Impeller and fan comprising same

Abstract

The application discloses a kind of impeller and the fan comprising it, including the blade of uniform distribution along the circumferential direction and the middle disc located in the middle region of blade, further comprising: first end ring, first end ring is set to the first end of blade, along the circumferential direction of blade, first end ring extends from the suction surface of blade to the pressure surface of blade and extends to between two adjacent blades, first end ring does not extend to the suction surface of adjacent blade;Second end ring, second end ring is set to the second end of blade, along the circumferential direction of blade, second end ring extends from the pressure surface of blade to the suction surface of blade and extends to between two adjacent blades, second end ring does not extend to the pressure surface of adjacent blade, along the axial direction of impeller, first end ring and second end ring do not overlap. First end ring and second end ring block the leakage of blade end, improve impeller work efficiency, reduce aerodynamic noise.In addition, first end ring and second end ring can utilize the effect of residual leakage flow to delay the flow separation of suction surface.

Description

Technical Field

[0001] This invention relates to the field of wind turbine technology, and particularly to an impeller and a wind turbine containing the same. Background Technology

[0002] Current fan impellers are typically made of plastic or metal. Plastic impellers, to allow for smooth ejection from the mold, lack an end ring at the blade tip. However, due to the pressure difference between the pressure and suction sides, fluid flows from the high-pressure area across the blade tip to the low-pressure area, creating leakage flow. This leakage flow then shears against the mainstream flow on the suction side, inducing vortices—the reason for leakage vortices in the gap between the blade tip and the volute. Leakage vortices worsen the internal flow, especially reducing the efficiency of the range hood in the user's home, and also causing additional aerodynamic noise. Summary of the Invention

[0003] The technical problem to be solved by the present invention is to overcome the defect of leakage vortex at the tip of the plastic impeller in the prior art, and to provide an impeller and a fan containing the impeller.

[0004] The present invention solves the above-mentioned technical problems through the following technical solution:

[0005] An impeller includes blades evenly distributed along a circumferential direction and a central disk located in the middle region of the blades; the impeller further includes:

[0006] A first end ring is disposed at the first end of the blade and extends along the circumferential direction of the blade from the suction surface of the blade toward the pressure surface of the blade and extends to the space between two adjacent blades. The first end ring does not extend to the suction surface of the adjacent blades.

[0007] The second end ring is disposed at the second end of the blade. Along the circumferential direction of the blade, the second end ring extends from the pressure surface of the blade toward the suction surface of the blade and extends to the space between two adjacent blades. The second end ring does not extend to the pressure surface of the adjacent blades. Along the axial direction of the impeller, the projections of the first end ring and the second end ring do not overlap.

[0008] In this design, by setting non-overlapping first and second end rings at the first and second ends of the blade, the blade can be smoothly ejected from the mold, facilitating processing. Furthermore, the first and second end rings significantly increase the distance the leakage flow needs to travel from the pressure surface to the suction surface, thereby reducing leakage flow. This enhances the blade's anti-leakage capability without axial overlap, reducing leakage, preventing leakage vortex formation, and ultimately improving impeller efficiency and reducing aerodynamic noise. In addition, the first end ring does not extend to the suction surface of adjacent blades, and the second end ring does not extend to the pressure surface of adjacent blades, balancing the impact of leakage flow at both ends on flow separation. This reduces leakage while utilizing the residual leakage flow to delay flow separation at the suction surface, resulting in better overall aerodynamic performance.

[0009] Preferably, along the axial direction of the impeller, the projections of the first end ring and the second end ring are spliced ​​together to form a complete annular structure.

[0010] In this scheme, the above settings are used to improve the correlation between leakage flow and suction surface flow separation.

[0011] Preferably, the end section of the first end ring near the suction surface of the adjacent blade has an arc structure, and the curvature of the end of the first end ring near the suction surface of the adjacent blade is less than the curvature of the suction surface of the blade.

[0012] The end section of the second end ring near the pressure surface of the adjacent blade has an arc structure, and the curvature of the end of the second end ring near the pressure surface of the adjacent blade is less than the curvature of the pressure surface of the blade.

