Fan assembly and air conditioner outdoor unit

Abstract

The invention relates to the technical field of air conditioners, in particular to a fan assembly and an air conditioner outdoor unit, and aims to solve the problem that an existing top air outlet type air conditioner outdoor unit fan is low in efficiency. In order to achieve the purpose, the draught fan assembly comprises a base; the air ring structure is connected with the base; the motor is connected with the impeller, and the impeller and the motor are both arranged in the air ring structure; wherein the base is internally provided with a flow gathering cavity, the cross sectional area of the flow gathering cavity is larger than that of the air ring structure, and the two ends of the base are open, so that airflow can enter the air ring structure through the flow gathering cavity. According to the air conditioner, the flow gathering cavity is formed between the air ring structure and the heat exchanger, the situation that movement of airflow is blocked due to the thickness of the heat exchanger can be avoided, therefore, air pressure provided by the fan assembly can be fully utilized, the energy conversion efficiency of the fan assembly is improved, and the energy consumption of the air conditioner equipment is reduced.

Description

Technical Field

[0001] This application relates to the technical field of air conditioners, and specifically provides a fan assembly and an outdoor unit of an air conditioner. Background Art

[0002] The outdoor unit of the top-outlet air conditioner refers to an air conditioner in which an opening is provided at the top of the outdoor unit, and a fan is installed at the opening at the top, so that during the operation of the air conditioner, the air flow can move from bottom to top and be discharged from the top of the outdoor unit. The natural convection heat dissipation effect of the top-outlet air conditioner is better, which can improve the refrigeration efficiency of the air conditioner and has the advantage of reducing noise.

[0003] In order to improve the heat exchange efficiency, the size of the fan at the top of the outdoor unit of the air conditioner is usually made as large as possible, almost close to the cross-sectional size of the outer casing of the outdoor unit. However, considering that the heat exchanger is located below the fan and the heat exchanger itself has a certain thickness, the heat exchanger will partially block the air inlet of the fan, thus affecting the efficiency of the fan.

[0004] Correspondingly, a new technical solution is needed in this field to solve the above problems. Summary of the Invention

[0005] This application aims to solve the above technical problems, that is, to solve the problem of low efficiency of the fan of the existing top-outlet type outdoor unit of the air conditioner.

[0006] In a first aspect, this application provides a fan assembly, which includes:

[0007] A base;

[0008] A wind ring structure, which is connected to the base;

[0009] An impeller and a motor connected to the impeller, both the impeller and the motor are arranged inside the wind ring structure;

[0010] Wherein, a flow concentrating cavity is provided inside the base, the cross-sectional area of the flow concentrating cavity is larger than the cross-sectional area of the wind ring structure, and both ends of the base are open, so that air flow can enter the wind ring structure through the flow concentrating cavity.

[0011] In a technical solution of the above fan assembly, the wind ring structure includes an equal-diameter part and a first diameter-changing part connected between the equal-diameter part and the base. Along the direction from the base to the equal-diameter part, the cross-sectional area of the first diameter-changing part gradually increases.

[0012] In a technical solution of the above fan assembly, the wind ring structure further includes a second diameter-changing part connected to one end of the equal-diameter part away from the first diameter-changing part. Along the direction from the equal-diameter part to the second diameter-changing part, the cross-sectional area of the second diameter-changing part gradually increases.

[0013] In a technical solution of the above-mentioned fan assembly, the following relationship is satisfied between the height h1 of the base and the diameter d1 of the impeller:

[0014] 0.7d1 ≤ h1 ≤ 0.11d1.

[0015] In a technical solution of the above-mentioned fan assembly, the inner surface of the first reduced-diameter portion is an arc surface.

[0016] In a technical solution of the above-mentioned fan assembly, the following relationship is satisfied between the radius r of the arc surface and the diameter d1 of the impeller:

[0017] 0.035d1 ≤ r ≤ 0.06d1.

[0018] In a technical solution of the above-mentioned fan assembly, the following relationship is satisfied between the height h2 of the first reduced-diameter portion and the radius r of the arc surface:

[0019] 0.9r1 ≤ h2 ≤ 1.5r1.

