Current collector, centrifugal fan and air conditioner

Abstract

The utility model provides a kind of current collector, centrifugal fan and air conditioner.The current collector is applied to fan, the fan includes impeller, the impeller is provided with blade, the current collector includes contraction section, the one end of the contraction section constitutes the entrance of the current collector, and along the direction away from the entrance, the flow area of the contraction section gradually reduces, the contraction section's profile is straight line, the profile of the contraction section and the plane where the entrance is located have angle θ, the angle θ and the blade inlet angle β1 of the blade and the blade outlet angle β2 are positively correlated.The current collector, centrifugal fan and air conditioner provided by the utility model, the profile of the contraction section of current collector is designed using the blade inlet angle β1 and blade outlet angle β2 of blade, so that the profile of the current collector can be matched with the size of impeller, airflow separation and turbulence phenomenon can be effectively reduced, so as to improve the efficiency of fan, reduce the purpose of noise and vibration.

Description

Technical Field

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

[0002] In the field of wind turbine technology, the collector, as a crucial component guiding airflow into the impeller, directly impacts the aerodynamic performance, efficiency, and noise level of the wind turbine. While the widely used conical collector is simple in structure and low in manufacturing cost, it suffers from significant flow losses and a sharp drop in efficiency under varying operating conditions, limiting the overall performance improvement of the wind turbine. In recent years, conical collectors have attracted attention due to their superior flow characteristics, offering improved pressure coefficient and total pressure efficiency while maintaining efficiency compared to traditional structures. However, existing conical collectors are mass-produced, making reliable matching impossible when applied to impellers with different structures. This leads to separation, eddies, and turbulence during airflow guidance, severely affecting the stability and noise reduction of the wind turbine. Utility Model Content

[0003] To address the technical problems of poor stability and low noise caused by the inability of the collector to match the impeller in the existing technology, a collector, centrifugal fan and air conditioner are provided that designs the profile of the collector according to the parameters of the impeller to improve the stability of the fan and reduce the noise of the fan.

[0004] A collector is applied to a fan, the fan including an impeller with blades, the collector including a converging section, one end of the converging section forming the inlet of the collector, and the flow area of ​​the converging section gradually decreasing along the direction away from the inlet, the profile of the converging section being a straight line, the profile of the converging section forming an angle θ with the plane where the inlet is located, the angle θ being positively correlated with the blade inlet angle β1 and the blade outlet angle β2.

[0005] The relationship between the included angle θ and the blade inlet angle β1 and the blade outlet angle β2 conforms to the following formula:

[0006] ;

[0007] Where h1 is the designed length of the contraction section in the direction of the rotation axis of the impeller; D is the diameter of the impeller inlet.

[0008] The design length h1 of the contraction section ranges from 0.15H to 0.3H, where H is the design length of the collector.

[0009] The collector further includes a transition section connected to the end of the contraction section away from the inlet. Along the direction away from the inlet, the flow area of ​​the transition section first decreases and then increases.

[0010] The transition section has an arc-shaped profile, and the radius R1 of the transition section is positively correlated with the blade inlet angle β1 and the blade outlet angle β2.

[0011] The relationship between the radius R1 of the transition section and the blade inlet angle β1 and the blade outlet angle β2 conforms to the following formula:

[0012] ;

[0013] Where h2 is the design length of the transition section in the direction of the rotation axis of the impeller; D is the diameter of the impeller inlet.

[0014] The design length h2 of the transition section ranges from 0.6H to 0.8H, where H is the design length of the collector.

[0015] The collector also includes a matching section connected to the end of the transition section away from the inlet, and the flow area of ​​the matching section gradually increases along the direction away from the inlet.

[0016] The profile of the matching segment is arc-shaped. The radius R2 of the matching segment is positively correlated with the blade inlet angle β1 of the blade, and the radius R2 of the matching segment is negatively correlated with the blade outlet angle β2.

[0017] The relationship between the radius R2 of the matching segment and the blade inlet angle β1 and the blade outlet angle β2 conforms to the following formula:

[0018] ;

[0019] Where h3 is the design length of the matching section in the direction of the impeller's rotation axis; D is the diameter of the impeller inlet.

[0020] The design length h3 of the matching segment ranges from 0.05H to 0.1H, where H is the design length of the collector.

[0021] At least a portion of the matching section extends into the impeller; or, the connection point between the matching section and the transition section is on the same plane as the impeller inlet.

[0022] A centrifugal fan, comprising the aforementioned collector.

[0023] An air conditioner includes the aforementioned collector or the aforementioned centrifugal fan.

