A fan and a range hood

Abstract

This utility model relates to a fan, including a volute and an impeller disposed within the volute. Multiple small holes are formed on the peripheral wall of the volute, and sound-absorbing cotton is attached to the outer periphery of the volute. The outline of the peripheral wall of the volute is a first spiral, and the outline of the outer periphery of the sound-absorbing cotton is a second spiral matching the spiral direction of the first spiral. The thickness of the sound-absorbing cotton at the starting point of the second spiral is less than the thickness at the ending point of the second spiral. The fan in this utility model uses a special sound-absorbing cotton outline, which can match the airflow changes within the volute, fully utilizing the sound absorption effect of the sound-absorbing cotton and improving noise reduction. This utility model also relates to a range hood, including the aforementioned fan.

Description

Technical Field

[0001] This utility model relates to a fan and a range hood that uses the fan. Background Technology

[0002] In existing technologies, the noise generated by range hoods is a significant factor affecting consumer comfort and poses certain health risks. The centrifugal fan is a key component of a range hood, and controlling its noise primarily involves controlling the noise of the centrifugal fan. Centrifugal fan noise, based on its source, mainly consists of four parts: outlet noise, inlet noise, motor noise, and casing noise. When gas flows through the fan, it is accelerated by the impeller, increasing its flow velocity. Upon leaving the impeller, the flow channel suddenly expands, causing a sharp change in velocity. The gas is then guided out by the volute casing, which acts as a collector and is the primary noise source.

[0003] To address the noise problem caused by the volute casing, existing fan manufacturers use perforated volute casings wrapped with sound-absorbing cotton of equal thickness on the outside. For example, the Chinese utility model patent "Volute Component and Range Hood" (CN222863681U, application number 202420919971.5) discloses a volute casing and component with perforated casings wrapped with sound-absorbing cotton of equal thickness. However, in order to accommodate changes in airflow and velocity, the casing's enclosure is spirally designed. Therefore, based on the airflow direction, the airflow volume, air pressure, and air velocity within the casing all change, resulting in varying noise sound pressure levels and power. Sound-absorbing cotton of equal thickness cannot accommodate these changes in airflow within the casing. To ensure good noise reduction, very thick sound-absorbing cotton is required, leading to high costs. Furthermore, due to space constraints, the thickness of the sound-absorbing cotton is often maximized within a limited space, making it difficult to guarantee effective noise reduction. In this type of structure, the sound-absorbing cotton often only serves as sound insulation, with poor sound absorption. Utility Model Content

[0004] The first technical problem to be solved by this utility model is to provide a fan that uses a special sound-absorbing cotton profile to match the airflow changes inside the volute, fully utilize the sound absorption effect of the sound-absorbing cotton, and improve the noise reduction effect, in contrast to the above-mentioned prior art.

[0005] The second technical problem to be solved by this utility model is to provide a range hood with better noise reduction effect compared with the above-mentioned prior art.

[0006] The technical solution adopted by this utility model to solve the first technical problem mentioned above is: a fan, including a volute and an impeller disposed inside the volute, wherein a plurality of small holes are provided on the peripheral wall of the volute, and sound-absorbing cotton is attached to the outer side of the peripheral wall of the volute.

[0007] The peripheral wall contour of the volute is a first spiral, and the outer peripheral wall contour of the sound-absorbing cotton is a second spiral that matches the spiral direction of the first spiral. The thickness of the sound-absorbing cotton at the starting point of the second spiral is less than the thickness at the ending point of the second spiral.

[0008] Preferably, both the first spiral and the second spiral are Fibonacci spirals, with the first number of the Fibonacci sequence corresponding to the first spiral being a1 and the first number of the Fibonacci sequence corresponding to the second spiral being a2, where a2 > a1.

[0009] Preferably, a2 = k * a1, 1.1 ≤ k ≤ 1.2.

[0010] Preferably, the maximum thickness of the sound-absorbing cotton is dd;

[0011] dd=(a2-a1)+(D2-D1) / 2; where D1 is the inner diameter of the impeller and D2 is the outer diameter of the impeller.

[0012] To ensure the stability of the sound-absorbing cotton structure and position, protect the sound-absorbing cotton from damage, and further enhance the noise reduction effect, the sound-absorbing cotton is wrapped with a protective shell. The protective shell includes multiple connected planar plates arranged along the outer periphery of the sound-absorbing cotton. Each planar plate is tangent to the midpoint of an arc segment in the second spiral line corresponding to the sound-absorbing cotton.

[0013] Preferably, the two ends of the protective shell are fixed to the air outlet of the volute.

[0014] Preferably, both the first spiral and the second spiral are Fibonacci spirals, and the first number of the Fibonacci sequence corresponding to the first spiral is a1;

[0015] Matching the spiral direction of the second spiral, the length of each planar plate along the circumferential direction is Ln, Ln=0.325*[D1+(n+1)*a1], where n is the arc segment number corresponding to the spiral direction of the second spiral.

