Fin structure imitating shark gill fissure
By adopting a shark gill slit fin structure in the intercooler and using the design of bionic curved surface fins and gill slits, the problem of poor synergy between velocity and temperature fields in traditional fin structures is solved, and more efficient heat exchange and better heat exchange performance are achieved.
Patent Information
- Application Number
- CN202510271714.4
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-03-09
- Publication Date
- 2025-04-15
AI Technical Summary
The heat exchange performance of existing intercoolers is low, mainly because the synergy between the velocity field and the temperature field when the air flows, resulting in insufficient heat exchange between cold and hot air.
The shark gill slit fin structure is adopted, including bionic curved fins and runner partitions. The bionic curved fins are arrayed from multiple shark-shaped curved fins. The presence of the gill slits causes the cold air to exchange heat with the gill slits during the flow process and mix with the cold air in the second runner, enhancing the heat exchange efficiency.
Through the fin structure of the shark gill fissure, the heat exchange performance of the intercooler is significantly enhanced, the outlet temperature of the cold air is greatly reduced, the heat exchange efficiency is improved, and the overall performance is improved.
Smart Images
Figure CN119825537A_ABST
Abstract
Description
Technical Field
[0001] The invention belongs to the technical field of cooling equipment, and in particular relates to a shark gill cleft fin structure. Background Art
[0002] The supercharged intercooling technology refers to the use of a turbocharger to compress the exhaust gas discharged by the car. After the exhaust gas is compressed, its density increases, and the air intake volume of the cylinder per unit time also increases, making the fuel burn more fully in the cylinder, thereby increasing the output power of the car while reducing the emission of pollutants. However, the temperature and pressure of the supercharged air will rise rapidly. If the supercharged air is directly sent into the combustion chamber, it is very easy to cause detonation. In order to avoid this phenomenon, the supercharged air needs to be cooled through an intercooler, thereby effectively reducing the pollutant content in the exhaust gas and improving the fuel combustion efficiency.
[0003] Traditional intercoolers use straight fins, which have the advantages of simple structure and easy processing. However, the flow channels are independent of each other, and the cold air in different flow channels cannot be fully mixed during the flow process, resulting in low heat exchange capacity. In order to solve this problem, intercoolers with louvered fins are widely used. However, when air flows through existing louvered fins, the velocity direction is basically parallel to the length direction of the fins and perpendicular to the heat flow direction. Therefore, the coordination between the velocity field and the temperature field is very poor, which will affect the heat exchange between the cold and hot air, resulting in low heat exchange performance of the intercooler. Summary of the invention
[0004] In view of the deficiencies in the prior art, the technical problem to be solved by the present invention is to provide a shark gill cleft fin structure.
[0005] The technical solution adopted by the present invention to solve the technical problem is:
[0006] A shark gill slit fin structure comprises a bionic curved surface fin and a flow channel partition; a plurality of bionic curved surface fin groups are arrayed between two flow channel partitions, each bionic curved surface fin group comprises two symmetrically arranged bionic curved surface fins, two bionic curved surface fins of the same bionic curved surface fin group are arranged facing each other and a first flow channel is formed therebetween, two bionic adjacent curved surface fins of adjacent bionic curved surface fin groups are arranged back to back and a second flow channel is formed therebetween, and the cross-sectional areas of the first flow channel and the second flow channel are periodically varied; the bionic curved surface fin is formed by an array of a plurality of shark-shaped curved surface fin monomers, a plurality of shark-shaped curved surface fin openings are provided in the middle of the shark-shaped curved surface fin monomers, and an inclined gill slit piece is provided at the edge of each shark-shaped curved surface opening.
[0007] Furthermore, the shapes of the shark-shaped curved fin monomers in the length and height directions satisfy the trigonometric function curve.
[0008] Furthermore, the amplitude of the trigonometric function curve is 0-2.
[0009] Furthermore, the inclination angle of the gill slit is 0-90°, the thickness of the gill slit is not greater than the thickness of the bionic curved fin, and the maximum distance between the free side of the gill slit and the external section of the shark-shaped curved fin monomer is not greater than 0.5W1, where W1 is the width at the entrance of the second flow channel.
[0010] Furthermore, the ratio of the width of the second flow channel to that of the first flow channel at the inlet is 0.5-1.5.
[0011] Furthermore, the thickness of the flow channel partition is 0.2-1 mm, and the thickness of the bionic curved fin is 0.1-0.3 mm.
[0012] Furthermore, the number of gill lobes on the shark-like curved fin monomer is 3-7, and the spacing between adjacent gill lobes is 0.1-1 mm.
