CN215927905U - Axial flow fan blade and air conditioner - Google Patents
Axial flow fan blade and air conditioner Download PDFInfo
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- CN215927905U CN215927905U CN202122007780.0U CN202122007780U CN215927905U CN 215927905 U CN215927905 U CN 215927905U CN 202122007780 U CN202122007780 U CN 202122007780U CN 215927905 U CN215927905 U CN 215927905U
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Abstract
The utility model provides an axial flow fan blade and an air conditioner, and relates to the technical field of air conditioners, wherein the axial flow fan blade comprises a hub and a plurality of blades arranged on the periphery of the hub, each blade is provided with a front edge and a tail edge which are opposite along the airflow direction, the front edge and the tail edge both extend to the hub from the outer end part of the blade, the tail edge is provided with a noise reduction notch which is sunken towards the front edge, and the included angle AOB formed among the sunken vertex A of the noise reduction notch, the junction B of the tail edge and the hub and the circle center O of the hub is between 48 degrees and 56 degrees. According to the utility model, the noise reduction notch is arranged, and meets the requirement of a certain size angle, the trailing edge gradient and the recess depth of the fan blade are increased, the pressure gradient distribution in the flow channel of the fan blade can be effectively improved, the secondary flow is inhibited, and the influence of the wake on the downstream flow is weakened, so that the static pressure of the blade is reduced, the material consumption is reduced, the energy consumption is reduced, the internal flow characteristic of the blade is effectively improved, and the aerodynamic noise is reduced.
Description
Technical Field
The utility model relates to the technical field of air conditioners, in particular to an axial flow fan blade and an air conditioner.
Background
The axial flow wind wheel is widely applied to various low-pressure ventilation occasions such as an air conditioner outdoor unit and the like due to large air volume, and the conventional axial flow fan blade of the air conditioner outdoor unit has the problems of large energy consumption and large noise due to unreasonable blade structure.
SUMMERY OF THE UTILITY MODEL
The utility model solves the problem of how to reduce energy consumption and pneumatic noise.
In order to solve the problems, the utility model adopts the following technical scheme.
In one aspect, the utility model provides an axial flow fan blade, which comprises a hub and a plurality of blades arranged on the periphery of the hub, wherein each blade is provided with a front edge and a tail edge which are opposite to each other in the airflow direction, the front edge and the tail edge both extend to the hub from the outer end part of the blade, a noise reduction notch which is sunken towards the front edge is arranged at the tail edge, and an included angle AOB formed among a sunken vertex A of the noise reduction notch, a junction B of the tail edge and the hub and the circle center O of the hub is between 48 degrees and 56 degrees.
The utility model provides an axial flow fan blade, wherein a noise reduction notch which is sunken towards a front edge is arranged at the tail edge of the blade, and an included angle AOB formed among a sunken vertex A of the noise reduction notch, a junction B of the tail edge and a hub and a circle center O of the hub is between 48 and 56 degrees. Through setting up the breach of making an uproar, and the breach of making an uproar satisfies certain size angle requirement, has increased fan blade trailing edge gradient and sunken degree of depth, can improve the pressure gradient distribution in the fan blade runner effectively, restrain the secondary flow and weaken the wake and flow the influence to the low reaches to reduce the static pressure of blade, reduce the consumptive material quantity, and reduce the energy consumption, and make it can effectively improve the internal flow characteristic of blade and reduce the pneumatics and make an uproar. Compared with the prior art, the axial flow fan blade provided by the utility model can reduce the energy consumption of the blade and reduce the aerodynamic noise.
Furthermore, an included angle ^ AOB formed among a sunken vertex A of the noise reduction notch, a junction B of the tail edge and the hub and a circle center O of the hub is 50 degrees.
Furthermore, an included angle AOC formed among a sunken vertex A of the noise reduction notch, a junction C of one end of the noise reduction notch close to the hub and the tail edge and a circle center O of the hub is between 2.9 and 35.1 degrees.
The axial flow fan blade provided by the utility model can further improve the internal flow characteristic of the blade and reduce the aerodynamic noise by limiting the initial end position of the noise reduction notch, thereby playing a role in reducing noise.
