CN1752455A - Crossflow fan - Google Patents
Crossflow fan Download PDFInfo
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- CN1752455A CN1752455A CN 200510106412 CN200510106412A CN1752455A CN 1752455 A CN1752455 A CN 1752455A CN 200510106412 CN200510106412 CN 200510106412 CN 200510106412 A CN200510106412 A CN 200510106412A CN 1752455 A CN1752455 A CN 1752455A
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Abstract
This cross flow fan 1 comprises 34 to 36 sheets of vanes. The pitches (angles) of the vanes are at random. Where the maximum pitch (angle) is Pmax and the minimum pitch (angle) is Pmin, a difference between the maximum pitch and the minimum pitch is formed so that the relation of 1.0 (deg)<=Pmax-Pmin<=2.5 (deg) can be established.
Description
Technical field
The present invention relates to the cross flow fan that a kind of for example air conditioner etc. uses.
Background technique
In traditional cross flow fan, propose a kind ofly to relax by the quantity (Z) of fin and use the technological scheme (for example opening the 2003-328980 communique) of generation of special sound (NZ sound) of the product representation of rotation number (N) with reference to the Japan Patent spy.
In above-mentioned communique, as shown in table 1, the blade pitgh of cross flow fan is at random, can relax by the quantity (Z) of blade and uses the generation of special sound (NZ sound) of the product representation of rotation number (N).
Yet as shown in table 1, in above-mentioned tradition constituted, maximum spacing (angle) Pmax was 13.64, and minimum separable (angle) Pmin is 7.67, and both poor P (P=Pmax-Pmin) are 5.97 (deg).Thus, when P surpassed certain certain value, stochastic behaviour became significantly, can alleviate the NZ sound of the product that depends on rotation number (N) and blade quantity (Z).
But when randomness became remarkable, fluid noise had the tendency of increase.For example, performances such as the higher harmonics of rotation sound (depending on the sound of rotation number (N)) significantly can become the reason of the unusual sound generation that is called thud thud sound.
Summary of the invention
For addressing the above problem, the object of the present invention is to provide a kind of cross flow fan that reduces the noise that fluid oscillation causes and improve wind pushing performance.
For reaching above-mentioned purpose, the blade quantity of cross flow fan of the present invention is more than 34, below 36, and the spacing of each blade (angle) is at random, is Pmax at maximum spacing (angle), when minimum separable (angle) was Pmin, the difference of maximum spacing and minimum separable satisfied following relationship:
1.0(deg)≤Pmax-Pmin≤2.5(deg)。
If ground carries out random alignment below 2.5 (deg) under this blade quantity the difference of maximum spacing and minimum separable being controlled at, can reduce fluid noise, suppress to depend on the generation of the rotation sound of rotation number (N).In addition, carry out random alignment abovely, can suitably alleviate the NZ sound that depends on rotation number (N) if the difference of maximum spacing and minimum separable is controlled at 1.0 (deg).
Again, it is that a kind of blade quantity is the cross flow fan that the difference of 35 and maximum spacing and minimum separable satisfies following relationship:
2.10(deg)≤Pmax-Pmin≤2.20(deg)。
Especially effect is remarkable when blade quantity is defined as 35, in this condition and range, significantly the suppression fluid noise, for example depend on the generation of the rotation sound (N sound) of rotation number (N).And, can effectively alleviate the NZ sound of the product that depends on rotation number (N) and blade quantity (Z).
Again, it is a kind of structure of the blade random alignment more than 2 kinds that the only flexure plane side (convex part) of each blade is different, owing to the convex part of each blade makes the wind speed profile difference of the portion of blowing out and suction portion, thereby can assist the mitigation of NZ sound.
Again, it is a kind of blade alternate structure arranged more than 2 kinds that the only flexure plane side (convex part) of each blade is different, by this configuration, in continuous spacing, can positively form the different flow pattern of wind speed profile, thus the mitigation of auxiliary NZ sound positively.
Thus, the present invention's cross flow fan that can obtain to reduce fluid noise and can reduce the NZ sound.As mentioned above, cross flow fan of the present invention can reduce noise (unusual sound) and can improve wind pushing performance, can create same effect in the machine (for example air conditioner) of carrying, thus applicable, thus on industry, can be used.
