WO2020082913A1 - 离心风叶、离心风机和空调器 - Google Patents

离心风叶、离心风机和空调器 Download PDF

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WO2020082913A1
WO2020082913A1 PCT/CN2019/104777 CN2019104777W WO2020082913A1 WO 2020082913 A1 WO2020082913 A1 WO 2020082913A1 CN 2019104777 W CN2019104777 W CN 2019104777W WO 2020082913 A1 WO2020082913 A1 WO 2020082913A1
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WIPO (PCT)
Prior art keywords
centrifugal
blade
centrifugal fan
hub
fan blade
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PCT/CN2019/104777
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English (en)
French (fr)
Inventor
李建建
王现林
吴俊鸿
李业强
廖俊杰
李树云
朱芳勇
何博
肖洪力
黄鑫
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珠海格力电器股份有限公司
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Publication of WO2020082913A1 publication Critical patent/WO2020082913A1/zh

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    • 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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • 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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • 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

Definitions

  • This application belongs to the field of fan technology, and specifically relates to a centrifugal fan blade, a centrifugal fan, and an air conditioner.
  • This application requires the priority of the patent application filed on October 24, 2018 to the State Intellectual Property Office of China with the application number 201811243141.0 and the invention titled "Centrifugal Fan Blade, Centrifugal Fan and Air Conditioner”.
  • the airflow suction is useless work, on the one hand, it reduces the aerodynamic efficiency of the fan blade, on the other hand, the sucked airflow interferes with the inlet airflow, and also generates vortex noise.
  • the patent CN105258227A adopts the scheme of combining axial flow and centrifugal fan blade.
  • the production process of this fan blade is complicated, there are many assembly procedures, and the cost is high.
  • the fan blade is actually axial air inlet, axial and circumferential air outlet, although the supply air volume increases, but it is not suitable for centrifugal fan blade occasions (that is, occasions requiring axial air inlet and circumferential air outlet).
  • Some patents such as CN203879801U use double centrifugal fan blade structure. Although this kind of solution can improve the air supply volume, it cannot solve the problem of weak airflow at the front disk of the centrifugal fan blade from the root cause, and the double centrifugal fan blade structure increases the difficulty of the manufacturing process and the cost is high. The total thickness and size are large, which limits the use occasion.
  • the technical problem to be solved by the present application is to provide a centrifugal fan blade, a centrifugal fan, and an air conditioner, which can effectively increase the airflow intensity of the front disk of the fan blade and avoid the phenomenon of airflow sucking back.
  • the present application provides a centrifugal fan blade, including a wheel disc and a first hub, a first centrifugal blade is fixedly arranged on the outer circumferential side of the wheel disc, and the first hub is fixedly arranged on the wheel disc On the inner peripheral side of the first centrifugal blade, a second centrifugal blade is provided at the air inlet end of the first hub, and the second centrifugal blade is located on the inner peripheral side of the first centrifugal blade.
  • the second hub is fixedly arranged on the air inlet end face of the first hub, and the second centrifugal blades are circumferentially arranged along the outer circumferential side of the second hub.
  • the first hub and the second hub are fixed by welding or integrally injection molded.
  • the first centrifugal blade and the second centrifugal blade rotate synchronously.
  • the projection of the second centrifugal blade on the central axis of the centrifugal blade is within the projection range of the first centrifugal blade on the central axis of the centrifugal blade.
  • N2 / N1 1/5.
  • ⁇ 2 / ⁇ 1 0.45.
  • ⁇ 3 / ⁇ 2 0.25.
  • H2 / H1 0.2.
  • H3 / H1 0.75.
  • the relationship between the outer diameter ⁇ 4 of the air inlet end face of the first hub and the outer diameter ⁇ 2 of the second centrifugal blade satisfies: ⁇ 4- ⁇ 2 ⁇ a.
  • a 4-10 mm.
  • the outer periphery of the first centrifugal blade is fixedly provided with a water ring, and the water ring is disposed on the air inlet side of the first centrifugal blade.
  • the second hub is provided with a shaft hole.
  • the rotation direction of the first centrifugal blade and the second centrifugal blade are the same
  • a centrifugal fan including a centrifugal fan blade, the centrifugal fan blade being the aforementioned centrifugal fan blade.
