CN117329162A - Impeller, fan and electronic equipment - Google Patents

Impeller, fan and electronic equipment Download PDF

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Publication number
CN117329162A
CN117329162A CN202211611297.6A CN202211611297A CN117329162A CN 117329162 A CN117329162 A CN 117329162A CN 202211611297 A CN202211611297 A CN 202211611297A CN 117329162 A CN117329162 A CN 117329162A
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CN
China
Prior art keywords
impeller
blades
blade
hub
fan
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Pending
Application number
CN202211611297.6A
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Chinese (zh)
Inventor
杨源儒
高向正
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Honor Device Co Ltd
Original Assignee
Honor Device Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Honor Device Co Ltd filed Critical Honor Device Co Ltd
Priority to CN202211611297.6A priority Critical patent/CN117329162A/en
Publication of CN117329162A publication Critical patent/CN117329162A/en
Pending legal-status Critical Current

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F04D29/282—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis
    • F04D29/283—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers the leading edge of each vane being substantially parallel to the rotation axis rotors of the squirrel-cage type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D25/00—Pumping installations or systems
    • F04D25/02—Units comprising pumps and their driving means
    • F04D25/08—Units comprising pumps and their driving means the working fluid being air, e.g. for ventilation
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
    • F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
    • F04D29/663—Sound attenuation

Abstract

The application discloses impeller, fan and electronic equipment, the tray includes interior support piece, outer support piece and at least one support, and wheel hub is fixed on interior support piece, and outer support piece is coaxial to be set up in the outside of interior support piece, and at least one support interval is connected in order to form at least one through hole between interior support piece and the outer support piece, and through hole department is used for forming air intake region; the plurality of blades use the inner support rotating shaft as the center of the annular array, the outer side of the inner support is distributed in the annular array, the third end part of each blade is connected with the outer support, and the fourth end part of each blade extends towards the direction away from the hub. The air inlet area is not provided with the blades, so that the air is not stirred by the blades in the air inlet area, the pneumatic noise in the air inlet area can be reduced, the noise of the fan is reduced, and the air quantity is increased. The number and the form of the blades of the core working area are reserved, so that the working capacity of the impeller is not reduced, and the heating device in the electronic equipment is optimally radiated.

Description

Impeller, fan and electronic equipment
Technical Field
The application relates to the technical field of fans, in particular to an impeller, a fan and electronic equipment.
Background
Fans are mounted on many electronic devices, and the fans are used for radiating heat from heat-generating components of the electronic devices. For some electronic devices, such as mobile phones and notebook computers, the installation space of the fan is smaller and smaller along with the smaller and smaller volume design of the electronic devices, so that the requirement on the silencing performance of the fan is higher.
In order to ensure the core of the impeller in the fan to function as a traditional fan, the fan is provided with a plurality of blades. Each blade is densely distributed, so that the flow area of an air inlet of the fan is reduced, the flow field at the position of the air inlet is disordered, and the noise is large. Thus, the mute performance of the fan cannot be improved.
Disclosure of Invention
The application provides an impeller, fan and electronic equipment to solve the problem that current fan noise can't improve silence performance greatly.
In a first aspect, the present application provides an impeller comprising: a hub; the tray comprises an inner supporting piece, an outer supporting piece and at least one bracket, wherein the hub is fixed on the inner supporting piece, the outer supporting piece is arranged on the outer side of the inner supporting piece, the outer supporting piece is identical to the rotating shaft of the inner supporting piece, the at least one bracket is connected between the inner supporting piece and the outer supporting piece at intervals, and at least one through hole is formed between the inner supporting piece and the outer supporting piece and used for circulating air; the blades take a rotating shaft as the center of the annular array, and are distributed in the annular array outside the inner support piece; wherein, along a first direction, each blade comprises a fifth end towards the hub and a sixth end away from the hub, the fifth end being connected with the outer support, the sixth end extending in a direction away from the hub; wherein the first direction is the radial direction of the hub.
The impeller that this application embodiment provided, each blade are connected with wheel hub through the tray, offer a plurality of through-holes on the tray, divide into interior support piece and outer support piece with the tray to and be used for connecting the support of interior support piece and outer support piece. The through holes are used for forming an air inlet area, and each blade fixed on the outer support piece is used for forming a working area. The air inlet area is not provided with the blades, so that the air is not stirred by the blades in the air inlet area, thereby reducing the aerodynamic noise of the air inlet area and reducing the noise of the fan. Only the blades of the working area are reserved, and the number and the blade form of the blades of the core working area can be kept, so that the working capacity of the impeller is not reduced. Therefore, the impeller can reduce fan noise on the premise of not changing the size of the fan and not affecting the performance of the fan.
In some embodiments of the present application, the inner support is of a circular structure, and the outer support is of an annular structure; the inner diameter of the outer support piece is larger than the outer diameter of the inner support piece, and an annular through hole area is formed between the inner support piece and the outer support piece. In this way, the tray forms the wake-up through hole area for forming the air inlet area, so that the blades are not arranged in the air inlet area, the aerodynamic noise of the air inlet area can be reduced, and the noise of the fan can be reduced.
In some embodiments of the present application, the at least one bracket is disposed in the annular through hole area at non-equidistant intervals; the two ends of each bracket are respectively connected between the inner support piece and the outer support piece, and the annular through hole area between the inner support piece and the outer support piece is divided into at least one through hole with different areas. Therefore, the brackets are distributed in an uneven distribution mode, the regularity of the bracket impact air flow can be destroyed, so that sound energy concentration of sound sources of different brackets on the band-pass filter and frequency multiplication thereof is restrained in the superposition process, and further, the discrete noise peak value on the corresponding frequency is weakened, and the sound quality is improved while the noise is reduced.
In some embodiments of the present application, the at least one through-flow hole forms an air intake area of the impeller, and the area formed by the plurality of blades is a work area of the impeller. Therefore, no fan blade agitates air at the position of the air inlet, so that the pneumatic noise at the position of the air inlet can be reduced, and the noise of the fan is reduced. While retaining the blades of the core work area to maintain the work capacity of the impeller.
In some embodiments of the present application, the at least one bracket is disposed along a radial direction of the inner bracket. An included angle is formed between two adjacent brackets, and the angle of at least one included angle is unequal; at least one vertex of the included angle is positioned at the center of the inner supporting piece. The sum of cosine values of at least one included angle is 0, and the sum of sine values of at least one included angle is 0. Therefore, the impeller can meet the dynamic balance condition, and noise improvement and structural damage caused by gravity center deviation during operation are avoided.
In some embodiments of the present application, the blade is disposed on one side of the outer support along the second direction, and the outer support includes a fourth connection surface facing the blade, where the plurality of blades are connected to the fourth connection surface; wherein the second direction is the axial direction of the hub. Therefore, the strength and stability of the impeller can be improved, and the deformation of the blade group during rotation of the impeller is reduced.
In some embodiments of the present application, the outer support is disposed in the middle of the plurality of blades along the second direction; the blade has a fourth axial height on one side of the outer support along the second direction; wherein the fourth axial height is 10% -90% of the total axial height of the blade. In this way, the strength of the blade group of the whole impeller can be larger, and the deformation of the blade group can be smaller. The outer support piece can divide the blade into upper and lower two-layer to force the wind of going out to divide into upper and lower two parts, prevent to mix, and then reduce noise, make the air-out more even.
In some embodiments of the present application, the outer diameter of the outer support is smaller than the outer diameter of the area surrounded by the plurality of blades and is larger than the inner diameter of the area surrounded by the plurality of blades; the inner diameter of the outer support piece is smaller than or equal to the inner diameter of the area surrounded by the blades. Therefore, the size of the outer support is determined based on the size of the area surrounded by the blades, and the fixing effect of the outer support and the functional force of the blades can be improved.
In a second aspect, the present application provides a fan comprising a motor, a housing and an impeller as described in the first aspect, the impeller being mounted in the housing, an output shaft of the motor being connected to a hub of the impeller, the motor being arranged to drive the impeller to rotate.
In a third aspect, the present application provides an electronic apparatus including a heat generating device and a fan as shown in the second aspect that radiates heat from the heat generating device.
Drawings
In order to more clearly illustrate the technical solutions of the present application, the drawings that are needed in the embodiments will be briefly described below, and it will be obvious to those skilled in the art that other drawings can be obtained from these drawings without inventive effort.
