Axial flow fan and air conditioner

Abstract

The application discloses an axial flow fan and an air conditioner, and relates to the technical field of air conditioners. The axial flow fan comprises a hub and a plurality of blades. The plurality of blades are fixedly connected to the circumferential surface of the hub in a ring array. The blades are oppositely provided with leading edges and trailing edges. The trailing edges are provided with notches which are recessed towards the leading edges. The notches are provided with vertices near the leading edges. The perpendicular line of the connecting line of the vertex and the midpoint of the hub intersects with the leading edge of the adjacent blade. Compared with the prior art, the axial flow fan provided by the application can improve the uniformity of the air flow, reduce the material cost, reduce the energy consumption and improve the air volume while reducing the weight of the axial flow fan due to the notches provided on the trailing edges and the vertices provided near the leading edges of the notches.

Description

Technical Field

[0001] This invention relates to the field of air conditioning technology, and in particular to an axial flow impeller and an air conditioner. Background Technology

[0002] Currently, in the application of air conditioner outdoor units, airflow is generally generated by driving an axial fan to rotate via a drive motor, thereby cooling the condenser and expelling the heat from the condenser to the outside. However, current axial fan impellers are relatively heavy, have high material costs, and consume a lot of energy. Furthermore, the airflow generated by the rotation of the axial fan is not uniform and has a small air volume. Summary of the Invention

[0003] The problem solved by this invention is how to improve the uniformity of the exhaust airflow, reduce material costs, reduce energy consumption, and increase the exhaust volume while reducing the weight of the axial flow impeller.

[0004] To solve the above problems, the technical solution of the present invention is implemented as follows:

[0005] In a first aspect, the present invention provides an axial flow impeller, comprising a hub and multiple blades. The multiple blades are fixedly connected to the circumferential surface of the hub in a circular array. Each blade has a leading edge and a trailing edge opposite to each other. The trailing edge has a notch recessed towards the leading edge, and the notch has a vertex near the leading edge. The perpendicular line connecting the vertex of one blade to the midpoint of the hub intersects the leading edge of the adjacent blade. Compared with the prior art, the axial flow impeller provided by the present invention, due to the notch on the trailing edge and the vertex located near the leading edge of the notch, can improve the uniformity of the outlet airflow while reducing the weight of the axial flow impeller, reducing material costs, reducing energy consumption, and increasing the air volume.

[0006] Furthermore, an endpoint is provided at the end of the leading edge furthest from the hub, and the perpendicular line connecting the vertex of one blade to the midpoint of the hub passes through the endpoint of the adjacent blade. This is to minimize the blade area while ensuring airflow convergence, reduce the weight of the axial flow impeller, and improve the uniformity of the outlet airflow.

[0007] Furthermore, the blades have inner and outer edges positioned opposite each other. The inner edge is connected to the hub, and the endpoint is the intersection of the outer edge and the leading edge. During blade rotation, the endpoint comes into contact with the air first, causing the airflow to flow from the leading edge to the blades.

[0008] Furthermore, the distance between the vertex of a blade and the endpoint of an adjacent blade ranges from 150 mm to 180 mm. A reasonable distance between the vertex of a blade and the endpoint of an adjacent blade can maximize the area of ​​the notch while ensuring the gathering effect, thereby reducing the weight of the axial flow impeller, lowering material costs, and reducing energy consumption.

[0009] Furthermore, the distance between the vertex of one blade and the endpoint of the adjacent blade is 165 mm.

[0010] Furthermore, on the orthographic projection plane of the axial flow impeller, with the midpoint of the hub as the center, the central angle of the arc formed between the vertex of one blade and the leading edge of an adjacent blade ranges from 45 degrees to 60 degrees. A reasonable central angle of the arc formed between the vertex of one blade and the leading edge of an adjacent blade can improve the effect of the leading edge of the blade in gathering the airflow exiting from the notch, thereby increasing the air volume.

[0011] Furthermore, on the orthographic projection plane of the axial flow wind turbine, with the midpoint of the hub as the center, the central angle of the arc formed between the vertex of one blade and the leading edge of the adjacent blade is 52 degrees.

[0012] Furthermore, the gap is designed in a V-shape. The V-shaped gap can guide the direction of airflow and improve the stability of airflow.

[0013] Furthermore, there are three blades, arranged in a circular array on the circumference of the hub. The hub can simultaneously drive all three blades to rotate, thereby creating an airflow.

