CN112797026A - Axial-flow type cooling fan matched with family car - Google Patents
Axial-flow type cooling fan matched with family car Download PDFInfo
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- CN112797026A CN112797026A CN202011610458.0A CN202011610458A CN112797026A CN 112797026 A CN112797026 A CN 112797026A CN 202011610458 A CN202011610458 A CN 202011610458A CN 112797026 A CN112797026 A CN 112797026A
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- 238000001816 cooling Methods 0.000 title claims abstract description 25
- 238000009434 installation Methods 0.000 claims abstract description 10
- 238000009827 uniform distribution Methods 0.000 claims abstract description 6
- 238000005452 bending Methods 0.000 claims description 10
- 230000013011 mating Effects 0.000 claims description 4
- 230000007704 transition Effects 0.000 claims description 4
- 229930091051 Arenine Natural products 0.000 claims 1
- 230000009286 beneficial effect Effects 0.000 abstract description 2
- 230000003068 static effect Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 5
- 230000000694 effects Effects 0.000 description 4
- 230000017525 heat dissipation Effects 0.000 description 3
- 238000004519 manufacturing process Methods 0.000 description 3
- 210000003205 muscle Anatomy 0.000 description 3
- 230000006872 improvement Effects 0.000 description 2
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000009471 action Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 230000001066 destructive effect Effects 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 210000005069 ears Anatomy 0.000 description 1
- 239000012530 fluid Substances 0.000 description 1
- 230000003116 impacting effect Effects 0.000 description 1
- 230000001788 irregular Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
- 230000003014 reinforcing effect Effects 0.000 description 1
- 238000000926 separation method Methods 0.000 description 1
- 230000003595 spectral effect Effects 0.000 description 1
- 238000006467 substitution reaction Methods 0.000 description 1
- 230000008093 supporting effect Effects 0.000 description 1
- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 description 1
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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
- F04D29/32—Rotors specially for elastic fluids for axial flow pumps
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
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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
- F04D29/38—Blades
- F04D29/384—Blades characterised by form
- F04D29/386—Skewed blades
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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
- F04D29/68—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers
- F04D29/681—Combating cavitation, whirls, noise, vibration or the like; Balancing by influencing boundary layers especially adapted for elastic fluid pumps
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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 invention relates to an axial flow cooling fan matched with a family car, comprising a hub which rotates around a central shaft of a motor, blades which extend outwards from the hub in a radial direction and are arranged around the central shaft of the hub; the top of the blade is connected with a guide ring surrounding the fan; the angle between the tail edge of any blade and the tail edge of the adjacent blade on the same blade section is a blade spacing angle A, wherein the ratio of the blade spacing angle A to the blade uniform distribution angle is 0.8-1.2, and the blade spacing angle A fluctuates along the circumferential direction of the rotating shaft; in the blade section from the root of the blade to 40% of the height of the blade, the installation angle is steep; in the blade section with the height of 40 percent of the blade height to 70 percent of the blade height, the installation angle is relatively flat, and plays a key role in flow; and 70% of the blade is high to the top of the blade, and the mounting angle is flat. The invention has the beneficial effect that the noise of the fan operation can be reduced while the flattening is realized.
Description
Technical Field
The invention relates to a fluid machine, in particular to a flattened fan.
Background
With the improvement of the heat dissipation requirement of the automobile engine in the whole automobile factory, the radiator fan is required to provide large air volume and high efficiency, the sound quality of the fan is taken as an important assessment index, and the order noise cannot be higher than the-10 dB (A) line of the total sound pressure level. It can be seen that sound quality research has become a new development for vehicle noise control, and the goal of sound quality improvement will be to meet the acoustic comfort requirements in the general sense and also embody the grade and features of the radiator fan. Although the fan used by the existing radiator fan has the capabilities of large air volume and high efficiency, the high requirement of the whole vehicle cannot be met no matter the total noise exceeds the boundary of 78dB (A) of the total sound pressure level of a whole vehicle factory or the level tone exceeds the boundary of-10 dB (A).
On the other hand, the flattened fan is a high-demand radiator module adapted to a large-resistance narrow space. The axial cooling fan for the household car comprises a brushless motor, and the motor drives the fan to synchronously rotate so as to enable air to flow, so that the effect of cooling the engine heat dissipation module is achieved. However, it is difficult to improve the noise at a low level because of the overall demand for miniaturization.