Furthermore, an included angle [ AOC ] formed among a sunken vertex A of the noise reduction notch, a junction C of one end of the noise reduction notch close to the hub and the tail edge and a circle center O of the hub is 13.6 degrees.
Furthermore, an included angle AOD formed among a sunken vertex A of the noise reduction notch, a junction D of one end of the noise reduction notch, which is far away from the hub, and the tail edge and a circle center O of the hub is between 4.4 and 14.4 degrees.
According to the axial flow fan blade provided by the utility model, the tail end part position of the noise reduction notch is limited, so that the internal flow characteristic of the blade can be further improved, the aerodynamic noise can be reduced, and the noise reduction effect can be realized.
Furthermore, an included angle AOD formed among a sunken vertex A of the noise reduction notch, a junction D of one end of the noise reduction notch, which is far away from the hub, and the tail edge and a circle center O of the hub is 5.5 degrees.
Further, a distance L1 between a concave apex A of the noise reduction notch and a center O of the hub is 1/2-6/7 of a distance L2 between an outboard end of the blade and the center O of the hub.
According to the axial flow fan blade provided by the utility model, the noise reduction notch is arranged at the rear half section of the tail edge, so that the rotor wake can be effectively reduced, the flow pressure characteristic change is small, the pneumatic noise is reduced, and the tone quality is improved. Meanwhile, the influence of the noise reduction notch on the structural strength of the blade can be reduced by arranging the rear half section, and the structural strength of the blade is ensured to meet the requirement.
Further, a distance L1 between a concave apex a of the noise reduction notch and a center O of the hub is 5/7 of a distance L2 between an outboard end of the blade and the center O of the hub.
Furthermore, one side of the blade, which is close to the hub, is also provided with a reinforcing rib, one end of the reinforcing rib is connected with the peripheral surface of the hub, and the other end of the reinforcing rib extends outwards.
According to the axial flow fan blade provided by the utility model, the reinforcing ribs are additionally arranged between the blade and the hub, so that the connection strength of the blade can be effectively enhanced.
In another aspect, the utility model provides an air conditioner, which includes an axial flow fan blade, where the axial flow fan blade includes a hub and a plurality of blades arranged on the periphery of the hub, each blade has a leading edge and a trailing edge opposite to each other in an airflow direction, and both the leading edge and the trailing edge extend from an outer end of the blade to the hub, a noise reduction notch recessed toward the leading edge is arranged at the trailing edge, and an included angle AOB formed between a recessed vertex a of the noise reduction notch, a junction B of the trailing edge and the hub, and a circle center O of the hub is between 48 ° and 56 °.
Drawings
Fig. 1 is a schematic structural view of an axial-flow fan blade provided in a first embodiment of the present invention at a first viewing angle;
fig. 2 is a schematic structural view of an axial-flow fan blade provided in the first embodiment of the present invention at a second viewing angle;
fig. 3 is a schematic structural view of an axial-flow fan blade provided in the first embodiment of the present invention at a third viewing angle;
fig. 4 is a schematic structural diagram of an axial-flow fan blade provided in the first embodiment of the present invention at a fourth viewing angle.
Description of reference numerals:
100-axial flow fan blades; 110-a hub; 111-end panels; 113-ribs; 130-a blade; 131-a leading edge; 133-trailing edge; 150-noise reduction notches; 170-reinforcing ribs.
Detailed Description
As disclosed in the background art, in the prior art, for an axial flow wind wheel, a conventional bent fan blade is usually adopted, the leading edge and the trailing edge of the conventional bent fan blade are both arc-shaped continuous structures, and the problems of high energy consumption and high noise exist because the structural parameters and the like of the fan blade are unreasonable.
Further, in the prior art, for the structure of the blade, a structure with a concave or convex trailing edge is provided to realize the adjustment of the internal flow characteristics. However, the size parameters of the existing concave or convex structures are still difficult to effectively reduce the energy consumption and the aerodynamic noise.
In order to solve the problems, the utility model provides an axial flow fan blade which can effectively reduce energy consumption and pneumatic noise. In order to make the aforementioned objects, features and advantages of the present invention comprehensible, embodiments accompanied with figures are described in detail below.