FIG. 1 is a perspective view of an impeller provided in the prior art;
FIG. 2 is a top view of a first impeller provided in an embodiment of the present application;
FIG. 3 is a perspective view of a first impeller provided in an embodiment of the present application;
FIG. 4 is a side view of a first impeller provided in an embodiment of the present application;
FIG. 5 is a top view of a second impeller provided in an embodiment of the present application;
FIG. 6 is a perspective view of a second impeller provided in an embodiment of the present application;
FIG. 7 is a side view of a second impeller provided in an embodiment of the present application;
FIG. 8 is a top view of a third impeller provided in an embodiment of the present application;
FIG. 9 is a perspective view of a third impeller provided in an embodiment of the present application;
FIG. 10 is a side view of a third impeller provided in an embodiment of the present application;
FIG. 11 is a top view of a fourth impeller provided in an embodiment of the present application;
FIG. 12 is a perspective view of a fourth impeller provided in an embodiment of the present application;
FIG. 13 is a top view of a fifth impeller provided in an embodiment of the present application;
FIG. 14 is a perspective view of a fifth impeller provided in an embodiment of the present application;
FIG. 15 is a side view of a fifth impeller provided in an embodiment of the present application;
FIG. 16 is a first fan performance graph provided by an embodiment of the present application;
FIG. 17 is a top view of a sixth impeller provided in an embodiment of the present application;
FIG. 18 is a schematic view of an included angle formed by a sixth impeller according to an embodiment of the present disclosure;
FIG. 19 is a perspective view of a sixth impeller provided in an embodiment of the present application;
FIG. 20 is a side view of a sixth impeller provided in an embodiment of the present application;
FIG. 21 is a perspective view of a seventh impeller provided in an embodiment of the present application;
FIG. 22 is a perspective view of a fan provided by an embodiment of the present application;
fig. 23 is a graph of a second fan performance profile provided by an embodiment of the present application.
Detailed Description
The technical solutions in the embodiments of the present application will be clearly described below with reference to the drawings in the embodiments of the present application. It will be apparent that the described embodiments are some, but not all, of the embodiments of the present application. Based on the embodiments of the present application, other embodiments that may be obtained by a person of ordinary skill in the art without making any inventive effort are within the scope of the present application.
Hereinafter, the terms "first," "second," and the like are used for descriptive purposes only and are not to be construed as indicating or implying relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first", "a second", etc. may explicitly or implicitly include one or more such feature. In the description of the present application, unless otherwise indicated, the meaning of "a plurality" is two or more.
Furthermore, in this application, directional terms "upper", "lower", "top", "bottom", etc. are defined with respect to the orientation in which the components are schematically disposed in the drawings, and it should be understood that these directional terms are relative concepts that are used for the description and clarity of the drawings and that may be varied accordingly with respect to the orientation in which the components are disposed in the drawings.
The electronic device according to the embodiments of the present application includes, but is not limited to, a mobile phone, a notebook computer, a tablet computer, a laptop computer, a personal digital assistant, or a wearable device. The following description will be made with reference to an electronic device as a mobile phone.
The electronic device may include a display screen, a housing, a circuit board, a battery, a fan, and the like. The display screen and the shell are buckled together to form a closed cavity, and devices such as a circuit board, a battery, a fan and the like are uniformly distributed in the closed cavity. The circuit board is used for controlling the display screen to display pictures, and the battery is used for providing electric quantity for electronic devices such as the display screen, the circuit board, the fan and the like in the electronic equipment. And electronic devices such as a circuit board, a battery and the like are easy to generate heat during operation, and the heat of the heating device can be dissipated through a fan in order to ensure the normal operation of electronic equipment.
The fan can include motor, shell and impeller etc. and the impeller is installed in the shell, and the output of motor is connected with the impeller, and the motor is used for driving the impeller rotation. In order to ensure the functional capability of the core of the impeller in the fan, the fan is provided with a plurality of blades.
Fig. 1 is a perspective view of an impeller.
As shown in fig. 1, the impeller in the conventional fan may include a blade 30a and a hub, etc. The region 10a in fig. 1 is for mounting a hub, and a plurality of blades 30a are arranged at circumferential positions of the hub. In fig. 1, the area inside the dotted circle is the air inlet area, and the area between the dotted circle and the outer edge of the impeller is the working area.
However, each fan blade 30a is densely arranged, so that the flow field of the air inlet area is disordered, the noise is large, and the fan blades 30a occupy a part of the area of the air inlet. For example, if the thickness of each fan blade 30a is 0.15mm, it can be calculated that the total area of the plurality of fan blades 30a in the intake area is about 21.5% of the intake area, which corresponds to only 78.5% of the area in the intake area for intake air, resulting in a decrease in the area into which air actually flows, i.e., a decrease in the flow area, an increase in the flow resistance in the intake area, and a resistance to air flowing into the fan. Thus, the mute performance of the fan cannot be improved, and the air quantity of the fan cannot be improved.
In order to improve the mute performance of the fan and increase the air quantity of the fan, the embodiment of the application provides an impeller, which adopts the staggered layout of long and short blades, can improve the inlet flow of part of blades, and reduces the noise of an air inlet of the fan, thereby improving the mute performance of the fan. Meanwhile, the number of blades in the air inlet area is reduced, the flow area of the air inlet is increased, the resistance of the fan at the air inlet is reduced, and accordingly the air quantity of the fan is increased.
Fig. 2 is a top view of a first impeller provided in an embodiment of the present application.
As shown in fig. 2, in some embodiments, the first impeller may comprise: hub 10, first mute ring 20, first blade 30, second blade 40, etc. Wherein:
The hub 10 includes an outer cylindrical surface 101 formed around its rotational axis, the outer cylindrical surface 101 being understood as a side surface of the hub 10 remote from the rotational axis in a first direction (radial direction of the hub 10). The hub 10 is connected with an output shaft of a motor in the fan, a rotating shaft of the hub 10 is coaxial with the output shaft of the motor, and the hub 10 is used for bearing the first blades 30 and driving the first blades 30 to rotate by driving force of the motor. The first mute ring 20 is used for fixing the first blade 30 and the second blade 40, and simultaneously, increasing the strength and rigidity of the first blade 30 and the second blade 40.
The first blades 30 serve to increase the intake area of the intake area and the second blades 40 serve to increase the work capacity of the impeller. The radial length of the second vane 40 is smaller than the radial length of the first vane 30, and the first vane 30 may be a long vane and the second vane 40 may be a short vane, for example. The first blades 30 and the second blades 40 are staggered to form a staggered arrangement mode of long and short blades, so that the core working area of the impeller can have a preset number of blades required by the working capacity, and the working capacity of the impeller can not be reduced. And the arrangement of the blades is reduced in the air inlet area, so that the flow area of the air inlet of the fan is increased, the flow of the fan is increased, and the noise of the fan is reduced.
For ease of illustration of direction and size, a three-dimensional coordinate system is established based on the impeller, with the x-axis direction and the y-axis direction both being radial directions of the impeller, and the z-axis being the axis of rotation of the impeller, with the origin point located on the axis of rotation of the impeller, i.e., the center of circle of the hub 10.
The hub 10 may have a flat circular structure, and the rotation axis (i.e., z-axis) of the hub 10 is coaxial with the output shaft of the motor. Illustratively, a hub 10Diameter D of (2) 10 May be about 26.6 mm.
The first mute ring 20 is of an annular structure, the first mute ring 20 is disposed on the outer side of the hub 10, and the first mute ring 20 is coaxially disposed with the hub 10, such that an annular through hole region (not shown in the figure) is formed between the hub 10 and the first mute ring 20.
For convenience of a specific description of the plurality of first blades 30 and the plurality of second blades 40, a radial direction of the hub 10 will be hereinafter referred to as a first direction, and an axial direction of the hub 10 will be hereinafter referred to as a second direction. As used herein, "inner" refers to an end that is closer to the axis of rotation in a first direction, and "outer" refers to an end that is farther from the axis of rotation in the first direction.
The plurality of first blades 30 are distributed in an annular array outside the outer cylindrical surface 101 with the rotation axis of the hub 10 as the center of the annular array. It will be appreciated that the plurality of first blades 30 are disposed at circumferentially spaced positions of the hub 10, and that the plurality of first blades 30 may be disposed at equal intervals or may be disposed at unequal intervals. The plurality of first vanes 30 extend in a first direction.
In a first direction, each first blade 30 may comprise a first end 301 facing the hub 10 and a second end 302 facing away from the hub 10, the first end 301 being connected to the outer cylindrical surface 101 and the second end 302 being connected to the first mute ring 20. Wherein the distance between the first end 301 and the rotational axis of the hub 10 is greater than or equal to the diameter D of the hub 10 10 . Each of the first blades 30 may be a blade having a plurality of bent portions, and the number of bent portions and the degree of bending of the bent portions of each of the first blades 30 may be the same. The line connecting the first end 301 to the second end 302 of each first blade 30 is not collinear with the line connecting the first end 301 to the rotation axis, so that the wind can be scooped better and the wind volume can be increased when the fan motor is driven to rotate.
Similarly, the plurality of second blades 40 are distributed in an annular array outside the outer cylindrical surface 101 with the rotation axis of the hub 10 as the center of the annular array. It will be appreciated that the plurality of second blades 40 are disposed at circumferentially spaced locations of the hub 10, and that the plurality of second blades 40 may or may not be disposed at equal intervals. The length direction of the plurality of second blades 40 extends in the radial direction of the hub 10.
The plurality of second blades 40 are spaced apart from the hub 10 and are staggered from the plurality of first blades 30. Illustratively, one second vane 40 is disposed between two adjacent first vanes 30, and one first vane 30 is disposed between two adjacent second vanes 40. Thus, the number of first blades 30 is the same as the number of second blades 40; the total number of first blades 30 and second blades 40 is the same as the preset number of blades required for the work area to meet the functional capacity. Illustratively, if the preset number of blades required to meet the functional force is seventy-four, then the first blade 30 is thirty-seven and the second blade 40 is thirty-seven.
