Air outlet component

Abstract

The present application provides an air outlet component, comprising: a cylinder, comprising an outer ring portion, wherein the outer ring portion is open from front to rear, allowing air to flow in from the rear end and out from the front end, and the variation amplitude of the diameter of the inner wall of the outer ring portion from rear to front is less than 5 mm; a braking assembly arranged coaxially with the outer ring portion, wherein the braking assembly is mounted on the cylinder and is radially accommodated inside the outer ring portion, the braking assembly comprises a fan and a motor, the fan comprises a wheel housing and a plurality of blades arranged at intervals on the outer surface of the wheel housing, and the motor is arranged on the radial inner side of the wheel housing; a flow guide member coaxially arranged with the outer ring portion, mounted on the front side of the cylinder and comprising an inner housing portion, wherein the difference between the maximum diameter of the wheel housing and the maximum diameter of the inner housing portion is less than 5 mm. The difference between the maximum diameter of the wheel housing and the maximum diameter of the inner housing portion is small, so that air can smoothly flow through the outer surface of the wheel housing and the outer surface of the inner housing portion, achieving low wind energy loss.

Description

Air outlet component TECHNICAL FIELD

[0001] The present application relates to the fan technical field, in particular to an air outlet component with good air outlet effect. BACKGROUND

[0002] At present, the size of daily electronic products is increasingly reduced, and the size and portability of the fan are also increasingly required. Although the conventional axial fan has a large air volume, the air pressure of the axial fan is generally small. In addition, the blades of the axial fan usually extend along the hub in a spiral manner, so that the airflow generated by the rotation of the fan blades is turbulent.

[0003] In order to reduce the turbulence generated by the fan blades and avoid the occurrence of invalid air outlet, a plurality of stationary vanes are usually arranged around the front of the fan blades. After the turbulence passes through the combing of the plurality of stationary vanes, the air can be combed to a certain extent. However, the combing of a single stationary vane on the airflow is limited, and in addition, the stationary vane will also cause a part of the airflow to rebound, so that the fan efficiency is low, and therefore a solution is urgently needed. SUMMARY

[0004] The main purpose of the present application is to provide an air outlet component, comprising: a cylinder body comprising an outer ring portion, the outer ring portion being through from front to back, the rear end being air inlet, the front end being air outlet, the diameter of the inner wall of the outer ring portion changing by less than 5mm from back to front; a brake assembly coaxially arranged with the outer ring portion, the brake assembly being mounted on the cylinder body and being radially accommodated inside the outer ring portion, the brake assembly comprising a fan and a motor, the fan comprising a wheel shell and a plurality of blades arranged at intervals on the outer surface of the wheel shell, the motor being arranged radially inside the wheel shell; a flow guide coaxially arranged with the outer ring portion, the flow guide being mounted on the front side of the cylinder body, the flow guide comprising an inner shell portion; wherein the maximum diameter of the wheel shell and the maximum diameter of the inner shell portion differ by less than 5mm. The maximum diameter of the wheel shell and the maximum diameter of the inner shell portion differ by a small amount, so that the air can smoothly flow through the outer surface of the wheel shell and the outer surface of the inner shell portion, and the air energy loss is small. BRIEF DESCRIPTION OF DRAWINGS

[0005] The embodiments of the present application will be described with reference to the accompanying drawings. The drawings of the present application are only used for describing the embodiments for the purpose of demonstration. Those skilled in the art can easily make other embodiments according to the steps described below without deviating from the principles of the present application.

[0006] FIG. 1-1 is a perspective view of a portable fan of the present application;

[0007] FIG. 1-2 is an exploded view of the portable fan of the present application;

[0008]

[0008] FIG. 1-3 is a side view of the portable fan of the present application;

[0009] Figures 1-4 are side cross-sectional views of the air outlet member and the contraction member in the portable fan of the present application;

[0010] Figure 1-5 is a top cross-sectional view of the portable fan of the present application;

[0011] Figure 1-6 is a rear cross-sectional view of the portable fan of the present application;

[0012] Figure 1-7 is another rear cross-sectional view of the portable fan of the present application;

[0013] Figure 1-8 is a perspective view of the blower in the portable fan of the present application;

[0014] Figure 2-1 is a perspective view of the portable fan of the present application;

[0015] Figure 2-2 is an exploded view of the portable fan of the present application;

[0016] Figure 2-3 is a schematic view of the stand, the housing and the static fan of the present application;

[0017] Figure 2-4 is a schematic view of the first blower of the present application;

[0018] Figure 2-5 is a side cross-sectional view of the portable fan of the present application;

[0019] Figure 2-6 is another side cross-sectional view of the portable fan of the present application;

[0020] Figure 2-7 is a rear cross-sectional view of the portable fan of the present application;

[0021] Figure 2-8 is another rear cross-sectional view of the portable fan of the present application;

[0022] Figure 3-1 is a perspective view of the portable fan of the present application;

[0023] Figure 3-2 is an exploded view of the portable fan of the present application;

[0024] Figure 3-3 is an exploded view of the housing and the static fan of the present application;

[0025] Figure 3-4 is a schematic view of the second blower of the present application;

[0026] Figure 3-5 is a side cross-sectional view of the portable fan of the present application;

[0027] Figure 3-6 is another side cross-sectional view of the portable fan of the present application;

[0028] Figure 3-7 is a rear cross-sectional view of the portable fan of the present application. DETAILED DESCRIPTION

[0029] With reference to the drawings, the technical solutions in the embodiments of the present application will be clearly and completely described below. It can be understood that the specific embodiments described here are only used to explain the present application, but not to limit the present application. In addition, it should be noted that, for the convenience of description, only the parts related to the present application are shown in the drawings, but not all the structures. Based on the embodiments in the present application, all other embodiments obtained by those skilled in the art without creative work are within the scope of the present application.

[0030] The terms "first", "second", and the like in the present application are used to distinguish different objects, and are not used to describe a specific order. In addition, the terms "include" and "have" and any variations thereof are intended to cover non-exclusive inclusion. For example, a process, method, system, product or device that includes a series of steps or units is not limited to the listed steps or units, but can optionally include steps or units not listed, or can optionally include other steps or units inherent to the process, method, product or device.

[0031] In this document, the term "embodiment" means that the specific features, structures or characteristics described in connection with the embodiment can be included in at least one embodiment of the present application. The phrase appears at various places in the specification does not necessarily all refer to the same embodiment, nor is it necessarily independent or alternative embodiments to each other. It is explicitly and implicitly understood by those skilled in the art that the embodiments described herein can be combined with other embodiments.

[0032] Scheme one

[0033] In one embodiment, as shown in Figure 1-1, a portable fan 1. In this embodiment, the portable fan 1 is a handheld fan, so the portable fan 1 includes a handheld part (not numbered, the same below), and a circuit board and a battery (not numbered, the same below) are arranged in the handheld part, the circuit board is used to control the circuit, and the battery is used to power. In other embodiments, the portable fan 1 can also be a clip fan, a desktop fan, a neck fan, etc.

[0034] In one embodiment, as shown in FIG. 1-2 to FIG. 1-4, the portable fan comprises a housing 1, an air outlet component and a contraction piece 6. The housing 1 is through from front to back, with air inlet at the back and air outlet at the front. The air outlet component is accommodated in the housing 1, which comprises a cylinder 2 and a braking assembly accommodated in the cylinder 2, the braking assembly comprising a fan 3 and a motor 4 driving the fan 3 to rotate to generate wind. The contraction piece 6 is accommodated in the housing 1 and arranged at the front side of the air outlet component, which comprises a contraction surface 61 at the inner side, arranged towards the air duct, and radially decreasing from back to front. The contraction piece 6 is arranged and has the contraction surface 61 towards the air duct, which is radially decreasing from back to front, which is conducive to the contraction and convergence of the air flow guided by the air outlet component, enhancing the wind pressure and increasing the wind power.

[0035] In one embodiment, as shown in FIG. 1-2, FIG. 1-3, FIG. 1-4 and FIG. 1-6, the cylinder 2 comprises an outer ring portion 21, an inner ring portion 22 and a plurality of first guide vanes 23 connecting the outer ring portion 21 and the inner ring portion 22. The outer ring portion 21 is through from front to back, with air inlet at the back and air outlet at the front, and the diameter of the inner wall of the outer ring portion 21 changes less than 5mm from back to front. The inner ring portion 22 is coaxially arranged with the outer ring portion 21, and extends radially unchanged from back to front. The air outlet component further comprises a flow guide piece 5 arranged in the axial direction between the cylinder 2 and the contraction piece 6, which is coaxially arranged with the outer ring portion 21 and installed at the front side of the cylinder 2. The flow guide piece 5 comprises an outer shell portion 51, an inner shell portion 52 and a plurality of second guide vanes 53 connecting the outer shell portion 51 and the inner shell portion 52, and the difference between the diameter of the inner wall of the outer shell portion 51 and the diameter of the inner wall of the outer ring portion 21 is less than 5mm.

