Two-stage diffuser high-speed high-wind-pressure fan

Abstract

The utility model discloses a two-stage pressure expansion's high -speed high wind pressure fan, including the casing, rotor subassembly, stator subassembly, fan blade subassembly, the fan blade includes the hub and the moving blade, the moving blade evenly distributes on the mounting surface of hub, the mounting surface is the rotary curved surface with the arc segment as the generatrix, the radius of rotary curved surface is gradually increased from the air inlet end to the air outlet end, the width of moving blade is gradually reduced from the air inlet end to the air outlet end, forms the moving wind channel between two adjacent moving blades, the cross -sectional area of moving wind channel is gradually increased from the air inlet end to the air outlet end, the cooperation clearance between the inner surface of fan blade cover and the long side of moving blade is equal or gradually expands from the air inlet end to the air outlet end, through the cooperation and design of the gradually expanding of moving wind channel and the cooperation clearance gradually expanding between fan blade cover and moving blade, have solved the technical problem of the air current pressure loss of the existing dust collector fan, resulting in the wind pressure reduction and the low output efficiency of the air volume.

Description

Technical Field

[0001] This utility model relates to the technical field of high-speed, high-pressure fans, and in particular to a two-stage diffuser high-speed, high-pressure fan. Background Technology

[0002] In the modern home cleaning industry, vacuum cleaners, as essential cleaning equipment, rely heavily on the air pressure and airflow of their fans for core performance. High air pressure and large airflow enable vacuum cleaners to generate powerful suction, achieving efficient cleaning of deep-seated dust, large particles of debris, and dirt in carpets and sofa crevices. As consumers' demands for cleaning effectiveness continue to rise, and cleaning scenarios become increasingly diverse, higher standards are being set for the air pressure and airflow of vacuum cleaner fans. However, most vacuum cleaners currently on the market use fans that are significantly insufficient in terms of air pressure and airflow, failing to meet users' needs for deep cleaning. From a structural design perspective, the impeller and volute of traditional vacuum cleaner fans are poorly matched. The shape, angle, and number of impeller blades lack precise aerodynamic optimization, resulting in low efficiency in converting mechanical energy into air pressure energy during rotation. For example, some fan impellers have a single blade angle, failing to effectively guide airflow, causing turbulence and significant energy loss in ineffective turbulence, making it difficult to increase air pressure. Meanwhile, the unreasonable design of the volute profile prevents it from fully collecting and guiding the airflow thrown out by the impeller, resulting in increased airflow resistance inside the volute and further reducing airflow output.

[0003] Regarding the internal airflow design, existing vacuum cleaner fans often have narrow and convoluted internal airflow ducts. This unreasonable duct structure severely hinders smooth airflow. When airflow passes through narrow sections, the velocity increases, leading to greater pressure loss. At bends, airflow easily forms vortices, consuming a significant amount of energy, resulting in a substantial reduction in the overall air pressure and airflow of the fan. Furthermore, some vacuum cleaners, in pursuit of miniaturization and portability, excessively compress the internal space of the fan, further worsening the airflow conditions and exacerbating the problem of insufficient air pressure and airflow.

[0004] For vacuum cleaners that integrate the fan assembly and motor, structural limitations also restrict improvements in air pressure and airflow. The integrated design makes it difficult to optimize key fan components. For example, it's impossible to flexibly adjust the shape and size of the fan shroud according to aerodynamic principles to optimize airflow paths. Simultaneously, vibrations generated by the motor are easily transmitted directly to the fan components, leading to unstable fan operation and affecting the stability of air pressure and airflow. Furthermore, the integrated structure increases the difficulty of product upgrades and iterations. When fan performance needs improvement, it often requires replacing the entire fan assembly, which is costly and time-consuming, making it difficult to quickly respond to market demands for high-performance vacuum cleaners. Utility Model Content

[0005] In order to overcome the shortcomings and deficiencies of the existing technology, this utility model provides a high-speed, high-pressure fan with two-stage diffusion, which solves the technical problems of large airflow pressure loss in traditional vacuum cleaner fans, resulting in reduced air pressure and low air volume output efficiency.

