Fan structure and sweeping robot
By adopting a mixed-flow impeller and air guide channel design in the vacuum cleaner's fan, the problems of high noise and insufficient vacuum in traditional fans have been solved, achieving higher suction capacity and lower noise, and extending the equipment's lifespan.
Patent Information
- Application Number
- CN202520604272.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- Filing Date
- 2025-04-01
- Publication Date
- 2026-01-30
- Estimated Expiration
- 2035-04-01
AI Technical Summary
Traditional robotic vacuum cleaners suffer from high noise levels and insufficient mechanical strength due to the high-speed rotation of centrifugal impellers in their fan systems, which limits the improvement of vacuum levels.
The design employs a mixed-flow impeller structure, combined with air guide channels and optimized airflow path design, to improve impeller strength and reduce turbulence, thereby enhancing the static pressure difference and aerodynamic performance of the airflow.
It improves the vacuum level and suction capacity of the fan, reduces noise, extends service life, and enhances the reliability and efficiency of the motor.
Smart Images
Figure CN223854493U_ABST
Abstract
Description
Technical Field
[0001] This application relates to the field of cleaning technology, and in particular to a fan structure and a sweeping robot. Background Technology
[0002] With the increasing popularity of smart cleaning equipment, the performance requirements for the core power component of robotic vacuum cleaners, the fan system, are becoming increasingly stringent. Traditional robotic vacuum cleaner fans generally adopt a structure combining a centrifugal impeller and a volute duct. The high-speed rotation of the centrifugal impeller generates negative pressure to suck up dust and debris from the ground.
[0003] Centrifugal impellers typically have a large outer diameter to meet the air volume requirements of sweepers. This results in extremely high linear velocities at the impeller edges when the fan rotates at high speed (e.g., linear velocities exceeding 150 m / s at 120,000 rpm). Under these conditions, significant noise is generated, severely limiting further improvements in the fan's vacuum level. Utility Model Content
[0004] This application provides a fan structure and a sweeping robot to solve the problem of difficulty in improving the vacuum degree of fans in the above-mentioned related technologies.
[0005] To achieve the above objectives, the embodiments of this application provide the following technical solutions:
[0006] A first aspect of this application provides a wind turbine structure, including:
[0007] The motor includes an output shaft and a plurality of first blades, the plurality of first blades being circumferentially spaced on the outside of the motor, and the output shaft being located at one end of the motor;
[0008] A mixed-flow impeller is fixedly connected to the output shaft. The mixed-flow impeller includes a first end and a second end along the axial direction. The first end is disposed close to the first blade, and the outer diameter of the first end is larger than the outer diameter of the second end.
[0009] A wind shield, at least partially covering the outside of the first blade and the mixing impeller, forms an air guide channel between the wind shield, a portion of the motor, the first blade, and the mixing impeller; wherein...
[0010] The air guide channel includes an air inlet and an air outlet. The air inlet is located at the second end of the mixing impeller, and the air outlet is located on one side of the outer periphery of the wind shroud.
[0011] Along the axial direction of the motor, the first blade and the end of the shroud facing away from the air inlet are spaced apart.
[0012] The fan structure provided in this application embodiment, by setting a mixed-flow impeller, can support higher rotational speeds due to the high structural strength of the mixed-flow impeller, which is beneficial to improving the vacuum level of the fan. By forming an air guide channel between the fan shroud, part of the motor, the first blade, and the mixed-flow impeller, airflow can be effectively guided, which helps to reduce airflow resistance and improve the overall efficiency of the fan.
[0013] By setting the outer diameter of the first end of the mixed-flow impeller to be larger than that of the second end, and allowing the airflow to enter from the second end, this design allows the airflow to gradually diffuse as it passes through the mixed-flow impeller, making the conversion of kinetic energy into static pressure smoother and more efficient. As the airflow passes through the gradually widening channel, its velocity decreases and the static pressure increases, thereby improving the fan's pressure output capacity.
[0014] By installing the first blade on the outside of the motor and spacing it from the end of the fan shroud away from the inlet, air enters through the inlet, is accelerated by the mixed-flow impeller, passes through the gap between the first blades, enters the guide channel at the end of the first blade away from the inlet, and then flows out from the outlet. Here, the airflow accelerated by the mixed-flow impeller decreases in speed as it passes through the gap between the first blades, and some of its kinetic energy is converted into static pressure (equivalent to the first diffusion). The airflow exiting from the gap between the first blades decreases in speed again within the guide channel at the end of the first blade away from the inlet, further increasing the static pressure (equivalent to the second diffusion). This creates a higher static pressure difference between the fan's inlet and outlet. This increased pressure difference directly enhances the fan's suction capacity and helps improve the fan's vacuum level.
