CN205654596U - Pipeline axial flow fan - Google Patents
Pipeline axial flow fan Download PDFInfo
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- CN205654596U CN205654596U CN201620498560.9U CN201620498560U CN205654596U CN 205654596 U CN205654596 U CN 205654596U CN 201620498560 U CN201620498560 U CN 201620498560U CN 205654596 U CN205654596 U CN 205654596U
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Abstract
The utility model discloses a pipeline axial flow fan, include wheel hub and install the last impeller of wheel hub, fixedly connected with a plurality of blade on the impeller, the action part of blade has high cross -sections such as six, be the P1 cross -section in proper order, the P2 cross -section, the P3 cross -section, the P4 cross -section, the P5 cross -section, the P6 cross -section, control factor through high cross -sections such as six in change blades, make the fan under the condition of rotational speed at 23000rpm, the fan flow can be increased to 0.2859m3s by 0.2444m3s, the amount of wind improves 16.99%, static pressure rising 1040Pa, static pressure efficiency brings up to 37.88% by 32.47%, air mass flow that can guide when effectively improving fan operation and the static pressure that can bear, the stall effect that the current fan of very big improvement takes place when the operation, and then the fan overall efficiency has been improved.
Description
Technical field
This utility model relates to fan art, particularly relates to a kind of pipeline tube-axial fan.
Background technology
The function of fan essentially consists in and guides air flowing and then reach the purpose of heat radiation, therefore, for making radiating efficiency good, fan must be good for the guiding usefulness of air, at present, dividing with the flow direction of air during fan work, fan has axial flow and radial-flow type two kinds.During tube-axial fan work, air is by flowing axially through fan, and impeller is arranged in circular air duct, and the blade on impeller is distortion, additionally has a circular arc air inlet, for avoiding the sudden contraction of air inlet.After motor impeller rotates, air is inhaled people by air inlet, through blade, it is thus achieved that energy, again through diffusion barrel, at this moment part kinetic energy transfers static pressure to, and air flows out, deliver to wind net, owing to air axially flows along impeller in fan all the time, so claiming tube-axial fan.Due to tube-axial fan simple in construction, manufacturing cost is relatively low and discharge quantity of fan is bigger, so being widely used for the device as various air-conditionings or heat radiation, but when reaching to a certain degree due to rotation speed of the fan, air can produce boundary layer separation at blade surface, therefore rotation speed of the fan can not obtain higher air mass flow the soonest, and now fan geostatic pressure change is the most relatively small.Although the stall problem of convection type fan has certain research at present, it is common that improved by the quantity adjusting blade, but the most effectively solve stall problem.
Utility model content
The main object of the present invention is for overcoming above-mentioned difficult point, a kind of pipeline tube-axial fan is provided, the air mass flow that can guide when being effectively improved fan running and the static pressure that can bear, dramatically improve the stall effect that existing fan is occurred in the running, and then improve fan overall efficiency.
nullFor achieving the above object，The technical solution adopted in the present invention is: a kind of pipeline tube-axial fan，Including wheel hub and the impeller being arranged on described wheel hub，Several blades it are fixedly connected with on described impeller，The working portion of described blade has six contour cross sections，It is followed successively by P1 cross section、P2 cross section、P3 cross section、P4 cross section、P5 cross section、P6 cross section，By cross-sectional length L to described six contour cross sections、Leading-edge radius R1、Leading edge ellipse ratio factor T、Leading edge both sides, blade profile cross section curve angle α、Blade profile entrance angle beta、Blade profile trailing edge radius R2、Blade profile trailing edge both sides curve angle theta、Outlet blade angle γ、Suction surface deformation factor、Pressure face deformation factor、Blade twist angle、Blade profile X is to displacement、Along Y-direction displacement、Design along Z-direction these factors of displacement，Improve fan overall efficiency.nullThese parameters control each change of blade respectively，Cross-sectional length L controls the total length of blade profile profile，Leading-edge radius R1 controls the curvilinear motion of blade profile profile head，Leading edge ellipse ratio factor T blade profile profile head is to the curvilinear motion of medium position，Leading edge both sides, blade profile cross section curve angle α controls the variable angle of blade profile profile head both sides curve，Blade profile entrance angle beta controls blade profile profile，Mean camber line leading edge locus and the variable angle of horizontal direction，Blade profile trailing edge radius R2 controls the curvilinear motion of blade profile profile afterbody，Blade profile trailing edge both sides curve angle theta，Control the change of blade profile profile afterbody upper and lower both sides curve angle，Outlet blade angle γ、Control the change of blade profile profile afterbody mean camber line and horizontal direction angle，Suction surface deformation factor、Control the curvilinear motion of blade profile suction surface，Pressure face deformation factor、Control the curvilinear motion of blade profile pressure face，Blade twist angle、Control the torsional variation of the whole curve of blade profile，Blade profile X controls the whole curve of blade profile to the movement of X-direction to displacement，Along Y-direction displacement、Control the whole curve of blade profile to the movement of Y-direction，The whole curve of blade profile is controlled to the movement of Z-direction along Z-direction displacement.
