CN102506029B - Impeller of centrifugal fan and centrifugal fan - Google Patents
Impeller of centrifugal fan and centrifugal fan Download PDFInfo
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- CN102506029B CN102506029B CN201110451085.1A CN201110451085A CN102506029B CN 102506029 B CN102506029 B CN 102506029B CN 201110451085 A CN201110451085 A CN 201110451085A CN 102506029 B CN102506029 B CN 102506029B
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- 238000005265 energy consumption Methods 0.000 abstract description 3
- 229920003266 Leaf® Polymers 0.000 description 82
- 230000008676 import Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 5
- 238000000926 separation method Methods 0.000 description 4
- 239000012530 fluid Substances 0.000 description 3
- 238000012986 modification Methods 0.000 description 3
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- 238000010408 sweeping Methods 0.000 description 2
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- 230000009286 beneficial effect Effects 0.000 description 1
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Abstract
The invention provides an impeller of a centrifugal fan and the centrifugal fan containing the impeller of the centrifugal fan. The impeller of the centrifugal fan comprises a wheel hub, vanes and a wheel cap, wherein the vanes are installed between the wheel hub and the wheel cap, the vanes comprise a backward long vane and a backward short vane, and the length of the flow direction of the long vane is greater than the length of the flow direction of the short vane; and moreover, the long vane and the short vane are in alternate distribution between the wheel hub and the wheel cap, and the inlet diameter of the short vane is greater than the inlet diameter of the long vane. According to the impeller of the centrifugal fan and the centrifugal fan containing the impeller of the centrifugal fan, the problems of lower pneumatic efficiency and larger energy consumption which are brought by the structure of a traditional centrifugal impeller can be solved.
Description
Technical field
The present invention relates to engineering machinery field, relate in particular to a kind of centrifugal blower fan blade wheel and centrifugal blower.
Background technique
Centrifugal blower is the mechanical energy that relies on input, improve supply gas the side by side machinery of body of gas pressure, it is a kind of driven fluid machinery, impeller is the vitals of centrifugal blower, the working principle of centrifugal blower is the effect that gas passes through centrifugal force, via its impeller center portion, suck, then flow through between blade, thereby flow out outward.
Impeller is comprised of the several parts of wheel hub, blade and wheel cap conventionally, take sweeping machine as example, it is 16 backward straight blade profile formula that the blade of the centrifugal blower fan blade wheel of its use adopts the number of blade more, as shown in Figure 1, this blade structure, be difficult to adapt to the flow performance of blower fan internal gas, easily form the rigid impulse to blade of air-flow, cause the pressure loss comparatively serious; In addition, in the conventional operating mode of sweeping machine Pneumatic System, centrifugal blower internal flow meeting forms certain flow separation and the separation of flow, especially in runner, form compared with maelstrom, during variable working condition, this eddy current is more violent, the existence of this type of eddy current narrows the valid circulation area of runner, increased again the friction of air-flow and blade wall, thereby caused the pneumatic efficiency of blower fan lower, increased operation consumption simultaneously.
Summary of the invention
The embodiment of the present invention provides a kind of centrifugal blower fan blade wheel and centrifugal blower, the problem that pneumatic efficiency is lower, energy consumption is larger of bringing in order to solve the structure of existing centrifugal blower fan blade wheel.
Based on the problems referred to above, a kind of centrifugal blower fan blade wheel that the embodiment of the present invention provides, comprise: wheel hub, blade and wheel cap, described blades installation is between described wheel hub and described wheel cap, described blade comprises backward linear leaf and short blade, described linear leaf flow to the length that flows to that length is greater than described short blade, and described linear leaf and described short blade be alternately distributed between described wheel hub and described wheel cap, the inlet diameter of described short blade is greater than the inlet diameter of described linear leaf.
Further, the outlet diameter D1 of described linear leaf and inlet diameter D2, and the outlet diameter D3 of described short blade and inlet diameter D4, meet following formula:
(D3-D4)/(D1-D2)＝1/3～1/2；
(D1-D3)/(D1-D2)＝0～0.2。
Further, the outlet diameter D1 of described linear leaf and inlet diameter D2 meet: D2/D1=0.35～0.55.
Further, the span of the outlet flow angle of described linear leaf is 35 °～45 °.
Further, described linear leaf and described short blade are evenly distributed between described wheel hub and described wheel cap.
Further, described short blade and between rear linear leaf circumferential position angle θ 1, and described short blade and between front linear leaf circumferential position angle θ 2, meet: θ 1/ θ 2=0.5～2.
