CN103062112A - Road cleaning equipment and centrifugal fan impeller thereof - Google Patents
Road cleaning equipment and centrifugal fan impeller thereof Download PDFInfo
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- CN103062112A CN103062112A CN201310009047XA CN201310009047A CN103062112A CN 103062112 A CN103062112 A CN 103062112A CN 201310009047X A CN201310009047X A CN 201310009047XA CN 201310009047 A CN201310009047 A CN 201310009047A CN 103062112 A CN103062112 A CN 103062112A
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- 238000004140 cleaning Methods 0.000 title claims abstract description 22
- 229920003266 Leaf® Polymers 0.000 claims description 88
- 230000010349 pulsation Effects 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 238000005265 energy consumption Methods 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 238000000926 separation method Methods 0.000 description 2
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 2
- 239000008358 core component Substances 0.000 description 1
- 238000009792 diffusion process Methods 0.000 description 1
- 238000004134 energy conservation Methods 0.000 description 1
- 238000005457 optimization Methods 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
- 230000006641 stabilisation Effects 0.000 description 1
- 238000011105 stabilization Methods 0.000 description 1
- 238000010408 sweeping Methods 0.000 description 1
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Abstract
The invention discloses a centrifugal fan impeller and a road cleaning device with the centrifugal fan impeller, wherein the centrifugal fan impeller comprises a wheel disc (3) and blades arranged on the wheel disc (3) along the circumferential direction, the blades comprise long blades (1), the long blades (1) sequentially comprise a first arc-shaped section (4) and a second arc-shaped section (5) in the direction from the center of the wheel disc (3) to the edge of the wheel disc (3), the long blades (1) are forward-type blades in the first arc-shaped section (4) and backward-type blades in the second arc-shaped section (5). The centrifugal fan impeller is good in pneumatic performance and low in noise, and after the centrifugal fan impeller is used, the road cleaning equipment is good in cleaning capacity and product performance.
Description
Technical field
The present invention relates to the blower fan field, particularly, relate to a kind of centrifugal blower fan blade wheel and a kind of road cleaning equipment with this centrifugal blower fan blade wheel.
Background technique
In the existing road cleaning equipment, centrifugal blower adopts impeller as shown in Figure 1 mostly, the impeller Leaf is the backward type blade, and the meridian molded line of blade is straight line or circular arc, this impeller easily produces eddy current in use and hinders mobile, generation flow separation, especially forms larger whirlpool and significantly pressure pulsation at the suction port place of blade, when variable working condition, eddy current is more violent, and eddy current is blower fan generation aerodynamic noise and the main cause that reduces flow.
Summary of the invention
The purpose of this invention is to provide a kind of centrifugal blower fan blade wheel and a kind of road cleaning equipment with this centrifugal blower fan blade wheel, described centrifugal blower fan blade wheel aeroperformance is good and noise is little.
To achieve these goals, the invention provides a kind of centrifugal blower fan blade wheel, this centrifugal blower fan blade wheel comprises wheel disc and along the blade of circumferential arrangement on described wheel disc, wherein, described blade comprises linear leaf, from the center of described wheel disc on the direction at the edge of described wheel disc, described linear leaf comprises the first arcuate segment and the second arcuate segment successively, described linear leaf is forward direction type blade at described the first arcuate segment, is the backward type blade at described the second arcuate segment.
Preferably, described linear leaf is respectively circular arc and tangent to each other the connection at the mean camberline at described the first arcuate segment place with the mean camberline of described linear leaf at described the second arcuate segment place, and described linear leaf is 0.4 ~ 0.6 at mean camberline and the described linear leaf at described the first arcuate segment place at the ratio of the radius of curvature of the mean camberline at described the second arcuate segment place.
Preferably, the outlet diameter of described linear leaf is that D1, inlet diameter are D2, the first arcuate segment of described linear leaf and the tie point of the second arcuate segment are D3 to the twice of the distance at the center of described wheel disc, and then the ratio of D2:D3:D1 is 1:1.46 ~ 1.57:2.17 ~ 2.36.
Preferably, the inlet air flow angle of described linear leaf is 27 ° ~ 33 °.
Preferably, the outlet flow angle of described linear leaf is 35 ° ~ 45 °.
