CN114688049A

CN114688049A - Fan subassembly and air conditioner

Info

Publication number: CN114688049A
Application number: CN202011560110.5A
Authority: CN
Inventors: 闫嘉超; 张冀喆; 薛永升; 胡小文; 陈鹏; 胡斯特
Original assignee: Midea Group Co Ltd; Guangdong Midea White Goods Technology Innovation Center Co Ltd
Current assignee: Midea Group Co Ltd; Guangdong Midea White Goods Technology Innovation Center Co Ltd
Priority date: 2020-12-25
Filing date: 2020-12-25
Publication date: 2022-07-01
Anticipated expiration: 2040-12-25
Also published as: CN114688049B

Abstract

The invention provides a fan assembly and an air conditioner, wherein the fan assembly comprises: the air duct comprises an air inlet and an air outlet which are communicated; the first-stage fan blades are arranged at the air inlet and comprise an air inlet section and an air supply section which are connected along the rotating axial direction of the first-stage fan blades, the air inlet section is positioned outside the air channel, and the air supply section is positioned in the air channel; the second-stage fan blades are arranged in the air duct and close to the air outlet; the driving assembly is respectively connected with the first-stage fan blade and the second-stage fan blade and is configured to drive the first-stage fan blade and the second-stage fan blade to rotate; the absolute value of the bend angle of the camber line of the first-stage fan blade in the air inlet section is smaller than that of the bend angle in the air supply section. The fan assembly provided by the invention can improve the air supply capacity of the fan assembly and reduce the operation noise of the fan assembly.

Description

Fan assembly and air conditioner

Technical Field

The invention relates to the technical field of air conditioners, in particular to a fan assembly and an air conditioner.

Background

In the related art, the noise reduction scheme of the fan assembly is divided into two types, one is a scheme for reducing the external noise of the air conditioner by adding a sound insulation and absorption material, and the other is a scheme for reducing the external noise level by controlling the source generating the noise. The former tends to increase the cost of the filler material, the sound damping structure, and the latter requires a higher level of design.

The scheme often uses the former as the owner at present, inhales the sound device through giving sound insulation and reduces the noise level, for example increases the puigging outside the wind channel, devices such as muffler reach the designing requirement, and control the source of noise, does not need extra device, can realize falling the mesh of making an uproar on the basis of the increase cost that does not show significantly. However, this will increase the production cost, and the additional soundproof layer will increase the production cost, reducing the market competitiveness; the use and maintenance cost is increased, and in use, the sound insulation layer is peeled off due to adhesion, so that the noise reduction level is influenced, and the use cost of a user is increased; the additional sound insulation layer can increase the volume and the weight of the product and reduce the application range of the product.

Disclosure of Invention

The present invention is directed to solving at least one of the problems of the prior art.

To this end, a first aspect of the invention provides a fan assembly.

A second aspect of the present invention provides an air conditioner.

A first aspect of the present invention provides a fan assembly comprising: the air duct comprises an air inlet and an air outlet which are communicated; the first-stage fan blades are arranged at the air inlet and comprise an air inlet section and an air supply section which are connected along the rotating axial direction of the first-stage fan blades, the air inlet section is positioned outside the air channel, and the air supply section is positioned in the air channel; the second-stage fan blade is arranged in the air duct and is close to the air outlet; the driving assembly is respectively connected with the first-stage fan blade and the second-stage fan blade and is configured to drive the first-stage fan blade and the second-stage fan blade to rotate; the absolute value of the bend angle of the camber line of the first-stage fan blade in the air inlet section is smaller than that of the bend angle in the air supply section.

The fan assembly provided by the invention comprises an air duct, a first-stage fan blade, a second-stage fan blade and a driving assembly. Wherein, the setting of first order flabellum is in the air intake department in wind channel, and the second level flabellum sets up in the wind channel to close on in the air outlet, drive assembly can drive first order flabellum and second level flabellum rotation respectively in the operation, make the air current under the combined action of first order flabellum and second level flabellum, in entering into the wind channel from the air intake, and after first back through first order flabellum and second level flabellum, blow off from the air outlet. And the first-stage fan blade is used as an upstream fan blade, the second-stage fan blade is used as a downstream fan blade, and the first-stage fan blade and the second-stage fan blade are matched to enable the air flow to be accelerated and pressurized under the combined action of the two stages of fan blades when passing through the air duct, so that the wind power is enhanced, the wind resistance is improved, and the air exhaust capability of the air flow through the external exhaust pipe is greatly enhanced.

In addition, in the rotating shaft direction of the first-stage fan blades, the first-stage fan blades comprise an air inlet section and an air supply section which are connected, the air inlet section and the air supply section use an air inlet as a boundary, the air inlet section is positioned outside the air channel, and the air supply section is positioned inside the air channel; i.e. the process is repeated. The air duct is arranged at the periphery of the air supply section of the first-stage fan blade in a wrapping mode. The absolute value of the bend angle of the camber line of the first-stage fan blade at the air inlet section is smaller than that of the bend angle at the air supply section. By the design, on one hand, the air supply capacity of the first-stage fan blade can be ensured through the air inlet section, the noise generated when the air flows in the air channel is reduced, particularly, the noise of the air flow between the first-stage fan blade and the second-stage fan blade can be reduced, on the other hand, air inlet is realized through the air inlet section, and the bending angle of the camber line of the first-stage fan blade at the air inlet section can be reduced, so that the improvement amount of the first-stage fan blade is reduced while the energy efficiency and the noise are reduced, and the manufacturing and processing difficulty of the first-stage fan blade is further reduced.

The fan assembly provided by the invention has the advantages that the acceleration and the pressurization of airflow are realized under the combined action of the two stages of fan blades when the airflow passes through the air duct, so that the wind power is enhanced, the wind resistance is improved, the working noise of the fan assembly is further reduced through the structural optimization of the first stage fan blades, the improvement amount of the first stage fan blades is reduced, and the manufacturing and processing difficulty of the first stage fan blades is further reduced.

Specifically, the definition of the mean camber line and the bend angle is explained as follows: any fan blade comprises a suction surface and a pressure surface which are opposite, and the blade section of the fan blade can be obtained by cutting the fan blade by a plane parallel to the rotation axis of the fan blade. In the blade profile section of the fan blade, the arc line with the same distance to the arc line of the suction surface and the arc line of the pressure surface is the mean arc line of the fan blade. A tangent to the point (the tangent extends toward the tip side) may be obtained at any point on the mean camber line of the fan blade, and an angle formed by the mean camber line of the fan blade and the tangent to the point in the extending direction of the tangent is defined as an angle of the mean camber line of the fan blade at the point. The angular difference between any two points on the mean camber line of the fan blade is defined as the bending angle of the mean camber line of the fan blade between the two end points.

A second aspect of the present invention provides an air conditioner comprising: a fan assembly as in the first aspect of the invention.

The air conditioner provided by the invention comprises the fan assembly according to the first aspect of the invention. Therefore, all the advantages of the fan assembly are achieved, and are not discussed in detail herein.

Additional aspects and advantages of the invention will be set forth in part in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention.