The geometric data of described six contour Cross section Design factors is: cross-sectional length L in described P1 cross section is 16.7mm, leading-edge radius R1 is 2mm, leading edge ellipse ratio factor T is 10, leading edge both sides, blade profile cross section curve angle α is 35.41 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.2mm, blade profile trailing edge both sides curve angle theta is 12 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.37, pressure face deformation factor is 0.35, blade twist angle is-1.75 °, blade profile X is 63.58mm to displacement, it is-0.28mm along Y-direction displacement, it is 0mm along Z-direction displacement；Cross-sectional length L in described P2 cross section is 16.1mm, leading-edge radius R1 is 1.9mm, leading edge ellipse ratio factor T is 11, leading edge both sides, blade profile cross section curve angle α is 35.38 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.18mm, blade profile trailing edge both sides curve angle theta is 12.68 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.34, pressure face deformation factor is 0.32, blade twist angle is-17.47 °, blade profile X is 63.36mm to displacement, it is-0.28mm along Y-direction displacement, it is 6.1mm along Z-direction displacement；Cross-sectional length L in described P3 cross section is 15.97mm, leading-edge radius R1 is 1.8mm, leading edge ellipse ratio factor T is 12, leading edge both sides, blade profile cross section curve angle α is 35.95 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.16mm, blade profile trailing edge both sides curve angle theta is 11.87 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.31, pressure face deformation factor is 0.38, blade twist angle is-31.98 °, blade profile X is 62.45mm to displacement, it is-0.28mm along Y-direction displacement, it is 12.2mm along Z-direction displacement；Cross-sectional length L in described P4 cross section is 15.9mm, leading-edge radius R1 is 1.7mm, leading edge ellipse ratio factor T is 13, leading edge both sides, blade profile cross section curve angle α is 38.82 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.14mm, blade profile trailing edge both sides curve angle theta is 10.89 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.28, pressure face deformation factor is 0.46, blade twist angle is-43.03 °, blade profile X is 61.11mm to displacement, it is-0.28mm along Y-direction displacement, it is 18.3mm along Z-direction displacement；Cross-sectional length L in described P5 cross section is 15.77mm, leading-edge radius R1 is 1.6mm, leading edge ellipse ratio factor T is 14, leading edge both sides, blade profile cross section curve angle α is 40.72 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.12mm, blade profile trailing edge both sides curve angle theta is 10.28 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.24, pressure face deformation factor is 0.52, blade twist angle is-50.58 °, blade profile X is 60.41mm to displacement, it is-0.28mm along Y-direction displacement, it is 24.4mm along Z-direction displacement；Cross-sectional length L in described P6 cross section is 15.1mm, leading-edge radius R1 is 1.5mm, leading edge ellipse ratio factor T is 15, leading edge both sides, blade profile cross section curve angle α is 40.5 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.1mm, blade profile trailing edge both sides curve angle theta is 10.1 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.2, pressure face deformation factor is 0.5, blade twist angle is-56.07 °, blade profile X is 60.76mm to displacement, it is-0.28mm along Y-direction displacement, it is 30.5mm along Z-direction displacement.
In technique scheme, it is preferred that described hub radius is 18mm, described hub outside diameter determines 36mm, and described impeller outer diameter is 91.2mm.
In technique scheme, it is preferred that be equidistantly provided with 11 blades on described impeller.
In technique scheme, it is preferred that described blade is PA66 blade.
