Fan, air-cooling heat dissipation system and electronic device

Abstract

This application relates to the field of communication equipment technology, and discloses a fan, an air-cooled heat dissipation system, and an electronic device. The fan includes a housing and a main body, with an air inlet hole on the cover plate. The main body is disposed within the housing and includes blades and a drive unit. The drive unit drives the blades to rotate around a first axis extending along a first direction. The blades are located on a radial side of the drive unit and include a first portion and a second portion connected radially. The second portion is further away from the drive unit than the first portion. The projection of the first portion onto a first plane perpendicular to the first axis lies within the projection of the air inlet hole onto the first plane. The projection of the second portion onto the first plane at least partially overlaps with the projection of the cover plate onto the first plane. The second portion includes a first side facing the cover plate, and the first portion protrudes from the first side along the first direction. This fan can accommodate both thin-film applications and aerodynamic performance requirements, while also maintaining the overall pressing characteristics of the electronic device and suppressing blade tip leakage noise.

Description

Technical Field

[0001] This application relates to the field of communication equipment technology, and in particular to a fan, an air-cooled heat dissipation system, and an electronic device. Background Technology

[0002] As electronic devices increasingly lean towards thinner and lighter designs, existing fans are no longer sufficient to meet the stacking requirements of ultra-thin chassis architectures. Taking laptops as an example, the current 3.5mm thick fans are no longer adequate for the overall chassis stacking, requiring even thinner fans to match ultra-thin end products. However, reducing fan thickness also limits the height of the fan blades and compresses the fan's air intake gap, resulting in a sharp decrease in airflow and an inability to meet the required aerodynamic performance. Summary of the Invention

[0003] Some embodiments of this application provide a fan, an air-cooled heat dissipation system, and an electronic device that can take into account both thin-film application scenarios and aerodynamic performance requirements. The following describes this application from multiple aspects, and the embodiments and beneficial effects of the following aspects can be referenced each other.

[0004] In a first aspect, embodiments of this application provide a fan. The fan includes a housing, a cover plate having an air inlet on the cover plate, and a main body disposed within the housing. The main body includes blades and a drive unit, the drive unit and the air inlet being disposed opposite each other along a first direction. The drive unit is used to drive the blades to rotate around a first axis, the first axis extending along the first direction, and the blades located on a radial side of the drive unit. The blades include a first portion and a second portion connected radially, the second portion being further away from the drive unit than the first portion. The projection of the first portion onto a first plane perpendicular to the first axis lies within the projection of the air inlet onto the first plane. The projection of the second portion onto the first plane at least partially overlaps with the projection of the cover plate onto the first plane. The second portion includes a first side facing the cover plate, and the first portion protrudes from the first side along the first direction.

[0005] In the aforementioned fan, the first part protrudes along a first direction, meaning that the blades in this application have increased height along the Z-direction on the side near the air inlet in the blade root region. Firstly, this increases the blade area without increasing the overall thickness of the fan. When the drive unit rotates the blades, the working area of ​​the blades is larger, resulting in increased airflow at the same rotational speed and stronger aerodynamic performance. Secondly, the drive unit and the air inlet are positioned opposite each other along the first direction, and the increased height of the blades in the first part closer to the drive unit helps reduce airflow leakage from the air inlet during fan operation, increasing the airflow from the air outlet at the same fan rotational speed, thereby enhancing the fan's aerodynamic performance.

[0006] In this application, after the blade is heightened in the first part, the upper gap between the blade and the cover plate, i.e. the minimum gap between the blade and the cover plate along the Z direction, is compressed. This helps to reduce the airflow leaking from the upper gap during the operation of the fan, i.e., to reduce blade tip leakage. This can effectively suppress the eddy current shedding noise caused by blade tip leakage, thereby achieving a certain noise reduction effect.

[0007] Viewed along the Z-direction, the first part is entirely within the range of the air inlet. The maximum radial dimension of the first part is less than or equal to the difference between the radius of the air inlet and the radius of the drive section. At least a portion of the second part is within the range of the cover plate. It can be understood that the first part is not obstructed by the cover plate in the Z-direction, thus providing usable Z-direction space to increase the blade height. The area where the second part is located (the area at least partially overlapping with the projected area of ​​the cover plate) is not increased in height. This avoids scraping of the fan blade cover plate under external pressure, improving the pressure resistance and pressing reliability of the electronic equipment and the fan. It also solves the problem of balancing the need for thinner and lighter electronic equipment with the aerodynamic performance requirements of the fan.

[0008] In one possible implementation of the first aspect described above, the radial distance between the first portion and the wall of the air inlet is greater than or equal to a first value. For example, the first value is 0.5 mm. This avoids the first portion being too close to the wall of the air inlet, which could affect the fan's air intake, thus ensuring the fan's operating performance and improving the fan's aerodynamic performance at the same noise level. It also reduces processing difficulty, satisfying industrial manufacturability while forming a stepped structure on the blades.

[0009] In one possible implementation of the first aspect described above, along the first direction, the height of the first portion protruding from the first side is less than or equal to the distance between the cover plate and the first side.

