Cross-flow impeller and air conditioner

Abstract

The utility model provides a cross-flow impeller and an air conditioner, and relates to the technical field of air conditioners. The cross-flow impeller comprises a wheel disc and a plurality of blades arranged in the circumferential direction of the wheel disc. The outlet angle of the blade is beta1, and the value range of beta1 meets the following relational expression that beta1 is larger than or equal to 15 degrees and smaller than or equal to 30 degrees. And the value range of beta2 meets the following relational expression: beta2 is more than or equal to 75 degrees and less than or equal to 90 degrees. By reasonably setting the value ranges of the inlet angles and the outlet angles of the blades, the aerodynamic performance, the efficiency and the working stability of the cross-flow impeller can be improved, and then the air supply amount of the air conditioner can be increased.

Description

TECHNICAL FIELD

[0001] The utility model relates to air conditioning technical field, specifically, a through flow impeller and air conditioner. BACKGROUND

[0002] The through flow impeller is widely used in the air conditioning field compared with the traditional axial fan and centrifugal fan and has the advantages of high efficiency, quiet, energy saving and airflow uniform distribution. Especially in the cylindrical cabinet machine application has the advantage.

[0003] The inlet angle and the outlet angle are two important parameters of the blade of the through flow impeller, the angle when airflow enters and leaves the blade. The two angles have a crucial influence on the aerodynamic performance, efficiency and working stability of the through flow fan.

[0004] The value setting of the inlet angle and the outlet angle of the existing through flow impeller is unreasonable, when the inlet angle or the outlet angle is set too large or too small, airflow may separate on the blade surface, vortex is formed, finally leads to the aerodynamic performance, efficiency and working stability of the through flow impeller are affected, and then the air supply of the air conditioner is affected. UTILITY MODEL CONTENTS

[0005] The utility model solves the problem that the value setting of the inlet angle and the outlet angle of the existing through flow impeller is unreasonable, when the inlet angle or the outlet angle is set too large or too small, airflow may separate on the blade surface, vortex is formed, finally leads to the aerodynamic performance, efficiency and working stability of the through flow impeller are affected, and then the air supply of the air conditioner is affected.

[0006] To solve the above problem, the utility model provides a kind of through flow impeller and air conditioner, by the value range of the inlet angle and the outlet angle of blade can be reasonably set to improve the aerodynamic performance, efficiency and working stability of through flow impeller, and then the air supply of air conditioner can be increased.

[0007] Firstly, the application provides a kind of through flow impeller, including wheel disc and the multiple blades of setting in the wheel disc circumferential, the outlet angle of the blade is β1, the value range of β1 meets the following relationship formula:

[0008] 15 °≤β1≤30 °;

[0009] The inlet angle of the blade is β2, the value range of β2 meets the following relationship formula:

[0010] 75 °≤β2≤90 °;

[0011] An end of the blade close to the outer periphery of the disc is an outer blade end, an end of the blade at the inner periphery of the disc is an inner blade end, the blade has a mean camber surface in the thickness direction of the blade, and the mean camber surface is a mean camber line in the projection of the disc; a line connecting an end of the mean camber line at the inner blade end and the center of the disc is an inner blade diameter R2, and a line connecting an end of the mean camber line at the outer blade end and the center of the disc is an outer blade diameter R1.

[0012] The inlet angle is an included angle between a tangent of the mean camber line close to the end of the inner blade end and a perpendicular of the inner blade diameter R2, and the outlet angle is an included angle between a tangent of the mean camber line close to the end of the outer blade end and a perpendicular of the outer blade diameter R1.

