Centrifugal impeller and purifier

Abstract

The application provides a centrifugal impeller and a purifier, the number of blades is multiple, the multiple blades are arranged along the circumference of the centrifugal impeller and are connected with a cover body, each blade of the multiple blades comprises at least two circular arc segments; a flow guide ring is located on the side of the blade away from the cover body and is connected with the blade; the multiple blades comprise adjacent first blades and second blades, the first blade comprises a first circular arc segment and a second circular arc segment, the first circular arc segment is closer to the axis of the centrifugal impeller than the second circular arc segment; the vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first circular arc segment is a first distance; the vertical distance between the side of the second circular arc segment away from the axis of the centrifugal impeller and the second blade is a second distance; the vertical distance between the side of the first circular arc segment away from the axis of the centrifugal impeller and the second blade is a third distance; the first distance is smaller than the second distance, and the second distance is smaller than the third distance. The application realizes the reduction of vortex between blades and the flow separation of air flow.

Description

TECHNICAL FIELD

[0001] The present application relates to the technical field of air purification, and specifically provides a centrifugal impeller and a purifier. BACKGROUND

[0002] At present, as a room air purification product, the air purifier is more and more favored by consumers because it can significantly reduce the small particles such as formaldehyde in the house. With the development of technology, consumers have higher and higher requirements for the performance and user experience of the purifier.

[0003] The air purifier is provided with a centrifugal impeller. In the related art, the blades of the centrifugal impeller extend in an arc shape. The structure of this kind of centrifugal impeller is not smooth in guiding the airflow between the blades, which leads to serious flow separation of the airflow between the blades, more turbulence between the blades, and greater impact of the airflow on the blades, resulting in greater noise. SUMMARY

[0004] The present application aims to at least solve one of the problems in the prior art or related art.

[0005] To this end, the first aspect of the present application provides a centrifugal impeller.

[0006] The second aspect of the present application provides another centrifugal impeller.

[0007] The third aspect of the present application provides still another centrifugal impeller.

[0008] The fourth aspect of the present application provides a purifier.

[0009] Therefore, the first aspect of the present application provides a centrifugal impeller, which comprises a cover body, blades and a flow guide ring. The number of blades is multiple, and the multiple blades are arranged along the circumference of the centrifugal impeller and connected with the cover body. Each blade of the multiple blades comprises at least two arc segments. The flow guide ring is located on the side of the blade away from the cover body and connected with the blade. The multiple blades comprise adjacent first and second blades. The at least two arc segments of the first blade comprise a first arc segment and a second arc segment, and the first arc segment is closer to the axis of the centrifugal impeller than the second arc segment. The vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first arc segment is a first distance. The vertical distance between the side of the second arc segment away from the axis of the centrifugal impeller and the second blade is a second distance. The vertical distance between the side of the first arc segment away from the axis of the centrifugal impeller and the second blade is a third distance. The first distance is smaller than the second distance, and the second distance is smaller than the third distance.

[0010] The centrifugal impeller provided by the application can be applied to purifiers and other fluid power machines such as pumps, fans and compressors.

[0011] Specifically, the centrifugal impeller comprises a cover body, blades and a flow guide ring. The cover body is a basic part of the centrifugal impeller and provides support and connection for the blades.

[0012] The plurality of blades are uniformly arranged along the circumference of the centrifugal impeller and connected to the cover body. Each blade is composed of at least two circular arc segments, which endows the blade with a specific shape and curvature.

[0013] The flow guide ring is located on the side of the blade away from the cover body and connected to the blade. The flow guide ring guides the fluid into the blade, optimizes the flow path of the fluid and reduces energy loss.

[0014] Taking adjacent first and second blades as an example, the first blade is composed of a first circular arc segment and a second circular arc segment. The first circular arc segment is located on the inner side of the blade and closer to the axis of the centrifugal impeller. The second circular arc segment is located on the outer side of the blade and away from the axis of the centrifugal impeller.

[0015] The vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first circular arc segment is a first distance; the vertical distance between the side of the second circular arc segment away from the axis of the centrifugal impeller and the second blade is a second distance; and the vertical distance between the side of the first circular arc segment away from the axis of the centrifugal impeller and the second blade is a third distance.

[0016] The first distance is smaller than the second distance, and the second distance is smaller than the third distance. The distance between the side of the second blade close to the axis of the centrifugal impeller and the first circular arc segment (the first distance) is smaller, so that the part of the blade close to the axis is more compact. The distance between the side of the second circular arc segment away from the axis and the second blade (the second distance) is larger, so that the blade is more open on the outer side.

[0017] The distance between the side of the first circular arc segment away from the axis of the centrifugal impeller and the second blade (the third distance) is between the first distance and the second distance. This design makes the blade present a curved shape of "compact inside and loose outside" between the inner and outer sides.

[0018] The application designs the profile of the blade, sets a double-circular-arc blade, and improves the curvature of the circular arc on the basis of the combination of the two circular arc segments by limiting the third distance. The fluid can flow more smoothly when passing through the blade, and the inter-blade vortex caused by flow turbulence is reduced.

[0019] The bending shape of the blade helps to guide the fluid to flow along the blade surface, reduces the separation phenomenon of the fluid and the blade surface, and improves the efficiency and performance of the centrifugal impeller.

[0020] In conclusion, the centrifugal impeller provided by the application realizes the reduction of inter-blade vortex and flow separation of airflow, improves the performance and efficiency of the centrifugal impeller, and improves the user's experience.

[0021] In addition, the centrifugal impeller in the above technical solution provided by the application can also have the following additional technical features:

[0022] In some technical solutions of the application, optionally, the angle of the inlet installation angle of the centrifugal impeller is a first angle; the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees.

[0023] In some technical solutions of the application, optionally, the angle of the outlet installation angle of the centrifugal impeller is a second angle; the second angle is greater than 9.2 degrees and less than or equal to 22.3 degrees.

[0024] In some technical solutions of the application, optionally, the outer circle radius of the centrifugal impeller is a first radius; the radius of the first arc segment is a second radius; the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63.

[0025] In some technical solutions of the application, optionally, the outer circle radius of the centrifugal impeller is a first radius; the radius of the second arc segment is a third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0026] According to the second aspect of the application, the application provides another centrifugal impeller, which comprises a cover body, blades and a flow guide ring, the number of blades is multiple, the multiple blades are arranged along the circumference of the centrifugal impeller and connected with the cover body, each of the multiple blades comprises at least two arc segments; the flow guide ring is located on the side of the blade away from the cover body and connected with the blade; wherein the multiple blades comprise adjacent first and second blades, the at least two arc segments of the first blade comprise a first arc segment and a second arc segment, the first arc segment is closer to the axis of the centrifugal impeller than the second arc segment; the vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first arc segment is a first distance; the vertical distance between the side of the second arc segment away from the axis of the centrifugal impeller and the second blade is a second distance; the first distance is less than the second distance, and the radius of the first arc segment is less than the radius of the second arc segment.

[0027] The centrifugal impeller provided by the second aspect of the present application can be applied to purifiers and other fluid power machines such as pumps, fans and compressors.

[0028] Specifically, the centrifugal impeller includes a cover, blades and a flow guide ring. The cover is the base part of the centrifugal impeller and provides support and connection for the blades.

[0029] The number of blades is multiple, and the multiple blades are uniformly arranged along the circumference of the centrifugal impeller and connected with the cover. Each blade is composed of at least two circular arc segments, which gives the blade a specific shape and curvature.

[0030] The flow guide ring is located on the side of the blade away from the cover and is connected with the blade. The flow guide ring guides the fluid into the blade, optimizes the flow path of the fluid and reduces energy loss.

[0031] Taking adjacent first and second blades as an example, the first blade is composed of a first circular arc segment and a second circular arc segment. The first circular arc segment is located on the inner side of the blade and is closer to the axis of the centrifugal impeller. The second circular arc segment is located on the outer side of the blade and is away from the axis of the centrifugal impeller.

[0032] The vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first circular arc segment is a first distance; the vertical distance between the side of the second circular arc segment away from the axis of the centrifugal impeller and the second blade is a second distance; the first distance is smaller than the second distance. The distance between the side of the second blade close to the axis and the first circular arc segment (the first distance) is smaller, so that the part of the blade near the axis is more compact. The distance between the side of the second circular arc segment away from the axis and the second blade (the second distance) is larger, so that the blade is more open on the outer side.

[0033] The radius of the first circular arc segment is smaller than the radius of the second circular arc segment. This design makes the blade present a curved shape of "tight inside and loose outside" between the inner and outer sides.

[0034] The present application designs the profile of the blade, sets a double circular arc blade, and by setting the radius of the first circular arc segment smaller than the radius of the second circular arc segment, improves the curvature of the circular arc on the basis of the combination of the two circular arc segments. The angle of the circular arc is larger, and the fluid can flow more smoothly when passing through the blade, reducing the inter-blade vortex caused by flow turbulence.

[0035] The curved shape of the blade helps to guide the fluid to flow along the surface of the blade, reducing the separation phenomenon of the fluid and the blade surface, thereby improving the efficiency and performance of the centrifugal impeller.

[0036] To sum up, the centrifugal impeller provided by the application realizes the reduction of inter-blade vortex and flow separation of air flow, improves the performance and efficiency of the centrifugal impeller, and improves the use experience of users by optimizing the profile configuration of the blade, adopting double-arc blades, and the angle of the arcs being relatively large.

[0037] In addition, the centrifugal impeller in the technical solution provided by the application can also have the following additional technical features:

[0038] In some technical solutions, optionally, the angle of the inlet installation angle of the centrifugal impeller is a first angle, the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees; and / or the angle of the outlet installation angle of the centrifugal impeller is a second angle, the second angle is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees; and / or the outer circle radius of the centrifugal impeller is a first radius, the radius of the first arc segment is a second radius, the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; and / or the outer circle radius of the centrifugal impeller is the first radius, the radius of the second arc segment is a third radius, the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0039] According to the third aspect of the application, the application further provides a centrifugal impeller, which comprises a cover body, blades and a flow guide ring. The number of blades is multiple, and the multiple blades are arranged along the circumference of the centrifugal impeller and connected with the cover body. The flow guide ring is located on the side of the blades away from the cover body and connected with the blades. Each blade in the multiple blades comprises at least two arc segments, and a gas flow channel is formed between two adjacent blades in the multiple blades, and the outlet end of the gas flow channel is narrowed.

[0040] The centrifugal impeller provided by the third aspect of the application mainly consists of three parts: a cover body, blades and a flow guide ring. The cover body is the basic structure of the centrifugal impeller, used to support and connect other parts. The blades are the key part of the centrifugal impeller, usually multiple in number, uniformly arranged along the circumference of the centrifugal impeller, and connected with the cover body. Each blade is composed of at least two arc segments to optimize fluid flow.

[0041] The flow guide ring is located on the side of the blades away from the cover body and connected with the blades. Its function is to guide and accelerate the flow of fluid, and also helps to reduce the generation of inter-blade vortex.

[0042] Compared with the traditional single-arc blade, the design of the double-arc blade of the application can more finely control the flow of fluid. By reasonably setting the radii and angles of the two arc segments, a smoother fluid transition can be achieved, reducing flow resistance and energy loss.

[0043] The air flow channel is formed between two adjacent blades, specifically, the air flow channel is the area between the two blades for air flow. The air outlet end of the air flow channel is narrowed, that is, the size of the air outlet end of the air flow channel towards one end of the outer part of the air outlet channel is larger than the size of the air outlet end of the air flow channel facing one end of the inner part of the air outlet channel.

[0044] When the centrifugal impeller rotates, fluid is sucked in and flows along the surface of the blade. Due to the double circular arc design of the blade, the transition of the fluid on the blade is smoother, reducing flow resistance and energy loss. At the same time, the narrowed air flow channel further accelerates the flow of the fluid, improving the efficiency of the centrifugal impeller. In addition, the presence of the guide ring also helps to guide the flow of the fluid, making it more concentrated and orderly.

[0045] The present application optimizes the blade design and narrows the air flow channel, reduces the flow resistance and energy loss, and improves the flow efficiency of the fluid. The narrowed air flow channel helps to suppress the formation of inter-blade eddies, further improving the efficiency of the centrifugal impeller. Due to the smoother and more orderly flow of the fluid, the noise and vibration generated by the centrifugal impeller during operation will also be reduced accordingly.

[0046] In addition, the centrifugal impeller in the above technical solution provided by the present application can also have the following additional technical features:

[0047] In some technical solutions of the present application, optionally, the air flow channel includes a first air flow channel and a second air flow channel, the second air flow channel is closer to the air outlet end relative to the first air flow channel, and the second air flow channel is narrowed from one end close to the first air flow channel to one end close to the air outlet end.

[0048] In some technical solutions of the present application, optionally, the at least two circular arc segments include a first circular arc segment and a second circular arc segment, the second circular arc segment is closer to the air outlet end relative to the first circular arc segment; and at least part of the second air flow channel is located between the second circular arc segments of the two adjacent blades.

[0049] In some technical solutions of the present application, optionally, the plurality of blades include adjacent first and second blades; the first blade has a second point close to the air outlet end, a second perpendicular line is drawn through the second point towards the pressure surface of the second blade, and the length of the second perpendicular line is a second distance; the first blade includes a third point between the air inlet end and the second point, and the first blade has at least one third point between the air inlet end and the second point, a third perpendicular line is drawn through the third point towards the pressure surface of the second blade, and the length of the third perpendicular line is a third distance; the second distance is less than the third distance.

[0050] In some technical solutions of the present application, optionally, the radius of the second circular arc segment is greater than the radius of the first circular arc segment.

[0051] In some embodiments of the present application, optionally, the connecting point of the first arc segment and the second arc segment is a first connecting point, and a circle surrounded by the first connecting points of the plurality of blades is a first circle; the center of the first arc segment is located inside the first circle; and / or the center of the second arc segment is located inside the first circle.

[0052] In some embodiments of the present application, optionally, the first air flow channel comprises a first air inlet end and a first air outlet end, the first air outlet end is smoothly connected with the air inlet end of the second air flow channel; the first air flow channel expands from the first air inlet end to the first air outlet end; or the first air flow channel is equidistant from the first air inlet end to the first air outlet end.

[0053] In some embodiments of the present application, optionally, in the case that the first air flow channel expands from the first air inlet end to the first air outlet end, the air inlet end of the second blade has a first point, a first perpendicular line is drawn from the first point to the negative pressure surface of the first blade, and the length of the first perpendicular line is a first distance; the first distance is less than the third distance.