First embodiment
Referring to fig. 1 to 4, the embodiment provides an axial flow fan blade 100, which reduces noise and material consumption by improving the structure of the blade 130, and solves the problem of large energy consumption of the fan.
The axial flow fan blade 100 provided by the embodiment comprises a hub 110 and a plurality of blades 130 arranged on the periphery of the hub 110, each blade 130 is provided with a leading edge 131 and a trailing edge 133 which are opposite to each other along the airflow direction, the leading edge 131 and the trailing edge 133 both extend to the hub 110 from the outer end of the blade 130, a noise reduction notch 150 which is recessed towards the leading edge 131 is arranged at the trailing edge 133, and an included angle AOB formed among a recessed vertex a of the noise reduction notch 150, a junction point B of the trailing edge 133 and the hub 110 and a circle center O of the hub 110 is between 48 ° and 56 °.
In this embodiment, the axial flow fan 100 is suitable for an air conditioner external unit and is installed on an output shaft of a motor of the air conditioner external unit, wherein the axial flow fan 100 and the motor together form a fan of the air conditioner external unit. Of course, the axial flow fan blade 100 mentioned in this embodiment may also be applied to other low-pressure ventilation occasions, which are not listed here.
It should be noted that in the present embodiment, there is one noise reduction notch 150, and the noise reduction notch is formed on the trailing edge 133, and the forming depth thereof can be limited by the included angle range of ═ AOB. In other preferred embodiments of the present invention, the number of the noise reduction notches 150 may also be multiple, multiple noise reduction notches 150 are distributed on the trailing edge 133 at intervals, each noise reduction notch 150 can achieve the functions of reducing noise and reducing the amount of consumed material, of course, each noise reduction notch 150 satisfies the limitation of the included angle range of ≦ AOB, and the details of the case of multiple noise reduction notches 150 are not described here.
In the axial-flow fan blade 100 provided by this embodiment, the trailing edge 133 of the blade 130 is provided with the noise reduction notch 150 that is recessed toward the leading edge 131, and an included angle AOB formed between a recessed vertex a of the noise reduction notch 150, a junction B of the trailing edge 133 and the hub 110, and a circle center O of the hub 110 is between 48 ° and 56 °. Through setting up the notch 150 of making an uproar, and the notch 150 of making an uproar satisfies certain size angle requirement, has increased fan blade trailing edge 133 gradient and sunken degree of depth, can improve the pressure gradient distribution in the fan blade runner effectively, restrain the secondary flow and weaken the wake and flow to the influence of low reaches to reduce the static pressure of blade 130, reduce the consumptive material volume, and reduce the energy consumption, and make it can effectively improve the internal flow characteristic of blade 130 and reduce aerodynamic noise.
It should be noted that the concave vertex a mentioned in the present embodiment refers to the deepest point of the noise reduction notch 150, i.e., the farthest point from the trailing edge 133. Meanwhile, the hub 110 is cylindrical, and the center of the cylinder is the center point of the hub 110. Also, the junction of the trailing edge 133 with the hub 110 refers to the starting point of the trailing edge 133 in the radial direction. The deepest point of the noise reduction notch 150, the initial point of the tail edge 133 and the included angle formed by the center of the hub 110 are limited, the center of the hub 110 and the initial point of the tail edge 133 are fixed point positions, the depth of the noise reduction notch 150 and the gradient of the tail edge 133 are limited by limiting the range of the included angle, and in the range of the angle, the depth of the noise reduction notch 150 and the gradient of the tail edge 133 are both in the optimal range, so that the pressure gradient distribution in a fan blade flow channel can be effectively improved, the static pressure of the blade 130 is reduced, the energy consumption is reduced, meanwhile, the weight reduction function is realized by arranging the notch, and the consumption of materials is reduced. And the secondary flow can be inhibited and the influence of the wake on the downstream flow can be weakened, thereby reducing the aerodynamic noise.
