 can be set according to the needs of the specific application scenario, and are not limited to the specific embodiments exemplified.

[0652] In some embodiments, the damping sleeve is provided with a first groove 31 and a second groove 32. However, the first interference area 3 on the damping sleeve is not limited to this; in some embodiments, the damping sleeve is provided with only the first groove 31 or the second groove 32.

[0653] The arrangement of the first groove 31 and the second groove 32 causes mechanical waves to undergo refraction, interference, diffraction, divergence, and dispersion at the interface between thick and thin media when they are transmitted between the sleeve 1 and the first interference zone 3. These phenomena accelerate the attenuation of mechanical waves, enhance the damping effect of the damping sleeve, and thus make the noise reduction effect of the damping sleeve more significant.

[0654] In some embodiments, the width of the first groove 31 is smaller than the width of the second groove 32. The smaller width of the first groove 31 compared to the second groove 32 creates grooves of different widths on the surface of the sleeve 1. The different widths of the grooves have different interference effects on the transmission of mechanical waves. After being attenuated by the different grooves, the mechanical waves interfere with each other when they meet during transmission, further accelerating the attenuation efficiency.

[0655] In some embodiments, the width ratio of the first groove 31 to the width ratio of the second groove 32 is 1.1-4. Within this range, the damping effect of the shock-absorbing sleeve is superior. In some embodiments, the width ratio of the first groove 31 to the width ratio of the second groove 32 is a non-integer value. A non-integer width ratio can prevent waveforms from the same vibration source from superimposing at other positions of the sleeve 1 through the first groove 31 and the second groove 32, causing vibrations with larger amplitudes, thus making the damping effect of the shock-absorbing sleeve even better.

[0656] In some embodiments, the first groove 31 and the second groove 32 are disposed opposite to each other on both sides of the sleeve 1. The first groove 31 and the second groove 32 are disposed opposite to each other so that the first groove 31 and the second groove 32 have the maximum distance in the radial direction. The mechanical wave attenuated by the first groove 31 and the second groove 32 has a sufficiently long interference distance, thereby increasing the attenuation rate.

[0657] Please refer to Figure 43, which is a cross-sectional view of the shock-absorbing sleeve AA in this embodiment.

[0658] As shown in Figure 43, in some embodiments, the second groove 32 forms a deformable notch 321 at the first end 11 of the sleeve 1, and the deformable notch 321 makes the first end 11 of the sleeve 1 an assembly end.

[0659] The second groove 32 forms a deformable notch 321 at the first end 11. The deformable notch 321 makes it easier for the first end 11 of the sleeve 1 to expand and open, facilitating the insertion of the motor into the shock-absorbing sleeve and improving the assembly efficiency between the shock-absorbing sleeve and the motor. At the same time, the deformable notch 321 completely cuts off the sleeve 1 and the first interference zone 3 in the circumferential direction, making the mechanical wave attenuation speed at this location faster.

[0660] In some embodiments, the shock-absorbing sleeve further includes a second interference zone 4, which has a thickness difference with its surrounding environment, and is distributed circumferentially along the inner wall of the sleeve 1.

[0661] In this embodiment, the second interference zone 4 is a groove or a protrusion on the surface of the sleeve 1. When the second interference zone 4 is a groove, its thickness is less than the thickness of the sleeve 1 at that location. When the second interference zone 4 is a protrusion, its thickness is greater than the thickness of the sleeve 1 at that location.

[0662] The second interference zone 4 is located on the inner surface of the sleeve 1. Regardless of whether the second interference zone 4 is a groove or a protrusion, after assembly with the motor, it will form an airbag structure (not shown in the figure) between the motor housing and the shock-absorbing sleeve. The airbag structure has a good buffering effect, improving the buffering effect of the shock-absorbing sleeve. At the same time, due to the thickness difference between the second interference zone 4 and the surrounding environment, mechanical waves will undergo refraction, interference, diffraction, divergence, and dispersion at the interface between thick and thin media. These phenomena will accelerate the attenuation of mechanical waves. Combined with the attenuation of mechanical waves by the first interference zone 3, the shock-absorbing effect of the shock-absorbing sleeve is further enhanced, thus making the noise reduction effect of the shock-absorbing sleeve more significant. The setting of the second interference zone 4 can also reduce the resistance during motor assembly, making the assembly between the motor and the shock-absorbing sleeve more efficient.

[0663] In some embodiments, the second interference zone 4 includes a plurality of third grooves 41, which are spaced apart circumferentially along the inner wall of the sleeve 1.

[0664] The number of third slots 41 can be 2, 3, 4 or more. The number of third slots 41 can be set according to the needs of specific application scenarios and is not limited to the number specified in the specific embodiment.