[0010] This design prevents the first part from protruding from the cover plate along the first direction and affecting the air intake, ensuring the fan's air intake effect and thus its operating performance. Furthermore, it ensures that the first part will not interfere with the cover plate or other components outside the fan, guaranteeing the overall reliability of the pressing mechanism.

[0011] In one possible implementation of the first aspect described above, the height of the first portion protruding from the first side along the first direction is greater than or equal to a second value. For example, the second value is 0.15 mm. This can reduce the processing difficulty of the first portion and satisfy industrial manufacturability while forming a stepped structure for the blade.

[0012] In one possible implementation of the first aspect described above, the first part and the second part are an integral structure.

[0013] In one possible implementation of the first aspect above, the first part is rectangular in shape; or, the first part includes a second side facing the air inlet, the second side being serrated or wavy.

[0014] Secondly, embodiments of this application provide an air-cooled heat dissipation system, which includes a heat transfer device, a heat dissipation device, and a fan in any possible implementation of the first aspect, wherein: the heat transfer device is connected to the heat dissipation device and is used to transfer the heat of the heat-generating component to the heat dissipation device; the fan is used to dissipate heat from the heat dissipation device.

[0015] It should be understood that the beneficial effects of the second aspect mentioned above can be referred to the description of the first aspect mentioned above, and will not be repeated here.

[0016] Thirdly, embodiments of this application provide an electronic device, which includes a heat-generating component and an air-cooled heat dissipation system in any possible implementation of the second aspect described above, wherein: a heat transfer device is connected to the heat-generating component.

[0017] It should be understood that the beneficial effects of the third aspect mentioned above can be referred to the description of the first aspect mentioned above, and will not be repeated here.

[0018] In one possible implementation of the third aspect described above, the electronic device further includes a housing, a heat-generating component, and a heat dissipation system disposed within the housing, wherein the maximum distance between the housing and the cover plate along the first direction is less than or equal to a third value. For example, the third value is 1.5 mm. Attached Figure Description

[0019] Figure 1A A cross-sectional schematic diagram of an electronic device is shown;

[0020] Figure 1B An airflow-thickness curve for a fan is shown;

[0021] Figure 1C A graph showing the relationship between the fan inlet clearance and the airflow of the fan cooling system is presented.

[0022] Figure 2 A cross-sectional schematic diagram of an electronic device according to an embodiment of this application is shown;

[0023] Figure 3 A schematic diagram of the structure of an air-cooled heat dissipation system according to an embodiment of this application is shown;

[0024] Figure 4A A schematic diagram of the structure of a fan according to an embodiment of this application is shown;

[0025] Figure 4B An exploded view of a fan according to an embodiment of this application is shown;

[0026] Figure 5A A cross-sectional schematic diagram of a portion of the structure of a fan according to an embodiment of this application is shown;

[0027] Figure 5B A cross-sectional schematic diagram of a partial structure of another fan in an embodiment of this application is shown;

[0028] Figure 5C A cross-sectional schematic diagram of a partial structure of another fan in an embodiment of this application is shown;

[0029] Figure 6A This shows a vector diagram of the flow field of a conventional fan in an electronic device;

[0030] Figure 6B This illustrates a vector diagram of the flow field of a fan in an electronic device, as provided in an embodiment of this application.

[0031] Figure 7 The diagram shows a comparison of airflow and air pressure between the fan provided in this embodiment and a conventional fan at the same noise level of 32 dBA.

[0032] Figure 8A A flow field information comparison diagram of a fan and a conventional fan at different gap values ​​is provided in an embodiment of this application.

[0033] Figure 8B This application provides a comparison diagram of flow field information between a fan and a conventional fan at different gap values ​​in an embodiment of the present application.

[0034] Figure 9A A fan provided in this application embodiment at different h step A comparison diagram of flow field information between a low-power fan and a conventional fan;

[0035] Figure 9B A fan provided in this application embodiment at different h step A comparison chart of flow field information between the value and that of a conventional fan. Detailed Implementation

[0036] The specific embodiments of this application will be described in detail below with reference to the accompanying drawings.

[0037] To make the objectives, technical solutions, and advantages of the embodiments of this application clearer, the technical solutions in the embodiments of this application will be described in detail below with reference to the accompanying drawings and specific implementation methods.

[0038] The embodiments of this application provide a fan, as well as an air-cooling heat dissipation system and electronic device including the fan. The fan provided by this application can take into account both thin-film application scenarios and aerodynamic performance requirements.

[0039] Figure 1A A cross-sectional schematic diagram of an electronic device 1a is shown.

[0040] Electronic device 1a includes a housing 12a, a heat-generating component, and a cooling system. The heat-generating component and the cooling system are housed within the housing 12a. The cooling system is connected to the heat-generating component and is used to dissipate heat from it. The cooling system includes a fan 100a, which may include blades 51a, a drive unit 52a, and a housing 4a. The drive unit 52a and the blades 51a are located within the housing 4a. The drive unit 52a drives the blades 51a to rotate, generating air pressure. The housing 4a typically includes a cover plate 41a, a frame 42a, and a bottom plate 43a. The cover plate 41a has an air inlet 411a, and the cover plate 41a, frame 42a, and bottom plate 43a together define an air outlet. Air enters the fan 100a through the air inlet 411a, is pressurized by the rotating blades 51a, and is then circumferentially ejected and exits through the air outlet, thereby driving airflow within the housing 12a to dissipate heat from the heat-generating component.