[0020] In a second aspect, the present application provides an outdoor unit of an air conditioner, which includes:

[0021] A housing having an opening at the top;

[0022] A heat exchanger disposed inside the housing;

[0023] The fan assembly according to any one of the first aspects, which is connected to the housing, the base is installed at the opening, and the orthographic projection of the wind ring structure on the bottom surface of the housing is located within the orthographic projection of the space formed by enclosing the inner wall surface of the heat exchanger on the bottom surface of the housing.

[0024] In a technical solution of the above-mentioned outdoor unit of an air conditioner, the base abuts against the top end of the heat exchanger, and the orthographic projection of the converging cavity on the bottom surface of the housing covers the orthographic projection of the space formed by enclosing the inner wall surface of the heat exchanger on the bottom surface of the housing.

[0025] In a technical solution of the above-mentioned outdoor unit of an air conditioner, the shape of the cross-section of the converging cavity is adapted to the shape of the cross-section of the housing.

[0026] In the case of adopting the above technical solution, in the present application, a flow concentration chamber is arranged inside the base. When the air conditioner is in operation, the fan assembly is started. Under the action of air pressure, the air flow inside the housing first enters the flow concentration chamber from bottom to top. The flow concentration chamber is located between the inside of the housing and the air duct structure, and undertakes the preliminary collection of the air flow inside the housing. On the premise that the flow concentration chamber is always filled with air flow, it is more conducive to the air flow flowing into the air duct structure. On the air flow path, the flow concentration chamber plays an intermediate buffering role for the air flow. Compared with the way of directly installing the air duct structure on the top of the heat exchanger, the collection and discharge of the air flow are smoother. Moreover, due to the setting of the base, the orthographic projection of the air duct structure on the bottom surface of the housing is located within the orthographic projection of the space formed by the inner wall surface of the heat exchanger on the bottom surface of the housing. In this way, it is possible to avoid the blockage of the air flow movement caused by the thickness of the heat exchanger itself, so that the air pressure provided by the fan assembly can be fully utilized, the energy conversion efficiency of the fan assembly is improved, and the energy consumption of the air conditioning equipment is reduced.

[0027] Furthermore, in the present application, the air duct structure is set as an equal-diameter part and a first variable-diameter part. The first variable-diameter part plays a role of transitional connection between the flow concentration chamber and the equal-diameter part. In this way, under the action of air pressure, the air flow in the flow concentration chamber can flow smoothly along the inner surface of the first variable-diameter part to the inside of the equal-diameter part, thereby reducing the kinetic energy loss of the air flow during the process from the flow concentration chamber to the equal-diameter part. In addition, the present application also sets a second variable-diameter part at the air outlet end of the equal-diameter part. When the air flow flows along the air duct structure to its outlet end, the air flow can quickly diffuse around along the inner wall of the second variable-diameter part, rapidly reducing the air pressure at the air outlet end of the air duct structure. In this way, it is more conducive to forming a pressure difference on both sides of the impeller, thereby quickly discharging the air flow inside the housing, improving the overall working efficiency of the fan assembly, and improving the heat dissipation efficiency of the outdoor unit of the air conditioner. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The following describes the preferred embodiments of the present application with reference to the drawings. In the drawings:

[0029] Figure 1 is a schematic diagram of the positional relationship between the fan and the heat exchanger of the top-outlet type outdoor unit of the air conditioner in the related art;

[0030] Figure 2 is a longitudinal sectional view of the outdoor unit of the air conditioner according to an embodiment of the present application;

[0031] Figure 3 is a three-dimensional state schematic diagram of hiding the housing of the outdoor unit of the air conditioner according to an embodiment of the present application;

[0032] Figure 4 is a schematic diagram of the fan assembly according to an embodiment of the present application;

[0033] Figure 5Schematic diagram of the internal structure of a fan assembly according to an embodiment of the present application;

[0034] Figure 6 Front view of a fan assembly according to an embodiment of the present application;

[0035] Figure 7 is Figure 6 top view of;

[0036] Figure 8 Front view of an impeller according to an embodiment of the present application.