[0036] In this embodiment, as shown in FIG. 1-2, FIG. 1-3, FIG. 1-4 and FIG. 1-6, the diameter of the inner wall of the outer ring portion 21 is unchanged from back to front, the diameter of the inner wall of the outer shell portion 51 is unchanged from back to front, and the diameter of the inner wall of the outer ring portion 21 is equal to the diameter of the inner wall of the outer shell portion 51. In this way, a through ventilation air duct is formed, reducing wind energy loss. The diameter of the inner wall of the outer shell portion 51 and the diameter of the inner wall of the outer ring portion 21 are 30-36mm, the diameter of the outer shell portion 51 and the outer ring portion 21 is small, and the overall volume of the portable fan is small and portable.

[0037] In one embodiment, as shown in FIG. 1-2, FIG. 1-3, FIG. 1-4 and FIG. 1-6, the maximum diameter of the converging surface 61 is equal to the diameter of the inner wall of the outer shell part 51, the minimum diameter of the converging surface 61 is greater than the maximum diameter of the inner shell part 52, and the minimum diameter of the converging surface 61 is 21.05-25.05 mm. The inner shell part 52 protrudes forward relative to the outer shell part 51, the front end of the inner shell part 52 is located radially inward of the converging surface 61, and the front end of the converging surface 61 is located forward of the front end of the inner shell part 52. There is a gap between the outer surface of the inner shell part 52 and the converging surface 61, forming a wind channel for wind convergence and guidance. The converging surface 61 has the effect of enhancing wind pressure, concentrating strong wind in the middle and then blowing it to the user, with good blowing effect.

[0038] In one embodiment, as shown in FIG. 1-2 to FIG. 1-4, the inner ring part 22 is provided with a base plate 221 and a hollow shaft cylinder 222 extending rearward from the base plate 221. The motor 4 includes a stator assembly 41 and a rotor assembly 42, and the stator assembly 41, the rotor assembly 42 and the fan 3 are fixedly nested in the shaft cylinder 222. The rotor assembly 42 includes a rotating shaft 421, a bearing 422 and a magnetic ring 423, the rotating shaft 421 and the bearing 422 are fixedly inserted in the shaft cylinder 222, the stator assembly 41 is arranged radially outward of the shaft cylinder 222, the magnetic ring 423 is arranged radially outward of the stator assembly 41, and the magnetic ring 423 is fixedly arranged radially inward of the wheel shell 31. The motor 4 is an external rotor motor 4, which is in the form of an external rotor and has a more compact and reasonable structure.

[0039] In one embodiment, as shown in FIG. 1-2 to FIG. 1-4, the axial length of the inner shell part 52 is 13-17 mm, the inner shell part 52 is radially reduced from rear to front, and the outer surface is in the shape of a sphere, guiding the convergence and forward flow of air flow. The inner side of the inner shell part 52 is provided with a column 521, and the column 521 is fixedly inserted rearward in the shaft cylinder 222.

[0040] In one embodiment, as shown in FIGS. 1-2 to 1-5, the brake assembly is coaxially arranged with the outer ring portion 21, is mounted at the rear side of the inner ring portion 22, and is radially accommodated inside the outer ring portion 21. The brake assembly includes a fan 3 and a motor 4, the fan 3 includes a wheel shell 31 and a plurality of blades 32 arranged at intervals on the outer surface of the wheel shell 31, and the motor 4 is arranged at the radially inner side of the wheel shell 31. The wheel shell 31 radially increases from the rear to the front, the inner ring portion 22 radially extends without change from the rear to the front, and the inner shell portion 52 radially decreases from the rear to the front. The wheel shell 31 partially guides the air flow forward, and the inner shell portion 52 guides the air flow forward. The maximum diameter of the wheel shell 31 and the diameter of the inner ring portion 22 differ by less than 5 mm, the maximum diameter of the inner shell portion 52 and the diameter of the inner ring portion 22 differ by less than 5 mm, and the maximum diameter of the wheel shell 31, the maximum diameter of the inner shell portion 52, and the diameter of the inner ring portion 22 are all in the range of 19.24-23.24 mm. That is, the maximum diameter of the wheel shell 31, the diameter of the inner ring portion 22, and the maximum diameter of the inner shell portion 52 differ by a small amount, the wheel shell 31, the inner ring portion 22, and the inner shell portion 52 smoothly transition between each other, the air flow can smoothly flow through the outer surfaces of the wheel shell 31, the inner ring portion 22, and the inner shell portion 52, and the air energy loss is small.

[0041] In the present embodiment, as shown in FIGS. 1-2 to 1-5, the maximum diameter of the wheel shell 31, the maximum diameter of the inner shell portion 52, and the diameter of the inner ring portion 22 are equal, the spacing between the front end of the wheel shell 31 and the inner ring portion 22 is 0.5-3 mm, and the spacing between the inner shell portion 52 and the inner ring portion 22 is 0.15-1 mm. The air flow can smoothly flow from the outer surface of the wheel shell 31 to the outer surface of the inner ring portion 22, and then to the outer surface of the inner shell portion 52. Furthermore, the radially increasing outer surface of the wheel shell 31 enhances the air pressure, the radially unchanged outer surface of the inner ring portion 22 reduces the air loss, and the radially decreasing inner shell portion 52 guides the air flow, and the structural design is very reasonable.

[0042] In one embodiment, as shown in FIG. 1-3, FIG. 1-4, FIG. 1-7 and FIG. 1-8, the wheel shell 31 comprises a rear end portion 311, an enlarged portion 312 radially increasing from the rear end portion 311, and a smooth portion 313 radially constant from the enlarged portion 312. The slope of the enlarged portion 312 decreases from rear to front, the axial length of the enlarged portion 312 is 12.9-16.9mm, and the axial length of the smooth portion 313 is 6.13-10.13mm. The longer axial length of the enlarged portion 312 is conducive to enhancing wind pressure, and the smooth portion 313 also has a certain axial length, which is conducive to accommodating the motor 4 in the smooth portion 313. The wheel shell 31 further comprises a fixing column 314 at the center of the inner side, which is used for fixedly connecting the rotating shaft 421.

[0043] In one embodiment, as shown in FIG. 1-3, FIG. 1-4, FIG. 1-7 and FIG. 1-8, each of the blades 32 comprises a blade root portion 321 connected with the wheel shell 31, a blade tip portion 322 opposite to the blade root portion 321, a leading edge portion 323 connecting the blade root portion 321 and the blade tip portion 322, and a trailing edge portion 324 connecting the blade root portion 321 and the blade tip portion 322, wherein the leading edge portion 323 and the trailing edge portion 324 are oppositely arranged. The front end of the blade root portion 321 is arranged within the range of 1.5mm before and after the connection between the enlarged portion 312 and the smooth portion 313, and it can be known that the blade root portion 321 is mainly arranged in the enlarged portion 312, and the blade 32 is also mainly arranged in the enlarged portion 312, which is conducive to air suction and air cutting of the blade 32 and to enhancing wind pressure.

[0044] In one embodiment, as shown in FIG. 1-3 to FIG. 1-6, each of the first guide vanes 23 comprises a first segment 231 and a second segment 232 extending rearward from the first segment 231. The first segment 231 is connected with both the inner ring portion 22 and the outer ring portion 21, and the second segment 232 is connected with only the outer ring portion 21, and the radially inner side of the second segment 232 is spaced apart from the wheel shell 31. The spacing between the rear end of the second segment 232 and the leading edge portion 323 is 1.25-3.25mm, and the spacing between the front end of the first segment 231 and the rear end of the second guide vane 53 is 0.4-1.4mm. That is, the axial spacing between the blade 32 and the first guide vane 23 is small, and the axial spacing between the first guide vane 23 and the second guide vane 53 is small, so that the wind can smoothly flow from the plurality of blades 32 to the plurality of first guide vanes 23, and then to the plurality of second guide vanes 53. And the spacing is provided between the blade 32 and the first guide vane 23 and between the first guide vane 23 and the second guide vane 53, which is conducive to pressure relief and avoids the occurrence of backflow caused by excessive wind pressure, and the wind energy loss is small.

