CN116428213A - Flat-disk fan impeller and design method thereof - Google Patents

Flat-disk fan impeller and design method thereof Download PDF

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Publication number
CN116428213A
CN116428213A CN202310255698.0A CN202310255698A CN116428213A CN 116428213 A CN116428213 A CN 116428213A CN 202310255698 A CN202310255698 A CN 202310255698A CN 116428213 A CN116428213 A CN 116428213A
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blade
inlet
impeller
coefficient
flat
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刘燕潇
朱金杰
马天杰
王俊泽
李蕾
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Zhejiang Shangfeng High Tech Special Wind Industry Co ltd
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Zhejiang Shangfeng High Tech Special Wind Industry Co ltd
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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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/20—Design optimisation, verification or simulation
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation

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  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

The application discloses a flat-disk fan impeller and a design method thereof, and belongs to the field of fans. The front disc and the rear disc are of a straight structure, and the main blades are fixedly connected with the front disc and the rear disc respectively in a welding way; and a sub-blade is arranged on one side of the pressed surface of the main blade, and the sub-blade is detachably connected with the main blade through a connecting piece. The flat disc type fan impeller has the beneficial effects of being simple in structure, low in manufacturing difficulty and short in maintenance time and the design method of the flat disc type fan impeller.

Description

Flat-disk fan impeller and design method thereof
Technical Field
The application relates to the technical field of fans, in particular to a flat-disk fan impeller and a design method thereof.
Background
The fan is widely applied to various fields of national economy as gas conveying equipment, and in the use process of the fan in various fields, as the front disc of the impeller mostly adopts an arc-shaped front disc or a conical impeller front disc, the manufacturing process of the fan is complex, and particularly, the large fan impeller with the arc-shaped front disc needs large spinning equipment, is complex in manufacturing and processing and has long manufacturing period.
Meanwhile, in the actual use process of the fan, the fan runs for a long time and contains special gases such as dust and the like, so that the abrasion of impeller blades can be caused, and the normal operation of the fan is influenced. When the fan is replaced, the whole rotor needs to be replaced, the replacement period is long, the downtime is long, and the normal production of users is affected. How to simplify the impeller structure and the manufacturing difficulty and reduce the maintenance time becomes a problem to be solved urgently in the fan industry.
Disclosure of Invention
The content of the present application is intended to introduce concepts in a simplified form that are further described below in the detailed description. The section of this application is not intended to identify key features or essential features of the claimed subject matter, nor is it intended to be used to limit the scope of the claimed subject matter.
In order to solve the technical problems mentioned in the background art section above, some embodiments of the present application provide a flat disk fan impeller, including a front disk, a rear disk and a plurality of main blades, where the front disk and the rear disk are in a flat structure, and the main blades are welded and fixedly connected with the front disk and the rear disk respectively; and a sub-blade is arranged on one side of the pressed surface of the main blade, and the sub-blade is detachably connected with the main blade through a connecting piece.
The invention also discloses a design method of the flat-disk fan impeller, which comprises the following steps:
a. calculating the effective diameter D of the impeller outlet 2 Impeller and vane inlet diameter D 0 、D 1 Blade inlet height b 1 Selecting blade inlet angle beta b1 Selecting blade outlet angle beta b2 Calculating blade outlet width value b 2 The number of blades Z;
b. calculation check omega 1 /ω 2 Value, judge whether to meet the preset omega 1 /ω 2 ；
c. Checking the air quantity and the air pressure, and judging whether the design requirement is met;
d. programming and calculating EXCEL, marking and classifying input value columns and process formula columns, and adjusting parameters of inlet and outlet angles of blades to enable b to be 1 ,b 2 Basically equal, output impeller parameters;
