Cabinet air conditioner and air conditioner

Abstract

The utility model provides a cabinet air conditioner and an air conditioner, and relates to the technical field of air conditioners. The cabinet air conditioner comprises an outer shell, a rear volute, a front volute, a heat exchanger and cross-flow fan blades. The outer shell is provided with a mounting cavity, an air inlet and an air supply outlet, the rear volute and the front volute are oppositely arranged in the mounting cavity, and the cross-flow fan blade is mounted in an air channel formed between the rear volute and the front volute. The cross-flow fan blade comprises a wheel disc and a plurality of blades arranged in the circumferential direction of the wheel disc, the radius of the wheel disc is R0, the length of the connecting line of one end, close to the outer circumferential edge of the wheel disc, of each blade and the center of the wheel disc is R1, the length of the connecting line of one end, close to the inner circumferential edge of the wheel disc, of each blade and the center of the wheel disc is R2, the installation angle of each blade is alpha, the chord length of each blade is L, and R0, R1, R2, L and alpha meet the condition that Lcos alpha = k1 * (R1-R2). Wherein 0.6 < = k1 < = 0.8. The aerodynamic performance of the cross-flow fan blade can be provided on the whole, and then the air supply capacity of the cabinet air conditioner is improved.

Description

Technical Field

[0001] This utility model relates to the field of air conditioning technology, and more specifically, to an air conditioning unit and an air conditioner. Background Technology

[0002] Cross-flow fans offer advantages over traditional axial and centrifugal fans, including high efficiency, quiet operation, energy saving, and even airflow distribution, making them widely used in the air conditioning industry. They are particularly advantageous in cylindrical cabinet air conditioners.

[0003] The structural parameters of a cross-flow fan blade have a crucial impact on its air delivery capacity. Proper design can significantly improve the fan's airflow efficiency, static pressure output, and overall performance. However, improperly configured relationships between the structural parameters of existing cross-flow fan blades can affect their aerodynamic performance, thereby impacting the air delivery capacity of the unit. Utility Model Content

[0004] The problem solved by this invention is that the relationship between the structural parameters of the existing cross-flow fan blades is not set reasonably, which will affect the aerodynamic performance of the cross-flow fan blades and thus affect the air delivery capacity of the cabinet air conditioner.

[0005] To address the aforementioned issues, this invention provides an air conditioning unit and an air conditioner that can improve the aerodynamic performance of the cross-flow fan blades, thereby enhancing the air delivery capacity of the air conditioner.

[0006] In a first aspect, this application provides an air conditioning unit, comprising:

[0007] The outer casing is provided with a mounting cavity and an air inlet and an air outlet communicating with the mounting cavity;

[0008] The rear volute and the front volute are disposed opposite to each other in the mounting cavity and form an air duct between them. One end of the air duct is an inlet and the other end is an outlet. The inlet is disposed corresponding to the air inlet and the outlet is disposed corresponding to the air outlet.

[0009] A heat exchanger is disposed within the mounting cavity and located between the air inlet and the air outlet; and,

[0010] A cross-flow fan blade is installed inside the air duct;

[0011] The cross-flow fan blade includes a rotor and multiple blades arranged around the rotor. The radius of the rotor is R0. The outer diameter of the blade is defined by a line connecting the end of the blade closest to the outer periphery of the rotor to the center of the rotor, and the length of the outer diameter is R1. The inner diameter of the blade is defined by a line connecting the end of the blade closest to the inner periphery of the rotor to the center of the rotor, and the length of the inner diameter is R2. The installation angle of the blade is α, and the chord length of the blade is L. R0, R1, R2, L, and α satisfy the following relationship:

[0012] Lcosα=k1*(R1-R2);

[0013] Where 0.6≤k1≤0.8.

