Centrifugal wind wheel, centrifugal fan and air conditioner

Abstract

According to the centrifugal wind wheel, the centrifugal fan and the air conditioner, a first blade section and a second blade section in the centrifugal wind wheel are arranged in the radial direction of the centrifugal wind wheel, part of the second blade section extends out of a base plate, and an airflow channel is formed between the second blade section and the first blade section; and air flow positioned on one side of the pressure surface or the suction surface of the blade can flow to the other side of the blade through the air flow channel. Therefore, the blade is designed in a sectional mode, the airflow channel is formed between the first blade section and the second blade section, and under the action of the pressure difference of the two sides of the blade, airflow located on the side of the pressure face of the blade can flow into the airflow channel and flow to the side of the suction face of the blade, so that jet flow ejected out of the suction face of the blade is formed; low-energy fluid on one side of the suction surface can be supplemented through jet flow, circulation separation on one side of the suction surface is reduced, and the jet flow can be subjected to vortex breaking treatment so as to relieve blockage of flowing vortexes to blade channels, and the working efficiency of the centrifugal wind wheel is improved.

Description

Technical Field

[0001] The present application relates to the field of household electrical appliances, and in particular to a centrifugal fan, a centrifugal blower and an air conditioner. Background Art

[0002] At present, centrifugal fans are optimized mainly by adjusting the parameters of the wind rotor blades and the parameters of the volute profile. For the wind rotor blades, the main adjustments are the inner diameter, inlet and outlet angles, and the center arc profile.

[0003] In the related art, centrifugal fans (such as forward centrifugal fans) have low efficiency due to the large turning angle and more separation of the airflow in the blade channel. Even through optimization such as adjustment of the inlet and outlet angles and the arc profile of the blades, it is still difficult to overcome the inherent characteristics of the forward centrifugal fan. Utility Model Content

[0004] The present application aims to solve at least one of the technical problems existing in the prior art. To this end, one purpose of the present application is to provide a centrifugal wind wheel with high air volume and good air supply effect.

[0005] The application also proposes a centrifugal fan.

[0006] The application also provides an air conditioner.

[0007] According to the centrifugal wind wheel of the first aspect embodiment of the present application, it includes: a chassis; a plurality of blades, the plurality of blades are arranged along the circumferential direction of the chassis, the blades include a first blade segment and a second blade segment, the first blade segment and the second blade segment are arranged along the radial direction of the centrifugal wind wheel, and a portion of the second blade segment extends out of the chassis and forms an airflow channel with the first blade segment, and the airflow on one side of the pressure side or the suction side of the blade can flow to the other side of the blade through the airflow channel.

[0008] According to the centrifugal wind wheel of the embodiment of the present application, the blades are designed in segments to form an air flow channel between the first blade segment and the second blade segment. Under the action of the pressure difference on both sides of the blade, the air flow on the pressure side of the blade can flow into the air flow channel and flow to the suction side of the blade to form a jet ejected from the suction side of the blade. The low-energy fluid on the suction side can be supplemented by the jet to reduce the flow separation on the suction side, and the jet can be processed by vortex breaking to reduce the blockage of the blade channel by the flow vortex, thereby improving the working efficiency of the centrifugal wind wheel.

[0009] In some embodiments of the present application, in the radial direction of the centrifugal impeller, the first blade segment and the second blade segment are arranged at intervals, and the trailing edge surface is formed at the distal end of the first blade segment, and the leading edge surface is formed at the proximal end of the second blade segment. The air flow channel is defined between the trailing edge surface and the leading edge surface.

[0010] In some embodiments of the present application, a communication groove is provided at the chassis. The communication groove penetrates the chassis along the axial direction of the centrifugal impeller, and the communication groove is communicated with the air flow channel.

[0011] In some embodiments of the present application, the communication groove is provided on the suction surface side of the second blade segment, and the communication groove extends from the outer peripheral wall of the chassis to the center side of the chassis.

[0012] In some embodiments of the present application, the blade is further provided with a connecting rib, and the connecting rib is connected between the first blade segment and the second blade segment.

[0013] In some embodiments of the present application, the trailing edge surface and the leading edge surface are arranged at equal intervals on the air flow path of the air flow channel; or, the distance between the trailing edge surface and the leading edge surface gradually decreases on the air flow path of the air flow channel.

[0014] In some embodiments of the present application, the distance between the proximal end of the first blade segment and the center of the chassis is R1, the minimum distance between the trailing edge surface of the first blade segment and the center of the chassis is R2, the minimum distance between the leading edge surface of the second blade segment and the center of the chassis is R3, and the distance between the distal end of the second blade segment and the center of the chassis is R4, and the relational expression is satisfied: R2 > (R1 + R4) / 2, and R3 > R2.

[0015] In some embodiments of the present application, the width dimension of the air flow channel in the air flow direction is W, and the relational expression is satisfied: 0.5%R4 ≤ W ≤ 2%R4.

[0016] In some embodiments of the present application, the included angle between the air inlet direction of the air flow channel and the pressure surface of the first blade segment is α, and the relational expression is satisfied: α < 30°; and / or, the included angle between the air outlet direction of the air flow channel and the suction surface of the second blade segment is β, and the relational expression is satisfied: β < 20°.