  • the centrifugal fan further includes a volute, and the centrifugal fan blade is disposed in the volute.
  • the volute is provided with an air inlet, and the air inlet is provided with a deflector ring.
  • an air conditioner including a centrifugal fan blade, the centrifugal fan blade being the aforementioned centrifugal fan blade.
  • the centrifugal fan blade provided by the present application includes a wheel disc and a first hub.
  • a first centrifugal blade is fixedly arranged on the outer circumferential side of the wheel disc.
  • the first hub is fixedly arranged on the wheel disc and is located inside the first centrifugal blade
  • On the peripheral side a second centrifugal blade is provided at the air inlet end of the first hub.
  • the second centrifugal blade is located on the inner peripheral side of the first centrifugal blade, and the rotation directions of the first and second centrifugal blades are the same.
  • the second centrifugal blade is provided at the air inlet end of the first hub, when the centrifugal blade is in operation, the airflow intensity of the blade front disc during the operation of the blade can be increased by the second centrifugal blade to avoid or reduce the The airflow intensity of the rear disc is different, resulting in a pressure difference, which in turn causes a phenomenon of sucking back, which increases the outflow of airflow from the centrifugal fan blades, thereby increasing the air output of the centrifugal fan blades.
  • FIG. 1 is a schematic diagram of a three-dimensional structure of a centrifugal fan blade according to an embodiment of the present application
  • FIG. 2 is a schematic structural diagram of a centrifugal fan blade according to an embodiment of the present application.
  • FIG. 3 is a schematic cross-sectional structure diagram of a centrifugal fan blade according to an embodiment of the present application
  • FIG. 4 is a schematic structural diagram of a centrifugal fan according to an embodiment of this application.
  • FIG. 5 is a cross-sectional structural view taken along line C-C of FIG. 4;
  • FIG. 6 is a schematic diagram of an enlarged structure at A in FIG. 5.
  • the centrifugal fan blade includes a disc 1 and a first hub 2, and a first centrifugal blade 3 is fixedly arranged on the outer circumferential side of the disc 1 along the circumferential direction.
  • the hub 2 is fixedly arranged on the wheel disc 1 and is located on the inner circumferential side of the first centrifugal blade 3.
  • the air inlet end of the first hub 2 is provided with a second centrifugal blade 4.
  • the second centrifugal blade 4 is located on the first centrifugal blade 3. Inner peripheral side.
  • the centrifugal blades 4 can be used to increase the airflow intensity of the blade front disk during the operation of the blades to avoid or reduce Due to the difference in airflow intensity between the front and rear discs, a pressure difference is generated, which in turn causes a phenomenon of back suction, which increases the outflow of airflow from the centrifugal fan blades, thereby increasing the airflow of the centrifugal fan blades, reducing the useless work of the airflow Fan efficiency.
  • the airflow can be effectively prevented from being sucked back, the intake airflow is no longer disturbed and can smoothly flow along the path, avoiding the generation of vortex noise and reducing the operating noise of the centrifugal fan blades.
  • centrifugal fan blade of this embodiment only needs to add the structure of the second centrifugal blade 4 to the structure of the original centrifugal fan blade, the manufacturing process is simple, the cost is low, and mass production is easy to realize.
  • the rotation directions of the first centrifugal blade 3 and the second centrifugal blade 4 are the same, which can more effectively improve the airflow efficiency and the airflow strength of the front disc of the blade.
  • a second hub 5 is fixedly arranged on the air inlet end face of the first hub 2, and the second centrifugal blades 4 are circumferentially arranged along the outer circumferential side of the second hub 5.
  • the second hub 5 is disposed on the air inlet end face of the first hub 2 and extends in the axial direction away from the first hub 2 to form a cylindrical shaft structure.
  • a plurality of second centrifugal blades 4 are arranged along the circumference of the first hub 2 To evenly distributed.
  • the first hub 2 and the second hub 5 are fixed by welding or integrally injection molded.
  • first hub 2 and the second hub 5 are welded and fixed, in the process of processing, the first hub 2 and the second hub 5 can be processed separately and welded together, which can reduce the first hub 2 and the second hub 5 Processing difficulty, simplify processing technology.
