阅读说明：本技术 离心风叶、离心风机、空调器和交通运输工具 (centrifugal fan blade, centrifugal fan, air conditioner and transportation means ) 是由 曹雷 邹建煌 耿付帅 和浩浩 于 2019-10-10 设计创作，主要内容包括：本发明提供一种离心风叶、离心风机、空调器和交通运输工具,离心风叶包括叶片,叶片设置有首尾依次连接的叶片前缘、压力面、叶片后缘和吸力面,压力面的型线和吸力面的型线均为样条曲线,压力面的型线的曲线方程为：y＝-0.781x<Sup>5</Sup>+1.3278x<Sup>4</Sup>-0.5351x<Sup>3</Sup>-1.0001x<Sup>2</Sup>+1.0287x-0.0832,其中,<Image he="134" wi="381" file="DDA0002228743360000011.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>0≤x≤1.5；吸力面的型线的曲线方程为：y＝0.44x<Sup>5</Sup>-1.8665x<Sup>4</Sup>+2.5144x<Sup>3</Sup>-2.225x<Sup>2</Sup>+1.0981x+0.0966；其中,<Image he="125" wi="355" file="DDA0002228743360000012.GIF" imgContent="drawing" imgFormat="GIF" orientation="portrait" inline="no"></Image>-0.2≤x≤1.2；坐标(x<Sub>p</Sub>,y<Sub>p</Sub>)为压力面曲线上的任意一点,坐标(x<Sub>s</Sub>,y<Sub>s</Sub>)为吸力面曲线上的任意一点,b为叶片弦长,x轴为沿着叶片弦长延伸的方向,y轴为垂直于叶片弦长的方向,坐标原点为叶片前缘的中心。该离心风叶高效且低噪。(The invention provides a centrifugal fan blade, a centrifugal fan, an air conditioner and a transportation tool, wherein the centrifugal fan blade comprises a blade, the blade is provided with a blade front edge, a pressure surface, a blade rear edge and a suction surface which are sequentially connected end to end, the molded lines of the pressure surface and the suction surface are spline curves, and the curve equation of the molded line of the pressure surface is as follows: y is-0.781 x 5 +1.3278x 4 ‑0.5351x 3 ‑1.0001x 2 +1.0287x-0.0832, wherein, X is more than or equal to 0 and less than or equal to 1.5; the curve equation of the profile of the suction surface is: y is 0.44x 5 ‑1.8665x 4 +2.5144x 3 ‑2.225x 2 +1.0981x + 0.0966; wherein the content of the first and second substances, -0.2. ltoreq. x. ltoreq.1.2; coordinate (x) p ，y p ) Is any point on the pressure surface curve, and has coordinate (x) s ，y s ) The coordinate origin is the center of the front edge of the blade. The centrifugal fan blade is efficient and low in noise.)

1. The centrifugal fan blade comprises a blade, wherein the blade is provided with a blade front edge, a pressure surface, a blade rear edge and a suction surface which are sequentially connected end to end;

The method is characterized in that:

The molded line of the pressure surface and the molded line of the suction surface are spline curves;

the curve equation of the molded line of the pressure surface is as follows:

y＝-0781x⁵+13278x⁴-05351x³-10001x²+10287x-00832；

Wherein the content of the first and second substances,0≤x≤1.5；

The curve equation of the profile of the suction surface is as follows:

y＝0.44x⁵-1.8665x⁴+2.5144x³-2.225x²+1.0981x+0.0966；

Wherein the content of the first and second substances,-0.2≤x≤1.2；

Coordinate (x)_p，y_p) Is any point on the pressure surface curve, and has coordinate (x)_s，y_s) Is a suction surfaceAt any point on the curve, b is the chord length of the blade, the x axis is the direction extending along the chord length of the blade, the y axis is the direction perpendicular to the chord length of the blade, and the origin of coordinates is the center of the leading edge of the blade.

2. The centrifugal fan blade of claim 1, wherein:

The number of the blades is multiple, an airflow channel is arranged between every two adjacent blades, and the width of the airflow channel is increased and then reduced from the inlet of the airflow channel to the outlet of the airflow channel.