[0045] In one embodiment, as shown in FIGS. 1-3 to 1-6, from back to front, the blades 32 extend clockwise spirally, the second segments 232 extend counterclockwise spirally, the first segments 231 extend straight, and the second vanes 53 extend first clockwise spirally and then straight. As can be seen, the air flow is guided multiple times from back to front, and is constantly combed and integrated, and finally flows straight forward, with small wind energy loss and low noise.

[0046] In one embodiment, as shown in FIGS. 1-2, 1-4, 1-6 and 1-7, the number of the blades 32 is 9, the number of the first vanes 23 is 7, and the number of the second vanes 53 is 7. It should be understood that when the number of static blades and dynamic blades is similar, the static blades can better comb and integrate the air flow generated by the dynamic blades. The first vanes 23 and the second vanes 53 are static blades, and the blades 32 are dynamic blades. The plurality of first vanes 23 and the plurality of second vanes 53 are arranged at intervals in the radial direction, and the projection of one first vane 23 in the axial direction is located between the projections of two adjacent second vanes 53 in the axial direction. In this way, on the basis of the combing of the first vanes 23 and the second vanes 53 in the axial direction, the combing range is also expanded in the radial direction, which can further ensure the combing and integration effect of the static blades, and the air outlet effect is better.

[0047] In one embodiment, as shown in FIGS. 1-3 to 1-5, the ratio of the axial length of the blade 32 to the axial length of the first vane 23 ranges from 7:8 to 11:12, and the ratio of the axial length of the first vane 23 to the axial length of the second vane 53 ranges from 12:7 to 8:3. As can be seen, the axial length of the blade 32 is close to the axial length of the first vane 23, and the axial length of the first vane 23 is slightly longer than the axial length of the blade 32, for combing the air flow generated by the blade 32 at the first time. The axial length of the first vane 23 is about twice the axial length of the second vane 53, and after the combing of the first vane 23, the air flow tends to be stable, and does not need to be guided for too long. Therefore, the axial length of the second vane 53 is shorter, which is conducive to reducing the wind energy loss and achieving good air outlet effect.

[0048] In one embodiment, as shown in FIG. 1-2, FIG. 1-3, FIG. 1-5 and FIG. 1-6, a soft shell 7 is further included. The soft shell 7 is arranged in the shell 1, and the soft shell 7 covers the outside of the barrel 2, the flow guide 5 and the contraction piece 6. The soft shell 7 includes an annular portion 71, and a front cover portion 72 and a rear cover portion 73 connected to the front and rear ends of the annular portion 71 respectively. The annular portion 71 covers the radially outer side of the outer ring portion 21, the outer shell portion 51 and the contraction piece 6. The front cover portion 72 is arranged at the front end of the contraction piece 6, and the edge of the front cover portion 72 is flush with the front end of the contraction surface 61. The rear cover portion 73 is arranged at the rear end of the outer ring portion 21, and the edge of the rear cover portion 73 is flush with the rear end of the inner wall of the outer ring portion 21. The soft shell 7 has the effect of buffering and shock absorption, and can better fix the barrel 2, the flow guide 5 and the contraction piece 6 in the shell. The radially outer side of the soft shell 7 can be provided with a convex bump or a convex rib to enhance the fixing effect. The radially inner side and / or the radially outer side of the soft shell 7 can also be provided with a recess to enhance the effect of buffering and shock absorption.

[0049] In one embodiment, as shown in FIG. 1-2, FIG. 1-3 and FIG. 1-5, a front guide 8, a rear guide 9 and an air inlet net 10 are further included. The front guide 8 is embedded in the front end of the shell 1, and the rear end of the front guide 8 abuts against the front cover portion 72. The front guide 8 includes a front guide surface 81 on the inner side, which radially increases from rear to front, and the rear end of the front guide surface 81 is flush with the edge of the front cover portion 72. The rear guide 9 is embedded in the rear end of the shell 1, and the front end of the rear guide 9 is clamped with the rear cover portion 73 to fix the air inlet net 10. The rear guide 9 includes a rear guide surface 91 on the inner side, and the front end of the rear guide surface 91 is flush with the edge of the rear cover portion 73. The wind converges into the shell 1 from the radially reduced rear guide surface 91, and the wind pressure, wind power and wind effect are enhanced in the shell 1, and finally the wind expands out from the radially expanded front guide surface 81, with good air outlet effect. The air inlet net 10 is densely provided with a plurality of air inlet micro-holes (not numbered, the same below), which can be circular or hexagonal, and the air inlet micro-holes have small diameters, which are beneficial to isolate dust impurities and blow out good air.

[0050] In one embodiment, as shown in FIGS. 1-2 to 1-5, the axial length of the shell 1 is 61-65 mm, the axial length of the shell 1, the front guide 8 and the rear guide 9 after installation is 66-70 mm, that is, the overall axial length is also not too long, the overall volume is small and portable. The axial length of the soft shell 7 is 54.5-58.5 mm, the axial length from the rear end of the outer ring part 21 to the front end of the contraction part 6 is 43.5-47.5 mm, and the soft shell 7 can well protect the cylinder 2, the flow guide 5 and the contraction part 6. The distance from the rear end of the wheel shell 31 to the rear end of the rear guide 9 is 3.8-7.8 mm, and the distance from the front end of the inner shell part 52 to the front end of the front guide 8 is 14.75-18.75 mm, which is conducive to wind gathering and wind power enhancement.

[0051] It should be understood that the "diameter is constant" and "diameter is equal" mentioned in the present application allow a certain error range and do not require complete accuracy and complete equality.

[0052] Scheme II

[0053] In one embodiment, as shown in FIGS. 2-1 and 2-2, it is a portable fan. The portable fan includes an air outlet part 100 and a support 7, the air outlet part 100 is arranged on the support 7, and a power supply part 8 is arranged in the support 7. In this embodiment, the portable fan is a desktop fan, and in other embodiments, the portable fan can also be one of a clip fan, a handheld fan, a neck-hanging fan and other portable fans.

[0054] In one embodiment, as shown in FIGS. 2-1 to 2-4, the air outlet part 100 includes a shell 1 and a brake assembly contained in the shell 1. The shell 1 penetrates front and back, the shell 1 inhales air at the rear end and exhales air at the front end, the power supply part 8 supplies power to the brake assembly, the brake assembly drives wind and blows the wind to the front end. It should be understood that in other embodiments, the shell 1 can also be provided with an air inlet area.

[0055] In one embodiment, as shown in FIGS. 2-1 to 2-4, the brake assembly comprises at least one static fan 3 fixed in the housing 1 and at least two fans rotating to generate wind around the rotating shaft 4. The rotating shaft 4 is arranged axially and fixed at the center of the static fan 3. At least two fans are fixed on the same rotating shaft 4, and the rotating shaft 4 drives the rotation of the fans. The rotating directions of the at least two fans are the same, and the wind is blown forward. By arranging at least two fans, at the same rotating speed, the at least two fans can provide greater wind pressure and wind volume than a single fan. The front side or the rear side of at least one fan is provided with the static fan 3. In combination with reference to FIG. 2-5, the brake assembly further comprises a motor 5 fixed to the rotating shaft 4 and accommodated in one static fan 3 and / or one fan. In this embodiment, the motor 5 is accommodated in one static fan 3 and one fan. The at least two fans are driven by the same motor 5. By driving at least two fans at the same rotating speed by one motor 5, greater wind pressure and more wind volume can be provided than a single fan. Moreover, only a single motor 5 is used, and the driving cost is lower. In this embodiment, the motor 5 is a single-phase motor. Of course, in other embodiments, the motor 5 can also be a three-phase motor. The motor 5 provides a working voltage range of 2-16.8V, and preferably, the motor 5 provides a working voltage range of 10-15V.

[0056] In one embodiment, as shown in FIGS. 2-2 to 2-5, each of the at least one static fan 3 and the at least two fans comprises a wheel shell and a plurality of blades arranged at intervals around the outer side of the wheel shell. The maximum diameter of the wheel shell of any one static fan 3 is less than 5mm different from the maximum diameter of the wheel shell of any one fan. That is, the diameter of the wheel shell of the static fan 3 is similar to the diameter of the wheel shell of the fan, the wind generated by the rotation of the blades of the fan is reduced by the wind resistance generated by the static fan 3, and the outflow effect is good. In this embodiment, the diameter of the wheel shell of the static fan 3 is equal to the diameter of the wheel shell of the fan, of course, without being limited thereto. The ratio of the maximum diameter of the wheel shell of the static fan 3 to the total diameter of the static fan 3 is 0.25-0.8. It should be understood that when the portable fan is a desktop fan, a clip fan and the like, which are slightly larger fans, the ratio of the maximum diameter of the wheel shell of the static fan 3 to the total diameter of the static fan 3 is smaller; when the portable fan is a handheld fan, a neck-hanging fan and the like, which are slightly smaller fans, the ratio of the maximum diameter of the wheel shell of the static fan 3 to the total diameter of the static fan 3 is larger, which mainly depends on the overall volume and the outflow area of the portable fan.