[0013] The application sets the outlet angle in the above range to ensure that the airflow is smoothly discharged from the blade surface, reducing the diffusion and separation of the airflow. A smaller outlet angle can make the airflow more concentrated, avoiding separation of the airflow at the trailing edge of the blade, thereby improving the static pressure output and flow rate of the cross-flow impeller, helping to reduce the turbulence and resistance of the airflow, reduce energy loss, and improve the aerodynamic efficiency of the fan blade. Setting the inlet angle in the above range can ensure that the airflow enters the blade surface at a nearly vertical angle, reducing the separation of the airflow at the leading edge of the blade. A larger inlet angle can make the airflow more smoothly adhere to the blade surface, avoiding the generation of airflow separation and vortex, thereby improving the aerodynamic efficiency of the fan blade, and also reducing the initial resistance of the airflow at low-speed start. Overall, the combination of the range of values of the inlet angle and the outlet angle can ensure that the airflow flows more smoothly on the entire blade surface. A larger inlet angle can make the airflow enter the blade at a nearly vertical angle, and a smaller outlet angle can make the airflow more concentrated, which can reduce the separation and vortex of the airflow, improve the aerodynamic efficiency of the cross-flow fan, and thereby improve the air volume and power of the air conditioner.

[0014] In an optional embodiment, the value of β1 is 18°, and the value of β2 is 83.6°.

[0015] The application sets the value of β1 to 18° and the value of β2 to 83.6° to improve the aerodynamic efficiency of the cross-flow fan, and thereby improve the air volume and power of the air conditioner.

[0016] In an optional embodiment, the thickness of the blade gradually thins from the inner blade end to the outer blade end.

[0017] The application gradually thins the blade thickness from the inner side end of the blade to the outer side end of the blade, which can optimize the guidance of the airflow, reduce the separation of the airflow on the blade surface, and avoid the generation of vortex. The outer side end of the blade is relatively thin, which can effectively reduce the airflow resistance, reduce the power consumption of the fan blade, and improve the overall efficiency. The inner side end of the blade needs to provide sufficient thickness to ensure mechanical strength and rigidity to avoid deformation or vibration during high-speed rotation because the airflow speed is relatively low.

[0018] In an optional embodiment, the inner side end of the blade and the outer side end of the blade are both circular arcs.

[0019] In the embodiment, the inner side end and the outer side end of the blade are both set as circular arcs, which can optimize the entry and exit of the airflow, reduce the generation of airflow separation and vortex.

[0020] In an optional embodiment, the inner side end of the blade has an inscribed circle radius Rm, and the outer side end of the blade has an inscribed circle radius Rn, and Rm and Rn satisfy the following relationship:

[0021] Rm=k*Rn;

[0022] Wherein, 1.2≤k≤3.

[0023] The application makes the radii of the inscribed circles at both ends satisfy the above value relationship, which can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan.

[0024] In an optional embodiment, the diameter of the inscribed circle of the inner side end of the blade is 1mm, and the diameter of the inscribed circle of the outer side end of the blade is 0.4mm.

[0025] The application sets the radii of the inscribed circles at both ends to the above values, which can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan.

[0026] In an optional embodiment, the blade has a pressure surface and a suction surface, both of which are arc surfaces and are tangent to the inscribed circles of the inner side end and the outer side end of the blade, and the middle arc line is a circular arc.

[0027] The application makes the projection of the middle arc surface on the wheel disc a circular arc, which can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan.

[0028] In an optional embodiment, the length of the line connecting one end of the blade close to the outer periphery of the wheel disc to the center of the wheel disc is R1, the length of the line connecting one end of the blade close to the inner periphery of the wheel disc to the center of the wheel disc is R2, the installation angle of the blade is a, the chord length of the blade is L, the number of the blades is Z, R1, R2, L, a and Z satisfy the following relationship:

[0029] Lcos a=k1*(R1-R2);

[0030] wherein 0.6≤k1≤0.8.

[0031] (R1-Lcos a) / R2<k2*cos(360 / Z);

[0032] wherein K2 is 1.1.

[0033] The embodiment sets the parameters of the cross-flow impeller to meet the above relationship, which can ensure that the effective length of the blade in the airflow direction and its radial expansion amount maintain a reasonable proportion to optimize the guidance and distribution of the airflow. By adjusting the installation angle a and the chord length L of the blade, the effective length of the blade 153 in the airflow direction determines the flow path of the airflow on the blade surface, so that the airflow enters and exits the blade smoothly, reduces vortex and separation phenomenon, and thus improves the aerodynamic efficiency of the impeller. The radial expansion amount (R1-R2) of the blade affects the rigidity of the blade, and the value of the effective length in the airflow direction can balance the rigidity and aerodynamic force of the blade to ensure its stability and reliability under working conditions. Through the above formula, the cross-flow impeller can operate efficiently and stably, thereby improving the air supply capacity of the air conditioner. Secondly, (R1-Lcos a) / R2<k2*cos(360 / Z) forms a constraint condition for the geometric structure of the blade and the airflow distribution, which can ensure that the airflow passage between the blades is wide enough to avoid airflow blockage or excessive turbulence between adjacent blades, so that the airflow flows smoothly inside the impeller, reduces the turbulence and resistance of the airflow, and improves the static pressure output and flow of the impeller.