3. the centrifugal fan blade of claim 2, wherein:

The maximum width of the airflow channel is w, and w/b is more than or equal to 0.65 and less than or equal to 0.9.

4. a centrifugal fan blade according to claim 3, wherein:

w/b＝0.75。

5. the centrifugal fan blade according to any one of claims 2 to 4, wherein:

The centrifugal fan further comprises a fan blade bottom plate, the fan blade bottom plate is annular, and a plurality of blades are uniformly arranged on the inner peripheral wall of the fan blade bottom plate along the circumferential direction of the fan blade bottom plate.

6. The centrifugal fan blade according to any one of claims 1 to 4, wherein:

The inlet setting angle of the vane is in the range of 38 DEG to 95 deg.

7. The centrifugal fan blade according to any one of claims 1 to 4, wherein:

The outlet setting angle of the vanes is in the range of 135-170 deg.

8. The centrifugal fan blade according to any one of claims 1 to 4, wherein:

The distance between the maximum thickness position of the blade and the center of the front edge of the blade is h, and h/b is more than or equal to 0.3 and less than or equal to 0.4.

9. The centrifugal fan blade of claim 8, wherein:

h/b＝0.33。

10. the centrifugal fan blade according to any one of claims 1 to 4, wherein:

the molded lines of the blade front edge are arc molded lines, elliptical arc molded lines, streamline molded lines, spindle molded lines or linear molded lines.

11. the centrifugal fan blade according to any one of claims 1 to 4, wherein:

The molded lines of the blade trailing edge are linear molded lines, arc molded lines or elliptical arc molded lines.

12. A centrifugal fan comprising a centrifugal impeller as claimed in any one of claims 1 to 11.

13. An air conditioner characterized by comprising the centrifugal fan according to claim 12.

14. a vehicle comprising the air conditioner of claim 13.

Technical Field

The invention relates to the technical field of air conditioners, in particular to a centrifugal fan blade, a centrifugal fan, an air conditioner and a transportation tool.

background

Along with the development of economy, the living standard of people is improved, the requirements of passengers on riding environments are higher and higher, particularly the requirements on comfort of the environments in the bus are higher and higher, the requirements comprise key parameters such as the noise level in the bus, temperature rise and temperature drop and the like, higher requirements are provided for the bus air conditioner, the noise level of a new national standard on the indoor side of the bus air conditioner is improved to 65dB (A) from the original 70dB (A), and the noise requirements are higher and higher.

The centrifugal fan is an air supply component at the indoor side of the bus air conditioner and is a main noise source at the indoor side of the bus air conditioner, and the increasingly strict noise requirement can be met only by improving the noise level of the centrifugal fan. The blade profile design of the centrifugal fan blade directly determines the performance of the fan, the blade profile with excellent performance is beneficial to improving the efficiency of the fan and reducing the noise of the fan, and the traditional fan blade mostly adopts a single-arc design, has higher noise and low efficiency and can not meet the requirement of the noise.

Disclosure of Invention

The first purpose of the invention is to provide a high-efficiency low-noise centrifugal fan blade, which can make airflow obtain larger pressure and flow, reduce the generation of vortex, improve the flow efficiency of the centrifugal fan blade and reduce the noise of the centrifugal fan blade.

The second purpose of the invention is to provide a centrifugal fan with the centrifugal fan blade.

a third object of the present invention is to provide an air conditioner having the above centrifugal fan.

the fourth purpose of the invention is to provide a transportation tool with the air conditioner.

In order to achieve the first object, the centrifugal fan blade provided by the invention comprises a blade, wherein the blade is provided with a blade front edge, a pressure surface, a blade rear edge and a suction surface which are sequentially connected end to end, the molded lines of the pressure surface and the suction surface are spline curves, and the curve equation of the molded line of the pressure surface is as follows: y is-0.781 x⁵+1.3278x⁴-0.5351x³-1.0001x²+1.0287x-0.0832, wherein,X is more than or equal to 0 and less than or equal to 1.5; the curve equation of the profile of the suction surface is: y is 0.44x⁵-1.8665x⁴+2.5144x³-2.225x²+1.0981x + 0.0966; wherein the content of the first and second substances,-0.2. ltoreq. x. ltoreq.1.2; coordinate (x)_p，y_p) Is any point on the pressure surface curve, and has coordinate (x)_s，y_s) The coordinate origin is the center of the front edge of the blade.

