Wave-shaped structure for heat dissipation of high-flow-speed fan air duct
By setting a bionic wave rib structure on the cooling channel of the radiator, the problem of insufficient cooling performance in the high-flow fan environment in the prior art is solved, and more efficient heat dissipation effect and more uniform heat exchange are achieved.
Patent Information
- Application Number
- CN202411340219.6
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2024-11-01
- Publication Date
- 2024-12-20
AI Technical Summary
It is difficult for existing radiators to effectively improve the heat exchange performance of the cooling channel in high-flow fan environments. The single rib arrangement is limited, and the wall design is not enough to meet complex flow needs.
By using a bionic wave structure design, bionic wave ribs are set on the end wall, the raised position and fluctuation degree are changed, the flow heat exchange characteristics and disturbance effects are enhanced, the quality exchange between the air conditioner and the mainstream is improved, and the comprehensive heat exchange performance of the channel is improved. Uniformity.
The heat exchange performance of the ribbed wall surface and the comprehensive heat exchange performance of the channels are significantly improved, the flow heat exchange characteristics are improved, the cooling effect is enhanced, and the heat exchange uniformity is improved by adjusting the position and degree of fluctuating protrusions.
Smart Images
Figure CN119163637A_ABST
Abstract
Description
Technical Field
[0001] The present application relates to the technical field of heat dissipation devices, and in particular to a wavy structure for heat dissipation in high-flow-rate fan ducts. Background Art
[0002] When the motor converts electrical energy into mechanical energy, it will inevitably generate a lot of heat. If this part of heat cannot be taken away in time, the motor temperature will easily become too high, which will cause a series of problems. Existing heat dissipation methods mainly rely on the selection and design of different strategies such as natural cooling, forced air cooling, water cooling or oil cooling in the cooling channel. At present, most radiators mainly rely on the arrangement of fins for heat dissipation, but the arrangement of a single fin is likely to magnify the defects of the fin itself, and the wall design is an optional method. Therefore, it is necessary to design a cooling channel that can enhance the comprehensive performance of the channel through rib-wall coupling design.
[0003] The information disclosed in this background technology section is only intended to enhance the understanding of the overall background of the application and should not be regarded as an admission or any form of suggestion that the information constitutes the prior art already known to ordinary technicians in the field. Summary of the invention
[0004] The object of the present invention is to provide a wave-shaped structure for heat dissipation in a high-flow fan duct, which enhances the heat exchange effect and improves the heat exchange performance of the duct by designing bionic wave-shaped fluctuations on the end wall.
[0005] In order to achieve the above objectives, this application is implemented by adopting the following technical solutions: A wavy structure for heat dissipation in a high-flow-rate fan duct comprises a first ribbed end wall, a second ribbed end wall and wavy ribs, wherein the first ribbed end wall and the second ribbed end wall are symmetrically arranged, the wave crests of the first ribbed end wall and the wave troughs of the second ribbed end wall are at the same flow direction position, the first ribbed end wall and the second ribbed end wall are bionic wavy, and the wavy ribs are evenly installed on the symmetrical planes of the first ribbed end wall and the second ribbed end wall.
[0006] Optionally, the wavy ribs include two forms: discontinuous ribs and continuous ribs.
[0007] Optionally, the first ribbed end wall and the second ribbed end wall have the same number of periods of undulating and wave-shaped ribs.
[0008] Optionally, the rib thickness of the corrugated rib is e, and the rib height is 2*e.
[0009] Optionally, the wave crest positions of the first ribbed end wall and the second ribbed end wall coincide with the wave crests or wave troughs of the wavy ribs.
[0010] Optionally, the wavy ribs have a fluctuation amplitude of 25%-30% of the channel width.
[0011] Optionally, the index of the comprehensive heat exchange performance of the first ribbed end wall and the second ribbed end wall is defined as follows:
[0012] In the formula , , is the density of cold air, is the cooling speed, is the static pressure difference of cold air at the inlet and outlet of the channel fluid domain, is the dimensionless Nusselt number.