[0013] Compared with the prior art, the present invention has the following beneficial effects:
[0014] The bionic curved fin of the present invention is composed of a plurality of shark-shaped curved fin monomer arrays. The shapes of the shark-shaped curved fin monomers in the length and height directions satisfy the trigonometric function curves. The traditional straight fins are curved to increase the heat exchange area. Moreover, the cross-sectional areas of the first flow channel and the second flow channel change periodically, so that the flow direction and velocity of the cold air in the flow process are constantly changing, which enhances the synergistic effect of the temperature field and the velocity field, destroys the boundary layer, strengthens the heat transfer, and thus greatly reduces the outlet temperature of the hot air. Due to the presence of the shark-shaped gill slit opening and the gill slits, a small portion of the cold air in the first flow channel flows out through the shark-shaped gill slit opening and mixes with the cold air in the second flow channel, which helps to improve the heat exchange efficiency by promoting the shuttling flow of the cold air in different flow channels. In the process of the cold air flowing out of the shark-shaped gill slit opening, it exchanges heat with the gill slits, further enhancing the heat exchange effect.
[0015] The simulation results show that compared with the traditional straight fin and louvered fin structures, the fin structure of the present invention can significantly enhance the comprehensive performance of the heat exchanger. Therefore, this structure is of great significance to improving the heat transfer performance of the heat exchanger. BRIEF DESCRIPTION OF THE DRAWINGS
[0016] Figure 1 is a schematic structural diagram of Example 1;
[0017] Figure 2 is a cross-sectional view of Example 1;
[0018] Figure 3 is a top view of the first flow channel;
[0019] Figure 4 1 is a temperature distribution diagram of the fin structure of Example 1 on the center plane in the height direction at different cold air inlet flow rates, where the cold air inlet flow rates of (a), (b) and (c) are 4 m / s, 6 m / s and 12 m / s respectively;
[0020] Figure 5 This is the temperature distribution diagram of the louver fin structure on the center plane in the height direction at different cold air inlet flow rates.
[0021] The cold air inlet velocity of (a), (b) and (c) are 4m / s, 6m / s and 12m / s respectively;
[0022] Figure 6 is a comparison diagram of j factor and f factor of Example 1 and different fin structures at different cold air inlet flow rates;
[0023] Figure 7 is a comparison diagram of JF factors of Example 1 and different fin structures at different cold air inlet flow rates;
[0024] Figure 8 is a schematic structural diagram of Example 2;
[0025] Fig. 9 is a comparison diagram of j factor and f factor of Example 2 and different fin structures at different cold air inlet flow rates;
[0026] Fig.10 is a comparison diagram of JF factors of Example 2 and different fin structures at different cold air inlet flow rates;
[0027] In the figure: 1-bionic curved fin; 2-flow channel baffle; 3-gill slit. DETAILED DESCRIPTION
[0028] Specific embodiments are given below in conjunction with the accompanying drawings. The specific embodiments are only used to introduce the technical solutions of the present invention in detail and are not intended to limit the protection scope of the present application.
[0029] The present invention provides a shark gill slit fin structure, comprising a bionic curved surface fin 1 and a flow channel partition 2; a plurality of bionic curved surface fin groups are arrayed between two flow channel partitions 2, each bionic curved surface fin group comprises two symmetrically arranged bionic curved surface fins 1, two bionic curved surface fins 1 of the same bionic curved surface fin group are arranged facing each other and a non-uniform first flow channel is formed therebetween, two bionic adjacent curved surface fins 1 of adjacent bionic curved surface fin groups are arranged back to back and a non-uniform second flow channel is formed therebetween, and cold air flows in the first flow channel and the second flow channel; the bionic curved surface fin 1 is formed by an array of a plurality of shark-shaped curved surface fin monomers, and adjacent shark-shaped curved surface fin monomers are connected, a plurality of shark-shaped curved surface fin openings are provided in the middle of the shark-shaped curved surface fin monomer, and an inclined gill slit 3 is provided at the edge of each shark-shaped curved surface opening.
[0030] The shapes of the shark-shaped curved fin monomer in the length and height directions satisfy the trigonometric function curve, so the cross-sectional areas of the first flow channel and the second flow channel are both periodically changed. The cross-sectional area of the first flow channel is cycled in the form of expansion and then contraction, with the maximum cross-sectional area at the maximum curvature of the two shark-shaped curved fin monomers arranged opposite to each other, and the minimum cross-sectional area at the side edge; the cross-sectional area of the second flow channel is cycled in the form of contraction and then expansion, with the minimum cross-sectional area at the maximum curvature of the two shark-shaped curved fin monomers arranged opposite to each other, and the maximum cross-sectional area at the side edge. The amplitude of the shark-shaped curved fin monomer is 0-2, and the wavelength can be set according to actual requirements. The wavelength has the greatest impact on the heat dissipation performance.
[0031] The thickness of the flow channel partition plate 2 is 0.2-1 mm, and the thickness of the bionic curved fin 1 is 0.1-0.3 mm.
