Air duct device

Abstract

This utility model relates to the field of ventilation equipment technology and discloses an air duct device, including an air guide shroud and an impeller. The air guide shroud has a first air inlet and multiple first air outlets. The first air inlet is located on the axial side of the air guide shroud. The multiple first air outlets are distributed at intervals along the circumference of the air guide shroud and are located on the circumferential wall of the air guide shroud. The impeller is rotatably disposed inside the air guide shroud, and multiple air blade channels are provided along the circumference of the impeller. The air blade channels have a second air inlet and a second air outlet. The second air inlet is located on the axial side of the impeller, and the second air outlet is located on the circumferential side of the impeller. The second air inlet of the air blade channel is connected to the first air inlet, and the second air outlet of the air blade channel is connected to the first air outlet. This utility model discharges airflow evenly and dispersedly radially through multiple circumferentially distributed first air outlets, changing the traditional axial air outlet mode to circumferential multi-angle air outlet, effectively optimizing the airflow distribution and improving the air delivery effect.

Description

Technical Field

[0001] This utility model relates to the field of ventilation equipment technology, specifically to air duct devices. Background Technology

[0002] In existing air conditioners and various ventilation equipment, a single type of fan blade is usually used as the core driving component to achieve air flow and circulation. Among them, axial fan blades have the significant characteristic of large air volume, and therefore have been widely used in many occasions where large amounts of air need to circulate rapidly.

[0003] However, when the axial fan blades are rotating, air enters from one side of the fan's axis, and after being propelled by the blades, it is still discharged from the other side along the same axis. The entire airflow direction is consistent with the axis of the fan blades. This single axial airflow mode means that air can only be delivered in a fixed direction, making it impossible to achieve multi-angle and multi-directional airflow according to actual needs. In some scenarios where there are high requirements for uniform airflow distribution and coverage, it is difficult to meet the usage requirements. Utility Model Content

[0004] In view of this, the present invention provides a duct device to solve the problem that axial flow fan blades cannot achieve multi-angle and multi-directional air outlet according to actual needs, and thus cannot meet the usage requirements.

[0005] This utility model provides a duct device, comprising:

[0006] The air guide shroud has a first air inlet and a plurality of first air outlets; the first air inlet is disposed on the axial side of the air guide shroud; the plurality of first air outlets are distributed at intervals along the circumference of the air guide shroud, and the first air outlets are disposed on the circumferential wall surface of the air guide shroud.

[0007] An impeller is rotatably disposed inside the air guide shroud, and multiple air blade channels are provided along the circumference of the impeller; the air blade channels have a second air inlet and a second air outlet, the second air inlet is disposed on the axial side of the impeller, and the second air outlet is disposed on the circumferential side of the impeller.

[0008] The second air inlet of the fan blade flow channel is connected to the first air inlet, and the second air outlet of the fan blade flow channel is connected to the first air outlet.

[0009] Beneficial effects: By setting the first air inlet on the axial side of the air guide shroud and distributing multiple first air outlets at intervals along the circumferential wall, and aligning the first air inlet with the axial second air inlet of the impeller flow channel and the first air outlet with the circumferential second air outlet of the impeller flow channel, as the impeller rotates inside the air guide shroud, the airflow can efficiently flow into the impeller flow channel from the first and second air inlets along the axial direction, achieving efficient axial air intake. Then, under the centrifugal force of the impeller rotation, the airflow entering the impeller impeller flow channel is forcibly turned and discharged radially evenly and dispersedly through the multiple circumferentially distributed first air outlets, changing the traditional axial air outlet mode to circumferential multi-angle air outlet, effectively optimizing the airflow distribution and improving the air delivery effect.

[0010] In one alternative embodiment, the impeller includes:

[0011] The central part is rotatably connected to the air guide cover;

[0012] Multiple blades are arranged circumferentially at intervals along the central portion, with the blade roots connected to the central portion and the blade edges extending radially away from the central portion; a fan blade flow channel is formed between two adjacent blades; a first gap is formed between the sides of two adjacent blades near the first air inlet, and the first gap forms the second air inlet of the fan blade flow channel; a second gap is formed between the blade edges of two adjacent blades, and the second gap forms the second air outlet of the fan blade flow channel.

[0013] Beneficial effects: The impeller supports the circumferentially spaced blades at its center, while utilizing the first gap on the inner side of adjacent blades to form a second air inlet and a second air outlet. When the impeller rotates, the airflow enters the blade channel through the second air inlet formed by the first gap. Guided by the blades and under the centrifugal force generated by the impeller's rotation, the airflow moves along the blade channel towards the blade edges and is finally discharged from the second air outlet formed by the second gap. Furthermore, its simple structure facilitates manufacturing and improves production efficiency. The optimized airflow path within the blade channel ensures smooth flow and low resistance from the axial second air inlet to the circumferential second air outlet, thereby enhancing the overall performance of the impeller.

[0014] In one alternative embodiment, the impeller further includes a fixing part, which is sleeved on the outer peripheral surface of the central part and connected to the side of the blade opposite to the first air inlet.

[0015] Beneficial effects: By attaching the fixing part to the outer periphery of the central part and connecting it to the side of the blade away from the first air inlet, the airflow entering the fan blade channel can be effectively blocked from leaking from the side of the blade away from the second air inlet. This ensures that the airflow can flow entirely within the fan blade channel and stably exit from the second gap between the blade edges of two adjacent blades. This ensures that the air drawn in by the axial flow is finally discharged radially from the circumferentially distributed first air outlet. Furthermore, the connection between the fixing part and the blade and the central part forms a stable support structure, enhancing the structural rigidity of the blade root and thus improving the overall deformation resistance of the impeller. This effectively suppresses the vibration that may occur under high-speed conditions due to centrifugal force, as well as the stress deformation caused by vibration, ensuring the long-term stable working performance of the impeller.