[0037] In the figure, the reference numerals refer to the following:

[0038] 1, housing; 2, heat exchanger; 3, fan assembly; 31, base; 311, converging chamber; 32, air ring structure; 321, equal-diameter part; 322, first diameter-changing part; 323, second diameter-changing part; 33, impeller; 34, motor.

[0039] 100, fan; 200, heat exchanger. Detailed implementation manners

[0040] The preferred implementation manners of the present application will be described below with reference to the accompanying drawings. Those skilled in the art should understand that these implementation manners are only used to explain the technical principle of the present application and are not used to limit the protection scope of the present application. Those skilled in the art can make adjustments according to needs to adapt to specific application scenarios.

[0041] It should be noted that in the description of the present application, the terms indicating directions or positional relationships such as "upper", "lower", "left", "right", "inner", "outer", etc. are based on the directions or positional relationships shown in the drawings. This is only for convenience of description and does not indicate or imply that the relevant devices or elements must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present application. In addition, ordinal numbers such as "first", "second", etc. are only used for descriptive purposes and cannot be understood as indicating or implying relative importance.

[0042] In addition, it should also be noted that in the description of the present application, unless otherwise clearly specified and limited, the terms "installation" and "connection" should be understood in a broad sense. For example, it can be a fixed connection, a detachable connection or an integral connection; it can be a mechanical connection or an electrical connection; it can be directly connected or indirectly connected through an intermediate medium. For those skilled in the art, the specific meanings of the above terms in the present application can be understood according to specific situations.

[0043] Refer to Figure 1, which is a schematic diagram of the positional relationship between the fan 100 and the heat exchanger 200 in a top-outlet air conditioner outdoor unit in the related art. Among them, in order to ensure the heat dissipation effect, the diameter of the air circle of the fan 100 is large enough and very close to the size of the cross-section of the outdoor unit housing. However, due to the certain thickness of the heat exchanger 200, the air circle completely covers the heat exchanger 200. During the operation of the air conditioner, the heat exchanger 200 blocks the outer edge part of the air circle, which will affect the movement process of the air flow, making the air pressure provided by the fan 100 unable to be fully utilized, reducing the energy conversion efficiency of the fan 100 and increasing the energy consumption of the equipment.

[0044] Referring to Figure 2 and Figure 3 , in which, Figure 2 is a longitudinal sectional view of an air conditioner outdoor unit according to an embodiment of the present application, Figure 3 is a three-dimensional schematic diagram with the housing of the air conditioner outdoor unit hidden. The air conditioner outdoor unit includes a housing 1, a heat exchanger 2, and a fan assembly 3.

[0045] Among them, the top of the housing 1 has an opening for installing the fan assembly 3. The fan assembly 3 is installed in the above-mentioned opening. The fan assembly 3 can be hermetically connected to the top of the housing 1 through locking parts such as bolts to close the above-mentioned opening. The heat exchanger 2 extends along the inner wall of the housing 1. To ensure that external air can enter the housing 1 and pass through the heat exchanger 2, only structures such as support columns are provided at the position of the side wall of the housing 1 corresponding to the heat exchanger 2 to ensure the overall structural strength of the equipment. When the air conditioner is running, the fan assembly 3 works. Under the action of air pressure, the external air enters through the side wall of the housing 1 and is discharged from the air outlet of the fan assembly 3, thereby taking away the heat on the surface of the heat exchanger 2. Of course, the housing 1 also has necessary components of the air conditioning system such as a compressor and a gas-liquid separator, which are not elaborated in this application.

[0046] According to actual needs, the upper part of the housing 1 can be wrapped outside the air circle structure 32, or the air circle structure 32 can be exposed. This application does not make specific restrictions on this.

[0047] Referring to Figure 4 , which is a schematic diagram of the fan assembly 3 according to an embodiment of the present application, and it includes a base 31, an air circle structure 32, an impeller 33, and a motor 34 connected to the impeller 33 and used to drive the impeller 33 to rotate.

[0048] Referring to Figure 5, which is a schematic internal structure diagram of the fan assembly 3 according to an embodiment of the present application. It should be noted that, in one implementation manner of the present application, the casing 1 of the outdoor unit of the air conditioner is of a square structure. Correspondingly, the overall shape of the base 31 can be selected as a square structure adapted to the shape of the top opening of the casing 1. A flow-condensing cavity 311 is formed inside the base 31, that is, the base 31 is a hollow housing, and the base 31 is adapted to the top opening of the casing 1 to close the top opening of the casing 1.