[0014] This application sets the parameters of the cross-flow fan blades to satisfy the above-mentioned relationships, ensuring a reasonable ratio between the effective length of the blades in the airflow direction and their radial expansion, thereby optimizing airflow guidance and distribution. By adjusting the blade's installation angle α and chord length L, the effective length of the blades in the airflow direction determines the airflow path on the blade surface, allowing the airflow to smoothly enter and exit the blades, reducing eddies and separation phenomena, and thus improving the aerodynamic efficiency of the fan blades. The radial expansion (R1-R2) of the blades affects their rigidity, while the value of the effective length in the airflow direction balances the blade's rigidity and aerodynamic forces, ensuring its stability and reliability under operating conditions. The above formula enables the efficient and stable operation of the cross-flow fan blades, thereby improving the air delivery capacity of the air conditioning unit.

[0015] In an optional embodiment, the minimum distance between the wheel and the front volute is d1, where d1 ≥ 5 mm, and the minimum distance between the wheel and the rear volute is d2, where d2 ≥ 5 mm.

[0016] This application sets d1≥5mm and d2≥5mm, which avoids interference between the cross-flow impeller and the front or rear volute when rotating, and allows the impeller diameter to be as large as possible, thereby improving the air delivery capacity.

[0017] In an optional implementation, R1 and R0 satisfy the following relationship:

[0018] R0 = R1 + d3;

[0019] Where d3≥1mm.

[0020] This application ensures that R0 and R1 satisfy the above formula and value range, which can ensure smooth airflow, reduce airflow short-circuiting, improve the structural stability of the fan blades, optimize the uniform distribution of airflow, and reduce noise and vibration.

[0021] In an optional implementation, the number of blades is Z, and R1, L, R2, α, and Z satisfy the following relationship:

[0022] (R1-Lcosα) / R2 <k2*cos(360 / Z);

[0023] The value of K2 is 1.1.

[0024] This application ensures that the blade parameters satisfy the above formula, forming constraints on the blade geometry and airflow distribution. This ensures that the airflow channels between blades are wide enough to avoid airflow blockage or excessive turbulence between adjacent blades, allowing the airflow to flow smoothly inside the blades, reducing airflow turbulence and resistance, and improving the static pressure output and flow rate of the blades.

[0025] In an optional implementation, the value of R0 is 71 mm and the value of R1 is 69.7 mm.

[0026] This application sets R0 to 71mm, which provides a larger disk radius, giving the blades more radial expansion space. This allows the blades to extend from the inside to the outside of the disk, creating a larger radial span, which helps optimize the aerodynamic design of the blades and improves the static pressure output and flow rate of the fan blades. Setting R1 to 69.7mm ensures that the radial clearance between the blade tip and the outer periphery of the disk is large enough to avoid obstructing the airflow when entering the fan blades. This helps improve the smoothness of airflow and the aerodynamic efficiency of the fan blades.

[0027] In an optional implementation, the value of L is 18.2 mm, and the value of α is 30.1°.

[0028] The chord length L of the blade determines its effective working area in the airflow direction. Setting the chord length to 18.2 mm in this application ensures the blade has an appropriate length to effectively guide airflow through the blades. This also helps improve airflow smoothness and the aerodynamic efficiency of the blades. Setting α to 30.1° ensures the blade has an appropriate installation angle, thereby generating sufficient lift and thrust to propel airflow through the blades, contributing to improved aerodynamic efficiency and flow output.

[0029] In an optional implementation, the value of Z is 35.

[0030] This application sets the number of blades Z to 35. This setting can more evenly divide the airflow, reduce the mutual interference between adjacent blades, ensure that the airflow flows evenly throughout the entire blade, and allow the airflow to pass through each blade more smoothly, reducing airflow turbulence and drag, and improving the aerodynamic performance of the blade.

[0031] In an optional embodiment, the exit angle of the blade is β1, and the range of values ​​for β1 satisfies the following relationship:

[0032] 15°≤β1≤30°;

[0033] The inlet angle of the blade is β2, and the range of values ​​for β2 satisfies the following relationship:

[0034] 75°≤β2≤90°;

[0035] The blade has a central arc surface that equally divides the blade thickness in the thickness direction, and the projection of the central arc surface onto the wheel is a central arc line;

[0036] Wherein, the inlet angle is the angle between the tangent of the middle arc line near the inner side of the blade and the perpendicular line to the inner diameter of the blade, and the outlet angle is the angle between the tangent of the middle arc line near the outer side of the blade and the perpendicular line to the outer diameter of the blade.