[0017] In some embodiments of the present application, the centrifugal impeller is further provided with a reinforcing ring, and the reinforcing ring is connected to a plurality of the second blade segments and is arranged on the side of the plurality of blades away from the chassis.

[0018] In some embodiments of the present application, in the radial direction of the centrifugal impeller, the first blade segment is arranged on the side of the second blade segment closer to the center of the chassis, and the distal end of the first blade segment in the direction away from the center is arranged on the suction surface side of the second blade segment, and the air flow channel is formed between the pressure surface of the first blade segment and the suction surface of the second blade segment.

[0019] In some embodiments of the present application, both the first blade segment and the second blade segment extend in an arc shape, and the arc radius of the first blade segment is R5, the arc radius of the second blade segment is R6, and they satisfy the relationship: R5 < R6.

[0020] The centrifugal fan according to the second aspect embodiment of the present application includes the above-mentioned centrifugal impeller.

[0021] The air conditioner according to the third aspect embodiment of the present application includes the above-mentioned centrifugal fan.

[0022] The additional aspects and advantages of the present application will be partly given in the following description, partly will become obvious from the following description, or will be understood through the practice of the present application. Description of the Drawings

[0023] The above and / or additional aspects and advantages of the present application will become obvious and easy to understand from the description of the embodiments in conjunction with the following drawings, where:

[0024] Figure 1 is a schematic diagram of an air conditioner according to an embodiment of the present application;

[0025] Figure 2 is an exploded view of an air conditioner according to an embodiment of the present application;

[0026] Figure 3 is a schematic structural diagram of a centrifugal impeller according to an embodiment of the present application;

[0027] Figure 4 is Figure 3 a partial enlarged view circled at A in

[0028] Figure 5 is Figure 3 a partial enlarged view circled at B in

[0029] Figure 6 is a bottom view of a centrifugal impeller according to an embodiment of the present application;

[0030] Figure 7 is Figure 6 a partial enlarged view circled at C in

[0031] Figure 8is a side view of a centrifugal impeller according to an embodiment of the present application;

[0032] Figure 9 is Figure 8 a sectional view taken along the center line D-D;

[0033] Figure 10 is Figure 9 an enlarged partial view circled at E;

[0034] Figure 11 is a schematic diagram of a centrifugal impeller according to an embodiment of the present application;

[0035] Figure 12 is a air volume-power curve graph of an embodiment of the present application and Comparative Example 1;

[0036] Figure 13 is a air volume-power curve graph of an embodiment of the present application and Comparative Example 2.

[0037] Reference numerals:

[0038] Air conditioner 1000; Centrifugal fan 100; Front panel 200; Air outlet 2001; Air return opening 2002; Heat exchanger 300; Bottom plate 400; Compressor 500; Motor 600; Outer cover 700;

[0039] Centrifugal impeller 10;

[0040] Chassis 1; Connecting groove 101;

[0041] Blade 2; Air flow channel 201; First blade segment 21; Trailing edge surface 211; Second blade segment 22; Leading edge surface 221; Connecting rib 23; Pressure surface 24; Suction surface 25; Reinforcing ring 3;

[0042] Upper volute 210; Lower volute 220. Detailed description of the specific embodiment

[0043] The embodiments of the present application will be described in detail below. Examples of the embodiments are shown in the drawings, where the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the drawings are exemplary only for explaining the present application and should not be construed as limiting the present application.

[0044] Reference will be made below to Figures 1 - 11 Describe the centrifugal impeller 10 according to an embodiment of the present application. The centrifugal impeller 10 is applied to the centrifugal fan 100, and the centrifugal impeller 10 can form an air flow by rotation to achieve the air supply function of the centrifugal fan 100.

[0045] The centrifugal impeller 10 according to an embodiment of the present application includes a chassis 1 and a plurality of blades 2.

[0046] Referring to Figure 3 , multiple blades 2 are arranged along the circumferential direction of the chassis 1, and the blade 2 includes a first blade segment 21 and a second blade segment 22. The first blade segment 21 and the second blade segment 22 are arranged along the radial direction of the centrifugal impeller 10, and a part of the second blade segment 22 extends out of the chassis 1. An air flow channel 201 is formed between the first blade segment 21 and the second blade segment 22. The air flow on one side of the pressure surface 24 or the suction surface 25 of the blade 2 can flow to the other side of the blade 2 through the air flow channel 201. Thus, a jet flow can be generated at the air flow channel 201 by using the pressure difference between the pressure surface 24 and the suction surface 25 of the blade 2, so as to energize the low-energy fluid on the suction surface 25, slow down the fluid separation, and at the same time perform vortex breaking treatment on the already formed vortex, reduce the blockage of the air flow in the blade channel, and further improve the working efficiency of the centrifugal impeller 10.