[0665] After the shock-absorbing sleeve is assembled with the motor, multiple third grooves 41 will form multiple independently spaced airbag structures between the shock-absorbing sleeve and the motor. The airbag structure has a good cushioning effect, improving the cushioning effect of the shock-absorbing sleeve.

[0666] Example 8

[0667] A blower device includes the fan assembly described in Examples 1-7, wherein the fan assembly serves as a core module component for assembling the blower device.

[0668] It should be noted that the air-blowing device in this embodiment includes (but is not limited to): bladeless fans, desktop fans, floor fans, spherical fans, neck fans, handheld fans, industrial fans, air conditioners, hair dryers, and other products that require the propulsion of airflow. The fan assemblies in embodiments 1-7 are assembled inside the housing of the aforementioned products.

[0669] It should be noted that any of the embodiments in this example can be implemented independently or in combination with one or more other embodiments. When implementing in combination, the combination method should not be limited to the combination methods listed in this example.

[0670] It should be noted that while preferred embodiments of this application are provided in the specification and accompanying drawings, this application can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are not intended to impose additional limitations on the content of this application; their purpose is to provide a more thorough and comprehensive understanding of the disclosure of this application. Furthermore, the above-described technical features can be combined with each other to form various embodiments not listed above, all of which are considered to be within the scope of this application's specification. Moreover, those skilled in the art can make improvements or modifications based on the above description, and all such improvements and modifications should fall within the protection scope of the appended claims.

Claims

1. A fan assembly, wherein, include: Fan housing; A mounting base, which is disposed within the fan housing and connected to the fan housing via multiple stationary blades; a motor assembly, which is mounted within the fan housing and connected to the mounting base; Fan blades, the fan blades being connected to the motor assembly; the plurality of stationary blades having guide serrations formed at the ends facing the fan blades; or, The mounting base is provided with a hollow tube, and the motor assembly is connected to the hollow tube. A first bearing and a support member are disposed inside the hollow tube. One end of the motor assembly's shaft is inserted into and exits the support member and the first bearing in sequence, and the other end of the shaft extends out of the hollow tube. The fan blade is connected to the end of the shaft extending out of the hollow tube. A first elastic member is compressed and disposed between the first bearing and the support member. One end of the first elastic member is connected to the support member, and the other end of the first elastic member is connected to the first inner ring or the first outer ring of the first bearing; or... A fan blade is connected to the motor assembly; one end of the motor assembly is inserted into the mounting base; there is an air inlet gap between the fan blade and the mounting base; there is a first assembly gap between the motor assembly and the mounting base; a first air outlet is provided on the mounting base; the air inlet gap, the first assembly gap, and the first air outlet form a first heat dissipation path; or... The fan blades, with the other end of the motor assembly inserted into and connected to the fan blades; or... A sleeve, which is fitted onto the fan housing; shock-absorbing protrusions, which are distributed on the surface and / or at both ends of the sleeve; a first interference zone, which is distributed on the surface and / or at both ends of the sleeve, having a thickness difference between the first interference zone and its surrounding environment, and located on the circumferential path of the sleeve and / or the shock-absorbing protrusions, for blocking the circumferential extension trend of the sleeve and / or the shock-absorbing protrusions.

2. The fan assembly according to claim 1, wherein, The fan blades are provided with multiple moving blades, and the ends of the multiple moving blades facing the mounting base are provided with trailing edge serrations.

3. The fan assembly according to claim 2, wherein, Each of the plurality of stationary blades extends and bends along the inner surface of the fan housing, and the plurality of moving blades extends and bends along the hub surface of the fan blades, with the bending direction of the plurality of stationary blades opposite to the rotation direction of the plurality of moving blades.

4. The fan assembly according to claim 2, wherein, The tooth marks of the guide saw teeth are set at an angle; and / or, The serrations on the trailing edge are set at an angle.

5. The fan assembly according to claim 4, wherein, The inclination direction of the tooth marks of the guide serrations is consistent with that of the tooth marks of the trailing edge serrations; or... The inclination direction of the tooth marks of the guide saw teeth is opposite to that of the tooth marks of the trailing edge saw teeth.

6. The fan assembly according to claim 5, wherein, The tooth marks of the guide serrations are inclined towards the fan housing, and the tooth marks of the trailing edge serrations are inclined towards the fan housing; or... The tooth marks of the guide serrations are inclined towards the fan housing, and the tooth marks of the trailing edge serrations are inclined towards the mounting base; or... The tooth marks of the guide saw teeth are inclined toward the mounting base, and the tooth marks of the tail edge saw teeth are inclined toward the fan housing.

