Flange structure for optimizing blower order noise

Abstract

This invention provides a flange structure for optimizing blower noise levels, comprising a flange, an impeller, and a motor. The flange has a through hole at its center, through which the motor output is connected to the impeller hub. The impeller hub is positioned opposite one end face of the flange, with a gap between the hub and the flange end face. Multiple recesses are distributed on the flange end face in a non-array, random arrangement. Each recess includes a first recess and a second recess of varying sizes, randomly and alternately distributed on the flange end face. The diameter of each recess is 3-8 mm, and the depth is 1 / 4-1 / 2 of its diameter.

Description

Technical Field

[0001] This invention relates to the field of automotive technology, and more specifically, to a flange structure for optimizing blower noise levels. Background Technology

[0002] With the rapid development of the new energy vehicle industry, the NVH performance of the air conditioning and heating system of vehicles has been placed under more stringent requirements. Traditional automotive air conditioning blower flanges often employ a smooth end-face structure, and the axial clearance between the flange and the impeller hub easily forms a stable eddy current resonance cavity. This significantly amplifies the order noise generated by the impeller rotation, creating high-frequency, sharp noise inside the vehicle, severely impacting driving comfort. Existing similar technologies typically employ noise reduction by attaching fiber-based sound-absorbing cotton to the inner wall of the blower casing. For example, Chinese patent application number CN202410778814.1 discloses an automotive air conditioning blower, comprising an air supply mechanism and a noise reduction mechanism. The noise reduction mechanism absorbs noise by setting a noise reduction cavity and sound-absorbing cotton within the casing body, utilizing a micro-perforated resonance cavity and porous sound-absorbing material. The design of the noise reduction cavity adjusts the resonance frequency by changing the shape and thickness of the inner casing, covering the high-frequency noise range.

[0003] However, this type of solution has obvious drawbacks: on the one hand, the sound-absorbing cotton will occupy the flow channel space, resulting in a decrease of 8% to 12% in the blower's air output efficiency, affecting the heat exchange and air supply performance of the air conditioning system; on the other hand, the sound-absorbing cotton is prone to aging, shedding, and powdering failure under the long-term scouring action of high temperature and high humidity airflow. The shed fiber debris can enter the passenger compartment with the air conditioning air supply, causing health hazards such as odors in the vehicle, respiratory irritation, and allergies. At the same time, fiber debris is easy to get into the impeller, significantly increasing the risk of impeller jamming, abnormal fan noise, and even failure of the entire machine. Summary of the Invention

[0004] To address the shortcomings of existing technologies, the purpose of this invention is to provide a flange structure that optimizes the order noise of a blower.

[0005] According to the present invention, a flange structure for optimizing the order noise of a blower includes a flange, an impeller, and a motor. The flange has a through hole at its center. The output end of the motor passes through the through hole and is connected to the hub of the impeller. The impeller hub is disposed opposite to one end face of the flange. There is a gap between the hub and the end face of the flange. Multiple pits are distributed on the end face of the flange. The pits are distributed in a non-array, disordered manner.

[0006] Preferably, the pits include a first pit and a second pit of different sizes, and the first pit and the second pit are randomly and alternately distributed on the end face of the flange.

[0007] Preferably, the diameter of the pit is 3-8 mm.

[0008] Preferably, the depth of the pit is 1 / 4 to 1 / 2 of the diameter.

[0009] Preferably, for impellers with an outer diameter of 120mm to 200mm, the equivalent diameter of the recess is set to 1 / 35 to 1 / 20 of the impeller's outer diameter.

[0010] Preferably, the arrangement of the pits includes a regular hexagonal arrangement, a concentric circle staggered arrangement, a rhombus arrangement, and a triangular arrangement.

[0011] Preferably, the impeller hub has multiple circumferentially distributed blades on its outer periphery.

[0012] Compared with the prior art, the present invention has the following beneficial effects: This invention, without altering the original assembly structure of the blower or sacrificing its airflow and pressure performance, creates an irregularly staggered array of two or more different convex and concave structural units on the flange surface. This disrupts the periodic flow of the fluid, effectively eliminating eddy current resonance between the flange and the impeller, and suppressing the blower's order noise. Simultaneously, the structure is characterized by simple manufacturing processes, ease of mass production, high reliability, and long service life, meeting the needs of large-scale vehicle applications.

[0013] The blower noise reduction flange disclosed in this invention features a simplified and rational structural design with a high degree of integration. It achieves efficient suppression of blower noise without requiring any additional assembly processes, while fully preserving the original blower's key performance parameters such as airflow, air pressure, and aerodynamic efficiency, without altering the overall system's fluid dynamics characteristics. Compared to traditional noise reduction solutions that rely on pasted sound-absorbing cotton, this structure fundamentally eliminates the inherent defects of sound-absorbing materials such as aging, shedding, and pulverization. It also eliminates the health and safety hazards posed by fiber debris entering the passenger compartment, as well as reliability risks such as jamming, abnormal noise, and even blower failure caused by foreign objects being drawn into the impeller. This structure is highly compatible with existing mold structures, injection molding processes, and vehicle assembly systems, and can directly replace traditional smooth-face flanges for mass replacement and large-scale application. While significantly optimizing high-frequency noise quality within the vehicle and improving driving acoustic comfort, it effectively reduces the product's life-cycle maintenance costs, significantly improving overall product reliability, service life, and core market competitiveness. Attached Figure Description

[0014] Other features, objects, and advantages of the present invention will become more apparent from the following detailed description of non-limiting embodiments with reference to the accompanying drawings: Figure 1 A schematic diagram showing the distribution of pits on the flange surface. In the diagram, 1 is the flange; 2 is the first recess; and 3 is the second recess. Detailed Implementation

[0015] The present invention will now be described in detail with reference to specific embodiments. These embodiments will help those skilled in the art to further understand the present invention, but do not limit the invention in any way. It should be noted that those skilled in the art can make several changes and improvements without departing from the concept of the present invention. These all fall within the protection scope of the present invention.

