Impeller, centrifugal fan and cleaning equipment

Abstract

The utility model discloses an impeller, a centrifugal fan and cleaning equipment, and belongs to the technical field of fans. The impeller comprises a first end cover, a second end cover and a plurality of blades arranged between the first end cover and the second end cover, the second end cover is provided with an air inlet, the central axis of the impeller is located in the middle of the blades, and the central axis of the impeller is located in the middle of the air inlet. The blades are backward bending blades, and the backward bending angles alpha of the blades are between 58 degrees and 64 degrees; the ratio of the diameter d of the air inlet to the outer diameter D of the impeller ranges from 0.54 to 0.62. According to the utility model, the impeller adopts the backward bending type blades, so that the energy consumption is lower and the efficiency is higher; the rear bending angles of the blades are arranged between 58 degrees and 64 degrees, and the ratio range of the diameter of the air inlet to the diameter of the impeller is controlled between 0.54 and 0.62, so that the efficiency of the fan can be improved, the suction power of the fan can be improved, and the cruising ability of the cleaning equipment is further improved; noise can be reduced, and user experience is improved.

Description

Technical Field

[0001] The utility model relates to the technical field of fans, in particular to an impeller, a centrifugal fan and a cleaning device. Background Art

[0002] With the rapid development of technology, cleaning devices such as floor sweeping robots and dust collectors have been widely used. These cleaning devices use a fan to generate negative pressure, effectively sucking dust, fine particles, etc. on the ground or other areas into the dust collection device, thus realizing efficient and convenient cleaning work. These cleaning devices not only improve the efficiency and quality of cleaning work, but also bring a comfortable and healthy living environment for people.

[0003] The battery life of cleaning devices is one of the important performances concerned by users. Insufficient battery life will cause the cleaning device to charge frequently, which is inconvenient to use. Taking the floor sweeping robot as an example, for a family with a large area, if the floor sweeping robot has insufficient battery life, it may not be able to complete the whole-house cleaning after one charge, resulting in the need to wait for the floor sweeping robot to charge again before continuing the cleaning, which is inconvenient for users.

[0004] The fan is the main energy-consuming component of cleaning devices such as floor sweeping robots. The power consumption of the fan greatly affects the working duration of the cleaning device. However, in related technologies, the fan structures in many cleaning devices are not reasonably designed, reducing the fan efficiency and being unfavorable for improving the battery life of the cleaning device. Content of the Utility Model

[0005] The purpose of the embodiments of the utility model is to provide an impeller, a centrifugal fan and a cleaning device. By optimizing the design of the impeller, the fan efficiency can be improved, the battery life of the cleaning device can be enhanced, and the noise is relatively small, thus improving the use experience of the cleaning device.

[0006] To achieve the above object, the utility model adopts the following technical solutions:

[0007] An impeller includes a first end cover, a second end cover and a plurality of blades arranged between the first end cover and the second end cover. The second end cover is provided with an air inlet. The central axis of the impeller is located among the plurality of blades, and the central axis of the impeller is located in the middle of the air inlet;

[0008] The blades are backward-curved blades, and the backward-curved angle α of the blades is between 58 degrees and 64 degrees;

[0009] The ratio of the diameter d of the air inlet to the outer diameter D of the impeller is between 0.54 and 0.62;

[0010] The outer diameter D of the impeller is between 39 mm and 47 mm.

[0011] Optionally, the impeller has an air outlet, which is located between the first end cover, the second end cover and the adjacent blades. The ratio of the height h of the air outlet to the outer diameter D of the impeller is between 0.06 and 0.12.

[0012] Optionally, the number of blades arranged between the first end cover and the second end cover is 7 to 9.

[0013] Optionally, the backward bend angle α of the blade is between 59 degrees and 63 degrees;

[0014] And / or, the ratio of the diameter d of the air inlet to the outer diameter D of the impeller is between 0.56 and 0.62;

[0015] And / or, the ratio of the height h of the air outlet to the outer diameter D of the impeller is between 0.07 and 0.11;

[0016] And / or, the diameter d of the air inlet is between 22.5 mm and 26.5 mm;

[0017] And / or, the outer diameter D of the impeller is between 40.77 mm and 47.3 mm.

[0018] Optionally, the backward bend angle α of the blade is 61.6 degrees to 61.8 degrees;

[0019] And / or, the ratio of the diameter d of the air inlet to the outer diameter D of the impeller is between 0.57 and 0.58;

[0020] And / or, the ratio of the height h of the air outlet to the outer diameter D of the impeller is between 0.07 and 0.09.

[0021] A centrifugal fan includes an impeller as described in the above solution, and also includes a volute; the volute has an inner cavity, and the impeller is arranged in the inner cavity.

