CN110892160A

CN110892160A - Fan and mobile terminal

Info

Publication number: CN110892160A
Application number: CN201880039253.6A
Authority: CN
Inventors: 杨果; 王剑亮; 杨宝海; 蓬莱谷忠孝
Original assignee: Huawei Technologies Co Ltd; Nidec Corp
Current assignee: Huawei Technologies Co Ltd; Nidec Corp
Priority date: 2018-02-02
Filing date: 2018-02-02
Publication date: 2020-03-17
Anticipated expiration: 2038-02-02
Also published as: EP3736449A4; EP3736449B1; CN110892160B; EP3736449A1; WO2019148468A1

Abstract

The application provides a fan and mobile terminal, this fan includes the casing to and set up in the casing and casing pivoted centrifugal impeller relatively, centrifugal impeller includes a plurality of blades, is provided with a plurality of grooves of arranging along blade radial direction on at least one blade in a plurality of blades, and the slope setting that the groove becomes certain angle relative to the tangential normal direction of blade radial direction. In use, the movement of the air flow relative to the blades is composed of the speed along the tangential direction of the blades and the speed relative to the radius of the centrifugal impeller, namely the final relative speed is not parallel to the normal direction of the blades (the direction perpendicular to the tangential direction of the radial direction of the blades), therefore, in order to enable the air to flow through the grooves in a smoother mode, the grooves arranged in the embodiment of the application are inclined relative to the radial direction, so that the length direction of the grooves and the direction of the relative speed are as same as possible, and the air passing performance on the grooves is improved. Thereby improving the passing effect and reducing the noise caused by the fan.

Description

Fan and mobile terminal

Technical Field

The application relates to the technical field of mobile terminals, in particular to a fan and a mobile terminal.

Background

Terminal products such as notebook computers and tablet computers need to be more and more light and thin in size due to light and thin requirements of users, and meanwhile, good heat dissipation performance is needed, so that better temperature experience is achieved. And to improve the user's quiet experience, a fan with lower noise is required. This requires a high air volume and low noise while having as small a size as possible for the radiator fan.

The traditional fan easily causes the deterioration of a flow field of an inlet air inlet area due to the reduction of the size, reduces the air quantity and influences the air supply effect of the fan.

Disclosure of Invention

The application provides a fan and a mobile terminal, which are used for improving the air output of the fan.

In a first aspect, the present application provides a fan, which includes a housing, the housing having an air inlet and an air outlet, and a centrifugal impeller disposed in the housing, the centrifugal impeller being rotatable relative to the housing to send air into the air inlet and into the air outlet; when the centrifugal impeller is specifically arranged, the centrifugal impeller comprises a plurality of blades, the blades are arranged around a driving shaft of the centrifugal impeller, in order to improve the air inlet effect, a plurality of grooves are formed in at least one of the blades, the grooves are arranged along the radial direction of the blades, and the grooves are obliquely arranged at a certain angle relative to the normal direction of the radial tangent line of the blades. Wherein, the radial direction of blade is along the extending direction who gradually keeps away from the drive shaft on the blade.

In use, the movement of the air flow relative to the blades is composed of the speed along the tangential direction of the blades and the speed relative to the radius of the centrifugal impeller, namely the final relative speed is not parallel to the normal direction of the blades (the direction perpendicular to the radial tangential direction of the blades), therefore, in order to enable the air to flow through the grooves in a smoother mode, the grooves arranged in the embodiment of the application are inclined relative to the radial direction, so that the length direction of the grooves and the direction of the relative speed are as same as possible, and the air passing performance on the grooves is improved. Thereby improving the passing effect and reducing the noise caused by the fan.

The grooves may be formed in various ways when they are specifically formed, as described below.

In a specific embodiment, the groove is a first groove inclined in a single direction, and the included angle between the length direction of the first groove and the normal direction of the radial tangent of the blade is an acute angle. The acute angle may be any angle between 3 ° and 75 °. So that the first grooves can be more matched with the relative speed, and the air passing performance is improved.