  • first hub 2 and the second hub 5 are integrally injection-molded, the overall structural strength between the first hub 2 and the second hub 5 can be improved, and the processing cost can be reduced.
  • the first centrifugal blade 3 and the second centrifugal blade 4 rotate synchronously, which can further improve the air outlet efficiency and air output of the centrifugal fan blade.
  • the projection of the second centrifugal blade 4 on the central axis of the centrifugal blade is within the projection range of the first centrifugal blade 3 on the central axis of the centrifugal blade, so that the second centrifugal blade 4 is completely located in the first In a centrifugal blade 3, the airflow flowing out from the circumferential direction of the second centrifugal blade 4 completely flows out from the circumferential direction of the first centrifugal blade 3 through the first centrifugal blade 3, so that the airflow of the second centrifugal blade 4 is completely used to strengthen the first
  • the airflow intensity of the fan blade front disc of the centrifugal blade 3 is more effective in avoiding the phenomenon of airflow sucking back.
  • N2 / N1 1/5.
  • the above-mentioned number of blades is determined according to the ratio.
  • the integer is taken according to the rounding principle.
  • ⁇ 2 / ⁇ 1 0.45.
  • the airflow strengthening effect is not good.
  • the circumferential diameter of the hub is too large, which affects the airflow intake of the first centrifugal blade 3. Limiting the ratio to the above range can better overcome the above problems.
  • ⁇ 3 / ⁇ 2 0.25.
  • H2 / H1 0.2, which can obtain better results in both manufacturing cost control and airflow enhancement.
  • H3 / H1 0.75, which can achieve better results in both manufacturing cost control and airflow enhancement.
  • a 4 to 10 mm.
  • a 6mm.
  • the outer periphery of the first centrifugal blade 3 is fixedly provided with a water ring 6, and the water ring 6 is provided on the air inlet side of the first centrifugal blade 3.
  • the water ring 6 is provided at the outer edge of the air inlet end of the first centrifugal blade 3 in the circumferential direction, which can effectively fix the first centrifugal blade 3, so that the first centrifugal blade 3 has good structural strength and stability.
  • the second hub 5 is provided with a shaft hole 7 for assembling a motor shaft.
  • the airflow outflow is increased, that is, the fan output is increased. Since the airflow no longer does the suction work, it also improves the efficiency of the fan. On the other hand, after the airflow is blocked, the intake airflow at the front panel is no longer disturbed by interference, thereby avoiding the generation of vortex noise and reducing the total value of the fan noise.
  • the aforementioned blade front disc refers to a height position near the water ring 6 of the first centrifugal blade 3, where a conventional multi-blade centrifugal blade is prone to airflow backflow phenomenon.
  • the above-mentioned fan blade rear disk refers to the height position of the first centrifugal blade 3 near the wheel disk 1 at which the air flow is strong.
  • the centrifugal fan includes a centrifugal fan blade, and the centrifugal fan blade is the above-mentioned centrifugal fan blade.
  • the centrifugal fan also includes a volute 8, in which the centrifugal fan blades are disposed.
  • the volute 8 is provided with an air inlet, and the air inlet is provided with a guide ring 9.
  • the deflector 9 has a decreasing cross-section along the flow direction of the airflow, so that the airflow forms a constricted structure and forms an effective flow guiding effect on the airflow.
