WO2025185035A1 - 叶片、叶轮及吸油烟机 - Google Patents

叶片、叶轮及吸油烟机

Info

Publication number
WO2025185035A1
WO2025185035A1 PCT/CN2024/106010 CN2024106010W WO2025185035A1 WO 2025185035 A1 WO2025185035 A1 WO 2025185035A1 CN 2024106010 W CN2024106010 W CN 2024106010W WO 2025185035 A1 WO2025185035 A1 WO 2025185035A1
Authority
WO
WIPO (PCT)
Prior art keywords
blade
impeller
blade body
airflow
present application
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
PCT/CN2024/106010
Other languages
English (en)
French (fr)
Other versions
WO2025185035A8 (zh
Inventor
李业强
吴金鑫
胡小文
胡斯特
陈鹏
李清
汪耀东
郑志伟
薛玮飞
李书奇
曲兴超
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
GD Midea Air Conditioning Equipment Co Ltd
Foshan Shunde Midea Washing Appliances Manufacturing Co Ltd
Original Assignee
GD Midea Air Conditioning Equipment Co Ltd
Foshan Shunde Midea Washing Appliances Manufacturing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by GD Midea Air Conditioning Equipment Co Ltd, Foshan Shunde Midea Washing Appliances Manufacturing Co Ltd filed Critical GD Midea Air Conditioning Equipment Co Ltd
Publication of WO2025185035A1 publication Critical patent/WO2025185035A1/zh
Publication of WO2025185035A8 publication Critical patent/WO2025185035A8/zh
Pending legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24C—DOMESTIC STOVES OR RANGES ; DETAILS OF DOMESTIC STOVES OR RANGES, OF GENERAL APPLICATION
    • F24C15/00—Details
    • F24C15/20—Removing cooking fumes

Definitions

  • the present application relates to the technical field of range hoods, and in particular to a blade, an impeller and a range hood.
  • impellers in range hoods are typically made of sheet metal, offering oil-free, corrosion-resistant, and high-temperature resistance.
  • the impeller blades are relatively simple in form. When the impeller is running at high speed, the airflow forms an angle with the horizontal plane when entering the impeller. This angle differs significantly from the geometric angle formed by the leading edge of the blades, resulting in significant airflow impact and separation at the air intake point of the impeller blades, generating significant noise.
  • the present application aims to solve at least one of the technical problems existing in the related art. To this end, the present application proposes a blade that reduces the noise generated by airflow impacting the blade.
  • the present application also proposes an impeller.
  • the present application also provides a range hood.
  • the present application proposes a blade, comprising:
  • the blade body has an arc-shaped cross-section, and the blade body has relative leading and trailing edges.
  • the leading edge of the blade body is provided with a bent wing, and the bent wing is provided on the arc-shaped convex side of the blade body; the bent wing has a connected transition connection section and a guide section, the transition connection section is connected to the blade body, and the guide section extends toward the arc-shaped convex side.
  • the guide section of the bent wing can guide the airflow entering the surface of the blade body, so that the airflow angle ⁇ formed by the airflow at the leading edge of the blade is adapted to the geometric angle ⁇ formed by the leading edge of the blade, thereby reducing the pressure pulsation caused by the impact of the inlet airflow, effectively increasing the impeller air volume, and eliminating the flow separation and noise caused by the airflow impacting the blade.
  • the bending radius of the transition connecting section is R1.
  • the chord length of the blade body is L.
  • the value of R1 ranges from 0.01L to 0.015L.
  • the radius of the guide section is R2.
  • the value of R2 ranges from 0.15L to 0.25L.
  • the chord length of the guide section is S.
  • the value of S ranges from 0.1 to 0.2L.
  • the trailing edge of the blade has a serrated structure.
  • the sawtooth structure extends along the height direction of the blade.
  • the sawtooth structure is an unequally spaced sawtooth structure.
  • the waveform of the sawtooth structure is a sine curve.
  • the frequency of the sinusoid is F.
  • the value of F ranges from 30 to 40.
  • the waveform of the sawtooth structure is a sine curve.
  • the amplitude of the sinusoid is A.
  • the value of A ranges from 0.03 to 0.04L.
  • the sawtooth structure includes a first sawtooth structure and a second sawtooth structure that are spaced apart from each other.
  • the height of the first sawtooth structure is H1.
