WO2020143153A1

WO2020143153A1 - Cross-flow wind wheel and air conditioner

Info

Publication number: WO2020143153A1
Application number: PCT/CN2019/088330
Authority: WO
Inventors: 陈学彬; 马列; 张敏; 周何杰
Original assignee: 广东美的制冷设备有限公司; 美的集团股份有限公司
Priority date: 2019-01-08
Filing date: 2019-05-24
Publication date: 2020-07-16
Also published as: CN111412179A

Abstract

Provided are a cross-flow wind wheel and an air conditioner, wherein the cross-flow wind wheel comprises a blade (10), in the cross section of the blade (10), the intersection points of the wing-shaped center line of the blade (10) and the outer side end and the inner side end of the blade (10) are defined as an outer side end point A and an inner side end point B, the connecting line of the outer side end point A and the inner side end point B is defined as the chord length L; the blade (10) has the maximum thickness and it is limited by a connecting line of two points DE of the blade (10); the tangent line of the point D of the blade (10) is vertical to the DE connecting line; the vertical connecting line of the D point of the blade (10) and the AB connecting line is defined as a DC connecting line, satisfying: 58% ≤AC / AB <61%. By optimizing the wing-shaped structure of the blade and improving the position distribution and change of the maximum thickness of the blade, the airflow flowing resistance can be effectively reduced, airflow separation is delayed, further the air volume loss, power and noise are reduced.

Description

Cross flow wind wheel and air conditioner

This application is based on the Chinese patent application with the application number 201910017751.7 and the application date is 2019-01-08 and claims the priority of the Chinese patent application. The entire content of the Chinese patent application is hereby incorporated by reference.

Technical field

This application relates to the technical field of air conditioners, in particular to a cross-flow wind wheel and air conditioners.

Background technique

The cross flow wind wheel has the characteristics of simple structure, low noise, stable air flow, and linear increase in air volume with length. It is widely used in indoor units of air conditioners.

The cross-flow impeller is a cylindrical impeller structure, which is composed of a plurality of blades spaced apart in the circumferential direction. The cross-flow impeller rotates so that the airflow can flow in from the blade gap on the inlet side and then flow out from the blade gap on the outlet side. The airflow passes through the blade gap on the inlet side and the outlet side, that is, the airflow passes through the cross-flow rotor twice. The front and rear ends of the same blade serve as the leading edge and the trailing edge, with different circumferential positions of the cross-flow rotor. change.

As shown in Figures 1 and 2, the pressure and suction surfaces of the blades of the existing cross-flow wind turbines are arc-shaped, and the thickness of the blades is about wing-shaped structures with small ends and large centers, making the leading and trailing edges of the blades It is similar to accommodate the situation where the leading and trailing edges of the blade are both the leading edge and the trailing edge.

In actual situations, the airflow state is different at different circumferential positions of the cross flow wind wheel. The blade design of this wing-shaped structure is not the optimal design, which will increase the airflow resistance and cause the loss of air volume, resulting in The noise and power of the same air volume are not in the optimal state.

Summary of the invention

The purpose of the present application is to solve at least one of the technical problems existing in the prior art, and to provide a cross-flow wind wheel and air conditioner to reduce the resistance of air flow, thereby reducing air volume loss, power and noise.

According to a first aspect of the present application, there is provided a cross-flow wind turbine including a blade, and in the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as the outer endpoint A. Inboard end point B, the connection between the outboard end point A and the inboard end point B is defined as the chord length L; the blade has the maximum thickness and is defined by the two-point DE connection line of the blade, and the tangent line D of the blade is The DE connection is vertical, satisfying: 11°≤∠DBE<13°; the vertical connection between the D point of the blade and the AB connection is defined as a DC connection, satisfying: 58%≤AC/AB<61%.

According to the cross flow wind turbine according to the first aspect of the present application, the two-point MN line of the blade divides the blade section into a first section and a second section. The tangent line of the M point of the blade is perpendicular to the MN line. The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2. When AK/AB=60%, it satisfies: 55%≤S1/(S1+S2)≤60%.

According to the cross-flow wind turbine according to the first aspect of the present application, the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is perpendicular to the FG line, satisfying: 1.8≤DE/FG ≤2.2.

According to the cross-flow wind wheel according to the first aspect of the present application, the center of the cross-flow wind wheel is defined as point O, which satisfies: 27°≤∠OAB≤30°.

According to the cross-flow wind wheel according to the first aspect of the present application, the diameter of the cross-flow wind wheel is d, satisfying: 13%≤d/L≤15%

According to a second aspect of the present application, there is provided a cross-flow wind turbine including a blade, and in the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as the outer endpoint A. Inboard end point B, the connection between the outboard end point A and the inboard end point B is defined as the chord length L; the blade has the maximum thickness and is defined by the two-point DE connection line of the blade, and the tangent line D of the blade is The DE connection is vertical, satisfying: 13°≤∠DBE<16°; the vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 61%≤AC/AB<65%.