In this embodiment, an included angle ═ AOB formed between a concave vertex a of the noise reduction notch 150, a junction point B of the trailing edge 133 and the hub 110, and a circle center O of the hub 110 is 50 °, wherein the ═ AOB uses the circle center O of the hub 110 as a vertex point, and can be known through a simulation test and an actual product test, when the ═ AOB is 50 °, noise of the fan can be minimized, and simultaneously energy consumption is greatly reduced compared with a contrast fan without the notch.
In the embodiment, an included angle ^ AOC formed between a concave vertex A of the noise reduction notch 150, a joint C of one end of the noise reduction notch 150 close to the hub 110 and the tail edge 133 and a circle center O of the hub 110 is between 2.9 and 35.1 degrees. By defining the starting end position of the noise reduction notch 150, the internal flow characteristics of the blade 130 can be further improved and aerodynamic noise can be reduced, thereby performing a noise reduction function.
It should be noted that, in this embodiment, the trailing edge 133 is entirely arc-shaped, and a noise reduction notch 150 is formed in the middle-rear section, the noise reduction notch 150 penetrates through the entire blade, and the notch is relatively perpendicular to the surface of the blade, so that the trailing edge 133 is partially interrupted by the noise reduction notch 150.
In the present embodiment, an included angle ≧ AOC formed between the recessed vertex a of the noise reduction notch 150, a junction C of one end of the noise reduction notch 150 close to the hub 110 and the trailing edge 133, and the center O of the hub 110 is 13.6 °. The angle AOC is known through simulation tests and actual product tests by taking the circle center O of the hub 110 as a vertex point, and when the angle AOC is 13.6 degrees, the noise and the energy consumption of the fan are both at a lower level. Of course, the setting of &herealso needs to be determined according to the size of the blade 130 and the width of the noise reduction notch 150, so that the fan is in the optimal state.
In the embodiment, an included angle ^ AOD formed between a concave vertex A of the noise reduction notch 150, a joint D of one end of the noise reduction notch 150, which is far away from the hub 110, and the tail edge 133 and a circle center O of the hub 110 is between 4.4 and 14.4 degrees. By defining the end portion position of the noise reduction notch 150, the internal flow characteristic of the blade 130 can be further improved and aerodynamic noise can be reduced, thereby performing a noise reduction function.
In the present embodiment, an included angle ≧ AOD formed between the recessed vertex a of the noise reduction notch 150, a junction D of the end of the noise reduction notch 150 away from the hub 110 and the trailing edge 133, and the center O of the hub 110 is 5.5 °. The angle AOD is known by a simulation test and an actual product test by taking the circle center O of the hub 110 as a vertex point, and when the angle AOD is 5.5 degrees, the noise and the energy consumption of the fan are both at a lower level. Of course, the setting of the angle AOD also needs to be determined according to the size of the blade 130 and the width of the noise reduction notch 150, so that the fan blade is in the optimal state.
It should be noted that, here, the noise reduction notch 150 is in an irregular U shape, and has two opposite end points along the extending direction of the trailing edge 133, wherein one end point is a joint point C, in the inside-out direction, the joint point C is a recessed starting point of the noise reduction notch 150, the other end point is a joint point D, in the inside-out direction, the joint point D is a recessed ending point of the noise reduction notch 150, and the recessed vertex is located between the joint point C and the joint point D.
It should be noted that the edge line of the noise reduction notch 150 in this embodiment is arc-shaped and can smoothly transition with the trailing edge 133, and in other preferred embodiments, the noise reduction notch 150 can also be a rectangular or triangular notch directly.
In the present embodiment, the distance L1 between the concave apex A of the noise attenuation notch 150 and the center O of the hub 110 is 1/2-6/7 of the distance L2 between the outboard end of the blade 130 and the center O of the hub 110. By providing the noise reduction notch 150 in the second half of the trailing edge 133, the rotor trail can be effectively reduced, and the flow pressure characteristic changes little, reducing aerodynamic noise and improving tone quality. Meanwhile, the influence of the noise reduction notch 150 on the structural strength of the blade 130 can be reduced by arranging the rear half section, and the structural strength of the blade 130 is ensured to meet the requirement.
It should be noted that, since the noise reduction notch 150 is in the shape of an irregular U, the position of the concave vertex a in this embodiment is used to calibrate the position of the noise reduction notch 150, wherein the farther the concave vertex a is from the center O of the hub 110, the farther the noise reduction notch 150 is from the center O of the hub 110 can be determined.
