WO2016066113A1 - Centrifugal blower and air conditioner having same - Google Patents

Centrifugal blower and air conditioner having same Download PDF

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Publication number
WO2016066113A1
WO2016066113A1 PCT/CN2015/093128 CN2015093128W WO2016066113A1 WO 2016066113 A1 WO2016066113 A1 WO 2016066113A1 CN 2015093128 W CN2015093128 W CN 2015093128W WO 2016066113 A1 WO2016066113 A1 WO 2016066113A1
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WIPO (PCT)
Prior art keywords
centrifugal fan
blade
impeller
hub
blades
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PCT/CN2015/093128
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French (fr)
Chinese (zh)
Inventor
廖俊杰
熊军
彭勃
刘池
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珠海格力电器股份有限公司
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Publication of WO2016066113A1 publication Critical patent/WO2016066113A1/en

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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
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • 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
    • F04D29/30—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
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence

Definitions

  • the present invention relates to the field of air conditioning technology, and in particular to a centrifugal fan and an air conditioner having the same.
  • the design of the blade profile has an important influence on the performance of the centrifugal fan.
  • most of the blades of the centrifugal fan adopt a single-stage or two-stage circular airfoil structure, and the blades of the airfoil have various types of inter-blade eddy currents, separation eddy currents and the like at the flow passage between the blades.
  • the unevenness which is easy to cause the outflowing airflow to be uneven, increases the aerodynamic noise, which greatly limits the efficiency of the centrifugal fan.
  • a primary object of the present invention is to provide a centrifugal fan and an air conditioner having the same to solve the problem of separation eddy current between blades in the prior art.
  • a centrifugal fan comprising: a hub; an impeller rear disc, sleeved on the hub; a plurality of vanes, a plurality of vanes disposed on the rear disc of the impeller and circumferentially Provided on the outer side of the hub, the height of the blade gradually tapers outwardly in the direction in which it extends.
  • the ratio of the maximum height h max of the blade to the minimum height h min is in the range of 1 to 2.
  • a side of the blade remote from the rear wheel of the impeller and a surface parallel to the rear disc of the impeller have a first angle ⁇ 1 , and the first angle ⁇ 1 is less than 90°.
  • the first included angle ⁇ 1 is in the range of 3° to 16°.
  • the side surface of the blade away from the rear disk of the impeller is curved.
  • a side of the blade facing the hub and a surface parallel to the rear disk of the impeller have a second angle ⁇ 2 , and the second angle ⁇ 2 is less than 85°.
  • the second included angle ⁇ 2 is in the range of 35° to 60°.
  • the centrifugal fan further includes an impeller front disc that is disposed on the plurality of vanes, and a surface of the impeller front disc facing the vane has a gap with a side of the vane away from the rear disc of the impeller.
  • the gap is in the range of 1.5 mm to 6 mm.
  • the centrifugal fan further includes an impeller front disc that is disposed on the plurality of blades, and the blade-facing surface of the impeller front disc is in contact with the side of the vane away from the rear disc of the impeller.
  • an air conditioner including a centrifugal fan is provided, and the centrifugal fan is the centrifugal fan described above.
  • the centrifugal fan comprises a hub, an impeller rear disc and a plurality of blades, the impeller rear disc is sleeved on the hub, and the plurality of blades are arranged on the rear disc of the impeller and arranged on the outer side of the hub in the circumferential direction, the blade The height gradually tapers outward in the direction in which it extends.
  • the centrifugal fan When the centrifugal fan is operated, the speed of the leading edge of the blade near the hub is smaller than the speed of the blade away from the trailing edge of the hub.
  • the above structure can increase the sweeping area of the leading edge of the blade, which can greatly reduce the blade.
  • the unevenness of the flow between the airflow, the structure with the streamlined airfoil, can fully reduce the velocity and pressure gradient at the inlet of the blade, so that the pressure difference near the wall of the blade is lower than the reverse pressure gradient that produces the separation flow. In this way, various types of turbulent flow are effectively avoided at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.
  • FIG. 1 is a top plan view showing a first embodiment of a centrifugal fan according to the present invention
  • Figure 2 is a side elevational view showing the deployment of the blade of the centrifugal fan of Figure 1;
  • Figure 3 is a schematic view showing the flow direction of the airflow of the centrifugal fan of Figure 2;
  • Fig. 4 is a side elevational view showing the unfolding of the blade of the second embodiment of the centrifugal fan according to the present invention.
