Axial flow wind wheel, fan and top air outlet component

Abstract

The invention discloses an axial flow wind wheel, a fan and a top air outlet component, the axial flow wind wheel comprises an impeller and an air guide ring, the impeller comprises a hub and a plurality of blades, and the blades are arranged in the circumferential direction of the hub and connected with the hub; the air guide ring surrounds the impeller, and convex ribs are formed on the inner circumferential wall of the air guide ring and extend in the circumferential direction of the air guide ring. According to the axial flow wind wheel, the protruding ribs extending in the circumferential direction are formed on the inner circumferential wall of the wind guide ring, the flowing resistance of airflow flowing in the blade top gaps can be increased through the protruding ribs, and therefore the leakage amount of the airflow from the blade top gaps is reduced, leakage losses are reduced, and the aerodynamic efficiency of the axial flow wind wheel is improved.

Description

Technical Field

[0001] The present invention relates to the field of fans, and in particular to an axial flow fan wheel, a fan and a top air outlet component. Background Art

[0002] Relevant technology points out that there is a blade tip gap between the impeller and the air guide ring of the axial flow fan. The existence of the blade tip gap causes the airflow in the high-pressure area of ​​the blade pressure surface to flow to the low-pressure area of ​​the blade suction surface, causing leakage loss and resulting in low aerodynamic efficiency of the axial flow fan. Summary of the Invention

[0003] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention provides an axial flow wind wheel that is conducive to improving aerodynamic efficiency.

[0004] The present invention also provides a wind turbine having the above-mentioned axial flow wind wheel.

[0005] The present invention also provides a top air outlet component having the above-mentioned fan.

[0006] According to the first aspect of the present invention, the axial flow wind wheel includes: an impeller, the impeller includes a hub and a plurality of blades, the plurality of blades are arranged along the circumference of the hub and connected to the hub; an air guide ring, the air guide ring surrounds the impeller, the inner peripheral wall of the air guide ring is formed with ribs, and the ribs extend along the circumference of the air guide ring.

[0007] According to the axial flow wind wheel of the embodiment of the present invention, ribs extending in the circumferential direction are formed on the inner circumferential wall of the air guide ring. The ribs can increase the flow resistance of the airflow when flowing in the blade tip gap, thereby reducing the leakage of the airflow from the blade tip gap, reducing leakage losses, and helping to improve the aerodynamic efficiency of the axial flow wind wheel.

[0008] In some embodiments, the ribs are multiple and arranged along the axial direction of the air guide ring, and grooves are defined between adjacent ribs.

[0009] In some embodiments, the grooves are multiple and arranged along the axial direction of the air guide ring.

[0010] In some embodiments, at least a portion of the blade top is constructed as a concave-convex portion, which is formed as an inner concave portion corresponding to the rib and an outer convex portion corresponding to the groove, and the outer convex portion protrudes toward the air guide ring relative to the inner concave portion.

[0011] In some embodiments, there are multiple grooves arranged along the axial direction of the air guide ring, and the outer convex parts and the inner concave parts are arranged in a one-to-one correspondence.

[0012] In some embodiments, at least a portion of the protrusion extends into the groove.

[0013] In some embodiments, on the axial cross-section of the axial flow wind wheel, the inner concave portion matches the shape of the convex rib and the gap is uniform, the outer convex portion matches the shape of the groove and the gap is uniform, and the gap between the inner concave portion and the convex rib is consistent with the gap between the outer convex portion and the groove.

[0014] In some embodiments, on the axial cross-section of the axial flow wind wheel, the ratio of the gap between the concave-convex portion and the air guide ring to the diameter of the impeller is 0.005 to 0.01.

[0015] In some embodiments, more than half of the length of the blade tip from the trailing edge to the leading edge of the blade is configured as the concave-convex portion, and the concave-convex portion is arranged closer to the trailing edge of the blade relative to the leading edge of the blade.

[0016] In some embodiments, on the axial cross-section of the axial flow wind wheel, the contour line of the rib is formed as an arc line that protrudes toward the impeller.

[0017] In some embodiments, a plurality of the ribs are continuously arranged along the axial direction of the air guide ring.

[0018] In some embodiments, the ratio of the axial dimensions of two adjacent ribs is 0.1-10, the ratio of the axial dimension of the rib to the diameter of the impeller is 0.001-0.1, and the ratio of the radial protrusion height of the rib to the diameter of the impeller is 0.001-0.02.

[0019] In some embodiments, the plurality of ribs are divided into first ribs and second ribs alternately arranged along the axial direction of the air guide ring, the axial dimension of the first rib is greater than the axial dimension of the second rib, and the radial protrusion height of the first rib is greater than or equal to the radial protrusion height of the second rib.

[0020] In some embodiments, the rib is formed as an annular rib extending along the entire circumference of the air guide ring.

[0021] A wind turbine according to an embodiment of the second aspect of the present invention comprises a motor and an axial flow wind wheel according to an embodiment of the first aspect of the present invention, wherein the motor is connected to the axial flow wind wheel to drive the axial flow wind wheel to move.

[0022] According to the fan of the embodiment of the present invention, the axial flow fan is provided with the axial flow wind wheel of the embodiment of the first aspect, thereby improving the working efficiency of the axial flow fan.

[0023] According to an embodiment of the third aspect of the present invention, the top air outlet component includes: a heat exchanger and a fan according to an embodiment of the second aspect of the present invention, the fan is arranged above the heat exchanger, the axis of the fan is vertical and the outlet is upward, and the top of the top air outlet component has an air outlet.