Preferably, described blade also comprises the short blade that has less extended length than described linear leaf, and described short blade is between adjacent two described linear leafs, and described short blade is near the distolateral setting of outlet of described linear leaf and be the backward type blade.
Preferably, the extended length of described short blade be described linear leaf extended length 1/3 ~ 1/2.
Preferably, described short blade is identical with the shape and size of described the second arcuate segment, and described short blade is arranged on the centre of adjacent two described linear leafs.
Preferably, described centrifugal blower fan blade wheel comprises 8 ~ 16 described linear leafs, and is provided with a described short blade between per two adjacent described linear leafs.
The present invention also provides a kind of road cleaning equipment, and this road cleaning equipment comprises centrifugal blower, and described centrifugal blower comprises above-mentioned centrifugal blower fan blade wheel.
Linear leaf comprises the first arcuate segment and the second arcuate segment in the centrifugal blower fan blade wheel of the present invention, and linear leaf is forward direction type blade at the first arcuate segment, linear leaf is the backward type blade at the second arcuate segment, forward direction type blade is strong to air-flow acting ability, can produce higher air pressure, the backward type blade is conducive to flowing of air-flow, so that can produce larger flow and can reduce noise, centrifugal blower fan blade wheel of the present invention in use, after entering from suction port, air-flow at first is subject to the effect of the first arcuate segment, the first arc does work by force to air-flow, so that the kinetic energy of air-flow and pressure increase, then air-flow arrives the second arcuate segment and flows out blade passage by the second arcuate segment water conservancy diversion along linear leaf, air current flow is smooth and easy, thereby suppress the generation Effective Raise flow efficiency of eddy current and reduce pressure pulsation, improve the pneumatic efficiency of blower fan and reduce noise, increase simultaneously the height-rise pressure of blower fan.
Other features and advantages of the present invention will partly be described in detail in embodiment subsequently.
Description of drawings
Accompanying drawing is to be used to provide a further understanding of the present invention, and consists of the part of specification, is used from explanation the present invention with following embodiment one, but is not construed as limiting the invention.In the accompanying drawings:
Fig. 1 is the structural representation according to the centrifugal blower fan blade wheel of prior art;
Fig. 2 is the structural representation according to centrifugal blower fan blade wheel of the present invention;
Fig. 3 is the partial enlarged drawing of the centrifugal blower fan blade wheel among Fig. 2.
Description of reference numerals
1 linear leaf, 2 short blades, 3 wheel discs
4 first arcuate segments, 5 second arcuate segments
Embodiment
Below in conjunction with accompanying drawing the specific embodiment of the present invention is elaborated.Should be understood that, embodiment described herein only is used for description and interpretation the present invention, is not limited to the present invention.
Embodiments of the invention provide a kind of centrifugal blower fan blade wheel, and with reference to shown in Figure 2, this centrifugal blower fan blade wheel comprises wheel disc 3 and along the blade of circumferential arrangement on wheel disc 3, described blade extends to the direction at the edge of wheel disc 3 along the center from wheel disc 3.Wherein, described blade comprises linear leaf 1, from the center of wheel disc 3 on the direction at the edge of wheel disc 3, linear leaf 1 comprises the first arcuate segment 4 and the second arcuate segment 5 successively, linear leaf 1 is forward direction type blade at the first arcuate segment 4, is the backward type blade at the second arcuate segment 5.
Particularly, in impeller shown in Figure 3, impeller is around turning clockwise, the tangent direction of the mean camberline (blade is along the center line in grain direction cross section) at the first arcuate segment 4 places of linear leaf 1 and the reciprocal angle of impeller circumferential speed are greater than 90 °, be forward direction type blade, the tangent direction of the mean camberline at the second arcuate segment 5 places of linear leaf 1 and the reciprocal angle of impeller circumferential speed are the backward type blade less than 90 °.In this case, because forward direction type blade is strong to air-flow acting ability, can produce higher air pressure, and the backward type blade is conducive to flowing of air-flow, so that can produce larger flow and can reduce noise, the centrifugal blower fan blade wheel of the present embodiment is in conjunction with both advantages, when work, air-flow enters the effect that at first is subject to the first arcuate segment 4 of linear leaf 1 behind the impeller of centrifugal blower from the suction port (being positioned at the proximal part of wheel disc 3) of impeller, 4 pairs of air-flows of the first arc do work by force, so that air-flow obtains certain kinetic energy and pressure, then air-flow arrives the second arcuate segment 5 along linear leaf, the air-flow that has larger kinetic energy and pressure by 5 pairs of the second arcuate segments carries out water conservancy diversion makes it have preferably mobile performance and the final blade passage that flows out, the guide functions of the second arcuate segment 5 by backward type, the generation of establishment eddy current, thereby make the more smooth and easy Effective Raise flow efficiency of air current flow and reduce pressure pulsation, improve the pneumatic efficiency of blower fan and reduce noise, be conducive to simultaneously improve the blower press liter.
