Centrifugal wind wheel, fan assembly and air conditioner

Abstract

The utility model discloses a centrifugal wind wheel, a fan assembly and an air conditioner, and relates to the technical field of centrifugal fans, the centrifugal wind wheel comprises a chassis and a plurality of blades; the multiple blades are evenly distributed on the base plate around the axis of the base plate, each blade is provided with an inwards-concave face, and each inwards-concave face comprises a first arc face and a second arc face which are sequentially connected from inside to outside; wherein the distance between the inner end of the first arc surface and the axis of the base plate is L1, the distance between the outer end of the second arc surface and the axis of the base plate is L2, the distance between the intersection point of the first arc surface and the second arc surface and the axis of the base plate is L3, L1 / L2 is larger than or equal to 0.55 and smaller than or equal to 0.65, and (L3-L1) / (L2-L1) is larger than or equal to 0.6 and smaller than or equal to 0.75. The technical scheme provided by the utility model is used for reducing the flow separation condition of air flow and reducing noise.

Description

Technical Field

[0001] This utility model relates to the field of fan technology, and in particular to a centrifugal impeller, a fan assembly, and an air conditioner. Background Technology

[0002] Fresh air fan components are used to introduce fresh air from outside and improve indoor air quality. On the one hand, the fan requires high back pressure during operation because air needs to pass through long ducts and filters; on the other hand, since the fan component is located indoors, noise is a key factor affecting product performance. In existing multi-blade centrifugal fans, the impeller is mostly a single circular arc blade, and the ratio of the distance from the inner end of the blade to the impeller shaft center is relatively small. Research has found that this type of blade structure is no longer suitable for the high back pressure operating environment of fresh air fans. Therefore, innovative impeller design is needed to meet the requirements of high air volume and low noise.

[0003] Currently, in the case of multi-blade centrifugal fans used in fresh air systems, the centrifugal impellers operate under high back pressure, resulting in significant flow separation within the air duct. This restricts the ability of fresh air fans to further increase air volume and reduce noise. Utility Model Content

[0004] This utility model proposes a centrifugal impeller, a fan assembly, and an air conditioner, with the aim of reducing the noise generated when the impeller rotates.

[0005] To achieve the above objectives, this utility model proposes a centrifugal impeller, comprising:

[0006] Chassis;

[0007] Multiple blades are evenly arranged around the axis of the chassis. Each blade has a concave surface, which includes a first arc surface and a second arc surface connected sequentially from the inside to the outside.

[0008] Wherein, the distance between the inner end of the first arc surface and the axis of the chassis is L1, the distance between the outer end of the second arc surface and the axis of the chassis is L2, the distance between the intersection point of the first arc surface and the second arc surface and the axis of the chassis is L3, 0.55≦L1 / L2≦0.65, 0.6≦(L3-L1) / (L2-L1)≦0.75.

[0009] In one embodiment, the inlet angle of the blade is α, where 50° < α < 70°; and the outlet angle of the blade is β, where 160° < β < 170°.

[0010] In one embodiment, the diameter of the first arc surface is smaller than the diameter of the second arc surface.

[0011] In one embodiment, the thickness of the blade is uniform.

[0012] In one embodiment, the inner end of the blade is provided with a rounded corner.

[0013] In one embodiment, the thickness of the blade first increases and then decreases in the direction from the inner end to the outer end;

[0014] And / or, the position with the maximum thickness of the blade is located at the junction of the first arc surface and the second arc surface.

[0015] In one embodiment, an air outlet channel is formed between two adjacent blades, and the width of the inner end of the air outlet channel is greater than the width of the outer end of the air outlet channel.

[0016] In one embodiment, the width of the air outlet channel first increases and then decreases in the direction from the inner end to the outer end.

[0017] In one embodiment, the number of the blades is N, 40 < N < 60, and / or, the height of the wind wheel is H, 20 mm < H < 60 mm.

[0018] In one embodiment, the connection line between the junction of the first arc surface and the second arc surface and the axis of the chassis is A, and the inner end and the outer end of the blade are respectively located on both sides of the connection line A.

[0019] The present utility model further provides a wind wheel assembly, including the above-mentioned centrifugal wind wheel.

[0020] The present utility model further provides an air conditioner, including the above-mentioned fan assembly.