[0024] According to the top air outlet component of the embodiment of the present invention, by providing the fan of the above-mentioned second embodiment, the air flow is driven to flow through the heat exchanger, which is beneficial to improving the heat exchange efficiency of the heat exchanger.

[0025] In some embodiments, the air guide ring intersects with the orthographic projection of the heat exchanger on a horizontal plane.

[0026] In some embodiments, the heat exchanger includes a plate-shaped heat exchange section. On a horizontal projection plane, the ratio of the vertical distance from the center of the air guide ring to the heat exchange section to the inner circle radius of the air guide ring is 0.8 to 1, or the ratio of the vertical distance from the center of the air guide ring to the outer contour of the heat exchange section to the inner circle radius of the air guide ring is 0.96 to 1.2.

[0027] In some embodiments, the top air outlet component also includes a mounting bracket, which is arranged above the heat exchanger, and the mounting bracket includes a frame and a support rod, the frame defines an air passage passing through in the up and down directions, and the support rod is connected to the frame and is vertically opposite to the air passage; the fan is arranged above the mounting bracket, the motor is located below the axial flow wind wheel, and the motor is fixedly connected to the support rod, and the air guide ring is fixedly connected to the frame.

[0028] Additional aspects and advantages of the present invention will be set forth in part in the description which follows and, in part, will be obvious from the description which follows, or may be learned by practice of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 is a schematic structural diagram of an axial flow wind wheel according to an embodiment of the present invention;

[0030] Figure 2 is an axial cross-sectional view of an axial flow wind wheel according to one embodiment of the present invention;

[0031] Figure 3 2. It is a schematic diagram of the coordination between the inner peripheral wall and the concave-convex portion of the air guide ring according to one embodiment of the present invention;

[0032] Figure 4 is a front view of an axial flow wind wheel according to one embodiment of the present invention;

[0033] Figure 5 is a partially enlarged view of an axial cross section of an axial flow wind wheel according to another embodiment of the present application;

[0034] Figure 6 is a structural schematic diagram of a fan according to an embodiment of the present invention;

[0035] Figure 7 This is a schematic structural diagram of a top air outlet component according to an embodiment of the present invention;

[0036] Figure 8 This is a schematic structural diagram of a hidden outer frame of an air outlet component according to an embodiment of the present invention;

[0037] Figure 9 is a bottom view of a hidden portion outer frame of a top air outlet portion according to one embodiment of the present invention;

[0038] Figure 10 It is a cross-sectional view of a top air outlet component according to one embodiment of the present application.

[0039] Reference numerals:

[0040] Top air outlet component 10000;

[0041] Fan 1000;

[0042] Axial flow wind wheel 100;

[0043] Impeller 1; hub 11; blade 12; blade tip 12a; trailing edge 12b; leading edge 12c; concave-convex portion 121; inner concave portion 1211; outer convex portion 1212;

[0044] Air guide ring 2; rib 21; first rib 211; second rib 212; groove 22;

[0045] Tip clearance 3;

[0046] Motor 200;

[0047] Heat exchanger 2000 ; heat exchange section 2001 ; mounting frame 4000 ; frame 41 ; air passage 41 a ; support rod 42 ; air outlet 5000 . DETAILED DESCRIPTION

[0048] The following describes embodiments of the present invention in detail, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are intended to be used to explain the present invention, and are not to be construed as limiting the present invention.

[0049] The disclosure below provides many different embodiments or examples for realizing different structures of the present invention. In order to simplify the disclosure of the present invention, the components and settings of specific examples are described below. Of course, they are merely examples and are not intended to limit the present invention. In addition, the present invention may repeat reference numbers and / or letters in different examples. This repetition is for the purpose of simplicity and clarity and does not in itself indicate the relationship between the various embodiments and / or settings discussed. In addition, the present invention provides examples of various specific processes and materials, but those skilled in the art will appreciate the applicability of other processes and / or the use of other materials.

[0050] The axial flow wind wheel 100 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0051] According to the axial flow wind wheel 100 of the embodiment of the present invention, Figure 1 and Figure 2 As shown, the axial flow wind wheel 100 includes: an impeller 1 and an air guide ring 2, the impeller 1 includes a hub 11 and a plurality of blades 12, the plurality of blades 12 are arranged along the circumference of the hub 11 and connected to the hub 11; the air guide ring 2 surrounds the impeller 1, and the inner circumferential wall of the air guide ring 2 is formed with a rib 21, and the rib 21 extends along the circumference of the air guide ring 2.

[0052] The axial flow wind wheel 100 includes an impeller 1 and an air guide ring 2. The impeller 1 includes a hub 11 located in the middle and a plurality of blades 12 connected to the hub 11. The blades 12 are arranged along the circumference of the hub 11. The air guide ring 2 surrounds the impeller 1 to improve the axial consistency of the airflow and enhance the axial air supply effect of the axial flow wind wheel 100.

[0053] There is a blade tip gap 3 between the blade tip 12a of the blade 12 and the air guide ring 2. When the impeller 1 rotates, the existence of the blade tip gap 3 will cause the airflow to bypass the blade tip 12a from the high-pressure area of ​​the pressure surface of the blade 12 and directly leak into the low-pressure area of ​​the suction surface of the blade 12, causing leakage loss and reducing the aerodynamic efficiency of the axial flow wind wheel 100.

