CN211737550U - Backward centrifugal cross-section noise reduction type centrifugal fan blade - Google Patents
Backward centrifugal cross-section noise reduction type centrifugal fan blade Download PDFInfo
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- CN211737550U CN211737550U CN201922074413.5U CN201922074413U CN211737550U CN 211737550 U CN211737550 U CN 211737550U CN 201922074413 U CN201922074413 U CN 201922074413U CN 211737550 U CN211737550 U CN 211737550U
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Abstract
The utility model discloses a backward centrifugal cross-section noise reduction type centrifugal fan blade, which comprises a wind wheel and arc-shaped blades distributed on the wind wheel, wherein the central line of each arc-shaped blade sequentially comprises A, B, C, D, E, F, G from the inner side of the wind wheel to the outer side of the wind wheel; the diameter of an inscribed circle on the center line of the point D is the largest; the improved blade profile of the fan enables the streamline of the wind flow to flow out along the shape of the blade when the wind wheel works, reduces the resistance in the flow channel, enables the internal flow field to be smoother when the fan rotates, is very beneficial to inhibiting the airflow separation, improves the flow efficiency of the airflow, and effectively solves the problems of small work of the fan impeller, high noise and the like.
Description
Technical Field
The utility model relates to a centrifugation fan blade technical field, especially a type of making an uproar centrifugation fan blade falls to centrifugal cross-section after.
Background
When the centrifugal fan blade works, according to the principle that airflow flows along the path of minimum resistance, the airflow enters a flow channel of the impeller at an angle close to the inlet angle beta 1A of the blade. Thus, for a given ventilator, the vane inlet relative velocity ω 1 always enters the vane without impact, regardless of the change in flow magnitude. Because the flow path of the impeller is not ideal, boundary layer separation occurs in the flow of air within the impeller path, particularly when the ventilator is operating at off-design flow rates. The position and size of the separation zone are related to the shape of the blades and the size of the inlet attack angle, wherein the inlet attack angle i is beta 1A-beta'. And when the inlet attack angle is not equal to zero, the boundary layer in the blade path is separated. When i <0, the working edge of the blade forms a closed vortex region, while at the non-working edge near the impeller exit, vortices can also be generated due to the sharp drop in air velocity. When i >0, boundary layer separation occurs at the non-working edge of the blade, and as the flow rate decreases, the separation increases rapidly, causing large eddy current losses. The process directly influences the air outlet efficiency of the fan blades, and the conventional centrifugal fan blades cause energy loss and noise problems due to the reason.
Disclosure of Invention
In order to overcome the not enough of prior art, the utility model provides a to the centrifugal fan blade of type of making an uproar of falling in centrifugal cross-section.
The utility model provides a technical scheme that its technical problem adopted is:
a backward centrifugal section noise reduction type centrifugal fan blade comprises a wind wheel and arc-shaped blades distributed on the wind wheel, wherein the center line of each arc-shaped blade sequentially comprises A, B, C, D, E, F, G from the inner side of the wind wheel to the outer side of the wind wheel; the diameter of an inscribed circle on the center line of the point D is the largest;
the functional relation between the diameter y of the inscribed circle corresponding to each point A to G in the arc-shaped blade and the ordinal number (x is 1, 2 and … 7) corresponding to each point A to G is that y is-0.935 x2+7.1924x-K, wherein K is 1.4-3.8. The utility model has the advantages that: the improved blade profile of the fan enables the streamline of the wind flow to flow out along the shape of the blade when the wind wheel works, reduces the resistance in the flow channel, enables the internal flow field to be smoother when the fan rotates, is very beneficial to inhibiting the airflow separation, improves the flow efficiency of the airflow, and effectively solves the problems of small work of the fan impeller, high noise and the like.
Drawings
The present invention will be further explained with reference to the drawings and examples.
Fig. 1 is a perspective view of the present invention;
fig. 2 is a schematic structural diagram of the present invention;
FIG. 3 is a comparison diagram of the working state of the present invention;
fig. 4 is a schematic diagram comparing the test results of the present invention.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention. Rather, the invention can be practiced without these specific details, i.e., those skilled in the art can more effectively describe the nature of their work to others skilled in the art using the description and illustrations herein.
Referring to fig. 1 and 2, a backward centrifugal cross-section noise reduction type centrifugal fan blade comprises a wind wheel 1 and arc-shaped blades 2 distributed on the wind wheel 1.
The midline of the arc-shaped blade 2 sequentially comprises A, B, C, D, E, F, G from the inner side of the wind wheel 1 to the outer side of the wind wheel 1.
The diameter of the inscribed circle on the midline of the point D is the largest.