[0054] In some embodiments of the present application, optionally, the angle of the inlet installation angle of the centrifugal impeller is a first angle, the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees; and / or the angle of the outlet installation angle of the centrifugal impeller is a second angle, the second angle is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees; and / or the outer circle radius of the centrifugal impeller is a first radius, the radius of the first arc segment is a second radius, and the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; and / or the outer circle radius of the centrifugal impeller is a first radius, the radius of the second arc segment is a third radius, and the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0055] In some embodiments of the present application, optionally, the cover body is concave towards the blade; and / or the outer diameter of the cover body is smaller than the outer diameter of the flow guide ring.

[0056] In some embodiments of the present application, optionally, the side edge of the blade in the circumferential direction of the centrifugal impeller comprises a first edge segment, a second edge segment and a third edge segment, the first edge segment is located on the side of the blade close to the flow guide ring, the second edge segment is located on the side of the blade close to the cover body, the two ends of the third edge segment are connected with the first edge segment and the second edge segment respectively, and the curvature of the third edge segment is greater than that of the second edge segment; and / or the distance between the first edge segment and the axis of the centrifugal impeller is a fourth distance, the fourth distance is constant from the side of the first edge segment close to the flow guide ring to the side away from the flow guide ring; and / or the distance between the second edge segment and the axis of the centrifugal impeller is a fifth distance, the fifth distance increases from the side of the second edge segment close to the cover body to the side away from the cover body.

[0057] In some embodiments of the present application, the second edge section is optionally recessed towards the direction of the flow guide ring.

[0058] In some embodiments of the present application, the distance between the third edge section and the axis of the centrifugal impeller is a sixth distance, the sixth distance decreasing from the side of the third edge section close to the first edge section to the side of the third edge section away from the first edge section.

[0059] According to the fourth aspect of the present application, the present application provides a purifier, which comprises a housing, a filtering component, a volute, a centrifugal impeller according to any of the above embodiments, and an air outlet grille. The housing comprises an air inlet grille; the filtering component is arranged in the air inlet grille and is provided with an air inlet channel; the volute is arranged in the housing and is in communication with the air inlet channel; the centrifugal impeller is located in the volute; and the air outlet grille is connected to the housing and is located on the side of the volute away from the air inlet channel.

[0060] The fourth aspect of the present application provides a purifier, which further comprises a housing, a filtering component, a centrifugal impeller according to any of the above embodiments, and an air outlet grille. The housing comprises an air inlet grille, which can be located at the front end of the purifier and is the entrance of air. The main function of the air inlet grille is to guide air into the interior of the purifier and prevent larger particulate matters or foreign matters from directly entering, so as to avoid damage to the internal components of the purifier.

[0061] The purifier further comprises a filtering component, which is arranged in the air inlet grille, contains filtering media such as filter screens, and is provided with an air inlet channel. The filtering component is the core component of the purifier and mainly functions to filter out dust, pollen, bacteria, viruses and other pollutants in the air through the filter screens and other media, so as to preliminarily purify the air.

[0062] The housing is the external structure of the purifier and is connected to the air inlet grille to form a closed space, which internally contains the filtering component, the volute, the centrifugal impeller and other components.

[0063] The housing not only plays a role of protecting the internal components, but also prevents the filtered air from leaking inside the purifier, thereby ensuring the purification effect.

[0064] The volute is arranged in the housing and is in communication with the air inlet channel, and the centrifugal impeller is located in the volute. The volute and the centrifugal impeller jointly constitute the fan system of the purifier. When the motor drives the centrifugal impeller to rotate, air is sucked into the volute, filtered by the filtering component, and then discharged from the air outlet of the volute, so as to ensure that the air is sufficiently circulated and filtered inside the purifier.

[0065] The air outlet grid is connected with the shell and is located on the side of the shell away from the air inlet channel. The air outlet grid is the outlet of the purified air. Through the air outlet grid, the user can feel the fresh air treated by the purifier. The design of the air outlet grid can adjust the direction and angle of the air outlet to meet the needs of different users.

[0066] In some embodiments of the present application, the shell is provided with an air inlet and an air outlet. The outer edge of the centrifugal impeller and the inner wall of the volute form a first airflow channel. The centrifugal impeller can drive the external gas of the shell to enter the shell through the air inlet, flow through the centrifugal impeller and the first airflow channel, and then flow out of the shell through the air outlet. The wall surface of the volute includes a plurality of surface groups, which are arranged around the circumference of the centrifugal impeller. Each surface group includes a first surface, a second surface, and a third surface, which are arranged along the circumference of the centrifugal impeller. The curvature of the first surface is less than or equal to the curvature of the third surface, and the curvature of the third surface is less than the curvature of the second surface.

[0067] In some embodiments of the present application, the volute includes a body having a first surface, a second surface, and a third surface, and a collector in the form of a ring located on the air inlet side of the centrifugal impeller.

[0068] In some embodiments of the present application, the length of the body in the first direction is a first length, the inner diameter of the side of the collector away from the centrifugal impeller is a first inner diameter, the ratio of the first inner diameter to the first length is greater than or equal to 0.68 and less than or equal to 0.85, and / or the length of the body in the first direction is a first length, the inner diameter of the side of the collector close to the centrifugal impeller is a second inner diameter, the ratio of the second inner diameter to the first length is greater than or equal to 0.55 and less than or equal to 0.65, and / or the height of the collector in the axial direction of the centrifugal impeller is a first height, the height of the volute in the axial direction of the centrifugal impeller is a second height, the ratio of the first height to the second height is greater than or equal to 0.11 and less than or equal to 0.22.

[0069] In some embodiments of the present application, the purifier further includes a support and a driving component. The support is located in the volute and has an air outlet channel between the support and the inner wall of the volute. The mounting end of the driving component is connected with the support, and the driving end of the driving component is connected with the centrifugal impeller to drive the centrifugal impeller to rotate.

[0070] In some embodiments of the present application, the purifier further includes a plurality of guide vanes, which are located in the air outlet channel and connected with the support.

[0071] In some embodiments of the present application, the purifier further includes a collector and a mesh cover. The collector is connected with the volute and located on the side of the centrifugal impeller close to the air inlet channel. The mesh cover is provided on the collector.

[0072] Additional aspects and advantages of the application will be set forth in part in the description which follows, and in part will become apparent to those skilled in the art upon examination of the following and / or by practice of the application. BRIEF DESCRIPTION OF DRAWINGS

[0073] The above and / or additional aspects and advantages of the present application will become apparent and be readily appreciated from the following description, including the appended drawings.

[0074] Figure 1 Structure diagram of a centrifugal impeller according to one embodiment of the present application;

[0075] Figure 2 Structure diagram of a centrifugal impeller according to one embodiment of the present application;

[0076] Figure 3 Structure diagram of a centrifugal impeller according to one embodiment of the present application; Figure 2 Cross-sectional view C-C of the centrifugal impeller in the illustrated embodiment;

[0077] Figure 4 Structure diagram of a centrifugal impeller according to one embodiment of the present application;

[0078] Figure 5 Structure diagram of a centrifugal impeller according to one embodiment of the present application;

[0079] Figure 6 Structure diagram of a centrifugal impeller according to one embodiment of the present application;

[0080] Figure 7 Velocity vector diagram of the centrifugal impeller in the illustrated embodiment; Figure 3

[0081] Velocity cloud diagram of the centrifugal impeller in the illustrated embodiment; Figure 8 Figure 3 Turbulent kinetic energy cloud diagram of the centrifugal impeller in the illustrated embodiment;

[0082] Figure 9 Figure 3 Structure diagram of a purifier according to one embodiment of the present application;

[0083] Figure 10 Structure diagram of a purifier according to one embodiment of the present application;

[0084] Figure 11 Structure diagram of a purifier according to one embodiment of the present application;

[0085] Figure 12 Cross-sectional view E-E of the purifier in the illustrated embodiment; Figure 11

[0086] ​​​Figure 13 Fig. 3 shows a structural schematic diagram of the purifier according to one embodiment of the present application;

[0087] Figure 14 Fig. 4 shows a structural schematic diagram of the purifier according to one embodiment of the present application; Figure 13 Fig. 5 shows a sectional view H-H of the purifier in the illustrated embodiment;

[0088] Figure 15 Fig. 6 shows a structural schematic diagram of the purifier according to one embodiment of the present application;

[0089] Figure 16 Fig. 7 shows a structural schematic diagram of the centrifugal impeller of the purifier according to one embodiment of the present application;

[0090] Figure 17 Fig. 8 shows a sectional view I-I of the centrifugal impeller in the illustrated embodiment; Figure 16

[0091] Figure 18 Fig. 9 shows a structural schematic diagram of the centrifugal impeller of the purifier according to one embodiment of the present application;

[0092] Figure 19 Fig. 10 is a velocity vector diagram of the single-arc centrifugal impeller;

[0093] Figure 20 Fig. 11 is a velocity cloud diagram of the single-arc centrifugal impeller;

[0094] Figure 21 Fig. 12 is a turbulent kinetic energy cloud diagram of the single-arc centrifugal impeller;

[0095] Fig. 13 is a schematic diagram of the purifier according to one embodiment of the present application; Figures 1 to 18 Correspondence between reference signs and component names in Fig. 13 is as follows:

[0096] ​100 Purifier, 110 Centrifugal Impeller, 112 Cover, 114 Blade, 116 Arc Segment, 118 First Blade, 120 First Arc Segment, 122 Second Arc Segment, 124 Second Blade, 126 Guide Ring, 128 Inlet Mounting Angle, 130 Outlet Mounting Angle, 132 Airflow Channel, 134 Air Outlet, 136 First Airflow Channel, 138 First Air Inlet, 140 First Air Outlet, 142 Second Airflow Channel, 144 Second Air Inlet, 146 Positive Pressure Surface, 147 Negative Pressure Surface, 148 Air Inlet, 150 First Point, 152 Second Point, 154 Third Point, 156 First Connection Point, 158 First Circle, 160 Side Edge, 162 First Edge Segment, 16 4 Second edge segment, 166 Third edge segment, 168 Housing, 170 Inlet, 172 Outlet, 174 Inlet grille, 178 Filter component, 179 Inlet channel, 180 Volute, 182 Body, 184 Surface assembly, 186 First surface, 188 Second surface, 190 Third surface, 192 Outlet grille, 194 Collector, 196 Inlet side, 198 Bracket, 200 Outlet channel, 202 Drive component, 204 Mounting end, 206 Drive end, 208 Guide vane, 210 Mesh cover, 212 Fixing part, 302 First reference point, 304 First tangent, 306 First auxiliary line, 308 Second reference point, 310 Second tangent, 312 Second auxiliary line. Detailed Implementation

[0097] To better understand the above-mentioned objectives, features, and advantages of the present invention, the present invention will be further described in detail below with reference to the accompanying drawings and specific embodiments. It should be noted that, unless otherwise specified, the embodiments and features described in these embodiments can be combined with each other.

[0098] Many specific details are set forth in the following description in order to provide a full understanding of the invention. However, the invention may also be practiced in other ways different from those described herein, and therefore the scope of protection of the invention is not limited to the specific embodiments disclosed below.

[0099] The following reference Figures 1 to 21 The centrifugal impeller 110 and purifier 100 in some embodiments of the present invention are described below.

[0100] like Figure 1 , Figure 2 , Figure 3 , Figure 4 and Figure 5As shown, in some embodiments of the present invention, a centrifugal impeller 110 is provided. The centrifugal impeller 110 includes a cover 112, blades 114, and a guide ring 126. Multiple blades 114 are arranged circumferentially along the centrifugal impeller 110 and connected to the cover 112. Each blade 114 includes at least two arc segments 116. The guide ring 126 is located on the side of the blades 114 away from the cover 112 and is connected to the blades 114. The multiple blades 114 include adjacent first blades 118 and second blades 124. The first blades 118 have at least two arc segments... 116 includes a first arc segment 120 and a second arc segment 122. The first arc segment 120 is closer to the axis of the centrifugal impeller 110 than the second arc segment 122. The vertical distance between the side of the second blade 124 closest to the axis of the centrifugal impeller 110 and the first arc segment 120 is the first distance. The vertical distance between the side of the second arc segment 122 furthest from the axis of the centrifugal impeller 110 and the second blade 124 is the second distance. The vertical distance between the side of the first arc segment 120 furthest from the axis of the centrifugal impeller 110 and the second blade 124 is the third distance. The first distance is less than the second distance, and the second distance is less than the third distance.

[0101] In this embodiment, the centrifugal impeller 110 proposed in this invention can be specifically applied to the purifier 100, and can also be applied to other fluid power machinery, such as pumps, fans, and compressors. This invention sets the profile structure of the blades 114 of the centrifugal impeller 110, and through a specific combination of arc segments 116, optimizes the shape of the blades 114, thereby improving the performance of the centrifugal impeller 110.

[0102] Specifically, the centrifugal impeller 110 includes a cover 112, blades 114, and a guide ring 126. The cover 112 is the basic part of the centrifugal impeller 110, providing a foundation for supporting and connecting the blades 114.

[0103] There are multiple blades 114, which are arranged circumferentially along the centrifugal impeller 110. Figure 1 The blades are evenly arranged in the direction indicated by arrow B and connected to the cover 112. Each blade 114 consists of at least two arc segments 116. This design gives the blades 114 a specific shape and curvature.

[0104] The guide ring 126 is located on the side of the blade 114 away from the cover 112 and is connected to the blade 114. The function of the guide ring 126 is to guide the fluid into the blade 114, optimize the fluid flow path, and reduce energy loss.

[0105] Taking the adjacent first vane 118 and second vane 124 as an example, the first vane 118 is composed of a first circular arc segment 120 and a second circular arc segment 122. The first circular arc segment 120 is located at the inner side of the vane 114, and is closer to the axis (D) of the centrifugal impeller 110. The second circular arc segment 122 is located at the outer side of the vane 114, and is away from the axis of the centrifugal impeller 110. Figure 2

[0106] As shown in FIG. 4, the vertical distance between the side of the second vane 124 close to the axis of the centrifugal impeller 110 and the first circular arc segment 120 is a first distance L1; the vertical distance between the side of the second circular arc segment 122 away from the axis of the centrifugal impeller 110 and the second vane 124 is a second distance L2; and the vertical distance between the side of the first circular arc segment 120 away from the axis of the centrifugal impeller 110 and the second vane 124 is a third distance L3. Figure 3 The vertical distance between the side of the second vane 124 close to the axis of the centrifugal impeller 110 and the first circular arc segment 120 is a first distance L1. Specifically, when measuring the first distance L1, on one hand, as shown in FIG. 5, in the tangential section of the centrifugal impeller 110 along the radial direction, a point is passed through the air inlet end of the second vane 124, and an auxiliary line is drawn on the negative pressure surface 147 of the first vane 118 along the normal direction of the first vane 118, which is perpendicular to the tangent of the negative pressure surface 147 of the first vane 118, and the length of the auxiliary line is the first distance L1.