  • the height of the second sawtooth structure is H2.
  • the value of H1/(H1+H2) ranges from 0.6 to 0.8.
  • an impeller comprising:
  • the disc body, the blades are arranged around the circumference of the disc body.
  • the radius of the disk is D1
  • the radius of the impeller is D2
  • the value range of D1/D2 is 0.75-0.85.
  • the impeller proposed in the present application includes the above-mentioned blades and thus also has the beneficial effects of the above-mentioned blades, which will not be described in detail here.
  • the present application also proposes a range hood, comprising:
  • the shell is provided with an air duct and a smoking port, the air duct is communicated with the volute, and the smoking port is communicated with the air duct.
  • the range hood proposed in the present application includes the above-mentioned impeller and thus also has the beneficial effects of the above-mentioned impeller, which will not be described in detail here.
  • FIG1 is a schematic diagram of the impeller structure provided by the present application.
  • FIG2 is a cross-sectional view of the impeller structure provided by the present application.
  • FIG3 is a partial enlarged view of point A in FIG2 ;
  • FIG4 is a partial enlarged view of point B in FIG3 ;
  • FIG5 is a schematic diagram of the blade structure provided in this application.
  • FIG6 is a partial enlarged view of point C in FIG5 .
  • connection should be understood in a broad sense. For example, they can refer to fixed connections, detachable connections, or integral connections; they can refer to mechanical connections or electrical connections; they can refer to direct connections or indirect connections through an intermediate medium. Those skilled in the art will understand the specific meanings of the above terms in the embodiments of this application based on the specific circumstances.
  • a first feature being “above” or “below” a second feature may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediate medium.
  • a first feature being “above,” “above,” and “above” a second feature may mean that the first feature is directly above or obliquely above the second feature, or simply means that the first feature is higher in level than the second feature.
  • a first feature being “below,” “below,” and “below” a second feature may mean that the first feature is directly below or obliquely below the second feature, or simply means that the first feature is lower in level than the second feature.
  • impellers in range hoods are typically made of sheet metal, offering oil-free, corrosion-resistant, and high-temperature resistance.
  • the impeller blades are relatively simple in design. When the impeller is running at high speed, the airflow forms an angle with the horizontal plane when entering the impeller. This angle differs significantly from the geometric angle formed by the leading edge of the blades, resulting in significant airflow impact and separation at the air intake point of the impeller blades, generating significant noise.
  • a guide plate is installed on the inner concave surface of the blade tail end to prevent gas loss at the outlet and reduce energy consumption.
  • the guide plate will cause airflow obstruction.
  • the present application provides a blade 110, comprising a blade body 111 and a bent wing 112.
  • the blade 110 provided by the present application is disposed in an impeller 10, which is disposed in a range hood to provide power for the range hood to extract oil fumes.
  • the cross-section of the blade body 111 is arcuate, and the blade body 111 has a leading edge 115 and a trailing edge 116 opposite each other.
  • the leading edge 115 of the blade 110 enters, flows along the surface of the blade body 111, and then flows out from the trailing edge 116 of the blade 110.
  • the leading edge 115 of the blade body 111 is provided with a bent wing 112, and the bent wing 112 is provided on the arcuate convex side 113 of the blade body 111.
  • the bent wing 112 has a transition section 1121 and a guide section 1122 connected to each other.
  • the transition section 1121 is connected to the blade body 111, and the guide section 1122 extends toward the arcuate convex side 113.
  • the airflow angle formed at the leading edge 115 of the blade 110 is ⁇
  • the geometric angle formed at the leading edge 115 of the blade 110 is ⁇ .
  • the airflow can flow along the guide section 1122, so that the airflow angle ⁇ and the geometric angle ⁇ formed by the leading edge 115 of the blade 110 can be adapted to prevent a large numerical difference between the airflow angle and the geometric angle, thereby reducing the pressure pulsation caused by the impact of the inlet airflow, effectively increasing the air volume of the impeller 10, and eliminating the flow separation and noise caused by the airflow impacting the blade 110.
  • the bent wing 112 is provided on the blade body.