[0047] It can be understood that the chassis 1 is an installation carrier for the blade 2. By driving the chassis 1 to rotate, multiple blades 2 can be driven to rotate synchronously to form an air flow at the centrifugal impeller 10. Based on the characteristics of the blade 2 itself, the blade 2 has a pressure surface 24 and a suction surface 25, and there is a pressure difference on both sides of the blade 2 (i.e., the pressure surface 24 side and the suction surface 25 side of the blade 2), and the air flow at the blade 2 will further transport the air flow outward along the extension direction of the pressure surface 24 of the blade 2. Herein, "outer" refers to the side away from the center of the chassis 1, which is also the radial outer side of the centrifugal impeller 10.

[0048] Referring to Figure 10 , in the present application, the blade 2 has a first blade segment 21 and a second blade segment 22, and an air flow channel 201 is formed between the first blade segment 21 and the second blade segment 22. When the air flow on the pressure surface 24 side flows to the air flow channel 201, under the action of the pressure difference on both sides of the blade 2, at least part of the air flow will flow into the air flow channel 201 and flow to the suction surface 25 side of the blade 2 through the air flow channel 201. Thus, a jet flow is formed on the suction surface 25 side of the blade 2. By supplementing the low-energy fluid on the suction surface 25 of the blade 2, the jet flow can reduce the gas flow separation on the suction surface 25 side of the blade 2, and can perform impact and fragmentation treatment on the already formed flow separation vortex, such as changing a large vortex into a small vortex, which can reduce the blockage of the flow vortex on the blade channel and improve the working efficiency of the impeller.

[0049] It should be noted that "large vortex" and "small vortex" refer to the relative comparison result of the vortex sizes before and after the jet vortex breaking treatment. That is to say, under the action of the jet vortex breaking treatment, the vortex size at the blade channel can be made smaller.

[0050] At present, the optimization of centrifugal fans is mainly achieved by adjusting the parameters of the wind rotor blades and the parameters of the volute profile. For the wind rotor blades, the inner diameter, inlet and outlet angles, and the center arc profile of the blades are mainly adjusted. In the related art, centrifugal fans (such as forward centrifugal fans) have a large turning angle and more separation of the airflow in the blade channel, which will lead to low efficiency of the centrifugal fan. Even through optimization such as adjusting the inlet and outlet angles and the center arc profile of the blades, it is still difficult to overcome the inherent characteristics of the fan structure (i.e., the above-mentioned forward centrifugal fan).

[0051] According to the centrifugal wind wheel 10 of the embodiment of the present application, the blade 2 is designed in sections to form an air flow channel 201 between the first blade segment 21 and the second blade segment 22. Under the action of the pressure difference on both sides of the blade 2, the air flow on the pressure surface 24 of the blade 2 can flow into the air flow channel 201 and flow to the suction surface 25 of the blade 2 to form a jet ejected from the suction surface 25 of the blade 2. The low-energy fluid on the suction surface 25 side can be supplemented by the jet to reduce the flow separation on the suction surface 25 side, and the jet can be processed by vortex breaking to reduce the blockage of the blade channel by the flow vortex, thereby improving the working efficiency of the centrifugal wind wheel 10.

[0052] Combination Figure 9 and Figure 10 As shown, in some embodiments of the present application, in the radial direction of the centrifugal wind wheel 10, the first blade segment 21 and the second blade segment 22 are spaced apart, and the distal end of the first blade segment 21 forms a trailing edge surface 211, and the proximal end of the second blade segment 22 forms a leading edge surface 221, and an airflow channel 201 is defined between the trailing edge surface 211 and the leading edge surface 221.

[0053] The blade 2 includes a first blade segment 21 and a second blade segment 22, and the first blade segment 21 and the second blade segment 22 both extend inward and outward directions of the chassis 1 in the radial direction. The "proximal end" refers to the end of the blade 2 segment (such as the first blade segment 21 and the second blade segment 22) that is close to the center of the chassis 1 in the extension direction, and the "distal end" refers to the end of the blade 2 segment (such as the first blade segment 21 and the second blade segment 22) that is far away from the center of the chassis 1 in the extension direction.

[0054] It should be noted that the above-mentioned "airflow channel 201" is set through the thickness direction of the blade 2. At this time, the blade 2 needs to have a certain thickness to ensure the formation effect of the airflow channel 201 at the blade 2. Among them, the thickness of the blade 2 can be gradually reduced from the proximal end to the distal end, such as: the blade 2 is constructed as an airfoil blade.

[0055] Reference Figure 10, specifically, on the chassis 1, the first blade segment 21 is arranged radially inside the second blade segment 22, and the distal end of the first blade segment 21 is arranged adjacent to the proximal end of the second blade segment 22. The trailing edge surface 211 formed by the first blade segment 21 at the distal end is arranged opposite to the leading edge surface 221 formed by the second blade segment 22 at the proximal end, so as to define and form the above-mentioned air flow channel 201 through the cooperation of the trailing edge surface 211 and the leading edge surface 221. The air flow on the pressure surface 24 side of the blade 2 will flow along the pressure surface 24 of the blade 2 towards the radially outer side of the centrifugal impeller 10 under the action of the first blade segment 21. When the air flow flows through the gap between the trailing edge surface 211 and the leading edge surface 221, due to the pressure difference between the pressure surface 24 side and the suction surface 25 side of the blade 2, the air flow can flow into the air flow channel 201 and be ejected from the port on the side of the air flow channel 201 adjacent to the suction surface 25 to form a jet flow.