According to the cross-flow wind turbine according to the second aspect of the present application, the two-point MN line of the blade divides the blade section into a first section and a second section. The tangent of the M point of the blade is perpendicular to the MN line. The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2. When AK/AB=60%, it satisfies: 51%≤S1/(S1+S2)≤53%.

According to the cross-flow wind turbine according to the second aspect of the present application, the blade has a minimum thickness and is defined by the two-point FG line of the blade, the tangent of the F point of the blade is perpendicular to the FG line, satisfying: 1.9≤DE/FG ≤2.3.

According to the cross-flow wind wheel according to the second aspect of the present application, the center of the cross-flow wind wheel is defined as point O, which satisfies: 26°≤∠OAB≤28.5°.

According to the cross flow wind wheel according to the second aspect of the present application, the diameter of the cross flow wind wheel is d, satisfying: 13%≤d/L≤15%.

According to a third aspect of the present application, there is provided a cross-flow wind turbine including a blade, and in the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as the outer endpoint A. Inboard end point B, the connection between the outboard end point A and the inboard end point B is defined as the chord length L; the blade has the maximum thickness and is defined by the two-point DE connection line of the blade, and the tangent line D of the blade is The DE connection is vertical, satisfying: 16°≤∠DBE<23°; the vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 65%≤AC/AB<75%.

According to the cross flow wind turbine according to the third aspect of the present application, the two-point MN line of the blade divides the blade section into a first section and a second section. The tangent line of the M point of the blade is perpendicular to the MN line. The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2. When AK/AB=60%, it satisfies: 50%≤S1/(S1+S2)≤56%.

According to the cross flow wind turbine according to the third aspect of the present application, the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is perpendicular to the FG line, satisfying: 1.8≤DE/FG ≤2.2.

According to the cross-flow wind wheel according to the third aspect of the present application, the center of the cross-flow wind wheel is defined as point O, which satisfies: 26.5°≤∠OAB≤29°.

According to the cross-flow wind wheel according to the third aspect of the present application, the diameter of the cross-flow wind wheel is d, which satisfies: 11%≤d/L≤14%.

According to a fourth aspect of the present application, there is provided a cross-flow wind turbine including a blade, and in the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as the outer endpoint A. Inboard end point B, the connection between the outboard end point A and the inboard end point B is defined as the chord length L; the blade has the maximum thickness and is defined by the two-point DE connection line of the blade, and the tangent line D of the blade is The DE connection is vertical, satisfying: 23°≤∠DBE<31°; the vertical connection between the D point of the blade and the AB connection is defined as a DC connection, satisfying: 75%≤AC/AB<85%.

According to the cross flow wind turbine according to the fourth aspect of the present application, the two-point MN line of the blade divides the blade section into a first section and a second section. The tangent line of the M point of the blade is perpendicular to the MN line, so The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2. When AK/AB=60%, it satisfies: 50%≤S1/(S1+S2)≤56%.

According to the cross-flow wind turbine according to the fourth aspect of the present application, the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is perpendicular to the FG line, satisfying: 2≤DE/FG ≤2.5.

According to the cross-flow wind wheel according to the fourth aspect of the present application, the center of the cross-flow wind wheel is defined as point O, which satisfies: 26.5°≤∠OAB≤29°.

According to the cross-flow wind wheel according to the fourth aspect of the present application, the diameter of the cross-flow wind wheel is d, which satisfies: 11%≤d/L≤14%.

According to a fifth aspect of the present application, there is provided an air conditioner including the cross-flow wind turbine according to the first, second, third or fourth aspect of the present application.

Beneficial effect: In the cross-flow wind turbine and air conditioner of this application, by optimizing the blade wing structure and improving the position distribution and change of the maximum thickness of the blade, it can effectively reduce the resistance of the air flow, delay the separation of the air flow, and thereby reduce the air volume loss, Power and noise; moreover, the maximum thickness of the blade is thicker than that of the traditional blade, which can improve the strength of the blade and enhance manufacturability.

BRIEF DESCRIPTION

The following further describes the present application in conjunction with the drawings and embodiments;

FIG. 1 is a schematic structural view of a cross-flow wind wheel in the prior art;

2 is a schematic diagram of the structure of blades in a cross-flow wind wheel in the prior art;

3 is a schematic structural diagram of Embodiment 1 of a cross-flow wind turbine of the present application;

4 is a schematic view of the blade structure of the blade in the first embodiment of the cross-flow wind turbine of the present application;

FIG. 5 is a schematic diagram of blade cross-sectional division in Embodiment 1 of a cross-flow wind turbine of the present application;

6 is a graph showing the relationship between the rotation speed and the air volume in the first embodiment of the cross-flow wind turbine of the present application;

7 is a graph showing the relationship between the air volume and power in the first embodiment of the cross-flow wind turbine of the present application;

FIG. 8 is a graph showing the relationship between stroke volume and noise in the first embodiment of the cross-flow wind turbine of the present application;