  • the curved convex side 113 of the leading edge 115 of 111 enables the guide section 1122 of the bent wing 112 to guide the airflow entering the surface of the blade body 111, so that the airflow angle ⁇ formed by the airflow at the leading edge 115 of the blade 110 is adapted to the geometric angle ⁇ formed by the leading edge 115 of the blade 110, thereby reducing the pressure pulsation caused by the impact of the inlet airflow, effectively increasing the air volume of the impeller 10, and eliminating the flow separation and noise caused by the airflow impacting the blade 110.
  • the bending radius of the transition section 1121 is R1
  • the chord length of the blade body 111 is L
  • the value range of R1 is 0.01L-0.015L.
  • the radius of the guide section 1122 is R2, and the value range of R2 is 0.15L-0.25L.
  • the radius R2 of the guide section 1122 can be 0.2L.
  • the chord length of the guide section 1122 is S, and the value of S ranges from 0.1L to 0.2L. This ensures that the guide section 1122 is of sufficient length to guide the airflow, so that the airflow angle ⁇ formed by the airflow at the leading edge 115 of the blade 110 is compatible with the geometric angle ⁇ formed by the leading edge 115 of the blade 110, thereby reducing the pressure pulsation caused by the impact of the inlet airflow, effectively increasing the air volume of the impeller 10, and eliminating the flow separation and noise caused by the airflow impacting the blade 110.
  • this length range also ensures that the guide section 1122 is not too long, avoiding the problem of airflow blockage caused by an overly long guide section 1122, further improving the operating efficiency of the range hood and reducing noise.
  • the trailing edge 116 of the blade 110 is a sawtooth structure 114, and the sawtooth structure 114 extends along the height direction of the blade 110. Since the multi-blade centrifugal impeller 10 has axial air intake, in a shorter blade path, the airflow is forced to quickly turn at a large angle to achieve radial air discharge, resulting in a low-speed separation zone with high speed at the trailing edge 116 of the blade 110 and low speed at the leading edge 115 of the blade 110.
  • the trailing edge 116 of the blade 110 When the trailing edge 116 of the blade 110 is configured as a sawtooth shape, the fluid's flow path changes as the fluid passes through the trailing edge 116 due to the change in shape of the trailing edge 116, thereby disrupting the fluid's continuity, reducing the velocity gradient, and thereby reducing the generation of shear forces. Furthermore, the sawtooth shape of the trailing edge 116 of the blade 110 can also break up shedding vortices, further reducing noise.
  • the trailing edge 116 of the blade 110 is configured in a sawtooth shape, which can reduce the shear force of the airflow itself, improve the aerodynamic performance of the blade 110, and reduce noise.
  • the serration structure 114 is an unequally spaced serration structure 114.
  • the unequally spaced serration structure 114 can provide a more complex fluid interference pattern. Compared with equidistant serrations, it can more effectively disrupt and disperse the vortex structure in the fluid. This dispersion effect helps to reduce the separation of the fluid on the surface of the blade 110 and reduce the formation of shedding vortices, thereby improving the aerodynamic performance and efficiency of the blade 110.
  • the unequally spaced serration structure 114 may also have a positive effect on the structural strength and durability of the blade 110. By optimizing the layout and size of the serrations, stress concentration points can be reduced, thereby improving the structural stability and service life of the blade 110.
  • the waveform of the sawtooth structure 114 is a sine curve, wherein the shape of the sine curve conforms to the image of the following function:
  • F is the frequency of the sine curve, and the value range of F is 30-40.
  • A is the amplitude of the sine curve, and the value range of A is 0.03-0.04L.
  • the leading edge 115 of the blade 110 is provided with a slot 1151, and the disc 120 is locked in the slot 1151.
  • the bottom groove wall of the slot 1151 separates the serration structure 114 to form a first serration structure 1141 and a second serration structure 1142.
  • the height of the first serration structure 1141 is H1
  • the height of the second serration structure 1142 is H2.
  • H1>H2 and the value range of H1/(H1+H2) is 0.6-0.8. Setting the height difference between H1 and H2 can further change the fluid dynamic characteristics of the trailing edge 116 of the blade 110, thereby optimizing the aerodynamic performance of the impeller 10.
  • the present application also proposes an impeller 10 comprising the aforementioned blades 110 and a disc 120, with the blades 110 disposed around the circumference of the disc 120.
  • the blades 110 can rotate about the disc 120, thereby dynamically adjusting the direction and speed of the airflow.
  • the arrangement of the blades 110 is not limited to this.