[0013] In this solution, the above settings are used to improve the effectiveness of preventing leakage.

[0014] Preferably, the two opposite ends of the first end ring near the suction surface of the adjacent blade are located at the midpoint of the two adjacent blades.

[0015] The two opposite ends of the second end ring near the pressure surface of the adjacent blade are located at the midpoint of the two adjacent blades.

[0016] In this scheme, the boundary positions of the first end ring and the second end ring are adjusted by the above settings, thereby ensuring the correlation between leakage flow and suction surface flow separation.

[0017] Preferably, along the circumferential direction of the blade, the extension dimension of the first end ring is greater than the extension dimension of the second end ring.

[0018] In this scheme, the above settings are used to balance the difference in coverage area of ​​the first end ring and the second end ring above the suction surface, ensuring that there is a certain degree of coherence between the leakage flow at the first and second ends of the blade and the flow separation at the suction surface.

[0019] Preferably, the outer diameter of the intermediate disk is smaller than the outer diameter of the impeller.

[0020] In this solution, by setting the first end ring and the second end ring, the outer diameter of the middle plate can be reduced accordingly. This avoids the situation where the outer diameter of the middle plate is too large and the mold cannot pass through the middle plate to the first end ring or the second end ring, and the situation where the outer diameter of the middle plate is too large and the inner diameter of the first end ring and the second end ring is small in order to allow the mold to come out smoothly during molding, resulting in poor blocking effect for leakage flow.

[0021] Preferably, the formula for calculating the outer diameter of the middle disk is D=D1+(D2-D1) / k, where the outer diameter of the middle disk is D, the inner diameter of the impeller is D1, the outer diameter of the impeller is D2, and k is a coefficient with a value range of 3 to 8.

[0022] In this scheme, the above settings are used to limit the outer diameter of the middle plate.

[0023] Preferably, the inner diameters of the first end ring and the second end ring are greater than or equal to the outer diameter of the middle disk.

[0024] In this solution, the above settings ensure that the projections of the middle plate, the first end ring, and the second end ring in the axial direction do not overlap, thus ensuring that the mold can be ejected normally.

[0025] Preferably, the outer diameters of the first end ring and the second end ring are the same as the outer diameter of the impeller.

[0026] In this scheme, the above-mentioned settings ensure that the area of ​​the first and second end rings blocking the leakage flow is guaranteed.

[0027] A fan, the fan comprising the impeller as described above.

[0028] In this solution, the fan includes the aforementioned impeller, which, during operation, utilizes the first and second end rings on the impeller blades to reduce leakage flow and simultaneously reduce flow separation at the suction surface, thereby improving the aerodynamic performance of the fan and reducing noise during operation.

[0029] The positive and progressive effects of this invention are as follows: By setting a first end ring and a second end ring with non-overlapping projections at the first and second ends of the blade, the blade can be smoothly ejected from the mold, facilitating processing. Furthermore, the first and second end rings significantly increase the distance the leakage flow needs to travel from the pressure surface to the suction surface, thereby reducing leakage flow. This enhances the blade's anti-leakage capability without axial overlap, reducing leakage, preventing leakage vortex formation, and thus improving impeller efficiency and reducing aerodynamic noise. In addition, the first end ring does not extend to the suction surface of adjacent blades, and the second end ring does not extend to the pressure surface of adjacent blades, balancing the impact of leakage flow at both ends on flow separation. This reduces leakage while utilizing the residual leakage flow to delay flow separation at the suction surface, resulting in better overall aerodynamic performance. Attached Figure Description

[0030] Figure 1 This is a perspective view of an impeller according to a preferred embodiment of the present invention.

[0031] Figure 2 This is a diagram showing the positional relationship between the second end ring and the blade in a preferred embodiment of the present invention.

[0032] Figure 3 This is a front view of an impeller according to a preferred embodiment of the present invention.

[0033] Figure 4 This is a diagram showing the positional relationship between the first end ring and the second end ring according to a preferred embodiment of the present invention.