[0056] As Figure 5 and Figure 7 shown, in some embodiments of the present application, a communication groove 101 is provided at the chassis 1. The communication groove 101 penetrates the chassis 1 along the axial direction of the centrifugal impeller 10, and the communication groove 101 is communicated with the air flow channel 201, so as to reduce the processing difficulty of the centrifugal impeller 10.

[0057] It should be noted that the centrifugal impeller 10 is usually processed and produced by a mold. Since the air flow channel 201 is formed between the first blade segment 21 and the second blade segment 22, it will be difficult to process and demold at the air flow channel 201, thereby increasing the processing difficulty of the centrifugal impeller 10.

[0058] In the present application, by providing a communication groove 101 that penetrates along the thickness direction and is communicated with the air flow channel 201 at the chassis 1, a demolding groove structure is formed at the position where the air flow channel 201 is adjacent to the chassis 1, so as to facilitate the centrifugal impeller 10 to be removed from the mold.

[0059] As Figure 5 shown, in a further embodiment of the present application, the communication groove 101 is arranged on the suction surface 25 side of the second blade segment 22, and the communication groove 101 extends from the outer peripheral wall of the chassis 1 towards the center side of the chassis 1 to a position communicated with the air flow channel 201.

[0060] Combined Figure 5 and Figure 10 shown, in the projection of the centrifugal impeller 10 in the axial direction, part of the communication groove 101 is communicated with one end of the air flow channel 201 adjacent to the chassis 1, and the extending direction of the other part of the communication groove 101 is the same as the direction towards the suction surface 25 side of the second blade segment 22, so as to reduce the demolding difficulty of the centrifugal impeller 10 without affecting the structure of the blade 2.

[0061] As Figure 4As shown, in some embodiments of the present application, the blade 2 is further provided with a connecting rib 23. The connecting rib 23 is connected between the first blade segment 21 and the second blade segment 22 to connect the distal end of the first blade segment 21 and the proximal end of the second blade segment 22 through the connecting rib 23, thereby enhancing the structural strength of the blade 2 to meet the strength requirements during the high-speed rotation of the blade 2, and preventing the circumferential dimension of the air flow channel 201 from changing when the centrifugal impeller 10 rotates.

[0062] Referring to Figure 3 and Figure 4 , in the axial direction of the centrifugal impeller 10, the connecting rib 23 is provided on the side of the blade 2 away from the chassis 1, and the connecting member is connected between the first blade segment 21 and the second blade segment 22 to enhance the structural strength of the first blade segment 21 and the second blade segment 22 on the side away from the chassis 1.

[0063] Referring to Figure 4 , in some embodiments, the surface of the connecting rib 23 away from the chassis 1 is flush with the end face of the blade 2 on the side away from the chassis 1, so that the structure at the blade 2 is connected, and the processing difficulty at the blade 2 can be reduced.

[0064] Furthermore, when the connecting rib 23 is only provided on the end side of the first blade segment 21 and the second blade segment 22 away from the chassis 1, the air flow channel 201 penetrates axially toward the chassis 1 side, and the air flow on the pressure surface 24 side of the blade 2 can be directed to the suction surface 25 side of the blade 2. That is to say, the air flow channel 201 between the first blade segment 21 and the second blade segment 22 continuously extends in the axial direction of the centrifugal impeller 10 to enhance the effect of supplementing the low-energy fluid on the suction surface 25 side of the blade 2.

[0065] In some embodiments of the present application, the centrifugal impeller 10 further includes a reinforcing ring 3. The reinforcing ring 3 is respectively connected to the second blade segments 22 of multiple blades 2 to further enhance the structural strength of the centrifugal impeller 10 at the second blade segments 22, so that the centrifugal impeller 10 can meet the strength requirements for high-speed rotation.

[0066] Referring to Figure 3 , in the axial direction of the centrifugal impeller 10, the reinforcing ring 3 is provided on the side of the blade 2 away from the chassis 1. Through the reinforcing ring 3, the structural strength of the blade 2 on the side away from the chassis 1 in the axial direction can be enhanced.

[0067] Referring to Figure 9 , in some embodiments of the present application, in the projection in the axial direction of the centrifugal impeller 10, at least part of the projection of the second blade segment 22 falls outside the projection of the chassis 1. That is to say, part of the blade 2 (i.e., at the second blade segment 22) extends to the circumferential outside of the chassis 1 to form a suspended structure, resulting in relatively weak structural strength of the part of the blade 2 extending out of the chassis 1.

[0068] Further combined with Figure 3 , in the present application, the centrifugal impeller 10 is provided with a reinforcing ring 3. The reinforcing ring 3 is connected to a plurality of second blade segments 22 and is arranged on the side of the plurality of blades 2 away from the chassis 1. Among them, the reinforcing ring 3 is configured as an annular shape, and the reinforcing ring 3 is respectively connected to a plurality of second blade segments 22 to enhance the structural strength at the blade 2.