[0022] Optionally, a housing inlet and a housing outlet are arranged on adjacent sides of the volute. The housing inlet is communicated with the inner cavity, and the housing outlet is communicated with the inner cavity; the position of the housing inlet corresponds to the position of the air inlet of the impeller;

[0023] The inner cavity includes a main channel section and a diffuser section; in the main channel section, the minimum distance Tmin between the inner wall of the volute and the outer circumference of the impeller is between 4.675 mm and 6.325 mm; the maximum distance Tmax between the inner wall of the volute and the outer circumference of the impeller is between 8.5 mm and 11.5 mm;

[0024] The diffuser section has a diffuser angle β, and the diffuser angle β is between 8 degrees and 16 degrees;

[0025] The bevel angle of the housing outlet is γ, and the bevel angle γ is between 8 degrees and 20 degrees; the plane where the housing outlet is located is the first plane, the plane on the side away from the central axis in the expansion section of the volute is the second plane, and the plane perpendicular to the second plane is the third plane. The included angle between the first plane and the third plane is the bevel angle γ.

[0026] Optionally, the Tmin is between 4.95 mm and 6.05 mm, and the Tmax is between 9 mm and 11 mm;

[0027] The expansion section has an expansion angle β, and the expansion angle β is between 8 degrees and 10.81 degrees;

[0028] The bevel angle of the housing outlet is γ, and the bevel angle γ is between 12.75 degrees and 17.25 degrees.

[0029] Optionally, the Tmin is 5.5 mm and the Tmax is 10 mm;

[0030] The expansion section has an expansion angle β, and the expansion angle β is 9.4 degrees;

[0031] The bevel angle of the housing outlet is γ, and the bevel angle γ is 15 degrees;

[0032] The centrifugal fan further includes a motor, the output shaft of the motor is connected to the impeller, and the motor is used to drive the impeller to rotate.

[0033] A cleaning device includes the centrifugal fan as described in the above solution.

[0034] The beneficial effects of the present utility model are as follows: In the impeller and the centrifugal fan, the impeller adopts backward-curved blades, and the backward-curved blades have lower energy consumption and higher efficiency; the backward-curved angle of the blades is set between 58 degrees and 64 degrees, and the ratio range of the diameter of the air inlet to the diameter of the impeller is controlled between 0.54 and 0.62, optimizing the impeller design, which can improve the efficiency of the fan, increase the suction power of the fan, and further improve the battery life of the cleaning device; and it can reduce noise and enhance the user experience. Description of the Drawings

[0035] The following further describes the present utility model in detail according to the drawings and embodiments.

[0036] Figure 1 It is a schematic diagram of the overall structure of the impeller according to the embodiment of the present utility model;

[0037] Figure 2 It is a cross-sectional view of the impeller according to the embodiment of the present utility model;

[0038] Figure 3 It isFigure 2 Enlarged view of part A in

[0039] Figure 4 Longitudinal sectional view of the impeller according to the embodiment of the present utility model;

[0040] Figure 5 One of the overall structural schematic diagrams of the centrifugal fan according to the embodiment of the present utility model (the power device is omitted in the figure);

[0041] Figure 6 Another overall structural schematic diagram of the centrifugal fan according to the embodiment of the present utility model (the power device is omitted in the figure);

[0042] Figure 7 One of the sectional views of the centrifugal fan according to the embodiment of the present utility model;

[0043] Figure 8 Side view of the centrifugal fan according to the embodiment of the present utility model;

[0044] Figure 9 Internal view of the volute of the centrifugal fan according to the embodiment of the present utility model (part of the volute is omitted);

[0045] Figure 10 Difference between the structural design of the centrifugal fan according to the embodiment of the present utility model and the structural design of the traditional fan;

[0046] Figure 11 Difference in experimental data between the centrifugal fan according to the embodiment of the present utility model and the traditional fan.

[0047] In the figure: 10. Impeller; 101. Air inlet; 102. Air outlet; 103. Central axis; 11. First end cover; 12. Second end cover; 121. Outer edge part; 122. Central part; 13. Blade; 131. Inner end of blade; 132. Outer end of blade; 133. Outer wall surface; 20. Volute; 201. Volute inlet; 202. Volute outlet; 203. Inner wall surface; 21. Main channel section; 22. Outer expansion section. Detailed implementation manners

[0048] To make the technical problems solved by the present utility model, the technical solutions adopted and the achieved technical effects clearer, the technical solutions of the embodiments of the present utility model will be further described in detail below with reference to the drawings. Obviously, the described embodiments are only part of the embodiments of the present utility model, rather than all of them. Based on the embodiments of the present utility model, all other embodiments obtained by those skilled in the art without creative efforts belong to the scope of protection of the present utility model.

[0049] In the description of the present utility model, unless otherwise clearly defined and limited, the terms "connected" and "fixed" shall be understood in a broad sense. For example, it may be a fixed connection, a detachable connection or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements or the interaction relationship between two elements. For those of ordinary skill in the art, the specific meanings of the above terms in the present utility model can be understood according to specific circumstances.