In the first direction, each second blade 40 may comprise a third end 401 towards the hub 10 and a fourth end 402 away from the hub 10, the third end 401 being located between the hub 10 and the first ring 20, and the third end 401 being at a first distance from the outer cylindrical surface 101 of the hub 10, the fourth end 402 being connected with the first ring 20. It will be appreciated that one end of the plurality of second blades 40 is connected to the first mute ring 20, and is fixed by the first mute ring 20, and the other end of the plurality of second blades 40 is suspended and faces the hub 10. The region in which both the first blade 30 and the second blade 40 are present is a work area, and the region in which only the first blade 30 is present is an air intake region.
The number of the first blades 30 is based on the requirement of air intake, and the functional force is not required to be considered. That is, the number of the first blades 30 may be reduced as much as possible in case of satisfying the self-strength of the impeller. The second blades 40 may increase the total number of blades in the working area, which may in turn increase the working capacity of the impeller.
In one implementation, the number of second blades 40 is n times the number of first blades 30; there are n second blades 40 between adjacent two first blades 30. Wherein n is a positive integer greater than or equal to 1. Illustratively, at n=1, the intake area has thirty-seven first blades 30, and the work area has seventy-four blade sets (thirty-seven first blades 30 and thirty-seven second blades 40).
In order to increase the flow area of the air inlet, adjacent blades are not contacted. In the air inlet area, two adjacent blades are first blades 30, and a first interval distance is reserved between the two adjacent first blades 30; in the working area, two adjacent blades are a first blade 30 and a second blade 40, and a second interval is arranged between the adjacent first blade 30 and the second blade 40. To better achieve scooping, the first separation distance may be greater than the second separation distance.
It will be appreciated that to further increase the amount of air intake, the number of first vanes 30 may be further reduced such that the first separation distance between two adjacent first vanes 30 increases. The smaller the number of the first blades 30, the larger the first separation distance, the larger the flow area of the air inlet, the larger the air inlet quantity, and the more noise is reduced. When the number of the first blades 30 is small, a plurality of second blades 40 (not shown) may be provided between adjacent two of the first blades 30 to function as an impeller without being lowered. For example, two second blades 40 are provided between two adjacent first blades 30, three second blades 40 are provided between two adjacent first blades 30, and so on.
In one implementation, the leaf surfaces of the plurality of first vanes 30 are parallel to the z-axis and the leaf surfaces of the plurality of second vanes 40 are parallel to the z-axis. When the impeller rotates, the air inflow direction is the z-axis direction, the blade group (the first blade 30 and the second blade 40) is parallel to the air inlet direction, and air can flow into the upper surface and the lower surface of the impeller in the z-axis direction, namely, bidirectional air inlet is realized. Meanwhile, the first blade 30 and the second blade 40 can be fully contacted with the airflow, so that the contact area between the blade group and the airflow is increased, the wind scooping area can be better, and the work doing area can be better.
Fig. 3 is a perspective view of a first impeller provided in an embodiment of the present application.
As shown in fig. 3, in some embodiments, the plurality of first and second blades 30 and 40 are each connected with the first connection surface 201 of the first mute ring 20 to increase the connection width in the radial direction, thereby more stably fixing the second and first blades 40 and 30.
In one implementation, the first mute ring 20 is disposed on one side of the plurality of first blades 30 and the plurality of second blades 40 in the second direction. The first mute ring 20 may include a first connection surface 201, an upper surface 202, and an outer ring surface 203, etc., the first connection surface 201 being a surface facing the plurality of first blades 30 and the plurality of second blades 40, the upper surface 202 being a surface remote from the plurality of first blades 30 and the plurality of second blades 40, and the outer ring surface 203 being an outer side wall surface for connecting the first connection surface 201 and the upper surface 202. It will be appreciated that the first mute ring 20 may further include an inner annular surface (not shown), which is another outer side wall surface for connecting the first connecting surface 201 and the upper surface 202. The inner annulus is adjacent the hub 10 and the outer annulus 203 is remote from the hub 10.
The plurality of first blades 30 and the plurality of second blades 40 are respectively connected to the first connection surface 201. In this way, the first mute ring 20 and the blade sets (the first blade 30 and the second blade 40) are distributed along the z-axis, so that the strength and stability of the impeller can be improved, and the deformation of the blade sets when the impeller rotates can be reduced.
Fig. 4 is a side view of a first impeller provided in an embodiment of the present application.
As shown in fig. 4, and in conjunction with what is shown in fig. 2, in some embodiments, the faces of the plurality of first vanes 30 and the faces of the plurality of second vanes 40 may be perpendicular to the first connection face 201.
Wherein, along the first direction, the first mute ring 20 has a first radial length L 20 In the second direction, the first mute ring 20 has a first axial height H 20 . First radial length L of first mute ring 20 20 May be the impeller diameter D Leaves of the plant 1% to 50%, for example: impeller diameter D Leaves of the plant 10% of (C). First radial length L of first mute ring 20 20 Is selected to meet the strength requirements and is not deformed into a substantially defined condition upon rotation. First axial height H of first mute ring 20 20 May be about 0.3 mm. First axial height H of first mute ring 20 under the condition of meeting the requirements of injection molding and strength 20 The smaller the better.
Optionally, a first radial length L 20 Greater than the first axial height H 20 First radial length L 20 Less than the radial length L of the second vane 40 in the first direction 40 . In this way, the first mute ring 20 may be made to have a certain width to improve the stability of fixing the first blade 30 and the second blade 40. To further improve the fixing effect, the first radial length L 20 May also be greater than or equal to the radial length L of the second vane 40 40 . While in other embodiments, the first radial length L 20 May also be smaller to form a first mute ring 20 having a bar-shaped configuration.
First radial length L of first mute ring 20 20 Can be defined by the inner diameter D of the first mute ring 20 20 in And outer diameter D 20 outsides Determining the radial length L of the second blade 40 40 An inner diameter D of an area surrounded by the plurality of second blades 40 40 in And outer diameter D 40 outsides And (5) determining. Illustratively, the inner diameter D of the first mute ring 20 20 in An outer diameter D smaller than an area surrounded by the plurality of first blades 30 30 outsides Inner diameter D of first mute ring 20 20 in Greater than or equal to the inner diameter D of the area surrounded by the plurality of second blades 40 40 in Wherein the inner diameter D of the first mute ring 20 20 in The diameter of the inner ring where the inner ring surface is located. While in other embodiments, the inner diameter D of the first mute ring 20 20 in May be greater than the inner diameter D of the area surrounded by the plurality of second vanes 40 40 in 。
Outer diameter D of first mute ring 20 20 outsides The outer annulus 203 of the first mute ring 20 may be the diameter of the outer annulus 203, on the same circle as the second end 302 of the first blade 30 and the fourth end 402 of the second blade 40. Wherein the outer ring surface 203 is located at an end of the first mute ring 20 away from the rotation axis in the first direction. Thus, the outer diameter D of the first mute ring 20 20 outsides And an outer diameter D of an area surrounded by the plurality of first blades 30 30 outsides Outer diameter D of the area surrounded by the plurality of second blades 40 40 outsides Equal, i.e. equivalent to the diameter D of the impeller Leaves of the plant To achieve the best fixing effect and scooping effect. Illustratively, at the diameter D of the impeller Leaves of the plant When the diameter is 54mm, D 30 outsides ＝D 20 outsides ＝D 40 outsides ＝D Leaves of the plant ＝54mm。
It will be appreciated that the first vane 30 is located between two adjacent second vanes 40, and that the second vanes 40 are located between two adjacent first vanes 30. The axial overall height H of the first 30 and second 40 blades 30 /H 40 Can be the same, regular wind scooping can be performed, and noise is avoided while the air quantity is improved. Wherein the axial total height of the blade group refers to the total height of the blade group in the z-axis direction. Exemplary, an axial overall height H of the first and second blades 30, 40 30 /H 40 The thicknesses of the first blade 30 and the second blade 40 may be about 3.7mm, and the thicknesses may be about 0.15mm, respectively, and the thicknesses may be the dimensions in the circumferential direction of the hub 10.
In some embodiments, each second blade 40, each first blade 30, and first mute ring 20 may be integrally injection molded, and the materials may be plastic.
According to the first impeller provided by the embodiment of the application, each first blade 30 is fixed between the hub 10 and the first mute ring 20, and each second blade 40 is fixed on the first mute ring 20, so that the strength of the impeller is increased, and deformation of each long second blade during rotation of the impeller is avoided. The first blades 30 and the second blades 40 are alternately arranged at intervals and distributed in an annular array outside the outer cylindrical surface 101 of the hub 10. The number of first blades 30 may be reduced as much as possible to increase the flow area of the intake area to increase the flow rate of the fan while reducing the noise of the fan. Meanwhile, a greater number of second blades 40 are provided in the working area so that the total number of blades in the working area is equal to the preset number required to satisfy the working capacity of the impeller, so as not to reduce the working capacity of the impeller.
Fig. 5 is a top view of a second impeller provided in an embodiment of the present application. Fig. 6 is a perspective view of a second impeller provided in an embodiment of the present application.
As shown in fig. 5 and 6, in some embodiments, the second impeller is different from the first impeller in that the connection position between the first mute ring 20 and the blade set (the first blade 30 and the second blade 40) is different, and the rest of the structures can refer to the content of the first impeller, which is not repeated herein.