[0015] The gradual reduction in airflow velocity and turbulence lowers the noise level during fan operation. The first blade is spaced apart from the end of the shroud away from the air inlet; this structure enhances fan stability, reduces vibration and wear, and extends the fan's lifespan. The motor is covered by the shroud, and airflow passes over the outside of the motor; this design aids in heat dissipation, prevents overheating, and improves motor reliability and lifespan.
[0016] In one possible implementation, the mixed-flow impeller includes a hub and a plurality of second blades; wherein,
[0017] The hub is fixedly connected to the output shaft;
[0018] Multiple second blades are arranged at circumferential intervals on the outer side of the hub, and an air intake channel is formed between two adjacent second blades;
[0019] The ends of multiple second blades facing away from the hub collectively form the outer contour of the mixing impeller, and the inner wall of the shroud located outside the mixing impeller matches the shape of the outer contour of the mixing impeller.
[0020] This configuration better guides airflow along the outer contour of the mixed-flow impeller, reducing airflow separation and turbulence. The optimized airflow path helps improve the efficiency and performance of the fan. Through precise matching, the airflow can more effectively convert kinetic energy into static pressure as it passes over the impeller. This increased efficiency enhances the fan's pressure output capacity. The matched geometry reduces energy loss due to irregular airflow paths, thus improving the overall energy efficiency of the fan. The smoother and more ordered airflow, coupled with reduced turbulence and eddies, lowers the noise level during fan operation. The matched design also reduces wind resistance and improves aerodynamic performance, enabling the fan to deliver higher flow rates and pressures at the same power output.
[0021] In one possible implementation, the second blade is spaced apart from the inner wall of the shroud in the radial direction of the mixing impeller; wherein,
[0022] The distance between the second blade and the inner wall of the wind shield is less than or equal to 1 mm.
[0023] By creating a gap between the second impeller and the inner wall of the shroud, the mixing impeller does not rub against the shroud's inner wall during rotation, allowing it to rotate at high speed. A smaller gap between the second impeller and the shroud effectively reduces airflow leakage, improving fan efficiency. This smaller gap also allows for more precise control of the airflow path, ensuring airflow follows a predetermined direction, reducing turbulence and eddies, and consequently lowering fan noise during operation.
[0024] In one possible implementation, the distance between the second blade and the inner wall of the shroud is less than or equal to 0.5 mm.
[0025] This configuration can further reduce airflow leakage between the impeller and the shroud, increase pressure output, enhance airflow control, and reduce noise, providing significant advantages for improving the performance of the fan.
[0026] In one possible implementation, in the radial direction of the motor, one end of the first blade is fixedly connected to the outer side of the motor, and the other end is fitted against the inner wall of the shroud.
[0027] By fixing one end of the first blade to the outside of the motor, stability during operation is ensured, reducing vibration and displacement. The close fit between the first blade and the inner wall of the shroud helps guide airflow along a predetermined path, reducing airflow separation and turbulence. This optimized airflow path contributes to improved system efficiency and performance. The close fit design effectively reduces airflow leakage between the first blade and the shroud, ensuring more airflow is effectively guided through the first blade for kinetic and static pressure conversion, enhancing diffusion and thus improving the fan's suction capacity. The smooth airflow and reduced turbulence also lower system operating noise.
[0028] In one possible implementation, a blank area is provided at the position of the motor opposite to the air outlet, and the blank area is the area where the first blade is not provided.
[0029] By leaving a blank area between the motor and the air outlet, airflow can be ensured to flow smoothly out of the outlet. This prevents airflow from being re-guided between the first blades or into the mixing impeller when passing through the blank area, thus improving airflow efficiency. In other words, it prevents airflow backflow. This also reduces airflow interference and lowers system noise. The blank area helps redistribute airflow, making it more evenly distributed at the outlet. This uniform airflow distribution helps improve system performance and efficiency. The presence of the blank area helps optimize aerodynamic performance, allowing the system to provide higher flow and pressure at the same power, thereby enhancing the fan's suction capacity.
[0030] In one possible implementation, the second blade is spirally wound around the outside of the hub along the axial direction of the mixed-flow impeller.
[0031] By spirally winding the second blade, airflow can be more effectively guided along the axial and radial directions of the mixed-flow impeller, helping to improve the kinetic energy conversion efficiency of the airflow and thus enhancing the performance of the fan. The spiral shape helps to gradually accelerate the airflow and increase its pressure, converting kinetic energy more efficiently into static pressure, thereby increasing the fan's pressure output capacity. The spiral winding design reduces airflow separation and turbulence generation on the blade surface, resulting in a smoother and more orderly airflow, which helps to improve the fan's efficiency and reduce noise. The spiral shape reduces wind resistance and improves aerodynamic performance, allowing the fan to deliver higher flow rates and pressures at the same power output. The spirally wound blade design provides a more uniform force distribution, reducing vibrations caused by asymmetrical airflow, thereby improving system reliability and service life.