Preferably, the mean camberline at the first arcuate segment 4 places of linear leaf 1 is respectively circular arc and tangent to each other the connection with the mean camberline at the second arcuate segment 5 places, and the ratio of the radius of curvature of the mean camberline at the mean camberline at the first arcuate segment 4 places of linear leaf 1 and the second arcuate segment 5 places of linear leaf 1 is 0.4 ~ 0.6.For making airflow smooth ground flow to the second arcuate segment 5 from the first arcuate segment 4, linear leaf 1 is respectively circular arc and tangent to each other the connection at the mean camberline at the first arcuate segment 4 places with mean camberline at the second arcuate segment 5 places, again since the degree of crook at the second arcuate segment 5 places of the degree of crook of the first arcuate segment 4 of linear leaf 1 and linear leaf 1 to pressure and the mobile important of air-flow, thereby, be controlled in the appropriate scope (be above-mentioned 0.4 ~ 0.6 scope) by the ratio with the radius of curvature of the mean camberline at the mean camberline at the first arcuate segment 4 places of linear leaf 1 and the second arcuate segment 5 places, so that linear leaf 1 namely can be increased to air pressure suitable size and can effectively guarantee air current flow efficient again getting up steam and guaranteeing air current flow this reaches state than balance aspect two.
Further preferably, the outlet diameter of linear leaf 1 is that D1, inlet diameter are D2, the first arcuate segment 4 of linear leaf 1 and the tie point of the second arcuate segment 5 are D3 to the twice of the distance at the center of wheel disc 3, and then the ratio of D2:D3:D1 is 1:1.46 ~ 1.57:2.17 ~ 2.36.Referring to Fig. 3, the outlet diameter D1 of linear leaf 1 refers to that the outlet edge of linear leaf 1 is to the twice of the distance at the center of wheel disc 3, the inlet diameter D2 of linear leaf 1 refers to that the ingress edge of linear leaf 1 is to the twice of the distance at the center of wheel disc 3, under these conditions, linear leaf 1 has the first arcuate segment 4 of suitable extended length and linear leaf 1 and the second arcuate segment 5 that suitable extended length ratio is arranged with respect to suction port, with the shape of further optimization linear leaf 1, make the combination property of the air pressure of centrifugal blower fan blade wheel and flow efficiency better.Preferentially, D1 is that 500mm ~ 520mm, D2 are that 220mm ~ 230mm, D3 are 335mm ~ 345mm.
Particularly, the inlet air flow angle of linear leaf 1 (being expressed as β among Fig. 3) is 27 ° ~ 33 °.Referring to Fig. 3, the inlet air flow angle β of linear leaf 1 refers to that linear leaf 1 is at tangent line and the angle of linear leaf 1 between the tangent line of an end place of suction port circle at an end place of suction port.In the centrifugal blower operation process, at the suction port place, significantly pressure pulsation appears in larger eddy current thereby air-flow is subject to blade effect meeting generation, if when being arranged on inlet air flow angle β in the above-mentioned scope, then can guarantee to flow into along the direction consistent with the tangent line of linear leaf 1 close suction port one end from the air-flow that suction port flows into, guarantee effectively that namely air-flow flows in the blade passage along the direction of linear leaf 1 smoothly, thereby greatly reduced the generation of suction port place eddy current, extraneous airflow smooth is entered in the blower fan, to a certain extent the aeroperformance of Effective Raise blower fan.