A kind of pipeline tube-axial fan provided in technical scheme, compared with prior art, have the advantages that by cross-sectional length L to described six contour cross sections, leading-edge radius R1, leading edge ellipse ratio factor T, leading edge both sides, blade profile cross section curve angle α, blade profile entrance angle beta, blade profile trailing edge radius R2, blade profile trailing edge both sides curve angle theta, outlet blade angle γ, suction surface deformation factor, pressure face deformation factor, blade twist angle, blade profile X is to displacement, along Y-direction displacement, design along Z-direction these factors of displacement, make fan in the case of being 23000rpm at rotating speed, the flow of the fan after improvement is by 0.2444m3/ s has increased to 0.2859m3/ s, air quantity improves 16.99%, static pressure increases 1040Pa, static pressure efficiency has been brought up to 37.88% by 32.47%, the air mass flow that can guide when being effectively improved fan running and the static pressure that can bear, improve the stall effect that existing fan is occurred in the running greatly, and then improve fan overall efficiency.
Accompanying drawing explanation
Fig. 1, structural representation of the present utility model.
Fig. 2, this utility model schematic cross-section.
A portion partial enlarged drawing in Fig. 3, Fig. 2.
B portion partial enlarged drawing in Fig. 4, Fig. 2.
C portion partial enlarged drawing in Fig. 5, Fig. 2.
D portion partial enlarged drawing in Fig. 6, Fig. 2.
Detailed description of the invention
nullWith detailed description of the invention, this utility model is described in further detail below in conjunction with the accompanying drawings: see Fig. 1 to Fig. 6，A kind of pipeline tube-axial fan，Including wheel hub and the impeller 2 being arranged on described wheel hub，Several blades 1 it are fixedly connected with on described impeller 2，The working portion of described blade 1 has six contour cross sections，It is followed successively by P1 cross section 3、P2 cross section 4、P3 cross section 5、P4 cross section 6、P5 cross section 7、P6 cross section 8，The geometric data of described six contour Cross section Design factors is: cross-sectional length L in described P1 cross section 3 is 16.7mm，Leading-edge radius R1 is 2mm，Leading edge ellipse ratio factor T is 10，Leading edge both sides, blade profile cross section curve angle α is 35.41 °，Blade profile entrance angle beta is 16 °，Blade profile trailing edge radius R2 is 0.2mm，Blade profile trailing edge both sides curve angle theta is 12 °，Outlet blade angle γ is 12 °，Suction surface deformation factor is 0.37，Pressure face deformation factor is 0.35，Blade twist angle is-1.75 °，Blade profile X is 63.58mm to displacement，It is-0.28mm along Y-direction displacement，It is 0mm along Z-direction displacement；Cross-sectional length L in described P2 cross section 4 is 16.1mm, leading-edge radius R1 is 1.9mm, leading edge ellipse ratio factor T is 11, leading edge both sides, blade profile cross section curve angle α is 35.38 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.18mm, blade profile trailing edge both sides curve angle theta is 12.68 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.34, pressure face deformation factor is 0.32, blade twist angle is-17.47 °, blade profile X is 63.36mm to displacement, it is-0.28mm along Y-direction displacement, it is 6.1mm along Z-direction displacement；Cross-sectional length L in described P3 cross section is 15.97mm, leading-edge radius R1 is 1.8mm, leading edge ellipse ratio factor T is 12, leading edge both sides, blade profile cross section curve angle α is 35.95 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.16mm, blade profile trailing edge both sides curve angle theta is 11.87 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.31, pressure face deformation factor is 0.38, blade twist angle is-31.98 °, blade profile X is 62.45mm to displacement, it is-0.28mm along Y-direction displacement, it is 12.2mm along Z-direction displacement；Cross-sectional length L in described P4 cross section is 15.9mm, leading-edge radius R1 is 1.7mm, leading edge ellipse ratio factor T is 13, leading edge both sides, blade profile cross section curve angle α is 38.82 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.14mm, blade profile trailing edge both sides curve angle theta is 10.89 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.28, pressure face deformation factor is 0.46, blade twist angle is-43.03 °, blade profile X is 61.11mm to displacement, it is-0.28mm along Y-direction displacement, it is 18.3mm along Z-direction displacement；Cross-sectional length L in described P5 cross section is 15.77mm, leading-edge radius R1 is 1.6mm, leading edge ellipse ratio factor T is 14, leading edge both sides, blade profile cross section curve angle α is 40.72 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.12mm, blade profile trailing edge both sides curve angle theta is 10.28 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.24, pressure face deformation factor is 0.52, blade twist angle is-50.58 °, blade profile X is 60.41mm to displacement, it is-0.28mm along Y-direction displacement, it is 24.4mm along Z-direction displacement；Cross-sectional length L in described P6 cross section is 15.1mm, leading-edge radius R1 is 1.5mm, leading edge ellipse ratio factor T is 15, leading edge both sides, blade profile cross section curve angle α is 40.5 °, blade profile entrance angle beta is 16 °, blade profile trailing edge radius R2 is 0.1mm, blade profile trailing edge both sides curve angle theta is 10.1 °, outlet blade angle γ is 12 °, suction surface deformation factor is 0.2, pressure face deformation factor is 0.5, blade twist angle is-56.07 °, blade profile X is 60.76mm to displacement, it is-0.28mm along Y-direction displacement, it is 30.5mm along Z-direction displacement.