[0016] In one optional embodiment, the fixing part is a conical annular structure, the fixing part includes an inner edge and an outer edge, the inner edge is connected to the outer peripheral surface of the central part, and the outer edge is located at the end of the fixing part away from the central part; along the direction from the inner edge to the outer edge, the radial distance between the generatrix of the conical annular structure and the axis of the impeller gradually increases.

[0017] Beneficial effects: By setting the fixing part as a conical annular structure, it conforms to the natural diffusion trajectory of airflow from axial intake to radial outflow; the smooth transition of the conical surface of the conical annular structure serves as the rear wall of the impeller flow channel, providing a low-resistance guiding channel for airflow, guiding the airflow near the second air outlet, preventing the airflow from diffusing in an unexpected direction, enhancing the directionality of airflow discharge, ensuring a smoother flow process from the second air inlet to the second air outlet, reducing energy loss, and thus improving the aerodynamic efficiency of the impeller and the stability of the flow field.

[0018] In one optional embodiment, on a cross section perpendicular to the extension direction of the blade, a first included angle α is formed between the blade surface and the tangent of the fixing part at the connection point; the angle range of the first included angle α is 0 degrees to 45 degrees.

[0019] Beneficial Effects: By setting a first angle α between the blades and the fixed part, an effective constraint is formed on the air entering the blade flow channel. After the air enters the flow channel, it can be stably retained within the flow channel under the spatial structure constraint formed by the first angle α. As the impeller rotates, the gas retained in the flow channel is forced to the second outlet of the flow channel and discharged under the action of centrifugal force, effectively reducing abnormal dispersion and turbulent flow in the flow channel, optimizing the impeller's air capture and driving efficiency, and thus improving the overall aerodynamic performance and energy conversion efficiency of the impeller. By limiting the first angle α to the range of 0 degrees to 45 degrees, a balance between airflow diffusion efficiency and flow stability is achieved while ensuring structural and technological feasibility. This avoids manufacturing and assembly difficulties caused by too small an angle, and also avoids airflow separation in the flow channel caused by too large an angle, preventing energy dissipation, improving the working efficiency of the impeller, and enabling the airflow to be efficiently turned along the curved surface of the conical fixed part, maximizing the aerodynamic performance of the impeller.

[0020] In one alternative embodiment, the first included angle α is the angle between the windward surface of the blade and the side wall of the fixing part facing the first air inlet.

[0021] Beneficial effects: By setting the first included angle α on the windward side of the blade, when the impeller rotates, the airflow will impact the windward side of the blade. At this time, the setting of the first included angle α can guide the airflow in a natural way, so that the airflow enters the blade flow channel more efficiently, reducing the impact loss of the airflow at the second air inlet of the blade flow channel, and further improving the impeller's ability to capture airflow and drive efficiency.

[0022] In one optional embodiment, an annular air duct is provided between the outer circle of the impeller's rotation trajectory and the circumferential wall of the air guide shroud, and the second air outlet is connected to the first air outlet through the annular air duct.

[0023] Beneficial effects: By setting an annular air duct between the circumcircle of the impeller's rotation trajectory and the circumferential wall of the air guide, the airflow, after exiting the second outlet, first enters and converges within the annular air duct. Since the annular air duct is a continuous circumferential structure, it buffers and equalizes the airflow. Subsequently, the airflow is evenly distributed to the circumferentially distributed first outlets through the annular air duct. This effectively solves the problem of uneven flow distribution that might occur if the airflow flows directly from the second outlet to each first outlet due to the difference in the relative positions of the first and second outlets, ensuring consistent airflow from each first outlet.

[0024] In one optional embodiment, an acceleration duct section is formed between two adjacent first air outlets along the rotation direction of the impeller, and the radial distance between the inner wall surface of the acceleration duct section and the circumcircle of the rotation trajectory of the impeller gradually increases along the airflow direction.

[0025] Beneficial Effects: Because the radial distance between the inner wall of the acceleration duct section and the circumcircle of the impeller's rotation trajectory gradually increases along the rotation direction, a gradually expanding flow channel is formed between two adjacent first air outlets. When the airflow enters the annular duct from the second air outlet, it flows along the annular duct towards each first air outlet. When passing through the acceleration duct section between two adjacent first air outlets, the gradually expanding flow channel structure effectively avoids the violent impact and vortices that would occur if the airflow suddenly passed from the relatively narrow annular duct through the first air outlet into the open space. This reduces airflow noise during impeller operation and minimizes energy loss due to vortices. Furthermore, the gradually expanding flow channel helps to smoothly guide the airflow, making it flow more smoothly towards the first air outlet, reducing wind resistance, improving airflow delivery efficiency, and achieving a more uniform, stable, and quiet airflow output.

[0026] In one optional embodiment, the acceleration air duct section is provided with air guide vanes at both ends along the airflow direction, one end of the air guide vane is connected to the inner wall surface of the acceleration air duct section, and the other end extends to the outer edge of the air guide shroud.

[0027] Beneficial effects: Since one end of the guide vane is connected to the inner wall of the acceleration duct section, when the airflow flows through the acceleration duct section to the first air outlet, the guide vane can directly receive the accelerated airflow, forcibly constraining the airflow and causing it to flow along the predetermined path guided by the guide vane. This effectively prevents the airflow from rapidly spreading outwards or forming turbulent vortices after leaving the annular duct due to loss of constraint. Furthermore, the other end of the guide vane extends to the outer edge of the air guide shroud, ensuring that the airflow is fully and completely discharged from the shroud under the guidance of the guide vane throughout its entire length, reducing energy dissipation caused by the airflow impacting the edge of the air guide shroud or causing disordered backflow.

