CN209743240U - Axial flow fan blade, air interchanger and air conditioner - Google Patents
Axial flow fan blade, air interchanger and air conditioner Download PDFInfo
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- CN209743240U CN209743240U CN201822165365.6U CN201822165365U CN209743240U CN 209743240 U CN209743240 U CN 209743240U CN 201822165365 U CN201822165365 U CN 201822165365U CN 209743240 U CN209743240 U CN 209743240U
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Abstract
The application provides an axial flow fan blade, a ventilation device and an air conditioner. The axial flow fan blade comprises a hub and a plurality of blades, wherein two surfaces of each blade are respectively a pressure surface on an air outlet side and a suction surface on an air inlet side, the radially outward edge part of each blade is a blade top, a first edge and a second edge are arranged at the blade top of each blade, the first edge bends and extends towards the suction surface, and the second edge bends and extends towards the pressure surface. The axial flow fan blade can improve the acting capacity of the blade, control of the leakage vortex of the blade top of the blade is achieved, and noise of the fan blade is reduced.
Description
Technical Field
The application relates to the technical field of impeller machinery, in particular to an axial flow fan blade, an air interchanger and an air conditioner.
Background
In general, a basic structure of a fan blade includes a hub as a rotating shaft and a plurality of blades radially arranged on the outer periphery of the hub, and the fan blade is driven to rotate by power, so that air flows in from the front edge of the blade, and is blown out from the rear edge of the blade after the pressure of the blade is increased, thereby forming a pressure surface and a suction surface.
In the operation process of the existing axial flow fan blade, a low-pressure area, namely a vortex, is often generated in the middle area of the top of the suction surface, the vortex is mainly caused by the fact that air flows to the low-pressure area of the suction surface through the high-pressure area of the pressure surface of the fan blade, and the phenomenon is called leakage. In addition, boundary layer separation occurs near the leading edge of the suction surface of the blade, resulting in the generation of vortices. In a word, the two conditions can cause the vortex noise of the fan blades, so that the total noise value of the fan is increased, and the overall performance of the whole air conditioner is influenced.
In order to reduce blade tip vortex, in the prior art, the blade tip of the axial flow fan blade is designed into a form that the pressure surface is bent or folded in the direction of the suction surface, as shown in fig. 1 to 6, wherein detailed bending figures are shown in fig. 7 to 8, and detailed folding figures are shown in fig. 9 to 10. The design intent is to control the diffusion of the tip vortex and avoid the secondary flow loss by reducing the pressure difference between the suction surface and the pressure surface at the tip. However, when the pressure difference of the suction pressure surface is reduced, the work capacity of the fan blades is reduced, and the air quantity generated by the fan blades is reduced.
When the axial flow fan blade in the existing design works in a rotating mode, 2 to 10 fan blade blades 4 are uniformly distributed or unevenly distributed upwards on the periphery of a hub 5 to apply work to air to generate air volume. At this time, the suction surface 1 of each fan blade 4 is the windward surface, so the pressure distribution on the surface of the suction surface 1 is a negative value; the pressure surface 3 on the back side of the corresponding fan blade 4 is on the leeward side, and the surface pressure distribution is a positive value. At a point at the interface of the two, there is therefore a significant pressure difference at the blade tip 2, which results in a natural leakage of the air flow from the pressure side 3 through the blade tip 2 to the suction side 1. The greater the pressure differential, the greater the motive force of the leakage flow.
When the blade top 2 of the axial flow fan blade is designed in the prior art, the folding structure shown in fig. 1 to 10 is adopted, and is of an L shape (the lower end of the L is the blade top), or a bending structure, and is of a J shape (the lower end of the J is the blade top), so that the pressure difference between a pressure surface and a suction surface is relieved, and the air flow leakage amount and the influence of the leakage air flow on the main flow are avoided. The key parameters of the flanging structure comprise a flanging included angle a1 or a2, a flanging position D2 and the range of the flanging on the blade top, and the key parameters of the flanging structure comprise a bending radius R1 or R2, a bending position D2 and the range of the bending on the blade top. Obviously, after the structure that the pressure surface is bent towards the suction surface in a single folding mode or in a bending mode is adopted, the working capacity of the blade 4 near the blade top can be reduced, namely the pressure of the pressure surface near the blade top is reduced, the pressure of the suction surface is increased, so that the working capacity of the blade 4 at the position is reduced, and the air volume generated by the axial-flow fan blade is reduced. In particular to an axial flow fan blade for an air conditioner, the main work doing area of the blade 4 is positioned at the top and the tail edge of the blade.