A. B, C, D, E, F, G the length of the arc between the points is according to：
The functional relation between the diameter y of the inscribed circle corresponding to each point A to G in the arc-shaped blade 2 and the ordinal number (x is 1, 2 and … 7) corresponding to each point A to G is that y is-0.935 x2+7.1924x-K, wherein K is 1.4-3.8. For example, the diameter y of an inscribed circle at the point A of the cambered vane 2, the serial number x of the point A is 1, and y is-0.935X 12+7.1924X 1-K; the diameter y of an inscribed circle at the midpoint E of the arc-shaped blade 2, the serial number x of the point E is 5, and y is-0.935 multiplied by 52+7.1924×5-K。
According to the drawing principle of the superior blade profile: loss Δ P of airflow through the blade pathwIts loss Δ PwAnd loss factorwIn connection withwAnd an equivalent diffusion angle thetaeqIt is related. At the optimum equivalent divergence angle thetaeqUnder the condition, the relative speed ω 1 is gradually changed to ω 2 to reduce the loss in the blade path. Due to the relative speed omega and the meridional speed C of the gas flowmIs gradually changed so that the blade setting angle beta at different radiiAIs also formed by beta1AGradually change to beta2AThe blade profile meeting the conditions has less blade path loss and higher working efficiency.
The newly designed blade structure is like a fish shape, so that the streamline flows out along the shape of the arc-shaped blade 2, and the resistance in the flow channel is reduced. The internal flow field is smoother when the fan rotates, the air flow separation is favorably inhibited, the flow efficiency of the air flow is improved, and the problems of small work of the fan impeller, high noise and the like are effectively solved. The fan power capability can be greatly improved, the fan noise can be reduced, and the fan power device can be widely applied to the field of air purifiers.
According to the above principle, the present invention can also make appropriate changes and modifications to the above embodiments. Therefore, the present invention is not limited to the specific embodiments disclosed and described above, and some modifications and changes to the present invention should fall within the protection scope of the claims of the present invention.
The following are examples of novel centrifugal fan blade technology, wherein "examples" as referred to herein refer to particular features, structures, or characteristics that may be included in at least one implementation of the present application. The appearances of the phrase "an embodiment" in various places in the specification are not necessarily all referring to the same embodiment, nor are separate or alternative embodiments mutually exclusive of other embodiments.
Example 1, the diameter of the rotor is 226 mm:
the diameter phi A corresponding to the arc-shaped blade A point in the wind wheel is 130mm,
point a corresponds to y 6.7274 mm;
example 2, rotor diameter 225 mm:
the diameter phi A corresponding to the arc-shaped blade A point in the wind wheel is 127.9mm,
point a corresponds to y 6.0168 mm;
example 3, rotor diameter 224 mm:
the diameter phi A corresponding to the arc-shaped blade A point in the wind wheel is 127.8mm,
point a corresponds to y 5.0673 mm;
example 4, rotor diameter 222 mm:
the diameter phi A corresponding to the arc-shaped blade A point in the wind wheel is 127.7mm,
point a corresponds to y 4.8611 mm;
example 5, the rotor diameter was 220 mm:
the diameter phi A corresponding to the arc-shaped blade A point in the wind wheel is 127.6mm,
point a corresponds to y 4.3274 mm.
Proved by practice, taking the fan blade of L266-119 as an example, the performance data of the new blade compared with the original blade experiment is shown in figure 3.
From the noise-air volume test data in fig. 4, it can be found that the noise in the new blade is reduced by 2dB at the same air volume at the middle and high levels, and the power is reduced by 5w, which is more than 10% of the original power. While other gears substantially maintain a noise advantage above 2 db.
Claims (1)
1. The utility model provides a type of making an uproar centrifugation fan blade falls in backward centrifugation cross-section, includes wind wheel (1) and arc blade (2) of distribution on wind wheel (1), its characterized in that:
the center line of the arc-shaped blade (2) sequentially comprises A, B, C, D, E, F, G from the inner side of the wind wheel (1) to the outer side of the wind wheel (1);
the diameter of an inscribed circle on the center line of the point D is the largest;
the functional relation between the diameter y of the inscribed circle corresponding to each point A to G in the arc-shaped blade (2) and the ordinal number (x is 1, 2 and … 7) corresponding to each point A to G is that y is-0.935 x2+7.1924x-K, wherein K is 1.4-3.8.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201922074413.5U CN211737550U (en) | 2019-11-26 | 2019-11-26 | Backward centrifugal cross-section noise reduction type centrifugal fan blade |
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| CN201922074413.5U CN211737550U (en) | 2019-11-26 | 2019-11-26 | Backward centrifugal cross-section noise reduction type centrifugal fan blade |
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Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043075A (en) * | 2019-11-26 | 2020-04-21 | 广东顺威精密塑料股份有限公司 | Centrifugal fan blade with improved backward centrifugal section |
| CN114607641A (en) * | 2022-03-23 | 2022-06-10 | 珠海格力电器股份有限公司 | Axial fan's stator structure and axial fan |
| CN111043075B (en) * | 2019-11-26 | 2024-07-02 | 广东顺威精密塑料股份有限公司 | Backward centrifugal section improved centrifugal fan blade applied to centrifugal fan |
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2019
- 2019-11-26 CN CN201922074413.5U patent/CN211737550U/en active Active
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111043075A (en) * | 2019-11-26 | 2020-04-21 | 广东顺威精密塑料股份有限公司 | Centrifugal fan blade with improved backward centrifugal section |
| CN111043075B (en) * | 2019-11-26 | 2024-07-02 | 广东顺威精密塑料股份有限公司 | Backward centrifugal section improved centrifugal fan blade applied to centrifugal fan |
| CN114607641A (en) * | 2022-03-23 | 2022-06-10 | 珠海格力电器股份有限公司 | Axial fan's stator structure and axial fan |
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