Drawings

The above and/or additional aspects and advantages of the present invention will become apparent and readily appreciated from the following description of the embodiments, taken in conjunction with the accompanying drawings of which:

FIG. 1 is a schematic structural view of a fan assembly (hidden drive assembly) according to one embodiment of the present invention;

FIG. 2 is a front view of the fan assembly of the embodiment shown in FIG. 1;

FIG. 3 is a cross-sectional view of a fan assembly of the embodiment shown in FIG. 1;

FIG. 4 is a simplified illustration of a cross-sectional view of the fan assembly of the embodiment shown in FIG. 3;

FIG. 5 is a schematic view of a fan blade;

FIG. 6 is a cross-sectional view of the fan blade of FIG. 5 taken along line C-C;

FIG. 7 is a blade-type cross-sectional view of a first stage fan blade in a fan assembly according to one embodiment of the present disclosure;

FIG. 8 is a blade-shaped cross-sectional view of a second stage fan blade in a fan assembly according to one embodiment of the present invention;

FIG. 9 is a sectional view of the first stage fan blades and the second stage fan blades of the fan assembly of one embodiment of the present invention;

fig. 10 is a front view of an air conditioner according to an embodiment of the present invention;

fig. 11 is a sectional view of the air conditioner of the embodiment shown in fig. 10.

Wherein, the correspondence between the reference numbers and the part names in fig. 1 to 11 is:

100 fan components, 102 air ducts, 104 air inlets, 106 air outlets, 108 first-stage fan blades, 110 air inlet sections, 112 air supply sections, 114 second-stage fan blades, 116 first motors, 118 second motors, 120 air inlet sections, 122 transition sections, 124 air outlet sections, 126 air guide rings, 128 driving components, 130 first areas, 132 second areas, 134 third areas, 136 fourth areas, 202 machine shells, 204 heat exchangers, 206 first supports and 208 second supports.

Detailed Description

In order that the above objects, features and advantages of the present invention can be more clearly understood, a more particular description of the invention will be rendered by reference to the appended drawings. It should be noted that the embodiments and features of the embodiments of the present application may be combined with each other without conflict.

In the following description, numerous specific details are set forth in order to provide a thorough understanding of the present invention, however, the present invention may be practiced otherwise than as specifically described herein, and thus the scope of the present invention is not limited by the specific embodiments disclosed below.

A fan assembly 100 and an air conditioner provided according to some embodiments of the present invention will be described with reference to fig. 1 to 11, in which arrows indicate the direction of air flow.

As shown in fig. 1, fig. 2, fig. 3 and fig. 10, in a first aspect, the present invention provides a fan assembly 100, including: the air duct 102 comprises an air inlet 104 and an air outlet 106 which are communicated with each other; the first-stage fan blades 108 are arranged at the air inlet 104, and along the rotating axial direction of the first-stage fan blades 108, the first-stage fan blades 108 comprise an air inlet section 110 and an air supply section 112 which are connected, the air inlet section 110 is positioned outside the air duct 102, and the air supply section 112 is positioned in the air duct 102; a second stage fan blade 114 disposed in the air duct 102 and close to the air outlet 106; a drive assembly 128 coupled to the first stage blade 108 and the second stage blade 114, respectively, and configured to drive the first stage blade 108 and the second stage blade 114 in rotation; the absolute value of the bend angle of the camber line of the first-stage fan blade 108 in the air inlet section 110 is smaller than that in the air supply section 112.

The fan assembly 100 of the present invention includes an air duct 102, first stage blades 108, second stage blades 114, and a drive assembly 128. The first-stage blades 108 are disposed in the air duct 102 and disposed adjacent to the air inlet 104, the second-stage blades 114 are disposed at the air outlet 106 of the air duct 102, and the driving assembly 128 can respectively drive the first-stage blades 108 and the second-stage blades 114 to rotate during operation, so that the air flow enters the air duct 102 from the air inlet 104 under the combined action of the first-stage blades 108 and the second-stage blades 114, and is blown out from the air outlet 106 after passing through the first-stage blades 108 and the second-stage blades 114. Moreover, the first-stage fan blades 108 are used as upstream fan blades, the second-stage fan blades 114 are used as downstream fan blades, and the cooperation of the first-stage fan blades 108 and the second-stage fan blades 114 enables the air flow to be accelerated and pressurized under the combined action of the two stages of fan blades when passing through the air duct 102, so that the wind power is enhanced, the wind resistance is improved, and the air exhaust capability of the air flow through the external exhaust pipe is greatly enhanced.

In addition, as shown in fig. 4 and fig. 7, in the rotation axis direction of the first-stage blades 108, the first-stage blades 108 include an air inlet section 110 and an air supply section 112 connected to each other, the air inlet section 110 and the air supply section 112 are defined by the air inlet 104, the air inlet section 110 is located outside the air duct 102, and the air section 112 is located inside the air duct 102; i.e. the process is repeated. The air duct 102 is disposed around the air supply section 112 of the first stage fan 108.

The camber line of the first stage fan blade 108 has a smaller absolute value of the bend angle at the air intake section 110 than the bend angle at the air blowing section 112. By the design, on one hand, the air supply capacity of the first-stage fan blades 108 can be ensured through the air inlet section 110, noise generated when air flows in the air duct 102 is reduced, particularly, noise of air flow between the first-stage fan blades 108 and the second-stage fan blades 114 can be reduced, on the other hand, air inlet is realized through the air inlet section 110, and the bending angle of the middle arc line of the first-stage fan blades 108 at the air inlet section 110 can be reduced, so that the energy efficiency and the noise are ensured, the improvement amount of the first-stage fan blades 108 is reduced, and the manufacturing and processing difficulty of the first-stage fan blades 108 is reduced.

According to the fan assembly 100 provided by the invention, the air flow is accelerated and pressurized under the combined action of the two stages of fan blades when passing through the air duct 102, so that the wind power is enhanced, the wind resistance is improved, the working noise of the fan assembly 100 is further reduced by optimizing the structure of the first stage fan blade 108, the improvement amount of the first stage fan blade 108 is reduced, and the manufacturing and processing difficulty of the first stage fan blade 108 is further reduced.

In particular, the blade comprises opposite suction and pressure surfaces, and the blade profile section can be obtained by cutting the blade in a plane parallel to the axis of rotation of the blade, as shown in fig. 5 and 6, and the camber line L3 is the arc in the blade profile section of the blade, as shown in fig. 6, with equal distances to the suction surface arc line L1 and the pressure surface arc line L2. A tangent to this point (a tangent extending toward the tip side) may be obtained at any point on the camber line L3 of the blade, and the included angle formed between the camber line L3 of the blade and the tangent to this point in the extending direction of the tangent is defined as the angle of the camber line L3 of the blade at this point. The angular difference between any two points on camber line L3 of the blade is defined as the bend angle between the two points of camber line L3 of the blade.

That is, as shown in fig. 6, two points are taken on the camber line L2 of the blade, each being O₁And O₂Camber line L2 of fan blade is at O₁Is alpha 1, the mean camber line L2 of the fan blade is O₂Is α 2. Then, camber line L2 of the fan blade is at O₁To O₂The angle between the corners is alpha 1-alpha 2.