When the first grooves are specifically arranged, the plurality of first grooves may be arranged on different surfaces of the blade, for example, when the blade has opposite top and bottom surfaces, the first grooves may be arranged on the top and bottom surfaces, or the first grooves may be arranged on the top or bottom surface. Where the blade has opposite sides, a first groove may also be provided on the sides of the blade. And when the first grooves are arranged on the surface of the blade, the first grooves may be arranged periodically or non-periodically.

In addition, different shapes can be adopted for the first grooves, and particularly, the cross section of the first grooves can be rectangular or triangular. Or have a streamlined oval shape, or other shapes.

For a single first groove, the height of the first groove is measured along the height direction of the blade and is between 0.1% and 25% of the total height of the blade, the width direction dimension of the first groove is measured along the radial length direction of the blade, and the width of the first groove is between 0.1% and 25% of the total length of the blade.

In another specific embodiment, the groove is a herringbone second groove, specifically, the second groove includes a first groove body and a second groove body which are inclined relatively, and included angles between the first groove body and the blade radial tangent direction and included angles between the second groove body and the blade radial tangent direction are acute angles respectively. The acute angle may be any angle between 3 ° and 75 °. And when the second grooves are specifically arranged, the periodicity of the arrangement surface and arrangement thereof can be referred to the description of the first grooves.

In order to further improve the air supply effect, a third groove is arranged on the outer end face of the blade. Further improving the ventilation effect.

Besides the groove, the air inlet effect of the fan can be improved by adding the guide ring. Specifically, the driving shaft of the centrifugal impeller is exposed out of the air inlet; and the guide ring is fixedly connected with the blades, and one surface of the guide ring, facing the driving shaft, is a guide surface. When air enters, the air flowing in from the air inlet is guided through the guide surface of the guide ring, so that the effect of the air when the air turns is improved, the vortex is reduced, the air circulation is improved, and the air inlet effect is improved. When the guide ring is used specifically, the guide ring can be used independently or combined with the grooves, so that the air supply effect is further improved.

When the guide ring is specifically arranged, the guide ring can be in an integral annular shape, or a segmented mode can be adopted, and at the moment, the guide ring comprises a plurality of arc sections which are arranged at intervals.

In addition, when the position of the guide ring is specifically arranged, the guide ring can be positioned inside the shell or exposed out of the air inlet. In a specific embodiment, the guide ring is exposed at the air inlet.

The cross section of the guide ring can be different shapes, such as a circular, oval or bullet shape.

In a second aspect, a fan is provided, which includes a housing, the housing having an air inlet and an air outlet, and a centrifugal impeller disposed in the housing, the centrifugal impeller being rotatable relative to the housing so as to send air into the air inlet and into the air outlet; when specifically setting up, this centrifugal impeller includes a plurality of blades, and this a plurality of blades encircle centrifugal impeller's drive shaft setting, in order to improve the air inlet effect, still include the guide ring, just the guide ring with a plurality of blade fixed connection, the guide ring orientation the one side of drive shaft is the spigot surface.

When the air inlet guide ring is used, air flowing in from the air inlet is guided through the guide surface of the guide ring during air inlet, so that the effect of the air during steering is improved, the vortex is reduced, the air circulation is improved, and the air inlet effect is improved.

When the guide ring is specifically arranged, the guide ring may be an integral ring, or may be segmented, for example, the guide ring includes a plurality of arc segments arranged at intervals.

In a third aspect, the present application further provides a mobile terminal comprising a housing and the fan of any of the above disposed within the housing. The effect of improving the air output of the fan and reducing the noise of the fan is achieved by adding the guide ring, the groove or the groove and the guide ring.

