Double-flow-channel cooling fan

Abstract

The utility model discloses a double-flow-channel cooling fan, and the fan comprises a fan frame which comprises a bottom plate, side plates extending upwards from the periphery of the bottom plate, and a top plate; the inner wall surface of the side plate comprises a tongue opening section, an arc-shaped section and a linear section, and a starting point A is formed at the connecting position of the tongue opening section and the arc-shaped section; a stator assembly and a fan wheel assembly; a flow channel is formed between the outer circumference of the fan wheel assembly and the cavity side wall. The splitter is arranged in the flow channel and supported between the inner wall surface of the bottom plate and the inner wall surface of the top plate, and the splitter extends along the flow channel to form an arc shape; wherein a straight line which passes through the starting point A and is perpendicular to the axis of the fan wheel assembly is defined as a starting point line L1, and the starting point end of the splitter is located on the starting point line L1; a straight line which passes through the terminal end of the splitter and is perpendicular to the axis of the fan wheel assembly is defined as a terminal line L2, the included angle A1 between the starting line L1 and the terminal line L2 is not smaller than 45 degrees and not larger than 90 degrees, and the double-flow-channel fan has better wind driving and heat dissipation performance.

Description

Technical Field

[0001] The present application relates to a double-channel cooling fan. Background Art

[0002] Cooling fans are widely used as common heat dissipation components in current consumer electronic devices. For related prior art, please refer to Chinese Patent Application Publication No. CN202011630450.0 (Prior Art 1). This patent application discloses a split-flow cooling fan, including a frame body and a fan wheel received in the frame body. The fan wheel has a fan wheel center line arranged in a first direction. An air outlet is formed on one side of the frame body. A flow channel is formed inside the frame body around the fan wheel. A plurality of guide vanes for evenly splitting the airflow are installed in the flow channel along the direction of airflow movement. By installing a plurality of guide vanes in the flow channel, the gas flow in the flow channel becomes more uniform, reducing airflow vortices, lowering aerodynamic noise and vibration noise, balancing the negative pressure area, and ensuring a larger actual air intake area.

[0003] However, through actual product testing, it is obtained that although the structural design of the plurality of guide vanes in the prior art can make the gas flow in the flow channel more uniform, reduce airflow vortices, lower aerodynamic noise and vibration noise, balance the negative pressure area, and ensure a larger actual air intake area.

[0004] But it will reduce the Pmax and Qmax values of the cooling fan to a certain extent. The Pmax and Qmax values are the endpoint values of the P-Q curve (cooling fan characteristic curve) of the cooling fan, where:

[0005] (1) Pmax: When the air volume is 0, in the state of a fixed volume in a certain closed space, it is the maximum static pressure value of the fan;

[0006] (2) Qmax: When the pressure difference between the two ends of the air inlet and the air outlet of the fan is 0, it is the flow rate, that is, the maximum flow rate of the fan;

[0007] (3) P-Q value: It is the corresponding value of the pressure difference between the two ends of the air inlet and the air outlet of the fan and the flow rate Q in the current state.

[0008] Generally speaking, the larger the Pmax value (maximum static pressure value) and the larger the Qmax value (maximum flow rate value) of the same model of fan, it can be generally determined that this model of fan has better heat dissipation performance.

[0009] The related prior art can also refer to the Chinese invention patent announcement No. CN115066139B (prior art 2). The heat dissipation module of the prior art is provided with a guide support body in the heat dissipation shell to support the cover plate and the plate body, so as to prevent the fan from being damaged when the volute is subjected to external pressure, and to ensure the rigidity of the volute; and to improve the velocity distribution of the airflow at the volute outlet position, so that the airflow velocity discharged from the outlet is uniform, and the heat dissipation efficiency of the heat dissipation fin group is improved, thereby improving the heat dissipation efficiency of the electronic equipment. However, it is found through research that the implementation scheme in the prior art is due to the design position of the partition 40 and the design of the guide support body 30, especially the design scheme that the partition 40 and the guide support body 30 are spaced along the flow direction of the flow channel, and the actual airflow in the flow channel still has the problem of turbulence (the prior art 1 also has this problem). The main problem is that the airflow will be divided and guided multiple times along the flow path in the flow channel. And it will also have an adverse effect on the Pmax and Qmax values ​​of the heat dissipation fan.

[0010] Due to the wide variety of fan structures in the prior art, it has become difficult to quickly design a fan with excellent performance in fan product design. For example, how should the guide vane / guide support body be specifically set (specific setting position, setting quantity, and shape) to improve the fan performance (especially the improvement of Pmax and Qmax values ​​that have a significant effect on the fan's heat dissipation performance). Utility Model Content

[0011] The purpose of this application is to provide a new dual-channel fan to solve the above-mentioned technical problems.

