CN215830796U - Backward centrifugal wind wheel, centrifugal fan and air conditioner - Google Patents
Backward centrifugal wind wheel, centrifugal fan and air conditioner Download PDFInfo
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- CN215830796U CN215830796U CN202121623542.6U CN202121623542U CN215830796U CN 215830796 U CN215830796 U CN 215830796U CN 202121623542 U CN202121623542 U CN 202121623542U CN 215830796 U CN215830796 U CN 215830796U
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Abstract
The utility model relates to a backward centrifugal wind wheel, a centrifugal fan and an air conditioner, wherein the backward centrifugal wind wheel comprises: a wheel disc (1); the wheel cover (4) and the wheel disc (1) are arranged side by side along the axial direction of the centrifugal wind wheel at intervals, and an air inlet is formed in the wheel cover (4); the centrifugal wind wheel comprises a plurality of blades (2), wherein the blades (2) are arranged side by side along the circumferential direction of the centrifugal wind wheel and are located between a wheel disc (1) and a wheel cover (4), and the distance between the tail edge of each blade (2) and the axis of the centrifugal impeller is gradually increased along the direction from the wheel disc (1) to the wheel cover (4). The trailing edge of each blade adopts a variable-diameter design, the top of each blade adopts a large diameter, the root of each blade adopts a small diameter, the added work amount of the blade profile at different blade heights is modulated and balanced, the non-uniform degree and the mixing degree of the airflow at the outlet of the wind wheel can be properly reduced, and the noise suppression is facilitated.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to a backward centrifugal wind wheel, a centrifugal fan and an air conditioner.
Background
At present, the tail edge of the fan blade of the backward centrifugal wind wheel is designed by adopting equal diameter. The design easily causes the air flow in the wind wheel to be concentrated towards the side of the wheel disk in the wind path, so that the local wind speed is too high, the wind outlet unevenness of the wind wheel is aggravated, and the problem of noise is further caused; and a part of backward centrifugal wind wheels adopting the variable-tail-edge diameter design are also adopted, but the design is mostly based on two-dimensional blade expansion, and the aerodynamic performance and the low-noise characteristic of the backward centrifugal wind wheels are not good enough.
SUMMERY OF THE UTILITY MODEL
The utility model aims to provide a backward centrifugal wind wheel, a centrifugal fan and an air conditioner which are beneficial to reducing noise.
According to an aspect of an embodiment of the present invention, there is provided a backward centrifugal wind wheel including:
a wheel disc;
the wheel cover and the wheel disc are arranged side by side along the axial direction of the centrifugal wind wheel at intervals, and an air inlet is formed in the wheel cover;
the blades are arranged side by side along the circumferential direction of the centrifugal wind wheel and are located between the wheel disc and the wheel cover, and the distance between the tail edges of the blades and the axis of the centrifugal impeller is gradually increased along the direction from the wheel disc to the wheel cover.
In some embodiments, the end of the trailing edge of the blade near the shroud is at a distance D2-2 from the axis of the centrifugal rotor, and the end of the trailing edge of the blade near the disk is at a distance D2-1 from the axis of the centrifugal rotor, where D2-2/D2-1 is 1.02-1.2.
In some embodiments, the height of the centrifugal rotor is H, wherein D2-1/H is 2.2-3.04.
In some embodiments, the diameter of the wind wheel's air inlet is Ds, where Ds/D2-1 is 0.81-0.95.
In some embodiments, the vanes have a vane outlet height H, and H/H is from 0.65 to 0.75.
In some embodiments, the centrifugal rotor has an air outlet area SRow boardThe area of the air inlet of the centrifugal wind wheel is SInto，SRow board/SIntoIs 1.25-1.45.
In some embodiments of the present invention, the,
the blade inlet mounting angle of the blade root part of the blade is 5-15 degrees; and/or
The blade inlet mounting angle of the blade top of the blade is 5-25 degrees.
In some embodiments, the blade inlet stagger angle of the blade increases in a direction from the root to the tip of the blade.
In some embodiments, the blade inlet stagger angle varies linearly in a direction from the root to the tip of the blade.
In some embodiments of the present invention, the,
the blade outlet mounting angle of the blade root of the blade is 35-45 degrees; and/or
The blade outlet mounting angle of the blade top of the blade is 20-35 degrees.
In some embodiments, the blade exit stagger angle of the blade decreases in a direction from the root to the tip of the blade.
In some embodiments, the blade exit stagger angle increases at a gradually increasing rate in a direction from the root to the tip of the blade.