Drawings

Fig. 1 is a schematic structural diagram of a fan according to an embodiment of the present disclosure;

FIG. 2 is a cross-sectional view of a fan provided in an embodiment of the present application;

fig. 3 is a schematic structural diagram of a centrifugal impeller provided in an embodiment of the present application;

FIGS. 4-8 are schematic cross-sectional views of guide rings provided in embodiments of the present application;

FIG. 9 is a schematic size diagram of a fan according to an embodiment of the present disclosure;

FIG. 10 is a cross-sectional dimension schematic of a guide ring provided in accordance with an embodiment of the present application;

FIG. 11 is a schematic structural diagram of another centrifugal impeller provided in the embodiments of the present application;

FIG. 12 is a schematic structural view of a blade according to an embodiment of the present disclosure;

FIG. 13 is a schematic structural view of another bucket provided in accordance with embodiments of the present application;

FIG. 14 is a schematic structural view of another bucket provided in accordance with embodiments of the present application;

fig. 15 is a schematic view of the direction of an internal flow field of a centrifugal impeller provided in an embodiment of the present application;

FIG. 16 is a schematic view of the internal flow field orientation of the blade shown in FIG. 13;

FIG. 17 is a schematic view of the internal flow field orientation of the blade shown in FIG. 14;

fig. 18 is a schematic structural diagram of a mobile terminal according to an embodiment of the present application.

Detailed Description

In order to make the objects, technical solutions and advantages of the present invention clearer, the present invention will be described in further detail with reference to the accompanying drawings, and it is apparent that the described embodiments are only a part of the embodiments of the present invention, not all of the embodiments. All other embodiments, which can be derived by a person skilled in the art from the embodiments given herein without making any creative effort, shall fall within the protection scope of the present invention.

Aiming at the gradual thinning development of the mobile terminal in the prior art, the fan in the mobile terminal in the prior art also needs to be continuously miniaturized for matching the mobile terminal, so that the air supply amount is reduced. In order to improve the problem of the air supply amount, embodiments of the present application provide a fan, and in the fan provided in the embodiments of the present application, the air supply amount of the fan is increased by improving the structure of the fan. To facilitate understanding of the fans provided in the embodiments of the present application, the following detailed description is provided in conjunction with the accompanying drawings and specific embodiments.

First, it should be noted that the fan provided in the embodiments of the present application is a centrifugal fan, and the centrifugal fan includes a housing and a centrifugal impeller disposed in the housing, wherein the centrifugal impeller is rotatably connected to the housing through a driving shaft, and an axis of the driving shaft is also an axis of the centrifugal impeller. The shell is provided with an air inlet and an air outlet, and when the air inlet is specifically arranged, the number of the air inlets can be one or two. When the air inlet is one, the air inlet is positioned at one side of the centrifugal impeller, and at the moment, the fan is a single-side air inlet fan. When the number of the air inlets is two, the two air inlets are oppositely arranged on two sides of the centrifugal impeller, and the fan is a fan with air inlet on two sides.

For convenience of description, the embodiment of the present application takes a single-side air intake fan as an example for explanation. As shown in fig. 1 and 2, fig. 1 shows a structural schematic diagram of the fan, fig. 2 shows a cross-sectional view of the fan, and as can be seen from fig. 2, the housing includes a top cover 10 and a bottom cover 20 which are oppositely arranged, and the top cover 10 and the bottom cover 20 are connected by a side wall. The air inlet is disposed on the top cover 10, the air outlet 70 is disposed on the side wall, and when the mobile terminal is used, air entering from the top cover 10 is conveyed to the air outlet 70 on the side wall by the centrifugal impeller 80 and then enters the mobile terminal. Specifically, referring to the arrowed lines in fig. 2, which indicate the air flow direction, it can be seen from fig. 2 that the air flow direction in the housing is bent by approximately ninety degrees when the air is circulated. And because the thickness of the top cover 10 at the air inlet is smaller and the gap between the top cover and the inner wall surface of the system where the top cover is located is also smaller, the air is bent greatly at the edge of the air inlet, vortex is easy to generate, and the air delivery volume of the air in the fan is influenced. In order to improve the loss of air at the air inlet during bending, the centrifugal impeller 80 provided in the embodiment of the present application is provided with the guide ring 40, and referring to fig. 3 together, fig. 3 shows the arrangement of the guide ring 40 on the centrifugal impeller 80. In a specific arrangement, the guide ring 40 is annular, and a center of the guide ring 40 is located on an axis of the centrifugal impeller 80, so as to ensure that the guide ring 40 can rotate synchronously with the centrifugal impeller 80 and can be relatively stationary with respect to the centrifugal impeller 80 during rotation. As shown in fig. 3, the guide ring 40 divides the area on the centrifugal impeller 80 into two areas, namely an area I and an area II, wherein the area I is the area corresponding to the air inlet, and when air enters from the area I, the air is guided by the guide ring 40, flows through the blades 81, and is guided by the blades 81 to enter the area II. In addition, the guide ring 40 may be formed in other manners besides the above-mentioned ring shape, for example, a ring shape formed by a plurality of discontinuous arc segments, or a ring shape with a notch, or other different shapes may be used.