[0037] Setting the blade inlet angle to the aforementioned range ensures that the airflow exits the blade at an appropriate angle, preventing abrupt changes in airflow direction or separation at the outlet. This helps reduce airflow turbulence and drag, improving the aerodynamic efficiency of the blade. Setting the outlet angle to the aforementioned range also reduces airflow impact and loss, further enhancing the aerodynamic performance of the blade.

[0038] In an optional implementation, β1 is 18° and β2 is 83.6°.

[0039] The above-mentioned values ​​adopted in this application can achieve smooth airflow throughout the entire blade, reduce airflow separation, eddies and energy loss, and improve the overall aerodynamic performance of the blade.

[0040] Secondly, this application also provides an air conditioner, including an outdoor unit and a cabinet unit as described in any of the above optional embodiments, wherein the outdoor unit and the cabinet unit are connected by a heat exchange pipe.

[0041] The cross-flow fan blades of the air conditioner cabinet unit provided in this application can operate efficiently and stably, thereby improving the air delivery capacity of the air conditioner cabinet unit. Attached Figure Description

[0042] Figure 1 A schematic diagram of the transverse cross-section of an air conditioner unit provided for an embodiment of this utility model;

[0043] Figure 2 This is a partially enlarged schematic diagram of the cross-flow impeller of an air conditioner cabinet unit provided in an embodiment of this utility model.

[0044] Icons: 100-Air conditioner cabinet unit; 110-Outer casing; 111-Mounting cavity; 112-Air inlet; 113-Air outlet; 120-Rear volute; 121-Air duct; 122-Inlet; 123-Outlet; 130-Front volute; 140-Heat exchanger; 150-Cross-flow fan blade; 151-Disc; 153-Blade. Detailed Implementation

[0045] The unreasonable relationship between the structural parameters of the existing cross-flow fan blades will affect the aerodynamic performance of the cross-flow fan blades, and thus affect the air delivery capacity of the cabinet air conditioner.

[0046] This utility model provides an air conditioning unit and an air conditioner that can improve the aerodynamic performance of the cross-flow fan blades, thereby improving the air delivery capacity of the air conditioner.

[0047] To make the above-mentioned objectives, features and advantages of this utility model more apparent and understandable, the specific embodiments of this utility model will be described in detail below with reference to the accompanying drawings.

[0048] Please refer to Figure 1 and Figure 2 This embodiment provides an air conditioner, which includes an outdoor unit and a cabinet unit 100. The outdoor unit and the cabinet unit 100 are connected by heat exchange pipes, thereby enabling heat exchange between the indoor and outdoor units. The cabinet unit 100 can be cylindrical.

[0049] In this embodiment, the air conditioner cabinet unit 100 includes an outer casing 110, a front volute 130, a rear volute 120, a heat exchanger 140, and a cross-flow fan blade 150. The outer casing 110 has a mounting cavity 111 and an air inlet 112 and an air outlet 113 communicating with the mounting cavity 111. The rear volute 120 and the front volute 130 are disposed opposite each other within the mounting cavity 111, forming an air duct 121 between them. One end of the air duct 121 is an inlet 122, and the other end is an outlet 123. The inlet 122 corresponds to the air inlet 112. The outlet 123 corresponds to the air outlet 113. The heat exchanger 140 is disposed within the mounting cavity 111 and located between the air inlet 112 and the air outlet 122. The cross-flow fan blade 150 is installed within the air duct 121. The rotation of the cross-flow fan blade 150 allows air outside the outer casing 110 to enter the mounting cavity 111 through the air inlet 112, flow through the heat exchanger 140, then through the inlet 122 into the air duct 121, and then through the impeller to the outlet 123 of the air duct 121, and finally flow into the room through the air outlet 113.