[0012] To achieve the above objectives, this application adopts the following technical solutions:

[0013] A dual-channel heat dissipation fan, comprising:

[0014] The fan frame includes a bottom plate, side plates extending upward from the bottom plate, and a top plate covering the side plates and arranged opposite to the bottom plate;

[0015] The fan frame is formed with a hollow cavity, an air inlet formed through the top plate, and an air outlet formed on the side plate;

[0016] The inner wall surface of the side plate includes a tongue segment, an arc segment and a straight segment, and the connection position of the tongue segment and the arc segment forms a starting point A;

[0017] A stator assembly is fixedly assembled in the cavity;

[0018] A fan wheel assembly is rotatably assembled in the cavity and electromagnetically coupled with the stator assembly, wherein the fan wheel assembly is provided with a hub and a plurality of fan blades extending outward from the outer circumference of the hub;

[0019] A flow channel is formed between the outer peripheral circle of the fan wheel assembly and the cavity side wall, and the width of the flow channel gradually expands along the flow channel from the starting point A;

[0020] A shunt piece is arranged in the flow channel and supported between the inner wall surface of the bottom plate and the inner wall surface of the top plate. The shunt piece extends in an arc along the flow channel and has a starting end and an ending end; wherein

[0021] Taking the axis O of the fan wheel assembly as an endpoint, a first ray L0 is formed passing through the starting point A;

[0022] The first ray L0 rotates 175 degrees along the flow channel with the axis O as an endpoint to form a second ray L1;

[0023] Taking the axis O as an endpoint, a third ray L2 is formed passing through the starting end;

[0024] The first ray L0 rotates 185 degrees along the flow channel with the axis O as an endpoint to form a fourth ray L3;

[0025] Taking the axis O as an endpoint, a fifth ray L4 is formed passing through the ending end;

[0026] The second ray L1, the fourth ray L3, the inner wall surface of the side plate, and the outer peripheral circle of the fan wheel assembly jointly enclose a starting area B, and the starting end of the shunt piece is located within the starting area B;

[0027] The included angle A1 between the third ray L2 and the fifth ray L4 is not less than 45 degrees and not greater than 90 degrees.

[0028] Further, the third ray L2 is formed by rotating the first ray L0 180 degrees along the flow channel with the axis O as an endpoint.

[0029] Further, the starting end is formed by rotating the starting point A 180 degrees along the flow channel with the axis O as an endpoint.

[0030] Further, the distance from the starting end to the inner wall surface of the side plate is equal to the distance from the starting end to the outer peripheral circle of the fan wheel assembly.

[0031] Further, the extending arc and curvature of the shunt piece with the starting end as an endpoint along the flow channel are the same as those of the arc segment with the starting point A as an endpoint along the flow channel.

[0032] Further, no structure supported between the inner wall surface of the bottom plate and the inner wall surface of the top plate is provided in the flow channel except for the one shunt piece.

[0033] Further, the included angle A1 between the third ray L2 and the fifth ray L4 is equal to 45 degrees or equal to 90 degrees.

[0034] Further, the flow splitter is integrally injection-molded from a plastic material and bonded to the bottom plate.

[0035] The beneficial effects of this application are as follows: Compared with the prior art, the dual-channel fan of this design has better air driving and heat dissipation performance. BRIEF DESCRIPTION OF THE DRAWINGS

[0036] The present application will be further described below in conjunction with the views and embodiments.

[0037] Figure 1 is a perspective schematic diagram of the dual-channel fan of the present application.

[0038] Figure 2 is Figure 1 a partial perspective exploded view of the dual-channel fan in [reference], specifically showing the perspective schematic diagram after the top plate is separated.

[0039] Figure 3 is a top view of the dual-channel fan of the present application after removing the top plate, specifically showing the form of the first embodiment.

[0040] Figure 4 is a top view of the dual-channel fan of the present application after removing the top plate, specifically showing the form of the second embodiment.

[0041] Figure 5 is a top view of the dual-channel fan of the present application after removing the top plate, specifically showing the form of the third embodiment.

[0042] Figure 6 is a top view of the dual-channel fan of the present application after removing the top plate, specifically showing the form of the fourth embodiment.

[0043] Figure 7 is Figure 3 another schematic diagram of the first embodiment shown in [reference], mainly used to show the starting area B (the area shaded by oblique lines).