[0034] In an alternative embodiment, the diameter of the wheel disc is R0, the value of R0 is 71 mm, the value of R1 is 69.7 mm, the value of L is 18.2 mm, the value of a is 30.1°, and the value of Z is 35.

[0035] The above specific parameter settings can further optimize the performance of the blade, thereby improving the air supply capacity and stability of the cross-flow impeller.

[0036] In the second aspect, the application also provides an air conditioner, which comprises an outer shell, a front volute, a rear volute, a heat exchanger, and the cross-flow impeller of any one of the above aspects.

[0037] The outer shell is provided with a mounting cavity, an air inlet, and an air outlet.

[0038] The rear volute and the front volute are oppositely arranged in the mounting cavity and form an air duct therebetween, one end of the air duct being an inlet and the other end being an outlet, the inlet being correspondingly arranged with the air inlet, and the outlet being correspondingly arranged with the air outlet.

[0039] A heat exchanger is arranged in the mounting cavity and located between the air inlet and the inlet;

[0040] The cross-flow impeller is arranged in the air duct.

[0041] The air volume of the air conditioner is significantly improved, so that heat exchange with indoor air can be better achieved. BRIEF DESCRIPTION OF DRAWINGS

[0042] Fig. 1 A transverse sectional view of the air conditioner cabinet provided in the embodiment of the present application is shown in the figure;

[0043] Fig. 2 A partial enlarged view of the cross-flow impeller of the air conditioner cabinet provided in the embodiment of the present application is shown in the figure;

[0044] Fig. 3 A blade view of the cross-flow impeller provided in the embodiment of the present application is shown in the figure.

[0045] Figure legend: 100-cross-flow impeller; 110-wheel disc; 130-blade; 131-blade inner end; 133-blade outer end; 135-middle camber surface; 137-pressure surface; 139-suction surface; 300-air conditioner cabinet; 310-outer shell; 311-mounting cavity; 312-air inlet; 313-air outlet; 320-rear volute; 321-air duct; 322-inlet; 323-outlet; 330-front volute; 340-heat exchanger. DETAILED DESCRIPTION

[0046] The inlet angle and outlet angle of the existing cross-flow impeller are not reasonably set, when the inlet angle or outlet angle is set too large or too small, airflow may separate on the surface of the blade 130, forming vortex, ultimately affecting the aerodynamic performance, efficiency and working stability of the cross-flow impeller, and further affecting the air supply volume of the air conditioner.

[0047] The cross-flow impeller and air conditioner provided by the present application can improve the aerodynamic performance of the cross-flow impeller, and further improve the air supply capacity of the air conditioner.

[0048] In order to make the above-mentioned purposes, features and advantages of the present application more obvious and easy to understand, the specific embodiments of the present application will be described in detail below with reference to the drawings.

[0049] Please refer to Figs. 1-3 The present embodiment provides an air conditioner, which comprises an air conditioner outdoor unit and an air conditioner cabinet 300. The air conditioner outdoor unit and the air conditioner cabinet 300 are connected through a heat exchange pipeline, so that heat exchange between the indoor and outdoor units can be achieved. The air conditioner cabinet 300 can be a cylindrical air conditioner cabinet 300.