[0006] This utility model achieves the above-mentioned objective through the following technical solution: a two-stage diffuser high-speed high-pressure fan, comprising a casing, a rotor assembly, a stator assembly, and a fan blade assembly. The casing includes an inner wall and an outer wall coaxially connected. The outer wall has an annular stepped structure, which is located on the outer or inner surface of the outer wall. The fan blade assembly includes a fan blade and a fan blade cover. One end of the fan blade cover is assembled, fixed, and positioned with the annular stepped structure. The annular stepped structure is coaxial with the stator mounting cavity and the first bearing mounting cavity. The fan blade includes a hub and moving blades. The moving blades are evenly distributed on the mounting surface of the hub. The mounting surface is a rotating surface with an arc segment as its generatrix. The radius of the rotating surface gradually increases from the air inlet end to the air outlet end. The width of the moving blades gradually decreases from the air inlet end to the air outlet end. A moving air duct is formed between two adjacent moving blades. The cross-sectional area of ​​the moving air duct gradually increases from the air inlet end to the air outlet end.

[0007] Preferably, the inner cavity of the inner wall includes a stator mounting cavity and a first bearing mounting cavity, and the space between the stator mounting cavity and the first bearing mounting cavity is a cavity with a positioning structure.

[0008] Preferably, the fit gap between the inner surface of the fan blade cover and the long side of the moving blade is 0.01-1.0 mm, and the fit gap is equal or gradually widens from the air inlet end to the air outlet end.

[0009] Preferably, a stationary blade is provided between the inner wall and the outer wall. At the end face of the stationary blade that mates with the fan blade, the air inlet angle of the stationary blade is consistent with the rotation direction of the fan blade. A stationary air duct is formed between two adjacent stationary blades. The cross-sectional shape of the stationary air duct gradually expands as it moves away from the axis.

[0010] Preferably, the rotor assembly includes a shaft, a bearing, and a magnetic ring, with a limiting structure between the bearing and the magnetic ring, the limiting structure being an elastic or rigid element.

[0011] Preferably, the bearings are disposed at both ends of the magnetic ring or at the same end of the magnetic ring.

[0012] Preferably, it also includes an end cap, which is a front end cap or a rear end cap.

[0013] Preferably, the front end cover is located at the front port of the mounting cavity near the fan blade assembly of the housing, and a second bearing mounting cavity is provided in the front end cover. The first bearing mounting cavity is integrally formed with the housing, and the stator assembly, the fan blade assembly and the first bearing are all installed into the inner cavity of the inner wall from the front port.

[0014] Preferably, the rear end cover is located at the rear port of the housing near the stator mounting cavity, and a second bearing mounting cavity is provided in the rear end cover. The first bearing mounting cavity is integrally formed with the housing. The stator assembly and the first bearing are installed into the inner cavity of the inner wall from the rear port, and the fan blade assembly is fixedly connected to the shaft of the rotor assembly from the other end.

[0015] Compared with the prior art, the beneficial effects obtained by this utility model are:

[0016] This utility model discloses a two-stage diffuser high-speed, high-pressure blower, comprising a casing, a rotor assembly, a stator assembly, and a fan blade assembly. The casing includes an inner wall and an outer wall coaxially connected. The outer wall has an annular stepped structure located on either the outer or inner surface of the outer wall. The fan blade assembly includes a fan blade and a fan blade shroud. One end of the fan blade shroud is assembled, fixed, and positioned with respect to the annular stepped structure. The annular stepped structure is coaxial with the stator mounting cavity and the first bearing mounting cavity. The fan blade includes a hub and moving blades. The moving blades are evenly distributed on the mounting surface of the hub, which is shaped like an arc segment. The rotating surface is the generatrix, and the radius of the rotating surface gradually increases from the air inlet to the air outlet. The width of the moving blade gradually decreases from the air inlet to the air outlet. A moving air duct is formed between two adjacent moving blades. The cross-sectional area of ​​the moving air duct gradually increases from the air inlet to the air outlet. The fit clearance between the inner surface of the fan blade cover and the long side of the moving blade is 0.01-1.0 mm. The fit clearance is equal or gradually expands from the air inlet to the air outlet. Through the coordinated design of the gradual expansion of the moving air duct and the gradual expansion of the fit clearance between the fan blade cover and the moving blade, the technical problems of large air pressure loss leading to reduced air pressure and low air volume output efficiency in existing vacuum cleaner fans are solved. Attached Figure Description

[0017] To more clearly illustrate the technical solutions in the embodiments of this utility model or the prior art, the accompanying drawings used in the description of the embodiments or the prior art will be briefly introduced below.

[0018] Figure 1 This is a schematic diagram of a high-speed, high-pressure blower with a front cover and two-stage diffuser, according to Embodiment 1 of this utility model.

[0019] Figure 2 This is a schematic diagram of a high-speed, high-pressure blower with a two-stage diffuser and a rear end cover, according to Embodiment 1 of this utility model.