Description of drawings
Fig. 1 is the plan view and the sectional view of basic comprising of the cross flow fan of the expression embodiment of the invention 1.
Fig. 2 is the performance plot of the cross flow fan characteristic of the expression embodiment of the invention 1.
Fig. 3 is the performance plot of the cross flow fan characteristic of the expression embodiment of the invention 2.
Fig. 4 is the plan view and the sectional view of basic comprising of the cross flow fan of the expression embodiment of the invention 3.
Fig. 5 is the sectional view of blade of the cross flow fan of the expression embodiment of the invention 3.
Fig. 6 is the sectional view of basic comprising of the cross flow fan of the expression embodiment of the invention 4.
Embodiment
Embodiments of the invention are described with reference to the accompanying drawings.
(embodiment 1)
Whole formations of cross flow fan represented in Fig. 1 summary.In the figure, cross flow fan 1 is equipped with 36 blades 3 at the periphery of demarcation strip 2, forms rows of blades 4 cylindraceous, is arranged with a plurality of cross flow fans 1 on axle direction.
At this, when P less than 1.0 the time too equal because the interval of adjacent vanes 3 is an intervals, so it is big to depend on the NZ change of tune of product of rotation number (N) and blade quantity (Z).In addition, when P greater than 2.5 the time, because the interval of adjacent vanes 3 is mixed with narrow interval and wide interval, so that fluid noise becomes is big.
As mentioned above, in the cross flow fan of present embodiment 1, the quantity of blade 3 is more than 34, below 36, the spacing of each blade 3 (angle) is at random, P is that the scope of Pmax-Pmin satisfies: 1.0 (deg)≤Pmax-Pmin≤2.5 (deg), thus can alleviate fluid noise and NZ sound.
(embodiment 2)
In the embodiment of the invention 2, the content identical with embodiment 1 invention no longer described.Blade quantity is 35, and is as shown in table 3, with the spacing angle at each blade 3 center of distance map 1 with P1, P2 ... expression.Wherein, Pmax=11.3 (deg), Pmin=9.1 (deg), its difference P is P=2.2.
Especially effect is remarkable when blade quantity is defined as 35.P when Fig. 3 represents that blade quantity is 35 and the relation of NZ sound and noise level (A level).Left side longitudinal axis N1 (NZ) expression NZ sound, right longitudinal axis N1 (A) represents noise level (A level), transverse axis is represented P.From this Fig. 3 as can be known: if P below 2.2, then noise level (dB (A)) can be significantly reduces.And as can be known: if P more than 2.1, then NZ sound (dB) can be significantly reduces.
At this, when P less than 1.0 the time too equal because the interval of adjacent vanes 3 is an intervals, so it is big to depend on the NZ change of tune of product of rotation number (N) and blade quantity (Z).In addition, when P greater than 2.5 the time, because the interval of adjacent vanes 3 is mixed with narrow interval and wide interval, so that fluid noise becomes is big.
When especially P was in 2.10～2.20 scopes, the interval of adjacent vanes 3 was in suitable scope, the significantly generation of suppression fluid noise, and the while can effectively alleviate the NZ sound of the product that depends on rotation number (N) and blade quantity (Z).
As mentioned above, in the cross flow fan of present embodiment 2, the quantity of blade 3 is 35, and the spacing of each blade 3 (angle) is at random, P is that the scope of Pmax-Pmin satisfies: 2.10 (deg)≤Pmax-Pmin≤2.20 (deg), thus can alleviate fluid noise and NZ sound.
Especially effect is remarkable when blade quantity is defined as 35, in the scope of above-mentioned condition, significantly the suppression fluid noise, for example depend on the generation of the rotation sound (N sound) of rotation number (N).And, can effectively alleviate the NZ sound of the product that depends on rotation number (N) and blade quantity (Z).
Moreover 35 of the quantity of blade 3 are the blade quantities that frequently adopts in the cross flow fan of use in refrigeration system, are related to the low noiseization of air conditioner.