And the outlet flow angle of linear leaf 1 (being expressed as α among Fig. 3) is 35 ° ~ 45 °.Referring to Fig. 3, the outlet flow angle α of linear leaf 1 refer to linear leaf 1 away from the tangent line at an end place of suction port and linear leaf 1 away from the angle between the tangent line of the end place circle of suction port.Outlet flow angle α is set like this can effectively reduces linear leaf 1 away from the interference to air-flow of an end of suction port, avoid runner to separate the generation in whirlpool, airflow smooth ground is flowed out from blade passage, reach the effect that improves air-flow velocity and reduction noise.
In addition, under the preferable case, described blade also comprises the short blade 2 that has less extended length than linear leaf 1, and short blade 2 is between adjacent two linear leafs 1, and short blade 2 is near the distolateral setting of outlet of linear leafs 1 and be the backward type blade.After short blade 2 is set, flow separation easily occurs what flow to linear leaf 1 when distolateral by importing and exporting in air-flow, namely in the outlet section side near linear leaf 1, air-flow is cut by short blade 2, suppressing eddy current produces, thereby guarantee that air-flow is full of the impeller space equably, the current stabilization diffusion, reduce eddy current loss, reduce pressure pulsation and reduce noise.
Wherein, the extended length of short blade 2 can be 1/3 ~ 1/2 of the extended length of linear leaf 1, disturbs so that this short blade 2 avoids when playing steady flow result pressurized effect to 4 pairs of air-flows of the first arcuate segment of linear leaf 1 to produce.
And particularly, as shown in Figures 2 and 3, in this embodiment, short blade 2 is identical with the shape and size of the second arcuate segment 5 of linear leaf 1, and short blade 2 is arranged on the centre of adjacent two linear leafs 1.
In addition, in the centrifugal blower fan blade wheel of above-mentioned mode of execution, centrifugal blower fan blade wheel preferably includes 8-16 linear leaf 1, and is provided with a short blade 2 between per two adjacent linear leafs 1, noise when in this case, centrifugal blower fan blade wheel turns round can be reduced in the less scope.
Embodiment shown in Fig. 2 and Fig. 3 finds by the blade design to impeller to be rear impeller behind the CFD analog simulation, eddy current produces and greatly reduces in the runner, and air-flow can smooth and easyly flow through runner, noise is little and can obtain larger total head liter.
Such as negative pressure type road cleaning equipment such as sweeping machines, blower fan is the core component of equipment, produce the negative-pressure pneumatic transport model by blower fan and finish road cleaning, the performance of blower fan is good and bad directly affect the working efficiency of road cleaning equipment and comprises the product performance such as noise, energy consumption, and for example blade that adopts in the existing road cleaning equipment is in the draught fan impeller of backward type blade because a large amount of eddy current of generation, the smooth and easy mobile increase that causes energy consumption and noise of obstruction air-flow in the runner.
Thereby the present invention also provides a kind of road cleaning equipment, and this road cleaning equipment comprises centrifugal blower, and described centrifugal blower comprises according to centrifugal blower fan blade wheel of the present invention.After adopting described centrifugal blower fan blade wheel, thereby air-flow can obtain larger pressure, increase the cleaning ability of the height-rise pressure raising road cleaning equipment of centrifugal blower, and airflow smooth flows through blade passage, suppress that eddy current produces, pressure pulsation reduces, make energy consumption and the reducing noise of described road cleaning equipment, to sum up, having centrifugal blower fan blade wheel efficient, energy-conservation and the low noise advantage according to road cleaning equipment of the present invention owing to use is of the present invention all is improved working efficiency and product performance.
Below describe by reference to the accompanying drawings preferred implementation of the present invention in detail; but; the present invention is not limited to the detail in the above-mentioned mode of execution; in technical conceive scope of the present invention; can carry out multiple simple variant to technological scheme of the present invention, these simple variant all belong to protection scope of the present invention.
Need to prove that in addition each the concrete technical characteristics described in above-mentioned embodiment in reconcilable situation, can make up by any suitable mode.
In addition, also can carry out combination in any between the various mode of execution of the present invention, as long as it is without prejudice to thought of the present invention, it should be considered as content disclosed in this invention equally.
Claims (10)
1. centrifugal blower fan blade wheel, this centrifugal blower fan blade wheel comprises wheel disc (3) and along the blade of circumferential arrangement on described wheel disc (3), it is characterized in that, described blade comprises linear leaf (1), from the center of described wheel disc (3) on the direction at the edge of described wheel disc (3), described linear leaf (1) comprises the first arcuate segment (4) and the second arcuate segment (5) successively, described linear leaf (1) is forward direction type blade at described the first arcuate segment (4), is the backward type blade at described the second arcuate segment (5).