In some embodiments, the blade outlet edges of the blades are inclined in a direction from the disk toward the shroud, in a direction opposite to the direction of rotation, with respect to the axial direction of the centrifugal impeller.
In some embodiments, the angle of inclination of the blade outlet in the direction of the disk towards the shroud with respect to the axial direction of the centrifugal impeller increases progressively in the direction from the root of the blade towards the tip of the blade.
In some embodiments, the tip portion of the blade outlet side of the blade is angularly out of phase by 15-25 degrees in the circumferential direction with respect to the root portion of the blade outlet side.
In some embodiments, the rate of change of the inclination angle gradually increases in a direction towards the top of the blade.
In some embodiments, the trailing edge of the blade is provided with a sawtooth structure,
in some embodiments, the saw tooth structure is one of a trapezoid, a triangle, and a sine wave.
In some embodiments, the distance between the trailing edge of the blade and the axis of the centrifugal impeller varies linearly in a direction approaching the shroud.
In some embodiments, the diameter of the inlet edge of the blade is D1, the diameter of the outlet edge of the centrifugal rotor is D2, and the inner-to-outer diameter ratio of the blade is D1/D2, wherein
The inner diameter ratio and the outer diameter ratio of the blade root part of the blade close to the wheel disc are 0.65-0.75; or
The inner diameter ratio and the outer diameter ratio of the top of the blade close to the wheel cover are 0.65-0.75.
In some embodiments, the inner to outer diameter ratio increases from the root to the tip
According to another aspect of the utility model, a centrifugal fan is also provided, and the centrifugal fan comprises the backward centrifugal wind wheel.
According to another aspect of the utility model, an air conditioner is also provided, and the air conditioner comprises the centrifugal fan.
By applying the technical scheme of the utility model, the trailing edge of the blade adopts a variable-diameter design, the blade top side adopts a larger diameter, the blade root side adopts a smaller diameter, and the uneven degree and the mixing degree of the airflow at the outlet of the wind wheel can be properly reduced by modulating and balancing the power adding amount of the blade profile at different blade heights, thereby being beneficial to inhibiting noise.
Other features of the present invention and advantages thereof will become apparent from the following detailed description of exemplary embodiments thereof, which proceeds with reference to the accompanying drawings.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the related art, the drawings needed to be used in the description of the embodiments or the related art will be briefly introduced below, it is obvious that the drawings in the following description are only some embodiments of the present invention, and for those skilled in the art, other drawings can be obtained according to these drawings without creative efforts.
FIG. 1 illustrates a schematic structural view of a rearward centrifugal wind rotor of an embodiment of the present invention;
FIG. 2 illustrates a top view structural schematic of a rearward centrifugal wind rotor of an embodiment of the present invention;
figure 3a shows a parametric schematic of a backward centrifugal wind rotor of an embodiment of the utility model;
FIG. 3b shows a schematic view of the inlet and outlet stagger angles of the blades of a rearward centrifugal wind rotor of an embodiment of the present invention;
FIG. 4 shows a schematic view of the blade exit pitch angle of a backward centrifugal wind rotor of an embodiment of the present invention;
FIG. 5 is a diagram showing a distribution rule of convex curves on a blade outlet installation angle of a backward centrifugal wind wheel according to an embodiment of the present invention;
FIG. 6 is a diagram showing a distribution rule of a convex curve on the blade outlet inclination angle of the backward centrifugal wind wheel according to the embodiment of the utility model;
FIG. 7 shows a schematic view of a sawtooth structure of a trailing edge of a blade of a backward centrifugal wind rotor according to an embodiment of the present invention; and
figure 8 shows a technical parameter comparison of a backward centrifugal wind rotor of an embodiment of the utility model with a prior art backward centrifugal wind rotor.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. The following description of at least one exemplary embodiment is merely illustrative in nature and is in no way intended to limit the utility model, its application, or uses. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.
As shown in fig. 1 to 4, the backward centrifugal wind wheel of the present embodiment includes a wheel disc 1, a wheel cover 4 and a plurality of blades 2, the wheel cover 4 and the wheel disc 1 are arranged side by side and at intervals along the axial direction of the centrifugal wind wheel, and an air inlet 6 is arranged on the wheel cover 4; the blades 2 are arranged side by side along the circumferential direction of the centrifugal wind wheel and are located between the wheel disc 1 and the wheel cover 4, and the distance between the tail edges of the blades 2 and the axis of the centrifugal impeller is gradually increased along the direction from the wheel disc 1 to the wheel cover 4.
In some embodiments, the distance between the trailing edge of the blade 2 and the axis of the centrifugal impeller varies linearly or curvilinearly in the direction approaching the shroud 4.