In the second impeller, the first mute ring 20 is provided in the middle of the plurality of first blades 30 and the plurality of second blades 40 in the second direction (z-axis direction). It will be appreciated that the first vane 30 and the first mute ring 20 are fixedly connected to the middle part of the axial total height of the first vane 30; the second blade 40 and the first mute ring 20 are fixedly connected to the middle part of the axial total height of the second blade 40. In this way, the strength of the blade group of the whole impeller can be larger, and the deformation of the blade group can be smaller.
The first mute ring 20 can divide the blade set (the first blade 30 and the second blade 40) into an upper layer and a lower layer, so that the outgoing wind can be forcedly divided into an upper part and a lower part, mixing is prevented, noise is further reduced, and the outgoing wind is more uniform.
Fig. 7 is a side view of a second impeller provided in an embodiment of the present application.
As shown in fig. 7, in some embodiments, the first vane 30 has a second axial height H in the second direction on one side of the first mute ring 20 30-1 Illustratively, the first vane 30 has a second axial height H on the upper surface 202 side of the first mute ring 20 30-1 . Wherein the second axial height H 30-1 Is the axial overall height H of the first vane 30 30 10 to 90 percent of the total weight of the product.
It will be appreciated that the location of the connection of the first mute ring 20 to the vane pack (first vane 30 and second vane 40) may be between 10% and 90% of the total axial height of the vane pack. The first mute ring 20 is illustratively located at the axial overall height (H 30 /H 40 ) 50% of the positions of (c). The first mute ring 20 can divide the blade set into an upper layer and a lower layer, so that the outgoing wind can be forcedly divided into an upper portion and a lower portion, mixing is prevented, noise is further reduced, and the outgoing wind is more uniform.
According to the second impeller provided by the embodiment of the application, on the basis that the flow area of the air inlet area is increased by reducing the number of the first blades 30 and arranging the second blades 40, the flow of the fan is increased, the noise of the fan is reduced, and the acting capacity of the impeller is not reduced, the blade group (the first blades 30 and the second blades 40) can be divided into an upper layer and a lower layer by using the first mute ring 20 fixed in the middle of the axial total height. Therefore, the discharged wind can be forcedly divided into an upper part and a lower part, mixing is prevented, noise is further reduced, and the air outlet is more uniform.
Fig. 8 is a top view of a third impeller provided in an embodiment of the present application.
As shown in fig. 8, in some embodiments, the third impeller differs from the first impeller and the second impeller in the relative positional relationship of the first mute ring 20 and the first blade 30 and the second blade 40. The other structures can refer to the contents of the first impeller and the second impeller, and are not repeated herein.
In the first impeller, the third end 401 of the plurality of second blades 40 is suspended relative to the first ring 20 and faces the hub 10, and the fourth end 402 is fixed to the first ring 20 and away from the hub 10. In the third impeller, the third ends 401 of the second plurality of blades 40 are connected to the first mute ring 20, and the fourth ends 402 are suspended opposite the hub 10 with respect to the first mute ring 20.
The inner ring of the first mute ring 20 may be located on the same circle as the third end 401, with the outer ring of the first mute ring 20 being located between the third end 401 and the fourth end 402. Outer diameter D of first mute ring 20 20 outsides The first mute ring 20 occupies as little area as possible to work the working area, so that the blade group of the impeller and the working capacity of the air can be improved. Outer diameter D of the area surrounded by the plurality of first vanes 30 30 outsides Equal to the outer diameter D of the area surrounded by the plurality of second blades 40 40 outsides 。
The first mute ring 20 is connected to a second position B of the plurality of first vanes 30 and a third end 401 of the plurality of second vanes 40, respectively, the second position being located between the first end 301 and the second end 302 of the first vanes 30. In the first direction (radial direction), the second position B has a third distance L from the outer cylindrical surface 101 of the hub 10 3 。
When the third end 401 is not protruded from the inner annular surface of the first mute ring 20 in the direction of the hub 10, i.e. the third end and the inner annular surface are flush, a third distance L 3 Equal to the first distance L between the third end 401 and the outer cylindrical surface 101 1 I.e. the inner diameter D of the first mute ring 20 20 in Can be equal to the inner diameter D of the area surrounded by the second blade 40 40 in Equal. When the third end 401 protrudes from the inner ring surface of the first mute ring 20 toward the hub 10, a third distance L 3 Greater than a first distance L between the third end 401 and the outer cylindrical surface 101 1 I.e. the inner diameter D of the first mute ring 20 20 in An inner diameter D smaller than the area surrounded by the second blade 40 40 in . When the third end 401 is spaced apart from the inner annular surface of the first mute ring 20 by a certain distance, a third distance L 3 Less than the first distance L between the third end 401 and the outer cylindrical surface 101 1 I.e. the inner diameter D of the first mute ring 20 20 in An inner diameter D greater than the area enclosed by the second vane 40 40 in 。
At a diameter D of the impeller Leaves of the plant Unchanged, i.e. D 30 outsides ＝D 40 outsides ＝D Leaves of the plant The size of the first mute ring 20 of the third impeller may be smaller than the size of the first mute ring 20 in the first impeller. Outer diameter D of first silent ring 20 of third impeller 20 outsides Smaller than the diameter D of the impeller Leaves of the plant Illustratively, the outer diameter D of the first mute ring 20 20 outsides May be the diameter D of the impeller Leaves of the plant About 80%. Inner diameter D of first mute ring 20 20 in May be the diameter D of the impeller Leaves of the plant About 70%.
Fig. 9 is a perspective view of a third impeller provided in an embodiment of the present application.
As shown in fig. 9, in some embodiments, the fixed positions of the first mute ring 20 and the blade group (the first blade 30 and the second blade 40) of the third impeller may refer to what is shown by the second impeller, that is, along the second direction (the z-axis direction), where the first mute ring 20 is disposed in the middle of the plurality of first blades 30 and the plurality of second blades 40. It will be appreciated that the first vane 30 and the first mute ring 20 are fixedly connected to the middle part of the axial total height of the first vane 30; the second blade 40 and the first mute ring 20 are fixedly connected to the middle part of the axial total height of the second blade 40. In this way, the strength of the blade group of the whole impeller can be larger, and the deformation of the blade group can be smaller.
Fig. 10 is a side view of a third impeller provided in an embodiment of the present application.
As shown in fig. 10, in some embodiments, the first vane 30 has a second axial height H on one side of the first mute ring 20 in the second direction 30-1 Illustratively, the first vane 30 has a second axial height H on the upper surface 202 side of the first mute ring 20 30-1 . Wherein the second axial height H 30-1 Is the axial overall height H of the first vane 30 30 10 to 90 percent of the total weight of the product.
It will be appreciated that the location of connection of the third first mute ring 20 to the vane pack may be between 10% and 90% of the total axial height of the vane pack. The first mute ring 20 is illustratively located at the axial overall height (H 30 /H 40 ) 50% of the positions of (c). The first mute ring 20 can divide the blade set (the first blade 30 and the second blade 40) into an upper layer and a lower layer, so that the outgoing wind can be forcedly divided into an upper part and a lower part, mixing is prevented, noise is further reduced, and the outgoing wind is more uniform.
In the third impeller provided in this embodiment of the present application, the first mute ring 20 may occupy as little height of the blade set as possible, or the first mute ring 20 reduces the working area occupied by the core of the blade, so that the working capacities of the blade set and the air of the impeller may be improved. Meanwhile, the first and second blades 30 and 40 are fixed at the middle position of the first mute ring 20 in the radial direction, so that the strength of the blade group can be increased, and the deformation amount of the fan during rotation can be reduced.
Fig. 11 is a top view of a fourth impeller provided in an embodiment of the present application. Fig. 12 is a perspective view of a fourth impeller provided in an embodiment of the present application.
As shown in fig. 11 and 12, in some embodiments, the fourth impeller is different from the third impeller in that the connection position between the first mute ring 20 and the blade set (the first blade 30 and the second blade 40) is different, and the rest of the structures can refer to the content of the third impeller, which is not repeated herein.
In the fourth impeller, the first mute ring 20 and the blade group (the first blade 30 and the second blade 40) are distributed along the z-axis, and the second end 302 of the first blade 30 and the first mute ring 20 are exemplarily fixedly connected to one side of the axial height (z-axis) of the first blade 30; the third end 401 of the second blade 40 is fixedly connected to the first mute ring 20 at one side of the axial height (z-axis) of the second blade 40.
Outer diameter D of first mute ring 20 20 outsides May be the outer diameter D of the impeller Leaves of the plant About 80%, and the outer diameter D of the first mute ring 20 20 outsides An inner diameter D greater than the area enclosed by the second vane 40 40 in . Inner diameter D of first mute ring 20 20 in Is the outer diameter D of the impeller Leaves of the plant About 50% of the total weight of the steel sheet is greater when the steel sheet meets the structural strength requirement.
According to the fourth impeller provided by the embodiment of the application, the first mute ring 20 is fixedly connected with the blade group through the upper structure and the lower structure, and the first mute ring 20 can occupy the height of the blade group as little as possible, or the first mute ring 20 reduces the position occupying the working area of the blade core, so that the working capacities of the blade group and the air of the impeller can be improved. Meanwhile, the first and second blades 30 and 40 are fixed at the middle position of the first mute ring 20 in the radial direction, so that the strength of the blade group can be increased, and the deformation amount of the fan during rotation can be reduced. Simultaneously, fix the top at the blade group with first silence ring 20, conveniently mould plastics, reduce injection mold cost.
