CN112524058B - Fan outer frame structure for inhibiting noise of cooling fan and modeling method thereof - Google Patents
Fan outer frame structure for inhibiting noise of cooling fan and modeling method thereof Download PDFInfo
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- CN112524058B CN112524058B CN202011414860.1A CN202011414860A CN112524058B CN 112524058 B CN112524058 B CN 112524058B CN 202011414860 A CN202011414860 A CN 202011414860A CN 112524058 B CN112524058 B CN 112524058B
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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
- F04D19/00—Axial-flow pumps
- F04D19/002—Axial flow fans
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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
- 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
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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
- F04D29/002—Details, component parts, or accessories especially adapted for elastic fluid pumps
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/325—Rotors specially for elastic fluids for axial flow pumps for axial flow fans
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/522—Casings; Connections of working fluid for axial pumps especially adapted for elastic fluid pumps
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/52—Casings; Connections of working fluid for axial pumps
- F04D29/54—Fluid-guiding means, e.g. diffusers
- F04D29/541—Specially adapted for elastic fluid pumps
- F04D29/545—Ducts
- F04D29/547—Ducts having a special shape in order to influence fluid flow
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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
- F04D29/663—Sound attenuation
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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)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a fan outer frame structure for inhibiting noise of an axial flow heat dissipation fan, which comprises a pipeline end wall, an inlet and outlet plane fixing support and a motor support, wherein the inlet and outlet plane fixing support is arranged on the pipeline end wall; the inlet and outlet plane fixing support is positioned on the outer side of the flow passage end wall and is connected with the outer surface of the flow passage end wall to form an integral structure; the end wall of the flow channel is a fixed wall interface of the fluid passage and is axially divided into an air inlet section, a middle section and an air outlet section; the motor support is any integer of column-shaped or blade-shaped support arranged on the plane of the fan outlet. The invention also discloses a method for manufacturing the outer frame structure of the fan. The invention can reduce the discrete tone noise of the cooling fan by a mode of acoustic mode cutoff, and can improve the air inlet flow of the axial flow cooling fan to further reduce the broadband and the discrete tone noise.
Description
Technical Field
The invention relates to the technical field of fan heat dissipation and noise reduction, in particular to a fan outer frame structure for inhibiting noise of an axial flow heat dissipation fan and a modeling method thereof.
Background
Axial-flow heat-dissipating fans are widely used for dissipating heat of various electronic devices, such as servers and communication router cabinets to realize forced convection heat exchange. With the integration of electronic devices becoming higher and higher, the demand for heat dissipation becomes more and more prominent, and the size of the heat dissipation fan used is gradually reduced, while the rotation speed is continuously increased to generate sufficient air volume. The heat dissipated by electronic devices arranged closely in a narrow space forms a high heat flux density, and usually a plurality of heat dissipation fans are combined to form a heat dissipation unit. The multiple fans operating at high speed create intolerable aerodynamic noise, which can cause significant trouble to people.
The main aerodynamic noise of the cooling fan at high rotation speed is the discrete single tone noise of blade passing frequency and harmonic waves thereof, which mainly comes from the mutual interference between the movable blade and the static blade. The dynamic and static interference structure of the cooling fan can generate acoustic modes which are transmitted along the axial direction, and the existing theory shows that the transmission of the acoustic modes in the pipeline meets the acoustic cutoff condition. In order to meet the installation requirements of arbitrary combination and arrangement of fans, a heat dissipation fan is often designed to be a square outer frame, and an installation hole is flush with an inlet and outlet plane; in addition, in order to keep the size of the fan as small as possible, the fan frame often fits the flow channel, which results in an incomplete air intake tapered section. The fan outer frame modeling mode introduces new noise sources, such as redundant interference noise caused by intake distortion. Although the common fan outer frame modeling mode is convenient to install and use, the common fan outer frame modeling mode is not necessary under some special conditions, and better noise reduction effect can be achieved under the condition that the installation is not influenced through the improvement of the outer frame modeling.
Therefore, those skilled in the art have made an effort to develop a fan frame structure capable of suppressing noise of an axial flow heat dissipation fan and a method for forming the same, so as to solve the noise problem of the heat dissipation fan at a high rotation speed.
Disclosure of Invention
In view of the defects in the prior art, the technical problem to be solved by the invention is how to achieve the acoustic cutoff of the pipeline and improve the inlet through the outer frame modeling of the fan on the premise of meeting the installation requirement so as to realize the effect of reducing the discrete noise and the broadband noise.
