Cross-flow wind wheel and air conditioner with same

Abstract

The cross-flow wind wheel comprises a rotating shaft and a wind wheel body, the wind wheel body is connected with the rotating shaft and comprises a plurality of blades, the blades are arranged in the circumferential direction of the rotating shaft at intervals, and each blade is provided with an inner end close to the rotating shaft, an outer end away from the rotating shaft, a pressure face and a negative pressure face. On the cross section of the wind wheel body, the arc length of the pressure surface is S, the diameter of a peripheral circle which takes the rotation center of the wind wheel body as the circle center and is tangent to the outer end is D1, and the ratio of S to D1 is 0.12-0.18. According to the cross-flow wind wheel provided by the embodiment of the invention, the relationship among the working capacity of the blades, the air volume and the power can be well balanced, so that the cross-flow wind wheel has relatively low power, relatively large air volume and relatively good static pressure rise.

Description

Technical Field

[0001] The present invention relates to the technical field of wind wheels, and in particular to a cross-flow wind wheel and an air conditioner having the same. Background Art

[0002] Crossflow impellers are widely used in air conditioners due to their smooth airflow and low noise. However, unlike axial flow impellers and centrifugal impellers, the airflow passing through the crossflow impeller needs to pass through the blades twice during the air guiding process, which makes it easy for the airflow to form a flow vortex inside the impeller. This vortex affects the flow capacity and noise of the air conditioner to varying degrees.

[0003] In the prior art, in order to reduce noise, inclined blades are usually used or the gaps between blades are set to be unequal, but this design will lead to a reduction in air volume, thereby reducing the working performance of the air conditioner. Summary of the invention

[0004] The present invention aims to solve at least one of the technical problems existing in the prior art. To this end, the present invention proposes a crossflow fan, which can reduce noise while ensuring air volume, which is beneficial to improving the working performance of the air conditioner and solves the technical problem that the crossflow fan in the prior art cannot balance noise and air volume.

[0005] The present invention also aims to provide an air conditioner having the above-mentioned cross-flow impeller.

[0006] According to an embodiment of the present invention, a crossflow wind wheel comprises: a rotating shaft; a wind wheel body, wherein the wind wheel body is connected to the rotating shaft and comprises a plurality of blades, wherein the plurality of blades are arranged at intervals in the circumferential direction of the rotating shaft, and wherein the blades have an inner end close to the rotating shaft, an outer end away from the rotating shaft, a pressure surface, and a negative pressure surface; wherein, on a cross section of the wind wheel body, an arc length of the pressure surface is S, a diameter of an outer circle having a rotation center of the wind wheel body as a center and tangent to the outer end is D1, and a ratio of S to D1 is 0.12 to 0.18.

[0007] According to the crossflow wind wheel of the embodiment of the present invention, by setting the ratio of the arc length of the pressure surface to the diameter of the outer circumference circle with the rotation center of the wind wheel body as the center and tangent to the outer end to 0.12-0.18, the size of the pressure surface is effectively guaranteed, so that the crossflow wind wheel can better balance the relationship between the working capacity of the blades and the air volume and power, thereby ensuring that the crossflow wind wheel has lower power, larger air volume and better static pressure rise, so as to improve the working performance of the crossflow wind wheel.

[0008] In some embodiments, the ratio of S to D1 is 0.14-0.16.

[0009] In some embodiments, on the cross section of the wind wheel body, the same straight line tangent to the inner end and the outer end is a first straight line, the distance between the first straight line and the tangent point between the inner end and the outer end of the blade is L, and the ratio of S to L is 1.02 to 1.12.

[0010] In some embodiments, the thickness of the blade increases first and then decreases from the inner end to the outer end.

[0011] In some embodiments, the maximum thickness position of the blade is located close to the outer end.

[0012] In some embodiments, on the cross section of the wind rotor body, the diameter of the inner circle with the rotation center of the wind rotor body as the center and tangent to the inner end is D2, and the diameter of the circle with the rotation center of the wind rotor body as the center and passing through the center of the maximum thickness position of the blade is Dm, and Dm, D2 and D1 satisfy the following conditions: (Dm-D2) / (D1-D2)=0.5~0.65.

[0013] In some embodiments, on the cross section of the wind wheel body, the same straight line tangent to the inner end and the outer end is a first straight line, the distance between the first straight line and the tangent point of the inner end and the outer end is L, the second straight line at the maximum thickness position of the blade has an intersection with the pressure surface, the distance between the intersection and the first straight line is C, and the ratio of C to L is 0.1 to 0.2.

[0014] In some embodiments, on the cross-section of the wind wheel body, the diameter of the first circle located at the inner end and tangent to both the pressure surface and the negative pressure surface is T1, and the diameter of the second circle located at the outer end and tangent to both the pressure surface and the negative pressure surface is T2, and T1 is greater than or equal to T2.

[0015] In some embodiments, the ratio of T1 to T2 is 1.0 to 1.2.

[0016] In some embodiments, the installation angle of the blade is 20° to 35°.

[0017] In some embodiments, the wind wheel body also includes: a first end plate and a second end plate, the first end plate and the second end plate are arranged opposite to each other, the plurality of blades are connected between the first end plate and the second end plate, and the rotating shaft includes a first shaft segment arranged on the first end plate and a second shaft segment arranged on the second end plate.