[0021] Through the structural optimization of the blade of the centrifugal wind wheel of the technical solution of the present utility model, the airflow attack angle can be improved, the occurrence of flow separation inside the wind wheel can be reduced, thereby reducing noise and enhancing the competitiveness of the product. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] In order to more clearly illustrate the technical solutions in the embodiments of the present utility model or the prior art, the following will briefly introduce the drawings required for the description of the embodiments or the prior art. Obviously, the following drawings are only some embodiments of the present utility model. For those of ordinary skill in the art, other drawings can be obtained based on the structures shown in these drawings without creative efforts.

[0023] Figure 1 It is a schematic structural view of a perspective of an embodiment of the centrifugal wind wheel provided by the present utility model;

[0024] Figure 2A schematic diagram of the structure of another embodiment of the centrifugal impeller provided by this utility model;

[0025] Figure 3 A schematic diagram of the blade structure of an embodiment of the centrifugal impeller provided by this utility model;

[0026] Figure 4 A schematic diagram of the key core assembly of another embodiment of the centrifugal impeller provided by this utility model;

[0027] Figure 5 A simulated internal velocity vector diagram of a centrifugal impeller according to an embodiment of this utility model.

[0028] Explanation of icon numbers:

[0029] 1. Centrifugal impeller; 11. Chassis; 12. Blade; 121. Concave surface; 122. First arc surface; 123. Second arc surface; 124. Rounded corner; 13. Air outlet duct. Detailed Implementation

[0030] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, and not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of the present utility model.

[0031] It should be noted that if the embodiments of this utility model involve directional indicators (such as up, down, left, right, front, back, etc.), the directional indicators are only used to explain the relative positional relationship and movement of the components in a specific posture. If the specific posture changes, the directional indicators will also change accordingly.

[0032] Furthermore, if the embodiments of this utility model involve descriptions such as "first" or "second," these descriptions are for descriptive purposes only and should not be construed as indicating or implying their relative importance or implicitly specifying the number of technical features indicated. Therefore, a feature defined with "first" or "second" may explicitly or implicitly include at least one of those features. Additionally, the use of "and / or" or "and / or" throughout the text includes three parallel solutions. For example, "A and / or B" includes solution A, solution B, or a solution where both A and B are satisfied simultaneously. Furthermore, the technical solutions of the various embodiments can be combined with each other, but this must be based on the ability of those skilled in the art to implement them. When the combination of technical solutions is contradictory or impossible to implement, it should be considered that such a combination of technical solutions does not exist and is not within the scope of protection claimed by this utility model.

[0033] Currently, there is significant flow separation within the impellers of the market, which limits the ability of fresh air fans to further increase air volume and reduce noise.

[0034] This application optimizes the centrifugal impeller, which can reduce airflow separation, further increase air volume, and reduce noise.

[0035] Please refer to Figure 1 , Figure 2 and Figure 3 As shown in the figure, an embodiment of this application provides a centrifugal impeller 1, including a chassis 11 and a plurality of blades 12. The plurality of blades 12 are evenly arranged around the axis of the chassis 11. Each blade 12 has a concave surface 121, which includes a first arc surface 122 and a second arc surface 123 connected sequentially from the inside to the outside. The distance between the inner end of the first arc surface 122 and the axis of the chassis 11 is L1, the distance between the outer end of the second arc surface 123 and the axis of the chassis 11 is L2, the distance between the inner end of the first arc surface 122 and the axis of the chassis 11 is L1, the distance between the outer end of the second arc surface 123 and the axis of the chassis 11 is L2, and the distance between the intersection point of the first arc surface 122 and the second arc surface 123 and the axis of the chassis 11 is L3. Among them, 0.55≦L1 / L2≦0.65, 0.6≦(L3-L1) / (L2-L1)≦0.75.