  • the air conditioner includes a centrifugal fan blade, which is the aforementioned centrifugal fan blade.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

一种离心风叶，包括轮盘（1）和第一轮毂（2），轮盘（1）的外周侧沿周向固定设置有第一离心叶片（3），第一轮毂（2）固定设置在轮盘（1）上，且位于第一离心叶片（3）的内周侧，第一轮毂（2）的进风端设置有第二离心叶片（4），第二离心叶片（4）位于第一离心叶片（3）的内周侧。以及一种包括离心风叶的离心风机和空调器。离心风叶能够有效增加风叶前盘的气流强度，避免发生气流回吸现象。

Description

离心风叶、离心风机和空调器 技术领域
本申请属于风机技术领域，具体涉及一种离心风叶、离心风机和空调器。本申请要求于2018年10月24日提交至中国国家知识产权局、申请号为201811243141.0、发明名称为“离心风叶、离心风机和空调器”的专利申请的优先权。
背景技术
常规多翼离心风叶，如专利CN205533411U，在运转过程中，风叶前盘附近处气流强度不足，风叶后盘处气流强劲。由于后盘气流强劲，前盘气流较弱，因此容易形成压力差，导致气流发生回吸的现象。
气流回吸为无用功，一方面降低了风叶气动效率，另一方面回吸的气流与进风气流相互干扰，还会产生涡流噪音。
为提高风叶效率，专利CN105258227A采用了轴流与离心风叶相结合的方案。此种风叶生产工艺复杂，装配工序多，成本较高。同时，该风叶实际为轴向进风，轴向和周向出风，虽然送风量增加，但不适用于离心风叶场合(即要求轴向进风、周向出风的场合)。
部分专利如CN203879801U，采用双离心风叶结构。此种方案虽然能够提升送风量，但无法从根源上解决离心风叶前盘处气流较弱的问题，并且双离心风叶结构增加了制造工艺难度，成本高，同时也增加了风叶的总厚度，尺寸较大，限制了使用场合。
发明内容
因此，本申请要解决的技术问题在于提供一种离心风叶、离心风机和空调器，能够有效增加风叶前盘的气流强度，避免发生气流回吸现象。
为了解决上述问题，本申请提供一种离心风叶，包括轮盘和第一轮毂，轮盘的外周侧沿周向固定设置有第一离心叶片，第一轮毂固定设置在轮盘上，且 位于第一离心叶片的内周侧，第一轮毂的进风端设置有第二离心叶片，第二离心叶片位于第一离心叶片的内周侧。
优选地，第一轮毂的进风端端面上固定设置有第二轮毂，第二离心叶片沿第二轮毂的外周侧周向排布。
优选地，第一轮毂和第二轮毂焊接固定或一体注塑成型。
优选地，第一离心叶片和第二离心叶片同步转动。
优选地，第二离心叶片在离心风叶的中心轴线上的投影位于第一离心叶片在离心风叶的中心轴线上的投影范围内。
优选地，第二离心叶片的数量N2与第一离心叶片的数量N1之间的关系满足：N2/N1＝1/12～1/3。
优选地，N2/N1＝1/5。
优选地，第二离心叶片的叶片外径φ2与第一离心叶片的叶片外径φ1之间满足：φ2/φ1＝0.4～0.5。
优选地，φ2/φ1＝0.45。
优选地，第二离心叶片的叶片外径φ2与第二离心叶片的叶片内径φ3之间的关系满足：φ3/φ2＝0.2～0.4。
优选地，φ3/φ2＝0.25。
优选地，第二离心叶片的轴向高度H2与第一离心叶片的轴向高度H1之间满足要求：H2/H1＝0.15～0.25。
优选地，H2/H1＝0.2。
优选地，第一轮毂的轴向高度H3与第一离心叶片的轴向高度H1之间的关系满足：H3/H1＝0.7～0.8。
优选地，H3/H1＝0.75。
优选地，第一轮毂的进风端端面外径φ4与第二离心叶片的叶片外径φ2之间的关系满足：φ4-φ2≥a。
优选地，a＝4～10mm。
优选地，第一离心叶片的外周侧固定设置有打水圈，打水圈设置在第一离心叶片的进风侧。
优选地，第二轮毂上设置有轴孔。
优选地，第一离心叶片和第二离心叶片的旋向相同
根据本申请的另一方面，提供了一种离心风机，包括离心风叶，该离心风叶为上述的离心风叶。
优选地，离心风机还包括蜗壳，离心风叶设置在蜗壳内。