[0107] Figure 3 On the other hand, the first distance L1 can also be measured in a projection manner. Specifically, the centrifugal impeller 110 is projected along the axis direction of the centrifugal impeller 110 to obtain a radial projection view of the centrifugal impeller 110, a point is passed through the air inlet end of the second vane 124, and an auxiliary line is drawn on the negative pressure surface 147 of the first vane 118 along the normal direction of the first vane 118, which is perpendicular to the tangent of the negative pressure surface 147 of the first vane 118, and the length of the auxiliary line is the first distance L1.

[0108] The vertical distance between the side of the second circular arc segment 122 away from the axis of the centrifugal impeller 110 and the second vane 124 is a second distance L2. Specifically, the centrifugal impeller 110 is planed to obtain a radial section view of the centrifugal impeller 110, a point is passed through the edge of the centrifugal impeller 110 far away from the axis on the side connecting the upper and lower ends of the first vane 118 with the cover 112 and the flow guide ring 126, and an auxiliary line is drawn on the positive pressure surface 146 of the second vane 124 along the normal direction of the second vane 124, which is perpendicular to the tangent of the positive pressure surface 146 of the second vane 124, and the length of the auxiliary line is the second distance L2.

[0109] The vertical distance between the side of the second circular arc segment 122 away from the axis of the centrifugal impeller 110 and the second vane 124 is a second distance L2. Specifically, the centrifugal impeller 110 is planed to obtain a radial section view of the centrifugal impeller 110, a point is passed through the edge of the centrifugal impeller 110 far away from the axis on the side connecting the upper and lower ends of the first vane 118 with the cover 112 and the flow guide ring 126, and an auxiliary line is drawn on the positive pressure surface 146 of the second vane 124 along the normal direction of the second vane 124, which is perpendicular to the tangent of the positive pressure surface 146 of the second vane 124, and the length of the auxiliary line is the second distance L2.​​

[0110] On the other hand, the second distance L2 is measured by projection, specifically, the centrifugal impeller 110 is projected along the axial direction of the centrifugal impeller 110 to obtain a radial projection view of the centrifugal impeller 110, on the radial projection view of the centrifugal impeller 110, a point is passed through the far side edge of the connecting position of the upper and lower ends of the first blade 118 and the cover 112 and the flow ring 126, and an auxiliary line is drawn on the pressure surface 146 of the second blade 124 along the normal direction of the second blade 124, the auxiliary line is perpendicular to the tangent of the pressure surface 146 of the second blade 124, and the length of the auxiliary line is measured to obtain the second distance L2.

[0111] The vertical distance between the side of the first circular segment 120 away from the axis of the centrifugal impeller 110 and the second blade 124 is the third distance L3, specifically, the first blade 114 also has an air inlet end 148, the centrifugal impeller 110 is planed, a radial section view of the centrifugal impeller 110 is obtained, on the radial section view of the centrifugal impeller 110, a middle point is passed through the air inlet end 148 of the first blade 114 and the connecting position of the upper and lower ends of the second blade 124 and the far side edge of the connecting position of the cover 112 and the flow ring 126 away from the axis, an auxiliary line is drawn on the pressure surface 146 of the second blade 124 along the normal direction of the second blade, the auxiliary line is perpendicular to the tangent of the pressure surface 146 of the second blade 124, and the length of the auxiliary line is measured to obtain the third distance L3. On the other hand, the third distance L3 is measured by projection, specifically, the centrifugal impeller 110 is projected along the axial direction of the centrifugal impeller 110 to obtain a radial projection view of the centrifugal impeller 110, on the radial projection view of the centrifugal impeller 110, a middle point is passed through the air inlet end 148 of the first blade 114 and the connecting position of the upper and lower ends of the second blade 124 and the far side edge of the connecting position of the cover 112 and the flow ring 126 away from the axis, an auxiliary line is drawn on the pressure surface 146 of the second blade 124 along the normal direction of the second blade, the auxiliary line is perpendicular to the tangent of the pressure surface 146 of the second blade 124, and the length of the auxiliary line is measured to obtain the third distance L3.

[0112] The first distance is smaller than the second distance, and the second distance is smaller than the third distance. The distance between the side of the second blade 124 close to the axis of the centrifugal impeller 110 and the first circular segment 120 (the first distance) is smaller, so that the part of the blade 114 is more compact near the axis. The distance between the side of the second circular segment 122 away from the axis and the second blade 124 (the second distance) is larger, so that the blade 114 is more open on the outer side.

[0113] The distance (third distance) between the first arc segment 120 and the second blade 124 away from the axis of the centrifugal impeller 110 is between the first distance and the second distance. This design makes the blade 114 present a bending shape of "tight inside and loose outside" between the inside and the outside.

[0114] The profile of the blade 114 is designed in the application, the double-arc blade 114 is arranged, and the third distance is limited, on the basis of the combination of the two arc segments, the arc degree of the arc is improved, the fluid can flow more smoothly when passing through the blade 114, and the inter-blade vortex caused by flow disorder is reduced.

[0115] The bending shape of the blade 114 helps to guide the fluid to flow along the surface of the blade 114, reduces the separation phenomenon of the fluid and the surface of the blade 114, and thus improves the efficiency and performance of the centrifugal impeller 110.

[0116] In summary, the centrifugal impeller 110 provided in the application optimizes the profile of the blade 114, adopts the double-arc blade 114, reduces the inter-blade vortex and the flow separation of the airflow, improves the performance and efficiency of the centrifugal impeller 110, and improves the use experience of the user.

[0117] Specifically, the centrifugal impeller 110 further comprises a fixing part 212 arranged on the cover 112 to realize the mounting and fixing of the centrifugal impeller 110.

[0118] Specifically, the rotation direction of the centrifugal impeller is the direction shown by A in the figure. Figure 1

[0119] As shown in the figure, Figure 4 In some embodiments of the application, the angle of the inlet installation angle 128 of the centrifugal impeller 110 is a first angle; the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees.

[0120] In this embodiment, the inlet installation angle 128 of the centrifugal impeller 110 is arranged in the application, the angle of the inlet installation angle 128 of the first arc segment 120 close to the axis of the centrifugal impeller 110 is a first angle, and specifically, the inlet installation angle 128 is the included angle between the direction of the fluid entering the blade 114 and the axis of the centrifugal impeller 110.

[0121] The first angle, i.e. the angle of the inlet installation angle 128, is between 16.8 degrees and 42.1 degrees. The design of the inlet installation angle 128 in the above numerical range can ensure that the fluid obtains a suitable speed and direction when entering the blade 114, thereby reducing flow disorder and energy loss, and helping to improve the efficiency and performance of the centrifugal impeller 110.

[0122] Specifically, as shown in the figure, Figure 4 ​As shown, the inlet installation angle 128 is: on a radial section of the centrifugal impeller 110, the projection of the outer circle of the first circular segment 120 on the side close to the axis of the centrifugal impeller 110 on the radial section is a first reference point 302, and the tangent to the outer circle of the first circular segment 120 passing through the first reference point 302 is a first tangent 304. On the radial section, the line perpendicular to the radius passing through the first reference point 302 is a first auxiliary line 306. The included angle between the first tangent 304 and the first auxiliary line 306 is the inlet installation angle 128.

[0123] Specifically, the angle of the inlet installation angle 128 can be 16.8 degrees, 17.8 degrees, 18.8 degrees, 19.8 degrees, 20.8 degrees, 21.8 degrees, 26.8 degrees, 30.8 degrees, 36.6 degrees, 39.2 degrees, or 42.1 degrees.

[0124] As shown, Figure 4 in some embodiments of the present application, the outlet installation angle 130 of the centrifugal impeller 110 is optionally an angle of a second angle; the second angle is greater than 9.2 degrees and less than or equal to 22.3 degrees.

[0125] In this embodiment, the present application sets the outlet installation angle 130 of the centrifugal impeller 110, and the angle of this outlet installation angle 130 is the second angle, which is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees.

[0126] The outlet installation angle 130 in the above numerical range helps to guide the fluid to flow out of the blade 114 more smoothly, reduces the generation of flow resistance and vortex, and thus optimizes the flow state of the fluid.

[0127] By precisely controlling the size of the second angle, the energy loss of the fluid in the centrifugal impeller 110 can be reduced, and thus the overall efficiency of the centrifugal impeller 110 can be improved.

[0128] The design of the outlet installation angle 130 in the above numerical range also helps to reduce the vibration and noise of the centrifugal impeller 110 and improve its running stability.

[0129] Specifically, as shown, Figure 4 the outlet installation angle 130 is: on a radial section of the centrifugal impeller 110, the projection of the outer circle of the second circular segment 122 on the side away from the axis of the centrifugal impeller 110 on the radial section is a second reference point 308, and the tangent to the outer circle of the second circular segment 122 passing through the second reference point 308 is a second tangent 310. On the radial section, the line perpendicular to the radius passing through the second reference point 308 is a second auxiliary line 312. The included angle between the second tangent 310 and the second auxiliary line 312 is the outlet installation angle 130.

[0130] Specifically, the second angle can be 9.2 degrees, 10 degrees, 14.3 degrees, 15 degrees, 17 degrees, 20 degrees, and 22.3 degrees.

[0131] As shown in FIG. 1, in some embodiments of the present application, the outer radius of the centrifugal impeller 110 is a first radius; the radius of the first circular arc segment 120 is a second radius; and the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63. Figure 3 In this embodiment, as shown in FIG. 2, the present application sets the ratio of the radius of the centrifugal impeller 110. The first radius refers to the outermost radius R0 of the centrifugal impeller 110, that is, the distance from the center of the centrifugal impeller 110 to the outer edge of the centrifugal impeller 110. This parameter is used to determine the overall size and shape of the centrifugal impeller 110.

[0132] Figure 3 The second radius specifically refers to the radius R1 of the first circular arc segment 120, that is, the distance from the center of the centrifugal impeller 110 to the center of curvature of the first circular arc segment 120.

[0133] The ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63.

[0134] The radius ratio in the above numerical range can ensure that the fluid maintains a better flow state when flowing inside the centrifugal impeller 110, reduces the generation of vortex and turbulent flow, and thus improves the efficiency of fluid delivery. By precisely controlling the radius ratio, the energy loss of the fluid in the centrifugal impeller 110 can be minimized, thereby improving the working efficiency of the entire fluid machine.

[0135] The radius ratio in the above numerical range also helps to maintain the overall strength and rigidity of the structure of the centrifugal impeller 110, preventing excessive stress concentration or deformation during high-speed rotation.

[0136] Specifically, the ratio of the second radius to the first radius can be 0.42, 0.44, 0.45, 0.46, 0.50, 0.55, 0.60, or 0.63.

[0137] Specifically, the ratio of the first radius and the second radius does not affect the wind volume improvement ratio effect, and the test results are shown in Table 1 below:

[0138] Table 1

[0139] Table 1

[0140]

[0141] ​It can be seen that when the ratio of the second radius to the first radius is 0.22, the airflow increase is 5.2%. When the ratio is 0.244, the airflow increase is 7.2%. When the ratio is 0.26, the airflow increase is 6.8%. When the ratio is 0.27, the airflow increase is 6.4%.

[0142] The radius ratios within the aforementioned range ensure that the fluid maintains a better flow pattern inside the centrifugal impeller 110, reducing the generation of eddies and turbulence, thereby improving the efficiency of fluid transport.

[0143] like Figure 3 As shown, in some embodiments of the present invention, optionally, the outer radius of the centrifugal impeller 110 is a first radius; the radius of the second arc segment 122 is a third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0144] In this embodiment, such as Figure 3 As shown, the ratio of the third radius to the first radius of the centrifugal impeller 110 is set. The first radius refers to the outer radius R0 of the centrifugal impeller 110, which is the distance from the center of the centrifugal impeller 110 to its outermost edge 160. This parameter determines the overall size of the centrifugal impeller 110. The third radius specifically refers to the radius R2 of the second arc segment 122, which is the distance from the center of the centrifugal impeller 110 to the center of curvature of the second arc segment 122.

[0145] The ratio of the third radius to the first radius must be greater than or equal to 0.61 and less than or equal to 0.72. By precisely controlling the ratio of the third radius to the first radius, the flow path of the fluid in the centrifugal impeller 110 can be optimized, flow resistance and eddy current losses can be reduced, thereby improving the hydrodynamic performance of the centrifugal impeller 110.

[0146] The radius ratio within the above-mentioned range helps to reduce energy loss of the fluid inside the centrifugal impeller 110, enabling more energy to be effectively converted into the fluid's kinetic or pressure energy, thereby improving the working efficiency of the centrifugal impeller 110.

[0147] The radius ratios within the aforementioned range can also ensure that the structural strength of the centrifugal impeller 110 meets the usage requirements, reduce stress concentration and vibration problems that may occur during high-speed rotation, and enhance the stability and reliability of the centrifugal impeller 110.

[0148] Specifically, the ratio of the third radius to the first radius can be 0.61, 0.62, 0.63, 0.64, 0.65, 0.66, 0.67, 0.68, 0.69, 0.70, 0.71 or 0.72.

[0149] Specifically, the wind volume promotion ratio effect is tested when the ratio of the first radius and the third radius is different, and the test results are shown in Table 2 below:

[0150] Table 2

[0151]

[0152] It can be seen that when the ratio of the third radius to the first radius is 0.32, the wind volume promotion ratio is 6.2%. When the ratio of the third radius to the first radius is 0.343, the wind volume promotion ratio is 8.3%. When the ratio of the third radius to the first radius is 0.36, the wind volume promotion ratio is 7.1%. When the ratio of the third radius to the first radius is 0.38, the wind volume promotion ratio is 5.8%.

[0153] The radius ratio in the above numerical range can ensure that the fluid maintains a good flow state when flowing inside the centrifugal impeller 110, reduces the generation of vortex and turbulence, and thus improves the efficiency of fluid delivery.

[0154] As shown in Figure 1 , Figure 2 and Figure 3 , in some embodiments of the present application, the present application provides another centrifugal impeller 110, which comprises a cover 112, blades 114 and a flow guide ring 126. The plurality of blades 114 are arranged along the circumference of the centrifugal impeller 110 and connected to the cover 112. Each of the plurality of blades 114 comprises at least two circular arc segments 116. The flow guide ring 126 is located on the side of the blades 114 away from the cover 112 and connected to the blades 114. The plurality of blades 114 comprises adjacent first blades 118 and second blades 124. The at least two circular arc segments 116 of the first blades 118 comprise a first circular arc segment 120 and a second circular arc segment 122, and the first circular arc segment 120 is closer to the axis of the centrifugal impeller 110 than the second circular arc segment 122. The vertical distance between the side of the second blades 124 close to the axis of the centrifugal impeller 110 and the first circular arc segment 120 is a first distance. The vertical distance between the side of the second circular arc segment 122 away from the axis of the centrifugal impeller 110 and the second blades 124 is a second distance. The first distance is smaller than the second distance, and the radius of the first circular arc segment 120 is smaller than the radius of the second circular arc segment 122.