Disclosure of Invention
The invention aims to overcome the defects of the prior art, and solves the problem that the total sound pressure level of the running fan is easy to exceed the limit while flattening and miniaturizing the fan.
To achieve the above object, there is provided an axial flow cooling fan for a sedan for home use, comprising a hub for rotational movement about a central axis of a motor, blades extending radially outwardly from the hub and arranged about the central axis of the hub; the top of the blade is connected with a guide ring surrounding the fan; the angle between the tail edge of any blade and the tail edge of the adjacent blade on the same blade section is a blade spacing angle A, wherein the ratio of the blade spacing angle A to the blade uniform distribution angle is 0.8-1.2, and the blade spacing angle A fluctuates along the circumferential direction of the rotating shaft; in the blade section from the root of the blade to 40% of the height of the blade, the installation angle is steep; in the blade section with the height of 40 percent of the blade height to 70 percent of the blade height, the installation angle is relatively flat, and plays a key role in flow; and 70% of the blade is high to the top of the blade, and the mounting angle is flat.
Each blade is provided with a root part and a top part, and a front edge and a tail edge are arranged between the root part and the top part; with aerodynamic design patterns and structures at the leading and trailing edges. The hub is connected with the root of the blade. The blade uniform distribution angle is the angle between the tail edges of the blades when the blades are uniformly distributed in the circumferential direction of the rotating shaft. Wherein the cross-section of each blade at the same radial distance from the central axis of the hub, i.e. the axis of rotation, is the blade cross-section.
Wherein the distance between the tip of each blade and the central axis of the hub (i.e. the axis of rotation) defines the effective radius of the blade. The included angle between the chord length line of the blade cascade and the vertical plane of the rotating shaft is recorded as the mounting angle. Blade characteristics referred to herein may be characterized as: the blade section from the root to the top of the blade presents a large installation angle and a small smooth transition angle.
Preferably, the chord length of the blade cascade of each blade section from the root of the blade to the position of 70% of the blade height is similar, and the chord length of the blade cascade of each blade section from the position of 70% of the blade height to the position of the top of the blade is gradually increased.
Preferably, the number of the blades is nine, and the maximum angle deviation between the two blades is 11.8 degrees.
Preferably, the blade pitch angles a are alternately arranged in a large and small manner along the circumferential direction of the rotating shaft.
Preferably, the forward bending angle of each blade section of the blade from the blade root to the blade height position of 70% gradually changes from 0 degrees to a negative angle, and a local backward bending radian line is formed; a positive angle forward bending angle with a large value is adopted between the position from 70% of the blade height to the top of the blade; the front edge curves of the blades are in arc connection transition.
And taking a connecting line of the rotating center and the leading edge point of the blade root as a datum line, and recording an included angle between the connecting line of the leading edge point of any blade section and the rotating center and the datum line as a forward bending angle of the blade section.
The arrangement of the guide ring can reduce the leakage of the blade top clearance and play a role in guiding. The blades are non-uniformly distributed along the circumferential direction, the passing frequency of the blades is the noise frequency caused by the blades when the blades rotate to sweep through a fixed point, sound waves with different frequencies are mutually superposed when different blades sweep through the fixed point, and the periodic phase change of the sound waves causes the superposed sound waves to periodically and alternately generate constructive or destructive interference, so that order sounds with fluctuating amplitudes are formed. The reasonable non-uniform angle between the blades is controlled by adopting the special blade spacing angle A, so that the effect of sound wave cancellation can be realized.
Through the distribution of the chord length of the blade cascade, the working capacity of the blade height area is improved, the integral pressure difference of the fan is improved, the optimal efficiency area is changed, and the fan can be more suitable for the heat dissipation requirement of a large-resistance cooling module.
The special arrangement of the front bend angle of the blade enables the flow channel of the blade to be lengthened, the gas flow is uniform, the vortex is not easy to generate, the stability of the flow field is improved, and the noise of vortex clusters is reduced.
Through the special setting of blade, can be with the blade more the flattening for the interval setting with its outer static fan housing muscle can further reduce, and the blade sets up with the special interval of its outer static fan housing muscle, has greatly improved the sound interference problem between rotating fan and the static fan housing muscle.