[0069] It can be understood that a support and reinforcement structure (i.e., the above-mentioned connecting ribs 23 and reinforcing ring 3) is provided at the second blade segment 22, which can enhance the structural strength at the second blade segment 22, so that the centrifugal impeller 10 can meet the strength requirements during high-speed rotation and prevent damage at the second blade segment 22 due to insufficient strength.

[0070] In some embodiments of the present application, the centrifugal impeller 10 is integrally formed, which can reduce the processing difficulty of the centrifugal impeller 10, improve production efficiency, and ensure the structural strength of the centrifugal impeller 10.

[0071] In some embodiments of the present application, the trailing edge surface 211 and the leading edge surface 221 are arranged at equal intervals on the air flow path of the air flow channel 201, so as to ensure the air flow effect at the air flow channel 201.

[0072] In some other embodiments of the present application, the distance between the trailing edge surface 211 and the leading edge surface 221 on the air flow path of the air flow channel 201 gradually decreases to form an air flow channel 201 with a gradually decreasing cross-sectional size of the flow cross-section, so as to accelerate the air flow velocity, improve the flow velocity of the jet ejected from the air flow channel 201, and enhance the jet formation effect at the blade 2.

[0073] It should be noted that the above-mentioned "air flow path" refers to: the air flow flows in through the air inlet formed on the pressure surface 24 side of the blade 2 through the air flow channel 201 and is discharged from the air outlet formed on the suction surface 25 side of the blade 2 by the air flow channel 201 after flowing through the air flow channel 201.

[0074] It can be understood that when the distance between the trailing edge surface 211 and the leading edge surface 221 remains the same or gradually decreases on the air flow path, the jet formation effect at the blade 2 can be ensured. If the cross-sectional size of the air flow channel 201 gradually increases on the air flow path, the air flow velocity flowing through the air flow channel 201 will gradually decrease, affecting the jet formation effect at the air flow channel 201.

[0075] Refer to Figure 9, in some embodiments of the present application, the trailing edge surface 211 of the first blade segment 21 and the leading edge surface 221 of the second blade segment 22 are both configured as arc surfaces, and the arc surfaces can play a good guiding role for the airflow to reduce the resistance when the airflow flows through the airflow passage 201. It should be noted that the trailing edge surface 211 of the first blade 2 and the leading edge surface 221 of the second blade segment 22 are not limited to arc surfaces, and can also be configured as flat surfaces, etc.

[0076] Referring to Figure 9 , in some embodiments of the present application, the distance between the proximal end of the first blade segment 21 and the center of the chassis 1 is R1, the minimum distance between the trailing edge surface 211 of the first blade segment 21 and the center of the chassis 1 is R2, the minimum distance between the leading edge surface 221 of the second blade segment 22 and the center of the chassis 1 is R3, and the distance between the distal end of the second blade segment 22 and the center of the chassis 1 is R4, and the relational expression is satisfied: R2 > (R1 + R4) / 2, and R3 > R2.

[0077] Combined with Figure 9 , the trailing edge surface 211 of the first blade segment 21 and the leading edge surface 221 of the second blade segment 22 are both configured to extend from the pressure surface 24 side of the blade 2 to the suction surface 25 side in a direction away from the center of the base. That is to say, the minimum distance between the trailing edge surface 211 of the first blade segment 21 and the center of the base is: the straight-line distance between the edge of the trailing edge surface 211 adjacent to the pressure surface 24 (i.e., the edge of the trailing edge surface 211 where the air inlet of the airflow passage 201 is formed) and the center of the base; the straight-line distance between the edge of the leading edge surface 221 adjacent to the pressure surface 24 (i.e., the edge of the leading edge surface 221 where the air inlet of the airflow passage 201 is formed) and the center of the base.

[0078] Thus, the air inlet position of the airflow passage 201 formed at the blade 2 can be set at a position exceeding 50% of the length of the blade 2, so as to ensure the air supply effect of the centrifugal impeller 10 and improve the jet flow effect generated by the blade 2 on the suction surface 25 side.

[0079] Referring to Figure 9 , in a further embodiment of the present application, the width dimension of the airflow passage 201 in the airflow direction is W, and the relational expression is satisfied: 0.5%R4 ≤ W ≤ 2%R4.

[0080] It should be noted that the width of the air flow channel 201 is defined by the distance between the trailing edge surface 211 of the first blade segment 21 and the leading edge surface 221 of the second blade segment 22. If the distance between the trailing edge surface 211 and the leading edge surface 221 is too small (e.g., 0.5%R4 > W), it will result in high machining accuracy requirements at blade 2, making the machining of the centrifugal impeller 10 difficult at blade 2, and having a large resistance to the air flow, resulting in a small gas flow rate through the air flow channel 201; if the distance between the trailing edge surface 211 and the leading edge surface 221 is too large (e.g., W > 2%R4), it will result in insufficient jet kinetic energy formed at the air flow channel 201, making it difficult to have an effective impact on the separation on the suction surface 25 side of blade 2.

[0081] Therefore, when the width dimension W of the air flow channel 201 satisfies the above parameter range, the manufacturing and machining difficulty at blade 2 and the jet formation effect can be balanced.

