CN217873417U

CN217873417U - Axial fan blade structure and axial fan

Info

Publication number: CN217873417U
Application number: CN202221851982.1U
Authority: CN
Inventors: 雷琼; 曹新海
Original assignee: Hefei Sufan Automobile Technology Co ltd
Current assignee: Hefei Sufan Automobile Technology Co ltd
Priority date: 2022-07-18
Filing date: 2022-07-18
Publication date: 2022-11-22
Anticipated expiration: 2032-07-18

Abstract

The utility model provides an axial fan blade structure and axial fan, including wheel hub, blade and bling, its characterized in that: the root part and the tip part of the blade are respectively connected with the hub and the blade ring, and a wind guide cavity is formed below the blade; the orthographic projection of the connecting end of the blade and the hub forms a first surface, the orthographic projection of the connecting end of the blade and the blade ring forms a second surface, and the wind inlet ends of the first surface and the second surface are both inclined upwards; the blade deflects from the root part to the tip part in a gentle trend, so that the inclination angle of the second surface is smaller than that of the first surface; the air inlet end of the blade is provided with a first blade surface which is horizontally bent and connected with the blade ring. The utility model provides a under the requirement of the high static pressure of axial fan, guarantee that the amount of wind is enough and improve the problem of noise.

Description

Axial fan blade structure and axial fan

Technical Field

The utility model belongs to the technical field of axial fan, concretely relates to axial fan blade structure and axial fan.

Background

The continuous development of new energy passenger cars, trucks and engineering machinery also drives the product and technical innovation in the field of heat dissipation. The axial flow heat radiation fan, which is an essential component of an automobile cooling system, has a long service life, low noise and high performance, and is a primary choice for a new energy vehicle heat radiation system.

At present, in the design and manufacturing process of an axial flow cooling fan, the optimal scheme of the axial flow fan is often difficult to achieve, some axial flow cooling fans have good cooling performance but high noise, some axial flow cooling fans have high rotating speed but cannot meet the requirement on balance performance, and the service life of a motor is shortened due to the fact that the balance of fan blades is affected by dust after the axial flow cooling fans are used for a long time.

Meanwhile, at present, the heat dissipation requirement is higher and higher, the static pressure is higher, the requirement on the air volume is also higher, and as the static pressure and the air volume are mutually restricted, the larger the air volume is, the larger the noise is. For example, the static pressure required to increase from a conventional pressure of 100-200Pa to 250-350Pa presents a greater challenge to both the air volume of the radiator fan and to noise abatement.

SUMMERY OF THE UTILITY MODEL

The utility model aims at providing an axial fan flabellum structure and axial fan to under the requirement of the high static pressure of solution axial fan, guarantee that the amount of wind is enough and improve the problem of noise.

The utility model provides a following technical scheme:

an axial flow fan blade structure comprises a hub, a blade and a blade ring, wherein the root part and the tip part of the blade are respectively connected with the hub and the blade ring to form an induced air cavity;

the orthographic projection of the connecting end of the blade and the hub forms a first surface, the orthographic projection of the connecting end of the blade and the blade ring forms a second surface, and the wind inlet ends of the first surface and the second surface are both inclined upwards; the blade deflects from the root part to the tip part in a gentle trend, so that the inclination angle of the second surface is smaller than that of the first surface;

the wind inlet end of the blade is provided with a first blade surface which is bent horizontally and is connected with the blade ring.

Preferably, the orthographic projections of the first surface and the second surface are intersected with each other, the top end of the second surface is lower than the top end of the first surface, and the bottom end of the second surface is higher than the bottom end of the first surface.

Preferably, the blade still includes integrated into one piece's blade surface two and blade surface three, blade surface two is connected with blade surface three respectively wheel hub with the leaf ring, the inlet end of blade surface two is angle one with wheel hub's lateral wall contained angle, blade surface three's inlet end is angle two with the lateral wall contained angle of leaf ring, angle one is less than angle two.

Preferably, the first angle is in the range of 58-62 °, and the second angle is in the range of 130-140 °.

Preferably, the wind inlet end of the first blade surface is in arc transition to the wind inlet end of the third blade surface.