  • the blades 110 are fixed around the disc 120, but can oscillate. This allows the blades 110 to adaptively adjust their angles based on changes in the airflow, similarly achieving effective airflow guidance and acceleration.
  • This impeller 10 is designed to improve airflow guidance efficiency and acceleration performance and is suitable for use in range hoods to optimize their intake and exhaust performance.
  • the impeller 10 proposed in the present application because it includes the aforementioned blades 110, also exhibits the beneficial effects of the blades 110.
  • the radius of the disk 120 is D1
  • the radius of the impeller 10 is D2
  • the value range of D1/D2 is 0.75-0.85.
  • the value of D1/D2 may be 0.8.
  • the test results of an existing impeller and the impeller 10 provided by this application in the same range hood are shown.
  • the existing impeller produces an air volume of 17.2 cm3 and a noise power of 67.6 dB.
  • the impeller 10 designed using this application achieves an air volume of 18.1 cm3 and a noise power of 66.2 dB.
  • the impeller 10 designed using this application achieves a 5% increase in air volume and a 1.4 dB reduction in noise.
  • the present application also provides a range hood (not shown in the figure), comprising the above-mentioned impeller 10, a volute (not shown in the figure), and a housing (not shown in the figure).
  • the impeller 10 is disposed in the volute, and the housing is provided with an air duct and a smoke outlet, the air duct being connected to the volute, and the smoke outlet being connected to the air duct.
  • the range hood proposed in the present application includes the above-mentioned impeller 10 and thus also has the beneficial effects of the above-mentioned impeller 10, which will not be described in detail here.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