[0020] Figure 3 This is a schematic diagram of the casing of a high-speed, high-pressure blower with a front cover and two-stage diffusion in Embodiment 1 of this utility model.

[0021] Figure 4 This is a schematic diagram of the casing of a high-speed, high-pressure blower with a rear end cover and two-stage diffuser, according to Embodiment 1 of this utility model.

[0022] Figure 5 This is a schematic diagram of the back cover with an external stop structure according to Embodiment 1 of this utility model.

[0023] Figure 6 This is a schematic diagram of the back cover with an inner stop structure according to Embodiment 1 of this utility model.

[0024] Figure 7 This is a schematic diagram of the fan blades of the high-speed, high-pressure fan with a front cover and two-stage diffuser according to this utility model.

[0025] Figure 8 This is a schematic diagram of the stationary fan blade of the high-speed, high-pressure fan with a front cover and two-stage diffusion.

[0026] Figure 9 This is a cross-sectional view of a high-speed, high-pressure blower with a front cover and two-stage diffuser, according to Embodiment 2 of this utility model.

[0027] Figure 10 This is a schematic diagram of a high-speed, high-pressure blower with a front cover and two-stage diffuser, according to Embodiment 2 of this utility model.

[0028] Reference numerals: 1-Housing; 11-Inner wall; 111-Stator mounting cavity; 112-First bearing mounting cavity; 113-Positioning structure; 12-Outer wall; 121-Annular stepped structure; 13-Stationary blade; 2-Rotor assembly; 21-Shaft; 22-Bearing; 23-Magnetic ring; 24-Limiting structure; 3-Stator assembly; 4-Fan blade assembly; 41-Fan blade; 411-Hub; 412-Moving blade; 42-Fan blade cover; 5-End cover; 51-Second bearing mounting cavity; 52-Outer stop structure; 53-Inner stop structure. Detailed Implementation

[0029] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. However, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention. Wherein, width represents the dimension along the radial direction (perpendicular to the axis of rotation), and length represents the dimension along the axial direction (along the axis of rotation).

[0030] Example 1

[0031] Please see Figures 1 to 8 A high-speed, high-pressure blower with two-stage diffuser supported at both ends includes a housing 1, a rotor assembly 2, a stator assembly 3, a fan blade assembly 4, and an end cover 5. The housing 1 includes an inner wall 11 and an outer wall 12 coaxially connected. The inner cavity of the inner wall 11 includes a stator mounting cavity 111 and a first bearing mounting cavity 112. The space between the stator mounting cavity 111 and the first bearing mounting cavity 112 is a cavity with a positioning structure 113. The positioning structure 113 is a limiting boss that extends above the inner surface of the inner wall 11.

[0032] The end cover 5 is provided with a second bearing mounting cavity 51, which is used to install a second bearing. The end cover 5 and the housing 1 are fitted together by an outer stop structure 52 with a stepped structure on the annular outer surface of the end cover 5 for limiting the fit. The end cover 5 is nested into the inner wall 11 of the housing 1. The outer stop structure 52 is used to limit the depth of the end cover 5 nested in. In another embodiment, the annular inner surface of the end cover 5 has a stepped structure for limiting the fit, namely an inner stop structure 53. The end of the inner wall 11 is embedded in the end cover 5 with the inner stop structure. The inner stop structure 53 is used to limit the depth of the end of the inner wall 11 nested in.

[0033] The end cover 5 is a front end cover, which is located at the front port of the mounting cavity near the fan blade assembly 4 of the housing 1. The first bearing mounting cavity 112 is integrally formed with the housing 1. The stator assembly 3, the fan blade assembly 4, and the first bearing are all installed into the inner cavity of the inner wall from the front port. In another embodiment, the end cover 5 is a rear end cover, which is located at the rear port of the housing 1 near the stator mounting cavity 111. The rear end cover has a second bearing mounting cavity 51. The first bearing mounting cavity 112 is integrally formed with the housing 1. The stator assembly 3 and the first bearing are installed into the inner cavity of the inner wall from the rear port. The fan blade assembly 4 is fixedly connected to the shaft 21 of the rotor assembly 2 from the other end.