Preferably, the first blade surface and the joint of the blade ring are connected with the first surface, and the thickness of the first blade surface is gradually reduced from the wind inlet end of the first blade surface to the first connection surface.

Preferably, the thickness of the second leaf surface is gradually increased from the wind inlet end to the wind outlet end and then gradually reduced.

Furthermore, a plurality of blades are distributed in a radial variable pitch mode in the space between the hub and the blade ring by taking the axis of the hub as the center.

Preferably, the spacing angles of adjacent blades are 46.8-48.6 degrees, 56.2-58.2 degrees, 48-50.5 degrees, 42-44 degrees, 54.8-56.2 degrees, 54.2-55.6 degrees and 52-54 degrees in sequence.

The utility model also provides an axial fan to the solution influences the static problem because of fan wind intracavity outside pressure differential.

The axial flow fan comprises a motor, a wind frame and the axial flow fan blade structure, wherein the wind frame and the hub are both connected with the motor; wherein:

the wind frame comprises an annular cover ring which coaxially covers the outer side of the blade ring and leaves a wind gap with the blade ring;

the blade ring comprises a side ring and a top ring which are integrally formed, and the top ring is turned over outwards from the top of the side ring to the upper part of the cover ring;

a side air gap is formed between the side ring and the side wall of the cover ring, and a top air gap is formed between the top ring and the top surface of the cover ring;

and the cover ring is also provided with an air guide part below the blade ring, the inner side wall of the air guide part protrudes below the side air gap, and high-pressure air flow enters the side air gap after the air guide part changes the direction and is exhausted from the top air gap.

Preferably, the outer diameter of the top ring is larger than or equal to that of the cover ring, the size of the side air gap is 2-4mm, the size of the top air gap is 2-3.5mm, the inner diameter of the air guide part is smaller than the outer diameter of the side ring by 0-2mm, and the distance between the top of the air guide part and the bottom of the side ring is 1-4mm.

The utility model has the advantages that:

the special blade shape of the utility model deflects the blade from the root to the tip with a gentle trend, so that the inclination angle of the second surface is smaller than that of the first surface, namely the wind inlet angle of the root of the blade is increased, thereby increasing the static pressure, and simultaneously, the wind inlet area of the tip which tends to be gentle gives consideration to the wind quantity; and the blade is prepared into a sectional structure of a first blade surface, a second blade surface and a third blade surface, the first blade surface is horizontally bent forwards from the third blade surface to form a wind breaking area, the vibration of the blade and a blade ring is resisted, and the working noise is effectively reduced.

Furthermore, the utility model discloses an asymmetric displacement between the leaf ring distributes, improves the resonant frequency section, avoids the system resonance and damages mechanical parts, on this basis, does the gradual change processing with the effective thickness of blade, and the thickness of blade surface one, blade surface two is held the convergent by the air inlet, and the thickness of blade surface three is held the first gradual change back convergent by the air inlet, has compromise blade intensity, wind noise and load energy consumption efficiency.

The special air guide part, the side air gap and the top air gap structure between the blade ring and the cover ring of the utility model have the advantages that the air inlet direction of the air flow enters the high pressure area from the low pressure area, and flows back along the bent air gap under the action of the pressure difference, so that the backflow amount is inhibited, and the static pressure of the fan is prevented from dropping; and simultaneously, the utility model discloses special air gap size has avoided the air gap undersize to produce "whistle sound" and has caused mechanical interference between leaf ring and the cover circle after long-term, consequently has the pressure boost to fall the effect of making an uproar on the whole.

Drawings

The accompanying drawings are included to provide a further understanding of the invention, and are incorporated in and constitute a part of this specification, illustrate embodiments of the invention, and together with the description serve to explain the invention and not to limit the invention. In the drawings:

fig. 1 is a schematic structural diagram of embodiment 1 of the present invention;

fig. 2 is a schematic top view of embodiment 1 of the present invention;

FIG. 3 isbase:Sub>A schematic cross-sectional view taken at A-A in FIG. 2;

FIG. 4 is a schematic cross-sectional view at B-B in FIG. 2;

fig. 5 is a schematic structural diagram of embodiment 2 of the present invention;

fig. 6 and 7 are schematic cross-sectional views of two positions of embodiment 2 of the present invention.