[0054] The axial flow rotor 100 of the embodiment of the present invention has ribs 21 formed on the inner circumferential wall of the air guide ring 2, extending along the circumference of the air guide ring 2. The ribs 21 protrude inward, that is, toward the center of the air guide ring 2. The ribs 21 may protrude in the radial direction of the air guide ring 2 or in a direction that is angled with the radial direction of the air guide ring 2. The ribs 21 increase the flow resistance within the blade tip gap 3, thereby reducing the amount of air leakage from the blade tip gap 3 and minimizing leakage losses, thereby improving the aerodynamic efficiency of the axial flow rotor 100.

[0055] Among them, the air guide ring 2 is coaxially arranged with the impeller 1, the circumferential direction of the air guide ring 2 is in the same direction as the circumferential direction of the hub 11, and the radial direction of the air guide ring 2 is in the same direction as the radial direction of the hub 11. Since the rib 21 is arranged on the air guide ring 2, the rib 21 is described with reference to the air guide ring 2 for easy understanding.

[0056] According to the axial flow wind wheel 100 of the embodiment of the present invention, by forming circumferentially extending ribs 21 on the inner circumferential wall of the air guide ring 2, the ribs 21 can increase the flow resistance of the airflow when flowing in the blade tip gap 3, thereby reducing the leakage amount of the airflow from the blade tip gap 3, reducing leakage losses, and helping to improve the aerodynamic efficiency of the axial flow wind wheel 100.

[0057] In some embodiments of the present invention, Figure 1 and Figure 2 As shown, there are multiple ribs 21 arranged along the axial direction of the air guide ring 2 , and grooves 22 are defined between adjacent ribs 21 .

[0058] There are multiple (i.e., at least two) ribs 21, and the multiple ribs 21 are arranged axially along the air guide ring 2, which can further increase the flow resistance of the airflow when flowing in the blade tip gap 3, thereby preventing the airflow from leaking through the blade tip gap 3, reducing leakage losses, and helping to improve the aerodynamic efficiency of the axial flow wind wheel 100.

[0059] For example, a plurality of ribs 21 can be arranged continuously along the axial direction of the air guide ring 2, and there is no gap between two ribs 21 adjacent to each other along the axial direction. At this time, the groove wall of the groove 22 is only defined by the ribs 21; for example, the contour line of the rib 21 is formed as an arc line protruding toward the impeller 1, then the groove bottom of the groove 22 is constructed as a pointed bottom form, and the side wall of the groove 22 is constructed as an arc form.

[0060] Alternatively, for example, multiple ribs 21 can also be arranged at axial intervals along the air guide ring 2, and there is a gap between two axially adjacent ribs 21. At this time, the groove wall of the groove 22 includes a portion defined by the ribs 21 and a portion connected between the two ribs 21.

[0061] In some embodiments of the present invention, Figure 2 As shown, there are multiple grooves 22 and they are arranged along the axial direction of the air guide ring 2 .

[0062] There are more than three ribs 21 , so that there are multiple grooves 22 (ie, at least two). The multiple ribs 21 are arranged along the axial direction of the air guide ring 2 , which can further increase the flow resistance of the airflow when flowing in the blade tip gap 3 .

[0063] In some embodiments of the present invention, Figure 3 and Figure 4As shown, at least part of the blade tip 12a of the blade 12 is constructed as a concave-convex portion 121, which is formed as an inner concave portion 1211 at the corresponding rib 21 and an outer convex portion 1212 at the corresponding groove 22. The outer convex portion 1212 protrudes relative to the inner concave portion 1211 toward the air guide ring 2. Figure 3 The profile of the blade tip 12a of the blade 12 shown in FIG. 1 is a swept projection of the blade tip 12a of the blade 12 projected along the circumferential direction onto the axial cross section of the air guide ring 2 .

[0064] The outer convex portion 1212 protrudes relative to the inner concave portion 1211 toward the air guide ring 2, where the direction toward the air guide ring 2 is toward the inner circumferential wall of the air guide ring 2. A radial space is defined between the tip 12a of the blade 12 and the inner circumferential wall of the air guide ring 2, and the outer convex portion 1212 protrudes toward the radial space. The outer convex portion 1212 may protrude in the radial direction of the air guide ring 2, or may protrude in a direction that forms an angle with the radial direction of the air guide ring 2.

[0065] The top 12a of the blade 12 is constructed with a concave-convex portion 121, which is formed as an inner concave portion 1211 at the corresponding rib 21, and is formed as an outer convex portion 1212 at the corresponding groove 22. The outer convex portion 1212 protrudes toward the air guide ring 2 relative to the inner concave portion 1211, and the inner concave portion 1211 is recessed toward the hub 11 relative to the outer convex portion 1212. Thus, the concave-convex portion 121 has a plurality of inner concave portions 1211 and outer convex portions 1212 arranged alternately one by one to form a generally sawtooth structure.

[0066] The present invention forms a concave-convex portion 121 on the tip 12a of the blade 12. When the blade 12 rotates, the concave-convex portion at the tip 12a can disperse the vortex at the tip gap 3, thereby reducing the vortex intensity and facilitating the reduction of vortex noise. The tip serrations disperse the vortex formed by the return flow, reducing broadband noise, lowering the return flow velocity and the amount of tip recirculation, thereby improving aerodynamic efficiency.

[0067] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, there are multiple grooves 22 arranged along the axial direction of the air guide ring 2, and the outer protrusions 1212 and the inner recesses 1211 are arranged in a one-to-one correspondence.

[0068] There are more than three ribs 21 , so that there are multiple grooves 22 . The multiple ribs 21 are arranged along the axial direction of the air guide ring 2 , which can further increase the flow resistance of the airflow when flowing in the blade tip gap 3 .