Therefore, as shown in fig. 7, for the present embodiment, the absolute values of the bending angles of the camber line of the first stage blade 108 at the air inlet section 110 are | β 1 — β 2 |; the camber line of the first stage fan blade 108 is at the bend angle of the blowing section 112, i.e. β 2- β 3. Wherein, P1 is the starting point of the mean camber line of the first-stage fan blade 108 at the air intake section 110, β 1 is the angle of the mean camber line of the first-stage fan blade 108 at P1; p2 is the end point of the mean camber line of the first stage blade 108 at the air intake section 110, β 2 is the angle of the mean camber line of the first stage blade 108 at P2; p3 is the end point of the mean camber line of the first stage blade 108 at the blowing section 112, β 3 is the angle of the mean camber line of the first stage blade 108 at P3; A-A represents the boundary between the air intake section 110 and the air delivery section 112.

In particular, since the mean camber line of the first-stage blades 108 is a continuous line, P2 is the end point of the mean camber line of the first-stage blades 108 at the air intake section 110, and is the beginning point of the mean camber line of the first-stage blades 108 at the air supply section 112.

In one embodiment of the present invention, as shown in fig. 7, the camber line of the first stage blades 108 is greater than 0 ° and less than or equal to 10 ° at the bend angle of the air intake section 110.

In this embodiment, as shown in FIG. 7, the camber line of the first stage fan blade 108 has a bend angle β 1- β 2 at the air intake section 110, and satisfies 0 ° < β 1- β 2 ≦ 10 °. In this embodiment, the bending angle of the mean camber line of the first-stage fan blade 108 in the air inlet section 110 is optimized, and the value range of the bending angle of the mean camber line of the first-stage fan blade 108 in the air inlet section 110 is ensured to be 0 ° to 10 °. It is noted that, during operation of fan assembly 100, first stage fan blades 108 are rotated by drive assembly 128 and may draw external air from the air inlet into air duct 102.

The range of beta 1-beta 2 is designed to be within 0-10 degrees, so that the suction force of the first-stage fan blades 108 to the air in the external environment can be effectively improved, the energy efficiency of the fan assembly 100 is greatly improved, the air inlet sections 110 of the first-stage fan blades 108 are matched with the air inlets 104 of the air channels 102, and the air suction and air supply performance of the fan assembly 100 is guaranteed under the condition that too large bending angles are not needed.

In a specific embodiment, the bend angle of the mean camber line of the first-stage fan blade 108 at the air intake section 110 is β 1- β 2, and the value of β 1- β 2 may be 2 °, 4 °, 5 °, 6 °, 7 °, 10 °, and the like.

In one embodiment of the present invention, as shown in FIG. 6, the camber line of the first stage blades 108 is greater than or equal to-10 ° and less than 0 ° at the bend angle of the intake section 110.

In this embodiment, as shown in fig. 7, the camber line of the first stage fan blade 108 has a bend angle β 1 to β 2 at the air intake section 110, and satisfies-10 ° ≦ β 1 to β 2 < 0 °. In this embodiment, the bending angle of the mean arc line of the first-stage fan blade 108 in the air inlet section 110 is optimized, and the value range of the bending angle of the mean arc line of the first-stage fan blade 108 in the air inlet section 110 is ensured to be-10 ° to 0 °. It is noted that, during operation of fan assembly 100, first stage fan blades 108 are rotated by drive assembly 128 and may draw external air from the air inlet into the interior of air chute 102.

The range of beta 1-beta 2 from-10 degrees to 0 degrees is designed, so that the suction force of the first-stage fan blades 108 to the air in the external environment can be effectively improved, the energy efficiency of the fan assembly 100 is greatly improved, the air inlet sections 110 of the first-stage fan blades 108 are matched with the air inlets 104 of the air channels 102, and the air suction and air supply performance of the fan assembly 100 is guaranteed under the condition that too large bending angles are not needed.

In an embodiment, the camber angle of the camber line of the first-stage fan blade 108 at the air inlet section 110 is β 1- β 2, and the value of β 1- β 2 may be-10 °, -8 °, -6 °, -5 °, -4 °, -2 °, etc.

In particular, the positive and negative conditions of the camber line of the first stage fan blade 108 at the bend angle of the intake section 110 are explained as follows: the camber line of the first stage blade 108 at P1 and P2 may be the same or different. When the camber lines of the first-stage fan blades 108 are the same at the positions P1 and P2, the camber line satisfies the condition that 0 DEG & lt beta 1-beta 2 & lt 10 DEG (namely the condition shown in FIG. 6); when the camber lines of the first stage blades 108 are different between the bending at P1 and the bending at P2, the camber line satisfies-10 DEG.ltoreq.1-beta.2 < 0 DEG (this is not shown in the figure).

In one embodiment of the present invention, as shown in FIG. 7, the camber line of the first stage blades 108 is greater than 0 ° and less than or equal to 45 ° at the flow delivery segment 112.

In this embodiment, as shown in fig. 7, the camber line of the first stage fan blade 108 has a bend angle β 2- β 3 in the blowing section 112, and satisfies 0 ° ≦ β 2- β 3 ≦ 45 °. In this embodiment, the bending angle of the mean arc line of the first-stage fan blade 108 in the air supply section 112 is optimized, and the value range of the bending angle β 2- β 3 of the mean arc line of the first-stage fan blade 108 in the air supply section 112 is ensured to be 0 ° to 45 °. It is noted that, when the fan assembly 100 operates, the first-stage blades 108 and the second-stage blades 114 cooperate, and after the airflow is sucked into the air duct 102 by the air inlet section 110 of the first-stage blades 108, the airflow continues to flow to the second-stage blades 114 under the action of the air inlet section 110 of the first-stage blades 108.

The design is that the beta 2-beta 3 is in the range from 0 degree to 45 degrees, the speed and the rotary direction of the air flow flowing to the second-stage fan blades 114 can be effectively controlled, on one hand, the air flow is ensured to be matched with the structure of the air channel 102 when flowing to the second-stage fan blades 114 from the air supply section 112, and the air flow can smoothly enter the second-stage fan blades 114 after flowing out from the air supply section 112, so that the resistance of the air flow blowing to the second-stage fan blades 114 is reduced, the air supply of the air supply section 112 can be more smooth, the probability of backflow is reduced, and the noise of the air flow when flowing inside the air channel 102 is also effectively reduced.

In a specific embodiment, the value of β 1- β 2 may be 10 °, 15 °, 20 °, 25 °, 30 °, 35 °, 40 °, 45 °, or the like.

In one embodiment of the present invention, as shown in FIG. 4, the ratio of the height of the air intake section 110 to the total height of the first stage blades 108 along the rotational axis of the first stage blades 108 is greater than or equal to 40% and less than or equal to 70%.

In this embodiment, as shown in fig. 4, the air duct 102 covers the air supply section 112 of the first stage fan 108, and the air inlet section 110 of the first stage fan 108 protrudes from the air inlet 104 and is located outside the air duct 102. As shown in fig. 4, the straight line a-a is opposite to the air inlet 104, the portion of the first stage blades 108 on the left side of the straight line a-a is the air inlet section 110, and the portion of the first stage blades 108 on the right side of the straight line a-a is the air supply section 112. In addition, along the rotating axial direction of the first-stage fan blades 108, the height of the air inlet section 110 is H1, the height of the air supply section 112 is H2, the total height of the first-stage fan blades 108 is H1+ H2, and the requirements that the ratio of H1/H1+ H2 is more than or equal to 40% and less than or equal to 70% are met.