Fig. 13 is a top view of a fifth impeller provided in an embodiment of the present application.
In some embodiments, as shown in fig. 13, the fifth impeller is different from the first impeller in terms of the number of mute rings, and the rest of the structures can refer to the content of the first impeller, which is not described herein.
In the fifth impeller, the fifth impeller may include: hub 10, first mute ring 20, first blade 30, second blade 40, second mute ring 50, etc. The plurality of first blades 30 and the plurality of second blades 40 are fixed by the two mute rings, so that the strength of the impeller can be further increased, and the deformation of the blade group during the rotation of the impeller is avoided.
The second mute ring 50 and the first mute ring 20 have annular structures with different sizes, and the diameter D of the second mute ring 50 is equal to 50 Straight less than the first mute ring 20Diameter D 20 When the second mute ring 50 is disposed between the first mute ring 20 and the hub 10, the second mute ring 50 is disposed coaxially with the hub 10. Exemplary, diameter D of second mute ring 50 50 Greater than the outer diameter D of the hub 10 10 。
The fixing of the first blade 30 and the second blade 40 is achieved through the two mute rings, so that an air inlet area and a working area of the impeller can be better divided, and the radial length of the first blade and the radial length of the second blade can be better selected, so that the impeller with the optimal shape is obtained.
The first mute ring 20 is located on the outside and is connected to the second ends 302 of the plurality of first blades 30 and the fourth ends 402 of the plurality of second blades 40, respectively. The second mute ring 50 is located inside, and when the axial height of the first blade 30 is the same as the axial height of the second blade 40, the second mute ring 50 is connected to the third ends 401 of the plurality of second blades 40, and the second mute ring 50 is connected to the first positions a of the plurality of first blades 30. The first position a is located between the first end 301 and the second end 302 of the first blade 30. When the axial height of the first blade 30 is different from the axial height of the second blade 40, the second mute ring 50 may be connected only with the third end 401 of the second blade 40, not with the first position a of the first blade 30.
Wherein the diameter D of the second mute ring 50 50 Can be equal to the inner diameter D of the area surrounded by the second blade 40 40 in Equal, or diameter D of second mute ring 50 50 in An inner diameter D smaller than the area surrounded by the second blade 40 40 in 。
In the fifth impeller, the first mute ring 20 and the second mute ring 50 replace the first mute ring 20 in the first impeller, and the two mute rings fix the blade group, so that the strength and stability of the impeller can be improved, and the deformation of the blade group during the rotation of the impeller is avoided. Thus, the radial length of the first and second ring 20, 50 in the fifth impeller may be less than the first radial length L of the first ring 20 in the first impeller 20 。
Radial length L of first mute ring 20 in first impeller 20 Diameter D of impeller Leaves of the plant 1% to50%; while the radial length L of the first and second ring 20, 50 in the fifth impeller 20 Can be equal and can be about 1mm, and the radial length L can be equal when the strength and the injection molding requirement are met 20 The smaller the better. Illustratively, in the radial direction length L 20 Smaller, a first mute ring 20 having a bar-shaped structure may be formed.
Diameter D of impeller Leaves of the plant Can be equal to the diameter D of the first mute ring 20 20 Equal, diameter D of the first mute ring 20 20 Can be equal to the outer diameter D of the area surrounded by the plurality of first vanes 30 30 outsides Outer diameter D of the area surrounded by the plurality of second blades 40 40 outsides Etc., exemplary, D 20 ＝D 30 outsides ＝D 40 outsides ＝D Leaves of the plant 。
Illustratively, the diameter D of the hub 10 Leaves of the plant May be 26.6mm, diameter D of the second mute ring 50 50 May be 40mm, diameter D of the first mute ring 20 30 May be 54mm.
Diameter D of the first mute ring 20 20 And diameter D of the second mute ring 50 50 May be determined based on the radial length of the first vane 30 and the radial length of the second vane 40. The sum of the radial length of the first blades 30 and the radius of the hub 10 may be the radius of the first mute ring 20, thereby determining the diameter D of the first mute ring 20 20 The method comprises the steps of carrying out a first treatment on the surface of the The radial length of the second vane 40 may determine the radial distance W between the second mute ring 50 and the first mute ring 20 0 Further determining the diameter D of the second mute ring 50 50 。
In some embodiments, the first mute ring 20 and the second mute ring 50 may each have an annular cylindrical structure, so that the cross-sectional shape of the ring body is circular, and the diameter may be 1mm. Thus, the wind resistance can be reduced and the air intake can be improved.
In some embodiments, each second blade 40, each first blade 30, first mute ring 20, and second mute ring 50 may be integrally injection molded, and the materials may be plastic.
Fig. 14 is a perspective view of a fifth impeller provided in an embodiment of the present application.
As shown in fig. 14, in some embodiments, the fixed connection manner of the mute ring set (the first mute ring 20 and the second mute ring 50) and the blade set in the fifth impeller may refer to the fixed connection manner of the first mute ring 20 and the blade set in the first impeller.
When the mute ring sets and the vane sets are distributed along the z-axis, the second mute ring 50 is disposed at one side of the plurality of first vanes 30 and the plurality of second vanes 40 along the second direction, and the second mute ring 50 may be positioned at the same location as the first mute ring 20. Illustratively, the second mute ring 50 and the first mute ring 20 are each disposed on the same side of the plurality of first vanes 30 and the plurality of second vanes 40.
The second mute ring 50 includes a third connection surface 501 facing the plurality of first blades 30 and the plurality of second blades 40, the second positions B of the plurality of first blades 30 and the third ends 401 of the plurality of second blades 40 being respectively connected to the third connection surface 501, the second ends 302 of the plurality of first blades 30 and the fourth ends 402 of the plurality of second blades 40 being respectively connected to the first connection surface 201 of the first mute ring 20, the first ends 301 of the plurality of first blades 30 being connected to the outer cylindrical surface 101 of the hub 10. It will be appreciated that the location where the first mute ring 20 is fixedly connected to the vane pack over the axial overall height may be the same as the location where the second mute ring 50 is fixedly connected to the vane pack over the axial overall height. Therefore, the strength and stability of the impeller can be improved, and the deformation of the blade group during rotation of the impeller is reduced.
Fig. 15 is a side view of a fifth impeller provided in an embodiment of the present application.
As shown in FIG. 15, in some embodiments, the axial heights H of the first and second mute rings 20, 50 are such that the mute ring sets and blade sets are distributed along the z-axis 20 /H 50 Equal, and can be 0.3mm, the smaller the better when meeting the strength and injection molding requirements. The axial overall height H of the first 30 and second 40 blades 30 /H 40 Equal, and may be about 3.7 mm. The outer annulus 203 of the first mute ring 20 is on the same circle as the second end 302 of the first blade 30 and the fourth end 402 of the second blade 40, i.e. the outer annulus 203 of the first mute ring 20 is aligned with the second end 302 of the first blade 30 and the fourth end 402 of the second blade 40.
In some embodiments, the fixed connection between the mute ring set (the first mute ring 20 and the second mute ring 50) and the blade set in the fifth impeller may also refer to the fixed connection between the first mute ring 20 and the blade set in the second impeller. I.e., in the second direction (z-axis direction), the second mute ring 50 is provided at the middle portions of the plurality of first blades 30 and the plurality of second blades 40; the first vane 30 has a third axial height on one side of the second mute ring 50 in the second direction; wherein the third axial height is 10% -90% of the total axial height of the first blade 30.
It will be appreciated that the location of the connection of the mute ring set to the vane set (first vane 30 and second vane 40) may be between 10% and 90% of the total axial height of the vane set. The related structures and structural views may refer to the corresponding contents of the second impeller and the fifth impeller, which are not described herein.
In some embodiments, in the fifth impeller, the first mute ring 20 and the blade set may be fixedly connected in a different manner than the second mute ring 50 and the blade set. Illustratively, the first mute ring 20 and the blade set are disposed in a distributed manner along the z-axis, and the second mute ring 50 is disposed in the middle of the axial overall height of the blade set. Alternatively, the first mute ring 20 is disposed in the middle of the axial overall height of the blade set, and the second mute ring 50 and the blade set are distributed along the z-axis.
In the fifth impeller provided in this embodiment, each first blade 30 is sequentially fixed through the hub 10, the second mute ring 50 and the first mute ring 20, and each second blade 40 is fixed between the first mute ring 20 and the second mute ring 50. The blade group is fixed through the first mute ring 20 and the second mute ring 50, so that the strength of the impeller can be increased, and the deformation of each long and short blade during the rotation of the impeller is avoided. The first blades 30 and the second blades 40 are alternately arranged at intervals and distributed in an annular array outside the outer cylindrical surface 101 of the hub 10. The number of first blades 30 may be reduced as much as possible to increase the flow area of the intake area formed by the first blades 30 to increase the flow rate of the fan while reducing the noise of the fan. Meanwhile, a greater number of second blades 40 are disposed in the working area coaxially outside the air intake area, so that the sum of the number of second blades 40 and the number of first blades 30 in the working area is equal to the preset number required to satisfy the working capacity of the impeller, so as not to reduce the working capacity of the impeller.