[0069] A groove 22 is defined between two adjacent ribs 21, so the ribs 21 and the grooves 22 are arranged alternately in sequence, and the convex and concave parts 121 corresponding to the ribs 21 and the grooves 22 are also constructed with the outer convex parts 1212 and the inner concave parts 1211 arranged alternately in sequence, and the outer convex parts 1212 and the inner concave parts 1211 are arranged one by one.

[0070] In this way, the blade tip gap 3 can be relatively uniform, which is beneficial to improving the aerodynamic performance of the axial flow wind wheel 100, reducing noise, improving the matching stability between the blades 12 and the air guide ring 2, and reducing interference.

[0071] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, the cross section of the tip gap 3 between the air guide ring 2 and the blade tip 12a is formed to extend in a wave shape in the axial direction, thereby improving the matching stability between the blade 12 and the air guide ring 2 and reducing interference.

[0072] In some embodiments of the present invention, Figure 5 As shown, at least a portion of the outer protrusion 1212 extends into the groove 22. The outer protrusion 1212 extends into the groove 22 along the radial direction of the air guide ring 2.

[0073] The concave-convex portion 121 not only breaks up the vortex at the blade tip gap 3, thereby reducing the vortex intensity and vortex noise; at least part of the outer convex portion 1212 extends into the groove 22, and in the axial direction of the axial flow wind wheel 100, at least part of the outer convex portion 1212 has an overlapping portion with the air guide ring 2, thereby reducing the leakage of airflow from the blade tip gap 3 and reducing leakage losses.

[0074] In some embodiments of the present invention, Figure 3 As shown, on the axial cross-section of the axial flow wind wheel 100, the inner concave portion 1211 matches the shape of the rib 21 and the gap is uniform, the outer convex portion 1212 matches the shape of the groove 22 and the gap is uniform, and the gap between the inner concave portion 1211 and the rib 21 is consistent with the gap between the outer convex portion 1212 and the groove 22.

[0075] It is worth mentioning that Figure 3 The outline of the middle air guide ring 2 is a contour diagram on the axial cross section of the axial flow wind wheel 100, while the contour line of the concave-convex portion 121 is a processed contour diagram, so as to better understand the technical solution of the present invention.

[0076] The gap between the inner concave portion 1211 and the rib 21 refers to the gap in the radial direction of the air guide ring 2 , and the gap between the outer convex portion 1212 and the groove 22 also refers to the gap in the radial direction of the air guide ring 2 .

[0077] By constructing the concave-convex portion 121 on the blade tip 12a of the blade 12, not only can the vortex at the blade tip gap 3 be broken up, thereby reducing the vortex intensity and the vortex noise, but the blade 12 can also cooperate one-to-one with the ribs 21 and the grooves 22 on the air guide ring 2, so that the gap between the concave-convex portion 121 and the inner circumferential wall of the air guide ring 2 remains consistent, which can improve the rotational stability of the blade 12. For example, when the axial flow wind wheel 100 is in an unstable working state, such as when foreign matter enters, since the gap between the concave-convex portion 121 and the inner circumferential wall of the air guide ring 2 remains consistent, the foreign matter is not easily stuck between the blade 12 and the air guide ring 2. However, when the gap between the blade 12 and the air guide ring 2 is abruptly reduced, the foreign matter entering the blade tip gap 3 can easily cause the blade 12 to get stuck or even break.

[0078] The gap between the concave-convex portion 121 and the inner circumferential wall of the air guide ring 2 is consistent. Therefore, the embodiment of the present invention forms a rib 21 on the inner circumferential wall of the air guide ring 2. It does not simply reduce the leakage loss of the blade tip 12a by reducing the blade tip gap 3. In fact, since the concave-convex portion 121 is formed on the blade tip 12a, the flow resistance of the airflow when flowing in the blade tip gap 3 can be increased while keeping the blade tip gap 3 unchanged, thereby reducing the leakage amount of the airflow from the blade tip gap 3 and reducing the leakage loss.

[0079] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, on the axial section of the axial flow wind wheel 100, the ratio of the gap d between the concave-convex portion 121 and the air guide ring 2 to the diameter D of the impeller 1 is 0.005-0.01, that is, d=0.005D-0.01D.

[0080] Optionally, the ratio of the gap d between the concave-convex portion 121 and the air guide ring 2 to the diameter D of the impeller 1 may be 0.0055, 0.006, 0.007, 0.008, 0.0095, etc.

[0081] In some embodiments of the present invention, Figure 4 As shown, the tip 12a of the blade 12 is configured as a concave-convex portion 121 over more than half of its length from the trailing edge 12b to the leading edge 12c of the blade 12 , and the concave-convex portion 121 is arranged closer to the trailing edge 12b of the blade 12 relative to the leading edge 12c of the blade 12 .

[0082] The tip 12a of the blade 12 is constructed as a concave-convex portion 121 over more than half of its length from the trailing edge 12b to the leading edge 12c of the blade 12. The concave-convex portion 121 has a large range, which is beneficial for breaking up the vortex at the tip gap 3.

[0083] In the related art, due to the existence of the thickness of the blade, a wake will be formed at the tail of the blade. In the embodiment of the present invention, the concave-convex portion 121 is arranged close to the trailing edge 12b of the blade 12. The concave-convex portion 121 breaks up the vortex near the trailing edge 12b of the blade 12, thereby reducing the vortex intensity and helping to reduce vortex noise.

[0084] In some embodiments of the present invention, the tip 12 a of the blade 12 is configured as a concave-convex portion 121 from the trailing edge 12 b of the blade 12 to the leading edge 12 c of the blade 12 .