e. according to the output impeller parameters, three-dimensional modeling and CFD analysis are carried out, the design result is checked, if the design requirement is met, a final design scheme is output; if the requirements are not met, the design parameters are adjusted according to the calculated performance parameters and the flow field information until the design requirements are met.
Further, in step a, D 2 The calculation formula of (2) is as follows:
D 2 ＝60*U 2 /n/π；
wherein n is s =5.54 n (Q/3600)/(0.5/(1.2×p/ρ)/(0.75); (based on the calculated n s Looking up FIG. 3-specific speed n s Map of relationship with pressure coefficient psi, select psi value
U 2 ＝(2P/ρ/ψ)^0.5；
Wherein Q is the flow rate (unit m of the input fan 3 P is the total pressure (unit Pa), n is the rotating speed (unit rpm) of the fan, and ρ is the density (unit kg/m) of the gas medium 3 ) Psi is the fan pressure coefficient, n s U is the specific rotation speed of the fan 2 The linear velocity of the impeller (unit m/s).
10. The flat disk fan impeller and design method thereof according to claim 3, wherein: d in step a 0 、D 1 The calculation formula of (2) is as follows:
D 0 ＝D 1 ＝k*((Q/3600/η v /n/μ 0 /(1-ν*ν))^(1/3))；
where k=3.25 ((ζ) i +ζ r +ζ 1 *ζ 1 *ζ b )/ζ b )^(1/6)；
Wherein ζ i Zeta is the air intake loss coefficient r Zeta for axial variation of radial loss coefficient b Zeta is the internal loss coefficient of the impeller 1 For the blade inlet coefficient, v is the hub-to-diameter ratio，η v Mu, for volumetric efficiency 0 The flow filling coefficient is the impeller inlet section, and k is the correction coefficient.
Further, in step a, b 1 The calculation formula of (2) is as follows:
b 1 ＝D 1 /4*(1-ν*ν)*μ o /ζ 1 /μ 1 ；
wherein mu 1 The vane inlet airflow is filled with coefficients.
Further, the calculation formula of Z in step a is as follows:
Z＝2.1*σ*(D 2 +D 1 )/(D 2 -D 1 )；
wherein sigma is the density of the blade grid, Z 1 For inlet blade number, Z 2 For the number of outlet blades, Z 1 、Z 2 And obtaining the Z through rounding obtained by calculation.
Further, in step a, b 2 The calculation formula of (2) is as follows:
b 2 ＝b 1 *ω 1 /ω 2 *μ 1 /μ 2 *(π*D 1 *SIN(β b1 /180*π)-δ*Z 1 )/(π*D 2 *SIN(β b2 /180*π)-Z 2 *δ)；
wherein beta is b1 Beta is b1' Rounding value, beta b1' ＝TANH(β b1' /π*180)；
TAN(β b1' /π*180)＝C 1r’ /U 1 ；
C 1r’ ＝Q/3600/η v /(D 1 *π*b 1 *μ 1 )；
U 1 ＝D 1 /2*(n*π/30)；
Wherein mu 2 For the vane outlet airflow filling coefficient, delta is vane thickness, beta b1 Is the blade inlet angle (degree), beta b1' C is the blade front inlet angle (degree) 1r’ For vane inlet front radial velocity, U 1 Is the impeller inlet linear velocity.
Further, ω is preset in step b 1 /ω 2 Calculation check ω=1.8 1 /ω 2 Value, determine whether ω is satisfied 1 /ω 2 ≤1.8；
Wherein omega 1 The calculation formula of (2) is as follows:
ω 1 ＝C 1r /SIN(β b1 /180*π)；
wherein C is 1r ＝C 1r’ /τ 1 ；
τ 1 ＝1-δ/SIN(β b1 /180*π)/D 1 /π*Z 1 ；
Wherein τ 1 C for the blade inlet section blocking coefficient 1r For vane inlet radial velocity, ω 1 Relative speed for vane inlet;
ω 2 the calculation formula of (2) is as follows:
ω 2 ＝C 2r /SIN(β b2 /180*π)；
wherein C is 2r ＝Q/3600/η v /π/D 2 /b 2 /τ 2 /μ 2 ；
τ 2 ＝1-δ/SIN(β b2 /180*π)/D 2 /π*Z 2 ；
Wherein τ 2 C is the blocking coefficient of the section of the blade outlet 2r For vane exit radial velocity, ω 2 Is the relative velocity of the blade outlet.
Further, the checking formula of the air volume in the step c is as follows:
Q＝η v *τ 1 *π*D 1 *b 1 *C 1r’ *3600；
the checking formula of wind pressure is as follows:
P＝η h *μ*ρ*π^2*n^2*(D 2 ^2-D 1 ^2*b 2 /b 1 *TANβ b1' /TAN(β b2 /180*π))/60^2；
wherein μ=1/(1+ (1.5+1.1×β) b2 /90)/24/(1-(D 1 /D 2 ) 2 ))
Wherein eta h For flow efficiency, μ is the slip coefficient.
The beneficial effects of this application lie in: the flat-disk fan impeller has the advantages of simplified impeller structure, low manufacturing difficulty and short maintenance time, and a design method thereof.
Drawings
The accompanying drawings, which are incorporated in and constitute a part of this application, are included to provide a further understanding of the application and to provide a further understanding of the application with regard to the other features, objects and advantages of the application. The drawings of the illustrative embodiments of the present application and their descriptions are for the purpose of illustrating the present application and are not to be construed as unduly limiting the present application.
In addition, the same or similar reference numerals denote the same or similar elements throughout the drawings. It should be understood that the figures are schematic and that elements and components are not necessarily drawn to scale.