[0041] As the design trend of electronic devices 1a leans towards thinner and lighter designs, the existing 3.5mm thick fan 100a (fan 100a with a Z-direction dimension of 3.5mm) can no longer meet the stacking requirements of ultra-thin overall architectures. A thinner fan 100a is needed to match the ultra-thin electronic devices 1a. Typically, the cover plate 41a of the ultra-thin fan 100a is generally 0.3mm to 0.4mm thick, the gap between the cover plate 41a and the blades 51a in the Z-direction ranges from 0.65mm to 0.7mm, and the gap between the base plate 43a and the blades 51a in the Z-direction ranges from 0.55mm to 0.6mm.

[0042] Taking a fan 100a with a thickness of 3mm as an example, the cover plate 41a has a thickness of 0.3mm, the gap between the cover plate 41a and the blade 51a along the Z direction is 0.65mm, the height of the blade 51a (i.e., the dimension of the blade 51a along the Z direction) is 1.1mm, the base plate 43a has a thickness of 0.4mm, and the gap between the base plate 43a and the blade 51a along the Z direction is 0.55mm. It can be seen that when the total thickness of the fan 100a is limited to 3mm, the height of the blade 51a is only 1.1mm, resulting in extremely limited aerodynamic performance.

[0043] Please see Figure 1B , Figure 1B This is an airflow-thickness curve for a 65mm × 65mm fan 100a, where the length and width (dimensions in both directions perpendicular to the Z-axis) of fan 100a are both 65mm. Figure 1B The horizontal axis represents the thickness of fan 100a (unit: mm), and the vertical axis represents the airflow of fan 100a (unit: cfm). From Figure 1BAs can be seen, when the thickness of fan 100a is less than 3.5mm, the air volume of fan 100a decreases exponentially. That is, as the thickness of fan 100a is further reduced, the aerodynamic performance of fan 100a drops sharply, and the current thin and light design cannot meet the required aerodynamic performance.

[0044] With the trend towards thinner and lighter electronic devices, the air intake gap of the fan 100a has also been further reduced. (See also...) Figure 1A The air intake gap of fan 100a can be understood as the maximum distance D between the outer casing 12a and the cover plate 41a of electronic device 1a along the Z direction.

[0045] Please see Figure 1C , Figure 1C The graph shows the relationship between the inlet gap of the 100a fan and the airflow of the air-cooled system. Figure 1C The horizontal axis represents the air intake gap of fan 100a (unit: mm), and the vertical axis represents the airflow of the air-cooled system (unit: cfm). As the electronic device 1a becomes thinner, the air intake gap of fan 100a is compressed. This increases the impedance of the air-cooled system, consequently reducing its airflow. When the air intake gap decreases to below 1.5 mm, the decrease in airflow becomes even more pronounced, indicating that the thinning of electronic device 1a cannot be reconciled with the airflow requirements of the air-cooled system.

[0046] Extensive design experience shows that in application scenarios where the overall thickness of the fan 100a is limited, the height of the blades 51a is also correspondingly restricted. As electronic devices 1a evolve towards thinner and lighter designs, the thickness of the fan 100a is further reduced, and an excessively low blade height leads to insufficient aerodynamic performance. Furthermore, when the air intake gap of the fan 100a is compressed, the airflow of the air-cooled system decreases even more significantly. In ultra-thin systems of electronic devices 1a, the existing structure of conventional fans 100a can no longer provide sufficient airflow to meet air-cooling requirements.

[0047] In view of this, this application provides a fan to replace the fan 100a in the aforementioned electronic device 1a. The fan provided by this application may include a housing and a main body. The main body is disposed within the housing and includes blades and a drive unit. The blades include a first portion and a second portion connected radially. The second portion is further away from the drive unit than the first portion. The second portion includes a first side facing the cover plate. The first portion protrudes from the first side in a first direction. That is, the blades in this application have increased height in the Z-direction on the side near the air inlet in the blade root region. Without increasing the overall thickness of the fan, the working area of ​​the blades is increased, achieving an increase in airflow at the same rotational speed. Increasing the height of the blades in the first portion, closer to the drive unit, also helps to reduce airflow leakage from the air inlet during fan operation, resulting in stronger aerodynamic performance. Therefore, it can solve the problem of balancing the need for thinner and lighter electronic devices with the aerodynamic performance requirements of fans.

[0048] The technical solution of this application is described below with reference to the accompanying drawings.

[0049] Figure 2 A cross-sectional schematic diagram of an electronic device 1 according to an embodiment of this application is shown.

[0050] like Figure 2 As shown, the electronic device 1 includes a housing 12, a heat-generating component 11, and a heat dissipation system 10. The housing 12 has a receiving cavity 121, and the heat-generating component 11 and the heat dissipation system 10 are disposed within the receiving cavity 121. The heat dissipation system 10 is connected to the heat-generating component 11 and is used to dissipate heat from the heat-generating component 11.