[0044] In order to make the purpose, technical solution and advantages of the present application clearer, the present application will be further described in detail below in conjunction with the drawings and specific embodiments. It should be understood that the specific embodiments described herein are only used to explain the present application and are not used to limit the present application.

[0045] In order to illustrate the technical solution described in the present application, the following will be illustrated by specific embodiments.

[0046] Please refer to Figures 1 to 3As shown, a double-flow channel fan disclosed in the present application is mainly used in electronic products such as laptops and tablets. The double-flow channel fan includes: a fan frame 1, a stator assembly, and a fan wheel assembly 2. Among them, the fan frame 1 includes a bottom plate 11, side plates 12 extending upward from the periphery of the bottom plate 11, and a top plate 13 covering above the side plates 12 and disposed opposite to the bottom plate 11. The fan frame 1 forms a hollow cavity 10, an air inlet 130 penetrating through the top plate 13, and an air outlet 120 formed on the side plate 12. The stator assembly is fixedly assembled in the cavity 10. The stator assembly generally includes a silicon steel sheet group, a plastic base frame integrally covering and fixing the silicon steel sheet group, and a coil group. The fan wheel assembly 2 is rotatably assembled in the cavity 10. The fan wheel assembly 2 is provided with a hub 21 and a plurality of fan blades 22 extending outward from the outer periphery of the hub 21. The fan wheel assembly 2 is electromagnetically coupled with the stator assembly and is driven to rotate, sucking air flow from the air inlet 130 and blowing it out through the air outlet 120 to achieve the effect of driving air for heat dissipation.

[0047] The inner wall surface of the side plate 12 includes a tongue section 121, an arc section 122, and a straight section 123. The connection position between the tongue section 121 and the arc section 122 is defined as the starting point A. The double-flow channel fan in the present application is a centrifugal cooling fan. A flow channel is formed between the outer circumference 20 of the fan wheel assembly 2 and the cavity side wall 12. The width of the flow channel gradually expands from the starting point A along the flow channel (shown as counterclockwise in the embodiment of the present application, which depends on the position of the tongue section 121).

[0048] Please refer to Figure 2 and Figure 3As shown, the dual-channel fan of the present application further includes a flow splitter 3 (first embodiment), which is disposed in the flow channel and supported between the inner wall surfaces of the bottom plate 11 and the top plate 13. The flow splitter 3 is integrally injection-molded from a plastic material and combined with the bottom plate 11. The flow splitter 3 extends along the flow channel (shown as extending counterclockwise in the embodiment of the present application, which depends on the position of the tongue section 121) in an arc shape. The flow channel is split into two flow channels at a specific position by the flow splitter 3. The flow splitter 3 extends in an arc shape along the flow channel and has a starting end 31 and an ending end 32. Among them, a first ray L0 is formed with the axis O of the fan wheel assembly as an endpoint passing through the starting point A; the first ray L0 rotates 175 degrees along the flow channel with the axis O as an endpoint to form a second ray L1; a third ray L2 is formed with the axis O as an endpoint passing through the starting end; the first ray L0 rotates 185 degrees along the flow channel with the axis O as an endpoint to form a fourth ray L3; a fifth ray L4 is formed with the axis O as an endpoint passing through the ending end. In the first embodiment, the first ray L0 and the third ray L2 are on the same straight line. More specifically: the starting end 31 is formed by rotating the starting point A 180 degrees along the flow channel with the axis O as an endpoint (shown as rotating counterclockwise 180 degrees in the embodiment of the present application, which depends on the position of the tongue section 121, and specifically can be referred to Figure 3 for illustration, A2 is equal to 18 degrees). Preferably: the included angle A1 between the third ray L2 and the fifth ray L4 is 90 degrees. In this embodiment (the first embodiment), the extending radian and curvature of the flow splitter 3 with the starting end 31 as an endpoint along the flow channel are the same as those of the arc section 122 with the starting point A as an endpoint along the flow channel.

[0049] Please refer to Figure 4 As shown, it is the second embodiment of the dual-channel fan of the present application. The only difference between the second embodiment and the first embodiment is: the extending length of the flow splitter 3 is different. In the second embodiment, the included angle A1 between the third ray L2 and the fifth ray L4 is 45 degrees.

[0050] Please refer to Figure 5 As shown, it is the third embodiment of the dual-channel fan of the present application. The only difference between the third embodiment and the first embodiment is: the position of the flow splitter 3 is different. In the third embodiment, the distance from the starting end 31 to the inner wall surface of the side plate is equal to the distance from the starting end 31 to the outer peripheral circle 20 of the fan wheel assembly. The length, extending radian and curvature of the flow splitter 3 in the third embodiment are exactly the same as those in the first embodiment.