  • the centrifugal fan of the first embodiment includes a hub 10, an impeller rear disk 20 and a plurality of blades 30.
  • the impeller rear disk 20 is sleeved on the hub 10, and the plurality of blades 30 are provided with the impeller rear disk 20.
  • the upper side is disposed circumferentially on the outer side of the hub 10, and the height of the vane 30 gradually decreases outward in the extending direction thereof.
  • the blade 30 is of an equal speed reducing airfoil.
  • the centrifugal fan of the first embodiment is applied.
  • the centrifugal fan comprises a hub 10, an impeller rear disc 20 and a plurality of blades 30.
  • the impeller rear disc 20 is sleeved on the hub 10, and the plurality of vanes 30 are disposed on the impeller rear disc 20 and along the circumference.
  • the height of the blade 30 gradually tapers outward in the direction in which it extends.
  • This structure in conjunction with the equal-speed deceleration airfoil, can sufficiently reduce the velocity and pressure gradient at the inlet of the blade 30, thereby causing the pressure difference near the wall surface of the blade 30 to be lower than that of the production.
  • the inverse pressure gradient of the separated flow is used to effectively avoid the generation of multi-class turbulent flow at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.
  • the ratio of the maximum height h max to the minimum height h min of the blade 30 is in the range of 1 to 2.
  • the front edge structure design as described above, which cooperates with the blade airfoil structure, can reduce the back pressure gradient of the inter-leaf flow passage, thereby suppressing the generation of the separation flow and the inter-leaf eddy current.
  • the side of the blade 30 away from the rear wheel 20 of the impeller and the surface parallel to the rear disc 20 of the impeller have a first angle ⁇ 1 , and the first angle ⁇ 1 is less than 90°.
  • the front edge structure design as described above, which cooperates with the blade airfoil structure, can reduce the back pressure gradient of the inter-leaf flow passage, thereby suppressing the generation of the separation flow and the inter-leaf eddy current.
  • the above structure makes the side of the blade 30 away from the rear wheel 20 of the impeller be inclined with respect to the surface of the rear disc 20 of the impeller, and the height of the outer edge of the blade can be changed by an equal amount to form a diagonal line.
  • the first included angle ⁇ 1 is in the range of 3° to 16°.
  • the side of the blade 30 facing the hub 10 and the surface parallel to the rear wheel 20 of the impeller have a second angle ⁇ 2 , and the second angle ⁇ 2 is less than 85. °.
  • the above structure allows the leading edge of the blade 30 to be at an angle to the rear disc 20 of the impeller, which can reduce the velocity gradient between the leading edges of the blade 30, thereby improving the airflow at the leading edge of the blade 30, and improving the outflow of the centrifugal fan.
  • the uniformity of the airflow improves the performance of the centrifugal fan and suppresses the generation of multiple types of eddy currents in the flow path between the blades 30, thereby achieving a lower noise effect.
  • the second included angle ⁇ 2 is in the range of 35° to 60°.
  • the flow of air between adjacent blades 30 of the centrifugal fan of the first embodiment is as shown in FIGS. 1 and 3, and the flow velocity distribution at the inlet section AA of the blade 30 is relatively uneven, and is effective by changing the leading edge of the blade 30.
  • the unevenness of the flow velocity on the inlet side of the blade 30 is reduced, and the flow velocity of the airflow after the airflow passes through the blade 30 gradually becomes stable, forming a uniform airflow as shown in the section BB, effectively improving the outflow of the centrifugal fan.
  • Uniformity which in turn improves fan performance, effectively reduces noise and reduces noise while the noise quality of the outgoing airflow is significantly improved.
  • the centrifugal fan of the second embodiment differs from the first embodiment in the shape of the side surface of the blade 30 away from the impeller rear disk 20.
  • the side of the blade 30 away from the rear wheel 20 of the impeller is inclined with respect to the surface of the rear disc 20 of the impeller, and in the second embodiment, the side of the vane 30 away from the rear disc 20 of the impeller is curved.
  • the arc shape makes the first angle ⁇ 1 change according to a certain rule, and the curved surface can better realize the flow guiding effect of the air flow in the inter-leaf flow channel.
  • the centrifugal fan further includes an impeller front disc 40 that is disposed on the plurality of vanes 30.
  • the surface of the impeller front disc 40 facing the vane 30 is in contact with the side of the vane 30 away from the impeller rear disc 20, that is, The impeller front disc 40 is combined with the vane 30 as a unit.