[0013] Optionally, the dimensionless Nusselt number of the first ribbed end wall and the second ribbed end wall increases linearly with the increase of the protrusion, and the dimensionless Nusselt number is defined as follows:
[0014] In the formula, h is the heat transfer coefficient, D is the characteristic length, is the thermal conductivity, Re is the inlet Reynolds number, Pr is the Prandtl number.
[0015] Compared with the prior art, the present invention has the following beneficial effects: The present invention proposes a staggered concave-convex ribbed wall structure based on bionic wavy topology, which further enhances the heat exchange effect by arranging a cooling structure with wavy ribs on the upper and lower surfaces of the cooling channel inside the motor radiator, and designing the ribbed end wall as a bionic wavy wall. Compared with a simple ribbed channel, the design of the bionic wavy end wall can improve the flow and heat exchange characteristics of certain areas in the original wavy rib channel by changing the position of the protrusions. The design of the bionic wavy end wall also improves the disturbance effect on the cold air, significantly promotes the mass exchange between the cold air and the mainstream in the ribless area close to the side wall of the channel, and significantly improves the heat exchange performance of the ribbed wall. At the same time, the comprehensive heat exchange performance of the channel is also improved. The design of the bionic wavy end wall can adjust the position of different wave protrusions and the degree of fluctuation according to the different arrangement of the spoiler rib structure to enhance the heat exchange uniformity of the channel. BRIEF DESCRIPTION OF THE DRAWINGS
[0016] In order to more clearly illustrate the embodiments of the present disclosure or the technical solutions in the prior art, the drawings required for use in the embodiments or the description of the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present disclosure. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.
[0017] Figure 1 This is a diagram of the cooling structure of the present invention, which is a coupling cooling structure of staggered concave-convex wall surface and continuous wavy ribs based on bionic wavy topology; Figure 2 This is a diagram of the cooling structure of the present invention, which is a coupling cooling structure of a staggered concave-convex wall surface and double discontinuous wavy ribs based on bionic wavy topology; Figure 3 It is a schematic diagram of the top plan structure of the cooling structure of the staggered concave-convex wall surface and the continuous wavy rib coupling based on the bionic wavy topology of the present invention; Figure 4 It is a side cross-sectional view of a cooling structure coupled with staggered concave-convex wall surfaces and continuous wavy ribs based on bionic wavy topology in the present invention; Figure 5 A schematic diagram of a single cycle of two cooling structures coupled with staggered concave-convex wall surfaces and continuous wavy ribs based on bionic wavy topology in the present invention; Figure 6 The comparison of the dimensionless Nusselt number of the ribbed wall in the scheme where the convex position of the wavy end wall along the stream direction coincides with the windward area of the wavy rib; Figure 7 Comparison of the distribution of dimensionless Nusselt number along the ribbed wall in the scheme where the convex position of the wavy end wall along the stream direction coincides with the leeward area of the wavy rib.