[0036] Specifically, the centrifugal impeller 1 is used in a centrifugal fan. The centrifugal impeller 1 is connected to a motor drive, and the rotation of the motor drives the centrifugal impeller 1 to rotate, thereby conveying the airflow from the duct to the room. The centrifugal impeller 1 includes an integrally formed chassis 11 and multiple blades 12. The chassis 11 is disc-shaped, and the multiple blades 12 are disposed on one of the two opposite end faces of the chassis 11, and the multiple blades 12 are evenly arranged around the axis of the chassis 11. Each blade 12 has a concave surface 121, which includes a first arc surface 122 and a second arc surface 123. The first arc surface 122 is connected to the second arc surface 123, and the first arc surface 122 is located near the axis of the chassis 11, while the second arc surface 123 is located near the circumference of the chassis 11. The distance between the inner end of the first arc surface 122 (i.e., the end of the first arc surface 122 near the axis of the chassis 11) and the axis of the chassis 11 is L1. The distance between the end of the second arc surface 123 (i.e., the end of the second arc surface 123 away from the axis of the chassis 11) and the axis of the chassis 11 is L2. The distance between the intersection point of the first arc surface 122 and the second arc surface 123 and the axis of the chassis 11 is L3. When L1, L2, and L3 satisfy the following conditions, the airflow angle can be improved, the internal flow separation of the impeller can be reduced, and the noise can be reduced, thereby enhancing the competitiveness of the product: 0.55≦L1 / L2≦0.65, 0.6≦(L3-L1) / (L2-L1)≦0.75.

[0037] Please refer to Figure 2 As shown, in an optional embodiment, the inlet angle of the blade 12 is α, 50° < α < 70°; the outlet angle of the blade 12 is β, 160° < β < 170°.

[0038] Specifically, the inlet angle refers to the angle between the blade 12 at the inlet of the wind turbine and the inlet direction, also known as the blade 12 inlet installation angle. The outlet angle refers to the angle between the blade 12 at the outlet of the wind turbine and the outlet direction, also known as the blade 12 outlet installation angle. The inlet and outlet angles are identical for each blade 12. The inlet angle directly affects the air intake of the wind turbine, thus influencing the turbine's performance curve. A suitable inlet angle ensures smooth airflow into the wind turbine, reducing energy loss. A too-small inlet angle leads to decreased flow rate and increased pressure. The outlet angle determines whether the wind turbine is forward-curved, radial-curved, or backward-curved, directly affecting the turbine's performance. A too-small outlet angle may result in a decrease in the outlet head. This application sets the inlet angle α in the range of 50°-70° and the outlet angle in the range of 160°-170°. In addition, by optimizing the distance L1 between the inner end of the first arc surface and the axis of the chassis 11, the distance L2 between the outer end of the second arc surface and the axis of the chassis 11, and the distance L3 between the intersection point of the first arc surface and the second arc surface and the axis of the chassis 11, a reasonable air duct design is achieved, which can improve the airflow angle and reduce the flow separation inside the impeller, thereby bringing the advantage of low noise.

[0039] In an optional embodiment, the diameter of the first arc surface 122 is smaller than the diameter of the second arc surface 123.

[0040] Specifically, the concave surface 121 of the blade 12 has a first arcuate surface 122 and a second arcuate surface 123 connected to each other. The first arcuate surface 122 is located near the front end (i.e., the inner end) of the blade 12. Setting the diameter of the first arcuate surface 122 to be relatively small helps the fluid to enter the impeller more smoothly, thereby reducing the impact and eddies of the fluid at the inlet. The second arcuate surface 123 is located at the rear end of the blade 12. Setting the diameter of the second arcuate surface 123 to be relatively large provides a larger fluid channel, allowing the fluid to diffuse more smoothly when leaving the blade 12. The large-diameter second arcuate surface 123 helps to increase the static pressure energy of the fluid, thereby increasing the head of the impeller.

[0041] In an optional embodiment, the blades 12 have a uniform thickness. Specifically, please refer to... Figure 3 In the illustrated embodiment, blade 12 has a uniform thickness. This uniform thickness design of blade 12 facilitates production and reduces manufacturing costs. It should be noted that uniform blade thickness means that the distance between the two surfaces of the blade is the same, and the thickness tolerance is within 5%.

[0042] In an optional embodiment, the inner end of the blade 12 is rounded.

[0043] Specifically, the inner end of blade 12 is the front end of blade 12. A rounded corner 124 at the front end of blade 12 makes the front end of blade 12 sharper and smoother. This structure helps to cut the fluid and increase the fluid's kinetic energy. Furthermore, the rounded corner 124 at the inner end of blade 12 can further increase the distance between the front ends of two adjacent blades 12, thus increasing the inlet size of blade 12 and facilitating fluid flow.

