CN117514902A - Impeller, centrifugal fan and electronic device - Google Patents
Impeller, centrifugal fan and electronic device Download PDFInfo
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- CN117514902A CN117514902A CN202311374322.8A CN202311374322A CN117514902A CN 117514902 A CN117514902 A CN 117514902A CN 202311374322 A CN202311374322 A CN 202311374322A CN 117514902 A CN117514902 A CN 117514902A
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- impeller
- hub
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- blade
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- 230000009286 beneficial effect Effects 0.000 description 21
- 238000000034 method Methods 0.000 description 11
- 230000008569 process Effects 0.000 description 7
- 230000003014 reinforcing effect Effects 0.000 description 7
- 238000010438 heat treatment Methods 0.000 description 6
- 230000008901 benefit Effects 0.000 description 5
- 238000010586 diagram Methods 0.000 description 5
- 230000006872 improvement Effects 0.000 description 5
- 230000009467 reduction Effects 0.000 description 5
- 238000009413 insulation Methods 0.000 description 4
- 230000007423 decrease Effects 0.000 description 3
- 238000013461 design Methods 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000012545 processing Methods 0.000 description 3
- 230000003190 augmentative effect Effects 0.000 description 2
- 238000005452 bending Methods 0.000 description 2
- 230000008859 change Effects 0.000 description 2
- 238000004891 communication Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 230000017525 heat dissipation Effects 0.000 description 2
- 238000003466 welding Methods 0.000 description 2
- 230000033228 biological regulation Effects 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 230000005674 electromagnetic induction Effects 0.000 description 1
- 230000003993 interaction Effects 0.000 description 1
- 239000003351 stiffener Substances 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
Classifications
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- 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
- F04D29/26—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
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- 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
- F04D29/666—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by means of rotor construction or layout, e.g. unequal distribution of blades or vanes
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- 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
- F04D29/667—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps by influencing the flow pattern, e.g. suppression of turbulence
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The embodiment of the application provides an impeller, a centrifugal fan and electronic equipment, relates to the technical field of fans. The impeller comprises a hub and blades fixedly connected to the hub. The camber line of the airfoil of the blade includes a first camber line portion that is curved toward the opposite direction of the rotation direction of the impeller and a second camber line portion that is curved toward the rotation direction of the impeller. The first arc line section comprises a leading edge end, the second arc line section comprises a trailing edge end, the leading edge end is located at one end of the first arc line section, which is close to the rotating shaft of the hub, the trailing edge end is located at one end of the second arc line section, which is far away from the rotating shaft of the hub, and one end of the first arc line section, which is far away from the rotating shaft of the hub, is connected with one end of the second arc line section, which is close to the rotating shaft of the hub. Thus, the air supply amount is larger when the centrifugal fan operates, and the generated noise is smaller.
Description
Technical Field
The embodiment of the application relates to the technical field of fans, in particular to an impeller, a centrifugal fan and electronic equipment.
Background
In electronic devices such as mobile phones, tablet computers, notebook computers, etc., centrifugal fans are often arranged, and the centrifugal fans can be used for generating air flow so as to improve the heat dissipation efficiency of the electronic devices. As the performance of electronic devices is continuously improved, the heat generated by the electronic devices is increasingly greater, and the requirement for the air supply amount of the centrifugal fan is also increasingly higher.
The centrifugal fan comprises an impeller, wherein the impeller comprises a hub and blades fixedly connected to the hub. In general, the blades fixedly connected to the hub are straight blades or C-like blades, and when the centrifugal fan is operated with a large air supply amount, a large noise is generated.
Disclosure of Invention
The embodiment of the application provides an impeller, a centrifugal fan and electronic equipment, and the air supply amount is larger when the centrifugal fan runs, and the generated noise is smaller.
A first aspect of the present application provides an impeller comprising a hub and blades fixedly attached to the hub. The camber line of the airfoil of the blade includes a first camber line portion that is curved toward the opposite direction of the rotation direction of the impeller and a second camber line portion that is curved toward the rotation direction of the impeller. The first arc line section comprises a leading edge end, the second arc line section comprises a trailing edge end, the leading edge end is located at one end of the first arc line section, which is close to the rotating shaft of the hub, the trailing edge end is located at one end of the second arc line section, which is far away from the rotating shaft of the hub, and one end of the first arc line section, which is far away from the rotating shaft of the hub, is connected with one end of the second arc line section, which is close to the rotating shaft of the hub.
The impeller that this application provided, the first pitch arc section of the opposite direction bending of orientation impeller's direction of rotation does benefit to the blade and forms great inlet angle, and then does benefit to the air flow channel that forms between two adjacent blades of air admission, meets with first pitch arc section, and the second pitch arc section of orientation impeller's direction of rotation crooked does benefit to and forms great outlet angle on the basis that the blade has great inlet angle, and then does benefit to the air outflow in the air flow channel that forms between two adjacent blades, and the blade has great inlet angle and outlet angle and does benefit to the air supply volume when improving centrifugal fan operation. In addition, through the design of the first arc segment, the wind resistance of the blade at one end close to the rotating shaft of the hub is small, vortex is not easy to form, air can flow into an air flow channel formed between two adjacent blades smoothly, the air can flow on the surface of the blade, the noise and the air flow loss during rotation of the impeller can be reduced, and the increase of the air supply quantity, the reduction of the noise and the improvement of the energy efficiency during operation of the centrifugal fan are facilitated. In addition, the camber line of the wing profile of the blade is formed by connecting the first camber line segment and the second camber line segment, the wing profile of the blade has strong capability of resisting the reverse pressure gradient, so that air attached to the surface of the blade during rotation of the impeller is not easy to separate from the blade, and the air flows smoothly in an airflow channel formed between two adjacent blades, thereby being beneficial to reducing noise and air flow loss during rotation of the impeller, and further being beneficial to increasing air supply quantity, reducing noise and improving energy efficiency during operation of the centrifugal fan. Moreover, the camber line of the wing profile of the blade is formed by connecting the first camber line segment and the second camber line segment, so that the pneumatic performance of the blade with a larger air inlet angle is better, the work efficiency of the blade with the larger air inlet angle on air during rotation is improved, the energy efficiency of the centrifugal fan with the blade with the larger air inlet angle during operation is improved, the wind pressure of air blown out from an air flow channel formed between two adjacent blades is increased, and the air supply quantity of the centrifugal fan during operation is further improved. Compared with a centrifugal fan with straight blades or C-shaped blades, when the noise generated is the same in decibel, the mean camber line of the wing profile of the blade comprises a first camber line section and a second camber line section, and the air quantity and the air pressure of the air supply of the centrifugal fan are larger. In addition, because the noise generated between the volute and the impeller of the centrifugal fan is smaller when the centrifugal fan operates, at the moment, a sound insulation box is not required to be additionally arranged on the volute, the requirement of smaller noise under larger air supply quantity can be met, the integral size of the centrifugal fan is smaller, and the centrifugal fan is favorably applied to lighter and thinner electronic equipment.
In one possible embodiment, the camber line of the airfoil of the blade is a curve with a continuous curvature.