[0024] The collector, centrifugal fan, and air conditioner provided by this utility model utilize the blade inlet angle β1 and blade outlet angle β2 to design the profile of the collector's converging section, so that the profile of the collector can match the size of the impeller. The airflow achieves a smooth transition before entering the impeller, which can effectively reduce airflow separation and turbulence, thereby improving fan efficiency and reducing noise and vibration. Attached Figure Description

[0025] Figure 1 A schematic diagram of the collector applied to a centrifugal fan according to an embodiment of this utility model;

[0026] Figure 2 A cross-sectional view of the collector provided in this embodiment of the utility model applied to a centrifugal fan;

[0027] Figure 3 A schematic diagram of the current collector provided in an embodiment of this utility model;

[0028] Figure 4 A schematic diagram of the blade, blade inlet angle, and blade outlet angle provided in an embodiment of this utility model;

[0029] Figure 5 A cross-sectional view of the current collector provided in an embodiment of this utility model;

[0030] Figure 6 The static pressure-airflow curves of the centrifugal fan using the collector of this application and the centrifugal fan using the conical arc collector in the prior art are provided for embodiments of this utility model.

[0031] In the picture:

[0032] 1. Impeller; 11. Blade; 21. Contraction section; 31. Inlet; 22. Transition section; 23. Matching section. Detailed Implementation

[0033] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only for explaining this utility model and are not intended to limit this utility model.

[0034] To enable those skilled in the art to better understand the present invention, the technical solutions of the present invention 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 invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort should fall within the protection scope of the present invention.

[0035] It should be noted that the terms "first," "second," etc., in the specification, claims, and accompanying drawings of this utility model are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such terms can be used interchangeably where appropriate for the embodiments of the utility model described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion; for example, a process, method, system, product, or apparatus that comprises a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units not explicitly listed or inherent to such processes, methods, products, or apparatus.

[0036] It should be noted that in the description of this utility model, the terms "upper," "lower," "left," "right," "inner," and "outer," which indicate directional or positional relationships, are based on the directional or positional relationships shown in the accompanying drawings. These are merely for ease of description and do not indicate or imply that the device or element must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0037] Furthermore, it should be noted that, in the description of this utility model, unless otherwise explicitly specified and limited, the terms "installation," "setting," and "connection" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a direct connection, an indirect connection through an intermediate medium, or a connection within two components. Those skilled in the art can understand the specific meaning of the above terms in this utility model according to the specific circumstances.

[0038] In the field of wind turbine technology, the collector, as a crucial component guiding airflow into the impeller, directly impacts the aerodynamic performance, efficiency, and noise level of the wind turbine. While the widely used conical collector is simple in structure and low in manufacturing cost, it suffers from significant flow losses and a sharp drop in efficiency under varying operating conditions, limiting the overall performance improvement of the wind turbine. In recent years, conical collectors have attracted attention due to their superior flow characteristics, offering improved pressure coefficient and total pressure efficiency while maintaining efficiency compared to traditional structures. However, existing conical collectors are mass-produced, making reliable matching impossible when applied to impellers with different structures. This leads to separation, eddies, and turbulence during airflow guidance, severely affecting the stability and noise reduction of the wind turbine.

[0039] Therefore, this application provides a method such as Figures 1 to 6The collector shown is applied to a fan, which includes an impeller 1 with blades 11. The collector includes a converging section 21, one end of which forms the inlet 31. The flow area of ​​the converging section 21 gradually decreases away from the inlet 31. The profile of the converging section 21 is a straight line, and the profile forms an angle θ with the plane containing the inlet 31. This angle θ is positively correlated with the blade inlet angle β1 and the blade outlet angle β2 of the blades 11. By designing the profile of the converging section 21 of the collector using the blade inlet angle β1 and the blade outlet angle β2 of the blades 11, the profile of the collector can be matched with the size of the impeller 1. This allows for a smooth transition of airflow before entering the impeller 1, effectively reducing airflow separation and turbulence. The blade inlet angle β1 refers to the angle between the leading edge of the blade (inlet end) and the airflow direction, and the blade outlet angle β2 refers to the angle between the trailing edge of the blade (outlet end) and the airflow direction. Since both the blade inlet angle and the blade outlet angle are related to the airflow direction, and since the blade 11 has already been installed during the impeller 1 production process, the airflow direction can be adjusted by adjusting the included angle θ of the contraction section 21. This allows the airflow direction to be adapted to the airflow direction corresponding to the impeller 1 design, so that the impeller 1 can operate as close to the design parameters as possible, thereby improving fan efficiency and reducing fan noise and vibration.