[0034] Explanation of reference numerals in the attached figures:

[0035] Leaf 1

[0036] Suction surface 11

[0037] Pressure surface 12

[0038] Mid-game 2

[0039] First end ring 3

[0040] Second end ring 4

[0041] Endpoint 5 Detailed Implementation

[0042] The present invention will be further illustrated by way of embodiments below, but the present invention is not limited to the scope of the embodiments described herein.

[0043] This embodiment provides an impeller, the specific structure of which is as follows: Figure 1 , Figure 2 , Figure 3 and Figure 4As shown, the impeller includes blades 1 evenly distributed along the circumference and a central disk 2 located in the middle region of the blades 1. The impeller also includes:

[0044] The first end ring 3 is disposed at the first end of the blade 1. Along the circumferential direction of the blade 1, the first end ring 3 extends from the suction surface 11 of the blade 1 toward the pressure surface 12 of the blade 1 and extends to the space between two adjacent blades 1. The first end ring 3 does not extend to the suction surface 11 of the adjacent blade 1.

[0045] The second end ring 4 is disposed at the second end of the blade 1. Along the circumferential direction of the blade 1, the second end ring 4 extends from the pressure surface 12 of the blade 1 toward the suction surface 11 of the blade 1 and extends to the space between two adjacent blades 1. The second end ring 4 does not extend to the pressure surface 12 of the adjacent blade 1. Along the axial direction of the impeller, the projections of the first end ring 3 and the second end ring 4 do not overlap.

[0046] Specifically, both the first end ring 3 and the second end ring 4 are arc-shaped plates and are flush with the first and second ends of the blade 1. The first end ring 3 extends from the suction surface 11 of the blade 1 toward the pressure surface 12 of the blade 1 and continues to the space between two adjacent blades 1, without sealing the gap between them. Similarly, the second end ring 4 extends from the pressure surface 12 of the blade 1 toward the suction surface 11 of the blade 1 and continues to the space between two adjacent blades 1, without sealing the gap between them. Compared to blades 1 without end rings, the first end ring 3 and the second end ring 4, by not sealing the gap between adjacent blades 1, significantly increase the distance that the leakage flow needs to travel from the pressure surface 12 to the suction surface 11. This effectively blocks the airflow leakage from the high-pressure area of ​​the blade 1 across the blade end to the low-pressure area, thereby reducing the leakage flow. This enhances the blade 1's anti-leakage capability without axial airflow accumulation, thus reducing leakage, preventing leakage vortex formation, improving impeller efficiency, and reducing aerodynamic noise.

[0047] Furthermore, the first end ring 3 does not extend to the suction surface 11 of the adjacent blade 1, and the second end ring 4 does not extend to the pressure surface 12 of the adjacent blade 1. Compared to a continuous circular structure for the end rings, this significantly increases the distance the leakage flow needs to travel from the pressure surface 12 to the suction surface 11. Simultaneously, some of the leakage flow flowing from the first and second ends of the blade 1 can also balance the flow separation of the blade 1. Specifically, while reducing leakage, the residual leakage flow delays the flow separation of the suction surface 11, resulting in better overall aerodynamic performance. This makes the fan system using this impeller adaptable to the resistance conditions of different user households.

[0048] It is understood that in this embodiment, a first end ring 3 and a second end ring 4 with non-overlapping projections are provided at the first and second ends of the blade 1 so that the blade 1 with the first end ring 3 and the second end ring 4 can be smoothly removed from the mold during the processing and manufacturing of the blade 1, avoiding interference between the continuous circular structure of the end rings and the mold.

[0049] In this embodiment, the projections of the first end ring 3 and the second end ring 4 are spliced ​​together along the axial direction of the impeller to form a complete annular structure.