[0050] In the present utility model, unless otherwise clearly defined and limited, the first feature being "above" or "below" the second feature may include the direct contact between the first and second features, or may include the situation where the first and second features are not in direct contact but in contact through additional features therebetween. Moreover, the first feature being "above", "over" and "on the top of" the second feature includes that the first feature is directly above and obliquely above the second feature, or merely means that the horizontal height of the first feature is higher than that of the second feature. The first feature being "below", "under" and "beneath" the second feature includes that the first feature is directly below and obliquely below the second feature, or merely means that the horizontal height of the first feature is lower than that of the second feature.

[0051] With the acceleration of the modern life rhythm and the increasing work pressure, cleaning devices such as floor sweeping robots, vacuum cleaners, and mite removers are widely used, liberating people from tedious daily cleaning work such as floor sweeping. Taking the floor sweeping robot as an example, when the floor sweeping robot is cleaning, it generally uses a rolling brush in cooperation with a side brush to rotate at high speed to sweep in garbage, and then through the vacuum negative pressure generated by a blower, the dust and garbage debris on the surface are sucked into the machine interior to complete the cleaning work.

[0052] The blower is the core component in cleaning devices such as floor sweeping robots that is responsible for generating air flow to suck in impurities such as dust and dirt. Therefore, the blower is the main energy-consuming component in the cleaning device. The power consumption of the blower directly affects the battery life of the cleaning device. The greater the power consumption, the faster the battery energy is consumed, and the shorter the working duration of the cleaning device. For example, if the design of the blower is unreasonable, resulting in low efficiency, then in order to maintain the same cleaning effect, the blower requires higher power consumption, thus shortening the working duration of the device. Among them, the power consumption of the blower mainly refers to the power or energy consumed by the blower during operation to generate air flow or maintain the air flow, and this power consumption is mainly used to overcome the resistance generated during air flow, such as frictional resistance, pipeline resistance, etc.

[0053] Taking a floor cleaning robot as an example, based on user experience and cleaning ability requirements, the standard walking linear speed of many floor cleaning robots is basically set at 0.25 m / s. Under the condition of taking a three-bedroom house with an area of 100 square meters as the standard simulation test environment, when a floor cleaning robot with map path planning function cleans the whole house once, the required working time is about 90 minutes. This requires the battery of the floor cleaning machine to provide at least 90 minutes of battery life. As the main energy-consuming component of the floor cleaning machine, the power consumption of the blower largely determines the working duration of the floor cleaning machine. Under the condition that other parameters remain unchanged, it is required that the efficiency of the blower and the motor be as high as possible. However, in the related technology, the efficiency of the blower of the floor cleaning robot is basically about 40%, which cannot meet the higher battery life requirements. How to further improve the battery life of the cleaning equipment while ensuring efficient cleaning and meeting the fundamental cleaning needs is an urgent problem to be solved at present.

[0054] To improve this problem, referring to Figures 1 to 9 , the present application provides an impeller 10, a centrifugal blower using the impeller 10, and a cleaning device using the centrifugal blower, so as to improve the efficiency of the blower, thereby enhancing the battery life of the cleaning device, improving the one-time dust removal efficiency, coverage rate, and cleaning ability of the cleaning device, and reducing the noise of the cleaning device in its standard working mode.

[0055] The cleaning device can be a floor cleaning robot, a sweeping and mopping multi-functional robot, a vacuum cleaner, etc.

[0056] In one embodiment, through the optimized design and mutual matching of the structures of the impeller 10 and the volute 20, the overall performance of the blower is improved. The maximum efficiency of the blower can reach about 48%, and the maximum suction power is about 33 w. When the suction power reaches 33 w, the driving power of the motor is about 69 w, realizing the improvement of the battery life of the floor cleaning robot and reducing the power consumption of the blower at the same time. Referring to Figure 10 . Figure 11 , compared with three traditional blowers, the high-efficiency blower of the present application has improved blower efficiency.

[0057] Please refer to Figures 1 to 9 , the structures of the impeller 10 and the centrifugal blower will be described below. The centrifugal blower includes an impeller 10, a volute 20, and a power device (not shown in the figure). The impeller 10 is arranged inside the volute 20, and the power device is used to drive the impeller 10 to rotate. The power device can be, but is not limited to, a motor, and can be connected to the first end cover 11 through the motor shaft of the motor to drive the impeller 10 to rotate.

[0058] Please continue to refer to Figure 1 . Figure 4, the impeller 10 includes a first end cover 11, a second end cover 12, and a plurality of blades 13. The impeller 10 has a central axis 103, and the first end cover 11 and the second end cover 12 are spaced apart in the direction of the central axis 103. The plurality of blades 13 are disposed between the first end cover 11 and the second end cover 12. The impeller 10 is provided with an air inlet 101 and an air outlet 102, and the air inlet 101 is provided at the middle position of the second end cover 12. Refer to Figure 2 , the plurality of blades 13 are spaced apart around the central axis 103, and the air outlet 102 is located between the first end cover 11, the second end cover 12, and two adjacent blades 13. Refer to Figure 4 , Figure 9 , the central axis 103 is located in the middle of the plurality of blades 13, and moreover, the central axis 103 is located in the middle of the air inlet 101, and the central axis 103 passes through the air inlet 101.