9 is a schematic structural diagram of Embodiment 2 of a cross-flow wind turbine of the present application;

10 is a schematic diagram of the blade structure of the blade in the second embodiment of the cross-flow wind turbine of the present application;

FIG. 11 is a schematic diagram of blade cross-sectional division in the second embodiment of the cross-flow wind turbine of the present application;

12 is a graph showing the relationship between the rotation speed and the air volume in the second embodiment of the cross-flow wind turbine of the present application;

13 is a graph showing the relationship between the air volume and power in the second embodiment of the cross-flow wind turbine of the present application;

14 is a graph showing the relationship between the air volume and noise in the second embodiment of the cross-flow wind turbine of the present application;

15 is a schematic structural diagram of Embodiment 3 of a cross-flow wind turbine of the present application;

16 is a schematic view of the blade structure of the third embodiment of the cross-flow wind turbine of the present application;

FIG. 17 is a schematic diagram of the sectional division of blades in the third embodiment of the cross-flow wind turbine of the present application;

18 is a graph showing the relationship between the rotation speed and the air volume in the third embodiment of the cross-flow wind turbine of the present application;

19 is a graph showing the relationship between the air volume and power in the third embodiment of the cross-flow wind turbine of the present application;

20 is a graph of the relationship between the stroke volume and noise in the third embodiment of the cross-flow wind turbine of the present application;

21 is a schematic structural diagram of Embodiment 4 of a cross-flow wind turbine of the present application;

22 is a schematic view of the blade structure of the fourth embodiment of the cross-flow wind turbine of the present application;

FIG. 23 is a schematic diagram of blade cross-section division of the fourth embodiment of the cross-flow wind turbine of the present application;

24 is a graph showing the relationship between the rotation speed and the air volume in the fourth embodiment of the cross-flow wind turbine of the present application;

25 is a graph showing the relationship between the air volume and power in the fourth embodiment of the cross-flow wind turbine of the present application;

FIG. 26 is a graph showing the relationship between air volume and noise in the fourth embodiment of the cross-flow wind turbine of the present application.

detailed description

This section will describe the specific embodiments of this application in detail. The preferred embodiments of this application are shown in the drawings. The role of the drawings is to supplement the description of the text part of the description with graphics, so that people can intuitively and visually understand this. Each technical feature and overall technical solution of the application, but it cannot be understood as a limitation to the protection scope of the application.

In the description of this application, it should be understood that the description of orientation is involved, for example, the orientation or positional relationship indicated by up, down, front, back, left, right, etc. is based on the orientation or positional relationship shown in the drawings, only In order to facilitate the description of the application and simplify the description, it does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be construed as limiting the application.

In the description of this application, several meanings are one or more, and multiple meanings are more than two, greater than, less than, exceeding, etc. are understood as excluding the number, and above, below, within, etc. are understood as including the number. If it is described that the first and second are only for the purpose of distinguishing technical features, they cannot be understood as indicating or implying relative importance or implicitly indicating the number of indicated technical features or implicitly indicating the order of indicated technical features relationship.

In the description of this application, unless otherwise clearly defined, the terms installation, installation, and connection should be broadly understood. Those skilled in the art can reasonably determine the specific meaning of the above terms in this application in conjunction with the specific content of the technical solution.

Referring to FIGS. 3 to 5, Embodiment 1 of the present application provides a cross-flow wind wheel and an air conditioner. The cross-flow wind wheel is provided inside an air conditioner (not shown) to provide heat exchange airflow for a heat exchanger inside the air conditioner. The wind impeller includes two oppositely disposed end plates and a cylindrical impeller disposed between the two end plates. The cylindrical impeller is composed of a plurality of blades 10 arranged in an arc shape at intervals in the circumferential direction, and adjacent blades 10 have The gap 20 for the inflow and outflow of airflow is driven by the drive motor to rotate the crossflow fan, so that the airflow can flow from the gap 20 located on the side of the airflow inlet (above the crossflow wheel) into the interior of the crossflow wheel, forming a flow vortex, and then from the airflow The blade gap 20 on the outlet side (below the cross-flow rotor) flows out.

4 shows a cross section of the blade profile of the cross flow wind turbine of the present application. In the cross section of the blade 10, the intersection of the airfoil center line of the blade 10 and the outer and inner ends of the blade is defined as the outer end point A and the inner end point B.

Among them, the wing-shaped center line is a well-known term in the technical field. The wing-shaped blade is composed of a series of continuous inscribed circles that are tangent to the arc surfaces on both sides, and the center of each inscribed circle is connected to form the wing-shaped center line, which can be understood Yes, the center line of the wing is a virtual line segment.

The direction of the cross flow wind wheel toward the center of rotation is inward, that is, the inside direction, and the direction away from the center of rotation is outward, that is, the outside direction. In the cross section of the blade 10, the outer end and the inner end of the blade are arcs, which respectively intersect the midline of the airfoil, and naturally form two endpoints, namely an outer endpoint A, an inner endpoint B, an outer endpoint A, and an inner endpoint B The two-point line is defined as the chord length L of the blade 10.