Specifically, the ratio of the height of the air intake section 110 to the total height of the first stage blades 108 is designed to be 40% to 70%, that is, the ratio of the height of the first stage blades 108 protruding from the air inlet 104 in the air blowing direction of the air duct 102 is designed. The first-stage fan blades 108 are designed to protrude out of the air inlet 104, the ratio of the height of the first-stage fan blades 108 to the total height of the first-stage fan blades 108 is 40% to 70%, beta 2-beta 3 is matched to be 0-45 degrees, a good rectification effect can be achieved on air flow, the air flow can smoothly flow from the first-stage fan blades 108 to the second-stage fan blades 114, smooth transition of the air flow on the two stages of fan blades is achieved, resistance of the air flow when the air flow blows to the second-stage fan blades 114 is reduced, air supply of the air supply section 112 can be made to be smoother, the probability of backflow is reduced, and noise of the air flow when the air flow flows in the air duct 102 is effectively reduced.

In an embodiment, the ratio of the height H1 of the air intake section 110 to the total height H1+ H2 of the first stage fan blades 108 may be 40%, 50%, 60%, 70%, etc.

In one embodiment of the present invention, as shown in FIG. 4, the ratio of the height of the blowing section 112 to the total height of the first stage blades 108 along the rotational axis of the first stage blades 108 is greater than or equal to 30% and less than or equal to 60%.

In this embodiment, as shown in fig. 4, the ratio of the height H2 of the blowing section 112 to the total height H1+ H2 of the first stage fan blades 108 is designed to be 30% to 60%, that is, the ratio of the height of the first stage fan blades 108 inside the air duct 102 in the blowing direction of the air duct 102 is designed. The ratio of H2 to H1+ H2 is designed to be 30% to 60%, and β 1- β 2 is designed to be 0 ° to 10 °, so as to ensure the flow rate and the rotational direction of the airflow flowing in the air supply section 112, and ensure the airflow to be matched with the structure of the air duct 102 when flowing from the air supply section 112 to the second stage fan blades 114 in the other direction, and ensure the airflow to smoothly enter the second stage fan blades 114 after flowing out from the air supply section 112, thereby reducing the resistance when blowing to the second stage fan blades 114, making the air supply of the air supply section 112 smoother, reducing the probability of backflow, and effectively reducing the noise when the airflow flows in the air duct 102.

In specific embodiments, the ratio of H2 to H1+ H2 may be 40%, 50%, 60%, 70%, etc.

In one embodiment of the present invention, as shown in fig. 4, the direction perpendicular to the rotation axis of the first stage blade 108 is taken as the radial direction of the first stage blade 108, and along the radial direction of the first stage blade 108, the first stage blade 108 includes a first region 130 and a second region 132, the first region 130 is located at the periphery of the second region 132; in the first region 130, the camber angle of the first stage blades 108 in the air intake section 110 is smaller than the camber angle in the air delivery section 112.

In this embodiment, as shown in FIG. 4, the radial direction of the first stage blade 108 is perpendicular to the axis of rotation of the first stage blade 108, and the radial center of the first stage blade 108 is connected to the drive assembly 128, so that the position of the radial opening into the blade tip is the main active area. Therefore, in the present embodiment, the first stage blade 108 is divided into a first region 130 and a second region 132 along the radial direction of the first stage blade 108, and the first region 130 is located at the periphery of the second region 132 and is closer to the blade tip, so that the second region 132 is the main active region. On the basis, the present embodiment only modifies the portion of the first region 130, so that the absolute value of the bending angle of the mean camber line of the first-stage fan blade 108 in the air intake section 110 is smaller than the bending angle in the air supply section 112 in the first region 130. In this way, the area of improvement to the first stage blade 108 may be reduced, thereby reducing the difficulty of machining and manufacturing.

In one embodiment of the present invention, as shown in FIG. 8, the ratio of the length of the second region 132 to the total length of the first region 130 and the second region 132 along the radial direction of the first stage blade 108 is greater than or equal to 65% and less than or equal to 100%.

In this embodiment, as shown in FIG. 9, the second region 132 has a length D1 and the total length of the first and

second regions

130 and 132 is D2 and satisfies 65% ≦ D1/D2 ≦ 100% in the radial direction of the first stage fan blades 108. Like this, through the radial proportion of first region 130 and second region 132 at first-stage flabellum 108 of rational division, rational design is to first-stage flabellum 108 in radial optimization area, can guarantee the energy efficiency and the noise reduction effect of first-stage flabellum 108 self on the one hand, and on the other hand can reduce staff's the work degree of difficulty and work load.

In specific embodiments, the value of D1/D2 may be 65%, 70%, 75%, 80%, 85%, 90%, 95%, etc.

In an embodiment of the present invention, as shown in fig. 4 and 8, along the rotation axis of the second stage blades 114, the second stage blades 114 include an air inlet section 120, a transition section 122 and an air outlet section 124 connected to each other, and the transition section 122 is located between the air inlet section 120 and the air outlet section 124; the camber line of the second stage blades 114 is greater at the transition section 122 than at the inlet section 120; the camber line of the second stage blades 114 is greater at the transition section 122 than at the outlet section 124.

In this embodiment, along the axial direction of rotation of the second stage blades 114, the second stage blades 114 include an air inlet section 120, a transition section 122, and an air outlet section 124 connected together. The air inlet section 120 is matched with the air supply section 112 of the first stage fan blade 108, and the transition section 122 is connected between the air inlet section 120 and the air outlet section 124. During the operation of the fan assembly 100, the airflow blown from the first-stage fan blade 108 firstly enters the air inlet section 120, then passes through the transition section 122 and the air outlet section 124 in sequence, and flows out from the air outlet of the air duct 102, thereby realizing two-stage pressurization and acceleration of the airflow. In addition, the camber line of second stage blades 114 is greater at transition section 122 than at inlet section 120; the camber line of the second stage blades 114 is greater at the transition section 122 than at the outlet section 124.

Thus, in the gas flowing direction, the bending angle of the middle arc line of the second stage fan blade 114 is increased and then decreased, and the bending angle of the middle arc line of the second stage fan blade 114 at the transition section 122 located at the middle part is ensured to be larger than the bending angles of the air inlet section 120 and the air outlet section 124 located at the two ends. By the design, the air supply capacity of the second-stage fan blades 114 can be ensured through the air inlet section 110, noise generated when the air flows in the air duct 102 is reduced, especially, flow transition of air flow between the first-stage fan blades 108 and the second-stage fan blades 114 can be ensured, resistance when the air flow blows to the second-stage fan blades 114 is reduced, air supply of the air supply section 112 can be more smooth, the probability of backflow is reduced, and the noise when the air flow flows in the air duct 102 is effectively reduced.