  • the integrated design facilitates the installation and positioning, and the increase of the weight of the impeller makes the dynamic balance characteristic have a certain improvement, and can better ensure the smoothness of the operation of the blade 30.
  • the gap is preferably in the range of 1.5 mm to 6 mm. After being added to the impeller front disc 40, the gap fit can reduce the leakage loss and prevent the axial turbulence of the impeller airflow, thereby achieving smooth outflow of the inter-leaf flow passage.
  • the present application also provides an air conditioner.
  • the embodiment of the air conditioner (not shown) according to the present application includes a centrifugal fan, and the centrifugal fan is the centrifugal fan described above.
  • the centrifugal fan includes a hub 10, an impeller rear disk 20, and a plurality of blades 30,
  • the impeller rear disc 20 is sleeved on the hub 10, and a plurality of vanes 30 are disposed on the impeller rear disc 20 and circumferentially disposed on the outer side of the hub 10, and the height of the vane 30 is gradually outwardly reduced in the extending direction thereof.
  • the centrifugal fan When the centrifugal fan is operated, the speed of the blade 30 near the leading edge of the hub 10 is smaller than the speed of the blade 30 away from the trailing edge of the hub 10.
  • the above structure can increase the sweeping area of the leading edge of the blade 30, such that The unevenness of the flow of the airflow between the blades 30 can be greatly reduced.
  • This structure in conjunction with the streamlined airfoil, can sufficiently reduce the velocity and pressure gradient at the inlet of the blade 30, thereby causing the pressure difference near the wall of the blade 30 to be lower than The reverse pressure gradient of the separated flow is generated, thereby effectively avoiding the generation of various types of turbulent flow at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.

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

Abstract

A centrifugal blower, which comprises: a hub (10); a rear impeller disk (20) which is sheathed on the hub (10); and a plurality of blades (30) arranged on the rear impeller disk (20), the plurality of blades (30) being arranged on the outside of the hub (10) circumferentially and the height of the blades (30) being gradually reduced outward in the extension direction thereof. Also disclosed is an air conditioner having the centrifugal blower mentioned above. The centrifugal blower has effectively solved the problem of the separation vortex between the blades in the prior art.

Description

离心式风机及具有其的空调器Centrifugal fan and air conditioner having the same 技术领域Technical field
本发明涉及空调技术领域，具体而言，涉及一种离心式风机及具有其的空调器。The present invention relates to the field of air conditioning technology, and in particular to a centrifugal fan and an air conditioner having the same.
背景技术Background technique
目前，在离心风机中，叶片型线的设计对于离心式风机性能有着重要影响。现有技术中，大部分离心式风机的叶片采用单段或两段式圆弧翼型结构，该类翼型的叶片在其叶片之间的流道处存在叶间涡流、分离涡流等多类不均匀现象，进而容易引发流出的气流不均匀，增大了气动噪声，这样在很大程度上限制了离心式风机效率的提升。At present, in the centrifugal fan, the design of the blade profile has an important influence on the performance of the centrifugal fan. In the prior art, most of the blades of the centrifugal fan adopt a single-stage or two-stage circular airfoil structure, and the blades of the airfoil have various types of inter-blade eddy currents, separation eddy currents and the like at the flow passage between the blades. The unevenness, which is easy to cause the outflowing airflow to be uneven, increases the aerodynamic noise, which greatly limits the efficiency of the centrifugal fan.
发明内容Summary of the invention
本发明的主要目的在于提供一种离心式风机及具有其的空调器，以解决现有技术中叶片之间存在分离涡流的问题。SUMMARY OF THE INVENTION A primary object of the present invention is to provide a centrifugal fan and an air conditioner having the same to solve the problem of separation eddy current between blades in the prior art.
为了实现上述目的，根据本发明的一个方面，提供了一种离心式风机，包括：轮毂；叶轮后盘，套设在轮毂上；多个叶片，多个叶片设置叶轮后盘上并沿周向设置在轮毂的外侧，叶片的高度沿其延伸方向逐渐地向外缩小。In order to achieve the above object, according to an aspect of the invention, a centrifugal fan is provided, comprising: a hub; an impeller rear disc, sleeved on the hub; a plurality of vanes, a plurality of vanes disposed on the rear disc of the impeller and circumferentially Provided on the outer side of the hub, the height of the blade gradually tapers outwardly in the direction in which it extends.
进一步地，叶片的最大高度hmax与最小高度hmin比值在1～2的范围内。Further, the ratio of the maximum height h max of the blade to the minimum height h min is in the range of 1 to 2.