Labeled as: 1. a hub; 2. a blade; 21. a first leaf surface 22 and a second leaf surface; 23. leaf surface III; 24. A first surface; 25. a second surface; 26. a first connecting surface; 3. a leaf ring; 31. a side ring; 32. a top ring; 4. a wind frame; 41. Assembling the frame; 42. a rib; 43. a cover ring; 431. a wind guide part; 44. a side air gap; 45. a windward gap; 5. and a wind inlet end.

Detailed Description

Example 1

As shown in fig. 1 to 4, an axial flow fan blade structure includes a hub 1, blades 2 and a blade ring 3, the hub 1 and the blade ring 3 are coaxially disposed, and a plurality of blades 2 are installed between the hub 1 and the blade ring 3. The root and the tip of the blade 2 are respectively connected with the hub 1 and the blade ring 3, and a wind guide cavity is formed below the blade to guide airflow from the upper part to the oblique lower part.

Specifically, the present embodiment is illustrated by taking the following dimensions as examples: the external diameter of the hub 1 is 149.5mm, the external diameter of the blade 2 is 303.5mm, and the projection effective length of a single blade in the horizontal plane along the axial direction is 76.75mm, and is about 46-54% of the size of the hub, preferably 51%.

The blade 2 comprises a first blade surface 21, a second blade surface 22 and a third blade surface 23 which are integrally formed, the second blade surface 22 and the third blade surface 23 are respectively connected with the hub 1 and the blade ring 3, the first blade surface 21 is bent forwards (namely towards the air inlet side) from the third blade surface 23 to form a horizontal plane approximately, and the air inlet end of the first blade surface 21 can be inclined upwards by 1-3 degrees in consideration of convenience in injection molding and demolding. The ratio of the area of the first leaf surface 21, the second leaf surface 22 and the third leaf surface 23 to the leaf is respectively as follows: 10-14%, 18-21% and 65-70%. The airflow enters the second blade surface 22 and the third blade surface 23 from the air inlet end of the front edge of the first blade surface 21 at a high speed, and quickly flies off the blades at the rear end of the third blade surface 23 after being pressurized at a high speed by the third blade surface 23.

The wind inlet end of the first blade surface 21 is in arc transition to the wind inlet end of the third blade surface 23, so that the overall strength of the blade is ensured, and the length of the wind inlet end of the first blade surface 21 accounts for 50-60% of the length of the wind inlet end of the whole blade. The connecting end of the first blade surface and the first blade ring is defined as a first connecting surface 26.

Referring to fig. 3 and 4, an orthographic projection of the connecting end of the blade 2 and the hub 1 on the side wall of the hub 1 forms a first plane 24, an orthographic projection of the connecting end of the blade 2 and the blade ring 3 on the side wall of the hub 1 forms a second plane 25, and wind inlet ends of the first plane 24 and the second plane 25 are both inclined upwards. The blade 2 is deflected from the root to the tip in a gentle trend so that the inclination angle of the second plane 25 is smaller than that of the first plane 24, and the first plane 24 intersects or intersects with the orthographic projection of the second plane 25 on the hub 1, that is, the top end of the second plane 25 is lower than that of the first plane 24, and the bottom end of the second plane 25 is not lower than that of the first plane 24.

The torsional shape of the blade 2 can ensure that the second blade surface 22 can obtain a larger wind inlet angle and increase the static pressure; meanwhile, the large air volume is considered in the gentle air inlet area with the third 23 leaf surfaces; and the structure that the level was buckled forward of blade surface one 21 has formed the area of breaking wind, because if do not establish the air fluctuation in the former induced air intracavity of blade surface one, can encourage blade and cascade to produce the vibration of rule, the utility model discloses a blade surface one destroys original induced air chamber and air vibrations propagation path to destroy or resisted the vibration of blade and cascade, reduced the vibration noise.

Specifically, referring to fig. 6, an included angle between the wind inlet end 5 of the second blade surface and the side wall of the hub is an angle a, an included angle between the wind inlet end 5 of the third blade surface 23 and the side wall of the blade ring 3 is an angle b, and the angle a is smaller than the angle b. Preferably, the range of angle one is 58-62 deg., and the range of angle two is 130-140 deg..