[0050] In the embodiment, the air conditioner cabinet 300 comprises an outer shell 310, a front volute 330, a rear volute 320, a heat exchanger 340 and a cross-flow impeller 100. The outer shell 310 is provided with a mounting cavity 311, an air inlet 312 and an air outlet 313 which communicate with the mounting cavity 311. The rear volute 320 and the front volute 330 are oppositely arranged in the mounting cavity 311 and form an air duct 321 therebetween. One end of the air duct 321 is an inlet 322 and the other end is an outlet 323. The inlet 322 is correspondingly arranged with the air inlet 312. The outlet 323 is correspondingly arranged with the air outlet 313. The heat exchanger 340 is arranged in the mounting cavity 311 and located between the air inlet 312 and the inlet 322. The cross-flow impeller 100 is installed in the air duct 321. The rotation of the cross-flow impeller 100 can make the air outside the outer shell 310 enter the mounting cavity 311 through the air inlet 312, flow through the heat exchanger 340, then flow into the air duct 321 through the inlet 322, and finally flow out of the air outlet 323 of the air duct 321 and then flow to the indoor through the air outlet 313.

[0051] Specifically, the cross-flow impeller 100 comprises a disc 110 and a plurality of blades 130 arranged circumferentially on the disc 110. The outlet angle of the blade 130 is β1, and the value range of β1 satisfies the following relationship:

[0052] 15°≤β1≤30°;

[0053] The inlet angle of the blade 130 is β2, and the value range of β2 satisfies the following relationship:

[0054] 75°≤β2≤90°.

[0055] In the embodiment, one end of the blade 130 close to the outer periphery of the disc 110 is a blade outer side end 133. One end of the blade 130 located at the inner periphery of the disc 110 is a blade inner side end 131. The blade 130 has a median camber surface 135 in the thickness direction which equally divides the thickness of the blade 130. The projection of the median camber surface 135 on the disc 110 is a median camber line. The line connecting one end of the median camber line located at the blade inner side end 131 and the center of the disc 110 is a blade inner diameter R2. The line connecting one end of the median camber line located at the blade outer side end 133 and the center of the disc 110 is a blade outer diameter R1. The inlet angle is the included angle between the tangent line of the median camber line close to one end of the blade inner side end 131 and the perpendicular line of the blade inner diameter R2, and the outlet angle is the included angle between the tangent line of the median camber line close to one end of the blade outer side end 133 and the perpendicular line of the blade outer diameter R1.

[0056] The outlet angle of the present embodiment is set to the above range, which can ensure that the airflow is smoothly discharged from the surface of the blade 130, and reduce the diffusion and separation of the airflow. A smaller outlet angle can make the airflow more concentrated, avoid separation of the airflow at the trailing edge of the blade 130, thereby improving the static pressure output and flow rate of the cross-flow impeller 100, and helping to reduce the turbulence and resistance of the airflow, reduce energy loss, and improve the aerodynamic efficiency of the fan blade. The inlet angle is set to the above range, which can ensure that the airflow enters the surface of the blade 130 at a nearly vertical angle, and reduce the separation of the airflow at the leading edge of the blade 130. A larger inlet angle can make the airflow more smoothly adhere to the surface of the blade 130, avoid the generation of airflow separation and vortex, thereby improve the aerodynamic efficiency of the fan blade, and also reduce the initial resistance of the airflow at low-speed start. Overall, the combination of the range of the inlet angle 322 and the outlet angle can ensure that the airflow flows more smoothly on the surface of the blade 130. A larger inlet angle 322 can make the airflow enter the blade 130 at a nearly vertical angle, and a smaller outlet angle can make the airflow more concentrated. This synergistic effect can reduce the separation and vortex of the airflow, improve the aerodynamic efficiency of the cross-flow impeller, and thereby improve the air volume and power of the air conditioner.

[0057] It should be noted that the smaller the inlet angle β2 and the outlet angle β1, the greater the curvature of the blade 130, and more vortexes will be formed near the blade 130, resulting in increased vortex noise. However, too small a curvature will also affect the efficiency of the blade 130, resulting in a decrease in air volume. The present example can simultaneously consider air volume, power and noise by reasonably setting the inlet angle and outlet angle 323.

[0058] In the present embodiment, the value of β1 is 18°, and the value of β2 is 83.6°.

[0059] The present embodiment sets the value of β1 to 18° and the value of β2 to 83.6°, which can improve the aerodynamic efficiency of the cross-flow impeller, and thereby improve the air volume and power of the air conditioner.