进一步地，叶片的远离叶轮后盘的侧面与平行于叶轮后盘的表面之间具有第一夹角θ1，第一夹角θ1小于90°。Further, a side of the blade remote from the rear wheel of the impeller and a surface parallel to the rear disc of the impeller have a first angle θ 1 , and the first angle θ 1 is less than 90°.
进一步地，第一夹角θ1在3°～16°的范围内。Further, the first included angle θ 1 is in the range of 3° to 16°.
进一步地，叶片的远离叶轮后盘的侧面为弧面状。Further, the side surface of the blade away from the rear disk of the impeller is curved.
进一步地，叶片的朝向轮毂的侧面与平行于叶轮后盘的表面之间具有第二夹角θ2，第二夹角θ2小于85°。Further, a side of the blade facing the hub and a surface parallel to the rear disk of the impeller have a second angle θ 2 , and the second angle θ 2 is less than 85°.
进一步地，第二夹角θ2在35°～60°范围内。Further, the second included angle θ 2 is in the range of 35° to 60°.
进一步地，离心式风机还包括盖设在多个叶片上的叶轮前盘，叶轮前盘的朝向叶片的表面与叶片的远离叶轮后盘的侧面之间具有间隙。Further, the centrifugal fan further includes an impeller front disc that is disposed on the plurality of vanes, and a surface of the impeller front disc facing the vane has a gap with a side of the vane away from the rear disc of the impeller.
进一步地，间隙在1.5mm～6mm范围内。Further, the gap is in the range of 1.5 mm to 6 mm.
进一步地，离心式风机还包括盖设在多个叶片上的叶轮前盘，叶轮前盘的朝向叶片的表面与叶片的远离叶轮后盘的侧面贴合。 Further, the centrifugal fan further includes an impeller front disc that is disposed on the plurality of blades, and the blade-facing surface of the impeller front disc is in contact with the side of the vane away from the rear disc of the impeller.
根据本发明的另一方面，提供了一种空调器，包括离心式风机，离心式风机为上述的离心式风机。According to another aspect of the present invention, an air conditioner including a centrifugal fan is provided, and the centrifugal fan is the centrifugal fan described above.
应用本发明的技术方案，离心式风机包括轮毂、叶轮后盘和多个叶片，叶轮后盘套设在轮毂上，多个叶片设置在叶轮后盘上并沿周向设置在轮毂的外侧，叶片的高度沿其延伸方向逐渐地向外缩小。当离心式风机工作时，叶片的靠近轮毂的前缘的速度相对于叶片的远离轮毂的后缘的速度要小，上述结构可以增大叶片的前缘的扫风面积，这样可以大大减小叶片之间气流流动的不均匀度，该结构配合流线形翼型，能充分降低叶片的入口处的速度与压力梯度，由此使叶片的壁面附近压差低于产生分离流的逆压梯度，以此有效地避免多类紊流流动在前缘产生，从而提高风机性能，实现降噪效果。Applying the technical solution of the present invention, the centrifugal fan comprises a hub, an impeller rear disc and a plurality of blades, the impeller rear disc is sleeved on the hub, and the plurality of blades are arranged on the rear disc of the impeller and arranged on the outer side of the hub in the circumferential direction, the blade The height gradually tapers outward in the direction in which it extends. When the centrifugal fan is operated, the speed of the leading edge of the blade near the hub is smaller than the speed of the blade away from the trailing edge of the hub. The above structure can increase the sweeping area of the leading edge of the blade, which can greatly reduce the blade. The unevenness of the flow between the airflow, the structure with the streamlined airfoil, can fully reduce the velocity and pressure gradient at the inlet of the blade, so that the pressure difference near the wall of the blade is lower than the reverse pressure gradient that produces the separation flow. In this way, various types of turbulent flow are effectively avoided at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.
附图说明DRAWINGS
构成本申请的一部分的说明书附图用来提供对本发明的进一步理解，本发明的示意性实施例及其说明用于解释本发明，并不构成对本发明的不当限定。在附图中：The accompanying drawings, which are incorporated in the claims of the claims In the drawing:
图1示出了根据本发明的离心式风机的实施例一的俯视结构示意图；1 is a top plan view showing a first embodiment of a centrifugal fan according to the present invention;
图2示出了图1的离心式风机的叶片展开的侧视示意图；Figure 2 is a side elevational view showing the deployment of the blade of the centrifugal fan of Figure 1;
图3示出了图2的离心式风机的气流流向的示意图；以及Figure 3 is a schematic view showing the flow direction of the airflow of the centrifugal fan of Figure 2;
图4示出了根据本发明的离心式风机的实施例二的叶片展开的侧视结构示意图。Fig. 4 is a side elevational view showing the unfolding of the blade of the second embodiment of the centrifugal fan according to the present invention.