优选地，蜗壳上设置有进风口，进风口设置有导流圈。
根据本申请的再一方面，提供了一种空调器，包括离心风叶，该离心风叶为上述的离心风叶。
本申请提供的离心风叶，包括轮盘和第一轮毂，轮盘的外周侧沿周向固定设置有第一离心叶片，第一轮毂固定设置在轮盘上，且位于第一离心叶片的内周侧，第一轮毂的进风端设置有第二离心叶片，第二离心叶片位于第一离心叶片的内周侧，且第一离心叶片和第二离心叶片的旋向相同。由于在第一轮毂的进风端设置有第二离心叶片，因此在离心风叶工作时，能够通过第二离心叶片增加风叶运行时风叶前盘的气流流通强度，避免或者减轻由于前、后盘气流强度不一而产生压力差，进而产生回吸的现象，增加了气流从离心风叶的流出量，从而提升了离心风叶的出风量。
附图说明
图1为本申请实施例的离心风叶的立体结构示意图；
图2为本申请实施例的离心风叶的结构示意图；
图3为本申请实施例的离心风叶的剖视结构示意图；
图4为本申请实施例的离心风机的结构示意图；
图5为图4的C-C向剖视结构图；
图6为图5的A处的放大结构示意图。
附图标记表示为：
1、轮盘；2、第一轮毂；3、第一离心叶片；4、第二离心叶片；5、第二轮毂；6、打水圈；7、轴孔；8、蜗壳；9、导流圈。
具体实施方式
结合参见图1至图6所示，根据本申请的实施例，离心风叶包括轮盘1和第一轮毂2，轮盘1的外周侧沿周向固定设置有第一离心叶片3，第一轮毂2固定设置在轮盘1上，且位于第一离心叶片3的内周侧，第一轮毂2的进风端设置有第二离心叶片4，第二离心叶片4位于第一离心叶片3的内周侧。
由于在第一轮毂2的进风端设置有第二离心叶片4，因此在离心风叶工作时，能够通过第二离心叶片4增加风叶运行时风叶前盘的气流流通强度，避免 或者减轻由于前、后盘气流强度不一而产生压力差，进而产生回吸的现象，增加了气流从离心风叶的流出量，从而提升了离心风叶的出风量，减小了气流的无用功，提升了风机效率。
此外，由于能够有效避免气流回吸，因此进风气流不再受到扰动，能够沿路径顺利流通，避免了涡流噪音产生，降低了离心风叶的运行噪音。
由于本实施例的离心风叶仅需在原有的离心风叶的结构上增加第二离心叶片4的结构即可，因此制作工艺简单，成本较低，易于实现大批量生产。
优选地，第一离心叶片3和第二离心叶片4的旋向相同，能够更加有效地提高气流流动效率，提高风叶前盘的气流流通强度。
第一轮毂2的进风端端面上固定设置有第二轮毂5，第二离心叶片4沿第二轮毂5的外周侧周向排布。通过设置第二轮毂5，能够更加方便进行第二离心叶片4的设置。第二轮毂5设置在第一轮毂2的进风端端面上，并向着远离第一轮毂2的轴向方向延伸，形成圆柱状轴结构，多个第二离心叶片4沿第一轮毂2的周向均匀分布。
第一轮毂2和第二轮毂5焊接固定或一体注塑成型。当第一轮毂2和第二轮毂5焊接固定时，在进行加工的过程中，第一轮毂2和第二轮毂5可以分开进行加工之后，焊接在一起，能够降低第一轮毂2和第二轮毂5的加工难度，简化加工工艺。当第一轮毂2和第二轮毂5一体注塑成型时，能够提高第一轮毂2和第二轮毂5之间的整体结构强度，降低加工成本。
优选地，第一离心叶片3和第二离心叶片4同步转动，能够进一步提高离心风叶的出风效率和出风量。
在本实施例中，第二离心叶片4在离心风叶的中心轴线上的投影位于第一离心叶片3在离心风叶的中心轴线上的投影范围内，从而使得第二离心叶片4完全位于第一离心叶片3内，从第二离心叶片4的周向流出的气流完全经过第一离心叶片3从第一离心叶片3的周向流出，使得第二离心叶片4的气流完全用来加强第一离心叶片3的风叶前盘的气流强度，更加有效地避免发生气流回吸现象。
优选地，第二离心叶片4的数量N2与第一离心叶片3的数量N1之间的关系满足：N2/N1＝1/12～1/3。
更优选地，N2/N1＝1/5。上述的叶片数量按照比例确定，当根据比例所确定的叶片数量不是整数时，则根据四舍五入原则取整数。通过设定上述的叶片数量比例关系，能够在获得较优的制造成本的同时有效强化气流流动效果，更 加有效地克服气流回吸现象。
第二离心叶片4的叶片外径φ2与第一离心叶片3的叶片外径φ1之间满足：φ2/φ1＝0.4～0.5。