[0014] Secondly, the present invention provides an air conditioner including the aforementioned axial flow impeller. The axial flow impeller includes a hub and multiple blades. The multiple blades are fixedly connected to the circumferential surface of the hub in a circular array. Each blade has a leading edge and a trailing edge opposite to each other. The trailing edge has a notch recessed towards the leading edge, and the notch has a vertex near the leading edge. The perpendicular line connecting the vertex of one blade to the midpoint of the hub intersects the leading edge of an adjacent blade. This air conditioner can improve the uniformity of the airflow while reducing the weight of the axial flow impeller, reducing material costs, reducing energy consumption, and increasing air volume. Attached Figure Description

[0015] Figure 1 This is an axonometric view of the axial flow wind turbine described in the first embodiment of the present invention;

[0016] Figure 2 This is a left view of the axial flow fan wheel described in the first embodiment of the present invention;

[0017] Figure 3 This is a top view of the axial flow fan wheel described in the first embodiment of the present invention;

[0018] Figure 4 This is a mathematical model diagram of the axial flow wind turbine described in the first embodiment of the present invention.

[0019] Explanation of reference numerals in the attached figures:

[0020] 100-Axial flow wind turbine; 110-Hub; 120-Blade; 121-Leading edge; 122-Tail edge; 123-Inner edge; 124-Outer edge; 125-Notch; 126-First groove; 127-Second groove; 128-Folded edge. Detailed Implementation

[0021] To make the above-mentioned objects, features and advantages of the present invention more apparent and understandable, specific embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

[0022] First Embodiment

[0023] Please refer to the reference. Figure 1 and Figure 2 This invention provides an axial flow impeller 100 for driving airflow. It can reduce the weight of the axial flow impeller 100 while improving the uniformity of the outlet airflow, reducing material costs, reducing energy consumption, and increasing the air volume.

[0024] It should be noted that the axial fan 100 is used in the outdoor unit of an air conditioner (not shown). The outdoor unit is installed outdoors and connected to the indoor unit (not shown). The outdoor and indoor units work together to regulate the indoor temperature. The outdoor unit includes a condenser (not shown), a drive motor (not shown), and a casing (not shown). The condenser, drive motor, and axial fan 100 are all installed inside the casing. The drive motor is connected to the axial fan 100 to rotate it. The position of the axial fan 100 corresponds to the position of the condenser, which is used for heat exchange with the refrigerant. The axial fan 100 can generate negative pressure during rotation, driving airflow to form an outlet airflow. This outlet airflow is used to cool the condenser, removing heat and ensuring its normal operation.

[0025] The axial flow impeller 100 includes a hub 110 and multiple blades 120. The hub 110 is cylindrical, and the multiple blades 120 are fixedly connected to the circumference of the hub 110 in a ring array. The hub 110 can drive the blades 120 to rotate, thereby driving airflow. The hub 110 is used to connect to a drive motor, which can drive the blades 120 to rotate through the hub 110.

[0026] In this embodiment, there are three blades 120 arranged in a circular array on the circumference of the hub 110. The hub 110 can simultaneously drive the three blades 120 to rotate, thereby creating an airflow. However, this is not the only embodiment. In other embodiments, the number of blades 120 can be four or five, and the number of blades 120 is not specifically limited.

[0027] Please refer to the reference. Figure 3 and Figure 4 It should be noted that the blade 120 is provided with a leading edge 121, a trailing edge 122, an inner edge 123, and an outer edge 124. The leading edge 121 and the trailing edge 122 are arranged opposite each other, and the inner edge 123 and the outer edge 124 are arranged opposite each other. The leading edge 121, the outer edge 124, the trailing edge 122, and the inner edge 123 are connected end to end to form the outline shape of the blade 120. Specifically, the inner edge 123 is the side of the blade 120 that connects to the hub 110, the outer edge 124 is the side of the blade 120 away from the hub 110, the leading edge 121 is the side of the blade 120 facing the wind during rotation, and the trailing edge 122 is the side of the blade 120 on the leeward side during rotation.

[0028] It is worth noting that the trailing edge 122 has a notch 125 recessed towards the leading edge 121. This notch 125 can reduce the weight of the axial flow impeller 100, reduce material costs, and reduce energy consumption. The notch 125 has a vertex near the leading edge 121. This vertex is the deepest point of the notch 125, the closest point on the sidewall of the notch 125 to the leading edge 121, and also the farthest point on the sidewall of the notch 125 from the trailing edge 122. Specifically, the perpendicular line connecting the vertex of one blade 120 to the midpoint of the hub 110 intersects the leading edge 121 of the adjacent blade 120. This ensures that the airflow exiting from the notch 125 of one blade 120 can be gathered back by the leading edge 121 of the adjacent blade 120, improving the uniformity of the outlet airflow and increasing the outlet volume.