[0032] In one possible implementation, the first blade is positioned at an angle to the axial direction of the motor; wherein,
[0033] When the mixing impeller rotates along the helical direction of the second blade, the direction of the airflow flowing out from the first end of the mixing impeller is the same as the tilt direction of the first blade.
[0034] By setting the first blade at an angle to the motor's axis, and with the mixing impeller rotating in the helical direction of the second blade, the airflow exiting from the first end of the mixing impeller follows the same direction as the tilt of the first blade. This allows the airflow drawn in by the rotating mixing impeller to be directly "thrown" into the space between the first blades after exiting from the first end. The airflow continues to flow in the same direction as when it was thrown out, ensuring a smooth transition between the mixing impeller and the first blades. This reduces turbulence and energy loss when the airflow enters the first blades, thus improving the overall efficiency of the fan structure. The consistent airflow direction reduces the formation of turbulence and eddies, which are often major sources of fan noise. Optimizing the airflow path can significantly reduce operating noise levels. Reducing turbulence and vibration decreases wear on mechanical components, extending the fan's lifespan and reducing maintenance requirements.
[0035] In one possible implementation, the first blade and the second blade are spaced apart along the axial direction of the motor.
[0036] By arranging the first and second blades axially spaced, the airflow path can be better managed, resulting in more orderly and efficient airflow through the system. This reduces airflow interference between blades, helps reduce turbulence and eddies, improves overall system efficiency, and also reduces vibration caused by uneven airflow, thereby increasing system stability and lifespan. Because the airflow is smoother and more orderly, system noise may be reduced during operation.
[0037] A second aspect of this application provides a sweeping robot, including a fan structure as described in any of the first aspects.
[0038] The sweeping robot in this embodiment can improve suction power, reduce noise, and enhance user experience by setting the fan structure described in the first aspect. Attached Figure Description
[0039] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.
[0040] Figure 1This is a schematic diagram of a fan structure provided in an embodiment of this application;
[0041] Figure 2 This is a cross-sectional structural diagram of a fan structure provided in an embodiment of this application;
[0042] Figure 3 This is a schematic diagram of the structure of a mixed-flow impeller for a fan provided in an embodiment of this application;
[0043] Figure 4 This is a partial structural diagram of a fan structure provided in an embodiment of this application;
[0044] Figure 5 This is a schematic diagram of another angle of a fan structure provided in an embodiment of this application;
[0045] Figure 6 This is an exploded structural diagram of a fan structure provided in an embodiment of this application;
[0046] Figure 7 This is a schematic diagram of the structure of a motor for a fan structure provided in an embodiment of this application.
[0047] Explanation of reference numerals in the attached figures:
[0048] 100 - Fan structure; 10 - Motor; 11 - First blade;
[0049] 12-Output shaft; 13-Blank area; 20-Fan shroud;
[0050] 21-First shell; 22-Second shell; 221-Side wall;
[0051] 222 - Bottom wall; 23 - Air inlet; 24 - Air outlet;
[0052] 30 - Mixed-flow impeller; 31 - First end; 32 - Second end;
[0053] 33-Second blade; 34-Hub; 40-Base;
[0054] 50 - Air guide channel; 51 - First diffuser zone; 52 - Second diffuser zone. Detailed Implementation
[0055] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.
[0056] Traditional sweeper fans generally adopt a structure combining a centrifugal impeller and a volute air duct. The high-speed rotation of the centrifugal impeller generates negative pressure to suck up dust and debris from the ground.
[0057] Centrifugal impellers are typically assembled from two or three metal blades to a hub using a riveting process. Stress concentration easily occurs at the riveted joints, leading to fatigue fracture or plastic deformation under high-speed conditions. Furthermore, to meet the airflow requirements of sweepers, impeller outer diameters are generally large (typically >40mm), resulting in extremely high impeller edge linear velocities (e.g., exceeding 150m / s at 120,000 rpm). Under these conditions, the mechanical strength of traditional riveted structures cannot sustain stable operation over the long term, limiting the actual operating speed of the impeller to below 120,000 rpm, severely restricting further improvements in the blower's vacuum level.
[0058] In addition, the high linear velocity of the centrifugal impeller and the inherent vibration characteristics of the riveted structure cause the fan to generate a lot of noise during operation, resulting in a poor user experience.