[0085] In some embodiments of the present invention, Figure 2 and Figure 3 As shown, on the axial cross section of the axial flow wind wheel 100 , the contour line of the rib 21 is formed as an arc line that protrudes toward the impeller 1 .

[0086] The contour line of the rib 21 is formed into an arc, which can reduce the vortex generated when the air flows through the edge of the rib 21, and can reduce the air flow separation compared to the rib 21 with a rectangular contour line, thereby helping to reduce the working noise of the axial flow impeller 100.

[0087] In some embodiments of the present invention, the outline of the rib 21 is a portion of a circle.

[0088] In some embodiments of the present invention, Figure 1 and Figure 2 As shown, a plurality of ribs 21 are continuously arranged along the axial direction of the air guide ring 2 .

[0089] There is no space between the contour lines of the ribs 21 , and the contour lines of adjacent ribs 21 are directly connected. The dense arrangement of multiple ribs 21 can further increase the flow resistance of the airflow when flowing in the blade tip gap 3 to reduce leakage loss.

[0090] like Figure 2 As shown, adjacent ribs 21 define grooves 22 extending radially outward relative to the ribs 21 , and the bottoms of the grooves 22 are pointed.

[0091] In other embodiments of the present invention, a plurality of ribs 21 are arranged at intervals along the axial direction of the air guide ring 2 to reduce manufacturing difficulty.

[0092] Adjacent ribs 21 define grooves 22 extending radially outward relative to the ribs 21, and the inner circumferential wall of the air guide ring 2 can define the bottom of the grooves 22; alternatively, the grooves 22 can be recessed outward relative to the inner circumferential wall of the air guide ring 2. The large size difference between the grooves 22 and the ribs 21 can increase the complexity of the structure at the blade tip gap 3, and can further increase the flow resistance of the airflow when flowing in the blade tip gap 3, thereby reducing leakage losses.

[0093] In some embodiments of the present invention, Figure 3 and Figure 5 As shown, the ratio of the axial dimensions L of two adjacent ribs 21 (e.g. Figure 3 L1 / L2, or L2 / L1) is 0.1 to 10, and the ratio of the axial dimension L of the rib 21 to the diameter D of the impeller 1 (e.g. Figure 3 L1 / D, or L2 / D) is 0.005 to 0.1, and the ratio of the radial protrusion height H of the rib 21 to the diameter D of the impeller 1 (e.g. Figure 3 H1 / D, or H2 / D) is 0.001 to 0.02.

[0094] The ratio of the difference between the axial dimensions of adjacent ribs 21 to the axial dimension of a single rib 21 is 0.1 to 10. The ratio of the axial dimensions of two adjacent ribs 21 can be relatively flexible. By setting the ribs 21 to different axial dimensions, noise of different frequencies can be reduced, which is beneficial to reducing the working noise of the axial flow wind wheel 100 and improving the scope of application.

[0095] The ratio of the radial protrusion height H of the rib 21 to the diameter D of the impeller 1 is 0.0001 to 0.02. The radial protrusion height of the rib 21 is the radial distance from any cylindrical surface S1, concentric with the hub 11 and extending through the air guide ring 2, to the cylindrical surface S1. The radial protrusion height H of the rib 21 is relatively small relative to the diameter D of the impeller 1. While not affecting the air-guiding function of the impeller 1, the provision of the rib 21 increases the flow resistance within the blade tip gap 3, thereby reducing leakage from the blade tip gap 3 and minimizing leakage losses, thereby improving the aerodynamic efficiency of the axial flow impeller 100.

[0096] The ratio of the axial dimension L of the rib 21 to the diameter D of the impeller 1 is 0.001 to 0.1. The axial dimension L of the rib 21 is relatively small relative to the diameter D of the impeller 1. While not affecting the airflow guiding function of the impeller 1, the provision of the rib 21 can increase the flow resistance within the blade tip gap 3, thereby reducing the amount of air leakage from the blade tip gap 3, reducing leakage losses, and thus improving the aerodynamic efficiency of the axial flow impeller 100.

[0097] Illustratively, the ratio of the axial dimensions L of two adjacent ribs 21 is 0.1, 0.4, 0.8, 1, 2, 4, 6, 8, 10, etc.

[0098] For example, the ratio of the axial dimension of the rib 21 to the diameter D of the impeller 1 may be 0.005, 0.01, 0.02, 0.05, 0.08, etc.

[0099] For example, the ratio of the radial protrusion height of the rib 21 to the diameter D of the wheel 1 may be 0.0002, 0.001, 0.005, 0.01, 0.012, etc.

[0100] In some embodiments of the present invention, Figure 3 As shown, the multiple ribs 21 are divided into a first rib 211 and a second rib 212 arranged axially along the air guide ring 2, the axial dimension L1 of the first rib 211 is greater than the axial dimension L2 of the second rib 212, and the radial protrusion height H1 of the first rib 211 is greater than or equal to the radial protrusion height H2 of the second rib 212.

[0101] When the impeller 1 rotates, the blades 12 periodically pass through fixed positions, generating low-frequency noise. When noise of the same frequency is superimposed on each other, the overall noise level is significantly increased. Therefore, by designing the axial dimension L1 of the first rib 211 and the axial dimension L2 of the second rib 212 to different values, the BPF (blade 12 pass frequency) is staggered, which can reduce the BPF superposition of low-frequency noise and alleviate the low-frequency noise problem.

[0102] Optionally, the radial protrusion height H1 of the first rib 211 is greater than the radial protrusion height H2 of the second rib 212, which can increase the complexity of the structure at the blade tip gap 3 and further increase the flow resistance of the airflow when flowing in the blade tip gap 3, so as to reduce leakage loss; or, also optionally, the radial protrusion height H1 of the first rib 211 is equal to the radial protrusion height H2 of the second rib 212, which is conducive to reducing the manufacturing difficulty.