其中，上述附图包括以下附图标记：Wherein, the above figures include the following reference numerals:
10、轮毂；20、叶轮后盘；30、叶片；40、叶轮前盘。10, the hub; 20, the rear wheel of the impeller; 30, the blade; 40, the front plate of the impeller.
具体实施方式detailed description
需要说明的是，在不冲突的情况下，本申请中的实施例及实施例中的特征可以相互组合。下面将参考附图并结合实施例来详细说明本发明。It should be noted that the embodiments in the present application and the features in the embodiments may be combined with each other without conflict. The invention will be described in detail below with reference to the drawings in conjunction with the embodiments.
如图1和图2所示，实施例一的离心式风机包括轮毂10、叶轮后盘20和多个叶片30，叶轮后盘20套设在轮毂10上，多个叶片30设置叶轮后盘20上并沿周向设置在轮毂10的外侧，叶片30的高度沿其延伸方向逐渐地向外缩小。叶片30采用等减速翼型。As shown in FIG. 1 and FIG. 2, the centrifugal fan of the first embodiment includes a hub 10, an impeller rear disk 20 and a plurality of blades 30. The impeller rear disk 20 is sleeved on the hub 10, and the plurality of blades 30 are provided with the impeller rear disk 20. The upper side is disposed circumferentially on the outer side of the hub 10, and the height of the vane 30 gradually decreases outward in the extending direction thereof. The blade 30 is of an equal speed reducing airfoil.
应用实施例一的离心式风机，离心式风机包括轮毂10、叶轮后盘20和多个叶片30，叶轮后盘20套设在轮毂10上，多个叶片30设置叶轮后盘20上并沿周向设置在轮毂10的外侧，叶片30的高度沿其延伸方向逐渐地向外缩小。当离心式风机工作时，叶片30的靠近轮毂10的前缘的速度相对于叶片30的远离轮毂10的后缘的速度要小，上述结构可以增大叶片30的前缘的扫风面积，这样可以大大减小叶片30之间气流流动的不均匀度，该结构配合等减速翼型，能充分降低叶片30的入口处的速度与压力梯度，由此使叶片30的壁面附近压差低于产 生分离流的逆压梯度，以此有效地避免多类紊流流动在前缘产生，从而提高风机性能，实现降噪效果。The centrifugal fan of the first embodiment is applied. The centrifugal fan comprises a hub 10, an impeller rear disc 20 and a plurality of blades 30. The impeller rear disc 20 is sleeved on the hub 10, and the plurality of vanes 30 are disposed on the impeller rear disc 20 and along the circumference. To the outside of the hub 10, the height of the blade 30 gradually tapers outward in the direction in which it extends. When the centrifugal fan is operated, the speed of the blade 30 near the leading edge of the hub 10 is smaller than the speed of the blade 30 away from the trailing edge of the hub 10. The above structure can increase the sweeping area of the leading edge of the blade 30, such that The unevenness of the flow of the airflow between the blades 30 can be greatly reduced. This structure, in conjunction with the equal-speed deceleration airfoil, can sufficiently reduce the velocity and pressure gradient at the inlet of the blade 30, thereby causing the pressure difference near the wall surface of the blade 30 to be lower than that of the production. The inverse pressure gradient of the separated flow is used to effectively avoid the generation of multi-class turbulent flow at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.
在实施例一中，叶片30的最大高度hmax与最小高度hmin比值在1～2的范围内。同前所述的前缘结构设计，其配合叶片翼型结构可降低叶间流道的逆压梯度，以此抑制分离流与叶间涡流的产生。In the first embodiment, the ratio of the maximum height h max to the minimum height h min of the blade 30 is in the range of 1 to 2. The front edge structure design as described above, which cooperates with the blade airfoil structure, can reduce the back pressure gradient of the inter-leaf flow passage, thereby suppressing the generation of the separation flow and the inter-leaf eddy current.