[0018] An air conditioner according to an embodiment of the present invention includes the aforementioned cross-flow impeller.

[0019] The air conditioner according to the embodiment of the present invention adopts the aforementioned crossflow impeller to effectively reduce the operating noise of the air conditioner and increase the air volume of the air conditioner, thereby ensuring the operating performance of the air conditioner and improving the user experience.

[0020] Additional aspects and advantages of the invention will become apparent from the following description, or may be learned by practice of the invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] The above and / or additional aspects and advantages of the present invention will become apparent and easily understood from the description of the embodiments in conjunction with the following drawings, in which:

[0022] Figure 1 Schematic diagram of a crossflow impeller according to some embodiments of the present invention.

[0023] Figure 2 1 is a cross-sectional view of a portion of a blade according to some embodiments of the present invention.

[0024] Figure 3 for Figure 2 A partial enlarged view of .

[0025] Figure 4 Graph showing the relationship between the ratio of S to D1 and static pressure according to some embodiments of the present invention.

[0026] Figure 5 FIG. 4 is a graph showing the relationship between the ratio of S to D1 and power according to some embodiments of the present invention.

[0027] Figure 6 Graph showing the relationship between the ratio of S to L and static pressure in some embodiments of the present invention.

[0028] Figure 7 Graph showing the relationship between the ratio of S to L and power according to some embodiments of the present invention.

[0029] Figure 8 The figure is a comparison chart of the air volume and noise of the crossflow impellers according to some embodiments of the present invention and the existing crossflow impellers.

[0030] Reference numerals:

[0031] 1000, crossflow impeller;

[0032] 100, rotation axis;

[0033] 110, first shaft section; 120, second shaft section;

[0034] 200, wind wheel body;

[0035] 210, leaves;

[0036] 211, inner end; 212, outer end; 213, pressure surface; 214, negative pressure surface;

[0037] 220, first end plate;

[0038] 230, second end plate;

[0039] 240, middle partition; 250, middle section;

[0040] SL1, first straight line; SL2, second straight line; P, intersection point; SL3, third straight line. DETAILED DESCRIPTION

[0041] Embodiments of the present invention are described in detail below, examples of which are shown in the accompanying drawings, wherein the same or similar reference numerals throughout represent the same or similar elements or elements having the same or similar functions. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain the present invention, and cannot be understood as limiting the present invention.

[0042] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the referred device or element must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0043] When the existing crossflow impeller is used in the indoor unit of a wall-mounted air conditioner, the air volume is often greatly reduced due to the low pressure of the crossflow impeller. After the air conditioner filter is dirty and clogged, the air volume is easily increased or decreased and the air supply is unstable. Surge phenomenon, which causes the cooling capacity of the air conditioner to be greatly reduced, affecting the user experience.

[0044] Therefore, how to further improve the surge of the crossflow impeller, increase the static pressure of the crossflow impeller, and improve the anti-attenuation characteristics of the crossflow impeller is the goal pursued by relevant researchers.

[0045] However, it should be noted that, unlike axial flow impellers and centrifugal impellers, the airflow inside a crossflow impeller passes through the blades twice, so the air inlet angle and air outlet angle of the blades also change with different circumferential positions. In the air inlet area, the outer end of the outer circumference of the blades of the crossflow impeller is the air inlet end, that is, forming the air inlet angle, and the inner end of the inner circumference of the blades belongs to the air outlet end, that is, forming the air outlet angle; in the exhaust area, the outer end of the outer circumference of the blades of the crossflow impeller belongs to the air outlet end, that is, forming the exhaust angle, and the inner end of the inner circumference of the blades belongs to the air inlet end, that is, forming the air inlet angle.

[0046] Based on the flow characteristics inside the crossflow impeller, the design of the crossflow impeller requires comprehensive consideration of the position of the maximum thickness of the blade, the inner end thickness of the blade, the outer end thickness of the blade, the arc length of the pressure surface of the blade, the chord length of the pressure surface of the blade, the installation angle of the blade, etc., as well as the role of the intake end and the exhaust end as well as the influence of the intake angle and the exhaust angle.

[0047] For example, the design of the arc length and curvature of the pressure surface of the blade cannot only be based on the design considerations of the air outlet, but also need to be based on the design considerations of the air inlet, so as to increase the pressure, increase the air volume and reduce the noise. Otherwise, it will lead to low pressure, high noise, surge, unstable air supply, small flow rate, etc. of the crossflow impeller.

[0048] To this end, the present application proposes a crossflow fan wheel 1000 that can better balance the relationship between the working capacity of the blade 210 and the air volume and power. The specific solution is to set the ratio of the arc length of the pressure surface 213 of the blade 210 to the diameter of the outer circle to 0.12-0.18, so as to effectively ensure the static pressure and air volume of the crossflow fan wheel 1000, improve the surging problem caused by the dirty filter or the increase of condensation water on the heat exchanger when the crossflow fan 1000 is used in the indoor unit of the air conditioner, thereby ensuring the working performance of the air conditioner and improving the user experience.

[0049] The crossflow impeller 1000 according to an embodiment of the present invention will be described below with reference to the accompanying drawings.

[0050] like Figure 1 As shown, a crossflow wind wheel 1000 according to an embodiment of the present invention includes: a rotating shaft 100 and a wind wheel body 200 .