[0049] In one implementation manner of the present application, the wind ring structure 32 includes an equal-diameter portion 321, a first diameter-changing portion 322, and a second diameter-changing portion 323 that are connected to each other. The inside of the wind ring structure 32 is communicated with the flow-condensing cavity 311 to form a passage for air flow. Among them, the equal-diameter portion 321 serves as the main body portion of the wind ring structure 32, and both the impeller 33 and the motor 34 are installed inside the equal-diameter portion 321. The first diameter-changing portion 322 is connected between the equal-diameter portion 321 and the base 31, and in the direction from the base 31 to the equal-diameter portion 321, the cross-sectional area of the first diameter-changing portion 322 gradually increases. The second diameter-changing portion 323 is connected to one end of the equal-diameter portion 321 away from the first diameter-changing portion 322, and in the direction from the equal-diameter portion 321 to the second diameter-changing portion 323, the cross-sectional area of the second diameter-changing portion 323 gradually increases.

[0050] Optionally, the inner surface of the first diameter-changing portion 322 in the present application is an arc surface, so that the air flow in the flow-condensing cavity 311 can flow smoothly along the arc surface of the first diameter-changing portion 322, reducing the pressure loss caused by air flow disturbance. Of course, in some other possible implementation manners of the present application, the inner surface of the first diameter-changing portion 322 can also be an inclined surface. At this time, the first diameter-changing portion 322 is integrally in the shape of a frustum of a cone, or the first diameter-changing portion 322 can also be a combination of the above two methods, that is, the inner surface of the first diameter-changing portion 322 includes both an arc surface and an inclined surface. The present application does not limit the specific shape of the first diameter-changing portion 322.

[0051] Similarly, the second diameter-changing portion 323 can also adopt the above-mentioned arc surface, inclined surface or the combination of arc surface and inclined surface, and the present application will not elaborate here.

[0052] It should be further noted that for the base 31, the cross-sectional area of the internal flow-condensing cavity 311 is larger than that of the air duct structure 32, and the orthographic projection of the flow-condensing cavity 311 on the upper surface of the base 31 is larger than the orthographic projection of the entire air duct structure 32 on the upper surface of the base 31. In this way, in the present application, by arranging the base 31 between the air duct structure 32 and the heat exchanger 2, when the air conditioner is in operation, the fan assembly 3 starts. Under the action of air pressure, the air flow in the housing 1 first enters the flow-condensing cavity 311 from bottom to top. The flow-condensing cavity 311 is located between the inside of the housing 1 and the air duct structure 32, and undertakes the initial collection of the air flow in the housing 1. On the premise that the flow-condensing cavity 311 is always filled with air flow, it is more conducive to the air flow flowing into the air duct structure 32, thereby improving the work efficiency of the impeller 33.

[0053] As described above, in the present application, by arranging the flow-condensing cavity 311 in the base 31, on the air flow path, the flow-condensing cavity 311 plays an intermediate buffering role for the air flow. Compared with the method of directly installing the air duct structure 32 on the top of the heat exchanger 2, the collection and discharge of the air flow are smoother. Moreover, due to the arrangement of the base 31, the orthographic projection of the air duct structure 32 on the bottom surface of the housing 1 is located within the orthographic projection of the space formed by the inner wall surface of the heat exchanger 2 on the bottom surface of the housing 1. In this way, it can be avoided that the movement of the air flow is blocked due to the thickness of the heat exchanger 2 itself, so that the air pressure provided by the fan assembly 3 can be fully utilized, improving the energy conversion efficiency of the fan assembly 3 and reducing the energy consumption of the air conditioning equipment.