[0082] As Figure 9 shown, in some embodiments of the present application, the included angle between the air inlet direction of the air flow channel 201 and the pressure surface 24 of the first blade segment 21 is α, and satisfies the relational expression: α < 30°.

[0083] Among them, the air inlet direction of the air flow channel 201 is determined by the inclination angle between the trailing edge surface 211 and the pressure surface 24 of the first blade segment 21. Thus, by designing the inclination angle of the trailing edge surface 211 relative to the pressure surface 24 of the first blade segment 21, the adjustment of the air inlet direction of the air flow channel 201 can be realized. When α satisfies the above parameter range, the smoothness of the air flow entering the air flow channel 201 on the pressure surface 24 side of blade 2 can be ensured.

[0084] As Figure 9 shown, in some embodiments of the present application, the included angle between the air outlet direction of the air flow channel 201 and the suction surface 25 of the second blade segment 22 is β, and satisfies the relational expression: β < 20°.

[0085] Among them, the air outlet direction of the air flow channel 201 is determined by the inclination angle between the leading edge surface 221 and the suction surface 25 of the second blade segment 22. Thus, by designing the inclination angle of the leading edge surface 221 relative to the suction surface 25 of the second blade segment 22, the adjustment of the jet ejection direction can be realized. When β satisfies the above parameter range, it can prevent the air flow generated on the suction surface 25 side of blade 2 by the air flow channel 201 from having a negative impact on the main flow formed by the centrifugal impeller 10.

[0086] Therefore, when α and β both satisfy the above parameter ranges, it can ensure that the air flow smoothly enters the air flow channel 201, and the jet ejected through the air flow channel 201 will not have a negative impact on the main flow formed by the centrifugal impeller 10.

[0087] As Figure 11As shown, in some embodiments of the present application, in the radial direction of the centrifugal impeller 10, the first blade segment 21 is disposed on the side of the second blade segment 22 closer to the center of the chassis 1, and the distal end of the first blade segment 21 and the proximal end of the second blade segment 22 are staggeredly arranged, and an air flow channel 201 is formed between the pressure surface 24 of the first blade segment 21 and the suction surface 25 of the second blade segment 22.

[0088] Referring to Figure 11 , on the chassis 1, the first blade segment 21 is disposed radially inside the second blade segment 22, and both the first blade segment 21 and the second blade segment 22 extend away from the center of the chassis 1. The distal end of the first blade segment 21 and the proximal end of the second blade segment 22 are staggeredly and spaced apart, so that a part of the pressure surface 24 of the first blade segment 21 is disposed opposite to a part of the suction surface 25 of the second blade segment 22, and the air flow channel 201 is defined and formed between the pressure surface 24 of the first blade segment 21 and the suction surface 25 of the second blade segment 22.

[0089] That is to say, the second blade segment 22 is disposed on the side opposite to the rotation direction of the impeller of the first blade segment 21, and the proximal end of the second blade segment 22 is staggered from the distal end of the first blade segment 21 to form an air flow channel 201 with a certain width.

[0090] Further, a part of the air flow at the blade 2 can flow along the pressure surface 24 of the first blade segment 21 to the side of the second blade segment 22, so that it can flow into the air flow channel 201. The air flow flowing through the air flow channel 201 can generate a jet on the side of the suction surface 25 of the second blade segment 22, so as to supplement the low-energy fluid on the side of the suction surface 25 through the jet, reduce the flow separation on the side of the suction surface 25, and the jet can perform vortex breaking treatment to reduce the blockage of the flow vortex on the blade passage and improve the working efficiency of the centrifugal impeller 10.

[0091] It should be noted that when the blade 2 is configured as a blade 2 with a constant thickness, the thickness of the blade 2 is generally relatively thin. Thus, the air flow channel 201 can be formed by staggering the arrangement of the first blade segment 21 and the second blade segment 22. The thicknesses of the first blade segment 21 and the second blade segment 22 are small, and both the first blade segment 21 and the second blade segment 22 can be configured as blade 2 segments with a constant thickness. Herein, "the blade 2 with a constant thickness is relatively thin" means compared with a blade 2 with a thickness distribution such as an airfoil blade 2. The blade 2 with a constant thickness can be configured as a metal part or a plastic part, etc.

[0092] As Figure 11 shown, in a further embodiment of the present application, both the first blade segment 21 and the second blade segment 22 extend in an arc shape, the arc radius of the first blade segment 21 is R5, the arc radius of the second blade segment 22 is R6, and the relational expression is satisfied: R5 < R6.

[0093] When the arc radius R5 of the first blade segment 21 is smaller than the arc radius R6 of the second blade segment 22, it is convenient to arrange the air flow channel 201 formed by the pressure surface 24 of the first blade segment 21 and the suction surface 25 of the second blade segment 22 to gradually decrease in width, so that the air flow velocity flowing through the air flow channel 201 can be increased, and the effect of forming a jet at the blade 2 can be enhanced.

[0094] It can be understood that in the above embodiment, the width of the air flow channel 201 is determined by the distance between the pressure surface 24 of the first blade segment 21 and the suction surface 25 of the second blade segment 22. When R5 < R6, at the air flow channel 201, the distance between the pressure surface 24 of the first blade segment 21 and the suction surface 25 of the second blade segment 22 gradually decreases in the air flow direction.