[0051] Among them, Figure 1 As shown, the wind wheel body 200 is connected to the rotating shaft 100 and includes a plurality of blades 210, and the plurality of blades 210 are arranged at intervals in the circumferential direction of the rotating shaft 100, and the blades 210 have an inner end 211 close to the rotating shaft 100, an outer end 212 away from the rotating shaft 100, a pressure surface 213 and a negative pressure surface 214. That is, relative to the rotating shaft 100 of the crossflow wind wheel 1000, the inner end 211 of the blade 210 is arranged close to the rotating shaft 100, and the outer end 212 of the blade 210 is arranged away from the rotating shaft 100.

[0052] In some embodiments, the pressure surface 213 and the negative pressure surface 214 are located between the inner end 211 and the outer end 212 , and the pressure surface 213 and the negative pressure surface 214 are arranged opposite to each other to ensure the structural performance of the blade 210 .

[0053] In addition, by connecting the wind rotor body 200 with the rotating shaft 100 , it is ensured that the rotating shaft 100 can drive the wind rotor body 200 to rotate when rotating, thereby ensuring the working performance of the crossflow wind rotor 1000 .

[0054] In some embodiments, the rotating shaft 100 is connected to the output end of the driving member, and the driving member is used to drive the rotating shaft 100 to rotate, so as to drive the wind wheel body 200 to rotate by the rotating shaft 100. The driving member mentioned here can be a rotating motor.

[0055] The rotation direction of the wind wheel body 200 is the tilting direction of the outer end 212 of the blade 210 , that is, the forward tilting direction.

[0056] like Figure 2 As shown, on the cross section of the wind rotor body 200, the arc length of the pressure surface 213 is S, the diameter of the outer circle with the rotation center of the wind rotor body 200 as the center and tangent to the outer end 212 is D1, and the ratio of S to D1 is 0.12 to 0.18.

[0057] It should be noted that the cross section of the wind rotor body 200 mentioned here can be understood as a plane perpendicular to the length direction of the wind rotor body 200 .

[0058] In some embodiments, on the cross section of the wind wheel body 200, there is a straight line that is tangent to the inner end 211 of the blade 210 and the outer end 212 of the blade 210. The straight line is the first straight line SL1. The point of intersection of the first straight line SL1 and the inner end 211 of the blade 210 is recorded as the first point of intersection, and the point of intersection of the first straight line SL1 and the outer end 212 of the blade 210 is recorded as the second point of intersection. Therefore, the arc length of the pressure surface 213 mentioned above can be understood as the sum of the total lengths of the arcs between the first point of intersection and the second point of intersection.

[0059] For the convenience of description, the diameter of the outer circle with the rotation center of the wind wheel body 200 as the center and tangent to the outer end 212 will be referred to as the diameter of the outer circle, that is, the diameter of the outer circle is D1.

[0060] Among them, when the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is less than 0.12, the arc length of the pressure surface 213 will be too short, thereby causing the work capacity of the blade 210 to be weak and reducing the static pressure of the crossflow wind wheel 1000; when the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is greater than 0.18, the arc length of the pressure surface 213 will be too long, resulting in a small flow rate and a large power of the crossflow wind wheel 1000.

[0061] Therefore, the present application sets the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle to 0.12-0.18, which can improve the working capacity of the blades 210 and ensure that the crossflow wind wheel 1000 has a good static pressure rise, while also improving the flow rate of the crossflow wind wheel 1000 and reducing the power of the crossflow wind wheel 1000.

[0062] It can be seen from the above structure that the crossflow wind wheel 1000 of the embodiment of the present invention sets the ratio of the arc length of the pressure surface 213 to the diameter of the outer circle to 0.12-0.18 to effectively ensure the arc length of the pressure surface 213, so that the crossflow wind wheel 1000 can better balance the relationship between the working capacity of the blades 210 and the air volume and power, thereby ensuring that the crossflow wind wheel 1000 has lower power, larger air volume and better static pressure rise, so as to improve the working performance of the crossflow wind wheel 1000.

[0063] It can be understood that, compared with the prior art, the crossflow blower 1000 of the present application not only has low operating noise, but also has lower power and larger air volume, so as to improve the working performance of the crossflow blower 1000.

[0064] In the description of the present invention, unless otherwise specified, "plurality" means two or more.

[0065] in, Figure 4 and Figure 5 It is shown that when the diameter of the outer circle is 106 mm, the length of the wind wheel body 200 is 680 mm, the rotation speed is 1000 r / min, and the corresponding wind volume is 780 m 3 / h working condition, the relationship between the static pressure value and the power value and the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is shown in the figure. Figure 4 It can be seen from FIG. 2 that when the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is less than 0.12, the static pressure rise is relatively small, and the static pressure value is lower than 20 Pa. Figure 4 and Figure 5 It can be seen that when the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is greater than 0.18, although the static pressure value increases, the power increases significantly. At this time, the power increases by 3w. When the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is in the range of 0.12 to 0.18, the power increase value is in the range of 1w.

[0066] Therefore, the present application sets the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle to 0.12-0.18, so as to better balance the relationship between the working capacity of the blades 210 of the crossflow wind wheel 1000 and the wind volume and power, so that the crossflow wind wheel 1000 has lower power and better static pressure rise.