[0028] In one optional embodiment, the air guide vane extends radially along the air guide shroud; or a second included angle θ is provided between the air guide surface of the air guide vane and the radial reference line of the air guide shroud; wherein the radial reference line is a straight line passing through the connection point of the air guide vane and the inner wall of the acceleration duct section, and the second included angle θ is an obtuse angle.

[0029] Beneficial effects: By adjusting the second angle θ between the air guide vane and the radial direction of the air guide shroud, the airflow direction when leaving the first air outlet can be flexibly set. When the air guide vane extends radially, the airflow will flow out along the radial direction of the air guide shroud; while when there is a second angle θ between the air guide vane and the radial direction, the airflow will change its outlet angle according to the tilt direction of the air guide vane. This not only enhances the directionality of air delivery, allowing the airflow to be accurately delivered to the target area, but also enables the duct device to adapt to the specific air delivery angle requirements of different application scenarios, improving the applicability and practicality of the duct device.

[0030] In one alternative embodiment, the second included angle θ formed between the guide surfaces of the two guide vanes at both ends of the acceleration duct section along the airflow direction and the radial reference line of the corresponding guide shroud is different. Attached Figure Description

[0031] To more clearly illustrate the technical solutions in the specific embodiments or related technologies of this utility model, the drawings used in the description of the specific embodiments or related technologies will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0032] Figure 1 This is a schematic diagram of the structure of a duct device according to an embodiment of the present utility model;

[0033] Figure 2 This is a side view of the air duct device according to an embodiment of the present utility model;

[0034] Figure 3 for Figure 2 Sectional view of AA in the middle;

[0035] Figure 4 for Figure 2 Cross-sectional view of the middle section (BB);

[0036] Figure 5 This is an exploded view of the air duct device according to an embodiment of the present utility model;

[0037] Figure 6 This is a schematic diagram of the impeller structure according to an embodiment of the present utility model;

[0038] Figure 7 This is a schematic diagram of the structure of the air guide cover according to an embodiment of the present utility model;

[0039] Figure 8 This is a simulation diagram of wind speed according to an embodiment of the present invention.

[0040] Explanation of reference numerals in the attached figures:

[0041] 10. Air guide shroud; L. Radial baseline;

[0042] 11. First air inlet; 12. First air outlet; 13. Circumferential wall; 14. First side wall; 15. Second side wall; 16. Annular air duct; 17. Acceleration air duct section; 18. Air guide vane; 181. Air guide surface;

[0043] 20. Impeller;

[0044] 21. Fan blade flow channel; 211. Second air inlet; 212. Second air outlet; 22. Center section; 23. Blade; 231. Windward side; 24. Fixing part; 241. Inner edge; 242. Outer edge. Detailed Implementation

[0045] To make the objectives, technical solutions, and advantages of the embodiments of this utility model clearer, the technical solutions of the embodiments of this utility model will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this utility model, not all embodiments. Based on the embodiments of this utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of this utility model.

[0046] In the description of this utility model, it should be noted that the terms "upper," "lower," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing this utility model and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first," "second," and "third" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0047] In the description of this utility model, it should be noted that, unless otherwise explicitly specified and limited, the terms "connected" and "linked" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model based on the specific circumstances.

[0048] Furthermore, the technical features involved in the different embodiments of this utility model described below can be combined with each other as long as they do not conflict with each other.

[0049] The following is combined Figures 1 to 8 The following describes embodiments of the present invention.

[0050] According to an embodiment of the present invention, a wind duct device is provided, including a wind guide shroud 10 and an impeller 20; the wind guide shroud 10 has a first air inlet 11 and a plurality of first air outlets 12; the first air inlet 11 is disposed on the axial side of the wind guide shroud 10; the plurality of first air outlets 12 are distributed at intervals along the circumference of the wind guide shroud 10, and the first air outlets 12 are disposed on the circumferential wall surface 13 of the wind guide shroud 10; the impeller 20 is rotatably disposed inside the wind guide shroud 10, and a plurality of air blade channels 21 are provided along the circumference of the impeller 20; the air blade channels 21 have a second air inlet 211 and a second air outlet 212, the second air inlet 211 is disposed on the axial side of the impeller 20, and the second air outlet 212 is disposed on the circumferential side of the impeller 20; wherein, the second air inlet 211 of the air blade channel 21 is connected to the first air inlet 11, and the second air outlet 212 of the air blade channel 21 is connected to the first air outlet 12.

[0051] In the above embodiment, the first air inlet 11 is set on the axial side of the air guide shroud 10, and multiple first air outlets 12 are distributed at intervals along the circumferential wall surface 13. At the same time, the first air inlet 11 corresponds to the axial second air inlet 211 of the fan blade flow channel 21, and the first air outlet 12 corresponds to the circumferential second air outlet 212 of the fan blade flow channel 21. As the impeller 20 rotates inside the air guide shroud 10, the airflow can flow into the fan blade flow channel 21 efficiently along the axial direction through the first air inlet 11 and the second air inlet 211, realizing the efficient intake of airflow from the axial direction. Then, under the centrifugal force of the impeller 20 rotation, the airflow entering the fan blade flow channel 21 of the impeller 20 is forced to turn and is evenly and dispersedly discharged radially through the multiple circumferentially distributed first air outlets 12, changing the traditional axial air outlet mode to circumferential multi-angle air outlet, effectively optimizing the airflow distribution and improving the air delivery effect.

[0052] Specifically, when the impeller 20 rotates, the airflow first enters the fan blade flow channel 21 along the axial direction through the first air inlet 11 and the second air inlet 211 of the air guide shroud 10. Under the action of the centrifugal force generated by the rotation of the impeller 20, the airflow is forced to change its direction in the fan blade flow channel 21, and finally discharged from the second air outlet 212 and the first air outlet 12 in sequence.

