Centrifugal fan wheel, fresh air module and air conditioner

Abstract

The application relates to the technical field of air conditioners, and discloses a centrifugal fan, a fresh air module and an air conditioner. The centrifugal fan provided by the application comprises a disc and a plurality of first fan blades, the plurality of first fan blades are arranged in a non-uniform interval on one side of the disc, and the phase angle difference values of adjacent first fan blades are in sinusoidal function distribution. The centrifugal fan, by arranging the plurality of first fan blades in a non-uniform interval on one side of the first disc, makes the air ducts formed between the first fan blades have different sizes, which not only helps to reduce the resonance of the first fan blades caused by the airflow passing through the air ducts, but also reduces the flow loss, improves the total pressure efficiency and air volume output of the centrifugal fan, and solves the problem of uneven airflow distribution during the operation of the centrifugal fan.

Description

Technical Field

[0001] This application belongs to the field of air conditioner technology, and particularly relates to centrifugal fan impellers, fresh air modules and air conditioners. Background Technology

[0002] Air conditioners with integrated fresh air modules are increasingly favored by users. These modules introduce outdoor air into the indoor space, effectively improving indoor air quality. However, existing fresh air modules suffer from uneven airflow distribution as they pass through the centrifugal impeller, generating significant turbulence noise.

[0003] Therefore, improvements to existing technologies are necessary.

[0004] The above information is provided as background information only to aid in understanding this disclosure and does not constitute an assertion or admission that any of the above content can be used as prior art relative to this disclosure. Utility Model Content

[0005] This application provides a centrifugal fan, a fresh air module, and an air conditioner to solve the problem of uneven airflow distribution when the centrifugal fan is running.

[0006] In a first aspect, embodiments of this application provide a centrifugal impeller, including a disc and a plurality of first blades, wherein the plurality of first blades are arranged sequentially at non-uniform intervals on one side of the disc, and the phase angle difference between adjacent first blades is distributed as a sine function.

[0007] In one possible implementation, the sinusoidal modulation formula for the phase angle difference between adjacent first blades is:

[0008]

[0009] Where i represents the number of the first wind turbine blade, n represents the total number of the first wind turbine blades, m represents the modulation period of the distribution angle of the first blade, A represents the modulation amplitude of the first blade, and Δθ i This represents the phase angle difference between the i-th blade and the (i-1)-th blade.

[0010] In one possible implementation, the wheel includes multiple sectors, and the modulation amplitude of the first wind blades located in different sectors is different. The sinusoidal modulation formula for the phase angle difference between adjacent first wind blades is:

[0011]

[0012] Where j represents the sector number, A j This represents the modulation amplitude of the j-th sector.

[0013] In one possible implementation, the centrifugal impeller further includes a plurality of disturbance blades, the impeller disc includes a plurality of disturbance points, the disturbance blades are used to replace the first blades located at the disturbance points, and the disturbance blades are offset relative to the first blades located at the corresponding disturbance points.

[0014] In one possible implementation, the offset between the first blade located at different disturbance points and the corresponding disturbance blade is different; the phase angle difference between the disturbance blade and the adjacent first blade satisfies:

[0015] ΔΘ k =Δθ k +B k

[0016] Where k represents the number of the disturbance point, Δθ k B represents the phase angle difference between the first blade at the disturbance point and the adjacent first blade. k Indicates the disturbance offset value, ΔΘ k This represents the phase angle difference between the disturbing blade and the adjacent first blade.

[0017] In one possible implementation, the centrifugal impeller further includes a plurality of second blades, which are sequentially and spaced apart on the side of the impeller away from the first blade, with each second blade corresponding to one of the first blades.

[0018] In one possible implementation, the phase angle difference between the second blade and the corresponding first blade follows a sinusoidal distribution.

[0019] In one possible implementation, the phase angle difference between the second blade and the corresponding first blade satisfies:

[0020] Δδ i =Δθ i +C sin(Φ i )

[0021] Where C represents the modulation amplitude of the first blade, Φ i Δδ represents the phase angle difference between the i-th blade and the 0th blade. i This represents the phase angle difference between the second blade and the corresponding first blade.

[0022] Secondly, embodiments of this application also provide a fresh air module, the fresh air module including the centrifugal impeller as described in any of the preceding claims.

[0023] Thirdly, embodiments of this application also provide an air conditioner, which includes the fresh air module as described above.