[0103] In some embodiments of the present invention, Figure 3 As shown, the first ribs 211 and the second ribs 212 are alternately arranged one by one along the axial direction of the air guide ring 2 .

[0104] Alternating the first ribs 211 and the second ribs 212 with different axial sizes helps to improve the superposition of BPF (blade 12 passing frequency) of low-frequency noise, and helps to reduce the working noise of the axial flow wind wheel 100.

[0105] It is understandable that the technical solution of the present invention is not limited to this. It is also possible to arrange one or more second ribs 212 after a plurality of first ribs 211 are arranged in series, and then arrange a plurality of first ribs 211 in sequence; it is also possible to arrange one or more first ribs 211 after a plurality of second ribs 212 are arranged in series, and then arrange a plurality of second ribs 212 in sequence.

[0106] In other embodiments of the present invention, the plurality of ribs 21 have a plurality of axial dimensions. Exemplarily, the axial dimensions of all the ribs 21 are different; or, further exemplary, the plurality of ribs 21 include several ribs 21 with the same axial dimensions.

[0107] By providing the ribs 21 with multiple axial dimensions, the frequencies of the BPF (passing frequency of the blades 12 ) are staggered, which can improve the BPF superposition of low-frequency noise and help reduce the operating noise of the axial flow impeller 100 .

[0108] Furthermore, the ribs 21 of different axial sizes are beneficial to reducing noises of different frequencies. By setting the ribs 21 to different axial sizes, noises of various frequencies can be reduced, which is beneficial to reducing the operating noise of the axial flow impeller 100.

[0109] In some embodiments of the present invention, Figure 1 and Figure 2 As shown, the rib 21 is formed as an annular rib extending along the entire circumference of the air guide ring 2 .

[0110] The ribs 21 are annular ribs that surround the entire circumference. The ribs 21 of the entire circle can increase the flow resistance of the airflow when it flows at any point in the blade tip gap 3, thereby reducing leakage losses.

[0111] In other embodiments of the present invention, the rib 21 includes a plurality of arc-shaped sub-ribs arranged at circumferential intervals along the air guide ring 2, and the circumferential spacing between adjacent sub-ribs is less than the circumferential length of the sub-ribs; the ends of two ribs 21 arranged at radial intervals can be aligned or spaced circumferentially.

[0112] According to the second embodiment of the present invention, the wind turbine 1000 is as follows: Figure 6 As shown, it includes a motor 200 and an axial flow wind wheel 100 according to the first embodiment of the present invention. The motor and the axial flow wind wheel 100 are connected to drive the axial flow wind wheel 100 to move.

[0113] According to the wind turbine 1000 of the present invention, the axial flow wind wheel 100 according to the first aspect is provided, thereby improving the working efficiency of the wind turbine 1000.

[0114] According to the third aspect of the present invention, the top air outlet component 10000 is as follows: Figure 7 and Figure 8 As shown, it includes a heat exchanger 2000 and a fan 1000 according to an embodiment of the second aspect of the present invention. The fan 1000 is arranged above the heat exchanger 2000, the axis of the fan 1000 is vertical and the outlet is upward, and the top of the top air outlet component 10000 has an air outlet 5000.

[0115] The fan 1000 is arranged above the heat exchanger 2000 and discharges air from the upper end of the top air outlet component 10000. Therefore, the fan 1000 is located downstream of the heat exchanger 2000, and the axis of the fan 1000 extends in the vertical direction. The fan 1000 draws the air flow from bottom to top through the heat exchanger 2000 and sends it out from the air outlet 5000 at the top of the top air outlet component 10000, which can speed up the heat exchange of the heat exchanger 2000.

[0116] According to the top air outlet component 10000 of the present invention, by providing the fan 1000 of the second aspect, the air flow is driven to flow through the heat exchanger 2000, which is beneficial to improving the heat exchange efficiency of the heat exchanger 2000.

[0117] In some embodiments of the present invention, Figure 9 As shown, the air guide ring 2 and the orthographic projection of the heat exchanger 2000 on the horizontal plane intersect.

[0118] The air guide ring 2 of the axial flow wind wheel 100 overlaps with the orthographic projection of the heat exchanger 2000 on the horizontal plane, so that the sizes of the axial flow wind wheel 100 and the heat exchanger 2000 are close. The air volume driven by the axial flow wind wheel 100 can meet the heat exchange requirements of the heat exchanger 2000, which is beneficial to improving the working stability of the top air outlet component 10000.

[0119] Because the orthographic projections of the air guide ring 2 of the axial-flow impeller 100 and the heat exchanger 2000 on the horizontal plane overlap, the outline dimensions of the heat exchanger 2000 are similar to those of the fan 1000 (their shapes need not be similar). As a result, airflow from the edge of the heat exchanger 2000 to the fan 1000 is prone to turbulence and noise. However, by providing the fan 1000 according to the second aspect, the airflow noise of the fan 1000 is low, which helps reduce the airflow noise generated by the airflow from the heat exchanger 2000 to the fan 1000. This improves the airflow effect while reducing the operating noise of the top air outlet component 10000.