In order to achieve the above object, the present invention provides a fan outer frame structure for suppressing noise of an axial flow heat dissipation fan, which comprises a flow passage end wall, an inlet and outlet plane fixing support and a motor support; the inlet and outlet plane fixing support is positioned on the outer side of the flow channel end wall and is connected with the outer surface of the flow channel end wall to form an integral structure;
the end wall of the flow channel is a fixed wall interface of the fluid passage and is axially divided into an air inlet section, a middle section and an air outlet section; the air inlet section is a diameter gradually-reducing section, the air outlet section is a diameter gradually-expanding section, and the middle section is a fixed diameter section; the through-flow diameter D of the middle section is determined by the impeller diameter and the blade tip clearance requirement; according to the assembling relation between the fan outer frame and the impeller, the interface between the middle section and the air inlet section exceeds the front edge of the impeller blade in the upstream direction by a certain axial distance L, which is determined by the acoustic mode cut-off condition; the air inlet section is cut into uneven numbers S;
the motor support is a columnar or blade-shaped support arranged on the plane of the fan outlet in any integer, the motor support extends inwards from the air outlet section to form an integral structure, the support number V of the motor support is determined according to the interference mode of the movable blade number B and the uneven number S of the air inlet section, and the fan impeller and the motor are arranged on the motor support through a motor shaft.
Further, the relation between the distance L of the middle section exceeding the front edge of the impeller blade and the through-flow diameter D of the middle section meets the condition that L/D is more than or equal to 0.08 and less than or equal to 0.48.
Further, the inlet and outlet plane fixing support and the edge of the air inlet section are parallel and level or not parallel and level in the axial direction, and an embedded runner end wall model and an extended runner end wall model are correspondingly formed.
Further, the air inlet section is complete or cut into an incomplete tapered section, the air outlet section is complete or cut into an incomplete diverging section, and the circumferential direction of the corresponding cross section is a complete circular arc or a circular arc cut off by a straight line.
Further, a circumferential acoustic mode generated by interference between the number of struts V supported by the motor and the number of moving blades B and the number of intake stage unevenness S satisfies m ≠ nB ± kV ± iS, n ═ 1,2,3 … denotes a harmonic number of blade passing frequencies, k ═ 0,1,2 … denotes a spatial harmonic number of interference caused by stationary blade unevenness, i ═ 0,1,2 … denotes a spatial harmonic number of interference caused by inlet unevenness, and the number of struts V iS selected such that m ≠ 0.
Further, the air inlet section and the middle section are provided with micro-perforated structures or wall surface sunken structures beyond the front edge part of the impeller.
Furthermore, the micro-perforated plate structure is tightly attached to the end wall of the flow channel, the aperture and the porosity of the micro-perforated plate change along with the frequency of main noise, the plate thickness of the micro-perforated plate is not more than 1mm, the aperture is not more than 1mm, and the porosity is within the range of 1% -3%.
Further, the recess of the wall surface recess structure is a part of ellipsoid shape formed by hollowing towards the inside of the wall surface.
Furthermore, the wall surface concave structure is a plurality of rows of concave areas which are arranged in a lattice manner along the axial direction and staggered or aligned along the circumferential direction, and the aperture, the depth and the arrangement density of the concave areas are changed along with the flowing state of the inlet air and the frequency of the main noise.
The invention provides a method for manufacturing a fan outer frame structure for inhibiting noise of an axial flow heat radiation fan, which comprises the following steps:
The invention has at least the following beneficial technical effects:
1. the fan outer frame structure for inhibiting the noise of the cooling fan provided by the invention has the advantages that the through-flow section with the unchanged diameter of the end wall of the fan flow channel extends upstream to exceed the front edge for a distance to form a local short pipeline to realize the sound cut-off of the pipeline, and the combined action of the number of the movable and static blades and the uneven number of the inlet has an inhibiting effect on the axial propagation of the interference sound mode of the constructed cooling fan.
2. The fan outer frame structure for inhibiting the noise of the cooling fan improves the air inlet flow of the fan through the air inlet section model, and further noise reduction is realized.
The conception, the specific structure and the technical effects of the present invention will be further described with reference to the accompanying drawings to fully understand the objects, the features and the effects of the present invention.