Specifically, as shown in fig. 8, for the present embodiment, the camber line of the second stage fan blade 114 is at the bend angle of the air intake section 110, i.e. θ 1- θ 2; the camber line of the second stage fan blade 114 is at the bend angle of the transition section 122, i.e. θ 2- θ 3; the camber line of the second stage blade 114 is at the bend angle θ 3- θ 4 of the air outlet section 124. Wherein Q1 is the beginning of the mean camber line of second stage blade 114 at the inlet section 120, and θ 1 is the angle of the mean camber line of second stage blade 114 at Q1; p2 is the beginning of the mean camber line of second stage blade 114 at transition 122, θ 2 is the angle of the mean camber line of second stage blade 114 at P2; q3 is the start of the camber line of second stage blade 114 at outlet 124, θ 3 is the angle of the camber line of second stage blade 114 at Q3; q4 is the end point of the mean camber line of second stage blade 114 at wind outlet 124, and θ 4 is the angle of the mean camber line of second stage blade 114 at Q4. Lines B1-B1 represent the boundary between the inlet section 120 and the transition section 122, and lines B2-B2 represent the boundary between the transition section 122 and the outlet section 124.

In particular, since the mean camber line of the second stage blades 114 is a continuous line, Q2 is the beginning of the mean camber line of the second stage blades 114 at the transition 122 and the ending of the mean camber line of the second stage blades 114 at the inlet 120; q3 is the beginning of the camber line of second stage blade 114 at outlet 124 and the end of the camber line of second stage blade 114 at transition 122.

In one embodiment of the present invention, as shown in FIG. 8, the camber line of second stage blades 114 is greater than 0 and less than or equal to 10 at the angle of incidence 120.

In this embodiment, as shown in FIG. 8, the camber line of the second stage blades 114 has a bend angle θ 1- θ 2 at the inlet section 120, and satisfies 0 ° < θ 1- θ 2 ≦ 10 °. After being pressurized and accelerated by the air inlet section 110 and the air supply section 112 of the first-stage fan blades 108, the airflow is transited from the first-stage fan blades 108 to the second-stage fan blades 114 under the cooperation of the air supply section 112 and the air inlet section 120. The bending angle of the mean camber line of the second-stage blades 114 in the air inlet section 120 is designed to be theta 1-theta 2 in the range of 0-10 degrees, so that the bending angle of the mean camber line of the second-stage blades 114 in the air inlet section 120 is matched with the bending angle of the mean camber line of the first-stage blades 108 in the air supply section 112 and the structural configuration of the air duct 102. Thus, it is ensured that the airflow blown from the first stage fan blade 108 can directly and smoothly enter the second stage fan blade 114, the flow transition of the airflow between the first stage fan blade 108 and the second stage fan blade 114 can be ensured, the resistance of the airflow blown to the second stage fan blade 114 is reduced, the air supply of the air supply section 112 can be more smooth, the probability of backflow is reduced, and the noise of the airflow flowing in the air duct 102 is also effectively reduced.

In a specific embodiment, the value of θ 1- θ 2 may be 1 °, 2 °, 3 °, 4 °, 5 °, 6 °, 7 °, 8 °, 9 °, 10 °, and the like.

In one embodiment of the present invention, as shown in fig. 8, the camber line of the second stage blades 114 at the air outlet section 124 is greater than 0 ° and less than or equal to 10 °.

In this embodiment, as shown in fig. 8, the camber line of the second stage blade 114 at the outlet section 124 has a bend angle θ 3- θ 4, and satisfies 0 ° < θ 3- θ 4 ≦ 10 °. After the air flow is accelerated and pressurized through the air outlet section 124 of the second-stage fan blade 114, the air flow can be directly discharged from the air outlet 106 of the air duct 102, the bend angle of the camber line of the second-stage fan blade 114 at the air outlet section 124 is designed to be 0-10 degrees, the rotating angle and the blowing speed of the air flow blown out by the second-stage fan are guaranteed, so that good separation between the air flow and the air outlet section 124 of the second-stage fan blade 114 is achieved, unnecessary noise cannot be generated at the separation position, more importantly, the noise cannot be generated when the air flow is in contact with other parts at the downstream of the air outlet 106, and the purpose of noise reduction is achieved.

In a specific embodiment, the value of θ 3- θ 4 may be 1 °, 2 °, 3 °, 4 °, 5 °, 6 °, 7 °, 8 °, 9 °, 10 °, and the like.

In one embodiment of the present invention, as shown in FIG. 8, the camber line of the second stage blades 114 at the transition section 122 is greater than or equal to 25 °.

In this embodiment, as shown in FIG. 8, the camber line of the second stage blade 114 has a bend angle θ 2- θ 3 at the transition section 122, and satisfies a condition that θ 2- θ 3 ≧ 25. The transition section 122 of the second stage blades 114 is preferably angled sufficiently to ensure that the airflow is accelerated through the second stage blades 114. Therefore, the camber line of the second-stage fan blade 114 designed in this embodiment is greater than or equal to 25 ° at the bend angle of the transition section 122, so that after the airflow is stably transited under the cooperation of the air supply section 112 and the air inlet section 120, an effective supercharging acceleration effect is obtained in the transition section 122, and then the first-stage fan blade 108 is matched to jointly form a two-stage supercharging effect, on one hand, the air supply capacity of the fan assembly 100 is ensured, on the other hand, the noise reduction effect of the fan assembly 100 is ensured, and especially, the noise reduction effect of the second-stage fan blade 114 is ensured.

In a specific embodiment, the value of θ 2- θ 3 may be 25 °, 30 °, 35 °, 40 °, 45 °, 50 °, and the like.

In one embodiment of the present invention, as shown in fig. 4, the ratio of the height of the air inlet section 120 to the total height of the second stage blades 114 along the rotational axis of the second stage blades 114 is greater than or equal to 10% and less than or equal to 20%.

In this embodiment, as shown in fig. 4, along the rotation axis of the second stage fan blades 114, the height of the air inlet section 120 is H3, the height of the transition section 122 is H4, and the height of the air outlet section 124 is H5. Along the rotation axial direction of the second-stage fan blades 114, the air inlet section 120 of the second-stage fan blades 114 is matched with the air supply section 112 of the first-stage fan blades 108 for use, so that the smooth transition of the airflow between the first-stage fan blades 108 and the second-stage fan blades 114 is realized, the backflow phenomenon is avoided, and the noise of the airflow in the air duct 102 during flowing is effectively reduced. Therefore, the ratio of the height H3 of the air inlet section 120 to the total height H3+ H4+ H5 of the second stage blades 114 along the rotation axis of the second stage blades 114 is 10% to 20%, which ensures the matching between the air inlet section 120 and the air supply section 112 on the one hand, and ensures that the air inlet section 120 has enough portion for the secondary pressurization and acceleration of the airflow to balance between noise reduction and wind power on the other hand.

In specific embodiments, the ratio of H3 to H3+ H4+ H5 may be 10%, 12%, 15%, 16%, 18%, 20%, etc.

In one embodiment of the present invention, as shown in FIG. 4, the ratio of the height of the transition section 122 to the total height of the second stage blades 114 along the rotational axis of the second stage blades 114 is greater than or equal to 40% and less than or equal to 80%.