[0059] To address the aforementioned technical problems, this application provides a fan structure and a sweeping robot. By incorporating a mixed-flow impeller into the fan structure, the impeller's higher structural strength allows for higher rotational speeds, thereby improving the fan's vacuum level. Furthermore, the mixed-flow impeller's structure reduces wind resistance, thus lowering fan noise and enhancing the user experience.
[0060] The fan structure and sweeping robot provided in the embodiments of this application will be described in detail below with reference to the accompanying drawings.
[0061] Figure 1 This is a schematic diagram of a fan structure provided in an embodiment of this application. Figure 2 This is a cross-sectional structural diagram of a fan structure provided in an embodiment of this application. Figure 3 This is a schematic diagram of a mixed-flow impeller for a fan structure provided in an embodiment of this application.
[0062] It should be noted that, for ease of description, in the embodiments of this application, the axial direction of the motor is taken as the x-direction, the radial direction is taken as the y-direction, the radial direction refers to the direction of the diameter passing through the center of the circle, and the circumferential direction is taken as the a-direction.
[0063] This application provides a fan structure 100, such as... Figure 1 and Figure 2 As shown, the fan structure 100 may include a motor 10, a mixing impeller 30, and a shroud 20. The motor 10 may include an output shaft 12 and a plurality of first blades 11, which are circumferentially spaced on the outside of the motor 10. The output shaft 12 is located at one end of the motor 10. The mixing impeller 30 is fixedly mounted on the output shaft 12 of the motor 10. The motor 10 drives the output shaft 12 to rotate, and the output shaft 12 drives the mixing impeller 30 to rotate during rotation. At least a portion of the shroud 20 covers the outside of the motor 10, the first blades 11, and the mixing impeller 30, forming an airflow channel 50 between the shroud 20, a portion of the motor 10, the first blades 11, and the mixing impeller 30.
[0064] The fan structure provided in this application embodiment, by setting a mixed-flow impeller 30, can support higher rotational speeds due to the high structural strength of the mixed-flow impeller 30, which is beneficial to improving the vacuum degree of the fan. By forming an air guide channel 50 between the fan shroud 20, part of the motor 10, the first blade 11, and the mixed-flow impeller 30, airflow can be effectively guided, which helps to reduce airflow resistance and improve the overall efficiency of the fan.
[0065] like Figure 2 As shown, the mixing impeller 30 includes a first end 31 and a second end 32 arranged along the x-direction. The first blade 11 is located at the first end 31 of the mixing impeller 30, and the outer diameter of the first end 31 is larger than the outer diameter of the second end 32. The air guide channel 50 may include an air inlet 23 and an air outlet 24, with the air outlet 24 located on one side of the outer periphery of the shroud 20. The air inlet 23 is located at the second end 32 of the mixing impeller 30, which is the end with the smaller outer diameter of the mixing impeller 30. Along the axial direction (x-direction) of the motor 10, the first blade 11 is spaced apart from the end of the shroud 20 opposite to the air inlet 23. In other words, along the axial direction of the motor, the end of the first blade 11 facing away from the air inlet 23 is provided with a part of the air guide channel 50 without the first blade 11. The airflow flowing out from the first blade 11 can collide with the inner wall of the shroud 20 in this part of the air guide channel 50, thereby converting some of the kinetic energy into static pressure. This can generate a higher static pressure difference between the air inlet 23 and the air outlet 24 of the fan, thereby improving the suction capacity of the fan structure 100.
[0066] It should be noted that in the embodiments of this application, "deviation" refers to a broad sense of deviation, and is not limited to a back-to-back parallel relative arrangement.
[0067] By setting the outer diameter of the first end 31 of the mixing impeller 30 to be larger than the outer diameter of the second end 32 of the mixing impeller 30, this design allows the airflow to gradually diffuse as it passes through the mixing impeller 30, making the process of converting kinetic energy into static pressure smoother and more efficient. As the airflow passes through the gradually widening channel, its velocity decreases and the static pressure increases, thereby improving the pressure output capacity of the fan.
[0068] By setting the first blade 11 on the outside of the motor 10 and spacing the first blade 11 from the end of the shroud 20 away from the air inlet 23, air enters from the air inlet 23, is accelerated by the mixing impeller 30, passes through the gap between the first blades 11, enters the air guide channel 50 at the end of the first blades 11 away from the air inlet 23, and then flows out from the air outlet 24. Here, when the airflow accelerated by the mixing impeller 30 passes through the gap between the first blades 11, the airflow velocity decreases, and some of the kinetic energy is converted into static pressure (equivalent to the first diffusion). The airflow flowing out from the gap between the first blades 11 has its velocity reduced again in the air guide channel 50 at the end of the first blades 11 away from the air inlet 23, further increasing the static pressure of the airflow (equivalent to the second diffusion). This allows a higher static pressure difference to be generated between the air inlet 23 and the air outlet 24 of the fan. This increase in pressure difference directly improves the fan's suction capacity and helps to improve the fan's vacuum level.