According to the scheme, the centrifugal fan blade can enable airflow to obtain larger pressure and flow, meanwhile, the generation of vortex is reduced, the flowing efficiency of the centrifugal fan blade is improved, and the noise of the centrifugal fan blade is reduced. Compared with the existing fan blade, the noise can be reduced by 3dB (A) to 5dB (A), the efficiency is improved by more than 30%, and the power is reduced by 8%.

Preferably, the number of the blades is multiple, an airflow channel is arranged between every two adjacent blades, and the width of the airflow channel is increased and then decreased from the inlet of the airflow channel to the outlet of the airflow channel.

the further proposal is that the maximum width of the airflow channel is w, and the w/b is more than or equal to 0.65 and less than or equal to 0.9.

In a further embodiment, w/b is 0.75.

Therefore, the width of the airflow channel is increased from the inlet to the outlet and then reduced, the speed of airflow is reduced and then increased when the airflow passes through the airflow channel, the length of the accelerating flow channel accounts for about 70% of the total length of the flow channel, the centrifugal fan blade is high in efficiency, the air quantity of the existing fan blade at high rotating speed can be achieved at low rotating speed, the centrifugal fan blade can operate under small centrifugal force, and therefore the centrifugal fan blade is guaranteed to operate safely and reliably.

According to a preferable scheme, the centrifugal fan further comprises a fan blade bottom plate, the fan blade bottom plate is annular, and the plurality of blades are uniformly arranged on the inner peripheral wall of the fan blade bottom plate along the circumferential direction of the fan blade bottom plate.

Preferably, the inlet setting angle of the blade is in the range of 38 ° to 95 °.

preferably, the outlet setting angle of the vanes is in the range of 135 ° to 170 °.

In a preferable scheme, the distance from the maximum thickness position of the blade to the center of the front edge of the blade is h, and h/b is more than or equal to 0.3 and less than or equal to 0.4.

In a further embodiment, h/b is 0.33.

Therefore, the centrifugal blade is designed into a blade profile with different thicknesses, the maximum thickness is positioned at the position about one third chord length away from the front edge of the blade, and the design accords with the optimal flow resistance.

In a preferred scheme, the profile of the blade leading edge is an arc profile, an elliptical arc profile, a streamline profile, a spindle profile or a linear profile.

In a preferred scheme, the molded line of the blade trailing edge is a straight line molded line, an arc molded line or an elliptic arc molded line.

In order to achieve the second object, the centrifugal fan provided by the invention comprises the centrifugal fan blade.

In order to achieve the third objective, the present invention provides an air conditioner including the centrifugal fan.

In order to achieve the fourth object, the invention provides a transportation vehicle comprising the air conditioner.

According to the scheme, the centrifugal fan blade can enable airflow to obtain larger pressure and flow, reduce the generation of vortex, improve the flow efficiency of the centrifugal fan blade and reduce the noise of the centrifugal fan blade. Compared with the existing fan blades, the noise can be reduced by 3dB (A) to 5dB (A), the efficiency is improved by more than 30%, and the power is reduced by 8%, so that the energy efficiency ratio of the bus air conditioner and the comfort requirement of the whole vehicle can be improved, and the cruising ability of the whole vehicle is improved.

Drawings

fig. 1 is a perspective view of an embodiment of a centrifugal fan blade of the present invention.

Fig. 2 is a top view of fig. 1.

Fig. 3 is a perspective view of an embodiment of the centrifugal fan blade of the present invention.

fig. 4 is a top view of fig. 3.

Fig. 5 is a graph of profile of a blade in an embodiment of a centrifugal fan blade according to the present invention.