In the drawings:
FIG. 1 is an overall schematic diagram according to an embodiment of the present application;
FIG. 2 is a schematic structural view of a portion of an embodiment;
FIG. 3 is a graph of the specific rotation speed n s And a pressure coefficient psi relationship graph.
Detailed Description
Embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. While certain embodiments of the present disclosure are shown in the drawings, it should be understood that the present disclosure may be embodied in various forms and should not be construed as limited to the embodiments set forth herein. Rather, these embodiments are provided so that this disclosure will be thorough and complete. It should be understood that the drawings and embodiments of the present disclosure are for illustration purposes only and are not intended to limit the scope of the present disclosure.
It should be noted that, for convenience of description, only the portions related to the present invention are shown in the drawings. Embodiments of the present disclosure and features of embodiments may be combined with each other without conflict.
It should be noted that the terms "first," "second," and the like in this disclosure are merely used to distinguish between different devices, modules, or units and are not used to define an order or interdependence of functions performed by the devices, modules, or units.
It should be noted that references to "one", "a plurality" and "a plurality" in this disclosure are intended to be illustrative rather than limiting, and those of ordinary skill in the art will appreciate that "one or more" is intended to be understood as "one or more" unless the context clearly indicates otherwise.
The present disclosure will be described in detail below with reference to the accompanying drawings in conjunction with embodiments.
As shown in fig. 1-2, a flat-disk fan impeller comprises a front disk 4, a rear disk 5 and a plurality of main blades 2, wherein the front disk 4 and the rear disk 5 are of a flat structure, and the main blades 2 are welded and fixedly connected with the front disk 4 and the rear disk 5 respectively to serve as a main body framework. Because the front disc of the impeller is straight and the blades are flat, the problems of complex manufacturing process and difficult replacement after the blades are worn of the conventional impeller can be effectively solved, production equipment such as a spinning machine and the like can be omitted, and the manufacturing process is simple. The main blade 2 is provided with a sub-blade 1 on one side of a pressed surface, namely an air inlet side, the sub-blade 1 is detachably connected with the main blade 2 through a connecting piece 3, and the material can be in the form of a butt welding wear-resistant layer blade or a special wear-resistant material blade. In this embodiment, the connecting member 3 is riveted or bolted, and the connection is more secure by using a multi-point arrangement. Preferably, the front plate 4 is arranged in an arc shape or a cone shape corresponding to the inlet position of the blade, so that the airflow is smoothly guided into the blade. When the dust concentration is high, the pressure surface inlet and outlet of the blade are most easily damaged, after the fan runs for a long time, only the sub-blade is required to be replaced when the impeller is replaced, the whole rotor is not required to be replaced, the damaged sub-blade can be removed on site of a user, the damaged sub-blade is extracted from the impeller, the new sub-blade is assembled, and the maintenance time and the shutdown loss of the user are reduced.
The design method of the fan impeller comprises the following steps:
a. calculating the effective diameter D of the impeller outlet 2 Impeller and vane inlet diameter D 0 、D 1 Blade inlet height b 1 Selecting blade inlet angle beta b1 Selecting blade outlet angle beta b2 Calculating blade outlet width value b 2 The number of blades Z;
b. calculation check omega 1 /ω 2 Value, judge whether to meet the preset omega 1 /ω 2 ；
c. Checking the air quantity and the air pressure, and judging whether the design requirement is met;
d. programming and calculating EXCEL, marking and classifying input value columns and process formula columns, and adjusting parameters of inlet and outlet angles of blades to enable b to be 1 ,b 2 Basically equal, output impeller parameters; the design process table of the whole machine is shown in table 1.
e. According to the output impeller parameters, three-dimensional modeling and CFD analysis are carried out, the design result is checked, if the design requirement is met, a final design scheme is output; if the requirements are not met, the design parameters are adjusted according to the calculated performance parameters and the flow field information until the design requirements are met.