[0059] The blades 13 of the impeller 10 adopt a backward-curved design. The bending direction of the backward-curved blades 13 is opposite to the rotation direction of the impeller 10. Taking Figure 2 as an example, the blade 13 is bent clockwise, and the impeller 10 is configured to rotate counterclockwise. In the figure, ω indicates the rotational angular velocity of the impeller 10. The backward-curved design of the blade 13 makes the adhesion of the fluid on the blade 13 better, the flow loss in the channels of the backward-curved blade 13 is small, the air flow is smoother, the flow loss is reduced, a better fan efficiency can be obtained, the efficiency and the negative pressure value are balanced, and moreover, it is beneficial to reduce the operation noise of the fan.

[0060] Refer to Figure 3 , the backward-curved angle of the blade 13 is α, the diameter of the air inlet 101 of the impeller 10 is d, the height of the air outlet 102 of the impeller 10 is h, and the outer diameter of the impeller 10 is D.

[0061] Refer to Figure 2 , Figure 3 , the backward-curved angle α of the blade 13 is determined in the following manner: One end of the blade 13 close to the central axis 103 is the leading end of the blade, and the end far from the central axis 103 is the outer end 132 of the blade. The outer end 132 is flush with or close to the outer peripheral edge of the first end cover 11; the backward-curved angle of the blade 13 is determined by a first reference line L1 and a second reference line L2. The first reference line L1 passes through the central axis 103 of the impeller 10 and the outer end 132 of the blade, and the second reference line L2 is tangent to the area of the convex arc surface of the blade 13 close to the outer end 132. The included angle between the first reference line L1 and the second reference line L2 is the backward-curved angle.

[0062] Refer to Figure 4 , the diameter d of the air inlet 101 of the impeller 10 refers to the radial dimension of the air inlet 101. Continue to refer to Figure 4, the height h of the air outlet 102 of the impeller 10 refers to the axial dimension of the air outlet 102; optionally, the height of the air outlet 102 of the impeller 10 is the distance between the outer edge of the first end cover 11 and the outer edge of the second end cover 12. The outer diameter D of the impeller 10 refers to the dimension of the whole impeller 10 in the radial direction; optionally, the first end cover 11 and the second end cover 12 are coaxially arranged, the diameters of the first end cover 11 and the second end cover 12 are the same, and the outer diameter D of the impeller 10 is equal to the diameter of the end cover.

[0063] In this application, the backward bend angle α of the blade 13 is between 58 degrees and 64 degrees, that is, 58° ≤ α ≤ 64°. And, the ratio of the diameter d of the air inlet 101 to the outer diameter D of the impeller 10 is between 0.54 and 0.62, that is, 0.54 ≤ d / D ≤ 0.62. Through the design of the backward bend angle, combined with the design of the ratio of the diameter of the air inlet 101 to the diameter of the impeller 10, when the impeller 10 is applied to a fan, it is beneficial to improve the performance of the impeller 10.

[0064] And, the outer diameter D of the impeller 10 is between 39 mm and 47 mm.

[0065] Among them, 58° ≤ α ≤ 64°, the range of the backward bend angle α is reasonable. On this basis, the fan can have higher efficiency. The larger the backward bend angle, the higher the fan efficiency, and the greater the circumferential speed of the outer circle of the impeller 10 required to reach the same vacuum degree.

[0066] 0.54 ≤ d / D ≤ 0.62, the range of d / D is reasonable, which can avoid the diameter of the air inlet 101 from being too large, so as to ensure that when reaching a higher vacuum degree, the fan consumes less power, which is beneficial to improving the fan efficiency. On this basis, the larger d / D is, the greater the air volume of the fan is, which is beneficial to improving the dust suction capacity of the cleaning equipment.

[0067] In one embodiment, the backward bend angle α of the blade 13 is between 59 degrees and 63 degrees.

[0068] Optionally, the backward bend angle α of the blade 13 is between 61.6 degrees and 61.8 degrees.

[0069] Optionally, the backward bend angle α of the blade 13 is 61.7 degrees.

[0070] In one embodiment, the ratio d / D of the diameter d of the air inlet 101 to the outer diameter D of the impeller 10 is between 0.56 and 0.62.

[0071] Optionally, the ratio d / D of the diameter d of the air inlet 101 to the outer diameter D of the impeller 10 is between 0.57 and 0.59.

[0072] Optionally, d / D is 0.58.

[0073] In one embodiment, the diameter d of the air inlet 101 is between 23 mm and 25 mm; and / or, the outer diameter D of the impeller 10 is between 42 mm and 44 mm; and / or, the height h of the air outlet 102 is between 3.4 mm and 3.6 mm.

[0074] Optionally, the diameter d of the air inlet 101 is between 22.5 mm and 26.5 mm, and the outer diameter D of the impeller 10 is between 40.77 mm and 47.3 mm. Exemplarily, d = 25 mm and D = 43 mm.