[0034] The outer wall 12 has an annular stepped structure 121, which is located on the outer or inner surface of the outer wall 12. The fan blade assembly 4 includes a fan blade 41 and a fan blade cover 42. One end of the fan blade cover 42 is assembled, fixed, and positioned with the annular stepped structure 121. The annular stepped structure 121 is coaxial with the stator mounting cavity 111 and the first bearing mounting cavity 112. The fan blade 41 includes a hub 411 and moving blades 412. The moving blades 412 are evenly distributed on the mounting surface of the hub 411. The mounting surface is a rotating surface with an arc segment as its generatrix, and the radius of the rotating surface gradually increases from the air inlet end to the air outlet end. The width of the moving blades 412 increases from the air inlet end to the air outlet end. The airflow tapers towards the inlet, forming a dynamic airflow duct between two adjacent moving blades. The cross-sectional area of ​​this duct gradually increases from the inlet to the outlet. The cross-sectional area of ​​the outlet of the moving blade 412 is more than 1.1 times that of the inlet, with a diffusion coefficient of less than 3 (the rate of change of cross-sectional area within a 1mm range). The number of moving blades 412 is greater than 3. The gradually increasing airflow duct ensures that the fluid velocity at the outlet of the fan blade is significantly higher than that at the inlet, increasing the fluid flow from the inlet to the outlet and improving the fan blade efficiency. When high-speed fluid flows through the blades, the pressure difference between the upper and lower blades easily creates vortices inside the blades. With more than 3 blades and a diffusion coefficient of less than 3, the pressure difference inside the fan blades is greatly reduced, vortices are decreased, and motor efficiency is improved.

[0035] The fitting gap between the inner surface of the fan blade cover 42 and the long side of the moving blade 412 is 0.01-1.0mm. The fitting gap is equal or gradually widens from the air inlet end to the air outlet end, and the widening coefficient is greater than or equal to 1. A stationary blade 13 is provided between the inner wall 11 and the outer wall 12. The two ends of the stationary blade 13 are fixedly connected to the inner wall 11 and the outer wall 12. At the end face of the stationary blade 13 that mates with the fan blade 41, the air inlet angle of the stationary blade 13 is consistent with the rotation direction of the fan blade 41. A stationary air duct is formed between two adjacent stationary blades 13. The cross-sectional shape of the stationary air duct gradually widens as it moves away from the axis. In another embodiment, the stationary blade 13 is a detachable component.

[0036] The rotor assembly 2 includes a shaft 21, a bearing 22, and a magnetic ring 23. A limiting structure 24 is provided between the bearing 22 and the magnetic ring 23. The limiting structure 24 is a spring; in another embodiment, the limiting structure 24 is a rigid metal component. The bearing 22 is disposed at both ends of the magnetic ring 23, meaning the motor is a motor with a two-end support structure. In another embodiment, the bearing 22 is disposed at the same end of the magnetic ring 23.

[0037] Example 2

[0038] Please see Figures 7 to 10A high-speed, high-pressure blower with a cantilever structure and two-stage diffuser includes a housing 1, a rotor assembly 2, a stator assembly 3, and a blade assembly 4. The housing 1 includes an inner wall 11 and an outer wall 12 coaxially connected. The inner cavity of the inner wall 11 includes a stator mounting cavity 111 and a first bearing mounting cavity 112. A cavity with a positioning structure 113 is located between the stator mounting cavity 111 and the first bearing mounting cavity 112. The positioning structure 113 is a limiting boss protruding above the inner surface of the inner wall 11, used to limit the axial movement of the stator assembly 2. Two bearings 22 are installed in the first bearing mounting cavity 112. A limiting structure, such as a metal bearing sleeve or a spring, is provided between the bearings 22. The shaft 21 of the rotor assembly 2 passes through the bearing hole of the first bearing mounting cavity 112. One end of the shaft 21 is connected to the bearing 22, the other end of the bearing 22 is connected to the magnetic ring 23, and the other end of the shaft 21 is connected to the fan blade assembly 4, forming a fan with a cantilever beam structure.

[0039] The outer wall 12 has an annular stepped structure 121, which is located on the outer or inner surface of the outer wall 12. The fan blade assembly 4 includes a fan blade 41 and a fan blade cover 42. One end of the fan blade cover 42 is assembled, fixed, and positioned with the annular stepped structure 121. The annular stepped structure 121 is coaxial with the stator mounting cavity 111 and the first bearing mounting cavity 112. The cross-section of the annular stepped structure 121 is wedge-shaped, with the sloped side facing the fan blade cover 42, which facilitates the direct snap-fit ​​and fixation of the fan blade cover 42 onto the outer wall 12. After assembly, axial positioning is achieved through the vertical surface of the step, ensuring the stability of the fan blade assembly 4 during operation.