The specific operation is as follows: the input fan flow q=12000 (unit m 3 Per h), fan total pressure p=3500 (unit Pa), fan rotational speed n=1450 (unit rpm), gas medium density ρ=1.2 (unit kg/m 3). Selecting an air intake loss coefficient ζ i =0, axial-to-radial loss coefficient ζ r =0.2, impeller internal loss coefficient ζ b Blade inlet coefficient ζ=0.2 1 =0.85, hub diameter ratio v=0.3, volumetric efficiency η v =0.95, impeller inlet section airflow fullness coefficient μ o =1, vane inlet airflow fullness coefficient μ 1 =0.9, blade outlet airflow fullness coefficient μ 2 Flow efficiency η =0.85 h Blade thickness δ=0.004 m, cascade density σ=1.8, =0.95.
According to formula n s =5.54 n (Q/3600)/(0.5/(1.2×p/ρ)/(0.75), calculating the fan specific rotation speed n s ，n s =32.23. From the calculated n S And fig. 3, selecting an appropriate fan pressure coefficient ψ, selecting ψ=1.123; according to formula U 2 = (2P/ρ/ψ)/(0.5), the impeller linear velocity U was calculated 2 =72 m/s; and according to formula D 2 ＝60*U 2 N/pi; calculating to obtain D 2 ＝0.95m。
Then according to the formula:
D 0 ＝D1＝k*((Q/3600/η v /n/μo/(1-ν*ν))^(1/3))
k＝3.25*((ζ i +ζ r +ζ 1 *ζ 1 *ζ b )/ζ b )^(1/6)
calculating to obtain D 0 ＝D 1 =0.493 m, correction coefficient k= 3.558.
According to the formula: b 1 ＝D 1 /4*(1-ν*ν)*μ o /ζ 1 /μ 1 Calculating to obtain b 1 ＝0.1466m。
From the calculated beta b1' Value selection of blade inlet angle beta b1 : according to the formula:
β b1' ＝TANH(TANβ b1' )/π*180
wherein TAN beta b1' ＝C 1r’ /U 1 ，
C 1r’ ＝Q/3600/η v /(D 1 *π*b 1 *μ 1 )，
U 1 ＝D 1 /2*(n*π/30)，
β b1' ＝TANH(TANβ b1' )/π*180
Wherein C is 1r’ For vane inlet front radial velocity, U 1 For impeller inlet linear velocity, beta b1' Is the blade front inlet angle;
calculating to obtain C 1r’ ＝17.17m/s，U 1 ＝37.43m/s，TANβ b1' ＝0.4587，β b1' ＝24.58°。
Selecting blade inlet angle beta b1 ＝27.8°。
According to the calculation formula: z=2.1 σ (D 2 +D 1 )/(D 2 -D 1 ) Calculated is z= =11.95, Z 1 、Z 2 Z is obtained by rounding the calculated Z 1 ＝Z 2 Taking 12 tablets.
Selecting blade outlet angle beta b2 =26.5°, according to the calculation formula:
b 2 ＝b 1 *ω 1 /ω 2 *μ 1 /μ 2 *(π*D 1 *SIN(β b1 /180*π)-δ*Z 1 )/(π*D 2 *SIN(β b2 /180*π)-Z 2 *δ)，
calculating to obtain b 2 ＝0.14688m。
Presetting omega in step b 1 /ω 2 ＝1.8，
ω 1 The calculation formula of (2) is as follows:
ω 1 ＝C 1r /SIN(β b1 /180*π)；
wherein C is 1r ＝C 1r’ /τ 1 ；
τ 1 ＝1-δ/SIN(β b1 /180*π)/D 1 /π*Z 1 ；
Wherein omega 1 For vane inlet relative velocity, C 1r For vane inlet radial velocity τ 1 The blocking coefficient of the inlet section of the blade;
calculated τ 1 ＝0.9335，C 1r ＝18.39m/s，ω 1 ＝39.44m/s。
ω 2 The calculation formula of (2) is as follows:
ω 2 ＝C 2r /SIN(β b2 /180*π)；
wherein C is 2r ＝Q/3600/η v /π/D 2 /b 2 /τ 2 /μ 2 ；
τ 2 ＝1-δ/SIN(β b2 /180*π)/D 2 /π*Z 2 ；
Wherein τ 2 C is the blocking coefficient of the section of the blade outlet 2r For vane exit radial velocity, ω 2 Is the relative velocity of the blade outlet.
Calculated τ 2 ＝0.964，C 2r ＝9.78m/s，ω 2 ＝＝21.9m/s，ω 1 /ω 2 =1.8, meeting the preset requirements.
The checking formula of the air quantity in the step c is as follows:
Q＝η v *τ 1 *π*D 1 *b 1 *C 1r’ *3600；
the checking formula of wind pressure is as follows:
P＝η h *μ*ρ*π^2*n^2*(D 2 ^2-D 1 ^2*b 2 /b 1 *TAN(β b1 /180*π)/TAN(β b2 /180*π))/60^2；
where μ is the slip coefficient, μ=1/(1+ (1.5+1.1×β) b2 /90)/24/(1-(D 1 /D 2 ) 2 ))
Calculated μ=0.906, air volume q= 12447m 3 And/h, wind pressure p=3830 Pa.
After the operation of the step d, three-dimensional modeling and CFD analysis are carried out according to the output impeller parameters, the CFD calculation is basically consistent with the actual prototype test result, and the air quantity is 12000m 3 And when the pressure is 3620Pa, the working condition efficiency is highest, the maximum efficiency of the fan is 86.6%, and the designed fan meets the requirements.
TABLE 1
Figure BDA0004129511670000091
Figure BDA0004129511670000101
The foregoing description is only of the preferred embodiments of the present disclosure and description of the principles of the technology being employed. It will be appreciated by those skilled in the art that the scope of the invention in the embodiments of the present disclosure is not limited to the specific combination of the above technical features, but encompasses other technical features formed by any combination of the above technical features or their equivalents without departing from the spirit of the invention. Such as the above-described features, are mutually substituted with (but not limited to) the features having similar functions disclosed in the embodiments of the present disclosure.