In one possible embodiment, the inlet angle of the blades is greater than or equal to 90 ° and less than or equal to 125 °. The air inlet angle of the blade is an included angle between the direction of a tangent line of the first arc section at the front edge end pointing to the outer side of the impeller and the linear speed direction of the front edge end when the impeller rotates.
In one possible embodiment, the outlet angle of the blade is greater than or equal to 110 ° and less than or equal to 130 °. The wind outlet angle of the blade is an included angle between the direction of the tangential line of the second arc line segment at the tail edge end pointing to the outer side of the impeller and the linear speed direction of the tail edge end when the impeller rotates.
In one possible embodiment, the length of the first arc segment is less than the length of the second arc segment.
In one possible embodiment, the trailing edge end is located forward of the leading edge end in the direction of rotation of the impeller.
In one possible embodiment, the impeller comprises a plurality of blades arranged at intervals along the circumference of the hub, an air flow channel being formed between two adjacent blades, an air inlet end of the air flow channel being formed between the ends of the two adjacent blades close to the rotation axis of the hub. The airflow channel includes a first flow path section and a second flow path section. The air inlet end is positioned at one end of the first flow passage section close to the rotating shaft of the hub, and one end of the first flow passage section far away from the rotating shaft of the hub is communicated with one end of the second flow passage section close to the rotating shaft of the hub. The through flow section of the first flow channel section gradually decreases from the air inlet end to the end of the first flow channel section communicated with the second flow channel section. The through flow section of the second flow channel section gradually increases from one end of the second flow channel section, which is communicated with the first flow channel section, to one end of the second flow channel section, which is far away from the rotating shaft of the hub.
In one possible embodiment, the ratio of the length of the first flow channel section in the direction of extension of the flow channel to the length of the second flow channel section in the direction of extension of the flow channel is greater than or equal to 1/3 and less than or equal to 3/5.
In one possible embodiment, the airflow channel further comprises a third flow path section, and the air outlet end of the airflow channel is formed between the ends of two adjacent blades, which are far away from the rotation axis of the hub. The air outlet end is positioned at one end of the third flow passage section far away from the rotating shaft of the hub, and one end of the second flow passage section far away from the rotating shaft of the hub is communicated with one end of the third flow passage section close to the rotating shaft of the hub. And the through flow section of the third flow passage section is kept unchanged from one end of the third flow passage section, which is communicated with the second flow passage section, to the air outlet end.
In one possible embodiment, the ratio of the length of the third flow channel section in the direction of extension of the gas flow channel to the length of the second flow channel section in the direction of extension of the gas flow channel is greater than or equal to 1/2 and less than or equal to 4/5.
In one possible embodiment, the camber line of the airfoil of the blade is a fourth-order bezier curve, and the leading edge end and the trailing edge end are the start control point and the end control point of the fourth-order bezier curve, respectively. After converting coordinates in the polar coordinate system of the impeller into coordinates in the rectangular coordinate system of the blade, in the rectangular coordinate system of the blade: the coordinates of the first intermediate control point, the second intermediate control point, the third intermediate control point, and the trailing edge are (x 1, y 1), (x 2, y 2), (x 3, y 3), (x 4, y 4) of the fourth-order bezier curve, respectively. The polar point in the impeller polar coordinate system is positioned on the rotating shaft of the hub, the polar angle of the front edge end in the impeller polar coordinate system is pi/2, the origin of the blade rectangular coordinate system is positioned at the front edge end, the horizontal axis direction in the blade rectangular coordinate system is the same as the polar axis direction in the impeller polar coordinate system, and the forward direction of the longitudinal axis of the blade rectangular coordinate system is the direction that the front edge end points to the outer side of the impeller along the radial direction of the impeller. -n is less than or equal to x1 is less than or equal to-0.4 n,0.8n is less than or equal to y1 is less than or equal to 1.4n,3.4n is less than or equal to x2 is less than or equal to 4n,3.2n is less than or equal to y2 is less than or equal to 3.8n,2.2n is less than or equal to x3 is less than or equal to 2.8n,5.4n is less than or equal to y3 is less than or equal to 6n,1.2n is less than or equal to x4 is less than or equal to 1.8n,7.2n is less than or equal to y4 is less than or equal to 7.8n, and n is a positive number.
A second aspect of the present application provides a centrifugal fan comprising a volute and an impeller according to any of the embodiments described above, the impeller being mounted in the volute, a hub of the impeller being in rotational connection with the volute.
A third aspect of the present application provides an electronic device comprising a housing and a centrifugal fan according to any of the embodiments described above, the volute of the centrifugal fan being mounted on the housing.
Drawings
Fig. 1 is a schematic diagram of an electronic device according to an embodiment of the present application;
fig. 2 is a schematic diagram of another electronic device according to an embodiment of the present application;
FIG. 3 is an exploded view of a centrifugal fan according to an embodiment of the present disclosure;
fig. 4 is an assembly schematic diagram of an impeller of a centrifugal fan in a volute according to an embodiment of the present disclosure;
FIG. 5 is a schematic view of an impeller according to an embodiment of the present disclosure;
FIG. 6 is a schematic illustration of camber lines of an airfoil of a blade according to the related art;
FIG. 7 is a schematic view of a camber line of an airfoil of a blade in a rectangular coordinate system of the blade according to an embodiment of the present application;
fig. 8 is a schematic view of a first airflow channel formed between two adjacent blades of an impeller according to an embodiment of the present disclosure.
Reference numerals illustrate:
1. a housing; 2. a heating module; 3. a centrifugal fan; 4. a first air inlet; 5. a first air outlet;
10. an impeller;
20. a volute;
21. a cover plate; 22. a side wall; 23. a bottom plate;
30. a drive motor;
31. a rotor; 32. a stator;
40. a second circuit board;
50. a second air inlet;
60. a second air outlet;
70. a second airflow passage;
100. a blade;
110. 110a, camber line of the airfoil; 111. a first arc segment; 1111. a leading edge end; 112. a second arc segment; 1121. a trailing edge end;
200. a hub;
300. a first airflow passage;
310. a first flow path section; 311. an air inlet end; 320. a second flow path section; 330. a third flow path segment; 331. an air outlet end;
400. a reinforcing ring;
t, the rotation direction of the impeller; alpha, alpha 0 An air inlet angle; beta, beta 0 An air outlet angle;
x, positive direction of horizontal axis of rectangular coordinate system of blade; y, the positive direction of the vertical axis of the rectangular coordinate system of the blade; p1, a first intermediate control point; p2, a second intermediate control point; and P3, a third intermediate control point.
Detailed Description
The terminology used in the description of the embodiments of the application is for the purpose of describing particular embodiments only and is not intended to be limiting of the application, as will be described in detail with reference to the accompanying drawings.
The present embodiments provide an electronic device that may include, but is not limited to, a cell phone, a tablet (portable android device, PAD), a notebook, a personal digital assistant (personal digital assistant, PDA), a server, a switch, a computing device, a vehicle-mounted device, a wearable device, a Virtual Reality (VR) terminal device, an augmented reality (augmented reality, AR) terminal device, a wireless terminal in industrial control (industrial control), a wireless terminal in unmanned (self driving), a wireless terminal in remote medical (remote media), a wireless terminal in smart grid (smart grid), a wireless terminal in transportation security (transportation safety), a wireless terminal in smart city (smart city), a wireless terminal in smart home (smart home), and the like.