Referring to fig. 2, in the present embodiment, the distribution structure of the blades 2 is further improved, seven blades 2 are distributed in a radial pitch-varying manner in the space between the hub 1 and the blade ring 3 with the axis of the hub as the center, preferably, the interval angles c1-c7 of adjacent blades are 46.8-48.6 °, 56.2-58.2 °, 48-50.5 °, 42-44 °, 54.8-56.2 °, 54.2-55.6 °, 52-54 ° in sequence, and more preferably, the interval angles of adjacent blades are 48 °, 57 °, 49 °, 42.7 °, 55.3 °, 55 °, 53 ° in sequence. The blades distributed in a variable pitch mode improve a resonance frequency section, damage to mechanical parts due to system resonance is avoided, and vibration noise is reduced.

The thickness of the blade 2 is improved, and the thickness of the first blade surface 21 is gradually reduced from the wind inlet end of the first blade surface 21 to the first connecting surface 26; the thickness of the second leaf surface 22 is gradually reduced from the air inlet end to the air outlet end; the thickness of the third leaf surface 23 gradually increases from the wind inlet end to the wind outlet end and then gradually decreases.

For example, in the backward direction from the wind inlet end 5, the thickness of the first blade surface 21 gradually changes from 2.2mm to 1.4mm, the thickness of the second blade surface gradually changes from 2.2mm to 1.8mm, the thickness of the third blade surface 23 gradually changes from 2.0mm to 3.2mm in the middle, and then gradually changes from 3.2mm in the middle to 1.8mm in the rear side. For conventional uniform thickness type blade, the thickness of blade in this embodiment gradually changes the setting, and the pressure that the middle part thickness of inlet end 5 and blade surface three received is great, and here thickness bodiness has improved blade 2's intensity, and the rear side of blade 2 thins gradually simultaneously, has alleviateed blade weight, has reduced wind noise and load energy consumption efficiency under the condition of guaranteeing the amount of wind.

The static pressure and air volume test data of the embodiment and the conventional axial flow fan are compared according to the GB/T1236-2017 test standard as follows:

from the above data, the larger the standard static pressure is, the more significant the increase of the air volume is.

Example 2

Referring to fig. 5 to 7, the present invention further provides an axial flow fan, which includes a motor, a wind frame 4 and an axial flow fan blade structure in embodiment 1, wherein the wind frame 4 is fixedly mounted on the motor, and the hub 1 is connected to an output shaft of the motor and is driven by the motor to rotate.

Referring to fig. 5, the wind frame 4 includes an assembly frame 41, ribs 42, and an annular cover 43, the assembly frame 41 is mounted on the motor, and the plurality of ribs 42 are connected between the assembly frame 41 and the cover 43, so as to ensure the overall mechanical strength of the wind frame.

The shroud ring 43 coaxially covers the outer side of the vane ring 3, and since there is no contact between the shroud ring 43 and the vane ring 3, an air gap is formed at the position when the vane rotates, the air flow flows from the low pressure area to the high pressure area from top to bottom, and due to the pressure difference, part of the air flow in the high pressure area flows back through the air gap to the outside, thereby affecting the static pressure of the fan.

Referring to fig. 6 and 7, in order to suppress static pressure, the blade ring 3 of the present embodiment includes a side ring 31 and a top ring 32 which are integrally formed, and the top ring 32 is folded outward from the top of the side ring 31 to above the shroud ring 43. A side air gap 44 is formed between the side ring 31 and the side wall of the cover ring 43, a top air gap 45 is formed between the top ring 32 and the top surface of the cover ring 43, and airflow turns through the side air gap 44 and then enters the top air gap 45, so that pressure difference backflow is effectively inhibited through large wind resistance.

The cover ring 43 is further provided with an air guide portion 431 below the blade ring 3, the air guide portion 431 is thick, and the inner wall of the air guide portion 431 protrudes inwards below the side air gap 44, so that high-pressure air can enter the side air gap 44 after turning an angle through the air guide portion 431 and is discharged from the top air gap 45, and backflow is further inhibited.