[0155] In this embodiment, the centrifugal impeller 110 proposed by the present application can be applied to the purifier 100 and other fluid power machines such as pumps, fans and compressors. The profile of the blade 114 of the centrifugal impeller 110 is configured to optimize the shape of the blade 114 by combining specific circular arc segments 116, thereby improving the performance of the centrifugal impeller 110.

[0156] Specifically, the centrifugal impeller 110 includes a cover 112, blades 114 and a guide ring 126. The cover 112 is the base part of the centrifugal impeller 110 and provides support and connection for the blades 114.

[0157] The blades 114 are multiple and arranged uniformly along the circumference of the centrifugal impeller 110 and connected to the cover 112. Each blade 114 is composed of at least two circular arc segments 116, which gives the blade 114 a specific shape and curvature.

[0158] The guide ring 126 is located on the side of the blade 114 away from the cover 112 and is connected to the blade 114. The guide ring 126 guides the fluid into the blade 114, optimizes the flow path of the fluid and reduces energy loss.

[0159] Taking the first blade 118 and the second blade 124 adjacent to each other as an example, the first blade 118 is composed of a first circular arc segment 120 and a second circular arc segment 122. The first circular arc segment 120 is located on the inner side of the blade 114 and closer to the axis of the centrifugal impeller 110. The second circular arc segment 122 is located on the outer side of the blade 114 and away from the axis of the centrifugal impeller 110.

[0160] The vertical distance between the side of the second blade 124 close to the axis of the centrifugal impeller 110 and the first circular arc segment 120 is the first distance; the vertical distance between the side of the second circular arc segment 122 away from the axis of the centrifugal impeller 110 and the second blade 124 is the second distance.

[0161] Specifically, as shown in Figure 3 Specifically, when measuring the first distance L1, on the other hand, as shown in Figure 3 on the radial cross-section of the centrifugal impeller 110, a point on the inlet end of the second blade 124, a tangent line of the negative pressure surface 147 of the first blade 118 is drawn along the normal direction of the first blade 118, and the length of the tangent line is measured to obtain the first distance L1.

[0162] On the other hand, the first distance L1 is measured by projection, specifically, the centrifugal impeller 110 is projected along the axial direction to obtain a radial projection view of the centrifugal impeller 110, on the radial projection view of the centrifugal impeller 110, a point is passed through on the air inlet end of the second blade 124, an auxiliary line is drawn on the negative pressure surface 147 of the first blade 118 along the direction of the normal line of the first blade 118, the auxiliary line is perpendicular to the tangent of the negative pressure surface 147 of the first blade 118, and the length of the auxiliary line is measured to obtain the first distance L1.

[0163] The vertical distance between the second circular segment 122 and the second blade 124 away from the axis of the centrifugal impeller 110 is the second distance L2, specifically, the centrifugal impeller 110 is planed to obtain a radial section view of the centrifugal impeller 110, on the radial section view of the centrifugal impeller 110, a point is passed through on the edge of the centrifugal impeller 110 away from the axis and connected to the upper and lower ends of the first blade 118 and the connecting position of the cover 112 and the flow guide ring 126, an auxiliary line is drawn on the positive pressure surface 146 of the second blade 124 along the direction of the normal line of the second blade 124, the auxiliary line is perpendicular to the tangent of the positive pressure surface 146 of the second blade 124, and the length of the auxiliary line is measured to obtain the second distance L2.

[0164] On the other hand, the second distance L2 is measured by projection, specifically, the centrifugal impeller 110 is projected along the axial direction to obtain a radial projection view of the centrifugal impeller 110, on the radial projection view of the centrifugal impeller 110, a point is passed through on the edge of the centrifugal impeller 110 away from the axis and connected to the upper and lower ends of the first blade 118 and the connecting position of the cover 112 and the flow guide ring 126, an auxiliary line is drawn on the positive pressure surface 146 of the second blade 124 along the direction of the normal line of the second blade 124, the auxiliary line is perpendicular to the tangent of the positive pressure surface 146 of the second blade 124, and the length of the auxiliary line is measured to obtain the second distance L2.

[0165] The first distance is smaller than the second distance, the distance between the side of the second blade 124 close to the axis and the first circular segment 120 (the first distance) is smaller, so that the part of the blade 114 is more compact near the axis. The distance between the side of the second circular segment 122 away from the axis and the second blade 124 (the second distance) is larger, so that the blade 114 is more open on the outer side.

[0166] As shown in FIG. 1, Figure 3 The radius R1 of the first circular segment 120 is smaller than the radius R2 of the second circular segment 122, which makes the blade 114 present a bending shape of "tight inside and loose outside" between the inner side and the outer side.

[0167] The present application designs the profile of the blade 114, sets the double-arc blade 114, and improves the radian of the arc on the basis of the combination of the two arc segments by setting the radius of the first arc segment 120 smaller than the radius of the second arc segment 122. The angle of the arc is larger, and the fluid can flow more smoothly when passing through the blade 114, reducing the inter-blade vortex caused by flow disorder.

[0168] The curved shape of the blade 114 helps to guide the fluid to flow along the surface of the blade 114, reduces the separation phenomenon of the fluid and the surface of the blade 114, and improves the efficiency and performance of the centrifugal impeller 110.

[0169] To sum up, the centrifugal impeller 110 provided by the present application optimizes the profile of the blade 114, adopts the double-arc blade 114, and has a larger angle of the arc, thereby reducing the inter-blade vortex and flow separation of the airflow, improving the performance and efficiency of the centrifugal impeller 110, and improving the user's experience.

[0170] As shown in FIG. Figure 4 In some embodiments, the angle of the inlet installation angle 128 of the centrifugal impeller 110 is a first angle, the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees; and / or the angle of the outlet installation angle 130 of the centrifugal impeller 110 is a second angle, the second angle is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees; and / or the outer circle radius of the centrifugal impeller 110 is a first radius, the radius of the first arc segment 120 is a second radius, the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; and / or the outer circle radius of the centrifugal impeller 110 is a first radius, the radius of the second arc segment 122 is a third radius, the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0171] In this embodiment, on the one hand, the angle of the inlet installation angle 128 of the centrifugal impeller 110 is a first angle, the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees. The present application sets the inlet installation angle 128 of the centrifugal impeller 110, and the angle of the inlet installation angle 128 on the side close to the axis of the centrifugal impeller 110 is the first angle. Specifically, the inlet installation angle 128 is the included angle between the direction of the fluid when entering the blade 114 and the axis of the centrifugal impeller 110.

[0172] The first angle, i.e., the angle of the inlet installation angle 128, is between 16.8 degrees and 42.1 degrees. The design of the inlet installation angle 128 in the above numerical range can ensure that the fluid obtains appropriate speed and direction when entering the blade 114, thereby reducing flow disorder and energy loss, and helping to improve the efficiency and performance of the centrifugal impeller 110.

[0173] Specifically, the angle of the inlet installation angle 128 can be 16.8 degrees, 17.8 degrees, 18.8 degrees, 19.8 degrees, 20.8 degrees, 21.8 degrees, 26.8 degrees, 30.8 degrees, 36.6 degrees, 39.2 degrees or 42.1 degrees.

[0174] In this embodiment, the outlet installation angle 130 of the centrifugal impeller 110 is a second angle; the second angle is greater than 9.2 degrees and less than or equal to 22.3 degrees. The present invention sets the outlet installation angle 130 of the centrifugal impeller 110 to be a second angle, which is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees.

[0175] The outlet installation angle 130 within the aforementioned numerical range helps guide the fluid to flow more smoothly out of the blades 114, reducing flow resistance and vortex generation, thereby optimizing the fluid flow state. By precisely controlling the size of the second angle, energy loss of the fluid in the centrifugal impeller 110 can be reduced, thus improving the overall efficiency of the centrifugal impeller 110. The outlet installation angle 130 design within the aforementioned numerical range also helps reduce vibration and noise of the centrifugal impeller 110, improving its operational stability.

[0176] Specifically, the second angle can be 9.2 degrees, 10 degrees, 14.3 degrees, 15 degrees, 17 degrees, 20 degrees, and 22.3 degrees.

[0177] like Figure 3 As shown, in this embodiment, the outer radius of the centrifugal impeller 110 is the first radius; the radius of the first arc segment 120 is the second radius; the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63. This invention sets the ratio of the radii of the centrifugal impeller 110. The first radius refers to the outermost radius of the centrifugal impeller 110, which is the distance from the center of the centrifugal impeller 110 to its outer edge. This parameter is used to determine the overall size and shape of the centrifugal impeller 110.

[0178] The second radius specifically refers to the radius of the first arc segment 120, which is the distance from the center of the centrifugal impeller 110 to the center of curvature of the first arc segment 120. The ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63. A radius ratio within this range ensures that the fluid maintains a better flow pattern inside the centrifugal impeller 110, reducing the generation of eddies and turbulence, thereby improving the efficiency of fluid transport. By precisely controlling the radius ratio, energy loss of the fluid within the centrifugal impeller 110 can be minimized, thus improving the overall efficiency of the fluid machinery.

[0179] The radius ratios within the aforementioned range also help maintain the overall strength and rigidity of the centrifugal impeller 110 structure, preventing excessive stress concentration or deformation during high-speed rotation.

[0180] Specifically, the ratio of the second radius to the first radius can be 0.42, 0.44, 0.45, 0.46, 0.50, 0.55, 0.60, or 0.63.

[0181] As shown in the embodiment, the outer radius of the centrifugal impeller 110 is the first radius; the radius of the second arc segment 122 is the third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72. Figure 3 The first radius refers to the outer radius of the centrifugal impeller 110, that is, the distance from the center of the centrifugal impeller 110 to the outermost edge 160 of the centrifugal impeller 110. This parameter determines the overall size of the centrifugal impeller 110. The third radius specifically refers to the radius of the second arc segment 122, that is, the distance from the center of the centrifugal impeller 110 to the center of curvature of the second arc segment 122. The ratio of the third radius to the first radius needs to be greater than or equal to 0.61 and less than or equal to 0.72. By precisely controlling the ratio of the third radius to the first radius, the flow path of the fluid in the centrifugal impeller 110 can be optimized, reducing flow resistance and vortex loss, thereby improving the fluid dynamics performance of the centrifugal impeller 110.

[0182] The radius ratio in the above numerical range helps to reduce the energy loss of the fluid inside the centrifugal impeller 110, so that more energy can be effectively converted into kinetic energy or pressure energy of the fluid, thereby improving the working efficiency of the centrifugal impeller 110. The radius ratio in the above numerical range can also ensure that the structural strength of the centrifugal impeller 110 meets the use requirements, reduces the stress concentration and vibration problems that may occur at high speed rotation, and enhances the stability and reliability of the centrifugal impeller 110.

[0183] Specifically, the ratio of the third radius to the first radius can be 0.61, 0.62, 0.63, 0.64, 0.65, 0.66, 0.67, 0.68, 0.69, 0.70, 0.71, or 0.72.

[0184] As shown in the embodiment, the outer radius of the centrifugal impeller 110 is the first radius; the radius of the second arc segment 122 is the third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0185] Figure 1 , Figure 2 , Figure 3 and Figure 13 ​As shown, in some embodiments of the present application, the present application also proposes a centrifugal impeller 110, which comprises a cover body 112, a plurality of blades 114 arranged along the circumference of the centrifugal impeller 110 and connected with the cover body 112, and a flow guide ring 126 located on the side of the blades 114 away from the cover body 112 and connected with the blades 114. Each blade 114 in the plurality of blades 114 comprises at least two circular arc segments 116, and an airflow passage 132 is formed between two adjacent blades 114 in the plurality of blades 114, and the air outlet end 134 of the airflow passage 132 is narrowed.

[0186] In this embodiment, the centrifugal impeller 110 proposed by the present application mainly consists of three parts: the cover body 112, the blades 114 and the flow guide ring 126. The cover body 112 serves as the basic structure of the centrifugal impeller 110, which is used to support and connect other parts. The blades 114 are the key part of the centrifugal impeller 110, usually in multiple numbers, uniformly arranged along the circumference of the centrifugal impeller 110, and connected with the cover body 112. Each blade 114 is composed of at least two circular arc segments 116 to optimize fluid flow.

[0187] The flow guide ring 126 is located on the side of the blades 114 away from the cover body 112 and connected with the blades 114. Its role is to guide and accelerate the flow of fluid, while also helping to reduce the generation of inter-blade eddy.

[0188] Compared with the traditional single circular arc blade 114, the design of the double circular arc blade 114 of the present application can more finely control the flow of fluid. By reasonably setting the radius and angle of the two circular arc segments 116, a smoother fluid transition can be achieved, reducing flow resistance and energy loss.

[0189] An airflow passage 132 is formed between two adjacent blades 114 in the blades 114. Specifically, the airflow passage 132 is the area for airflow passage between the two blades 114. The air outlet end 134 of the airflow passage 132 is narrowed, i.e. the size of the air outlet end 134 of the airflow passage 132 towards the outside of the airflow passage 132 is greater than the size of the air outlet end 134 of the airflow passage 132 facing the inside of the airflow passage 132, for example, the edge width of the air outlet end 134 of the airflow passage 132 towards the outside of the airflow passage 132 is greater than the edge width of the air outlet end 134 of the airflow passage 132 facing the inside of the airflow passage 132.

[0190] Specifically, as shown in Figure 17 For the width variation of the airflow passage 132 between two adjacent blades 114 in the blades 114, specifically from the cross-sectional view or projection view of the blades 114, the width variation of the airflow passage between the two adjacent blades 114.

[0191] In the case of a change in the air passage between adjacent two blades from the cross-section of the blade 114, the width of the air flow passage 132 between the adjacent two blades 114 is observed from the cross-section of the rightmost end point of the blade 114 to the air inlet end 148 when the cross-section is cut, and is observed from the cross-section that is cut when the cross-section is cut.

[0192] Specifically, as shown in Figure 2 When the blade 114 is planed, the part of the first edge section 162 is exposed by planing from the lower part to the upper part of the middle part of the blade 114, i.e., the position where the planing line C-C is located, and the change in the air passage between the adjacent two blades is observed from the first edge section 162.