In the cross section of the blade 10, the blade 10 has a concave arc line 11 and a convex arc line 12, the blade 10 has a point D on the concave arc line 11 and an E point on the convex arc line 12, due to the thickness of the blade 10 It is variable. Naturally, the maximum thickness of the blade 10 exists. The maximum thickness is defined by the DE two-point line. Specifically, there is a tangent to the concave arc line 11 through the point D, which is perpendicular to the DE line. The maximum length of the DE line is the maximum thickness of the blade 10. In Example 1 of the present application, the maximum thickness of the blade 10 is thicker than the standard blade of the prior art, satisfying: 11°≤∠DBE<13°, preferably ∠DBE = 12.79°.

Correspondingly, the blade 10 also has a minimum thickness. Similarly, the minimum thickness is defined by the FG two-point line. After the F point, there is a tangent to the concave arc line 11 that is perpendicular to the FG line. The FG line The minimum length of is the minimum thickness of the blade 10, and the ratio between the maximum thickness of the blade 10 and the minimum thickness satisfies: 1.8≤DE/FG≤2.2, preferably DE/FG=2.01.

There are point C on the AB line, and the two points on the CD line, so that the CD line is perpendicular to the AB line. Here, the length ratio of the AC two point line and the AB two point line is limited to satisfy: 58%≤ AC/AB<61%, preferably AC/AB=60%. In this way, the position of the maximum thickness of the blade 10 in the chord direction is determined. By improving the position distribution and change of the maximum thickness of the blade 10, the resistance of the air flow is small, and the separation of the air flow on the suction surface can also be delayed , Enhance the function of the blades and increase the air volume; At the same time, because the airflow delays the separation on the suction surface, it can reduce the number of shed vortices, thereby reducing power loss and reducing aerodynamic noise.

In addition, since the maximum thickness design of the blade 10 is thicker than the standard blade of the prior art, it is possible to increase the strength of the blade and enhance manufacturability.

Referring to FIG. 5, in the section of the blade 10, the concave arc line 11 and the convex arc line 12 respectively have M points and N points, and the MN two-point line divides the blade section into the first section and the first section. Two sections with two sections, the area of the first section is S1, and the area of the second section is S2. Specifically, there is a tangent to the concave arc line 11 passing through the point M, which is perpendicular to the MN connection line. There are K points and MK points on the line, so that the MK line is perpendicular to the AB line. Here, when AK/AB=60%, it meets: 55%≤S1/(S1+S2) ≤60%, preferably S1/(S1+S2)=57.1%.

Referring to FIG. 3, the center of the cross-flow wind wheel is defined as point O, and the blades 10 are arranged at intervals along the circumferential direction. The inclination angle of each blade 10 satisfies: 27°≤∠OAB≤30°, preferably ∠OAB=28.87° The diameter of the cross flow wind wheel is d, and the ratio of the size of the blade 10 to the cross flow wind wheel satisfies: 13%≦d/L≦15%, preferably d/L=13.7%.

Based on the first embodiment above, the cross-flow wind wheel of the first embodiment of the present application is compared with the standard cross-flow wind wheel of the prior art. The standard cross-flow wind wheel of the prior art has blades with small ends and large middle Symmetrical wing structure.

Referring to FIG. 6, it can be seen that, compared with the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 1 of the present application increases the maximum air volume by about 7% at the same rotation speed.

Referring to FIG. 7, it can be seen that, compared to the cross-flow wind wheel of the prior art, the power of the cross-flow wind wheel in Example 1 of the present application decreases by 3% under the same air volume.

Referring to FIG. 8, it can be seen that the cross-flow wind wheel of Example 1 of the present application reduces noise by 1 decibel under the same air volume (high air volume) compared to the prior art cross-flow wind turbine; at the same air volume (low air volume) In the case, the noise drops by 1.5 dB.

In the embodiment of the present application, a cross-flow wind wheel, by optimizing the wing-shaped structure of the blade, improves the position distribution and change of the maximum thickness of the blade, and achieves the effects of reducing air volume loss, power and noise.

Referring to FIGS. 9 to 11, Embodiment 2 of the present application provides a cross-flow wind wheel and an air conditioner. The cross-flow wind wheel is provided inside an air conditioner (not shown) to provide heat exchange airflow for a heat exchanger inside the air conditioner. The wind impeller includes two oppositely disposed end plates and a cylindrical impeller disposed between the two end plates. The cylindrical impeller is composed of a plurality of blades 10 arranged in an arc shape at intervals in the circumferential direction, and adjacent blades 10 have The gap 20 for the inflow and outflow of airflow is driven by the drive motor to rotate the crossflow fan, so that the airflow can flow from the gap 20 located on the side of the airflow inlet (above the crossflow wheel) into the interior of the crossflow wheel, forming a flow vortex, and then from the airflow The blade gap 20 on the outlet side (below the cross-flow rotor) flows out.