[0051] Please refer to Figure 6As shown, this is the fourth embodiment of the dual-channel fan of the present application. The only difference between the fourth embodiment and the second embodiment is: the position of the flow dividing piece 3 is different. In the fourth embodiment, the distance from the starting end 31 to the inner wall surface of the side plate is equal to the distance from the starting end 31 to the outer peripheral circle 20 of the fan wheel assembly (which is the same as the third embodiment). The length, extending radian and curvature of the flow dividing piece 3 in the fourth embodiment are exactly the same as those in the second embodiment.

[0052] In the design, the fourth embodiment is used as the experimental sample for simulation testing, and the prior art one and prior art two solutions in the background art are used as the simulation comparison objects. The following experimental data are obtained through single unit testing simulation (simulating a single fan itself):

[0053] It can be seen that for the single unit testing of the dual-channel fan of the present application, both the maximum flow rate value and the maximum static pressure value are improved to varying degrees.

[0054] In addition, in the design, the fourth embodiment is used as the experimental sample for simulation testing, and the prior art one and prior art two solutions in the background art are used as the simulation comparison objects. The following experimental data are obtained through system entry testing simulation (simulating when assembled into a notebook computer system):

[0055] Similarly, it can be seen that for the system entry testing of the dual-channel fan of the present application, the actual flow rate value is also improved.

[0056] Similarly, in the design of the present application, Figure 3 and Figure 4 In the shown embodiment, the included angle A1 between the third ray L2 and the fifth ray L4 is increased by 5 degrees starting from 30 degrees as a test simulation sample until the included angle A1 between the third ray L2 and the fifth ray L4 is 100 degrees. Software testing simulation is carried out according to the above scheme. Finally, it is obtained that: when the included angle A1 between the third ray L2 and the fifth ray L4 is between 45 degrees and 90 degrees, the performance is improved.

[0057] Similarly, in the design of the present application, Figure 5 and Figure 6 In the shown embodiment, the included angle A1 between the third ray L2 and the fifth ray L4 is increased by 5 degrees starting from 30 degrees as a test simulation sample until the included angle A1 between the third ray L2 and the fifth ray L4 is 100 degrees. Software testing simulation is also carried out according to the above scheme. Finally, it is obtained that: when the included angle A1 between the third ray L2 and the fifth ray L4 is between 45 degrees and 90 degrees, the performance is improved.

[0058] Specifically, during the testing, the included angle A1 between the above-mentioned third ray L2 and the fifth ray L4 is selected as: 30 degrees, 35 degrees, 40 degrees, 45 degrees, 50 degrees, 55 degrees, 60 degrees, 65 degrees, 70 degrees, 75 degrees, 80 degrees, 85 degrees, 90 degrees, 95 degrees, 100 degrees.

[0059] The design finds that the specific design positions of the starting end 32 are not limited to only the two cases of Embodiment 1 and Embodiment 2, and Embodiment 3 and Embodiment 4. Please refer to Figure 7 As shown, the second ray L1, the fourth ray L3, the inner wall surface of the side plate, and the outer circumference 20 of the fan wheel assembly jointly enclose a starting area B ( Figure 7 the area of the diagonal shaded part in the figure). Designing the starting end 31 of the flow dividing piece 3 within the starting area B has a positive effect on improving the performance of the above-mentioned fan. Only Embodiment 1, Embodiment 2, Embodiment 3, and Embodiment 4 are relatively optimal design schemes of this application.

[0060] When the centrifugal fan of this application rotates to drive the air, the air is sucked in from the air inlet 130, pressurized at the tongue position in the flow channel (that is, the position of the flow channel close to the starting point A) to increase the flow velocity of the air flow in the flow channel, and then rotates and drives along the flow channel and blows out from the air outlet 120. By adding a deflector 3 in this application and designing the starting end 31 of the deflector 3 on the third ray L2 (here, the third ray L2 is formed by rotating the first ray L0 180 degrees with the axis O as the end point along the flow channel), or within a certain surrounding area (that is, the starting area B mentioned above); a double-tongue structure is formed in the flow channel of the fan, and the air is pressurized again at the flow channel position of the starting end 31 of the deflector 3 to further increase the flow velocity of the air flow in the flow channel, thereby realizing the improvement of the performance of the above-mentioned fan. In addition, setting the positions of the above two tongue pressurizations to be symmetric at 180 degrees or nearly symmetric at 180 degrees can effectively reduce noise and make the entire fan operate more stably.