Drawings
FIG. 1 is a schematic three-dimensional assembly of an embodiment of an integral inlet section with an embedded flow passage end wall according to the present invention;
FIG. 2 is a schematic rear perspective three-dimensional assembly of an embodiment of the integral intake section of the end wall of the embedded flowpath of the present invention;
fig. 3 is a schematic assembly view of an embodiment of an in-line flow path end wall S-4 incomplete inlet section of the present invention;
fig. 4 is a schematic view of the assembly of an embodiment of the present invention with an embedded flow passage end wall S-6 incomplete inlet section;
FIG. 5 is an assembled schematic view of an embodiment of an epitaxial flow channel end wall of the present invention;
fig. 6 is an assembly view of an embodiment of an epitaxial flow channel end wall with a wall recess structure of the present invention.
Wherein: 1-flow channel end wall, 2-inlet and outlet plane fixing support, 3-movable vane impeller, 4-air inlet section, 5-middle section, 6-air outlet section, 7-motor support, 8-incomplete air inlet section, 9-bell mouth and 10-wall surface concave structure.
Detailed Description
The technical contents of the preferred embodiments of the present invention will be more clearly and easily understood by referring to the drawings attached to the specification. The present invention may be embodied in many different forms of embodiments and the scope of the invention is not limited to the embodiments set forth herein.
In the drawings, structurally identical elements are represented by like reference numerals, and structurally or functionally similar elements are represented by like reference numerals throughout the several views.
Example 1
As shown in fig. 1 and fig. 2, the embodiment discloses a fan outer frame structure with an embedded complete air inlet section of a flow channel end wall, which includes a flow channel end wall 1, an inlet and outlet plane fixing support 2, and a motor support 7; the inlet and outlet plane fixing support 2 is positioned on the outer side of the flow channel end wall 1 and is connected with the outer surface of the flow channel end wall 1 to form an integral structure. The flow channel end wall 1 is a fixed wall boundary of a fluid passage and is axially divided into an air inlet section 4, a middle section 5 and an air outlet section 6; the gas inlet section 4 is a diameter reducing section, the gas outlet section 6 is a diameter reducing section, and the middle section 5 is a fixed diameter section; the through-flow diameter D of the middle section 5 is determined by the diameter of the impeller and the blade tip clearance required by meeting the aerodynamic performance requirement of the fan; according to the assembly relation of the outer frame and the impeller, the interface of the middle section 5 and the air inlet section 4 exceeds the impeller blade in the upstream direction by a certain axial distance L, which is determined by the acoustic mode cut-off condition; the intake section 4 is cut into uneven numbers S.
The motor supports 7 are column-shaped or blade-shaped supports arranged on the plane of the fan outlet in any integer, extend inwards from the air outlet section 6 to form an integral structure, and the support number V of the motor supports 7 is determined according to the interference sound mode generated by the moving blade number B and the uneven number S of the air inlet section. The fan impeller and the motor are arranged on the motor support 7 through a motor shaft.
As shown in fig. 1, the axial-flow heat dissipation fan with the dynamic-static interference structure generates discrete single-tone noise related to the rotation speed N (unit rpm) and the number B of moving blades, i.e., a single tone with the blade passing frequency BPF ═ B × N/60 and its harmonics, and generates an acoustic mode (m, N) propagating along the axial direction at the corresponding single-tone frequency, where m is the number of circumferential modes and N is the number of radial modes. These acoustic modes are rotating and propagating outward in the free market. Extending the intermediate section 5 upstream a distance L forms a short pipe section of diameter D and length L. Due to the cut-off effect of the acoustic mode of the pipeline, the acoustic mode propagated upstream by the fan is cut off in a certain rule in the short pipeline area, whether the specific acoustic mode is cut off or not is related to the diameter D and the rotating speed N of the fan, and the cut-off effect is related to the axial distance L.
The inner diameter D of the middle section 5 is determined according to the requirement of the impeller diameter and the blade top clearance of the cooling fan, and the acoustic mode cut-off condition f < c0kmnThe/2 π can result in acoustic modes (m, n) which are cut off at different frequencies f, where c0Is the speed of sound, kmnIs the radial wave number associated with the mode numbers m and n and the pipe diameter D, the larger m and n are, the larger k ismnThe larger the mode, the easier it is to cut off. The modes of these cutoffs decay exponentially within the pipe, with the amplitude varying with the distance traveled within the pipe as | Ae-j·kx·xWhere A is the modal amplitude without cutoff, kxIs the circumferential wavenumber, x is the axial propagation distance, kmnThe larger k isxThe smaller, i.e. the larger m, n, the faster the amplitude decays. In order to achieve a certain acoustic mode stopping effect, in combination with the external dimension axial limitation of the fan installation, when the influence on the flow performance is small, the axial distance x of the middle section 5 beyond the front edge of the impeller blade is selected to be L, and the axial distance x is selected within the range of 0.08-L/D-0.48.