7. The fan assembly according to claim 2, wherein, The tooth marks of the guide saw teeth correspond and fit with the tooth marks of the trailing edge saw teeth; or... The tooth marks of the guide saw teeth are misaligned with the tooth marks of the tail edge saw teeth.

8. The fan assembly according to claim 1, wherein, The fan assembly further includes: a second bearing, wherein the first and second bearings are respectively disposed at both ends of the hollow tube, the support member is disposed between the first and second bearings, and one end of the rotating shaft is sequentially inserted into and passes through the second bearing, the support member, and the first bearing; and / or, The motor assembly is a three-phase motor; and / or, The motor assembly is powered by a battery.

9. The fan assembly of claim 8, wherein, The first supporting end of the support member abuts against the second inner ring or the second outer ring of the second bearing, and the second supporting end of the support member is connected to the first elastic member; and / or The rated operating voltage of the motor assembly is 6-8.4V or 9-12.6V; and / or, The rated operating current of the motor assembly is 0.1-2.9A or 0.08-2.7A; and / or, The rated power of the motor assembly is 0.6-25W or 0.7-33W; and / or, The motor assembly rotates at a speed of 14,000-48,000 revolutions per minute.

10. The fan assembly of claim 8, wherein, A second elastic element is compressibly disposed between the support member and the second bearing. One end of the second elastic element is connected to the first support end of the support member, and the other end of the second elastic element is connected to the second inner ring and the second outer ring of the second bearing; or... A second elastic element is compressed between the second bearing and the motor housing of the motor assembly. One end of the second elastic element is connected to the motor housing, and the other end of the second elastic element abuts against the second bearing.

11. The fan assembly of claim 8, wherein, The support member is interference-fitted with the hollow tube, and the thickness of the first support end of the support member gradually decreases along the direction from the second support end to the first support end.

12. The fan assembly of claim 11, wherein, The support member has a first deformation notch at the second support end; and / or, The support member has a second deformation notch at the second support end; and / or, The outer surface of the support member has raised ridges.

13. The fan assembly of claim 12, wherein, The first deformation notch and the second deformation notch are disposed opposite to each other; and / or, The protrusion height of the convex ridge gradually decreases along the direction from the second support end to the first support end; and / or, The end of the protruding ridge facing the first support end smoothly transitions to the surface of the support member.

14. The fan assembly of claim 1, wherein, The mounting base includes: a connecting cylinder, which is connected to the fan housing via the plurality of stationary blades; one end of the motor assembly is inserted into the connecting cylinder; and a first assembly gap exists between the connecting cylinder and the motor assembly; and / or... The outer diameter of the mounting base is the same as the maximum outer diameter of the hub of the fan blades; and / or, The motor assembly is a three-phase motor; and / or, The motor assembly is powered by a battery.

15. The fan assembly of claim 14, wherein, The mounting base further includes a connecting ring and a hollow tube. The connecting ring is disposed inside the connecting cylinder, the hollow tube is connected to the connecting ring, and the motor assembly is connected to the hollow tube.

16. The fan assembly of claim 14, wherein, The motor assembly includes a motor stator and a motor rotor. The motor stator is connected to the mounting base, and the motor rotor is sleeved on the motor stator. One end of the motor rotor is inserted into the mounting base, and there is a first assembly gap between the motor rotor and the mounting base.

17. The fan assembly of claim 16, wherein, The motor rotor has an air inlet opening, and there is a coil gap between the motor stators. The air inlet opening, the coil gap, and the first air outlet hole form a second heat dissipation passage. And / or, The motor rotor has an air inlet opening, and there is a coupling gap between the motor stator and the motor rotor. The air inlet opening, the coupling gap, and the first air outlet hole form a third heat dissipation channel.

18. The fan assembly of claim 17, wherein, The motor rotor includes a magnetic ring and a motor housing. The magnetic ring is sleeved on the motor stator, and the motor housing is sleeved on the magnetic ring. There is a first assembly gap between the motor housing and the mounting base. One end of the motor housing is inserted into the mounting base, and the air inlet is provided at the end of the motor housing facing the fan blade.

19. The fan assembly of claim 17, wherein, The motor assembly further includes: a rotating shaft, one end of which is connected to the mounting base, and the other end of which is connected to the fan blades; a motor rotor is connected to the rotating shaft, and the end of the motor rotor facing the fan blades is inserted into the fan blades; a second assembly gap exists between the fan blades and the motor rotor; the second assembly gap, the air inlet, the coil gap, and the first air outlet form a second heat dissipation passage.

20. The fan assembly of claim 1, wherein, The first interference zone includes: at least one first groove extending from a first end of the sleeve to a second end of the sleeve; and / or, The first interference zone includes at least one second groove extending from the first end of the sleeve to the second end of the sleeve.

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