Fig. 16 is a first fan performance graph provided by an embodiment of the present application.
As shown in fig. 16, in some embodiments, the fan performance of the fan scheme using the first impeller to the fifth impeller is tested with the conventional fan blade scheme, and when testing, test noise is set first, and the test noise is kept at 38 dB; the voltage corresponding to 38dB is again selected, for example, the voltage may be 5V to test at a constant voltage (5V) at 38 dB. The voltage and the noise are in nonlinear corresponding relation, and different voltages have different noises.
In the testing process, the air quantity of the fan is changed, the corresponding air pressure value is tested, and a first fan Performance (PQ) curve can be obtained based on the corresponding relation between different air quantities and air pressures.
Because the fan is influenced by impedance and environment when rotating, the working range of the fan is between 20 and 80 percent of the maximum air quantity. Then it can be seen from the test result that the maximum air volume of the fan is about 2.7CFM, and the working range of the fan is between (0.54-2) CFM. It can be seen that in this operating range, the fan PQ of the fan scheme employing long and short bladed impellers is higher than the PQ of normal blades.
The first to fifth impellers provided in the foregoing embodiments adopt a staggered arrangement of long and short blades, so that the total number of blades and the blade form of the core working area of the impeller can be increased, and the working capacity of the impeller is not reduced. By reducing the number of blades in the air inlet area, the vortex noise of the air inlet is reduced, so that the noise of the fan is reduced; on the premise of not changing the size of the fan and not affecting the performance of the fan, the noise of the fan is reduced, so that the mute performance of the fan is improved and the air quantity of the fan is increased.
The embodiment of the application also provides a sixth impeller, which adopts a mode of short blades and a tray with through holes, wherein the blades are not arranged in the air inlet area, only the blades in the working area are reserved, the inlet flow of part of the blades can be improved, and the noise of the air inlet of the fan is reduced. Meanwhile, blades are not arranged in the air inlet area, the through flow area of the air inlet is increased through the through flow holes formed by the tray, and then the resistance of the fan at the air inlet is reduced, and the air quantity of the fan is increased.
Fig. 17 is a top view of a sixth impeller provided in an embodiment of the present application.
As shown in fig. 17, in some embodiments, the sixth impeller may comprise: hub 10, tray 60, blades 70, etc. Wherein:
the hub 10 may be the hub 10 used for the first to fifth impellers provided in the foregoing embodiments, and the blades 70 may be the first blades 30 or the second blades 40 of the first to fifth impellers provided in the foregoing embodiments. The tray 60 is used for bearing the hub 10, and for fixing the blades 70 by the outer side position of the tray 60, the tray 60 realizes the increase of the flow area of the air inlet area of the impeller, and the blades 70 fixed at the outermost side realize the working capacity of the impeller.
The tray 60 may include an inner tray 601, an outer tray 602, at least one bracket 603, and the like. The inner support 601 may have a plate-like circular structure, the hub 10 is fixed on the inner support 601, the rotation axis of the hub 10 is the same as the rotation axis of the inner support 601, and the outer diameter D of the inner support 601 601 outside May be greater than or equal to the diameter D of the hub 10 10 。
The outer support 602 has an annular structure, and the inner diameter D of the outer support 602 602 inside Greater than the outer diameter D of the inner support 601 601 outside . The outer support member 602 is sleeved on the outer side of the inner support member 601, the outer support member 602 is the same as the rotation axis of the inner support member 601, and an annular through hole area (not shown in the figure) is formed between the inner support member 601 and the outer support member 602. The annular through hole area is used for forming an air inlet area so as to improve the flow area.
The at least one bracket 603 may be the same size, and the at least one bracket 603 is connected between the inner and outer brackets 601 and 602 at intervals to form at least one through-flow hole 604 between the inner and outer brackets 601 and 602, the through-flow hole 604 being used to form an air intake area, increasing the through-flow area. At least one of the brackets 603 is disposed along a radial direction of the inner support 601 to form a radial bracket set, and illustratively, at least one of the brackets 603 is disposed along an x-axis direction and a y-axis direction.
At least one bracket 603 is disposed in the annular through hole area at unequal intervals, and two ends of each bracket 603 are respectively connected between the inner support 601 and the outer support 602 to divide the annular through hole area between the inner support 601 and the outer support 602 into at least one through hole 604 with different areas. The tray 60 of the impeller is provided with flow holes 604, so that the inlet air flow on the upper side and the lower side of the impeller can be communicated, and the acting capacity of the impeller blades is maximized.
The through holes 604 are opened on the tray 60, and the through holes 604 can be used for communicating air flows of air inlets on the upper side and the lower side of the tray 60 along the z-axis direction, namely, air flows of air inlets on the upper side and the lower side of the fan. When air intake on one side of the fan is blocked, air intake on the other side can fill the area where the blades 70 are positioned through the tray 60, so that the work doing capability of the blades 70 is prevented from being reduced.
Circumferential width W of bracket 603 603 And the number determines the number and area (radial width and circumferential length) of the through-holes 604 opened in the tray 60, wherein the circumferential direction can be understood as an annular array direction centered on the rotation axis of the hub 10. Illustratively, the circumferential width W of the bracket 603 603 The thickness may be about 3mm, and the smaller the thickness is, the better the strength of the tray 60 is. The distance between two adjacent brackets 603 determines the circumferential length of the through-holes 604, the radial length of the brackets 603 determines the radial width of the through-holes 604, and the distance between the diameter of the hub 10 and the inner ring side of the outer carrier 602 determines the radial width of the through-holes 604. The radial width of the through-flow holes 604 may be represented by the inner diameter of the through-flow holes 604, the diameter D of the hub 10 10 The size determines the inner diameter of the through-flow holes 604. As an example, the inner diameter of the through-flow holes 604 may be the diameter D of the hub 10 10 The smaller the value, the better the strength is, by increasing the size by about 5 mm.
Fig. 18 is a schematic view illustrating an included angle formed by a sixth impeller according to an embodiment of the present application.
As shown in fig. 18, in some embodiments, at least one of the brackets 603 is disposed at non-equidistant intervals within the annular through-hole region, and each bracket 603 is disposed along the radial direction of the inner support 601 such that an included angle is formed between two adjacent brackets 603. The apexes of the respective angles are located at the center of the inner support 601 (or at the same point on the rotation axis of the hub 10), and the angles of the respective angles formed on the tray 60 are not equal. In this way, the through-holes 604 formed in the tray 60 may be provided with a non-uniform distribution feature in the circumferential direction, i.e., the through-holes 604 may be circumferentially distributed about the z-axis and may be different in size.
The number of the brackets 603 may be five to eleven, or less than five or more than eleven brackets 603 may be provided as required. Taking the example of seven brackets 603 disposed between the inner bracket 601 and the outer bracket 602 as an illustration, the seven brackets 603 may form seven angles and seven through holes 604.
Exemplary, the first and second brackets 6031, 6032 may form a first included angle θ 1 And a first through-hole 6041, the second bracket 6032 and the third bracket 6033 can form a second included angle theta 2 And a second through-flow hole 6042, the third bracket 6033 and the fourth bracket 6034 may form a third included angle θ 3 And a third flow-through hole 6043, a fourth angle θ can be formed between the fourth bracket 6034 and the fifth bracket 6035 4 And a fourth flow hole 6044, the fifth bracket 6035 and the sixth bracket 6036 may form a fifth included angle θ 5 And a fifth through-hole 6045, the sixth bracket 6036 and the seventh bracket 6037 can form a sixth included angle theta 6 And a sixth through-hole 6046, the seventh support 6037 and the first support 6031 can form a seventh included angle θ 7 And a seventh through-hole 6047.
In order to enable the impeller to meet the dynamic balance condition, noise improvement and structural damage caused by gravity center deviation during operation of the impeller are avoided, the angles of all included angles are required to be between 0 and 2 pi, and the total angle of all included angles is 2 pi. And the sum of cosine values of at least one included angle is 0, and the sum of sine values of at least one included angle is 0.
By way of example only, and not by way of limitation,
where i is the number of included angles, θ is the angle of included angle, and Z is the total number of included angles formed by each bracket 603 and is also the number of openings.
Note that, the included angle θ formed between the adjacent brackets 603 i The non-uniform distribution scheme (θ 1 -θ 7 ) The range of variation of the included angle is 50% -70% of (360/7) at maximum, relative to the uniformly distributed scheme (360/7). If the fluctuation range is too large, the distance between the plurality of brackets 603 is too short, and the area of the partial through-flow holes 604 is too small, thereby affecting the flow effect. However, the lack of fluctuation of the included angle results in insignificant non-uniformity of the through-holes 604 and insufficient improvement of the discrete noise.
In some embodiments, when determining the included angle, one of the brackets 603 may be used as a reference, and a plurality of included angles may be formed between each of the other brackets 603 and the reference bracket 603. Then, each included angle satisfies the following relationship:
0＝θ 1 <θ 2 <θ 3 <…<θ z-1 <θ z <2π。
in some embodiments, the brackets 603 may also be disposed in the annular through hole area at equal intervals, so that the angles formed by two adjacent brackets 603 are equal, that is, the brackets 603 are uniformly distributed. The effect on reducing fan noise may be different for the uniform distribution scheme and the non-uniform distribution scheme.