[0054] It should also be noted that since the air duct structure 32 in the present application is set as the equal-diameter part 321 and the first variable-diameter part 322, the first variable-diameter part 322 plays a role of transitional connection between the flow-condensing cavity 311 and the equal-diameter part 321. In this way, under the action of air pressure, the air flow in the flow-condensing cavity 311 can flow smoothly along the inner surface of the first variable-diameter part 322 into the equal-diameter part 321, thereby reducing the kinetic energy loss during the process of the air flow from the flow-condensing cavity 311 to the equal-diameter part 321 (the flow-condensing cavity 311 is designed as a rectangular structure adapted to the housing 1 or the heat exchanger 2, while the overall cross-section of the air duct structure 32 is circular. Therefore, when the air flow flows in the channels with different cross-sections, kinetic energy loss will be generated due to the mutual friction and collision between the air flow and the inner wall of the channel).

[0055] On the other hand, the setting of the first variable-diameter part 322 can also make the diameter of the equal-diameter part 321 relatively smaller. When a cylinder with a smaller diameter is adopted for the equal-diameter part 321, the shielding of the heat exchanger 2 on the impeller 33 can be minimized, which is beneficial to exerting the overall work capacity of the fan assembly 3.

[0056] In addition, since the present application also provides a second reduced-diameter portion 323 at the air outlet end of the equal-diameter portion 321, when the air flow flows along the air duct structure 32 to its outlet end, the air flow can quickly diffuse around along the inner wall of the second reduced-diameter portion 323, rapidly reducing the air pressure at the air outlet end of the air duct structure 32. In this way, it is more conducive to forming a pressure difference on both sides of the impeller 33, thereby quickly discharging the air flow in the housing 1, improving the overall working efficiency of the fan assembly 3, and improving the heat dissipation efficiency of the outdoor unit of the air conditioner.

[0057] Referring to Figure 2 , the relative positional relationship between the fan assembly 3 and the heat exchanger 2 is introduced. As pointed out above, the cross-sectional shapes of the base 31 and the converging chamber 311 are both rectangular, which is considered that in actual production and processing, the outer shape of the outdoor unit of the air conditioner is generally a square structure. Setting the cross-sectional shape of the converging chamber 311 as rectangular is conducive to guiding the air flow in the housing 1 to converge into the converging chamber 311, preventing the side wall of the base 31 from blocking the space formed by enclosing the heat exchanger 2, thereby forming an air pressure blind area and affecting the exhaust process.

[0058] Of course, the cross-sectional shapes of the base 31 and the converging chamber 311 can be determined according to the shapes of the housing 1 and the heat exchanger 2. When the housing 1 is cylindrical, the cross-sectional shapes of the base 31 and the converging chamber 311 can also be set as circular.

[0059] In an implementation manner of the present application, the orthographic projection of the converging chamber 311 on the bottom surface of the housing 1 covers the orthographic projection of the space formed by enclosing the inner wall surface of the heat exchanger 2 on the bottom surface of the housing 1. In this way, when the fan assembly 3 operates, the air flow is more likely to flow upward along the inner wall surface of the heat exchanger 2 into the converging chamber 311. When part of the edge of the converging chamber 311 is located inside the heat exchanger 2, under the action of air pressure, the air flow converges towards the converging chamber 311, and the air flow is likely to separate from the surface of the heat exchanger 2. Through the above setting of the present application, it is beneficial for the air flow to sweep along the surface of the heat exchanger 2, thereby enhancing the heat dissipation effect and improving the refrigeration efficiency of the air conditioning equipment.

[0060] Referring to Figure 6 , Figure 7 and Figure 8 , the dimensions of the fan assembly 3 are introduced. Among them, Figure 6 is the front view of the fan assembly 3 according to an embodiment of the present application, Figure 7 is Figure 6 the top view of Figure 8 is the front view of the impeller 33.

[0061] Figure 6 In Figure 6Taking the first diameter-changing part 322 as an arc segment as an example for illustration, thus r is the radius of the arc segment of the first diameter-changing part 322. d2 is the diameter of the equal-diameter part 321, and d3 is the maximum diameter of the second diameter-changing part 323.

[0062] Figure 7 In it, d1 is the diameter of the impeller 33, L is the transverse width of the base 31, M is the longitudinal width of the base 31, and the values of L and M depend on the size of the casing 1. Among them, L ≤ M, that is, L is the short-side dimension. It can be understood that when the cross-sectional shape of the casing 1 is square, L = M.