[0050] Specifically, the cross-flow fan blade 150 includes a rotor 151 and multiple blades 153 arranged around the rotor 151. The radius of the rotor 151 is R0. The outer diameter of the blade is defined by a line connecting the end of the blade 153 near the outer periphery of the rotor 151 to the center of the rotor 151, and the length of the outer diameter is R1. The inner diameter of the blade is defined by a line connecting the end of the blade 153 near the inner periphery of the rotor 151 to the center of the rotor 151, and the length of the inner diameter is R2. The installation angle of the blade 153 is α, and the chord length of the blade 153 is L. R0, R1, R2, L, and α satisfy the following relationship:

[0051] Lcosα=k1*(R1-R2);

[0052] Where 0.6≤k1≤0.8.

[0053] In this embodiment, the parameters of the cross-flow fan blade 150 are set to satisfy the above-mentioned relationship, ensuring a reasonable ratio between the effective length of the blade 153 in the airflow direction and its radial expansion, thereby optimizing airflow guidance and distribution. By adjusting the installation angle α and chord length L of the blade 153, the effective length of the blade 153 in the airflow direction determines the flow path of the airflow on the surface of the blade 153, thus allowing the airflow to smoothly enter and leave the blade 153, reducing eddies and separation phenomena, and improving the aerodynamic efficiency of the fan blade. The radial expansion (R1-R2) of the blade 153 affects the rigidity of the blade 153, while the value of the effective length in the airflow direction balances the rigidity and aerodynamic forces of the blade 153, ensuring its stability and reliability under operating conditions. The above formula enables the efficient and stable operation of the cross-flow fan blade 150, thereby improving the air delivery capacity of the air conditioning unit 100.

[0054] It should be noted that R0 is the radius of the disk 151, representing the distance from the center of the disk 151 to its outer periphery. R1 is the length of the line connecting the end of the blade 153 closest to the outer periphery of the disk 151 to the center of the disk 151, i.e., the radius of the tip of the blade 153, also known as the inner diameter of the blade. R2 is the length of the line connecting the end of the blade 153 closest to the inner periphery of the disk 151 to the center of the disk 151, i.e., the radius of the root of the blade 153, also known as the outer diameter of the blade. L is the chord length of the blade 153, representing the length of the blade 153 along the airflow direction. The angle of attack (or angle of attack) of the blade 153 represents the tilt angle of the blade 153 relative to the airflow direction. k1 is a proportionality coefficient, related to the material, geometry, and other parameters of the blade 153.

[0055] Furthermore, Lcosα = k1*(R1-R2) represents the relationship between the geometry of blade 153 and its installation angle. Lcosα indicates the effective length of blade 153 in the airflow direction. Since blade 153 is inclined, the effective length actually involved in guiding the airflow is the projected length of the chord length L. R1-R2 represents the radial extension of blade 153 from its root to its tip, i.e., the radial span of blade 153 on the impeller 151. (R1-R2) represents the radial length difference of blade 153. k1 is used to adjust the relationship between the radial extension of blade 153 and the effective length in the airflow direction. Generally, by adjusting the installation angle α and chord length L of blade 153, the effective length of blade 153 in the airflow direction can be controlled. This determines the flow path of the airflow on the surface of blade 153, ensuring that the airflow smoothly enters and leaves blade 153, reducing eddies and separation phenomena, thereby improving the aerodynamic efficiency of the fan blade. The radial extension R1-R2 of blade 153 affects its rigidity, while the effective length Lcosα in the airflow direction balances the rigidity and aerodynamic forces of blade 153, ensuring its stability and reliability under operating conditions. Therefore, by optimizing blade 153 as described above, the cross-flow impeller can simultaneously achieve aerodynamic performance, structural stability, and installation angle adjustment.