In this embodiment, as shown in FIG. 4, along the rotational axis of the second stage blades 114, the airflow entering the transition section 122 may be accelerated by the second pressurization of the transition section 122. Therefore, the ratio of the height H4 of the transition section 122 to the total height H3+ H4+ H5 of the second stage blades 114 is 40% to 80%, which ensures that the transition section 122 has a sufficient height, i.e. the second stage blades 114 have sufficient capability of pressurizing and accelerating the airflow, so as to effectively ensure that the wind power of the airflow is enhanced under the acceleration and pressurization of the second stage blades 114, and the wind resistance is improved, thereby greatly enhancing the air exhaust capability of the airflow through the external exhaust duct.

In specific embodiments, the ratio of H4 to H3+ H4+ H5 may be 40%, 45%, 50%, 55%, 60%, 65%, 70%, 75%, 80%, etc.

In an embodiment of the present invention, as shown in fig. 4, along the rotation axis of the second stage blades 114, the ratio of the height of the air outlet section 124 to the total height of the second stage blades 114 is greater than or equal to 10% and less than or equal to 20%.

In this embodiment, as shown in fig. 4, the airflow is separated from the air outlet section 124 after two pressurized accelerations. Along the rotation axial direction of the second-stage fan blade 114, the ratio of the height H5 of the air outlet section 124 to the total height H3+ H4+ H5 of the second-stage fan blade 114 is designed to be 10% to 20%, that is, the ratio of the height of the air outlet section 124 in the rotation axial direction of the second-stage fan blade 114 is reasonably designed, so that the air flow can be ensured to have a good air outlet effect after passing through the air outlet section 124, the direct separation effect of the air flow and the air outlet section 124 is ensured, and the noise reduction effect is realized. In addition, the ratio of the height H5 of the air outlet section 124 to the total height H3+ H4+ H5 of the second-stage fan blades 114 is designed to be 10% to 20%, the height ratio of the height H4 of the transition section 122 in the rotation axial direction of the second-stage fan is also ensured, and the pressurizing and accelerating capacity of the second-stage fan to the air flow is further ensured.

In specific embodiments, the ratio of the degree H5 to H3+ H4+ H5 may be 10%, 12%, 15%, 16%, 18%, 20%, etc.

In one embodiment of the present invention, as shown in fig. 9, the direction perpendicular to the rotation axis of the second stage blades 114 is taken as the radial direction of the second stage blades 114, and along the radial direction of the second stage blades 114, the second stage blades 114 include a third region 134 and a fourth region 136, the third region 134 is located at the periphery of the fourth region 136; in the third region 134, the camber line of the second stage blades 114 is greater at the transition section 122 than at the inlet section 120; the camber line of the second stage blades 114 is greater at the transition section 122 than at the outlet section 124.

In this embodiment, as shown in FIG. 9, the radial direction of the second stage blades 114 is perpendicular to the rotation axis of the second stage blades 114, and the radial center of the second stage blades 114 is connected to the driving assembly 128, so that the position of the radial opening into the blade tip is the main active region. Therefore, in the present embodiment, the second-stage blades 114 are divided into a third region 134 and a fourth region 136 along the radial direction of the second-stage blades 114, and the third region 134 is located at the periphery of the fourth region 136 and is closer to the blade tip, so that the third region 134 is the main active region. On the basis, the present embodiment only modifies a portion of the third region 134, such that the camber line of the second-stage blades 114 in the third region 134 is larger at the transition section 122 than at the inlet section 120; the camber line of the second stage blades 114 is greater at the transition section 122 than at the outlet section 124. In this way, the area of improvement to the second stage blades 114 is reduced, thereby reducing the difficulty of machining and manufacturing.

In one embodiment of the present invention, as shown in fig. 9, the ratio of the length of the fourth region 136 to the total length of the third region 134 and the fourth region 136 along the radial direction of the second stage fan blade 114 is greater than or equal to 65% and less than or equal to 100%.

In this embodiment, as shown in FIG. 9, in the radial direction of the second stage fan blades 114, the length of the fourth region 136 is D3, the total length of the third region 134 and the fourth region 136 is D4, and 65% ≦ D3/D4 ≦ 100%. Therefore, by reasonably dividing the radial ratio of the third region 134 and the fourth region 136 in the second-stage fan blade 114 and reasonably designing the optimized area of the second-stage fan blade 114 in the radial direction, on one hand, the energy efficiency and the noise reduction effect of the second-stage fan blade 114 can be ensured, and on the other hand, the working difficulty and the workload of workers can be reduced.

In specific embodiments, the value of D3/D4 may be 65%, 70%, 75%, 80%, 85%, 90%, 95%, or the like.

In one embodiment of the present invention, as shown in fig. 1 and 3, the fan assembly 100 further includes: the wind-guiding ring 126 comprises a straight line section, and the inner wall of the straight line section forms the wind channel 102.

In this embodiment, fan assembly 100 also includes a wind deflector 126. The air guide ring 126 is sleeved on the peripheries of the first-stage fan blades 108 and the second-stage fan blades 114, the air guide ring 126 is provided with a straight line section, and the inner wall of the straight line section forms the air duct 102.

In addition, an expansion section can be further arranged at the inlet or the outlet of the wind guide ring 126, but the line A-A in FIG. 4 is based on the position of the straight line section. That is, it is only necessary to ensure that the air inlet section 110 of the first stage fan blade 108 protrudes from the straight section.

In one embodiment of the present invention, the fan assembly 100 further comprises: the mesh enclosure is disposed in the air duct 102 and located at the air outlet 106.

In this embodiment, the fan assembly 100 further includes a mesh enclosure. The mesh enclosure is arranged at the air outlet 106 of the air guide ring 126, so that on one hand, external impurities are prevented from entering the air guide ring 126 to cause abnormal operation of the fan, and parts in the air guide ring 126 are effectively protected from being damaged; on the other hand, the danger caused by the fact that people or other animals touch the first-stage fan blades 108 and the second-stage fan blades 114 when the fan assembly 100 works is avoided, and the safety of the air conditioner is improved.

In one embodiment of the present invention, as shown in FIG. 1, the drive assembly 128 includes: a first motor 116 coupled to the first stage blades 108 and configured to drive the first stage blades 108 to rotate; a second motor 118 coupled to the second stage blades 114 and configured to drive the second stage blades 114 to rotate; wherein the axis of rotation of the output shaft of the first motor 116 is collinear with the axis of rotation of the output shaft of the second motor 118, and the direction of rotation of the first stage blades 108 is opposite to the direction of rotation of the second stage blades 114.

In this embodiment, as shown in fig. 1, the drive assembly 128 includes a first motor 116 and a second motor 118. The first motor 116 drives the first-stage fan blades 108 to rotate, the second motor 118 drives the second-stage fan blades 114 to rotate in the opposite direction, and the rotation axes of the output shafts of the first motor 116 and the second motor 118 are collinear, so that the two-stage fan blades are arranged in series, and a counter-rotating fan capable of rotating in the opposite directions (hereinafter referred to as counter-rotating) relative to the first-stage fan blades 108 and the second-stage fan blades 114 is formed; furthermore, the first stage fan blades 108 are used as upstream fan blades, the second stage fan blades 114 are used as downstream fan blades, and the opposite rotation of the upstream fan blades and the downstream fan blades improves the wind pressure and the wind resistance, so that the air supply is smoother, and the backflow probability is reduced.