[0050] Specifically, the first end ring 3 located at the first end of the blade 1 extends from the suction surface 11 of the blade 1 toward the pressure surface 12 of the blade 1 and continues to extend between two adjacent blades 1. Along the axial direction of the impeller, the projection of the first end ring 3 corresponds to the second end ring 4 located at the second end of the blade 1, which extends from the pressure surface 12 of the blade 1 toward the suction surface 11 of the blade 1 and continues to extend to the remaining area between two adjacent blades 1. The projection of the first end ring 3 and the second end ring 4 can form a complete annular structure when joined. Similarly, the projection of the second end ring 4 and the first end ring 3 can form a complete annular structure when joined. Compared to the situation where the projection of the first end ring 3 and the second end ring 4 cannot form a complete annular structure, the formation of a complete annular structure when joined can improve the correlation between leakage flow and flow separation at the suction surface 11. That is, the impeller can reduce leakage flow, while the residual leakage flow still leads to a decrease in the highest flow efficiency. However, the leakage flow can suppress flow separation at the suction surface 11 when it deviates from the high efficiency point. This indicates that the presence of minute leakage flow is advantageous in dealing with complex operating conditions, thus providing better adaptability and operational performance in user households with certain resistance.

[0051] In this embodiment, the end section of the first end ring 3 near the suction surface 11 of the adjacent blade 1 has an arc structure, and the curvature of the end of the first end ring 3 near the suction surface 11 of the adjacent blade 1 is less than the curvature of the suction surface 11 of the blade 1.

[0052] The end section of the second end ring 4 near the pressure surface 12 of the adjacent blade 1 has an arc structure, and the curvature of the end of the second end ring 4 near the pressure surface 12 of the adjacent blade 1 is less than the curvature of the pressure surface 12 of the blade 1.

[0053] Specifically, the first end ring 3 extends from the suction surface 11 of the blade 1 toward the pressure surface 12 of the blade 1, and continues to extend toward the suction surface 11 of the adjacent blade 1. The cross-section of the end of the first end ring 3 toward the suction surface 11 of the adjacent blade 1 is an arc structure, and the curvature of the arc structure is less than the curvature of the suction surface 11. That is to say, the cross-section of the arc structure is closer to a straight line than the cross-section of the suction surface 11. The smaller curvature of the arc structure means that the distance traveled by the leak when passing through the arc structure is greater than the distance traveled when the curvature of the arc structure is the same as or greater than the curvature of the suction surface 11, thereby improving the effect of preventing leakage.

[0054] Similarly, the second end ring 4 extends from the pressure surface 12 of the blade 1 toward the suction surface 11 of the blade 1, and continues to extend toward the pressure surface 12 of the adjacent blade 1. The cross-section of the end of the second end ring 4 toward the pressure surface 12 of the adjacent blade 1 has an arc structure, and the curvature of the arc structure is less than the curvature of the pressure surface 12. The purpose is also to increase the leakage bypass stroke to improve the leakage blocking effect.

[0055] In this embodiment, the two opposite ends 5 of the first end ring 3 near the suction surface 11 of the adjacent blade 1 are located at the midpoint of the two adjacent blades 1.

[0056] The two opposite ends 5 of the second end ring 4, which are close to the pressure surface 12 of the adjacent blade 1, are located at the midpoint of the two adjacent blades 1.

[0057] Specifically, the two opposite ends 5 are the starting and ending points of the first end ring 3, which has an arc structure, toward the suction surface 11 of the adjacent blade 1. Similarly, the two opposite ends 5 are the starting and ending points of the second end ring 4, which has an arc structure, toward the pressure surface 12 of the adjacent blade 1. By setting the two opposite endpoints 5 at the midpoints of two adjacent blades 1, the boundary positions of the first end ring 3 and the second end ring 4 are limited. That is, the extension length of the first end ring 3 toward the suction surface 11 of the adjacent blade 1 and the extension length of the second end ring 4 toward the pressure surface 12 of the adjacent blade 1 are limited. This avoids the first end ring 3 and the second end ring 4 having too small an extension size, resulting in poor leakage blocking effect. At the same time, limiting the boundary positions of the first end ring 3 and the second end ring 4 can also improve the suppression effect of the first end ring 3 and the second end ring 4 on the flow separation of the suction surface 11. Specifically, compared with no end rings, when the boundary positions of the first end ring 3 and the second end ring 4 extend toward the adjacent blade 1, part of the leakage flow is blocked, and the residual leakage flow is used to suppress the flow separation of the suction surface 11 when deviating from the high efficiency point. That is, limiting the boundary positions of the first end ring 3 and the second end ring 4 ensures the correlation between the leakage flow and the flow separation of the suction surface 11, so that the two work together to improve the aerodynamic performance of the impeller.