本申请涉及吸油烟机技术领域，提供一种叶片、叶轮及吸油烟机。该叶片包括叶片本体，叶片本体的截面呈弧形，叶片本体具有相对的前缘和尾缘，叶片本体的前缘设有折弯型翼，且折弯型翼设于叶片本体的弧形凸面侧；折弯型翼具有相连接的过渡连接段和导流段，过渡连接段与叶片本体连接，导流段朝向弧形凸面侧延伸。根据本申请提出的叶片，通过将折弯型翼设置于叶片本体前缘的弧形凸面侧，使折弯型翼的导流段可以对进入叶片本体表面的气流进行导流，使得气流在叶片前缘形成的气流角α与叶片前缘形成的几何角β相适配，从而降低进口气流冲击产生压力脉动，有效的提升叶轮风量，消除气流冲击叶片而产生的流动分离和噪声。

Description

叶片、叶轮及吸油烟机
相关申请的交叉引用
本申请要求于2024年03月07日提交的申请号为2024204491139，名称为“叶片、叶轮及吸油烟机”的中国专利申请的优先权，其通过引用方式全部并入本文。
技术领域
本申请涉及吸油烟机技术领域，尤其涉及一种叶片、叶轮及吸油烟机。
背景技术
相关技术中，吸油烟机中叶轮一般采用钣金材料制作，具备不沾油、抗腐蚀及耐高温的性能。但叶轮受到工艺的限制，叶片的形式较为单一。在叶轮高速运行中，气流进入叶轮时，气流会与水平面形成气流角，此气流角与叶片前缘形成的几何角角度相差较大，导致在叶轮的叶片前缘进气位置产生较大的气流冲击和分离，形成较大的噪声。
发明内容
本申请旨在至少解决相关技术中存在的技术问题之一。为此，本申请提出一种叶片，降低气流冲击叶片产生的噪声。
本申请还提出一种叶轮。
本申请还提出一种吸油烟机。
本申请提出一种叶片，包括：
叶片本体，所述叶片本体的截面呈弧形，所述叶片本体具有相对的前缘和尾缘，所述叶片本体的前缘设有折弯型翼，且所述折弯型翼设于所述叶片本体的弧形凸面侧；所述折弯型翼具有相连接的过渡连接段和导流段，所述过渡连接段与所述叶片本体连接，所述导流段朝向所述弧形凸面侧延伸。
根据本申请提出的叶片，通过将折弯型翼设置于叶片本体前缘的弧形凸面侧，使折弯型翼的导流段可以对进入叶片本体表面的气流进行导流，使得气流在叶片前缘形成的气流角α与叶片前缘形成的几何角β相适配，从而降低进口气流冲击产生压力脉动，有效的提升叶轮风量，消除气流冲击叶片而产生的流动分离和噪声。
在一些实施例中，所述过渡连接段的折弯半径为R1。
在一些实施例中，所述叶片本体的弦长长度为L。
在一些实施例中，R1的取值范围为0.01L-0.015L。
根据本申请的一个实施例，所述导流段的半径为R2。
在一些实施例中，R2的取值范围为0.15L-0.25L。
根据本申请的一个实施例，所述导流段的弦长长度为S。
在一些实施例中，S的取值范围为0.1-0.2L。
根据本申请的一个实施例，所述叶片的尾缘呈锯齿结构。
在一些实施例中，所述锯齿结构沿所述叶片的高度方向延伸。
根据本申请的一个实施例，所述锯齿结构为不等距锯齿结构。
根据本申请的一个实施例，所述锯齿结构的波形为正弦曲线。
在一些实施例中，所述正弦曲线的频率为F。
在一些实施例中，F的取值范围为30-40。
在一些实施例中，所述锯齿结构的波形为正弦曲线。
在一些实施例中，所述正弦曲线的振幅为A。
在一些实施例中，A的取值范围为0.03-0.04L。
在一些实施例中，，所述锯齿结构包括相间隔的第一锯齿结构和第二锯齿结构。
在一些实施例中，所述第一锯齿结构的高度为H1。
在一些实施例中，所述第二锯齿结构的高度为H2。
在一些实施例中，H1>H2。
在一些实施例中，H1/(H1+H2)的取值范围为0.6-0.8。
本申请还提出一种叶轮，包括：
上述的叶片；
盘体，所述叶片围绕所述盘体圆周设置。
在一些实施例中，所述盘体的半径为D1，所述叶轮的半径为D2，D1/D2的取值范围为0.75-0.85。
根据本申请提出的叶轮，因包括上述的叶片，因此也具有上述叶片的有益效果，此处不再赘述。
本申请还提出一种吸油烟机，包括：
上述的叶轮；
蜗壳，所述叶轮设于所述蜗壳内；
壳体，所述壳体设有风道和吸烟口，所述风道与所述蜗壳连通，且所述吸烟口与所述风道连通。
根据本申请提出的吸油烟机，因包括上述的叶轮，因此也具有上述叶轮的有益效果，此处不再赘述。
本申请的附加方面和优点将在下面的描述中部分给出，部分将从下面的描述中变得明显，或通过本申请的实践了解到。
附图说明
为了更清楚地说明本申请实施例或相关技术中的技术方案，下面将对实施例或相关技术描述中所需要使用的附图作简单地介绍，显而易见地，下面描述中的附图仅仅是本申请的一些实施例，对于本领域普通技术人员来讲，在不付出创造性劳动的前提下，还可以根据这些附图获得其他的附图。