[0069] Figure 2 The dashed line with an arrow in the middle represents the direction of airflow.
[0070] The gradual reduction in airflow velocity and turbulence reduces noise during fan operation. The first blade 11 is spaced apart from the end of the shroud 20 away from the air inlet 23; this structure enhances fan stability, reduces vibration and wear, and extends fan lifespan. The motor 10 is partially covered by the shroud 20, and airflow passes over its outer side; this design aids in motor heat dissipation, prevents overheating, and improves motor reliability and lifespan.
[0071] In one possible implementation, the second blade 33 is spaced apart from the inner wall of the shroud 20 in the radial (y-direction) direction of the mixing impeller 30. The distance between the second blade 33 and the inner wall of the shroud 20 is less than or equal to 1 mm. For example, the distance between the second blade 33 and the inner wall of the shroud 20 can be 1 mm, 0.9 mm, 0.8 mm, 0.7 mm, 0.6 mm, 0.5 mm, 0.4 mm, 0.3 mm, 0.2 mm, 0.1 mm, etc. In this embodiment, the distance between the second blade 33 and the inner wall of the shroud 20 is not further limited.
[0072] By creating a gap between the second blade 33 and the inner wall of the shroud 20, the mixing impeller 30 does not rub against the inner wall of the shroud 20 during rotation, allowing the mixing impeller 30 to rotate at high speed. A smaller gap between the second impeller and the inner wall of the shroud 20 effectively reduces airflow leakage, thus improving fan efficiency. A smaller gap also allows for more precise control of the airflow path, ensuring the airflow flows in a predetermined direction, reducing turbulence and eddies, and consequently lowering fan noise during operation.
[0073] See also Figure 2 As shown, the fan shroud 20 may include a first housing 21 and a second housing 22 disposed opposite to each other along the axial direction (x direction) of the motor 10. An air guide channel 50 is formed between the first housing 21 and the second housing 22. The first housing 21 is located outside the mixing impeller 30, and the portion of the first housing 21 located outside the mixing impeller 30 extends along the outer contour of the mixing impeller 30 and matches the shape of the outer contour of the mixing impeller 30. An air inlet 23 is located on the side of the first housing 21 facing away from the second housing 22.
[0074] The second housing 22 is located at the end of the first housing 21 opposite to the air inlet 23. The second housing 22 may include a bottom wall 222 and a side wall 221. The side wall 221 is arranged around the motor 10, and the bottom wall 222 is located at the end of the side wall 221 opposite to the air inlet 23. The side wall 221 surrounds the outside of the first blade 11 on the motor 10. One end of the bottom wall 222 is connected to the side wall 221 in the radial direction (y direction), and the other end is fixedly connected to the motor 10. There is a gap between the inner wall of the bottom wall 222 and the first blade 11. This gap can perform secondary diffusion of the airflow passing through the first blade 11. That is, a second diffusion region 52 is formed between the bottom wall 222 and the first blade 11.
[0075] Combination Figure 1 and Figure 2 As shown, in this embodiment of the fan structure 100, the fan shroud 20 is a volute fan shroud 20, shaped like a snail's shell. The air inlet 23 is located at one end in the axial direction (x direction), and the air outlet 24 is located on one side in the circumferential direction (a direction). This arrangement can form multiple diffusion zones within the air guide channel 50. For example, the first blade 11 is the first diffusion zone 51, and the portion of the air guide channel 50 between the first blade 11 and the bottom wall 222 of the second shell 22 is the second diffusion zone 52. By setting multiple diffusion zones, the static pressure difference between the air inlet 23 and the air outlet 24 can be increased, thereby improving the suction capacity of the fan structure 100, reducing turbulence, and lowering noise.
[0076] In this embodiment, the fan cover 20 can be fixedly connected to the motor 10. For example, the second housing 22 is fixedly connected to the fan. Figure 2 As shown, part of the bottom wall 222 of the second housing 22 extends into the interior of the motor 10 and is fixedly connected to the motor 10, which can improve the stability of the fan structure 100.
[0077] Of course, in other embodiments, the second housing 22 can also be directly fixedly connected to the outer wall of the motor 10. In this embodiment, the connection method of the motor 10 and the second housing 22 is not further limited.
[0078] See also Figure 2 As shown, the fan structure 100 may further include a base 40, which is located at the end of the motor 10 away from the output shaft 12 and is fixedly connected to the motor 10. The base 40 can be used to fix the fan structure 100 to the sweeping robot. By providing the base 40, the fan structure 100 can be easily assembled into the sweeping robot.