FIG. 10 shows a cross section of a blade profile of a cross flow wind turbine of the present application. In the cross section of the blade 10, the intersection of the airfoil center line of the blade 10 and the outer and inner ends of the blade is defined as an outer end point A and an inner end point B.

In the cross section of the blade 10, the blade 10 has a concave arc line 11 and a convex arc line 12, the blade 10 has a point D on the concave arc line 11 and an E point on the convex arc line 12, due to the thickness of the blade 10 It is variable. Naturally, the maximum thickness of the blade 10 exists. The maximum thickness is defined by the DE two-point line. Specifically, there is a tangent to the concave arc line 11 through the point D, which is perpendicular to the DE line. The maximum length of the DE line is the maximum thickness of the blade 10. In Example 2 of the present application, the maximum thickness of the blade 10 is thicker than the standard blade of the prior art, satisfying: 13°≤∠DBE<16°, preferably ∠DBE = 13.16°.

Correspondingly, the blade 10 also has a minimum thickness. Similarly, the minimum thickness is defined by the FG two-point line. After the F point, there is a tangent to the concave arc line 11 that is perpendicular to the FG line. The FG line The minimum length of is the minimum thickness of the blade 10, and the ratio between the maximum thickness of the blade 10 and the minimum thickness satisfies: 1.9≤DE/FG≤2.3, preferably DE/FG=2.11.

There are point C on the AB line, and the two points on the CD line make the CD line perpendicular to the AB line. Here, the length ratio between the AC two point line and the AB two point line is limited to satisfy: 61%≤ AC/AB<65%, preferably AC/AB=61.8%. In this way, the position of the maximum thickness of the blade 10 in the chord direction is determined. By improving the position distribution and change of the maximum thickness of the blade 10, the resistance of the air flow is small, and the separation of the air flow on the suction surface can also be delayed , Enhance the function of the blades and increase the air volume; At the same time, because the airflow delays the separation on the suction surface, it can reduce the number of shed vortices, thereby reducing power loss and reducing aerodynamic noise.

Referring to FIG. 11, in the section of the blade 10, the concave arc line 11 and the convex arc line 12 respectively have M points and N points, and the MN two-point line divides the blade section into the first section and the first section. Two sections with two sections, the area of the first section is S1, and the area of the second section is S2. Specifically, there is a tangent to the concave arc line 11 passing through the point M, which is perpendicular to the MN connection line. There are K points on the line and MK two points on the line, making the MK line perpendicular to the AB line. Here, when AK/AB=60%, meet: 51%≤S1/(S1+S2) ≤55%, preferably S1/(S1+S2)=53.6%.

Referring to FIG. 9, the center of the cross-flow wind wheel is defined as point O, and the blades 10 are arranged at intervals along the circumferential direction. The angle of inclination of each blade 10 satisfies: 26°≤∠OAB≤28.5°, preferably ∠OAB=27.38° The diameter of the cross-flow wind wheel is d, and the ratio of the size of the blade 10 to the cross-flow wind wheel satisfies: 13%≦d/L≦15%, preferably d/L=14%.

Based on the second embodiment above, the cross-flow wind wheel of the second embodiment of the present application is compared with the standard cross-flow wind wheel of the prior art. The standard cross-flow wind wheel of the prior art has blades with small ends and large middle Symmetrical wing structure.

Referring to FIG. 12, it can be seen that, compared to the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 2 of the present application increases the maximum air volume by about 5.9% at the same speed.

Referring to FIG. 13, it can be seen that, compared with the cross-flow wind wheel of the prior art, the power of the cross-flow wind wheel of Example 2 of the present application decreases by 3.6% under the same air volume.

Referring to FIG. 14, it can be seen that the cross-flow wind wheel of Example 2 of the present application reduces noise by 1 decibel under the same air volume (high air volume) compared with the prior art cross-flow wind turbine; at the same air volume (low air volume) In this case, the noise drops by 1.2 dB.

In the second embodiment of the present application, the cross-flow wind wheel, by optimizing the blade wing structure, improves the position distribution and change of the maximum thickness of the blade, and achieves the effects of reducing air volume loss, power and noise.

Referring to FIGS. 15-17, Embodiment 3 of the present application provides a cross-flow wind wheel and an air conditioner. The cross-flow wind wheel is provided inside an air conditioner (not shown) to provide heat exchange airflow for a heat exchanger inside the air conditioner. The wind impeller includes two oppositely disposed end plates and a cylindrical impeller disposed between the two end plates. The cylindrical impeller is composed of a plurality of blades 10 arranged in an arc shape at intervals in the circumferential direction, and adjacent blades 10 have The gap 20 for the inflow and outflow of airflow is driven by the drive motor to rotate the crossflow fan, so that the airflow can flow from the gap 20 located on the side of the airflow inlet (above the crossflow wheel) into the interior of the crossflow wheel, forming a flow vortex, and then from the airflow The blade gap 20 on the outlet side (below the cross-flow rotor) flows out.