Referring to fig. 1 and 3 together, wherein fig. 1 shows a schematic cross-sectional view of the guide ring 40, it can be seen from the structure shown in fig. 1 that the guide ring 40 has a guide surface 41, the guide surface 41 is an inner side surface of the guide ring 40, and when the centrifugal impeller 80 is assembled, the guide surface 41 faces the axis of the centrifugal impeller 80. When the centrifugal impeller 80 rotates, air flows through the guide surface 41, the air bends along the guide surface 41, in order to improve the flow effect of the air during bending, the guide surface 41 is an arc-shaped guide surface, and the arc line of the edge of the guide surface 41 shown in fig. 1 may be a different streamline arc line such as an arc, an elliptic arc, and the like. The edge of the guide surface 41 may not be curved or may be non-streamlined. In particular, the air flowing effect during bending can be improved only by ensuring that the guide surface 41 of the guide ring 40 has a certain radian. The guide ring has two functions, one part adopts a streamline design, and the air resistance is reduced; the other part functions to reduce the turbulence created by the fluid flowing through the cover plate 10. The guide surface 41 therefore has a partial effect even if it is not streamlined, and therefore the particular cross-sectional shape of the guide ring 40 is not limited in any way here. As shown in fig. 4 to 8, fig. 4 to 8 show different cross-sectional shapes of the guide ring 40, and as can be seen from fig. 4 to 8, the cross-section of the guide ring 40 provided in the present embodiment may have different shapes such as a circle, an ellipse, a bullet, a racetrack, and the like. When the guide ring 40 is specifically provided, the cross-sectional shape thereof may be a regular shape, an irregular shape, a symmetrical or asymmetrical shape, or other different shapes.