[0057] In one embodiment, as shown in FIGS. 2-2 to 2-5, the braking assembly includes one static fan 3 and two blowers, one static fan 3 is arranged between the two blowers. In other embodiments, the braking assembly can include two static fans 3 and two blowers, the static fans 3 and the blowers are alternately and spacedly arranged; or the braking assembly can include three static fans 3 and two blowers, the static fans 3 and the blowers are alternately and spacedly arranged. The number of static fans 3 and the number of blowers are not limited thereto.

[0058] In one embodiment, as shown in FIGS. 2-2 to 2-5, the braking assembly includes one static fan 3 and two blowers, one static fan 3 is arranged between the two blowers. The static fan 3 includes a static wheel shell 31 and a plurality of static blades 32, the diameter of the static wheel shell 31 is constant in the axial direction. In this embodiment, the static fan 3 is integrally formed with the shell 1, and the static blades 32 are directly connected to the shell 1. In other embodiments, the static fan 3 and the shell 1 can also be separately formed, and the static blades 32 are fixed to the shell 1 by screwing, clamping or other fixing methods. The inner side of the static wheel shell 31 is provided with a support structure 33, and the rotating shaft 4 and the motor 5 are fixed to the support structure 33. The axial center line of the rotating shaft 4 is deviated from the axial center line of the static fan 3 by less than 3mm, so that the two blowers can be more balanced after being installed on the rotating shaft 4, which is beneficial to the dynamic balance of the two blowers. The rotating shaft 4 is provided with a plurality of limiting members 6, and the front and rear ends of the rotating shaft 4 pass through the wheel shells of the blowers, and the limiting members 6 are arranged on the inner side and / or the outer side of the wheel shells of the blowers to limit the blowers in the axial direction. In this embodiment, the limiting members 6 are arranged on the outer side of the wheel shells of the blowers, which can prevent the blowers from rotating off the rotating shaft 4. The connection between the limiting members 6 and the rotating shaft 4 can be threaded connection or other connection methods. As shown in FIGS. 2-4 and 2-8, the cross section of the part of the rotating shaft 4 fixed to the blowers is in the shape of "D", so that the blowers can be more easily rotated when the rotating shaft 4 rotates.

[0059] In one embodiment, as shown in FIGS. 2-2 to 2-5, the brake assembly comprises one static fan 3 and two fans, one static fan 3 is arranged between the two fans. The rear fan is the first fan 2a, and the front fan is the second fan 2b. The first fan 2a comprises a first dynamic wheel shell 21a and a plurality of first dynamic blades 22a, and the second fan 2b comprises a second dynamic wheel shell 21b and a plurality of second dynamic blades 22b. The inner side of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b has a space, which can match the inner side of the static wheel shell 31 to accommodate the motor 5. The first dynamic wheel shell 21a opens forward, and the second dynamic wheel shell 21b opens backward. The openings of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b are opposite and both face the inside of the shell 1, which is conducive to forming a safe environment for the motor 5. The first dynamic wheel shell 21a comprises an end portion 211, an enlarged portion 212 and a smooth portion 213 connected in sequence from front to back, and the second dynamic wheel shell 21b comprises a smooth portion 213, an enlarged portion 212 and an end portion 211 connected in sequence from front to back. The diameter of the end portion 211 is smaller than the diameter of the smooth portion 213, and the diameter of the enlarged portion 212 increases from the end portion 211 to the smooth portion 213, that is, the diameter of the enlarged portion 212 of the first fan 2a increases radially from back to front, and the diameter of the enlarged portion 212 of the second fan 2b decreases radially from back to front. In this embodiment, the diameter of the end portion 211 is 28.18-32.18mm, the diameter of the smooth portion 213 is 60-64mm, the length of the smooth portion 213 in the axial direction is 23.2-27.2mm, and the length of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b in the axial direction is 36-40mm. A plurality of first dynamic blades 22a are connected to the smooth portion 213, and a plurality of second dynamic blades 22b are connected to the smooth portion 213. The diameter of the smooth portion 213 is the maximum diameter of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b, and the length of the smooth portion 213 in the axial direction is more than half of the length of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b in the axial direction, respectively. Therefore, the plurality of first dynamic blades 22a and the second dynamic blades 22b are arranged on the smooth portion 213, which can better cut and blow air. Moreover, the airflow flows through the end portion 211, the enlarged portion 212, the smooth portion 213, the smooth portion 213, the enlarged portion 212 and the end portion 211 in sequence from back to front. The airflow first increases in pressure, then flows smoothly forward, and finally converges and is discharged. The structure design is reasonable. In other embodiments, a plurality of first dynamic blades 22a can be connected to the smooth portion 213 and the enlarged portion 212, and a plurality of second dynamic blades 22b can be connected to the smooth portion 213 and the enlarged portion 212.

[0060] In one embodiment, as shown in FIGS. 2-2 to 2-4, the number of the first moving blades 22a and the second moving blades 22b is 12, and the number of the stationary blades 32 is 5. The number of the first moving blades 22a, the second moving blades 22b and the stationary blades 32 is not limited to this.

[0061] In one embodiment, as shown in FIGS. 2-2, 2-5 to 2-8, the front side edge of the blade is the leading edge, the rear side edge is the trailing edge, the connecting part of the leading edge and the trailing edge and connecting the wheel shell is the blade root, and the connecting part of the leading edge and the trailing edge and opposite to the blade root is the blade tip. The leading edge and the trailing edge of the first moving blade 22a are both "S" shaped, and the first moving blade 22a twists and bends from the blade root to the blade tip first in the same direction as the rotating direction, and then twists and bends in the opposite direction of the rotating direction. This arrangement can increase the wind pressure and the wind volume, and control the wind resistance. The blade root of the first moving blade 22a extends from rear to front, the blade root of the stationary blade 32 extends from rear to front, and the blade root of the second moving blade 22b extends from rear to front. In this embodiment, the extending direction of the blade root of the first moving blade 22a is the same as the extending direction of the blade root of the second moving blade 22b, and the extending direction of the blade root of the stationary blade 32 is opposite to the extending direction of the blade root of the first moving blade 22a. The wind generated by the first moving blade 22a is combed and transmitted by the blade root of the stationary blade 32 with opposite extending direction, which can reduce the wind resistance and the noise, avoid backflow, and make the wind of the first fan 2a better transition to the second fan 2b.

[0062] In one embodiment, as shown in FIGS. 2-5 to 2-8, the included angle between the connecting line of the front and rear ends of the blade root of the first moving blade 22a and the axial direction is 30-80°. The larger the angle, the greater the pressure between the front and rear surfaces of the blade, and the greater the wind pressure at the same rotating speed. However, if the pressure on the rear surface is too large, backflow phenomenon may occur, which may reduce the performance of the fan. Therefore, the preferred included angle range is 30-80°, which can improve the wind pressure and the wind volume. The included angle between the connecting line of the front and rear ends of the blade root of the first moving blade 22a and the connecting line of the front and rear ends of the blade tip of the first moving blade 22a is 5-25°. This angle also reflects the curvature of the blade. The larger the angle, the greater the kinetic energy of the gas at the same rotating speed, and the greater the wind volume and the wind pressure. However, the resistance on the blade is also greater, and the torque of the motor 5 is also greater. Therefore, the preferred range is 5-25°, which can improve the wind pressure and the wind volume. The second moving blade 22b and the first moving blade 22a have the same structure and the same performance.