[0032] The number of gill slits 3 on the shark-shaped curved fin monomer is 3-7, the spacing between adjacent gill slits 3 is 0.1-1 mm, the inclination angle θ of the gill slits 3 is 0-90°, the thickness of the gill slits 3 is not greater than the thickness of the bionic curved fin 1, and the maximum distance between the free side of the gill slit 3 and the external section of the shark-shaped curved fin monomer is not greater than 0.5W1, where W1 is the width at the entrance of the second flow channel.
[0033] The heights of the first flow channel and the second flow channel are set according to actual requirements, and the ratio W1 / W of the width at the inlet of the second flow channel to that of the first flow channel is 0.5-1.5.
[0034] The working principle and workflow of the present invention are:
[0035] The cold air enters the first flow channel and the second flow channel respectively. Due to the flow-guiding effect of the bionic curved fin 1 and the continuous change in the cross-sectional area of the flow channel, the flow direction and speed of the cold air are constantly changing, thereby generating eddies, enhancing the turbulence intensity, destroying the boundary layer of the cold air, and strengthening the heat exchange between the bionic curved fin 1 and the cold air. When the cold air flows through the first flow channel, a small portion of the cold air flows out through the shark-like gill slit opening, which is equivalent to a jet at the moment of flowing out, causing the boundary layer to be destroyed. Moreover, the cold air after flowing out is guided by the gill slit 3 and exchanges heat with it during the guiding process, further increasing the heat exchange area. The cold air after flowing out is finally mixed with the cold air in the second flow channel, which can further enhance the heat exchange effect. The application scope of the present invention includes but is not limited to intercoolers, tube-fin heat exchangers and plate-fin heat exchangers.
[0036] Example 1
[0037] The shark-like gill slit fin structure of this embodiment includes two bionic curved fin groups, the thickness of the flow channel partition 2 is 0.3mm, the flow channel height is 6mm, the flow channel length is 40mm, the thickness of the bionic curved fin is 0.2mm, the thickness of the gill slit 3 is 0.1mm, the inclination angle of the gill slit 3 is 45°, the number of gill slits 3 on the shark-like curved fin monomer is 3, the amplitude of the trigonometric function curve in the length direction of the shark-like curved fin monomer is 0.75mm, the wavelength is 4mm, the amplitude of the trigonometric function curve in the height direction of the shark-like curved fin monomer is 0.5mm, and the wavelength is 6mm; the ratio W1 / W of the width at the entrance of the second flow channel to the first flow channel is 1.22, wherein the width W1 at the entrance of the second flow channel is 3.3mm, the spacing between the gill slits 3 is 0.16, and the maximum distance between the free side of the gill slit 3 and the external section of the shark-like curved fin monomer is 0.8mm.
[0038] Figure 4 The temperature distribution diagram of the fin structure of this embodiment on the center plane in the height direction at different cold air inlet flow rates, wherein the cold air inlet flow rates of (a), (b) and (c) are 4m / s, 6m / s and 12m / s respectively; Figure 5 Figure 2 is the temperature distribution diagram of the louver fin structure on the center plane in the height direction at different cold air inlet flow rates, where the cold air inlet flow rates of (a), (b) and (c) are 4m / s, 6m / s and 12m / s respectively.
[0039] Depend on Figure 4 , 5It can be seen that the low temperature zone (temperature less than 310K) of the fin structure of this embodiment is concentrated in the front half of the flow channel under different cold air inlet flow rates; for the louver fin structure, the low temperature zone extends all the way to the flow channel outlet, and the higher the cold air inlet flow rate, the more low temperature zones there are, especially when the cold air inlet flow rate is 12m / s, the cold air has basically flowed out of the flow channel without sufficient heat exchange with the fins. Therefore, the fin structure of this embodiment has a better heat exchange effect, which is due to the larger contact area between the fin structure of this embodiment and the cold air, and the enhanced synergy between the velocity field and the temperature field. Specifically, a flow channel with a periodically changing cross-sectional area is formed between the two bionic curved fins. The cold air has a reduced flow velocity in the expansion section of the flow channel, and the static pressure increases, generating a violent vortex, while the flow velocity increases in the contraction section, and the static pressure decreases, which washes the boundary layer of the cold air and makes the boundary layer thinner, thereby enhancing heat transfer. At the same time, a small amount of cold air in the first flow channel flows out through the shark-like gill slit opening and is fully mixed with the cold air in the second flow channel, which promotes the mutual shuttling of cold air between different flow channels, making the angle between the flow direction and the speed direction smaller, and the boundary layer is destroyed when flowing through the gill slits, making the heat exchange between the cold air and the fins more sufficient, thereby allowing the cold air temperature to rise rapidly and improving the temperature uniformity. As for the louver fin structure, after the cold air enters the flow channel, only the flow direction of a very small part of the cold air close to the fin is changed due to the existence of the louver, but most of the cold air in the center area of the flow channel is basically not disturbed by the louver during the flow process. The cold air in the center area of the flow channel flows rapidly through the flow channel at a speed parallel to the flow direction, so the low temperature area spreads to the flow channel outlet position, so the heat exchange effect between the cold air and the fin is poor, and the uniformity of the temperature distribution is poor.