Fig. 1 is a schematic diagram of an electronic device according to an embodiment of the present application.
As shown in fig. 1, in the embodiment of the application, an electronic device may include a housing 1, a heating module 2 and a centrifugal fan 3, where the heating module 2 may be installed in the housing 1, the centrifugal fan 3 may be installed on the housing 1, the housing 1 may have a first air inlet 4 and a first air outlet 5, the centrifugal fan 3 may be used to generate an air flow to drive air at the heating module 2 to flow out of the housing 1 from the first air outlet 5, and air flowing out of the housing 1 from the first air outlet 5 may take heat in the housing 1 to improve the heat dissipation efficiency of the electronic device.
For example, the heat generating module 2 may be a motherboard module, a service board module, a power module, etc., and when the electronic device is operated, the heat generating module 2 generates heat, and the heat generated by the heat generating module 2 may be transferred to the air in the housing 1.
For example, the heat generating module 2 may include a first circuit board (printed circuit board, PCB) fixedly connected with the housing 1 and a chip (not shown) mounted on the first circuit board. The chip may include, but is not limited to, a central processing unit (central processing unit, CPU), a graphics processor (graphics processing unit, GPU), etc.
Illustratively, the centrifugal fan 3 may be mounted within the housing 1.
Fig. 2 is a schematic diagram of another electronic device according to an embodiment of the present application.
As shown in fig. 2, the centrifugal fan 3 may be mounted outside the housing 1, for example. The centrifugal fan 3 can be used for driving air outside the shell 1 to flow into the shell 1 through the first air inlet 4, the original air in the shell 1 can be pressed out of the first air outlet 5 through the air flowing into the shell 1 through the first air inlet 4, and the centrifugal fan 3 arranged outside the shell 1 can drive the air at the heating module 2 to flow out of the shell 1 from the first air outlet 5.
Fig. 3 is an exploded view of a centrifugal fan according to an embodiment of the present application, and fig. 4 is an assembled schematic view of an impeller of the centrifugal fan in a volute according to an embodiment of the present application.
As shown in fig. 3 and 4, in the embodiment of the present application, the centrifugal fan 3 may include a volute 20 and an impeller 10, the volute 20 may be used to be mounted on the housing 1, the impeller 10 is mounted in the volute 20, and the impeller 10 is rotatably connected with the volute 20. The volute 20 is provided with a second air inlet 50 and a second air outlet 60, the second air inlet 50 and the second air outlet 60 are both communicated with the inner cavity of the volute 20, the rotating impeller 10 can be used for driving air in the volute 20 to flow, so that the air in the volute 20 is blown out from the second air outlet 60, the air outside the volute 20 flows into the volute 20 through the second air inlet 50, air flow can be generated, and the air blown out from the volute 20 through the second air outlet 60 can be used for driving the air at the heating module 2 to flow out of the housing 1 from the first air outlet 5 on the housing 1.
For example, the volute 20 may include a cover 21, a side wall 22 and a bottom plate 23, where the cover 21 and the bottom plate 23 are disposed opposite to each other, the side wall 22 is located between the cover 21 and the bottom plate 23, two ends of the side wall 22 are fixedly connected to the cover 21 and the bottom plate 23, respectively, an inner cavity of the volute 20 is formed between the cover 21, the bottom plate 23 and the side wall 22, the inner cavity of the volute 20 may be used as an inner flow path of the centrifugal fan 3, and at least one of the cover 21 and the bottom plate 23 has the second air inlet 50.
Illustratively, the cover 21 has a second air inlet 50 and the base 23 does not have a second air inlet 50.
Thus, the centrifugal fan 3 can be supplied with air from one side, so that the vortex formed in the volute 20 due to inconsistent air inlet direction can be reduced, the noise generated by the air vibration in the volute 20 can be reduced, and the noise generated when the centrifugal fan 3 is operated can be reduced. In addition, the air flows smoothly in the volute 20, so that the air has higher flow speed in the volute 20, and the air supply quantity of the centrifugal fan 3 during operation is improved.
The second air inlet 50 is illustratively a circular opening having an axis coincident with the rotational axis of the impeller 10.
Illustratively, both ends of the second air outlet 60 extend to the bottom plate 23 and the cover plate 21, that is, both ends of the second air outlet 60 connected to the bottom plate 23 and the cover plate 21 are open structures.
In this way, the through-flow cross section of the second air outlet 60 can be made larger, which is advantageous for improving the air volume of the centrifugal fan 3. In addition, the reverse flow of the air in the volute 20 formed at the second air outlet 60 can be reduced, the formation of vortex in the volute 20 can be reduced, so that the air can smoothly flow out of the volute 20 through the second air outlet 60, noise generated by the vibration of the air in the volute 20 can be reduced, the air can have a higher flow speed in the volute 20, and the noise generated when the centrifugal fan 3 is operated can be reduced, and the air supply quantity when the centrifugal fan 3 is operated can be improved.
In the embodiment of the present application, the centrifugal fan 3 may further include a driving motor 30, and the driving motor 30 is used to drive the impeller 10 to rotate.
By way of example, the drive motor 30 may include, but is not limited to, an electric motor, a hydraulic motor, and the like.
In some examples, the driving motor 30 may include a stator 32 and a rotor 31, where the stator 32, the rotor 31 and the impeller 10 are coaxially disposed, the stator 32 is fixedly connected with the volute 20, the rotor 31 is fixedly connected with the impeller 10, the rotor 31 is rotationally connected with the stator 32, and the stator 32 is used to drive the rotor 31 to rotate so as to drive the impeller 10 to rotate relative to the volute 20.
Illustratively, the centrifugal fan 3 may further include a second circuit board 40, the second circuit board 40 may be fixedly mounted on an inner wall of the bottom plate 23, the driving motor 30 may be mounted on the second circuit board 40, and the second circuit board 40 may be electrically connected with the driving motor 30 to supply power to the driving motor 30. The second circuit board 40 can achieve speed regulation of the driving motor 30 by adjusting the magnitude of the voltage and current supplied to the driving motor 30. For example, the stator 32 of the driving motor 30 may be fixedly mounted on the second circuit board 40 and electrically connected with the second circuit board 40.
Illustratively, the stator 32 of the drive motor 30 may drive the rotor 31 to rotate by electromagnetic induction.
In the embodiment of the present application, the impeller 10 includes a hub 200 and a plurality of blades 100 disposed at intervals along the circumferential direction of the hub 200, the blades 100 are fixedly connected to the hub 200, the hub 200 is rotatably connected to the volute 20, and the impeller 10 rotates around the rotation axis of the hub 200.
For example, blade 100 may be fixedly coupled to hub 200 by welding, clamping, fastening, integrally forming, etc.
Illustratively, the hub 200 may be rotatably coupled to the volute 20 by a drive motor 30.
In the example in which the driving motor 30 includes the stator 32 and the rotor 31, the stator 32, the rotor 31 and the hub 200 are coaxially disposed, and the rotor 31 is fixedly connected with the hub 200.