SUMMERY OF THE UTILITY MODEL
In order to solve the problems existing in the prior art, the main objective of the present application is to provide an axial flow fan blade, an air interchanger and an air conditioner, so as to effectively control the diffusion of the tip vortex of the blade.
Another objective of the present application is to provide an axial-flow fan blade, in which two bending or folding structures exist at the same time, so as to control the turbulence degree of the airflow leaking from the blade tip and reduce the turbulence noise generated by the axial-flow fan blade.
At least one embodiment of this application provides an axial fan blade, including wheel hub and a plurality of blade, each the two sides of blade are the pressure surface of air-out side and the suction surface of air inlet side respectively, each the radial outside border position of blade is the blade top, each the blade top department of blade is provided with first limit and second limit, first limit to the suction surface is buckled and is extended, the second limit to the pressure surface is buckled and is extended.
According to an embodiment of the application, the first and second sides are of a bent or hemmed configuration with respect to the blade body.
According to an embodiment of the present application, the maximum outer diameter of the first side is equal to the maximum outer diameter of the second side.
According to an embodiment of the application, the maximum outer diameter of the first side is smaller than the maximum outer diameter of the second side.
According to an embodiment of the present application, the first edge and the second edge are disposed over the entire length of the blade tip.
According to an embodiment of the present application, the first edge and the second edge are disposed at the local range of the blade tip.
According to an embodiment of the application, the maximum outer diameter of the first side is larger than the maximum outer diameter of the second side.
According to an embodiment of the application, the first edge is an arc bend having a first radius, the second edge is an arc bend having a second radius, and the first radius is smaller than the second radius.
According to an embodiment of the application, the first edge is a hem with the blade body having a first included angle, the second edge is a hem with the blade body having a second included angle, and the first included angle is smaller than the second included angle.
According to an embodiment of the application, the first edge is an arc-shaped bend, and the second edge is a folded edge having a second included angle with the blade body.
According to an embodiment of the present application, the first edge and the second edge are disposed within a range of 0.4 to 0.6 of the total length of the blade tip.
According to an embodiment of the present application, it can also be considered that there is provided an air interchanger including an axial flow fan blade, where the axial flow fan blade is the axial flow fan blade as described above.
According to an embodiment of the present application, it can also be considered that an air conditioner is provided, which includes the axial flow fan blade described above.
The beneficial effects obtained by adopting the optional technical scheme are as follows: the structure of the blade top is changed into a three-dimensional space section from the original two-dimensional sideline structure. The structure can play a role in buffering pressure, relieving air flow leakage and controlling flow, thereby improving the working capacity of the axial flow fan blade, increasing the air quantity, and reducing noise by controlling the leakage vortex at the blade top.
compared with the existing fan blade, the fan blade has the advantages that the acting capacity of the fan blade is improved, the control of the leakage vortex of the blade top of the fan blade is realized, and the noise of the fan blade is reduced.
drawings
FIG. 1: the prior edgefold axial flow fan blade is in front view structure schematic diagram.
FIG. 2: the side structure schematic diagram of the existing flanged axial-flow fan blade.
FIG. 3: the prior edgefold axial flow fan blade is in a schematic view of a overlooking structure.
FIG. 4: the prior bending axial flow fan blade is in a front view structure schematic diagram.
FIG. 5: the side view structure of the existing bending axial flow fan blade is schematically shown.
FIG. 6: the prior bent axial flow fan blade is in a schematic view of a overlooking structure.
FIG. 7: a detailed structural schematic diagram of a folding structure of an existing folding axial flow fan blade figure 2 is shown.
FIG. 8: a detailed structural schematic diagram of a folding structure of an existing folding axial flow fan blade figure 3 is shown.