(embodiment 3)
Whole formations of the cross flow fan of the embodiment of the invention 3 represented in Fig. 4 summary.In the figure, cross flow fan is equipped with 36 blades 3 at the periphery of demarcation strip 2, forms rows of blades 4 cylindraceous.Fig. 5 (a), Fig. 5 (b), Fig. 5 (c) are the amplification views of each blade 3a, 3b, 3c.Shown in Fig. 5 (a), Fig. 5 (b), Fig. 5 (c), three kinds of the shapes of the recess of each blade 3a, 3b, 3c are all identical, and three kinds of the flexure plane sides of each blade 3a, 3b, 3c (convex part) are all inequality.
Specifically, be set at: convex other blades of radius ratio 3b, the 3c partly that forms blade 3a is big.The convex radius partly that forms blade 3b, 3c is identical, and especially the interior circumferential portion of the convex of blade 3c part forms with film.
In the same manner the spacing (angle) of this blade 3 is arranged randomly with previous embodiment 1, with P is that 1.2 (deg) are configured, its result is identical with embodiment 1, can alleviate fluid noise and NZ sound, and, owing to the flexure plane side (convex part) of each blade 3a, 3b, 3c makes the wind speed profile difference of the portion of blowing out and suction portion, thereby can assist the mitigation of NZ sound.In addition, because of the shape of the recess of each blade 3a, 3b, 3c is identical, can keep aerodynamic quality, thereby can guarantee wind pushing performance.
(embodiment 4)
Fig. 6 is the plan view of the cross flow fan of the embodiment of the invention 4. Blade 3a, 3b shown in Fig. 5 (a), Fig. 5 (b) staggered (replacing) arranged.
In the same manner the spacing (angle) of this blade 3 is arranged randomly with previous embodiment 1, with P is that 1.2 (deg) are configured, its result is identical with embodiment 1, can alleviate fluid noise and NZ sound, and, owing to the flexure plane side (convex part) of each blade 3a, 3b makes the wind speed profile difference of the portion of blowing out and suction portion, thereby can assist the mitigation of NZ sound.In addition, because of the shape of the recess of each blade 3a, 3b is identical, can keep aerodynamic quality, thereby can guarantee wind pushing performance.
Table 1 table 2 table 3
| Spacing No | Spacing (degree) | TOTAL(degree) |
| P1 P2 P3 P4 P5 P6 P7 P8 P9 P10 P11 P12 P13 P14 P15 P16 P17 P18 P19 P20 P21 P22 P23 P24 P25 P26 P27 P28 P29 P30 P31 P32 P33 P34 P35 | 10.00 10.31 9.20 11.64 10.37 10.67 9.41 12.26 8.36 10.25 11.47 8.27 11.33 11.08 9.36 11.29 7.67 13.44 10.10 9.97 8.08 10.27 13.64 8.33 9.89 10.71 9.54 12.51 7.95 11.76 7.92 13.47 10.81 7.80 10.87 | 9.60 19.40 29.10 38.70 48.50 58.40 68.30 78.30 88.00 98.00 108.10 118.30 128.60 138.90 149.60 159.70 170.10 180.40 190.60 200.70 210.50 220.60 230.10 240.00 249.80 259.50 270.10 279.70 289.40 299.40 309.20 319.10 329.10 339.30 360.00 |
| 360.00 | ||
| MAX MIN | 13.64 7.67 | |
| Δ | 5.97 |
| Spacing No | Spacing (degree) | TOTAL(degree) |
| P1 P2 P3 P4 P5 P6 P7 P8 P9 P10 P11 P12 P13 P14 P15 P16 P17 P18 P19 P20 P21 P22 P23 P24 P25 P26 P27 P28 P29 P30 P31 P32 P33 P34 P35 P36 | 9.60 9.80 9.70 9.60 9.80 9.90 9.90 10.00 9.70 10.00 10.10 10.20 10.30 10.30 10.70 10.10 10.40 10.30 10.20 10.10 9.80 10.10 9.50 9.90 9.80 9.70 10.60 9.60 9.70 10.00 9.80 9.90 10.00 10.20 10.40 10.30 | 9.60 19.40 29.10 38.70 48.50 58.40 68.30 78.30 88.00 98.00 108.10 118.30 128.60 138.90 149.60 159.70 170.10 180.40 190.60 200.70 210.50 220.60 230.10 240.00 249.80 259.50 270.10 279.70 289.40 299.40 309.20 319.10 329.10 339.30 349.70 360.00 |
