CN204493271U - A kind of centrifugal blower fan blade wheel - Google Patents
A kind of centrifugal blower fan blade wheel Download PDFInfo
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- CN204493271U CN204493271U CN201520081238.1U CN201520081238U CN204493271U CN 204493271 U CN204493271 U CN 204493271U CN 201520081238 U CN201520081238 U CN 201520081238U CN 204493271 U CN204493271 U CN 204493271U
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Abstract
A kind of centrifugal blower fan blade wheel, comprise wheel disc and be arranged on the blade on wheel disc, it is characterized in that: described blade comprises wide blade and narrow blades, leaf road is formed between two adjacent wide blades, described narrow blades is located at Ye Daonei, the distance d2 of leaf road length d1 in a circumferential direction, narrow blades and adjacent wide blade pressure surface, satisfy condition: 1/4<d2/d1<1/2, the radial width d3 of narrow blades, the radial width d4 of wide blade, satisfy condition 1/3<d3/d4<2/3.The utility model has the advantage of: the radial width of the narrow blades being positioned at Ye Daonei is designed to 1/3 to 2/3 of wide blade radial width by this centrifugal blower fan blade wheel, and the distance of narrow blades and adjacent wide blade pressure surface is designed to 1/4 to 1/2 of leaf road length, thus the obstruction at blade inlet place can be effectively reduced, reduce the leaf road angle of flare, make the noise reduction of blower fan and pressure and flow loss less, namely under not losing the prerequisite of aerodynamic performance, aerodynamic noise can be reduced as much as possible as far as possible.
Description
Technical field
The utility model relates to a kind of centrifugal blower, especially relates to a kind of centrifugal blower fan blade wheel.
Background technique
Impeller is the vitals of centrifugal blower, and the working principle of centrifugal blower is the effect of gas by centrifugal force, sucks through its impeller central position, then flows through the leaf road between blade and flows out outward.Research finds, the flowing diffusion degree in centrifugal blower fan blade wheel passage is comparatively large, easily produces airflow breakaway, and near the suction surface at particularly impeller rear portion, segregation phenomenon is serious, causes the distribution of impeller outlet circumference air-flow very uneven.Because wheel speed is higher, thus uneven impeller outlet air-flow can produce strong unsteady interaction with the static part of around non-axisymmetric distribution, this is the one of the main reasons producing centrifugal blower aerodynamic noise, particularly discrete noise, and brings adverse effect to the aeroperformance of blower fan.
The energy loss of blower fan is divided into flow losses, volumetric loss and mechanical loss, wherein based on flow losses.Because gas has viscosity, there is friction in various degree and the loss such as to be separated in draught fan impeller and spiral case, fan efficiency is made to be difficult to reach desirable, centrifugal fan blade plays a major role to the actual flow situation in impeller, reasonably optimizing vane type line and blade pattern, effectively can promote blower fan and other combination properties.Periodicity effect between blade wake passing and snail tongue is the reason that fundamental frequency (blade passing frequency) noise becomes the main aerodynamic noise of centrifugal blower.
At present, the research of Aerodynamic Performance of Centrifugal Fan and aerodynamic noise is mostly conceived to change the aspects such as the inclination angle of snail tongue, volute shape, blade shape and quantity both at home and abroad.Some researchs of recent domestic show, it is more more even than the single-row blade of employing that reasonable Arrangement big and small blade can make centrifugal impeller output flow parameter circumferentially distribute, to the unsteady flo w impact loss reduced between impeller and static part and aerodynamic noise favourable.In addition, aeroperformance and aerodynamic noise also usually also exist the relation of restriction mutually, and the lifting of a side brings the decline of the opposing party sometimes, and the method simultaneously can improving Aerodynamic Performance of Centrifugal Fan and aerodynamic noise is the main target that current research is pursued.In order to reduce the noise peak at fundamental frequency place, some scholars have proposed the structure becoming to adopt variable pitch impeller by Impeller Design, the noise peak at fundamental frequency place disperseed, thus reduce total noise level with this.
Model utility content
Technical problem to be solved in the utility model is for above-mentioned prior art present situation, provides a kind of centrifugal blower fan blade wheel that can effectively reduce leaf road air flow swirl.
The utility model solves the problems of the technologies described above adopted technological scheme: this centrifugal blower fan blade wheel, comprise wheel disc and be arranged on the blade on wheel disc, it is characterized in that: described blade comprises wide blade and narrow blades, leaf road is formed between two adjacent wide blades, described narrow blades is located at Ye Daonei, leaf road length d1 in a circumferential direction, the distance d2 of narrow blades and adjacent wide blade pressure surface, satisfy condition: 1/4<d2/d1<1/2, the radial width d3 of narrow blades, the radial width d4 of wide blade, satisfy condition 1/3<d3/d4<2/3.