[0016] The technical solution adopted by this utility model to solve the second technical problem mentioned above is: a range hood, including the aforementioned fan.

[0017] Compared with the prior art, the advantages of this utility model are as follows: The fan in this invention has sound-absorbing cotton set outside the volute, and the outer peripheral wall contour of the sound-absorbing cotton is defined. The outer peripheral wall contour of the sound-absorbing cotton is made into a spiral to match the spiral direction of the spiral of the volute peripheral wall, so that the sound-absorbing cotton is in a non-uniform thickness state. This can effectively match the changes in noise sound pressure level and noise sound power caused by changes in airflow, air pressure, and air speed inside the volute. Based on the special structural setting of the outer contour of the sound-absorbing cotton as a spiral, the thickness change of the sound-absorbing cotton can just match the noise sound pressure level and noise sound power corresponding to the airflow inside the volute, achieving better sound insulation and sound absorption effects, and the noise reduction effect is more prominent.

[0018] In addition, based on the special design of the outer contour of the sound-absorbing cotton, it occupies a small volume while meeting the noise reduction requirements, which is conducive to the utilization of the space inside the range hood and can save the cost of sound-absorbing cotton.

[0019] Range hoods using this fan are quieter and offer a better user experience. Attached Figure Description

[0020] Figure 1 This is a perspective view of the fan in an embodiment of this utility model.

[0021] Figure 2 This is a cross-sectional view of the fan in an embodiment of this utility model.

[0022] Figure 3 This is a diagram showing the markings of the fan in an embodiment of this utility model. Detailed Implementation

[0023] The present invention will be further described in detail below with reference to the accompanying drawings and embodiments.

[0024] like Figure 1 Paper Figure 3 As shown, the fan in this embodiment includes a volute 1, an impeller 2 disposed inside the volute 1, sound-absorbing cotton 3 disposed on the outer periphery of the volute 1, and a protective shell 4 wrapped around the sound-absorbing cotton 3 and connected to the volute 1.

[0025] When the fan is working, external airflow enters the volute 1 through one side of the impeller 2, and flows along the guide direction of the volute 1 under the rotation of the impeller 2, and is finally discharged through the outlet of the volute 1. Under the action of the impeller 2, the airflow entering the volute 1 changes in its flow direction, and its air volume, air velocity, and air pressure will all change. In order to effectively match this change in airflow, the contour line of the peripheral wall of the volute 1 is set as a first spiral. In addition, multiple small holes 11 are opened on the peripheral wall of the volute 1, and sound-absorbing cotton 3 is attached to the outside of the peripheral wall of the volute 1. In this way, the airflow interacts with the small holes 11 and the sound-absorbing cotton 3, thereby using the sound-absorbing cotton 3 to isolate and absorb the noise generated by the airflow, achieving a noise reduction effect.

[0026] Accordingly, in this embodiment, the outer peripheral wall contour of the sound-absorbing cotton 3 is set as a second spiral line matching the spiral direction of the first spiral line. That is, along the flow direction of the airflow inside the volute 1, the thickness of the sound-absorbing cotton 3 gradually increases. Specifically, the thickness of the sound-absorbing cotton 3 at the starting position of the second spiral line is less than the thickness at the ending position of the second spiral line. Along the flow direction of the airflow, the airflow rate inside the volute 1 increases, the airflow pressure increases, and the airflow velocity increases. Although the first spiral contour of the peripheral wall of the volute 1 can alleviate the noise to a certain extent, the thickness variation of the sound-absorbing cotton 3 is still needed to match the airflow variation inside the volute 1, thereby achieving a basically consistent noise reduction effect along the airflow direction.

[0027] In this embodiment, both the first spiral and the second spiral are Fibonacci spirals. The first number of the Fibonacci sequence corresponding to the first spiral is a1, and the first number of the Fibonacci sequence corresponding to the second spiral is a2, where a2 > a1.

[0028] In this embodiment, a2 = k*a1, 1.1 ≤ k ≤ 1.2, and k can preferably be 1.12.

[0029] Corresponding to the end position of the second spiral, the thickness of the sound-absorbing cotton 3 reaches its maximum. In this embodiment, the maximum thickness of the sound-absorbing cotton 3 is dd, where dd = a2 - a1 + D2 - D1 / 2; where D1 is the inner diameter of the impeller 2 and D2 is the outer diameter of the impeller 2.