[0053] Specifically, there is no limit to the number of first air outlets 12, but there are at least two first air outlets 12.

[0054] In a specific implementation, the air guide shroud 10 provides a closed channel structure for airflow. The air guide shroud 10 is provided with a first air inlet 11 and multiple first air outlets 12, realizing the intake and exhaust of airflow. The first air inlet 11 is located on the axial side of the air guide shroud 10, which can directly face the external environment space, making it easy to efficiently capture the surrounding air. The multiple first air outlets 12 are distributed at intervals along the circumferential wall 13 of the air guide shroud 10. This distribution method can make the exhaust airflow evenly distributed in the circumferential direction, improving the range and uniformity of air delivery.

[0055] In a specific implementation, the impeller 20, as the core component for airflow drive, is rotatably mounted inside the air guide shroud 10, and its rotation provides power for the airflow. Multiple airflow channels 21 are evenly arranged along the circumference of the impeller 20, serving as the paths for airflow within the impeller 20. Each airflow channel 21 has a second air inlet 211 and a second air outlet 212. The second air inlet 211 is correspondingly located on the axial side of the impeller 20 and is connected to the first air inlet 11 of the air guide shroud 10, ensuring that air drawn in from the first air inlet 11 can smoothly enter the airflow channel 21. The second air outlet 212 is located on the circumferential side of the impeller 20 and is connected to the first air outlet 12 of the air guide shroud 10, allowing the airflow after being acted upon by the impeller 20 to be discharged through the first air outlet 12.

[0056] In a specific embodiment, the air guide shroud 10 is an axially extending cylindrical shell, with an internal hollow cavity for accommodating the impeller 20 and for airflow. A first sidewall 14 and a second sidewall 15 are arranged opposite each other in the axial direction of the air guide shroud 10. Both the first sidewall 14 and the second sidewall 15 are circular plate-like structures, parallel and spaced apart. The circumferential wall 13 is cylindrical, with its two ends fixedly connected to the edges of the first sidewall 14 and the second sidewall 15, respectively. The first sidewall 14, the second sidewall 15, and the circumferential wall 13 together form the air guide shroud 10.

[0057] Specifically, the first air inlet 11 is located in the central area of ​​the first side wall 14. The first air inlet 11 is connected to the hollow cavity inside the air guide shroud 10 and is located on the same axis as the air guide shroud 10. It can guide the airflow in the environment to enter the hollow cavity along the axis. The impeller 20 is installed in the hollow cavity of the air guide shroud 10 and is rotatably connected to the second side wall 15.

[0058] Specifically, the impeller 20 is driven to rotate by a motor or other driving components.

[0059] In one embodiment of this invention, the first air inlet 11 is a circular through-hole. Because the outline of the circular through-hole is smooth and continuous, when air flows axially towards the first air inlet 11, the smooth and continuous outline of the circular through-hole guides the airflow smoothly into the hollow cavity of the air guide shroud 10, preventing abrupt changes in airflow direction at the first air inlet 11 due to encountering an abrupt boundary, thus effectively preventing turbulence. Simultaneously, the smooth airflow reduces friction and impact between the airflow and the boundary of the first air inlet 11, thereby reducing noise.

[0060] In another embodiment of this invention, the first air inlet 11 is a polygonal through-hole, such as a triangle, quadrilateral, or hexagon. When the first air inlet 11 is a polygonal through-hole, it can enhance the structural strength of the air guide shroud 10 at that location, making the air guide shroud 10 less prone to deformation when subjected to external pressure or internal airflow impact, thereby improving the overall deformation resistance of the air guide shroud 10 structure and ensuring the structural reliability of the air guide shroud 10 during long-term use.

[0061] Specifically, three, four or more first air outlets 12 are evenly provided along the circumferential direction on the circumferential wall surface 13.

[0062] In one embodiment of this invention, the first air outlet 12 is designed as a circular through-hole. The outline of the circular through-hole is smooth and continuous, without any sharp corners or irregular undulations. When airflow flows out from the second air outlet 212 and reaches the first air outlet 12, the smooth and continuous boundary of the circular through-hole guides the airflow smoothly and steadily out of the first air outlet 12 in the radial direction. This ensures that the airflow will not undergo abrupt changes in direction due to abrupt boundary changes during the outflow process, thereby effectively avoiding airflow turbulence and impact, and reducing noise caused by irregular airflow movement.

[0063] In another embodiment of this invention, the first air outlet 12 adopts a polygonal through-hole structure, such as a triangular, quadrilateral, or hexagonal polygonal shape. When the first air outlet 12 is a polygonal through-hole, the structural strength of the air guide shroud 10 at this location is enhanced. This makes the air guide shroud 10 less prone to deformation when subjected to the high-speed impact of internal airflow and external pressure, thereby improving the overall deformation resistance of the air guide shroud 10 structure and ensuring that the air guide shroud 10 can work stably for a long time under complex working conditions, maintaining its good air guiding performance.

[0064] In one embodiment, the impeller 20 includes a central portion 22 and a plurality of blades 23; the central portion 22 is rotatably connected to the air guide shroud 10; the plurality of blades 23 are arranged circumferentially at intervals along the central portion 22, the blade roots of the blades 23 are connected to the central portion 22, and the blade edges of the blades 23 extend radially away from the central portion 22; a wind vane flow channel 21 is formed between two adjacent blades 23; a first gap is formed between the sides of two adjacent blades 23 near the first air inlet 11, and the first gap forms a second air inlet 211 of the wind vane flow channel 21; a second gap is formed between the blade edges of two adjacent blades 23, and the second gap forms a second air outlet 212 of the wind vane flow channel 21.