The invention has the beneficial effect that the noise of the fan operation can be reduced while the flattening is realized.
Drawings
FIG. 1 is a schematic view of a family car mating axial flow cooling fan of the present invention;
FIG. 2 is a schematic view of a prior art fan that has been well implemented in production;
FIG. 3 is a side schematic view of a family car mating axial flow cooling fan of the present invention;
FIG. 4 is a schematic diagram showing the variation of the ratio of the spacing angle to the size of the uniform distribution angle of the axial flow cooling fan for a sedan car;
FIG. 5 is a schematic diagram showing the variation of the blade inclination angle of the axial flow cooling fan matched with the sedan car of the present invention;
FIG. 6 is a schematic view showing the variation trend of the chord length of the blade row of the matched axial flow cooling fan of the sedan;
FIG. 7 is a schematic view showing the variation trend of the blade bending angle of the axial flow cooling fan matched with the sedan car of the present invention;
FIG. 8 is a graph comparing the air volume versus static pressure curves for an embodiment of a sedan-type matched axial flow cooling fan of the present invention and a prior art fan;
FIG. 9 is a graph of impeller speed versus sound pressure level for a fitted prior art fan;
FIG. 10 is a graph of impeller speed versus sound pressure level for an axial flow cooling fan embodiment fitted to a sedan in accordance with the present invention;
FIG. 11 is a campbell plot of impeller noise with a conventional fan;
FIG. 12 is a chart of impeller noise campbell for an embodiment of an axial flow cooling fan matched to a sedan car of the present invention;
wherein:
1-hub 2-blade 3-guide ring
Detailed Description
The invention is further described below with reference to the following figures and specific examples.
An axial flow cooling fan for a sedan home mating shown in fig. 1 and 3 to 7 comprises a hub 1 for rotational movement about a central axis of a motor, nine blades 2 extending radially outwardly from the hub 1 and arranged about the central axis of the hub, the overall center of mass being located at the axis of rotation; the top of the blade 2 is connected with a guide ring 3 surrounding the fan; the angle between the tail edge of any blade 2 and the tail edge of the adjacent blade 2 on the same blade section is a blade spacing angle A, wherein the ratio of the blade spacing angle A to the blade uniform distribution angle is 0.8-1.2, the blade spacing angle A fluctuates in size along the circumferential direction of the rotating shaft and is alternately arranged in a large mode and a small mode, and the maximum angle deviation between the two blades is 11.8 degrees; in the blade section from the root of the blade 2 to 40% of the blade height, the installation angle is steep; in the blade section with the height of 40 percent of the blade height to 70 percent of the blade height, the installation angle is relatively flat, and plays a key role in flow; and 70% of the blade is high to the top of the blade, and the mounting angle is flat.
The chord length of the blade cascade of each blade section of the blade 2 from the root of the blade to the position of 70% of the blade height is similar, and the chord length of the blade cascade of each blade section of the blade 2 from the position of 70% of the blade height to the position of the top of the blade is gradually increased.
The forward bending angle of the section of each blade of the blade 2 from the root of the blade to the position of 70% of the blade height is gradually changed from 0 degrees to a negative angle to form a local backward bending radian line; a positive angle forward bending angle with a large value is adopted between the position from 70% of the blade height to the top of the blade; the front edge curves of the blades are in arc connection transition.
The mounting hole on the wheel hub 1 is assembled with the brushless motor into a whole through a coupling structure, the fan and the fan cover are assembled into a radiator fan assembly, and the radiator fan assembly, a water tank condenser and other components are assembled together to form a cooling module of the automobile.
Compared with the existing fan which is well installed in production, the fan of the embodiment has the same size, and the performance advantages are mainly reflected as follows:
1. the fan design matching system is suitable for narrow space, the internal flow field is improved through reasonable blade design, and the flat design can effectively reduce the dynamic and static interference effect and improve the noise while saving the space;
2. the system resistance 0pa after the loading module is approximately corresponding to the resistance of the fan assembly body, and the resistance is the effective resistance; under the same flow condition, the pressure difference required by the fan is low, and under the same condition, the corresponding pressure difference is lower than that of the existing fan;
3. in the trial production of small-batch samples, the test of a wind tunnel test bed proves that the fan can replace the existing high-static-pressure fan under the working condition of lower static pressure, and the test air volume-pressure difference performance after the matching system is shown in figure 8.