Specifically, the outer diameter of the top ring 32 is slightly larger than or equal to the outer diameter of the cover ring 43, the size of the side air gap 44 is 2-4mm, the size of the top air gap is 2-3.5mm, the inner diameter of the air guiding part 431 is smaller than the outer diameter of the side ring 31 by 0-2mm, and the distance from the top of the air guiding part 431 to the bottom of the side ring 31 is 1-4mm. Through the specific size configuration, the air gap is ensured to be large enough, the assembly is convenient, the mechanical interference can not be caused after the long-term use, and the whistle generated in the backflow area is avoided; meanwhile, the air gap is not too large, and backflow can be effectively inhibited.

Although the present invention has been described in detail with reference to the foregoing embodiments, it will be apparent to those skilled in the art that modifications may be made to the embodiments described in the foregoing embodiments, or equivalents may be substituted for elements thereof. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims

1. The utility model provides an axial fan blade structure, includes wheel hub, blade and bling, its characterized in that: the root part and the tip part of the blade are respectively connected with the hub and the blade ring, so that a wind guide cavity is formed below the blade;

the orthographic projection of the connecting end of the blade and the hub on the side wall of the hub forms a first surface, the orthographic projection of the connecting end of the blade and the blade ring on the side wall of the hub forms a second surface, and the wind inlet ends of the first surface and the second surface are both inclined upwards; the blade deflects from the root part to the tip part in a gentle trend, so that the inclination angle of the second surface is smaller than that of the first surface;

the air inlet end of the blade is provided with a first blade surface which is horizontally bent and connected with the blade ring.

2. The axial fan blade structure according to claim 1, wherein the orthographic projection of the first surface and the second surface cross each other, the top end of the second surface is lower than the top end of the first surface, and the bottom end of the second surface is not lower than the bottom end of the first surface.

3. The axial flow fan blade structure of claim 2, wherein the blade further comprises a second blade surface and a third blade surface which are integrally formed, the second blade surface and the third blade surface are respectively connected with the hub and the blade ring, an included angle between the air inlet end of the second blade surface and the side wall of the hub is an angle one, an included angle between the air inlet end of the third blade surface and the side wall of the blade ring is an angle two, and the angle one is smaller than the angle two.

4. The axial fan blade structure according to claim 3, wherein said first angle is in the range of 58-62 °, and said second angle is in the range of 130-140 °.

5. The axial flow fan blade structure of claim 3, wherein the wind inlet end of the first blade face is in arc transition to the wind inlet end of the third blade face, and the length of the wind inlet end of the first blade face accounts for 50-60% of the length of the wind inlet end of the whole blade.

6. The axial fan blade structure according to claim 3, wherein a connection point between the first blade surface and the blade ring is a first connection surface, and a thickness of the first blade surface is gradually reduced from an air inlet end of the first blade surface to the first connection surface; the thickness of the third leaf surface is gradually increased from the wind inlet end to the wind outlet end and then gradually reduced.

7. The axial flow fan blade structure of claim 3, wherein the plurality of blades are radially spaced in the space between the hub and the blade ring around the axial center of the hub.

8. The axial fan blade structure of claim 7, wherein the angle interval between adjacent blades is 46.8-48.6 °, 56.2-58.2 °, 48-50.5 °, 42-44 °, 54.8-56.2 °, 54.2-55.6 °, 52-54 °.

9. An axial-flow fan, characterized by comprising a motor, a wind frame and the axial-flow fan blade structure of any one of claims 1-8, wherein the wind frame and the hub are both connected with the motor; wherein:

and the cover ring is also provided with an air guide part below the blade ring, the inner side wall of the air guide part protrudes below the side air gap, and high-pressure air flow enters the side air gap after the direction of the high-pressure air flow is changed by the air guide part and is exhausted from the top air gap.

10. The axial flow fan according to claim 9, wherein an outer diameter of the top ring is greater than or equal to an outer diameter of the shroud ring, a size of the side air gap is 2-4mm, a size of the top air gap is 2-3.5mm, an inner diameter of the wind guide portion is less than the outer diameter of the side ring by 0-2mm, and a distance between a top of the wind guide portion and a bottom of the side ring is 1-4mm.