[0029] In this embodiment, the notch 125 is V-shaped, with the pointed end of the notch 125 pointing in the same direction as the rotation of the blade 120, i.e., from the trailing edge 122 to the leading edge 121. The V-shaped notch 125 can guide the airflow direction and improve the stability of the airflow. During the rotation of the blade 120, airflow forms an exhaust airflow along the surface of the blade 120, flowing from the leading edge 121 to the trailing edge 122. During this process, part of the exhaust airflow flows out through the notch 125 and is gathered back by the next blade 120. However, this is not the only embodiment; in other embodiments, the notch 125 can also be W-shaped or U-shaped, and the shape of the notch 125 is not specifically limited.

[0030] It should be noted that the end of the leading edge 121 away from the hub 110 is provided with an endpoint. The perpendicular line of the line connecting the vertex of a blade 120 and the midpoint of the hub 110 passes through the endpoint of an adjacent blade 120. This is to minimize the area of ​​the blade 120 while ensuring the airflow gathering effect, reduce the weight of the axial flow impeller 100, and improve the uniformity of the outlet airflow.

[0031] In this embodiment, the inner edge 123 is connected to the hub 110, and its endpoint is the intersection of the outer edge 124 and the leading edge 121. The endpoint is the point on the outer edge 124 that is farthest from the trailing edge 122, and also the point on the leading edge 121 that is farthest from the inner edge 123. Specifically, during the rotation of the blade 120, the endpoint is the first to come into contact with the air, so that the airflow flows from the leading edge 121 to the blade 120.

[0032] Furthermore, the distance between the vertex of one blade 120 and the endpoint of the adjacent blade 120 ranges from 150 mm to 180 mm. A reasonable distance between the vertex of one blade 120 and the endpoint of the adjacent blade 120 can maximize the area of ​​the notch 125 while ensuring the gathering effect, thereby reducing the weight of the axial flow impeller 100, reducing material costs, and reducing energy consumption.

[0033] In this embodiment, the distance between the vertex of one blade 120 and the endpoint of an adjacent blade 120 is 165 mm. However, it is not limited to this. In other embodiments, the distance between the vertex of one blade 120 and the endpoint of an adjacent blade 120 can be 150 mm or 180 mm. There is no specific limitation on the distance between the vertex of one blade 120 and the endpoint of an adjacent blade 120.

[0034] It is worth noting that on the orthographic projection plane of the axial flow impeller 100, with the midpoint of the hub 110 as the center, the central angle of the arc formed between the vertex of a blade 120 and the leading edge 121 of an adjacent blade 120 ranges from 45 degrees to 60 degrees. A reasonable central angle of the arc formed between the vertex of a blade 120 and the leading edge 121 of an adjacent blade 120 can improve the effect of the leading edge 121 of the blade 120 on the airflow flowing out from the notch 125, thereby increasing the air volume.

[0035] In this embodiment, on the orthographic projection plane of the axial flow wind turbine 100, with the midpoint of the hub 110 as the center, the central angle of the arc formed between the vertex of a blade 120 and the leading edge 121 of an adjacent blade 120 is 52 degrees. However, it is not limited to this. In other embodiments, the central angle of the arc formed between the vertex of a blade 120 and the leading edge 121 of an adjacent blade 120 can be 45 degrees or 60 degrees. There is no specific limitation on the central angle of the arc formed between the vertex of a blade 120 and the leading edge 121 of an adjacent blade 120.

[0036] For ease of understanding, the vertex of blade 120 is named a, the endpoint of blade 120 is named b, the midpoint of hub 110 is named o, the distance between the vertex of one blade 120 and the endpoint of the adjacent blade 120 is denoted as H, and the central angle of the arc formed between the vertex of one blade 120 and the leading edge 121 of the adjacent blade 120 is denoted as C.

[0037] It is worth noting that the blade 120 has multiple first grooves 126 and multiple second grooves 127. The first grooves 126 are located near the trailing edge 122, and the first grooves 126 are circular. The multiple first grooves 126 are densely distributed in a dot-like pattern, which is flexible in layout to solve the problem of vortex concentration on the blade 120. The second grooves 127 are located near the leading edge 121, and the groove walls between the multiple second grooves 127 are distributed on the blade 120 in a leaf vein pattern. The groove walls between two adjacent second grooves 127 form a V-shape to better guide the airflow from the leading edge 121 of the blade 120 to the trailing edge 122 of the blade 120, and send the airflow to the next blade 120, thereby realizing the function of rectifying the airflow and reducing the noise generated by the blade 120 during rotation.