The structure of the guide ring 40 when it is installed on the centrifugal fan will be described below by taking the guide ring 40 shown in fig. 4 as an example in cross section. Referring to fig. 9 and 10 together, for convenience of description, first, the meanings of the letters in fig. 9 and 10 will be described. r1 is the radius of the drive shaft 50, r2 is the outer diameter of the top cover 10, r3 is the radius of the center point of the cross section of the guide ring 40, r4 is the radius of the air inlet 30, a is the distance from the upper surface of the guide ring 40 to the upper surface of the top cover 10, b is the width of the cross section of the guide ring 40, c is the thickness of the top cover 10, d is the distance from the outer side of the guide ring 40 to the inner side of the top cover 10, and h is the height of the guide ring 40. In a particular arrangement, as shown in FIG. 9, the guide ring 40 is positioned between the drive shaft 50 and the outer diameter of the overcap 10, i.e., r1 ≦ r3 ≦ r 2. When the above arrangement is adopted, the guide ring 40 may be located inside the top cover 10 (located inside the air inlet 30) in the radial direction, and in this case, r1 is not less than r3 is not less than r 4. When the setting mode is adopted, d is more than or equal to 0; when d is 0, one end surface of the guide ring 40 away from the drive shaft 50 is brought into contact with the inner surface of the top cover 10. The structure that the guide ring 40 is embedded in the top cover 10 can also be adopted, and in this case, r4 is more than or equal to r3 is more than or equal to r 2. And d < 0. At this time, the guide ring 40 is located outside the air inlet 30 and between the top cover 10 and the blades 81. When two different setting modes are adopted, a is different, when the guide ring 40 is positioned in the air inlet 30, a is more than or equal to-3 mm and less than or equal to +3mm, wherein the negative size represents that the upper surface of the guide ring 40 is higher than the upper surface of the top cover 10, the positive distance represents that the upper surface of the guide ring 40 is lower than the upper surface of the top cover 10, and the 0 size represents that the guide ring 40 is flush with the upper cover plate in height. When the guide ring 40 is positioned outside the air inlet 30, a is more than or equal to c. That is, the height from the upper surface of the guide ring 40 to the upper surface of the top cover 10 is greater than the thickness of the top cover 10, that is, the height of the guide ring 40 is smaller than the gap between the vane 81 and the top cover 10. In a specific embodiment, the guide ring 40 is located at the air inlet 30, that is, the guide surface 41 of the guide ring 40 is closer to the driving shaft 50 than the inner side surface of the top cover 10, so that the effect of air turning can be improved by the guide surface 41 at the air inlet 30.

Referring also to fig. 10, fig. 10 shows the dimensions of the guide ring 40, the height h of the guide ring 40 being between 0.01mm and 5mm, and the width b of the guide ring 40 being between 0.01mm and 15mm, e.g. h is 0.02mm and b is 0.05 mm; h is 0.05mm, b is 0.08 mm; h is 0.5mm, b is 1 mm; h is 2mm, b is 5 mm; h is 4mm, b is 10 mm; and the like in different sizes.

When the guide ring 40 is fixed to the centrifugal impeller 80, the guide ring 40 may be fixed to the blades 81 of the centrifugal impeller 80 by various means such as adhesion, welding, or connection by a connecting member. In addition, the guide ring 40 and the centrifugal impeller 80 can be integrally formed. Any connection or preparation method can be applied to the fan provided by the embodiment of the application.

The guide ring 40 provided in the embodiment of the present application has the following effects, in addition to the effects of improving the air in turning, mentioned in the above description: because the guide ring 40 and the blades 81 are fixed relatively, when the centrifugal impeller 80 rotates, the relative positions of the impeller 80 and the guide ring 40 are fixed, and when air circulates, the blades 81 and the guide ring 40 on both sides of the air are fixed relatively, which facilitates the air circulation. In the prior art, when the centrifugal impeller rotates and the top cover relatively rotates relative to the blades, air flows through the blades on two sides of the air and the top cover relatively moves, and therefore certain disorder can be caused to the air flow. As can be seen from the above description, the fan provided in the embodiment of the present application can improve the effect of air circulation by relatively fixedly arranging the impeller 80 and the guide ring 40, thereby increasing the air output.

In the embodiment of the present application, in addition to the above-described embodiment in which the air blowing amount is improved by the guide ring 40, the air blowing amount may be improved by improving other structures on the centrifugal impeller 80. As shown in fig. 11, fig. 11 shows another fan structure provided in the embodiment of the present application. In the configuration shown in fig. 11, the air blowing amount is improved by improving the configuration of the blades 81 on the centrifugal impeller 80. With continued reference to fig. 11, in the present embodiment, the amount of air supply is improved by providing grooves 811 in the impeller 80 in the radial direction of the blades 81, where the radial direction of the blades 81 refers to the extending direction of the blades 81 gradually away from the drive shaft. In a specific embodiment, a rectangular blade is used for description, and for convenience of description of the structure and the arrangement position of the groove 811, the surfaces of the blade 81 are named, and as shown in fig. 11, five surfaces of the blade 81 are a top surface 812, a bottom surface (a surface opposite to the top surface 812), a left side surface 813, a right side surface (a surface opposite to the left side surface 813), and an outer end surface 814. The top surface 812 and the bottom surface are two surfaces perpendicular to the axis of the centrifugal impeller 80, the left side surface 813, the right side surface and the outer end surface 814 are three side surfaces between the top surface 812 and the bottom surface, the outer end surface 814 is an end surface of the blade 81 away from the axis, and the left side surface 813 and the right side surface are side surfaces on two sides of the outer end surface 814 respectively. Further, along the running direction of the vane 81, the direction from the axis of the centrifugal impeller 80 toward the outer end face 814 of the vane 81 is the radial direction of the vane 81.