[0065] In the above embodiment, the central portion 22 supports the circumferentially spaced blades 23. Simultaneously, a second air inlet 211 is formed by the first gap on the inner side of adjacent blades 23, and a second air outlet 212 is formed by the second gap. When the impeller 20 rotates, the airflow enters the impeller channel 21 from the second air inlet 211 formed by the first gap. Guided by the blades 23 and under the centrifugal force generated by the rotation of the impeller 20, the airflow flows along the impeller channel 21 towards the blade edge of the blades 23, and finally exits from the second air outlet 212 formed by the second gap. Furthermore, its structure is simple, easy to process and shape during manufacturing, improving production efficiency. The optimized airflow path within the impeller channel 21 ensures smooth flow and low resistance from the axial second air inlet 211 to the circumferential second air outlet 212, thereby improving the overall performance of the impeller 20.

[0066] In a specific embodiment, the central portion 22 extends axially and has an overall cylindrical structure, which not only facilitates processing and manufacturing but also provides a stable mounting base for the blades 23. Furthermore, the central portion 22 and the air guide shroud 10 are located on the same axis, ensuring the concentricity of the impeller 20 when rotating within the air guide shroud 10, avoiding vibration and noise caused by eccentricity, and ensuring uniform airflow distribution within the flow channel.

[0067] In a specific implementation, multiple blades 23 are arranged at uniform intervals along the circumference of the center portion 22, which can ensure that the mass distribution of the impeller 20 is uniform during rotation, thereby ensuring its dynamic balance performance, reducing the additional vibration and energy loss generated when the impeller 20 rotates at high speed, and improving the stability and service life of operation.

[0068] Specifically, the blade root of the blade 23 is fixedly connected to the outer peripheral surface of the center 22, and the connection method can be integral molding or welding, etc.; the blade edge of the blade 23 extends radially away from the center 22, and its extension length is designed according to the inner diameter of the air guide shroud 10 to ensure that a preset gap is reserved between the blade edge of the blade 23 and the circumferential wall 13 of the air guide shroud 10, so as to avoid friction or collision between the impeller 20 and the circumferential wall 13 of the air guide shroud 10, and ensure that the impeller 20 can rotate smoothly inside the air guide shroud 10.

[0069] Specifically, the overall shape of the blade 23 is designed according to the airflow guidance requirements, and can be straight, curved, or twisted.

[0070] In a specific embodiment, a fan-blade channel 21 is formed between two adjacent blades 23. This fan-blade channel 21 extends radially from the outer side of the center portion 22 to the blade edge of the blade 23, providing a clear path for the airflow inside the impeller 20. After entering through the second air inlet 211 of the fan-blade channel 21, the airflow flows radially within the channel and is finally discharged from the second air outlet 212 of the fan-blade channel 21. This radially extending channel structure, combined with the centrifugal force of the impeller 20, can effectively drive the airflow to accelerate.

[0071] In one embodiment, the impeller 20 further includes a fixing part 24, which is sleeved on the outer peripheral surface of the central part 22 and connected to the side of the blade 23 away from the first air inlet 11.

[0072] In the above embodiment, by attaching the fixing part 24 to the outer periphery of the central part 22 and connecting it to the side of the blade 23 away from the first air inlet 11, the airflow entering the fan blade channel 21 can be effectively blocked from leaking from the side of the blade 23 away from the second air inlet 211. This ensures that the airflow can flow entirely within the fan blade channel 21 and stably exit from the second gap between the blade edges of two adjacent blades 23, ensuring that the air drawn in by the axial flow is finally discharged radially from the circumferentially distributed first air outlet 12. Furthermore, the connection between the fixing part 24, the blade 23, and the central part 22 forms a stable support structure, enhancing the structural rigidity of the root of the blade 23 and thus improving the overall deformation resistance of the impeller 20. This effectively suppresses the vibration that the blade 23 may generate due to centrifugal force under high-speed operating conditions, as well as the stress deformation caused by the vibration, ensuring the long-term stable working performance of the impeller 20.

[0073] In a specific embodiment, the blade 23 is fixedly connected to the fixing part 24 by means of welding or integral molding.

[0074] In one embodiment, the fixing part 24 is a conical annular structure, which includes an inner edge 241 and an outer edge 242. The inner edge 241 is connected to the outer peripheral surface of the central part 22, and the outer edge 242 is located at the end of the fixing part 24 away from the central part 22. Along the direction from the inner edge 241 to the outer edge 242, the radial distance between the generatrix of the conical annular structure and the axis of the impeller 20 gradually increases.

[0075] In the above embodiment, by setting the fixing part 24 as a conical annular structure, it conforms to the natural diffusion trajectory of the airflow from axial intake to radial outflow. The smooth transition of the conical surface of the conical annular structure serves as the rear wall of the fan blade flow channel 21, providing a low-resistance guiding channel for the airflow. This guides the airflow near the second air outlet 212, preventing the airflow from diffusing in an unexpected direction, enhancing the directionality of the airflow discharge, and ensuring a smoother flow process from the second air inlet 211 to the second air outlet 212. This reduces energy loss and thereby improves the aerodynamic efficiency and flow field stability of the impeller 20.