[0060] In a group of comparative examples, the outlet angle β1 is kept unchanged, and the air volume with an inlet angle β2 of 90° is taken as a reference. When the inlet angle β2 is 83.6°, the curvature is increased by 10.2%, the air volume is increased by 4.8%, and the power is increased by 6.9%. The inlet angle β2 is kept unchanged, and the air volume with an outlet angle β1 of 30° is taken as a reference. When the outlet angle β1 is 18°, the curvature is increased by 16.7%, the air volume is increased by 7.0%, and the power is increased by 11.8%.

[0061] In the present embodiment, the thickness of the blade 130 gradually decreases from the inner side end 131 to the outer side end 133.

[0062] The embodiment gradually thins the thickness of the blade 130 from the inner side end 131 to the outer side end 133 of the blade, which can optimize the guidance of the airflow, reduce the separation of the airflow on the surface of the blade 130, and avoid the generation of vortex. The thinner outer side end 133 can effectively reduce the airflow resistance, reduce the power consumption of the fan blade, and improve the overall efficiency. The inner side end 131 of the blade has a relatively low airflow speed, and the blade 130 needs to provide sufficient thickness to ensure mechanical strength and rigidity to avoid deformation or vibration during high-speed rotation.

[0063] It should be noted that the outer side end 133 of the blade is the main area where the airflow enters the fan blade, and the airflow speed is relatively high. If the outer side end is too thick, it will increase the resistance of the airflow, resulting in energy loss. The thinner outer side end 133 of the blade can reduce the friction between the airflow and the surface of the blade 130, reduce the airflow resistance, and make the airflow flow more smoothly through the blade 130. At the inner side end 131 of the blade, the airflow speed is relatively low, and the blade 130 needs to provide sufficient thickness to ensure mechanical strength and rigidity to avoid deformation or vibration during high-speed rotation. As the airflow flows along the surface of the blade 130, the airflow speed gradually increases, especially at the outer side end 133 of the blade, where the airflow speed reaches a maximum value. At this time, the thinner blade 130 can reduce the obstruction to the airflow, making the airflow flow more smoothly through the blade 130, reducing the turbulence and resistance of the airflow. The thinner outer side end can also reduce the separation of the airflow at the tip of the blade 130, avoid the generation of vortex, and thus improve the aerodynamic efficiency of the fan blade.

[0064] For reference Figs. 1-3 In the embodiment, the inner side end 131 and the outer side end 133 of the blade are both circular arcs. The embodiment sets the inner side end and the outer side end of the blade 130 to be circular arcs, which can optimize the entry and exit of the airflow, reduce the generation of airflow separation and vortex.

[0065] In the embodiment, in an optional implementation, the inner side end 131 of the blade has an inscribed circle radius Rm, and the outer side end 133 of the blade has an inscribed circle radius Rn, which satisfy the following relationship:

[0066] Rm=k*Rn;

[0067] Wherein, 1.2≤k≤3.

[0068] The embodiment makes the radii of the inscribed circles at both ends satisfy the above value relationship, which can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan.

[0069] For reference Figs. 1-3 Further, the diameter of the inscribed circle of the inner side end 131 of the blade is 1mm, and the diameter of the inscribed circle of the outer side end 133 of the blade is 0.4mm.

[0070] The maximum inscribed circle is at the inlet angle and the minimum inscribed circle is at the outlet angle, and setting the radii of the inscribed circles at the two positions to the above values can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan. The blade 130 is connected by a series of inscribed circles on the camber line formed by the projection of the blade 130, and after the camber line is determined, the thickness of the blade is determined by the radius of the corresponding inscribed circle. When the overall thickness of the blade 130 is reduced, the air volume increases, but the noise also increases. The above values can effectively balance the air volume and noise.

[0071] In the embodiment, the blade 130 has a pressure surface 137 and a suction surface 139, both of which are arc surfaces and are tangent to the inscribed circles of the inner side end 131 and the outer side end 133 of the blade 130. The blade 130 has a camber surface 135 that equally divides the thickness of the blade 130 in the thickness direction, and the projection of the camber surface 135 on the wheel disc 110 is a circular arc.