In the embodiment, a square outer frame can be selected without special requirements in installation, and the inlet and outlet plane fixing support 2 is flush with the edges of the air inlet section 4 and the air outlet section 6 to form an end wall model of the embedded flow channel. If the length and the width of the fixing support are not limited, the size of the inlet and outlet plane fixing support 2 can exceed the maximum diameter of the air inlet section 4 and the air outlet section 6, the complete air inlet section and the complete air outlet section are reserved, and the diameter reducing or gradually expanding rule of the air inlet section and the air outlet section is selected to be linear change.
As shown in fig. 3, if the length and width are required to be as small as possible, the access plane fixing bracket 2 is as close as possible to the middle section 5, but obviously not smaller than the diameter of the middle section 5. According to the formula of calculation of the interference axial mode, m iS λ B ± kV ± iS, λ iS 1,2,3 …, k, i iS 0,1,2 …, V ≠ m- λ B ± iS)/(± k) (k ≠ 0), since the moving blade number B iS 7, the inlet nonuniformity number S iS 4, in order to avoid the case that m iS 0, m ≠ 0 iS substituted into the expression of V, and V ≠ 1,3,5,7,9,11,13,15 iS obtained when λ iS 1 (it iS meaningless to calculate only 15 or less, and more supported numbers are meaningless); v ≠ 1,2,3,5,6,7,10,14 when λ ≠ 2; v ≠ 1,3,5,9,13 when λ ≠ 3; BPF harmonics with λ >3 may not be considered with smaller amplitudes, so the number of supports V is a better choice, 4,8, 12.
As shown in fig. 4, when considering an application scenario in which fans are closely arranged in parallel, the regular hexagonal outer frame can more effectively use space than the square outer frame. In this case, the number of moving blades B is 7, the number of inlet unevenness S is 6, and the number of supports V can be selected to be 6 or 12 by substituting m ≠ 0 into the expression of V to obtain V ≠ 1,2,3,4,5,7, and the like when λ is 1,2, and 3.
Specifically, when the fan outer frame structure is used, firstly, a fan outer frame structure is manufactured according to the impeller of the cooling fan and the external size, wherein the diameter D of the middle section 5 is determined according to the requirements of the diameter of the impeller and the clearance of the blade top, the axial distance L of the middle section 5 exceeding the front edge of the blade of the impeller is determined according to the acoustic mode stop condition, the shape, the size and the axial position of the inlet and outlet plane fixing support 2 are determined according to the installation requirement, the tapered shape of the air inlet section 4 and the tapered shape of the air outlet section 6 are determined according to the position and the shape of the inlet and outlet plane fixing support 2, and the support number V is designed according to the interference acoustic mode generated by the number B of movable blades and the uneven number S of the air inlet section; then assemble fan frame structure and electrode and impeller, test noise index, judge whether further set up the microperforated panel and avoid the sunk structure.
Example 2
As shown in fig. 5, when external installation is required, such as improvement of inlet flow influence of backflow caused by heat dissipation components under parallel fans, and when the fans are not required to be closely arranged, the inlet/outlet plane fixing support 2 and the edge of the air inlet section 4 are not flush to form an extended flow channel end wall model, and the flared tapered section is matched to eliminate the influence of backflow as much as possible. The inlet and outlet plane fixing bracket 2 can be close to the middle section 5 in size without influencing the integrity of the air inlet section 4. The rest of the design is similar to example 1.
Example 3
As shown in fig. 6, based on embodiments 1 and 2, the air inlet section 4 may further be provided with a micro-perforated plate or a wall recess structure, and corresponding micro-perforated plate and recess structure parameters are determined according to the flow state and the radiation noise frequency under the main operating condition of the fan. If a micro-perforated plate structure is adopted, the micro-perforated plate structure is tightly attached to the end wall 1 of the flow channel, the aperture and the porosity change along with the frequency of main noise, the plate thickness of the micro-perforated plate is not more than 1mm, the aperture is not more than 1mm, and the porosity is within the range of 1% -3%. If a wall surface sunken structure is adopted, the sunken part is in the shape of a partial ellipsoid hollowed into the wall surface, a plurality of rows are formed along the axial direction, the notches are staggered or aligned along the circumferential direction to form a lattice arrangement area, the aperture, the depth and the arrangement density of the lattice arrangement area change along with the air inlet flowing state and the main noise frequency, and the flow and noise comprehensive test is required.