[0063] In one embodiment, as shown in FIGS. 2-5 to 2-8, the first runner shell 21a and the static runner shell 31 are spaced apart by 1.5-3 mm in the axial direction, the static runner shell 31 and the second runner shell 21b are spaced apart by 1.5-3 mm in the axial direction, the first runner shell 21a, the static runner shell 31 and the second runner shell 21b are spaced apart by a small distance and have a small difference in diameter, so that the wind can flow smoothly and the wind energy loss is small. The first runner blade 22a and the static runner blade 32 are spaced apart by 10.5-14.5 mm in the axial direction, the static runner blade 32 and the second runner blade 22b are spaced apart by 9.7-13.7 mm in the axial direction, the first runner blade 22a, the static runner blade 32 and the second runner blade 22b have a suitable interval between the adjacent two, which can control the wind pressure and avoid backflow caused by excessive wind pressure, and can also smoothly send the wind forward. The tip of the first runner blade 22a and the shell 1 are spaced apart by 0.5-3.5 mm in the radial direction, and the tip of the second runner blade 22b and the shell 1 are spaced apart by 0.5-3.5 mm in the radial direction. A suitable interval can increase the wind pressure while avoiding noise caused by airflow friction.

[0064] In one embodiment, as shown in FIGS. 2-2, 2-5 and 2-6, the brake assembly further comprises an air inlet cover arranged at the rear of the shell 1 and an air outlet cover arranged at the front of the shell 1. It should be understood that the air inlet cover and the air outlet cover can also be regarded as static fans 3, and the air inlet cover and the air outlet cover have the functions of flow regulation and flow guidance.

[0065] Scheme three

[0066] In one embodiment, as shown in FIGS. 3-1, 3-2 and 3-5, the portable fan. The air outlet component 100 is arranged on the support 6, and the power supply 7 is arranged in the support 6. In this embodiment, the portable fan is a handheld fan, and in other embodiments, the portable fan can also be one of a clip fan, a desktop fan, a hanging neck fan and other portable fans.

[0067] In one embodiment, as shown in FIGS. 3-2, 3-3 and 3-5, the air outlet component 100 comprises a shell 1 and a brake assembly received in the shell 1, the shell 1 penetrates through the front and rear, the shell 1 is air-inlet at the rear end and air-outlet at the front end, the power supply 7 supplies power to the brake assembly, and the brake assembly drives wind and blows the wind to the front end. It should be understood that in other embodiments, the shell 1 can also be provided with an air inlet area. In addition, the outer side of the shell 1 is provided with a buffer (not numbered), and the outer side of the buffer is provided with an outer shell (not numbered, the same below), and the outer shell is fixed with the support 6.

[0068] In one embodiment, as shown in FIG. 3-2, FIG. 3-3 and FIG. 3-5, the brake assembly comprises at least two static fans fixed in the housing 1, at least two air fans and at least two rotating shafts 4, the air fans rotating around the rotating shafts 4 to generate wind. The at least two rotating shafts 4 are arranged axially, and each of the rotating shafts 4 is fixed at the center of one of the static fans. The at least two air fans are arranged on the same axis, and each of the air fans is fixed on one of the rotating shafts 4, the rotating shafts 4 driving the air fans to rotate, and the at least two air fans blowing wind forward. By arranging the at least two air fans, the at least two air fans can provide greater wind pressure and wind volume than a single air fan at the same rotating speed. The brake assembly further comprises at least two motors 5, each of the motors 5 being fixed on one of the rotating shafts 4 and being accommodated in one of the static fans and / or one of the air fans. In this embodiment, the motors 5 are substantially accommodated in the air fans. Each of the air fans is driven by one of the motors 5. At the same wind volume and wind pressure requirement, the rotating speed of the at least two air fans can be lower than that of a single air fan. The lower rotating speed can reduce the manufacturing difficulty and production cost of the motors 5, and can also reduce the noise of the motors 5. It can be understood that the static fans, the rotating shafts 4, the air fans and the motors 5 are in one-to-one correspondence. In this embodiment, the motors 5 are single-phase motors. Of course, in other embodiments, the motors 5 can also be three-phase motors. The working voltage range provided by the motors 5 is 2-16.8V, and preferably, the working voltage range provided by the motors 5 is 2-4.2V.

[0069] In one embodiment, as shown in FIG. 3-2 to FIG. 3-5, each of the at least two static fans and the at least two air fans comprises a wheel shell and a plurality of blades arranged on the outer side of the wheel shell. The maximum diameter of the wheel shell of any one of the static fans is less than 5mm different from the maximum diameter of the wheel shell of any one of the air fans, that is, the diameters of the wheel shells of the static fans and the air fans are similar, and the wind generated by the rotation of the blades of the air fans receives less wind resistance generated by the static fans, and the air outlet effect is good. The ratio of the maximum diameter of the wheel shell of the static fan to the total diameter of the static fan is 0.15-0.8. It should be understood that when the portable fan is a desktop fan, a clip fan or the like, which is a slightly larger fan, the ratio of the maximum diameter of the wheel shell of the static fan to the total diameter of the static fan is smaller; when the portable fan is a handheld fan, a neck-hanging fan or the like, which is a slightly smaller fan, the ratio of the maximum diameter of the wheel shell of the static fan to the total diameter of the static fan is larger. This mainly depends on the overall volume and air outlet area of the portable fan.

[0070] In one embodiment, as shown in FIGS. 3-2 to 3-5, the braking assembly comprises two static fans and two blowers, the two static fans are arranged between the two blowers, and the rotation directions of the two blowers are opposite. Of course, in other embodiments, the static fans and the blowers can be alternately arranged, and the rotation directions of the two blowers can also be the same. In addition, the number of static fans and the number of blowers are not limited in this way.

[0071] In one embodiment, as shown in FIGS. 3-2 to 3-5, the braking assembly comprises two static fans and two blowers, the two static fans are arranged between the two blowers. The static fan at the rear side is a first static fan 3a, which comprises a first static wheel shell 31a and a plurality of first static blades 32a. The static fan at the front side is a second static fan 3b, which comprises a second static wheel shell 31b and a plurality of second static blades 32b. The diameters of the first static wheel shell 31a and the second static wheel shell 31b are constant in the axial direction, the first static wheel shell 31a and the second static wheel shell 31b are arranged in abutment, and the first static blades 32a and the second static blades 32b are spaced apart by 0.2-1 mm. In this embodiment, the shell 1 is formed in two parts, which are arranged in abutment. In other embodiments, the shell 1 can also be integrally formed. In this embodiment, the first static fan 3a is integrally formed with a part of the shell 1, and the first static blades 32a are directly connected to a part of the shell 1. The second static fan 3b is integrally formed with another part of the shell 1, and the second static blades 32b are directly connected to another part of the shell 1. In other embodiments, the first static fan 3a and the part of the shell 1 can also be formed separately, and the first static blades 32a are fixed to the part of the shell 1 by screwing, clamping or other fixing methods. The second static fan 3b and the other part of the shell 1 can also be formed separately, and the second static blades 32b are fixed to the other part of the shell 1 by screwing, clamping or other fixing methods. The inner sides of the first static wheel shell 31a and the second static wheel shell 31b are provided with support structures 311, and the rotating shaft 4 and the motor 5 are fixed to the support structures 311 correspondingly.

[0072] In one embodiment, as shown in FIGS. 3-2 to 3-5, the brake assembly comprises two static fans and two blowers, and the two static fans are arranged between the two blowers. The rear-side blower is the first blower 2a, and the front-side blower is the second blower 2b. The first blower 2a comprises a first dynamic wheel shell 21a and a plurality of first dynamic blades 22a, and the second blower 2b comprises a second dynamic wheel shell 21b and a plurality of second dynamic blades 22b. The first dynamic wheel shell 21a is open towards the front, the second dynamic wheel shell 21b is open towards the rear, the first dynamic wheel shell 21a and the second dynamic wheel shell 21b are oppositely open and are both arranged towards the inside of the shell 1, which is conducive to forming a safe environment for the motor 5. The first dynamic wheel shell 21a comprises an end portion 211, an enlarged portion 212 and a smooth portion 213 connected in sequence from front to back, and the second dynamic wheel shell 21b comprises a smooth portion 213, an enlarged portion 212 and an end portion 211 connected in sequence from back to front. The diameter of the end portion 211 is smaller than the diameter of the smooth portion 213, and the diameter of the enlarged portion 212 increases from the end portion 211 to the smooth portion 213, that is, the diameter of the enlarged portion 212 of the first blower 2a increases radially from back to front, and the diameter of the enlarged portion 212 of the second blower 2b decreases radially from back to front. In this embodiment, the diameter of the end portion 211 is 12.3-16.3 mm, the diameter of the smooth portion 213 is 19.24-23.24 mm, the length of the smooth portion 213 in the axial direction is 6.1-10.1 mm, and the length of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b in the axial direction is 15-19 mm. A plurality of first dynamic blades 22a are connected to the smooth portion 213 and the enlarged portion 212, and a plurality of second dynamic blades 22b are connected to the smooth portion 213 and the enlarged portion 212. The diameter of the smooth portion 213 is the maximum diameter of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b, and the length of the smooth portion 213 in the axial direction accounts for a large proportion of the length of the first dynamic wheel shell 21a and the second dynamic wheel shell 21b in the axial direction. Therefore, the plurality of first dynamic blades 22a and the plurality of second dynamic blades 22b are arranged on the smooth portion 213 and the enlarged portion 212, which can better cut and blow air. Moreover, the airflow flows in sequence from back to front through the end portion 211, the enlarged portion 212, the smooth portion 213, the smooth portion 213, the enlarged portion 212 and the end portion 211, and the airflow is first pressurized, then flows smoothly forward, and finally converges and is discharged, which is a reasonable structure design. In other embodiments, a plurality of first dynamic blades 22a can be connected to the smooth portion 213, and a plurality of second dynamic blades 22b can be connected to the smooth portion 213.