[0040] The fan blade 41 includes a hub 411 and moving blades 412. The hub 411 is integrally molded from high-strength aluminum alloy or engineering plastic, which has good lightweight and rigidity. The hub 411 has a shaft hole in the center, which is connected to the motor shaft by a key or interference fit to ensure reliable transmission. The inner wall of the shaft hole is provided with anti-slip texture to enhance the stability of the connection.

[0041] The moving blades 412 are evenly distributed on the mounting surface of the hub 411, typically numbering 6-12. The mounting surface is a rotating surface with an arc segment as its generatrix, the radius of which gradually increases from the inlet to the outlet, forming a unique gradually expanding blade layout. The width of the moving blades 412 gradually decreases from the inlet to the outlet, typically 15-25mm at the inlet and 8-15mm at the outlet. The moving blades 412 employ aerodynamic design, featuring a streamlined cross-section and a thickness that gradually decreases from the root to the tip, approximately 3-5mm at the root and 1-2mm at the tip. A dynamic airflow channel is formed between adjacent moving blades, with its cross-sectional area gradually increasing from the inlet to the outlet, approximately 200-400mm² at the inlet and 400-800mm² at the outlet, helping to reduce wind resistance and improve airflow acceleration.

[0042] The fit clearance between the inner surface of the fan blade cover 42 and the long side of the moving blade 412 is 0.01-1.0mm. The fit clearance can be designed to be equal from the air inlet end to the air outlet end to ensure the uniformity of airflow; or it can be designed to be gradually expanded, with a gap of 0.01mm at the air inlet end and a gap of 1.0mm at the air outlet end, to further reduce airflow leakage and improve fan efficiency.

[0043] A stationary blade 13 is provided between the inner wall 11 and the outer wall 12. It is made of sheet metal, stamped and then surface-treated, such as anodized or painted, to improve corrosion resistance. At the end face of the stationary blade 13 that mates with the fan blade 41, the air inlet angle of the stationary blade 13 is consistent with the rotation direction of the fan blade 41, typically 20°-45°. This angle is optimized through aerodynamic simulation to effectively guide the airflow discharged from the fan blade 41 and reduce turbulence. A stationary air duct is formed between two adjacent stationary blades 13. The cross-sectional shape of the stationary air duct gradually expands away from the axis, and its specific shape can be approximated as a trapezoid or a gradually opening arc. This shape helps reduce airflow pressure loss and allows for smoother airflow discharge. The length of the stationary blade 13 is determined by the distance between the inner wall 11 and the outer wall 12, generally between 30-80 mm, and the thickness of the stationary blade 13 is approximately 1-3 mm to ensure sufficient strength and rigidity.

[0044] The stator assembly 3 includes a stator core, stator windings, insulation structure, and base. The stator core is made of high-permeability silicon steel sheets with a thickness of 0.35-0.5mm, and the surface of the silicon steel sheets is coated with an insulating coating with a thickness of approximately 0.02-0.03mm to reduce eddy current losses. The stator core has uniformly distributed stator slots on its inner circumference. The slot type is usually semi-closed or open, and the number of slots is determined according to the number of poles and power of the motor, generally between 24 and 48 slots. The outer diameter of the stator core is designed according to the motor power. For small-power motors (<500W), the outer diameter of the core is approximately 80-120mm, while for large-power motors (≥500W), the outer diameter can reach 150-200mm. The two ends of the stator core are fastened with pressure rings and bolts to ensure that the stacking coefficient is not less than 0.95. The stator windings are made of high-strength enameled round copper wire, with the enamel coating of polyesterimide-polyamideimide composite coating, achieving a heat resistance rating of H (180℃). The stator windings are typically double-layered, with a pitch of y = (0.8 - 0.9)τ (τ being the pole pitch). Each phase winding consists of multiple coil groups connected in series or parallel, with star (Y) or delta (△) connections depending on the motor design requirements. The ends of the stator windings are secured with cable ties or thermosetting resin to prevent loosening due to vibration during motor operation. The insulation structure consists of slot insulation placed within the stator slots, using DMD (polyester film-polyester fiber nonwoven composite foil) material with a thickness of approximately 0.2-0.3 mm. The slot insulation extends 5-8 mm beyond the core slot openings at both ends to enhance insulation performance. Phase-to-phase insulation, also made of DMD material, is used between the stator windings and the stator core to ensure electrical isolation between each phase winding. For high-voltage motors, anti-corona treatment is applied to the winding ends by coating with semiconductor paint or wrapping with semiconductor tape to reduce the electric field strength at the ends and prevent partial discharge. The frame is made of die-cast aluminum alloy or stamped steel plate. Aluminum alloy frames are lightweight and have good heat dissipation, while steel plate frames are high-strength and low-cost. The inner wall of the frame is fixed to the stator core by interference fit or epoxy resin bonding to ensure that the stator core does not shift during motor operation. The frame is equipped with heat dissipation fins. The height and spacing of the heat dissipation fins are designed according to the motor power and heat dissipation requirements. Typically, the height of the heat dissipation fins is 15-30mm and the spacing is 20-40mm to increase the heat dissipation area and improve heat dissipation efficiency.