FIG. 16 shows a cross section of the blade profile of the cross flow wind turbine of the present application. In the cross section of the blade 10, the intersection of the wing-shaped center line of the blade 10 and the outer and inner ends of the blade is defined as the outer end point A and the inner end point B.

In the cross section of the blade 10, the blade 10 has a concave arc line 11 and a convex arc line 12, the blade 10 has a point D on the concave arc line 11 and an E point on the convex arc line 12, due to the thickness of the blade 10 It is variable. Naturally, the maximum thickness of the blade 10 exists. The maximum thickness is defined by the DE two-point line. Specifically, there is a tangent to the concave arc line 11 through the point D, which is perpendicular to the DE line. The maximum length of the DE line is the maximum thickness of the blade 10. In Example 3 of the present application, the maximum thickness of the blade 10 is thicker than the standard blade of the prior art, satisfying: 16°≤∠DBE<23°, preferably ∠DBE = 19.76°.

Correspondingly, the blade 10 also has a minimum thickness. Similarly, the minimum thickness is defined by the FG two-point line. After the F point, there is a tangent to the concave arc line 11 that is perpendicular to the FG line. The FG line The minimum length of is the minimum thickness of the blade 10, and the ratio between the maximum thickness of the blade 10 and the minimum thickness satisfies: 1.8≤DE/FG≤2.2, preferably DE/FG=2.03.

There are point C on the AB line, and the two points on the CD line make the CD line perpendicular to the AB line. Here, the length ratio between the AC two point line and the AB two point line is limited to meet: 65% ≤ AC/AB<75%, preferably AC/AB=70.1%. In this way, the position of the maximum thickness of the blade 10 in the chord direction is determined. By improving the position distribution and change of the maximum thickness of the blade 10, the resistance of the air flow is small, and the separation of the air flow on the suction surface can also be delayed , Enhance the function of the blades and increase the air volume; At the same time, because the airflow delays the separation on the suction surface, it can reduce the number of shed vortices, thereby reducing power loss and reducing aerodynamic noise.

Referring to FIG. 17, in the cross section of the blade 10, the concave arc line 11 and the convex arc line 12 respectively have M points and N points, and the MN two-point line divides the blade section into the first section and the first section. Two sections with two sections, the area of the first section is S1, and the area of the second section is S2. Specifically, there is a tangent to the concave arc line 11 passing through the point M, which is perpendicular to the MN connection line. There are K points and MK points on the line, so that the MK line is perpendicular to the AB line. Here, when AK/AB=60%, it meets: 50%≤S1/(S1+S2) ≤56%, preferably S1/(S1+S2)=53.6%.

Referring to FIG. 15, the center of the cross-flow wind wheel is defined as point O, and the blades 10 are arranged at intervals along the circumferential direction. The inclination angle of each blade 10 satisfies: 26.5°≦∠OAB≦29°, preferably ∠OAB=27.57° The diameter of the cross-flow wind wheel is d, and the ratio of the size of the blade 10 to the cross-flow wind wheel satisfies: 11%≦d/L≦14%, preferably d/L=12.6%.

Based on the third embodiment above, the cross-flow wind turbine of the third embodiment of the present application is compared with the standard cross-flow wind turbine of the prior art. The standard cross-flow wind turbine of the prior art has blades with small ends and large middle Symmetrical wing structure.

Referring to FIG. 18, it can be seen that, compared with the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 3 of the present application increases the maximum air volume by about 5.9% at the same speed.

Referring to FIG. 19, it can be seen that, compared with the cross-flow wind wheel of the prior art, the power of the cross-flow wind wheel of Example 3 of the present application decreases by 6.2% under the same air volume.

Referring to FIG. 20, it can be seen that, compared to the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 3 of the present application reduces noise by 0.8 decibels under the same air volume (high air volume).

In the third embodiment of the present application, the cross-flow wind wheel optimizes the wing-shaped structure of the blade, improves the position distribution and change of the maximum thickness of the blade, and achieves the effects of reducing air volume loss, power and noise.

Referring to FIGS. 21 to 23, Embodiment 4 of the present application provides a cross-flow wind wheel and an air conditioner. The cross-flow wind wheel is provided inside an air conditioner (not shown) to provide heat exchange airflow for a heat exchanger inside the air conditioner. The wind impeller includes two oppositely disposed end plates and a cylindrical impeller disposed between the two end plates. The cylindrical impeller is composed of a plurality of blades 10 arranged in an arc shape at intervals in the circumferential direction, and adjacent blades 10 have The gap 20 for the inflow and outflow of airflow is driven by the drive motor to rotate the crossflow fan, so that the airflow can flow from the gap 20 located on the side of the airflow inlet (above the crossflow wheel) into the interior of the crossflow wheel, forming a flow vortex, and then from the airflow The blade gap 20 on the outlet side (below the cross-flow rotor) flows out.