[0072] The embodiment makes the projection of the camber surface 135 on the wheel disc 110 a circular arc, which can significantly improve the aerodynamic performance, efficiency and working stability of the cross-flow fan.

[0073] Please refer to Figs. 1-3 In the embodiment, the length of the line connecting the end of the blade 130 close to the outer periphery of the wheel disc 110 to the center of the wheel disc 110 is R1, the length of the line connecting the end of the blade 130 close to the inner periphery of the wheel disc 110 to the center of the wheel disc 110 is R2, the installation angle of the blade 130 is α, the chord length of the blade 130 is L, the number of blades 130 is Z, and R1, R2, L, α and Z satisfy the following relationship:

[0074] Lcosα=k1*(R1-R2);

[0075] (R1-Lcosα) / R2<k2*cos(360 / Z);

[0076] Wherein, 0.6≤k1≤0.8, and the value of K2 is 1.1.

[0077] By setting the parameters of the cross-flow impeller 100 to satisfy the above relationship, a reasonable proportion between the effective length of the blade 130 in the airflow direction and the radial expansion amount of the blade 130 can be ensured, so as to optimize the guidance and distribution of the airflow. By adjusting the installation angle a and the chord length L of the blade 130, the effective length of the blade 130 in the airflow direction can be controlled, which determines the flow path of the airflow on the surface of the blade 130, so that the airflow enters and exits the blade 130 smoothly, reduces vortex and separation phenomena, and thus improves the aerodynamic efficiency of the impeller. The radial expansion amount (R1-R2) of the blade 130 affects the rigidity of the blade 130, and the value of the effective length in the airflow direction can balance the rigidity and aerodynamic force of the blade 130, and ensure the stability and reliability of the blade 130 under working conditions. Through the above formula, the cross-flow impeller 100 can be operated efficiently and stably, so as to improve the air supply capacity of the air conditioner cabinet 300.

[0078] It should be noted that R0 is the radius of the wheel disc 110, representing the distance from the center of the wheel disc 110 to the outer periphery. R1 is the length of the line connecting the end of the blade 130 close to the outer periphery of the wheel disc 110 to the center of the wheel disc 110, i.e. the radius of the tip of the blade 130. R2 is the length of the line connecting the end of the blade 130 close to the inner periphery of the wheel disc 110 to the center of the wheel disc 110, i.e. the radius of the root of the blade 130. L is the chord length of the blade 130, representing the length of the blade 130 in the airflow direction. The installation angle (or attack angle) of the blade 130 represents the inclination angle of the blade 130 relative to the airflow direction. k1 is a proportional coefficient related to the material, geometric shape and other parameters of the blade 130.

[0079] Please refer to Figs. 1-3Further, Lcos a = k1*(R1-R2) is the relationship between the geometry of the blade 130 and the installation angle. Lcos a represents the effective length of the blade 130 in the direction of the airflow. Since the blade 130 is inclined, the effective length actually participating in the airflow guiding is the projection length of the chord length L. R1-R2 represents the radial expansion of the blade 130 from the root to the tip, i.e. the radial span of the blade 130 on the disc 110. And (R1-R2) represents the radial length difference of the blade 130. k1 is used to adjust the relationship between the radial expansion of the blade 130 and the effective length in the direction of the airflow. Generally, by adjusting the installation angle a and the chord length L of the blade 130, the effective length of the blade 130 in the direction of the airflow can be controlled to determine the flow path of the airflow on the surface of the blade 130, which can ensure that the airflow enters and exits the blade 130 smoothly, reduces vortex and separation phenomenon, thereby improving the aerodynamic efficiency of the impeller. The radial expansion R1-R2 of the blade 130 will affect the rigidity of the blade 130, and the value of the effective length Lcos a in the direction of the airflow can balance the rigidity and aerodynamic force of the blade 130, and ensure its stability and reliability under working conditions. It can be seen that by optimizing the blade 130 as described above, the cross-flow impeller 100 can simultaneously consider aerodynamic performance, structural stability and installation angle adjustment.