[0075] In one embodiment, in addition to optimizing the impeller 10 by means of the backward bend angle α of the blade 13 and the ratio of the diameter d of the air inlet 101 to the outer diameter D of the impeller 10, the impeller 10 is controlled by means of the ratio of the height h of the air outlet 102 to the outer diameter D of the impeller 10. The height of the air outlet 102 of the impeller 10 affects both the air volume of the blower and the blower efficiency. The larger the ratio of h to D, the larger the air volume of the air outlet and the higher the efficiency, but the power consumed to reach the same vacuum degree increases. In this application, by controlling the ratio of d / D within a certain range, the blower efficiency and the improvement of the vacuum degree are taken into account, and the endurance capacity, adsorption force, and cleaning power of the cleaning device are taken into account.

[0076] In this embodiment, the height of the air outlet 102 is such that the ratio h / D of h to the outer diameter D of the impeller 10 is between 0.06 and 0.12, that is, 0.06 ≤ h / D ≤ 0.12.

[0077] Optionally, the height of the air outlet 102 is such that the ratio h / D of h to the outer diameter D of the impeller 10 is between 0.07 and 0.11.

[0078] Optionally, the height of the air outlet 102 is such that the ratio h / D of h to the outer diameter D of the impeller 10 is between 0.07 and 0.09.

[0079] Optionally, the ratio of the height h of the air outlet 102 to the outer diameter D of the impeller 10 is 0.08139.

[0080] In one embodiment, the number of blades 13 provided in the impeller 10 ranges from 7 to 9. A reasonable number of blades 13 is crucial for the blower efficiency. The configuration of this embodiment can achieve a relatively high efficiency of the blower, so that the blower can reach a relatively high negative pressure under the same driving power and improve the cleaning power of the cleaning device.

[0081] Optionally, the number of blades 13 provided in the wheel is 7, 8, or 9.

[0082] In one embodiment, the first end cover 11 is disc-shaped or substantially disc-shaped as a whole, and the second end cover 12 includes a central portion 122 and an outer edge portion 121 surrounding the central portion 122. The outer edge portion 121 is arranged axially spaced from the first end cover 11, and the outer edge portion 121 is parallel or substantially parallel to the first end cover 11 to cooperate with defining the air outlet 102, so that the air outlet is more stable. The central portion 122 is approximately trumpet-shaped, and the air inlet 101 is arranged in the central area of the central portion 122. The part of the central portion 122 where the air inlet 101 is arranged is located on the side away from the first end cover 11 where the central portion 122 and the outer edge portion 121 are connected. The inner diameter of the central portion 122 gradually increases from the air inlet 101 to the side close to the first end cover 11, and the inner surface of the central portion 122 is a curved surface. It can be understood that the central portion 122 of the second end cover 12 close to the air inlet side is approximately trumpet-shaped, and the inner curved surface of the central portion 122 can more effectively guide the gas into the impeller 10, reduce the deflection and turbulence of the airflow when entering the impeller 10, improve the stability and uniformity of the airflow, reduce airflow losses, and thereby improve the overall efficiency and vacuum degree of the fan.

[0083] In one embodiment, the end of the blade 13 close to the central axis 103 is the blade inner end 131, and the end away from the central axis 103 is the blade outer end 132. The blade inner end 131 is located outside the air inlet 101 area, and the blade outer end 132 extends to the area close to the outer edge of the first end cover 11 and the second end cover 12 to cooperate and define the air outlet 102. From the blade inner end 131 to the blade outer end 132, the height of the blade 13 gradually decreases.

[0084] It should be noted that the above description of the shapes of the first end cover 11, the second end cover 12, and the blades 13 is not the only limitation to the present application.

[0085] Please continue to refer to the following Figures 5 to 9 , the volute 20 in the centrifugal fan, and the cooperation between the impeller 10 and the volute 20 are further described.

[0086] In one embodiment, the volute 20 is a volute 20 with radial involutes and axial involutes, that is, the shape of the inner wall surface 203 of the volute 20 is based on the radial involute and the axial involute, which helps to evenly distribute and stably flow the airflow inside the volute 20, reduce eddy currents and energy losses, and help improve the static pressure recovery capacity of the fan. The enhancement of the static pressure recovery capacity helps to improve the air extraction capacity of the fan. When the fan is running, it can more effectively inhale, compress and transport the gas, thereby maintaining or improving the vacuum degree.

[0087] The volute 20 has an inner cavity, and the impeller 10 is disposed in the inner cavity. The power device is omitted in the drawings and not shown; exemplarily, the power device is a motor, and the output shaft of the motor extends into the volute 20 through the shaft hole on the lower side of the volute 20 to be connected to the first end cover 11 of the impeller 10 so as to transmit torque to the impeller 10 and drive the impeller 10 to rotate.