At present, the tail edge of backward centrifugal fan blade adopts the equal diameter design more, and the diameter also is the distance between blade to the axis of impeller, and this kind of design leads to the air current among the wind wheel easily to the reel side in the wind path and concentrates for local wind speed is too high, and aggravation wind wheel air-out inhomogeneity further induces the noise problem. In the embodiment, the trailing edge of the blade is designed by combining variable diameter with a three-dimensional blade, the top of the blade is of a large diameter, the root of the blade is of a small diameter, and the uneven degree and the mixing degree of the airflow at the outlet of the wind wheel can be properly reduced by modulating and balancing the power adding amount of the blade profile at different blade heights, so that the noise suppression is facilitated.
As shown in fig. 1, the root portion 21 of the blade 2 is the end of the blade 2 close to the disk 1, and the tip portion 22 of the blade 2 is the end of the blade 2 close to the shroud 4.
The distance between the end of the tail edge of the blade 2 close to the wheel cover 4 and the axis of the centrifugal wind wheel is D2-2, the distance between the end of the tail edge of the blade 2 close to the wheel disc 1 and the axis of the centrifugal wind wheel is D2-1, and preferably, the distance between D2-2/D2-1 is 1.02-1.2.
In this embodiment, the centrifugal wind wheel is designed to have a large flatness. The height of the centrifugal wind wheel is H, and preferably, D2-1/H is 2.2-3.04. The wind wheel is adjusted to be in parameter proportion of large flatness, large air suction port and large air exhaust port, so that the radial size of the wind wheel can be fully utilized, and the axial height of the wind wheel can be effectively shortened. Meanwhile, a balance point is sought between the expansion of the airflow passage and the guarantee of the effective work doing area of the blade, so that the better aerodynamic performance and noise characteristic of the wind wheel are obtained.
In the embodiment, the wind wheel air inlet adopts a large-diameter air inlet design. The diameter of the air suction port of the wind wheel is Ds, and the Ds/D2-1 is 0.81-0.95.
In the embodiment, the wind wheel exhaust port adopts a large outlet height design, the outlet height of the blade 2 is H, and H/H is 0.65-0.75.
In this embodiment, the centrifugal wind wheel has an exhaust port area SRow boardThe area of the air inlet of the centrifugal wind wheel is SIntoPreferably SRow board/SIntoIs 1.25-1.45. Wind wheel exhaust port area SRow boardThe area of the conical surface which rotates 360 degrees by taking the generatrix of the exhaust port as a characteristic curve; wind wheel air inlet area SIntoThe area of the circular surface having the diameter Ds.
The diameter of a blade inlet of the blade 2 is D1, the outer diameter of the centrifugal wind wheel is D2, and the inner diameter-to-outer diameter ratio of the blade is D1/D2, wherein the inner diameter-to-outer diameter ratio of a blade root of the blade 2 is 0.6-0.75; the inner diameter ratio and the outer diameter ratio of the top of the blade 2 are 0.65-0.8.
In some embodiments, the inner to outer diameter ratio increases from the root to the tip.
As shown in fig. 3b, based on the middle-line of the two-dimensional section airfoil profile of the blade at a certain blade height, the middle-line intersects with the blade inlet edge at a point, the rotation direction of the tangent of the middle-line along the point and the arc tangent of the inlet edge corresponding to the point forms an included angle which is the blade inlet installation angle in the patent. The blade outlet installation angle is characterized in that a middle molded line of a two-dimensional section airfoil of a blade at a certain blade height is taken as a reference, the middle molded line is intersected with an inlet edge of the blade at one point, and an included angle formed by the middle molded line along the tangent line of the point and the reverse rotation direction of the arc tangent line of the corresponding inlet edge is the blade outlet installation angle in the patent.
The blade inlet stagger angle of the blade root of the blade 2 is preferably 5-15 degrees; the blade inlet stagger angle of the blade tip of the blade 2 is preferably 5-25 degrees.
In some embodiments, the blade inlet stagger angle of the blade 2 increases gradually in a direction towards the blade tip of the blade 2. Preferably, the blade inlet stagger angle varies linearly in a direction close to the blade tip of the blade 2.
The blade outlet setting angle of the blade root of the blade 2 is preferably 35 degrees to 45 degrees; the blade outlet setting angle of the blade tip of the blade 2 is preferably 20 degrees to 35 degrees.
The blade outlet setting angle of the blade 2 is gradually reduced in a direction near the blade tip of the blade 2. Preferably, the rate of change of the vane inlet setting angle gradually increases in a direction close to the tip of the vane 2, and as shown in fig. 5, in a coordinate system having the abscissa as the displacement toward the tip of the vane and the ordinate as the vane outlet setting angle, the curve of the vane outlet setting angle is an upwardly convex curve.