图1是本申请提供的叶轮结构示意图；
图2是本申请提供的叶轮结构剖面图；
图3是图2的A处局部放大图；
图4是图3的B处局部放大图；
图5是本申请提供的叶片结构示意图；
图6是图5的C处局部放大图。
附图标记：
10、叶轮；
110、叶片；111、叶片本体；112、折弯型翼；1121、过渡连接段；1122、导流段；113、凸面侧；114、锯齿结构；1141、第一锯齿结构；1142、第二锯齿结构；115、前缘；1151、卡槽；116、尾缘；
120、盘体。
具体实施方式
下面结合附图和实施例对本申请的实施方式作进一步详细描述。以下实施例用于说明本申请，但不能用来限制本申请的范围。
在本申请实施例的描述中，需要说明的是，术语“中心”、“纵向”、“横向”、“上”、“下”、“前”、“后”、“左”、“右”、“竖直”、“水平”、“顶”、“底”、“内”、“外”等指示的方位或位置关系为基于附图所示的方位或位置关系，仅是为了便于描述本申请实施例和简化描述，而不是指示或暗示所指的装置或元件必须具有特定的方位、以特定的方位构造和操作，因此不能理解为对本申请实施例的限制。此外，术语 “第一”、“第二”、“第三”仅用于描述目的，而不能理解为指示或暗示相对重要性。
在本申请实施例的描述中，需要说明的是，除非另有明确的规定和限定，术语“相连”、“连接”应做广义理解，例如，可以是固定连接，也可以是可拆卸连接，或一体连接；可以是机械连接，也可以是电连接；可以是直接相连，也可以通过中间媒介间接相连。对于本领域的普通技术人员而言，可以具体情况理解上述术语在本申请实施例中的具体含义。
在本申请实施例中，除非另有明确的规定和限定，第一特征在第二特征“上”或“下”可以是第一和第二特征直接接触，或第一和第二特征通过中间媒介间接接触。而且，第一特征在第二特征“之上”、“上方”和“上面”可是第一特征在第二特征正上方或斜上方，或仅仅表示第一特征水平高度高于第二特征。第一特征在第二特征“之下”、“下方”和“下面”可以是第一特征在第二特征正下方或斜下方，或仅仅表示第一特征水平高度小于第二特征。
在本说明书的描述中，参考术语“一个实施例”、“一些实施例”、“示例”、“具体示例”、或“一些示例”等的描述意指结合该实施例或示例描述的具体特征、结构、材料或者特点包含于本申请实施例的至少一个实施例或示例中。在本说明书中，对上述术语的示意性表述不必须针对的是相同的实施例或示例。而且，描述的具体特征、结构、材料或者特点可以在任一个或多个实施例或示例中以合适的方式结合。此外，在不相互矛盾的情况下，本领域的技术人员可以将本说明书中描述的不同实施例或示例以及不同实施例或示例的特征进行结合和组合。
申请人发现，吸油烟机中叶轮一般采用钣金材料制作，具备不沾油、抗腐蚀及耐高温的性能。但叶轮受到工艺的限制，叶片的形式较为单一。在叶轮高速运行中，气流进入叶轮时，气流会与水平面形成气流角，此气流角与叶片前缘形成的几何角角度相差较大，导致在叶轮的叶片前缘进气位置产生较大的气流冲击和分离，形成较大的噪声。
因此，相关技术中，会在叶片尾端的内凹面设置导流板，使导流板阻挡气体在出口流动的损失，并降低能耗。但由于气流经过叶轮做功后，在叶轮出口的速度较快，导流板反而会造成气流阻塞。
如图2至图4所示，本申请提供一种叶片110，包括叶片本体111和折弯型翼112。在一些实施例中，本申请提供的叶片110设置于叶轮10内，该叶轮10设置在吸油烟机内，用于为吸油烟机提供抽吸油烟的动力。
如图3和图4所示，叶片本体111的截面呈弧形，且叶片本体111具有相对的前缘115和尾缘116，在叶片本体111工作时，叶片110的前缘115进入，沿着叶片本体111表面流动，然后从叶片110的尾缘116流出。叶片本体111的前缘115设有折弯型翼112，且折弯型翼112设于叶片本体111的弧形凸面侧113。折弯型翼112具有相连接的过渡连接段1121和导流段1122，过渡连接段1121与叶片本体111连接，导流段1122朝向所述弧形凸面侧113延伸。
其中，如图4所示，气流进入叶片本体111表面时，在叶片110前缘115形成的气流角为α，叶片110前缘115形成的几何角为β，在气流进入叶片本体111表面时，气流可以贴合导流段1122流动，从而使气流角α与叶片110前缘115形成的几何角β可以相适配，防止气流角与几何角产生较大的数值差，从而降低进口气流冲击产生压力脉动，有效的提升叶轮10风量，消除气流冲击叶片110而产生的流动分离和噪声。