[0067] In some embodiments, Figure 1 As shown, the wind wheel body 200 further includes a first end plate 220 and a second end plate 230, the first end plate 220 and the second end plate 230 are arranged opposite to each other, a plurality of blades 210 are connected between the first end plate 220 and the second end plate 230, and the rotating shaft 100 includes a first shaft section 110 provided at the first end plate 220 and a second shaft section 120 provided at the second end plate 230. The plurality of blades 210 are connected between the first end plate 220 and the second end plate 230, so that the first end plate 220 and the second end plate 230 cooperate to support and fix the plurality of blades 210, so as to improve the structural stability of the plurality of blades 210, thereby ensuring the working performance of the plurality of blades 210, that is, ensuring the working performance of the crossflow wind wheel 1000.

[0068] At the same time, by configuring the rotating shaft 100 to include a first shaft segment 110 and a second shaft segment 120, and arranging the first shaft segment 110 on the first end plate 220 and the second shaft segment 120 on the second end plate 230, the connection between the wind rotor body 200 and the rotating shaft 100 is ensured, ensuring that the rotating shaft 100 can effectively drive the wind rotor body 200 to rotate, and ensuring that the first shaft segment 110 and the second shaft segment 120 can be relatively arranged at both ends of the wind rotor body 200, so as to facilitate the use of the first shaft segment 110 and the second shaft segment 120 to cooperate in supporting the wind rotor body 200, thereby improving the stability of the wind rotor body 200 during rotation and further ensuring the working performance of the wind rotor body 200.

[0069] In some embodiments, a shaft sleeve is rotatably provided on one of the shaft segments (the first shaft segment 110 or the second shaft segment 120), and the shaft sleeve is fixedly connected to an external structural member. While utilizing the external structural member to support the wind rotor body 200, the shaft segment can also rotate smoothly, thereby ensuring that the rotating shaft 100 can effectively drive the wind rotor body 200 to rotate.

[0070] In some embodiments, Figure 1 As shown, the wind wheel body 200 also includes at least one middle partition 240, and a plurality of blades 210 are arranged between two adjacent middle partitions 240, between the middle partition 240 and the first end plate 220, and between the middle partition 240 and the second end plate 230 to form a middle section 250 of the cross-flow wind wheel 1000.

[0071] It should be noted that the diameter D1 of the outer circle tangent to the outer end 212 mentioned above does not refer to the maximum outer diameter of the middle partition 240. Generally speaking, the maximum outer diameter of the middle partition 240 is 2 mm to 3 mm larger than D1.

[0072] In some embodiments, the crossflow impeller 1000 is formed by injection molding of polymer materials to ensure the structural performance of the crossflow impeller 1000 .

[0073] It should be noted that when the cross-flow wind wheel 1000 is formed by injection molding of polymer materials, the blades 210 of the cross-flow wind wheel 1000 have a demolding slope, and the arc length of the pressure surface 213 and the diameter of the outer circle with the rotation center of the wind wheel body 200 as the center and tangent to the outer end 212 mentioned above refer to the blade profile data of the cross section of the blade 210 in the middle of the longest middle section 250 of the cross-flow wind wheel 1000.

[0074] In some embodiments, the length of the plurality of middle sections 250 of the crossflow impeller 1000 is generally 50 mm to 80 mm, and the demoulding angle of the blades 210 is generally 1 / 400 to 1 / 250.

[0075] Optionally, the draft angle of the blade 210 is 1 / 300.

[0076] In some embodiments, the ratio of S to D1 is 0.14 to 0.16, so as to further ensure the working capacity of the blades 210, ensure that the crossflow impeller 1000 has a good static pressure rise, and at the same time increase the flow rate of the crossflow impeller 1000 and reduce the power of the crossflow impeller 1000.

[0077] In some embodiments, the ratio of S to D1 is 0.14, 0.15, or 0.16, etc.

[0078] In a specific example, the diameter D1 of the outer circle of the blade 210 is 106 mm, and the arc length S of the pressure surface 213 is 15.37 mm. At this time, the ratio of the arc length S of the pressure surface 213 to the diameter D1 of the outer circle is 0.145, so as to effectively balance the relationship between the working capacity of the blade 210 and the wind volume and power.

[0079] In some embodiments, Figure 2 As shown, on the cross section of the wind rotor body 200, the same straight line tangent to the inner end 211 and the outer end 212 is the first straight line SL1, and the distance between the first straight line SL1 and the inner end 211 and the outer end 212 of the blade 210 is L, and the ratio of S to L is 1.02 to 1.12. Here, it means that on the cross section of the wind rotor body 200, the same straight line tangent to both the inner end 211 and the outer end 212 is recorded as the first straight line SL1, and the first straight line SL1 has a tangent point with both the inner end 211 of the blade 210 and the outer end 212 of the blade 210. For ease of understanding, the tangent point between the first straight line SL1 and the inner end 211 of the blade 210 is recorded as the first tangent point, and the tangent point between the first straight line SL1 and the outer end 212 of the blade 210 is recorded as the second tangent point, and the distance between the first tangent point and the second tangent point is L.

[0080] It should be noted that, since the sum of the total lengths of the arcs between the first tangent point and the second tangent point is recorded as the arc length of the pressure surface 213 above, the distance L between the first tangent point and the second tangent point mentioned above can also be understood as the chord length of the pressure surface 213.