Further, the quantity of described linear leaf and the quantity of described short blade are respectively in 8～12 span.
Further, the blade profile of described linear leaf and/or short blade one of is following blade profile:
Circular arc type, straight line type, parabolic shape and hyperbolic-type.
Further, when the blade profile of described linear leaf and described short blade are circular arc type, the radius of arc R1 of described linear leaf and the radius of arc R2 of described short blade meet: R2/R1=0.95～1.05.
Further, the outlet diameter D1 of described linear leaf and the radius of arc R1 of described linear leaf meet: R1/D1=0.6～0.7.
Further, the radius of arc R1 of described linear leaf and the radius of arc R2 of described short blade are equal, and the span of the blade profile angle β of short blade and linear leaf is-5 °～5 °; Described blade profile angle β is: if arrange a linear leaf through the described short blade centre of form, the angle through linear leaf and the short blade of the described short blade centre of form.
The centrifugal blower that the embodiment of the present invention provides, comprises the above-mentioned centrifugal blower fan blade wheel that the embodiment of the present invention provides.
The beneficial effect of the embodiment of the present invention comprises:
The centrifugal blower fan blade wheel that the embodiment of the present invention provides and the centrifugal blower that comprises this centrifugal blower fan blade wheel, adopt the blade of backward linear leaf and two kinds of forms of short blade, and linear leaf and short blade are alternately distributed, the inlet diameter of short blade is greater than the inlet diameter of linear leaf, short blade is located between two linear leafs like this, can isolate the circulation whirlpool in air-flow path between linear leaf, avoided the impact of eddy current on runner circulation area, significantly reduce centrifugal blower internal flow loss, thereby the output power that has improved centrifugal blower, has reduced operation consumption.
Further, the centrifugal blower fan blade wheel that the embodiment of the present invention provides and the linear leaf of centrifugal blower and the blade profile of short blade that comprise this centrifugal blower fan blade wheel all adopt circular arc type, because circular arc type is relative better with centrifugal blower internal flow feature consistency, the inner generation separation whirlpool that is difficult for of centrifugal blower runner, further reduce centrifugal blower fan blade wheel flow blockage coefficient, the increase that less flow blockage coefficient is blade provides may, more total leaf number can further improve the useful horsepower of centrifugal blower, reduces power consumption simultaneously.
Accompanying drawing explanation
Fig. 1 is the structural representation of the blade of centrifugal blower fan blade wheel in prior art;
The overall structure schematic diagram of the centrifugal blower fan blade wheel that Fig. 2 provides for the embodiment of the present invention;
The schematic diagram of the blade structure of the centrifugal blower fan blade wheel that Fig. 3 provides for the embodiment of the present invention;
Centrifugal blower fan blade wheel upper half part CONSTRUCTED SPECIFICATION schematic diagram that Fig. 4 provides for the embodiment of the present invention.
Embodiment
Below in conjunction with Figure of description, a kind of centrifugal blower fan blade wheel that the embodiment of the present invention is provided and the embodiment of centrifugal blower describe.
The centrifugal blower fan blade wheel that the embodiment of the present invention provides, as shown in Figure 2 similarly to the prior art, comprise: wheel hub 1, blade 2 and the several parts of wheel cap 3, blade 2 is installed between wheel hub 1 and wheel cap 3, difference is, inventive embodiments is improved the blade of existing centrifugal blower fan blade wheel, shown in Fig. 3 is the schematic diagram of the blade integral structure of the centrifugal blower fan blade wheel that provides of the embodiment of the present invention, as can be seen from Figure 3, the centrifugal blower fan blade wheel that the embodiment of the present invention provides provides the blade of two kinds of forms, be backward linear leaf 4 and backward short blade 5, wherein:
The length that flows to of linear leaf 4 (is the distance that fluid is passed by along linear leaf surface to outlet from import, if straight line type linear leaf, be approximately equal to linear leaf from import to the straight length outlet, if curved linear leaf, be approximately equal to linear leaf from import to the length of curve outlet) be greater than short blade 5 flow to the length (distance that to be fluid pass by along short blade surface to outlet from import, if straight line type short blade, be approximately equal to short blade from import to the length outlet, if curved short blade, be approximately equal to short blade from import to the length of curve outlet),
The inlet diameter of short blade 5 is greater than the inlet diameter of linear leaf 4.
As shown in Figure 3, when the centrifugal blower fan blade wheel that the embodiment of the present invention provides is worked, be rotated in a clockwise direction.