With continued reference to fig. 11, in order to improve the air intake effect of the fan, the fan provided in the embodiment of the present application is provided with a plurality of grooves 811 on at least one of the blades 81, and the plurality of grooves 811 are arranged along the radial direction of the blade 81, and the grooves 811 are obliquely arranged at an angle with respect to the normal direction of the radial tangent of the blade 81. As shown in fig. 12 and 14, each groove 811 is disposed obliquely with respect to the radial direction of the blade 81, both ends of the groove 811 are open, and the length direction of the groove 811 forms a predetermined angle with the normal direction of the radial tangent of the blade 81, wherein the length direction of the groove 811 is a direction from one opening of the groove 811 to the other opening, the radial tangent direction of the blade 81 is the radial direction of the blade 81 when the blade 81 is a straight blade, and the radial tangent direction of the arc line on the blade 81 when the blade 81 is an arc-shaped blade.

Referring first to fig. 12, a fan provided in an embodiment of the present invention may have a first trench 815 disposed on a portion of a blade 81, and the first trench 815 is disposed on a top surface 812 of the blade 81, and when the first trench 815 is disposed, a length direction of the first trench 815 is inclined with respect to a normal direction of a radial tangent of the blade 81, and an angle between the length direction of the first trench 815 and the normal direction of the tangent of the blade 81 is an acute angle, as shown in fig. 12, an angle between the length direction of the first trench 815 and the radial direction of the blade 81 is α, wherein α is between 3 ° and 75 °, such as 10 °, 20 °, 30 °, 40 °, 50 °, and the like, wherein a height of a single first trench 815 is measured along a height direction of the blade 81, such as between 0.1% and 25% of the total height of the blade 81, a width direction is measured along the radial length direction of the blade 81, and a total length of the first trench 815 may be between 0.1% and 25% of the total length of the first trench 81, and when a plurality of first trenches 815 are disposed on a plurality of the first trench 815 and a plurality of the first trench 815 grooves are disposed on a left side surface 814, or a non-periodic surface 814, a plurality of the first trench 815, a non-periodic surface 815, a periodic surface of the first trench 815, a non-periodic surface 814, a periodic surface of the first trench 815, or a non-periodic surface of the first trench 815, which is not disposed on a non-periodic surface of the first trench 815, and a non-periodic surface of the same type of the blade 81, and a non-periodic surface of the same type of.

In addition, as for the cross-sectional shape of the first trench 815, various shapes may be adopted, such as a streamlined elliptical first trench 815 included in the first trench 815 shown in fig. 13, or a regular rectangular and triangular first trench 815. Of course, the shape of the first trench 815 is not limited to the above-listed shapes of the trenches 811. In particular, the first grooves 815 provided on the same plane may be grooves 811 having the same cross-sectional shape, or may be grooves 811 having different cross-sectional shapes.

Referring to fig. 14, the groove 811 provided in the embodiment of the present application may be a second groove 816 in addition to the first groove 815 described above, wherein the second groove 816 includes two portions forming a herringbone groove, specifically, the second groove 816 includes a first groove body 8161 and a second groove body 8162, wherein the first groove body 8161 and the second groove body 8162 are relatively inclined, and a length direction of the first groove body 8161 and the second groove body 8162 forms a set angle with a normal direction of a tangent of the blade 81. In specific arrangement, the size and the cross-sectional shape of the first slot body 8161 and the second slot body 8162 in the second groove 816 can refer to the size and the cross-sectional shape of the first groove 815 shown in fig. 12, and detailed description thereof is omitted.