[0081] Among them, when the arc length S of the pressure surface 213 is constant, if the chord length L of the pressure surface 213 is too small, that is, the ratio of S to L is greater than 1.12, it will cause the blade 210 to be too bent, or the middle part of the blade 210 to be too convex, thereby increasing the flow loss and increasing the power of the crossflow wind wheel 1000; when the arc length S of the pressure surface 213 is constant, if the chord length L of the pressure surface 213 is too large, that is, the ratio of S to L is less than 1.02, it will cause the blade 210 to be too straight, which will weaken the static pressure lift of the blade 210.

[0082] That is to say, when the ratio of S to L is less than 1.02, the work capacity of the blade 210 is weak and the static pressure is low; when the ratio of S to L is greater than 1.12, although the work capacity of the blade 210 is enhanced, the power consumption of the crossflow wind wheel 1000 will be significantly increased, the efficiency of the wind wheel body 200 will be reduced, and the small vortices in the internal flow of the crossflow wind wheel 1000 will increase, which will also increase the aerodynamic noise.

[0083] Therefore, the present application sets the ratio of S to L to 1.02-1.12 to effectively balance the relationship between the static pressure rise and power of the blades 210 of the crossflow wind wheel 1000, so that the crossflow wind wheel 1000 has lower power and better static pressure rise to improve the working performance of the crossflow wind wheel 1000.

[0084] in, Figure 6 and Figure 7 It is shown that when the diameter of the outer circle is 106 mm, the length of the wind wheel body 200 is 680 mm, the rotation speed is 1000 r / min, and the corresponding wind volume is 780 m 3 / h working condition, the relationship between the static pressure value and the power value and the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 is shown in FIG. Figure 6 It can be seen from FIG. 2 that when the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 is less than 1.02, the static pressure rise is relatively small, and the static pressure value is lower than 20 Pa at this time; Figure 4 and Figure 5 It can be seen that when the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 is greater than 1.12, although the static pressure value increases, the power increases significantly. At this time, the power increases by about 4w. When the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 is in the range of 1.02 to 1.12, the power increase value is in the range of 1.5w.

[0085] Therefore, the present application sets the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 to 1.02-1.12, so as to better balance the relationship between the working capacity of the blades 210 of the crossflow wind wheel 1000 and the wind volume and power, so that the crossflow wind wheel 1000 has lower power and better static pressure rise.

[0086] In some embodiments, the ratio of S to L is 1.05 to 1.1, so as to effectively balance the relationship between the static pressure rise and power of the blades 210 of the crossflow wind wheel 1000, so that the crossflow wind wheel 1000 has lower power and better static pressure rise, thereby improving the working performance of the crossflow wind wheel 1000.

[0087] In some embodiments, the ratio of S to L is 1.05, 1.06, 1.07, 1.08, 1.09 or 1.1, etc.

[0088] In a specific example, the diameter D1 of the outer circle of the blade 210 is 106 mm, the arc length S of the pressure surface 213 is 15.37 mm, and the chord length L of the pressure surface 213 is 14.63 mm. At this time, the ratio of the arc length S of the pressure surface 213 to the chord length L of the pressure surface 213 is 1.05, so that the cross-flow wind wheel 1000 has better anti-surge ability and anti-dirt and blockage ability, and at the same time, the cross-flow wind wheel 1000 has better static pressure rise and a larger air volume value.

[0089] In some embodiments, Figure 2 and Figure 3 As shown, the thickness of the blade 210 increases first and then decreases from the inner end 211 to the outer end 212. That is, in the direction from the inner end 211 to the outer end 212, the thickness of the blade 210 increases first and then decreases, so that the maximum thickness position of the blade 210 can be formed between the inner end 211 and the outer end 212, avoiding flow separation on the negative pressure surface 214 during the air intake and air outlet process, thereby reducing the noise generated by the crossflow impeller 1000 during operation.

[0090] The thickness of the blade 210 mentioned here may be understood as the maximum length of a vertical line between the pressure surface 213 and the negative pressure surface 214 of the blade 210 , which is perpendicular to the pressure surface 213 .

[0091] In some embodiments, the maximum thickness of the blade 210 is 0.01 to 0.015 times the diameter of the wind wheel body 200 , that is, when the diameter D1 of the outer circumference of the blade 210 is 100 mm, the maximum thickness of the blade 210 is 1 mm to 1.5 mm.

[0092] In some embodiments, Figure 2 and Figure 3As shown, the maximum thickness position Tmax of the blade 210 is arranged close to the outer end 212 to further avoid flow separation on the negative pressure surface 214 during the air intake and air outlet process, thereby reducing the noise generated by the crossflow impeller 1000 during operation and ensuring the working performance of the crossflow impeller 1000.

[0093] In some embodiments, Figure 2 As shown, on the cross section of the wind rotor body 200, the diameter of the inner circle with the rotation center of the wind rotor body 200 as the center and tangent to the inner end 211 is D2, and the diameter of the circle with the rotation center of the wind rotor body 200 as the center and passing through the maximum thickness position Tmax of the blade 210 is Dm. Dm, D2 and D1 satisfy the following conditions: (Dm-D2) / (D1-D2)=0.5~0.65. Among them, when the ratio of (Dm-D2) / (D1-D2) is less than 0.5, the maximum thickness position Tmax of the blade 210 will be close to the inner end 211 of the blade 210. This will cause the negative pressure surface 214 of the blade 210 to easily experience flow separation in the air intake area of ​​the crossflow wind wheel 1000 during actual application, thereby increasing the noise in the air intake area, that is, increasing the working noise of the wind wheel body 200, and causing an increase in air intake loss; when the ratio of (Dm-D2) / (D1-D2) is greater than 0.65, in the exhaust area, the negative pressure surface 214 of the blade 210 is prone to flow separation, thereby increasing the noise in the exhaust area, causing an increase in the air outlet loss, and easily generating discontinuous vortex shedding sound, thereby increasing the noise value of the crossflow wind wheel 1000 and increasing the static pressure loss.