优选地，φ2/φ1＝0.45。当该比值取得过小时，气流强化效果不佳，当该比值取得过大时，轮毂周向直径尺寸过大，影响第一离心叶片3的气流进风。将比值限定在上述范围内，则能够较好地克服上述的问题。
第二离心叶片4的叶片外径φ2与第二离心叶片4的叶片内径φ3之间的关系满足：φ3/φ2＝0.2～0.4。
优选地，φ3/φ2＝0.25。通过设定第二离心叶片4的叶片外径和叶片内径的比例关系，能够综合考虑离心叶片强度和气流强化效果之间的关系，获得较佳的离心风叶机构。
第二离心叶片4的轴向高度H2与第一离心叶片3的轴向高度H1之间满足要求：H2/H1＝0.15～0.25。
优选地，H2/H1＝0.2，可以在制造成本控制和气流强化两方面均获得较好的效果。
第一轮毂2的轴向高度H3与第一离心叶片3的轴向高度H1之间的关系满足：H3/H1＝0.7～0.8。
优选地，H3/H1＝0.75，可以在制造成本控制和气流强化两方面均获得较好的效果。
第一轮毂2的进风端端面外径φ4与第二离心叶片4的叶片外径φ2之间的关系满足：φ4-φ2≥a。
在本实施例中，a＝4～10mm。优选地，a为6mm。通过限定第一轮毂2的进风端端面与第二离心叶片4的叶片之间的关系，能够保证第一轮毂2的进风端端面边缘有足够的倒圆角空间，同时可以确保第一轮毂2的结构强度和模具要求。
第一离心叶片3的外周侧固定设置有打水圈6，打水圈6设置在第一离心叶片3的进风侧。打水圈6沿周向方向设置在第一离心叶片3的进风端外缘处，能够有效固定第一离心叶片3，使得第一离心叶片3具有良好的结构强度和稳定性。
第二轮毂5上设置有轴孔7，该轴孔7用于装配电机轴。
通过采用本实施例的离心风叶，在第一轮毂2处，周向均匀地布置数个第二离心叶片4。风机运转时，第二离心叶片4随之旋转做功，对前盘处气流出 风流动具有补强作用。通过强化此处的气流出风流动，阻断了气流回吸路径。
气流回吸路径被阻断后，一方面，气流流出量增加，即增加风机出风量，由于气流不再做回吸无用功，因此也提升了风机效率。另一方面，气流回吸被阻断后，前盘处进风气流不再被干扰扰动，从而避免了涡流噪音的产生，降低了风机噪音总值。
采用该风叶与常规多翼离心风叶进行实验对比测试，各工况转速下，风量提升10％～20％，效率提升5～12％，噪音总值降低1～2.6dB。
上述的风叶前盘是指第一离心叶片3的打水圈6附近的高度位置，常规多翼离心风叶在此处易产生气流回流现象。
上述的风叶后盘是指第一离心叶片3在轮盘1附近的高度位置，此位置处气流流动强劲。
结合参见图4至图6所示，根据本申请的实施例，离心风机包括离心风叶，该离心风叶为上述的离心风叶。
离心风机还包括蜗壳8，离心风叶设置在蜗壳8内。
蜗壳8上设置有进风口，进风口设置有导流圈9。该导流圈9沿着气流的流动方向，截面递减，从而使得气流形成收缩结构，对气流形成有效的导流作用。
根据本申请的实施例，空调器包括离心风叶，该离心风叶为上述的离心风叶。
本领域的技术人员容易理解的是，在不冲突的前提下，上述各有利方式可以自由地组合、叠加。
以上仅为本申请的较佳实施例而已，并不用以限制本申请，凡在本申请的精神和原则之内所作的任何修改、等同替换和改进等，均应包含在本申请的保护范围之内。以上仅是本申请的优选实施方式，应当指出，对于本技术领域的普通技术人员来说，在不脱离本申请技术原理的前提下，还可以做出若干改进和变型，这些改进和变型也应视为本申请的保护范围。

Claims (25)

  1. 一种离心风叶，其特征在于，包括轮盘(1)和第一轮毂(2)，所述轮盘(1)的外周侧沿周向固定设置有第一离心叶片(3)，所述第一轮毂(2)固定设置在所述轮盘(1)上，且位于所述第一离心叶片(3)的内周侧，所述第一轮毂(2)的进风端设置有第二离心叶片(4)，所述第二离心叶片(4)位于所述第一离心叶片(3)的内周侧。
  2. 根据权利要求1所述的离心风叶，其特征在于，所述第一轮毂(2)的进风端端面上固定设置有第二轮毂(5)，所述第二离心叶片(4)沿所述第二轮毂(5)的外周侧周向排布。
  3. 根据权利要求2所述的离心风叶，其特征在于，所述第一轮毂(2)和所述第二轮毂(5)焊接固定或一体注塑成型。
  4. 根据权利要求2所述的离心风叶，其特征在于，所述第一离心叶片(3)和所述第二离心叶片(4)同步转动。