In the present embodiment, a distance L1 between a concave apex a of the noise reduction notch 150 and a center O of the hub 110 is 5/7 of a distance L2 between an outboard end of the blade 130 and the center O of the hub 110. By directly limiting the position of the recess apex A in this embodiment, the noise reduction notch 150 is closer to the outer end of the blade 130.
It should be noted that, in this embodiment, a certain distance is provided between the joint D of the noise reduction notch 150 and the trailing edge 133 and the outer end of the fan blade, for example, the distance between the joint D and the outer end of the fan blade is between 5 mm and 20mm, so that the joint D does not excessively approach the outer end of the fan blade to affect the structural strength of the fan blade, and the air leakage phenomenon caused by the flaring of the noise reduction notch 150 to the outer end of the fan blade is avoided.
In this embodiment, a rib 170 is further disposed on one side of the blade 130 close to the hub 110, one end of the rib 170 is connected to the outer circumferential surface of the hub 110, and the other end extends outward. Specifically, two reinforcing ribs 170 are provided on each blade 130, the two reinforcing ribs 170 extend radially outward from the outer circumferential surface of the hub 110, and the connecting strength of the blade 130 can be effectively enhanced by additionally providing the reinforcing ribs 170 between the blade 130 and the hub 110.
In the present embodiment, the hub 110 has a hollow cylindrical shape, and an end plate 111 is integrally provided at one end, and a mounting hole through which an output shaft of the power supply unit is passed is opened at a central position of the end plate 111. Still be provided with many integrative ribs 113 that set up on wheel hub 110's inside wall, every rib 113 all extends to the middle part position of end panel 111 to increased wheel hub 110's structural strength on the one hand, increased the joint strength between wheel hub 110 and the end panel 111 on the other hand.
In summary, the embodiment provides an axial flow fan blade 100, wherein a noise reduction notch 150 recessed toward the leading edge 131 is disposed at the trailing edge 133 of the blade 130, and an included angle AOB formed between a recessed vertex a of the noise reduction notch 150, a junction B of the trailing edge 133 and the hub 110, and a circle center O of the hub 110 is 50 °. Through setting up the notch 150 of making an uproar, and the notch 150 of making an uproar satisfies certain size angle requirement, has increased fan blade trailing edge 133 gradient and sunken degree of depth, can improve the pressure gradient distribution in the fan blade runner effectively, restrain the secondary flow and weaken the wake and flow to the influence of low reaches to reduce the static pressure of blade 130, reduce the consumptive material volume, and reduce the energy consumption, and make it can effectively improve the internal flow characteristic of blade 130 and reduce aerodynamic noise.
Second embodiment
The present embodiment provides an air conditioner, which includes an air conditioner casing, a motor and an axial flow fan blade 100, wherein the basic structure and principle of the axial flow fan blade 100 and the generated technical effects are the same as those of the first embodiment, and for the sake of brief description, corresponding contents in the first embodiment may be referred to where this embodiment is not mentioned in part.
In the embodiment, the axial flow fan blade 100 comprises a hub 110 and a plurality of blades 130 arranged on the periphery of the hub 110, each blade 130 has a leading edge 131 and a trailing edge 133 which are opposite in the airflow direction, the leading edge 131 and the trailing edge 133 both extend from the outer end of the blade 130 to the hub 110, a noise reduction notch 150 which is recessed towards the leading edge 131 is arranged at the trailing edge 133, an included angle AOB formed by a recessed vertex a of the noise reduction notch 150, a junction point B of the trailing edge 133 and the hub 110 and a circle center O of the hub 110 is between 48 ° and 56 °, the motor and the axial flow fan blade 100 are both arranged in an air-conditioning casing, and the hub 110 is arranged on an output shaft of the motor.
In this embodiment, the air conditioner is an air conditioner external unit, a fan cavity is formed in an air conditioner shell, the motor is arranged in the fan cavity, the hub 110 of the axial flow fan blade 100 is in transmission connection with an output shaft of the motor, the motor and the axial flow fan blade 100 jointly form a fan structure of the air conditioner external unit, and other parts and structures of the air conditioner external unit can refer to the existing air conditioner external unit.