Illustratively, an end of blade 100 proximate to the rotational axis of hub 200 is coupled to an outer wall of hub 200.
In this way, hub 200 has less effect on the flow of air between adjacent blades 100.
For example, the blades 100 of the impeller 10 may be equally spaced along the circumference of the hub 200.
In this embodiment, a first air flow channel 300 is formed between two adjacent blades 100 and the cover plate 21, and between the two adjacent blades 23, an air inlet end 311 of the first air flow channel 300 is formed between the two adjacent blade 100 ends close to the rotating shaft of the hub 200, an air outlet end 331 of the first air flow channel 300 is formed between the two adjacent blade 100 ends far away from the rotating shaft of the hub 200, and the air inlet end 311 is communicated with the second air inlet 50. The second airflow channel 70 is formed between the outer rotating contour formed by the rotating path of the end part of the blade 100 far away from the rotating shaft of the hub 200 and the side wall 22, the cover plate 21 and the bottom plate 23, the air outlet end 331 is communicated with the second air outlet 60 through the second airflow channel 70, when the impeller 10 rotates, air outside the volute 20 enters the first airflow channel 300 through the second air inlet 50, the impeller 10 drives the air in the first airflow channel 300 to perform centrifugal motion, so that the air in the first airflow channel 300 enters the second airflow channel 70 through the air outlet end 331, and the second airflow channel 70 guides the air entering the second airflow channel to the second air outlet 60 so as to blow the air in the volute 20 out through the second air outlet 60.
In some examples where the second air intake 50 is a circular opening having an axis coincident with the rotational axis of the impeller 10, the radius of the second air intake 50 may be greater than the radius of the rotational inner profile formed by the rotational path of the end of the blade 100 near the rotational axis of the hub 200, that is, the radius of the second air intake 50 may be greater than the distance from the rotational axis of the hub 200 of the end of the blade 100 near the rotational axis of the hub 200.
The distance between the outer rotation contour formed by the rotation path of the end of the blade 100 away from the rotation axis of the hub 200 and the side wall 22 may be gradually increased from the volute tongue (not shown) of the side wall 22 to the second air outlet 60, so that the through-flow cross section of the second air flow channel 70 is gradually increased from the volute tongue of the side wall 22 to the second air outlet 60. The volute tongue of the side wall 22 may be disposed adjacent to the second air outlet 60.
Fig. 5 is a schematic view of an impeller according to an embodiment of the present application. Wherein the T direction is the rotation direction of the impeller 10.
As shown in FIG. 5, camber line 110 of the airfoil of blade 100 includes a leading edge 1111 and a trailing edge 1121, with leading edge 1111 being located at an end of camber line 110 of the airfoil of blade 100 near the rotational axis of hub 200 and trailing edge 1121 being located at an end of camber line 110 of the airfoil of blade 100 remote from the rotational axis of hub 200.
The section of the airfoil of the blade 100 is perpendicular to the extending direction of the blade 100 from the end near the bottom plate 23 to the end near the cover plate 21. For example, when the blade 100 extends in the axial direction of the rotation axis of the impeller 10 from the end near the bottom plate 23 to the end near the cover plate 21, the section where the airfoil of the blade 100 is located may be perpendicular to the rotation axis of the impeller 10.
The camber line 110 of the airfoil of the blade 100 is a continuous line segment formed by inscribed circles of the profile lines of the airfoil of the blade 100, that is, the points on the camber line 110 of the airfoil of the blade 100 are equidistant from the profile lines of the airfoil of the blade 100 on both sides thereof. After the camber line 110 of the airfoil of the blade 100 is determined, the profile of the airfoil of the blade 100 may be determined according to the distribution rule of the thickness of the blade 100, and thus the shape of the blade 100 may be determined.
In some examples, the blade 100 may be a plate-like structure of equal thickness.
In the embodiment of the present application, the blades 100 of the impeller 10 have an air inlet angle α and an air outlet angle β, where the air inlet angle α of the blades 100 is an angle between a direction along which a tangent line of a camber line 110 of an airfoil of the blades 100 at a leading edge 1111 points to an outer side of the impeller 10 and a linear velocity direction of the leading edge 1111 when the impeller 10 rotates, and the air outlet angle β of the blades 100 is an angle between a direction along which a tangent line of a camber line 110 of an airfoil of the blades 100 at a trailing edge 1121 points to an outer side of the impeller 10 and a linear velocity direction of the leading edge 1111 when the impeller 10 rotates.
In order to provide the centrifugal fan 3 with a large air supply amount, it is necessary to provide the air inlet angle α of the blade 100 with a large angle.
In the related art, the blades of the centrifugal fan are often straight blades or C-like blades, that is, the camber lines of the airfoils of the blades are straight line segments or C-like line segments. Fig. 6 is a schematic view of camber lines of an airfoil of a blade in the related art. As shown in fig. 6, for example, the camber line 110a of the airfoil of the blade may include two camber lines curved toward the rotation direction of the impeller and a straight line segment connecting the two camber lines, the straight line segment being tangent to both the two camber lines, and the two camber lines being connected to the straight line segment such that the camber line 110a of the airfoil of the blade is a C-like line segment. In the related art, the air inlet angle alpha of the blade 0 When the angle of the blade is larger, the air in the first airflow channel is seriously separated from the surface of the blade when flowing, the pneumatic performance of the blade is poorer, so that the noise is larger when the impeller rotates, the acting efficiency of the blade on the air is lower, and the noise and the energy efficiency are larger when the centrifugal fan operates. In order to prevent the noise generated by the operation of the centrifugal fan from being excessive, the air inlet angle alpha of the blades of the centrifugal fan in the related art 0 Usually less than 80 °, but at this time, the air intake of the first air flow passage is small, which results in a small air intake of the centrifugal fan.
In some related art, there is a scheme of adding a sound insulation box to the outside of a scroll case of a centrifugal fan to reduce noise transmitted to a user and the outside environment. However, after the sound insulation box is added, the overall size of the centrifugal fan is larger, which is unfavorable for applying the centrifugal fan to lighter and thinner electronic equipment.
Based on this, as shown in fig. 5, and referring to fig. 3 and 4, in the present embodiment, the camber line 110 of the airfoil of the blade 100 includes a first camber line segment 111 and a second camber line segment 112, the first camber line segment 111 is curved toward the opposite direction of the rotation direction of the impeller 10, that is, in the rotation direction of the impeller 10, both ends of the first camber line segment 111 are located in front of the camber line tip of the first camber line segment 111. The second arc segment 112 is curved toward the rotation direction of the impeller 10, that is, both ends of the second arc segment 112 are located behind the arc top of the second arc segment 112 in the rotation direction of the impeller 10. The first arc segment 111 includes a leading edge 1111 and the second arc segment 112 includes a trailing edge 1121, the leading edge 1111 being located at an end of the first arc segment 111 near the rotational axis of the hub 200, the trailing edge 1121 being located at an end of the second arc segment 112 remote from the rotational axis of the hub 200, the end of the first arc segment 111 remote from the rotational axis of the hub 200 being joined to an end of the second arc segment 112 near the rotational axis of the hub 200.