  5. 根据权利要求1所述的离心风叶，其特征在于，所述第二离心叶片(4)在所述离心风叶的中心轴线上的投影位于所述第一离心叶片(3)在所述离心风叶的中心轴线上的投影范围内。
  6. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第二离心叶片(4)的数量N2与所述第一离心叶片(3)的数量N1之间的关系满足：N2/N1＝1/12～1/3。
  7. 根据权利要求6所述的离心风叶，其特征在于，N2/N1＝1/5。
  8. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第二离心叶片(4)的叶片外径φ2与所述第一离心叶片(3)的叶片外径φ1之间满足：φ2/φ1＝0.4～0.5。
  9. 根据权利要求8所述的离心风叶，其特征在于，φ2/φ1＝0.45。
  10. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第二离心叶片(4)的叶片外径φ2与所述第二离心叶片(4)的叶片内径φ3之间的关系满足：
    φ3/φ2＝0.2～0.4。
  11. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，φ3/φ2＝0.25。
  12. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第二离心叶片(4)的轴向高度H2与所述第一离心叶片(3)的轴向高度H1之间 满足要求：H2/H1＝0.15～0.25。
  13. 根据权利要求12所述的离心风叶，其特征在于，H2/H1＝0.2。
  14. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第一轮毂(2)的轴向高度H3与所述第一离心叶片(3)的轴向高度H1之间的关系满足：H3/H1＝0.7～0.8。
  15. 根据权利要求14所述的离心风叶，其特征在于，H3/H1＝0.75。
  16. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第一轮毂(2)的进风端端面外径φ4与所述第二离心叶片(4)的叶片外径φ2之间的关系满足：φ4-φ2≥a。
  17. 根据权利要求16所述的离心风叶，其特征在于，a＝4～10mm。
  18. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第一离心叶片(3)的外周侧固定设置有打水圈(6)，所述打水圈(6)设置在所述第一离心叶片(3)的进风侧。
  19. 根据权利要求2所述的离心风叶，其特征在于，所述第二轮毂(5)上设置有轴孔(7)。
  20. 根据权利要求1至5中任一项所述的离心风叶，其特征在于，所述第一离心叶片(3)和所述第二离心叶片(4)的旋向相同。
  21. 一种离心风叶，其特征在于，包括轮盘(1)和第一轮毂(2)，所述轮盘(1)的外周侧沿周向设置有第一离心叶片(3)，所述第一轮毂(2)与所述轮盘(1)相连接，所述第一轮毂(2)的进风端设置有第二离心叶片(4)，所述第二离心叶片(4)位于所述第一离心叶片(3)的内周侧。
  22. 一种离心风机，包括离心风叶，其特征在于，所述离心风叶为权利要求1至21中任一项所述的离心风叶。
  23. 根据权利要求22所述的离心风机，其特征在于，所述离心风机还包括蜗壳(8)，所述离心风叶设置在所述蜗壳(8)内。
  24. 根据权利要求23所述的离心风机，其特征在于，所述蜗壳(8)上设置有进风口，所述进风口设置有导流圈(9)。
  25. 一种空调器，包括离心风叶，其特征在于，所述离心风叶为权利要求1至21中任一项所述的离心风叶。
PCT/CN2019/104777 2018-10-24 2019-09-06 离心风叶、离心风机和空调器 WO2020082913A1 (zh)

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