[0063] Figure 8 In it, h5 is the height of the impeller 33.

[0064] In an embodiment of the present application, the following relationship is satisfied between the height of the base 31 and the diameter of the impeller 33: 0.07d1 ≤ h1 ≤ 0.11d1.

[0065] The function of the converging cavity 311 has been described above. It is located between the wind ring structure 32 and the heat exchanger 2. On the one hand, it is to prevent the heat exchanger 2 from directly blocking the wind ring structure 32 in the vertical direction. On the other hand, the converging cavity 311 also plays a role in collecting the airflow inside the heat exchanger. Therefore, limiting the height of the base 31 within the above range can ensure that a certain amount of airflow can be stored in the converging cavity 311, so that the airflow in the converging cavity 311 enters the equal-diameter part 321 along the first diameter-changing part 322. On the other hand, affected by the overall height design of the air conditioner outdoor unit, the base 31 cannot be too high.

[0066] Optionally, the following relationship is satisfied between the radius of the arc surface of the first diameter-changing part 322 and the diameter of the impeller 33: 0.035d1 ≤ r ≤ 0.06d1. The following relationship is satisfied between the height of the first diameter-changing part 322 and the radius of the arc surface of the first diameter-changing part 322: 0.9r1 ≤ h2 ≤ 1.5r1.

[0067] Theoretically, the larger the value of r, the better the fluidity of the airflow along the inner surface of the first diameter-changing part 322, and the higher the working efficiency of the fan assembly 3. However, affected by the overall size of the equipment and the sizes of the various components of the fan assembly 3, the value of r is limited within the above range. Of course, the height of h2 should be determined based on the value of r. After determining the optimal value of r based on the above factors, the specific value of h2 is then determined within the above range.

[0068] The following relationship is satisfied between the diameter d2 of the equal-diameter part 321 and the value of L: 0.91L ≤ d2 ≤ 0.94L. The following relationship is satisfied between the height h3 of the equal-diameter part 321 and the height h5 of the impeller 33: 0.9h5 ≤ h3 ≤ 1.2h5.

[0069] The diameter of the equal-diameter part 321 is important for the fan assembly 3. The diameter of the equal-diameter part 321 also determines the diameter of the impeller 33, and both jointly affect the work efficiency of the fan assembly 3. When the diameter of the equal-diameter part 321 is too large, although the generated wind pressure is large and the air volume is sufficient, it will be blocked by the heat exchanger 2, resulting in the underutilization of the wind pressure and reducing the efficiency of the fan assembly 3. Moreover, when the diameter of the equal-diameter part 321 is too large, it will also affect the size of the second variable-diameter part 323, restricting the size design of the second variable-diameter part 323. Therefore, after the diameter of the equal-diameter part 321 increases to the critical value, increasing the diameter further will not only reduce the efficiency but also generate significant noise due to excessive air flow disturbance inside the casing 1. Therefore, controlling d2 within the above range is conducive to ensuring the work efficiency of the fan assembly 3 and reducing the noise of the outdoor unit of the air conditioner while maximizing the wind pressure.

[0070] For a general wind ring structure, the height of the wind ring is generally greater than the height of the impeller, so that the wind ring covers the entire impeller, which can reduce the air pressure loss at the tip clearance and improve the work efficiency. However, for the wind ring structure 32 of the present application, due to the existence of the first variable-diameter part 322, the height of the equal-diameter part 321 can be slightly less than the height of the impeller 33, and the leading edge of the impeller 33 can be placed in the area where the first variable-diameter part 322 is located. In this way, the air pressure loss will not be particularly significant, and in practice, it can be determined according to requirements, and the height of the equal-diameter part 321 can be controlled within the above range.

[0071] The following relationship is satisfied between the maximum diameter d3 of the second variable-diameter part 323 and the diameter d2 of the equal-diameter part 321: 1.05d2 ≤ d3 ≤ 1.2d2. The following relationship is satisfied between the height h4 of the second variable-diameter part 323 and the height h3 of the equal-diameter part 321: 0.25h3 ≤ h4 ≤ 0.5h3.