2. centrifugal blower fan blade wheel according to claim 1, wherein, the mean camberline that described linear leaf (1) is located at described the first arcuate segment (4) is respectively circular arc and tangent to each other the connection with the mean camberline that described linear leaf (1) is located at described the second arcuate segment (5), and the ratio of the radius of curvature of the mean camberline that the mean camberline that described linear leaf (1) is located at described the first arcuate segment (4) and described linear leaf (1) are located at described the second arcuate segment (5) is 0.4 ~ 0.6.
3. centrifugal blower fan blade wheel according to claim 2, wherein, the outlet diameter of described linear leaf (1) is that D1, inlet diameter are D2, first arcuate segment (4) of described linear leaf (1) and the tie point of the second arcuate segment (5) are D3 to the twice of the distance at the center of described wheel disc (3), and then the ratio of D2:D3:D1 is 1:1.46 ~ 1.57:2.17 ~ 2.36.
4. the described centrifugal blower fan blade wheel of any one according to claim 1-3, wherein, the inlet air flow angle of described linear leaf (1) is 27 ° ~ 33 °.
5. the described centrifugal blower fan blade wheel of any one according to claim 1-3, wherein, the outlet flow angle of described linear leaf (1) is 35 ° ~ 45 °.
6. centrifugal blower fan blade wheel according to claim 1, wherein, described blade also comprises the short blade (2) that has less extended length than described linear leaf (1), described short blade (2) is positioned between adjacent two described linear leafs (1), and described short blade (2) is near the distolateral setting of outlet of described linear leaf (1) and be the backward type blade.
7. centrifugal blower fan blade wheel according to claim 6, wherein, the extended length of described short blade (2) be described linear leaf (1) extended length 1/3 ~ 1/2.
8. centrifugal blower fan blade wheel according to claim 6, wherein, described short blade (2) is identical with the shape and size of described the second arcuate segment (5), and described short blade (2) is arranged on the centre of adjacent two described linear leafs (1).
9. centrifugal blower fan blade wheel according to claim 6 is characterized in that, described centrifugal blower fan blade wheel comprises 8 ~ 16 described linear leafs (1), and is provided with a described short blade (2) between per two adjacent described linear leafs (1).
10. road cleaning equipment, this road cleaning equipment comprises centrifugal blower, it is characterized in that, described centrifugal blower comprises according to claim 1 the described centrifugal blower fan blade wheel of any one in-9.
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| CN201310009047.XA CN103062112B (en) | 2013-01-10 | 2013-01-10 | Road cleaning equipment and centrifugal fan impeller thereof |
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| CN201310009047.XA CN103062112B (en) | 2013-01-10 | 2013-01-10 | Road cleaning equipment and centrifugal fan impeller thereof |
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| CN103062112A true CN103062112A (en) | 2013-04-24 |
| CN103062112B CN103062112B (en) | 2016-07-20 |
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Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307024A (en) * | 2013-06-28 | 2013-09-18 | 开平市永强风机制造有限公司 | Impeller structure of air blower |
| CN104251230A (en) * | 2013-06-28 | 2014-12-31 | 苏州宝时得电动工具有限公司 | Centrifugal impeller and blowing and sucking device comprising same |
| CN104314867A (en) * | 2014-11-13 | 2015-01-28 | 中国北车集团大连机车研究所有限公司 | Centrifugal fan vane wheel with splitter vanes and for railway vehicle cooling system |