Specifically, as shown in fig. 1, by adopting the counter-rotating design of the first-stage fan blade 108 and the second-stage fan blade 114, the work-doing capability of the motor is enhanced, and meanwhile, the rotating speeds of the first-stage fan blade 108 and the second-stage fan blade 114 are significantly lower than those of single axial flow fans of the same class, so that the service life is prolonged, and the requirement of high rotating speed on the high strength of the fan blade structure is reduced. The arrangement enables the air flow to be accelerated and pressurized under the combined action of the two stages of fan blades when passing through the outdoor unit of the air conditioner, so that the wind power is enhanced, the wind resistance is improved, and the air exhaust capability of the air flow through the external exhaust pipe is greatly enhanced.

In addition, as shown in fig. 2, since the rotation directions of the first stage blades 108 and the second stage blades 114 are opposite, the torque acting on the rotating shaft is relatively balanced, thereby reducing the vibration of the machine body and the noise caused by the vibration, and further improving the use experience of the user.

Further, as shown in fig. 10, the drive assembly 128 further includes a first bracket 206 and a second bracket 208. The first bracket 206 is used for supporting the first motor 116, and the second bracket 208 is used for supporting the second motor 118. The arrangement that the first bracket 206 is positioned at the same side of the first-stage fan blades 108 and the second-stage fan blades 114 or between the first-stage fan blades 108 and the second-stage fan blades 114, and the second bracket 208 is positioned at the same side of the first-stage fan blades 108 and the second-stage fan blades 114 or between the first-stage fan blades 108 and the second-stage fan blades 114 realizes the adjustment of the relative positions of the motor and the two-stage fan blades according to the size of the inner space of the air conditioner under the condition of not influencing the use performance, thereby ensuring reasonable structural layout.

As shown in fig. 10 and 11, a second aspect of the present invention provides an air conditioner including: a fan assembly 100 as in any of the embodiments described above.

The air conditioner provided by the invention comprises the fan assembly 100 of any one of the embodiments. Accordingly, all of the benefits of the fan assembly 100 described above are not discussed herein.

Further, as shown in fig. 11, the air conditioner further includes a cabinet 202 and a heat exchanger 204. Fan assembly 100 is disposed within enclosure 202 and is used in conjunction with heat exchanger 204 to reduce the temperature of heat exchanger 204.

In an embodiment, the air conditioner includes an outdoor unit, and the blower assembly 100 is disposed in the outdoor unit.

In a specific embodiment, the air conditioner further comprises an air conditioner indoor unit, and the air conditioner indoor unit is connected with the air conditioner outdoor unit to adjust the temperature and the humidity of the indoor environment.

The embodiment relates to a design scheme of an impeller of a counter-rotating axial flow fan matched with the geometric form of an air guide ring. The air conditioning system is composed of a cold and heat source and an air conditioning system, and is used for processing air so as to meet the requirement of body feeling comfort of a user. Generally, the phase change of a refrigerant is utilized to provide cold energy, and a heating system provides heat. When the general air conditioner outdoor unit is used, certain noise can be generated, and the influence on the daily life of people is caused. The size of the aerodynamic noise of the air conditioner depends on the design level of the impeller and the air duct.

The existing noise reduction schemes of the air conditioner are generally divided into two categories, one is a scheme of reducing the external noise of the air conditioner by adding sound insulation and absorption materials, and the other is a scheme of reducing the external noise level by controlling the source generating the noise. The former tends to increase the cost of the filler material, the sound damping structure, and the latter requires a higher level of design.

Present current technical scheme often uses the former as the main, inhales the sound device through giving sound insulation and reduces noise level, for example increases puigging, devices such as muffler outside the wind channel, reaches the design requirement, and controls the source of noise, does not need extra device, can realize falling the purpose of making an uproar on the basis of increasing the cost not showing significantly.

The disadvantages of the prior art solutions are as follows: the production cost is increased, and the additional sound insulation layer can increase the production cost and reduce the market competitiveness; the use and maintenance cost is increased, and in use, the sound insulation layer is peeled off due to adhesion, so that the noise reduction level is influenced, and the use cost of a user is increased; the weight and the volume are increased, and the additional sound insulation layer can increase the volume and the weight of the product and reduce the application range of the product.

Aiming at the problems in the prior art, the invention provides a design scheme for matching the wind guide ring 126 with the blade top load, which can obviously improve the energy efficiency of an air conditioner and reduce noise.

Specifically, as shown in fig. 10 and 11, the air duct 102 of the external air conditioner with counter-rotating design includes two impellers (first stage fan 108 and second stage fan 114) with opposite rotation directions, a bracket (first bracket 206 and second bracket 208) for supporting the impellers, a driving assembly 128 (first motor 116 and second motor 118) for powering the impellers, and an air duct 102 system (air guiding ring 126).

As shown in fig. 1, fig. 2 and fig. 3, in the technical solution adopted in this embodiment, the fan assembly 100 mainly includes a first stage fan blade 108, a second stage fan blade 114 and an air guiding ring 126; the air duct 102 is formed by the straight section of the air guiding ring 126.

FIG. 9 is a partition diagram applied in the present embodiment. As shown in fig. 9, the action areas of the design of this embodiment are: a first region 130 of the first stage blade 108, and a third region 134 of the second stage blade 114. The ratio of the length D1 of the first region 130 to the total length D2 of the first region 130 and the second region 132 is about 65%, and the ratio of the length D3 of the third region 134 to the total length D4 of the third region 134 and the fourth region 136 is about 65%.

FIG. 4 is an axial sectional view of the present embodiment. As shown in FIG. 4, a line A-A is a position of the air inlet 104 of the air duct 102, and the line A-A divides the first stage fan 108 into an air inlet section 110 and an air supply section 112; wherein, the ratio of the thickness H1 of the air inlet section 110 to the total thickness H1+ H2 of the first-stage fan blades 108 is 40-70%. Line B1-B1 and line B2-B2 divide second stage fan blades 114 into an air inlet section 120, a transition section 122 and an air outlet section 124; wherein, the ratio of the thickness H3 of the air inlet section 120 to the total thickness H3+ H4+ H5 of the second-stage fan blades 114 is 10% to 20%, and the ratio of the total thickness H3+ H4 of the air inlet section 120 and the transition section 122 to the total thickness H3+ H4+ H5 of the second-stage fan blades 114 is 80% to 90%.

Fig. 5 and 6 are views for explaining the camber line and the bend angle of the camber line of the fan blade defined in the present embodiment. For any fan blade, the fan blade includes opposite suction and pressure surfaces, and as shown in fig. 5 and 6, the blade profile cross section of the fan blade can be obtained by cutting the fan blade with a plane parallel to the rotation axis of the fan blade, and as shown in fig. 6, in the blade profile cross section of the fan blade, the arc lines with equal distances to the suction surface arc line L1 and the pressure surface arc line L2 are the mean arc line L2 of the fan blade. A tangent to this point (a tangent extending toward the tip side) may be obtained at any point on the camber line L2 of the blade, and the included angle formed between the camber line L2 of the blade and the tangent to this point in the extending direction of the tangent is defined as the angle of the camber line L2 of the blade at this point. The angular difference between any two points on camber line L2 of the blade is defined as the bend angle between the two points of camber line L2 of the blade.