[0030] To ensure the structural and positional stability of the sound-absorbing cotton 3, protect it from damage, and further enhance noise reduction, a protective shell 4 is provided around the sound-absorbing cotton 3. The protective shell 4 includes multiple connected planar plates 41 arranged along the outer periphery of the sound-absorbing cotton 3. Each planar plate 41 is tangent to the midpoint of an arc segment in the second spiral line corresponding to the sound-absorbing cotton 3. The two ends of the protective shell 4 are fixed to the air outlet of the volute 1. Matching the spiral direction of the second spiral line, the length of each planar plate 41 in the circumferential direction is Ln, where Ln = 0.325 * [D1 + n + 1 * a1], and n is the arc segment number corresponding to the spiral direction of the second spiral line.

[0031] In this invention, the fan has sound-absorbing cotton 3 installed outside the volute 1, and the outer peripheral wall contour of the sound-absorbing cotton 3 is defined. The outer peripheral wall contour of the sound-absorbing cotton 3 is made into a spiral to match the spiral direction of the spiral of the volute 1, so that the sound-absorbing cotton 3 is in a non-uniform thickness state. This can effectively match the changes in noise sound pressure level and noise sound power caused by changes in airflow, air pressure, and air velocity inside the volute 1. Based on this special structural setting of the outer contour of the sound-absorbing cotton 3 being set as a spiral, the thickness change of the sound-absorbing cotton 3 can be precisely matched to the noise sound pressure level and noise sound power corresponding to the airflow inside the volute 1, achieving better sound insulation and sound absorption effects, and the noise reduction effect is more prominent.

[0032] In addition, based on the special design of the outer contour of the sound-absorbing cotton 3, it occupies a small volume while meeting the noise reduction requirements, which is conducive to the utilization of the space inside the range hood and can save the cost of the sound-absorbing cotton 3.

[0033] The fan in this invention can ensure that the sound-absorbing cotton 3 takes into account the three aspects of airflow intensity, aerodynamic performance and acoustic performance during the rotation of the impeller 2, so as to better insulate and absorb sound and achieve a better noise reduction effect.

[0034] This utility model also relates to a range hood, including the aforementioned fan. The range hood using the aforementioned fan is quieter and provides a better user experience.

[0035] In the specification and claims of this utility model, terms indicating direction, such as "front," "rear," "upper," "lower," "left," "right," "side," "top," and "bottom," are used to describe various exemplary structural parts and elements of the invention. However, the use of these terms is merely for illustrative purposes and is based on the exemplary orientations shown in the accompanying drawings. Since the embodiments disclosed in this invention can be arranged in different orientations, these terms indicating direction are for illustrative purposes only and should not be considered as limitations. For example, "upper" and "lower" are not necessarily limited to directions opposite to or consistent with the direction of gravity.

Claims

1. A fan, comprising a volute (1) and an impeller (2) disposed within the volute (1), characterized in that: The volute (1) has multiple small holes (11) on its peripheral wall, and sound-absorbing cotton (3) is attached to the outside of the peripheral wall of the volute (1). The peripheral wall contour of the volute (1) is a first spiral, and the outer peripheral wall contour of the sound-absorbing cotton (3) is a second spiral that matches the spiral direction of the first spiral. The thickness of the sound-absorbing cotton (3) at the starting point of the second spiral is less than the thickness at the ending point of the second spiral.

2. The fan according to claim 1, characterized in that: Both the first spiral and the second spiral are Fibonacci spirals. The first number of the Fibonacci sequence corresponding to the first spiral is a1, and the first number of the Fibonacci sequence corresponding to the second spiral is a2, where a2 > a1.

3. The fan according to claim 2, characterized in that: a2 = k * a1, 1.1 ≤ k ≤ 1.

2.

4. The fan according to claim 2, characterized in that: The maximum thickness of the sound-absorbing cotton (3) is dd; dd=(a2-a1)+(D2-D1) / 2; where D1 is the inner diameter of the impeller (2) and D2 is the outer diameter of the impeller (2).

5. The fan according to any one of claims 1 to 4, characterized in that: The sound-absorbing cotton (3) is wrapped with a protective shell (4). The protective shell (4) includes a plurality of connected planar plates (41) arranged along the outer periphery of the sound-absorbing cotton (3). Each planar plate (41) is tangent to the midpoint of an arc segment in the second spiral line corresponding to the sound-absorbing cotton (3).

6. The fan according to claim 5, characterized in that: The two ends of the protective shell (4) are fixed to the air outlet of the volute (1).

7. The fan according to claim 5, characterized in that: Both the first spiral and the second spiral are Fibonacci spirals, and the first number in the Fibonacci sequence corresponding to the first spiral is a1. Matching the spiral direction of the second spiral, the length of each planar plate (41) along the circumferential direction is Ln, Ln=0.325*[D1+(n+1)*a1], where n is the arc segment number corresponding to the spiral direction of the second spiral.

8. A range hood, characterized in that: Includes the wind turbine as described in any one of claims 1 to 7.

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