[0080] Secondly, (R1-Lcos a) / R2<k2*cos(360 / Z) forms a constraint condition for the geometry of the blade 130 and the airflow distribution, which can ensure that the airflow passage between the blades 130 is wide enough to avoid airflow blocking or excessive turbulence between adjacent blades 130, so that the airflow flows smoothly inside the impeller, reduces the turbulence and resistance of the airflow, and improves the static pressure output and flow of the impeller.

[0081] It is worth noting that the part of (R1-Lcosα) / R2 represents the ratio of the radial expansion of the blade 130 on the disc 110 to the radius of the root of the blade 130. R1-Lcosα represents the effective radial length of the blade 130 from the root to the tip, which can obtain a dimensionless ratio reflecting the relative expansion degree of the blade 130 on the disc 110. k2*cos(360 / Z) represents the ratio of the air flow passage width between adjacent blades 130 to the radius of the root of the blade 130, which is used to adjust the air flow passage width between the blades 130 to ensure that the air flow can smoothly pass through the space between the adjacent blades 130. If the radial expansion of the blade 130 is too large, the air flow passage between the adjacent blades 130 will become narrow, causing the air flow to be unable to flow smoothly, and vortex and separation phenomena are easy to occur. By limiting the radial expansion of the blade 130, it can ensure that the air flow has enough space to flow between the adjacent blades 130, reduce the turbulence and resistance of the air flow, and improve the aerodynamic performance of the impeller. Proper blade 130 spacing can reduce the air flow interference between adjacent blades 130 and reduce air flow loss. When the air flow passage between the blades 130 is too narrow, the adjacent blades 130 will interfere with each other, causing the air flow velocity to be uneven and increasing energy loss. By setting a reasonable blade 130 spacing, the interference can be reduced to ensure that the air flow can smoothly pass through the impeller, reducing energy loss. When the blade 130 rotates at high speed, complex flow phenomena will occur between the adjacent blades 130, especially in the case of narrow passages, the interaction of the air flow will be more intense, causing the blade 130 to vibrate more. By setting a reasonable blade 130 spacing, the interaction can be reduced to ensure smooth flow of the air flow, reduce vibration and noise of the blade 130, and prolong the service life of the impeller. By setting the above formula, the aerodynamic performance of the impeller can be optimized to ensure that the impeller can operate efficiently under different working conditions. Proper blade 130 spacing can reduce air flow turbulence and resistance, improve static pressure output and flow of the impeller. Setting k2 to 1.1 can maximize the use of space between the blades 130 while ensuring smooth flow of the air flow, ensuring that the aerodynamic performance and efficiency of the impeller reach the best state.

[0082] Please refer to Figs. 1-3 In this embodiment, the diameter of the disc 110 is R0, the value of R0 is 71mm, the value of R1 is 69.7mm, the value of L is 18.2mm, the value of α is 30.1°, and the value of Z is 35. The above specific parameters can further optimize the performance of the blade 130, and further improve the air supply capacity and stability of the cross-flow impeller 100.

[0083] In summary, the outlet angle is set to the above value range in the embodiment, which can ensure that the airflow is smoothly discharged from the surface of the blade 130 and reduce the diffusion and separation of the airflow. The smaller outlet angle can make the airflow more concentrated, avoid the separation of the airflow at the trailing edge of the blade 130, and thus improve the static pressure output and flow rate of the cross-flow impeller 100, which is helpful to reduce the turbulence and resistance of the airflow, reduce the energy loss, and improve the aerodynamic efficiency of the fan blade. The inlet angle is set to the above value range, which can ensure that the airflow enters the surface of the blade 130 at a nearly vertical angle, reduce the separation of the airflow at the leading edge of the blade 130, and the larger inlet angle can make the airflow more smoothly adhere to the surface of the blade 130, avoid the separation and vortex of the airflow, and thus improve the aerodynamic efficiency of the fan blade, and also reduce the initial resistance of the airflow at low-speed start. Overall, the value range of the inlet angle and the outlet angle can ensure that the airflow flows more smoothly on the entire surface of the blade 130, the larger inlet angle can make the airflow enter the blade 130 at a nearly vertical angle, and the smaller outlet angle can make the airflow more concentrated, and the synergistic effect can reduce the separation and vortex of the airflow, improve the aerodynamic efficiency of the cross-flow fan, and thus improve the air volume and power of the air conditioner.