The blade outlet edges of the blades 2 are inclined in the direction opposite to the rotation direction with respect to the axial direction of the centrifugal impeller from the disk 1 to the shroud 4. The angle of inclination of the vane outlet with respect to the axial direction of the centrifugal impeller gradually increases in a direction close to the tip of the vane 2.
The angular phase difference in the circumferential direction of the tip portion of the blade outlet side of the blade 2 with respect to the root portion of the blade outlet side is 15 to 25 degrees. The rate of change of the angle of inclination of the blade outlet side increases gradually in the direction from the root to the tip of the blade as shown in fig. 6.
The blade chord length, the blade inlet and outlet placement angles and the blade outlet inclination angle are comprehensively optimized, a small chord length blade profile design is adopted at the blade root of the blade main body, a large chord length blade profile design is adopted at the blade top of the blade main body, and meanwhile, the blade outlet placement angle and the blade outlet inclination angle adopt an upward convex curve distribution rule, so that the blade profile power adding amount at different blade heights can be modulated and distributed, and meanwhile, the large-range jet-wake structure generated at the blade outlet side close to the wheel cover can be restrained, the larger momentum loss is caused, and the induced pneumatic noise problem is solved.
Because the variable diameter design can bring certain air volume attenuation, in the utility model, the tail edge sawtooth is additionally arranged on the edge of the outlet of the blade, so that the air volume attenuation effect brought by the variable diameter design can be improved to a certain extent. Meanwhile, the anti-separation capacity of the boundary layer can be improved, the working efficiency of the wind wheel is improved, the running aerodynamic noise is improved, and the fan blade material cost under the same technical index can be reduced to a certain extent.
The outlet edge of the vane is located at the trailing edge of the vane. The trailing edge of the blade 2 is provided with a sawtooth structure, and the sawtooth structure is one of a trapezoid, a triangle and a sine wave. As shown in fig. 7, the length of the upper base of the trapezoid is c, the length of the lower base of the trapezoid is D, and the length of the waist of the trapezoid is e, wherein e/D2 is 0.004-0.022; D/D2 is 0.004-0.022; the preferred range of c/D2 is 0.002-0.07.
In this embodiment, the blade cross-section adopts imitative long-eared owl wing section as basic airfoil section to further carry out the deformation design, revise its thickening distribution law, back end structural strength in the promotion airfoil section.
As shown in fig. 8, the abscissa is the amount of wind, and the ordinate is the noise, and the backward centrifugal wind wheel of this embodiment promotes wind wheel work efficiency for prior art's centrifugal fan increase amount of wind, reduces the consumption, is showing and is improving wind noise level, reduces wind wheel material cost simultaneously.
According to another aspect of the utility model, a centrifugal fan is also provided, and the centrifugal fan comprises the backward centrifugal wind wheel.
According to another aspect of the present invention, there is also provided an air conditioner including the centrifugal fan described above.
The present invention is not limited to the above exemplary embodiments, and any modifications, equivalent replacements, improvements, etc. within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (23)
1. A backward centrifugal wind wheel, comprising:
a wheel disc (1);
the wheel cover (4) and the wheel disc (1) are arranged side by side along the axial direction of the centrifugal wind wheel at intervals, and an air inlet (6) is formed in the wheel cover (4);
the centrifugal wind wheel comprises a plurality of blades (2), wherein the blades (2) are arranged side by side along the circumferential direction of the centrifugal wind wheel and are located between a wheel disc (1) and a wheel cover (4), and the distance between the tail edge of each blade (2) and the axis of the centrifugal impeller is gradually increased along the direction from the wheel disc (1) to the wheel cover (4).
2. Rearward centrifugal wind rotor according to claim 1, characterized in that the end of the trailing edge of the blade (2) close to the shroud (4) is at a distance D2-2 from the axis of the centrifugal wind rotor, and the end of the trailing edge of the blade (2) close to the disc (1) is at a distance D2-1 from the axis of the centrifugal wind rotor, where D2-2/D2-1 is 1.02-1.2.
3. The backward centrifugal wind rotor of claim 2, wherein the centrifugal wind rotor has a height H, wherein D2-1/H is 2.2-3.04.
4. Backward centrifugal wind rotor according to claim 1, characterized in that the diameter of the wind rotor's air inlet (6) is Ds, where Ds/D2-1 is 0.81-0.95.
5. Backward centrifugal wind wheel according to claim 1, characterized in that the blades (2) have a blade outlet height H, H/H being 0.65-0.75.