[0079] See also Figure 2 As shown, the first blade 11 and the second blade 33 are spaced apart along the axial direction of the motor 10.
[0080] By arranging the first blade 11 and the second blade 33 at axial intervals, the airflow path can be better managed, making the airflow more orderly and efficient as it passes through the system. This reduces airflow interference between blades, helps reduce the generation of turbulence and eddies, improves the overall efficiency of the system, and also reduces vibration caused by uneven airflow, thereby improving the system's stability and service life. Because the airflow is smoother and more orderly, the noise level during system operation may be reduced.
[0081] like Figure 3 As shown, the mixed-flow impeller includes a hub 34 and a plurality of second blades 33, wherein the hub 34 is fixedly connected to the output shaft 12. The plurality of second blades 33 are spaced circumferentially along the outer side of the hub 34, forming an air inlet channel between adjacent second blades 33. The ends of the plurality of second blades 33 radially away from the hub 34 collectively form the outer contour of the mixed-flow impeller 30. The inner wall of the portion of the shroud 20 located outside the mixed-flow impeller 30 matches the shape of the outer contour of the mixed-flow impeller 30 (see [reference]). Figure 2 (As shown).
[0082] This configuration better guides airflow along the outer contour of the mixing impeller 30, reducing airflow separation and turbulence. The optimized airflow path helps improve the efficiency and performance of the fan. Through precise matching, the airflow can more effectively convert kinetic energy into static pressure as it passes over the impeller. This increased efficiency enhances the fan's pressure output capability. The matched geometry reduces energy loss due to irregular airflow paths, thus improving the overall energy efficiency of the fan. The smoother and more ordered airflow, along with reduced turbulence and eddies, lowers the noise level during fan operation. The matched design also reduces wind resistance and improves aerodynamic performance, enabling the fan to deliver higher flow rates and pressures at the same power output.
[0083] See also Figure 3 As shown, the second blade 33 is spirally wound around the outside of the hub 34 along the axial direction of the mixed flow impeller 30.
[0084] By spirally winding the second blade 33, airflow can be more effectively guided along the axial and radial directions of the mixing impeller 30, helping to improve the kinetic energy conversion efficiency of the airflow and thus enhancing the performance of the fan. The spiral shape helps to gradually accelerate the airflow and increase its pressure, converting kinetic energy more efficiently into static pressure, thereby increasing the fan's pressure output capacity. The spiral winding design reduces airflow separation and turbulence generation on the blade surface, making the airflow smoother and more orderly, which helps to improve the fan's efficiency and reduce noise. The spiral shape reduces wind resistance and improves aerodynamic performance, enabling the fan to provide higher flow and pressure at the same power. The spirally wound blade design can provide a more uniform force distribution, reducing vibration caused by asymmetrical airflow, thereby improving system reliability and service life.
[0085] It should be noted that, in this embodiment, the specific torsion angle of the spiral winding of the second blade 33 is not further limited, and can be set according to the actual situation. Alternatively, in some embodiments, the second blade 33 may also be arranged along the axial direction of the hub 34. In this embodiment, the arrangement direction of the second blade 33 is not further limited.
[0086] In some embodiments, the mixed-flow impeller 30 can be a 3D mixed-flow impeller. The fluid entering the 3D mixed-flow impeller flows in a direction between radial and axial, forming a mixed flow, with the outlet direction inclined to the axis. The blades of the 3D mixed-flow impeller employ a three-dimensional twisted design, with the cross-sectional shape continuously varying along the blade height and flow direction to adapt to the requirements of mixed flow. The three-dimensional twisted blades more closely conform to the actual streamlines, reducing flow separation and secondary flow losses, and improving energy conversion efficiency. The three-dimensional design can suppress turbulence and cavitation, reduce noise and vibration, and improve operational stability. Compared to traditional centrifugal impellers, the mixed-flow impeller 30 can shorten its axial length through optimized flow channels, making it easier to install in low-profile robotic vacuum cleaners. Of course, in other embodiments, the mixed-flow impeller 30 can also be other types of mixed-flow impellers.
[0087] Figure 4 This is a partial structural diagram of a fan structure 100 provided in an embodiment of this application.
[0088] See Figure 4 As shown, in the radial direction (y direction) of the motor 10, one end of the first blade 11 is fixedly connected to the outer side of the motor 10, and the other end is fitted to the inner wall of the shroud 20.
[0089] For example, one end of the first blade 11 can be fixedly connected to the outside of the motor 10 by welding or integral molding. In this embodiment, the connection method between the first blade 11 and the motor 10 is not further limited.