[0073] In one embodiment, as shown in FIGS. 3-3 to 3-6, the leading side of the blade is the leading edge, the trailing side is the trailing edge, the connecting part of the leading edge and the trailing edge and the wheel shell is the blade root, and the connecting part of the leading edge and the trailing edge opposite to the blade root is the blade tip. The leading edge and the trailing edge of the first moving blade 22a are straight lines, and the first moving blade 22a extends radially and twists and bends from the blade root to the blade tip, which can increase the wind pressure and improve the air volume. The blade root of the first moving blade 22a extends obliquely from back to front, the blade root of the first stationary blade 32a and the second stationary blade 32b extends axially straight forward, and the second moving blade 22b extends obliquely from back to front. In this embodiment, the extending direction of the blade root of the first moving blade 22a is opposite to the extending direction of the blade root of the second moving blade 22b, and the blade root of the first stationary blade 32a and the second stationary blade 32b extends straight, so that the second moving blade 22b directly combs the air flow of the first moving blade 22a, and the transition of the first stationary blade 32a and the second stationary blade 32b can reduce the wind resistance and noise.

[0074] In one embodiment, when the stationary fan and the fan are alternately and spacedly arranged, the rotating directions of the two fans are the same. The blade root of the first moving blade 22a extends obliquely from back to front, the second moving blade 22b extends obliquely from back to front, the rotating directions of the first moving blade 22a and the second moving blade 22b are the same, and the extending direction of the blade root of the first moving blade 22a is the same as the extending direction of the blade root of the second moving blade 22b.

[0075] In one embodiment, as shown in FIGS. 3-3 to 3-6, the included angle between the connecting line of the front and back ends of the blade root of the first moving blade 22a and the axial direction is 30-80°. The greater the angle, the greater the pressure between the front and back surfaces of the blade, and the greater the wind pressure at the same speed. However, if the back surface pressure is too large, a backflow phenomenon may occur, which reduces the performance of the fan. Therefore, the preferred included angle range is 30-80°. The included angle between the connecting line of the front and back ends of the blade root of the first moving blade 22a and the connecting line of the front and back ends of the blade tip of the first moving blade 22a is 5-25°, which also reflects the curvature of the blade. The greater the angle, the greater the kinetic energy of the gas at the same speed, and the greater the air volume and wind pressure. However, the greater the resistance of the blade, the greater the torque required for the motor 5. Therefore, the preferred range is 5-25°, which can improve the wind pressure and air volume. The second moving blade 22b and the first moving blade 22a have the same structure and the same performance.

[0076] In one embodiment, as shown in FIGS. 3-5 to 3-7, the first dynamic wheel shell 21a and the first static wheel shell 31a are spaced apart in the axial direction by 0.5-3.5 mm, the second static wheel shell 31b and the second dynamic wheel shell 21b are spaced apart in the axial direction by 0.5-3.5 mm, the first dynamic wheel shell 21a, the first static wheel shell 31a, the second static wheel shell 31b, and the second dynamic wheel shell 21b are small in spacing and similar in diameter, so that the wind can flow smoothly and the wind energy loss is small. The first dynamic blade 22a and the first static blade 32a are spaced apart in the axial direction by 3-6.2 mm, the second static blade 32b and the second dynamic blade 22b are spaced apart in the axial direction by 3-6.2 mm, the first dynamic blade 22a, the first static blade 32a, the second static blade 32b, and the second dynamic blade 22b are appropriately spaced apart, which can control the wind pressure and avoid backflow caused by excessive wind pressure, and can also smoothly send the wind forward. The tip of the first dynamic blade 22a and the shell 1 are spaced apart in the radial direction by 0.5-3.5 mm, and the appropriate spacing can increase the wind pressure while avoiding noise caused by airflow friction.

[0077] In one embodiment, as shown in FIGS. 3-1, 3-2, and 3-5, the brake assembly further comprises an air inlet cover 3c arranged at the rear of the shell 1 and an air outlet cover 3d arranged at the front of the shell 1. It should be understood that the air inlet cover 3c and the air outlet cover 3d can also be arranged as the structure of the static fan, or as shown in FIGS. 3-2 and 3-5, the air inlet cover 3c can be arranged as a structure having a plurality of micro-holes, which can be circular or regular hexagonal. The air inlet cover 3c and the air outlet cover 3d both have the functions of flow guiding and flow guiding.

[0078] The above is only a preferred embodiment of the present application, and does not limit the patent scope of the present application, and any equivalent structure or equivalent process transformation using the content of the specification and drawings, or direct or indirect application in other related technical fields, are also included in the patent protection scope of the present application.

Claims

1. An air outlet member, wherein, The air outlet component comprises: a cylinder body comprising an outer ring portion, the outer ring portion being through from front to back, the rear end being an air inlet, the front end being an air outlet, the diameter of the inner wall of the outer ring portion changing by less than 5mm from back to front; a brake assembly coaxially arranged with the outer ring portion, the brake assembly being mounted on the cylinder body and radially accommodated inside the outer ring portion, the brake assembly comprising a fan and a motor, the fan comprising a wheel shell and a plurality of blades arranged at intervals on the outer surface of the wheel shell, the motor being arranged radially inside the wheel shell; a flow guide coaxially arranged with the outer ring portion, the flow guide being mounted on the front side of the cylinder body, the flow guide comprising an inner shell portion; wherein the difference between the maximum diameter of the wheel shell and the maximum diameter of the inner shell portion is less than 5mm.

2. The air outlet component according to claim 1, wherein the cylinder body further comprises an inner ring portion and a plurality of first guide vanes connecting the outer ring portion and the inner ring portion, the inner ring portion being coaxially arranged with the outer ring portion, the inner ring portion extending radially unchanged from back to front; the brake assembly is mounted on the rear side of the inner ring portion; the flow guide further comprises an outer shell portion and a plurality of second guide vanes connecting the inner shell portion and the outer shell portion; wherein the difference between the maximum diameter of the wheel shell and the diameter of the inner ring portion is less than 5mm, the difference between the maximum diameter of the inner shell portion and the diameter of the inner ring portion is less than 5mm, and the difference between the diameter of the inner wall of the outer shell portion and the diameter of the inner wall of the outer ring portion is less than 5mm; the diameter of the inner wall of the outer ring portion is unchanged from back to front, the diameter of the inner wall of the outer shell portion is unchanged from back to front, the diameter of the inner wall of the outer shell portion is equal to the diameter of the inner wall of the outer ring portion, and the diameter of the inner wall of the outer shell portion and the diameter of the inner wall of the outer ring portion are 30-36mm; the wheel shell radially increases from back to front, the inner shell portion radially decreases from back to front, and the maximum diameter of the wheel shell, the maximum diameter of the inner shell portion and the diameter of the inner ring portion are all in the range of 19.24-23.24mm; the distance between the front end of the wheel shell and the inner ring portion is 0.5-3mm, and the distance between the inner shell portion and the inner ring portion is 0.15-1mm; the inner ring portion is provided with a base plate and a hollow shaft cylinder extending rearward from the base plate, the motor comprises a stator assembly and a rotor assembly, and the stator assembly, the rotor assembly and the fan are fixedly nested in the shaft cylinder; the rotor assembly comprises a rotating shaft, a bearing and a magnetic ring, the rotating shaft and the bearing are fixedly inserted in the shaft cylinder, the stator assembly is arranged radially outside the shaft cylinder, the magnetic ring is arranged radially outside the stator assembly, and the magnetic ring is fixedly arranged radially inside the wheel shell.