[0193] Specifically, between the middle part of the blade 114 and the air outlet end 134, the air flow passage 132 is designed in a gradually narrowing shape. This design helps to accelerate the flow of fluid while reducing the generation of inter-blade eddies. Because inter-blade eddies consume energy and reduce the efficiency of the centrifugal impeller 110, their formation can be effectively suppressed by narrowing the air flow passage 132.

[0194] When the centrifugal impeller 110 rotates, fluid is sucked in and flows along the surface of the blade 114. Due to the double circular arc design of the blade 114, the transition of fluid on the blade 114 is smoother, reducing flow resistance and energy loss. At the same time, the narrowed air flow passage 132 further accelerates the flow of fluid, improving the efficiency of the centrifugal impeller 110. In addition, the presence of the flow guide ring 126 also helps to guide the flow of fluid, making it more concentrated and orderly.

[0195] The present application optimizes the design of the blade 114 and narrows the air flow passage 132, reducing flow resistance and energy loss, and improving the efficiency of fluid flow. The narrowed air flow passage 132 helps to suppress the formation of inter-blade eddies, further improving the efficiency of the centrifugal impeller 110. Due to the smoother and more orderly flow of fluid, the noise and vibration generated by the centrifugal impeller 110 during operation will also be reduced accordingly.

[0196] As shown in Figure 5 In some embodiments of the present application, the air flow passage 132 includes a first air flow passage 136 and a second air flow passage 142, the second air flow passage 142 is closer to the air outlet end 134 relative to the first air flow passage 136, and the second air flow passage 142 is narrowed from one end close to the first air flow passage 136 to one end close to the air outlet end 134.

[0197] In this embodiment, the airflow passage 132 is defined to include a first airflow passage 136 and a second airflow passage 142, the first airflow passage 136 being located in the middle portion of the blade 114 to a region closer to the outflow end 134 but further away from the second airflow passage 142.

[0198] The second airflow passage 142 is located in a region close to the outflow end 134, adjacent to the first airflow passage 136 but closer to the outflow end 134 of the centrifugal impeller 110.

[0199] From one end close to the first airflow passage 136 to one end close to the outflow end 134, the second airflow passage 142 presents a gradually narrowing shape, specifically, the first airflow passage 136 through which the gas flows becomes narrower in this section. This design increases the flow rate by reducing the cross-sectional area of the fluid, thereby increasing the dynamic pressure energy of the fluid. Due to the narrowing design, the flow rate of the fluid increases when passing through the second airflow passage 142, and the flow becomes more concentrated and orderly, thereby improving the flow efficiency.

[0200] The narrowing passage design helps to reduce or suppress the formation of inter-blade eddies, as eddies are usually generated in areas with low flow rate and turbulent flow.

[0201] As shown in Figure 2 , Figure 3 , Figure 4 , Figure 5 and Figure 6 , in some embodiments of the present application, optionally, the at least two arc segments 116 include a first arc segment 120 and a second arc segment 122, the second arc segment 122 being closer to the outflow end 134 relative to the first arc segment 120; at least part of the second airflow passage 142 is located between the second arc segments 122 of adjacent two blades 114.

[0202] In this embodiment, the blade 114 is provided with at least two arc segments 116 including a first arc segment 120 and a second arc segment 122.

[0203] The first arc segment 120 is located at the front end of the blade 114, connected to or close to the cover 112. The second arc segment 122 is closer to the outflow end 134 relative to the first arc segment 120. The second arc segment 122 is designed more finely, aiming to further optimize the flow path of the fluid by changing the curvature and angle, and improve the flow efficiency.

[0204] The first airflow channel 136 is located in the area from the middle of the blade 114 to a region closer to the outlet end 134 but farther than the second airflow channel 142. The second airflow channel 142 is closer to the outlet end 134 and is located between the second arc segments 122 of adjacent blades 114. Due to the design of the second arc segment 122, the second airflow channel 142 will gradually narrow in shape near the outlet end 134.

[0205] The design of the second arc segment 122 and the narrowed second airflow channel 142 helps to make the fluid flow more smoothly through the blade 114, reducing the inter-blade vortex caused by flow turbulence, thereby improving flow efficiency.

[0206] As the second airflow passage 142 narrows near the outlet 134, the fluid velocity increases as it passes through, which helps to increase the dynamic pressure energy of the fluid and may improve the head or efficiency of the centrifugal impeller 110.

[0207] By optimizing the design of the blades 114 and the airflow channel 132, energy loss caused by poor or turbulent fluid flow can be reduced, thereby improving the overall performance of the centrifugal impeller 110.

[0208] like Figure 3 As shown, in some embodiments of the present invention, optionally, the plurality of blades 114 include adjacent first blades 118 and second blades 124; the first blade 118 has a second point 152 near the air outlet end 134, and a second perpendicular line is drawn from the second point 152 toward the positive pressure surface 146 of the second blade 124, the length of the second perpendicular line being a second distance; the air inlet end of the first blade includes a third point 154 between the second point and the air outlet end of the first blade, and a third perpendicular line is drawn from the third point 154 toward the positive pressure surface 146 of the second blade 124, the length of the third perpendicular line being a third distance; the second distance is less than the third distance.

[0209] In this embodiment, the centrifugal impeller 110 includes a plurality of blades 114 arranged circumferentially along the centrifugal impeller 110 and connected to the cover 112. Two adjacent blades 114 are a first blade 118 and a second blade 124.

[0210] Second point 152: Located on the first blade 118 near the air outlet 134.

[0211] Specifically, such as Figure 17 As shown, the centrifugal impeller 110 is cut radially, and the second point 152 is any point on the side edge K away from the axis D where the first blade 118 connects its upper and lower ends with the cover 112 and the guide ring 126.

[0212] Specifically, when the second point 152 is determined, a radial projection view of the centrifugal impeller 110 can be formed by projecting the second point 152 in the axial direction of the centrifugal impeller 110. The second point 152 is any point on the projection line of the edge K in the radial projection view. Figure 18

[0213] The third point 154 is located between the air inlet end 148 of the first blade 118 and the second point 152.

[0214] Specifically, as shown in FIG. 1B, the centrifugal impeller 110 is sliced along the radial direction. In the radial cross-section, the third point 154 is located between the air inlet end 148 of the first blade 118 and the second point 152. Figure 3

[0215] Specifically, the third point 154 can be the midpoint between the air inlet end 148 of the first blade 118 and the second point 152.

[0216] The second vertical line is perpendicular to the axis of the centrifugal impeller 110 and points to the pressure surface 146 of the second blade 124, starting from the second point 152. As shown in FIG. 1B, the length of this vertical line is defined as the second distance L2. Figure 3 The third vertical line is also perpendicular to the axis of the centrifugal impeller 110 and points to the pressure surface 146 of the second blade 124, starting from the third point 154. The length of this vertical line is defined as the third distance L3.

[0217] The second distance is less than the third distance, i.e., the distance between the first blade 118 and the pressure surface 146 of the second blade 124 is shorter near the air outlet end 134.

[0218] During the rotation of the centrifugal impeller 110, the fluid is sucked in from the air inlet end 148 and flows along the surface of the blade 114 to the air outlet end 134. By designing the second point 152 and the second vertical line, it is ensured that the distance between the first blade 118 and the second blade 124 is shorter near the air outlet end 134 (i.e., the second distance is less than the third distance). Such design helps the fluid flow more smoothly between the blades 114, reducing vortex and energy loss.

[0219] As the fluid flows more smoothly between the blades 114, the centrifugal impeller 110 can better convert the kinetic energy of the fluid into mechanical energy, thereby improving the working efficiency of the centrifugal impeller 110. This design is particularly important for improving the performance of the centrifugal impeller 110 in high-speed or high-flow conditions.

[0220] As shown in FIG. 1B, in some embodiments of the present application, the radius of the second circular arc segment 122 is greater than the radius of the first circular arc segment 120. Figure 3

[0221] ​​​In this embodiment, the radius of the second circular segment 122 is larger than the radius of the first circular segment 120. Such design helps to make the fluid flow more smoothly between the vanes 114, reducing the energy loss and vortex. As the fluid flow between the vanes 114 is more smooth, the centrifugal impeller 110 can better convert the kinetic energy of the fluid into mechanical energy, thus improving the working efficiency of the centrifugal impeller 110.

[0222] As shown in FIG. 1, in some embodiments of the present application, optionally, the connection point of the first circular segment 120 and the second circular segment 122 is the first connection point 156, and the first connection points 156 of the plurality of vanes 114 enclose a circle, which is the first circle 158; the center of the first circular segment 120 is located inside the first circle 158; and / or the center of the second circular segment 122 is located inside the first circle 158. Figure 6

[0223] In this embodiment, each vane 114 is composed of at least two circular segments 116, i.e. the first circular segment 120 and the second circular segment 122, wherein the second circular segment 122 is closer to the outflow end 134 than the first circular segment 120.

[0224] The first connection point 156 is the connection point of the first circular segment 120 and the second circular segment 122, and the first connection points 156 of the plurality of vanes 114 enclose a circle, which is the first circle 158.

[0225] The center of the first circular segment 120 is located inside the first circle 158, or the center of the second circular segment 122 is located inside the first circle 158. In some designs, both the centers of the first circular segment 120 and the second circular segment 122 can be located inside the first circle 158.

[0226] When the center of the first circular segment 120 or the second circular segment 122 is located inside the first circle 158, such design helps to make the fluid flow smoothly on the vanes 114. Because the center is located inside, the radius of curvature of the circular segment 116 is relatively small with respect to the distance between the vanes 114, so that the fluid can flow more smoothly along the curve of the vanes 114 when passing through the vanes 114, reducing the generation of flow loss and vortex.

[0227] By optimizing the design of the circular segment 116 of the vane 114, the fluid flow in the centrifugal impeller 110 is more orderly and efficient. This helps to improve the head, flow or efficiency of the centrifugal impeller 110, so that it can maintain high performance under different working conditions.

[0228] Placing the center of the circular segment 116 inside the first circle 158 also helps to enhance the structural strength of the vane 114. Such design makes the vane 114 have better stress distribution and ability to resist deformation when bearing load. ​

[0229] Specifically, such as Figure 6 As shown, the diameter d1 of the first circle 158 can be 53.2 mm.

[0230] Furthermore, such as Figure 6 As shown, the line connecting the points on the inner ends of multiple blades 114 forms a second circle, and the diameter d2 of the second circle can be 35.15 mm.

[0231] Furthermore, such as Figure 6 As shown, the circle in the middle region of multiple blades 114 is the third circle, and the diameter d3 of the third circle can be 24.94 mm.

[0232] By limiting the diameter of the three types of circles mentioned above, the blade 114 has better stress distribution and resistance to deformation when bearing load.

[0233] like Figure 5 As shown, in some embodiments of the present invention, optionally, the first airflow channel 136 includes a first air inlet 138 and a first air outlet 140, the first air outlet 140 being smoothly connected to the air inlet 148 of the second airflow channel 142; the first airflow channel 136 is expanded from the first air inlet 138 to the first air outlet 140; or the first airflow channel 136 is equidistant from the first air inlet 138 to the first air outlet 140.

[0234] In this embodiment, the structure of the first airflow channel 136 is configured to include a first air inlet section and a first air outlet section 140. The first air inlet section 138 is the starting part of the first airflow channel 136, from which gas enters the channel. The first air outlet section 140 is the ending part of the first airflow channel 136, from which gas flows out of the channel and connects to the air inlet section 148 of the second airflow channel 142.

[0235] The first airflow channel 136 gradually widens from the first air inlet 138 to the first air outlet 140. This design helps the gas to gradually accelerate within the channel and reduces flow resistance.

[0236] Another design involves maintaining an equidistant distance from the inlet 148 to the outlet 134 in the first airflow channel 136. Specifically, equidistant distance means that during the airflow process, the width or distance of the first airflow channel 136 remains consistent or equal at different positions, without significant contraction or expansion. The width or cross-sectional area of ​​the channel remains constant along its entire length. This design can maintain a stable gas flow rate and is suitable for certain specific application scenarios.

[0237] For the expanding channel, the gas flow rate gradually increases as the channel expands. This design helps the gas to gain higher kinetic energy when passing through the centrifugal impeller 110.

[0238] For the equidistant channel, the gas flow rate remains stable within the channel. This design ensures the stability and consistency of the gas flow, which is suitable for situations that require precise control of gas flow.

[0239] The expanding channel design helps to reduce the flow loss of the gas within the channel. As the channel gradually expands, the gas flow rate gradually increases, and the flow resistance correspondingly decreases, thereby improving the flow efficiency of the gas.

[0240] The smooth connection between the first air outlet end 140 and the air inlet end 148 of the second airflow channel 142 ensures the smooth entry of the gas from the first airflow channel 136 into the second airflow channel 142, reducing flow resistance and vortex formation. This smooth connection design helps to improve the overall performance of the centrifugal impeller 110.

[0241] As shown in Figure 2 and Figure 3 , in some embodiments of the present application, optionally, in the case of the first airflow channel 136 expanding from the first air inlet end 138 to the first air outlet end 140, the air inlet end 148 of the second blade 124 has a first point 150, and a first perpendicular line is drawn from the first point 150 to the negative pressure surface of the first blade 118, with the length of the first perpendicular line being a first distance; the first distance is less than the third distance.

[0242] In this embodiment, the first airflow channel 136 gradually expands from the first air inlet end 138 to the first air outlet end 140. This design helps the gas to gradually accelerate within the channel and reduces flow resistance.

[0243] The air inlet end 148 of the second blade 124 has a first point 150. A first perpendicular line is drawn from the first point 150 perpendicular to the axis of the centrifugal impeller 110 and pointing to the negative pressure surface of the first blade 118.

[0244] Specifically, the first point 150 is any point on the edge of the second blade 124 near the axis, which is connected to the upper and lower ends and the cover 112 and the flow guide ring 126.

[0245] Specifically, as shown in Figure 2 , the centrifugal impeller 110 is planed along the axis direction, Figure 2 any point on the edge J is the first point 150.

[0246] Specifically, the first point 150 can also be determined by projection. Specifically, the centrifugal impeller 110 is projected along the radial direction to obtain an axial projection view of the centrifugal impeller 110. Any point on the edge J in the axial projection view is the first point 150.

[0247] The length of the first vertical line is defined as the first distance. The third point 154 is located between the air inlet end 148 of the first blade 118 and the first point 150 of the second blade 124. The third vertical line originates from the third point 154, is perpendicular to the axis of the centrifugal impeller 110, and points towards the positive pressure surface 146 of the second blade 124. The length of the third vertical line is defined as the third distance.