| 360.00 | ||
| MAX MIN | 10.70 9.50 | |
| Δ | 1.20 |
| Spacing No | Spacing (degree) | TOTAL(degree) |
| P1 P2 P3 P4 P5 P6 P7 P8 P9 P10 P11 P12 P13 P14 P15 P16 P17 P18 P19 P20 P21 P22 P23 P24 P25 P26 P27 P28 P29 P30 P31 P32 P33 P34 P35 | 11.00 11.10 11.00 11.30 11.00 10.90 10.80 10.90 10.50 10.90 10.90 10.30 10.20 10.10 10.90 9.90 9.80 10.10 9.60 9.90 9.40 10.90 9.20 9.10 11.00 9.20 9.40 10.50 9.10 9.80 9.70 10.20 9.80 11.20 10.40 | 9.60 19.40 29.10 38.70 48.50 58.40 68.30 78.30 88.00 98.00 108.10 118.30 128.60 138.90 149.60 159.70 170.10 180.40 190.60 200.70 210.50 220.60 230.10 240.00 249.80 259.50 270.10 279.70 289.40 299.40 309.20 319.10 329.10 339.30 360.00 |
| 360.00 | ||
| MAX MIN | 11.30 9.10 | |
| Δ | 2.20 |
Claims (4)
1, a kind of cross flow fan (1), it is characterized in that, the quantity of blade (3) is more than 34, below 36, the spacing (angle) of each blade (3) is at random, at maximum spacing (angle) is Pmax, minimum separable (angle) during for Pmin, and the difference of maximum spacing and minimum separable satisfies following relationship:
1.0(deg)≤Pmax-Pmin≤2.5(deg)。
2, cross flow fan as claimed in claim 1 is characterized in that, the quantity of blade (3) is 35, and the difference of maximum spacing and minimum separable satisfies following relationship:
2.10(deg)≤Pmax-Pmin≤2.20(deg)。
3, cross flow fan as claimed in claim 1 is characterized in that, the blade random alignment more than 2 kinds that the only flexure plane side (convex part) of each blade (3) is different.
4, cross flow fan as claimed in claim 1 is characterized in that, the blade alternates more than 2 kinds that the only flexure plane side (convex part) of each blade (3) is different are arranged.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2004276851 | 2004-09-24 | ||
| JP2004276851 | 2004-09-24 | ||
| JP2005254222 | 2005-09-02 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN1752455A true CN1752455A (en) | 2006-03-29 |
| CN100540918C CN100540918C (en) | 2009-09-16 |
Family
ID=36679426
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CNB2005101064124A Active CN100540918C (en) | 2004-09-24 | 2005-09-23 | Cross flow fan |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN100540918C (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102192188A (en) * | 2010-03-09 | 2011-09-21 | 罗伯特·博世有限公司 | Hand-held machine tool fan |
| CN103573694A (en) * | 2012-07-26 | 2014-02-12 | 珠海格力电器股份有限公司 | Cross-flow impeller, cross-flow fan and wall-mounted air conditioner |
-
2005
- 2005-09-23 CN CNB2005101064124A patent/CN100540918C/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102192188A (en) * | 2010-03-09 | 2011-09-21 | 罗伯特·博世有限公司 | Hand-held machine tool fan |
| CN103573694A (en) * | 2012-07-26 | 2014-02-12 | 珠海格力电器股份有限公司 | Cross-flow impeller, cross-flow fan and wall-mounted air conditioner |
| CN103573694B (en) * | 2012-07-26 | 2016-08-10 | 珠海格力电器股份有限公司 | Cross-flow impeller, cross-flow fan and wall-mounted air conditioner |
Also Published As
| Publication number | Publication date |
|---|---|
| CN100540918C (en) | 2009-09-16 |
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