[0095] Refer to Figure 12 , Figure 12 which is a comparison chart of the air volume-power curves of the centrifugal impeller of the embodiment of the present application and the centrifugal impeller of Comparative Example 1.

[0096] Among them, Comparative Example 1 is a centrifugal impeller with a blade height dimension of 60 mm, and the blade is a prototype blade in the prior art without a jet structure; an embodiment of the present application is a centrifugal impeller with a blade height dimension of 60 mm, and a jet structure is provided at the blade.

[0097] Refer to Figure 13 , Figure 13 which is a comparison chart of the air volume-power curves of the centrifugal impeller of the embodiment of the present application and the centrifugal impeller of Comparative Example 2.

[0098] Among them, Comparative Example 2 is a centrifugal impeller with a blade height dimension of 50 mm, and the blade is a prototype blade in the prior art without a jet structure; an embodiment of the present application is a centrifugal impeller with a blade height dimension of 50 mm, and a jet structure is provided at the blade.

[0099] Therefore, through the test comparison with the prototype impeller (i.e., Comparative Example 1 and Comparative Example 2), under different impeller schemes and different working air volumes, the power of the centrifugal impeller of the embodiment of the present application is lower than that of the prototype centrifugal impeller at the same air volume, and the advantage is more obvious at a large air volume. Taking the 50 mm blade height impeller as an example, in the working air volume range of 260 - 280 CMH, the centrifugal impeller of the embodiment of the present application can reduce the power at the same air volume by 5.5% - 6.2% on the basis of the prototype centrifugal impeller. That is to say, under the condition of the same air volume, the centrifugal impeller in the present application has a lower power; under the condition of the same power, the centrifugal impeller in the present application has a higher air volume.

[0100] In summary, the centrifugal impeller 10 according to the embodiment of the present application has at least the following advantages:

[0101] (1) An air flow channel 201 is provided at the blade 2. A jet flow can be generated at the air flow channel 201 by using the pressure difference between the pressure surface 24 and the suction surface 25 of the blade 2, so as to energize the low-energy fluid on the suction surface 25 side of the blade 2, slow down the separation, and perform vortex breaking treatment on the already formed vortices, reduce the air flow blockage in the passage, and improve the work efficiency.

[0102] (2) The centrifugal impeller 10 has high structural strength, can meet the strength requirements when the blade 2 rotates at high speed, and can prevent the circumferential dimension of the air flow channel 201 from changing when the centrifugal impeller 10 rotates.

[0103] The centrifugal fan 100 according to an embodiment of the present application includes the above-mentioned centrifugal impeller 10. By providing the above-mentioned centrifugal impeller 10, the efficiency of the centrifugal fan 100 can be improved.

[0104] As Figure 2 shown, in some embodiments of the present application, the centrifugal fan 100 further includes a volute, and the centrifugal impeller 10 is arranged in the volute. Among them, the volute includes an upper volute 210 and a lower volute 220, and an air outlet channel is formed at the upper volute 210 on the radial side of the centrifugal impeller 10. The air flow formed by the rotation of the centrifugal impeller 10 can flow into the air outlet channel to realize the air supply function of the centrifugal fan 100.

[0105] The air conditioner 1000 according to an embodiment of the present application includes the above-mentioned centrifugal fan 100. A jet flow is formed at the blade 2 of the centrifugal impeller 10 in the centrifugal fan 100, which can improve the efficiency of the centrifugal fan 100, and thus can further improve the air supply effect of the air conditioner 1000.

[0106] In some embodiments of the present application, the air conditioner 1000 further includes a housing, and the housing includes a front panel 200, a bottom plate 400 and an outer cover 700. The centrifugal fan 100 is arranged in the housing jointly defined by the front panel 200, the bottom plate 400 and the outer cover 700, and a gas flow channel is defined between the volute of the centrifugal fan 100 and the housing. The centrifugal fan 100 can supply air to the gas flow channel to realize the air supply function of the air conditioner 1000.

[0107] Among them, the bottom plate 400 is an installation carrier for devices such as the centrifugal fan 100 and the compressor 500 in the air conditioner 1000.

[0108] Referring to Figure 2 , an air outlet 2001 and an air return port 2002 are formed at the front panel 200. The air outlet 2001 is communicated with the gas flow channel, and the air return port 2002 is communicated with the air inlet of the volute. That is to say, both the air outlet 2001 and the air return port 2002 of the air conditioner 1000 are provided on the front side of the air conditioner 1000.

[0109] In some embodiments of the present application, the air conditioner 1000 further includes a motor 600, which is arranged inside the housing and is used to cooperate with the centrifugal fan 100 to drive the centrifugal impeller 10 to rotate, so as to realize the air supply function of the centrifugal fan 100.

[0110] In some embodiments of the present application, the air conditioner 1000 further includes a heat exchanger 300, which is arranged between the panel and the centrifugal fan 100 and is used to exchange heat with the air entering the centrifugal fan 100 through the return air inlet 2002.