[0072] On the premise of meeting the design requirements of the size of the outdoor unit of the air conditioner, when the maximum diameter of the second variable-diameter part 323 is as large as possible, the pressure difference formed on both sides of the impeller 33 is more significant, and the efficiency of the fan assembly 3 is higher. The height h4 of the second variable-diameter part 323 is affected by the overall height of the fan assembly 3. On the premise of meeting the size requirements and determining the maximum diameter d of the second variable-diameter part 323, the higher the height of the second variable-diameter part 323, the smoother and more stable the diffusion process of the air flow, and the higher the efficiency of the fan assembly 3.

[0073] As shown in the following table, the inventor tested the static efficiency of the fan assembly 3 of the present application according to actual tests, and at the same time compared it with a traditional fan assembly (the traditional fan is a form in which the diameter of the wind ring structure is close to the size of the casing of the outdoor unit of the air conditioner, and the wind ring structure is in direct contact with the top of the heat exchanger).

[0074] Among them, the static efficiency reflects the ratio between the output power and the input power of the fan. Therefore, the larger the static efficiency, the higher the energy conversion efficiency during the operation of the fan, and the better the performance of the fan. It can be seen that the fan assembly 3 of the present application has a higher energy conversion efficiency than traditional fans, and the performance has been significantly improved.

[0075] So far, the technical solution of the present application has been described in conjunction with the preferred embodiments shown in the drawings. However, those skilled in the art can easily understand that the protection scope of the present application is obviously not limited to these specific embodiments. Without departing from the principle of the present application, those skilled in the art can make equivalent changes or substitutions to the relevant technical features, and the technical solutions after these changes or substitutions will fall within the protection scope of the present application.

Claims

1. A fan assembly, characterized in that, Comprising: A base; A wind ring structure, which is connected to the base; An impeller and a motor connected to the impeller, both the impeller and the motor are arranged inside the wind ring structure; Wherein, a flow concentrating cavity is provided inside the base, the cross-sectional area of the flow concentrating cavity is larger than the cross-sectional area of the wind ring structure, and both ends of the base are open, so that air flow can enter the wind ring structure through the flow concentrating cavity.

2. The fan assembly according to claim 1, characterized in that, The wind ring structure includes an equal-diameter part and a first diameter-changing part connected between the equal-diameter part and the base. In the direction from the base to the equal-diameter part, the cross-sectional area of the first diameter-changing part gradually increases.

3. The fan assembly according to claim 2, characterized in that, The wind ring structure further includes a second diameter-changing part connected to one end of the equal-diameter part away from the first diameter-changing part. In the direction from the equal-diameter part to the second diameter-changing part, the cross-sectional area of the second diameter-changing part gradually increases.

4. The fan assembly according to claim 2, wherein, The following relationship is satisfied between the height h1 of the base and the diameter d1 of the impeller: 0.7d1 ≤ h1 ≤ 0.11d1.

5. The blower assembly according to claim 2, wherein The inner surface of the first diameter-changing part is an arc surface.

6. The fan assembly according to claim 5, characterized in that, The following relationship is satisfied between the radius r of the arc surface and the diameter d1 of the impeller: 0.035d1 ≤ r ≤ 0.06d1.

7. The fan assembly according to claim 6, wherein, The following relationship is satisfied between the height h2 of the first diameter-changing part and the radius r of the arc surface: 0.9r1≤h2≤1.5r1。 8. An outdoor unit of an air conditioner, characterized in that, Comprising: A casing, which has an opening at the top; A heat exchanger, which is arranged inside the casing; The fan assembly according to any one of claims 1 to 7, which is connected to the casing, the base is installed at the opening, and the orthographic projection of the wind ring structure on the bottom surface of the casing is located within the orthographic projection on the bottom surface of the casing of the space surrounded by the inner wall surface of the heat exchanger.

9. The outdoor air conditioner according to claim 8, characterized in that, The base abuts against the top end of the heat exchanger, and the orthographic projection of the flow concentrating cavity on the bottom surface of the casing covers the orthographic projection on the bottom surface of the casing of the space surrounded by the inner wall surface of the heat exchanger.

10. The outdoor air conditioner according to claim 9, characterized in that, The shape of the cross-section of the flow concentrating cavity is adapted to the shape of the cross-section of the casing.

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