[0088] The shell inlet 201 and the shell outlet 202 are provided on adjacent sides, and both the shell inlet 201 and the shell outlet 202 communicate with the inner cavity. Refer to Figure 5 , the position of the shell inlet 201 corresponds to the position of the air inlet 101 of the impeller 10. The shell inlet 201 is used to provide a clearance for the air inlet 101 of the impeller 10. The air flow enters the interior of the impeller 10 through the air inlet 101 of the impeller 10. When the impeller 10 rotates, the gas passes through the channels between two adjacent blades 13 and is then pushed out of the impeller 10 through the air outlet 102 into the volute 20. The inner cavity of the volute 20 has a main channel section 21 and a diffuser section 22. The volute tongue of the volute 20 is provided in the main channel section 21, and the shell outlet 202 is located at the end of the diffuser section 22. The gas enters the main channel section 21 from the impeller 10, is sent through the main channel section 21 into the diffuser section 22, and finally is sent out from the shell outlet 202 of the volute 20.

[0089] In an embodiment, please refer to Figure 7 , in the volute 20, from the volute tongue to the diffuser section 22 and the shell outlet 202 of the volute 20, the distance between the outer circumference of the impeller 10 and the inner wall of the volute 20 gradually increases.

[0090] Please continue to refer to Figure 7 , in the main channel section 21 of the volute 20, the distance between the inner wall of the volute 20 and the outer circumference of the impeller 10 is T. In the drawings, the inner wall of the volute 20 is the inner wall surface 203, and the outer circumference of the impeller 10 is the outer wall surface 133. The minimum distance Tmin between the inner wall of the volute 20 and the outer circumference of the impeller 10 is between 4.675 mm and 6.325 mm; the maximum distance Tmax between the inner wall of the volute 20 and the outer circumference of the impeller 10 is between 8.5 mm and 11.5 mm.

[0091] Exemplarily, as Figure 7 shown, both the third reference line L3L3 and the fourth reference line L4L4 pass through the central axis 103 of the impeller 10, and the third reference line L3L3 is perpendicular to the fourth reference line L4L4. The third reference line L3 passes through the volute tongue or near the volute tongue. The distance between the intersection point of the outer wall surface 133 of the impeller 10 and the third reference line L3L3 and the intersection point of the inner wall surface 203 of the volute 20 and the third reference line L3L3 is Tmin; the fourth reference line L4 is close to the diffuser section 22. The distance between the intersection point of the outer wall surface 133 of the impeller 10 and the fourth reference line L4L4 and the intersection point of the inner wall surface 203 of the volute 20 and the fourth reference line L4L4 is Tmax.

[0092] Among them, the minimum distance Tmin between the outer circumference of the impeller 10 and the inner wall of the volute 20 has an important impact on the fan noise. When other parameters remain unchanged, the smaller Tmin is, the greater the fan noise will be. The maximum distance Tmax between the outer circumference of the impeller 10 and the inner wall of the volute 20 affects the overall size of the whole machine and is restricted by the overall size of the whole machine. In this embodiment, Tmin and Tmax are controlled within the aforementioned ranges, taking into account the requirements of high efficiency, compactness, and low noise of the fan, and improving the practicability of the fan.

[0093] Optionally, the minimum distance Tmin between the inner wall of the volute 20 and the outer circumference of the impeller 10 is between 4.95 mm and 6.05 mm; the maximum distance Tmax between the inner wall of the volute 20 and the outer circumference of the impeller 10 is between 9 mm and 11 mm.

[0094] Optionally, the minimum distance Tmin between the inner wall of the volute and the outer circumference of the impeller 10 is 5.5 mm; the maximum distance Tmax between the inner wall of the volute 20 and the outer circumference of the impeller 10 is 10 mm.

[0095] In one embodiment, please refer to Figure 8 , the expansion section 22 of the volute 20 is located behind the main channel section 21, and is used to further guide the air flow and reduce its flow velocity and increase the static pressure. The expansion section 22 has an expansion angle β, and the expansion angle β is between 8 degrees and 16 degrees. Controlling the expansion angle within this range is beneficial to taking into account various requirements such as high efficiency, compactness, and high vacuum degree of the fan. It can be understood that in order to achieve the same expansion effect, the larger the expansion angle is, the larger the overall size of the volute 20 required will be. Refer to Figure 8 , the expansion angle β is determined by the fifth reference line L5 and the sixth reference line L6, and the fifth reference line L5 and the sixth reference line L6 intersect at the position where the expansion section 22 is connected to the main channel section 21.

[0096] It can be understood that referring to Figure 8 , Figure 9 , the top plate of the volute 20 is the air inlet side, and the top plates of the volute 20 in the two regions of the main channel section 21 and the expansion section 22 are flush. The bottom plate of the volute 20 in the expansion section 22 is inclined downward relative to the bottom plate of the volute 20 in the main channel section 21. In this way, not only is the expansion angle provided to further guide the air flow and reduce its flow velocity and increase the static pressure, but also the overall structural shape of the volute 20 is more conducive to assembly and cooperation with other components.