FIG. 22 shows a cross section of a blade profile of a cross flow wind turbine of the present application. In the cross section of the blade 10, the intersection of the wing-shaped center line of the blade 10 and the outer and inner ends of the blade is defined as an outer end point A and an inner end point B.

In the cross section of the blade 10, the blade 10 has a concave arc line 11 and a convex arc line 12, the blade 10 has a point D on the concave arc line 11 and an E point on the convex arc line 12, due to the thickness of the blade 10 It is variable. Naturally, the maximum thickness of the blade 10 exists. The maximum thickness is defined by the DE two-point line. Specifically, there is a tangent to the concave arc line 11 through the point D, which is perpendicular to the DE line. The maximum length of the DE line is the maximum thickness of the blade 10. In Example 4 of the present application, the maximum thickness of the blade 10 is thicker than the standard blade of the prior art, satisfying: 23°≤∠DBE<31°, preferably ∠DBE = 27.74°.

Correspondingly, the blade 10 also has a minimum thickness. Similarly, the minimum thickness is defined by the FG two-point line. After the F point, there is a tangent to the concave arc line 11 that is perpendicular to the FG line. The FG line The minimum length of is the minimum thickness of the blade 10, and the ratio between the maximum thickness of the blade 10 and the minimum thickness satisfies: 2≤DE/FG≤2.5, preferably DE/FG=2.27.

There are point C on the AB line, and the two points on the CD line make the CD line perpendicular to the AB line. Here, the length ratio of the AC two point line and the AB two point line is limited to meet: 75%≤ AC/AB<85%, preferably AC/AB=76.16%. In this way, the position of the maximum thickness of the blade 10 in the chord direction is determined. By improving the position distribution and change of the maximum thickness of the blade 10, the resistance of the air flow is small, and the separation of the air flow on the suction surface can also be delayed , Enhance the function of the blades and increase the air volume; At the same time, because the airflow delays the separation on the suction surface, it can reduce the number of shed vortices, thereby reducing power loss and reducing aerodynamic noise.

Referring to FIG. 23, in the cross section of the blade 10, the concave arc line 11 and the convex arc line 12 respectively have M points and N points, and the MN two-point line divides the blade section into the first section and the first section. Two sections with two sections, the area of the first section is S1, and the area of the second section is S2. Specifically, there is a tangent to the concave arc line 11 passing through the point M, which is perpendicular to the MN connection line. There are K points and MK points on the line, so that the MK line is perpendicular to the AB line. Here, when AK/AB=60%, it meets: 50%≤S1/(S1+S2) ≤56%, preferably S1/(S1+S2)=53.2%.

Referring to FIG. 21, the center of the cross-flow wind wheel is defined as point O, and the blades 10 are arranged at intervals along the circumferential direction. The angle of inclination of each blade 10 satisfies: 26.5°≤∠OAB≤29°, preferably ∠OAB=27.55° The diameter of the cross-flow wind wheel is d, and the ratio of the size of the blade 10 to the cross-flow wind wheel satisfies: 11%≦d/L≦14%, preferably d/L=12.6%.

Based on the above fourth embodiment, the cross-flow wind wheel of the fourth embodiment of the present application is compared with the standard cross-flow wind wheel of the prior art. The standard cross-flow wind wheel of the prior art has blades with small ends and large middle Symmetrical wing structure.

Referring to FIG. 24, it can be seen that, compared to the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 4 of the present application increases the maximum air volume by about 7.6% at the same speed.

Referring to FIG. 25, it can be seen that, compared with the cross-flow wind wheel of the prior art, the power of the cross-flow wind wheel of Embodiment 4 of the present application decreases by 6% under the same air volume.

Referring to FIG. 26, it can be seen that, compared with the cross-flow wind wheel of the prior art, the cross-flow wind wheel of Example 4 of the present application reduces noise by 1.6 decibels under the same air volume (high air volume).

In the fourth embodiment of the present application, the cross-flow wind wheel optimizes the airfoil structure of the blade, improves the position distribution and change of the maximum thickness of the blade, and achieves the effects of reducing air volume loss, power, and noise.

The embodiments of the present application have been described in detail above with reference to the drawings, but the present application is not limited to the above embodiments, and within the scope of the knowledge possessed by ordinary technical personnel in the technical field, various items can be made without departing from the purpose of the present application Kind of change.