Fig. 6 is a partially enlarged view at C in fig. 2.

Fig. 7 is a simulated flow field diagram of a conventional fan blade.

fig. 8 is a simulated flow field diagram of an embodiment of the centrifugal fan blade of the present invention.

Fig. 9 is a noise curve diagram of the centrifugal fan blade according to the embodiment of the present invention and the conventional fan blade in different gears.

the invention is further explained with reference to the drawings and the embodiments.

Detailed Description

Centrifugal fan blade embodiment

Referring to fig. 1 and 2, the centrifugal fan blade of this embodiment includes an integrally formed fan blade bottom plate 1 and a plurality of blades 2, and fan blade bottom plate 1 is ring shape, and a plurality of blades 2 are evenly arranged on the internal perisporium of fan blade bottom plate 1 along the circumference of fan blade bottom plate 1.

Referring to fig. 3 and 4, each blade 2 is provided with a blade leading edge 21, a pressure surface 22, a blade trailing edge 23 and a suction surface 24 which are connected end to end in sequence, and the molded line 221 of the pressure surface 22 and the molded line 241 of the suction surface 24 are spline curves. The molded line 211 of the blade front edge 21 is an arc molded line, the molded line 231 of the blade rear edge 23 is a linear molded line, the blade rear edge 23 is connected to the blade bottom plate 1, the blade front edge 21 extends towards the axis of the blade bottom plate 1, and the blade front edge 21, the pressure surface 22, the blade rear edge 23 and the suction surface 24 all extend along the axial direction of the blade bottom plate 1. The molded line 221 of the pressure surface 22 is a curve presented by the pressure surface 22 projected along the axis of the fan blade base plate 1, the molded line 241 of the suction surface 24 is a curve presented by the suction surface 24 projected along the axis of the fan blade base plate 1, the molded line 211 of the blade leading edge 21 is a curve presented by the blade leading edge 21 projected along the axis of the fan blade base plate 1, and the molded line 231 of the blade trailing edge 23 is a curve presented by the blade trailing edge 23 projected along the axis of the fan blade base plate 1.

Referring to fig. 5, point a is any point on the profile 221 of the pressure surface 22 and has the coordinate (x)_p，y_p) Relative coordinate isThe curve equation for profile 221 of pressure face 22 is:

Order toX is more than or equal to 0 and less than or equal to 1.5, then

y＝-0.781x⁵+1.3278x⁴-0.5351x³-1.0001x²+1.0287x-0.0832。

The point B is any point on the profile line 241 of the suction surface 24 and has the coordinate of (x)_s，y_s) Relative coordinate isThe curve equation for profile line 241 of suction surface 24 is:

Order tox is more than or equal to-0.2 and less than or equal to 1.2, then

y＝0.44x⁵-1.8665x⁴+2.5144x³-2.225x²+1.0981x+0.0966；

Where b is the chord length of the blade, the x-axis is the direction extending along the chord length of the blade, the y-axis is the direction perpendicular to the chord length of the blade, and the origin of coordinates 0 is the center of the leading edge 21 of the blade.

Designing the blade 2 according to the curve equation of the pressure surface 22 and the curve equation of the suction surface 24, selecting a proper blade chord length b according to different diameters of centrifugal fan blades, and designing and controlling the shape of the blade 2 by using the parameter equations of the pressure surface 22 and the suction surface 24 through relative coordinates.

The distance between the maximum thickness position D of the blade 2 and the center of the blade leading edge 21 is h, the ratio of h to the chord length b of the blade directly affects the resistance characteristic of the blade 2, and further affects the flow efficiency of the centrifugal fan blade, when h/b is not less than 0.3 and not more than 0.4, the flow resistance is small, and preferably, h/b is 0.33. The centrifugal blade 2 is designed by adopting a blade profile with different thicknesses, and the maximum thickness position D is positioned at the position about 21-third chord length away from the front edge of the blade, so that the design accords with the optimal flow resistance.