在实施例一中，叶片30的远离叶轮后盘20的侧面与平行于叶轮后盘20的表面之间具有第一夹角θ1，第一夹角θ1小于90°。同前所述的前缘结构设计，其配合叶片翼型结构可降低叶间流道的逆压梯度，以此抑制分离流与叶间涡流的产生。上述结构使得叶片30的远离叶轮后盘20的侧面相对于叶轮后盘20的表面为斜面，叶片外缘的高度可呈等量变化，形成一段斜线。优选地，第一夹角θ1在3°～16°的范围内。In the first embodiment, the side of the blade 30 away from the rear wheel 20 of the impeller and the surface parallel to the rear disc 20 of the impeller have a first angle θ 1 , and the first angle θ 1 is less than 90°. The front edge structure design as described above, which cooperates with the blade airfoil structure, can reduce the back pressure gradient of the inter-leaf flow passage, thereby suppressing the generation of the separation flow and the inter-leaf eddy current. The above structure makes the side of the blade 30 away from the rear wheel 20 of the impeller be inclined with respect to the surface of the rear disc 20 of the impeller, and the height of the outer edge of the blade can be changed by an equal amount to form a diagonal line. Preferably, the first included angle θ 1 is in the range of 3° to 16°.
如图1和图3所示，在实施例一中，叶片30的朝向轮毂10的侧面与平行于叶轮后盘20的表面之间具有第二夹角θ2，第二夹角θ2小于85°。上述结构使得叶片30的前缘与叶轮后盘20呈一定的角度，这样可以减少叶片30的前缘各点间速度梯度，进而改善叶片30的前缘处的气流，提高了离心式风机流出的气流的均匀性，提升离心式风机性能，抑制了叶片30之间的流道的多类涡流的产生，从而实现较低噪声的效果。为了进一步地降低噪声，优选地，第二夹角θ2在35°～60°范围内。As shown in FIGS. 1 and 3, in the first embodiment, the side of the blade 30 facing the hub 10 and the surface parallel to the rear wheel 20 of the impeller have a second angle θ 2 , and the second angle θ 2 is less than 85. °. The above structure allows the leading edge of the blade 30 to be at an angle to the rear disc 20 of the impeller, which can reduce the velocity gradient between the leading edges of the blade 30, thereby improving the airflow at the leading edge of the blade 30, and improving the outflow of the centrifugal fan. The uniformity of the airflow improves the performance of the centrifugal fan and suppresses the generation of multiple types of eddy currents in the flow path between the blades 30, thereby achieving a lower noise effect. In order to further reduce noise, it is preferable that the second included angle θ 2 is in the range of 35° to 60°.
实施例一的离心式风机的相邻叶片30之间的气流流向如图1和图3所示，在叶片30的入口截面A-A处的流速分布较为不均匀，通过改变叶片30的前缘，有效地降低了叶片30的入口侧的流速的不均匀度，气流经过叶片30之后气流的流速逐渐趋于平稳，形成如截面B-B处所示的均匀气流，有效地提高了离心式风机的流出的气流均匀性，进而提升了风机性能，从而有效地降低噪声，降低噪声的同时流出气流的噪音音质得到了明显的改善。The flow of air between adjacent blades 30 of the centrifugal fan of the first embodiment is as shown in FIGS. 1 and 3, and the flow velocity distribution at the inlet section AA of the blade 30 is relatively uneven, and is effective by changing the leading edge of the blade 30. The unevenness of the flow velocity on the inlet side of the blade 30 is reduced, and the flow velocity of the airflow after the airflow passes through the blade 30 gradually becomes stable, forming a uniform airflow as shown in the section BB, effectively improving the outflow of the centrifugal fan. Uniformity, which in turn improves fan performance, effectively reduces noise and reduces noise while the noise quality of the outgoing airflow is significantly improved.
图4示出了本申请的离心式风机的实施例二的结构，实施例二的离心式风机与实施例一的区别在于叶片30的远离叶轮后盘20的侧面的形状不同。在实施例一中，叶片30的远离叶轮后盘20的侧面相对于叶轮后盘20的表面为斜面，而在实施例二中，叶片30的远离叶轮后盘20的侧面为弧面状。弧面状使得第一夹角θ1按一定的规律变化，弧形面能较优的实现气流在叶间流道的导流作用。4 shows the structure of the second embodiment of the centrifugal fan of the present application. The centrifugal fan of the second embodiment differs from the first embodiment in the shape of the side surface of the blade 30 away from the impeller rear disk 20. In the first embodiment, the side of the blade 30 away from the rear wheel 20 of the impeller is inclined with respect to the surface of the rear disc 20 of the impeller, and in the second embodiment, the side of the vane 30 away from the rear disc 20 of the impeller is curved. The arc shape makes the first angle θ 1 change according to a certain rule, and the curved surface can better realize the flow guiding effect of the air flow in the inter-leaf flow channel.