4. The fan is matched with a cooling module specified by a customer, and the rotating speed of the cooling module is 2400rpm under the condition of specific resistance, so that the required air volume 2300m of the existing fan under the same boundary condition is achieved3H; meanwhile, the total sound pressure level of the fan is 75.5dB (A), and the total sound pressure level of the existing fan is generally about 78.5dB (A). The existing fan single body exceeds the control line 78dB (A) of the whole vehicle factory. It can be seen that the fan achieves the feature of reducing the overall sound pressure level, see the comparison of fig. 9 with fig. 10.
5. The fan is tested according to the noise standard acoustics requirement, and the order noise curve is an important assessment index required by the fan. From the test results derived from the fig. 10 speed-sound pressure level curve, the fan has an order noise lower than the-10 db (a) control curve, which is the key to effectively improve the unpleasant sound and improve the pleasant feeling.
6. The noise campbell diagram, i.e. the frequency-rotation speed curve, the frequency is the abscissa, and the rotation speed is the ordinate, from which the variation characteristics of all frequency components of the rotor vibration in the whole rotation speed range can be obtained. From the existing fan test results, as shown in the frequency-rotation speed curve of fig. 11, ordinal numbers of orders 7, 9, 16, 24, etc. are the harmonic times of the rotation speed; from the test results of the fan, as seen in the frequency-rotation speed curve of fig. 12, ordinals order8, 9, 18, 24, etc. are the harmonic times of the rotation speed; each slope represents the spectral line variation of the subharmonic during the variation of the rotation speed. Obviously, the amplitude fluctuation of each order of sound of the fan is not large, which is the best representation of good sound quality of the new fan. Meanwhile, comparing the conventional fan campbell diagram (fig. 11) with the fan campbell diagram (fig. 12), under the same coordinate, the luminance of the conventional fan order line is significantly higher than that of the new fan order line, which indicates that the conventional fan order pitch is higher than the fan order pitch.
From the perspective of this embodiment, the fan geometry has the following advantages:
1. nine blades of the fan adopt non-uniform angles, so that the total sound pressure level of the fan is greatly reduced, the order noise is improved, and the comfort level and the pleasure degree of ears of people are facilitated.
2. The forward-bent blade structure optimizes the flow field through a proper forward-bent angle, and plays a role in reducing noise; meanwhile, the fan has the characteristics that the number of the blades is more than chord length, and the air volume is improved by the pressure reducing head under the condition of equal power;
3. the blades have the flat characteristic, and under the condition of narrow space, the distance between the fan and the fixed support is enlarged, so that the dynamic and static interference effect is effectively reduced; the noise of the vortex mass impacting the bracket is improved, namely the noise caused by the vortex generated by the separation of the gas boundary layer when the impeller rotates at high speed is improved.
4. In order to obtain a stable flow field and to be able to operate at a higher static pressure efficiency under specific working conditions (static pressure, flow rate), the fan forms a variable-circulation flow pattern. The full pressure is increased along the radius, the blade top is fully utilized to do work, the blade root load is reduced, mechanical energy is effectively converted into wind energy, the flow field is optimized, the efficiency is improved, and the noise is reduced.
5. The top of the blade adopts a structure of a guide ring, so that the strength of the blade is improved, the large changes of a forward bending angle and a blade wing type installation angle caused by radial straightening of the blade under the action of centrifugal force during high-speed rotation are overcome, and the operating performance of the fan is ensured not to have large changes. Meanwhile, due to the supporting and reinforcing effect of the guide ring, irregular shaking of the blades during high-speed rotation is overcome, abnormal noise caused by shaking of the blades is avoided, and the comfort degree of sound is optimized.
While the preferred embodiments of the present invention have been described in detail, it will be understood by those skilled in the art that the invention is not limited to the embodiments disclosed, but is capable of numerous equivalents and substitutions, all of which are within the scope of the invention as defined by the appended claims.