[0038] In this embodiment, the outer edge 124 is provided with a folded edge 128. The folded edge 128 can improve the strength of the outer edge 124, thereby improving the strength of the entire blade 120, preventing the blade 120 from deforming or bending. In addition, the folded edge 128 can also limit the airflow to prevent the airflow from escaping outward and ensure the air volume.

[0039] The axial flow impeller 100 of this invention has multiple blades 120 fixedly connected to the circumferential surface of a hub 110 in a circular array. Each blade 120 has a leading edge 121 and a trailing edge 122 opposite to each other. The trailing edge 122 has a notch 125 recessed towards the leading edge 121. The notch 125 has a vertex near the leading edge 121. The perpendicular line connecting the vertex of one blade 120 to the midpoint of the hub 110 intersects the leading edge 121 of the adjacent blade 120. Compared with the prior art, the axial flow impeller 100 provided by this invention, due to the notch 125 on the trailing edge 122 and the vertex located near the leading edge 121 of the notch 125, can improve the uniformity of the outlet airflow while reducing the weight of the axial flow impeller 100, reducing material costs, reducing energy consumption, and increasing the air volume.

[0040] Second Embodiment

[0041] This invention provides an air conditioner (not shown) for regulating indoor temperature. The air conditioner includes an outdoor unit and an indoor unit, with the outdoor unit comprising a casing, a condenser, a drive motor, and an axial flow fan 100. The basic structure, principle, and technical effects of the axial flow fan 100 are the same as in the first embodiment. For brevity, any parts not mentioned in this embodiment can be referred to the corresponding content in the first embodiment.

[0042] In this embodiment, the outdoor unit of the air conditioner is installed outdoors and connected to the indoor unit. The outdoor and indoor units work together to regulate the indoor temperature. The condenser, drive motor, and axial fan 100 are all installed inside the casing. The drive motor is connected to the axial fan 100, and the position of the axial fan 100 corresponds to the position of the condenser. The axial fan 100 can generate negative pressure during rotation, driving airflow to form an exhaust airflow. This exhaust airflow can cool the condenser, removing heat and ensuring its normal operation, thereby enabling the indoor unit to heat or cool the room.

[0043] The beneficial effects of the air conditioner described in this embodiment are the same as those of the first embodiment, and will not be repeated here.

[0044] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. An axial flow impeller, characterized in that, The device includes a hub (110) and multiple blades (120). The multiple blades (120) are fixedly connected to the circumferential surface of the hub (110) in a ring array. Each blade (120) has a leading edge (121) and a trailing edge (122) opposite to each other. The trailing edge (122) has a notch (125) that is recessed toward the leading edge (121). The notch (125) has a vertex near the leading edge (121). The perpendicular line of the line connecting the vertex of one blade (120) to the midpoint of the hub (110) intersects the leading edge (121) of the adjacent blade (120). The leading edge (121) is provided with an endpoint at one end away from the hub (110), and the perpendicular line of the line connecting the vertex of one blade (120) and the midpoint of the hub (110) passes through the endpoint of an adjacent blade (120); The blade (120) has an inner edge (123) and an outer edge (124) opposite to each other. The inner edge (123) is connected to the hub (110), and the endpoint is the intersection of the outer edge (124) and the leading edge (121).

2. The axial flow impeller according to claim 1, characterized in that, The distance between the vertex of one blade (120) and the endpoint of the adjacent blade (120) ranges from 150 mm to 180 mm.

3. The axial flow impeller according to claim 2, characterized in that, The distance between the vertex of one blade (120) and the endpoint of the adjacent blade (120) is 165 mm.

4. The axial flow impeller according to claim 1, characterized in that, On the orthographic projection plane of the axial flow wind turbine, with the midpoint of the hub (110) as the center, the central angle of the arc formed between the vertex of one blade (120) and the leading edge (121) of the adjacent blade (120) ranges from 45 degrees to 60 degrees.

5. The axial flow impeller according to claim 4, characterized in that, On the orthographic projection plane of the axial flow wind turbine, with the midpoint of the hub (110) as the center, the central angle of the arc formed between the vertex of one blade (120) and the leading edge (121) of the adjacent blade (120) is 52 degrees.

6. The axial flow impeller according to claim 1, characterized in that, The notch (125) is V-shaped.

7. The axial flow impeller according to claim 1, characterized in that, The number of blades (120) is three, and the three blades (120) are arranged in a ring array on the circumferential surface of the hub (110).

8. An air conditioner, characterized in that, Including the axial flow wind turbine as described in any one of claims 1 to 7.

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