[0248] The first distance is less than the third distance. This means that, on the axial projection of the centrifugal impeller 110, the distance from the air inlet end 148 of the second blade 124 to the negative pressure surface of the first blade 118 (the first distance) is less than the distance from the air inlet end 148 of the first blade 118 to the positive pressure surface 146 of the second blade 124 (the third distance).

[0249] As the first airflow channel 136 gradually expands from the inlet end 148 to the outlet end 134, the gas gradually accelerates within the channel. Simultaneously, because the first distance is smaller than the third distance, the gas travels a shorter path from the inlet end 148 of the second blade 124 to the negative pressure surface of the first blade 118. This helps reduce flow resistance and vortex formation, thereby optimizing fluid flow.

[0250] By optimizing fluid flow, the centrifugal impeller 110 can more effectively convert the kinetic energy of the gas into mechanical energy, thereby improving the working efficiency of the centrifugal impeller 110. This design is particularly important for improving the performance of the centrifugal impeller 110 under high speed or high flow conditions.

[0251] like Figure 3 and Figure 4 As shown, in some embodiments of the present invention, optionally, the inlet mounting angle 128 of the centrifugal impeller 110 is a first angle, the first angle being greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees; and / or the outlet mounting angle 130 of the centrifugal impeller 110 is a second angle, the second angle being greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees; and / or the outer radius of the centrifugal impeller 110 is a first radius, the radius of the first arc segment 120 is a second radius, the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; and / or the outer radius of the centrifugal impeller 110 is a first radius, the radius of the second arc segment 122 is a third radius, the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0252] In this embodiment, the angle of the inlet installation angle 128 of the centrifugal impeller 110 is a first angle, which is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees. The present application sets the inlet installation angle 128 of the centrifugal impeller 110, and the angle of the first arc segment 120 on the side close to the axis of the centrifugal impeller 110 is the first angle, specifically, the angle between the direction of the fluid when entering the blade 114 and the axis of the centrifugal impeller 110.

[0253] The first angle, i.e. the angle of the inlet installation angle 128, is between 16.8 degrees and 42.1 degrees. The design of the inlet installation angle 128 in the above numerical range can ensure that the fluid obtains a suitable speed and direction when entering the blade 114, thereby reducing flow turbulence and energy loss, and helping to improve the efficiency and performance of the centrifugal impeller 110.

[0254] Specifically, the angle of the inlet installation angle 128 can be 16.8 degrees, 17.8 degrees, 18.8 degrees, 19.8 degrees, 20.8 degrees, 21.8 degrees, 26.8 degrees, 30.8 degrees, 36.6 degrees, 39.2 degrees or 42.1 degrees.

[0255] In this embodiment, the angle of the outlet installation angle 130 of the centrifugal impeller 110 is a second angle; the second angle is greater than 9.2 degrees and less than or equal to 22.3 degrees. The present application sets the outlet installation angle 130 of the centrifugal impeller 110, and the angle of this outlet installation angle 130 is the second angle, which is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees.

[0256] The outlet installation angle 130 in the above numerical range helps to guide the fluid to flow out of the blade 114 more smoothly, reduces flow resistance and the generation of eddy, and thus optimizes the flow state of the fluid. By precisely controlling the size of the second angle, the energy loss of the fluid in the centrifugal impeller 110 can be reduced, thereby improving the overall efficiency of the centrifugal impeller 110. The design of the outlet installation angle 130 in the above numerical range also helps to reduce the vibration and noise of the centrifugal impeller 110, and improve its running stability.

[0257] Specifically, the second angle can be 9.2 degrees, 10 degrees, 14.3 degrees, 15 degrees, 17 degrees, 20 degrees and 22.3 degrees.

[0258] In this embodiment, the outer radius of the centrifugal impeller 110 is a first radius; the radius of the first circular segment 120 is a second radius; the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63. The present application sets the ratio of the radii of the centrifugal impeller 110, and the first radius refers to the outermost radius of the centrifugal impeller 110, that is, the distance from the center of the centrifugal impeller 110 to the outer edge of the centrifugal impeller 110. This parameter is used to determine the overall size and shape of the centrifugal impeller 110.

[0259] The second radius specifically refers to the radius of the first circular segment 120, that is, the distance from the center of the centrifugal impeller 110 to the center of curvature of the first circular segment 120. The ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63. The radius ratio in the above numerical range can ensure that the fluid maintains a better flow state when flowing inside the centrifugal impeller 110, reduces the generation of vortex and turbulent flow, and thus improves the efficiency of fluid delivery. By precisely controlling the radius ratio, the energy loss of the fluid in the centrifugal impeller 110 can be minimized, thereby improving the working efficiency of the entire fluid machine.

[0260] The radius ratio in the above numerical range also helps to maintain the overall strength and rigidity of the structure of the centrifugal impeller 110, preventing excessive stress concentration or deformation during high-speed rotation.

[0261] Specifically, the ratio of the second radius to the first radius can be 0.42, 0.44, 0.45, 0.46, 0.50, 0.55, 0.60, or 0.63.

[0262] In this embodiment, the outer radius of the centrifugal impeller 110 is a first radius; the radius of the second circular segment 122 is a third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.72.

[0263] The first radius refers to the outer radius of the centrifugal impeller 110, that is, the distance from the center of the centrifugal impeller 110 to the outermost edge 160 of the centrifugal impeller 110. This parameter determines the overall size of the centrifugal impeller 110. The third radius specifically refers to the radius of the second circular segment 122, that is, the distance from the center of the centrifugal impeller 110 to the center of curvature of the second circular segment 122. The ratio of the third radius to the first radius needs to be greater than or equal to 0.61 and less than or equal to 0.72. By precisely controlling the ratio of the third radius to the first radius, the flow path of the fluid in the centrifugal impeller 110 can be optimized, reducing flow resistance and vortex loss, thereby improving the fluid dynamics performance of the centrifugal impeller 110.

[0264] The radius ratio of the above numerical range helps to reduce the energy loss of the fluid inside the centrifugal impeller 110, so that more energy can be effectively converted into the kinetic energy or pressure energy of the fluid, thereby improving the working efficiency of the centrifugal impeller 110. The radius ratio of the above numerical range can also ensure that the structural strength of the centrifugal impeller 110 meets the use requirements, reduces the stress concentration and vibration problems that may occur at high speed rotation, and enhances the stability and reliability of the centrifugal impeller 110.

[0265] Specifically, the ratio of the third radius to the first radius can be 0.61, 0.62, 0.63, 0.64, 0.65, 0.66, 0.67, 0.68, 0.69, 0.70, 0.71 or 0.72.

[0266] In some embodiments of the present application, the cover 112 is concave towards the blades 114; and / or the outer diameter of the cover 112 is smaller than the outer diameter of the flow guide ring 126.

[0267] In this embodiment, on the one hand, the cover 112 is concave towards the blades 114, that is, the inner side surface of the cover 112 is recessed towards the blades 114, forming a recessed space between the cover 112 and the blades 114. The design of the cover 112 being concave towards the blades 114 helps to improve the flow of fluid between the blades 114. By forming a recessed space, the fluid can flow more smoothly through the blades 114, reducing vortex and flow resistance.

[0268] Improving the efficiency of the centrifugal impeller 110: Optimized fluid flow can reduce energy loss and improve the working efficiency of the centrifugal impeller 110.

[0269] Reducing noise and vibration: Reducing vortex and flow resistance also helps to reduce the noise and vibration generated when the centrifugal impeller 110 is running.

[0270] On the other hand, the outer diameter of the cover 112 is smaller than the outer diameter of the flow guide ring 126: The cover 112 is a protective part on the centrifugal impeller 110, while the flow guide ring 126 is usually a structure surrounding the outside of the centrifugal impeller 110, used to guide the fluid into or out of the centrifugal impeller 110.

[0271] This design makes the outer diameter of the cover 112 smaller than the outer diameter of the flow guide ring 126, thereby forming an annular space between the cover 112 and the flow guide ring 126. The design of the cover 112 having an outer diameter smaller than the outer diameter of the flow guide ring 126 can make the fluid more stable when entering or leaving the centrifugal impeller 110. The annular space can act as a buffer zone to reduce the change in fluid velocity and the formation of turbulence. This design can also enhance the structural stability of the centrifugal impeller 110. Because there is an annular space between the cover 112 and the flow guide ring 126, the stress concentration phenomenon caused by the change in fluid pressure can be reduced, improving the durability of the centrifugal impeller 110.

[0272] As Figure 1 , Figure 2 , Figure 15 , Figure 16 , Figure 17 and Figure 18 indicated, in some embodiments of the application, optionally, the side edge 160 of the blade 114 in the circumferential direction of the centrifugal impeller 110 includes a first edge section 162, a second edge section 164, and a third edge section 166, the first edge section 162 is located on one side of the blade 114 close to the guide ring 126, the second edge section 164 is located on one side of the blade 114 close to the cover body 112, the two ends of the third edge section 166 are connected with the first edge section 162 and the second edge section 164 respectively, and the curvature of the third edge section 166 is greater than that of the second edge section 164; and / or the distance between the first edge section 162 and the axis of the centrifugal impeller 110 is a fourth distance, the fourth distance is constant from the side of the first edge section 162 close to the guide ring 126 to the side away from the guide ring 126; and / or the distance between the second edge section 164 and the axis of the centrifugal impeller 110 is a fifth distance, the fifth distance increases from the side of the second edge section 164 close to the cover body 112 to the side away from the cover body 112.

[0273] In this embodiment, on the one hand, the side edge 160 of the blade 114 in the circumferential direction of the centrifugal impeller 110 includes a first edge section 162, a second edge section 164, and a third edge section 166, to achieve the arrangement of the blade 114. The first edge section 162 is located on one side of the blade 114 close to the guide ring 126 to achieve the arrangement of the first edge section 162; the second edge section 164 is located on one side of the blade 114 close to the cover body 112 to achieve the arrangement of the second edge section 164; the two ends of the third edge section 166 are connected with the first edge section 162 and the second edge section 164 respectively, that is, the third edge section 166 is located between the first edge section 162 and the second edge section 164. The curvature of the third edge section 166 is greater than that of the second edge section 164, by adjusting the curvatures of the second edge section 164 and the third edge section 166, the diameter of the centrifugal impeller 110 at the second edge section 164 and the diameter of the centrifugal impeller 110 at the third edge section 166 are adjusted. Since the curvature of the third edge section 166 is greater than that of the second edge section 164, the diameter of the centrifugal impeller 110 at the second edge section 164 is smaller than the diameter of the centrifugal impeller 110 at the third edge section 166, that is, the diameter of the centrifugal impeller 110 at the gas flow inlet is greater than the diameter of the centrifugal impeller 110 at the gas flow outlet. Compared with the way that each blade 114 is arranged in the axial direction, the arrangement of the blade 114 in the application can reduce the resistance of the centrifugal impeller 110, improve the flow of the centrifugal impeller 110, and thus improve the work efficiency and air volume of the centrifugal impeller 110.

[0274] In this embodiment, on the other hand, as shown in Figure 2 and Figure 16 the distance between the first edge section 162 and the axis of the centrifugal impeller 110 is a fourth distance L4, which is constant from the side of the first edge section 162 close to the guide ring 126 to the side far away from the guide ring 126, to achieve the arrangement of the first edge section 162, ensuring that the airflow can maintain a stable flow state when entering the centrifugal impeller 110, avoiding airflow turbulence caused by changes to the first edge section 162.

[0275] Specifically, projecting the centrifugal impeller 110 along the axis direction of the centrifugal impeller 110 can form a radial projection plane of the centrifugal impeller 110, and the fourth distance L4 can be obtained by measuring the distance between the first edge section 162 and the axis of the centrifugal impeller 110. Specifically, planing the centrifugal impeller 110 along the radial direction of the centrifugal impeller 110 can form a radial sectional view of the centrifugal impeller 110, and the fourth distance L4 can be obtained by measuring the distance between the first edge section 162 and the axis of the centrifugal impeller 110.

[0276] Specifically, projecting the centrifugal impeller 110 from bottom to top obtains a structural schematic diagram of the centrifugal impeller 110 as shown in Figure 18 .

[0277] In this embodiment, on the other hand, as shown in Figure 2 the distance between the second edge section 164 and the axis of the centrifugal impeller 110 is a fifth distance L5, which increases from the side of the second edge section 164 close to the cover body 112 to the side far away from the cover body 112, to achieve the arrangement of the second edge section 164, so that the airflow entering the centrifugal impeller 110 can accelerate the flow velocity of the airflow when flowing into the position of the second edge section 164, ensuring that the resistance at the outlet of the airflow is reduced, reducing the vortex and backflow of the airflow, thereby improving the air purification effect.

[0278] Specifically, projecting the centrifugal impeller 110 along the axis direction of the centrifugal impeller 110 can form a radial projection plane of the centrifugal impeller 110, and the fifth distance L5 can be obtained by measuring the distance between the second edge section 164 and the axis of the centrifugal impeller 110.

[0279] Specifically, planing the centrifugal impeller 110 along the radial direction of the centrifugal impeller 110 can form a radial sectional view of the centrifugal impeller 110, and the fourth distance L4 can be obtained by measuring the distance between the second edge section 164 and the axis of the centrifugal impeller 110.

[0280] As shown in Figure 2As shown, in some embodiments of the present invention, optionally, the second edge segment 164 is recessed in the axial direction of the centrifugal impeller 110 toward the guide ring 126.

[0281] In this embodiment, the second edge segment 164 of the centrifugal impeller 110 is recessed towards the guide ring 126 in the axial direction (direction indicated by arrow L) to achieve an optimized design of the second edge segment 164. This design enhances the air intake capacity at the position of the second edge segment 164, optimizes the airflow, reduces turbulence and eddies in the airflow at the second edge segment 164, improves the air purification capacity, increases the air volume of the centrifugal impeller 110, and also reduces the noise of the purifier 100 during operation.

[0282] like Figure 2 As shown, in some embodiments of the present invention, optionally, the distance between the third edge segment 166 and the axis of the centrifugal impeller 110 is a sixth distance, which decreases from the side of the third edge segment 166 closer to the first edge segment 162 to the side farther away from the first edge segment 162.

[0283] In this embodiment, such as Figure 2 As shown, the distance between the third edge segment 166 and the axis of the centrifugal impeller 110 is the sixth distance. Figure 2 In the L6 section, the sixth distance decreases from the side of the third edge segment 166 closer to the first edge segment 162 to the side farther away from the first edge segment 162, so as to achieve the arrangement of the third edge segment 166. This allows a gradually narrowing channel to be formed at the position of the third edge segment 166. When the airflow enters the position of the third edge segment 166 from the position of the first edge segment 162, the airflow velocity increases due to the decrease in the cross-sectional area of ​​the centrifugal impeller 110 at the position of the third edge segment 166. This reduces the turbulence and eddies of the air inside the centrifugal impeller 110, thereby reducing the noise generated by the airflow and improving the air purification efficiency.