3. The air outlet component according to claim 2, wherein the wheel shell comprises a rear end portion, an enlarged portion radially increasing from the rear end portion forward, and a smooth portion radially unchanged from the enlarged portion forward, the slope of the enlarged portion continuously decreases from back to front, the axial length of the enlarged portion is 12.9-16.9mm, and the axial length of the smooth portion is 6.13-10.13mm. The wheel shell further comprises a fixing column at the center of the inner side, which is used for fixing the rotating shaft; The inner shell part is radially reduced from back to front, and the axial length of the inner shell part is 13-17 mm; A column is arranged at the center of the inner side of the inner shell part, and the column is inserted into and fixed to the shaft cylinder; Each of the blades comprises a blade root connected to the wheel shell, a blade tip opposite to the blade root, a leading edge connecting the blade root and the blade tip, and a trailing edge connecting the blade root and the blade tip, and the leading edge and the trailing edge are oppositely arranged; The front end of the blade root is arranged within the range of 1.5 mm from the front and back of the joint between the enlarged part and the smooth part.

4. The air outlet component according to claim 3, wherein, Each of the first vanes comprises a first segment and a second segment extending rearward from the first segment, the first segment is connected to both the inner ring part and the outer ring part, the second segment is only connected to the outer ring part, and the radially inner side of the second segment is spaced apart from the wheel shell; From back to front, the blades extend clockwise in a spiral, the second segments extend counterclockwise in a spiral, the first segments extend straight, and the second vanes extend clockwise in a spiral first and then extend straight; The spacing between the rear end of the second segment and the leading edge is 1.25-3.25 mm, and the spacing between the front end of the first segment and the rear end of the second vane is 0.4-1.4 mm; The number of the blades is 9, the number of the first vanes is 7, and the number of the second vanes is 7; The first vanes and the second vanes are arranged in a radial direction with spacing, and the projection of one first vane in an axial direction is located between the projections of two adjacent second vanes in the axial direction.

5. The air outlet component according to claim 1, wherein, The ratio of the axial length of the blade to the axial length of the first vane is in the range of 7:8-11:12, and the ratio of the axial length of the first vane to the axial length of the second vane is in the range of 12:7-8:

3.

6. The air outlet component according to claim 1, applied to a portable fan, wherein, The shell body is provided with an air inlet at the rear side and an air outlet at the front side; The air outlet component is accommodated in the shell body; The contraction member is accommodated in the shell body and arranged at the front side of the air outlet component, and comprises a contraction surface at the inner side, which is arranged towards the air duct and is radially reduced from back to front.

7. The air outlet component according to claim 6, wherein, The cylinder body comprises an outer ring part, an inner ring part, and a plurality of first vanes connecting the outer ring part and the inner ring part; The air outlet component further comprises a flow guide member arranged in the axial direction between the cylinder body and the contraction member, and the flow guide member comprises an outer shell part, an inner shell part, and a plurality of second vanes connecting the outer shell part and the inner shell part; The diameter of the inner wall of the outer ring part is constant from back to front, the diameter of the inner wall of the outer shell part is constant from back to front, and the diameter of the inner wall of the outer ring part is equal to the diameter of the inner wall of the outer shell part. The brake assembly comprises a fan and a motor, the fan comprises a wheel shell and a plurality of blades arranged around the outside of the wheel shell, and the motor is accommodated in the inside of the wheel shell; The wheel shell increases radially from back to front, the inner ring part extends radially from back to front without change, and the inner shell part decreases radially from back to front, the maximum diameter of the wheel shell and the diameter of the inner ring part differ by less than 5mm, the maximum diameter of the inner shell part and the diameter of the inner ring part differ by less than 5mm, and the maximum diameter of the wheel shell, the maximum diameter of the inner shell part and the diameter of the inner ring part are all in the range of 19.24-23.24mm; The distance between the front end of the wheel shell and the inner ring part is 0.5-3mm, and the distance between the inner shell part and the inner ring part is 0.15-1mm; The maximum diameter of the converging surface is equal to the diameter of the inner wall of the outer shell part, the minimum diameter of the converging surface is greater than the maximum diameter of the inner shell part, and the minimum diameter of the converging surface is 21.05-25.05mm; The inner shell part protrudes forward relative to the outer shell part, the front end of the inner shell part is located radially inside the converging surface, and the front end of the converging surface is located in front of the front end of the inner shell part.

8. The air outlet component according to claim 7, wherein Further comprising a soft shell, the soft shell is arranged in the shell body, and the soft shell covers the outside of the barrel, the flow guide and the converging part; The soft shell comprises an annular part, a front edge part and a rear edge part connected to the front and rear ends of the annular part respectively, the annular part covers the radially outer side of the outer ring part, the outer shell part and the converging part, the front edge part is arranged at the front end of the converging part, and the edge of the front edge part is flush with the front end of the converging surface, the rear edge part is arranged at the rear end of the outer ring part, and the edge of the rear edge part is flush with the rear end of the inner wall of the outer ring part; Further comprising a front guide part, a rear guide part and an air inlet mesh, the front guide part is embedded in the front end of the shell body, and the rear end of the front guide part abuts against the front edge part, the front guide part comprises a front guide surface located on the inner side, and the front guide surface increases radially from back to front, and the rear end of the front guide surface is flush with the edge of the front edge part; The rear guide part is embedded in the rear end of the shell body, and the front end of the rear guide part and the rear edge part sandwich and fix the air inlet mesh, the rear guide part comprises a rear guide surface located on the inner side, and the rear guide surface decreases radially from back to front, and the front end of the rear guide surface is flush with the edge of the rear edge part; The axial length of the shell body is 61-65mm, the axial length of the shell body, the front guide part and the rear guide part after installation is 66-70mm, the axial length of the soft shell is 54.5-58.5mm, the axial length from the rear end of the outer ring part to the front end of the converging part is 46.8-50.5mm, the axial length from the rear end of the wheel shell to the front end of the inner shell part is 43.5-47.5mm, the distance from the rear end of the wheel shell to the rear end of the rear guide part is 3.8-7.8mm, and the distance from the front end of the inner shell part to the front end of the front guide part is 14.75-18.75mm.

9. The air outlet component according to claim 7, wherein, the number of the vanes is 9, the number of the first vanes is 7, the number of the second vanes is 7, the first vanes and the second vanes are spaced apart in the radial direction, the projection of one first vane in the axial direction is between the projections of two adjacent second vanes in the axial direction; the spacing between the first vane and the vane in the axial direction is 1.25-3.25 mm, and the spacing between the second vane and the first vane in the axial direction is 0.4-1.4 mm.

10. The air outlet component according to claim 7, wherein, the first vane comprises a first section and a second section extending rearward from the first section, the first section connects the inner ring and the outer ring, and the second section only connects the outer ring, and the radial inner side of the second section is spaced apart from the wheel housing; from rear to front, the vanes extend clockwise, the second section extends counterclockwise, the first section extends straight, and the second vane first extends clockwise and then extends straight.

11. The air outlet member of claim 1 applied to a portable fan, wherein, comprising: a housing, extending through from front to rear, with an air inlet at the rear end and an air outlet at the front end; a braking assembly, accommodated in the housing, for blowing air towards the front end; wherein the braking assembly comprises: at least one static fan, fixed in the housing; a rotating shaft, arranged in the axial direction and fixed at the center of the static fan; at least two air fans, fixed on the same rotating shaft, the rotating shaft drives the air fans to rotate, the rotating directions of the at least two air fans are the same, and the air fans blow air forward, and the front side or the rear side of at least one air fan is provided with the static fan; wherein the rotating shaft of at least one static fan and the rotating shaft of at least two air fans each comprise a wheel housing and a plurality of vanes spaced apart and arranged around the outer side of the wheel housing, and the maximum diameter of the wheel housing of any one static fan and the maximum diameter of the wheel housing of any one air fan differ by less than 5 mm.

12. The air outlet component according to claim 11, wherein, the braking assembly comprises a motor, the motor is fixed to the rotating shaft and accommodated in one static fan and / or one air fan, and at least two air fans are driven by the same motor; the vanes of the static fan are connected to the housing, and the ratio of the maximum diameter of the wheel housing of the static fan to the total diameter of the static fan is 0.25-0.8; the braking assembly comprises one static fan and two air fans, and one static fan is arranged between the two air fans; or the braking assembly comprises two static fans and two air fans, and the static fans and the air fans are alternately and spaced apart; or the braking assembly comprises three static fans and two air fans, and the static fans and the air fans are alternately and spaced apart; When the brake assembly comprises one static fan and two blowers, the axial centerline of the rotating shaft and the axial centerline of the static fan are deviated by less than 3mm, the rotating shaft is provided with a plurality of limiting members, the front and rear ends of the rotating shaft are arranged outside the wheel shell of the blower, the limiting members are arranged on the inner side and / or the outer side of the wheel shell of the blower to limit the blower in the axial direction, and the cross section of the part of the rotating shaft fixed to the blower is in the shape of "D".