[0040] Specifically, the relationship between the included angle θ and the blade inlet angle β1 and the blade outlet angle β2 of the blade 11 conforms to the following formula:

[0041] ;

[0042] Where h1 is the design length of the contraction section 21 along the rotation axis of the impeller 1; D is the diameter of the impeller inlet. The design length h1 of the contraction section 21 is determined according to the design dimensions and installation position of the fan. The changes in the blade inlet angle β1 and the blade outlet angle β2 directly affect the value of the included angle θ, thereby adjusting the inclination of the profile of the contraction section 21. This ensures that the airflow reaches a suitable wind speed and pressure after passing through the contraction section 21, preparing it for entry into the impeller 1. This effectively reduces airflow separation and turbulence, achieving the technical effects of improving fan efficiency and reducing noise and vibration.

[0043] Preferably, the design length h1 of the contraction section 21 ranges from 0.15H to 0.3H, where H is the design length of the collector. That is, the contraction section 21 accounts for no more than 30% of the collector. Due to the determined angle θ, the contraction section 21 can adjust the airflow with a relatively small axial length, providing more axial length for other structures in the collector. This allows the collector to further optimize the airflow under the adjustment of the contraction section 21, ensuring that the airflow entering the impeller 1 is as close as possible to the design parameters of the impeller 1, thereby improving fan efficiency and reducing noise and vibration.

[0044] Furthermore, the collector also includes a transition section 22, which is connected to the end of the contraction section 21 away from the inlet 31. Along the direction away from the inlet 31, the flow area of ​​the transition section 22 first decreases and then increases. The transition section 22 further optimizes the airflow. The reduction in flow area further guides the airflow discharged from the contraction section 21, changing the linear adjustment of the airflow within the contraction section 21 into a curved adjustment, reducing the rate of change of airflow velocity and wind pressure. This reduces separation and turbulence during the adjustment process, preparing for the increase in flow area. Simultaneously, since the flow area at the impeller 1 inlet is larger than the minimum flow area of ​​the transition section 22, the increased flow area is designed to adapt the airflow into the impeller 1 inlet, ensuring that the impeller 1 receives the set airflow. The gradual increase in flow area also avoids excessive changes in flow area that could cause airflow separation and turbulence, achieving the technical effects of improving fan efficiency and reducing noise and vibration.

[0045] In one implementation, the profile of the transition section 22 is arc-shaped, and the radius R1 of the transition section 22 is positively correlated with the blade inlet angle β1 and the blade outlet angle β2 of the blade 11. By designing the profile of the collector transition section 22 using the blade inlet and outlet angles of the blade 11, the profile of the collector can be matched with the size of the impeller 1, allowing for a smooth transition of airflow before entering the impeller 1. This effectively reduces airflow separation and turbulence. Furthermore, by adjusting the radius R1 of the transition section 22, and based on the adjustment of the contraction section 21, the airflow direction is further adjusted to match the airflow direction corresponding to the impeller 1 design. This ensures that the impeller 1 operates as close to its design parameters as possible, thereby improving fan efficiency and reducing fan noise and vibration.

[0046] Specifically, the relationship between the radius R1 of the transition section 22 and the blade inlet angle β1 and the blade outlet angle β2 of the blade 11 conforms to the following formula:

[0047] ;

[0048] Where h2 is the designed length of the transition section 22 along the rotation axis of the impeller 1; D is the diameter of the impeller inlet. The designed length h2 of the transition section 22 is determined according to the design dimensions and installation position of the fan. At this time, the changes in the blade inlet angle β1 and the blade outlet angle β2 will directly affect the value of the radius R1 of the transition section 22, thereby adjusting the curvature of the transition section 22. This allows the airflow to reach a suitable wind speed and wind pressure after passing through the transition section 22, preparing the airflow for entry into the impeller 1. This effectively reduces airflow separation and turbulence, achieving the technical effects of improving fan efficiency and reducing noise and vibration.

[0049] The design length h2 of the transition section 22 ranges from 0.6H to 0.8H, where H is the design length of the collector. The shape of the filter section is fully utilized to further optimize the airflow direction, ensuring that the airflow reaches suitable wind speed and pressure after passing through the transition section 22, thus preparing the airflow for entry into the impeller 1.

