CN109595198B

CN109595198B - Fan impeller

Info

Publication number: CN109595198B
Application number: CN201811496624.1A
Authority: CN
Inventors: 唐育萍; 徐绍斌
Original assignee: Foshan City Nanhai Popula Fan Co ltd
Current assignee: Foshan City Nanhai Popula Fan Co ltd
Priority date: 2018-12-07
Filing date: 2018-12-07
Publication date: 2023-09-01
Anticipated expiration: 2038-12-07
Also published as: CN109595198A

Abstract

The application discloses a fan impeller, which comprises a substrate, wherein blades are vertically arranged on the side surface of the substrate, a plurality of blades are arranged along the circumference of the center of the substrate in an array, the blades are arc-shaped, the arc centers of the blades are arranged in the substrate, the near-center end of the blades is an inlet angle, the telecentric end of the blades is an outlet angle, the connecting line from the outlet angle to the center of the substrate is a telecentric radius, the included angle formed by the tangent line of the outlet angle and the perpendicular line of the telecentric radius is A, the range of A is 148-152 degrees, the arc radius of the blades is R, the arc length of the blades is L, the diameter of the substrate is D, and the distance from the arc center of the blades to the center of the substrate is R, R: d=0.45 to 0.47, l: d=0.4 to 0.42, r: the application adopts long flow passage and round blades, and the structure configuration between adjacent blades is more reasonable, thereby effectively improving the air outlet efficiency of the blades and reducing noise.

Description

Fan impeller

Technical Field

The present application relates to a fan impeller.

Background

The existing fan blades are designed in a straight plate mode, or are designed into small arc plates, flow channels formed by the blades are short, air inlet quantity is difficult to improve, structural arrangement among the blades is unreasonable, airflow resistance of the blades is easy to be large, surging phenomenon is easy to occur to the blades after air outlet, noise is large, long-term working connection structure is easy to loosen, and power is large when required air quantity is achieved.

Disclosure of Invention

The application aims to solve the technical problems that: there is a need for a fan impeller that reduces drag generated during rotation of the blades, improves operating efficiency, reduces noise generated during operation, and improves structural stability.

The application solves the technical problems as follows: the utility model provides a fan impeller, includes the base plate, the side of base plate is provided with the blade perpendicularly, the blade is followed the centre of a circle circumference array of base plate is provided with a plurality of pieces, the blade is circular-arc, the arc center of blade is in the base plate, the near-heart end of blade is the entry angle, the distal end of blade is the exit angle, the exit angle extremely the line at base plate centre of a circle is telecentric radius, telecentric radius fits the diameter that forms the fitting circle diameter that is less than the diameter of base plate, the tangent line at exit angle with the contained angle that perpendicular line at telecentric radius formed is A, the scope of A is 148 degrees to 152 degrees, the arc radius of blade is R, the arc length of blade is L, the diameter of base plate is D, the arc center of blade to the distance at base plate centre of a circle is R, R: d=0.45 to 0.47, l: d=0.4 to 0.42, r: d=0.225 to 0.235.

As a further improvement of the above technical solution, a distance between a tangent line of an inlet angle of any one of the blades and a tangent line of an outlet angle of an adjacent blade is a flow channel outlet width, and a value of the flow channel outlet width is d, L: d=2.96.

As a further improvement of the technical scheme, A is 152 degrees.

As a further improvement of the above technical scheme, R: d=0.466.

As a further improvement of the above technical scheme, L: d=0.415.

As a further improvement of the above technical scheme, r: d=0.233.

As a further improvement of the technical scheme, one end of the blade, which is far away from the base plate, is provided with a front disc, the front disc is of a revolving body structure, a generatrix of the front disc is arc-shaped, and the outer diameter of the front disc gradually increases along the direction from the front disc to the base plate.

As a further improvement of the technical scheme, the radius of the circular arc of the front disc busbar is M, R: m=2.74.

The beneficial effects of the application are as follows: the fan resistance is effectively reduced by adopting the spherical arc-shaped fan blades, the flow passage is prolonged, the gas energizing opportunity is increased, the phenomenon that the air outlet backward inclined blades produce surging is avoided, the noise generated during the operation of the fan is reduced, the power consumption is reduced, the fan resistance is further reduced by adopting the circular arc-shaped design of the front disc of the fan, the smooth and efficient air flow passing through the air inlet inner space is ensured, and the fan can be applied to environment-friendly ventilation, spray painting and dust removal, oil fume silencer matching, waste gas treatment and the like.