[0044] In an optional embodiment, the thickness of the blade 12 increases first and then decreases in the direction extending from the inner end to the outer end; and / or, the maximum thickness of the blade 12 is located at the junction of the first arc surface 122 and the second arc surface 123.

[0045] Specifically, please refer to Figure 4 As shown, in this embodiment, the blade 12 is a non-uniform thickness blade, with its wall thickness increasing and then decreasing from the front end to the rear end. When the wind turbine rotates, especially at high speeds, it needs to withstand significant pressure. This application designs the blade 12's wall thickness to increase first and then decrease, which improves the mechanical strength of the blade 12, thereby extending the wind turbine's service life and reducing operating and maintenance costs. Furthermore, the initial increase followed by decrease in blade thickness also optimizes fluid flow performance and improves wind turbine efficiency. In this embodiment, the maximum thickness of the blade 12 is located at the junction of the first arc surface 122 and the second arc surface 123.

[0046] In an optional embodiment, an air outlet channel 13 is formed between two adjacent blades 12, and the width of the inner end of the air outlet channel 13 is greater than the width of the rear end of the air outlet channel 13.

[0047] Specifically, the wind turbine of this application includes a chassis 11 and a plurality of blades 12. The blades 12 are evenly arranged on the end face of the chassis 11, and an air outlet channel 13 is formed between two adjacent blades 12. The width of the end of the air outlet channel 13 near the axis of the chassis 11 is greater than the width of the end of the air outlet channel 13 away from the axis of the chassis 11. Designing the inner end of the air outlet channel 13 to be wider can reduce the impact angle when the fluid enters the air outlet channel 13 between the blades 12, reduce the fluid kinetic energy loss, and allow the fluid to enter the channel more evenly. The outer end of the air outlet channel 13 is designed to be narrower so that the fluid is accelerated and compressed at the rear end of the air outlet channel 13, forming higher pressure energy. The narrower air outlet channel 13 helps to increase the fluid velocity and pressure, thereby improving the head and efficiency of the wind turbine.

[0048] In an alternative embodiment, the number of blades 12 is N, where 40 < N < 60, and / or, the height of the wind wheel is H, where 20 mm < H < 60 mm. Specifically, the centrifugal wind wheel 1 of the present application has multiple blades 12, and in the art, multiple blades 12 means that the number of blades 12 is greater than 32. In this embodiment, the number of blades 12 is set between 40 and 60. The height of the wind wheel is set within the range of 20 mm - 60 mm. It can be understood that the height of the wind wheel is the sum of the thickness of the chassis 11 and the height of the blades 12.

[0049] In an alternative embodiment, the line connecting the intersection of the first arc surface 122 and the second arc surface 123 to the axis of the chassis 11 is A, and the inner end and the outer end of the blade 12 are respectively located on both sides of the line A.

[0050] Specifically, as Figure 3 shown, the first arc surface 122 is provided at the front end of the second arc surface 123, and the line connecting their intersection to the axis O of the chassis 11 is A. The front end of the blade 12 is provided on the left side of the line A, and the rear end of the blade 12 is provided on the right side of the line A. The two ends of the blade 12 are arranged on the left and right sides of the line A to further improve the airflow attack angle, reduce the separation of the fluid flow inside the wind wheel, thereby reducing noise and enhancing the competitiveness of the product.

[0051] In an alternative embodiment, the inlet angle of the blade 12 is 60°, and the outlet angle of the blade 12 is 165°; L1 / L2 is 0.6; (L3 - L1) / (L2 - L1) = 0.69; the number of blades 12 is 43.

[0052] As Figure 5 shown in the internal velocity vector diagram of the simulation wind wheel, it can be seen that the fluid flow state of this embodiment is good, and there is no flow separation in the main flow channel.

[0053] As shown in the actual measurement values of the noise in the following table for different L1 / L2 value schemes, the noise is the lowest when the value of L1 / L2 is 0.6.

[0054]

[0055] An embodiment of the present application further provides a fan assembly, which includes the above-mentioned centrifugal wind wheel 1. It can be understood that the fan assembly further includes an upper volute and a lower volute, and the upper volute and the lower volute form a receiving cavity for accommodating the centrifugal wind wheel 1. The upper volute has an air inlet, and the upper volute and the lower volute are combined into one body and form an air outlet. The air flow enters the front end of the blade 12 from the air inlet, passes through the air outlet channel 13 between two adjacent blades 12, and then is sent out to the outside from the air outlet.