[0094] Therefore, the present application sets (Dm-D2) / (D1-D2) to 0.5~0.65 to effectively solve the technical problem that flow separation is prone to occur on the negative pressure surface 214 of the blade 210 in the air intake area and the exhaust area, thereby reducing the noise and static pressure loss of the crossflow wind wheel 1000, and making the crossflow wind wheel 1000 have a better static pressure rise.

[0095] In some embodiments, the blade height of the blade 210 is defined as Dh, Dh=(D1-D2) / 2. The above setting allows the maximum thickness position Tmax of the blade 210 to be located at 0.5 to 0.65 times the blade height.

[0096] In some embodiments, Dm, D2 and D1 satisfy the following condition: (Dm-D2) / (D1-D2)=0.55~0.6, so that the maximum thickness position Tmax of the blade 210 can be located in the upper half of the blade height, so that the maximum thickness position Tmax of the blade 210 can be close to the outer end 212 of the blade 210, reducing the noise and static pressure loss of the crossflow impeller 1000.

[0097] In some embodiments, (Dm-D2) / (D1-D2)=0.55, 0.56, 0.565, 0.57, 0.58, 0.59 or 0.6, etc.

[0098] In some embodiments, Figure 3 As shown, on the cross section of the wind rotor body 200, the same straight line tangent to the inner end 211 and the outer end 212 is the first straight line SL1, and the distance between the first straight line SL1 and the tangent point of the inner end 211 and the outer end 212 is L. The second straight line SL2 where the maximum thickness position Tmax of the blade 210 is located has an intersection point P with the pressure surface 213, and the distance between the intersection point P and the first straight line SL1 is C, and the ratio of C to L is 0.1 to 0.2. Here, it means that the second straight line SL2 perpendicular to the pressure surface 213 is at the maximum thickness position Tmax of the blade 210, and there is an intersection point P between the second straight line SL2 and the pressure surface 213, and the ratio of the distance C between the intersection point P and the first straight line SL1 to the chord length L of the pressure surface 213 is 0.1 to 0.2.

[0099] The distance C between the intersection point P and the first straight line SL1 mentioned here can be understood as the length of a straight line passing through the intersection point P and perpendicular to the first straight line SL1. The straight line can be understood as Figure 3 The third straight line SL3 in the figure, that is, the distance C between the intersection point P and the first straight line SL1 is the length of the third straight line SL3.

[0100] In the description of the present invention, features defined as “first”, “second”, and “third” may explicitly or implicitly include one or more such features, and are used to distinguish and describe the features, without any distinction of order or importance.

[0101] It should be noted that when the ratio of C to L is less than 0.1, the curvature of the blade 210 will be too small, that is, the blade 210 will be too straight, which will easily lead to a decrease in the static pressure of the crossflow impeller 1000, which is not conducive to overcoming resistance and is prone to surge; when the ratio of C to L is greater than 0.2, the curvature of the blade 210 will be too large, that is, the blade 210 will be too convex. At this time, the air outlet flow area of ​​the negative pressure surface 214 of the blade 210 is prone to airflow separation, and at the same time will significantly increase the power of the motor.

[0102] Therefore, the present application sets the ratio of C to L to 0.1-0.2 to effectively ensure the curvature of the blade 210, so that the crossflow impeller 1000 has better anti-surge capability, better static pressure rise and larger air volume value.

[0103] In some embodiments, the ratio of C to L is 0.12 to 0.18, so as to further ensure the anti-surge capability, static pressure rise and air volume value of the crossflow impeller 1000.

[0104] In some embodiments, the ratio of C to L is 0.12, 0.13, 0.14, 0.15, 0.16, 0.17 or 0.18, etc.

[0105] In a specific example, the diameter D1 of the outer circle of the blade 210 is 106 mm, the chord length L of the pressure surface 213 is 14.63 mm, the distance C between the intersection P and the first straight line SL1 is 2.1 mm, and the ratio of C to L is 0.1435 to ensure the working performance of the crossflow wind wheel 1000.

[0106] In some embodiments, Figure 3 As shown, on the cross section of the wind wheel body 200, the diameter of the first circle located at the inner end 211 and tangent to the pressure surface 213 and the negative pressure surface 214 is T1, and the diameter of the second circle located at the outer end 212 and tangent to the pressure surface 213 and the negative pressure surface 214 is T2, and T1 is greater than or equal to T1. That is to say, at the inner end 211 of the blade 210, there is a first circle tangent to the pressure surface 213 and the negative pressure surface 214, and the diameter of the first circle is T1; at the outer end 212 of the blade 210, there is a second circle tangent to the pressure surface 213 and the negative pressure surface 214, and the diameter of the second circle is T2, and the diameter T1 of the first circle is greater than or equal to the diameter T2 of the second circle, which can help ensure smooth outlet flow of the blade 210, thereby reducing aerodynamic noise.