Drawings

In order to more clearly illustrate the technical solutions in the embodiments of the present application, the drawings that are required to be used in the description of the embodiments will be briefly described below. It is evident that the drawings described are only some embodiments of the application, but not all embodiments, and that other designs and drawings can be obtained from these drawings by a person skilled in the art without inventive effort.

Fig. 1 is a schematic front view of a base plate and a blade according to the present application.

Fig. 2 is a schematic diagram of the overall side view of the present application.

In the figure: 1-base plate, 2-blade, 3-front tray, 4-inlet duct.

Detailed Description

The conception, specific structure, and technical effects produced by the present application will be clearly and completely described below with reference to the embodiments and the drawings to fully understand the objects, features, and effects of the present application. It is apparent that the described embodiments are only some embodiments of the present application, but not all embodiments, and that other embodiments obtained by those skilled in the art without inventive effort are within the scope of the present application based on the embodiments of the present application. In addition, all connection relationships mentioned herein do not refer to direct connection of the components, but rather, refer to a connection structure that may be better formed by adding or subtracting connection aids depending on the particular implementation. The technical features in the application can be interactively combined on the premise of no contradiction and conflict.

Referring to fig. 1 and 2, a fan impeller includes a base plate 1, a blade 2 is vertically disposed on a side surface of the base plate 1, a plurality of blades 2 are disposed along a circumferential array of a center of a circle of the base plate 1, the blade 2 is arc-shaped, an arc center of the blade 2 is in the base plate 1, a near-center end of the blade 2 is an entrance angle, a distal end of the blade 2 is an exit angle, a line from the exit angle to the center of the base plate 1 is a telecentric radius, a diameter of a fitting circle formed by fitting the telecentric radius is smaller than a diameter of the base plate 1, an included angle formed by a tangent line of the exit angle and a perpendicular line of the telecentric radius is a, a range of a is 148-152 degrees, an arc radius of the blade 2 is R, an arc length of the blade 2 is L, a diameter of the base plate 1 is D, a distance from the arc center of the blade 2 to the center of the base plate 1 is R, and R: d=0.45 to 0.47, l: d=0.4 to 0.42, r: the application designs the whole blade 2 into circular arc shape, and the design position of the blade 2 on the base plate 1 is required, the angle formed by the tangent line of the outlet angle and the perpendicular line of the telecentric radius is A, the circular arc radius of the blade 2 is R, the arc length of the blade 2 is L, the diameter of the base plate 1 is D, the distance from the center of the arc of the blade 2 to the center of the base plate 1 is R, the length units are uniform in the numerical limits, the ratio of the circular arc radius R of the blade 2 to the diameter D of the base plate 1 is in the range of 0.45-0.47, the value of the circular arc radius R of the blade 2 can be determined, the ratio of the circular arc length L of the blade 2 to the diameter D of the base plate 1 is in the range of 0.4-0.42, the ratio of the diameter of the blade 2 to the base plate 5 is in the range of 0.225-0.235, the fitting circle diameter of the blade 2 is smaller than the diameter of the base plate 1, the outlet angle is always uniform, the ratio of the blade 2 to the diameter D is in the range of the base plate 1 is increased, the air inlet angle is increased, the fan can be prevented from being increased by the ratio of the circular arc radius R to the diameter D of the base plate 1 to the base plate 1, the fan is reduced, the fan is prevented from generating the air flow noise in the range of the fan is reduced, and the fan is reduced in the range of the air inlet angle is reduced, and the fan is more than the fan has the required, and the fan has the fan noise condition that can be more than the fan noise is more than the fan noise and has the fan noise.

Further as a preferred embodiment, the distance between the tangent line of the inlet angle of any one of the blades 2 and the tangent line of the outlet angle of the adjacent blade 2 is the width of the outlet of the flow channel, and the value of the width of the outlet of the flow channel is d, L: d=2.96, can confirm the quantity that blade 2 set up according to L and d's ratio, and this ratio is provided with 8 under the blade 2, and the structure is more reasonable, further improves the intake.

Further as a preferred embodiment, a is 152 degrees, R: d=0.466, l: d=0.415, r: d=0.233, which is the optimal structural design.

Further as a preferred embodiment, a front disc 3 is disposed at an end of the blade 2 away from the base plate 1, the front disc 3 is in a revolving structure, a generatrix of the front disc 3 is in an arc shape, and the outer diameter of the front disc 3 gradually increases along the direction from the front disc 3 to the base plate 1, and the arc-shaped front disc 3 makes the airflow resistance smaller.