Example 4
For the complex series-parallel arrangement of fans, the outer frame structure of the fans in the embodiments 1 to 3 is also applicable, and different outer frame structures can be correspondingly designed to meet the installation requirements.
The fan outer frame structure for inhibiting the noise of the cooling fan and the modeling method thereof can reduce the discrete single tone noise of the cooling fan in an acoustic mode cut-off mode, improve the air inlet flow of the axial flow cooling fan, realize the further reduction of the broadband and the discrete single tone noise, and have good technical effects.
The foregoing detailed description of the preferred embodiments of the invention has been presented. It should be understood that numerous modifications and variations could be devised by those skilled in the art in light of the present teachings without departing from the inventive concepts. Therefore, the technical solutions available to those skilled in the art through logic analysis, reasoning and limited experiments based on the prior art according to the concept of the present invention should be within the scope of protection defined by the claims.
Claims (1)
1. A method for manufacturing a fan outer frame structure for inhibiting noise of an axial flow heat radiation fan comprises a flow channel end wall, an inlet and outlet plane fixing support and a motor support, wherein the inlet and outlet plane fixing support is positioned on the outer side of the flow channel end wall and is connected with the outer surface of the flow channel end wall to form an integral structure, the flow channel end wall is a fixed wall interface of a fluid passage and is axially divided into an air inlet section, a middle section and an air outlet section, the air inlet section is a diameter reducing section, the air outlet section is a diameter gradually expanding section, the middle section is a fixed diameter section, the through-flow diameter D of the middle section is determined by the requirements of the diameter of an impeller and the clearance of a blade tip, according to the assembly relationship of the fan outer frame and the impeller, the interface of the middle section and the air inlet section exceeds the front edge of the impeller blade by a section of axial distance L in the upstream direction and is determined by the acoustic mode stop condition, the air inlet section is cut into uneven numbers S, wall surface concave structures are arranged on the portions, exceeding the front edge of the impeller, of the air inlet section and the middle section, the motor support is a columnar or blade-shaped support arranged on the plane of a fan outlet in any integer, the air outlet section extends inwards to form an integral structure by intersecting with an axis, the support number V of the motor support is determined according to the interference mode of the moving blade number B and the uneven number S of the air inlet section, and the fan impeller and the motor are arranged on the motor support through a motor shaft, and the method is characterized by comprising the following steps of:
step 1, a fan outer frame structure is manufactured according to a fan impeller and the external size, the diameter D of the middle section is determined according to the impeller diameter and the blade top gap requirement, the axial distance L of the middle section exceeding the front edge of an impeller blade is determined according to the outer frame, the impeller assembly relation and the acoustic mode cutoff condition, the shape, the size and the axial position of an inlet and outlet plane fixed support are determined according to the installation requirement, the tapered shape of an air inlet section and the tapered shape of an air outlet section are determined according to the position and the shape of the inlet and outlet plane fixed support, and the support number V is designed according to the interference mode generated by the moving blade number B and the uneven number S of the air inlet section;
step 2, assembling the fan outer frame structure in the step 1 with a motor and an impeller, and testing noise indexes;
step 3, determining whether a micro-perforated plate and a wall surface sunken structure are further arranged according to the noise index of the fan assembled in the step 2, and determining corresponding micro-perforated and sunken structure parameters according to the flow state and the radiation noise frequency under the main working condition of the fan; go back to step 2 and so on.
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| CN202011414860.1A CN112524058B (en) | 2020-12-04 | 2020-12-04 | Fan outer frame structure for inhibiting noise of cooling fan and modeling method thereof |
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| CN202011414860.1A CN112524058B (en) | 2020-12-04 | 2020-12-04 | Fan outer frame structure for inhibiting noise of cooling fan and modeling method thereof |
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| 电子器件轴流冷却风扇气动噪声周向模态试验;孙宗翰，田杰，欧阳华， 等;《机械工程学报》;20200930;第56卷(第18期);164-171页 * |
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