Each blade 70 on the outside of the outer carrier 602 is connected to the hub 10, and a plurality of brackets 603 are reserved for connecting the hub 10 to the outer blade 70 when the flow holes 604 are opened in the tray 60. However, when the fan rotates, the support 603 is driven to rotate synchronously, and the high-speed rotating support 603 slides through the airflow passing through the through holes 604, so that corresponding pneumatic noise is generated. If these brackets 603 are evenly distributed, a discrete noise f will be formed at a particular frequency:
Where n is the fan speed, Z is the number of through holes 604, and i is the harmonic number.
Concentration of acoustic energy also occurs at the frequency multiplication of the band pass filter, creating peaks in the frequency spectrum. The peak of the discrete noise may increase the total sound pressure level of the noise or give a sharp sense of a specific frequency to the person, and the sound quality may be deteriorated.
The uneven distribution design of the brackets 603 can destroy the regularity of the air flow impacted by the brackets 603, so as to inhibit the sound energy concentration of the band-pass filter and the frequency multiplication thereof in the superposition process of sound sources of different brackets 603, further weaken the discrete noise peak value on the corresponding frequency, and realize the improvement of sound quality while reducing noise.
The embodiment of the application adopts a non-uniform distribution mode, maximizes the non-uniformity degree of the bracket 603 while not damaging the flow capacity of the through holes 604, and has lower noise and better sound quality when the bracket 603 is arranged relatively uniformly.
Referring again to fig. 17, the plurality of blades 70 are distributed in an annular array on the outside of the inner carrier 601 with the rotation axis of the inner carrier 601 being the center of the annular array. It will be appreciated that the plurality of vanes 70 may be disposed at circumferentially spaced locations of the outer carrier 602, and that the plurality of vanes 70 may be disposed at equal intervals or may be disposed at unequal intervals. The length direction of the plurality of blades 70 extends in the radial direction of the hub 10, and illustratively, the plurality of blades 70 are disposed in the x-axis direction and the y-axis direction. The width direction of the plurality of blades 70 is parallel to the axial direction of the hub 10, and the length direction of the plurality of blades 70 extends in the radial direction of the hub 10 such that the blades 70 are parallel to the air intake direction for scooping wind.
The air inlet direction is the z-axis direction, and the blades 70 are parallel to the air inlet direction, and two adjacent blades 70 are in a parallel state, so that the space between the adjacent blades 70 is communicated with the upper surface and the lower surface of the z-axis direction of the impeller, and air can flow into the upper surface and the lower surface of the z-axis direction of the impeller, namely, bidirectional air inlet is realized. And the length direction of the blade 70 is in the radial direction of the x axis and the y axis, when the impeller rotates, the blade 70 can be fully contacted with the air flow, the contact area of the blade 70 and the air flow is increased, and the blade 70 in the work area can perform work better.
The number of blades 70 is equal to the preset number of blades required to maintain the impeller's functional capacity. For example, where the predetermined number of blades required to maintain impeller functioning is seventy-four, the number of blades 70 may be at least seventy-four.
In a first direction (radial direction), each blade 70 comprises a fifth end 701 facing the hub 10 and a sixth end 702 facing away from the hub 10, the fifth end 701 being connected with the outer carrier 602. Each of the blades 70 may be a blade having a plurality of curved portions, and the number of curved portions and the degree of curvature of the curved portions may be the same for each of the blades 70. The blade 70 having the curved portion can better scoop wind when rotated by the fan motor, and improve the wind volume and the work capability.
The plurality of blades 70 are linked to the hub 10 by the tray 60, the at least one through-flow aperture 604 forming the intake area of the impeller, and the area formed by the plurality of blades 70 acting as the work area of the impeller. In this way, the air inlet area is increased by enlarging the total area of the through holes 604 as much as possible without providing the blades 70 in the air inlet area, and then no blades agitate the air in the air inlet position, so as to reduce the aerodynamic noise in the air inlet position and reduce the noise of the fan. And a plurality of blades 70 are arranged at the outer edge of the tray 60, and the working capacity of the impeller can be not affected by the plurality of blades 70.
In some embodiments, the outer diameter D of the outer bracket 602 602 outside An outer diameter D smaller than the area enclosed by the plurality of blades 70 70 outside of And an outer diameter D of the outer bracket 602 602 outside An inner diameter D greater than the area enclosed by the plurality of blades 70 70 in . Thus, the end of the blade 70 far away from the hub 10 protrudes outside the outer support 602, so that better work can be performed by using the blade 70, and the work capability of the impeller can be improved.
Outer diameter D of the area surrounded by the plurality of blades 70 70 outside of Diameter D of the impeller Leaves of the plant Inner diameter D of outer bracket 602 602 inside An inner diameter D less than or equal to the area enclosed by the plurality of blades 70 70 in The end of the blade 70 facing the hub 10 does not protrude inside the outer bracket 602. Since the inner side of the outer bracket 602 is used to form the through-flow holes 604, this canThe end of the vane 70 facing the hub 10 is prevented from occupying part of the space of the through-flow hole 604 formed at the inner side of the outer bracket 602, thereby preventing a decrease in the flow area. In other embodiments, the inner diameter D of the outer poppet 602 may be sufficient if the area of the through-flow aperture 604 formed on the inner side of the outer poppet 602 is large enough 602 inside May be greater than the inner diameter D of the area enclosed by the plurality of vanes 70 70 in In this way, even if one end of the vane 70 facing the hub 10 occupies a part of the space of the through-hole 604 formed inside the outer bracket 602, the intake air amount is not affected.
Radial length L of blade 70 70 May be greater than the difference in the inner and outer diameters of the outer carrier 602, and illustratively, the radial length L of the vane 70 70 Can be about 3 to 9 mm. Inner diameter D of outer bracket 602 602 inside About the inner diameter D of the area enclosed by the plurality of vanes 70 70 in About 80% of the total weight of the blade is larger as the strength and the fixed blade 70 are satisfied. Outer diameter D of outer bracket 602 602 outside About the inner diameter D of the area surrounded by the plurality of blades 70 70 in About 120%, the smaller the blade 70 is, the better the strength requirement and the fixed blade 70 requirement are satisfied.
Fig. 19 is a perspective view of a sixth impeller provided in an embodiment of the present application.
As shown in fig. 19, in some embodiments, a plurality of blades 70 may be fixedly coupled with the outer carrier 602 with a certain contact area, thereby more stably fixing the blades 70.
When the vane 70 and the outer bracket 602 are distributed along the z-axis, the vane 70 is disposed at one side of the outer bracket 602 along the second direction (z-axis direction), and the outer bracket 602 includes a fourth connection surface 6021 facing the vane 70, and the plurality of vanes 70 are connected to the fourth connection surface 6021. It will be appreciated that the vane 70 and the outer bracket 602 are fixedly attached to one side of the overall axial height (z-axis direction) of the vane 70. In this way, each blade 70 is fixed to one side of the outer support 602, and the plurality of blades 70 are located on the same side of the hub 10 as the tray 60 to improve the strength and stability of the impeller and reduce the deformation of the blade set when the impeller rotates. The wind scooping is carried out by each through hole 604 formed on the outer support 602, the blade 70 above the outer support 602 does work, and the wind scooping area and the work area in the axial direction of the z axis are increased, so that the wind inlet quantity and the work effect are further increased, the flow area of the wind inlet of the fan is increased on the premise of keeping the functional force, the flow of the fan is increased, and meanwhile, the noise of the fan is reduced.
Fig. 20 is a side view of a sixth impeller provided in an embodiment of the present application.
As shown in FIG. 20, in some embodiments, the axial overall height H of the blade 70 70 Determining blade functioning force, the axial overall height H of the blade 70 70 May be about 3.7 mm. Axial height H of tray 60 60 Can be determined according to the requirements of specific processing technology, and the axial height H of the tray 60 can be determined under the condition of meeting the requirements of strength and technology 60 The smaller the better. Wherein the axial height is the thickness in the z-axis direction.
In the sixth impeller provided in this embodiment, each blade 70 is connected to the hub 10 through the tray 60, and a plurality of through holes 604 are formed in the tray 60 to divide the tray 60 into an inner support 601 and an outer support 602, and a bracket 603 for connecting the inner support 601 and the outer support 602. The through holes 604 are used to form air inlet areas to increase the air volume, and the blades 70 mounted on the outer support 602 are used to form work areas. The air inlet area is not provided with the blades, so that the air is not stirred by the blades in the air inlet area, thereby reducing the aerodynamic noise of the air inlet area and reducing the noise of the fan. Only the blades of the working area are reserved, so that the number and the form of the blades of the core working area can be increased, and the working capacity of the impeller is not reduced. Therefore, the impeller can reduce fan noise on the premise of not changing the size of the fan and not affecting the performance of the fan.
Fig. 21 is a perspective view of a seventh impeller provided in an embodiment of the present application.
In some embodiments, as shown in fig. 21, the seventh impeller is different from the sixth impeller in that the connection position between the outer support member 602 and the blade 70 is different, and the rest of the structures may refer to the content of the sixth impeller, which is not described herein. For example, the outer support 602 and the vane 70 of the seventh impeller may be fixedly connected to the first mute ring 20 and the second vane 40 of the third impeller.
In the seventh impeller, in the second direction (z-axis direction), the outer mount 602 is provided in the middle of the plurality of blades 70. In this way, the strength of the blade group of the whole impeller can be larger, and the deformation of the blade group can be smaller.