[0107] In some embodiments, the ratio of T1 to T2 is 1.0 to 1.2, so that the diameter T1 of the first circle can be greater than or equal to the diameter T2 of the second circle, thereby ensuring smooth flow at the outlet of the blade 210 and reducing aerodynamic noise, that is, reducing the noise generated by the crossflow impeller 1000 during operation.

[0108] In some embodiments, the ratio of T1 to T2 is 1.0, 1.1, 1.2, etc.

[0109] In a specific example, the diameter T1 of the first circle is 0.5 mm, and the diameter T2 of the second circle is 0.45 mm. At this time, the ratio of T1 to T2 is 1.1, so that the diameter T1 of the first circle is set to be larger than the diameter T2 of the second circle.

[0110] In some embodiments, the installation angle of the blade 210 is 20° to 35°. Figure 2 As shown in A, when the installation angle of the blade 210 is less than 20°, the airflow noise will increase; when the installation angle of the blade 210 is greater than 35°, the work capacity of the blade 210 will be weakened and the static pressure will be reduced.

[0111] Therefore, the present application sets the installation angle of the blade 210 to 20° to 35°, so that the crossflow impeller 1000 has lower airflow noise, larger air volume and better static pressure rise.

[0112] It should be noted that, in some embodiments, on the cross section of the wind rotor body 200, the first straight line SL1 is extended toward the outer circle tangent to the outer end 212 and connected to the outer circle to form an intersection, and the intersection is connected with the rotation center of the wind rotor body 200 to form a center line RL. The installation angle of the blade 210 mentioned above can be understood as the angle between the center line RL and the first straight line SL1.

[0113] In some embodiments, the installation angle of the blades 210 is 25° to 32°, so as to further reduce the airflow noise and ensure the working capacity of the blades 210, so that the crossflow impeller 1000 has a better static pressure rise.

[0114] In some embodiments, the installation angle of the blade 210 is 25°, 26°, 27°, 28°, 29°, 30°, 31° or 32°, etc.

[0115] In a specific example, the diameter D1 of the outer circumference of the blade 210 is 106 mm, and the installation angle of the blade 210 is 27°.

[0116] In summary, the crossflow wind wheel 1000 of the present application can better balance the relationship between the working capacity of the blades 210 and the air volume and power by creatively setting the arc length S of the pressure surface 213, the chord length L of the pressure surface 213, the maximum thickness position Tmax of the blades 210, the installation angle of the blades 210, etc.

[0117] in, Figure 8 FIG. 1 shows a comparison of the wind volume and noise of the crossflow wind wheel 1000 of the present application and a conventional crossflow wind wheel when the diameter D1 of the outer circle is 100 mm, the length of the wind wheel body 200 is 680 mm, and the rotation speed is 900 r / min. Figure 8 It can be seen that the noise of the crossflow impeller 1000 of the present application is about 2dB lower than that of the conventional crossflow impeller, and has better resistance to wind volume attenuation and surge.

[0118] The crossflow impeller 1000 of the present application will be described in detail below with reference to the accompanying drawings.

[0119] like Figure 1 As shown, the crossflow wind wheel 1000 includes a rotating shaft 100 and a wind wheel body 200 .

[0120] Among them, Figure 1As shown, the wind wheel body 200 also includes a first end plate 220, a second end plate 230 and a plurality of blades 210. The first end plate 220 and the second end plate 230 are arranged opposite to each other, and the plurality of blades 210 are connected between the first end plate 220 and the second end plate 230 and are arranged at intervals in the circumferential direction of the rotating shaft 100.

[0121] like Figure 1 As shown, the rotating shaft 100 includes a first shaft segment 110 and a second shaft segment 120 . The first shaft segment 110 is disposed on the first end plate 220 , and the second shaft segment 120 is disposed on the second end plate 230 , so that the wind wheel body 200 is connected to the rotating shaft 100 .

[0122] Combination Figure 1 and Figure 2 As shown, the blade 210 has an inner end 211 close to the rotating axis 100, an outer end 212 away from the rotating axis 100, a pressure surface 213 and a negative pressure surface 214. On the cross section of the wind rotor body 200, the arc length of the pressure surface 213 is S, and the diameter of the outer circle with the rotation center of the wind rotor body 200 as the center and tangent to the outer end 212 is D1. The ratio of S to D1 is 0.145.

[0123] like Figure 2 As shown, on the cross section of the wind wheel body 200, the same straight line tangent to the inner end 211 and the outer end 212 is the first straight line SL1, the distance between the first straight line SL1 and the tangent point of the inner end 211 and the outer end 212 of the blade 210 is L, and the ratio of S to L is 1.05.

[0124] like Figure 2 and Figure 3 As shown, the thickness of the blade 210 increases first and then decreases from the inner end 211 to the outer end 212 , and the maximum thickness position Tmax of the blade 210 is arranged close to the outer end 212 .

[0125] like Figure 2 As shown, on the cross section of the wind rotor body 200, the diameter of the inner circle with the rotation center of the wind rotor body 200 as the center and tangent to the inner end 211 is D2, and the diameter of the circle with the rotation center of the wind rotor body 200 as the center and passing through the maximum thickness position Tmax of the blade 210 is Dm, (Dm-D2) / (D1-D2)=0.565.