[0024] Compared with the prior art, this application has the following beneficial effects:

[0025] The centrifugal impeller provided in this application embodiment, by non-uniformly spacing multiple first blades on one side of the first impeller, creates air ducts with different sizes between the first blades. This not only helps to reduce resonance of the first blades when airflow passes through the air duct, but also reduces flow loss, improves the total pressure efficiency and air volume output of the centrifugal impeller, and solves the problem of uneven airflow distribution when the centrifugal impeller is running. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this application, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0027] To gain a more complete understanding of this application and its beneficial effects, the following description will be provided in conjunction with the accompanying drawings. In the following description, the same reference numerals denote the same parts.

[0028] Figure 1 This is a schematic diagram of the centrifugal impeller provided in an embodiment of this application. Detailed Implementation

[0029] To illustrate the possible application scenarios, technical principles, implementable specific solutions, and achievable objectives and effects of this application in detail, the following description, in conjunction with the listed specific embodiments and accompanying drawings, provides a detailed explanation. The embodiments described herein are merely illustrative of the technical solutions of this application and are therefore intended to limit the scope of protection of this application.

[0030] In the description of this application, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, features defined with "first" and "second" may explicitly or implicitly include one or more features.

[0031] The technical solutions in the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings.

[0032] This application provides a centrifugal fan, a fresh air module, and an air conditioner to solve the problem of uneven airflow distribution during centrifugal fan operation. The following description will be provided in conjunction with the accompanying drawings.

[0033] This application provides a centrifugal impeller, including a disc 1 and a plurality of first blades 2. The plurality of first blades are arranged at non-uniform intervals on one side of the disc, and the phase angle difference between adjacent first blades is distributed in a sinusoidal function.

[0034] By non-uniformly spacing multiple first fan blades on one side of the first impeller, the air ducts formed between the first fan blades have different sizes. This not only helps to reduce the resonance of the first fan blades when the airflow passes through the air duct, but also reduces flow loss, improves the total pressure efficiency and air volume output of the centrifugal impeller, and solves the problem of uneven airflow distribution when the centrifugal impeller is running.

[0035] The sinusoidal modulation formula for the phase angle difference between adjacent first blades is:

[0036]

[0037] Where i represents the number of the first wind turbine blade, n represents the total number of the first wind turbine blades, m represents the modulation period of the distribution angle of the first blade, A represents the modulation amplitude of the first blade, and Δθ i This represents the phase angle difference between the i-th blade and the (i-1)-th blade.

[0038] The rotary disc comprises multiple sectors, and the modulation amplitude of the first blade located in different sectors is different. The sinusoidal modulation formula for the phase angle difference between adjacent first blades is:

[0039]

[0040] Where j represents the sector number, A j This represents the modulation amplitude of the j-th sector.

[0041] In this embodiment, the number of sectors is set to three, each sector being the same size, with A1 having a value of 2°, A2 having a value of 1°, and A3 having a value of 3°. In some embodiments of this application, the number of sectors is set to multiple, with each sector having a different size and a different modulation amplitude. By making different sectors have different modulation amplitudes, the acoustic resonant path can be disrupted, and the local discrete frequencies of the acoustic wave can be weakened, thereby achieving a noise reduction effect.

[0042] The centrifugal impeller also includes multiple disturbance blades, and the impeller includes multiple disturbance points. The disturbance blades are used to replace the first blades located at the disturbance points, and the disturbance blades are offset relative to the first blades located at the corresponding disturbance points.

[0043] The degree of offset between the first blade located at different disturbance points and the corresponding disturbance blade is different; the phase angle difference between the disturbance blade and the adjacent first blade satisfies:

[0044] ΔΘ k =Δθ k +B k

[0045] Where k represents the number of the disturbance point, Δθ kB represents the phase angle difference between the first blade at the disturbance point and the adjacent first blade. k Indicates the disturbance offset value, ΔΘ k This represents the phase angle difference between the disturbing blade and the adjacent first blade.

[0046] Specifically, in this embodiment, a disturbance blade is provided every eleven first blades, and the shape of the disturbance blade is the same as that of the first blade. k The value range is 1°-3°. The setting of the disturbance blades can create local disturbance peaks in the sound wave, break the synchronization of the sound field, enhance the sound field dispersion ability, and help reduce the resonance amplification of the sound wave.