[0097] Optionally, the expansion angle β is between 8 degrees and 10.34 degrees.

[0098] Optionally, the expansion angle β is between 8.46 degrees and 10.34 degrees.

[0099] Optionally, the expansion angle β is 9.4 degrees.

[0100] In one embodiment, please refer to Figure 7 , the housing outlet 202 of the volute 20 is formed by bevel cutting. In other words, at the end of the expansion section 22 of the volute 20, the end of the expansion section 22 of the volute 20 is cut by an inclined plane, and the outlet after bevel cutting is used as the housing outlet 202. Please continue to refer to Figure 7 , the bevel cutting angle of the housing outlet 202 is γ, the plane where the housing outlet 202 is located is the first plane S1, the plane on the side of the expansion section 22 of the volute 20 away from the central axis 103 is the second plane S2, and the plane perpendicular to the second plane S2 is the third plane S3. The included angle between the first plane S1 and the third plane S3 is the bevel cutting angle γ.

[0101] Among them, the bevel cutting angle γ is between 8 degrees and 20 degrees. The bevel cutting method provides the housing outlet 202 of the volute 20 to increase the area of the outlet of the volute 20, further improving the static pressure recovery ability of the volute 20 and achieving the goal of improving the overall efficiency of the machine. Among them, the larger the bevel cutting angle, the larger the outlet area of the volute 20 and the better the expansion effect; if the bevel cutting angle is too large, the outlet section of the volute 20 will be shortened, which is not conducive to the rectification and uniform recovery of the airflow by the volute 20. Controlling the bevel cutting angle within the foregoing range is beneficial to improving the vacuum degree of the fan.

[0102] Optionally, the bevel cutting angle γ is between 12.75 degrees and 17.25 degrees.

[0103] Optionally, the bevel cutting angle γ is between 13.5 degrees and 16.5 degrees.

[0104] Optionally, the bevel cutting angle γ is 15 degrees.

[0105] In one embodiment, refer to Figure 10 , the configuration method of the impeller 10 and the volute 20 is described as follows:

[0106] The backward bend angle α of the blade 13 is 61.7 degrees. The ratio d / D of the diameter d of the air inlet 101 to the outer diameter D of the impeller 10 is 0.5814. The diameter of the air inlet 101 is 25 mm, and the outer diameter D of the impeller 10 is 43 mm. The ratio h / D of the height h of the air outlet 102 to the outer diameter D of the impeller 10 is 0.0814. The number of blades 13 is 7. The minimum radial distance Tmin between the outer wall surface 133 of the impeller 10 and the inner wall surface 203 of the volute 20 is 5.5 mm, the maximum radial distance Tmax between the outer wall surface 133 of the impeller 10 and the inner wall surface 203 of the volute 20 is 10 mm, the expansion angle β of the volute 20 is 9.4 degrees, and the bevel cutting angle γ of the volute 20 is 15 degrees.

[0107] In this embodiment, through the design of parameters such as α, d / D, h / D, the number of blades 13, Tmin, Tmax, β, γ, etc., the performance of the impeller 10 and the volute 20 can be optimized. Through the optimized cooperation of the impeller 10 and the volute 20, the effects of improving the fan efficiency, reducing the fan power consumption, and increasing the battery life of the cleaning device can be achieved.

[0108] Based on the Figure 10 optimized design of the impeller 10 and the volute 20 in the illustrated embodiment, relevant experimental tests were carried out on this fan. Figure 11 The experimental results are shown. The maximum efficiency of this fan can reach 48%, and the maximum suction power is 33.15w. By matching the design of the fan impeller 10 and the volute 20, when the suction power reaches 33.15w, the driving power of the motor is 68.8w, achieving the improvement of the cleaning ability of the sweeping robot and at the same time reducing the fan power consumption.

[0109] It should be noted that taking the sweeping robot in the related technology as an example, through experiments, under the same input voltage, input current, and input power, the efficiency of the existing sweeping robot fan is basically about 40%. The fan in this embodiment can reach an efficiency of 48% under the same conditions, with an efficiency increase of about 20%. While ensuring efficient cleaning and meeting the basic cleaning needs, the battery life of the sweeping machine is improved.

[0110] In the description of this article, it should be understood that the orientation or positional relationships such as "upper", "lower", "left", "right", etc. are based on the orientation or positional relationships shown in the drawings, and are only for the convenience of description and simplifying the operation, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation of the present invention. In addition, the terms "first" and "second" are only used for distinction in description and have no special meaning.

[0111] In the description of this specification, the description referring to terms such as "one embodiment", "example", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms do not necessarily refer to the same embodiment or example.

[0112] In addition, it should be understood that although this specification is described according to embodiments, not every embodiment only contains an independent technical solution. This narrative way of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each embodiment can also be appropriately combined to form other embodiments that can be understood by those skilled in the art.