FIG. 9: the detailed structural schematic diagram of the bending structure of the existing bending axial flow fan blade figure 5.
FIG. 10: a detailed structural schematic diagram of a bending structure of an existing bending axial flow fan blade figure 6 is shown.
FIG. 11: an orthographic view structure diagram of the display device is provided.
FIG. 12: the structure schematic diagram is looked to one side in this application embodiment.
FIG. 13: a schematic top view structure of the embodiment of the present application.
FIG. 14: the detailed structure schematic diagram of a leaf top bending in the embodiment of the application.
FIG. 15: the second embodiment of the present application is a schematic front view structure.
FIG. 16: the structure schematic diagram is looked to two sides in this application embodiment.
FIG. 17: the second embodiment of the present application is a schematic top view structure.
FIG. 18: the detailed structure schematic diagram of the second bending structure in the embodiment of the application.
FIG. 19: the two-blade top edge folding or bending area structure schematic diagram is provided.
FIG. 20: the third embodiment of the application shows the folding structure in detail.
FIG. 21: and a relative speed distribution comparison diagram at a position close to the blade top circumference at the downstream of the fan blade.
FIG. 22: and a comparison graph of the speed distribution of the fan blade close to the blade top.
1. A suction surface; 2. leaf tops; 3. a pressure surface; 4. a blade; 5. a hub;
a1, a2, a 3-fold angle;
R1, R2, R3 — bending radii at different points;
D1, D2, D3 — diameters at different points;
b1, b 2-different included angles of circle center.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present application clearer, the technical solutions in the embodiments of the present application will be clearly and completely described below with reference to the drawings in the embodiments of the present application, and it is obvious that the described embodiments are some embodiments of the present application, but not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present application.
The embodiment of the application provides an axial fan blade, mainly includes wheel hub 5 and a plurality of blade 4, each the two sides of blade 4 are respectively for the suction surface 1 of the pressure surface 3 and the air inlet side of air-out side, each the radial outside border position of blade 4 is the blade top 2, each 2 departments of blade top of blade 4 are provided with first limit 21 and second limit 22, first limit 21 to the extension is buckled to suction surface 1, second limit 22 to the extension is buckled to pressure surface 3.
The blade top of the existing fan blade is matched with a static part around the fan blade to form a certain gap, airflow at the gap is relatively disordered, and the fan blade is a main area of secondary flow, leakage and backflow and is a main noise source for generating noise. Therefore, the design of the structure has a remarkable influence on the performance of the fan blade. No matter the blade top of the existing axial flow fan blade is of a hem structure L-shaped or a bending structure J-shaped, and the outermost blade top is a single two-dimensional curve together with the fan blade with a gentle and non-bending structure on the blade top, so that airflow can easily generate secondary flow, leakage, backflow and other turbulent flows through a crack formed by the airflow and surrounding static components.
The axial flow fan blade structure provided by the embodiment of the application has the bending towards the pressure surface 3 and the suction surface 1 respectively at the blade top of the blade 4, so that the blade can be formed, or the structure of the folded edge is Y-shaped, the structure of the blade top and the surrounding static parts form an area with a triangular section, and the crack is changed into a three-dimensional space interval from the original two-dimensional sideline structure. The three-dimensional space shape can be changed by adjusting parameters such as a1/a3, R1/R3, b1/b2 and the like, so that the effects of buffering pressure, relieving air flow leakage and controlling flow can be achieved, the working capacity of the axial flow fan blade can be improved, the air quantity is increased, and the noise is reduced by controlling the leakage vortex at the blade top.
The following is an example of the present application with reference to specific embodiments thereof:
a1, a2 and a3 are folded at included angles;
The bending radii of the R1, R2 and R3 are different;
Diameters at various points of D1, D2, D3;
b1 and b2 are different in included angle of circle center.
Definition a 1: in fig. 7, the two folding surfaces are tangent along the folding line, and the included angle between the two tangent lines is a 1; the same definition a 2: in fig. 8, the two folding surfaces are tangent along the folding line, and the included angle between the two tangent lines is a 2; definition a 3: in fig. 20, the three folding surfaces of the common folding line are tangent along the folding line, the included angle between the tangent of the inner side surface of the blade and the tangent of the first folding surface is a1, and the included angle between the tangent of the inner side surface of the blade and the tangent of the second folding surface is a 3.