[0056] The centrifugal impeller 1 of the wind turbine assembly of this application achieves a reasonable air duct design through optimized blades 12, which can improve the airflow angle and reduce the occurrence of flow separation inside the impeller, thereby reducing noise and enhancing product competitiveness. Each blade 12 has a concave surface 121, which includes a first arc surface 122 and a second arc surface 123 connected sequentially from the inside to the outside. The distance between the inner end of the first arc surface 122 and the axis of the chassis 11 is L1, the distance between the outer end of the second arc surface 123 and the axis of the chassis 11 is L2, the distance between the inner end of the first arc surface 122 and the axis of the chassis 11 is L1, the distance between the outer end of the second arc surface 123 and the axis of the chassis 11 is L2, and the distance between the intersection point of the first arc surface 122 and the second arc surface 123 and the axis of the chassis 11 is L3. Among them, 0.55≦L1 / L2≦0.65, 0.6≦(L3-L1) / (L2-L1)≦0.75.

[0057] This application also provides an air conditioner that includes the aforementioned fan assembly. The fan assembly of this application optimizes the blades 12 of the centrifugal impeller 1, achieving a reasonable air duct design, which improves the airflow angle of attack, reduces flow separation within the impeller, thereby reducing noise and enhancing product competitiveness.

[0058] The above description is merely an exemplary embodiment of the present utility model and does not limit the patent scope of the present utility model. Any equivalent structural transformations made based on the technical concept of the present utility model and the contents of the present utility model specification and drawings, or direct / indirect applications in other related technical fields, are included within the patent protection scope of the present utility model.

Claims

1. A centrifugal impeller, characterized in that, Comprising: A chassis; A plurality of blades, the plurality of blades being evenly arranged around the axis of the chassis on the chassis, each blade having a concave surface, the concave surface including a first arc surface and a second arc surface connected in sequence from inside to outside; Wherein, the distance between the inner end of the first arc surface and the axis of the chassis is L1, the distance between the outer end of the second arc surface and the axis of the chassis is L2, and the distance between the intersection point between the first arc surface and the second arc surface and the axis of the chassis is L3, 0.55 ≦ L1 / L2 ≦ 0.65, 0.6 ≦ (L3 - L1) / (L2 - L1) ≦ 0.

75.

2. The centrifugal impeller as described in claim 1, characterized in that, The inlet angle of the blade is α, 50° < α < 70°; the outlet angle of the blade is β, 160° < β < 170°.

3. The centrifugal impeller as described in claim 1, characterized in that, The diameter of the first arc surface is smaller than the diameter of the second arc surface.

4. The centrifugal impeller as described in claim 1, characterized in that, The thickness of the blades is consistent.

5. The centrifugal impeller as described in claim 4, characterized in that, The inner ends of the blades are provided with rounded corners.

6. The centrifugal impeller as described in claim 1, characterized in that, The thickness of the blades shows a trend of increasing first and then decreasing in the direction from the inner end to the outer end; And / or, the position with the maximum thickness of the blades is located at the junction of the first arc surface and the second arc surface.

7. The centrifugal impeller as described in claim 1, characterized in that, An air outlet channel is formed between two adjacent blades, and the width of the inner end of the air outlet channel is greater than the width of the outer end of the air outlet channel.

8. The centrifugal impeller as described in claim 7, characterized in that, The width of the air outlet channel increases first and then decreases in the direction from the inner end to the outer end.

9. The centrifugal impeller as described in claim 1, characterized in that, The number of the blades is N, 40 < N < 60, and / or, the height of the wind wheel is H, 20 mm < H < 60 mm.

10. The centrifugal impeller as described in claim 1, characterized in that, The connection line between the intersection point between the first arc surface and the second arc surface and the axis of the chassis is A, and the inner end and the outer end of the blade are respectively located on both sides of the connection line A.

11. A fan assembly, characterized in that, Comprising a centrifugal wind wheel according to any one of claims 1-10.

12. An air conditioner, characterized in that, Comprising a fan assembly according to claim 11.

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