Claims (5)
1. An axial flow cooling fan for a sedan household mating, comprising a hub (1) for rotational movement about a central motor axis, characterized in that blades (2) extend radially outwardly from the hub and are arranged about the hub central axis; the top of the blade (2) is connected with a guide ring (3) surrounding the fan; the angle between the tail edge of any blade (2) and the tail edge of the adjacent blade (2) on the same blade section is a blade spacing angle A, wherein the ratio of the blade spacing angle A to the blade uniform distribution angle is 0.8-1.2, and the blade spacing angle A fluctuates along the circumferential direction of the rotating shaft; in the blade section from the root of the blade (2) to 40% of the blade height, the installation angle is steep; in the blade section with the height of 40 percent of the blade height to 70 percent of the blade height, the installation angle is relatively flat, and plays a key role in flow; and 70% of the blade is high to the top of the blade, and the mounting angle is flat.
2. The sedan matched axial flow cooling fan according to claim 1, wherein the chord length of the blade (2) is similar for each blade section from the root to the 70% blade height position, and the chord length of the blade (2) is gradually increased for each blade section from the 70% blade height to the tip position.
3. Family car matched axial cooling fan according to claim 1, characterized in that said blades (2) are nine in number, the maximum angular deviation between two blades being 11.8 °.
4. The coupe-matched axial flow cooling fan according to claim 1, wherein the blade pitch angle a is alternately large and small in the circumferential direction of the rotating shaft.
5. The family car matched axial flow cooling fan according to claim 1, characterized in that the blade (2) changes gradually from 0 ° to a negative angle from the blade root to the forward bend angle of each blade section at 70% blade height, forming a local backward camber line; a positive angle forward bending angle with a large value is adopted between the position from 70% of the blade height to the top of the blade; the front edge curves of the blades are in arc connection transition.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011610458.0A CN112797026A (en) | 2020-12-30 | 2020-12-30 | Axial-flow type cooling fan matched with family car |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202011610458.0A CN112797026A (en) | 2020-12-30 | 2020-12-30 | Axial-flow type cooling fan matched with family car |
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| Publication Number | Publication Date |
|---|---|
| CN112797026A true CN112797026A (en) | 2021-05-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202011610458.0A Pending CN112797026A (en) | 2020-12-30 | 2020-12-30 | Axial-flow type cooling fan matched with family car |
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Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2804445Y (en) * | 2005-07-13 | 2006-08-09 | 张益华 | Six-vane axial-flow cooling fan |
| CN201599250U (en) * | 2009-12-28 | 2010-10-06 | 邱荣泉 | Mini cooling fan |
| CN105156365A (en) * | 2015-10-14 | 2015-12-16 | 联想(北京)有限公司 | Fan and electronic equipment |
| CN108167229A (en) * | 2018-02-28 | 2018-06-15 | 华南理工大学 | A kind of cooling fan and its aerodynamic noise computational methods of blade inlet edge protrusion |
| CN109737098A (en) * | 2019-03-01 | 2019-05-10 | 上海诺地乐通用设备制造有限公司 | A kind of axial wheel with cleavable blade |
| CN110307178A (en) * | 2019-06-27 | 2019-10-08 | 上海马陆日用友捷汽车电气有限公司 | A kind of low-noise impeller |
| US20190353083A1 (en) * | 2017-11-15 | 2019-11-21 | Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg | Cooling fan module |
-
2020
- 2020-12-30 CN CN202011610458.0A patent/CN112797026A/en active Pending
Patent Citations (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN2804445Y (en) * | 2005-07-13 | 2006-08-09 | 张益华 | Six-vane axial-flow cooling fan |
| CN201599250U (en) * | 2009-12-28 | 2010-10-06 | 邱荣泉 | Mini cooling fan |
| CN105156365A (en) * | 2015-10-14 | 2015-12-16 | 联想(北京)有限公司 | Fan and electronic equipment |
| US20190353083A1 (en) * | 2017-11-15 | 2019-11-21 | Brose Fahrzeugteile Gmbh & Co. Kommanditgesellschaft, Wuerzburg | Cooling fan module |
| CN108167229A (en) * | 2018-02-28 | 2018-06-15 | 华南理工大学 | A kind of cooling fan and its aerodynamic noise computational methods of blade inlet edge protrusion |
| CN109737098A (en) * | 2019-03-01 | 2019-05-10 | 上海诺地乐通用设备制造有限公司 | A kind of axial wheel with cleavable blade |
| CN110307178A (en) * | 2019-06-27 | 2019-10-08 | 上海马陆日用友捷汽车电气有限公司 | A kind of low-noise impeller |
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Application publication date: 20210514 |
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