In technique scheme, described hub radius is 18mm, and described hub outside diameter is 36mm, and the external diameter of described impeller 2 is 91.2mm.
In technique scheme, described impeller 2 is equidistantly provided with 11 blades 1.
In technique scheme, described blade 1 is PA66 blade.
By cross-sectional length L to described six contour cross sections, leading-edge radius R1, leading edge ellipse ratio factor T, leading edge both sides, blade profile cross section curve angle α, blade profile entrance angle beta, blade profile trailing edge radius R2, blade profile trailing edge both sides curve angle theta, outlet blade angle γ, suction surface deformation factor, pressure face deformation factor, blade twist angle, blade profile X is to displacement, along Y-direction displacement, design along Z-direction these factors of displacement, make fan in the case of being 23000rpm at rotating speed, the flow of the fan after improvement is by 0.2444m3/ s has increased to 0.2859m3/ s, air quantity improves 16.99%, static pressure increases 1040Pa, static pressure efficiency has been brought up to 37.88% by 32.47%, the air mass flow that can guide when being effectively improved fan running and the static pressure that can bear, improve the stall effect that existing fan is occurred in the running greatly, and then improve fan overall efficiency.
Protection domain of the present utility model includes but not limited to embodiment of above; protection domain of the present utility model is as the criterion with claims, replacement that any those skilled in the art making this technology is readily apparent that, deforms, improves and each fall within protection domain of the present utility model.
Claims (4)
- null1. a pipeline tube-axial fan，Including wheel hub and the impeller (2) being arranged on described wheel hub，Several blades (1) it are fixedly connected with on described impeller (2)，It is characterized in that，The working portion of described blade (1) has six contour cross sections，It is followed successively by P1 cross section (3)、P2 cross section (4)、P3 cross section (5)、P4 cross section (6)、P5 cross section (7)、P6 cross section (8)，The geometric data of described six contour Cross section Design factors is: cross-sectional length L of described P1 cross section (3) is 16.7mm，Leading-edge radius R1 is 2mm，Leading edge ellipse ratio factor T is 10，Leading edge both sides, blade profile cross section curve angle α is 35.41 °，Blade (1) cross section entrance angle beta is 16 °，Blade (1) cross section trailing edge radius R2 is 0.2mm，Trailing edge both sides, blade (1) cross section curve angle theta is 12 °，Blade (1) angle of outlet γ is 12 °，Suction surface deformation factor is 0.37，Pressure face deformation factor is 0.35，Blade (1) windup-degree is-1.75 °，Blade (1) cross section X is 63.58mm to displacement，It is-0.28mm along Y-direction displacement，It is 0mm along Z-direction displacement；Cross-sectional length L of described P2 cross section (4) is 16.1mm, leading-edge radius R1 is 1.9mm, leading edge ellipse ratio factor T is 11, leading edge both sides, blade profile cross section curve angle α is 35.38 °, blade (1) cross section entrance angle beta is 16 °, blade (1) cross section trailing edge radius R2 is 0.18mm, trailing edge both sides, blade (1) cross section curve angle theta is 12.68 °, blade (1) angle of outlet γ is 12 °, suction surface deformation factor is 0.34, pressure face deformation factor is 0.32, blade (1) windup-degree is-17.47 °, blade (1) cross section X is 63.36mm to displacement, it is-0.28mm along Y-direction displacement, it is 6.1mm along Z-direction displacement；Cross-sectional length L of described P3 cross section (5) is 15.97mm, leading-edge radius R1 is 1.8mm, leading edge ellipse ratio factor T is 12, leading edge both sides, blade profile cross section curve angle α is 35.95 °, blade (1) cross section entrance angle beta is 16 °, blade (1) cross section trailing edge radius R2 is 0.16mm, trailing edge both sides, blade (1) cross section curve angle theta is 11.87 °, blade (1) angle of outlet γ is 12 °, suction surface deformation factor is 0.31, pressure face deformation factor is 0.38, blade twist angle is-31.98 °, blade (1) cross section X is 62.45mm to displacement, it is-0.28mm along Y-direction displacement, it