Preferably, the relation of described d1 and d2 and d3 and d4 satisfies condition: d2/d1=1/3 and d3/d4=1/2.Learn according to research, for forward centrifugal blower fan, the radial width adding narrow blades is larger, and its total head is higher, but the amplitude raised reduces, and, within the specific limits, narrow blades moves from suction surface to pressure side, and pressure and efficiency all become large, but after narrow blades is respective leaves road length 1/3 from the distance of pressure side, the pressure near pressure side reduces on the contrary.So, adopt said structure, be more conducive to reducing even to eliminate leaf road air flow swirl, thus be more conducive to reducing the obstruction at blade inlet place and reduce the leaf road angle of flare, so make the noise reduction of blower fan and pressure and flow loss less.
Further preferably, described narrow blades and adjacent wide blade are bending to the same side.
Narrow blades can have multiple different distributed architecture, and a kind of preferred version is, described wide blade and narrow blades spaced apart, be namely equipped with a slice narrow blades at each described Ye Daonei.Like this, the quantity of narrow blades is identical with the quantity of wide blade.
Another kind of preferred version is between described two adjacent narrow blades, be provided with the wide blade of at least two panels.
Another preferred version is, is provided with four wide blades between described two adjacent narrow blades.Namely the quantity of narrow blades is 1/4 of wide blade quantity.
Narrow blades can be arranged on the diverse location in leaf road, and a kind of preferred version is, described narrow blades is located at the air outlet place in leaf road.
Another kind of preferred version is that described narrow blades is located at the suction port place in leaf road.Experiment finds, after the suction port employing narrow blades in leaf road, obviously can reduce the air flow swirl even eliminating whole leaf road.
Compared with prior art, the utility model has the advantage of: the radial width of the narrow blades being positioned at Ye Daonei is designed to 1/3 to 2/3 of wide blade radial width by this centrifugal blower fan blade wheel, and the distance of narrow blades and adjacent wide blade pressure surface is designed to 1/4 to 1/2 of leaf road length, leaf road air flow swirl can be effectively reduced, thus the obstruction at blade inlet place can be effectively reduced and reduce the leaf road angle of flare, make the noise reduction of blower fan and pressure and flow loss less, namely can under not losing the prerequisite of aerodynamic performance as far as possible, reduce aerodynamic noise as much as possible.
Accompanying drawing explanation
Fig. 1 is the structural representation of the utility model embodiment one;
Fig. 2 is the sectional view of the utility model embodiment one;
Fig. 3 is the enlarged diagram of part A in Fig. 2;
Fig. 4 is the structural representation of the utility model embodiment two;
Fig. 5 is the structural representation of the utility model embodiment three;
Fig. 6 is the structural representation of the utility model embodiment four;
Fig. 7 is the structural representation of the utility model embodiment five;
Fig. 8 is the structural representation of the utility model embodiment six.
Embodiment
Below in conjunction with accompanying drawing, embodiment is described in further detail the utility model.
Embodiment one:
As shown in Figure 1 to Figure 3, wide blade 2, narrow blades 3 that the impeller in the present embodiment comprises wheel disc 1 and is arranged on wheel disc 1, wide blade 2 is distributed on the excircle of wheel disc 1 evenly and at intervals, forms leaf road 4 between the wide blade 2 of two panels.Narrow blades 3 is located in leaf road 4, and is provided with four wide blades 2 between two adjacent narrow blades 3, and namely the quantity of narrow blades 3 is 1/4 of wide blade 2 quantity, and such as the centrifugal blower fan blade wheel of routine, if wide blade 2 quantity is 60, then the quantity of narrow blades 3 is 15.Further, narrow blades 3 and adjacent wide blade 2 are bending to the same side.
In addition, in the present embodiment, narrow blades 3 is located at the suction port place in leaf road 4, experiment shows, after leaf road suction port arranges narrow blades 3, leaf road air-flow produces whirlpool hardly, can effectively reduce the obstruction at blade inlet place, reduce the leaf road angle of flare to reduce from loss, reduce slip coefficient simultaneously and improve acting ability.If leaf road 4 length is in a circumferential direction d1, the concave surface of wide blade 2 is pressure side 21, and the convex surface of wide blade 2 is suction surface 22, and narrow blades 3 is d2 with the distance of adjacent wide blade 2 pressure side 21, then satisfy condition: d2/d1=1/3.If the radial width of narrow blades 3 is d3, the radial width of wide blade 2 is d4, then satisfy condition: d3/d4=1/2.Adopt after said structure, the noise reduction of blower fan and pressure and flow loss less, namely can under not losing the prerequisite of aerodynamic performance as far as possible, reduction aerodynamic noise as much as possible.
Embodiment two:
As shown in Figure 4, in the present embodiment, narrow blades 3 is located at the suction port place in leaf road 4, is provided with the wide blade 2 of two panels between two adjacent narrow blades 3, and namely the quantity of narrow blades 3 is the half of wide blade 2 quantity.All the other structures are identical with the structure in embodiment one, do not launch to describe at this.
Embodiment three:
As shown in Figure 5, in the present embodiment, narrow blades 3 is located at the suction port place in leaf road 4, in each leaf road 4, be equipped with a slice narrow blades 3, and namely narrow blades 3 is identical and spaced apart with the quantity of wide blade 2.All the other structures are identical with the structure in embodiment one, do not launch to describe at this.