[0051] In this embodiment of the application, electronic device 1 may include mobile phones (including candybar phones and foldable phones), laptops, tablets, handheld computers, virtual reality (VR) devices, augmented reality (AR) devices, routers, etc.

[0052] The heat-generating component 11 is a component within the electronic device 1 that generates a significant amount of heat, including but not limited to the CPU (Central Processing Unit), GPU (Graphics Processing Unit), and SoC (System-on-a-Chip). Heat-generating components 11, such as CPUs, GPUs, and SoC chips, integrate hundreds of billions or even trillions of transistors. This high integration results in extremely high heat flux density and enormous heat generation during operation. Therefore, the electronic device 1 needs to be equipped with a fan-cooled heat dissipation system 10 to promptly remove the heat from the heat-generating components 11, ensuring the operational performance of the electronic device 1.

[0053] Specifically, the outer casing 12 is provided with an inlet 122 and an outlet 123 that communicate with the receiving cavity 121. The air-cooled heat dissipation system 10 can drive air to flow from the inlet 122 to the outlet 123 so that a pressure difference is formed between the receiving cavity 121 and the external environment of the electronic device 1. Air with a lower external ambient temperature is drawn into the receiving cavity 121 through the inlet 122 on the outer casing 12, and heat dissipation is achieved for the heat-generating component 11 by forced convection. The air that has absorbed heat flows out from the outlet 123 on the outer casing 12 under the action of the pressure difference.

[0054] The structure of the air-cooled heat dissipation system 10 applied to electronic device 1 in this application is described below.

[0055] Figure 3 A schematic diagram of the structure of an air-cooled heat dissipation system 10 in an embodiment of this application is shown.

[0056] like Figure 2 and Figure 3 As shown, the air-cooled heat dissipation system 10 includes a heat transfer device 2, a heat dissipation device 3, and a fan 100. The heat transfer device 2 is connected to the heat dissipation device 3 and is used to transfer the heat of the heat-generating component 11 to the heat dissipation device 3. The fan 100 is used to dissipate heat from the heat dissipation device 3.

[0057] Among them, the heat transfer device 2 can be a device with high heat transfer performance such as a VC (vapor chamber) or a heat pipe, and the heat dissipation device 3 can be a heat exchange enhanced device such as a plate-fin heat sink or a pin-fin heat sink. The heat transfer device 2 can efficiently transfer the heat from the heat-generating components 11 such as the CPU, GPU, and SoC chip to the heat dissipation device 3, avoiding a large amount of heat accumulating on the heat-generating components 11. The heat transfer device 2 can increase the heat exchange area with the air within the limited space of the electronic device 1, thereby improving the heat exchange efficiency.

[0058] Furthermore, the fan 100 has an air inlet 411 and an air outlet 44. The fan 100 can generate a pressure difference by driving its internal blades 51 to rotate at high speed, thereby forcing airflow so that air flows from the air inlet 411 to the air outlet 44. The heat dissipation device 3 is arranged opposite to the air outlet 44 of the fan 100.

[0059] In the specific heat dissipation process of the air-cooled heat dissipation system 10, the heat transfer device 2 conducts the heat of the heat-generating component 11 to the heat dissipation device 3. The fan 100 can drive the air to flow from the air inlet 411 to the air outlet 44, so that the cavity 121 and the external environment of the electronic device 1 are formed with a pressure difference. The air with a lower external temperature is drawn into the cavity 121 through the inlet 122 on the outer casing 12 and enters the fan 100 through the air inlet 411. The blades 51 inside the fan 100 rotate at high speed, driving the air to blow from the air outlet 44 to the heat dissipation device 3. The air flows over the surface of the heat dissipation device 3 and absorbs the heat in the heat dissipation device 3. The air temperature rises and flows out from the outlet 123 on the outer casing 12 under the action of the pressure difference, thereby realizing the heat dissipation effect of the air-cooled heat dissipation system 10 on the heat-generating component 11.

[0060] It should be noted that the structures illustrated in the embodiments of this application do not constitute a specific limitation on the air-cooled heat dissipation system. In other embodiments, the air-cooled heat dissipation system may include more or fewer components than illustrated.

[0061] The structure and working principle of the fan 100 provided in the embodiments of this application will be described below with reference to the accompanying drawings.

[0062] Figure 4A This paper shows a schematic diagram of the structure of a fan 100 according to an embodiment of the present application. Figure 4B An exploded view of a fan 100 according to an embodiment of this application is shown.

[0063] In various embodiments of this application, the length direction of the fan 100 can be the X direction. The width direction of the fan 100 can be the Y direction. The thickness direction or height direction of the fan 100 can be the Z direction. The X, Y, and Z directions intersect each other. For example, the X, Y, and Z directions can be perpendicular to each other. In this application, the thickness dimension of the fan 100 or the height dimension of the blade 51 is a dimension along the Z direction, which will not be elaborated further below.