[0047] The centrifugal impeller also includes multiple second blades 2, which are sequentially and spaced apart on the side of the impeller away from the first blade. Each second blade corresponds to one of the first blades. The phase angle difference between the second blade and its corresponding first blade follows a sinusoidal function distribution. The phase angle difference between the second blade and its corresponding first blade satisfies:

[0048] Δδ1=Δθ i +C sin(Φ i )

[0049] Where C represents the modulation amplitude of the first blade, Φ i Δδ represents the phase angle difference between the i-th blade and the 0th blade. i This represents the phase angle difference between the second blade and the corresponding first blade.

[0050] The placement of the second fan blade enhances the air collection capacity at the bottom of the rotor. In this embodiment, the value of C is 1°. By offsetting the second fan blade from the corresponding first fan blade in terms of angle, the propagation path of the sound wave can be interrupted, which helps to reduce noise.

[0051] This application also provides a fresh air module, which includes the centrifugal impeller as described above. Since this fresh air module has the aforementioned centrifugal impeller, it possesses at least some or all of the beneficial effects of the aforementioned centrifugal impeller, which will not be elaborated upon here.

[0052] This application also provides an air conditioner that includes the fresh air module described above. Since this air conditioner has the aforementioned fresh air module, it possesses at least some or all of the beneficial effects of the aforementioned fresh air module, which will not be elaborated upon here.

[0053] In the above embodiments, the descriptions of each embodiment have different focuses. For parts not described in detail in a certain embodiment, please refer to the relevant descriptions in other embodiments.

[0054] Finally, it should be noted that although the above embodiments have been described in the text and drawings of this application, this should not limit the scope of patent protection of this application. Any technical solutions that are based on the essential concept of this application and utilize the content described in the text and drawings of this application, resulting in equivalent structural or procedural substitutions or modifications, as well as the direct or indirect application of the technical solutions of the above embodiments to other related technical fields, are all included within the scope of patent protection of this application.

Claims

1. A centrifugal impeller, characterized in that, It includes a wheel and multiple first wind blades, which are arranged sequentially at non-uniform intervals on one side of the wheel, and the phase angle difference between adjacent first wind blades is distributed as a sine function.

2. The centrifugal impeller according to claim 1, characterized in that, The sinusoidal modulation formula for the phase angle difference between adjacent first blades is: Where i represents the number of the first wind turbine blade, n represents the total number of the first wind turbine blades, m represents the modulation period of the distribution angle of the first blade, A represents the modulation amplitude of the first blade, and Δθ i This represents the phase angle difference between the i-th blade and the (i-1)-th blade.

3. The centrifugal impeller according to claim 2, characterized in that, The disk comprises multiple sectors, and the modulation amplitude of the first wind blades located in different sectors is different. The sinusoidal modulation formula for the phase angle difference between adjacent first wind blades is: Where j represents the sector number, A j This represents the modulation amplitude of the j-th sector.

4. The centrifugal impeller according to claim 3, characterized in that, The centrifugal impeller also includes multiple disturbance blades, and the impeller includes multiple disturbance points. The disturbance blades are used to replace the first blades located at the disturbance points, and the disturbance blades are offset relative to the first blades located at the corresponding disturbance points.

5. The centrifugal impeller according to claim 4, characterized in that, The degree of offset between the first wind blade located at different disturbance points and the corresponding disturbance wind blade is different; the phase angle difference between the disturbance wind blade and the adjacent first wind blade satisfies: DTH k =Δθ k +B k Where k represents the number of the disturbance point, Δθ k B represents the phase angle difference between the first blade at the disturbance point and the adjacent first blade. k Indicates the disturbance offset value, ΔΘ k This represents the phase angle difference between the disturbing blade and the adjacent first blade.

6. The centrifugal impeller according to claim 1, characterized in that, The centrifugal impeller also includes a plurality of second blades, which are arranged sequentially at intervals on the side of the impeller away from the first blade, and the second blades correspond one-to-one with the first blades.

7. The centrifugal impeller according to claim 6, characterized in that, The phase angle difference between the second blade and the corresponding first blade follows a sinusoidal distribution.

8. The centrifugal impeller according to claim 7, characterized in that, The phase angle difference between the second blade and the corresponding first blade satisfies: Dd i =Δθ i +C sin(Φ i ) Where C represents the modulation amplitude of the first blade, Φ i Δδ represents the phase angle difference between the i-th blade and the 0th blade. i This represents the phase angle difference between the second blade and the corresponding first blade.

9. A fresh air module, characterized in that, The fresh air module includes a centrifugal fan as described in any one of claims 1-8.

10. An air conditioner, characterized in that, The air conditioner includes the fresh air module as described in claim 9.

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