[0090] For example, the other end of the first blade 11 is fitted against the inner wall of the shroud 20. The first blade 11 can be fixedly connected to the inner wall of the shroud 20, for example, by welding or bonding. This can improve the stability of the fan structure 100. Of course, the first blade 11 and the inner wall of the shroud 20 may not have a fixed connection; for example, they can be fitted but not fixed. In this embodiment, the connection relationship between the first blade 11 and the inner wall of the shroud 20 is not further limited.
[0091] By fixing one end of the first blade 11 to the outside of the motor 10, the stability of the first blade 11 during operation can be ensured, reducing vibration and displacement. The close fit between the first blade 11 and the inner wall of the shroud 20 helps guide the airflow along a predetermined path, reducing airflow separation and turbulence. This optimized airflow path helps improve the efficiency and performance of the system. The close fit design between the first blade 11 and the inner wall of the shroud 20 effectively reduces airflow leakage between the first blade 11 and the shroud 20, ensuring that more airflow is effectively guided through the first blade 11 for kinetic energy and static pressure conversion, improving the diffusion effect, and thus enhancing the suction capacity of the fan. Due to the smooth airflow and reduced turbulence, the noise during system operation can be reduced.
[0092] Figure 5 This is a schematic diagram of another angle of a fan structure 100 provided in an embodiment of this application. Figure 6 This is an exploded structural diagram of a fan structure 100 provided in an embodiment of this application.
[0093] like Figure 5 and Figure 6 As shown, a blank area 13 is provided at the position opposite to the air outlet 24 of the motor 10. The blank area 13 is the area where no first blade 11 is provided. It can also be understood that multiple first blades 11 are evenly distributed along the circumference of the motor 10, but no first blade 11 is provided at the position corresponding to the air outlet 24.
[0094] By leaving a blank area 13 between the motor 10 and the air outlet 24, airflow can be ensured to flow smoothly out of the air outlet 24. This prevents airflow from being re-guided between the first blades or into the mixing impeller when passing through the blank area, thus improving airflow efficiency. In other words, it prevents airflow backflow. This also reduces corresponding airflow interference and lowers system operating noise. The blank area 13 helps redistribute airflow, making it more evenly distributed at the air outlet 24. This uniform airflow distribution helps improve system performance and efficiency. The presence of the blank area 13 helps optimize aerodynamic performance, enabling the system to provide higher flow rate and pressure at the same power, thereby improving the fan's suction capacity.
[0095] In this embodiment, the number of second blades 33 is not further limited.
[0096] See Figure 7 As shown, the first blade 11 is set at an angle to the axis of the motor 10. When the mixing impeller 30 rotates along the helical direction of the second blade 33, the direction of the airflow flowing out from the first end 31 of the mixing impeller 30 is the same as the tilt direction of the first blade 11.
[0097] Figure 7 The dashed line with arrows between the first and second blades indicates the direction of airflow, and direction b indicates the rotation direction of the mixing impeller 30. It can be understood that the first blade 11 is angled relative to the axis of the motor 10, meaning the first blade 11 is inclined relative to the radial plane (cross-section) of the motor 10. The first blade 11 includes a third end 111 and a fourth end 112. In direction c, the third end 111 is closer to the first end 31 of the mixing impeller 30, and the fourth end 112 is farther from the first end 31 of the mixing impeller 30 relative to the third end 111. In the rotation direction b, the fourth end 112 is located in front of the third end 111.
[0098] In this embodiment of the application, in the direction (c direction) from the second end 32 to the first end 31 of the mixed flow impeller 30, the angle θ between the first blade 11 and the axial direction of the motor 10 is an acute angle.
[0099] It should be noted that during operation, the rotation direction of the mixing impeller 30 is usually the same as the helical direction of the second blade 33. That is, during operation, the mixing impeller 30 rotates in the same helical direction as the second blade 33.
[0100] For example, the second blade 33 is spirally wound around the outside of the motor 10 along the axial direction of the motor 10, wherein the spiral direction of the first blade 11 is opposite to the spiral direction of the second blade 33.
[0101] For example, the first blade 11 is wound in a clockwise spiral, and the second blade 33 is wound in a counterclockwise spiral. Alternatively, the first blade 11 is wound in a counterclockwise spiral, and the second blade 33 is wound in a clockwise spiral. In the embodiments of this application, the spiral directions of the first blade 11 and the second blade 33 are not further limited.