The definitions of R1, R2 and R3 are similar to a1, a2 and a3, wherein the different points are tangent lines with the broken line, but tangent circles are formed at the broken line, and the radiuses of the tangent circles are respectively named as R1, R2 and R3.
D1 is a maximum diameter tangent to the outer diameter of the fan blade, namely the outermost diameter of the suction surface bending or flanging structure, and is drawn by taking the rotating shaft as the center of a circle and the rotating shaft as the normal line, D2 is a circle drawn by taking the rotating shaft as the center of a circle and the rotating shaft as the normal line, and the diameter of the circle, namely D2, is obtained by suddenly changing the line by the flanging structure folding line or the bending structure curvature; d3 is the outmost diameter of the bending or folding structure which is drawn by taking the rotating shaft as the center of a circle and the rotating shaft as the normal line and has the pressure surface.
b 1-the starting position point of the outermost round point, bend or fold of the front edge of the blade along the incoming flow direction of the airflow, and the included angle between the connecting line of the two points and the circle center; b 2-the starting position point of the outermost round point, bend or fold of the blade trailing edge along the incoming flow direction of the airflow, and the included angle between the connecting line of the two points and the circle center.
Example one
Fig. 11 is a schematic front view structure, fig. 12 is a schematic side view structure, fig. 13 is a schematic top view structure, and fig. 14 is a detailed structure of a leaf top bend according to an embodiment of the present application.
As shown in the figure, the blade tip 2 of the blade 4 is provided with a bend respectively towards the pressure surface 3 and the suction surface 1, namely a first edge 21 and a second edge 22, and the blade tip 2 is integrally shaped (the upper end is the blade tip 2) or folded edge structure which is in a Y shape (the upper end of the Y is the blade tip 2). The first edge 21 is bent towards the suction surface 1 to one side to form a structure with a bending radius R1, so that the range of a positive pressure area of the pressure surface is not affected, and the acting capacity of the fan blade is guaranteed. The second edge 22 is also bent towards the pressure surface 3 side to generate a structure with the bending radius R3, so that the pressure of the pressure surface 3 near the blade top is ensured to be increased, and the leakage of airflow caused by overlarge pressure difference between the pressure surface 3 and the suction surface 1 is reduced. In this embodiment, the structure of the blade tip 2 is changed from the original two-dimensional edge line structure to a three-dimensional space interval. The structure can play a role in buffering pressure, relieving air flow leakage and controlling flow, thereby improving the working capacity of the axial flow fan blade, increasing the air quantity, and reducing noise by controlling the leakage vortex at the blade top.
It should be understood by those skilled in the art that the full-range double-sided bending embodiment is more suitable for the blade embodiment with low wind speed and large blade area.
in this embodiment, the first side 21 is an arcuate bend having a first radius R1, the second side 22 is an arcuate bend having a second radius R3, and the first radius R1 is greater than the second radius R3.
Example two
Fig. 15 is a schematic front view structure diagram of a second embodiment of the present application, fig. 16 is a schematic side view structure diagram of the second embodiment of the present application, fig. 17 is a schematic top view structure diagram of the second embodiment of the present application, fig. 18 is a detailed structure diagram of a second bending structure of the second embodiment of the present application, and fig. 19 is a schematic structural diagram of a two-leaf top folding edge or a bending region of the second embodiment of the present application.
as shown in the figure, the local range of the blade top 2 of the blade 4 is provided with bends towards the pressure surface 3 and the suction surface 1 respectively, the local range of the blade top, namely b1 in fig. 19 to the initial position point of the outermost round point, bend or fold of the front edge of the blade 4 along the incoming flow direction of the airflow, and the included angle between the two points and the connecting line of the circle center; b 2-the starting point of the outermost round point, bend or fold of the back edge of the blade 4 along the incoming flow direction of the airflow, and the included angle between the connecting line of the two points and the circle center. The whole range of the blade top is a bent or folded structure, so that b1 is 0; if the local range of the leaf apex is defined, b1/(b1+ b2) is (0, 1). In one embodiment, b1/(b1+ b2) is selected to be in the range of (0.4-0.6), i.e., this range is preferred to match the surrounding stationary components. It should be understood by those skilled in the art that the embodiment with the double-sided bend at the local range is more suitable for the blade embodiment with the small blade surface at the higher wind speed.