6. The backward centrifugal wind wheel of claim 1, wherein the centrifugal wind wheel has an air outlet area of SRow boardThe area of the air inlet of the centrifugal wind wheel is SInto，SRow board/SIntoIs 1.25-1.45.
7. Backward centrifugal wind wheel according to claim 1,
the blade inlet installation angle of the blade root (21) of the blade (2) is 5-15 degrees; and/or
The blade inlet installation angle of the blade top (22) of the blade (2) is 5-25 degrees.
8. Backward centrifugal wind rotor according to claim 1, characterized in that the blade (2) has a blade inlet setting angle that gradually increases in the direction from the root to the tip of the blade (2).
9. Backward centrifugal wind rotor according to claim 8, characterized in that the blade inlet setting angle varies linearly in the direction from the root to the tip of the blade (2).
10. Backward centrifugal wind wheel according to claim 1,
the blade outlet installation angle of the blade root (21) of the blade (2) is 35-45 degrees; and/or
The blade outlet installation angle of the blade top (22) of the blade (2) is 20-35 degrees.
11. Backward centrifugal wind rotor according to claim 1, characterized in that the blade exit setting angle of the blade (2) is gradually decreasing in the direction from the blade root (21) to the blade tip (22) of the blade (2).
12. Backward centrifugal wind rotor according to claim 11, characterized in that the blade exit setting angle increases gradually in the direction from the root to the tip of the blade (2).
13. Backward centrifugal wind rotor according to claim 1, characterized in that the blade exit edge of the blades (2) is inclined in the direction opposite to the direction of rotation with respect to the axial direction of the centrifugal impeller from the direction of the disk (1) towards the shroud (4).
14. Backward centrifugal wind rotor according to claim 13, characterized in that the angle of inclination of the blade outlet with respect to the axial direction of the centrifugal impeller in the direction of the wheel disc (1) towards the shroud (4) gradually increases in the direction from the root of the blade (2) towards the tip of the blade.
15. Backward centrifugal wind rotor according to claim 13, characterized in that the blade tips of the blade outlet sides of the blades (2) are angularly phase-shifted in the circumferential direction by 15-25 degrees with respect to the blade roots of the blade outlet sides.
16. The backward centrifugal wind rotor of claim 14, wherein the rate of change of the inclination angle gradually increases in a direction from a blade root to a blade tip.
17. Rearward centrifugal wind rotor according to claim 1, characterized in that the trailing edge of the blades (2) is provided with a saw tooth structure.
18. The backward centrifugal wind rotor of claim 17, wherein the saw tooth structure is one of trapezoidal, triangular, and sinusoidal.
19. Rearward centrifugal wind rotor according to claim 1, characterized in that the distance between the trailing edge of the blades (2) and the axis of the centrifugal impeller varies linearly in the direction close to the shroud (4).
20. Backward centrifugal wind rotor according to claim 1, characterized in that the blade (2) has a blade inlet side diameter of D1, an outlet side diameter of D2 and an inner to outer diameter ratio of D1/D2, wherein
The inner diameter ratio and the outer diameter ratio of the blade root part of the blade (2) close to the wheel disc (1) are 0.65-0.75; or
The inner diameter ratio and the outer diameter ratio of the top of the blade (2) close to the wheel cover (4) are 0.65-0.75.
21. The backward centrifugal wind rotor of claim 20, wherein the inner-to-outer diameter ratio gradually increases from the root portion to the tip portion.
22. A centrifugal wind turbine comprising a backward centrifugal wind rotor according to any one of claims 1 to 20.
23. An air conditioner comprising the centrifugal fan of claim 22.
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| Application Number | Priority Date | Filing Date | Title |
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| CN202121623542.6U CN215830796U (en) | 2021-07-16 | 2021-07-16 | Backward centrifugal wind wheel, centrifugal fan and air conditioner |
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| CN202121623542.6U CN215830796U (en) | 2021-07-16 | 2021-07-16 | Backward centrifugal wind wheel, centrifugal fan and air conditioner |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114321005A (en) * | 2022-03-01 | 2022-04-12 | 佛山市南海九洲普惠风机有限公司 | Low-noise forward-bent centrifugal fan impeller |
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2021
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114321005A (en) * | 2022-03-01 | 2022-04-12 | 佛山市南海九洲普惠风机有限公司 | Low-noise forward-bent centrifugal fan impeller |
| CN114321005B (en) * | 2022-03-01 | 2022-05-13 | 佛山市南海九洲普惠风机有限公司 | Low-noise forward-bent centrifugal fan impeller |
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