In this way, the first arc segment 111 curved in the opposite direction to the rotation direction of the impeller 10 is beneficial to forming a larger air inlet angle α by the blade 100, so that air enters the first air flow channel 300, the second arc segment 112 connected with the first arc segment 111 and curved in the rotation direction of the impeller 10 is beneficial to forming a larger air outlet angle β on the basis that the blade 100 has the larger air inlet angle α, so that air in the first air flow channel 300 flows out, and the blade 100 has the larger air inlet angle α and the air outlet angle β, so that the air quantity during operation of the centrifugal fan 3 is improved. In addition, through the design of the first arc segment 111, the wind resistance of the blade 100 at one end close to the rotation axis of the hub 200 is small, and the vortex is not easy to form, so that air can flow into the first airflow channel 300 smoothly, the air is facilitated to flow on the surface of the blade 100, the noise and the air flow loss during the rotation of the impeller 10 can be reduced, and the increase of the air supply quantity, the reduction of the noise and the improvement of the energy efficiency during the operation of the centrifugal fan 3 are facilitated. In addition, the camber line 110 of the airfoil of the blade 100 is formed by connecting the first camber line segment 111 and the second camber line segment 112, so that the capability of the airfoil of the blade 100 for resisting the reverse pressure gradient is strong, the air attached to the surface of the blade 100 during rotation of the impeller 10 is not easy to separate from the blade 100, the air flows smoothly in the first airflow channel 300, the noise and the flow loss of the air during rotation of the impeller 10 are reduced, and the increase of the air supply quantity, the reduction of the noise and the improvement of the energy efficiency during the operation of the centrifugal fan 3 are further facilitated. Moreover, the camber line 110 of the airfoil profile of the blade 100 is formed by connecting the first camber line segment 111 and the second camber line segment 112, so that the aerodynamic performance of the blade 100 with a larger air inlet angle alpha is better, the working efficiency of the blade 100 with the larger air inlet angle alpha on air when rotating is improved, the energy efficiency of the blade 100 with the larger air inlet angle alpha when the centrifugal fan 3 operates is improved, the wind pressure of the air flowing out from the air outlet end 331 is increased, and the air quantity of the centrifugal fan 3 when operating is further improved. When the decibels of the generated noise are the same, the air volume and the air pressure of the air supply are both larger in the centrifugal fan 3 in which the camber line 110 of the airfoil of the blade 100 includes the first and second camber line segments 111 and 112, compared to the centrifugal fan in which the blade is a straight blade or a C-like blade. In addition, because the noise generated between the volute 20 and the impeller 10 is smaller when the centrifugal fan 3 is running, at this time, the requirement of smaller noise under larger air supply volume can be met without additionally installing a sound insulation box outside the volute 20, the integral size of the centrifugal fan 3 can be smaller, and the centrifugal fan 3 can be applied to lighter and thinner electronic equipment.
In the present application, unless otherwise specified, the description of the relative relationship of the structures on the blade 100 such as the first arc segment 111, the second arc segment 112, the leading edge 1111, the trailing edge 1121, and the like refers to the relative relationship of the structures on the same blade 100.
In some examples, the impeller 10 may further include a reinforcing ring 400, the reinforcing ring 400 being disposed coaxially with the rotation axis of the hub 200, and one end of all the blades 100 of the impeller 10, which is far from the rotation axis of the hub 200, may be fixedly connected by the reinforcing ring 400, the reinforcing ring 400 being fixedly connected to a side of the blades 100 facing the cover plate 21 or a side of the blades 100 facing the base plate 23.
In this way, the strength of the blade 100 is enhanced, so that the blade 100 is not easy to deform when the impeller 10 rotates, and the designed noise, air inlet and aerodynamic performance are maintained. In addition, the reinforcing ring 400 is fixedly connected to the side of the blade 100 facing the cover plate 21 or the side of the blade 100 facing the bottom plate 23, so that the influence of the reinforcing ring 400 on the air in the first air flow channel 300 flowing into the second air flow channel 70 through the air outlet end 331 is less.
Illustratively, the stiffener ring 400 may be fixedly coupled to the blade 100 by welding, clamping, integrally forming, or the like.
In some examples, the camber line 110 of the airfoil of the blade 100 may be a tangentially continuous curve.
Thus, the blade 100 is easier to machine and less expensive to manufacture.
In some examples, the camber line 110 of the airfoil of the blade 100 may be a curve with a continuous curvature.
In this way, when the impeller 10 rotates, the air in the first air flow channel 300 is facilitated to adhere to the surface of the blade 100 to flow, and the air in the first air flow channel 300 is not easy to separate from the surface of the blade 100 during flowing, so that noise and air flow loss during rotation of the impeller 10 are facilitated to be reduced. In addition, the blade 100 is also less difficult and costly to machine.
In some examples, the camber line 110 of the airfoil of the blade 100 may be a curve with a continuous change in curvature.
In this way, when the impeller 10 rotates, the air flowing in the first airflow channel 300 has a better adhesion effect on the surface of the blade 100, the air in the first airflow channel 300 is not easy to separate from the surface of the blade 100 when flowing, the noise is smaller when the impeller 10 rotates, and the flowing loss of the air is smaller.
In some possible embodiments, the inlet air angle α of the blade 100 is greater than or equal to 90 ° and less than or equal to 125 °. At this time, the intake angle α of the blade 100 is an angle between a direction along the tangential line of the first arc segment 111 at the leading edge 1111 directed to the outside of the impeller 10 and a linear velocity direction of the leading edge 1111 when the impeller 10 rotates.
Thus, the air inlet angle α of the blade 100 is larger, which is beneficial for air to enter the first air flow channel 300, and the air inlet of the first air flow channel 300 is smoother, which is beneficial for the first air flow channel 300 to have larger air inlet amount and is beneficial for improving the air inlet amount of the centrifugal fan 3. In addition, the air inlet end 311 is not easy to form vortex, which is beneficial to reducing noise generated by rotation of the impeller 10 and air flow loss. In addition, the degree of bending of the first arc segment 111 can be made smaller, and when the air at the portion of the surface of the blade 100 corresponding to the first arc segment 111 is guided to the portion of the surface of the blade 100 corresponding to the second arc segment 112, the air is not easily separated from the surface of the blade 100, which is beneficial to reducing noise generated by rotation of the impeller 10 and flow loss of the air. Furthermore, the length of the first arc segment 111 is shorter, the length of the second arc segment 112 is longer, the working efficiency of the blade 100 on the air is higher when the blade rotates, which is beneficial to improving the energy efficiency of the centrifugal fan 3 when the centrifugal fan operates and increasing the wind pressure of the air flowing out from the wind outlet end 331, and is beneficial to further improving the wind quantity of the centrifugal fan 3 when the centrifugal fan operates. In addition, the length of the first arc segment 111 is shorter, and the length of the second arc segment 112 is longer, which is favorable for reducing the wind resistance of the air inlet of the first air flow channel 300, and then, the air in the first air flow channel 300 is attached to the surface of the blade 100 to flow, so that the noise generated by the rotation of the impeller 10 and the flow loss of the air are favorable for reducing.
By way of example, the inlet air angle α of the blade 100 may include, but is not limited to, 90 °, 95 °, 98 °, 100 °, 104 °, 107 °, 110 °, 112 °, 115 °, 118 °, 120 °, 121 °, 125 °, and the like.