Referring to fig. 6, an airflow channel 25 is disposed between two adjacent blades 2, and from an inlet 251 of the airflow channel 25 to an outlet 252 of the airflow channel 25, the width of the airflow channel 25 increases first and then decreases, the maximum width of the airflow channel 25 is w, when w/b is greater than or equal to 0.65 and less than or equal to 0.9, the efficiency of the centrifugal fan blade is high, and preferably, w/b is 0.75. The width of the airflow channel 25 is increased and then decreased from the inlet 251 to the outlet 252, the speed of the airflow passing through the airflow channel 25 is decreased and then increased, the length of the acceleration channel accounts for about 70% of the total length of the flow channel, the centrifugal fan blade has high efficiency, and the air volume of the existing fan blade at high rotating speed can be reached at low rotating speed, so that the centrifugal fan blade can operate under smaller centrifugal force, and the safe and reliable operation of the centrifugal fan blade is ensured. As shown in fig. 7 and 8, the centrifugal fan blade of the present invention has a large high-speed area, the airflow passing through the blade 2 can obtain more energy, the efficiency of the centrifugal fan blade is significantly higher than that of the existing fan blade, and the actual test results of the prototype are shown in fig. 9 and table 1, and it can be known from the test results that the noise of the centrifugal fan blade of the present invention at each gear is 3dB (a) to 5dB (a) lower than that of the existing fan blade, the efficiency is improved by more than 30%, and the power is reduced by 8%.

Table 1: the invention relates to a noise, air quantity and power data comparison table of a centrifugal fan blade and the existing fan blade

The blade 2 can be used for centrifugal blades of different types, can be a double-suction impeller or a single-suction impeller, and can be used for air-conditioning fans of different types, such as a bus air-conditioning centrifugal fan, a ducted air conditioner centrifugal fan, a range hood centrifugal fan and the like. The height of the blades 2 can be selected according to the specific structure and the prototype requirement, the number of the blades 2 can be selected from 16 to 85, and the inlet installation angle beta of the blades 2₁Inlet setting angle beta of the blade 2 in the range of 38 DEG to 95 DEG₁Determines the inflow of the airflow, the flow disorder degree in the blade channel is influenced by over and under values, and the outlet installation angle beta of the blade 2₂the outlet setting angle beta of the blade 2 is within the range of 135 DEG to 170 DEG₂The static pressure capacity of the unit is determined, and a large value is often adopted for a high static pressure fan. Blade inlet setting angle beta₁the included angle between the tangent line of the blade airfoil profile bone line at the finger inlet 251 and the circumferential direction and the installation angle beta of the blade outlet₂Which refers to the angle of the tangent to the bone line at the exit 252 with respect to the circumferential direction.

In addition, the profile of the leading edge of the blade may be an elliptical arc profile, a streamline profile, a spindle profile, a linear profile, or the like. The profile of the trailing edge of the blade can also be an arc profile or an elliptical arc profile or the like.

Centrifugal Fan embodiment

The centrifugal fan of this embodiment includes the centrifugal fan blade in the above-mentioned centrifugal fan blade embodiment.

Air conditioner embodiment

The air conditioner comprises the centrifugal fan in the centrifugal fan embodiment.

Embodiments of a transportation means

The transportation means includes the air conditioner in the above-mentioned air conditioner embodiment, and the transportation means may be a bus or the like.

Therefore, the centrifugal fan blade can enable air flow to obtain larger pressure and flow, reduce the generation of vortex, improve the flow efficiency of the centrifugal fan blade and reduce the noise of the centrifugal fan blade. Compared with the existing fan blades, the noise can be reduced by 3dB (A) to 5dB (A), the efficiency is improved by more than 30%, and the power is reduced by 8%, so that the energy efficiency ratio of the bus air conditioner and the comfort requirement of the whole vehicle can be improved, and the cruising ability of the whole vehicle is improved.

Finally, it should be emphasized that the above-described preferred embodiments of the present invention are merely examples of implementations, not limitations, and various changes and modifications may be made by those skilled in the art, without departing from the spirit and scope of the invention, and any changes, equivalents, improvements, etc. made within the spirit and scope of the present invention are intended to be embraced therein.