[0056] Furthermore, the minimum distance between the wheel 151 and the front volute 130 is d1, where d1 ≥ 5 mm, and the minimum distance between the wheel 151 and the rear volute 120 is d2, where d2 ≥ 5 mm.

[0057] In this embodiment, d1≥5mm and d2≥5mm are set to avoid interference between the cross-flow impeller and the front volute 130 or the rear volute 120 when rotating, and to make the impeller diameter as large as possible, thereby improving the air delivery capacity.

[0058] Specifically, d1 is set to 5mm and d2 is also set to 5mm. This setting ensures that the larger wheel 151 has a better air delivery effect without interference.

[0059] Please refer to Figure 1 and Figure 2 Furthermore, R1 and R0 satisfy the following relationship:

[0060] R0 = R1 + d3;

[0061] Where d3≥1mm.

[0062] This embodiment ensures that R0 and R1 satisfy the above formula and value range, which can ensure smooth airflow, reduce airflow short-circuiting, improve the structural stability of the fan blades, optimize the uniform distribution of airflow, and reduce noise and vibration.

[0063] In this embodiment, the number of blades 153 is Z, and R1, L, R2, α, and Z satisfy the following relationship:

[0064] (R1-Lcosα) / R2 <k2*cos(360 / Z);

[0065] The value of K2 is 1.1.

[0066] This embodiment ensures that the parameters of blade 153 satisfy the above formula, which forms the constraint conditions for the geometric structure and airflow distribution of blade 153. This ensures that the airflow channels between blades 153 are wide enough to avoid airflow blockage or excessive turbulence between adjacent blades 153, allowing the airflow to flow smoothly inside the blade, reducing airflow turbulence and resistance, and improving the static pressure output and flow rate of the blade.

[0067] It should be noted that (R1-Lcosα) / R2 represents the ratio of the radial expansion of blade 153 on disk 151 to the root radius of blade 153. R1-Lcosα represents the effective radial length of blade 153 from root to tip, which can be obtained as a dimensionless ratio reflecting the relative expansion of blade 153 on disk 151. k2*cos(360 / Z) represents the ratio of the width of the airflow channel between adjacent blades 153 to the root radius of blade 153, used to adjust the width of the airflow channel between blades 153 to ensure that the airflow can pass smoothly through the space between adjacent blades 153. If the radial expansion of blade 153 is too large, the airflow channel between adjacent blades 153 will become narrow, causing the airflow to be unable to pass smoothly, which can easily generate vortices and separation phenomena. By limiting the radial expansion of blade 153, sufficient space for airflow between adjacent blades 153 can be ensured, reducing airflow turbulence and drag, and improving the aerodynamic performance of the fan blade. An appropriate blade spacing (153) can reduce airflow interference between adjacent blades (153) and decrease airflow loss. When the airflow channel between blades (153) is too narrow, adjacent blades (153) will interfere with each other, resulting in uneven airflow velocity and increased energy loss. By setting a reasonable blade spacing (153), this interference can be reduced, ensuring that the airflow can pass smoothly through the blades and reducing energy loss. When the blades (153) rotate at high speed, the airflow will generate complex flow phenomena between adjacent blades (153), especially when the channel is narrow, the interaction of the airflow will be more intense, leading to increased blade vibration (153). By setting a reasonable blade spacing (153), this interaction can be reduced, ensuring smooth airflow, reducing blade vibration and noise, and extending the service life of the blades. The above formula can also optimize the aerodynamic performance of the blades, ensuring that the blades maintain efficient operation under different working conditions. An appropriate blade spacing (153) can reduce airflow turbulence and resistance, and improve the static pressure output and flow rate of the blades. Setting k2 to 1.1 ensures smooth airflow while maximizing the use of the space between blades 153, thus ensuring optimal aerodynamic performance and efficiency of the fan blades.

[0068] Please refer to Figure 1 and Figure 2 Furthermore, R0 is set to 71 mm and R1 is set to 69.7 mm.