[0102] By setting the first blade 11 at an angle to the axis of the motor 10, and when the mixing impeller 30 rotates along the helical direction of the second blade 33, the direction of the airflow exiting from the first end 31 of the mixing impeller 30 is the same as the tilt direction of the first blade 11. This allows the airflow drawn in by the rotating mixing impeller 30 to be directly "thrown" into the space between the first blades 11 after exiting from the first end 31. The airflow continues to flow in the direction it was thrown out into the channel between the first blades 11, allowing for a smooth transition between the mixing impeller 30 and the first blades 11. This reduces turbulence and energy loss when the airflow enters the first blades 11, thereby improving the efficiency of the entire fan structure. The consistency of the airflow direction reduces the formation of turbulence and eddies, which are often one of the main sources of noise in fan structures. By optimizing the airflow path, the noise level during operation can be significantly reduced. Reducing turbulence and vibration reduces wear on mechanical components, thereby extending the service life of the fan structure and reducing maintenance requirements.
[0103] This application also provides a robotic vacuum cleaner, including the fan structure 100 as described in any of the above embodiments. The robotic vacuum cleaners in this application include, but are not limited to, mopping robots or combined sweeping and mopping robots. In this application, the specific type of robotic vacuum cleaner is not further limited.
[0104] The robotic vacuum cleaner in this embodiment can improve suction power, reduce noise, and enhance user experience by setting the aforementioned fan structure 100.
[0105] The various embodiments or implementation methods described in this specification are presented in a progressive manner. Each embodiment focuses on the differences from other embodiments, and the same or similar parts between the embodiments can be referred to each other.
[0106] In the description of this application, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, and are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.
[0107] In the description of this application, it should be understood that the terms “comprising” and “having” as used herein, and any variations thereof, are intended to cover non-exclusive inclusion, for example, a process, method, system, product, or apparatus that includes a series of steps or units is not necessarily limited to those steps or units that are expressly listed, but may include other steps or units that are not expressly listed or that are inherent to such process, method, product, or apparatus.
[0108] Unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the connection within two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances. Furthermore, the terms "first," "second," etc., are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated.
[0109] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of this application, and are not intended to limit them. Although this application has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some or all of the technical features therein. Such modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the scope of the technical solutions of the embodiments of this application.
Claims
1. A fan structure, characterized by comprising: The fan structure comprises: a motor comprising an output shaft and a plurality of first blades, the plurality of first blades being circumferentially spaced apart on the outside of the motor, the output shaft being located at one end of the motor; a mixed flow impeller fixedly connected with the output shaft, the mixed flow impeller comprising a first end and a second end in the axial direction, the first end being arranged close to the first blades, and the outer diameter of the first end being greater than the outer diameter of the second end; a shroud at least partially covering the outside of the motor and the mixed flow impeller, and a guide channel being formed between the shroud, part of the motor, the first blades and the mixed flow impeller; wherein the guide channel comprises an air inlet and an air outlet, the air inlet being located at the second end of the mixed flow impeller, and the air outlet being located at one side of the outer periphery of the shroud; in the axial direction of the motor, the first blades are spaced apart from one end of the shroud away from the air inlet.
2. The fan structure according to claim 1, characterized by The mixed flow impeller comprises a hub and a plurality of second blades; wherein the hub is fixedly connected with the output shaft; the plurality of second blades are circumferentially spaced apart on the outside of the hub, and an air inlet channel is formed between adjacent two second blades; one end of the plurality of second blades away from the hub collectively forms the outer contour of the mixed flow impeller, and the inner wall of the shroud located on the outside of the mixed flow impeller matches the shape of the outer contour of the mixed flow impeller.
3. The fan structure according to claim 2, characterized by In the radial direction of the mixed flow impeller, the second blades are spaced apart from the inner wall of the shroud; wherein the spacing between the second blades and the inner wall of the shroud is less than or equal to 1 mm.
4. The fan structure according to claim 3, characterized by The spacing between the second blades and the inner wall of the shroud is less than or equal to 0.5 mm.
5. The fan structure according to any one of claims 1 to 4, characterized in that, In the radial direction of the motor, one end of the first blades is fixedly connected with the outside of the motor, and the other end is arranged in abutment with the inner wall of the shroud.
6. The fan structure according to claim 5, wherein The position of the motor opposite to the air outlet is provided with a blank area, and the blank area is an area without the first blades.
7. The fan structure according to any one of claims 2 to 4, wherein The second blades are spirally wound on the outside of the hub in the axial direction of the mixed flow impeller.
8. The fan structure according to claim 7, characterized by The first blades are arranged at an angle with the axial direction of the motor; wherein when the mixed flow impeller rotates in the spiral direction of the second blades, the direction of the airflow out of the first end of the mixed flow impeller is the same as the inclination direction of the first blades.
9. The fan structure according to any one of claims 2 to 4, wherein In the axial direction of the motor, the first blades and the second blades are spaced apart.
10. A robot vacuum cleaner characterised in that, The fan structure comprises any one of claims 1-9.