[0076] In one embodiment of this invention, the outer diameter of the fixing part 24 is equal to or greater than the radial distance of the blade edge of the blade 23. When the outer diameter of the fixing part 24 is equal to the radial distance of the blade edge of the blade 23, the outer edge 242 of the fixing part 24 is flush with the blade edge of the blade 23 in the radial direction; when the outer diameter of the fixing part 24 is greater than the radial distance of the blade edge of the blade 23, the outer edge 242 of the fixing part 24 extends beyond the blade edge of the blade 23 in the radial direction. This structural arrangement can effectively seal the fan blade flow channel 21, ensuring that the airflow entering the fan blade flow channel 21 can only be discharged from the second air outlet 212 of the fan blade flow channel 21. This effectively blocks the airflow in the fan blade flow channel 21 from flowing into the area between the fixing part 24 and the second sidewall 15, thereby avoiding ineffective airflow loss, ensuring full utilization of the airflow, and improving the airflow utilization rate. The outer diameter of the fixing part 24 refers to the diameter of the circle containing the outer edge 242 of the conical annular structure, and the radial distance of the blade edge of the blade 23 is the distance from the blade edge of the blade 23 to the axis of the impeller 20.

[0077] In a specific implementation, along the direction from the inner edge 241 to the outer edge 242 of the conical annular structure, from near the center 22 to away from the center 22, the distance between two adjacent blades 23 gradually increases. As the airflow flows radially outward in the flow channel, its volume tends to expand due to factors such as pressure changes. The gradually increasing distance can provide more flow space for the airflow, effectively reducing the obstruction caused by space limitation during the flow process, reducing energy loss, and ensuring that the airflow entering the impeller flow channel 21 can be discharged efficiently and smoothly from the second air outlet 212 of the flow channel, further improving the aerodynamic performance of the impeller 20.

[0078] In a specific embodiment, the inner edge 241 of the fixing part 24 is fixedly connected to the outer peripheral surface of the central part 22 by means of welding or integral molding.

[0079] In one embodiment, on a cross section perpendicular to the extension direction of the blade 23, a first included angle α is formed between the blade surface of the blade 23 and the tangent of the fixing part 24 at the connection point.

[0080] In the above embodiment, by setting a first included angle α between the blade 23 and the fixed part 24, an effective constraint effect can be formed on the air entering the fan blade flow channel 21. When the air enters the fan blade flow channel 21, under the spatial structure constraint formed by the first included angle α, the air can be stably retained in the fan blade flow channel 21. As the impeller 20 rotates, the gas retained in the fan blade flow channel 21 is forced to be guided to the second air outlet 212 of the fan blade flow channel 21 and discharged under the action of centrifugal force, effectively reducing the abnormal dispersion and turbulent flow of air in the fan blade flow channel 21, optimizing the air capture and driving efficiency of the impeller 20, and thus improving the overall aerodynamic performance and energy conversion efficiency of the impeller 20.

[0081] In one embodiment, the first included angle α ranges from 0 degrees to 45 degrees.

[0082] In the above embodiments, by limiting the first included angle α to the range of 0 degrees to 45 degrees, a balance between airflow diffusion efficiency and flow stability is achieved while ensuring the feasibility of the structure and process. This avoids the manufacturing and assembly difficulties caused by an excessively small included angle, as well as the flow separation phenomenon of airflow in the flow channel caused by an excessively large included angle, thus preventing energy dissipation, improving the working efficiency of the impeller 20, and enabling the airflow to be efficiently turned by closely following the curved surface of the conical fixed part 24, thereby maximizing the aerodynamic performance of the impeller 20.

[0083] In one embodiment, the first included angle α is the included angle between the windward surface 231 of the blade 23 and the side wall of the fixing part 24 facing the first air inlet 11.

[0084] In the above embodiment, by setting the first included angle α on the windward surface 231 of the blade 23, when the impeller 20 rotates, the airflow will impact the windward surface 231 of the blade 23. At this time, the setting of the first included angle α can guide the airflow in a natural way, so that the airflow enters the blade flow channel 21 more efficiently, reducing the impact loss of the airflow at the second air inlet 211 of the blade flow channel 21, and further improving the impeller 20's ability to capture airflow and drive efficiency.

[0085] In one embodiment, an annular air duct 16 is provided between the outer circle of the rotation trajectory of the impeller 20 and the circumferential wall 13 of the air guide shroud 10, and the second air outlet 212 is connected to the first air outlet 12 through the annular air duct 16.

[0086] In the above embodiment, an annular air duct 16 is provided between the circumcircle of the rotation trajectory of the impeller 20 and the circumferential wall 13 of the air guide shroud 10. When the airflow flows out from the second air outlet 212, it first enters the annular air duct 16 and gathers within it. Since the annular air duct 16 is a continuous annular structure along the circumference, it can buffer and equalize the airflow. Subsequently, the airflow is evenly distributed to each of the circumferentially distributed first air outlets 12 through the annular air duct 16. This effectively solves the problem of uneven flow distribution that may occur due to the difference in the relative positions of each first air outlet 12 and the second air outlet 212 when the airflow flows directly from the second air outlet 212 to each of the first air outlets 12, ensuring the consistency of the airflow from each of the first air outlets 12.

[0087] In a specific embodiment, when the impeller 20 rotates around its axis, the rotation trajectory formed by its outermost edge has a circumscribed circle. An annular space is reserved between this circumscribed circle and the circumferential wall 13 of the air guide shroud 10, and this annular space constitutes the annular air duct 16. The annular air duct 16 is continuously distributed around the circumference of the air guide shroud 10, with its inner boundary being the circumscribed circle of the impeller 20's rotation trajectory and its outer boundary being the inner side of the circumferential wall 13 of the air guide shroud 10. At the same time, the annular air duct 16 is directly connected to the second air outlet 212 of the air blade flow channel 21, that is, the airflow discharged from the second air outlet 212 can directly enter the annular air duct 16; and the annular air duct 16 is also connected to a plurality of first air outlets 12 that are spaced apart circumferentially on the air guide shroud 10, so that the airflow in the annular air duct 16 can flow to each of the first air outlets 12.