[0064] refer to Figure 4A and Figure 4B The fan 100 includes a housing 4 and a main body 5. The housing 4 includes a cover plate 41 with an air inlet 411. The main body 5 is disposed inside the housing 4 and includes blades 51 and a drive unit 52. The blades 51 are located on the radial side of the drive unit 52, that is, the blades 51 are located on the radial outer side of the drive unit 52. For example, the radial direction of the drive unit 52 can be... Figure 4A The direction indicated by the dashed arrow. The drive unit 52 and the air inlet 411 are along the first direction (e.g., ...). Figure 4A and Figure 4BThe drive unit 52 is positioned relative to the Z-direction shown, and is used to drive the blade 51 to rotate about the first axis 53, which extends along the first direction. It can be understood that the radial direction of the drive unit 52 is perpendicular to the first axis 53 and intersects with the first axis 53.

[0065] Specifically, the housing 4 of the fan 100 may further include a frame 42 and a base plate 43, the frame 42 being connected to the cover plate 41 and the base plate 43 respectively, and the cover plate 41 and the base plate 43 being located at opposite ends of the frame 42 along a first direction, such as... Figure 4A and Figure 4B As shown, the cover plate 41, the frame 42 and the bottom plate 43 are arranged along the Z direction. The frame 42, the cover plate 41 and the bottom plate 43 together define the cavity and the air outlet 44 that communicates with the cavity. The air inlet 411 communicates with the cavity, and the main body 5 is located inside the cavity.

[0066] The drive unit 52 can convert electrical energy into mechanical energy through the motor windings (stator) and rotor to drive the blades 51 to rotate, thereby generating a pressure difference that drives the airflow to enter from the air inlet 411 and flow out from the air outlet 44.

[0067] In the heat dissipation process of the air-cooled heat dissipation system 10, the fan 100 is specifically used. The heat transfer device 2 conducts the heat of the heat-generating component 11 to the heat dissipation device 3. The drive part 52 of the fan 100 drives the blades 51 to rotate around the first axis 53. A low-pressure area is formed at the air inlet 411. Air with a lower ambient temperature is drawn into the receiving cavity 121 through the inlet 122 on the outer casing 12 and enters the fan 100 through the air inlet 411. The blades 51 inside the fan 100 rotate at high speed. The air is thrown out from the air outlet 44 and blown towards the heat dissipation device 3. The air flows over the surface of the heat dissipation device 3 and absorbs the heat in the heat dissipation device 3. The air temperature rises and flows out from the outlet 123 on the outer casing 12 under the action of the pressure difference, thereby realizing the heat dissipation of the heat-generating component 11.

[0068] Figure 5A A cross-sectional schematic diagram of a portion of the structure of a fan 100 according to an embodiment of this application is shown.

[0069] In this application, the blade 51 includes a first portion 511 and a second portion 512 connected radially. The second portion 512 is further away from the drive unit 52 than the first portion 511. That is, the blade 51 is connected to the drive unit 52 through the first portion 511, the root end of the blade 51 is located on the first portion 511, and the free end of the blade 51 is located on the second portion 512. In other words, the first portion 511 is the inner part of the blade 51 near the drive unit 52 (i.e., the root region of the blade 51), and the second portion 512 is the outer part of the blade 51 away from the drive unit 52 (i.e., the outer ring region of the blade 51).

[0070] The second part 512 includes a first side 5121 facing the cover plate 41. The first part 511 protrudes from the first side 5121 along a first direction, that is, the first part 511 is higher than the first side 5121 along the first direction. It can be understood that the side of the second part 512 facing the cover plate 41 is the first side 5121, and the side of the first part 511 facing the air inlet 411 is the second side 5111. Along the Z direction, the second side 5111 is closer to the cover plate 41 than the first side 5121, so that the blade 51 forms a stepped structure in the radial direction.

[0071] That is, in this application, the blade 51 has its height increased along the Z-direction on the side of the root region of the blade 51 near the air inlet 411. Firstly, without increasing the overall thickness of the fan 100 (the dimension of the fan 100 along the Z-direction), the area of ​​the blade 51 is increased. When the drive unit 52 drives the blade 51 to rotate, the working area of ​​the blade 51 is larger, achieving an increase in airflow at the same rotational speed, thus enhancing the aerodynamic performance of the fan 100. Secondly, the drive unit 52 and the air inlet 411 are arranged opposite each other along the first direction. The increased height of the first part 511 of the blade 51 closer to the drive unit 52 helps reduce the airflow leakage from the air inlet 411 during the operation of the fan 100, increasing the airflow from the air outlet 44 at the same rotational speed of the fan 100, thereby enhancing the aerodynamic performance of the fan 100.

[0072] The projection of the first portion 511 onto the first plane perpendicular to the first axis 53 lies within the projection of the air inlet 411 onto the first plane. That is, when viewed along the Z-direction, the first portion 511 is completely within the range of the air inlet 411. The maximum radial dimension of the first portion 511 is less than or equal to the difference between the radius of the air inlet 411 and the radius of the drive unit 52. The projection of the second portion 512 onto the first plane at least partially overlaps with the projection of the cover plate 41 onto the first plane. That is, when viewed along the Z-direction, at least a portion of the second portion 512 lies within the range of the cover plate 41.