[0069] In this embodiment, setting R0 to 142mm provides a larger radius for the impeller 151, offering more radial expansion space for the blades 153. This allows the blades 153 to extend from the inner to the outer side of the impeller 151, creating a larger radial span. This helps optimize the aerodynamic design of the blades 153 and improves the static pressure output and flow rate of the fan blades. Setting R1 to 139.4mm ensures a sufficiently large radial clearance between the tip of the blades 153 and the outer periphery of the impeller 151, preventing airflow obstruction when entering the fan blades. This contributes to improved airflow smoothness and the aerodynamic efficiency of the fan blades.

[0070] Please refer to Figure 1 and Figure 2 In this embodiment, L is 18.2 mm and α is 30.1°.

[0071] The chord length L of blade 153 determines its effective working area in the airflow direction. Setting the chord length of blade 153 to 18.2 mm in this application ensures that blade 153 has an appropriate length to effectively guide airflow through the blades. This also helps improve airflow smoothness and the aerodynamic efficiency of the blades. Setting α to 30.1° ensures that blade 153 has an appropriate installation angle, thereby generating sufficient lift and thrust to propel airflow through the blades, contributing to improved aerodynamic efficiency and flow output.

[0072] In this embodiment, the value of Z is 35.

[0073] This application sets the number Z of blades 153 to 35. This setting can more evenly divide the airflow, reduce the mutual interference between adjacent blades 153, ensure that the airflow flows evenly throughout the entire blade, and allow the airflow to pass through each blade 153 more smoothly, thereby reducing airflow turbulence and drag and improving the aerodynamic performance of the blade.

[0074] Of course, in other embodiments of this application, the parameters of blade 153 can also be adaptively adjusted using the above formula to meet different needs.

[0075] Please refer to Figure 1 and Figure 2 In this embodiment, the exit angle of blade 153 is β1, and the range of values ​​for β1 satisfies the following relationship:

[0076] 15°≤β1≤30°;

[0077] The inlet angle of blade 153 is β2, and the range of values ​​for β2 satisfies the following relationship:

[0078] 75°≤β2≤90°.

[0079] The blade has a mid-arc surface that equally divides the blade thickness in the thickness direction, and the projection of the mid-arc surface onto the disk is the mid-arc line. Figure 2 (As shown by the dashed line). The inlet angle is the angle between the tangent of the middle arc line near the inner side of the blade and the perpendicular line to the inner diameter of the blade, and the outlet angle is the angle between the tangent of the middle arc line near the outer side of the blade and the perpendicular line to the outer diameter of the blade.

[0080] In this embodiment, setting the inlet angle of blade 153 to the aforementioned range ensures that the airflow exits from outlet 123 of blade 153 at an appropriate angle, preventing abrupt changes or separation of the airflow at outlet 123. This helps reduce airflow turbulence and drag, improving the aerodynamic efficiency of the fan blade. Setting the outlet angle to the aforementioned range also reduces airflow impact and loss, further enhancing the aerodynamic performance of the fan blade.

[0081] Furthermore, β1 is 18° and β2 is 83.6°.

[0082] The above-mentioned values ​​in this embodiment can achieve smooth airflow throughout the entire blade, reduce airflow separation, eddies and energy loss, and improve the overall aerodynamic performance of the blade.

[0083] In summary, by setting the parameters of the cross-flow fan blade 150 to satisfy the above-mentioned relationships, this embodiment ensures that the effective length of the blade 153 in the airflow direction and its radial expansion maintain a reasonable ratio, thereby optimizing the guidance and distribution of airflow. By adjusting the installation angle α and chord length L of the blade 153, the effective length of the blade 153 in the airflow direction determines the flow path of the airflow on the surface of the blade 153, thus allowing the airflow to smoothly enter and leave the blade 153, reducing eddies and separation phenomena, and improving the aerodynamic efficiency of the fan blade. The radial expansion (R1-R2) of the blade 153 affects the rigidity of the blade 153, while the value of the effective length in the airflow direction can balance the rigidity and aerodynamic forces of the blade 153, ensuring its stability and reliability under operating conditions. The above formula enables the efficient and stable operation of the cross-flow fan blade 150, thereby improving the air delivery capacity of the air conditioning unit 100.