[0050] Furthermore, the collector also includes a matching section 23, which is connected to the end of the transition section 22 away from the inlet 31. The flow area of ​​the matching section 23 gradually increases in the direction away from the inlet 31. The matching section 23 further guides the airflow into the impeller 1, preventing separation and turbulence caused by the lack of structural constraints before entering the impeller 1, thus ensuring the working efficiency and stability of the impeller 1. Simultaneously, the matching section 23 can suppress airflow leakage through the gap between the collector and the impeller 1, further ensuring the airflow of the impeller 1 and the working efficiency of the fan.

[0051] The matching section 23 has an arc-shaped profile. The radius R2 of the matching section 23 is positively correlated with the blade inlet angle β1 of the blade 11, and negatively correlated with the blade outlet angle β2. This causes the flow area corresponding to the matching section 23 to gradually increase away from the inlet 31. In this way, the matching section 23 can maintain the optimized airflow effect of the transition section 22, while restricting the airflow flowing towards the periphery of the impeller 1, ensuring the air intake of the impeller 1 and improving the working efficiency of the fan.

[0052] Specifically, the relationship between the radius R2 of the matching segment 23 and the blade inlet angle β1 and the blade outlet angle β2 of the blade 11 conforms to the following formula:

[0053] ;

[0054] Where h3 is the design length of the matching section 23 along the rotation axis of the impeller 1; D is the diameter of the impeller inlet. The design length h3 of the matching section 23 is determined according to the design dimensions and installation position of the fan. At this time, the changes in the blade inlet angle β1 and the blade outlet angle β2 will directly affect the value of the radius R2 of the matching section 23, thereby adjusting the curvature of the matching section 23. This allows the airflow to reach a suitable wind speed and pressure after passing through the transition section 22, preparing the airflow for matching into the impeller 1. This effectively reduces airflow separation and turbulence, achieving the technical effects of improving fan efficiency and reducing noise and vibration.

[0055] The design length h3 of the matching section 23 ranges from 0.05H to 0.1H, where H is the design length of the collector. As the final structure of the collector, the matching section 23 enables the interconnection between the collector and the impeller 1, preventing airflow leakage from the gap between the collector and the impeller 1.

[0056] It is important to emphasize that the transition between the contraction section 21 and the transition section 22 is smooth. By determining the included angle θ of the contraction section 21 and the design length h1 of the contraction section 21, the connection position between the contraction section 21 and the transition section 22 can be determined. Then, the radius R1 of the transition section 22 is determined and the transition section 22 is made tangent to the contraction section 21. This allows us to determine the profile position of the transition section 22 and the center position of the circle corresponding to the profile of the transition section 22. Finally, the radius R2 of the matching section 23 is determined and the transition section 22 is made tangent to the matching section 23. This allows us to determine the profile position of the matching section 23 and the center position of the circle corresponding to the profile of the matching section 23, thus completing the structural design of the collector.

[0057] When designing the collector, first determine the design height H of the collector according to the requirements of the fan, and then determine the design length h1 of the contraction section 21, the design length h2 of the transition section 22 and the design length h3 of the matching section 23 respectively. Then calculate the included angle θ, at which point the shape of the contraction section 21, the diameter d1 of the contraction section 21 forming the inlet 31, and the diameter d2 of the end of the contraction section 21 away from the inlet 31 can be obtained, thus completing the shape design of the contraction section 21.

[0058] Based on the diameter d2 of the end of the contraction section 21 away from the inlet 31, the radius R1 of the transition section 22, and the design length h2 of the transition section 22, and by making the connection position of the transition section 22 tangent to the contraction section 21, the shape of the transition section 22 and the diameter d3 of the end of the transition section 22 away from the contraction section 21 are obtained, and the shape design of the transition section 22 is completed.

[0059] Based on the end diameter d3 of the transition section 22 away from the contraction section 21, the radius R2 of the matching section 23, and the design length h3 of the matching section 23, and by making the connection position of the matching section 23 tangent to the transition section 22, the shape of the matching section 23 and the end diameter d4 of the matching section 23 away from the transition section 22 are obtained, thus completing the shape design of the matching section 23.

[0060] At least part of the matching section 23 extends into the impeller 1, that is, the end of the collector is located inside the impeller 1, and the airflow of the collector can flow directly into the impeller 1, ensuring the working efficiency of the impeller 1. At the same time, the shape of the matching section 23 can block the impeller inlet to a certain extent, thereby preventing the airflow from leaking from the impeller inlet, further ensuring the air volume and working efficiency of the impeller 1.

[0061] Preferably, the connection position between the matching section 23 and the transition section 22 is on the same plane as the inlet of the impeller 1.