[0073] It is understood that the first part 511 of the blade 51 is located within the projection range of the air inlet 411. The first part 511 is not blocked by the cover plate 41 in the Z direction. Therefore, the first part 511 has usable space in the Z direction to increase the height of the blade 51. The area where the second part 512 is located (at least part of the area that overlaps with the projection area of ​​the cover plate 41) is not increased. This can prevent the blade 51 of the fan 100 from rubbing against the cover plate 41 under external pressure, improve the pressure resistance and pressing reliability of the electronic device 1 and the fan 100 in the Z direction, and improve the operating stability of the fan 100.

[0074] like Figure 6AThe figure shows a flow field vector diagram of a conventional fan in an electronic device. When the fan's air inlet gap is small (e.g., less than 1.5 mm), the leakage at the fan blade tip becomes more complex, and the eddy current shedding noise caused by the blade tip leakage is one of the main noise sources of the fan.

[0075] like Figure 6B The diagram shows the flow field vector of the fan 100 in the electronic device 1 provided in this application embodiment. In some implementations of this application, the maximum distance between the outer shell 12 and the cover plate 41 along the first direction is less than or equal to a third value, for example, the third value can be 1.5mm, that is, the air inlet gap of the fan 100 is less than or equal to 1.5mm, which can meet the ultra-thin design requirements of the electronic device 1. However, after the blade 51 in this application is raised in the first part 511, the upper gap between the blade 51 and the cover plate 41, that is, the minimum gap between the blade 51 and the cover plate 41 along the Z direction, is compressed, which is beneficial to reduce the airflow leaking from the upper gap during the operation of the fan 100, that is, to reduce blade tip leakage, which can effectively suppress the eddy current shedding noise caused by blade tip leakage, thereby achieving a certain noise reduction effect.

[0076] Figure 7 This is a comparison chart of airflow and air pressure of the fan 100 provided in this embodiment and a conventional fan at the same noise level of 32 dBA. Figure 7 The horizontal axis represents the fan's air volume (unit: cfm), and the vertical axis represents the fan's air pressure (unit: mmAq). The broken line with a triangle in the figure represents the fan 100 provided in the embodiment of this application, and the broken line with the origin represents a conventional fan. The blade height of the conventional fan is the same as the height of the second part 512 in the fan 100 of this application, and the dimensions of other components are the same.

[0077] Therefore, it can be seen that, under the same noise level, the airflow and air pressure of the fan 100 in this application are significantly improved compared to a conventional fan, and the individual performance of the fan 100 is improved. It can also be deduced that when the fan 100 in this application reaches the same individual performance as a conventional fan, the aerodynamic noise generated by the fan 100 in this application is lower.

[0078] As can be seen, the fan 100 provided in this application embodiment increases the working area of ​​the blades 51 to improve airflow by using the stepped structure of the blades 51 without increasing the overall thickness of the fan 100 or affecting the pressing characteristics of the electronic device 1. This can improve the aerodynamic performance of the fan 100 and suppress blade tip leakage noise, thus achieving a balance between high performance and low noise operation of the ultra-thin fan 100.

[0079] In some implementations, such as Figure 5AAs shown, the first part 511 is rectangular in shape, that is, the area of ​​the first part 511 that protrudes from the second part 512 is a regular rectangular block. The first part 511 and the second part 512 form a stepped structure, which is simple in shape and easy to process.

[0080] Figure 5B A cross-sectional schematic diagram of a portion of the structure of another fan 100 in an embodiment of this application is shown. Figure 5C A cross-sectional schematic diagram of a portion of the structure of another fan 100 in an embodiment of this application is shown.

[0081] In other embodiments, the first portion 511 includes a second side 5111 facing the air inlet 411, the second side 5111 being serrated or wavy. For example... Figure 5B As shown, the second side 5111 is serrated. (As...) Figure 5C As shown, the second side 5111 is wavy. It is understood that this application does not limit the specific shape of the first part 511, as long as it can achieve the goal of increasing the working area of ​​the blades 51 to improve the air volume without affecting the air intake hole 411.

[0082] In some feasible solutions, the first part 511 and the second part 512 are an integral structure. That is, the blade 51 is molded as a whole. Adopting an integral structure can ensure the structural strength and integrity of the blade 51, which is conducive to simplifying the manufacturing process and reducing production costs.

[0083] The following describes the performance advantages of the fan 100 in this application embodiment, as well as the specific dimensions of the first part 511 and the second part 512, based on simulation and experimental data.

[0084] Figure 8A This application provides a flow field information comparison diagram of a fan 100 under different gap values ​​and a conventional fan, as part of an embodiment of the present application. In the fan 100 of this application, the height of the first portion 511 protruding from the first side 5121 along the first direction is 0.65mm. Figure 8A The horizontal axis in the figure represents the radial spacing gap (unit: mm) between the walls of the first part 511 and the air inlet 411. Figure 8A The vertical axis on the left represents the fan's maximum airflow Qmax (unit: cfm). Figure 8A The leftmost bar chart represents the maximum airflow of a conventional fan, while the other bars represent the maximum airflow of fan 100 in this application under different gap values. Figure 8A The line graph in the figure shows the percentage increase or decrease in maximum airflow of fan 100 under the different schemes compared to a conventional fan.