[0084] While the present invention has been disclosed above, it is not limited thereto. Any person skilled in the art can make various modifications and alterations without departing from the spirit and scope of the present invention; therefore, the scope of protection of the present invention should be determined by the scope defined in the claims.

Claims

1. A cabinet air conditioner, characterized in that, include: The outer casing (110) is provided with a mounting cavity (111) and an air inlet (112) and an air outlet (113) communicating with the mounting cavity (111); A rear volute (120) and a front volute (130) are disposed opposite to each other in the mounting cavity (111) and form an air duct (121) between them. One end of the air duct (121) is an inlet (122) and the other end is an outlet (123). The inlet (122) is disposed corresponding to the air inlet (112) and the outlet (123) is disposed corresponding to the air outlet (113). A heat exchanger (140) is disposed within the mounting cavity (111) and located between the air inlet (112) and the inlet (122); and, A cross-flow fan blade (150) is installed inside the air duct (121); The cross-flow fan blade (150) includes a disk (151) and multiple blades (153) arranged around the disk (151). The radius of the disk (151) is R0. The outer diameter of the blade is defined by a line connecting the end of the blade (153) near the outer periphery of the disk (151) to the center of the disk (151), and the length of the outer diameter is R1. The inner diameter of the blade is defined by a line connecting the end of the blade (153) near the inner periphery of the disk (151) to the center of the disk (151), and the length of the inner diameter is R2. The installation angle of the blade (153) is α, and the chord length of the blade (153) is L. R0, R1, R2, L, and α satisfy the following relationship: Lcosα=k1*(R1-R2); Where 0.6≤k1≤0.

8.

2. The air conditioner unit according to claim 1, characterized in that, The minimum distance between the wheel (151) and the front volute (130) is d1, where d1 ≥ 5 mm, and the minimum distance between the wheel (151) and the rear volute (120) is d2, where d2 ≥ 5 mm.

3. The air conditioner unit according to claim 1, characterized in that, R1 and R0 satisfy the following relationship: R0 = R1 + d3; Where d3≥1mm.

4. The air conditioner unit according to claim 1, characterized in that, The number of blades (153) is Z, and R1, L, R2, α, and Z satisfy the following relationship: (R1-Lcosα) / R2 <k2*cos(360 / Z); The value of K2 is 1.

1.

5. The air conditioner unit according to any one of claims 1-4, characterized in that, The value of R0 is 71 mm, and the value of R1 is 69.7 mm.

6. The air conditioner unit according to any one of claims 1-4, characterized in that, The value of L is 18.2 mm, and the value of α is 30.1°.

7. The air conditioner cabinet unit according to claim 4, characterized in that, The value of Z is 35.

8. The air conditioner unit according to any one of claims 1-4, characterized in that, The exit angle of the blade (153) is β1, and the range of values ​​for β1 satisfies the following relationship: 15°≤β1≤30°； The inlet angle of the blade (153) is β2, and the range of values ​​for β2 satisfies the following relationship: 75°≤β2≤90°； The blade has a central arc surface that equally divides the blade thickness in the thickness direction, and the projection of the central arc surface onto the wheel is a central arc line; Wherein, the inlet angle is the angle between the tangent of the middle arc line near the inner side of the blade and the perpendicular line to the inner diameter of the blade, and the outlet angle is the angle between the tangent of the middle arc line near the outer side of the blade and the perpendicular line to the outer diameter of the blade.

9. The air conditioner cabinet unit according to claim 8, characterized in that, The value of β1 is 18°, and the value of β2 is 83.6°.

10. An air conditioner, characterized in that, It includes an outdoor air conditioning unit and a cabinet air conditioning unit as described in any one of claims 1-9, wherein the outdoor air conditioning unit and the cabinet air conditioning unit are connected by a heat exchange pipe.

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