[0058] In this embodiment, along the circumferential direction of the blade 1, the extension dimension of the first end ring 3 is greater than the extension dimension of the second end ring 4.

[0059] Since the first end ring 3 extends along the suction surface 11 of blade 1 towards the pressure surface 12 of blade 1 and continues towards the suction surface 11 of adjacent blade 1, the extension dimension of the first end ring 3 is set to be larger than the extension dimension of the second end ring 4 to ensure the suppression effect on flow separation on the suction surface 11 of blade 1, thereby improving the effect of suppressing flow separation. Viewed from the axial direction of the impeller, the increased projected dimension of the first end ring 3 and the decreased extension dimension of the second end ring 4 still allow for the formation of a complete annular structure. Simultaneously, since the second end ring 4 extends along the pressure surface 12 of blade 1 towards the suction surface 11 of blade 1 and continues towards the pressure surface 12 of adjacent blade 1, its impact on flow separation on the suction surface 11 is relatively small. Therefore, by increasing the extension dimension of the first end ring 3 and decreasing the extension dimension of the second end ring 4, the difference in the coverage area of ​​the first end ring 3 and the second end ring 4 above the suction surface 11 is balanced, ensuring that there is a certain degree of coherence between the leakage flow at the first and second ends of blade 1 and the flow separation on the suction surface 11.

[0060] In this embodiment, the outer diameter of the middle disk 2 is smaller than the outer diameter of the impeller.

[0061] Specifically, the outer diameter of the impeller is the diameter of the side of the blade 1 away from the axis. The middle disk 2 has a disc structure, and the outer diameter of the middle disk 2 is smaller than the outer diameter of the impeller, so that the middle disk 2 will not protrude from the edge of the blade 1 away from the axis.

[0062] Furthermore, due to the provision of the first end ring 3 and the second end ring 4, compared to an impeller without end rings, the impeller in this embodiment allows a portion of the material from the outer edge of the original central disk 2 to move along the axial direction of the impeller to the first and second ends of the blades 1 to form the first end ring 3 and the second end ring 4. Therefore, the outer diameter of the central disk 2 can be correspondingly reduced, avoiding situations where the outer diameter of the central disk 2 is too large, preventing the mold from passing through the central disk 2 to the first end ring 3 or the second end ring 4, and avoiding situations where the outer diameter of the central disk 2 is too large, resulting in a small inner diameter of the first end ring 3 and the second end ring 4 to facilitate the mold's smooth ejection during molding, leading to poor blocking effect for leakage flow. It can be understood that the inner diameter of the first end ring 3 and the second end ring 4 in this embodiment is the diameter of the edge of the first end ring 3 and the second end ring 4 closest to the axis.

[0063] Furthermore, in this embodiment, the formula for calculating the outer diameter of the middle disk 2 is D=D1+(D2-D1) / k, where the outer diameter of the middle disk 2 is D, the inner diameter of the impeller is D1, the outer diameter of the impeller is D2, and k is a coefficient with a value range of 3~8.

[0064] Specifically, the inner diameter of the impeller is the diameter of the edge of blade 1 near the axis, and the outer diameter of the impeller is the diameter of the edge of blade 1 away from the axis. By constructing a calculation formula for the middle disk 2, the inner diameter and outer diameter of the impeller are substituted into the calculation formula to obtain the outer diameter of the middle disk 2, thereby limiting the outer diameter of the middle disk 2 and preventing a series of adverse effects caused by an excessively large outer diameter of the middle disk 2.

[0065] In this embodiment, the inner diameter of the first end ring 3 and the second end ring 4 is greater than or equal to the outer diameter of the middle plate 2.