The structure that this application adopted both sides to bend or hem can be external diameter such as both sides, also can vary external diameter. In fig. 18, D1 is the outermost diameter of the fan blade, that is, the outermost diameter of the bending or flanging structure of the pressure surface 3, and D3 is the outermost diameter of the bending or flanging structure of the suction surface 1, wherein D1 is greater than or equal to D3. Thereby reducing the air leakage from the pressure surface 3 to the suction surface 1, i.e. the air leakage in the direction opposite to the air flow.
Namely, the first side 21 and the second side 22, the blade top 2 is integrally formed (the upper end is the blade top 2), or the folded edge structure is formed in a Y shape (the upper end of the Y is the blade top 2). The first edge 21 is bent towards the suction surface 1 to one side to form a structure with a bending radius R1, so that the range of a positive pressure area of the pressure surface is not affected, and the acting capacity of the fan blade is guaranteed. The second edge 22 is also bent towards the pressure surface 3 side to generate a structure with the bending radius R3, so that the pressure of the pressure surface 3 near the blade top is ensured to be increased, and the leakage of airflow caused by overlarge pressure difference between the pressure surface 3 and the suction surface 1 is reduced. In this embodiment, the first side 21 is an arc-shaped bend having a first radius R1, the second side 22 is an arc-shaped bend having a second radius R3, and the first radius R1 is smaller than the second radius R3.
In this embodiment, the structure of the blade tip 2 is changed from the original two-dimensional edge line structure to a three-dimensional space interval. The structure can play a role in buffering pressure, relieving air flow leakage and controlling flow, thereby improving the working capacity of the axial flow fan blade, increasing the air quantity, and reducing noise by controlling the leakage vortex at the blade top.
EXAMPLE III
Fig. 20 is a detailed view of the folding structure of the third embodiment of the present application. As shown in the figure, the first side 21 and the second side 22 are respectively folded edges, wherein the included angle between the first side 21 and the blade 4 is a1, the included angle between the second side 22 and the blade 4 is a3, the relationship between the two is a1 ≦ a3, or R1 ≦ R3. The bend or fold structure towards the pressure side may even be approximately a straight plate "y" (the upper end of y being the tip), i.e. R3 is infinite or a3 is 180 °.
First set of comparative experiments
In addition, the applicant has conducted a comparative test on the conventional axial flow fan blade shown in fig. 1 to 10 and the axial flow fan blade shown in the first embodiment of the present application, and the structure of the comparative test is shown in table one.
Table I, comparison of simulation calculation result data
| Structure of the product | 3Flow m3/h calculated by simulation |
| Existing axial flow fan blade | 0.6749 |
| Example one | 0.6829 |
As shown in fig. 21, the relative velocity distribution at a position near the blade top circumference downstream of the air outlet blade is shown, and the representative noise with small relative velocity fluctuation is relatively small, so that the noise of the fan blade in the embodiment of the present application has advantages over the existing fan blade structure.
First set of comparative experiments
On the other hand, the applicant performed comparative tests on the conventional axial-flow fan blade shown in fig. 1 to 10 and the axial-flow fan blade shown in the second embodiment of the present application, and the structure of the comparative experiments is shown in table two.
And comparing data of simulation calculation results of the patent structures, wherein the flow generated by the fan blade with the patent structure is slightly larger.
| structure of the product | 3Flow m3/h calculated by simulation |
| fan blade without patent structure | 0.7274 |
| Fan blade with patent structure | 0.7515 |
Second, there is blade simulation calculation result chart comparison table of patent structure
The velocity distribution of the fan blade near the blade top is shown in fig. 22, a diagram a shows the structural expression of the existing fan blade, two large vortices exist at the upstream and downstream of the blade top, and a diagram B shows the structural fan blade according to the embodiment of the present application, the vortices at the upstream and downstream of the blade top are suppressed to a certain extent, and part of turbulent flow is controlled in a space formed by the blade top and a static area around the fan blade.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solutions of the present application, and not to limit the same; although the present application has been described in detail with reference to the foregoing embodiments, it should be understood by those of ordinary skill in the art that: the technical solutions described in the foregoing embodiments may still be modified, or some technical features may be equivalently replaced; and such modifications or substitutions do not depart from the spirit and scope of the corresponding technical solutions in the embodiments of the present application.