In some possible embodiments, the outlet angle β of the blade 100 is greater than or equal to 110 ° and less than or equal to 130 °. At this time, the air outlet angle β of the blade 100 is an angle between a direction along the tangential line of the second arc segment 112 at the trailing edge 1121 and the outside of the impeller 10 and a linear velocity direction of the trailing edge 1121 when the impeller 10 rotates.
In this way, the air outlet angle β of the vane 100 is larger, so that the air can flow out of the first air flow channel 300 more smoothly, which is beneficial to improving the air quantity of the centrifugal fan 3. In addition, the blade 100 has higher working efficiency on air when rotating, which is beneficial to improving the energy efficiency of the centrifugal fan 3 when running and increasing the wind pressure of the air flowing out from the wind outlet end 331, and is beneficial to further improving the wind quantity of the centrifugal fan 3 when running.
Exemplary, the outlet angle β of the blade 100 may include, but is not limited to, 110 °, 112 °, 114 °, 115 °, 118 °, 120 °, 123 °, 126 °, 128 °, 130 °, and the like.
In some possible embodiments, the length of the first arc segment 111 is less than the length of the second arc segment 112.
In this way, the longer length of the second arc segment 112 can make the working efficiency of the blade 100 on the air higher when rotating, which is beneficial to improving the energy efficiency of the centrifugal fan 3 when operating and increasing the wind pressure of the air flowing out from the wind outlet end 331, and is beneficial to further improving the wind quantity of the centrifugal fan 3 when operating. In addition, the length of the first arc segment 111 is shorter, and the length of the second arc segment 112 is longer, which is beneficial to reducing the air resistance of the air inlet of the first air flow channel 300, and then, the air in the first air flow channel 300 is attached to the surface of the blade 100 to flow, which is beneficial to reducing the noise generated by the rotation of the impeller 10 and the flow loss of the air.
In some possible embodiments, trailing edge 1121 is forward of leading edge 1111 in the direction of rotation of impeller 10.
In this way, the blade 100 with the larger air inlet angle α has the larger air outlet angle β, so that air flows out of the first air flow channel 300 more smoothly, and the working efficiency of the blade 100 on air is higher when rotating.
Fig. 7 is a schematic view of a camber line of an airfoil of a blade in a rectangular coordinate system of the blade according to an embodiment of the present application. The X direction is the forward direction of the transverse axis of the rectangular coordinate system of the blade, the Y direction is the forward direction of the longitudinal axis of the rectangular coordinate system of the blade, P1 is a first intermediate control point, P2 is a second intermediate control point, and P3 is a third intermediate control point.
As shown in fig. 7, in some possible embodiments, the camber line 110 of the airfoil of the blade 100 is a fourth-order bezier curve, and the leading edge 1111 and the trailing edge 1121 are the start control point and the end control point, respectively, of the fourth-order bezier curve.
In this way, the airfoil design and manufacture of the blade 100 is easier. In addition, the formed vane 100 has better aerodynamic performance, and when the impeller 10 rotates, the air in the first air flow channel 300 is beneficial to being attached to the surface of the formed vane 100 to flow, and the air in the first air flow channel 300 is not easy to separate from the surface of the vane 100 when flowing, so that noise and air flow loss when the impeller 10 rotates are reduced.
In some examples where camber line 110 of the airfoil of blade 100 is a fourth-order Bezier curve, after converting coordinates in the polar coordinate system of the impeller to coordinates in the rectangular coordinate system of the blade, in the rectangular coordinate system of the blade: the coordinates of the first intermediate control point P1, the second intermediate control point P2, and the third intermediate control point P3 of the fourth-order bezier curve are (x 1, y 1), (x 2, y 2), (x 3, y 3), and (x 4, y 4), respectively. Wherein, the pole in the impeller polar coordinate system is located on the rotation axis of the hub 200, the polar angle of the front edge 1111 in the impeller polar coordinate system is pi/2, the origin of the blade rectangular coordinate system is located at the front edge 1111, the horizontal axis direction in the blade rectangular coordinate system is the same as the polar axis direction in the impeller polar coordinate system, and the forward direction of the vertical axis of the blade rectangular coordinate system is the direction that the front edge 1111 points to the outside of the impeller 10 along the radial direction of the impeller 10. -n is less than or equal to x1 is less than or equal to-0.4 n,0.8n is less than or equal to y1 is less than or equal to 1.4n,3.4n is less than or equal to x2 is less than or equal to 4n,3.2n is less than or equal to y2 is less than or equal to 3.8n,2.2n is less than or equal to x3 is less than or equal to 2.8n,5.4n is less than or equal to y3 is less than or equal to 6n,1.2n is less than or equal to x4 is less than or equal to 1.8n,7.2n is less than or equal to y4 is less than or equal to 7.8n, and n is a positive number.
In this way, the angles of the air inlet angle α and the air outlet angle β of the blade 100 are larger, which is beneficial to the air entering the first air flow channel 300 and the air flowing out of the first air flow channel 300, so that the air supply amount when the centrifugal fan 3 operates is larger. In addition, the wind resistance of the blade 100 at one end close to the rotation axis of the hub 200 is small, and the vortex is not easy to form, so that the air can flow into the first airflow channel 300 more smoothly, the air can flow on the surface of the blade 100, the noise and the air flow loss during the rotation of the impeller 10 can be reduced, and the increase of the air supply quantity, the reduction of the noise and the improvement of the energy efficiency during the operation of the centrifugal fan 3 can be facilitated. In addition, the wing profile of the vane 100 has higher fitting degree with the flow field of the air in the first airflow channel 300, and the wing profile of the vane 100 has strong capability of resisting the reverse pressure gradient, so that the air flowing on the surface of the vane 100 is not easy to separate from the vane 100 when the impeller 10 rotates, the air flows in the first airflow channel 300 more smoothly, the noise and the flow loss of the air when the impeller 10 rotates are reduced, and the increase of the air supply quantity, the reduction of the noise and the improvement of the energy efficiency when the centrifugal fan 3 operates are facilitated. Moreover, due to the fact that the wing profile of the blade 100 is high in the degree of fitting with the flow field of the air in the first air flow channel 300, the aerodynamic performance of the blade 100 is good, the working efficiency of the blade 100 on the air during rotation is high, the energy efficiency of the centrifugal fan 3 during operation is high, the wind pressure of the air flowing out of the air outlet end 331 is high, and the air supply amount of the centrifugal fan 3 during operation is high. In addition, the size of the blades 100 can be adjusted by adjusting the size of n, so that the centrifugal fan 3 with larger air supply amount and smaller generated noise with different sizes can be manufactured conveniently.