[0113] The technical principle of the present invention is described above in combination with specific embodiments. These descriptions are only for explaining the principle of the present invention and cannot be interpreted as limiting the protection scope of the present invention in any way. Based on the explanations here, technicians in this field can think of other specific implementation methods of the present invention without creative work, and these methods will fall within the protection scope of the present invention.

Claims

1. An impeller, characterized in that, It includes a first end cover (11), a second end cover (12), and a plurality of blades (13) disposed between the first end cover (11) and the second end cover (12). The second end cover (12) is provided with an air inlet (101). The central axis (103) of the impeller (10) is located in the middle of the plurality of blades (13), and the central axis (103) of the impeller (10) is located in the middle of the air inlet (101). The blade (13) is a backward-curved blade, and the backward-curved angle α of the blade (13) is between 58 degrees and 64 degrees. The ratio of the diameter d of the air inlet (101) to the outer diameter D of the impeller (10) is between 0.54 and 0.

62. The outer diameter D of the impeller (10) is between 39 mm and 47 mm.

2. The impeller according to claim 1, wherein The impeller (10) has an air outlet (102). The air outlet (102) is located between the first end cover (11), the second end cover (12), and the adjacent blade (13). The ratio of the height h of the air outlet (102) to the outer diameter D of the impeller (10) is between 0.06 and 0.

12.

3. The impeller according to claim 1, characterized in that, The number of blades (13) disposed between the first end cover (11) and the second end cover (12) is 7 to 9.

4. The impeller according to claim 2, wherein, The backward-curved angle α of the blade (13) is between 59 degrees and 63 degrees. and / or, the ratio of the diameter d of the air inlet (101) to the outer diameter D of the impeller (10) is between 0.56 and 0.

62. and / or, the ratio of the height h of the air outlet (102) to the outer diameter D of the impeller (10) is between 0.07 and 0.

11. and / or, the diameter d of the air inlet (101) is between 22.5 mm and 26.5 mm. and / or, the outer diameter D of the impeller (10) is between 40.77 mm and 47.3 mm.

5. The impeller according to claim 2, characterized in that, The backward-curved angle α of the blade (13) is between 61.6 degrees and 61.8 degrees. and / or, the ratio of the diameter d of the air inlet (101) to the outer diameter D of the impeller (10) is between 0.5713 and 0.

59. and / or, the ratio of the height h of the air outlet (102) to the outer diameter D of the impeller (10) is between 0.07 and 0.

09. and / or, the diameter d of the air inlet (101) is between 23 mm and 25 mm. and / or, the outer diameter D of the impeller (10) is between 42 mm and 44 mm. and / or, the height h of the air outlet (102) is between 3.4 mm and 3.6 mm.

6. A centrifugal fan, characterized in that, It includes the impeller (10) according to any one of claims 1-5, and further includes a volute (20); the volute (20) has an inner cavity, and the impeller (10) is disposed in the inner cavity.

7. The centrifugal fan according to claim 6, wherein, The adjacent two sides of the volute (20) are provided with a shell inlet (201) and a shell outlet (202). The shell inlet (201) is communicated with the inner cavity, and the shell outlet (202) is communicated with the inner cavity; the position of the shell inlet (201) corresponds to the position of the air inlet (101) of the impeller (10). The inner cavity includes a main channel section (21) and a diffuser section (22); in the main channel section (21), the minimum distance Tmin between the inner wall of the volute (20) and the outer circumference of the impeller (10) is between 4.675 mm and 6.325 mm; the maximum distance Tmax between the inner wall of the volute (20) and the outer circumference of the impeller (10) is between 8.5 mm and 11.5 mm; The diffuser section (22) has a diffuser angle β, and the diffuser angle β is between 8 degrees and 16 degrees; The bevel angle of the volute outlet (202) is γ, and the bevel angle γ is between 8 degrees and 20 degrees; the plane where the volute outlet (202) is located is the first plane, the plane on the side of the diffuser section (22) of the volute (20) away from the central axis (103) is the second plane, and the plane perpendicular to the second plane is the third plane, and the included angle between the first plane and the third plane is the bevel angle γ.

8. The centrifugal fan according to claim 7, characterized in that, The Tmin is between 4.95 mm and 6.05 mm, and the Tmax is between 9 mm and 11 mm; The diffuser section (22) has a diffuser angle β, and the diffuser angle β is between 8 degrees and 10.81 degrees; The bevel angle of the volute outlet (202) is γ, and the bevel angle γ is between 12.75 degrees and 17.25 degrees.

9. The centrifugal fan according to claim 7, characterized in that, The Tmin is 5.5 mm, and the Tmax is 10 mm; The diffuser section (22) has a diffuser angle β, and the diffuser angle β is 9.4 degrees; The bevel angle of the volute outlet (202) is γ, and the bevel angle γ is 15 degrees; The centrifugal fan further includes a motor, the output shaft of the motor is connected to the impeller (10), and the motor is used to drive the impeller (10) to rotate.

10. A cleaning device, characterized in that, A centrifugal fan comprising the centrifugal fan according to any one of claims 6-9.

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