[0045] It also includes a PCB board, which is fixedly installed at the end of the stator assembly 3, and is fixedly connected by positioning posts and positioning holes, and is insulated and shielded.

[0046] The above examples are merely specific embodiments of this utility model. Obviously, this utility model is not limited to the above embodiments, and many similar modifications are possible. All variations that can be directly derived or conceived by those skilled in the art from the content disclosed in this utility model should be considered within the scope of protection of this utility model.

Claims

1. A high-speed, high-pressure blower with two-stage diffuser, characterized in that, The device includes a housing, a rotor assembly, a stator assembly, and a fan blade assembly. The housing includes an inner wall and an outer wall coaxially connected. The outer wall has an annular stepped structure located on either the outer or inner surface of the outer wall. The fan blade assembly includes a fan blade and a fan blade cover. One end of the fan blade cover is assembled, fixed, and positioned with the annular stepped structure. The annular stepped structure is coaxial with the stator mounting cavity and the first bearing mounting cavity. The fan blade includes a hub and moving blades. The moving blades are evenly distributed on the mounting surface of the hub. The mounting surface is a rotating surface with an arc segment as its generatrix. The radius of the rotating surface gradually increases from the air inlet end to the air outlet end. The width of the moving blades gradually decreases from the air inlet end to the air outlet end. A moving air duct is formed between two adjacent moving blades. The cross-sectional area of ​​the moving air duct gradually increases from the air inlet end to the air outlet end. The fit clearance between the inner surface of the fan blade cover and the long side of the moving blade is 0.01-1.0 mm. The fit clearance is equal or gradually increases from the air inlet end to the air outlet end.

2. The high-speed, high-pressure blower with two-stage diffuser as described in claim 1, characterized in that, The inner wall cavity includes a stator mounting cavity and a first bearing mounting cavity, and the space between the stator mounting cavity and the first bearing mounting cavity is a cavity with a positioning structure.

3. The high-speed, high-pressure blower with two-stage diffuser as described in claim 1, characterized in that, A stationary blade is provided between the inner wall and the outer wall. At the end face of the stationary blade that mates with the fan blade, the air inlet angle of the stationary blade is consistent with the rotation direction of the fan blade. A stationary air duct is formed between two adjacent stationary blades. The cross-sectional shape of the stationary air duct gradually expands as it moves away from the axis.

4. The high-speed, high-pressure blower with two-stage diffuser as described in claim 1, characterized in that, The rotor assembly includes a shaft, a bearing, and a magnetic ring. A limiting structure is included between the bearing and the magnetic ring. The limiting structure is an elastic element or a rigid element.

5. The high-speed, high-pressure blower with two-stage diffuser as described in claim 4, characterized in that, The bearings are located at both ends of the magnetic ring or at the same end of the magnetic ring.

6. The high-speed, high-pressure blower with two-stage diffuser as described in claim 1, characterized in that, It also includes end caps, which are either front end caps or rear end caps.

7. The high-speed, high-pressure blower with two-stage diffuser as described in claim 6, characterized in that, The front end cover is located at the front port of the mounting cavity near the fan blade assembly of the housing. A second bearing mounting cavity is provided in the front end cover. The first bearing mounting cavity is integrally formed with the housing. The stator assembly, the fan blade assembly, and the first bearing are all installed into the inner cavity of the inner wall from the front port.

8. The high-speed, high-pressure blower with two-stage diffuser as described in claim 6, characterized in that, The rear end cover is located at the rear port of the housing near the stator mounting cavity. A second bearing mounting cavity is provided in the rear end cover. The first bearing mounting cavity is integrally formed with the housing. The stator assembly and the first bearing are installed into the inner cavity of the inner wall from the rear port. The fan blade assembly is fixedly connected to the shaft of the rotor assembly from the other end.

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