[0062] A centrifugal fan includes the aforementioned collector. Comparative tests were conducted on the collector of this application and a conventional conical collector from the prior art. The blade inlet angle β1 was set to a range of 8° to 12°, the blade outlet angle β2 to a range of 40° to 45°, the impeller inlet diameter D to a range of 430mm ± 5mm, and the overall height H of the collector to 103mm ± 3mm. Figure 6 As shown, curve a1 is the pressure performance curve of the centrifugal fan equipped with the collector of this application, and curve a2 is the pressure performance curve of the centrifugal fan equipped with the conventional conical arc collector in the prior art. It can be seen that under different static pressures, the air volume of the centrifugal fan equipped with the collector of this application is increased by 7% to 15% compared with the centrifugal fan equipped with the conventional conical arc collector in the prior art, which effectively improves the working efficiency of the centrifugal fan.

[0063] An air conditioner includes the aforementioned collector or the aforementioned centrifugal fan.

[0064] The embodiments described above are merely illustrative of several implementations of this utility model, and while the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of this utility model patent. It should be noted that those skilled in the art can make various modifications and improvements without departing from the concept of this utility model, and these all fall within the protection scope of this utility model. Therefore, the protection scope of this utility model patent should be determined by the appended claims.

Claims

1. A collector for use in a fan, the fan including an impeller (1) having blades (11) disposed thereon, characterized in that: The collector includes a converging section (21), one end of which forms the inlet (31) of the collector. The flow area of ​​the converging section (21) gradually decreases along the direction away from the inlet (31). The profile of the converging section (21) is a straight line. The profile of the converging section (21) has an angle θ with the plane where the inlet (31) is located. The angle θ is positively correlated with the inlet angle β1 and the outlet angle β2 of the blade (11).

2. The current collector according to claim 1, characterized in that: The relationship between the included angle θ and the inlet angle β1 and outlet angle β2 of the blade (11) conforms to the following formula: ； Where h1 is the design length of the contraction section (21) in the direction of the rotation axis of the impeller (1); D is the diameter of the inlet of the impeller (1).

3. The current collector according to claim 1 or 2, characterized in that: The design length h1 of the contraction section (21) ranges from 0.15H to 0.3H, where H is the design length of the collector.

4. The current collector according to claim 1, characterized in that: The collector also includes a transition section (22), which is connected to the end of the contraction section (21) away from the inlet (31). Along the direction away from the inlet (31), the flow area of ​​the transition section (22) first decreases and then increases.

5. The current collector according to claim 4, characterized in that: The profile of the transition section (22) is arc-shaped, and the radius R1 of the transition section (22) is positively correlated with the inlet angle β1 and the outlet angle β2 of the blade (11).

6. The current collector according to claim 5, characterized in that: The relationship between the radius R1 of the transition section (22) and the inlet angle β1 and outlet angle β2 of the blade (11) conforms to the following formula: ； Where h2 is the design length of the transition section (22) in the direction of the rotation axis of the impeller (1); D is the diameter of the inlet of the impeller (1).

7. The current collector according to any one of claims 4 to 6, characterized in that: The design length h2 of the transition section (22) ranges from 0.6H to 0.8H, where H is the design length of the collector.

8. The current collector according to claim 4, characterized in that: The collector also includes a matching section (23), which is connected to the end of the transition section (22) away from the inlet (31). The flow area of ​​the matching section (23) gradually increases in the direction away from the inlet (31).

9. The current collector according to claim 8, characterized in that: The profile of the matching segment (23) is arc-shaped. The radius R2 of the matching segment (23) is positively correlated with the inlet angle β1 of the blade (11), and the radius R2 of the matching segment (23) is negatively correlated with the outlet angle β2 of the blade (11).

10. The current collector according to claim 9, characterized in that: The relationship between the radius R2 of the matching segment (23) and the inlet angle β1 and outlet angle β2 of the blade (11) conforms to the following formula: ； Where h3 is the design length of the matching section (23) in the direction of the rotation axis of the impeller (1); D is the diameter of the inlet of the impeller (1).

11. The current collector according to any one of claims 8 to 10, characterized in that: The design length h3 of the matching segment (23) ranges from 0.05H to 0.1H, where H is the design length of the collector.

12. The current collector according to any one of claims 8 to 10, characterized in that: At least part of the matching section (23) extends into the impeller (1); or, the connection position of the matching section (23) and the transition section (22) is on the same plane as the inlet of the impeller (1).

13. A centrifugal fan, characterized in that: The collector includes any one of claims 1 to 12.

14. An air conditioner, characterized in that: Includes the collector according to any one of claims 1 to 12 or the centrifugal fan according to claim 13.

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