13. The air outlet component according to claim 12, wherein, The brake assembly comprises a motor fixed to the rotating shaft and accommodated in one static fan and / or one blower, and at least two blowers are driven by the same motor; The ratio of the maximum diameter of the wheel shell of the static fan to the total diameter of the static fan is 0.25-0.8; The brake assembly comprises one static fan and two blowers, and one static fan is arranged between the two blowers; Or the brake assembly comprises two static fans and two blowers, and the static fans and the blowers are alternately and spacedly arranged; Or the brake assembly comprises three static fans and two blowers, and the static fans and the blowers are alternately and spacedly arranged; When the brake assembly comprises one static fan and two blowers, the rear blower is the first blower, the front blower is the second blower, the first blower comprises a first dynamic wheel shell and a plurality of first dynamic blades, the second blower comprises a second dynamic wheel shell and a plurality of second dynamic blades, the first dynamic wheel shell is open forward, and the second dynamic wheel shell is open backward; The first dynamic wheel shell comprises an end portion, an expanding portion and a smooth portion connected in sequence from front to back, the second dynamic wheel shell comprises a smooth portion, an expanding portion and an end portion connected in sequence from front to back, the diameter of the end portion is smaller than that of the smooth portion, and the diameter of the expanding portion increases from the end portion to the smooth portion; the static fan comprises a static wheel shell and a plurality of static blades, and the diameter of the static wheel shell is constant in the axial direction.

14. The air outlet component according to claim 13, wherein, The plurality of first dynamic blades are connected to the smooth portion, or the plurality of first dynamic blades are connected to the smooth portion and the expanding portion; The plurality of second dynamic blades are connected to the smooth portion, or the plurality of second dynamic blades are connected to the smooth portion and the expanding portion; the diameter of the end portion is 28.18-32.18mm, the diameter of the smooth portion is 60-64mm, the length of the smooth portion in the axial direction is 23.2-27.2mm, and the length of the first dynamic wheel shell and the second dynamic wheel shell in the axial direction is 36-40mm.

15. The air outlet component according to claim 13, wherein, The leading edge and the trailing edge of the first moving blade are both "S" shaped, the first moving blade twists and bends in the same direction as the rotation direction from the blade root to the blade tip, and then twists and bends in the opposite direction as the rotation direction, the blade root of the first moving blade extends from back to front, the blade root of the stationary blade extends from back to front, the blade root of the second moving blade extends from back to front, the extending direction of the blade root of the first moving blade is the same as the extending direction of the blade root of the second moving blade, and the extending direction of the blade root of the stationary blade is opposite to the extending direction of the blade root of the first moving blade; The included angle between the line connecting the front and back ends of the blade root of the first moving blade and the axial direction is 30-80°, the included angle between the line connecting the front and back ends of the blade root of the first moving blade and the line connecting the front and back ends of the blade tip of the first moving blade is 5-25°, and the plurality of second moving blades and the plurality of first moving blades are structurally identical; The axial distance between the first moving wheel shell and the stationary wheel shell is 1.5-3 mm, the axial distance between the stationary wheel shell and the second moving wheel shell is 1.5-3 mm, the axial distance between the first moving blade and the stationary blade is 10.5-14.5 mm, and the axial distance between the stationary blade and the second moving blade is 9.7-13.7 mm; The radial distance between the blade tip of the first moving blade and the shell is 0.5-3.5 mm, and the radial distance between the blade tip of the second moving blade and the shell is 0.5-3.5 mm.

16. The air outlet member of claim 1, applied to a portable fan, wherein, It comprises: a shell, which is through from front to back, with air inlet at the back end and air outlet at the front end; a braking assembly, which is accommodated in the shell and blows air towards the front end; wherein the braking assembly comprises: at least two stationary fans, which are fixed in the shell; at least two rotating shafts, which are arranged axially, with each corresponding to a stationary fan fixed at the center; at least two air fans, which are located on the same axis, with each corresponding to a rotating shaft fixed thereon, and the rotating shaft drives the air fan to rotate, and at least two air fans blow air forward; wherein at least two stationary fans and at least two air fans each comprise a wheel shell and a plurality of blades arranged on the outer side of the wheel shell, and the maximum diameter of the wheel shell of any stationary fan and the maximum diameter of the wheel shell of any air fan differ by less than 5 mm.

17. The air outlet component according to claim 16, wherein the braking assembly comprises at least two motors, each corresponding to a rotating shaft and being accommodated in a stationary fan and / or an air fan, each air fan is driven by a motor, and the ratio of the maximum diameter of the wheel shell of the stationary fan to the total diameter of the stationary fan is 0.15-0.8; the braking assembly comprises two stationary fans and two air fans, the two stationary fans are arranged between the two air fans, and the rotating directions of the two air fans are opposite; or the stationary fans and the air fans are alternately and spacedly arranged, and the rotating directions of the two air fans are the same. When two of the static fans are arranged between two of the fans, the static fan on the rear side is a first static fan, the first static fan comprises a first static wheel shell and a plurality of first static blades, the static fan on the front side is a second static fan, the second static fan comprises a second static wheel shell and a plurality of second static blades, the diameters of the first static wheel shell and the second static wheel shell are constant in the axial direction, the first static wheel shell and the second static wheel shell are arranged in abutment, and the first static blades and the second static blades are spaced apart by 0.2-1 mm; When two of the static fans are arranged between two of the fans, the fan on the rear side is a first fan, the fan on the front side is a second fan, the first fan comprises a first dynamic wheel shell and a plurality of first dynamic blades, and the second fan comprises a second dynamic wheel shell and a plurality of second dynamic blades, the first dynamic wheel shell is open towards the front, and the second dynamic wheel shell is open towards the rear; The first dynamic wheel shell comprises an end portion, an enlarged portion and a smooth portion which are sequentially connected in the front-rear direction, the second dynamic wheel shell comprises a smooth portion, an enlarged portion and an end portion which are sequentially connected in the front-rear direction, the diameter of the end portion is smaller than the diameter of the smooth portion, and the diameter of the enlarged portion increases from the end portion to the smooth portion.

18. The air outlet component according to claim 17, wherein The plurality of first dynamic blades are connected to the smooth portion and the enlarged portion, or the plurality of first dynamic blades are connected to the smooth portion; The plurality of second dynamic blades are connected to the smooth portion and the enlarged portion, or the plurality of second dynamic blades are connected to the smooth portion; the diameter of the end portion is 12.3-16.3 mm, the diameter of the smooth portion is 19.24-23.24 mm, and the length of the first dynamic wheel shell and the second dynamic wheel shell in the axial direction is 15-19 mm; The front edge and the rear edge of the first dynamic blade are straight lines, the first dynamic blade extends in a radially twisted and curved manner from a blade root portion to a blade tip portion, the blade root portion of the first dynamic blade extends obliquely from rear to front, the included angle between the line connecting the front and rear ends of the blade root portion of the first dynamic blade and the axial direction is 30-80°, the included angle between the line connecting the front and rear ends of the blade root portion of the first dynamic blade and the line connecting the front and rear ends of the blade tip portion of the first dynamic blade is 5-25°, and the plurality of second dynamic blades and the plurality of first dynamic blades are arranged in axial symmetry; and the blade root portions of the first static blades and the second static blades extend axially in a straight line towards the front.

19. The air outlet component according to claim 17, wherein The spacing between the first dynamic wheel shell and the first static wheel shell in the axial direction is 0.5-3.5 mm, the spacing between the second static wheel shell and the second dynamic wheel shell in the axial direction is 0.5-3.5 mm, the spacing between the first dynamic blade and the first static blade in the axial direction is 3-6.2 mm, the spacing between the second static blade and the second dynamic blade in the axial direction is 3-6.2 mm, the spacing between the blade tip portion of the first dynamic blade and the housing in the radial direction is 0.5-3.5 mm, and the spacing between the blade tip portion of the second dynamic blade and the housing in the radial direction is 0.5-3.5 mm.

20. A portable fan, wherein The portable fan can be any one of a desktop fan, a clip fan, a handheld fan, and a neck fan. The portable fan can be any one of a desktop fan, a clip fan, a handheld fan, and a neck fan.

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