[0061] In this application, only one flow dividing piece 3 is provided in the flow channel. Except for the flow dividing piece 3, no structure is provided in the flow channel to support between the inner wall surface of the bottom plate 11 and the inner wall surface of the top plate 13. At the same time, innovative optimizations are made to the starting end 31, the ending end 32, and the extending path of the flow dividing piece 3, and finally the performance of the double-flow channel fan of this application is effectively improved. In addition, the flow dividing piece 3 can play a role in supporting the top plate 13, preventing the fan frame 1 from being damaged when subjected to external pressure, and can ensure the stiffness of the fan frame 1.

[0062] For those skilled in the art, it is obvious that this application is not limited to the details of the above-mentioned exemplary embodiments, and without departing from the spirit or basic characteristics of this application, this application can be implemented in other specific forms. Therefore, from any point of view, the embodiments should be regarded as exemplary and non-limiting. The scope of this application is defined by the appended claims rather than the above description. Therefore, all changes falling within the meaning and scope of the equivalent elements of the claims are intended to be included in this application.

[0063] In addition, it should be understood that although this specification is described by way of examples, not every example only contains an independent technical solution. This narrative manner of the specification is only for clarity. Those skilled in the art should regard the specification as a whole, and the technical solutions in each example can also be appropriately combined to form other design manners understandable by those skilled in the art.

Claims

1. A double-channel cooling fan, characterized in that, Comprising: A fan frame, including a bottom plate, side plates extending upward from the periphery of the bottom plate, and a top plate covering the upper part of the side plates and disposed opposite to the bottom plate; The fan frame is formed with a hollow cavity, an air inlet formed through the top plate, and an air outlet formed on the side plates; The inner wall surface of the side plates includes a tongue section and an arc section, and a starting point (A) is formed at the connection position of the tongue section and the arc section; A stator assembly fixedly assembled in the cavity; A fan wheel assembly rotatably assembled in the cavity and electromagnetically coupled with the stator assembly. The fan wheel assembly is provided with a hub and a plurality of fan blades extending outward from the outer periphery of the hub; A flow channel is formed between the outer peripheral circle of the fan wheel assembly and the side wall of the cavity, and the width of the flow channel shows a gradually expanding trend along the flow channel starting from the starting point (A); A shunt piece is disposed in the flow channel and supported between the inner wall surface of the bottom plate and the inner wall surface of the top plate. The shunt piece extends in an arc shape along the flow channel and has a starting end and an ending end; Wherein A first ray (L0) is formed with the axis (O) of the fan wheel assembly as an endpoint passing through the starting point (A); The first ray (L0) rotates 175 degrees around the axis (O) along the flow channel to form a second ray (L1); A third ray (L2) is formed with the axis (O) as an endpoint passing through the starting end; The first ray (L0) rotates 185 degrees around the axis (O) along the flow channel to form a fourth ray (L3); A fifth ray (L4) is formed with the axis (O) as an endpoint passing through the ending end; The second ray (L1), the fourth ray (L3), the inner wall surface of the side plates, and the outer peripheral circle of the fan wheel assembly jointly enclose a starting area (B), and the starting end of the shunt piece is located in the starting area (B); The included angle (A1) between the third ray (L2) and the fifth ray (L4) is not less than 45 degrees and not greater than 90 degrees.

2. The double-channel cooling fan according to claim 1, characterized in that, The third ray (L2) is formed by rotating the first ray (L0) 180 degrees around the axis (O) along the flow channel.

3. The double-channel cooling fan according to claim 2, characterized in that, The starting end is formed by rotating the starting point (A) 180 degrees around the axis (O) along the flow channel.

4. The double-channel cooling fan according to claim 2, characterized in that: The distance from the starting end to the inner wall surface of the side plates is equal to the distance from the starting end to the outer peripheral circle of the fan wheel assembly.

5. The double-channel cooling fan according to claim 1 or 2 or 3 or 4, characterized in that, The extending arc and curvature of the shunt piece with the starting end as an endpoint along the flow channel are the same as those of the arc section with the starting point (A) as an endpoint along the flow channel.

6. The double-channel cooling fan according to claim 1, characterized in that, No structure supported between the inner wall surface of the bottom plate and the inner wall surface of the top plate is provided in the flow channel except for the one shunt piece.

7. The double-channel cooling fan according to claim 1, characterized in that, The included angle (A1) between the third ray (L2) and the fifth ray (L4) is equal to 45 degrees or equal to 90 degrees.

8. The double-channel cooling fan according to claim 1, characterized in that, The shunt piece is integrally injection-molded from a plastic material and bonded to the bottom plate.

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