根据本申请实施例的叶片110，通过将折弯型翼112设置于叶片本体 111前缘115的弧形凸面侧113，使折弯型翼112的导流段1122可以对进入叶片本体111表面的气流进行导流，使得气流在叶片110前缘115形成的气流角α与叶片110前缘115形成的几何角β相适配，从而降低进口气流冲击产生压力脉动，有效的提升叶轮10风量，消除气流冲击叶片110而产生的流动分离和噪声。
如图3和图4所示，在本申请的一个实施例中，过渡连接段1121的折弯半径为R1，所述叶片本体111的弦长长度为L，R1的取值范围为0.01L-0.015L。这样，可以确定过渡连接段1121的折弯角度，从而确定导流段1122相对于叶片本体111的倾斜角度，以确保导流段1122能够有效地引导气流，减少气流在叶片110前缘115处的冲击和分离，进而减少噪声。
如图4所示，在本申请的一个实施例中，导流段1122的半径为R2，R2的取值范围为0.15L-0.25L，例如，导流段1122的半径R2可以为0.2L。通过调节导流段1122的曲率，进而改变气流在导流段1122上的流动路径，进一步确保导流段1122能够有效地引导气流。这样，有助于降低吸油烟机在运行过程中产生的风量和噪音，提升设备的整体性能。
如图4所示，在本申请的一个实施例中，导流段1122的弦长长度为S，S的取值范围为0.1L-0.2L。这样可以确保导流段1122有足够的长度来引导气流，使得气流在叶片110前缘115形成的气流角α与叶片110前缘115形成的几何角β相适配，从而降低进口气流冲击产生压力脉动，有效的提升叶轮10风量，消除气流冲击叶片110而产生的流动分离和噪声。同时，这个长度范围也可以保证导流段1122不会过长，避免导流段1122过长导致的气流阻塞问题，进一步提高吸油烟机的工作效率和降低噪音。
如图5和图6所示，在本申请的一个实施例中，叶片110的尾缘116呈锯齿结构114，且锯齿结构114沿叶片110的高度方向延伸。由于多翼离心叶轮10的是轴向进气的，在较短的叶道中，会迫使气流快速的大角度折转实现径向出气，所以出现叶片110尾缘116处速度高、叶片110前缘115出速度低的低速分离区。由于叶片110尾缘116处气体流动的速度显著高于叶片110前缘115处气体流动的速度流动速度，导致气体在叶片110尾缘116出口时会产生速度梯度，从而引起气流的剪切效应。这种剪切力会导致流体在叶片110尾缘116形成涡旋，也就是脱落涡。脱落涡不仅会降低叶片110的气动性能，还会产生噪声。
当叶片110尾缘116设置为锯齿形状时，流体在通过叶片110尾缘116时，由于叶片110尾缘116的形状变化，流体的流动路径也会发生变化，从而打破流体的连续性，降低速度梯度，进而减少剪切力的产生。同时，锯齿形状的叶片110尾缘116也可以打散脱落涡，进一步降低噪声。
因此，叶片110尾缘116设置为锯齿形状，可以降低气流自身的剪切力，提高叶片110的的气动性能，降低噪声。
如图5所示，在本申请的一个实施例中，锯齿结构114为不等距锯齿结构114，不等距锯齿结构114可以提供更复杂的流体干扰模式，与等距锯齿相比，它能更有效地打乱和分散流体中的涡旋结构。这种分散作用有助于减少流体在叶片110表面的分离，降低脱落涡的形成，从而提高叶片110的气动性能和效率。此外，不等距锯齿结构114还可能对叶片110的结构强度和耐久性产生积极影响。通过优化锯齿的布局和尺寸，可以减少应力集中点，从而提高叶片110的结构稳定性和使用寿命。
如图5和图6所示，在本申请的一个实施例中，锯齿结构114的波形为正弦曲线，其中，正弦曲线的形状符合如下函数的图像：
xt＝Hn*t^2，t∈0-1，n＝1,2；
yt＝A*sin(2π*F*t)，t∈0-1，
其中，F为正弦曲线的频率，且F的取值范围为30-40。A为正弦曲线的振幅，A的取值范围为0.03-0.04L。
如图1和图5所示，在本申请的一些实施例中，叶片110的前缘115设有卡槽1151，盘体120卡设于卡槽1151内，卡槽1151的底部槽壁将锯齿结构114间隔开形成第一锯齿结构1141和第二锯齿结构1142。其中第一锯齿结构1141的高度为H1，第二锯齿结构1142的高度为H2，H1>H2，H1/(H1+H2)的取值范围为0.6-0.8。设置H1和H2的高度差异，可以进一步改变叶片110尾缘116的流体动力学特性，从而优化叶轮10的气动性能。