In the second direction (z-axis direction), the blade 70 has a fourth axial height on one side (fourth connection face 6021) of the outer bracket 602; wherein the fourth axial height is the axial overall height H of the blade 70 70 10 to 90 percent of the total weight of the product. It will be appreciated that the vane 70 and the outer bracket 602 are fixedly attached to a central portion of the axial height of the vane 70, which may be 10% to 90% of the total axial height of the vane 70 in the z-axis direction. The outer support 602 may divide the blade 70 into an upper layer and a lower layer, so that the outgoing wind may be forcedly divided into an upper portion and a lower portion, preventing mixing, and further reducing noise, so that the outgoing wind is more uniform.
In the seventh impeller provided in this embodiment, the sixth impeller increases the flow area of the air inlet area by forming the through hole 604 in the tray 60, and increases the flow of the fan, so that the outer support 602 is fixed in the middle of the axial overall height of the blade 70 on the basis of reducing the noise of the fan and not reducing the working capacity of the impeller, and the blade 70 can be divided into an upper layer and a lower layer. Therefore, the discharged wind can be forcedly divided into an upper part and a lower part, mixing is prevented, noise is further reduced, and the air outlet is more uniform.
Fig. 22 is a perspective view of a fan provided in an embodiment of the present application.
As shown in fig. 22, in some embodiments, the fan may include a housing 100, a motor, and an impeller as provided by the various embodiments described above. The housing 100 is a shell having a receiving cavity in which the motor and the impeller provided by any of the embodiments described above are placed. Through holes 110 are formed in the upper and lower surfaces of the casing 100, and the hub 10 and the air inlet area of the impeller are exposed from the through holes 110. Thus, two air inlets are formed at the upper and lower surfaces of the housing 100, and the wind direction is perpendicular to the upper and lower surfaces of the housing 100, i.e., perpendicular to the surface of the hub 10. It will be appreciated that the wind direction is in the z-axis direction.
Taking the case that the sixth impeller is disposed in the casing 100 as an example, the rotation axis of the sixth impeller coincides with the central axis of the through hole 110, which is the z-axis. The inner ring side of the outer carrier 602 in the sixth impeller may be aligned with the edge of the through hole 110, and the blades 70 on the outer ring side of the outer carrier 602 in the sixth impeller are located in the casing 100, and the dotted line 120 is the outside of the area surrounded by each blade 70. In this way, each through-hole 604 formed on the inner ring side of the outer bracket 602 may be exposed from the through-hole 110, so as to form an air inlet area at the through-hole 110, and increase the air volume. Air enters the corresponding air inlet area from top to bottom (or from bottom to top) along the z-axis direction, and when the impeller rotates, the air does work at each blade 70 positioned in the casing 100, so that the work capability of the impeller is not reduced. And no blade agitates the air in the air inlet area, thereby reducing the aerodynamic noise in the air inlet area and the noise of the fan.
Through the through holes 604, air flows at the air inlets at the upper side and the lower side of the casing 100 can be communicated, i.e. the air flows at the air inlets at the upper side and the lower side of the fan can be communicated. When air intake on one side of the fan is blocked, air intake on the other side can fill the area where the blades 70 are positioned through the tray 60, so that the work doing capability of the blades 70 is prevented from being reduced.
Fig. 23 is a graph of a second fan performance profile provided by an embodiment of the present application.
As shown in fig. 23, in some embodiments, the fan performance of the fan scheme using the sixth impeller or the seventh impeller is tested with the conventional fan blade scheme, and when testing, test noise is set first, and the test noise is kept at 38 dB; the voltage corresponding to 38dB is again selected, for example, the voltage may be 5V to test at a constant voltage (5V) at 38 dB. The voltage and the noise are in nonlinear corresponding relation, and different voltages have different noises.
In the testing process, the air quantity of the fan is changed, the corresponding air pressure value is tested, and a second fan Performance (PQ) curve can be obtained based on the corresponding relation between different air quantities and air pressures.
Because the fan is influenced by impedance and environment when rotating, the working range of the fan is between 20 and 80 percent of the maximum air quantity. Then it can be seen from the test result that the maximum air volume of the fan is about 2.7CFM, and the working range of the fan is between (0.54-2) CFM. It can be seen that in this operating range, the fan PQ of the fan scheme using either the sixth impeller or the seventh impeller is higher than the PQ of the normal blades.
According to the fan provided by the embodiment of the application, the impeller provided by the different embodiments can improve the number of blades and the form of the blades of the core working area, so that the working capacity of the impeller is not reduced. Simultaneously, the blades in the air inlet area are reduced or eliminated, and the vortex noise in the air inlet area is reduced, so that the noise of the fan is reduced. Therefore, on the premise of not changing the size of the fan and not affecting the performance of the fan, the noise of the fan can be reduced, the mute function of the fan is optimal, and the air quantity of the fan is increased.
It is noted that other embodiments of the present application will be apparent to those skilled in the art from consideration of the specification and practice of the application disclosed herein. This application is intended to cover any variations, uses, or adaptations of the application following, in general, the principles of the application and including such departures from the present disclosure as come within known or customary practice within the art to which the application pertains. It is intended that the specification and examples be considered as exemplary only, with a true scope of the application being indicated by the following claims.
It is to be understood that the present application is not limited to the precise arrangements and instrumentalities shown in the drawings, which have been described above, and that various modifications and changes may be effected without departing from the scope thereof. The scope of the application is limited only by the appended claims.

Claims (12)

1. An impeller, comprising:
a hub (10);
the tray (60), the tray (60) includes interior support piece (601), outer support piece (602) and at least one support (603), wheel hub (10) is fixed on interior support piece (601), outer support piece (602) set up in the outside of interior support piece (601), outer support piece (602) with the rotation axis of interior support piece (601) is the same, at least one support (603) interval is connected in between interior support piece (601) and outer support piece (602), in interior support piece (601) with form at least one through-flow hole (604) between outer support piece (602), through-flow hole (604) are used for the circulation air;
the blades (70), the blades (70) take the rotation shaft as the center of the annular array, and the blades are distributed in the annular array outside the inner support (601); wherein, in a first direction, each blade (70) comprises a fifth end (701) facing the hub (10) and a sixth end (702) facing away from the hub (10), the fifth end (701) being connected with the outer bracket (602), the sixth end (702) extending in a direction facing away from the hub (10);
wherein the first direction is a radial direction of the hub (10).
2. The impeller of claim 1, wherein the inner carrier (601) is of circular configuration and the outer carrier (602) is of annular configuration;
the inner diameter of the outer support (602) is larger than the outer diameter of the inner support (601), and an annular through hole area is formed between the inner support (601) and the outer support (602).
3. The impeller of claim 2, wherein at least one of the brackets (603) is disposed non-equidistantly spaced within the annular through-hole region;
the two ends of each bracket (603) are respectively connected between the inner support piece (601) and the outer support piece (602), and the annular through hole area between the inner support piece (601) and the outer support piece (602) is divided into at least one through hole (604) with different areas.
4. An impeller according to claim 3, characterized in that at least one of the through-flow holes (604) forms an air intake area of the impeller, and the area formed by the plurality of blades (70) is a work area of the impeller.
5. An impeller according to claim 3, characterized in that at least one of the brackets (603) is arranged in the radial direction of the inner carrier (601).
6. The impeller according to claim 5, characterized in that two adjacent brackets (603) form an included angle, the angle of at least one of said included angles being unequal;
At least one vertex of the included angle is positioned at the center of the inner supporting piece (601).
7. The impeller of claim 6, wherein the sum of cosine values of at least one of said included angles is 0 and the sum of sine values of at least one of said included angles is 0.
8. The impeller of claim 1, wherein the impeller is configured to move,
the blade (70) is arranged on one side of the outer support (602) along the second direction, the outer support (602) comprises a fourth connecting surface (6021) facing the blade (70), and a plurality of blades (70) are connected with the fourth connecting surface (6021);
wherein the second direction is an axial direction of the hub (10).
9. The impeller of claim 1, wherein the impeller is configured to move,
in a second direction, the outer bracket (602) is disposed in the middle of the plurality of blades (70);
in the second direction, the blade (70) has a fourth axial height on one side of the outer bracket (602);
wherein the fourth axial height is 10% -90% of the total axial height of the blade (70).
10. The impeller of claim 1, wherein the outer diameter of the outer carrier (602) is smaller than the outer diameter of the area surrounded by the plurality of blades (70) and larger than the inner diameter of the area surrounded by the plurality of blades (70);
The inner diameter of the outer support (602) is less than or equal to the inner diameter of the area surrounded by the plurality of blades (70).
11. A fan comprising a motor, a housing and an impeller according to any one of claims 1-10, said impeller being mounted in said housing, an output shaft of said motor being connected to a hub (10) of said impeller, said motor being arranged to drive said impeller in rotation.
12. An electronic device comprising a heat generating device and the fan of claim 11 for dissipating heat from the heat generating device.
CN202211611297.6A 2022-12-14 2022-12-14 Impeller, fan and electronic equipment Pending CN117329162A (en)

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CN116146530A (en) * 2022-12-14 2023-05-23 荣耀终端有限公司 Impeller, fan and electronic equipment

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