Claims

A cross-flow wind wheel, including blades, characterized by:

In the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as an outer endpoint A and an inner endpoint B, and the outer endpoint A is connected to the inner endpoint B The line is defined as the chord length L;

The blade has a maximum thickness and is defined by the two-point DE line of the blade, and the tangent of the D point of the blade is perpendicular to the DE line, satisfying: 11°≤∠DBE<13°;

The vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 58%≤AC/AB<61%.
The cross-flow wind wheel according to claim 1, wherein the two-point MN line of the blade divides the blade section into a first section and a second section, and the tangent line of the M point of the blade is perpendicular to the MN line , The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2, when AK/AB=60%, Satisfaction: 55%≤S1/(S1+S2)≤60%.
The cross-flow wind wheel according to any one of claims 1-2, wherein the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is connected to the FG The line is vertical, satisfying: 1.8≤DE/FG≤2.2.
The cross-flow wind wheel according to any one of claims 1 to 3, wherein the center of the cross-flow wind wheel is defined as point O, which satisfies: 27°≤∠OAB≤30°.
The cross-flow wind wheel according to any one of claims 1 to 4, wherein the diameter of the cross-flow wind wheel is d, which satisfies: 13%≤d/L≤15%.
A cross-flow wind wheel, including blades, characterized by:

In the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as an outer endpoint A and an inner endpoint B, and the outer endpoint A is connected to the inner endpoint B The line is defined as the chord length L;

The blade has a maximum thickness and is defined by the two-point DE line of the blade, the tangent of the D point of the blade is perpendicular to the DE line, satisfying: 13°≤∠DBE<16°;

The vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 61%≤AC/AB<65%.
The cross-flow wind wheel according to claim 6, wherein the two-point MN line of the blade divides the blade section into a first section and a second section, and the tangent line of the M point of the blade is perpendicular to the MN line , The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2, when AK/AB=60%, Satisfaction: 51%≤S1/(S1+S2)≤53%.
The cross-flow wind wheel according to any one of claims 6-7, wherein the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F-point of the blade is connected to the FG The line is vertical, satisfying: 1.9≤DE/FG≤2.3.
The cross-flow wind wheel according to any one of claims 6-8, wherein the center of the cross-flow wind wheel is defined as point O, which satisfies: 26°≤∠OAB≤28.5°.
The cross-flow wind wheel according to any one of claims 6-9, wherein the diameter of the cross-flow wind wheel is d, satisfying: 13%≤d/L≤15%.
A cross-flow wind wheel, including blades, characterized by:

In the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as an outer endpoint A and an inner endpoint B, and the outer endpoint A is connected to the inner endpoint B The line is defined as the chord length L;

The blade has a maximum thickness and is defined by the two-point DE line of the blade, and the tangent of the D point of the blade is perpendicular to the DE line, satisfying: 16°≤∠DBE<23°;

The vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 65%≤AC/AB<75%.
The cross-flow wind wheel according to claim 11, wherein the two-point MN line of the blade divides the blade section into a first section and a second section, and the tangent line of the M point of the blade is perpendicular to the MN line , The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2, when AK/AB=60%, Satisfaction: 50%≤S1/(S1+S2)≤56%.
The cross-flow wind wheel according to any one of claims 11-12, wherein the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is connected to the FG The line is vertical, satisfying: 1.8≤DE/FG≤2.2.
The cross-flow wind wheel according to any one of claims 11 to 13, wherein the center of the cross-flow wind wheel is defined as point O, which satisfies: 26.5°≤∠OAB≤29°.
The cross-flow wind wheel according to any one of claims 11 to 14, wherein the diameter of the cross-flow wind wheel is d, which satisfies: 11%≤d/L≤14%.
A cross-flow wind wheel, including blades, characterized by:

In the cross section of the blade, the intersection of the blade's wing-shaped center line with the outer and inner ends of the blade is defined as an outer endpoint A and an inner endpoint B, and the outer endpoint A is connected to the inner endpoint B The line is defined as the chord length L;

The blade has a maximum thickness and is defined by the two-point DE line of the blade, the tangent of the D point of the blade is perpendicular to the DE line, satisfying: 23°≤∠DBE<31°;

The vertical connection between the point D of the blade and the AB connection is defined as a DC connection, satisfying: 75%≤AC/AB<85%.
The cross-flow wind wheel according to claim 16, wherein the two-point MN line of the blade divides the blade section into a first section and a second section, and the tangent line of the M point of the blade is perpendicular to the MN line , The vertical connection between the M point of the blade and the AB connection is defined as the MK connection, the area of the first section is S1, and the area of the second section is S2, when AK/AB=60%, Satisfaction: 50%≤S1/(S1+S2)≤56%.
The cross-flow wind wheel according to any one of claims 16 to 17, wherein the blade has a minimum thickness and is defined by the two-point FG line of the blade, and the tangent of the F point of the blade is connected to the FG The line is vertical, satisfying: 2≤DE/FG≤2.5.
The cross-flow wind wheel according to any one of claims 16 to 18, wherein the center of the cross-flow wind wheel is defined as point O, which satisfies: 26.5°≤∠OAB≤29°.
The cross-flow wind wheel according to any one of claims 16 to 19, wherein the diameter of the cross-flow wind wheel is d, which satisfies: 11%≤d/L≤14%.
An air conditioner, characterized by comprising the cross-flow wind wheel according to any one of claims 1-20.