[0066] Specifically, the diameter of the edge of the first end ring 3 and the second end ring 4 near the axis is greater than the inner diameter of the impeller. In the axial direction of the impeller, the projections of the first end ring 3 and the second end ring 4 do not overlap with the middle disk 2. This ensures that the impeller can be properly ejected from the mold when the impeller is manufactured using the mold, and avoids the situation where the projections of the first end ring 3 and the second end ring 4 overlap with the middle disk 2, which would cause structural interference and prevent the impeller from being properly ejected from the mold.

[0067] In this embodiment, the outer diameters of the first end ring 3 and the second end ring 4 are the same as the outer diameter of the impeller. Compared to having outer diameters larger than the impeller's outer diameter, having outer diameters the same as the impeller's outer diameter avoids obstruction of airflow between the impeller and the volute, ensuring the impeller's aerodynamic performance. Furthermore, compared to having outer diameters smaller than the impeller's outer diameter, it avoids gaps in the area between adjacent blades 1 where leakage flow needs to be blocked, thus ensuring the area of ​​the first end rings 3 and 4 that blocks leakage flow is adequately covered.

[0068] This embodiment also provides a fan that includes the impeller described above. When the fan is running, the first end ring 3 and the second end ring 4 on the blades 1 of the impeller are used to reduce leakage flow and reduce flow separation at the suction surface 11, thereby improving the aerodynamic performance of the fan and reducing the noise during operation.

[0069] While specific embodiments of the present invention have been described above, those skilled in the art should understand that these are merely illustrative examples, and the scope of protection of the present invention is defined by the appended claims. Those skilled in the art can make various changes or modifications to these embodiments without departing from the principles and essence of the present invention, but all such changes and modifications fall within the scope of protection of the present invention.

Claims

1. An impeller, the impeller comprising a plurality of blades evenly distributed along a circumferential direction and a central disk located in the middle region of the blades, characterized in that, The impeller also includes: A first end ring is disposed at the first end of the blade and extends along the circumferential direction of the blade from the suction surface of the blade toward the pressure surface of the blade and extends to the space between two adjacent blades. The first end ring does not extend to the suction surface of the adjacent blades. The second end ring is disposed at the second end of the blade. Along the circumferential direction of the blade, the second end ring extends from the pressure surface of the blade toward the suction surface of the blade and extends to the space between two adjacent blades. The second end ring does not extend to the pressure surface of the adjacent blades. Along the axial direction of the impeller, the projections of the first end ring and the second end ring do not overlap. Along the axial direction of the impeller, the projections of the first end ring and the second end ring are spliced ​​together to form a complete circular structure; The end section of the first end ring near the suction surface of the adjacent blade has an arc structure, and the curvature of the end of the first end ring near the suction surface of the adjacent blade is less than the curvature of the suction surface of the blade. The end section of the second end ring near the pressure surface of the adjacent blade has an arc structure, and the curvature of the end of the second end ring near the pressure surface of the adjacent blade is less than the curvature of the pressure surface of the blade. The formula for calculating the outer diameter of the middle disk is D=D1+(D2-D1) / k, where the outer diameter of the middle disk is D, the inner diameter of the impeller is D1, the outer diameter of the impeller is D2, and k is a coefficient with a value range of 3~8.

2. The impeller as described in claim 1, characterized in that, The two opposite ends of the first end ring near the suction surface of the adjacent blade are located at the midpoint of the two adjacent blades. The two opposite ends of the second end ring near the pressure surface of the adjacent blade are located at the midpoint of the two adjacent blades.

3. The impeller as described in claim 1, characterized in that, Along the circumferential direction of the blade, the extension dimension of the first end ring is greater than the extension dimension of the second end ring.

4. The impeller as described in claim 1, characterized in that, The outer diameter of the middle disk is smaller than the outer diameter of the impeller.

5. The impeller as described in claim 1, characterized in that, The inner diameters of the first end ring and the second end ring are greater than or equal to the outer diameter of the middle plate.

6. The impeller as described in claim 1, characterized in that, The outer diameters of the first end ring and the second end ring are the same as the outer diameter of the impeller.

7. A fan, characterized in that, The fan includes an impeller as described in any one of claims 1-6.

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