In the process of converting the coordinates in the impeller polar coordinate system into the coordinates in the rectangular coordinate system of the blade, the coordinates in the impeller polar coordinate system can be converted into the coordinates in the rectangular coordinate system of the blade by a conversion method of the polar coordinate system and the rectangular coordinate system, and then the coordinates in the rectangular coordinate system of the impeller can be converted into the coordinates in the rectangular coordinate system of the blade by a translation method and the like. The origin of the rectangular coordinate system of the impeller is located on the rotation axis of the hub 200, the horizontal axis in the rectangular coordinate system of the impeller coincides with the polar axis in the polar coordinate system of the impeller, the forward direction of the vertical axis of the rectangular coordinate system of the impeller is the direction that the rotation axis of the hub 200 points to the outside of the impeller 10 along the radial direction of the impeller 10, and the units of the abscissa and the units of the ordinate in the rectangular coordinate system of the blade are the same, for example, the units of the abscissa and the units of the ordinate in the rectangular coordinate system of the blade may be meters, decimeters, centimeters, and the like.
Illustratively, n may include, but is not limited to, 0.1, 0.01, 0.2, 0.5, 1, 1.5, 2, 3, 5, 8, 10, 100, etc.
Exemplary, units of abscissa and units of ordinate in the rectangular blade coordinate system are in units of decimeters, in the rectangular blade coordinate system, the first intermediate control point P1 of the fourth-order Bezier curve may have a coordinate (-0.06,0.1), the second intermediate control point P2 has a coordinate (0.36,0.34), the third intermediate control point P3 has a coordinate (0.24,0.56), the trailing edge 1121 has a coordinate (0.14,0.74), and the leading edge 1111 has a coordinate (0, 0)
Fig. 8 is a schematic view of a first airflow channel formed between two adjacent blades of an impeller according to an embodiment of the present disclosure.
As shown in fig. 8, in some possible embodiments, the first gas flow channel 300 includes a first flow channel section 310 and a second flow channel section 320. The air inlet end 311 is located at an end of the first flow path segment 310 near the rotational axis of the hub 200, and an end of the first flow path segment 310 remote from the rotational axis of the hub 200 communicates with an end of the second flow path segment 320 near the rotational axis of the hub 200. The through-flow cross section of the first flow path section 310 gradually decreases from the air inlet end 311 to the end of the first flow path section 310 that communicates with the second flow path section 320. The through-flow cross section of the second flow path section 320 gradually increases from the end of the second flow path section 320 that communicates with the first flow path section 310 to the end of the second flow path section 320 that is away from the rotational axis of the hub 200.
Thus, when the air flows in the first flow channel section 310, the flow speed gradually decreases, the pressure slowly increases, the impact of the air flow with higher turbulence degree can be restrained while the air inlet end 311 is smoothly fed, the air can smoothly flow in the first air flow channel 300, the noise and the flowing loss of the air when the impeller 10 rotates can be reduced, the flow speed gradually increases when the air flows in the second flow channel section 320, the air supply amount when the centrifugal fan 3 operates can be improved, the noise when the centrifugal fan 3 operates is smaller, and the air supply amount is larger.
In some possible embodiments, the ratio of the length of the first flow channel segment 310 along the direction of extension of the first flow channel 300 to the length of the second flow channel segment 320 along the direction of extension of the first flow channel 300 is greater than or equal to 1/3 and less than or equal to 3/5.
Thus, the noise generated when the air flows through the first flow passage section 310 and the second flow passage section 320 and the aerodynamic performance of the first flow passage section 310 and the second flow passage section 320 are well balanced, so that the noise is small and the air supply amount is large when the centrifugal fan 3 is operated.
Illustratively, the ratio of the length of the first flow path segment 310 along the direction of extension of the first flow path 300 to the length of the second flow path segment 320 along the direction of extension of the first flow path 300 may include, but is not limited to, 1/3, 2/5, 1/2, 3/5, etc.
In some possible embodiments, the first air flow channel 300 further comprises a third flow channel section 330. The air outlet 331 is located at an end of the third flow path section 330 away from the rotational axis of the hub 200, and an end of the second flow path section 320 away from the rotational axis of the hub 200 communicates with an end of the third flow path section 330 near the rotational axis of the hub 200. The through-flow cross section of the third flow path section 330 remains unchanged from the end of the third flow path section 330 that communicates with the second flow path section 320 to the air outlet end 331.
In this way, the influence of the air pressure change of the air outlet end 331 on the air flow in the first air flow channel 300 when the impeller 10 rotates can be reduced, and the air flows smoothly and stably in the first air flow channel 300, which is beneficial to reducing the noise generated when the air flows through the first air flow channel 300.
It should be understood that the constant flow cross section of the third flow path section 330 in the present application does not mean that the flow cross section of the third flow path section 330 is kept absolutely constant, and the flow cross section of the third flow path section 330 may have a certain error from one end of the third flow path section 330, which is in communication with the second flow path section 320, to the air outlet end 331 due to the production process or the like.
In some possible embodiments, the ratio of the length of the third flow path section 330 along the extension direction of the first flow path 300 to the length of the second flow path section 320 along the extension direction of the first flow path 300 is greater than or equal to 1/2 and less than or equal to 4/5.
In this way, the noise generated when the air flows through the first air flow channel 300 and the aerodynamic performance of the first air flow channel 300 are well balanced, so that the noise is smaller and the air supply amount is larger when the centrifugal fan 3 operates.
Illustratively, the ratio of the length of the third flow path segment 330 along the direction of extension of the first flow path 300 to the length of the second flow path segment 320 along the direction of extension of the first flow path 300 may include, but is not limited to, 1/2, 3/5, 2/3, 4/5, etc.
In some examples where the first airflow channel 300 includes the first, second, and third flow channel sections 310, 320, 330, the ratio of the length of the first flow channel section 310 to the length of the first airflow channel 300 may be greater than or equal to 1/5 and less than or equal to 1/4, e.g., the ratio of the length of the first flow channel section 310 to the length of the first airflow channel 300 may be 1/5. The ratio of the sum of the length of the first flow path section 310 and the length of the second flow path section 320 to the length of the first air flow path 300 may be greater than or equal to 7/12 and less than or equal to 9/12, for example, the ratio of the sum of the length of the first flow path section 310 and the length of the second flow path section 320 to the length of the first air flow path 300 may be 2/3.
In this way, the noise generated when the air flows through the first air flow channel 300 and the aerodynamic performance of the first air flow channel 300 are well balanced, so that the noise is smaller and the air supply amount is larger when the centrifugal fan 3 operates.
In this application, unless otherwise specified, descriptions of the relative relationships of the portions of the first airflow channel 300, such as the first airflow channel 310, the second airflow channel 320, the third airflow channel 330, the air inlet end 311, the air outlet end 331, and the like, refer to the relative relationships of the portions of the same first airflow channel 300.
In the description of the embodiments of the present application, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "connected," and "connected" are to be construed broadly, and may be, for example, fixedly connected, indirectly connected through an intermediary, or may be in communication with each other between two elements or in an interaction relationship between two elements. The specific meaning of the above terms in the embodiments of the present application will be understood by those of ordinary skill in the art according to the specific circumstances.
The embodiments or implications herein must have a particular orientation, be constructed and operate in a particular orientation, and therefore should not be construed as limiting the embodiments herein. In the description of the embodiments of the present application, the meaning of "a plurality" is two or more, unless specifically stated otherwise.