在实施例二中，离心式风机还包括盖设在多个叶片30上的叶轮前盘40，叶轮前盘40的朝向叶片30的表面与叶片30的远离叶轮后盘20的侧面贴合，即叶轮前盘40与叶片30组合为一整体。一体化设计便于安装定位，同时叶轮重量的增加使其动平衡特性有一定的提高，能较好地保证叶片30运转的平稳性。当然，在图中未示出的实施方式中，叶轮前盘40的朝向叶片30的表面与叶片30的远离叶轮后盘20的侧面之间具有间隙。间隙优选在1.5mm～6mm范围内。加入叶轮前盘40后，通过间隙配合，在降低泄漏损失的同时，还可防止叶轮气流的轴向窜动，实现叶间流道的平稳出流。In the second embodiment, the centrifugal fan further includes an impeller front disc 40 that is disposed on the plurality of vanes 30. The surface of the impeller front disc 40 facing the vane 30 is in contact with the side of the vane 30 away from the impeller rear disc 20, that is, The impeller front disc 40 is combined with the vane 30 as a unit. The integrated design facilitates the installation and positioning, and the increase of the weight of the impeller makes the dynamic balance characteristic have a certain improvement, and can better ensure the smoothness of the operation of the blade 30. Of course, in an embodiment not shown in the figures, there is a gap between the surface of the impeller front disk 40 facing the blade 30 and the side of the blade 30 remote from the impeller rear disk 20. The gap is preferably in the range of 1.5 mm to 6 mm. After being added to the impeller front disc 40, the gap fit can reduce the leakage loss and prevent the axial turbulence of the impeller airflow, thereby achieving smooth outflow of the inter-leaf flow passage.
本申请还提供一种空调器，根据本申请的空调器(图中未示出)的实施例包括离心式风机，离心式风机为上述的离心式风机。离心式风机包括轮毂10、叶轮后盘20和多个叶片30， 叶轮后盘20套设在轮毂10上，多个叶片30设置叶轮后盘20上并沿周向设置在轮毂10的外侧，叶片30的高度沿其延伸方向逐渐地向外缩小。当离心式风机工作时，叶片30的靠近轮毂10的前缘的速度相对于叶片30的远离轮毂10的后缘的速度要小，上述结构可以增大叶片30的前缘的扫风面积，这样可以大大减小叶片30之间气流流动的不均匀度，该结构配合流线形翼型，能充分降低叶片30的入口处的速度与压力梯度，由此使叶片30的壁面附近压差低于产生分离流的逆压梯度，以此有效地避免多类紊流流动在前缘产生，从而提高风机性能，实现降噪效果。The present application also provides an air conditioner. The embodiment of the air conditioner (not shown) according to the present application includes a centrifugal fan, and the centrifugal fan is the centrifugal fan described above. The centrifugal fan includes a hub 10, an impeller rear disk 20, and a plurality of blades 30, The impeller rear disc 20 is sleeved on the hub 10, and a plurality of vanes 30 are disposed on the impeller rear disc 20 and circumferentially disposed on the outer side of the hub 10, and the height of the vane 30 is gradually outwardly reduced in the extending direction thereof. When the centrifugal fan is operated, the speed of the blade 30 near the leading edge of the hub 10 is smaller than the speed of the blade 30 away from the trailing edge of the hub 10. The above structure can increase the sweeping area of the leading edge of the blade 30, such that The unevenness of the flow of the airflow between the blades 30 can be greatly reduced. This structure, in conjunction with the streamlined airfoil, can sufficiently reduce the velocity and pressure gradient at the inlet of the blade 30, thereby causing the pressure difference near the wall of the blade 30 to be lower than The reverse pressure gradient of the separated flow is generated, thereby effectively avoiding the generation of various types of turbulent flow at the leading edge, thereby improving the performance of the fan and achieving the noise reduction effect.
以上所述仅为本发明的优选实施例而已，并不用于限制本发明，对于本领域的技术人员来说，本发明可以有各种更改和变化。凡在本发明的精神和原则之内，所作的任何修改、等同替换、改进等，均应包含在本发明的保护范围之内。 The above description is only the preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes can be made to the present invention. Any modifications, equivalent substitutions, improvements, etc. made within the spirit and scope of the present invention are intended to be included within the scope of the present invention.