Claims (15)
1. The utility model provides an axial fan blade, includes wheel hub (5) and a plurality of blade (4), each the two sides of blade (4) are pressure surface (3) and the suction surface (1) of air inlet side of air-out side respectively, each the radial outside border position of blade (4) is the top of a leaf, its characterized in that:
the blade top of each blade (4) is provided with a first edge (21) and a second edge (22), the first edge (21) bends and extends towards the suction surface (1), and the second edge (22) bends and extends towards the pressure surface (3).
2. The axial-flow blade according to claim 1, characterized in that said first edge (21) and said second edge (22) are of a bent or folded structure with respect to the body of the blade (4).
3. The axial-flow blade according to claim 1, characterized in that the maximum outer diameter of said first edge (21) is equal to the maximum outer diameter of said second edge (22).
4. The axial-flow blade according to claim 1, characterized in that the maximum outer diameter of said first edge (21) is greater than the maximum outer diameter of said second edge (22).
5. The axial-flow fan blade according to claim 1, wherein the first edge (21) and the second edge (22) are arranged over the entire length of the blade tip.
6. The axial-flow fan blade according to claim 1, wherein the first edge (21) and the second edge (22) are disposed in the local range of the blade tip.
7. The axial-flow fan blade according to claim 1, wherein the first edge (21) and the second edge (22) are arranged in a range of 0.4-0.6 of the total length of the blade top.
8. The axial-flow blade according to claim 1, characterized in that the maximum outer diameter of said first edge (21) is smaller than the maximum outer diameter of said second edge (22).
9. The axial-flow fan blade according to claim 1, wherein said first edge (21) is an arc-shaped bend having a first radius, and said second edge (22) is an arc-shaped bend having a second radius.
10. The axial flow fan blade of claim 9, wherein said first radius is less than said second radius.
11. The axial-flow blade according to claim 1, characterized in that said first edge (21) is a folded edge of said blade (4) body having a first angle, and said second edge (22) is a folded edge of said blade (4) body having a second angle.
12. the axial-flow fan blade according to claim 11, wherein the first included angle is smaller than the second included angle.
13. The axial-flow fan blade according to claim 1, wherein the first edge (21) is an arc-shaped bend, and the second edge (22) is a folded edge having a second included angle with the main body of the blade (4).
14. An air interchanger, comprising an axial flow fan blade, characterized in that the axial flow fan blade is the axial flow fan blade of any one of claims 1 to 13.
15. An air conditioner, comprising an axial flow fan blade, characterized in that the axial flow fan blade is the axial flow fan blade of any one of claims 1 to 13.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201822165365.6U CN209743240U (en) | 2018-12-19 | 2018-12-19 | Axial flow fan blade, air interchanger and air conditioner |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201822165365.6U CN209743240U (en) | 2018-12-19 | 2018-12-19 | Axial flow fan blade, air interchanger and air conditioner |
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| Publication Number | Publication Date |
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| CN209743240U true CN209743240U (en) | 2019-12-06 |
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Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109538532A (en) * | 2018-12-19 | 2019-03-29 | 珠海格力电器股份有限公司 | Axial-flow leaf, air interchanger and air conditioner |
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2018
- 2018-12-19 CN CN201822165365.6U patent/CN209743240U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN109538532A (en) * | 2018-12-19 | 2019-03-29 | 珠海格力电器股份有限公司 | Axial-flow leaf, air interchanger and air conditioner |
| WO2020125128A1 (en) * | 2018-12-19 | 2020-06-25 | 珠海格力电器股份有限公司 | Axial flow fan blade, ventilation device and air conditioner |
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