The terms first, second, third, fourth and the like in the description and in the claims of embodiments of the application and in the above-described figures, if any, are used for distinguishing between similar objects and not necessarily for describing a particular sequential or chronological order. It is to be understood that the data so used may be interchanged where appropriate such that embodiments of the present application described herein may be capable of implementation in sequences other than those illustrated or described herein, for example. Furthermore, the terms "comprises," "comprising," and "having," and any variations thereof, are intended to cover a non-exclusive inclusion, such that a process, method, system, article, or apparatus that comprises a list of steps or elements is not necessarily limited to those steps or elements expressly listed but may include other steps or elements not expressly listed or inherent to such process, method, article, or apparatus.
The term "plurality" herein refers to two or more. The term "and/or" is herein merely an association relationship describing an associated object, meaning that there may be three relationships, e.g., a and/or B, may represent: a exists alone, A and B exist together, and B exists alone. In addition, the character "/" herein generally indicates that the front and rear associated objects are an "or" relationship; in the formula, the character "/" indicates that the front and rear associated objects are a "division" relationship.
It will be appreciated that the various numerical numbers referred to in the embodiments of the present application are merely for ease of description and are not intended to limit the scope of the embodiments of the present application.
It should be understood that, in the embodiments of the present application, the sequence number of each process described above does not mean that the execution sequence of each process should be determined by the function and the internal logic of each process, and should not constitute any limitation on the implementation process of the embodiments of the present application.
Claims (13)
1. An impeller is characterized by comprising a hub and blades fixedly connected to the hub;
the camber line of the airfoil of the blade comprises a first camber line segment and a second camber line segment, wherein the first camber line segment is bent towards the opposite direction of the rotation direction of the impeller, and the second camber line segment is bent towards the rotation direction of the impeller;
The first arc line segment comprises a leading edge end, the second arc line segment comprises a trailing edge end, the leading edge end is located at one end of the first arc line segment, which is close to the rotating shaft of the hub, the trailing edge end is located at one end of the second arc line segment, which is far away from the rotating shaft of the hub, and one end of the first arc line segment, which is far away from the rotating shaft of the hub, is connected with one end of the second arc line segment, which is close to the rotating shaft of the hub.
2. The impeller of claim 1, wherein the camber line of the airfoil of the blade is a curve having a continuous curvature.
3. The impeller of claim 1 or 2, wherein the inlet angle of the blades is greater than or equal to 90 ° and less than or equal to 125 °;
the air inlet angle of the blade is an included angle between the direction of the tangent line of the first arc section at the front edge end pointing to the outer side of the impeller and the linear speed direction of the front edge end when the impeller rotates.
4. An impeller according to any one of claims 1 to 3, wherein the outlet angle of the blades is greater than or equal to 110 ° and less than or equal to 130 °;
the wind outlet angle of the blade is an included angle between the direction of the tangential line of the second arc section at the tail edge end pointing to the outer side of the impeller and the linear speed direction of the tail edge end when the impeller rotates.
5. The impeller of any one of claims 1-4, wherein the length of the first arc segment is less than the length of the second arc segment.
6. The impeller according to any one of claims 1-5, characterized in that the trailing edge end is located in front of the leading edge end in the direction of rotation of the impeller.
7. The impeller according to any one of claims 1 to 6, characterized in that the impeller comprises a plurality of said blades arranged at intervals along the circumference of the hub, an air flow passage being formed between two adjacent said blades, an air inlet end of said air flow passage being formed between the ends of two adjacent said blades adjacent the rotational axis of the hub;
the airflow channel includes a first flow channel section and a second flow channel section;
the air inlet end is positioned at one end of the first flow passage section close to the rotating shaft of the hub, and one end of the first flow passage section far away from the rotating shaft of the hub is communicated with one end of the second flow passage section close to the rotating shaft of the hub;
the through flow section of the first flow channel section is gradually reduced from the air inlet end to one end of the first flow channel section communicated with the second flow channel section;
the through flow cross section of the second flow channel section gradually increases from one end of the second flow channel section, which is communicated with the first flow channel section, to one end of the second flow channel section, which is far away from the rotating shaft of the hub.
8. The impeller according to claim 7, characterized in that a ratio of a length of the first flow passage section in an extending direction of the air flow passage to a length of the second flow passage section in the extending direction of the air flow passage is greater than or equal to 1/3 and less than or equal to 3/5.
9. The impeller according to claim 7 or 8, characterized in that the air flow channel further comprises a third flow channel section, an air outlet end of the air flow channel being formed between the ends of two adjacent blades remote from the rotational axis of the hub;
the air outlet end is positioned at one end of the third flow passage section far away from the rotating shaft of the hub, and one end of the second flow passage section far away from the rotating shaft of the hub is communicated with one end of the third flow passage section near the rotating shaft of the hub;
and the through flow section of the third flow passage section is kept unchanged from one end, communicated with the second flow passage section, of the third flow passage section to the air outlet end.
10. The impeller according to claim 9, characterized in that the ratio of the length of the third flow passage section in the direction of extension of the air flow passage to the length of the second flow passage section in the direction of extension of the air flow passage is greater than or equal to 1/2 and less than or equal to 4/5.
11. The impeller according to any one of claims 1-10, characterized in that the camber line of the airfoil of the blade is a fourth-order bezier curve, the leading edge end and the trailing edge end being respectively a start control point and an end control point of the fourth-order bezier curve;
after converting coordinates in the polar coordinate system of the impeller into coordinates in the rectangular coordinate system of the blade, in the rectangular coordinate system of the blade: the coordinates of a first intermediate control point, a second intermediate control point and a third intermediate control point of the fourth-order Bezier curve are (x 1, y1, x2, y2, x3, y 3) and (x 4, y 4), respectively;
the polar point in the impeller polar coordinate system is positioned on the rotating shaft of the hub, the polar angle of the front edge end in the impeller polar coordinate system is pi/2, the origin point of the blade rectangular coordinate system is positioned at the front edge end, the horizontal axis direction in the blade rectangular coordinate system is the same as the polar axis direction in the impeller polar coordinate system, and the forward direction of the longitudinal axis of the blade rectangular coordinate system is the direction that the front edge end points to the outer side of the impeller along the radial direction of the impeller;
-n is less than or equal to x1 is less than or equal to-0.4 n,0.8n is less than or equal to y1 is less than or equal to 1.4n,3.4n is less than or equal to x2 is less than or equal to 4n,3.2n is less than or equal to y2 is less than or equal to 3.8n,2.2n is less than or equal to x3 is less than or equal to 2.8n,5.4n is less than or equal to y3 is less than or equal to 6n,1.2n is less than or equal to x4 is less than or equal to 1.8n,7.2n is less than or equal to y4 is less than or equal to 7.8n, and n is a positive number.
12. A centrifugal fan comprising a volute and an impeller according to any one of claims 1-11, said impeller being mounted in said volute, a hub of said impeller being in rotational connection with said volute.
13. An electronic device comprising a housing and the centrifugal fan of claim 12, the volute of the centrifugal fan being mounted on the housing.
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| CN202311374322.8A CN117514902A (en) | 2023-10-20 | 2023-10-20 | Impeller, centrifugal fan and electronic device |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202311374322.8A CN117514902A (en) | 2023-10-20 | 2023-10-20 | Impeller, centrifugal fan and electronic device |
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