The linear leaf 4 of the centrifugal blower fan blade wheel that further, the embodiment of the present invention provides and/or the blade profile of short blade 5 can be one of following blade profiles:
Circular arc type, straight line type, parabolic shape, hyperbolic-type and other common line styles etc.
The blade profile of linear leaf 4 and short blade 5 can be identical, also can be different, and the embodiment of the present invention does not limit this.
Fig. 3 only all adopts circular arc type as example take the blade profile of linear leaf 4 and short blade 5, and those skilled in the art can be on the basis of Fig. 3, knows concrete structure corresponding to other common line styles by inference.
Circular arc type, due to relative better with centrifugal blower internal flow feature consistency, is difficult in centrifugal blower runner producing separating whirlpool, and therefore, in embodiments of the present invention, centrifugal blower fan blade wheel preferably adopts linear leaf and the short blade of circular arc type.
Fig. 4 is the centrifugal blower fan blade wheel upper half part detail schematic diagram shown in Fig. 3, as can be seen from Figure 4, the outlet diameter (being that the outlet edge of linear leaf is to the twice of the distance in centrifugal blower axle center) of linear leaf 4 is D1, and inlet diameter (being that the import of linear leaf is to the twice of the distance in centrifugal blower axle center) is D2; The outlet diameter (being that the outlet edge of short blade is to the twice of the distance in centrifugal blower axle center) of short blade 5 is D3, and inlet diameter (being that the import of short blade is to the twice of the distance in centrifugal blower axle center) is D4.
Preferably, in the embodiment of the present invention, D1, D2, D3 and D4, meet following formula:
(D3-D4)/(D1-D2)＝1/3～1/2；(1)
(D1-D3)/(D1-D2)＝0～0.2。(2)
From above formula (1), can find out, short blade 5 flow to length be linear leaf 4 flow to 1/3～1/2 of length;
From above formula (2), can find out, the radial distance (D1-D3) between linear leaf 4 outlets and short blade 5 outlets, and the ratio of the radial distance (D1-D2) between linear leaf 4 outlets and linear leaf 4 imports is 0～0.2.
Under special circumstances, the outlet diameter of linear leaf 4 and short blade 5 can equate.
Further, for linear leaf, its outlet diameter D1 and inlet diameter D2 meet: D2/D1=0.35～0.55.
Preferably, as shown in Figure 4, the span of the outlet flow angle α of linear leaf 4 is 35 °～45 °.
Adopting in the equally distributed situation of linear leaf, as shown in Figure 4, according to the sense of rotation of impeller, it is clockwise sense of rotation, short blade 5 and between rear linear leaf 4 (counterclockwise upper that linear leaf adjacent with short blade 5) circumferential position angle (centre of form that is short blade 5 is that radius is justified to the distance at wheel rotation center, the centre of form of short blade and with the central angle between rear linear leaf 4 in footpath, in other words be the short blade centre of form and the angle of the pressure side with footpath) be θ 1, (centre of form that is short blade 5 is that radius is justified to the distance at wheel rotation center for this short blade 5 and the position angle between front linear leaf 4 (be on clockwise direction that linear leaf) adjacent with short blade 5, the centre of form of short blade and with the central angle between front linear leaf 4 in footpath, in other words be the short blade centre of form and the angle of the suction surface with footpath) be θ 2, preferably, the span of θ 1/ θ 2 is 0.5～2.
Preferably, in the embodiment of the present invention, the quantity of linear leaf 4 and short blade 5 is respectively in 8～12 scope, in other words, the blade amt amount of centrifugal blower fan blade wheel is in 16～24 scope, and the centrifugal blower fan blade wheel of more existing 16 blades, because blade quantity suitably increases, guaranteed that centrifugal blower has higher total head liter, has improved the overall power of centrifugal blower.
Preferably, the linear leaf 4 of the centrifugal blower fan blade wheel that the embodiment of the present invention provides and the blade profile of short blade 5 all adopt in the situation of circular arc type, and the radius of arc R1 of linear leaf 4 and the radius of arc R2 of short blade 5 meet: R2/R1=0.95～1.05;
The outlet diameter D1 of linear leaf 4 and the radius of arc R1 of this linear leaf 4 meet: R1/D1=0.6～0.7.
Under special circumstances, for example, in the radius of arc R1 of linear leaf 4 situation equal with the radius of arc R2 of short blade 5, short blade 5 is-5 °～5 ° with the span of the blade profile angle β of linear leaf 4, the concrete meaning of blade profile angle is: if arrange a linear leaf through the short blade centre of form, be somebody's turn to do the angle through linear leaf and this short blade of the short blade centre of form.