Further as preferred embodiment, the front tray 3 is kept away from the one end of blade 2 is provided with an air inlet section of thick bamboo 4, air inlet section of thick bamboo 4 is solid of revolution structure, the generating line of air inlet section of thick bamboo 4 include straight section, with the arc section that straight section one end is connected, the centre of a circle of arc section set up in air inlet section of thick bamboo 4's outside, the arc section keep away from straight section's one end stretches into in the front tray 3, straight section's structural design can make air inlet section of thick bamboo 4 install more easily, adopts curved air inlet section of thick bamboo 4, can further reduce the noise of intaking, reduces air current resistance, reduces vortex and backflow loss for more unobstructed high-efficient when the air current gets into the impeller.

Further as a preferred embodiment, the radius of the arc of the generatrix of the front disc 3 is M, R: m=2.74, the arc radius of the arc segment is N, R: n=2.74, which is the optimal structural design.

In order to further verify the working effect of the fan, a first set of experimental tests are performed, the existing fan impeller adopting the straight plate type and the short flow channel is tested, the fan impeller is connected with 8 air channels, 8 different working conditions are obtained, and experimental data are shown in table 1:

table 1:

circular arc-shaped blades are adopted, and R: d=0.45, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 2:

table 2:

circular arc-shaped blades are adopted, and R: d=0.46, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 3:

table 3:

circular arc-shaped blades are adopted, and R: d=0.466, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 4:

table 4:

circular arc-shaped blades are adopted, and R: d=0.47, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 3:

table 5:

as can be seen from tables 1 to 5, the axial static efficiency of the fan is relatively improved and the impeller power and the sound level are relatively reduced after the circular arc-shaped blades are used compared with those of the straight-plate type and short-flow-path fan blades, so that the circular arc-shaped blades have higher efficiency than the conventional straight-plate type blades, lower power consumption and lower noise under the same air output, and the circular arc-shaped blades have lower noise compared with those of tables 2 to 5, and are shown in the following table 2 to table 5: d is between 0.45 and 0.466, the axial static efficiency is in an ascending trend, the impeller power is in a descending trend, and the sound level is in a descending trend compared with the sound level A, but when R: when D is 0.47, relative R: at D of 0.466, the shaft static efficiency is relatively reduced, the impeller power is relatively increased, and the sound level is substantially unchanged from a, so that when R: d is 0.466, which is the optimum value of the structure.

After maintaining R: on the basis of D being 0.466, changing the ratio of L to D, and carrying out a second group of experimental measurement, taking L: d=0.4, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 6:

table 6:

taking L: d=0.41, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 7:

table 7:

taking L: d=0.415, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 8:

table 8:

taking L: d=0.42, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 9:

table 9:

as can be seen from tables 6 to 9, in L: d is between 0.4 and 0.415, the axial static efficiency is in an ascending trend, the impeller power is in a descending trend, the sound level is lower than that of A, the efficiency of the fan is in a continuously increasing trend, but when L: at D of 0.42, relative L: at D of 0.415, the shaft static efficiency is relatively reduced, the impeller power is relatively increased, and the sound level is substantially unchanged from a, so that when L: d is 0.415, which is the optimum value of the structure.

After maintaining R: d is 0.466, L: on the basis of 0.415, the ratio of R to R is changed, a third set of experimental measurement is performed, R is taken, d=0.225, and the R is connected with 8 air channels to obtain 8 different working conditions, and experimental data are shown in table 10:

table 10:

taking r, d=0.23, connecting it with 8 air channels to obtain 8 different working conditions, and obtaining experimental data as shown in table 11:

table 11:

taking r: d=0.233, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 12:

table 12:

taking r: d=0.235, which was connected to 8 air ducts to obtain 8 different conditions, and experimental data were shown in table 13:

table 13:

as can be seen from tables 10 to 13, in the case that r: D is between 0.225 and 0.235, the axial static efficiency is in an upward trend, the impeller power is in a downward trend, the sound level is lower than that of the A sound level, the efficiency of the fan is in a continuous improvement trend, and theoretically r: d=0.235, the fan efficiency reaches an optimal value, but in actual production, when r: when d=0.235, since the blades are at the edge of the base plate, the centrifugal force of the blades is large during the high-speed rotation of the impeller, which easily results in unstable structure, and when r: d=0.233, the blade both keeps higher air-out efficiency to do not influence the stability of structure, keep in steady state when the impeller rotates, consequently, take r in the aspect of synthesizing life and the structural stability: d=0.233 is the optimum value.