In addition, when the first groove 815 and the second groove 816 are specifically provided, the first groove 815 or the second groove 816 may be located on all the blades 81 of the fan, or may be located on several blades 81 of the fan. The blades 81 featuring grooves 811 may be distributed periodically or non-periodically. Either a few continuous blades 81 have the characteristics of channel 811 or discontinuous blades 81 have the characteristics of channel 811. The distribution of the wind power needs to be determined according to actually tested wind volume and noise spectrum characteristics.

In order to facilitate understanding of the grooves 811 provided in the embodiments of the present application, the following description will be made in detail with reference to the principle thereof. As shown in fig. 15, the centrifugal impeller 80 of the fan rotates relative to the top cover 10, and the top and bottom surfaces of the blades 81 are spaced apart from the top cover 10 and the bottom cover 20, respectively. The relative movement of the air flow between the cover 10 and the vanes 81 is shown in figure 15: the movement of the airflow relative to the blades 81 is synthesized by the velocity Vt tangential to the blades 81 of the centrifugal impeller 80 and Vr relative to the radius of the centrifugal impeller 80, i.e. the final relative velocity at a certain point of the blades 81 is Va; the direction of Va varies with the radius of the vane 81, and as can be seen from fig. 15, the resultant speed Va of the relative movement is not parallel to the normal direction of the vane 81 (the direction perpendicular to the radial direction of the vane 81), so that in order to allow the air between the centrifugal impeller 80 and the top cover 10 to flow through the groove 811 in a smoother manner, the direction of the groove 811 provided in the embodiment of the present application should be as same as the direction of Va as possible, thereby improving the air permeability on the groove 811.

The direction of Va is geometrically different with the radius of the blade 81; varies in motion with the rotational speed of the centrifugal impeller 80; there is thus a suitable angular choice as a function of the radial position of the grooves 811 at the blades 81 and the rotational speed of the centrifugal impeller 80 at the usual operating point. Typical angles are between 3 ° and 75 °. In the structure shown in fig. 16, the first trench 815 is arranged to have a length direction as parallel as possible to Va after synthesis. In addition, in order to break up the large eddy currents to a greater extent, a chevron-shaped blade 81 groove 811 layout may be used, as shown in particular with reference to fig. 17. As shown in fig. 16 and 17, the inclined grooves 811 allow air to flow more smoothly through the grooves 811, and thus improve the air flow effect.

As can be seen from the above description, when the grooves 811 are used, the groove features of the surface of the blade 81 force the large vortices flowing over the surface of the blade 81 to break up into small vortices, thereby distributing the energy of the turbulence over a wider frequency band, reducing the concentration of the energy of the noise; meanwhile, the large vortex is scattered, the possibility that air blocks the flow channel is reduced, particularly under the non-design working condition, the air flowing state is worsened, the air can smoothly flow through the flow channel between the blades, and the air quantity is improved.

In one embodiment, as mobile terminal devices such as notebooks and tablets become thinner and thinner, the fan becomes thinner and thinner, and the height and thickness of the blade are greatly limited. In order to maximize the characteristics of the grooves, the fan provided by the embodiment of the present application is configured with oblique grooves or herringbone grooves at the top of the blades according to the flow characteristics of the blades. And the groove arrangement of adjacent blades can be staggered so as to achieve the effect of maximally scattering the large vortex, thereby improving the air inlet effect of the fan and reducing the noise.