Dotted portion as shown in Figure 4 represents when being if arranging the linear leaf 4 through short blade 5 centres of form ' (all linear leafs is evenly arranged wheel hub and wheel cap), this linear leaf 4 ' blade profile (linear leaf 4 shown in Fig. 4 ' cut the situation of certain length for the two ends of linear leaf), as can be seen from Figure 4, when short blade 5 is rotated counterclockwise β angle along self centre of form, its blade profile with should through linear leaf 4 of the short blade centre of form ' blade profile overlap.
The embodiment of the present invention also provides a kind of centrifugal blower, and this centrifugal blower comprises the above-mentioned centrifugal blower fan blade wheel that the embodiment of the present invention provides.The centrifugal blower fan blade wheel that this centrifugal blower use embodiment of the present invention provides is as its critical piece, and the structural relation of centrifugal blower fan blade wheel and miscellaneous part, can, with reference to the structural relation of impeller and miscellaneous part in existing centrifugal blower, not repeat them here.
The centrifugal blower fan blade wheel that the embodiment of the present invention provides and the centrifugal blower that comprises this centrifugal blower fan blade wheel, adopt the blade of backward linear leaf and two kinds of forms of short blade, and linear leaf and short blade are alternately distributed, the inlet diameter of short blade is greater than the inlet diameter of linear leaf, short blade is located between two linear leafs like this, can isolate the circulation whirlpool in air-flow path between linear leaf, avoided the impact of eddy current on runner circulation area, significantly reduce centrifugal blower internal flow loss, thereby the output power that has improved centrifugal blower, has reduced operation consumption.
Further, the centrifugal blower fan blade wheel that the embodiment of the present invention provides and the linear leaf of centrifugal blower and the blade profile of short blade that comprise this centrifugal blower fan blade wheel all adopt circular arc type, because circular arc type is relative better with centrifugal blower internal flow feature consistency, the inner generation separation whirlpool that is difficult for of centrifugal blower runner, further reduce centrifugal blower fan blade wheel flow blockage coefficient, the increase that less flow blockage coefficient is blade provides may, more total leaf number can further improve the useful horsepower of centrifugal blower, reduces power consumption simultaneously.
The embodiment of the present invention, by vane type line reasonable in design, linear leaf outlet flow angle and short blade position distribution etc., has significantly reduced the vortex structure in linear leaf outlet port, substantially can avoid the inner secondary vortex flow that produces of impeller channel, and overall aeroperformance is good; By the verification experimental verification of preferred embodiment provided by the invention, under similarity condition, the operation consumption of the embodiment of the present invention can decline closely 20%, and energy-saving effect is remarkable.
The scheme of the embodiment of the present invention and the energy consumption comparison of existing scheme, as following table 1:
Table 1
Obviously, those skilled in the art can carry out various changes and modification and not depart from the spirit and scope of the present invention the present invention.Like this, if within of the present invention these are revised and modification belongs to the scope of the claims in the present invention and equivalent technologies thereof, the present invention is also intended to comprise these changes and modification interior.
Claims (11)
1. a centrifugal blower fan blade wheel, comprise: wheel hub, blade and wheel cap, described blades installation is between described wheel hub and described wheel cap, it is characterized in that, described blade comprises backward linear leaf and short blade, described linear leaf flow to the length that flows to that length is greater than described short blade, and described linear leaf and described short blade edge between described wheel hub and described wheel cap is circumferentially alternately distributed, the inlet diameter of described short blade is greater than the inlet diameter of described linear leaf, the outlet diameter D1 of described linear leaf and inlet diameter D2, and the outlet diameter D3 of described short blade and inlet diameter D4, meet following formula:
(D3-D4)/(D1-D2)=1/3～1/2；
(D1-D3)/(D1-D2)=0～0.2。
2. centrifugal blower fan blade wheel as claimed in claim 1, is characterized in that, the outlet diameter D1 of described linear leaf and inlet diameter D2 meet: D2/D1=0.35～0.55.
3. centrifugal blower fan blade wheel as claimed in claim 1, is characterized in that, the span of the outlet flow angle of described linear leaf is 35 °～45 °.
4. centrifugal blower fan blade wheel as claimed in claim 1, is characterized in that, described linear leaf and described short blade edge between described wheel hub and described wheel cap is circumferentially evenly distributed.
5. centrifugal blower fan blade wheel as claimed in claim 4, is characterized in that, described short blade and between rear linear leaf circumferential position angle θ 1, and described short blade and between front linear leaf circumferential position angle θ 2, meet: θ 1/ θ 2=0.5～2.