Claims (9)

1. A flat-disk fan impeller comprises a front disk, a rear disk and a plurality of main blades, wherein the front disk and the rear disk are of flat structures, and the main blades are fixedly connected with the front disk and the rear disk respectively in a welding way; the method is characterized in that: and one side of the pressed surface of the main blade is provided with a sub-blade, and the sub-blade is detachably connected with the main blade through a connecting piece.
2. The method of designing a flat-disk fan impeller of claim 1, wherein: the method comprises the following steps:
a. calculating the effective diameter D of the impeller outlet 2 Impeller and vane inlet diameter D 0 、D 1 Blade inlet height b 1 Blade front inlet angle beta b1’ Selecting the inlet angle beta of the blade b1 Selecting blade outlet angle beta b2 Calculating blade outlet width value b 2 The number of blades Z;
b. calculation check omega 1 /ω 2 Value, judge whether to meet the preset omega 1 /ω 2 ；
c. Checking the air quantity and the air pressure, and judging whether the design requirement is met;
d. programming and calculating EXCEL, marking and classifying input value columns and process formula columns, and adjusting parameters of inlet and outlet angles of blades to enable b to be 1 ,b 2 Basically equal, output impeller parameters;
e. according to the output impeller parameters, three-dimensional modeling and CFD analysis are carried out, the design result is checked, if the design requirement is met, a final design scheme is output; if the requirements are not met, the design parameters are adjusted according to the calculated performance parameters and the flow field information until the design requirements are met.
3. The flat disk fan impeller and design method thereof according to claim 2, characterized in that: d in step a 2 The calculation formula of (2) is as follows:
D 2 ＝60*U 2 /n/π；
wherein n is s =5.54 n (Q/3600)/(0.5/(1.2×p/ρ)/(0.75); (based on the calculated ns, look up FIG. 3-relation between the specific rotation speed ns and the pressure coefficient ψ, select the value ψ)
U 2 ＝(2P/ρ/ψ)^0.5；
Wherein Q is the flow rate (unit m of the input fan 3 Per h), P is the total pressure (unit Pa), n is the rotation speed (unit rpm), ρ is the density of the gas mediumDegree (unit kg/m) 3 ) Psi is the fan pressure coefficient, n s U is the specific rotation speed of the fan 2 The linear velocity of the impeller (unit m/s).
4. The flat disk fan impeller and design method thereof according to claim 3, wherein: d in step a 0 、D 1 The calculation formula of (2) is as follows:
D 0 ＝D 1 ＝k*((Q/3600/η v /n/μ 0 /(1-ν*ν))^(1/3))；
where k=3.25 ((ζ) i +ζ r +ζ 1 *ζ 1 *ζ b )/ζ b )^(1/6)；
Wherein ζ i Zeta is the air intake loss coefficient r Zeta for axial variation of radial loss coefficient b Zeta is the internal loss coefficient of the impeller 1 For the inlet coefficient of the blade, v is the hub diameter ratio, eta v Mu, for volumetric efficiency o The flow filling coefficient is the impeller inlet section, and k is the correction coefficient.
5. The flat disk fan impeller and design method thereof according to claim 4, wherein: b in step a 1 The calculation formula of (2) is as follows:
b 1 ＝D 1 /4*(1-ν*ν)*μ o /ζ 1 /μ 1 ；
wherein mu 1 The vane inlet airflow is filled with coefficients.
6. The flat disk fan impeller and design method thereof according to claim 2, characterized in that: the calculation formula of Z in step a is as follows:
Z＝2.1*σ*(D 2 +D 1 )/(D 2 -D 1 )；
wherein sigma is the density of the blade grid, Z 1 For inlet blade number, Z 2 For the number of outlet blades, Z 1 、Z 2 And obtaining the Z through rounding obtained by calculation.
7. According to claimThe flat disk fan impeller of claim 5 and its design method, characterized in that: b in step a 2 The calculation formula of (2) is as follows:
b 2 ＝b 1 *ω 1 /ω 2 *μ 1 /μ 2 *(π*D 1 *SIN(β b1 /180*π)-δ*Z 1 )/(π*D 2 *SIN(β b2 /180*π)-Z 2 *δ)；
wherein beta is b1 Beta is b1' Rounding value, beta b1' ＝TANH(β b1' /π*180)；
TAN(β b1' /π*180)＝C 1r’ /U 1 ；
C 1r’ ＝Q/3600/η v /(D 1 *π*b 1 *μ 1 )；
U 1 ＝D 1 /2*(n*π/30)；
Wherein mu 2 For the vane outlet airflow filling coefficient, delta is vane thickness, beta b1 Is the blade inlet angle (degree), beta b1' C is the blade front inlet angle (degree) 1r’ For vane inlet front radial velocity, U 1 Is the impeller inlet linear velocity.
8. The flat disk fan impeller and design method thereof according to claim 7, wherein: presetting omega in step b 1 /ω 2 ＝1.8，ω 1 The calculation formula of (2) is as follows:
ω 1 ＝C 1r /SIN(β b1 /180*π)；
wherein C is 1r ＝C 1r’ /τ 1 ；
τ 1 ＝1-δ/SIN(β b1 /180*π)/D 1 /π*Z 1 ；
C 1r’ ＝Q/3600/η v /(D 1 *π*b 1 *μ 1 )；
Wherein C is 1r’ For vane inlet forward radial velocity τ 1 C for the blade inlet section blocking coefficient 1r For vane inlet radial velocity, ω 1 Relative speed for vane inlet;
ω 2 the calculation formula of (2) is as follows:
ω 2 ＝C 2r /SIN(β b2 /180*π)；
wherein C is 2r ＝Q/3600/η v /π/D 2 /b 2 /τ 2 /μ 2 ；
τ 2 ＝1-δ/SIN(β b2 /180*π)/D 2 /π*Z 2 ；
Wherein τ 2 C is the blocking coefficient of the section of the blade outlet 2r For vane exit radial velocity, ω 2 Is the relative velocity of the blade outlet.
9. The flat disk fan impeller and design method thereof according to claim 2, characterized in that: the checking formula of the air quantity in the step c is as follows:
Q＝η v *τ 1 *π*D 1 *b 1 *C 1r’ *3600；
the checking formula of wind pressure is as follows:
P＝η h *μ*ρ*π^2*n^2*(D 2 ^2-D 1 ^2*b 2 /b 1 *TAN(β b1 /180*π)/TAN(β b2 /180*π))/60^2；
wherein μ=1/(1+ (1.5+1.1×β) b2 /90)/24/(1-(D 1 /D 2 ) 2 ))
Wherein eta h For flow efficiency, μ is the slip coefficient.
CN202310255698.0A 2023-03-16 2023-03-16 Flat-disk fan impeller and design method thereof Pending CN116428213A (en)

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Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116822417A (en) * 2023-07-21 2023-09-29 内蒙古工业大学 Wind turbine blade surface wind pressure analysis method

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116822417A (en) * 2023-07-21 2023-09-29 内蒙古工业大学 Wind turbine blade surface wind pressure analysis method
CN116822417B (en) * 2023-07-21 2024-06-11 内蒙古工业大学 Wind turbine blade surface wind pressure analysis method

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