[0040] Figure 6 This is a comparison chart of the j factor and f factor of this embodiment and different fin structures at different cold air inlet flow rates; the j and f factors reflect the heat exchange performance and flow resistance characteristics of the fin structure, respectively. As can be seen from the figure, the heat exchange performance of the fin structure of this embodiment is significantly improved, and it always has the largest j factor. Compared with the louver fin structure, the j factor is increased by an average of 36.34%, and the maximum improvement is 51.07% when the cold air inlet flow rate is 12m / s. Compared with the straight fin structure, the j factor is increased by an average of 67.62%, and the maximum improvement is 76.24% when the cold air inlet flow rate is 12m / s. Although the fin structure of this embodiment will cause an increase in flow resistance (f factor), it does not affect the improvement of the overall performance.
[0041] Figure 7This is a comparison chart of the JF factor of this embodiment and different fin structures at different cold air inlet flow rates. As can be seen from the figure, the fin structure of this embodiment always has the greatest comprehensive performance (JF factor), and compared with the louver fin structure and the straight fin structure fin, the comprehensive performance is improved by an average of 15.16% and 32.37%.
[0042] Through the above comparative analysis, it can be found that the heat exchange capacity and comprehensive performance of the fin structure of this embodiment are greatly improved.
[0043] Example 2
[0044] The difference between this embodiment and embodiment 1 is that the wavelength of the trigonometric function curve in the length direction of the shark-shaped curved fin monomer is changed from 4 mm to 8 mm. Figure 8 .
[0045] Fig. 9 is a comparison diagram of the j factor and f factor of this embodiment and different fin structures at different cold air inlet flow rates; Fig.10 This is a comparison chart of the JF factor of this embodiment and different fin structures at different cold air inlet flow rates. The comprehensive performance of the fin structure of this embodiment is significantly enhanced. Compared with the straight fin and louver fin structures, the comprehensive performance is improved by 35.34% and 17.74% on average. Compared with Example 1, the comprehensive performance is further improved. This is mainly because the pressure drop caused by the increase in wavelength at the same amplitude is smaller, so the friction is smaller, and the heat transfer performance (j factor) does not change much, so better comprehensive performance is obtained.
[0046] Any matters not described in the present invention are applicable to the prior art.
Claims
1. A shark gill cleft fin structure, characterized in that: The fin structure comprises a bionic curved surface fin and a flow channel partition; a plurality of bionic curved surface fin groups are arrayed between two flow channel partitions, each bionic curved surface fin group comprises two symmetrically arranged bionic curved surface fins, two bionic curved surface fins of the same bionic curved surface fin group are arranged facing each other and a first flow channel is formed therebetween, two bionic adjacent curved surface fins of adjacent bionic curved surface fin groups are arranged facing each other and a second flow channel is formed therebetween, and the cross-sectional areas of the first flow channel and the second flow channel vary periodically; The bionic curved fin is formed by an array of multiple shark-shaped curved fin monomers, a plurality of shark-shaped gill openings are arranged in the middle of the shark-shaped curved fin monomers, and an inclined gill slit is arranged at the edge of each shark-shaped gill opening.
2. The shark gill cleft fin structure according to claim 1, characterized in that: The shapes of the shark-shaped curved fin monomer in the length and height directions both satisfy the trigonometric function curve.
3. The shark gill cleft fin structure according to claim 2, characterized in that: The amplitude of the trigonometric function curve is 0-2.
4. The shark gill cleft fin structure according to claim 1, characterized in that: The inclination angle of the gill slit is 0-90°, the thickness of the gill slit is not greater than the thickness of the bionic curved fin, and the maximum distance between the free side of the gill slit and the external section of the shark-shaped curved fin monomer is not greater than 0.5W1, where W1 is the width at the entrance of the second flow channel.
5. The shark gill cleft fin structure according to claim 1, characterized in that: The ratio of the width of the second flow channel to the width of the first flow channel at the inlet is 0.5-1.
5.
6. The shark gill cleft fin structure according to claim 1, characterized in that: The thickness of the flow channel partition is 0.2-1 mm, and the thickness of the bionic curved fin is 0.1-0.3 mm.
7. The shark gill cleft fin structure according to claim 1, characterized in that: The number of gill lobes on the shark-shaped curved fin monomer is 3-7, and the spacing between adjacent gill lobes is 0.1-1 mm.