6. the centrifugal blower fan blade wheel as described in claim 1-5 any one, is characterized in that, the quantity of described linear leaf and the quantity of described short blade are respectively in 8～12 span.
7. the centrifugal blower fan blade wheel as described in claim 1-5 any one, is characterized in that, one of the blade profile of described linear leaf and/or short blade is following blade profile:
Circular arc type, straight line type, parabolic shape and hyperbolic-type.
8. centrifugal blower fan blade wheel as claimed in claim 7, is characterized in that, when the blade profile of described linear leaf and described short blade are circular arc type, the radius of arc R1 of described linear leaf and the radius of arc R2 of described short blade meet: R2/R1=0.95～1.05.
9. centrifugal blower fan blade wheel as claimed in claim 8, is characterized in that, it is characterized in that, the outlet diameter D1 of described linear leaf and the radius of arc R1 of described linear leaf meet: R1/D1=0.6～0.7.
10. centrifugal blower fan blade wheel as claimed in claim 8, is characterized in that, the radius of arc R1 of described linear leaf and the radius of arc R2 of described short blade are equal, and the span of the blade profile angle β of short blade and linear leaf is-5 °～5 °; Described blade profile angle β is: if arrange a linear leaf through the described short blade centre of form, the angle through linear leaf and the short blade of the described short blade centre of form.
11. 1 kinds of centrifugal blowers, is characterized in that, described centrifugal blower comprises the centrifugal blower fan blade wheel as described in claim 1-10 any one.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201110451085.1A CN102506029B (en) | 2011-12-29 | 2011-12-29 | Impeller of centrifugal fan and centrifugal fan |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110451085.1A CN102506029B (en) | 2011-12-29 | 2011-12-29 | Impeller of centrifugal fan and centrifugal fan |
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| CN102506029A CN102506029A (en) | 2012-06-20 |
| CN102506029B true CN102506029B (en) | 2014-04-16 |
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| CN102797702A (en) * | 2012-08-20 | 2012-11-28 | 上海通用风机股份有限公司 | Narrowly welded impeller of small-flow centrifugal fan and centrifugal fan |
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| CN104653515B (en) * | 2015-02-15 | 2017-04-05 | 浙江理工大学 | A kind of double-suction type centrifugal fan |
| CN105570191A (en) * | 2016-02-29 | 2016-05-11 | 珠海格力电器股份有限公司 | Centrifugal fan and air conditioner |
| 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 |
| CN110043507B (en) * | 2019-05-23 | 2024-06-07 | 萨震压缩机（上海）有限公司 | Energy-saving centrifugal impeller |
| CN113250978B (en) * | 2020-02-11 | 2024-05-07 | 宏碁股份有限公司 | Heat radiation fan |
| CN111550439B (en) * | 2020-06-17 | 2024-05-28 | 浙江科贸智能机电股份有限公司 | Impeller of backward centrifugal ventilator |
| CN114146513B (en) * | 2021-12-01 | 2022-12-02 | 无锡曲速智能科技有限公司 | Light-weight fog gun |
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| CN2165276Y (en) * | 1993-07-01 | 1994-05-18 | 玉环县水泵厂 | High-efficiency vane wheel |
| EP1174159A2 (en) * | 2000-07-19 | 2002-01-23 | MAP Medizintechnik für Arzt und Patient GmbH & Co. KG | Breathing gas feed device |
| CN2531147Y (en) * | 2001-12-07 | 2003-01-15 | 王凯 | Fan blade |
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2011
- 2011-12-29 CN CN201110451085.1A patent/CN102506029B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0280205A2 (en) * | 1987-02-19 | 1988-08-31 | BMW ROLLS-ROYCE GmbH | Radial compressor |
| CN2165276Y (en) * | 1993-07-01 | 1994-05-18 | 玉环县水泵厂 | High-efficiency vane wheel |
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| CN2531147Y (en) * | 2001-12-07 | 2003-01-15 | 王凯 | Fan blade |
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Effective date of registration: 20170622 Address after: 410000 Hunan province Changsha hi tech Development Zone, Lin Yulu No. 288 Patentee after: ZOOMLION ENVIRONMENTAL INDUSTRY Co.,Ltd. Address before: 410013 Yuelu District, Hunan, silver basin Road, No. 361, No. Patentee before: ZOOMLION HEAVY INDUSTRY SCIENCE&TECHNOLOGY Co.,Ltd. |