根据上述函数，当n＝1时，函数图形为第一锯齿结构1141的形状；当n＝2时，函数图形为第二锯齿结构1142的形状。
如图1和图2所示，本申请还提出一种叶轮10，包括上述的叶片110和盘体120，叶片110围绕盘体120的圆周设置。其中，叶片110可以围绕盘体120转动，通过这种方式，叶片110可以动态地调整气流的方向和速度。当然，叶片110的设置形式并不仅限于此，在其它一些示例中，叶片110被固定在盘体120周围，但叶片110自身可以摆动，这样，叶片110可以根据气流的变化自适应地调整其角度，同样实现对气流的有效导引和加速。这种叶轮10设计旨在提升气流的导向效率和加速性能，适用于吸油烟机中，以优化其吸气和排风效果。根据本申请提出的叶轮10，因包括上述的叶片110，因此也具有上述叶片110的有益效果。
如图2所示，在本申请的一些实施例中，盘体120的半径为D1，叶轮10的半径为D2，D1/D2的取值范围为0.75-0.85，例如，D1/D2的取值可以为0.8。
如表1所示，表1为现有叶轮与本方案提供的叶轮10在同一吸油烟机内的测试效果。可以看到，在相同转速下，现有叶轮产生的风量为17.2CMM，噪音声功率为67.6dB，采用本申请方案设计的叶轮10风量达到18.1CMM，噪音声功率66.2dB。本申请方案设计的叶轮10与现有叶轮10相比，风量提升5％，噪音降低1.4d B。
表1整机性能测试结果
本申请还提出一种吸油烟机(图中未示出)，包括上述的叶轮10、蜗壳(图中未示出)以及壳体(图中未示出)。其中叶轮10设于蜗壳内，壳体设有风道和吸烟口，风道与蜗壳连通，且吸烟口与所述风道连通。
根据本申请提出的吸油烟机，因包括上述的叶轮10，因此也具有上述叶轮10的有益效果，此处不再赘述。
最后应说明的是，以上实施方式仅用于说明本申请，而非对本申请的限制。尽管参照实施例对本申请进行了详细说明，本领域的普通技术人员应当理解，对本申请的技术方案进行各种组合、修改或者等同替换，都不脱离本申请技术方案的范围，均应涵盖在本申请的权利要求范围中。

Claims (12)

  1. 一种叶片，包括：
    叶片本体，所述叶片本体的截面呈弧形，所述叶片本体具有相对的前缘和尾缘，所述叶片本体的前缘设有折弯型翼，且所述折弯型翼设于所述叶片本体的弧形凸面侧；所述折弯型翼具有相连接的过渡连接段和导流段，所述过渡连接段与所述叶片本体连接，所述导流段朝向所述弧形凸面侧延伸。
  2. 根据权利要求1所述的叶片，其中，所述过渡连接段的折弯半径为R1，所述叶片本体的弦长长度为L，R1的取值范围为0.01L-0.015L。
  3. 根据权利要求1或2所述的叶片，其中，所述导流段的半径为R2，R2的取值范围为0.15L-0.25L。
  4. 根据权利要求1-3任一项所述的叶片，其中，所述导流段的弦长长度为S，S的取值范围为0.1-0.2L。
  5. 根据权利要求1-4任一项所述的叶片，其中，所述叶片的尾缘呈锯齿结构，所述锯齿结构沿所述叶片的高度方向延伸。
  6. 根据权利要求5所述的叶片，其中，所述锯齿结构为不等距锯齿结构。
  7. 根据权利要求6所述的叶片，其中，所述锯齿结构的波形为正弦曲线，所述正弦曲线的频率为F，F的取值范围为30-40。
  8. 根据权利要求5-7任一项所述的叶片，其中，所述锯齿结构的波形为正弦曲线，所述正弦曲线的振幅为A，A的取值范围为0.03-0.04L。
  9. 根据权利要求5-8任一项所述的叶片，其中，所述锯齿结构包括相间隔的第一锯齿结构和第二锯齿结构，所述第一锯齿结构的高度为H1，所述第二锯齿结构的高度为H2，H1>H2，H1/(H1+H2)的取值范围为0.6-0.8。
  10. 一种叶轮，包括：
    权利要求1-9任一项所述的叶片；
    盘体，所述叶片围绕所述盘体圆周设置。
  11. 根据权利要求10所述的叶轮，其中，所述盘体的半径为D1，所述叶轮的半径为D2，D1/D2的取值范围为0.75-0.85。
  12. 一种吸油烟机，包括：
    权利要求10-11任一项所述的叶轮；
    蜗壳，所述叶轮设于所述蜗壳内；
    壳体，所述壳体设有风道和吸烟口，所述风道与所述蜗壳连通，且所述吸烟口与所述风道连通。
PCT/CN2024/106010 2024-03-07 2024-07-17 叶片、叶轮及吸油烟机 Pending WO2025185035A1 (zh)

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