[0284] Specifically, by projecting a projection onto the centrifugal impeller 110 along its axial direction, a radial projection surface of the centrifugal impeller 110 can be formed. The sixth distance L6 can be obtained by measuring the distance between the third edge segment 166 and the axis of the centrifugal impeller 110.

[0285] Specifically, a radial cross-sectional view of the centrifugal impeller 110 can be formed by planing the centrifugal impeller 110 along its radial direction. The sixth distance L6 can be obtained by measuring the distance between the third edge segment 166 and the axis of the centrifugal impeller 110.

[0286] like Figure 10 , Figure 11 and Figure 12As shown, in some embodiments of the present application, optionally, the present application proposes a purifier 100, which comprises a shell 168, a filter component 178, an outer shell, a centrifugal impeller 110 as in any of the above embodiments, and an air outlet grille 192. The filter component 178 is arranged in the air inlet grille 174, and is provided with an air inlet channel 179; the volute 180 is arranged in the shell 168 and is in communication with the air inlet channel 179; the centrifugal impeller 110 is located in the volute 180; and the air outlet grille 192 is connected to the shell 168 and is located on the side of the volute 180 away from the air inlet channel 179.

[0287] In this embodiment, the purifier 100 further comprises a filter component 178 arranged in the air inlet grille 174, which contains filter media such as filter screens and is provided with an air inlet channel 179. The filter component 178 is the core component of the purifier 100, and its main function is to filter out dust, pollen, bacteria, viruses and other pollutants in the air through the filter media such as filter screens, so as to preliminarily purify the air.

[0288] The shell 168 is the external structure of the purifier 100, which is connected to the air inlet grille 174 to form a closed space containing the filter component 178, the volute 180, the centrifugal impeller 110 and other components.

[0289] The shell 168 not only plays a role in protecting the internal components, but also prevents the filtered air from leaking inside the purifier 100, thereby ensuring the purification effect.

[0290] The volute 180 is arranged in the shell 168 and is in communication with the air inlet channel 179, and the centrifugal impeller 110 is located in the volute 180. The volute 180 and the centrifugal impeller 110 together constitute a fan system of the purifier 100. When the motor drives the centrifugal impeller 110 to rotate, air is sucked into the volute 180, filtered by the filter component 178, and then discharged from the air outlet of the volute 180, thereby ensuring that the air is fully circulated and filtered inside the purifier 100.

[0291] The air outlet grille 192 is connected to the shell 168 and is located on the side of the shell 168 away from the air inlet channel 179. The air outlet grille 192 is the outlet of the purified air, through which the user can feel the fresh air treated by the purifier 100. The design of the air outlet grille 192 can adjust the direction and angle of the air outlet to meet the needs of different users.

[0292] As Figure 13 , Figure 14 and Figure 15As shown, in some embodiments of the present application, the shell 168 is optionally provided with an air inlet 170 and an air outlet 172; the outer edge of the centrifugal impeller 110 and the inner wall of the volute 180 form a first airflow channel 136, and the centrifugal impeller 110 can drive the external gas of the shell 168 to enter the shell 168 through the air inlet 170, flow through the centrifugal impeller 110 and the first airflow channel 136, and then flow out of the shell 168 through the air outlet 172; wherein the wall surface of the volute 180 comprises a plurality of face groups 184, the plurality of face groups 184 are arranged around the circumference of the centrifugal impeller 110, each face group 184 in the plurality of face groups 184 comprises a first surface 186, a second surface 188 and a third surface 190, and the first surface 186, the second surface 188 and the third surface 190 are arranged along the circumference of the centrifugal impeller 110; the curvature of the first surface 186 is less than or equal to the curvature of the third surface 190, and the curvature of the third surface 190 is less than the curvature of the second surface 188.

[0293] In this embodiment, the shell 168 is provided with an air inlet 170 and an air outlet 172, the volute 180 is arranged in the shell 168, the centrifugal impeller 110 is arranged in the volute 180, the outer edge of the centrifugal impeller 110 and the inner wall of the volute 180 form a first airflow channel 136, and the centrifugal impeller 110 can drive the external gas of the shell 168 to enter the shell 168 through the air inlet 170, flow through the centrifugal impeller 110 and the first airflow channel 136, and then flow out of the shell 168 through the air outlet 172. By providing the air inlet 170 and the air outlet 172, the gas flow can be smoother.

[0294] When the purifier 100 is working, the rotation of the centrifugal impeller 110 can drive the gas flow, and the volute 180 can facilitate the installation of the centrifugal impeller 110 while also serving as a flow guide, thereby improving the airflow velocity and flow rate of the purifier 100. The rotating airflow around the centrifugal impeller 110 can be guided to accelerate the axial flow rate of the purifier 100 and improve the flow guiding efficiency. The wall surface of the volute 180 comprises a plurality of face groups 184, which are arranged around the circumference of the centrifugal impeller 110 to guide the airflow in the circumferential direction of the centrifugal impeller 110, thereby avoiding poor airflow.

[0295] Each face group 184 in the plurality of face groups 184 comprises a first surface 186, a second surface 188 and a third surface 190, and the first surface 186, the second surface 188 and the third surface 190 are arranged along the circumference of the centrifugal impeller 110. When the purifier 100 is working, the centrifugal impeller 110 rotates to drive the gas in the purifier 100 to flow rapidly, thereby reducing the air pressure in the area of the centrifugal impeller 110 in the purifier 100 and driving external gas into the area of the centrifugal impeller 110 to achieve rapid driving of the gas.

[0296] The first surface 186, the second surface 188 and the third surface 190 guide the airflow, by being arranged on the radial section of the purifier 100, the curvature of the first surface 186 is less than or equal to the curvature of the third surface 190, and the curvature of the third surface 190 is less than the curvature of the second surface 188, so that the first surface 186 is relatively flat relative to the third surface 190, and the third surface 190 is relatively flat relative to the second surface 188, which can reduce the airflow vortex at the corners inside the volute 180, and avoid the accumulation of rotating airflow in the volute 180. The airflow is guided through the first surface 186, the second surface 188 and the third surface 190 to improve the axial airflow speed of the purifier 100, increase the airflow flow rate driven out of the purifier 100, and increase the wind speed at the inlet of the volute 180, which can improve the overall wind speed and flow rate, and also reduce the turbulence noise by improving the smoothness of the airflow.

[0297] When the purifier 100 is working, the airflow in the purifier 100 flows to the volute 180 after contacting the positive pressure surface 146, the volute 180 can guide the airflow, and the centrifugal impeller 110 is assembled inside the volute 180. On the inner wall surface of the volute 180, the first surface 186, the second surface 188 and the third surface 190 are arranged along the circumference of the centrifugal impeller 110. The number of the first surface 186 can be four, and one second surface 188 is arranged on each side of each first surface 186 in the circumferential direction of the centrifugal impeller 110. The third surface 190 is arranged between two consecutive second surfaces 188. The cross-sectional area of the first airflow passage 136 increases from the edge midpoint of the first surface 186 to the edge midpoint of the second surface 188, and the flow speed of the airflow in the first airflow passage 136 decreases. The airflow passage 132 is the same or slightly decreases from the edge midpoint of the second surface 188 to the edge midpoint of the third surface 190, so that the airflow is accelerated again from the midpoint position area of the first surface 186 to the narrowest position of the first airflow passage 136 to the second surface 188. The airflow flowing from the position area of the third surface 190 to the first surface 186 is accelerated. Since there is a region with a larger cross-sectional area, i.e., a wider airflow passage 132, and a region with a smaller cross-sectional area, i.e., a narrower airflow passage 132, in the first airflow passage 136, the flow speed of the airflow exists an acceleration process and a deceleration process under the guidance of the first airflow passage 136. The airflow is guided through the first airflow passage 136 to reduce the accumulation and rotation of the airflow on the wall surface, avoid the airflow circulating along the volute 180, increase the axial speed of the airflow inside the volute 180, avoid the airflow blocking inside the volute 180, increase the speed at the inlet of the volute 180, thereby increase the air volume of the purifier 100, and reduce the working noise of the purifier 100.

[0298] Furthermore, by setting the curvature of the first surface 186 to be less than or equal to the curvature of the third surface 190, and the curvature of the third surface 190 to be less than the curvature of the second surface 188, the friction and resistance of airflow within the volute 180 can be reduced through the design of three continuous curved surfaces, thereby reducing energy loss and improving the working efficiency of the purifier 100.

[0299] Furthermore, by setting surfaces with different curvatures, the structural strength of the volute 180 can also be improved, enabling it to withstand greater airflow pressure and mechanical loads.

[0300] like Figure 15 As shown, in some embodiments of the present invention, optionally, the volute 180 includes: a body 182 having a first surface 186, a second surface 188 and a third surface 190; and a collector 194, which is annular and located on the air intake side 196 of the centrifugal impeller 110.

[0301] In this embodiment, the volute 180 includes a body 182 and a collector 194. The body 182 has a first surface 186, a second surface 188, and a third surface 190. The collector 194 is annular and located on the air inlet side 196 of the centrifugal impeller 110. It can reduce airflow turbulence and eddy generation, making the airflow more stable. The first surface 186, the second surface 188, and the third surface 190 on the body 182 can also reduce vortices generated in the internal corners of the volute 180, improve the airflow guiding efficiency of the volute 180, prevent airflow from being difficult to expel within the volute 180, increase axial wind speed, and also help to efficiently convert the kinetic energy of the airflow into static pressure energy, thereby improving the overall efficiency of the fan.

[0302] Furthermore, by setting the volute 180 to include the main body 182 and the collector 194, the structural support of the purifier 100 can be improved, and the overall stability of the purifier 100 can be enhanced.

[0303] Furthermore, the collector 194 can also protect the centrifugal impeller 110, preventing foreign objects from directly entering the centrifugal impeller 110 and causing damage.

[0304] like Figure 14As shown in some embodiments of the present application, optionally, the length of the body 182 in the first direction is a first length, the inner diameter of the collector 194 away from one side of the centrifugal impeller 110 is a first inner diameter, the ratio of the first inner diameter to the first length is greater than or equal to 0.68 and less than or equal to 0.85; and / or the length of the body 182 in the first direction is a first length, the inner diameter of the collector 194 close to one side of the centrifugal impeller 110 is a second inner diameter, the ratio of the second inner diameter to the first length is greater than or equal to 0.55 and less than or equal to 0.65; and / or the height of the collector 194 in the axial direction of the centrifugal impeller 110 is a first height, the height of the volute 180 in the axial direction of the centrifugal impeller 110 is a second height, the ratio of the first height to the second height is greater than or equal to 0.11 and less than or equal to 0.22.

[0305] In this embodiment, as Figure 13 and Figure 14 shown, the length of the body 182 in the first direction is a first length D1, the inner diameter of the collector 194 away from one side of the centrifugal impeller 110 is a first inner diameter D2, the ratio of the first inner diameter to the first length is greater than or equal to 0.68 and less than or equal to 0.85, by setting the ratio of the first inner diameter to the first length in the range of 0.68 to 0.85, the smoothness of the airflow guiding the centrifugal impeller 110 can be improved, and the uniformity and stability of the airflow can be ensured. By controlling the ratio of the inner diameter to the length, the flow path of the airflow can be optimized, the turbulence and vortex of the airflow can be reduced, and the working efficiency of the purifier 100 can be improved. By limiting the range of the ratio of the first inner diameter to the first length, the lightweight design of the collector 194 can be realized while ensuring the structural strength, and the overall performance of the purifier 100 can be improved.

[0306] The length of the body 182 in the first direction is a first length; the inner diameter of the collector 194 close to one side of the centrifugal impeller 110 is a second inner diameter D3; the ratio of the second inner diameter to the first length is greater than or equal to 0.55 and less than or equal to 0.65, by limiting the range of the ratio of the second inner diameter to the first length, the turbulence and vortex of the airflow when entering the centrifugal impeller 110 can be reduced, thereby improving the stability and efficiency of the airflow, and improving the working efficiency of the centrifugal impeller 110. By optimizing the air inlet 170, the centrifugal impeller 110 can more effectively absorb and compress the airflow.

[0307] As Figure 13 and Figure 14As shown, the height of the collector 194 in the axial direction of the purifier 100 is a first height H1, and the height of the volute 180 in the axial direction of the purifier 100 is a second height H2. By setting the ratio of the first height to the second height to be greater than or equal to 0.11 and less than or equal to 0.22, air flow turbulence and vortex can be reduced, thereby reducing energy loss and improving the overall efficiency of the fan. The air flow vortex at the corners inside the volute 180 can also be reduced, avoiding the accumulation of rotating air flow inside the volute 180. By optimizing the ratio of the height of the collector 194 to the height of the volute 180, the structural compactness can be improved while ensuring the flow guiding efficiency, facilitating installation.

[0308] As shown in Figure 7 , Figure 8 and Figure 9 , in some embodiments of the present application, the purifier 100 further comprises a bracket 198 and a driving component 202. The bracket 198 is located inside the volute 180 and has an air outlet passage 200 between the inner wall of the volute 180; the mounting end 204 of the driving component 202 is connected with the bracket 198, and the driving end 206 of the driving component 202 is connected with the centrifugal impeller 110 to drive the centrifugal impeller 110 to rotate. The purifier 100 further comprises: guide vanes 208, the guide vanes 208 are a plurality of guide vanes 208 located inside the air outlet passage 200 and connected with the bracket 198. A mesh cover 210 is provided on the collector 194.

[0309] In this embodiment, the purifier 100 further comprises a bracket 198 and a driving component 202, which work together to ensure the efficiency and stability of air purification.

[0310] The bracket 198 is located inside the volute 180 and has an air outlet passage 200 between the inner wall of the volute 180, through which the purified air flows out smoothly. At the same time, the bracket 198 can maintain the stability of the internal structure of the volute 180.

[0311] Through the bracket 198, the air outlet passage 200 is built to ensure the smoothness of air flow, avoid air flow not smooth or dead angle caused by structural obstruction, optimize the efficiency of air purification, and improve the performance of the purifier 100.

[0312] The mounting end 204 of the driving component 202 is connected with the bracket 198, and the driving component 202 is used to transmit power to the centrifugal impeller 110.

[0313] The driving end 206 of the driving component 202 is directly connected with the centrifugal impeller 110 or connected through a transmission mechanism to drive the centrifugal impeller 110 to rotate.

[0314] Through the driving component 202, precise adjustment of air flow can be realized to meet the air purification requirements in different scenarios.