[0084] Although the utility model discloses as above, the utility model is not limited to this. Any person skilled in the art, without departing from the spirit and scope of the utility model, can make various changes and modifications, therefore the protection scope of the utility model should be the range limited by the claims.

Claims

1. A crossflow impeller, characterized by, The impeller (110) comprises a plurality of blades (130) arranged circumferentially on the impeller (110), an outlet angle of the blade (130) is β1, and a value range of β1 satisfies the following relationship: 15°≤β1≤30°； An inlet angle of the blade (130) is β2, and a value range of β2 satisfies the following relationship: 75°≤β2≤90°； One end of the blade (130) close to an outer periphery of the impeller (110) is a blade outer side end (133), one end of the blade (130) located at an inner periphery of the impeller (110) is a blade inner side end (131), the blade (130) has a median camber surface (135) in a thickness direction of the blade (130), the median camber surface (135) is a median camber line in a projection of the impeller (110), a line connecting one end of the blade inner side end (131) and a center of the impeller (110) is a blade inner diameter R2, and a line connecting one end of the blade outer side end (133) and the center of the impeller (110) is a blade outer diameter R1. The inlet angle is an included angle between a tangent of one end of the median camber line close to the blade inner side end (131) and a perpendicular line of the blade inner diameter R2, and the outlet angle is an included angle between a tangent of one end of the median camber line close to the blade outer side end (133) and a perpendicular line of the blade outer diameter R1.

2. The crossflow impeller of claim 1, wherein The value of β1 is 18°, and the value of β2 is 83.6°.

3. The crossflow impeller of claim 1, wherein, The thickness of the blade (130) gradually decreases from the blade inner side end (131) to the blade outer side end (133).

4. The crossflow impeller of claim 3, wherein The blade inner side end (131) and the blade outer side end (133) are both circular arcs.

5. The crossflow impeller of claim 4, wherein, The blade inner side end (131) has an inscribed circle radius Rm, the blade outer side end (133) has an inscribed circle radius Rn, and Rm and Rn satisfy the following relationship: Rm=k*Rn; wherein 1.2≤k≤3.

6. The crossflow impeller of claim 4 or 5, wherein The diameter of the inscribed circle of the blade inner side end (131) is 1 mm, and the diameter of the inscribed circle of the blade outer side end (133) is 0.4 mm.

7. The crossflow impeller of any one of claims 4-5, wherein, The blade (130) has a pressure surface (137) and a suction surface (139), the pressure surface (137) and the suction surface (139) are both arc surfaces, and both are tangent to the inscribed circles of the blade inner side end (131) and the blade outer side end (133), and the median camber line is a circular arc.

8. The crossflow impeller of any one of claims 1-5, wherein, The installation angle of the blade (130) is α, the chord length of the blade (130) is L, the number of the blades (130) is Z, R1, R2, L, α and Z satisfy the following relationship: Lcosα=k1*(R1-R2); wherein 0.6≤k1≤0.8; (R1-Lcosα) / R2<k2*cos(360 / Z); wherein the value of K2 is 1.

1.

9. The crossflow impeller of claim 8, wherein, The diameter of the impeller (110) is R0, the value of R0 is 71 mm, the value of R1 is 69.7 mm, the value of L is 18.2 mm, the value of α is 30.1°, and the value of Z is 35.

10. An air conditioner characterized by comprising: The shell (310), the front volute (330), the rear volute (320), the heat exchanger (340) and the cross-flow impeller of any one of claims 1-9 are comprised; The shell (310) is provided with a mounting cavity (311), an air inlet (312) and an air outlet (313) communicating with the mounting cavity (311); The rear volute (320) and the front volute (330) are oppositely arranged in the mounting cavity (311) and form an air duct (321) therebetween, one end of the air duct (321) being an inlet (322) and the other end being an outlet (323), the inlet (322) being correspondingly arranged with the air inlet (312) and the outlet (323) being correspondingly arranged with the air outlet (313); The heat exchanger (340) is arranged in the mounting cavity (311) and located between the air inlet (312) and the inlet (322); The cross-flow impeller is mounted in the air duct (321).

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