[0085] It is known that the air volume of a conventional fan at a speed of 6500 rpm and an outlet impedance of 30 Pa back pressure is 1.52 cfm. At the same speed, the air volume of the fan 100 in this embodiment is up to 1.68 cfm, which is about 10% higher than the air volume at the same speed. The aerodynamic performance of the fan 100 in this embodiment is significantly improved.

[0086] Figure 8B This application provides a comparison diagram of flow field information between a fan 100 and a conventional fan under different gap values. In the fan 100 of this application, the height of the first portion 511 protruding from the first side 5121 along the first direction is 0.65mm. Figure 8B The horizontal axis in the figure represents the radial spacing gap (unit: mm) between the walls of the first part 511 and the air inlet 411. Figure 8B The vertical axis on the left represents the fan's maximum wind speed Vmax (unit: m / s). Figure 8B The leftmost bar in the graph represents the maximum wind speed of a conventional fan, while the other bars represent the maximum wind speed of fan 100 in this application under different gap values. Figure 8B The line graph in the figure shows the percentage increase or decrease in maximum wind speed of fan 100 under the different schemes compared to a conventional fan.

[0087] It is known that the maximum wind speed of a conventional fan at a speed of 6500 rpm is 22.51 m / s, while at the same speed, the highest wind speed of the fan 100 in this embodiment is 23.19 m / s. Figure 8B As shown, when gap=0.5mm, the maximum wind speed of fan 100 in this embodiment is 22.45m / s, which is 0.27% lower than that of a conventional fan. Therefore, it can be seen that the noise performance of fan 100 in this application is comparable to that of a conventional fan when the speed is the same.

[0088] Based on the simulation and experimental data above, in some feasible solutions, the radial distance between the first part 511 and the wall of the air inlet 411 is greater than or equal to a first value, which can specifically be 0.5 mm. For example... Figure 5A As shown, the radial distance between the first part 511 and the wall of the air inlet 411 is gap, such that gap is greater than or equal to a first value, for example, gap ≥ 0.5mm. This avoids the air intake of the fan 100 being affected by the small distance between the first part 511 and the wall of the air inlet 411, thus ensuring the operating performance of the fan 100 and improving the aerodynamic performance of the fan 100 at the same noise level. It also reduces the processing difficulty, satisfying industrial manufacturability while forming a stepped structure on the blade 51.

[0089] Figure 9AA fan 100 provided in this application embodiment at different h step A comparison diagram of flow field information between the fan 100 and a conventional fan is provided. In the fan 100 of this application, the radial distance gap between the first part 511 and the hole wall of the air inlet 411 is 0.5 mm. Figure 9A The horizontal axis in the figure represents the height h of the first part 511 protruding from the first side 5121 along the first direction. step (Unit: mm) Figure 9A The vertical axis on the left represents the fan's maximum airflow Qmax (unit: cfm). Figure 9A The leftmost bar in the graph represents the maximum airflow of a conventional fan, while the remaining bars represent the maximum airflow of the fan 100 in this application at [h]. step These represent the maximum air volume corresponding to different numerical schemes. Figure 9A The line graph in the figure shows the percentage increase or decrease in maximum airflow of fan 100 under the different schemes compared to a conventional fan.

[0090] It is known that a conventional fan has an airflow of 1.52 cfm at a speed of 6500 rpm. At the same speed, the fan 100 in this embodiment of the application, with the change in airflow h... step As the fan speed increases, the maximum air volume of the fan 100 also increases, reaching a maximum of 1.68 cfm. At the same rotation speed, the air volume increases by about 10%, and the aerodynamic performance of the fan 100 in this embodiment is significantly improved.

[0091] Figure 9B A fan 100 provided in this application embodiment at different h step A comparison diagram of flow field information between the fan 100 and a conventional fan is provided. In the fan 100 of this application, the radial distance gap between the first part 511 and the hole wall of the air inlet 411 is 0.5 mm. Figure 9B The horizontal axis in the figure represents the height h of the first part 511 protruding from the first side 5121 along the first direction. step (Unit: mm) Figure 9B The vertical axis on the left represents the fan's maximum wind speed Vmax (unit: m / s). Figure 9B The leftmost bar in the graph represents the maximum wind speed of a conventional fan, while the remaining bars represent the maximum wind speed of the fan 100 in this application. step These represent the maximum wind speeds corresponding to different numerical schemes. Figure 9B The line graph in the figure shows the percentage increase or decrease in maximum wind speed of fan 100 under the different schemes compared to a conventional fan.

[0092] It is known that the maximum wind speed of a conventional fan at a speed of 6500 rpm is 22.51 m / s. At the same speed, the fan 100 in this embodiment has a lower wind speed compared to a conventional fan. Figure 9B As shown, when gap=0.5mm, the maximum wind speed of fan 100 in this embodiment is 22.45m / s, which is 0.27% lower than that of a conventional fan, meaning that the noise level will be slightly reduced.