[0120] The ribs 21 are provided at least on the inner circumferential wall of the air guide ring 2, where the tip clearances 3 are formed with the blades 12. For example, the air guide ring 2 may comprise a straight cylindrical ring of uniform diameter, the impeller 1 being disposed within the straight cylindrical ring, and the tip clearances 3 being formed between the blades 12 and the inner circumferential wall of the straight cylindrical ring. Therefore, the ribs 21 may be provided at least on the inner circumferential wall of the straight cylindrical ring. For example, the air guide ring 2 may consist solely of a straight cylindrical ring. In another example, the air guide ring 2 may consist of both a straight cylindrical ring and a flared ring, with the flared ring connected to one axial end of the straight cylindrical ring and having a gradually increasing diameter.

[0121] In some embodiments of the present invention, Figure 8 and Figure 9 As shown, heat exchanger 2000 includes a plate-shaped heat exchange section 2001. On a horizontal projection plane, the ratio of the perpendicular distance L3 from the center of air guide ring 2 to heat exchange section 2001 to the inner radius R1 of air guide ring 2 is 0.8 to 1. The "inner ring of air guide ring 2" refers to the inner ring of the aforementioned straight cylindrical ring, and the outer ring of air guide ring 2 refers to the outer ring of the straight cylindrical ring.

[0122] "Plate-shaped" can be a flat plate or a curved plate. For example, when the heat exchange section 2001 is flat, the heat exchanger 2000 may include one heat exchange section 2001. The heat exchanger 2000 may also include multiple plate-shaped heat exchange sections 2001. For example, Figure 9 As shown, the heat exchanger 2000 includes a plurality of heat exchange sections 2001, which are sequentially connected to form a ring with a gap, such as a U-shape, an open U-shape, etc. For example, when the heat exchange section 2001 is a curved plate, the heat exchanger 2000 as a whole can be arc-shaped, etc.

[0123] On a horizontal projection plane, the ratio of the perpendicular distance L3 from the center of the air guide ring 2 to the heat exchange section 2001 to the inner radius R1 of the air guide ring 2 is 0.8 to 1. Therefore, the perpendicular distance L3 from the center of the air guide ring 2 to the heat exchange section 2001 is smaller than the inner radius R1 of the air guide ring 2. The airflow flowing out from the inner side of the heat exchanger 2000 can be completely gathered by the air guide ring 2, thereby improving the heat exchange efficiency of the heat exchanger 2000. The heat exchanger 2000 has a certain thickness, so that the orthographic projections of the air guide ring 2 and the heat exchanger 2000 on the horizontal plane intersect.

[0124] For example, the ratio of the vertical distance L3 from the center of the air guide ring 2 to the heat exchange section 2001 to the inner circle radius R1 of the air guide ring 2 can be 0.82, 0.85, 0.9, 0.95, 0.99, etc.

[0125] In some embodiments of the present invention, Figure 9 As shown, the ratio of the vertical distance L4 from the center of the air guide ring 2 to the outer contour of the heat exchange section 2001 to the inner circle radius R1 of the air guide ring 2 on the horizontal projection plane is 0.96-1.2.

[0126] Depending on the size of the heat exchange section 2001, the perpendicular distance L4 from the center of the air guide ring 2 to the outer contour of the heat exchange section 2001 can be greater than or less than the inner radius R1 of the air guide ring 2. The perpendicular distance from the center of the air guide ring 2 to the outer contour of the heat exchange section 2001 can be greater than the inner radius R1 of the air guide ring 2 to ensure that the orthographic projections of the air guide ring 2 and the heat exchanger 2000 on the horizontal plane intersect. The perpendicular distance from the center of the air guide ring 2 to the outer contour of the heat exchange section 2001 can also be less than the inner radius R1 of the air guide ring 2 to meet the assembly requirements of the heat exchanger 2000.

[0127] In some embodiments of the present invention, Figure 10 As shown, the ratio of the inner circle radius R1 of the air guide ring 2 to the outer circle radius R2 of the air guide ring 2 is 0.92 to 0.98.

[0128] When the ratio of the inner and outer circle radii of the air guide ring 2 is too large, the wind flow area of ​​the air guide ring 2 occupies a smaller overall volume, reducing the air outlet efficiency; when the ratio of the inner and outer circle radii of the air guide ring 2 is too small, the structural stability of the air guide ring 2 is poor, which is not conducive to the stable operation of the air guide ring 2.

[0129] Therefore, the optimal ratio of the inner radius R1 of the air guide ring 2 to the outer radius R2 of the air guide ring 2 is designed to be 0.92-0.98, which can increase the wind flow area of ​​the air guide ring 2, improve the air outlet efficiency, and the structural stability of the air guide ring 2 is relatively strong.

[0130] In some embodiments of the present invention, Figure 8 and Figure 9 As shown, the top air outlet component also includes a mounting frame 4000, which is arranged above the heat exchanger 2000. The mounting frame 4000 includes a frame 41 and a support rod 42. The frame 41 defines an air passage 41a that passes through in the up and down directions. The support rod 42 is connected to the frame 41 and is vertically opposite to the air passage 41a; the fan 1000 is arranged above the mounting frame 4000, the motor 200 is located below the axial flow wind wheel 100, and the motor 200 is fixedly connected to the support rod 42, and the air guide ring 2 is fixedly connected to the frame 41.

[0131] The mounting frame 4000 plays a supporting role. The fan 1000 is installed on the mounting frame 4000. The impeller 1 and the air guide ring 2 are fixedly connected to the mounting frame 4000 respectively, which can improve the installation stability of the axial flow wind wheel 100 and ensure the relative position relationship between the impeller 1 and the air guide ring 2, thereby ensuring that the blade tip clearance 3 meets the design requirements, which can improve the working reliability and aerodynamic performance of the axial flow wind wheel 100.