| CN106837861A (en) * | 2017-04-11 | 2017-06-13 | 大唐环境产业集团股份有限公司 | A kind of draught fan impeller and the method that denitration dilution wind system pipeline air quantity is improved with it |
| CN108119413A (en) * | 2017-12-26 | 2018-06-05 | 珠海格力电器股份有限公司 | Centrifugal blade, centrifugal fan and air conditioner |
| CN109236737A (en) * | 2018-11-23 | 2019-01-18 | 常州朗奇威电器有限公司 | A kind of centrifugal impeller for motor radiating |
| CN109578135A (en) * | 2018-10-29 | 2019-04-05 | 上海泰豪智能节能技术有限公司 | A kind of mute power supply of novel locomotive |
| CN111140536A (en) * | 2018-11-02 | 2020-05-12 | 河北众邦节能科技服务有限公司 | Semi-open type shunting small-flow high-pressure centrifugal fan impeller |
| CN111441989A (en) * | 2019-01-17 | 2020-07-24 | 追创科技(苏州)有限公司 | Fixed impeller, motor and dust collector |
| CN111795001A (en) * | 2020-07-06 | 2020-10-20 | 追觅科技(上海)有限公司 | Impeller and bladeless fan |
| US20200370562A1 (en) * | 2017-11-07 | 2020-11-26 | Aeronet Inc. | Impeller having primary blades and secondary blades |
| CN112032103A (en) * | 2019-06-03 | 2020-12-04 | 日本电产株式会社 | Impeller, air supply device and dust collector |
| CN114962325A (en) * | 2022-06-20 | 2022-08-30 | 太仓欣华盈电子有限公司 | High-efficiency fan blade and centrifugal fan |
| CN116292394A (en) * | 2023-05-11 | 2023-06-23 | 佛山市南海九洲普惠风机有限公司 | Retroverted centrifugal impeller with long and short composite blades |
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Cited By (17)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103307024A (en) * | 2013-06-28 | 2013-09-18 | 开平市永强风机制造有限公司 | Impeller structure of air blower |
| CN104251230A (en) * | 2013-06-28 | 2014-12-31 | 苏州宝时得电动工具有限公司 | Centrifugal impeller and blowing and sucking device comprising same |
| CN104251230B (en) * | 2013-06-28 | 2016-09-14 | 苏州宝时得电动工具有限公司 | Receded disk impeller and include the suction and blowing device of this receded disk impeller |
| CN104314867A (en) * | 2014-11-13 | 2015-01-28 | 中国北车集团大连机车研究所有限公司 | Centrifugal fan vane wheel with splitter vanes and for railway vehicle cooling system |
| CN104314867B (en) * | 2014-11-13 | 2016-08-17 | 中国北车集团大连机车研究所有限公司 | The rail vehicle cooling system centrifugal blower fan blade wheel of band splitterr vanes |
| CN106837861A (en) * | 2017-04-11 | 2017-06-13 | 大唐环境产业集团股份有限公司 | A kind of draught fan impeller and the method that denitration dilution wind system pipeline air quantity is improved with it |
| US20200370562A1 (en) * | 2017-11-07 | 2020-11-26 | Aeronet Inc. | Impeller having primary blades and secondary blades |
| CN108119413A (en) * | 2017-12-26 | 2018-06-05 | 珠海格力电器股份有限公司 | Centrifugal blade, centrifugal fan and air conditioner |
| CN109578135A (en) * | 2018-10-29 | 2019-04-05 | 上海泰豪智能节能技术有限公司 | A kind of mute power supply of novel locomotive |
| CN111140536A (en) * | 2018-11-02 | 2020-05-12 | 河北众邦节能科技服务有限公司 | Semi-open type shunting small-flow high-pressure centrifugal fan impeller |
| CN109236737A (en) * | 2018-11-23 | 2019-01-18 | 常州朗奇威电器有限公司 | A kind of centrifugal impeller for motor radiating |
| CN111441989A (en) * | 2019-01-17 | 2020-07-24 | 追创科技(苏州)有限公司 | Fixed impeller, motor and dust collector |
| CN112032103A (en) * | 2019-06-03 | 2020-12-04 | 日本电产株式会社 | Impeller, air supply device and dust collector |
| CN111795001A (en) * | 2020-07-06 | 2020-10-20 | 追觅科技(上海)有限公司 | Impeller and bladeless fan |
| CN114962325A (en) * | 2022-06-20 | 2022-08-30 | 太仓欣华盈电子有限公司 | High-efficiency fan blade and centrifugal fan |
| CN116292394A (en) * | 2023-05-11 | 2023-06-23 | 佛山市南海九洲普惠风机有限公司 | Retroverted centrifugal impeller with long and short composite blades |
| CN116292394B (en) * | 2023-05-11 | 2023-07-18 | 佛山市南海九洲普惠风机有限公司 | Retroverted centrifugal impeller with long and short composite blades |
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