[0018] Description of reference numerals: 1. First ribbed end wall; 2. Second ribbed end wall; 3. Wave-shaped ribs. DETAILED DESCRIPTION
[0019] The following will be combined with the drawings in the embodiments of the present application to clearly and completely describe the technical solutions in the embodiments of the present application. Obviously, the described embodiments are only part of the embodiments of the present application, not all of the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present application and its application or use. Example
[0020] A wave-shaped structure for heat dissipation in high-speed fan ducts, such as Figure 1~Figure 5As shown, it comprises a first ribbed end wall 1, a second ribbed end wall 2 and a corrugated rib 3, the first ribbed end wall 1 and the second ribbed end wall 2 are symmetrically arranged, the first ribbed end wall 1 and the second ribbed end wall 2 are at the same flow direction position, the ribbed end wall is bionic corrugated, the corrugated ribs 3 are evenly installed on the symmetric surfaces of the two ribbed end walls, and the cooling structure with corrugated ribs 3 is arranged on the upper and lower surfaces of the cooling channel inside the motor radiator, and the ribbed end wall surface is designed as a bionic corrugated wall surface to further enhance the heat exchange effect. Compared with a simple ribbed channel The design of the bionic wavy end wall can improve the flow and heat transfer characteristics of certain areas in the original wavy rib 3 channel by changing the position of the protrusions. The design of the bionic wavy end wall also improves the disturbance effect on the cold air, significantly promotes the mass exchange between the cold air and the mainstream in the ribless area close to the side wall of the channel, and significantly improves the heat transfer performance of the ribbed wall. At the same time, the comprehensive heat transfer performance of the channel is also improved. The design of the bionic wavy end wall can adjust the position of different wave protrusions and the degree of fluctuation according to the different arrangements of the spoiler rib structures to enhance the heat transfer uniformity of the channel.
[0021] The wavy ribs 3 include two types: discontinuous ribs and continuous ribs. For different rib structures, the bionic wall surface has different effects on improving the heat exchange performance of the channel.
[0022] The rib thickness of the wavy rib 3 is e, the rib height is 2*e, the crest position of the bionic wavy end wall coincides with the crest or trough of the wavy rib 3, and the fluctuation amplitude of the wavy rib 3 is 25%-30% of the channel width, ensuring the heat dissipation effect of the entire structure.
[0023] like Figure 1 to Figure 7 As shown in the figure, when the convex position of the first ribbed end wall 1 and the second ribbed end wall 2 along the flow direction coincides with the windward area of the corrugated rib 3, the dimensionless Nusselt number of the first ribbed end wall 1 and the second ribbed end wall 2 increases linearly with the increase of the convexity, indicating that under the coupling effect of the corrugated end wall surface at this position, the double-interrupted S-ribs can obtain better heat exchange performance, but the corresponding pressure loss also increases significantly. When the convex position of the corrugated end wall surface along the flow direction coincides with the leeward area of the corrugated rib 3, the overall dimensionless Nusselt number of the first ribbed end wall 1 and the second ribbed end wall 2 remains basically unchanged. However, due to the change in channel shape, the near-wall flow path has obvious changes, but the total channel pressure loss can maintain the same level. In order to comprehensively compare the heat transfer performance of several different staggered concave-convex ribbed wall structures based on bionic wave-shaped topology, when the bulges of the bionic wave-shaped first ribbed end wall 1 and the second ribbed end wall 2 coincide with the windward area of the double intermittent wave-shaped ribs 3 along the flow direction, the channel obtains the best heat transfer performance; when the bulges of the bionic wave-shaped first ribbed end wall 1 and the second ribbed end wall 2 coincide with the leeward area of the continuous wave-shaped ribs 3 along the flow direction, the channel obtains the best comprehensive thermal performance.
[0024] Overall dimensionless Nusselt number Comprehensive heat transfer performance index Displaced convex_continuous rib 1.976 0.235 Displacement concave_continuous rib 1.818 0.269 Dislocation convex_interrupted rib 2.236 0.263 Dislocation concave_interrupted rib 1.773 0.264 The comprehensive heat transfer performance indicators of the first ribbed end wall 1 and the second ribbed end wall 2 are defined as follows:
[0025] In the formula , , is the density of cold air, is the cooling speed, is the static pressure difference of cold air at the inlet and outlet of the channel fluid domain, is the dimensionless Nusselt number.
[0026] The dimensionless Nusselt number of the first ribbed end wall 1 and the second ribbed end wall 2 increases linearly with the increase of the protrusion, and the dimensionless Nusselt number is defined as follows:
[0027] In the formula, h is the heat transfer coefficient, D is the characteristic length, is the thermal conductivity, Re is the inlet Reynolds number, Pr is the Prandtl number. Example
[0028] Based on the first embodiment, an implementation method of a wavy structure for heat dissipation in a high-speed fan duct is provided: The first ribbed end wall 1 and the second ribbed end wall 2 have the same number of periods of the undulating and corrugated ribs 3, both showing 10 periods.