is 12.2mm along Z-direction displacement；Cross-sectional length L of described P4 cross section (6) is 15.9mm, leading-edge radius R1 is 1.7mm, leading edge ellipse ratio factor T is 13, leading edge both sides, blade profile cross section curve angle α is 38.82 °, blade (1) cross section entrance angle beta is 16 °, blade (1) cross section trailing edge radius R2 is 0.14mm, trailing edge both sides, blade (1) cross section curve angle theta is 10.89 °, blade (1) angle of outlet γ is 12 °, suction surface deformation factor is 0.28, pressure face deformation factor is 0.46, blade (1) windup-degree is-43.03 °, blade (1) cross section X is 61.11mm to displacement, it is-0.28mm along Y-direction displacement, it is 18.3mm along Z-direction displacement；Cross-sectional length L of described P5 cross section (7) is 15.77mm, leading-edge radius R1 is 1.6mm, leading edge ellipse ratio factor T is 14, leading edge both sides, blade profile cross section curve angle α is 40.72 °, blade (1) cross section entrance angle beta is 16 °, blade (1) cross section trailing edge radius R2 is 0.12mm, trailing edge both sides, blade (1) cross section curve angle theta is 10.28 °, blade (1) angle of outlet γ is 12 °, suction surface deformation factor is 0.24, pressure face deformation factor is 0.52, blade (1) windup-degree is-50.58 °, blade (1) cross section X is 60.41mm to displacement, it is-0.28mm along Y-direction displacement, it is 24.4mm along Z-direction displacement；Cross-sectional length L of described P6 cross section (8) is 15.1mm, leading-edge radius R1 is 1.5mm, leading edge ellipse ratio factor T is 15, leading edge both sides, blade profile cross section curve angle α is 40.5 °, blade (1) cross section entrance angle beta is 16 °, blade (1) cross section trailing edge radius R2 is 0.1mm, trailing edge both sides, blade (1) cross section curve angle theta is 10.1 °, blade (1) angle of outlet γ is 12 °, suction surface deformation factor is 0.2, pressure face deformation factor is 0.5, blade (1) windup-degree is-56.07 °, blade (1) cross section X is 60.76mm to displacement, it is-0.28mm along Y-direction displacement, it is 30.5mm along Z-direction displacement.
- 2. a kind of pipeline tube-axial fan as claimed in claim 1, it is characterised in that described hub radius is 18mm, and described hub outside diameter is 36mm, and described impeller (2) external diameter is 91.2mm.
- 3. a kind of pipeline tube-axial fan as claimed in claim 1, it is characterised in that be equidistantly provided with 11 blades (1) on described impeller (2).
- 4. a kind of pipeline tube-axial fan as described in claim 1 or 3, it is characterised in that described blade (1) is PA66 blade.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620498560.9U CN205654596U (en) | 2016-05-30 | 2016-05-30 | Pipeline axial flow fan |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201620498560.9U CN205654596U (en) | 2016-05-30 | 2016-05-30 | Pipeline axial flow fan |
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| Publication Number | Publication Date |
|---|---|
| CN205654596U true CN205654596U (en) | 2016-10-19 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201620498560.9U Active CN205654596U (en) | 2016-05-30 | 2016-05-30 | Pipeline axial flow fan |
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| CN (1) | CN205654596U (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111927825A (en) * | 2020-07-24 | 2020-11-13 | 东风马勒热系统有限公司 | Open fan |
-
2016
- 2016-05-30 CN CN201620498560.9U patent/CN205654596U/en active Active
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111927825A (en) * | 2020-07-24 | 2020-11-13 | 东风马勒热系统有限公司 | Open fan |
| CN111927825B (en) * | 2020-07-24 | 2022-06-28 | 东风马勒热系统有限公司 | Open fan |
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| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| TR01 | Transfer of patent right |
Effective date of registration: 20200410 Address after: 210000 19 Su Yuan Avenue, Jiangning economic and Technological Development Zone, Nanjing, Jiangsu Patentee after: NANJING TIANFU SOFTWARE Co.,Ltd. Address before: 315000, No. 375, Jiangdong North Road, Ningbo, Zhejiang, 006 (19-1) Patentee before: NINGBO HIPOINT INDUSTRIAL DESIGN Co.,Ltd. |
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| TR01 | Transfer of patent right |