In the embodiment, the shape of the blade 130 of the axial flow fan blade 100 is improved, and the structural parameters of the blade are limited, so that the internal flow characteristic of the axial flow fan blade 100 is effectively improved, and the aerodynamic noise and the energy consumption of the fan are reduced.
Although the present invention is disclosed above, the present invention is not limited thereto. Various changes and modifications may be effected therein by one skilled in the art without departing from the spirit and scope of the utility model as defined in the appended claims.
Claims (10)
1. The axial flow fan blade is characterized by comprising a hub (110) and a plurality of blades (130) arranged on the periphery of the hub (110), wherein each blade (130) is provided with a leading edge (131) and a trailing edge (133) which are opposite in the airflow direction, the leading edge (131) and the trailing edge (133) both extend to the hub (110) from the outer end of the blade (130), a noise reduction notch (150) which is sunken towards the leading edge (131) is arranged at the trailing edge (133), and an included angle AOB formed among a sunken vertex A of the noise reduction notch (150), a joint B of the trailing edge (133) and the hub (110) and a circle center O of the hub (110) is between 48 and 56 degrees.
2. The axial-flow fan blade as claimed in claim 1, wherein an included angle AOB formed between a concave vertex a of the noise reduction notch (150), a junction point B of the trailing edge (133) and the hub (110), and a circle center O of the hub (110) is 50 °.
3. The axial-flow fan blade as claimed in claim 1, wherein an included angle AOC formed between a concave vertex A of the noise reduction notch (150), a junction C of one end of the noise reduction notch (150) close to the hub (110) and the trailing edge (133), and a circle center O of the hub (110) is between 2.9 ° and 35.1 °.
4. The axial-flow fan blade according to claim 3, wherein an included angle AOC formed between a concave vertex A of the noise reduction notch (150), a joint C of one end of the noise reduction notch (150) close to the hub (110) and the trailing edge (133) and a circle center O of the hub (110) is 13.6 degrees.
5. The axial-flow fan blade as claimed in claim 1, wherein an included angle AOD formed between a concave vertex A of the noise reduction notch (150), a junction D of one end of the noise reduction notch (150) far away from the hub (110) and the trailing edge (133), and a circle center O of the hub (110) is between 4.4 ° and 14.4 °.
6. The axial-flow fan blade according to claim 5, wherein an included angle AOD formed between a concave vertex A of the noise reduction notch (150), a junction D of one end of the noise reduction notch (150) far away from the hub (110) and the trailing edge (133), and a circle center O of the hub (110) is 5.5 degrees.
7. The axial-flow fan blade according to claim 1, wherein a distance L1 between a concave vertex a of the noise reduction notch (150) and a center O of the hub (110) is 1/2-6/7 of a distance L2 between an outboard end of the blade (130) and the center O of the hub (110).
8. The axial-flow fan blade according to claim 7, wherein a distance L1 between a concave vertex A of the noise reduction notch (150) and a center O of the hub (110) is 5/7 of a distance L2 between an outboard end of the blade (130) and the center O of the hub (110).
9. The axial-flow fan blade according to claim 1, wherein a reinforcing rib (170) is further disposed on one side of the blade (130) close to the hub (110), one end of the reinforcing rib (170) is connected to the outer circumferential surface of the hub (110), and the other end of the reinforcing rib extends outwards.
10. An air conditioner characterized by comprising the axial-flow fan blade as claimed in any one of claims 1 to 9.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202122007780.0U CN215927905U (en) | 2021-08-24 | 2021-08-24 | Axial flow fan blade and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202122007780.0U CN215927905U (en) | 2021-08-24 | 2021-08-24 | Axial flow fan blade and air conditioner |
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| CN215927905U true CN215927905U (en) | 2022-03-01 |
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| CN202122007780.0U Active CN215927905U (en) | 2021-08-24 | 2021-08-24 | Axial flow fan blade and air conditioner |
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- 2021-08-24 CN CN202122007780.0U patent/CN215927905U/en active Active
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