[0111] In the description of the present application, it should be understood that the orientation or positional relationship indicated by the terms "center", "longitudinal", "transverse", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. is based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present application and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of the present application.

[0112] In the description of the present application, the "first feature" and "second feature" may include one or more of such features.

[0113] In the description of the present application, the meaning of "a plurality" is two or more.

[0114] In the description of the present application, the first feature being "above" or "below" the second feature may include the first and second features being in direct contact, or may include the first and second features not being in direct contact but being in contact through additional features therebetween.

[0115] In the description of the present application, the first feature being "above", "above" and "on" the second feature includes the first feature being directly above and obliquely above the second feature, or merely indicating that the first feature is at a higher horizontal height than the second feature.

[0116] In the description of this specification, the description with reference to terms such as "one embodiment", "some embodiments", "schematic embodiments", "examples", "specific examples", or "some examples", etc. means that the specific features, structures, materials, or characteristics described in connection with the embodiment or example are included in at least one embodiment or example of the present application. In this specification, the schematic representations of the above terms do not necessarily refer to the same embodiment or example. Moreover, the specific features, structures, materials, or characteristics described may be combined in any one or more embodiments or examples in a suitable manner.

[0117] Although embodiments of the present application have been shown and described, those of ordinary skill in the art can understand that various changes, modifications, substitutions, and variations can be made to these embodiments without departing from the principles and spirit of the present application. The scope of the present application is defined by the claims and their equivalents.

Claims

1. A centrifugal wind wheel, characterized in that: include: Chassis; A plurality of blades are arranged along the circumferential direction of the chassis, the blades include a first blade segment and a second blade segment, the first blade segment and the second blade segment are arranged along the radial direction of the centrifugal wind wheel, and a portion of the second blade segment extends out of the chassis and forms an airflow channel with the first blade segment, and the airflow on one side of the pressure surface or the suction surface of the blade can flow to the other side of the blade through the airflow channel.

2. The centrifugal wind wheel according to claim 1, characterized in that: In the radial direction of the centrifugal wind wheel, the first blade segment and the second blade segment are spaced apart, and the distal end of the first blade segment forms a trailing edge surface, and the proximal end of the second blade segment forms a leading edge surface, and the airflow channel is defined between the trailing edge surface and the leading edge surface.

3. The centrifugal wind wheel according to claim 2, characterized in that: The chassis is provided with a communication groove, the communication groove is arranged through the chassis along the axial direction of the centrifugal wind wheel, and the communication groove is communicated with the air flow channel.

4. The centrifugal wind wheel according to claim 3, characterized in that: The communication groove is arranged on one side of the suction surface of the second blade segment, and the communication groove extends from the outer peripheral wall of the chassis to the center side of the chassis.

5. The centrifugal wind wheel according to claim 2, characterized in that: The blade is further provided with a connecting rib, and the connecting rib is connected between the first blade segment and the second blade segment.

6. The centrifugal wind wheel according to claim 2, characterized in that: The trailing edge surface and the leading edge surface are arranged at equal intervals on the air flow path of the air flow channel; Alternatively, the distance between the trailing edge surface and the leading edge surface on the airflow flow path of the airflow channel gradually decreases.

7. The centrifugal wind wheel according to claim 2, characterized in that: The distance between the proximal end of the first blade segment and the center of the chassis is R1, the minimum distance between the trailing edge surface and the center of the chassis is R2, the minimum distance between the leading edge surface and the center of the chassis is R3, and the distance between the distal end of the second blade segment and the center of the chassis is R4, and the relationship is satisfied: R2> / 2, and R3>R2.

8. The centrifugal wind wheel according to claim 7, characterized in that: The width dimension of the airflow channel in the airflow flow direction is W, and satisfies the relationship: 0.5% R4≤W≤2% R4.

9. The centrifugal wind wheel according to claim 2, characterized in that: The angle between the air inlet direction of the airflow channel and the pressure surface of the first blade segment is α, and the relationship is satisfied: α<30°; And / or, the angle between the air outlet direction of the airflow channel and the suction surface of the second blade segment is β, and satisfies the relationship: β<20°.

10. The centrifugal wind wheel according to claim 1, characterized in that: The centrifugal wind wheel is also provided with a reinforcement ring, which is connected to the plurality of second blade segments and is arranged on a side of the plurality of blades away from the chassis.

11. The centrifugal wind wheel according to claim 1, characterized in that: In the radial direction of the centrifugal wind wheel, the first blade segment is arranged on the side of the center of the second blade segment close to the chassis, and the distal end of the first blade segment is arranged on the side of the suction surface of the second blade segment, and the airflow channel is formed between the pressure surface of the first blade segment and the suction surface of the second blade segment.

12. The centrifugal wind wheel according to claim 11, characterized in that: The first blade segment and the second blade segment both extend in an arc shape, and the arc radius of the first blade segment is R5, and the arc radius of the second blade segment is R6, and the relationship is satisfied: R5<R6.

13. A centrifugal fan, characterized in that: It comprises a centrifugal wind wheel according to any one of claims 1-12.

14. An air conditioner, characterized in that: Comprising the centrifugal fan according to claim 13.

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