[0029] Different from the first embodiment, the geometric parameters in a single cycle remain the same, ensuring that the first ribbed end wall 1 and the second ribbed end wall 2 can be installed correspondingly, thereby improving the heat dissipation effect.
[0030] In the description of the present application, it should be understood that the terms "center", "longitudinal", "lateral", "up", "down", "front", "back", "left", "right", "inside", "outside", etc., indicating the orientation or position relationship, are based on the orientation or position relationship shown in the drawings, and are only used to explain the relative position relationship, movement, etc. between the components in a certain posture. If the specific posture changes, the directional indication will also change accordingly. It is only for the convenience of describing the present application and simplifying the description, and does not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation to the present application.
[0031] In the description of this application, it should be noted that, unless otherwise clearly specified and limited, the terms "installed", "connected", and "connected" should be understood in a broad sense, for example, it can be a fixed connection, a detachable connection, or an integral connection; it can be a mechanical connection or an electrical connection; it can be a direct connection, or it can be indirectly connected through an intermediate medium, or it can be the internal communication of two components. For ordinary technicians in this field, the specific meanings of the above terms in this application can be understood by specific circumstances.
[0032] The above is only a preferred implementation of the present application. It should be pointed out that for ordinary technicians in this technical field, several improvements and modifications can be made without departing from the technical principles of the present application. These improvements and modifications should also be regarded as the scope of protection of the present application.
Claims
1. A wavy structure for heat dissipation in a high-speed fan duct, characterized in that: The invention comprises a first ribbed end wall (1), a second ribbed end wall (2) and a wavy rib (3); the first ribbed end wall (1) and the second ribbed end wall (2) are symmetrically arranged; the wave crest of the first ribbed end wall (1) and the wave trough of the second ribbed end wall (2) are at the same flow direction position; the first ribbed end wall (1) and the second ribbed end wall (2) are bionic wavy; and the wavy rib (3) is evenly installed on the symmetrical planes of the first ribbed end wall (1) and the second ribbed end wall (2).
2. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The wavy ribs (3) include two forms: discontinuous ribs and continuous ribs.
3. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The first ribbed end wall (1) and the second ribbed end wall (2) have the same number of periods of the undulation and wave-shaped ribs (3).
4. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The rib thickness of the corrugated rib (3) is e, and the rib height is 2*e.
5. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The wave crest positions of the first ribbed end wall (1) and the second ribbed end wall (2) coincide with the wave crests or wave troughs of the wavy ribs (3).
6. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The wavy rib (3) has a fluctuation amplitude of 25%-30% of the channel width.
7. The wavy structure for heat dissipation in a high-speed fan duct according to claim 1, characterized in that: The index of the comprehensive heat exchange performance of the first ribbed end wall (1) and the second ribbed end wall (2) is defined as follows: TP=(N / N0) / (f / f0) 1 / 3 Where f0 = 0.507Re -0.3 f=Δp / (0.5ρU 2 ), ρ is the cold gas density, U is the cold gas velocity, Δp is the cold gas static pressure difference between the inlet and outlet of the channel fluid domain, and (Nu / Nu0) is the dimensionless Nusselt number.
8. The wavy structure for heat dissipation in a high-speed fan duct according to claim 7, characterized in that: The dimensionless Nusselt number of the first ribbed end wall (1) and the second ribbed end wall (2) increases linearly with the increase of the protrusion, and the dimensionless Nusselt number is defined as follows: Nu / Nu0=(hD / λ) / 0.023Re 0.8 Pr 0.4 Where h is the heat transfer coefficient, D is the characteristic length, λ is the thermal conductivity, Re is the inlet Reynolds number, and Pr is the Prandtl number.