That is, as shown in fig. 5 and 6, two points are taken on the camber line L2 of the fan blade, which are O1 and O2, respectively, the angle of the camber line L2 of the fan blade at O1 is α 1, and the angle of the camber line L2 of the fan blade at O2 is α 2. Then, the camber line L2 of the fan blade is α 1- α 2 at the section from O1 to O2.

FIG. 7 is a sectional view of the blade profile of the first stage blade 108. the blade profile of the first stage blade 108 has the following characteristics: the bend angle of the mean camber line of the first-stage fan blade 108 in the air inlet section 110 is 0-10 degrees, and the bend angle of the mean camber line of the first-stage fan blade 108 in the air supply section 112 is less than 45 degrees.

FIG. 8 is a sectional view of the blade profile of the second stage blade 114. the blade profile of the second stage blade 114 has the following characteristics: the camber line of the second stage blades 114 at the inlet section 120 is less than or equal to 10 °, and the camber line of the second stage blades 114 at the outlet section 124 is greater than 25 °.

In the embodiment, the inlet of the wind guiding ring 126 is not a straight line but a curved line, and the position of the line a-a in fig. 4 should be calculated based on the position of the straight section.

In an embodiment, the bending angle of the mean arc line of the first stage blade 108 in the air inlet section 110 may be negative, that is, the bending direction of the mean arc line of the first stage blade 108 in the air supply section 112 of the air inlet section 110 may be different, but the absolute value of the bending angle of the mean arc line of the first stage blade 108 in the air inlet section 110 should satisfy 0 ° to 10 °.

In the description of the present invention, the terms "plurality" or "a plurality" refer to two or more, and unless otherwise specifically limited, the terms "upper", "lower", and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings, and are merely for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus should not be construed as limiting the present invention; the terms "connected," "mounted," "secured," and the like are to be construed broadly and include, for example, fixed connections, removable connections, or integral connections; may be directly connected or indirectly connected through an intermediate. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.

In the description herein, the description of the terms "one embodiment," "some embodiments," "specific embodiments," etc., means that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and various modifications and changes will occur to those skilled in the art. 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. A fan assembly, comprising:

the air channel comprises an air inlet and an air outlet which are communicated;

the first-stage fan blade is arranged at the air inlet and comprises an air inlet section and an air supply section which are connected along the rotating axial direction of the first-stage fan blade, the air inlet section is positioned outside the air channel, and the air supply section is positioned in the air channel;

the second-stage fan blade is arranged in the air duct and is close to the air outlet;

the driving assembly is respectively connected to the first-stage fan blade and the second-stage fan blade and is configured to drive the first-stage fan blade and the second-stage fan blade to rotate;

the absolute value of the bend angle of the camber line of the first-stage fan blade in the air inlet section is smaller than that of the bend angle of the air supply section.

2. The fan assembly of claim 1,

the middle arc line of the first-stage fan blade is positioned at the bent angle of the air inlet section and is larger than 0 degree and smaller than or equal to 10 degrees; or

The bend angle of the camber line of the first-stage fan blade in the air inlet section is more than or equal to-10 degrees and less than 0 degree;

the camber line of the first-stage fan blade is larger than or equal to 0 degree and smaller than or equal to 45 degrees at the bending angle of the air supply section.

3. The fan assembly of claim 1,

along the rotating axial direction of the first-stage fan blades, the ratio of the height of the air inlet section to the total height of the first-stage fan blades is more than or equal to 40% and less than or equal to 70%; and/or

Along the rotating axial direction of the first-stage fan blades, the ratio of the height of the air supply section to the total height of the first-stage fan blades is greater than or equal to 30% and less than or equal to 60%.

4. The fan assembly of any of claims 1 to 3,

taking the direction perpendicular to the rotation axis of the first-stage fan blade as the radial direction of the first-stage fan blade, wherein the first-stage fan blade comprises a first area and a second area along the radial direction of the first-stage fan blade, and the first area is positioned at the periphery of the second area;

in the first region, the absolute value of the bend angle of the camber line of the first-stage fan blade in the air inlet section is smaller than that of the bend angle of the air supply section.

5. The fan assembly of claim 4,

the ratio of the length of the second region to the total length of the first region and the second region is greater than or equal to 65% and less than or equal to 100% in the radial direction of the first stage fan blade.

6. The fan assembly of claim 1,

the second-stage fan blade comprises an air inlet section, a transition section and an air outlet section which are connected along the rotation axial direction of the second-stage fan blade, and the transition section is positioned between the air inlet section and the air outlet section;

the bend angle of the camber line of the second-stage fan blade at the transition section is larger than that at the wind inlet section;

the camber line of the second-stage fan blade is arranged at the bending angle of the transition section and is larger than the bending angle of the air outlet section.

7. The fan assembly of claim 6,

the bending angle of the camber line of the second-stage fan blade at the air inlet section is more than 0 degree and less than or equal to 10 degrees;

the bending angle of the camber line of the second-stage fan blade at the air outlet section is more than 0 degree and less than or equal to 10 degrees;

the bend angle of the camber line of the second-stage fan blade in the transition section is larger than 25 degrees.

8. The fan assembly of claim 6,

the ratio of the height of the air inlet section to the total height of the second-stage fan blades is greater than or equal to 10% and less than or equal to 20% along the rotating axial direction of the second-stage fan blades; and/or

The ratio of the height of the transition section to the total height of the second-stage fan blades is more than or equal to 40% and less than or equal to 80% along the rotation axial direction of the second-stage fan blades; and/or

Along the rotating axial direction of the second-stage fan blades, the ratio of the height of the air outlet section to the total height of the second-stage fan blades is greater than or equal to 10% and less than or equal to 20%.

9. The fan assembly of any of claims 6 to 8,

taking the direction perpendicular to the rotation axis of the second-stage fan blade as the radial direction of the second-stage fan blade, wherein the second-stage fan blade comprises a third area and a fourth area, and the third area is positioned at the periphery of the fourth area;

in the third area, the bending angle of the camber line of the second-stage fan blade in the transition section is larger than that in the wind inlet section; the camber line of the second-stage fan blade is arranged at the bending angle of the transition section and is larger than the bending angle of the air outlet section.

10. The fan assembly of claim 9,

in the radial direction of the second-stage fan blade, the ratio of the length of the fourth area to the total length of the third area and the fourth area is greater than or equal to 65% and less than or equal to 100%.

11. The fan assembly of claim 1, further comprising:

the air guide ring comprises a straight line section, and the inner wall of the straight line section forms the air duct; and/or

And the mesh enclosure is arranged on the air duct and is positioned at the air outlet.

12. The fan assembly of claim 11, wherein the drive assembly comprises:

the first motor is connected with the first-stage fan blades and is configured to drive the first-stage fan blades to rotate;

the second motor is connected with the second-stage fan blade and is configured to drive the second-stage fan blade to rotate;

the rotating axis of the output shaft of the first motor is collinear with the rotating axis of the output shaft of the second motor, and the rotating direction of the first-stage fan blades is opposite to that of the second-stage fan blades.

13. An air conditioner, comprising:

a fan assembly as claimed in any of claims 1 to 12.