[0088] In one embodiment, along the rotation direction of the impeller 20, an acceleration duct section 17 is formed between two adjacent first air outlets 12, and along the airflow direction, the radial distance between the inner wall surface of the acceleration duct section 17 and the outer circle of the rotation trajectory of the impeller 20 gradually increases.

[0089] In the above embodiment, since the radial distance between the inner wall of the acceleration duct section 17 and the circumcircle of the impeller 20's rotation trajectory gradually increases along the rotation direction, a gradually expanding flow channel is formed between two adjacent first air outlets 12. When the airflow flows into the annular duct 16 from the second air outlet 212, it flows along the annular duct 16 towards each of the first air outlets 12. When passing through the acceleration duct section 17 between two adjacent first air outlets 12, the gradually expanding flow channel structure can effectively avoid the violent impact and vortex generated when the airflow suddenly passes through the first air outlet 12 from the relatively narrow annular duct 16 into the open space outside. This reduces the airflow noise during impeller 20 operation and also reduces energy loss caused by vortices. Furthermore, the gradually expanding flow channel helps to smoothly guide the airflow, making the airflow smoother as it flows towards the first air outlet 12, reducing wind resistance, improving airflow delivery efficiency, and achieving a more uniform, stable, and quiet airflow output.

[0090] In a specific implementation, the accelerating air duct section 17 is the air duct area formed between the continuous wall portion of the circumferential wall 13 of the air guide shroud 10 between the two first air outlets 12 and the outer circle of the rotation trajectory of the impeller 20. Specifically, each first air outlet 12 has two ends distributed circumferentially. In two adjacent first air outlets 12, the inner wall of the circumferential wall 13 of the air guide shroud 10 between the rear end of the preceding first air outlet 12 and the front end of the following first air outlet 12 forms the inner wall of the accelerating air duct section 17. The radial distance between this inner wall and the outer circle of the rotation trajectory of the impeller 20 gradually increases along the rotation direction of the impeller 20.

[0091] In one embodiment, the acceleration air duct section 17 is provided with air guide vanes 18 at both ends along the airflow direction. One end of the air guide vane 18 is connected to the inner wall surface of the acceleration air duct section 17, and the other end extends to the outer edge of the air guide cover 10.

[0092] In the above embodiment, since one end of the air guide vane 18 is connected to the inner wall of the acceleration duct section 17, when the airflow flows through the acceleration duct section 17 to the first air outlet 12, the air guide vane 18 can directly receive the accelerated airflow, forming a forced constraint on the airflow, causing the airflow to flow along the predetermined path guided by the air guide vane 18, effectively preventing the airflow from rapidly spreading outwards or forming turbulent vortices after leaving the annular duct 16 due to loss of constraint. Furthermore, the other end of the air guide vane 18 extends to the outer edge of the air guide shroud 10, ensuring that the airflow is fully and completely discharged from the shroud under the guidance of the air guide vane 18 throughout its entire length, reducing energy dissipation caused by the airflow hitting the edge of the air guide shroud 10 or causing disordered backflow.

[0093] In specific embodiments, each first air outlet 12 of the air guide shroud 10 is provided with at least one air guide vane 18. In one embodiment, one end of the air guide vane 18 is fixedly connected to the inner wall surface of the acceleration air duct section 17, with the connection position located at the front end of the next first air outlet 12 adjacent to the acceleration air duct section 17; the other end of the air guide vane 18 extends away from the rotation center of the impeller 20 until it reaches the outer edge of the air guide shroud 10. In another embodiment, one end of the air guide vane 18 is fixedly connected to the inner wall surface of the acceleration air duct section 17, with the connection position located at the rear end of the previous first air outlet 12 adjacent to the acceleration air duct section 17; the other end of the air guide vane 18 extends away from the rotation center of the impeller 20 until it reaches the outer edge of the air guide shroud 10.

[0094] Specifically, the other end of the air guide vane 18 extends away from the rotation center of the impeller 20 until it reaches the outer edge of the first sidewall 14; and the outer end of the air guide vane 18 is flush with or slightly beyond the outer edge of the first sidewall 14.

[0095] In one embodiment, the air guide vane 18 extends radially along the air guide shroud 10; or a second included angle θ is provided between the air guide surface 181 of the air guide vane 18 and the radial reference line L of the air guide shroud 10; wherein the radial reference line L is a straight line passing through the connection point of the air guide vane 18 and the inner wall of the acceleration duct section 17, and the second included angle θ is an obtuse angle.

[0096] In the above embodiment, by adjusting the second angle θ between the air guide vane 18 and the air guide shroud 10 in the radial direction, the airflow direction when leaving the first air outlet 12 can be flexibly set. When the air guide vane 18 extends radially, the airflow will flow out in the radial direction of the air guide shroud 10; while when the air guide vane 18 is provided with a second angle θ between it and the radial direction, the airflow will change its outlet angle according to the tilt direction of the air guide vane 18. This not only enhances the directionality of air delivery, allowing the airflow to be accurately delivered to the target area, but also enables the duct device to adapt to the requirements of specific air delivery angles in different application scenarios, thereby improving the applicability and practicality of the duct device.

[0097] In one embodiment of this invention, the air guide vane 18 extends radially along the air guide shroud 10. At this time, the air guide vane 18 extends radially outward from the inner wall of the acceleration duct section 17 to the outer edge of the air guide shroud 10, and its extension trajectory is consistent with the radial direction of the air guide shroud 10. In another embodiment of this invention, a second included angle θ is provided between the air guide vane 18 and the radial direction of the air guide shroud 10. That is, the center line of the air guide vane 18 does not coincide with the radial line of the air guide shroud 10, but is inclined at a certain angle. This angle is the second included angle θ, and the size of the second included angle θ can be set according to the actual air supply requirements.