[0093] Based on the simulation and experimental data described above, in some feasible solutions, along the first direction, the height of the first portion 511 protruding from the first side 5121 is less than or equal to the distance between the cover plate 41 and the first side 5121. For example, when the distance between the cover plate 41 and the first side 5121 along the first direction is 0.65 mm, the height of the first portion 511 protruding from the first side 5121 is less than or equal to 0.65 mm. Figure 5A As shown, along the first direction, the height of the first part 511 protruding from the first side 5121 is h. step The distance between cover plate 41 and the first side 5121 is h. gap , making h step ≤h gap This design prevents the first part 511 from protruding from the cover plate 41 in the first direction and affecting the air intake 411, thus ensuring the air intake effect of the fan 100 and its operating performance. In addition, it also ensures that the first part 511 will not interfere with the cover plate 41 or other components outside the fan 100, meeting the overall pressing reliability requirements.

[0094] In some feasible solutions, along the first direction, the height of the first portion 511 protruding from the first side 5121 is greater than or equal to a second value. Specifically, the second value can be 0.15 mm. For example... Figure 5A As shown, along the first direction, the height of the first part 511 protruding from the first side 5121 is h. step , making h step Greater than or equal to the second value, for example, h step A thickness of ≥0.15mm can reduce the processing difficulty of the first part 511, and meet the manufacturability requirements for industrial production while forming a stepped structure in the blade 51.

[0095] For example, along the first direction, the height of the first part 511 protruding from the first side 5121 can be 0.15mm, 0.2mm, 0.3mm, 0.4mm, 0.5mm, 0.6mm, 0.65mm, etc.

[0096] The above description illustrates the implementation of this application through specific embodiments. Those skilled in the art can easily understand other advantages and effects of this application from the content disclosed in this specification. Although the description of this application is presented in conjunction with some embodiments, this does not mean that the features of this application are limited to these embodiments, and this application can also be implemented without using these details. Furthermore, to avoid confusion or obscuring the focus of this application, some specific details have been omitted in the description. It should be noted that, unless otherwise specified, the embodiments and features in the embodiments of this application can be combined with each other.

[0097] In the description of this application, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "outer", "inner", "circumferential", "radial", "axial", etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on this application.

[0098] In the description of this application, it should be noted that, unless otherwise expressly specified and limited, the terms "set," "install," "connect," and "fit" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal communication between two components. Those skilled in the art can understand the specific meaning of the above terms in this application based on the specific circumstances.

Claims

1. A fan (100), characterized in that, include: The housing (4) includes a cover plate (41) on which an air inlet (411) is provided. The main body (5) is disposed inside the housing (4). The main body (5) includes a blade (51) and a drive unit (52). The drive unit (52) and the air inlet (411) are arranged opposite to each other along a first direction. The drive unit (52) is used to drive the blade (51) to rotate around a first axis (53). The first axis (53) extends along the first direction. The blade (51) is located on the radial side of the drive unit (52). The blade (51) includes a first part (511) and a second part (512) connected along the radial direction. The second part (512) is further away from the drive unit (52) than the first part (511). The projection of the first part (511) onto a first plane perpendicular to the first axis (53) is located within the projection of the air inlet (411) onto the first plane. The projection of the second part (512) onto the first plane at least partially overlaps with the projection of the cover plate (41) onto the first plane. The second portion (512) includes a first side (5121) facing the cover plate (41), and the first portion (511) protrudes from the first side (5121) along the first direction.

2. The fan (100) according to claim 1, characterized in that, Along the radial direction, the distance between the walls of the first portion (511) and the air inlet (411) is greater than or equal to a first value.

3. The fan (100) according to claim 2, characterized in that, The first value is 0.5 mm.

4. The fan (100) according to claim 1, characterized in that, Along the first direction, the height of the first portion (511) protruding from the first side (5121) is less than or equal to the distance between the cover plate (41) and the first side (5121).

5. The fan (100) according to claim 1, characterized in that, Along the first direction, the height of the first portion (511) protruding from the first side (5121) is greater than or equal to the second value.

6. The fan (100) according to claim 5, characterized in that, The second value is 0.15 mm.

7. The fan (100) according to claim 1, characterized in that, The first part (511) and the second part (512) are an integral structure.

8. The fan (100) according to claim 1, characterized in that, The first part (511) is rectangular in shape; Alternatively, the first portion (511) includes a second side facing the air inlet (411), the second side being serrated or wavy.

9. A wind-cooled heat dissipation system (10), characterized in that, Includes a heat transfer device (2), a heat dissipation device (3), and a fan (100) according to any one of claims 1-8, wherein: The heat transfer device (2) is connected to the heat dissipation device (3) and is used to transfer the heat of the heat-generating component (11) to the heat dissipation device (3). The fan (100) is used to dissipate heat from the heat dissipation device (3).

10. An electronic device (1), characterized in that, Includes a heat-generating component (11) and a wind-cooled heat dissipation system (10) as described in claim 9, wherein: The heat transfer device (2) is connected to the heating element (11).

11. The electronic device (1) according to claim 10, characterized in that, It also includes a housing (12), the heating component (11) and the air-cooled heat dissipation system (10) are disposed inside the housing (12), and the maximum distance between the housing (12) and the cover plate (41) along the first direction is less than or equal to a third value.

12. The electronic device (1) according to claim 11, characterized in that, The third value is 1.5 mm.

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