[0315] The purifier 100 further comprises guide vanes 208, which are mainly used for guiding and controlling the flow of air flow, decelerating, pressurizing and rectifying the high-speed air flow thrown out by the centrifugal impeller 110, and ensuring that the air flow can uniformly pass through the air outlet channel 200, thereby improving the overall performance of the purifier 100.

[0316] The number of guide vanes 208 in the purifier 100 is multiple, and the multiple guide vanes 208 are located in the air outlet channel 200 and connected with the bracket 198, so that the stability and reliability of the guide vanes 208 during the working process can be improved.

[0317] The mesh cover 210 is arranged on the flow collector 194, and is mainly used for protecting the flow collector 194 to prevent large particles of dust or sundries from entering the flow collector 194 and causing damage or reducing the purification effect. Meanwhile, the mesh cover 210 can also play a certain filtering role, and can preliminarily filter out some larger particles of pollutants in the air to provide more favorable conditions for the subsequent purification process.

[0318] The purifier 100 provided by the application comprises an air inlet grille 174, a filter component 178 (the filter component 178 is specifically a filter core), a mesh cover 210, a flow collector 194, a volute 180, a centrifugal impeller 110, a driving component 202 (the driving component 202 is specifically a motor), a bracket 198, guide vanes 208, an air outlet grille 192 and a shell 168.

[0319] The main working principle of the purifier 100 is that the air to be purified enters through the air inlet grille 174, is purified by the filter core, and then passes through the mesh cover 210, the flow collector 194, the volute 180, the centrifugal impeller 110 and the guide vanes 208, and finally the purified air is discharged through the air outlet grille 192, so as to achieve the purpose of purifying the air.

[0320] The motor mainly provides the driving force for the rotation of the centrifugal impeller 110. The rotation of the centrifugal impeller 110 causes a high negative pressure area to be formed near the centrifugal impeller 110, so that a pressure difference is formed between the air inlet grille 174 and the centrifugal impeller 110, thereby enabling the air to be sucked in for purification. Therefore, the core component that determines the performance of the entire purifier 100 is the centrifugal impeller 110, which mainly determines the air volume, power and noise of the purifier 100.

[0321] The centrifugal impeller of the existing purifier has single circular arc blades, which cannot smoothly guide the inter-blade air flow, resulting in serious flow separation of the inter-blade air flow. Moreover, the original wind wheel design parameters are not iteratively optimized, resulting in relatively large air flow impact on the blades and serious flow separation. The simulation results are as followsFigure 19 、 Figure 20 and Figure 21 , wherein, Figure 19 the arrow F in points to the vortex and backflow, Figure 20 the arrow G in points to the low speed area, Figure 21 the arrow H in points to the high end kinetic energy area, the above reasons will cause the purifier air volume, noise, power loss.

[0322] In order to reduce the flow separation between the leaves, the profile of the blade 114 is redesigned, the profile of the blade 114 is designed as double circular arc through multi-objective optimization and design, the guidance of the airflow is more smooth, the flow separation between the leaves is weakened, the inlet installation angle 128 and the outlet installation angle 130 of the centrifugal impeller 110 are redesigned and optimized, the centrifugal impeller 110 is designed and optimized, the impact of the airflow on the blade 114 is reduced, and the flow separation between the leaves basically disappears, and the simulation results are shown in Figure 7 、 Figure 8 and Figure 9 , which not only can significantly improve the air volume of the purifier 100, but also can reduce the noise and power, and the final design parameters are as follows:

[0323] R0: the outer radius of the centrifugal impeller 110, that is, the outer diameter of the centrifugal impeller 110.

[0324] Outlet installation angle 130, which affects the pressure and flow, and the value range is 9.2 degrees to 22.3 degrees, and specifically, the degree of the outlet installation angle 130 is 14.3 degrees.

[0325] Inlet installation angle 128, which affects the airflow angle of attack, and the value range is 16.8 degrees to 42.1 degrees, and specifically, the degree of the inlet installation angle 128 is 29.3 degrees.

[0326] The center of the first circular segment 120 is Y0 in Figure 3 , and the circular arc radius is R1, R1 / R0=0.42-0.63, and specifically, R1 / R0=0.505.

[0327] The center of the second circular segment 122 close to the outlet installation angle 130 is M0 in Figure 3 , and the circular arc radius is R2, R2 / R0=0.61-0.72, and specifically, R2 / R0=0.709.

[0328] According to the above parameters, the profile of the blade 114 of the centrifugal impeller 110 is designed, and the inlet installation angle 128 and the outlet installation angle 130 of the blade 114 are designed according to the above parameter interval, which can reduce the flow separation of the airflow between the blades 114 and the impact of the airflow on the blades 114 as much as possible, and the simulation results are shown in Figure 7 ,Figure 8 and Figure 9 As shown in the figure, the whole machine of the purifier 100 is guaranteed to have high air volume, low noise and low power, the air volume is increased by more than 20%, the noise is reduced by 3dB, the power is reduced by 25%, the static pressure efficiency of the fan working point is increased by more than 69%, and the performance and service life of the purifier 100 are greatly improved.

[0329] In the claims, the specification, and the drawings of the present application, the term "multiple" refers to two or more, unless otherwise expressly specified and limited by context, the terms "upper", "lower", and the like indicate the orientation or positional relationship shown in the drawings based on the orientation or positional relationship shown in the drawings, and are only for the convenience of describing the present application and making the description process more simple, and are not intended to indicate or imply that the device or element described has the specific orientation, is constructed and operated in a specific orientation, therefore these descriptions cannot be understood as a limitation on the present application; the terms "connection", "installation", "fixation" and the like should be understood in a broad sense, for example, "connection" can be a fixed connection between multiple objects, or a detachable connection between multiple objects, or an integral connection; it can be a direct connection between multiple objects, or an indirect connection between multiple objects through an intermediate medium. For those skilled in the art, the specific meaning of the above terms in the present application can be understood according to the specific circumstances of the above data.

[0330] In the claims, the specification, and the drawings of the present application, the description of the terms "one embodiment", "some embodiments", "a specific embodiment" and the like 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 application. In the claims, the specification and the drawings of the present application, the illustrative description of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0331] The above only describes the preferred embodiments of the present application and is not intended to limit the present application. For those skilled in the art, the present application can have various modifications and changes. Any modification, equivalent replacement, improvement, etc. made within the spirit and principles of the present application shall be included in the protection scope of the present application.

Claims

1. A centrifugal impeller, characterized by The centrifugal impeller comprises: a cover body; a plurality of blades arranged along the circumference of the centrifugal impeller and connected to the cover body, each of the plurality of blades comprising at least two circular arc segments; a flow guide ring located on the side of the blade away from the cover body and connected to the blade; wherein the plurality of blades comprises adjacent first and second blades, the at least two circular arc segments of the first blade comprise a first circular arc segment and a second circular arc segment, the first circular arc segment being closer to the axis of the centrifugal impeller than the second circular arc segment; the vertical distance between the side of the second blade close to the axis of the centrifugal impeller and the first circular arc segment is a first distance; the vertical distance between the side of the second circular arc segment away from the axis of the centrifugal impeller and the second blade is a second distance; the vertical distance between the side of the first circular arc segment away from the axis of the centrifugal impeller and the second blade is a third distance; the first distance is smaller than the second distance, and the second distance is smaller than the third distance; the outer circle radius of the centrifugal impeller is a first radius; the radius of the first circular arc segment is a second radius; the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; the radius of the second circular arc segment is a third radius; the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.

72.

2. The centrifugal impeller of claim 1, wherein the angle of the inlet installation angle of the centrifugal impeller is a first angle; the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees.

3. The centrifugal impeller of claim 1, wherein the angle of the outlet installation angle of the centrifugal impeller is a second angle; the second angle is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees.

4. A centrifugal impeller, characterized by The centrifugal impeller comprises: a cover body; a plurality of blades arranged along the circumference of the centrifugal impeller and connected to the cover body; a flow guide ring located on the side of the blade away from the cover body and connected to the blade; wherein each of the plurality of blades comprises at least two circular arc segments, and a gas flow channel is formed between two adjacent blades of the plurality of blades, the outflow end of the gas flow channel being narrowed; the gas flow channel comprises a first gas flow channel and a second gas flow channel, the second gas flow channel being closer to the outflow end than the first gas flow channel, and the second gas flow channel being narrowed from one end close to the first gas flow channel to one end close to the outflow end; the plurality of blades comprises adjacent first and second blades; the first blade has a second point close to the outflow end, a second perpendicular line is drawn through the second point towards the pressure surface of the second blade, and the length of the second perpendicular line is a second distance; the first blade has a third point between the air inlet end and the second point, a third perpendicular line is drawn through the third point towards the pressure surface of the second blade, and the length of the third perpendicular line is a third distance; the second distance is smaller than the third distance; the first gas flow channel comprises a first air inlet end and a first air outlet end, and the first air outlet end is smoothly connected to the second air inlet end of the second gas flow channel; The first air flow channel expands from the first air inlet end to the first air outlet end; or The first air flow channel is equidistant from the first air inlet end to the first air outlet end; In the case that the first air flow channel expands from the first air inlet end to the first air outlet end, the air inlet end of the second blade has a first point, a first perpendicular line is drawn from the first point to the negative pressure surface of the first blade, and the length of the first perpendicular line is a first distance; The first distance is less than the third distance.

5. The centrifugal impeller of claim 4, wherein The at least two circular arc segments include a first circular arc segment and a second circular arc segment, and the second circular arc segment is closer to the air outlet end than the first circular arc segment; At least part of the second air flow channel is located between the second circular arc segments of two adjacent blades.

6. The centrifugal impeller of claim 5, wherein The radius of the second circular arc segment is greater than the radius of the first circular arc segment.

7. The centrifugal impeller of claim 5, wherein The connection point of the first circular arc segment and the second circular arc segment is a first connection point, and the first connection points of the plurality of blades enclose a first circle; The center of the first circular arc segment is located inside the first circle; and / or The center of the second circular arc segment is located inside the first circle.

8. The centrifugal impeller of claim 5, wherein The angle of the inlet installation angle of the centrifugal impeller is a first angle, the first angle is greater than or equal to 16.8 degrees and less than or equal to 42.1 degrees; and / or The angle of the outlet installation angle of the centrifugal impeller is a second angle, the second angle is greater than or equal to 9.2 degrees and less than or equal to 22.3 degrees; and / or The outer circle radius of the centrifugal impeller is a first radius, the radius of the first circular arc segment is a second radius, and the ratio of the second radius to the first radius is greater than or equal to 0.42 and less than or equal to 0.63; and / or The outer circle radius of the centrifugal impeller is a first radius, the radius of the second circular arc segment is a third radius, and the ratio of the third radius to the first radius is greater than or equal to 0.61 and less than or equal to 0.

72.

9. The centrifugal impeller according to any one of claims 4 to 8, characterized in that The cover body is concave towards the blade; and / or The outer diameter of the cover body is smaller than the outer diameter of the flow guide ring.

10. The centrifugal impeller according to any one of claims 4 to 8, characterized in that The side edge of the blade in the circumferential direction of the centrifugal impeller includes a first edge segment, a second edge segment and a third edge segment, the first edge segment is located on the side of the blade close to the flow guide ring, the second edge segment is located on the side of the blade close to the cover body, the two ends of the third edge segment are connected with the first edge segment and the second edge segment respectively, and the curvature of the third edge segment is greater than that of the second edge segment; and / or The distance between the first edge segment and the axis of the centrifugal impeller is a fourth distance, and the fourth distance is constant from the side of the first edge segment close to the flow guide ring to the side away from the flow guide ring; And / or The distance between the second edge segment and the axis of the centrifugal impeller is a fifth distance, and the fifth distance increases from the side of the second edge segment close to the cover body to the side away from the cover body.

11. The centrifugal impeller of claim 10, wherein In the axial direction of the centrifugal impeller, the second edge segment is recessed towards the direction close to the flow guide ring.

12. The centrifugal impeller of claim 10, wherein, A sixth distance between the third edge segment and the axis of the centrifugal impeller decreases from a side of the third edge segment closer to the first edge segment to a side of the third edge segment farther from the first edge segment.

13. A purifier characterized by comprising: Comprise: A housing comprising an air inlet grille; A filter component disposed in the air inlet grille, the filter component being provided with an air inlet channel; A volute disposed in the housing, in communication with the air inlet channel; The centrifugal impeller as claimed in any one of claims 1 to 12, located in the volute; An air outlet grille connected with the housing, located on a side of the volute away from the air inlet channel.

14. The purifier of claim 13, wherein, The housing is provided with an air inlet and an air outlet; A first air flow channel is formed between the outer edge of the centrifugal impeller and the inner wall of the volute, and the centrifugal impeller can drive the external gas of the housing to enter the housing from the air inlet, flow through the centrifugal impeller and the first air flow channel, and then flow out of the housing from the air outlet; Wherein, the wall surface of the volute comprises a plurality of face groups, and a plurality of face groups are arranged around the circumference of the centrifugal impeller, and each of the plurality of face groups comprises a first surface, a second surface and a third surface, and the first surface, the second surface and the third surface are arranged along the circumference of the centrifugal impeller; The curvature of the first surface is less than or equal to the curvature of the third surface, and the curvature of the third surface is less than the curvature of the second surface.

15. The purifier of claim 14, wherein, The volute comprises: A body having the first surface, the second surface and the third surface; A collector in the form of a ring located on the air inlet side of the centrifugal impeller.

16. The purifier of claim 15, wherein The length of the body in the first direction is a first length, the inner diameter of the side of the collector away from the centrifugal impeller is a first inner diameter, and the ratio of the first inner diameter to the first length is greater than or equal to 0.68 and less than or equal to 0.85; and / or The length of the body in the first direction is a first length, the inner diameter of the side of the collector closer to the centrifugal impeller is a second inner diameter, and the ratio of the second inner diameter to the first length is greater than or equal to 0.55 and less than or equal to 0.65; and / or The height of the collector in the axial direction of the centrifugal impeller is a first height, the height of the volute in the axial direction of the centrifugal impeller is a second height, and the ratio of the first height to the second height is greater than or equal to 0.11 and less than or equal to 0.

22.

17. The purifier according to claim 15 or 16, characterized in that Further comprising: A bracket located in the volute and having an air outlet channel between the inner wall of the volute; A drive component, the mounting end of the drive component being connected with the bracket, the drive end of the drive component being connected with the centrifugal impeller, and the drive component being capable of driving the centrifugal impeller to rotate; A plurality of guide vanes located in the air outlet channel and connected with the bracket; A mesh cover provided on the collector.

Images