[0098] In one embodiment, the angle of the second included angle θ formed between the air guide surfaces 181 of the two air guide vanes 18 at both ends of the airflow direction of the acceleration duct section 17 and the radial reference line L of the corresponding air guide shroud 10 is different.

[0099] In a specific implementation, after the impeller 20 is started, the fan blades capture ambient air through the first air inlet 11 of the air guide shroud 10 and introduce it into the fan blade flow channel 21. At this time, the incoming air already has a certain velocity. Subsequently, through the steering action of the fixing part 24, the velocity direction of the air is adjusted to radial, and a radial initial velocity is obtained. Due to the centrifugal force generated by the high-speed rotation of the impeller 20, the air contained in the fan blade flow channel 21 is thrown out from the second air outlet 212 of the flow channel. After being superimposed with the radial initial velocity, it is further accelerated, forming a high-speed airflow with a spiral circumferential motion. These high-speed airflows with spiral circumferential motion are rectified and accelerated by the acceleration duct section 17, enter the space between the air guide vanes 18, and after being further guided and oriented by the air guide vanes 18, they are transformed into airflow with a pure radial velocity, and finally delivered from the first air outlet 12 of the air guide shroud 10, completing the air delivery process.

[0100] Although embodiments of the present invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the present invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. An air duct arrangement, characterized in that include: The air guide shroud (10) has a first air inlet (11) and a plurality of first air outlets (12); the first air inlet (11) is disposed on the axial side of the air guide shroud (10); the plurality of first air outlets (12) are distributed at intervals along the circumference of the air guide shroud (10), and the first air outlets (12) are disposed on the circumferential wall surface (13) of the air guide shroud (10); An impeller (20) is rotatably disposed inside the air guide shroud (10), and a plurality of air blade channels (21) are provided along the circumference of the impeller (20); the air blade channels (21) have a second air inlet (211) and a second air outlet (212), the second air inlet (211) is disposed on the axial side of the impeller (20), and the second air outlet (212) is disposed on the circumferential side of the impeller (20); The second air inlet (211) of the fan blade flow channel (21) is connected to the first air inlet (11), and the second air outlet (212) of the fan blade flow channel (21) is connected to the first air outlet (12).

2. The air duct arrangement of claim 1, wherein The impeller (20) includes: The central part (22) is rotatably connected to the air guide shroud (10); Multiple blades (23) are arranged circumferentially around the central portion (22), with the blade roots of the blades (23) connected to the central portion (22) and the blade edges of the blades (23) extending radially away from the central portion (22); a fan blade channel (21) is formed between two adjacent blades (23); a first gap is formed between the sides of two adjacent blades (23) near the first air inlet (11), and the first gap forms the second air inlet (211) of the fan blade channel (21); a second gap is formed between the blade edges of two adjacent blades (23), and the second gap forms the second air outlet (212) of the fan blade channel (21).

3. The air duct arrangement of claim 2, wherein, The impeller (20) also includes a fixing part (24), which is sleeved on the outer peripheral surface of the central part (22) and connected to the side of the blade (23) away from the first air inlet (11).

4. The air duct arrangement of claim 3, wherein The fixing part (24) is a conical annular structure. The fixing part (24) includes an inner edge (241) and an outer edge (242). The inner edge (241) is connected to the outer peripheral surface of the central part (22), and the outer edge (242) is located at the end of the fixing part (24) away from the central part (22). Along the direction from the inner edge (241) to the outer edge (242), the radial distance between the generatrix of the conical annular structure and the axis of the impeller (20) gradually increases.

5. The air duct arrangement of claim 3, wherein, On a cross section perpendicular to the extension direction of the blade (23), the blade surface of the blade (23) and the tangent of the fixing part (24) at the connection point form a first included angle α; The angle range of the first included angle α is 0 degrees to 45 degrees.

6. The air duct arrangement of claim 5, wherein The first included angle α is the included angle between the windward surface (231) of the blade (23) and the side wall of the fixing part (24) facing the first air inlet (11).

7. The air duct arrangement of any one of claims 1 to 6, wherein, An annular air duct (16) is provided between the outer circle of the rotation trajectory of the impeller (20) and the circumferential wall (13) of the air guide shroud (10), and the second air outlet (212) is connected to the first air outlet (12) through the annular air duct (16).

8. The air duct arrangement of any one of claims 1 to 6, wherein, Along the rotation direction of the impeller (20), an acceleration duct section (17) is formed between two adjacent first air outlets (12). Along the airflow direction, the radial distance between the inner wall surface of the acceleration duct section (17) and the outer circle of the rotation trajectory of the impeller (20) gradually increases.

9. The air duct arrangement of claim 8, wherein, The acceleration air duct section (17) is provided with air guide vanes (18) at both ends along the airflow direction. One end of the air guide vane (18) is connected to the inner wall of the acceleration air duct section (17), and the other end extends to the outer edge of the air guide cover (10).

10. The air duct arrangement of claim 9, wherein, The air guide vane (18) extends radially along the air guide shroud (10); or a second included angle θ is provided between the air guide surface (181) of the air guide vane (18) and the radial reference line (L) of the air guide shroud (10); wherein the radial reference line (L) is a straight line passing through the radial direction of the air guide shroud (10) at the connection point between the air guide vane (18) and the inner wall of the acceleration duct section (17), and the second included angle θ is an obtuse angle.

11. The air duct arrangement of claim 10, wherein, The angle of the second included angle θ formed between the air guide surface (181) of the two air guide vanes (18) at both ends of the acceleration air duct section (17) along the airflow direction and the radial reference line (L) of the corresponding air guide shroud (10) is different.

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