[0132] The mounting frame 4000 includes a frame 41 at its edge, which defines a vertically extending air passage 41a. A support rod 42 is connected to the frame 41 and extends toward the center of the mounting frame 4000. The support rod 42 can be positioned within the air passage 41a, above, or below the air passage 41a. The provision of the support rod 42 reduces airflow obstruction while facilitating the placement of the axial flow impeller 100, thereby facilitating airflow.

[0133] In some embodiments of the present invention, there are multiple support rods 42 and they extend from multiple sides of the frame 41 to the middle of the mounting frame 4000. The motor 200 is fixedly connected to the multiple support rods 42, which can improve the layout stability of the motor 200.

[0134] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "vertical", "horizontal", "top", "bottom", "inside", "outside", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0135] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature identified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.

[0136] In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, they may refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection, or communication; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0137] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0138] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representations of the above terms do 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. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification and features of different embodiments or examples without contradiction.

[0139] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. An axial flow wind wheel, characterized in that: include: An impeller, the impeller comprising a hub and a plurality of blades, wherein the plurality of blades are arranged along the circumference of the hub and connected to the hub; An air guide ring surrounds the impeller, and an inner peripheral wall of the air guide ring is formed with ribs, and the ribs extend along the circumference of the air guide ring.

2. The axial flow wind wheel according to claim 1, characterized in that: There are multiple ribs arranged along the axial direction of the air guide ring, and grooves are defined between adjacent ribs.

3. The axial flow wind wheel according to claim 2, characterized in that: There are multiple grooves and they are arranged along the axial direction of the air guide ring.

4. The axial flow wind wheel according to claim 2, characterized in that: At least part of the blade top is constructed as a concave-convex portion, which is formed as an inner concave portion corresponding to the rib and an outer convex portion corresponding to the groove, and the outer convex portion protrudes relative to the inner concave portion toward the air guide ring.

5. The axial flow wind wheel according to claim 4, characterized in that: There are multiple grooves arranged along the axial direction of the air guide ring, and the outer convex parts and the inner concave parts are arranged in a one-to-one correspondence.

6. The axial flow wind wheel according to claim 5, characterized in that: At least a portion of the convex portion extends into the groove.

7. The axial flow wind wheel according to claim 5, characterized in that: On the axial cross-section of the axial flow wind wheel, the inner concave portion matches the shape of the convex rib and the gap is uniform, the outer convex portion matches the shape of the groove and the gap is uniform, and the gap between the inner concave portion and the convex rib is consistent with the gap between the outer convex portion and the groove.

8. The axial flow wind wheel according to claim 5, characterized in that: On the axial cross section of the axial flow impeller, the ratio of the gap between the concave-convex portion and the air guide ring to the diameter of the impeller is 0.005 to 0.

01.

9. The axial flow wind wheel according to claim 8, characterized in that: More than half of the length of the blade tip from the trailing edge of the blade to the leading edge of the blade is configured as the concave-convex portion, and the concave-convex portion is arranged closer to the trailing edge of the blade relative to the leading edge of the blade.

10. The axial flow wind wheel according to any one of claims 2 to 9, characterized in that: On the axial cross section of the axial flow wind wheel, the contour line of the rib is formed as an arc line protruding toward the impeller.

11. The axial flow wind wheel according to claim 10, characterized in that: The plurality of ribs are continuously arranged along the axial direction of the air guide ring.

12. The axial flow wind wheel according to claim 11, characterized in that: The ratio of the axial dimensions of two adjacent ribs is 0.1-10, the ratio of the axial dimension of the rib to the diameter of the impeller is 0.001-0.1, and the ratio of the radial protruding height of the rib to the diameter of the impeller is 0.001-0.

02.

13. The axial flow wind wheel according to claim 11, characterized in that: The multiple ribs are divided into first ribs and second ribs arranged along the axial direction of the air guide ring, the axial size of the first rib is larger than the axial size of the second rib, and the radial protrusion height of the first rib is greater than or equal to the radial protrusion height of the second rib.

14. The axial flow wind wheel according to claim 1, characterized in that: The convex rib is formed as an annular convex rib extending along the entire circumference of the air guide ring.

15. A fan, characterized in that: include: A motor and an axial flow wind wheel according to any one of claims 1 to 14, wherein the motor is connected to the axial flow wind wheel to drive the axial flow wind wheel to move.

16. A top air outlet component, characterized in that: include: A heat exchanger and a fan according to claim 15, wherein the fan is arranged above the heat exchanger, the axis of the fan is vertical and the outlet is upward, and the top of the top air outlet component has an air outlet.

17. The air ejection component according to claim 16, characterized in that: The air guide ring and the orthographic projection of the heat exchanger on the horizontal plane intersect.

18. The air ejection component according to claim 17, characterized in that: The heat exchanger includes a plate-shaped heat exchange section. On a horizontal projection plane, the ratio of the vertical distance from the center of the air guide ring to the heat exchange section to the inner circle radius of the air guide ring is 0.8 to 1; or, the ratio of the vertical distance from the center of the air guide ring to the outer contour of the heat exchange section to the inner circle radius of the air guide ring is 0.96 to 1.

2.

19. The air ejection component according to claim 18, characterized in that: The heat exchanger further comprises a mounting frame, the mounting frame being arranged above the heat exchanger, the mounting frame comprising a frame and a support rod, the frame defining an air passage extending vertically therethrough, the support rod being connected to the frame and vertically opposite to the air passage; The fan is arranged above the mounting frame, the motor is located below the axial flow wind wheel, the motor is fixedly connected to the support rod, and the air guide ring is fixedly connected to the frame.

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