The guide ring 40 and the groove 811 provided in the above embodiments can be used alone to improve the air intake effect of the fan, so as to increase the air output of the fan, and can also be used in a combined manner to improve the air output of the fan. At this time, the above-described first groove 815 or second groove 816 is provided in the blade 81 of the centrifugal impeller 80, or both the first groove 815 and second groove 816 are provided, and the guide ring 40 is provided in the centrifugal impeller 80, and when the guide ring 40 is provided, the position where the guide ring 40 is provided is set in the manner described in the above-described embodiment, the guide ring 40 divides the region on the centrifugal impeller 80 into two regions, i.e., the region I and the region II, respectively, and the position where the first groove 815 or second groove 816 is provided is located in the region II. When the structure of the guide ring 40 and the groove 811 is adopted, the fan has the effect of improving the bending of the air by the guide ring 40 and the effect of improving the air flowing through the blades 81 by the groove 811, so that the air output of the fan can be effectively improved.

As shown in fig. 18, an embodiment of the present application further provides a mobile terminal, where the mobile terminal includes any one of the fans 100 described above, and when the mobile terminal is specifically configured, the mobile terminal is a common mobile terminal such as a notebook, a tablet computer, and the like. As shown in fig. 18, the fan 100 is disposed in the housing 200 of the mobile terminal, and the fan 100 improves the amount of air blown by the fan 100 and reduces the noise of the fan 100 by adding a guide ring, adding a groove, or adding both a groove and a guide ring.

The above description is only for the specific embodiments of the present invention, but the scope of the present invention is not limited thereto, and any person skilled in the art can easily conceive of the changes or substitutions within the technical scope of the present invention, and all the changes or substitutions should be covered within the scope of the present invention. Therefore, the protection scope of the present invention shall be subject to the protection scope of the appended claims.

Claims

A fan, comprising: the casing, and set up and be in just can be relative in the casing pivoted centrifugal impeller, centrifugal impeller includes a plurality of blades, be provided with a plurality of edges on at least one blade in a plurality of blades the slot that the radial direction of blade was arranged, just the slot is relative the slope setting that the normal direction of the radial tangent line of blade becomes certain angle.
The fan as claimed in claim 1, wherein the grooves are first grooves inclined in a single direction, and an angle between a length direction of the first grooves and a normal direction of a radial tangent of the blade is an acute angle.
The fan as claimed in claim 2, wherein the blade has top and bottom surfaces opposite to each other, wherein the top and/or bottom surfaces are provided with the first grooves.
The fan as claimed in claim 2, wherein the first grooves have a rectangular or triangular cross-section.
The fan as claimed in claim 1, wherein the groove is a herringbone second groove, and the second groove includes a first groove body and a second groove body which are inclined with respect to each other, and the first groove body and the second groove body form an included angle with a normal direction of a radial tangent of the blade at a certain angle.
A fan according to any of claims 2 to 5 wherein the blade has an outer face on which is provided a third groove.
The fan according to any one of claims 1 to 6, wherein the fan has an air inlet, and a driving shaft of the centrifugal impeller is exposed at the air inlet;

still include the guide ring, just the guide ring with a plurality of blade fixed connection, the guide ring orientation the one side of drive shaft is the spigot surface.
The fan as claimed in claim 7, wherein the guide ring comprises a plurality of arc segments arranged at intervals.
The fan as claimed in claim 7, wherein the guide ring is exposed at the intake port.
The fan as claimed in claim 7, wherein the guide ring has a circular, elliptical or bullet-shaped cross-section.
A fan, comprising: the centrifugal impeller comprises a driving shaft and a plurality of blades connected with the driving shaft;

still include the guide ring, just the guide ring with a plurality of blade fixed connection, the guide ring orientation the one side of drive shaft is the spigot surface.
The fan as claimed in claim 11, wherein the guide ring comprises a plurality of arc segments spaced apart from each other.
The fan as claimed in claim 11, wherein the guide ring is exposed at the intake port.
The fan as claimed in claim 11, wherein the guide ring has a circular, elliptical or bullet-shaped cross-section.
A mobile terminal, characterized in that it comprises a fan according to any of claims 1 to 14.