[0126] like Figure 3 As shown, the second straight line SL2 where the maximum thickness position Tmax of the blade 210 is located has an intersection point P with the pressure surface 213 , the distance between the intersection point P and the first straight line SL1 is C, and the ratio of C to L is 0.1435.

[0127] like Figure 3As shown, on the cross section of the wind wheel body 200, the diameter of the first circle located at the inner end 211 and tangent to both the pressure surface 213 and the negative pressure surface 214 is T1, T1=0.5mm, and the diameter of the second circle located at the outer end 212 and tangent to both the pressure surface 213 and the negative pressure surface 214 is T2, T2=0.45mm.

[0128] like Figure 2 As shown, the installation angle A of the blade 210 is 27°.

[0129] An air conditioner according to an embodiment of the present invention will be described below.

[0130] An air conditioner according to an embodiment of the present invention includes: a crossflow impeller 1000 .

[0131] The crossflow wind wheel 1000 is the aforementioned crossflow wind wheel 1000 , and the crossflow wind wheel 1000 will not be described in detail here.

[0132] It can be seen from the above structure that the air conditioner according to the embodiment of the present invention adopts the aforementioned cross-flow fan wheel 1000 to effectively reduce the working noise of the air conditioner and increase the air volume of the air conditioner, thereby ensuring the working performance of the air conditioner and improving the user experience.

[0133] In the description of the present invention, it should be noted that, unless otherwise clearly specified and limited, the terms "installation" and "connection" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection. For ordinary technicians in this field, the specific meanings of the above terms in the present invention can be understood according to specific circumstances.

[0134] The crossflow impeller 1000 according to the embodiment of the present invention and other structures of the air conditioner having the same are well known to those skilled in the art and will not be described in detail here.

[0135] In the description of this specification, the description with reference to the terms "embodiment", "example", etc. means that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic representation of the above terms does not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner.

[0136] Although the embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions and variations may be made to the embodiments without departing from the principles and spirit of the present invention, and that the scope of the present invention is defined by the claims and their equivalents.

Claims

1. A crossflow impeller, It is characterized in that include: Axis of rotation; A wind rotor body, the wind rotor body is connected to the rotating shaft and comprises a plurality of blades, the plurality of blades are arranged at intervals in the circumferential direction of the rotating shaft, and the blades have an inner end close to the rotating shaft, an outer end away from the rotating shaft, a pressure surface and a negative pressure surface; Among them, on the cross section of the wind rotor body, the arc length of the pressure surface is S, the diameter of the outer circle with the rotation center of the wind rotor body as the center and tangent to the outer end is D1, and the ratio of S to D1 is 0.12 to 0.

18.

2. The crossflow impeller according to claim 1, It is characterized in that The ratio of S to D1 is 0.14 to 0.

16.

3. The crossflow impeller according to claim 1, It is characterized in that On the cross section of the wind wheel body, the same straight line tangent to the inner end and the outer end is a first straight line, the distance between the first straight line and the tangent point between the inner end and the outer end of the blade is L, and the ratio of S to L is 1.02 to 1.

12.

4. The crossflow impeller according to claim 1, It is characterized in that The thickness of the blade increases first and then decreases from the inner end to the outer end.

5. The crossflow impeller according to claim 4, It is characterized in that The maximum thickness position of the blade is arranged close to the outer end.

6. The crossflow impeller according to claim 4, It is characterized in that On the cross section of the wind rotor body, the diameter of the inner circle with the rotation center of the wind rotor body as the center and tangent to the inner end is D2, the diameter of the circle with the rotation center of the wind rotor body as the center and passing through the center of the maximum thickness position of the blade is Dm, and Dm, D2 and D1 satisfy the following conditions: (Dm-D2) / (D1-D2)=0.5~0.

65.

7. The crossflow impeller according to claim 4, It is characterized in that On the cross section of the wind wheel body, the same straight line tangent to the inner end and the outer end is a first straight line, and the distance between the first straight line and the tangent point of the inner end and the outer end is L. The second straight line at the maximum thickness position of the blade has an intersection with the pressure surface, and the distance between the intersection and the first straight line is C. The ratio of C to L is 0.1 to 0.

2.

8. The crossflow impeller according to claim 4, It is characterized in that On the cross section of the wind wheel body, the diameter of the first circle located at the inner end and tangent to both the pressure surface and the negative pressure surface is T1, the diameter of the second circle located at the outer end and tangent to both the pressure surface and the negative pressure surface is T2, and T1 is greater than or equal to T2.

9. The crossflow impeller according to claim 8, It is characterized in that The ratio of T1 to T2 is 1.0 to 1.

2.

10. The crossflow impeller according to any one of claims 1 to 9, It is characterized in that The installation angle of the blade is 20° to 35°.

11. The crossflow impeller according to any one of claims 1 to 9, It is characterized in that The wind wheel body also includes: A first end plate and a second end plate, the first end plate and the second end plate are arranged opposite to each other, a plurality of blades are connected between the first end plate and the second end plate, and the rotating shaft includes a first shaft section arranged on the first end plate and a second shaft section arranged on the second end plate.

12. An air conditioner, It is characterized in that It comprises a crossflow wind wheel according to any one of claims 1-11.

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