Embodiment four:
As shown in Figure 6, in the present embodiment, narrow blades 3 is located at the air outlet place in leaf road 4, in each leaf road 4, be equipped with a slice narrow blades 3, and namely narrow blades 3 is identical and spaced apart with the quantity of wide blade 2.If the length in leaf road 4 is d1, if narrow blades 3 is d2 with the distance of adjacent wide blade 2 pressure side, then meet d2/d1=1/3, if the radial width of narrow blades 3 is d3, the radial width of wide blade 2 is d4, then meet and d3/d4=1/2.
Embodiment five:
As shown in Figure 7, in the present embodiment, narrow blades 3 is located at the air outlet place in leaf road 4, the wide blade 2 of two panels is provided with between two adjacent narrow blades 3, namely the quantity of narrow blades 3 is the half of wide blade 2 quantity, and all the other structures are identical with the structure in embodiment four, does not launch to describe at this.
Embodiment six:
As shown in Figure 8, in the present embodiment, narrow blades 3 is located at the air outlet place in leaf road 4, and be separated with the leaf road 4 that does not arrange narrow blades 3 between every three narrow blades 3, all the other structures are identical with the structure in embodiment four, does not launch to describe at this.
The foregoing is only preferred implementation of the present utility model; should be understood that; for those of ordinary skills; do not departing under principle prerequisite of the present utility model; multiple remodeling or improvement can be carried out to the utility model; such as can also adopt other structures spaced apart between narrow blades and wide blade, these are all regarded as within protection domain of the present utility model.
Claims (8)
1. a centrifugal blower fan blade wheel, the blade comprising wheel disc (1) and be arranged on wheel disc, it is characterized in that: described blade comprises wide blade (2) and narrow blades (3), leaf road (4) is formed between two adjacent wide blades (2), described narrow blades (3) is located in leaf road (4), leaf road (4) length d1 in a circumferential direction, the distance d2 of narrow blades (3) and adjacent wide blade (2) pressure side (21), satisfy condition: 1/4<d2/d1<1/2, the radial width d3 of narrow blades (3), the radial width d4 of wide blade (2), satisfy condition 1/3<d3/d4<2/3.
2. centrifugal blower fan blade wheel according to claim 1, is characterized in that: the relation of described d1 and d2 and d3 and d4 satisfies condition: d2/d1=1/3 and d3/d4=1/2.
3. centrifugal blower fan blade wheel according to claim 1, is characterized in that: described narrow blades (3) and adjacent wide blade (2) are bending to the same side.
4. centrifugal blower fan blade wheel according to claim 1, it is characterized in that: described wide blade (2) is spaced apart with narrow blades (3), namely in each described leaf road (4), be equipped with a slice narrow blades (3).
5. centrifugal blower fan blade wheel according to claim 1, is characterized in that: between described two adjacent narrow blades (3), be provided with the wide blade of at least two panels (2).
6. centrifugal blower fan blade wheel according to claim 5, is characterized in that: between described two adjacent narrow blades (3), be provided with four wide blades (2).
7. the centrifugal blower fan blade wheel according to claim arbitrary in claim 1 to 6, is characterized in that: described narrow blades (3) is located at the air outlet place in leaf road (4).
8. the centrifugal blower fan blade wheel according to claim arbitrary in claim 1 to 6, is characterized in that: described narrow blades (3) is located at the suction port place in leaf road (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520081238.1U CN204493271U (en) | 2015-02-05 | 2015-02-05 | A kind of centrifugal blower fan blade wheel |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201520081238.1U CN204493271U (en) | 2015-02-05 | 2015-02-05 | A kind of centrifugal blower fan blade wheel |
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| CN204493271U true CN204493271U (en) | 2015-07-22 |
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| CN201520081238.1U Active CN204493271U (en) | 2015-02-05 | 2015-02-05 | A kind of centrifugal blower fan blade wheel |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109944828A (en) * | 2019-04-01 | 2019-06-28 | 青岛海尔智能技术研发有限公司 | A kind of centrifugal blower and electric appliance |
| CN111350691A (en) * | 2020-04-17 | 2020-06-30 | 山东攀峰通风设备有限公司 | High-pressure centrifugal fan impeller |
| CN113530883A (en) * | 2021-07-15 | 2021-10-22 | 广东顺威精密塑料股份有限公司 | Combined centrifugal impeller |
-
2015
- 2015-02-05 CN CN201520081238.1U patent/CN204493271U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109944828A (en) * | 2019-04-01 | 2019-06-28 | 青岛海尔智能技术研发有限公司 | A kind of centrifugal blower and electric appliance |
| CN111350691A (en) * | 2020-04-17 | 2020-06-30 | 山东攀峰通风设备有限公司 | High-pressure centrifugal fan impeller |
| CN113530883A (en) * | 2021-07-15 | 2021-10-22 | 广东顺威精密塑料股份有限公司 | Combined centrifugal impeller |
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