Claims (11)

  1. 一种离心式风机，包括：A centrifugal fan comprising:
    轮毂(10)；Wheel hub (10);
    叶轮后盘(20)，套设在所述轮毂(10)上；An impeller rear disc (20) is sleeved on the hub (10);
    多个叶片(30)，多个所述叶片(30)设置所述叶轮后盘(20)上并沿周向设置在所述轮毂(10)的外侧，a plurality of blades (30), a plurality of said blades (30) being disposed on said impeller rear disk (20) and circumferentially disposed outside said hub (10)
    其特征在于，所述叶片(30)的高度沿其延伸方向逐渐地向外缩小。It is characterized in that the height of the blade (30) gradually decreases outward in the direction in which it extends.
  2. 根据权利要求1所述的离心式风机，其特征在于，所述叶片(30)的最大高度hmax与最小高度hmin比值在1～2的范围内。The centrifugal fan according to claim 1, characterized in that the ratio of the maximum height h max to the minimum height h min of the blade (30) is in the range of 1 to 2.
  3. 根据权利要求1所述的离心式风机，其特征在于，所述叶片(30)的远离所述叶轮后盘(20)的侧面与平行于所述叶轮后盘(20)的表面之间具有第一夹角θ1，所述第一夹角θ1小于90°。A centrifugal fan according to claim 1, wherein a side of said blade (30) remote from said impeller rear disk (20) and a surface parallel to said impeller rear disk (20) have An angle θ 1 , the first angle θ 1 is less than 90°.
  4. 根据权利要求3所述的离心式风机，其特征在于，所述第一夹角θ1在3°～16°的范围内。The centrifugal fan according to claim 3, wherein said first included angle θ 1 is in the range of 3° to 16°.
  5. 根据权利要求1所述的离心式风机，其特征在于，所述叶片(30)的远离所述叶轮后盘(20)的侧面为弧面状。The centrifugal fan according to claim 1, characterized in that the side surface of the blade (30) remote from the impeller rear disk (20) is curved.
  6. 根据权利要求1所述的离心式风机，其特征在于，所述叶片(30)的朝向所述轮毂(10)的侧面与平行于所述叶轮后盘(20)的表面之间具有第二夹角θ2，所述第二夹角θ2小于85°。The centrifugal fan according to claim 1, characterized in that the side of the blade (30) facing the hub (10) has a second clamp between the surface parallel to the rear disc (20) of the impeller The angle θ 2 , the second angle θ 2 is less than 85°.
  7. 根据权利要求6所述的离心式风机，其特征在于，所述第二夹角θ2在35°～60°范围内。The centrifugal fan according to claim 6, wherein said second included angle θ 2 is in the range of 35° to 60°.
  8. 根据权利要求1所述的离心式风机，其特征在于，所述离心式风机还包括盖设在多个所述叶片(30)上的叶轮前盘(40)，所述叶轮前盘(40)的朝向所述叶片(30)的表面与所述叶片(30)的远离所述叶轮后盘(20)的侧面之间具有间隙。The centrifugal fan according to claim 1, wherein the centrifugal fan further comprises an impeller front disc (40) covered on the plurality of the vanes (30), the impeller front disc (40) There is a gap between the surface facing the blade (30) and the side of the blade (30) remote from the rear disk (20) of the impeller.
  9. 根据权利要求8所述的离心式风机，其特征在于，所述间隙在1.5mm～6mm范围内。The centrifugal fan according to claim 8, wherein the gap is in the range of 1.5 mm to 6 mm.
  10. 根据权利要求1所述的离心式风机，其特征在于，所述离心式风机还包括盖设在多个所述叶片(30)上的叶轮前盘(40)，所述叶轮前盘(40)的朝向所述叶片(30)的表面与所述叶片(30)的远离所述叶轮后盘(20)的侧面贴合。The centrifugal fan according to claim 1, wherein the centrifugal fan further comprises an impeller front disc (40) covered on the plurality of the vanes (30), the impeller front disc (40) The surface facing the blade (30) is in contact with the side of the blade (30) remote from the rear wheel (20) of the impeller.
  11. 一种空调器，包括离心式风机，其特征在于，所述离心式风机为权利要求1至10中任一项所述的离心式风机。 An air conditioner comprising a centrifugal fan, wherein the centrifugal fan is the centrifugal fan according to any one of claims 1 to 10.
PCT/CN2015/093128 2014-10-29 2015-10-28 Centrifugal blower and air conditioner having same WO2016066113A1 (en)

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