After maintaining R: d is 0.466, L: d is 0.415, taking r: d=0.233, the range of an included angle a formed by a tangent line of an outlet angle and a perpendicular line of a telecentric radius is changed, a fourth set of experimental measurement is performed, a=148 degrees is taken, the experimental measurement is connected with 8 air channels, 8 different working conditions are obtained, and experimental data are shown in table 14:

table 14:

taking a=150 degrees, connecting the air duct with 8 air ducts to obtain 8 different working conditions, and obtaining experimental data as shown in table 15:

table 15:

taking a=152 degrees, connecting the air duct with 8 air ducts to obtain 8 different working conditions, and obtaining experimental data as shown in table 16:

table 16:

taking a=153 degrees, connecting the air duct with 8 air ducts to obtain 8 different working conditions, and obtaining experimental data as shown in table 17:

table 17:

as is clear from tables 14 to 17, the axial static efficiency is increased between 148 and 152 degrees, the impeller power is decreased, and the fan efficiency is increased continuously compared with the sound level a, but when a is 153 degrees, the axial static efficiency is relatively decreased compared with the sound level a because the total pressure in the impeller is decreased compared with the sound level a when a is 152 degrees, the impeller power is relatively increased, and the sound level a is basically unchanged compared with the sound level a, so that the optimum value of the structure is obtained at this time when a is 152 degrees.

The length units of the above four groups of experiments are unified as CM.

In summary, by combining the experimental measurements of the first to fourth groups, by changing the radian of the blade, the arc length of the blade, the position of the blade on the substrate, and the swing angle of the blade, we obtain the following ratio R: d=0.466, l: d=0.415, r: d=0.233, when a=152 degrees, the structure of fan impeller reaches the optimum, has effectively reduced fan resistance to prolonged the runner, made gas energization chance increase, avoided giving vent to anger the phenomenon that the retroverted blade produced "surge", reduced the noise that produces when the fan operates, reduced the consumption, and front disc, the inlet air section of thick bamboo of fan adopt convex design equally, R: m is 2.74, R: n is 2.74, fan resistance is further reduced, air intake noise is reduced, vortex and backflow losses are reduced, smooth and efficient air flow passing through an air intake inner space is ensured, compared with other centrifugal fan products of the same type, the fan is increased in proportion per hour, the fan efficiency reaches 88%, the power of a matched motor is small, and the noise of the matched motor is 10-15% lower than that of the similar fan, so that the fan can be applied to environment-friendly ventilation, spray painting and dust removal, oil fume silencer matching, waste gas treatment and the like.

While the preferred embodiment of the present application has been described in detail, the application is not limited to the embodiments, and various equivalent modifications and substitutions can be made by those skilled in the art without departing from the spirit of the application, and these modifications and substitutions are intended to be included in the scope of the present application as defined in the appended claims.

Claims

1. A fan impeller, characterized in that: including base plate (1), the side of base plate (1) is provided with blade (2) perpendicularly, blade (2) are followed the centre of a circle circumference array of base plate (1) is provided with a plurality of pieces, blade (2) are circular-arc, the arc center of blade (2) is in base plate (1), the nearly heart end of blade (2) is the entry angle, the telecentric end of blade (2) is the exit angle, the exit angle extremely the line at base plate (1) centre of a circle is telecentric radius, telecentric radius fits the diameter of the circle that forms and is less than the diameter of base plate (1), the tangent line at exit angle with the contained angle that the perpendicular line at telecentric radius formed is A, the scope of A is 148 degrees to 152 degrees, the arc radius of blade (2) is R, the arc length of blade (2) is L, the diameter of base plate (1) is D, the distance of the arc center of blade (2) to base plate (1) centre of a circle is R. D=0.45 to 0.47, l: d=0.4 to 0.42, r: d=0.225 to 0.235, wherein the distance between the tangent line of the inlet angle of any blade (2) and the tangent line of the outlet angle of the adjacent blade (2) is the width of the outlet of the flow channel, and the value of the width of the outlet of the flow channel is D, L: d=2.96, the one end that blade (2) kept away from base plate (1) is provided with front disc (3), front disc (3) are solid of revolution, the generating line of front disc (3) is circular-arc, the external diameter of front disc (3) is followed front disc (3) extremely the direction of base plate (1) increases gradually.

2. A fan impeller according to claim 1, wherein: a is 152 degrees.

3. A fan impeller according to claim 1, wherein: r: d=0.466.

4. A fan impeller according to claim 1, wherein: l: d=0.415.

5. A fan impeller according to claim 1, wherein: r: d=0.233.

6. A fan impeller according to claim 1, wherein: the arc radius of the front disc (3) bus is M, R: m=2.74.