[0016] A flange structure for optimizing the order noise of a blower includes a flange, an impeller, and a motor. The flange has a through hole at its center, and the output end of the motor passes through the through hole and is connected to the hub of the impeller. The impeller hub has multiple circumferentially distributed blades on its outer periphery.

[0017] In this embodiment, the impeller hub is disposed opposite to one end face of the flange, and there is a gap between the hub and the flange end face. Multiple recesses are distributed on the flange end face, including first and second recesses of different sizes. The first and second recesses are randomly and alternately distributed on the flange end face. Based on the above scheme, the pit array can adopt any geometric arrangement, including but not limited to regular hexagonal arrangement, concentric circle staggered arrangement, and also rhomboid arrangement, triangular arrangement, random irregular arrangement, etc. By rationally planning the spatial distribution density and spacing of the pit units, the flow field disturbance between the flange end face and the impeller gap can be uniformly covered throughout the entire area, effectively avoiding local flow field resonance, thereby obtaining a more balanced, stable and controllable order noise suppression effect, and adapting to the noise reduction requirements under different working conditions.

[0018] It should be noted that the pits are evenly distributed on the flange end face in an array. In order to avoid the coupling with the impeller rotation frequency caused by the regular periodic grid arrangement, which would induce new order noise and resonant howling, this solution adopts an irregular arrangement. The pits are not arranged in neat rows and columns, and there is no fixed row or column spacing. They do not repeat periodically, and no completely replicated repeating points can be found in any local area. At the same time, the pits of different sizes are randomly interspersed and not fixedly alternating between large and small. They are scattered and dispersed, breaking up the original regular inter-periodic vortices and destroying the inherent periodicity of the flow field. This can reduce noise without generating new aerodynamic noise, and does not affect air volume or air pressure.

[0019] Understandably, the inner wall features a smooth curved surface design with no sharp edges or corners to avoid generating additional eddy current interference.

[0020] In this embodiment, the diameter of the pit is 3-8mm. Preferably, the depth of the pit is 1 / 4-1 / 2 of the diameter. Preferably, for an impeller with an outer diameter of 120mm-200mm, the equivalent diameter of the pit is set to 1 / 35-1 / 20 of the impeller's outer diameter.

[0021] It should be noted that the gap between the blower impeller and the flange is usually 4-10mm. Tests have shown that the diameter of the recess cannot be larger than the gap size. If it is too large, it will become a cavity and increase noise. If it is too small, it will not achieve the effect of smooth flow and noise reduction. 3-8mm is in line with the classic characteristics of turbulence control recess. At the same time, the depth of the recess is 1 / 4 to 1 / 2 of the diameter. This is the golden ratio determined by combining the optimal range of fluid depth-to-diameter ratio for noise reduction, avoiding secondary eddies, flange structural rigidity, and processing technology simulation and experimental calibration.

[0022] In this embodiment, the arrangement of the pits includes a regular hexagonal arrangement, a concentric circle staggered arrangement, a rhombus arrangement, and a triangular arrangement.

[0023] Working principle: By using the non-periodic distribution of the pit array, the stable flow field formed by the traditional smooth end face is broken, and the formation conditions of the vortex resonance cavity are destroyed, thereby achieving effective suppression of order noise. At the same time, it ensures that the blower's air output efficiency is not reduced and the air volume is not lost, completely avoiding the hidden dangers caused by the shedding and pulverization of traditional fiber sound-absorbing cotton.

[0024] In the description of this application, it should be understood that the terms "upper", "lower", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0025] Specific embodiments of the present invention have been described above. It should be understood that the present invention is not limited to the specific embodiments described above, and those skilled in the art can make various changes or modifications within the scope of the claims, which do not affect the essence of the present invention. Unless otherwise specified, the embodiments and features described in this application can be arbitrarily combined with each other.

Claims

1. A flange plate structure for optimizing the order noise of a blower, characterized by, The device includes a flange, an impeller, and a motor. The flange has a through hole at its center. The output end of the motor passes through the through hole and is connected to the hub of the impeller. The impeller hub is positioned opposite one end face of the flange. There is a gap between the hub and the end face of the flange. Multiple pits are distributed on the end face of the flange in a non-array, disordered arrangement.

2. The flange structure for optimizing the blower order noise according to claim 1, wherein The pits include a first pit and a second pit of different sizes, which are randomly and alternately distributed on the end face of the flange.

3. The flange structure for optimizing the blower order noise according to claim 1, wherein The diameter of the pit is 3-8mm.

4. The flange structure for optimizing blower noise levels according to claim 3, characterized in that, The depth of the pit is 1 / 4 to 1 / 2 of its diameter.

5. The flange structure for optimizing blower noise levels according to claim 1, characterized in that, For impellers with an outer diameter of 120mm to 200mm, the equivalent diameter of the recess is set to 1 / 35 to 1 / 20 of the impeller's outer diameter.

6. The flange structure for optimizing blower noise levels according to claim 1, characterized in that, The arrangement of the pits includes regular hexagonal arrangement, concentric circle staggered arrangement, rhombus arrangement and triangular arrangement.

7. The flange structure for optimizing blower noise levels according to claim 1, characterized in that, The impeller hub has multiple circumferentially distributed blades.

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